US20040024504A1 - System and method for operating a rollover control system during an elevated condition - Google Patents

Abstract

A method of controlling a safety system38of a vehicle10include determining a roll rate, determining a first control pressure in response to roll rate, determining a roll angle, and determining a second control pressure in response to the roll angle. The method further includes determining a final control pressure in response to the first control pressure and the second control pressure and controlling the safety system in response to the final control pressure.

Description

RELATED APPLICATIONS
• The present invention claims priority to U.S.[0001]provisional applications 60/401,416 and 60/401,464 filed Aug. 5, 2002, and is related to U.S. patent applications entitled “SYSTEM AND METHOD FOR DETERMINING AN AMOUNT OF CONTROL FOR OPERATING A ROLLOVER CONTROL SYSTEM” (Attorney Docket No. 202-1221/FGT-1691) and “SYSTEM AND METHOD FOR OPERATING A ROLLOVER CONTROL SYSTEM IN A TRANSITION TO A ROLLOVER CONDITION” (Attorney Docket No. 203-0816/FGT-1869), the disclosures of which are incorporated by reference herein.
TECHNICAL FIELD
• The present invention relates generally to a control apparatus for controlling a system of an automotive vehicle in response to sensed dynamic behavior, and more specifically, to a method and apparatus for adjusting the activation based on heightened vehicle operating conditions.[0002]
BACKGROUND
• Dynamic control systems for automotive vehicles have recently begun to be offered on various products. Dynamic control systems typically control the yaw of the vehicle by controlling the braking effort at the various wheels of the vehicle. Yaw control systems typically compare the desired direction of the vehicle based upon the steering wheel angle and the direction of travel. By regulating the amount of braking at each corner of the vehicle, the desired direction of travel may be maintained. Typically, the dynamic control systems do not address rollover (wheels lifting) of the vehicle. For high profile vehicles in particular, it would be desirable to control the rollover characteristic of the vehicle to maintain the vehicle position with respect to the road. That is, it is desirable to maintain contact of each of the four tires of the vehicle on the road.[0003]
• In vehicle rollover control, it is desired to alter the vehicle attitude such that its motion along the roll direction is prevented from achieving a predetermined limit (rollover limit) with the aid of the actuation from the available active systems such as controllable brake system, steering system and suspension system. Although the vehicle attitude is well defined, direct measurement is usually impossible.[0004]
• During a potential vehicular rollover event, wheels on one side of the vehicle start lifting, and the roll center of the vehicle shifts to the contact patch of the remaining tires. This shifted roll center increases the roll moment of inertia of the vehicle, and hence reduces the roll acceleration of the vehicle. However, the roll attitude could still increase rapidly. The corresponding roll motion when the vehicle starts side lifting deviates from the roll motion during normal driving conditions.[0005]
• When the wheels start to lift from the pavement, it is desirable to confirm this condition. This allows the system to make an accurate determination as to the appropriate correction. If wheels are on the ground, or recontact the ground after a lift condition, this also assists with accurate control.[0006]
• Some systems use position sensors to measure the relative distance between the vehicle body and the vehicle suspension. One drawback to such systems is that the distance from the body to the road must be inferred. This also increases the number of sensors on the vehicle. Other techniques use sensor signals to indirectly detect wheel lifting qualitatively.[0007]
• One example of a wheel lifting determination can be found in Ford patent U.S. Pat. No. 6,356,188 and U.S. patent application (Attorney Docket 202-0433/FGT-[0008]1683 PA), the disclosures of which are incorporated by reference herein. The system applies a change in torque to the wheels to determine wheel lift. The output from such a wheel lifting determination unit can be used qualitatively. This method is an active determination since the basis of the system relies on changing the torque of the wheels by the application of brakes or the like. In some situations it may be desirable to determine wheel lift without changing the torque of a wheel.
• Due to the inevitable dead spots due to the vehicle configuration, wheel lift detection methods may be not able to identify all the conditions where four wheels are absolutely grounded in a timely and accurate fashion. For example, if the torques applied to the wheels have errors, if the vehicle reference computation has errors or there is not enough excitation in the torque provided, the wheel lift detection may provide erroneous information or no information about the roll trending of the vehicle. Wheel lift information may also be safe-guarded by information regarding the vehicle roll angle information from the various sensors.[0009]
• In certain driving conditions where the vehicle is moving with all four wheels contacting ground and the wheel lift detection does not detect the grounding condition, the roll information derived from the various sensors may be the sole information for identify vehicle roll trending. If in such driving cases, the vehicle experiences very large lateral acceleration and large roll rate, the grounded conditions might be replaced by erroneous lifting conditions. That is, those signals may predict that the vehicle is in a divergent roll event but the actual vehicle is not in a rolling event at all. Such cases include when the vehicle is driven on a mountain road, off-road or banked road, tire compression or an impact may cause a large normal load. The increased normal load causes a force component to be added to the lateral acceleration sensor output. Hence, a larger than 1 g lateral acceleration is obtained but the actual lateral acceleration of the vehicle projected along the road surface might be in 0.6 g range. An off-road driving condition may also be an off-camber driving condition. When a low speed vehicle is driven on an off-camber road with some hard tire compression or impact, the control system may be fooled to activate un-necessarily.[0010]
• In order to reduce false activations, it would therefore be desirable to provide a rollover detection system that sensitizes and desensitizes the roll control determination.[0011]
SUMMARY
• The present invention improves the operation of a rollover stability control system (RSC) by controlling the safety device to provide improved performance. One way in which the improvement may be implemented is by controlling or improving the brake pressure prediction to improve the feel and performance time of the system.[0012]
• In one embodiment, a method of controlling a safety system of a vehicle include determining a roll rate, determining a first control pressure in response to roll rate, determining a roll angle, and determining a second control pressure in response to the roll angle. The method further includes determining a final control pressure in response to the first control pressure and the second control pressure and controlling the safety system in response to the final control pressure.[0013]
• One advantage of the invention is that some or all of the ways in which to improve the system set forth herein may be used alone or simultaneously to improve the rollover control system.[0014]
• Other advantages and features of the present invention will become apparent when viewed in light of the detailed description of the preferred embodiment when taken in conjunction with the attached drawings and appended claims.[0015]
BRIEF DESCRIPTION OF THE DRAWINGS
• FIG. 1 is a diagrammatic view of a vehicle with variable vectors and coordinator frames.[0016]
• FIG. 2 is an end view of an automotive vehicle on a bank with definitions of various angles including global roll angle, relative roll angle, wheel departure angle (WDA), road bank angle and body-to-road angle.[0017]
• FIG. 3A is an end view of an on-camber divergent vehicle tendency.[0018]
• FIG. 3B is an end view of an automotive vehicle in an off-camber divergent condition.[0019]
• FIG. 3C is an end view of a vehicle in an on-camber convergent condition.[0020]
• FIG. 3D is an end view of a vehicle in an off-camber convergent condition.[0021]
• FIG. 4A is a block diagram of a stability control system.[0022]
• FIG. 4B is a block diagram of the[0023]controller26 used in the stability control system depicted in FIG. 4A.
• FIG. 5 is a block diagrammatic view of the unit[0024]27 depicted in FIG. 4B, which is used for quantitatively and qualitatively determining rollover trend of a vehicle.
• FIG. 6 is a detailed block diagram of a transition controller of the present embodiment.[0025]
• FIG. 7 is flow chart of the operation of one embodiment of the transition controller.[0026]
• FIG. 8 is a detailed block diagram of a PID controller of the present embodiment.[0027]
• FIG. 9 is flow chart of the operation of one embodiment of the PID controller.[0028]
• FIG. 10 is plot of a proportional peak hold strategy.[0029]
DETAILED DESCRIPTION
• In the following figures the same reference numerals will be used to identify the same components. The present teachings may be used in conjunction with a yaw control system or a rollover control system for an automotive vehicle. However, the present teachings may also be used with a deployment device such as airbag or roll bar.[0030]
• Referring to FIG. 1, an[0031]automotive vehicle10 on a road surface11 with a safety system is illustrated with the various forces and moments thereon.Vehicle10 has front right and front lefttires12aand12band rear right tires and rearleft tires13aand13b, respectively. Thevehicle10 may also have a number of different types offront steering systems14aandrear steering systems14bincluding having each of the front and rear wheels configured with a respective controllable actuator, the front and rear wheels having a conventional type system in which both of the front wheels are controlled together and both of the rear wheels are controlled together, a system having conventional front steering and independently controllable rear steering for each of the wheels, or vice versa. Generally, the vehicle has a weight represented as Mg at the center of gravity of the vehicle, where g=9.8 m/s²and M is the total mass of the vehicle.
• As mentioned above, the system may also be used with active/semi-active suspension systems, anti-roll bar or other safety devices deployed or activated upon sensing predetermined dynamic conditions of the vehicle.[0032]
• The[0033]sensing system16 is part of acontrol system18. Thesensing system16 may use a standard yaw stability control sensor set (including lateral acceleration sensor, yaw rate sensor, steering angle sensor and wheel speed sensor) together with a roll rate sensor and a longitudinal acceleration sensor. The various sensors will be further described below. Thewheel speed sensors20 are mounted at each corner of the vehicle, and the rest of the sensors ofsensing system16 may be mounted directly on the center of gravity of the vehicle body, along the directions x,y and z shown in FIG. 1. As those skilled in the art will recognize, the frame from b₁, b₂and b₃is called abody frame22, whose origin is located at the center of gravity of the car body, with the b₁corresponding to the x axis pointing forward, b₂corresponding to the y axis pointing off the driving side (to the left), and the b₃corresponding to the z axis pointing upward. The angular rates of the car body are denoted about their respective axes as ω_xfor the roll rate, ω_yfor the pitch rate and ω_zfor the yaw rate. The calculations set forth herein may take place in aninertial frame24 that may be derived from thebody frame22 as described below.
• The angular rate sensors and the acceleration sensors are mounted on the vehicle car body along the body frame directions b[0034]₁, b₂and b₃, which are the x-y-z axes of the vehicle's sprung mass.
• The[0035]longitudinal acceleration sensor36 is mounted on the car body located at the center of gravity, with its sensing direction along b₁-axis, whose output is denoted as a_x. Thelateral acceleration sensor32 is mounted on the car body located at the center of gravity, with its sensing direction along b₂axis, whose output is denoted as a_y.
• The other frame used in the following discussion includes the road frame, as depicted in FIG. 1. The road frame system r[0036]₁r₂r₃is fixed on the driven road surface, where the r₃axis is along the average road normal direction computed from the normal directions of the four-tire/road contact patches.
• In the following discussion, the Euler angles of the body frame b[0037]₁b₂b₃with respect to the road frame r₁r₂r₃are denoted as θ_xr, θ_yrand θ_zr, which are also called the relative Euler angles.
• Referring now to FIG. 2, the relationship of the various angles of the[0038]vehicle10 relative to the road surface11 is illustrated. One angle is a wheel departure angle θ_wda, which is the angle from the axle or the wheel axis to the road surface11. Also shown is a reference road bank angle θ_bank, which is shown relative to thevehicle10 on a road surface. Thevehicle10 has avehicle body10aand vehicle suspension10b. The relative roll angle θ_xris the angle between the wheel axle and thebody10a. The global roll angle θ_xis the angle between the horizontal plane (e.g., at sea level) and thevehicle body10a.
• Referring now to FIG. 3A,[0039]vehicle10 is illustrated in an on-camber divergent state. The on-camber divergent state refers to the vehicle having a greater than zero wheel departure angle, a greater than zero relative roll angle, and a moment represented byarrow25 tending to increase the relative roll angle and the wheel departure angle. In this example, the bank angle is less than zero.
• In FIG. 3B, when the bank angle is greater than zero, the wheel departure angle is greater than zero, the relative roll angle is greater than zero and the moment is also to the right or increasing the relative roll angle and the wheel departure angle, the vehicle is in an off-camber divergent state.[0040]
• Referring now to FIG. 3C, a bank angle of less than zero, a wheel departure angle greater than zero, and a relative roll angle greater than zero is shown with a[0041]roll moment25 acting to the left. Thus, the vehicle is in an on-camber convergent state. That is, the convergent state refers to the vehicle tending towards not overturning.
• Referring now to FIG. 3D, when the bank angle is greater than 0, the wheel departure angle is greater than zero, and the relative roll angle is greater than zero and the roll moment is tending to the left, the vehicle is in an off-camber convergent state. That is, the vehicle is tending toward not rolling over.[0042]
• Referring now to FIG. 4A, one embodiment of a roll[0043]stability control system18 is illustrated in further detail having acontroller26 used for receiving information from a number of sensors which may include ayaw rate sensor28, aspeed sensor20, alateral acceleration sensor32, aroll rate sensor34, a steering angle sensor (hand wheel position)35, alongitudinal acceleration sensor36, and steeringangle position sensor37.
• In one embodiment, the sensors are located at the center of gravity of the vehicle. Those skilled in the art will recognize that the sensors may also be located off the center of gravity and translated equivalently thereto.[0044]
• Lateral acceleration, roll orientation and speed may be obtained using a global positioning system (GPS). Based upon inputs from the sensors,[0045]controller26 may control asafety device38. Depending on the desired sensitivity of the system and various other factors, not all thesensors20,28,32,34,35,36, and37, or various combinations of the sensors, may be used in a commercial embodiment.Safety device38 may control anairbag40, an active braking system41, an active front steering system42, an active rear steering system43, anactive suspension system44, and an activeanti-roll bar system45, or combinations thereof. Each of the systems40-45 may have their own controllers for activating each one. As mentioned above, thesafety system38 may be at least the active braking system41.
• [0046]Roll rate sensor34 may sense the roll condition of the vehicle based on sensing the height of one or more points on the vehicle relative to the road surface. Sensors that may be used to achieve this include a radar-based proximity sensor, a laser-based proximity sensor and a sonar-based proximity sensor.
• [0047]Roll rate sensor34 may also sense the roll condition based on sensing the linear or rotational relative displacement or displacement velocity of one or more of the suspension chassis components which may include a linear height or travel sensor, a rotary height or travel sensor, a wheel speed sensor used to look for a change in velocity, a steering wheel position sensor, a steering wheel velocity sensor and a driver heading command input from an electronic component that may include steer by wire using a hand wheel or joy stick.
• The roll condition may also be sensed by sensing the force or torque associated with the loading condition of one or more suspension or chassis components including a pressure transducer in active air suspension, a shock absorber sensor such as a load cell, a strain gauge, the steering system absolute or relative motor load, the steering system pressure of the hydraulic lines, a tire lateral force sensor or sensors, a longitudinal tire force sensor, a vertical tire force sensor or a tire sidewall torsion sensor.[0048]
• The roll condition of the vehicle may also be established by one or more of the following translational or rotational positions, velocities or accelerations of the vehicle including a roll gyro, the[0049]roll rate sensor34, theyaw rate sensor28, thelateral acceleration sensor32, a vertical acceleration sensor, a vehicle longitudinal acceleration sensor, lateral or vertical speed sensor including a wheel-based speed sensor, a radar-based speed sensor, a sonar-based speed sensor, a laser-based speed sensor or an optical-based speed sensor.
• Based on the inputs from[0050]sensors20,28,32,34,35,36,37,controller26 determines a roll condition and controls any one or more of the safety devices40-45.
• [0051]Speed sensor20 may be one of a variety of speed sensors known to those skilled in the art. For example, asuitable speed sensor20 may include a sensor at every wheel that is averaged bycontroller26. Thecontroller26 translates the wheel speeds into the speed of the vehicle. Yaw rate, steering angle, wheel speed and possibly a slip angle estimate at each wheel may be translated back to the speed of the vehicle at the center of gravity. Various other algorithms are known to those skilled in the art. For example, if speed is determined while speeding up or braking around a corner, the lowest or highest wheel speed may not be used because of its error. Also, a transmission sensor may be used to determine vehicle speed.
• Referring now to FIGS. 4A and 4B,[0052]controller26 is illustrated in further detail. There are two major functions in controller26: the rollover trend determination, which is called asensor fusion unit27A, and the feedbackcontrol command unit27B. Thesensor fusion unit27A can be further decomposed as awheel lift detector50, atransition detector52 and a vehicleroll angle calculator66.
• Referring now to FIG. 5, the[0053]sensor fusion unit27A is illustrated in further detail. Thesensor fusion unit27A receives the various sensor signals,20,28,32,34,35,36,37 and integrates all the sensor signals with the calculated signals to generate signals suitable for roll stability control algorithms. From the various sensor signals wheel lift detection may be determined by thewheel lift detector50.Wheel lift detector50 includes both active wheel lift detection and active wheel lift detection, and wheel grounding condition detection. Wheel lift detector is described in co-pending U.S. provisional application serial No. 60/400,375 (Attorney Docket 202-0433/FGT-1683PRV) filed Aug. 1, 2002, and U.S. patent application (Attorney Docket 202-0433/FGT-1683PA) which are incorporated by reference herein. The modules described below may be implemented in hardware or software in a general purpose computer (microprocessor). From the wheellift detection module50, a determination of whether each wheel is absolutely grounded, possibly grounded, possibly lifted, or absolutely lifted may be determined.Transition detection module52 is used to detect whether the vehicle is experiencing aggressive maneuver due to sudden steering wheel inputs from the driver. The sensors may also be used to determine a relative roll angle in relativeroll angle module54. Relative roll angle may be determined in many ways. One way is to use theroll acceleration module58 in conjunction with the lateral acceleration sensor. As described above, the relative roll angle may be determined from the roll conditions described above.
• The various sensor signals may also be used to determine a relative pitch angle in relative[0054]pitch angle module56 and a roll acceleration inroll acceleration module58. The outputs of the wheellift detection module50, thetransition detection module52, and the relativeroll angle module54 are used to determine a wheel departure angle in wheeldeparture angle module60. Various sensor signals and the relative pitch angle in relativepitch angle module56 are used to determine a relative velocity total inmodule62. The road referencebank angle block64 determines the bank angle. The relative pitch angle, the roll acceleration, and various other sensor signals as described below are used to determine the road reference bank angle. Other inputs may include a roll stability control event (RSC) and/or the presence of a recent yaw stability control event, and the wheel lifting and/or grounding flags.
• The global roll angle of the vehicle is determined in global[0055]roll angle module66. The relative roll angle, the wheel departure angle, and the roll velocity total blocks are all inputs to the global roll angletotal module66. The global roll angle total block determines the global roll angle θ_x. Anoutput module68 receives the global roll angletotal module66 and the road reference bank angle from the road referencebank angle module64. A roll signal for control is developed inroll signal module70. The roll signal for control is illustrated asarrow72. A sensitizing and desensitizingmodule74 may also be included in theoutput module68 to adjust the roll signal for control.
• In the reference road[0056]bank angle module64, the reference bank angle estimate is calculated. The objective of the reference bank estimate is to track a robust but rough indication of the road bank angle experienced during driving in both stable and highly dynamic situations, and which is in favor for roll stability control. That is, this reference bank angle is adjusted based on the vehicle driving condition and the vehicle roll condition. Most importantly, when compared to the global roll estimate, it is intended to capture the occurrence and physical magnitude of a divergent roll condition (two wheel lift) should it occur. This signal is intended to be used as a comparator against the global roll estimate for calculating the error signal which is fed back to rollstability controller26.
• In parallel with the above a[0057]transition controller76 may implemented as will be further described below. The roll signal forcontrol72 may be used as an input to a proportional-integral-derivative controller78. The terminology for thePID controller78 refers to its functions. However, the function of double derivative may be added and a function such as integral may be used. For clarity the PID controller will be used for the controller even if all of the function proportional, integral or derivative functions are not used or if the double derivative is used. In parallel to the process above, a transitional controller may also be used. Thetransitional controller78. One embodiment for example includes just the proportional and derivative functions.
• The outputs of[0058]controller76 and thecontroller78 are provided to an arbitration module80, which ultimately controls the safety system. In the present example, the safety system is a hydraulic safety system such as a rollover control system using brakes. The arbitration module80 may, for example, simply choose the highest brake pressure requested from the transition controller and the PID controller. Of course, a weighting may also be performed.
• Referring now to FIG. 6, the operation of the[0059]transition controller76 is described in further detail. In this module, RSC control for the transitional portion of a dynamic maneuver is performed. The transitional portion is the region in which the outputs of the sensors are sill linear. That is, none are saturated. As briefly described below, the transition controller may perform all or some of the following.
• Caliper pre-charge functionality. During control interventions requiring maximum pressure build rates, significant delays in pressure builds occur due to the relatively large volume of fluid required to establish caliper pressure in the lower pressure range. The higher volume consumption is due to the air gap between the rotor and linings, as well as the high effective compliance of the brake system at low pressures. The[0060]transition controller76 includes pre-charging functionality to mitigate initial delays in establishing caliper pressure by applying low levels of pressure when steering activity suggests an RSC event is eminent.
• Yaw Damping. The under-damped nature of the yaw dynamics of the vehicle can result in yaw rate overshoot in transitional maneuvers. Excessive yaw rate overshoot in limit maneuvers results in excessive side slip angles which can result in lateral forces that significantly exceed the steady state cornering capacity of the vehicle and can significantly reduce the roll stability margin of the vehicle. As a preventative measure, yaw damping may be provided to minimize the occurrence of excessive lateral forces and vehicle side slip angles that might expose the vehicle to excessive lateral forces and tripping mechanisms. The phase of the brake interventions resulting from this module introduces significant yaw damping during aggressive maneuvers. A goal is to provide as much yaw damping as possible without inhibiting the responsiveness of the vehicle or becoming intrusive.[0061]
• Roll Damping. For sufficiently aggressive transitional maneuvers, the roll momentum can result in a lifting of the center of gravity of the vehicle at the end of the transition and may result in excessive wheel lift. It is an objective of this module to introduce effective roll damping before the occurrence of wheel lift by rounding off the build up lateral force when needed as they approach their peak levels in the final phase of the transition.[0062]
• Pressure Build Prediction. In addition to the caliper pre-charge functionality, pressure build prediction and actuator delay compensation have been introduced in this module. Limitations in pressure build rates are compensated for by projecting forward when a pre-determined pressure level is likely to be requested, based on the relative roll angle, roll rate, roll acceleration, and estimated caliper pressure. Pressure is built during the transition so that the desired peak pressure can be achieved when it is needed to reduce the effects of limited pressure build rates.[0063]
• Feed forward control. In this module, steering information, front side slip angle information and relative roll information is used to achieve a feed forward component of control from the point of view of the[0064]PID controller78. Feed forward information is used to build significant pressure where needed to reduce the demands on thePID controller78 for a given RSC event and to extend the functional envelop of the RSC system. For mild and moderate events, stability performance is achieved with lower levels of PID intervention. In conjunction with feed-forward control, PID control is able to handle more extreme maneuvers than would be possible without feed-forward control for two primary reasons. First, by the time thePID controller78 has requested intervention, the vehicle will be in a more stable condition due to the feed forward control. Second, when thePID controller78 does request pressure, significant pressure will already exist in the caliper, allowing the PID controller to achieve the required pressure much more quickly.
• Gradient Control. Proportional plus Derivative control is implemented for roll angle and front linear side slip angle in the[0065]PID controller78. For thePID controller78, relative roll is used for the proportional term, and roll velocity is used for the derivative term. Because relative roll is used, this controller is robust to integration errors that might occur in the total roll estimate. As a result, it is possible to make thetransition controller76 more sensitive than the PID controller without the adverse consequences of integrator drift in the state estimates.
• Establish initial conditions for[0066]PID controller78. Because this module is designed to lead the PID control intervention in a given maneuver, PID control can be initiated at significantly higher pressure, requiring less error to achieve the critical pressure required to stabilize the vehicle.
• Progressive Pressure Build. The[0067]transition controller76 builds and decreases pressure with a minimum amount of jerk. This supports smooth transparent interventions and reduces the potential for exciting pitch dynamics in the vehicle.
• Transparency. The[0068]transition controller76 may also builds pressure in parallel with the transition in lateral acceleration. Because the longitudinal acceleration is building at the same time as the reversal in lateral acceleration, the pitch motion is more in phase with the roll motion, resulting in a coherent body motion. Additionally, because the build up of longitudinal acceleration is much smaller than the change in lateral acceleration, the brake intervention becomes overshadowed by the lateral jerk.
• Referring now to FIG. 6, the[0069]transition controller76 includes the following inputs: a filtered steering angle rate (FILTERED_STEER_ANGLE_RATE)input90, a final wheel lift status (FINAL_WHEEL_LIFT_STATUS)92, a filtered lateral acceleration (FLT_LAT_ACC)input94, a filtered roll rate (FLT_ROLL_RATE)input96, a filtered yaw rate (FLT_YAW_RATE)signal98, a Get_aycreverse movement input100, aGet_rsc_disabled input102, a PID_INCREASE_REQUESTED_PRESSURE[FL]input104, a PID_INCREASE_REQUESTED_PRESSURE[FR]input106, a PID_STBLZ_PRES[FL]input108, a PID_STBLZ_PRES[FR] input110, a RECENT_LEFT_WHEEL_LIFT input112, aRECENT_PID_ACTIVATION input114, aRECENT_PID_CONTROL input116, aRECENT_RIGHT_WHEEL_LIFT input118, aREF_VELOCITY_YC input119, aREL_ROLL_ANGLE input120, aRSC_Disable_after_sensor_self_test input122, anRSC_DISABLED input124, aSLOW_FLT_YAW_ACC input126, aStatus_first_run input128, aSTEERING_WHEEL_ANGLE input130, aWDA_LIFT_SUSPECTED input132, Z1_REL_ROLL_ANGLE input134, ass_dpss_YAW_ACCELERATION2 input136, aAYC_SLIP_ANGLE_RATE_RA input138, aWHEEL_DEPARTURE_ANGLE input140, and a Predicted_AY_from_SWA input144.
• The[0070]transition controller78 has the following outputs FLPrechargeActive (flag)output150, a FLPrechargePress (bar)output152, a FRPrechargeActive (flag)output154, a FRPrechargePress (bar) output156, anINST_BANK_ANGLE_EST output158, a LEFT_TO_RIGHT_TRANSITION (flag)output160, and a RIGHT_TO_LEFT_TRANSITION (flag)output162.
• The[0071]transition controller78 also has predefined calibratable parameter that have the following definitions:

  	Scale_LNR_REAR_LATA_FILTER: In the present example
  	a value of 1024.0 unitless was used.
  	value_LNR_REAR_LATA_LOW_PASS_FILTER_FREQ: In the
  	present example a value of 10.0 Hz was used.
  	p_ALPHA_LNR_REAR_LATA_FILTER_COEFF: (LOOP_TIME*

  	value_LNR_REAR_LATA_LOW_PASS_FILTER_FREQ*
  	scale_LNR_REAR_LATA_FILTER )

  p_BETA_LNR_REAR_LATA_FILTER_COEFF:((1.0−(LOOP_TIME*

  	value_LNR_REAR_LATA_LOW_PASS_FILTER_FREQ))*
  	scale_LNR_REAR_LATA_FILTER)

• BASE_MATCHING_PRESSURE: In the present example a value of −177.0 bar was used. The matching pressure for the precharge prediction at a mu level of zero.[0072]
• MATCHING_PRESSURE_MU_GAIN: In the present example a value of 3000 bar/g was used. The gain with which the matching pressure is increased as mu is increased.[0073]
• EXPECTED_SWA_LEAD_TIME_MU_GAIN: The gain for determining how far in advance the predicted steering wheel angle sign crossing will cause a positive or negative SWA expected flag. In the following example, values 0.4-0.5 sec/g were used.[0074]
• SpeedDpndntAyChng (linear interpolation function of vehicle speed): The speed dependent threshold for determining if the driver is requesting a rapid change in lateral acceleration. The following table illustrates the numbers used in the present example.[0075]

  		SpeedDpndntAyChng
  	V(mps)	(mps2/sec)

  	0	33
  	17.9	33
  	22.4	30
  	26.79	25
  	31.3	16
  	83	11

• RECENT_RAPID_AY_TIME: In the present example a value of 150 loops was used. The time in loops for which the recent rapid ay flag is held high after the rate of change of the lateral acceleration requested by the driver exceeds the threshold.[0076]
• LARGE_ROUGH_MU: In the present example a value of 0.7 g's was used. Large rough mu threshold for determining significant dynamics.[0077]
• RECENT_LARGE_ROUGH_MU_TIME: In the present example a value of 150 loops was used. The time in loops for which the recent large rough mu flag is held high after the rough mu estimate exceeds a predetermined threshold.[0078]
• KP_REL_ROLL: In the present example a value of 8.0 bar/deg was used. Proportional pressure gain for relative roll feedback.[0079]
• KD_REL_ROLL: In the present example a value of 2.0 bar/deg/s was used. Derivative pressure gain for relative roll feedback.[0080]
• REL_ROLL_DB: In the present example a value of 5.4 deg was used. Deadband for proportional feedback on relative roll.[0081]
• REL_ROLL_PD_PRESS_FILT: In the present example a value of 1.0/5.0 unitless was used. Filter coefficient used in filtering the relative roll Proportional plus derivative feedback requested pressure.[0082]
• KP_SS_LIN_FRONT: In the present example a value of 10.0 bar/deg was used. Proportional pressure gain for front linear side slip angle feedback.[0083]
• KD_SS_LIN_FRONT: In the present example a value of 2.5 bar/deg/s was used. Derivative pressure gain for front linear side slip angle feedback.[0084]
• FT_CRNRG_CMPLNCE Front cornering compliance: In the present example, values between 6 and 8.18 deg/g were used.[0085]
• RR_CR NRG_CMPLNCE Rear cornering compliance: In the present example, values between 3 and 5 deg/g were used.[0086]
• SS_LIN_FRONT_DB: In the present example a value of 8.2 deg/g was used. Deadband for proportional feedback on front linear side slip angle feedback.[0087]
• SS_LIN_PD_PRESS_FILT: In the present example a value of 1.0/16.0 unitless was used. Filter coefficient used in filtering the front linear side slip angle proportional plus derivative feedback requested pressure.[0088]
• MAX_PRECHARGE_TIME: In the present example a value of 70 loops was used. Time in loops after which under certain conditions, the precharge pressure is forced down at the maximum rate.[0089]
• PRECHARGE_BUILD_TIME: In the present example a value of 20 loops was used. Time in loops before which under certain conditions, the precharge pressure is ramped down at the target build rate.[0090]
• TARGET_BUILD_RATE: In the present example a value of 100.0 bar/sec was used. The target build rate for the precharge strategy while in prediction mode.[0091]
• LARGE_DYNAMICS_BUILD_RATE: In the present example a value of 250.0 bar/sec was used. The pressure build rate for the precharge strategy when either the relative roll or front linear side slip angle PD pressures exceed the current precharge pressure on a given corner of the vehicle.[0092]
• VELOCITY_MIN[0093]_—10: In the present example a value of 10.0 mps was used. Minimum velocity below which the precharge strategy will not be enabled.
• ROUGH_MU_HOLD_TIME: In the present example a value of 150 counts was used. The time in loops for which the rough mu estimate will be held high after an increase in value.[0094]
• ROUGH_MU_RAMP_DOWN_RATE: In the present example a value of 0.2 g's/sec was used. The rate at which the rough mu estimate will be ramped down after the rough mu hold time is exceeded.[0095]
• BASE_PRESSURE_MU_GAIN: In the present example a value of 15.0 bar/g was used. The gain for determining the precharge pressure from rough mu, due to rapid steering input.[0096]
• RATE_LIMIT_dAY_FROM_SWA: In the present example, values between 70 mps2/s/s; and 140 mps2/s/s were used. The rate limit for the decrease in value of the rate limited signal representing the rate of change of lateral acceleration being requested by the driver.[0097]
• MIN_FL_REL_ROLL_PD_PRESS: In the present example a value of −320 bar was used. Lower bound for relative roll proportional/derivative pressure.[0098]
• MAX_FL_REL_ROLL_PD_PRESS: In the present example a value of −320 bar was used. Upper bound for relative roll proportional/derivative pressure.[0099]
• FAST_PRESS_REDUCTION_RATE: In the present example a value of 200 bar/s was used. The fast pressure reduction rate for the precharge strategy while in prediction mode.[0100]
• AVG_Steering_Ratio: In the present example a value of 16 deg/deg was used. The ratio of steering to wheel.[0101]
• Rel_Roll_Vel_FLT_Coeff: In the present example a value of (16) {fraction (1/16)}[0102]^thfilter coefficient was used in filtering relative roll velocity.
• MIN_REF_VELOCITY_YC: In the present example a value of 0.01 kph was used to prevent divide by 0 when the reference velocity is too small.[0103]
• lin_frnt_vel_filter_coeff: In the present example a value of (16.0) {fraction (1/16)}[0104]^thfilter coefficient was used in filtering linear front velocity.
• max_RoughMU: In the present example a value of 1.0 was used. Upper bound for Rough MU upper and lower[0105]
• min_RoughMU: In the present example a value of 0.1 was used. Lower bound for Rough MU upper and lower[0106]
• MAX_THRESHOLD_FOR_PREDICTED_POS_SWA: In the present example a value of −90 degrees was used. SWA threshold for predicting crossover to the left.[0107]
• MIN_THRESHOLD_FOR_PREDICTED_POS_SWA: In the present example a value of 90 degrees was used. SWA threshold for predicting crossover to the right.[0108]
• MIN_POS_SWA_THRESHOLD: In the present example a value of 0.1 degree was used. The SWA threshold for predicting crossover to the left.[0109]
• MAX_POS_SWA_THRESHOLD: In the present example a value of −0.1 degree was used. The SWA threshold for predicting crossover to the right.[0110]
• FRNT_SLIP_ANGLE_THRESHOLD_POS_SIG_DYN: In the present example a value of 0.4 Force threshold was used in setting Significant_Dynamics flag.[0111]
• VELOCITY_MIN_TO_EXIT[0112]_—7: In the present example a value of 7.0 m/s was used. Lower bound on longitudinal velocity for setting ENABLE_RSC_PRECHARGE flag.
• MIN_SLIP_ANGLE_FOR_PRCHG_ACT: In the present example a value of 0.1 degrees was used. Minimum slip angle for precharge_active flags.[0113]
• TRANSITION_AY_THRESHOLD: In the present example a value of 0.5 G's was used. Lateral acceleration threshold to initiate moderate ay counters.[0114]
• TRANSITION_HOLD_TIME: In the present example a value of 100 loops was used. Initial value for moderate ay counters.[0115]
• VHCL_MASS: In the present example a value of 3033.0 kg was used. Vehicle mass.[0116]
• CG_TO_RR_AXLE: In the present example a value of 1.471 m was used. Distance from vehicle center of gravity to rear axle.[0117]
• CG_TO_FRT_AXLE: In the present example a value of 1.546 m was used. Distance from vehicle center of gravity to front axle.[0118]
• AY_SNSR_TO_RR_AXLE: In the present example a value of −1.791 m was used. Distance from ay sensor to rear axle.[0119]
• WHEEL_BASE (CG_TO_FRT_AXLE+CG_TO_RR_AXLE)[0120]
• AY_TO_CG (CG_TO_RR_AXLE+AY_SNSR_TO_RR_AXLE)[0121]
• YAW_MMT_INERTIA: In the present example a value of 6303.5 kg-m/s{acute over ()}2 was used. Moment of inertia about the Z axis.[0122]
• G_TO_MPS2: In the present example a value of 9.81 m/s{acute over ()}2/G was used. Convert from G's to m/S{acute over ()}2.[0123]
• value_MAX_ANGLE (45.0 degrees): Upper limit for the estimate of the instantaneous bank angle[0124]
• MAX_ANGLE (value_MAX_ANGLE/deg_RES_ROLL_ANGLE)[0125]
• ss_RES_dAYFromSWA: In the present example a value of 0.004375 was used. Scaling for dAYFromSWA.[0126]
• MIN_dAY_FROM_SWA: In the present example a value of −100.00/ss_RES dAYFromSWA was used. Lower limit for dAYFromSWA.[0127]
• MAX_dAY_FROM SWA: In the present example a value of 100.00/ss_RES_dAYFromSWA was used. Upper limit for dAYFromSWA.[0128]
• LARGE_SWA_RATE_THRESH: In the present example a value of 700 deg/s was used. Threshold to reset recent large swa rate timers.[0129]
• RECENT_WHEEL_LIFT_TIME: In the present example a value of 1/looptime was used. Initial value for recent wheel lift timers.[0130]
• rpss_RES_YAW_ACC (dpss_RES_YAW_ACC *pc_DEG_TO_RAD): Scaling for yaw acceleration in radians.[0131]
• MIN_dAY_FROM_YAW_ACC: In the present example a value of −100.0/ss_RES_dAYFromSWA was used. Lower limit for ssDAyFromYawAcc.[0132]
• MAX_dAY_FROM_YAW_ACC: In the present example a value of 100.00/ss_RES_dAYFromSWA was used. Upper limit for ssDAyFromYawAcc.[0133]
• p_dpg_RR_CRNRG_CMPLNCE: In the present example a value of 4.68 deg/g U228 was used. Rear cornering compliance.[0134]
• dps_RES_BETA_PRIME(rps_RES_YAW_RATE*pc_RAD_TO_DEG): Scaling for ssDAyFromBetaPRA.[0135]
• MIN_dAY_FROM_BETAPRA: In the present example a value of −140.0/ss_RES dAYFromSWA was used. Lower limit for ssDAyFromBetaPRA.[0136]
• MAX_dAY_FROM_BETAPRA: In the present example a value of 140.0/ss_RES_dAYFromSWA was used. Upper limit for ssDAyFromBetaPRA.[0137]
• YawAcc2SWARate_x_tab: In the present example a value of {0, 30, 50, 70, 203} MPH was used. X interpolation table for ssYawAcc2SWARateFraction.[0138]
• YawAcc2SWARate_y_tab: In the present example a value of {0.66, 0.66, 0.60, 0.50, 0.50} fraction was used. Y interpolation table for ssYawAcc2SWARateFraction.[0139]
• YawAcc2SWARate_len: In the present example a value of 5 unitless was used. The number of entries in the interpolation tables for ssYawAcc2SWARateFraction.[0140]
• BetaDotRA2SWARate_x_tab: In the present example a value of {0, 30, 50, 203} MPH was used. X interpolation table for ssBetaDotRA2SWARateFraction.[0141]
• BetaDotRA2SWARate_y_tab: In the present example a value of {0.35, 0.35, 0.50, 0.50} fraction was used. Y interpolation table for ssBetaDotRA2SWARateFraction.[0142]
• BetaDotRA2SWARate_len: In the present example a value of 4 unitless was used. The number of entries in the interpolation tables for ssBetaDotRA2SWARateFraction.[0143]
• Build_rate_x_tab: In the present example a value of {0, 30, 50, max} mps2/sec was used. X lookup table for build rate.[0144]
• Build_rate_y_tab: In the present example a value of {[0145]100,100,250,250} bar/sec was used. Y lookup table for build rate.
• Build_rate_tab_len: In the present example a value of 4 unitless was used. Length of build rate lookup tables for interpolation.[0146]
• FRNT_SLIP_ANGLE_THRESHOLD_POS_SIG_DYN: In the present example a value of 0.4 G was used. Threshold for Front linear slip angle.[0147]
• MIN_MATCH_PRESS[0148]_—2_PD_PRESS_DELTA: In the present example a value of 1.0 bar was used. Lower limit on PDRelRollMatchPressDelta.
• MIN_INST_BUILD_RATE: In the present example a value of 100.0 bar was used. Minimum for InstRelRollBuildRate.[0149]
• MAX_INST_BUILD_RATE: In the present example a value of 300.0 bar was used. Maximum for InstRelRollBuildRate.[0150]
• TARGET_DUMP_RATE: In the present example a value of 150 bar/s was used. Rate for reducing pressure.[0151]
• UPPER_BOUND_ON_TIME_FOR_DETECTION: In the present example a value of 0.400 was used. Upper bound in time for increasing swa detection.[0152]
• YAW_RATE_PD_PRESS_FILT: In the present example a value of 1.0/16.0 was used. Corresponds to roughly 2 Hz cutoff.[0153]
• AY_FROM_SWA_THRESH_FOR_DIRECTION_CHANGE: In the present example a value of 0.5 g was used. Sign dependent threshold used in the first set of conditions that must exist to disable the yaw rate PD controller from increasing final requested pressure—when the magnitude of predicted lateral acceleration from steering wheel angle drops below this threshold.[0154]
• TIME_FOR_DETECTING_SWA_DIRECTION_CHANGE: In the present example a value of 0.020 sec was used. Minimum contiguous time used to indicate a steering wheel direction change—used as the second set of conditions to disable the yaw rate PD controller from increasing final requested pressure.[0155]
• SWA_VEL_FOR_DETECTING_SWA_DIRECTION_CHANGE: In the present example a value of 400 deg/s was used. Sign dependent steering velocity threshold which is multiplied by parameter TIME_FOR_DETECTING_SWA_DIRECTION_CHANGE to define the minimum change required in steering wheel angle magnitude, defining the third condition that must be met before disabling the yaw rate PD controller.[0156]
• Rsc_kp_yaw_rate Yaw Rate Controller Kp[0157]
• Rsc_kd_yaw_rate Yaw Rate Controller Kd[0158]
• Referring now to FIG. 7, a flowchart of one embodiment of the operation of the[0159]transition controller76 is illustrated. It should be noted that not all steps may be included in an actual embodiment. Further, the parameters and constants are set forth by way of example and are not meant to be limiting. Instep180, the various sensors described above are read. Instep182 various inputs from other sensors are obtained. These inputs correspond to inputs90-142 of FIG. 6. Instep184 the local variables described above are obtained. These local variables include the lateral force, slip angle and lateral velocity at the front axle. These are determined as follows:

  	FrontLatForce=((VHCL_MASS*CG_TO_RR_AXLE/WHEEL_BASE)
  	*FLT_LAT_ACC)

  +(SLOW_FLT_YAW_ACC*((VHCL_MASS*CG_TO_RR_AXLE

  	*AY_TO_CG)
  	+YAW_MMT_INERTIA)/(WHEEL_BASE);

  FrontLnrSlipAngle=−FrontLatForce*(FT_CRNRG_CMPLNCE

  	*WHEEL_BASE)/(VHCL_MASS*CG_TO_RR_AXLE*G_TO—
  	MPS2);

  CurrentFrontLnrLatVel=FrontLnrSlipAngle*REF—

  	VELOCITY_YC;

• Also the lateral force, slip angle and lateral velocity at the rear axle are determined as follows:[0160]

  	RearLatAcc=FLT_LAT_ACC+(SLOW_FLT_YAW_ACC*AY_SNSR_TO—

  RR AXLE);

  RearLatForce=(VHCL_MASS*(CG_TO_FRT_AXLE/WHEEL_BASE)

  	*FLT_LAT_ACC)+(SLOW_FLT_YAW_ACC*((VHCL_MASS*CG—
  	TO_FRT_AXLE*AY_TO_CG)−YAW_MMT_INERTIA)
  	/WHEEL_BASE;

  RearLnrSlipAngle=(−1) *RearLatForce* (RR_CRNRG—

  	CMPLNCE*WHEEL_BASE)/(VHCL_MASS*CG_TO_FRT_AXLE
  	*G_TO_MPS2);

  CurrentRearLnrLatVel=RearLnrSlipAngle*REF_VELOCITY—

  	YC;

• In[0161]step186 the component of the lateral acceleration at the rear axle due to the change in linear lateral velocity at the rear axle is calculated as follows:

  RearLnrLatAcc=(CurrentRearLnrLatVel-REAR_LNR—

  LAT_VEL)/LOOP_TIME;

  FltRearLnrLatA=ALPHA_LNR_REAR_LATA_FILTER_COEF

  	F*RearLnrLatAcc+BETA_LNR_REAR_LATA_FILTER—
  	COEFF*REAR_LNR_LAT_ACC;

• In step[0162]188 the instantaneous bank angle based on rear axle information is determined as follows:

  	SineOfInstBnkAngle=((RearLatAcc-FltRearLnrLatA)

  −(FLT_YAW_RATE*REF_VELOCITY_YC))*MPS2_TO_G;

  //Limit magnitude of Bank.Angle to 45 degrees if

  	(SineOfInstBnkAngle<=−SCALED_ASIN_INPUT_LIMIT)
  	INST_BANK_ANGLE_EST = −1.0 * MAX_ANGLE;

  else if(SineOfInstBnkAngle>=SCALED_ASIN_INPUT—

  LIMIT)INST_BANK_ANGLE_EST= MAX_ANGLE;

  	else INST_BANK_ANGLE_EST=COMPUTE_ARC_SINE_OF_INPUT
  	(SineOflnstBnkAngle);

• In step[0163]190 the rate of change of requested lateral acceleration based on steering velocity is determined. A product of the steering velocity multiplied by the steering gain of the vehicle is obtained, where the steering gain is defined as the ratio of the lateral acceleration to steering wheel angle in a steady state turn. This gain is expressed as a function of speed. The product is passed through a low pass filter to achieve the resultant rate of change of lateral acceleration being requested by the driver. This signal is used to help define the strength of the transition being requested by the driver. This determined in the flowing:

  	temp_For_SWA=REF_VELOCITY_YC*REF_VELOCITY_YC/

  (RAD_TO_DEG*WHEEL_BASE*G_TO_MPS2);

  K_SWA_TO_AY=temp_For_SWA*G_TO_MPS2/(1+temp_For_SWA

  *(FT_CRNRG_CMPLNCE-RR_CRNRG_CMPLNCE));

  dAYFromSWA=LIMIT(FILTERED_STEER_ANGLE_RATE*K_S

  	WA_TO_AY/AVG_Steering_Ratio, min_dAY_from_SWA,
  	max_dAY_from_SWA);

• In step[0164]192 a rate limited lateral acceleration from steering wheel angle dAYfromSWA is determined. The delay factor in the response of the power steering system may cause the system to have to catch-up to the pressure desired by the vehicle operator. For very aggressive steering inputs, power steering catch-up can cause a significant reduction in steering velocity for up to 200 ms. This can cause an interruption in pressure build when it is needed most. To prevent this, rate limited versions of dAYfromSWA are implemented for both the positive and negative directions. Each signal is allowed to increase in value as rapidly as the input signal. However, the decrease in value is rate limited by RATE_LIMIT_dAY_FROM_SWA. Both signals are limited to positive values and represent the magnitude of the rate of change in the positive and negative direction respectively. This is determined as follows:
• if(dAYFromSWA>POSRateLimiteddAYFromSWA)POSRate LimiteddAYFromSWA=dAYFromSWA;[0165]
• else[0166]

  	{
  	POSRateLimiteddAYFromSWA−=RATE_LIMIT_dAY—

  FROM_SWA*LOOPTIME;

  if(POSRateLimiteddAYFromSWA<dAYFromSWA)POSRate

  LimiteddAYFromSWA=dAYFromSWA;

  }

  POSRateLimiteddAYFromSWA=MAX(0,POSRateLimited

  dAYFromSWA);

  if(−

  dAYFromSWA>NEGRateLimiteddAYFromSWA)NEGRateLimited

  dAYFromSWA=−dAYFromSWA;

  else

  	{
  	NEGRateLimiteddAYFromSWA−=RATE_LIMIT_dAY—

  FROM_SWA*LOOPTIME;

  if(NEGRateLimiteddAYFromSWA<(−1*dAYFromSWA))

  NEGRateLimiteddAYFromSWA=−1*dAYFromSWA

  }

  NEGRateLimiteddAYFromSWA=MAX(0,NEGRateLimiteddAY

  	FromSWA);

• In step[0167]194 a change in lateral acceleration from yaw acceleration dAYfromYawAcc and a change in lateral acceleration from the rate of change of the side slip at the rear axle in dAyFromBetaPRA is determined. Each signal is allowed to increase in value as rapidly as the input signal. These signals are scaled to provide a similar profile to DAyFromSWA. Final max and min DAyDt's are calculated by comparing dAYfromYawAccScldToSWA, dAyFromBetaPRAScldToSWA, and dAYFromSWA. These DayDt's can be positive or negative. Max and min rate limited DayDt's are calculated by comparing dAYfromYawAccScldToSWA, dAyFromBetaPRAScldToSWA, and rate limited DAyFromSWA's. These rate limited DayDt's are always positive. They are calculated as follows:

  	ssDAyFromYawAcc=LIMIT((ss_dpss_YAW_ACCELERATION2

  	*ss_mps_REF_VELOCITY_YC/(ss_RES_dAYFromSWA/
  	(rpss_RES_YAW_ACC*mps_RES_REF_VELOCITY_YC))),
  	MIN_dAY_FROM_YAW_ACC, MAX_dAY_FROM_YAW_ACC);

  ssDAyFromBetaPRA =LIMIT ((AYC_SLIP_ANGLE_RATE_RA

  	*(1024.0)/ ((ss_RES_DayFromSWA*p_dpg_RR—
  	CRNRG_CMPLNCE*1024.0)/(dps_RES_BETA_PRIME
  	*pc_G_TO_MPS2))), MIN_dAY_FROM_BETAPRA,
  	MAX_dAY_FROM_BETAPRA);

  ssYawAcc2SWARateFraction=AYC_INTPOL2 (ss_mps_REF—

  	VELOCITY_YC, YawAcc2SWARate_x_tab,YawAcc2SWA
  	Rate_y_tab, YawAcc2SWARate_len);

  ssBetaDotRA2SWARateFraction=AYC_INTPOL2 (ss_mps_REF—

  	VELOCITY_YC, BetaDotRA2SWARate_x_tab,
  	BetaDotRA2SWARate_y_tab, BetaDotRA2SWARate
  	len);

  ssDAyFrmYwAccScldToSWA=ssDAyFromYawAcc*ssYawAcc2

  SWARateFraction/(1024.0);

  ssDAyFrmBetaPScldToSWA=ssDAyFromBetaPRA*ssBetaDot

  RA2SWARateFraction/(1024.0);

  ssFinalMaxDAyDt=max(dAYFromSWA, ssDAyFrmYwAccScld

  ToSWA);

  ssFinalMaxDAyDt=max(ssFinalMaxDAyDt, ssDAyFrmBeta

  PScldToSWA);

  ssFinalMaxRtLmtdDAyDt=max(POSRateLimiteddAYFromSWA,

  	ssDAyFrmYwAccScldToSWA); ssFinalMaxRtLmtdDAy
  	Dt=max(ssFinalMaxRtLmtdDAyDt,ssDAyFrmBetaPScld
  	ToSWA);

  ssFinalMinDAyDt=min(dAYFromSWA, ssDAyFrmYwAccScld

  ToSWA);

  ssFinalMinDAyDt=min(ssFinalMinDAyDt, ssDAyFrmBeta

  PScldToSWA);

  	/*Since NEGRateLimiteddAYFromSWA is limited to
  	positive values, use MAX of negated DAy's derived
  	from YawAcc and BetaP*/
  	ssFinalMinRtLmtdDAyDt=max(NEGRateLimiteddAYFromSWA,

  ((−1) *ssDAyFrmYwAccScldToSWA));

  ssFinalMinRtLmtdDAyDt=max(ssFinalMinRtLmtdDAyDt,

  	((−1) *ssDAyFrmBetaPScldToSWA));

• In step[0168]196 a rough estimate of the mu level of the road surface is determined. The primary objective is not precise estimation of the mu level (although one could be used), but an indication of the lateral forces expected to be experienced after the transition. The Rough MU estimate is allowed to increase with the magnitude of the lateral acceleration. The value is held high for the period ROUGH_MU_HOLD_TIME following any loop in which the Rough MU estimate is increased by the lateral acceleration. Then it is allowed to ramp down at a predefined ramp rate. The important property for this calculation is that it preserves for the duration of the event, the lateral forces experienced immediately before the transition. This information is then used as a predictor of what the forces are likely to be seen after the transition. This is in turn used to determine the pressure build profile during the transition. The Rough MU signals are bounded between 1.0 and 0.1.
• A Rough MU Upper is determined by:[0169]

  if(FLT_LAT_ACC > RoughMUUpper*G_TO_MPS2)

  	{
  	ROUGH_MU_UPPER_TIMER=0;
  	RoughMUUpper=FLT_LAT_ACC/G_TO_MPS2;
  	}

  else

  	{
  	if(ROUGH_MU_UPPER_TIMER<ROUGH_MU_HOLD_TIME)

  ROUGH_MU_UPPER_TIMER++;

  else ss_RoughMUUpper−=ROUGH_MU_RAMP_DOWN—

  RATE*LOOP_TIME);

  }

  if(RoughMUUpper>max_RoughMU)RoughMUUpper=max—

  RoughMU;

  if(RoughMUUpper<min_RoughMU)RoughMUUpper

  	=min_RoughMU;

• A Rough MU Lower is determined by:[0170]

  	if(−FLT_LAT_ACO>RoughMULower*G_TO_MPS2)

  	{
  	ROUGH_MU_LOWER_TIMER=0;
  	RoughMULower=−FLT_LAT_ACC/G_TO_MPS2;
  	}

  else

  	{
  	if(ROUGH_MU_LOWER_TIMER<ROUGH_MU_HOLD_TIME)

  ROUGH_MU_LOWER_TIMER++;

  	else ss_RoughMULower−=(ROUGH_MU_RAMP_DOWN—
  	RATE*LOOP_TIME);
  	}

  if(RoughMULower>max_RoughMU)RoughMULower=max_Rough

  MU;

  if(ss_RoughMULower<min_RoughMU)RoughMULower=min—

  	RoughMU;
  	A Final Rough MU is determined by:

  	RoughMU=max(RoughMUUpper,RoughMULower);

• In step[0171]198 a Matching Pressure is determined. The matching pressure is calculated based on the Rough MU level. Higher mu levels result in higher matching pressure. The matching pressure is used in the prediction strategy to compensate for the finite build rate available from the hydraulic system. The matching pressure is determined in the following:

  MatchingPressure=BASE_MATCHING_PRESSURE+RoughMU*

  MATCHING_PRESSURE_MU_GAIN;

  if (MatchingPressure<0.0)MatchingPressure=0.0;

• In step[0172]200 a predicted SWA sign change is determined. In this section two flags are calculated POS_SWA_EXPECTED and NEG_SWA_ESPECTED. POSSWA_EXPECTED is set to true if the steering wheel angle is positive in the current loop or expected to be positive within a certain period of time. This period of time or signal lead is mu dependent and is intended to allow more lead in building the caliper precharge pressure for higher mu estimates. It has been experimentally determined that has indicated that on high mu and for large steering rates, initiating the pressure build after the sign crossing of the steering wheel angle may not allow adequate pressure to be built during the transition to cancel the resulting dynamic oversteer. A similar calculation is performed for the negative direction. The prediction of sign change of SWA is determined by:

  	POS_SWA_EXPECTED=(RoughMU*FILTERED—
  	STEER_ANGLE_RATE

  	*EXPECTED_SWA_LEAD_TIME_MU_GAIN+
  	min(STEERING—
  	WHEEL_ANGLE, MAX_THRESHOLD_FOR—
  	PREDICTED_POS—
  	SWA)>MIN_POS_SWA_THRESHOLD)||
  	(STEERING_WHEEL—
  	ANGLE>MIN_POS_SWA_THRESHOLD);

  NEG_SWA_EXPECTED=(RoughMU*FILTERED—

  	STEER_ANGLE_RATE
  	*EXPECTED_SWA_LEAD_TIME_MU—
  	GAIN+max(STEERING—
  	WHEEL_ANGLE, MIN_THRESHOLD_FOR—
  	PREDICTED_POS—
  	SWA)<MAX_POS_SWA_THRESHOLD)||
  	(STEERING_WHEEL—
  	ANGLE<MAX_POS_SWA_THRESHOLD);

• In[0173]step202 the RSC Precharge Status flags are enabled. The enable flag is true in any loop for which the precharge pressure can be implemented. In the present example the vehicle should be above a minimum speed and the rollover stability control (RSC) system must not be disabled for the flag to be true, otherwise it will be forced to a false state. A recent PID event or a combination of sufficientlyhigh steering100 velocities and recent large lateral acceleration may also be required for the flag to be set true.
• Several steps are used in setting the flags. First, it is determined whether a rapid change in lateral acceleration has recently occurred. This is used as an indicator that a transitional maneuver is occurring. The code for such is:[0174]

  if(max(FinalMaxDAyDt,-FinalMinDAyDt)>SpeedDpndntAy

  	Chng)Recent_Rapid_AY_Counter=RECENT_RAPID_AY—
  	TIME;

  else if (Recent_Rapid_AY_Counter>0)Recent_Rapid_AY—

  Counter--;

  RECENT_RAPID_AY=Recent_Rapid_AY_Counter > 0;

• Next it is determined whether a large rough mu has recently been experienced. This flag is used to indicate that a near limit condition is or has recently occurred.[0175]
• RECENT_LARGE_ROUGH_MU=RoughMU>LARGE_ROUGH_MU;[0176]
• Then it is determined whether a moderate linear slip is or has recently occurred at the front axle as in:[0177]

  	if (ABS(FrontLnrSlipAngle)>((FRNT_SLIP_ANGLE—

  	THRESHOLD_POS_SIG_DYN*FT_CRNRG—
  	CMPLNCE)))
  	RECENT_MODERATE_FRONT_AXLE_LNR—
  	SLIP_COUNTER=
  	(RECENT_MODERATE_FRONT—
  	LINEAR_SLIP/LOOP_TIME);

  else

  if

  (

  	RECENT_MODERATE_FRONT_AXLE_LNR_SLIP—
  	COUNTER>0)

  	RECENT_MODERATE_FRONT_AXLE_LNR_SLIP—
  	COUNTER--;

• Then, it is determined whether a recent absolutely lifted has been determined for a wheel OR whether a recent pre lift has been sensed. This is set forth in code by:[0178]

  if (((FINAL_WHEEL_LIFT_STATUS[FL]
  ==ABSOLUTELY—

  	LIFTED)&&(FLT_LAT_ACC>S16_RND(0.85/g—
  	RES_LAT—
  	ACC)))||WDA_LIFT—
  	SUSPECTED[FL])

  {

  	RECENT_LEFT_WHEEL_LIFT_TIMER=
  	RECENT_WHEEL_LIFT—

  TIME;

  }

  else if (RECENT_LEFT_WHEEL_LIFT_TIMER)RECENT—

  LEFT—

  WHEEL_LIFT_TIMER--;

  if (RECENT_LEFT_WHEEL_LIFT_TIMER)RECENT_LEFT—

  WHEEL—

  LIFT=TRUE;

  else

  RECENT_LEFT_WHEEL_LIFT=FALSE;

  if

  (((FINAL_WHEEL_LIFT_STATUS[FR]==

  ABSOLUTELY_LIFTED)

  	&&(FLT_LAT_ACC<S16_RND((−0.85)/g—
  	RES_LAT—
  	ACC)))||WDA_LIFT_SUSPECTED[FR])

  {

  	RIGHT_WHEEL_LIFT_TIMER=RECENT—
  	WHEEL_LIFT—

  TIME;

  }

  else

  if

  (RECENT_RIGHT_WHEEL_LIFT_TIMER)RECENT—

  RIGHT_WHEEL—

  LIFT_TIMER--;

  if (RECENT_RIGHT_WHEEL_LIFT_TIMER)RECENT—

  RIGHT—

  WHEEL_LIFT=TRUE;

  else

  	RECENT_RIGHT_WHEEL_LIFT=FALSE;

• Another factor is if significant dynamics are present which might warrant a precharge intervention. The significant dynamics variable is an intermediate variable taking into consideration the above recent rapid lateral acceleration, large rough mu, linear slip, lift status, and prelift sensing. The code is implemented as:[0179]

  SIGNIFICANT_DYNAMICS=

  	(RECENT_PID_CTRL
  	||(RECENT_RAPID_AY&&RECENT_LARGE_ROUGH_MU)
  	||((max(FinalMaxDAyDt,-FinalMinDAyDt)>Speed

  	DpndntAyChng)&&(RECENT_MODERATE_FRONT—
  	AXLE_LNR_SLIP_COUNTER>0))

  	||(FL_Precharge_Press)
  	||(FR_Precharge_Press)
  	||RECENT_LEFT_WHEEL_LIFT
  	||RECENT_RIGHT_WHEEL_LIFT
  	||Predicted_AY_from_SWA>=1.4*g&&FrontLnrSlip

  	Angle<=−0.85*FT_CRNRG_CMPLNCE&&WHEEL
  	DEPARTURE_ANGLE>=0.1

  ||Predicted_AY_from_SWA<=−1.4*g&&FrontLnrSlip

  	Angle>=0.85*FT_CRNRG_CMPLNCE&&WHEEL—
  	DEPARTURE_ANGLE<=−0.1

• Then based on the significant dynamics variable, the precharge pressures and other variables by the following:[0180]

  if (SIGNIFICANT_DYNAMICS

  	&&(REF_VELOCITY_YC>VELOCITY_MIN_10
  	||((FL_Precharge_Press>0||FR_Precharge—

  Press>0)

  &&(REF_VELOCITY_YC>VELOCITY_MIN_TO_EXIT—

  7)))

  	&& !Get_rsc_disabled
  	&& !Get_ayc_reverse_movement
  	&& !Status_first_run
  	&& !RSC_Disable_after_sensor_self_test
  	)

  ENABLE_RSC_PRECHARGE=TRUE;

  else	ENABLE_RSC_PRECHARGE=FALSE;

• In[0181]step204 Precharge Timers are managed. Precharge timers are used to allow the precharge strategy to occur during or immediately after the transitional portion of an event. This serves as additional screening criteria to prevent unnecessary precharge interventions.
• If the rear linear slip angle is consistent with a left hand turn or the significant dynamics flag indicates there is no significant dynamic activity, the left timer is zeroed out. Otherwise it is incremented to the maximum precharge time. If the rear linear slip angle is consistent with a right hand turn or the significant dynamics flag indicates there is no significant dynamic activity, the right timer is zeroed out. Otherwise it is incremented to the maximum precharge time. This ensures that within a defined period of time, after a dynamic event, a precharge event will not be initiated, reducing the possibility of unnecessary intervention. This is set forth as:[0182]

  	If (RearLnrSlipAngle<=0

  	||!SIGNIFICANT_DYNAMICS
  	||RECENT_PID_ACTIVATION
  	||RECENT_RIGHT_WHEEL_LIFT)

  FL_Precharge_Timer=0;

  else if(FL_Precharge_Timer<MAX_PRECHARGE_TIME)

  FL_Precharge_Timer++;

  if(RearLnrSlipAngle>=0

  	||!SIGNIFICANT_DYNAMICS
  	||RECENT_PID_ACTIVATION
  	||RECENT_LEFT_WHEEL_LIFT)

  FR_Precharge_Timer=0;

  else if(FR_Precharge_Timer<MAX_PRECHARGE_TIME)

  	FR_Precharge_Timer++;

• In[0183]step206 individual caliper pre-charge status flags are determined. The status flags indicate whether the pre-charge function is active on a given wheel in a given loop. Pre-charge must be enabled in any loop for which the pre-charge strategy is active. If the precharge timer on a given wheel is below the maximum precharge time, the function can become activated on that wheel based on steering information or side slip angle information. Additionally, the precharge function will remain active on a specific wheel as long as there is a non-zero pressure being requested on that wheel.
• The continuous time of consistent sign for SSLIN Front or Rear is monitored.[0184]

  	if (FrontLnrSlipAngle>MIN_SLIP_ANGLE—
  	FOR_PRCHG_ACT

  	|| RearLnrSlipAngle>MIN—
  	SLIP_ANGLE_FOR—

  PRCHG_ACT)

  	{
  	if (PSTV_SS_LIN<MIN_CONT_TIME_WITH—
  	CONSISTENT_SIGN)

  PSTV_SS_LIN++;

  	}
  	else if (PSTV_SS_LIN>0)PSTV_SS_LIN--;
  	if (FrontLnrSlipAngle<MIN_SLIP_ANGLE—
  	FOR_PRCHG—

  	ACT
  	||RearLnrSlipAngle<MIN—
  	SLIP_ANGLE_FOR—

  PRCHG_ACT)

  	{
  	if (NGTV_SS_LIN<MIN_CONT_TIME_WITH—
  	CONSISTENT_SIGN)

  NGTV_SS_LIN++;

  	}
  	else if (NGTV_SS_LIN>0) NGTV_SS_LIN --;

• Then the front left precharge active status flags are determined.[0185]

  	FL_PRECHARGE_ACTIVE=ENABLE_RSC—
  	PRECHARGE&&((((NEG—

  	SWA_EXPECTED
  	/*Allow FL transition control to activate if
  	FR has transition pressure and SWA direction
  	is heading towards the right (heading towards
  	a negative value)*/

  	&&((FinalMinDAyDt<(-SpeedDpndntAyChng))
  	||(FR_Precharge_Press>(0.0) )))

  	||(RearLnrSlipAngle>MIN_SLIP_ANGLE—
  	FOR_PRCHG_ACT)

  ||(FrontLnrSlipAngle>MIN_SLIP_ANGLE_FOR—

  	PRCHG_ACT))
  	&&FL_Precharge_Timer<MAX_PRECHARGE—

  TIME)

  	||FL_Precharge_Press>0.0)
  	||PSTV_SS_LIN>=MIN_CONT_TIME_WITH—
  	CONSISTENT SIGN

• When the front right precharge active status flags are determined:[0186]

  	FR_PRECHARGE_ACTIVE=ENABLE_RSC—

  PRECHARGE&&(((POS_SWA_EXPECTED

  	/*Allow FR transition control to activate if FL has
  	transition pressure and SWA direction is heading
  	towards the left (heading towards a positive
  	value)*/

  &&((FinalMaxDAyDt>SpeedDpndntAyChng)||(FL—

  P recharge_Press>(0.0)))

  ||(RearLnrSlipAngle<MIN_SLIP_ANGLE—

  FOR_PRCHG_ACT)

  ||(FrontLnrSlipAngle<MIN_SLIP—

  	AANGLE_FOR_PRCHG_CT))&&FR_Precharge—
  	Timer<MAX_PRECHARGE_TIME)

  	||FR_Precharge_Press>0.0);
  	||PSTV_SS_LIN>=MIN_CONT_TIME—
  	WITH_CONSISTENT_SIGN

• In[0187]step208 calculate moderate lateral acceleration transition flags. If a lateral acceleration of a defined magnitude precedes a transition controller event associated with the opposite direction of turning within a predefined period of time, then a moderate transition flag is set for that direction until the transition controller event has been exited. These flags are used in the wheel departure angle calculation to bias any changes in total roll angle and reference bank angle towards an increasing roll signal for control.
• First a counter (moderate-positive-AY-counter) is implemented which is set to a transition hold time any time the filtered lateral acceleration exceeds the transition threshold, and is decremented to zero by one count per if the lateral acceleration is not exceeding the transition lateral acceleration threshold.[0188]

  	if(FLT_LAT_ACC>TRANSITION_AY—

  	THRESHOLD)MODERATE_POSITIVE—
  	AY_COUNTER=TRANSITION—
  	HOLD_TIME;

  else if (MODERATE_POSITIVE_AY—

  	COUNTER>0)MODERATE_POSITIVE—
  	AY_COUNTER--;

• Next, the recent positive lateral acceleration flag is calculated. This flag is set to true if the counter is greater than zero, otherwise it is set to false for a zero value of the counter.[0189]

  	if(MODERATE_POSITIVE_AY_COUNTER>0)RECENT—

  POSITIVE_AY=TRUE;

  	else RECENT_POSITIVE_AY=FALSE;

• The counter is now implemented for moderate negative lateral acceleration values. The negative counter is set to a transition hold time any time the filtered lateral acceleration falls below the negative of the transition threshold, and is decremented to zero by one count per if the lateral acceleration is not below the negative of the transition threshold.[0190]

  if(FLT_LAT_ACC<-TRANSITION_AY_THRESHOLD)

  	MODERATE_NEGATIVE_AY_COUNTER=TRANSITION—
  	HOLD_TIME;

  else if(MODERATE_NEGATIVE_AY_COUNTER>0)MODERATE—

  NEGATIVE_AY_COUNTER--;

• Similar to above, the recent negative lateral acceleration flag is calculated. This flag is set to true if the counter is greater than zero, otherwise it is set to false for a zero value of the counter.[0191]

  	if(MODERATE_NEGATIVE_AY_COUNTER>0)RECENT—

  POSITIVE_AY=TRUE;

  	else RECENT POSITIVE_AY=FALSE;

• Next, the right to left transition flag is determined based on the recent negative lateral acceleration flag and the front right transition controller active flag. If both flags are set to true, then the right to left transition flag is set to true. If the front right transition controller active flag is false, the right to left transition controller flag is set to false. Otherwise, the value is held from the previous loop. This results in a flag that remains true until the front right transition controller event is exited.[0192]

  	if(RECENT_NEGATIVE_AY&&FR_Precharge—

  Press)RIGHT_TO_LEFT_TRANSITION=TRUE;

  	else
  	if(!FR_Precharge_Press)RIGHT_TO_LEFT—

  TRANSITION=FALSE;

  	else
  	RIGHT_TO_LEFT_TRANSITION=RIGHT_TO—
  	LEFT_TRANSITION;

• Now the same calculation is performed for a left to right transition flag. If the recent negative lateral acceleration flag is true and the front left transition controller active flag if true, then the left to right transition flag is set to true. If the front left transition controller active flag is false, the left to right transition controller flag is set to false. Otherwise, the value is held from the previous loop. This results in a flag that remains true until the front left transition controller event is exited.[0193]

  if(RECENT_POSITIVE_AY&&FL_Precharge_Press) LEFT_TO—

  RIGHT_TRANSITION=TRUE;

  else if(!FL_Precharge_Press) LEFT_TO_RIGHT—

  TRANSITION=FALSE;

  else LEFT_TO_RIGHT_TRANSITION=LEFT_TO_RIGHT—

  TRANSITION;

• Then a timer is created to limit duration of high target slip request in the following:[0194]

  	if
  	(union_PRECHARGE_FLAGS.st_PRECHARGE.bf—

  	bool_RIGHT_TO_LEFT—
  	TRANSITION==TRUE)

  	{
  	if (R2L_TRANSITION_COUNTER<TIME_LIMIT_TO—

  	REQ_EXCSV_SLIP_AFTER_TRANSITION)R2L—
  	TRANSITION_COUNTER++;

  	}
  	else
  	{ R2L_TRANSITION_COUNTER=0;
  	}
  	if
  	(union_PRECHARGE_FLAGS.st_PRECHARGE.bf_bool—

  LEFT_TO_RIGHT_TRANSITION==TRUE)

  {

  if (L2R_TRANSITION_COUNTER<TIME_LIMIT_TO—

  	REQ_EXCSV_SLIP_AFTER_TRANSITION)L2R—
  	TRANSITION COUNTER++;

  	}
  	else

  {

  L2R TRANSITION COUNTER=0;

  	}

• In[0195]step210 the rate of change of relative roll angle is determined. The relative roll velocity is calculated by simple differentiation of the relative roll angle placed in series with a first order low pass filter as in:

  REL_ROLL_VELOCITY+=((REL_ROLL_ANGLE-Z1_REL—

  	ROLL_ANGLE)/LOOP_TIME)-REL_ROLL_VELOCITY)/Rel—
  	Roll_Vel_FLT_Coeff;

• In[0196]step212, the rate of change of linear front slip angle is determined. Similarly, the linear front tire side slip angle velocity is calculated by simple differentiation of the linear front side slip angle placed in series with a first order low pass filter.

  	Temp=MAX(min_Ref_Velocity_YC,Ref_Velocity_YC);
  	Lin_Front_Vel+=((CurrentFrontLnrLatVel-FRONT_LNR—

  LAT_VEL)*(rad_to_deg/LOOP_TIME)/

  Temp-Lin_Front_Vel)/lin_frnt_vel_filter—

  	coeff;

• In step[0197]214 a lower target build rate is used, yielding larger prediction pressures when steady state limit driving is detected. This is set forth in:

  if
  ((Predicted_AY_from_SWA>=1.4*g&&(FrontLnrSlipAngle

  	<=−0.85*FT_CRNRG_CMPLNCE))
  	&&(WHEEL_DEPARTURE_ANGLE>=(0.1/deg_RES_ROLL—

  	ANGLE))) || (Predicted_AY_from_SWA<=−.4*g
  	&&(FrontLnrSlipAngle>=(0.85*FT_CRNRG—
  	CMPLNCE)

  &&(WHEEL_DEPARTURE_ANGLE<=(−0.1/deg—

  RES_ROLL_ANGLE)))

  )

  {

  RECENT_STEADY_STATE_CORNERING_TIMER

  =RECENT_STDY_STATE_TURN_NEAR_LIMIT;

  }

  else

  {

  if (RECENT_STEADY_STATE_CORNERING_TIMER>0)RECENT—

  STEADY_STATE_CORNERING_TIMER-

  }

  if (RECENT_STEADY_STATE_CORNERING_TIMER>0)

  {

  TrgtBldRateStdyState=TARGET_BUILD_RATE;

  } else

  {

  TrgtBldRateStdyState=Rsc_target_build—

  rate;

  }

• In[0198]step216 an instantaneous caliper precharge requested pressure levels based on relative roll information is determined. First, a pressure is calculated based on proportional plus derivative control on roll information. Relative roll angle is used for the proportional term, roll velocity is used for the derivative term. The relative roll angle is used because it provides the required level of accuracy during the critical portion of the transition, during the zero crossing, and because it is not influenced by banks and is not influenced by integrator error or errors in reference road bank. This accuracy allows tighter thresholds than would be allowable for the PID controller. Additionally, this signal offers a high level of consistency and repeatability in the timing of the pressure build that is a critical property for the initial portion of the control intervention. The PD pressure is filtered as required to achieve an adequately smooth signal.
• Next the derivative of the PID pressure is calculated for determining the instantaneous relative roll pressure. The instantaneous pressure provides a predictive functionality for the PD controller. It is intended to provide a mechanism to compensate for the finite rate at which pressure can be built. Additionally, it can provide a significant smoothing effect on the leading edge of the pressure trace without delaying the pressure build. This is helpful in building the required level of pressure while minimizing the excitation of the pitching mode of the vehicle. The instantaneous pressure is that pressure which would need to be in the caliper in the current loop such that if the pressure is increased at the target build rate, the matching pressure would be achieved at the same time the PID controller is expected to request the matching pressure. The point in time for which the PID controller is expected to request the matching pressure is obtained by taking the derivative of the PID pressure and projecting forward to the point in time when the intersects the matching pressure.[0199]
• Front left relative roll instantaneous pressure is determined by:[0200]

  	FLRelRollPDPress+=(KP_REL_ROLL*(−REL_ROLL_ANGLE

  	−REL_ROLL_DB)−KD_REL_ROLL*FLT—
  	ROLL_RATE
  	−FLRelRollPDPressZ1)*REL_ROLL—
  	PD_PRESS_FILT

  FLRelRollPDPress=min(FLRelRollPDPress, MAX_FL_REL—

  ROLL_PD_PRESS);

  FLRelRollPDPress=max(FLRelRollPDPress, MIN_FL_REL—

  ROLL_PD_PRESS);

  dFLRelRollPDPress=FLRelRollPDPress−FLRelRollPD

  PressZ1;

  	FLRelRollPDPressZ1=FLRelRollPDPress;
  	FLRelRollInstPress=MatchingPressure−(Matching

  	Pressure−FLRelRollPDPress) *TARGET_BUILD—
  	RATE /max(TARGET_BUILD_RATE, dFLRelRoll
  	PDPress /LOOP_TIME);

• Then the Front Right relative roll instantaneous pressure is determined by:[0201]

  FRRelRollPDPress+=(KP_REL_ROLL* (REL_ROLL ANGLE−REL—

  	ROLL_DB)+KD_REL_ROLL*FLT_ROLL_RATE−FRRelRoll
  	PDPressZ1)*REL_ROLL_PD_PRESS_FILT)

  FRRelRollPDPress=min(FRRelRollPDPress, MAX_FL_REL—

  ROLL_PD_PRESS);

  FRRelRollPDPress=max(FRRelRollPDPress, MIN_FL_REL—

  ROLL_PD_PRESS);

  dFRRelRollPDPress=FRRelRollPDPress−FRRelRollPD

  PressZ1;

  FRRelRollPDPressZ1=FRRelRollPDPress;

  FRRelRollInstPress=MatchingPressure−(Matching

  	Pressure−FRRelRollPDPress) *TARGET_BUILD_RATE
  	/max(TARGET_BUILD_RATE, dFRRelRollPDPress
  	/LOOP_TIME);

• In[0202]step218 the conditions for applying the Yaw Rate PID controller to prevent a pressure increase from the yaw rate controller when driver is steering out of a turn are determined.
• When transitioning from a right to a left turn, determine when change in SWA direction to the left has been well established; use as a condition for blocking the YAW RATE PD controller from further increasing transition pressure on FL wheel[0203]

  	if ((STEERING_WHEEL_ANGLE−Z1_STEERING_WHEEL_ANGLE)

  >=0)

  {

  	if (INCREASING_SWA_COUNTER<(UPPER_BOUND_ON—
  	TIME_FOR_DETECTION/LOOP_TIME_SEC))
  	{ INCREASING_SWA_COUNTER++;
  	}
  	if (POSITIVE_DELTA_SWA_INT<UPPER_BOUND_ON—
  	DELTA_SWA_INT)
  	{ //Accumulate positive delta SWA POSITIVE—

  	DELTA_SWA_INT+=(STEERING_WHEEL_ANGLE−Z1—
  	STEERING_WHEEL_ANGLE);

  }

  	}
  	else // SWA is heading to the right
  	{

  	INCREASING_SWA_COUNTER=0; // Reset increasing
  	SWA counter POSITIVE_DELTA_SWA_INT=0; // Reset

  	delta SWA integration
  	}
  	if
  	(LARGE_LAT_ACC_COUNTER==0 || (Predicted_AY_from_SWA>−

  	AY_FROM_SWA_THRESH_FOR_DIRECTION_CHANGE
  	&&INCREASING_SWA_COUNTER>=TIME_FOR_DETECTING—
  	SWA_DIRECTION_CHANGE&&POSITIVE_DELTA_SWA_INT
  	>=(SWA_VEL_FOR_DETECTING_SWA_DIRECTION_CHANGE
  	*TIME_FOR_DETECTING_SWA_DIRECTION_CHANGE))

  	)
  	// Disable YawRate PD controller on FL from
  	increasing transition pressure if LatAcc at CG
  	magnitude did not exceed lateral accel threshold
  	(tunable parameter set to 0.5 g's) within the past
  	3 seconds or anytime the predicted Ay from SWA is
  	greater than (-0.5 g) and SWA and SWA_VEL indicate
  	a consistent positive sign trend
  	ROLL_FLAG.bf_bool_FL_DISABLE_YR_PD_PR_INC=TRUE;
  	}
  	else
  	{
  	ROLL_FLAG.bf_bool_FL_DISABLE_YR_PD_PR_INC=FALSE;
  	}

• In the case when transitioning from a left to a right turn, it is determined when a change in SWA direction to the right has been well established; to use as a condition for blocking the YAW RATE PD controller from further increasing this transition pressure on FR wheel, the following is used:[0204]

  	if (STEERING_WHEEL_ANGLE−Z1_STEERING_WHEEL_ANGLE

  <=0)

  {

  if

  (DECREASING_SWA_COUNTER<UPPER_BOUND_ON_TIME_FOR—

  	DETECTION/LOOP_TIME_SEC)
  	{ // Increase counter each loop delta

  	SWA is not negative DECREASING_SWA—
  	COUNTER ++;

  	}
  	if (NEGATIVE_DELTA_SWA_INT>−UPPER_BOUND_ON—

  DELTA_SWA_INT)

  { // Accumulate positive delta SWANEGATIVE—

  	DELTA_SWA_INT+=STEERING_WHEEL_ANGLE−Z1—
  	STEERING_WHEEL_ANGLE;

  }

  	}
  	else // SWA is heading to the left
  	DECREASING_SWA_COUNTER=0; // Reset decreasing

  	SWA counter
  	NEGATIVE_DELTA_SWA_INT=0; // Reset delta SWA
  	integration

  	}
  	if
  	(LARGE_LAT_ACC_COUNTER==0 || (Predicted_AY_from_SWA

  	<AY_FROM_SWA_THRESH_FOR_DIRECTION_CHANGE&&
  	DECREASING_SWA_COUNTER>=TIME_FOR_DETECTING_SWA—
  	DIRECTION_CHANGE&&NEGATIVE_DELTA_SWA_INT<=
  	(SWA_VEL_FOR_DETECTING_SWA_DIRECTION_CHANGE
  	*TIME_FOR_DETECTING_SWA_DIRECTION_CHANGE))

  	)
  	//Disable YawRate PID controller on FR from
  	increasing transition pressure if LatAcc at CG
  	magnitude did not exceed lateral accel threshold
  	(tunable parameter set to 0.5 g's) within the past
  	3 seconds or anytime the predicted Ay from SWA is
  	less than +0.5 g and SWA and SWA_VEL indicate a
  	consistent negative sign trend
  	{

  ROLL_FLAG.bf_bool_FR_DISABLE_YR_PD_PR_INC

  =TRUE;

  	}
  	else
  	{

  ROLL_FLAG.bf_bool_FR_DISABLE_YR_PD_PR_INC

  =FALSE;

  	}

• Then the instantaneous caliper precharge requested pressure levels based on yaw rate are determined.[0205]

  	FLYawRatePDPress=LIMIT((FL_YAW_RATE_PD_PRESS_Z1+

  	(Rsc_kp_yaw_rate*(−FLT_YAW_RATE−SpeedDpndnt
  	YRDB))−Rsc_kd_yaw_rate*SLOW_FLT_YAW_ACC−FL—
  	YAW_RATE_PD_PRESS_Z1)/(1.0/YAW_RATE_PD_PRESS—
  	FILT)), MIN_PD_PRESS, MAX_PD_PRESS);

  dFLYawRatePDPress=FLYawRatePDPress−FL_YAW_RATE_PD—

  PRESS_Z1;

  	FL_YAW_RATE_PD_PRESS_Z1=FLYawRatePDPress;
  	#if (USE_LOWER_TARGET_BUILD_RATE_FOR_STEADY_STATE—

  	TURNS) FLYawRateInstPress=MatchingPressure
  	−(MatchingPressure−FLYawRatePDPress)*TrgtBld
  	RateStdyState/max(TrgtBldRateStdyState, dFLYaw
  	RatePDPress/LOOP_TIME_SEC));

  	#else
  	FLYawRateInstPress=MatchingPressure−(Matching

  	Pressure−FLYawRatePDPress) *Rsc_target—
  	build_rate/max(Rsc_target_build_rate,
  	dFLYawRatePDPress/LOOP_TIME_SEC));

  #endif

  FRYawRatePDPress=LIMIT((FR_YAW_RATE_PD_PRESS—

  	Z1+(Rsc_kp_yaw_rate*(FLT_YAW_RATE−
  	SpeedDpndntYRDB)+Rsc_kd_yaw_rate*SLOW—
  	FLT_YAW_ACC)−FR_YAW_RATE_PD_PRESS_Z1)/
  	(1.0/YAW_RATE_PD_PRESS_FILT)), MIN_PD—
  	PRESS, MAX_PD_PRESS);

  dFRYawRatePDPress=FRYawRatePDPress−FR_YAW_RATE—

  PD_PRESS_Z1;

  	FR_YAW_RATE_PD_PRESS_Z1=FRYawRatePDPress;
  	#if (USE_LOWER_TARGET_BUILD_RATE_FOR_STEADY—

  	STATE_TURNS) FRYawRateInstPress=Matching
  	Pressure−(MatchingPressure−FRYawRatePD
  	Press) *ss_bps_TrgtBldRateStdyState/max
  	(TrgtBldRateStdyState, dFRYawRatePDPress*
  	(1.0/LOOP_TIME_SEC)));

  #else

  FRYawRateInstPress=MatchingPressure− (Matching

  	Pressure−FRYawRatePDPress) *Rsc_target—
  	build_rate/max(Rsc_target_build_rate,
  	dFRYawRatePDPress*(1.0/LOOP_TIME_SEC)));

  	#endif

• In[0206]step220 the instantaneous caliper precharge pressures based on front linear slip angle are determined. In this section, calculations are performed which are similar to those used for the Relative Roll PD pressure. Instead of Relative Roll angle for the proportional term, the linear side slip angle of the front axle is used. Instead of roll velocity, the rate of change of the front linear slip angle is used for the derivative term.
• First, the Front Left front “front linear slip angle” instantaneous pressure is determined by:[0207]

  FLSSLinFrontPDPress+=(KP_SS_LIN_FRONT*(FrontLnrSlip

  Angle−

  SS_LIN_FRONT_DB)+KD_SS_LIN_FRONT*Lin_Front_Vel−FLSS

  LinFrontPDPressZ1)*SS_LIN_PD_PRESS_FILT;

  dFLSSLinFrontPDPress=FLSSLinFrontPDPress−FLSS

  LinFrontPDPressZ1;

  FLSSLinFrontPDPressZ1=FLSSLinFrontPDPress;

  FLSSLinFrontInstPress=MatchingPressure−(Matching

  	Pressure−FLSSLinFrontPDPress)*TARGET_BUILD—
  	RATE/max(TARGET_BUILD_RATE, dFLSSLinFront
  	PDPress /LOOP_TIME);

• Then Front Right front “front linear slip angle” instantaneous pressure is determined by:[0208]

  FRSSLinFrontPDPress+=(KP_SS_LIN_FRONT*(−Front

  	LnrSlipAngle−SS_LIN_FRONT_DB)−KD_SS_LIN_FRONT*
  	Lin_Front_Vel−FRSSLinFrontPDPressZ1)*SS_LIN—
  	PD_PRESS_FILT;

  dFRSSLinFrontPDPress=FRSSLinFrontPDPress−FRSSLin

  FrontPDPressZ1;

  FRSSLinFrontPDPressZ1=FRSSLinFrontPDPress;

  FRSSLinFrontInstPress=MatchingPressure−(Matching

  	Pressure−FRSSLinFrontPDPress)*TARGET_BUILD—
  	RATE/max(TARGET_BUILD_RATE, dFRSSLinFront
  	PDPress/LOOP_TIME);

• In[0209]step222 the instantaneous build rate based on the slope of instantaneous PID pressure in relation to the matching pressure and the length of time it would take for the prior value of precharge pressure to reach the matching pressure level is determined.
• First the front left FL instantaneous build rate based on RelRoll PD information is determined.[0210]

  	PDRelRollMatchPressDelta[FL]=MatchingPressure−

  FLRelRollPDPress;

  	if (PDRelRollMatchPressDelta[FL]<=0)
  	{
  	InstRelRollBuildRate[FL]=(MIN_INST_BUILD_RATE);
  	}
  	else
  	{

  	//Put lower limit on denominator to avoid
  	divide by zero
  	PDRelRollMatchPressDelta[FL]=max(PDRelRoll

  	MatchPressDelta[FL], (MIN_MATCH_PRESS_2—
  	PD_PRESS_DELTA));

  	//Calculate RelRoll based build rate, and
  	bound between 100 and 300 bar/s
  	InstRelRollBuildRate[FL]=

  LIMIT((((MatchingPressure−FL_Precharge—

  	Press)*(dFLRelRollPDPress*(1.0/LOOP
  	TIME)))/PDRelRollMatchPressDelta
  	[FL]), (MIN_INST_BUILD_RATE), (MAX—
  	INST_BUILD_RATE));

  	}

• Then the FL instantaneous build rate based on Yaw Rate PD information is determined.[0211]

  ssPDYawRateMatchPressDelta[FL]=ss_MatchingPressure−

  ss_FLYawRatePDPress;

  if (ssPDYawRateMatchPressDelta[FL]<=0)

  {

  ssInstYawRateBuildRate[FL]=MIN_INST_BUILD_RATE

  /bar_RES_BRAKE_PRESSR;

  }

  else

  { //Put lower limit on denominator to avoid

  	divide by zeros
  	sPDYawRateMatchPressDelta[FL]=max(ssPDYawRate
  	MatchPressDelta[FL],

  MIN_MATCH_PRESS_2_PD_PRESS_DELTA/bar_RES_BRAKE—

  PRESSR);

  	//Calculate YawRate based build rate, and
  	bound between 100 and 300 bar/s
  	ssInstYawRateBuildRate[FL]

  	=LIMIT(((ss_MatchingPressure−ss_FL—
  	Precharge_Press)*ss dFLYawRatePDPress
  	*1.0/p_LOOP_TIME_SEC/ssPDYawRateMatch
  	PressDelta[FL]),

  MIN_INST_BUILD_RATE/bar_RES_BRAKE—

  PRESSR,

  MAX_INST_BUILD_RATE/bar_RES_BRAKE—

  PRESSR);

  }

• Then the FL instantaneous build rate based on SSLinFront PD information is determined.[0212]
• Then the FL instantaneous build rate based on SSLinFront PD information is determined.[0213]

  	PDSSLinMatchPressDelta[FL]=MatchingPressure-FLSS

  LinFrontPDPress;

  	if (PDSSLinMatchPressDelta[FL]<=0)
  	{

  InstSSLinFrntBuildRate[FL]=(MIN_INST—

  BUILD_RATE);

  	}
  	else
  	{

  	//Put lower limit on denominator to avoid
  	divide by zero
  	PDSSLinMatchPressDelta[FL]=max(PDSSLin

  	MatchPressDelta[FL], (MIN_MATCH—
  	PRESS_2_PD_PRESS_DELTA));

  	//Calculate SSLinFront based build rate,
  	and bound between 100 and 300 bar/s
  	InstSSLinFrntBuildRate[FL]=

  	LIMIT((((MatchingPressure−FL—
  	Precharge_Press)*(dFLSSLinFrontPD
  	Press*(1.0/LOOP_TIME))) /

  PDSSLinMatchPressDelta[FL]),

  (MIN_INST_BUILD_RATE),(MAX_INST_BUILD—

  RATE));

  	}

• Then a final FL instantaneous build rate by taking maximum of RelRoll and SSLinFront rates.[0214]
• InstBuildRate[FL]=max(InstRelRollBuildRate[FL], InstSSLinFrntBuildRate[FL]);[0215]
• The same process is repeated for the front right FR. First, the FR instantaneous build rate based on RelRoll PD information is determined.[0216]

  	PDRelRollMatchPressDelta[FR]=MatchingPressure−FR

  RelRollPDPress;

  	if (PDRelRollMatchPressDelta[FR]<=0)
  	{

  InstRelRollBuildRate[FR]=(MIN_INST_BUILD—

  RATE);

  	}
  	else
  	{

  	//Put lower limit on denominator to avoid
  	divide by zero
  	PDRelRollMatchPressDelta[FR]=max(PDRel

  	RollMatchPressDelta[FR], (MIN_MATCH—
  	PRESS_2_PD_PRESS_DELTA));

  	//Calculate RelRoll based build rate, and
  	bound between 100 and 300 bar/s
  	InstRelRollBuildRate[FR]=

  	LIMIT((((MatchingPressure−FR—
  	Precharge_Press)
  	(dFRRelRollPDPress*(1.0/LOOP_TIME)))
  	/PDRelRollMatchPressDelta[FR]),
  	(MIN_INST_BUILD_RATE), (MAX_INST—
  	BUILD RATE));

  	}

• Then the calculation of FR instantaneous build rate based on Yaw Rate PD information is performed by:[0217]

  ssPDYawRateMatchPressDelta[FR]=ss_MatchingPressure

  −ss_FRYawRatePDPress;

  if (ssPDYawRateMatchPressDelta[FR]<=0)

  {

  ssInstYawRateBuildRate[FR]=MIN_INST_BUILD—

  RATE/bar_RES_BRAKE_PRESSR;

  }

  else

  {	//Put lower limit on denominator to avoid

  	divide by zero
  	ssPDYawRateMatchPressDelta[FR]=max(ssPD

  YawRateMatchPressDelta[FR],

  MIN_MATCH_PRESS_2_PD_PRESS_DELTA/bar_RES_BRAKE—

  PRESSR);

  	//Calculate YawRate based build rate, and
  	bound between 100 and 300 bar/s
  	ssInstYawRateBuildRate[FR]=
  	LIMIT(((ss_MatchingPressure−ss_FR—

  Precharge_Press)*

  ss_dFRYawRatePDPress*1.0/p_LOOP_TIME—

  SEC/

  ssPDYawRateMatchPressDelta[FR]),

  MIN_INST_BUILD_RATE/bar_RES—

  BRAKE_PRESSR,—

  MAX_INST_BUILD_RATE/bar_RES—

  	BRAKE_PRESSR);

• After, the FR instantaneous build rate based on SSLinFront PD information is determined by:[0218]

  	PDSSLinMatchPressDelta[FR]=MatchingPressure−FRSS

  LinFrontPDPress;

  	if (ssPDSSLinMatchPressDelta[FR]<=0)
  	{

  InstSSLinFrntBuildRate[FR]=(MIN_INST—

  BUILD_RATE);

  	}
  	else
  	{

  	//Put lower limit on denominator to avoid
  	divide by zero
  	PDSSLinMatchPressDelta[FR]=max(PDSSLin

  MatchPressDelta[FR],

  (MIN_MATCH_PRESS_2_PD_PRESS—

  DELTA));

  	//Calculate SSLinFront based build rate,
  	and bound between 100 and 300 bar/s
  	InstSSLinFrntBuildRate[FR]=

  LIMIT((((MatchingPressure−FR—

  Precharge_Press)

  *(dFRSSLinFrontPDPress*(1.0/LOOP—

  TIME)))

  /PDSSLinMatchPressDelta[FR]),

  	(MIN_INST_BUILD_RATE),(MAX
  	INST_BUILD_RATE));

  	}

• Then the final FR instantaneous build rate by taking maximum of RelRoll and SSLinFront rates InstBuildRate[FR]=max(InstRelRollBuildRate[FR], InstSSLinFrntBuildRate[FR]);[0219]
• In[0220]step224, the requested pressures for each caliper are determined as follows.
• Front left requested pressures are determined by:[0221]

  	FLInstPressRequest=0.0;
  	FLInstPressRequest=max(FLInstPressRequest, FLRel

  RollInstPress);

  FLInstPressRequest=max(FLInstPressRequest, FLSS

  LinFrontInstPress);

  FLInstPressRequest=max(FLInstPressRequest,ss_FLYaw

  RateInstPress);

  FLInstPressRequest=min(FLInstPressRequest, Matchinq

  Pressure);

  FLInstPressRequest=max(FLInstPressRequest, FLRel

  RollPDPress);

  FLInstPressRequest=max(FLInstPressRequest, FLSS

  LinFrontPDPress);

  FLInstPressRequest=max(FLInstPressRequest,ss_FLYaw

  		RatePDPress);

• Front right requested pressures are determined by:[0222]

  	FRInstPressRequest=0.0;
  	FRInstPressRequest=max(FRInstPressRequest, FRRel

  RollInstPress);

  FRInstPressRequest=max(FRInstPressRequest, FRSS

  LinFrontInstPress);

  FRInstPressRequest=max(FRInstPressRequest,ss_FRYaw

  RateInstPress);

  FRInstPressRequest=min(FRInstPressRequest, Matching

  Pressure);

  FRInstPressRequest=max(FRInstPressRequest, FRRel

  RollPDPress);

  FRInstPressRequest=max(FRInstPressRequest, FRSS

  LinFrontPDPress);

  FRInstPressRequest=max(FRInstPressRequest,ss_FRYaw

  		RatePDPress);

• In[0223]step226 the front left caliper precharge requests are updated:

  	if (FL_PRECHARGE _ACTIVE
  	{

• If the RelRoll or SSLin PD pressure requests an increase, the requested pressures are ramped up.[0224]

  if ((FLRelRollPDPress>FL_Precharge_Press)||(FLSSLin

  FrontPDPress>FL_Precharge_Press)

  ||FLYawRatePDPress>FL_Precharge_Press)

  	{
  	FL_Precharge_Press+=LARGE_DYNAMICS_BUILD_RATE*

  LOOP_TIME;

  }

• If the instantaneous pressure requests an increase, the requested pressures are ramped up.[0225]

  else if (FLInstPressRequest>ss_FL_Precharge_Press)

  	{
  	if (RECENT_PID_ACTIVATION[FL]||RECENT_RIGHT—

  WHEEL_LIFT )

  {

  FL_Precharge_Press+=LARGE_DYNAMICS_BUILD—

  RATE*LOOP_TIME;

  	}
  	else
  	{

  FL_Precharge_Press+=(InstBuildRate[FL]

  *LOOP_TIME);

  }

• If the steering information suggests a transitional event, the pressure is ramped up to a low mu dependent value in the following:[0226]

  	else if(NEG_SWA_EXPECTED

  &&FinalMinRtLmtdDAyDt >SpeedDpndntAy

  Chng

  &&FL_Precharge_Press<RoughMU*BASE—

  PRESSURE_MU_GAIN)

  	{
  	FL_Precharge_Press+=TARGET_BUILD_RATE
  	*LOOP_TIME;
  	}

• If a pressure increase is not requested AND no PID pressure increase is requested, the requested pressure is ramped down.[0227]

  else if ((FL_Precharge_Timer<PRECHARGE_BUILD_TIME)

  &&((PID_STBLZ_PRES[FL]>FL_Precharge_Press)

  ||(!PID_FL_INCREASE_REQUESTED_PRESSURE))

  &&(REL_ROLL_ANGLE>-REL_ROLL_DB)

  &&FinalMinRtLmtdDAyDt<Speed

  DpndntAyChng)

  	{
  	FL_Precharge_Press-=TARGET_DUMP_RATE*LOOP—

  TIME;

  }

• Any time the timer is above the build time AND no PID pressure increase is requested AND RelRollAngle is smaller than the RelRollDB, a reduction in pressure is forced.[0228]

  	if(FL_Precharge_Timer>=PRECHARGE_BUILD_TIME

  &&(PID_STBLZ_PRES[FL]>FL_Precharge_Press

  ||!PID_INCREASE_REQUESTED_PRESSURE

  [FL])

  	&&REL_ROLL_ANGLE>-REL_ROLL_DB)
  	{
  	temp=FL_Precharge_Press/(max(1,MAX—

  PRECHARGE_TIME-FL_Precharge_Timer);

  temp=min(2*TARGET_DUMP_RATE*LOOP_TIME,

  temp);

  temp=max(TARGET_DUMP_RATE*LOOP_TIME,

  temp);

  	FL_Precharge_Press−=temp;
  	}

  FL_Precharge_Press=max(0.0,FL_Precharge—

  Press);

  }

  else

  	{
  	FL_Precharge_Press=0.0;
  	}

• In a similar manner the front right precharge request is updated.[0229]

  	If (FR_PRECHARGE_ACTIVE)

  	{

• If the RelRoll or SSLin PD pressure requests an increase, the requested pressure is ramped up.[0230]

  if (FRRelRollPDPress>FR_Precharge_Press||FRSSLin

  FrontPDPress>FR_Precharge_Press

  ||FRYawRatePDPress>FR_Precharge—

  Press)

  	{
  	FR_Precharge_Press+=LARGE_DYNAMICS_BUILD_RATE

  *LOOP_TIME;

  	}

• If the instantaneous pressure requests an increase, the requested pressure is ramped up.[0231]

  	else if(FRInstPressRequest>FR_Precharge_Press)

  	{
  	if (RECENT_PID_ACTIVATION[FR]||RECENT_LEFT—

  WHEEL_LIFT)

  {

  FR_Precharge_Press+=LARGE_DYNAMICS—

  BUILD_RATE*p_LOOP_TIME_SEC;

  	}
  	else
  	{
  	FR_Precharge_Press+=(InstBuildRate[FR]*LOOP—

  TIME);

  	}

• If the steering information suggests a transitional event, the pressure is ramped up to a low mu dependent value[0232]

  	else if(POS_SWA_EXPECTED

  	&&FinalMaxRtLmtdDAyDt>SpeedDpndntAyChng
  	&&FR_Precharge_Press<RoughMU*BASE_PRESSURE—

  MU_GAIN)

  	{
  	FR_Precharge_Press+=TARGET_BUILD_RATE*LOOP—

  TIME;

  	}

• If a pressure increase is not requested AND no PID pressure increase requested, then the requested pressure is ramped down.[0233]

  	else if (FR_Precharge_Timer<PRECHARGE_BUILD_TIME

  &&(PID_STBLZ_PRES[FR]>FR_Precharge_Press

  ||!PID_INCREASE_REQUESTED_PRESSURE

  [FR])

  	&&REL_ROLL_ANGLE<REL_ROLL_DB
  	&&FinalMaxRtLmtdDAyDt<SpeedDpndntAyChng

  	{
  	FR_Precharge_Press−=TARGET_DUMP—

  RATE*LOOP_TIME;

  	}

• Any time the timer is above the build time AND no PID pressure increase is requested AND RelRollAngle is smaller than the RelRollDB, force a reduction in pressure.[0234]

  	if((FR_Precharge_Timer>=PRECHARGE_BUILD_TIME

  &&(PID_STBLZ_PRES[FR]>FR_Precharge_Press

  ||!PID_INCREASE_REQUESTED_PRESSURE[FR])

  &&REL_ROLL_ANGLE<REL_ROLL_DB)

  	{
  	temp=FR_Precharge_Press/(max(1,MAX

  _PRECHARGE_TIME-FR_Precharge_Timer);

  temp=min(2*TARGET_DUMP_RATE*LOOP_TIME,

  temp);

  temp=max(TARGET_DUMP_RATE*LOOP_TIME,

  temp);

  	FL_Precharge_Press−=temp;
  	}

  FR_Precharge_Press=max(0.0,FR_Precharge—

  Press);

  }

  else

  	{
  	FR_Precharge_Press=0.0;
  	}

• In[0235]step228 the old values for next loop are updated.

  SS_Lin_Rear_Z1=RearLnrSlipAngle;
  REAR_LNR_LAT_VEL=CurrentRearLnrLatVel;
  FRONT_LNR_LAT_VEL=CurrentFrontLnrLatVel;
  REAR_LNR_LAT_ACC=FltRearLnrLatA;
  Z1_STEERING_WHEEL_ANGLE=STEERING_WHEEL_ANGLE;

• PID Controller[0236]
• Referring now to FIG. 8, the[0237]PID controller78 calculates front control pressures; using some or all of Proportional, Integral, Derivative and Double Derivative feedback control logic, required to control excessive two wheel lift during non-tripped rolling motion. For short the controller is referred to as a PID controller even though all the functions may not be provided. The “I” integral and “DD” double derivative functions are the most likely not to be present. When this controller acts on a signal it is referred to as PID control even though all the functions may not be provided. The control pressure is applied to the outer front wheel when the vehicle is experiencing high lateral acceleration while turning and concurrently experiencing wheel lift on the inner side of the turn. PID intervention is based on the requested PID feedback pressure, as well as vehicle velocity and lateral acceleration exceeding specified thresholds; when the vehicle is moving in a forward direction. Intervention ends when PID pressure falls below a threshold reflective of stabilization of roll motion, or if driver is braking when PID pressure falls within an offset of driver pressure and slip of wheel being controlled indicates a level of stability appropriate for handoff to the anti-lock braking system.
• Essentially, the[0238]PID controller78 acts when more aggressive control is needed. Thetransition controller76 acts before the vehicle is in an aggressive maneuver. This is typically below a threshold where the sensors are still in a linear region. Above the linear threshold, the PID takes over to aggressively control the vehicle. Aggressive control applies greater braking pressure to prevent the vehicle from rolling over.
• In general, the Proportional, Integral, Derivative and Double Derivative, if present, terms are added together to form the total requested control pressure on each wheel. A brief explanation of each term follows.[0239]
• The proportional term acts on a roll angle error input signal, thus the term proportional since the resulting requested control pressure will be proportional to the roll angle error magnitude by a factor K_P. A proportional peak hold strategy was added to mitigate a bouncing mode which can occur in certain aggressive maneuvers. The initiation of this strategy is contingent on the vehicle having experienced a recent divergence in roll rate magnitude.[0240]
• The input to the derivative term is roll rate signal, which serves as a leading indicator of roll angle instability and thus provide an early lead on controlling the transient behavior of roll angle. The gain factor K_D multiplies the roll rate signal minus a deadband to generate a derivative pressure term. KD is an experimentally derived term. If K_D is unduly high, unnecessary control interventions may be caused (sensitive system) and the system made susceptible to input signal noise.[0241]
• The double derivative term is used to capture the roll stability tendency of the vehicle. The roll acceleration signal will exhibit wide-ranging oscillations during control, so the gain factor K_DD 's influence on the overall PID stabilizing pressure should be set to a minimum.[0242]
• The integral control pressure is used to drive the steady state roll angle error toward zero. A bounded version of the roll angle error signal is multiplied by a gain factor K_I, then integrated to provide a requested integrator pressure. The reason for bounding the input is to prevent integrator windup.[0243]
• The[0244]PID controller78 has various inputs. The inputs include a lateral acceleration at the center of gravity (CG_FLT_LAT_ACC (m/s/s)input300, a filtered roll rate (FLT_ROLL_RATE (deg/s)input302, a (ROLL_ACCELERATION (deg/s/s)input304, (ROLL_ANGLE_TOTAL (deg) input306, a (REFERENCE_BANK_ANGLE (deg)input308, a front left brake pressure estimate (BRAKE_PRESSR_ESTMT [FL] (bar)input312, a front right (BRAKE_PRESSR_ESTMT [FR] (bar)input314, a driver requested pressure (DRIVER_REQ_PRESSURE (bar)316, a (RSC_REFERENCE_VELOCITY (m/s) input317, a (SLIP_RATIO [FL] (%)input318, a (SLIP_RATIO [FR] (%)input320, (RIGHT_TO_LEFT_TRANSITION (Boolean)input322, (LEFT_TO_RIGHT_TRANSITION (Boolean)input324, (DRIVER_BRAKING_FLAG (Boolean)input326, a roll system disabled (RSC_DISABLED (Boolean)input328, (REVERSE_MOVEMENT (Boolean)input330, (STATUS_FIRST_RUN (Boolean)input332, (RSC_IN_CYCLE (Boolean)input334, (AYC_IN_CYCLE (Boolean)input336 and a roll signal for control input338.
• The PID controller has various outputs including (PID_ACTIVE [FL] (Boolean)[0245]output350, (PID_ACTIVE [FR] (Boolean)output352, a stabilizer pressure (PID_STBLZ_PRESSURE [FL] (bar)output354, (PID_STBLZ_PRESSURE [FR] (bar)output356, (RECENT_AYC_CNTRL_EVENT (Boolean)output358, (RECENT_PID_CNTRL_EVENT (Boolean)output360, (INCREASE_REQUESTED_PRESSURE [FL] (Boolean)output362, (INCREASE_REQUESTED_PRESSURE [FR] (Boolean)output364.
• The[0246]PID controller78 includes the various calibratable parameters. The parameters are shown for his example. The parameters in implementation may be varied based on the vehicle configuration. Proportional dead band PROP_DB (linear interpolation function of vehicle speed): Absolute value of Proportional deadband above which the error signal input to the proportional controller becomes positive, thus yielding a positive requested proportional pressure. At nominal speeds, the value is chosen in the vicinity of the vehicle roll gradient experienced near 1 g of lateral acceleration.

  	RSC_REFERENCE_VELOCITY	PROP_DB
  	(m/s)	(deg)

  	0	7.0
  	16.0	5.2
  	32.0	5.2
  	83.0	4.6

• Another is proportional gain factor K_P_UP (linear interpolation function of vehicle speed): Proportional gain factor that multiplies the roll angle error signal when above PROP_DB, thus generating a positive proportional term of the requested PID stabilizing pressure.[0247]

  	RSC_REFERENCE_VELOCITY	K_P_UP
  	(m/s)	(bar/deg)

  	0	30.0
  	18.0	30.0
  	35.0	30.0
  	83.0	30.0

• Proportional gain factor K_P_DOWN (linear interpolation function of vehicle speed): Proportional gain factor that multiplies the roll angle error signal when below PROP_DB, thus generating a negative proportional term of the requested PID stabilizing pressure.[0248]

  	RSC_REFERENCE_VELOCITY	K_P_DOWN
  	(m/s)	(bar/deg)

  	0	40.0
  	18.0	40.0
  	35.0	40.0
  	83.0	40.0

• LARGE_ROLL_RATE_THRESH (in this example a value of 30.0 deg/s is used): Roll rate magnitude above which recent large roll rate timer is set to the maximum value.[0249]
• RECENT_LARGE_ROLL_RATE (0.5 sec): Time duration assigned to recent large roll rate timer when roll rate magnitude exceeds LARGE_ROLL_RATE_THRESH.[0250]
• PROP_HOLD_ANGLE_THRESHOLD (in this example a value of 1.48*Roll_gradient is used): Roll angle at which the proportional pressure starts tracking peak proportional pressure.[0251]
• PROP_PEAK_HOLD_TIME (in this example a value of 0.5 sec is used): Time duration that the proportional peak hold pressure is latched once magnitude of roll signal for control falls below PROP_HOLD_ANGLE_THRESHOLD.[0252]
• PROP_PEAK_RAMP_DOWN_RATE (in this example a value of 250 bar/s is used): Ramp down rate of prior proportional peak to a new lower prop peak pressure when roll signal for control still exceeds hold angle, or ramp down rate to upstream proportional pressure if roll signal for control has not exceeded hold angle within the last PROP_PEAK_HOLD_TIME seconds.[0253]
• DERIV_DB (linear interpolation function of lateral acceleration): Absolute value of derivative deadband, used outside of PID control, above which the error signal input to the derivative controller becomes positive, thus yielding a positive requested derivative pressure. Values are chosen to prevent roll rate noise at low lateral acceleration levels from inducing nuisance PID interventions.[0254]

  	CG_FLT_LAT_ACC	DERIV_DB
  	(m/s/s)	(deg/sec)

  	0	5.0
  	4.0	5.0
  	7.0	0.0
  	100.0	0.0

• DERIV_DB_DURING_PID_CONTROL (in this example a value of −[0255]20 deg/s is used). During PID intervention the deadband is set to a constant (non-lateral acceleration dependent) negative value, providing a phase advance on the PID pressure to mitigate roll oscillation during aggressive maneuvers.
• K_D_UP (linear interpolation function of vehicle speed): Derivative gain factor that multiplies the roll rate error signal when roll rate is above DERIV_DB; generating a positive derivative term of the requested PID stabilizing pressure.[0256]

  	RSC_REFERENCE_VELOCITY	K_D_UP
  	(m/s)	(bar/deg/s)

  	0	1.0
  	18.0	1.0
  	35.0	1.0
  	83.0	1.0

• K_D_DOWN (linear interpolation function of vehicle speed): Derivative gain factor that multiplies the roll rate error signal when roll rate is below DERIV_DB; generating a negative derivative term of the requested PID stabilizing pressure.[0257]

  	RSC_REFERENCE_VELOCITY	K_D_DOWN
  	(m/s)	(bar/deg/s)

  	0	0.2
  	18.0	0.2
  	35.0	0.2
  	83.0	0.2

• K_DD_UP (in this example a value of 0. bar/deg/s/s is used): Double derivative gain factor that multiplies the roll acceleration signal when RSC intervention is active and roll acceleration sign matches that of the turn; generating a positive double derivative term of the requested PID stabilizing pressure.[0258]
• K_DD_DOWN (in this example a value of 0 bar/deg/s/s is used): Double derivative gain factor that multiplies the roll acceleration signal when RSC intervention is not active or roll acceleration sign is opposite that of the turn; generating a nil double derivative term of the requested PID stabilizing pressure.[0259]
• INTG_DB (linear interpolation function of vehicle speed): Absolute value of Integral deadband above which the error signal input to the Integral term becomes positive. At nominal speeds, value is chosen in the vicinity of the vehicle roll gradient experienced near 1 g of lateral acceleration.[0260]

  	RSC_REFERENCE_VELOCITY	INTG_DB
  	(m/s)	(deg)

  	0	7.0
  	16.0	5.2
  	32.0	5.2
  	83.0	4.6

• MAX_INTGRTR_ERROR (in this example a value of 5.0 deg is used): Absolute value of upper bound on the error signal input to the Integral controller. The purpose of this parameter is to prevent integrator windup.[0261]
• MIN_INTGRTR_ERROR (in this example a value of 5.0 deg is used): Absolute value of lower bound on the error signal input to the Integral controller. The purpose of this parameter is to avoid integrator windup.[0262]
• K_I (in this example a value of 10.0 bar/deg.s is used): Integral gain factor multiplying the bounded roll angle error signal times loop time, generating the integral term of the requested stabilizing pressure.[0263]
• PRESSURE_INCREASE_DELTA_FOR_INFLECTION_ADJUST (in this example a value of 10 bar is used): The pressure delta that the pressure estimate has to increase by before the downward adjustment of the PID pressure, to an offset (PRESSURE_OFFSET_DURING_PID_RAMP_UP) from the pressure estimate, occurs.[0264]
• PRESSURE_OFFSET_DURING_PID_RAMP_UP (in this example a value of 20 bar is used): Specifies the maximum delta between PID pressure and estimated pressure, once the inflection adjustment begins.[0265]
• LMTD_RAMP_DOWN_RATE (in this example a value of −400 bar/s is used): Maximum decrease rate that the PID requested pressure is allowed to ramp down at.[0266]
• MAX_PRESSURE_DECREASE_TO_ENTER_LMTD_RAMP_DOWN (in this example a value of −0.5 bar is used): Negative delta pressure of the underlying P+I+D+DD sum required to enter the limited PID ramp down mode.[0267]
• MIN_PRESSURE_INCREASE_TO_STAY_IN_LMTD_RAMP_DOW N (in this example a value of 0.5 bar is used): Positive delta pressure of the underlying P+I+D+DD sum above which limited PID ramp down mode exits.[0268]
• MAX_RAMP_DOWN_RATE (in this example a value of −300 bar/s is used): Ramp down rate used when opposite front wheel requests PID intervention concurrently as inside wheel is ramping down PID requested pressure.[0269]
• ENTER_THRES (in this example a value of 30.0 bar is used): PID requested pressure threshold for either front wheel, above which the flag PID_ACTIVE is set. A true value for the aforementioned flag constitutes one of the necessary conditions for activating RSC.[0270]
• LAT_ACC_ACTVTION_THRSHLD (in this example a value of 5.0 m/s/s is used): Absolute value of vehicle lateral acceleration threshold above which the variable LARGE_LAT_ACC_COUNTER is initialized to LAT_ACC[0271]_{COUNTERINIT. A nonzero value of this counter is a necessary condition for activating RSC.}
• LAT_ACC_COUNTER_INIT (in this example a value of 3.0 sec is used): Time duration assigned to LARGE_LAT_ACC_COUNTER when vehicle lateral acceleration magnitude exceeds LARGE_ROLL_RATE_THRESH.[0272]
• EXIT_THRES (in this example a value of 10.0 bar is used): PID requested pressure threshold for either front wheel below which the flag PID_ACTIVE resets to false, thus exiting PID control.[0273]
• WHEEL_STABLE_IN_SLIP (in this example a value of −15% is; used): Maximum slip ratio observed on PID controlled wheel before PID intervention can exit.[0274]
• MIN_PID_PRES_FOR_FORCED_CONTROL_EXIT (in this example a value of 9 bar is used): PID pressure threshold below which PID intervention is forced to exit, in case wheel is allowed to lock for an extended period thus not allowing the WHEEL_STABLE_IN_SLIP criteria to be met.[0275]
• RECENT_PID_EVNT_THRSHLD (in this example a value of 0.7 sec is used): Period of time during which the history of any PID intervention is logged.[0276]
• RECENT_AYC_EVNT_THRSHLD (in this example a value of 0.7 sec is used): Period of time during which the history of any AYC intervention is logged.[0277]
• PID_MINIMUM_ACTIVATION_SPEED (in this example a value of 7.0 m/s is used): Vehicle speed below which RSC system will not activate.[0278]
• MAXIMUM_SPEED_TO_CONTINUE_PID (in this example a value of 5.0 m/s is used: If vehicle speed falls below this threshold during PID intervention, PID control exits.[0279]
• MAXIMUM_STBLZ_PRESSURE (in this example a value of 255.0 bar is used).[0280]
• LOOP_TIME_SEC: (in this example a value of 0.007 sec is used): Sampling time of input signals, as well as maximum allowable execution time of stability control system logic.[0281]
• Compute PID Desired Braking Pressures Logic[0282]
• The description of the PID feedback controller for non-tripped roll events follows. An explanation of the calculation of each term is included, and a C-language implementation of the computation is also included.[0283]
• Referring now to FIG. 9, a flowchart illustrating the operation of the[0284]PID controller78 is illustrated. Instep400 the sensors of the system are read. Instep402 the various inputs described above are obtained.
• In step[0285]404 a derivative term of the roll stabilizing requested pressures for each front wheel is determined. During PID intervention or if a recent moderately aggressive transition maneuver (as indicated from the transition controller), the derivative deadband determined instep406 is set to a constant negative threshold (DERIV_DB DURING PID CONTROL) to provide for a prediction of normal load oscillations. Otherwise the derivative deadband (DERIV_DB) is a function of the vehicle's lateral acceleration, nearing zero as the lateral acceleration increases beyond 0.7 g's.
• For left turns (positive roll angle), compute derivative pressure term for outer (right) front wheel.[0286]

  	if (PID_ACTIVE[FR]||RIGHT_TO_LEFT_TRANSITION)

  derivative_db=DERIV_DB_DURING_PID_CONTROL;

  else

  derivative_db=DERIV_DB;

  if ((FLT_ROLL_RATE-derivative_db) >0) DrvtvPres

  [FR]=K_D_UP*(FLT_ROLL_RATE-derivative_db);

  else

  DrvtvPres[FR]=K_D_DOWN*(FLT_ROLL_RATE-

  	Derivative_db);

• For right turns (negative roll angle), compute derivative pressure term for outer (left) front wheel.[0287]

  	if (PID_ACTIVE[FL]||LEFT_TO_RIGHT_TRANSITION)

  derivative_db=DERIV_DB_DURING_PID_CONTROL;

  else

  derivative_db=DERIV_DB;

  if ((FLT_ROLL_RATE+derivative_db)<0)DrvtvPres[FL]=

  (−1.0)*K_D_UP*(FLT_ROLL_RATE+derivative_db);

  else

  DrvtvPres[FL]=(−

  	1.0)*K_D_DOWN*(FLT_ROLL_RATE+derivative_db);

• In[0288]step406, the double derivative term of the roll stabilizing requested pressures for each front wheel, based on roll acceleration signal is determined. This term is effective during RSC intervention, as K_DD_DOWN is set to zero.
• For left turns (positive roll angle), the double derivative pressure term for outer (right) front wheel is determined.[0289]

  if ((ROLL_ACCELERATION>0)&&RSC_IN_CYCLE)DDPres[FR]

  =K_DD_UP*ROLL_ACCELERATION;

  else

  	DDPres[FR]=K_DD_DOWN*ROLL_ACCELERATION;

• For right turns (negative roll angle), compute derivative pressure term for outer (left) front wheel.[0290]

  if ((ROLL_ACCELERATION<0)&&RSC_IN_CYCLE)DDPres[FL]

  =(−1.0)*K_DD_UP*ROLL_ACCELERATION;

  else

  	DDPres[FL]=(−1.0)*K_DD_DOWN*ROLL_ACCELERATION;

• In step[0291]408 a proportional term of the roll stabilizing requested pressures for each front wheel is determined. A roll signal for control is determined based on the vehicle angle. In the present example the ROLL_SIG_FOR_CONTROL is based on the difference between ROLL_ANGLE_TOTAL and REFERENCE_BANK_ANGLE as set forth in:

  	ROLL_SIG_FOR_CONTROL=ROLL_ANGLE_TOTAL−
  	REFERENCE—

  	BANK_ANGLE;

• The proportional term is based on roll angle error signal formed by subtracting a deadband, of value PROP_DB, from the input control signal ROLL_SIG_FOR_CONTROL. This error signal is then multiplied by the proportional gain factor K_P to obtain the proportional pressure term.[0292]
• For left turns (positive roll angle), compute proportional pressure term for outer (right) front wheel.[0293]

  	if ((ROLL_SIG_FOR_CONTROL-PROP_DB)>0)PropPres[FR]

  =(ROLL_SIG_FOR_CONTROL−PROP_DB)*K_P_UP;

  else

  PropPres[FR]=(ROLL_SIG_FOR_CONTROL−PROP_DB)

  	*K_P_DOWN;

• A history of recent large positive roll rate is kept. The history is used as a screening criteria for initiating proportional peak hold logic described thereafter. RECENT_LARGE_PSTV_ROLL_RATE_TIMER is used to keep track of this criteria.[0294]

  if (FLT_ROLL_RATE>LARGE_ROLL_RATE_THRESH)
  {

  RECENT_LARGE_PSTV_ROLL_RATE_TIMER=

  RECENT_LARGE_ROLL_RATE;

  }

  else if (RECENT_LARGE_PSTV_ROLL_RATE_TIMER>0)

  {

  RECENT_LARGE_PSTV_ROLL_RATE_TIMER−−;

  }

  if (RECENT_LARGE_PSTV_ROLL_RATE_TIMER>0)RECENT—

  LARGE_PSTV_ROLL_RATE=TRUE ;

  else

  	RECENT_LARGE_PSTV_ROLL_RATE=FALSE;

• Proportional peak hold logic: When a large positive roll divergence starts building, as indicated by roll signal for control exceeding PROP_HOLD_ANGLE_THRESHOLD and corroborated by the existence of a recent large positive roll rate, a constant base level of PID pressure to achieve a consistent level of deep slip on the wheel is maintained. This helps mitigate vehicle bounce during aggressive maneuvers. The constant base level is obtained by holding the peak value of the proportional term until the next proportional peak that exceeds the threshold, or until a timer (PROP_PEAK_HOLD_TIMER[FR]) runs out.[0295]
• FIG. 10 depicts the intended proportional peak hold strategy. In region A the proportional signal is held. In region B, because the new proportional peak pressure is increasing, the proportional hold pressure is allowed to track to a new peak. In region C the proportional pressure decreases, so the hold pressure is ramped down. In Region D the hold pressure continues to ramp down since the proportional pressure continues to decrease. It should be noted that the proportional peak hold value is held at least until the timer is reset. The countdown timer is maintained at its peak value until the roll signal for control drops below the proportional hold angle threshold.[0296]
• This is set forth in the following logic:[0297]

  	if ((ROLL_SIG_FOR_CONTROL>PROP_HOLD_ANGLE—

  	THRESHOLD)
  	&&(RECENT_LARGE_PSTV_ROLL_RATE||(PROP_PEAK—

  HOLD_TIMER[FR]>0)))

  	{ //roll angle exceeds threshold AND recent large
  	positive roll rate was seen or have already entered
  	prop peak hold mode, //enter/keep in prop peak hold
  	mode
  	if (PROP_PEAK_HOLD_TIMER[FR]==0)
  	{  //first divergent oscillation indicated

  by a null prop hold timer

  	INITIAL_DIVERGENT_OSCILLATION[FR]=TRUE;
  	}
  	if (INITIAL_DIVERGENT_OSCILLATION[FR])
  	{  //prop hold logic for first divergent

  	oscillation
  	PROP_PEAK_HOLD_TIMER[FR]=PROP_HOLD_LOOPS;
  	//set timer to max value during divergence
  	if (PropPres[FR]>=PREFERENCE_PROP_PEAK_HOLD

  [FR])

  {  //PropPres is still rising, let PeakHold

  track it

  REFERENCE_PROP_PEAK_HOLD[FR]=PropPres

  	[FR];
  	PROP_PEAK_HOLD[FR]=FALSE;

  	}
  	else
  	{  //PropPres is no longer rising, assign latched

  	PeakHold to PropPres
  	PropPres[FR]=REFERENCE_PROP_PEAK_HOLD[FR];
  	PROP_PEAK_HOLD[FR]=TRUE;
  	}

  	}
  	else //prop hold logic for subsequent divergent

  oscillations

  {

  PROP_PEAK_HOLD_TIMER[FR]=PROP_HOLD_LOOPS;//set

  	timer to max value during
  	divergence//Logic to handle transitions
  	to a higher or lower subsequent
  	proportional peak roll signal
  	if (PropPres[FR]>NEW_PROP_PEAK_HOLD[FR])

  {  //Prop Pres is still rising, assign a

  	NewPeakHold to track it
  	NEW_PROP_PEAK_HOLD[FR]=PropPres[FR];
  	TRACKING_NEXT_PEAK[FR]=TRUE;//flag
  	indicating NewPeakHold is in tracking
  	mode RAMP_DOWN_TO_NEW_PROP_PEAK[FR]
  	=FALSE; //reset ramp down once tracking
  	peak starts

  	}
  	else
  	{  //PropPres is no longer rising, reset

  	tracking flag
  	TRACKING_NEXT_PEAK[FR]=FALSE;

  	}
  	//Logic to handle transition from Reference
  	PeakHold to NewPeakHold
  	if

  ((PropPres[FR]>REFERENCE_PROP_PEAK_HOLD[FR])&&

  TRACKING_NEXT_PEAK[FR])

  {  //allow PropPres increase above prior PeakHold

  during tracking mode

  PROP_PEAK_HOLD[FR]=FALSE;

  	}
  	else if ((PropPres[FR]>REFERENCE_PROP_PEAK_HOLD

  [FR])&&!TRACKING_NEXT_PEAK[FR])

  {  //NewPeakHold is latched and is > prior

  	PeakHold, so REFERENCE_PROP_PEAK_HOLD[FR]=NEW—
  	PROP_PEAK_HOLD[FR];//assign NewPeakHold

  //to PeakHold, and

  	PropPres[FR]=REFERENCE_PROP_PEAK_HOLD[FR]
  	//assign latched NewPeakHold to PropPres
  	RAMP_DOWN_TO_NEW_PROP_PEAK[FR]=FALSE;
  	//since ramp up to NewPeakHold occurred,
  	//ramp down is not active
  	PROP_PEAK_HOLD[FR]=TRUE;

  	}
  	else if ((PropPres[FR]<REFERENCE_PROP_PEAK—

  HOLD[FR]))

  	{
  	if (!TRACKING_NEXT_PEAK[FR]

  &&(REFERENCE_PROP_PEAK_HOLD[FR]>NEW_PROP—

  PEAK_HOLD[FR]))

  {  //NewPeakHold is latched and is<prior

  	PeakHold, REFERENCE_PROP_PEAK_HOLD[FR]
  	−=PROP_PEAK_RAMP_DOWN_RATE*LOOP_TIME_SEC;
  	//ramp down prior PeakHold toNewPeak
  	Hold, RAMP_DOWN_TO_NEW_PROP_PEAK[FR]=TRUE;

  //indicate ramp down is in effect

  	if (REFERENCE_PROP_PEAK_HOLD[FR]<NEW—
  	PROP_PEAK_HOLD[FR])

  {  //ramp down of prior PeakHold brings it

  	to NewPeakHold level, // assign NewPeak
  	Hold to PeakHold, and REFERENCE_PROP_PEAK—
  	HOLD[FR]=NEW_PROP_PEAK_HOLD[FR];
  	RAMP_DOWN_TO_NEW_PROP_PEAK[FR]=FALSE;
  	//indicate end of ramp down//of PeakHold
  	towards NewPeakHold
  	}

  	}
  	PropPres[FR]=REFERENCE_PROP_PEAK_HOLD[FR];//assign
  	PeakHold to PropPresPROP_PEAK_HOLD[FR]=TRUE;

  }

  }

  	}
  	else
  	{  //roll angle is <=threshold, so decrement

  	timer and assign PropPres to PeakHold if
  	(PROP_PEAK_HOLD_TIMER[FR]>1)

  {    //PropHold timer is>1, therefore hold

  	PropPres INITIAL_DIVERGENT—
  	OSCILLATION[FR]=FALSE; //first divergent
  	oscillation of prop peak hold mode has
  	ended PROP_PEAK_HOLD_TIMER[FR]−−;
  	//decrement PropHold timer
  	if (RAMP_DOWN_TO_NEW_PROP_PEAK[FR])

  {  //ramp down of prior PeakHold to NewPeakHold

  is not completed, continue till done

  REFERENCE_PROP_PEAK_HOLD[FR]−PROP_PEAK—

  RAMP_DOWN_RATE*LOOP_TIME_SEC;

  {  //ramp down prior PeakHold to NewPeakHold

  if (REFERENCE_PROP_PEAK_HOLD[FR]<NEW—

  PROP_PEAK_HOLD[FR])

  {  //ramp down of prior PeakHold brings

  	it to NewPeakHold level,
  	//assign NewPeakHold to PeakHold
  	REFERENCE_PROP_PEAK_HOLD[FR]=NEW—
  	PROP_PEAK_HOLD[FR];
  	RAMP_DOWN_TO_NEW_PROP_PEAK[FR]
  	=FALSE;//indicate end of ramp down
  	of

  //PeakHold towards NewPeakHold

  }

  	}
  	else
  	{  //ramp down from old to new PeakHold
  	has ended or was not in effect, so reset
  	NewPeakHold state

  NEW_PROP_PEAK_HOLD[FR]=0;

  	}
  	if (PropPres[FR]<REFERENCE_PROP_PEAK_HOLD[FR])
  	{ //overwrite decreasing PropPres with
  	PeakHold during peak hold mode

  PropPres[FR]=REFERENCE_PROP_PEAK_HOLD

  [FR];

  PROP_PEAK_HOLD[FR]=TRUE;

  	}
  	else
  	{  //PropPres is higher than PeakHold, allow

  	PropPres increase above PeakHold by
  	PROP_PEAK_HOLD[FR]=FALSE; //exiting prop
  	hold mode and keeping upstream PropPres

  }

  	}
  	else //PropHold timer<=1, ramp out of prop PeakHold

  	if it existed //otherwise upstream PropPres
  	value is kept unchanged

  {

  	if (PROP_PEAK_HOLD_TIMER[FR]==1)
  	{  //prop hold mode was in effect, set flag
  	indicating ramp down of PeakHold to PropPres

  	RAMP_DOWN_PROP_HOLD_TO_PROP_PRES[FR]
  	=TRUE;

  	PROP_PEAK_HOLD_TIMER[FR]=0;
  	}
  	if (RAMP_DOWN_PROP_HOLD_TO_PROP_PRES[FR])

  {  //ramp down of PeakHold to PropPres

  if (REFERENCE_PROP_PEAK_HOLD[FR]>(PropPres[FR]

  +PROP_PEAK_RAMP_DOWN_RATE*LOOP_TIME_SEC))

  {

  REFERENCE_PROP_PEAK_HOLD[FR]−=PROP_PEAK—

  	RAMP_DOWN_RATE*LOOP_TIME_SEC;//ramp
  	down prior PeakHold to NewPeakHold
  	PropPres[FR]=REFERENCE_PROP_PEAK—
  	HOLD[FR];

  	}
  	else //PeakHold reached upstream PropPres, end
  	ramp down and exit prop hold logic
  	{

  	REFERENCE_PROP_PEAK_HOLD[FR]=0;
  	RAMP_DOWN_PROP_HOLD_TO_PROP_PRES[FR]

  =FALSE;

  }

  	}
  	else //ramp down of PeakHold to PropPres has ended,
  	or
  	{  //roll angle never exceeded threshold,
  	therefore REFERENCE_PROP_PEAK_HOLD[FR]=0;//reset
  	reference prop peak pressure
  	}
  	NEW_PROP_PEAK_HOLD[FR]=0;
  	PROP_PEAK_HOLD[FR]=FALSE;
  	RAMP_DOWN_TO_NEW_PROP_PEAK[FR]=FALSE;

  }

  	}

• For right turns (negative roll angle), compute proportional pressure term for outer (left) front wheel by:[0298]

  if ((ROLL_SIG_FOR_CONTROL+PROP_DB)<0)

  	PropPres[FL]=(−1.0)*(ROLL_SIG_FOR_CONTROL+PROP—
  	DB)*K_P_UP;

  else

  PropPres[FL]=(−1.0)*(ROLL_SIG_FOR_CONTROL+PROP—

  	DB)*K_P_DOWN;

• Keep history of recent large negative roll rate, which is used as a screening criteria for initiating proportional peak hold logic thereafter. RECENT_LARGE_NGTV_ROLL_RATE_TIMER is used to keep track of this criteria.[0299]

  if (FLT_ROLL_RATE<(−1*LARGE_ROLL_RATE_THRESH))
  {

  	RECENT_LARGE_NGTV_ROLL_RATE_TIMER=
  	RECENT_LARGE_ROLL_RATE;

  }

  else if (RECENT_LARGE_NGTV_ROLL_RATE_TIMER>0)

  {

  RECENT_LARGE_NGTV_ROLL_RATE_TIMER−−;

  }

  if (RECENT_LARGE_NGTV_ROLL_RATE_TIMER>0)RECENT—

  LARGE_NGTV_ROLL_RATE=TRUE;

  else

  	RECENT_LARGE_NGTV_ROLL_RATE=FALSE;

• When a large negative roll divergence starts building, as indicated by roll signal for control exceeding PROP_HOLD_ANGLE_THRESHOLD and corroborated by the existence of a recent large negative roll rate, this strategy serves to keep a constant base level of PID pressure to achieve a consistent level of deep slip on the wheel and thus help mitigate vehicle bounce during aggressive maneuvers. The constant base level is obtained by holding the peak value of the proportional term until the next proportional peak that exceeds the threshold, or until PROP_PEAK_HOLD_TIMER[FL] runs out.[0300]

  if ((ROLL_SIG_FOR_CONTROL<(−1.0*PROP_HOLD_ANGLE—

  	THRESHOLD))
  	&&(RECENT_LARGE_NGTV_ROLL_RATE||(PROP_PEAK—
  	HOLD_TIMER[FL]>0))

  )

  {  //roll angle exceeds threshold AND recent

  large negative roll rate was seen or have already

  entered prop peak hold mode,

  //enter/keep in prop peak hold mode

  if (PROP_PEAK_HOLD_TIMER[FL]==0)

  {    //first divergent oscillation indicated

  	by a null prop hold timer
  	INITIAL_DIVERGENT_OSCILLATION[FL]=TRUE;

  }

  if (INITIAL_DIVERGENT_OSCILLATION[FL])

  {    //prop hold logic for first divergent

  	oscillation
  	PROP_PEAK_HOLD_TIMER[FL]=PROP_HOLD_LOOPS;
  	//set timer to max value during
  	divergence

  if (PropPres[FL]>=REFERENCE_PROP_PEAK_HOLD

  [FL])

  {  //PropPres is still rising, let PeakHold

  	track it
  	REFERENCE_PROP_PEAK_HOLD[FL]=PropPres

  [FL];

  PROP_PEAK_HOLD[FL]=FALSE;

  	}
  	else

  {    //PropPres is no longer rising, assign

  	latched PeakHold to PropPres
  	PropPres[FL]=REFERENCE_PROP_PEAK_HOLD
  	[FL];
  	PROP_PEAK_HOLD[FL]=TRUE;

  }

  }

  else   //prop hold logic for subsequent

  divergent oscillations

  {

  	PROP_PEAK_HOLD_TIMER[FL]=PROP_HOLD_LOOPS;
  	//set timer to max value during divergence

  //Logic to handle transitions to a higher

  	or lower subsequent proportional peak roll
  	signal

  if (PropPres[FL]>NEW_PROP_PEAK_HOLD[FL])

  {  //PropPres is still rising, assign a

  	NewPeakHold to track it
  	NEW_PROP_PEAK_HOLD[FL]=PropPres[FL];
  	TRACKING_NEXT_PEAK[FL]=TRUE;//flag
  	indicating NewPeakHold is in tracking
  	mode
  	RAMP_DOWN_TO_NEW_PROP_PEAK[FL]=FALSE;
  	//reset ramp down once tracking peak
  	starts

  }

  else

  {  //PropPres is no longer rising, reset tracking

  	flag
  	TRACKING_NEXT_PEAK[FL]=FALSE;

  }

  //Logic to handle transition from ReferencePeakHold

  to NewPeakHold

  if

  ((PropPres[FL]>REFERENCE_PROP_PEAK_HOLD[FL])

  &&TRACKING_NEXT_PEAK[FL])

  {  //allow PropPres increase above prior PeakHold

  during tracking modePROP_PEAK_HOLD[FL]=FALSE;

  }

  else if ((PropPres[FL]>REFERENCE_PROP_PEAK—

  HOLD[FL])&&!TRACKING_NEXT_PEAK[FL])

  {  //NewPeakHold is latched and is>prior

  PeakHold, so REFERENCE_PROP_PEAK_HOLD[FL]=NEW—

  PROP_PEAK_HOLD[FL];

  //assign NewPeakHold

  //to PeakHold, and PropPres [FL]

  =REFERENCE_PROP_PEAK_HOLD[FL];

  //assign latched NewPeakHold to PropPres

  RAMP_DOWN_TO_NEW_PROP_PEAK[FL] =FALSE;

  //since ramp up to NewPeakHold occurred,

  // ramp down is not active PROP_PEAK_HOLD

  [FL]=TRUE;

  }

  else if ((PropPres[FL]<REFERENCE_PROP_PEAK_HOLD

  [FL]))

  {

  if (!TRACKING_NEXT_PEAK[FL]&&(REFERENCE_PROP—

  PEAK_HOLD[FL]>NEW_PROP_PEAK_HOLD[FL]))

  {  //NewPeakHold is latched and is<prior

  PeakHold, REFERENCE_PROP_PEAK_HOLD[FL]−=PROP_PEAK—

  RAMP_DOWN_RATE*LOOP_TIME_SEC;

  //ramp down prior PeakHold to

  NewPeakHold, RAMP_DOWN_TO_NEW_PROP_PEAK[FL]=TRUE;

  //indicate ramp down is in effect

  if (REFERENCE_PROP_PEAK_HOLD[FL]<NEW_PROP_PEAK—

  HOLD[FL])

  {  //ramp down of prior PeakHold brings it to

  NewPeakHold level, //assign NewPeakHold to

  PeakHold, and REFERENCE_PROP_PEAK_HOLD[FL]=NEW—

  PROP_PEAK_HOLD[FL];

  RAMP_DOWN_TO_NEW_PROP_PEAK[FL]=FALSE; //indicate

  end of ramp down

  // of PeakHold towards NewPeakHold

  }

  }

  PropPres[FL]=REFERENCE_PROP_PEAK_HOLD[FL];

  	//assign  PeakHold  to  PropPres
  	PROP_PEAK_HOLD[FL]=TRUE;

  }

  }

  }

  else

  {  //roll angle is<=threshold, so decrement timer

  and assign PropPres to PeakHold

  if (PROP_PEAK_HOLD_TIMER[FL]>1)

  {  //PropHold timer is > 1, therefore hold

  PropPres

  INITIAL_DIVERGENT_OSCILLATION[FL]=FALSE;

  //first divergent oscillation of prop peak hold

  mode has ended PROP_PEAK_HOLD_TIMER[FL]−−;

  //decrement PropHold timer

  if (RAMP_DOWN_TO_NEW_PROP_PEAK[FL])

  {  //ramp down of prior PeakHold to NewPeakHold

  is not completed, continue till done

  REFERENCE_PROP_PEAK_HOLD[FL]−=PROP—

  PEAK_RAMP_DOWN_RATE*LOOP_TIME_SEC;

  // ramp down prior PeakHold to NewPeakHold

  if (REFERENCE_PROP_PEAK_HOLD[FL]<NEW_PROP—

  PEAK_HOLD[FL])

  {  //ramp down of prior PeakHold brings it to

  NewPeakHold level,

  //assign NewPeakHold to PeakHoldREFERENCE—

  PROP_PEAK_HOLD[FL]=NEW_PROP_PEAK_HOLD[FL];

  RAMP_DOWN_TO_NEW_PROP_PEAK[FL]=FALSE; //indicate

  end of ramp down of //PeakHold towards NewPeakHold

  }

  }

  else

  {  //ramp down from old to new PeakHold has

  	ended or was not in effect, so reset New
  	PeakHold stateNEW_PROP_PEAK_HOLD

  [FL]=0;

  }

  if (PropPres[FL]<REFERENCE_PROP_PEAK_HOLD[FL])

  {  //overwrite decreasing PropPres with PeakHold

  during peak hold mode PropPres[FL]=REFERENCE_PROP—

  PEAK_HOLD[FL];PROP_PEAK_HOLD[FL]=TRUE;

  }

  else

  	{  //PropPres is higher than PeakHold, allow
  	PropPres increase above PeakHold by
  	PROP_PEAK_HOLD[FL]=FALSE;

  //exiting prop hold mode and keeping upstream

  PropPres

  }

  }

  else //PropHold timer<=1, ramp out of prop PeakHold

  if it existed

  //otherwise upstream PropPres value is kept

  unchanged

  {

  if (PROP_PEAK_HOLD_TIMER[FL]==1)

  {  //prop hold mode was in effect, set flag

  indicating ramp down of PeakHold to PropPres

  RAMP_DOWN_PROP_HOLD_TO_PROP_PRES[FL]=TRUE;

  PROP_PEAK_HOLD_TIMER[FL]=0;

  }

  if (RAMP_DOWN_PROP_HOLD_TO_PROP_PRES[FL])

  {  //ramp down of PeakHold to PropPres

  if (REFERENCE_PROP_PEAK_HOLD[FL]>(PropPres[FL]

  +PROP_PEAK_RAMP_DOWN_RATE*LOOP_TIME_SEC))

  {

  REFERENCE_PROP_PEAK_HOLD[FL]−=PROP—

  PEAK_RAMP_DOWN_RATE*LOOP_TIME_SEC;

  //ramp down prior PeakHold to NewPeakHoldPropPres

  [FL]=REFERENCE_PROP_PEAK_HOLD[FL];

  }

  else //PeakHold reached upstream PropPres, end

  ramp down and exit prop hold logic

  {

  REFERENCE_PROP_PEAK_HOLD[FL]=0;

  RAMP_DOWN_PROP_HOLD_TO_PROP_PRES[FL]=FALSE;

  }

  }

  else //ramp down of PeakHold to PropPres has ended,

  or

  {  //roll angle never exceeded threshold,

  therefore REFERENCE_PROP_PEAK_HOLD[FL]=0;

  //reset reference prop peak pressure

  }

  	NEW_PROP_PEAK_HOLD[FL]=0;
  	PROP_PEAK_HOLD[FL]=FALSE;
  	RAMP_DOWN_TO_NEW_PROP_PEAK[FL]=FALSE;

  }

  }

• Referring back to FIG. 9, in[0301]step412 an intermediate sum of the P, D and DD pressures for front left and front right wheels may be obtained as follows:

  	//Calculate current loop's value of P_D_DD sum for

  	front right wheel P_D_DD_Sum [FR]=PropPres[FR]
  	+DrvtvPres[FR]+DDPres[FR];

  //Calculate current loop's value of P_D_DD sum for

  	front left wheel P_D_DD_Sum [FL]=PropPres[FL]
  	+DrvtvPres[FL]+DDPres[FL];

• In[0302]step414 an integral term of the roll stabilizing requested pressures for each front wheel is determined. A deadband, of value INTG_DB, is subtracted from ROLL_SIG_FOR_CONTROL to form the input error signal to the integral pressure term.
• For the integral term, special precaution has to be taken regarding integral windup. Integrator windup is a condition that occurs when the input error signal remains large; which in turn causes the integrator term to grow (wind up) to very large values. Even after the roll angle falls within the target deadband, the integrator term takes an excessively long time to unwind; thus continuing to needlessly command control pressure. In order to avoid this situation, the following steps are applied: Impose an upper and lower bound on the input error signal [ROLL_SIG_FOR_CONTROL—INTG_DB], defined by MAX_INTGRTR_ERROR and MIN_INTGRTR_ERROR respectively. This limits the error term that gets added (integrated) each execution loop and compute an integral pressure term based on this bound input error signal.[0303]
• For left turns (positive roll angle), the integral pressure term for outer (right) front wheel is determined by:[0304]

  	//Compute raw value of Integral error for right
  	wheel IntegralError[FR]=ROLL_SIG_FOR_CONTROL−
  	INTG_DB;
  	//Put bounds on min and max values of the integral
  	error, to prevent integrator windup IntegralError
  	[FR]=LIMIT (IntegralError[FR], ((−1)*MIN_INTGRTR—
  	ERROR), MAX_INTGRTR_ERROR);
  	//Compute cumulative Integrator term IntegPres[FR]=
  	INTGRAL_PRESSR[FR]+(IntegralError[FR]*K_I*LOOP—
  	TIME_SEC);
  	INTGRAL_PRESSR[FR]=IntegPres[FR];
  	//Limit integral term to be as negative as the P,
  	D, DD sum is positive, so as not to delay //a fast
  	ramping positive P+D+DD pressure
  	if ((INTGRAL_PRESSR[FR]<0)&&(P_D_DD_Sum[FR]>0)
  	&&(INTGRAL_PRESSR[FR]<(−P_D_DD_Sum[FR])) )

  INTGRAL_PRESSR[FR]=−P_D_DD_Sum[FR];

  //If both integral pressure and PD sum are

  negative, zero out the integral pressure term

  //so as not to delay total req. pressure from

  	ramping up when the PD sum does become
  	positive

  else if ((INTGRAL_PRESSR[FR]<0)&&(P_D_DD_Sum

  	[FR]<0))INTGRAL_PRESSR[FR]=0;

• For right turns (negative roll angle), the integral pressure term for outer (left) front wheel is determined by:[0305]

  	//Compute raw value of Integral error for right

  	wheel IntegralError[FL]=ROLL_SIG_FOR_CONTROL+
  	INTG_DB;

  //Put bounds on min and max values of the integral

  	error, to prevent integrator windup Integral
  	Error[FL]=LIMIT(IntegralError[FL],((−1)*MAX—
  	INTGRTR_ERROR), MIN_INTGRTR_ERROR);

  //Compute cumulative Integrator term IntegPres[FL]=

  	INTGRAL_PRESSR[FL]−(IntegralError[FR]*
  	K_I*LOOP_TIME_SEC);

  	INTGRAL_PRESSR[FL]=IntegPres[FL];
  	// Limit integral term to be as negative as the P,
  	D, DD sum is positive, so as not to delay
  	// a fast ramping positive P+D+DD pressure
  	if ((INTGRAL_PRESSR[FL]<0)&&(P_D_DD_Sum
  	[FL]>0)&&(INTGRAL_PRESSR[FL]<(−P_D_DD_Sum
  	[FL]))) INTGRAL_PRESSR[FL]=−P_D_DD—
  	Sum[FL];
  	//If both integral pressure and PD sum are
  	negative, zero out the integral pressure term //so
  	as not to delay total req. pressure from ramping up
  	when the PD sum does become positive
  	else if ((INTGRAL_PRESSR[FL]<0)&&(P_D_DD_Sum[FL]<

  	0))INTGRAL_PRESSR[FL]=0;

• In step[0306]416 the ramp down rate of PID requested pressure while PID intervention is active is limited. The hydraulic control unit can release pressure faster than it can build it. So to provide for a more uniform PID pressure request, the ramp down rate of PID pressure is limited to the symmetrical value of the hydraulics build rate. This helps keep a consistent level of slip on the control wheel which in turn reduces possible roll oscillations. This is performed by the following logic:

  for (WheelIndex=FL; WheelIndex<=FR; WheelIndex++)
  {
  //Calculate upstream unlimited delta pressure
  request Raw_DeltaP[WheelIndex]=INTGRAL_PRESSR
  [WheelIndex]+P_D_DD_Sum[WheelIndex]−Z1—
  PID_DD_SUM
  [WheelIndex];
  //Conditions for entering and keeping in ramp down

  	limit logic if (PID_ACTIVE[WheelIndex]
  	&&(((Raw—
  	DeltaP[WheelIndex]<MAX_PRESSURE—
  	DECREASE_TO—
  	ENTER_LMTD_RAMP_DOWN)&&!LIMITED—
  	RAMP_DOWN—
  	RATE_MODE[WheelIndex])

  ||((Raw_DeltaP[WheelIndex]<MIN_PRESSURE—

  INCREASE_TO—

  	STAY_IN_LMTD_RAMP_DOWN)&&LIMITED—
  	RAMP_DOWN—
  	RATE_MODE[WheelIndex])))

  {

  //Set limited ramp down rate mode to true LIMITED—

  	RAMP_DOWN_RATE_MODE
  	[WheelIndex] =TRUE;

  LmtdRampDownRate=LMTD_RAMP—

  DOWN_RATE;

  //If opposite front wheel starts requesting PID

  pressure, override ramp down rate by mirror value

  of max

  //hydraulics build rate if (PID_ACTIVE[CROSS_AXLE—

  WHEEL(WheelIndex)])

  {

  LmtdRampDownRate=MAX_RAMP_DOWN_RATE;

  }

  //calculate delta pressure decrease term for

  current loop, by capping lower limit to

  LmtdRampDownRate

  //Given that the delta will be negative, take the

  maximum of it and the ramp down rate limitLmtd—

  DeltaP_For_RmpDwn[WheelIndex]=max(Raw_DeltaP

  [WheelIndex], LmtdRampDownRate);

  }

  else //Limited ramp down rate mode was not entered

  {

  //Set limited ramp down rate mode to false

  state

  LIMITED_RAMP_DOWN_RATE_MODE[WheelIndex]=FALSE;

  }

  }

• In[0307]step418 the total PID requested pressure of the current loop is determined according to the following four modes:

  for (WheelIndex=FL; WheelIndex<=FR;
  WheelIndex++)
  {

  	//Save P,I,D,DD sum for next
  	loopZ1_PID_DD—

  	SUM[WheelIndex]=P_D_DD—
  	Sum[WheelIndex]+
  	INTGRAL_PRESSR[WheelIndex];

  (1) If in ramp down mode, decrement by limited ramp

  down delta if (LIMITED_RAMP_DOWN—

  RATE_MODE

  [WheelIndex])

  {

  	PIDStblzPres[WheelIndex]=PID—
  	STBLZ_PRES[Wheel

  Index]+Lmtd_DeltaP_For_RmpDwn[WheelIndex];

  }

  (2) If total increasing PID pressure is positive

  and PID control is active, limit pressure increase

  delta to take into account actuator drive limits.

  The limit becomes effective once pressure estimate

  increases by PRESSURE_INCREASE_DELTA_FOR_INFLECTION—

  ADJUST from initial pressure estimate value upon

  activation, then will remain in effect as long as

  pressure estimate remains above the exit threshold

  (EXIT_THRES)

  else if (PID_ACTIVE [WheelIndex]

  	&&((P_D_DD_Sum[WheelIndex]+INTGRAL_PRESSR
  	[WheelIndex])>0)
  	&&((((BRAKE_PRESSR—
  	ESTMT[WheelIndex]−PRES—
  	EST_UPON_PID_INCREASE[WheelIndex])>
  	PRESSURE_INCREASE_DELTA—
  	FOR_INFLECTION_ADJUST)
  	&&(!INITIAL_ADJUST_HAS—
  	OCCURRED[WheelIndex]))

  ||((BRAKE_PRESSR_ESTMT

  [WheelIndex]>EXIT_THRES)

  	&&(INITIAL_ADJUST_HAS—
  	OCCURRED[WheelIndex])))
  	)

  {

  if ((PID_STBLZ_PRES[WheelIndex]+Raw—

  DeltaP[Wheel

  	Index]−BRAKE_PRESSR—
  	ESTMT[WheelIndex])>
  	PRESSURE_OFFSET_DURING—
  	PID_RAMP_UP)

  {

  	PIDStblzPres[WheelIndex]=BRAKE—
  	PRESSR_ESTMT

  	[WheelIndex]+ PRESSURE_OFFSET—
  	DURING_PID—
  	RAMP_UP;

  }

  else

  {

  	PIDStblzPres[WheelIndex]=PID—
  	STBLZ_PRES[Wheel
  	Index]+Raw_DeltaP[WheelIndex];

  }

  	//Logic for detecting initial adjustment of
  	req. pressure towards pressure estimate during
  	ramp up phase
  	if (!INITIAL_ADJUST_TO_PRES—
  	ESTMT [WheelIndex]
  	&&!INITIAL_ADJUST_HAS—
  	OCCURRED[WheelIndex])
  	{

  	INITIAL_ADJUST_TO_PRES—
  	ESTMT [WheelIndex]=
  	TRUE;
  	INITIAL_ADJUST_HAS—
  	OCCURRED[WheelIndex]=
  	TRUE;

  	}
  	//Set INITIAL_ADJUST_TO_PRES—
  	ESTMT flag for
  	only one loop's duration per activation cycle

  else

  	INITIAL_ADJUST_TO_PRES—
  	ESTMT [Wheel
  	Index]=FALSE;

  }

  (3)If total increasing PID pressure is positive and

  PID control is active, but pressure estimate has

  not yet increased over the activation pressure

  estimate by PRESSURE_INCREASE_DELTA_FOR_INFLECTION—

  ADJUST, assign total PID pressure to prior total

  plus the upstream unlimited delta pressure

  increase.

  else if (PID_ACTIVE [WheelIndex]

  &&((P_D_DD_Sum

  [WheelIndex]+INTGRAL—

  PRESSR[WheelIndex])>0))

  {

  	PIDStblzPres[WheelIndex]=PID—
  	STBLZ_PRES[Wheel
  	Index]+Raw—
  	DeltaP[WheelIndex];

  }

  (4) If PID control is active but underlying P,I,D,DD

  pressure sum is negative, OR PID is not active, the

  total PID pressure is assigned to the underlying

  P,I,D,DD pressure sum.

  else

  	PIDStblzPres[WheelIndex]=P—
  	D_DD_Sum[Wheel
  	Index]+INTGRAL—
  	PRESSR[WheelIndex];
  	PIDStblzPres[WheelIndex]=LIMIT
  	(PIDStblzPres
  	[WheelIndex], 0, MAXIMUM—
  	STBLZ_PRESSURE);

  }   /*End for loop*/

• The PID control entrance and exit strategy is performed in[0308]step420. A history of vehicle lateral acceleration exceeding a given large threshold is kept to be used as a screening criteria for PID activation is performed.

  if (ABS(CG_FLT_LAT_ACC)>LAT_ACC_ACTVTION_THRSHLD)

  	LARGE_LAT_ACC_COUNTER=LAT_ACC—
  	COUNTER_INIT;

  else if (LARGE_LAT_ACC_COUNTER>0)

  	LARGE_LAT_ACC_COUNTER--;

• PID control is enabled in the following.[0309]

  if ((LARGE_LAT_ACC_COUNTER>0)

  	// Large lat acc or recent history of large
  	lat acc
  	&&((REF_VELOCITY_YC>PID_MINIMUM_ACTIVATION—
  	SPEED)||

  	((PID_ACTIVE [FL]||PID_ACTIVE[FR])&&
  	(REF_VELOCITY_YC>MAXIMUM_SPEED_TO—
  	CONTINUE_PID))

  )

  	&&(!RSC_DISABLED)	//RSC system is enabled,
  	no shutdowns exist

  &&(!REVERSE_MOVEMENT)

  //Allow activation

  only going forward

  &&(!STATUS_FIRST_RUN)

  //Allow activation

  only after first run becomes false

  )

  EnablePIDControl=TRUE;

  else

  	EnablePIDControl=FALSE;

• Activating/deactivating individual wheel PID control, figuring in Driver Brake Apply is determined in[0310]step422. This is set forth in the following code:

  	for (WheelIndex=FL; WheelIndex<=FR;
  	WheelIndex++)
  	{

  	if (PID_ACTIVE [WheelIndex])
  	{  //PID control already active on wheel,
  	check for existence of de-activation
  	conditions
  	if (!EnablePIDControl||

  	//Enforce exit when PID pressure
  	goes below 9 bar(PIDStblzPres
  	[WheelIndex]<=MIN—
  	PID_PRES_FOR—
  	FORCED_CONTROL_EXIT)||
  	//Once PID control pressure gets
  	within ˜10 bar of driver pressure
  	AND ((PIDStblzPres[WheelIndex]<
  	(DRIVER_REQ_PRESSURE+
  	EXIT_THRES))
  	&& //PID control pressure is less
  	than or equal to wheel pressure
  	estimate (in case pressure build
  	//is in a slow build mode and thus
  	not reflecting driver pressure) AND
  	*/(PIDStblzPres[WheelIndex]<=
  	(BRAKE—
  	PRESSR_ESTMT[WheelIndex]))
  	&&
  	//wheel slip ratio is greater than˜
  	−15% to indicate appropriateness for
  	ABShandoff */(SLIP_RATIO
  	[WheelIndex]>=
  	WHEEL_STABLE_IN_SLIP)))

  {

  PID_ACTIVE[WheelIndex]=FALSE;

  INTGRAL_PRESSR[WheelIndex]=0;

  //Reset key

  state variables

  	PRES_EST_UPON_PID_INCREASE
  	[WheelIndex]=0;
  	REFERENCE_PROP_PEAK_HOLD
  	[WheelIndex]=0;
  	PROP PEAK_HOLD_TIMER
  	[WheelIndex]=0;
  	RAMP_DOWN_PROP_HOLD_TO—
  	PROP_PRES[WheelIndex]=
  	FALSE;

• If driver is braking upon PID exit, a flag is set to desensitize PID re-entry[0311]

  if (DRIVER_BRAKING_FLAG)

  EXIT_PID_DURING_DRIVER_BRAK[WheelIndex]=TRUE;

  else

  EXIT_PID_DURING_DRIVER_BRAK[WheelIndex]=FALSE;

  }

  }    //End PID_ACTIVE==TRUE

  else	//PID control not active on wheel, check

  if conditions exist for activation

  	{
  	//reset initial PID pressure adjust (toward
  	pressure estimate) flag for next PID
  	activation
  	INITIAL_ADJUST_HAS_OCCURRED[WheelIndex]=FALSE;
  	//Keep forcing prop peak hold exit until PID
  	reactivation by resetting key state variables
  	PROP_PEAK_HOLD_TIMER[WheelIndex]=0;
  	REFERENCE_PROP_PEAK_HOLD[WheelIndex]=0;
  	RAMP_DOWN_PROP_HOLD_TO_PROP_PRES[WheelIndex]=
  	FALSE;
  	//If driver is no longer braking, allow PID
  	entry at entrance threshold
  	if (!DRIVER_BRAKING_FLAG)
  	{

  	EXIT_PID_DURING_DRIVER_BRAK[WheelIndex]=
  	FALSE;

  	}
  	if ((//If driver is no longer braking OR
  	driver is braking but PID intervention had not
  	//been called for yet, allow PID entry at
  	entrance threshold
  	((PIDStblzPres[WheelIndex]>=ENTER_THRES)&&
  	(!EXIT_PID_DURING_DRIVER_BRAK[WheelIndex]))
  	//If PID recently exit due to driver braking
  	and driver is still braking, allow PID
  	intervention once
  	//PID pressure exceeds pressure estimate plus
  	a threshold, to provide for hysteresis
  	||(EXIT_PID_DURING_DRIVER_BRAK[WheelIndex]&&
  	(PIDStblzPres[WheelIndex]>=ENTER_THRES)

  	&&(PIDStblzPres[WheelIndex]>=(BRAKE—
  	PRESSR_ESTMT[WheelIndex]+EXIT_THRES))

  	//Can also enter at lower threshold if had
  	recent PID event and driver is not braking
  	||((PIDStblzPres[WheelIndex]>=EXIT_THRES)&&REC
  	ENT_PID_CTRL&&(!DRIVER_BRAKING_FLAG))
  	)&&EnablePIDControl
  	)

  {

  	PID_ACTIVE[WheelIndex]=TRUE;
  	//Latch pressure estimate at PID activation,
  	for use in PID pressure adjustment toward
  	estimate during ramp up phase

  PRES_EST_UPON_PID_INCREASE[WheelIndex]=

  	BRAKE_PRESSR_ESTMT[WheelIndex];
  	//If driver is braking, include the minimum of
  	driver pressure or pressure estimate into the
  	PID pressure state

  PIDStblzPres[WheelIndex]+=min(DRIVER_REQ—

  	PRESSURE, BRAKE_PRESSR_ESTMT[WheelIndex]);
  	//Put an upper and lower bound on the final
  	PID requested pressure value

  PIDStblzPres[WheelIndex]=LIMIT(PIDStblz

  	Pres[WheelIndex], 0, MAXIMUM_STBLZ_PRESSURE);
  	}

  }

• The PID pressure is then applied to the brake system to prevent the vehicle from rolling over. The change in the current loop's delta requested pressure is also determined.[0312]

  	DeltaPIDStblzPres[WheelIndex]=PIDStblzPres

  [WheelIndex]-PID_STBLZ_PRES[WheelIndex];

  //Update INCREASE_REQUESTED_PRESSURE flag

  based on previous loop's delta pressure value

  if ((DELTA_PID_STBLZ_PRES[WheelIndex]>=0)

  //Do not set flag when req pressure

  is less than enter threshold value

  	&&(PIDStblzPres[WheelIndex]>ENTER—
  	THRES)

  )

  	INCREASE_REQUESTED_PRESSURE[Wheel
  	Index]=TRUE;

  else

  INCREASE_REQUESTED_PRESSURE_[Wheel

  	Index]=FALSE;

• Global variables with local versions are updated in[0313]step426.

  	PID_STBLZ_PRES[WheelIndex]=PIDStblzPres[Wheel
  	Index];
  	DELTA_PID_STBLZ_PRES[WheelIndex]=DeltaPIDStblzPres
  	[WheelIndex];

  	}	/*End for loop*/

• PID requested pressure if corresponding flag is false is set to zero in the following:[0314]

  	if (!PID_ACTIVE[FL])PID_STBLZ_PRES[FL]=0;
  	if (!PID_ACTIVE[FR])PID_STBLZ_PRES[FR]=0;

• A history of when the last PID control is kept in the following:[0315]

  if (PID_ACTIVE [FL]||PID_ACTIVE[FR])
  RECENT_PID_EVNT—

  CNTR=RECENT_PID_EVNT_THRSHLD;

  else if (RECENT_PID_EVNT_CNTR>0)RECENT_PID_EVNT—

  CNTR−−;

  if (RECENT_PID_EVNT_CNTR>0)RECENT—

  PID_CNTRL_EVENT=

  TRUE;

  else

  	RECENT_PID_CNTRL_EVENT=FALSE;

• A history of when last in Active Yaw Control is also kept in the following:[0316]

  if
  (AYC_IN_CYCLE)RECENT_AYC_EVNT_CNTR=

  RECENT_AYC_EVNT_THRSHLD;

  else if (RECENT_AYC_EVNT_CNTR>0)RECENT_AYC_EVNT—

  CNTR−−;

  if (RECENT_AYC_EVNT_CNTR>0)RECENT_AYC—

  CNTRL_EVENT=TRUE;

  else

  	RECENT_AYC_CNTRL_EVENT=FALSE;

• While the invention has been described in connection with one or more embodiments, it should be understood that the invention is not limited to those embodiments. On the contrary, the invention is intended to cover all alternatives, modifications, and equivalents, as may be included within the spirit and scope of the appended claims.[0317]

Claims (23)

What is claimed is:

1. A system for controlling a safety system of an automotive vehicle comprising:

a first controller generating a first control signal;

a second controller generating a second control signal;

an arbitration module coupled to the first controller and the second controller, said arbitration module choosing the higher of the first control signal and the second control signal to a final control signal; and

the safety system coupled to the arbitration module, said safety system operated corresponding to the final control signal.

2. A system as recited inclaim 1 wherein the first controller comprises a transition controller.

3. A system as recited inclaim 1 wherein the second controller comprises a proportional-derivative controller.

4. A system as recited inclaim 1 wherein the second controller comprises a proportional-integral derivative controller.

5. A system as recited inclaim 1 wherein the second controller comprises a proportional-integral-derivative-double derivative controller.

6. A system as recited inclaim 1 wherein the first signal and the second control signal comprise pressure signals.

7. A system as recited inclaim 1 wherein the first signal and the second control signal comprise pressure request signals.

8. A system as recited inclaim 1 wherein the safety system comprises a rollover control system.

9. A system of operating a rollover control system of an automotive vehicle comprising:

a first controller generating a first pressure control signal;

a second controller generating a second pressure control signal;

an arbitration module coupled to the first controller and the second controller, said arbitration module choosing the higher of the first pressure control signal and the second pressure control signal to a final pressure control signal; and

the safety system coupled to the arbitration module, said safety system operated with the final pressure control signal.

10. A system as recited inclaim 9 wherein the first controller comprises a transition controller.

11. A system as recited inclaim 9 wherein the second controller comprises a proportional-derivative controller.

12. A system as recited inclaim 9 wherein the second controller comprises a proportional-integral derivative controller.

13. A system as recited inclaim 9 wherein the second controller comprises a proportional-integral-derivative-double derivative controller.

14. A system as recited inclaim 9 wherein the first signal and the second control signal comprises pressure signals.

15. A system as recited inclaim 9 wherein the first signal and the second control signal comprise pressure request signals.

16. A system as recited inclaim 9 wherein the safety system comprises a rollover control system.

17. A method of controlling a hydraulic safety system of an automotive vehicle comprising:

determining an angular vehicle position;

in a first controller generating a first control signal; and

when the angular position is greater than a threshold, generating a second control signal from a second controller.

18. A method as recited inclaim 17 wherein the threshold corresponds substantially to a linear region and non-linear region.

19. A method as recited inclaim 17 wherein the angular vehicle position comprises a roll angle.

20. A method as recited inclaim 17 wherein the angular position corresponds to two-wheel lift.

21. A method as recited inclaim 17 wherein angular position is inferred by a requested PID signal.

22. A method of operating a safety system in an automotive vehicle comprising:

in a non-divergent region of dynamics of the vehicle, operating the safety system with a transition controller; and

in a divergent region of dynamics of the vehicle, operating the safety system with a proportional-derivative controller.

23. A method as recited inclaim 22 wherein the proportional-derivative controller comprises a PID controller.

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