US20110219787A1 - Variable pid enable for compressor control algorithm - Google Patents
Variable pid enable for compressor control algorithmDownload PDFInfo
- Publication number
- US20110219787A1 US20110219787A1US12/723,887US72388710AUS2011219787A1US 20110219787 A1US20110219787 A1US 20110219787A1US 72388710 AUS72388710 AUS 72388710AUS 2011219787 A1US2011219787 A1US 2011219787A1
- Authority
- US
- United States
- Prior art keywords
- evaporator temperature
- operating condition
- actual
- temperature
- initial
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 238000000034methodMethods0.000claimsdescription19
- 230000000977initiatory effectEffects0.000claimsdescription3
- 238000013459approachMethods0.000description1
- 238000001816coolingMethods0.000description1
- 238000012937correctionMethods0.000description1
- 238000010438heat treatmentMethods0.000description1
- 238000012986modificationMethods0.000description1
- 230000004048modificationEffects0.000description1
Images
Classifications
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3205—Control means therefor
- B60H1/3216—Control means therefor for improving a change in operation duty of a compressor in a vehicle
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/025—Motor control arrangements
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3236—Cooling devices information from a variable is obtained
- B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
- B60H2001/3261—Cooling devices information from a variable is obtained related to temperature of the air at an evaporating unit
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3269—Cooling devices output of a control signal
- B60H2001/327—Cooling devices output of a control signal related to a compressing unit
- B60H2001/3272—Cooling devices output of a control signal related to a compressing unit to control the revolving speed of a compressor
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
Definitions
- the present disclosureis directed to control systems, and more specifically to a proportional integral derivative (PID) evaporator temperature control scheme.
- PIDproportional integral derivative
- compressorsare used to control an evaporator temperature and thereby allow for heating and cooling.
- the evaporator temperatureis typically adjusted by changing the compressor speed.
- electrical control systemsare used. It is known in the art to use a proportional integral derivative (PID) control scheme on a micro-controller to control these systems.
- PID controllerwill have an input of the current temperature of the evaporator and the current speed of the compressor. The PID controller then attempts to drive the evaporator temperature to a desired temperature by making corresponding adjustments to the compressor speed.
- Adjusting the compressor speed at a set frequencyentails operating the control algorithm at the specific time interval regardless of any change in the actual temperature of the evaporator. Once the evaporator temperature has reached approximately the desired temperature minor fluctuations in temperature can occur with the evaporator temperature remaining within acceptable tolerances. Running the control scheme, and adjusting the compressor speed, consistently at the desired frequency can therefore result in unnecessary adjustments to the compressor speed, and unneeded use of electrical power.
- a control system for operating a compressorthat establishes an initial condition, detects changes in the initial condition, and operates a controller when the changes in the initial condition exceed a predetermined maximum value. The controller then establishes a new initial condition and continues to detect changes from the new initial condition.
- a control scheme for controlling a compressor speedwhich establishes a target evaporator temperature and an initial evaporator temperature.
- the methoddetects the actual temperature of the evaporator and compares it to a previous sensed evaporator temperature to determine a change in evaporator temperature since the last iteration of the control signal.
- the methodalso detects the actual evaporator temperature and compares the actual temperature with the target temperature to determine a difference between the actual temperature and the target temperature.
- the difference between the actual temperature and the target temperatureis used to initiate operation of a control algorithm whenever the change in temperature exceeds the predetermined value. Initiating operation when the temperature change exceeds a predetermined value provides for actuation of the control algorithm to adjust the speed of the compressor only when required to obtain a desired temperature.
- FIG. 1schematically illustrates a vehicle which has a compressor, evaporator, and a compressor controller.
- FIG. 2illustrates a block flowchart of a compressor control system using a proportional integral derivative controller (PID controller).
- PID controllerproportional integral derivative controller
- FIG. 3illustrates a block flowchart of a compressor control system with an additional ⁇ t check block.
- FIG. 4illustrates a sample graph of an evaporator temperature over time.
- FIG. 1schematically illustrates a vehicle 10 which has a compressor 20 and an evaporator 30 located in the front engine compartment.
- the evaporator 30 and the compressor 20are controlled by an on-board electronic controller 40 which is capable of adjusting the speed of the compressor 20 and thereby adjusting the temperature of the evaporator 30 .
- the controller 40can be a micro-processor located within the standard control system of the vehicle, or any other type of controller.
- the example compressor 20is controlled by a proportional integral derivative (PID) control scheme.
- PIDproportional integral derivative
- FIG. 2illustrates a flowchart of a control scheme 100 for controlling an evaporator temperature 114 by adjusting the compressor speed 118 .
- a target evaporator temperature 110is either input into the system 100 , or manufactured into the controller 40 operating the control scheme 110 .
- a summation block 112subtracts an actual evaporator temperature 114 from the target temperature 110 , and transfers the resultant value into a PID controller 116 .
- the PID controller 116also accepts an input of an actual compressor speed 118 which is determined by a compressor speed sensor 120 .
- the PID controller 116performs a control cycle, it outputs a command 122 which pushes the compressor 124 toward the desired compressor speed 118 .
- the compressor speed 118affects the evaporator temperature 114 in a predictable manner. For example, an increase in compressor speed causes a change in evaporator temperature in one direction, and a decrease in evaporator speed will cause a temperature movement in the other direction.
- the evaporator temperature 114is sensed by a sensor 128 , which outputs the evaporator temperature 114 .
- the example control system shown in FIG. 2includes a condition check within the evaporator temperature block 114 .
- the condition checkevaluates a specific condition, such as evaporator temperature, and determines how much the condition has changed since the last control cycle.
- a control cycleis a single iteration of the control scheme 100 which determines an adjustment to the compressor speed using the control scheme 100 . If the change in condition exceeds a predefined amount, a control cycle is performed.
- the control system 100utilizes a double feedback loop, in that it uses the current evaporator temperature 114 compared with the target evaporator temperature 110 as one input into the PID controller 116 .
- the control scheme 100also utilizes the current compressor speed 118 as a second input into the PID controller 116 .
- the feedback loopsensure that as the temperature of the evaporator approaches that of the desired target temperature 110 , a progressively smaller input is sent to the PID controller 116 , thereby causing the PID controller 116 to perform a smaller adjustment to the compressor speed 118 .
- FIG. 3illustrates the example control system 100 of FIG. 1 , with a separate ⁇ t check block 210 .
- ⁇ trepresents the difference between the current evaporator temperature 114 and the evaporator temperature 114 from the previous evaporator temperature data reading from the evaporator temperature sensor.
- the ⁇ t check block 210prevents the PID controller 116 from operating whenever ⁇ t is below a predetermined value. This allows the PID controller 210 to recalculate a desired compressor speed 122 only when a speed correction is necessary.
- the ⁇ t check block 210Each time the ⁇ t check block 210 passes a value to the summation block 112 , it also stores that value as an “initial value.” The initial value is then compared to the incoming sensed evaporator temperature 114 to determine the ⁇ t value. When the ⁇ t value exceeds a predetermined ⁇ t value, the ⁇ t check block 210 passes the current evaporator temperature 114 to the summation block 112 , and the PID controller 116 operates a control iteration.
- a timing component 220can be utilized to prompt operation of a control iteration, in addition to a change in condition prompting the control cycle, as is indicated in the ⁇ t check block 210 .
- the timing component 220determines how much time has passed since a value has been passed to the summation block 112 . If a predetermined maximum time has elapsed, the actual evaporator temperature 114 is passed to the summation block 112 regardless of the ⁇ t value. By way of example, the maximum time could be set to three minutes, thereby ensuring that the control scheme is operated at least every three minutes. This allows the control system 100 to make minor necessary adjustments to the compressor speed 118 , without constant unnecessary adjustments to the compressor speed 118 .
- Illustrated in FIG. 4is a sample graph 300 of evaporator temperature control operations using the above described system.
- the line 310represents the temperature of the evaporator over time
- the axis 312represents temperature
- the axis 314represents time.
- Each of the bars 316represent a control cycle which is run by the controller. Since the controller uses the ⁇ t value to determine when to operate a control cycle, that is the control cycle is only run when ⁇ t is greater than a certain number, the bars are closer together at the beginning of the time period when the temperature is changing at the fastest rate. As the time progresses and the temperature changes at a slower rate, the ⁇ t minimum is not exceeded for longer periods, and the control cycles 316 are spaced farther apart.
- the evaporator temperature 310has reached the desired temperature line 318 .
- the example system illustrated hereincludes the optional maximum time element described above, and as such the latest three control cycles 316 are evenly distributed and were initiated because a maximum time had elapsed since the last control cycle 316 .
- An example of the above described systemuses the control scheme to drive an evaporator temperature to a desired value by adjusting a compressor speed.
- the systeminitially detects an actual evaporator temperature when it is first turned on, and this temperature is set as the initial operating condition.
- the control systemthen polls the evaporator temperature and compares actual temperatures to the initial operating condition. When the difference between the two values exceeds a predefined amount, the control scheme operates one cycle of the PID controller.
- the PID controlleraccepts the evaporator temperature as a control input and determines an adjustment to the compressor speed which is necessary to drive the evaporator temperature to the desired value.
- the controllerthen resets the “initial operating condition” to be the actual operating condition at the start of the control cycle, and the system returns to polling the actual evaporator temperature.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Feedback Control In General (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Description
- The present disclosure is directed to control systems, and more specifically to a proportional integral derivative (PID) evaporator temperature control scheme.
- In the automotive field, as well as other fields, compressors are used to control an evaporator temperature and thereby allow for heating and cooling. The evaporator temperature is typically adjusted by changing the compressor speed. In order to ensure that the compressor is operated at the proper speed for a desired evaporator temperature, electrical control systems are used. It is known in the art to use a proportional integral derivative (PID) control scheme on a micro-controller to control these systems. Typically the PID controller will have an input of the current temperature of the evaporator and the current speed of the compressor. The PID controller then attempts to drive the evaporator temperature to a desired temperature by making corresponding adjustments to the compressor speed.
- Current control systems determine adjustments to the compressor speed at a set frequency. By way of example, some control algorithms recalculate the needed compressor speed every 8 seconds, or at some desired time interval. Adjusting the compressor speed at a set frequency entails operating the control algorithm at the specific time interval regardless of any change in the actual temperature of the evaporator. Once the evaporator temperature has reached approximately the desired temperature minor fluctuations in temperature can occur with the evaporator temperature remaining within acceptable tolerances. Running the control scheme, and adjusting the compressor speed, consistently at the desired frequency can therefore result in unnecessary adjustments to the compressor speed, and unneeded use of electrical power.
- Disclosed is a control system for operating a compressor that establishes an initial condition, detects changes in the initial condition, and operates a controller when the changes in the initial condition exceed a predetermined maximum value. The controller then establishes a new initial condition and continues to detect changes from the new initial condition.
- Additionally disclosed is a control scheme for controlling a compressor speed which establishes a target evaporator temperature and an initial evaporator temperature. The method detects the actual temperature of the evaporator and compares it to a previous sensed evaporator temperature to determine a change in evaporator temperature since the last iteration of the control signal. The method also detects the actual evaporator temperature and compares the actual temperature with the target temperature to determine a difference between the actual temperature and the target temperature. The difference between the actual temperature and the target temperature is used to initiate operation of a control algorithm whenever the change in temperature exceeds the predetermined value. Initiating operation when the temperature change exceeds a predetermined value provides for actuation of the control algorithm to adjust the speed of the compressor only when required to obtain a desired temperature.
- These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
FIG. 1 schematically illustrates a vehicle which has a compressor, evaporator, and a compressor controller.FIG. 2 illustrates a block flowchart of a compressor control system using a proportional integral derivative controller (PID controller).FIG. 3 illustrates a block flowchart of a compressor control system with an additional Δt check block.FIG. 4 illustrates a sample graph of an evaporator temperature over time.FIG. 1 schematically illustrates avehicle 10 which has acompressor 20 and anevaporator 30 located in the front engine compartment. Theevaporator 30 and thecompressor 20 are controlled by an on-boardelectronic controller 40 which is capable of adjusting the speed of thecompressor 20 and thereby adjusting the temperature of theevaporator 30. Thecontroller 40 can be a micro-processor located within the standard control system of the vehicle, or any other type of controller. Theexample compressor 20 is controlled by a proportional integral derivative (PID) control scheme.FIG. 2 illustrates a flowchart of acontrol scheme 100 for controlling anevaporator temperature 114 by adjusting thecompressor speed 118. Initially atarget evaporator temperature 110 is either input into thesystem 100, or manufactured into thecontroller 40 operating thecontrol scheme 110. Asummation block 112 subtracts anactual evaporator temperature 114 from thetarget temperature 110, and transfers the resultant value into aPID controller 116. ThePID controller 116 also accepts an input of anactual compressor speed 118 which is determined by acompressor speed sensor 120. When thePID controller 116 performs a control cycle, it outputs acommand 122 which pushes thecompressor 124 toward the desiredcompressor speed 118. Thecompressor speed 118 affects theevaporator temperature 114 in a predictable manner. For example, an increase in compressor speed causes a change in evaporator temperature in one direction, and a decrease in evaporator speed will cause a temperature movement in the other direction.- The
evaporator temperature 114 is sensed by asensor 128, which outputs theevaporator temperature 114. The example control system shown inFIG. 2 includes a condition check within theevaporator temperature block 114. The condition check evaluates a specific condition, such as evaporator temperature, and determines how much the condition has changed since the last control cycle. A control cycle is a single iteration of thecontrol scheme 100 which determines an adjustment to the compressor speed using thecontrol scheme 100. If the change in condition exceeds a predefined amount, a control cycle is performed. - The
control system 100, utilizes a double feedback loop, in that it uses thecurrent evaporator temperature 114 compared with thetarget evaporator temperature 110 as one input into thePID controller 116. Thecontrol scheme 100 also utilizes thecurrent compressor speed 118 as a second input into thePID controller 116. The feedback loops ensure that as the temperature of the evaporator approaches that of the desiredtarget temperature 110, a progressively smaller input is sent to thePID controller 116, thereby causing thePID controller 116 to perform a smaller adjustment to thecompressor speed 118. FIG. 3 illustrates theexample control system 100 ofFIG. 1 , with a separateΔt check block 210. Δt represents the difference between thecurrent evaporator temperature 114 and theevaporator temperature 114 from the previous evaporator temperature data reading from the evaporator temperature sensor. TheΔt check block 210 prevents thePID controller 116 from operating whenever Δt is below a predetermined value. This allows thePID controller 210 to recalculate a desiredcompressor speed 122 only when a speed correction is necessary. Each time theΔt check block 210 passes a value to thesummation block 112, it also stores that value as an “initial value.” The initial value is then compared to the incoming sensedevaporator temperature 114 to determine the Δt value. When the Δt value exceeds a predetermined Δt value, theΔt check block 210 passes thecurrent evaporator temperature 114 to thesummation block 112, and thePID controller 116 operates a control iteration.- Alternatively, a
timing component 220 can be utilized to prompt operation of a control iteration, in addition to a change in condition prompting the control cycle, as is indicated in theΔt check block 210. Thetiming component 220 determines how much time has passed since a value has been passed to thesummation block 112. If a predetermined maximum time has elapsed, theactual evaporator temperature 114 is passed to thesummation block 112 regardless of the Δt value. By way of example, the maximum time could be set to three minutes, thereby ensuring that the control scheme is operated at least every three minutes. This allows thecontrol system 100 to make minor necessary adjustments to thecompressor speed 118, without constant unnecessary adjustments to thecompressor speed 118. - Illustrated in
FIG. 4 is asample graph 300 of evaporator temperature control operations using the above described system. In thegraph 300, the line310 represents the temperature of the evaporator over time, theaxis 312 represents temperature, and theaxis 314 represents time. Each of thebars 316 represent a control cycle which is run by the controller. Since the controller uses the Δt value to determine when to operate a control cycle, that is the control cycle is only run when Δt is greater than a certain number, the bars are closer together at the beginning of the time period when the temperature is changing at the fastest rate. As the time progresses and the temperature changes at a slower rate, the Δt minimum is not exceeded for longer periods, and thecontrol cycles 316 are spaced farther apart. By the end of the time period the evaporator temperature310 has reached the desiredtemperature line 318. The example system illustrated here includes the optional maximum time element described above, and as such the latest threecontrol cycles 316 are evenly distributed and were initiated because a maximum time had elapsed since thelast control cycle 316. - An example of the above described system uses the control scheme to drive an evaporator temperature to a desired value by adjusting a compressor speed. The system initially detects an actual evaporator temperature when it is first turned on, and this temperature is set as the initial operating condition. The control system then polls the evaporator temperature and compares actual temperatures to the initial operating condition. When the difference between the two values exceeds a predefined amount, the control scheme operates one cycle of the PID controller. The PID controller accepts the evaporator temperature as a control input and determines an adjustment to the compressor speed which is necessary to drive the evaporator temperature to the desired value. The controller then resets the “initial operating condition” to be the actual operating condition at the start of the control cycle, and the system returns to polling the actual evaporator temperature.
- Although an example embodiment has been disclosed, a worker of ordinary skill in this art would recognize that certain modifications would come within the scope of this invention. For that reason, the following claims should be studied to determine the true scope and content of this invention.
Claims (17)
1. A method for operating a control scheme comprising the steps of:
a controller establishing a desired output condition of a controlled system, and an initial operating condition of said controlled system;
said controller detecting an actual operating condition of said controlled system and determining a difference between said initial operating condition and said actual operating condition;
said controller initiating a control cycle when a magnitude of said difference between said initial operating condition and said actual operating condition exceeds a predetermined value; and
said controller establishing a new initial operating condition based on said actual operating condition.
2. The method ofclaim 1 , wherein said control system comprises a proportional integral derivative (PID) control scheme.
3. The method ofclaim 2 , wherein said step of said controller initiating a control cycle when a magnitude of said difference between said initial operating condition and said actual operating condition exceeds a predetermined value comprises operating said PID control scheme when a preset time has elapsed and said difference between said initial operating condition and said actual operating condition is less than or equal to said predetermined value.
4. The method ofclaim 2 , wherein said initial operating condition comprises an evaporator temperature.
5. The method ofclaim 4 , wherein said step of said controller detecting an actual operating condition of said controlled system and determining a difference between said initial operating condition and said actual operating condition comprises sensing an evaporator temperature, comparing said sensed evaporator temperature to an initial evaporator temperature, and determining a difference between said sensed evaporator temperature and said initial evaporator temperature.
6. The method ofclaim 1 , wherein said step of a controller establishing a desired output condition of a controlled system, and an initial operating condition of said controlled system further comprises storing said initial operating condition in a memory component of said controller.
7. The method ofclaim 6 , wherein said step of said controller establishing a new initial operating condition based on said actual operating condition comprises sensing an actual condition of a component and overwriting a currently stored initial condition with said sensed actual condition.
8. The method ofclaim 1 , wherein said step of said controller detecting an actual operating condition of said controlled system and determining a difference between said initial operating condition and said actual operating condition comprises sensing a component at an established frequency, thereby determining a current value of said actual operating condition.
9. The method ofclaim 8 , wherein said step of said controller detecting an actual operating condition of said controlled system and determining a difference between said initial operating condition and said actual operating condition further comprises comparing said current value of said actual operating condition to said initial operating condition value, thereby determining a change in said operating condition.
10. The method ofclaim 9 , further comprising the step of comparing said change in said operating condition to said predetermined value.
11. A method for controlling compressor speed comprising the steps of;
establishing a target evaporator temperature and a minimum change in an actual temperature;
establishing an initial evaporator temperature value;
determining an actual evaporator temperature;
determining a change in evaporator temperature based on said actual evaporator temperature and said initial evaporator temperature;
comparing an actual evaporator temperature with said target evaporator temperature and determining a difference between said actual evaporator temperature and said target evaporator temperature;
inputting said difference between said actual evaporator temperature and said target evaporator temperature into a control algorithm when said change in evaporator temperature exceeds said minimum change in temperature, thereby operating a control cycle; and
adjusting a compressor speed based on an output of said control cycle.
12. The method ofclaim 11 , further comprising the step of establishing a maximum time between control cycles.
13. The method for controlling a compressor speed ofclaim 11 , wherein said step of inputting said difference between said actual evaporator temperature and said target evaporator temperature into a control algorithm when said change in evaporator temperature exceeds said minimum change in temperature further comprises inputting said difference between said actual evaporator temperature and said target evaporator temperature into a control algorithm when said change in evaporator temperature has not exceeded said minimum change in temperature and a maximum time has elapsed.
14. The method ofclaim 11 , wherein said control algorithm comprises a Proportional Integral Derivative (PID) control system
15. The method ofclaim 11 , further comprising the step of determining a target or desired compressor speed.
16. The method ofclaim 15 , wherein said step of inputting said difference between said actual evaporator temperature and said target evaporator temperature into a control algorithm when said change in evaporator temperature exceeds said minimum change in temperature further comprises inputting an actual compressor speed into said control algorithm.
17. The method ofclaim 1 , wherein said step of inputting said difference between said actual evaporator temperature and said target evaporator temperature into a control algorithm when said change in evaporator temperature exceeds said minimum change in temperature further comprises resetting said initial evaporator temperature to said actual evaporator temperature.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US12/723,887US20110219787A1 (en) | 2010-03-15 | 2010-03-15 | Variable pid enable for compressor control algorithm |
| US14/286,490US9920968B2 (en) | 2010-03-15 | 2014-05-23 | Variable PID enable for compressor control algorithm |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US12/723,887US20110219787A1 (en) | 2010-03-15 | 2010-03-15 | Variable pid enable for compressor control algorithm |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| US14/286,490ContinuationUS9920968B2 (en) | 2010-03-15 | 2014-05-23 | Variable PID enable for compressor control algorithm |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| US20110219787A1true US20110219787A1 (en) | 2011-09-15 |
Family
ID=44558625
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| US12/723,887AbandonedUS20110219787A1 (en) | 2010-03-15 | 2010-03-15 | Variable pid enable for compressor control algorithm |
| US14/286,490Active2031-06-22US9920968B2 (en) | 2010-03-15 | 2014-05-23 | Variable PID enable for compressor control algorithm |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| US14/286,490Active2031-06-22US9920968B2 (en) | 2010-03-15 | 2014-05-23 | Variable PID enable for compressor control algorithm |
Country Status (1)
| Country | Link |
|---|---|
| US (2) | US20110219787A1 (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20130074537A1 (en)* | 2011-09-23 | 2013-03-28 | Ford Global Technologies, Llc | Method for operating a vehicle climate control system |
| FR2996498A1 (en)* | 2012-10-08 | 2014-04-11 | Renault Sa | System for controlling air-conditioned compressor of car, has physical parameter regulation unit connected to output of temperature regulation unit and determining rotational speed of compressor with respect to measurement of parameter |
| CN108891230A (en)* | 2018-07-26 | 2018-11-27 | 延锋伟世通电子科技（南京）有限公司 | PID+FF feedforward closed loop control method based on pure electric automobile motor compressor |
| CN109017215A (en)* | 2018-07-26 | 2018-12-18 | 延锋伟世通电子科技（南京）有限公司 | PID+FF feedforward closed loop control method based on pure electric automobile PTC |
| US10215436B1 (en)* | 2011-05-02 | 2019-02-26 | John M. Rawski | Full spectrum universal controller |
| WO2019141845A1 (en)* | 2018-01-22 | 2019-07-25 | Renault S.A.S | Device for controlling a cooling assembly for a motor vehicle |
| CN110154682A (en)* | 2019-05-24 | 2019-08-23 | 浙江吉利控股集团有限公司 | Temperature control method and system for vehicle air conditioner |
| CN114440494A (en)* | 2022-02-17 | 2022-05-06 | 广东芬尼克兹节能设备有限公司 | Compressor frequency adjusting method and device, computer equipment and storage medium |
| CN116572698A (en)* | 2023-04-21 | 2023-08-11 | 东风汽车集团股份有限公司 | Electric compressor fusion control method and device based on CO2 heat pump system |
| US20250296405A1 (en)* | 2024-03-22 | 2025-09-25 | Fca Us Llc | Vehicle cabin dehumidification control system |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11060776B2 (en) | 2019-03-27 | 2021-07-13 | Follett Corporation | Method for controlling a refrigeration device |
| CN110341438A (en)* | 2019-06-26 | 2019-10-18 | 北京长城华冠汽车科技股份有限公司 | Compressor rotary speed control method, device, storage medium and on-board air conditioner |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050120740A1 (en)* | 2002-01-10 | 2005-06-09 | Shinichi Enomoto | Cooling apparatus and a thermostat with the apparatus installed therein |
| US7100387B2 (en)* | 2002-09-13 | 2006-09-05 | Whirlpool Corporation | Method for controlling a multiple cooling compartment refrigerator, and refrigerator using such method |
| US20060213208A1 (en)* | 2005-03-22 | 2006-09-28 | Izumi Iwaki | Valve control system, valve control apparatus and valve control method |
| US7249882B2 (en)* | 2005-10-14 | 2007-07-31 | Delta Electronics Inc. | Method for determining integration initial value of PID controller |
| US20070277544A1 (en)* | 2006-06-06 | 2007-12-06 | Denso Corporation | Air conditioning system |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6089034A (en)* | 1998-11-12 | 2000-07-18 | Daimlerchrysler Corporation | Controller for reversible air conditioning and heat pump HVAC system for electric vehicles |
| US6038871A (en)* | 1998-11-23 | 2000-03-21 | General Motors Corporation | Dual mode control of a variable displacement refrigerant compressor |
| US6889762B2 (en)* | 2002-04-29 | 2005-05-10 | Bergstrom, Inc. | Vehicle air conditioning and heating system providing engine on and engine off operation |
- 2010
- 2010-03-15USUS12/723,887patent/US20110219787A1/ennot_activeAbandoned
- 2014
- 2014-05-23USUS14/286,490patent/US9920968B2/enactiveActive
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20050120740A1 (en)* | 2002-01-10 | 2005-06-09 | Shinichi Enomoto | Cooling apparatus and a thermostat with the apparatus installed therein |
| US7100387B2 (en)* | 2002-09-13 | 2006-09-05 | Whirlpool Corporation | Method for controlling a multiple cooling compartment refrigerator, and refrigerator using such method |
| US20060213208A1 (en)* | 2005-03-22 | 2006-09-28 | Izumi Iwaki | Valve control system, valve control apparatus and valve control method |
| US7762094B2 (en)* | 2005-03-22 | 2010-07-27 | Fujkoki Corporation | Valve control system, valve control apparatus and valve control method |
| US7249882B2 (en)* | 2005-10-14 | 2007-07-31 | Delta Electronics Inc. | Method for determining integration initial value of PID controller |
| US20070277544A1 (en)* | 2006-06-06 | 2007-12-06 | Denso Corporation | Air conditioning system |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10215436B1 (en)* | 2011-05-02 | 2019-02-26 | John M. Rawski | Full spectrum universal controller |
| US9688116B2 (en)* | 2011-09-23 | 2017-06-27 | Ford Global Technologies, Llc | Method for operating a vehicle climate control system |
| US11104208B2 (en) | 2011-09-23 | 2021-08-31 | Ford Global Technologies, Llc | Method for operating a vehicle climate control system |
| US20130074537A1 (en)* | 2011-09-23 | 2013-03-28 | Ford Global Technologies, Llc | Method for operating a vehicle climate control system |
| FR2996498A1 (en)* | 2012-10-08 | 2014-04-11 | Renault Sa | System for controlling air-conditioned compressor of car, has physical parameter regulation unit connected to output of temperature regulation unit and determining rotational speed of compressor with respect to measurement of parameter |
| WO2019141845A1 (en)* | 2018-01-22 | 2019-07-25 | Renault S.A.S | Device for controlling a cooling assembly for a motor vehicle |
| FR3077030A1 (en)* | 2018-01-22 | 2019-07-26 | Renault S.A.S | DEVICE FOR CONTROLLING A COOLING ASSEMBLY FOR A MOTOR VEHICLE |
| CN109017215A (en)* | 2018-07-26 | 2018-12-18 | 延锋伟世通电子科技（南京）有限公司 | PID+FF feedforward closed loop control method based on pure electric automobile PTC |
| CN108891230A (en)* | 2018-07-26 | 2018-11-27 | 延锋伟世通电子科技（南京）有限公司 | PID+FF feedforward closed loop control method based on pure electric automobile motor compressor |
| CN110154682A (en)* | 2019-05-24 | 2019-08-23 | 浙江吉利控股集团有限公司 | Temperature control method and system for vehicle air conditioner |
| CN114440494A (en)* | 2022-02-17 | 2022-05-06 | 广东芬尼克兹节能设备有限公司 | Compressor frequency adjusting method and device, computer equipment and storage medium |
| CN116572698A (en)* | 2023-04-21 | 2023-08-11 | 东风汽车集团股份有限公司 | Electric compressor fusion control method and device based on CO2 heat pump system |
| US20250296405A1 (en)* | 2024-03-22 | 2025-09-25 | Fca Us Llc | Vehicle cabin dehumidification control system |
Also Published As
| Publication number | Publication date |
|---|---|
| US9920968B2 (en) | 2018-03-20 |
| US20140250928A1 (en) | 2014-09-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20110219787A1 (en) | Variable pid enable for compressor control algorithm | |
| US8915262B2 (en) | Mass flow controller algorithm with adaptive valve start position | |
| US10520959B2 (en) | Temperature control device and auto-tuning method | |
| US12382553B2 (en) | Control device of water purifier, water purifier, and control method thereof | |
| CN104236018B (en) | Air conditioner control method and air conditioner control device | |
| KR101427955B1 (en) | Method for controlling water pump of vehicle and system thereof | |
| US7971604B2 (en) | Flow controller delivery of a specified-quantity of a fluid | |
| US20060213208A1 (en) | Valve control system, valve control apparatus and valve control method | |
| US20140121853A1 (en) | Feedback control method, feedback control apparatus, and feedback control program | |
| US7757505B2 (en) | Predictive capacity systems and methods for commercial refrigeration | |
| CN107196581B (en) | Control device, method and computer readable medium for fine tuning servo motor | |
| US20160089759A1 (en) | Control system of machine tool | |
| JP2019191760A5 (en) | ||
| US20140271235A1 (en) | Dynamic speed control for pump motor | |
| EP2725817B1 (en) | Energy conservation controller and energy conservation control system | |
| US6497108B2 (en) | Defrost control method for reducing freezer package temperature deviation | |
| US10260788B2 (en) | System and method for controlling an electronic expansion valve | |
| EP3012559B1 (en) | Selecting control strategy for an expansion valve | |
| US7668606B2 (en) | Control device for controlling a control object at a ratio of on-time to off-time for a time-proportional output | |
| US10248137B2 (en) | Method for controlling flow rate of fluid, mass flow rate control device for executing method, and mass flow rate control system utilizing mass flow rate control device | |
| CN105276882A (en) | Exhaust temperature control method for condensing unit | |
| US10457119B2 (en) | Air conditioning system for motor vehicles | |
| JP2006105437A (en) | COOLING SYSTEM CONTROL DEVICE AND COOLING SYSTEM CONTROL SYSTEM | |
| US10883748B2 (en) | Method for controlling a compressor system | |
| KR101094988B1 (en) | Half Saturated Proportional Integral Controller |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| AS | Assignment | Owner name:CONTINENTAL AUTOMOTIVE SYSTEMS US, INC., MICHIGAN Free format text:ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KEEN, ELLIOTT DAVID;RODEN, MARK PHILLIP;SHAW, SHANNON MARIE;REEL/FRAME:024080/0282 Effective date:20100310 | |
| AS | Assignment | Owner name:CONTINENTAL AUTOMOTIVE SYSTEMS, INC., MICHIGAN Free format text:MERGER;ASSIGNOR:CONTINENTAL AUTOMOTIVE SYSTEMS US, INC.;REEL/FRAME:033034/0225 Effective date:20121212 | |
| STCB | Information on status: application discontinuation | Free format text:ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |