DUAL VALVE ACCESSORY THAT ALLOWS THE RAPID PRESSURE MEASUREMENTCROSS REFERENCE WITH RELATED APPLICATIONS This application is related to a United States of America patent application entitled "Dual Seal Fitting for Enabling Quick Measurement of Brake Cylinder Pressure, Serial No. 08 / 901,096, filed July 28, 1997. The copending application is assigned to the assignee of this invention and its teachings are incorporated herein by reference.
FIELD OF THE INVENTION The present invention relates in general to a mechanism through which access to the pressure to be measured is obtained. More particularly, the invention relates to a dual valve accessory which allows the rapid measurement of the pressure contained within a charge detector of the freight brake equipment or empty load and loaded on a rail car.
BACKGROUND OF THE INVENTION A typical freight or freight train includes one or more locomotives, a plurality of railcars and a pneumatic train line referred to as a brake tube. HeP1448 / 98MX brake tube consists of a series of individual tube sections interconnected with each other. A section of pipe secured to the bottom side of each rail car is interconnected with another section of pipe by a flexible coupler located between each car or railcar. The brake tube supplies the pressurized air required by the brake control system to load or fill the various tanks and operate the air brake equipment in each rail car or truck in the freight train. The operator of the train located in the main locomotive can manipulate the brake lever to apply and release the brakes on the railway wagons as desired. The brake lever can move from and between a release position at one end where the brake line pressure is at its maximum and the brakes are fully released to an emergency position at the other end where the pressure at The brake line is minimal and the brakes are fully applied. Brake lever positions thus include brake release, minimum application of service brakes, full application of service brakes and application of emergency brakes. When the brakes are released, the tanks and the brake tube are usually charged at the same pressure: normally 90 psi in a freight train and 110 psi in a trainPassenger P1-H8 / 98MX. When the brakes are applied, the pressure in the brake line is reduced by a valve located in the main locomotive. The exact amount at which the pressure is reduced depends on which of the application positions the brake lever is placed on. It is this pressure reduction that tells the brake control valve in each rail car to supply pressurized air from the appropriate tanks to the brake cylinders. The brake cylinders convert this pressure into mechanical force that the brake shoes apply to decelerate or stop the rotation of the wheels of the railway car or van. Figure 1 illustrates a schematic diagram of the air brake equipment of a typical freight rail car equipped with empty and loaded brake equipment. Air brake equipment typically includes one or more brake cylinders, an emergency air reservoir, an auxil air reservoir, and an "ABD" valve or air brake control valve of a similar type. The operation of the air brake control valve as well as a description of its components is well known in the railway industry. Each freight rail car may include empty and loaded brake equipment such as a proportional load valve P-1 and a load sensing valveP1448 / 98MX of type S-1 or one of type ELX, all of these are manufactured by the Westinghouse Air Brake Company (WABCO) and are well known in the art of brake control. The objective of the empty and loaded brake equipment is to reduce braking in the rail car if it is empty and allow a stronger braking to the rail car if it is loaded. On a freight or freight train with railway wagons equipped with empty and loaded brake equipment, the braking is applied more evenly throughout the train in accordance with the load carried by the railway cars or vans. This tends to reduce the clearance between adjacent railway wagons and improves the overall handling of the freight or freight train. Considering the operation of a load sensing valve, the load sensing valve S-1, for example, automatically detects whether the railcar is loaded or empty by generally measuring the ratio between the body of the rail car and the upper part of the side frame of the railcar. bogie Each railway car usually has two bogies, one at each end. Each bogie includes the wheels and axles and other parts that form the structure that supports the body of the rail car. Springs or suspension springs are used to dampen vibrations that would otherwise be transmitted from the wheels to the body of the wagonP1448 / 98MX rail and that otherwise may damage the cargo being transported. These suspension springs are flexed or compressed to an extent proportional to the weight of the load carried by the railway car. Normally mounted on the underside of the body of the rail car, the load sensing valve S-1 uses its detector arm to measure the distance between the body of the rail car and the upper part of the side frame of the bogie. When loaded, the body of the rail car additionally compresses the springs, thereby reducing the distance between the body of the rail car and the side frame of the bogie. Therefore, the distance that the detector arm can travel is limited. Conversely, when the railway car is empty, the springs are less compressed, thus increasing as much as possible the distance between the body of the railway car and the side frame of the bogie. The distance that the detector arm can travel is then the maximum. When the load detector S-1 detects that the rail car is empty, its internal mechanism serves to regulate the flow of air to the load valve P-1. When the railway car is empty, the valve proportional to the load P-l controls the air flow to the brake cylinder, so that the pressure in theP1448 / 98MX brake cylinder is about 60% of what it would be if the rail car was loaded no matter how much pressure is reduced in the brake line. During brake applications, the balancing volume is used to maintain a satisfactory relationship between the pressure in the empty and loaded brake equipment and that of the control valve and its tanks when the rail car is empty. The empty and loaded brake equipment such as that of the type alluded to in this document is described in U.S. Patent Nos. 5,005,915 and 5,100,207. These patents are assigned to the assignee of the present invention and their teachings are incorporated herein by reference. Regardless of whether it is of type S-1 or of type ELX, the load sensing valve has one or more internal chambers or conduits. An interconnecting tube connects at least one of these chambers or conduits to the brake cylinder as shown, for example, in the scheme of Figure 1. A load sensing valve S-1 of the type shown schematically in Figure 1 , is illustrated in Figure 2. The left side of the housing of the load sensing valve has a generally cylindrical portion flanked by two bolts. Between these bolts and screwed into a threaded hole in theP1448 / 98MX cylindrical portion there is a tube plug. Removal of the tube plug provides direct access to the chamber communicating with the brake cylinder by the interconnected tube shown in Figure 1. The tapped hole in the housing can thus be used as an access port through the tube. which has access to the pressure in the brake cylinder from the load sensing valve. The American Association of Railroads (A.A.R.) has proposed that each railway wagon of a freight train be provided with a mechanism that would allow the pressure inside the brake cylinder to be read quickly. Currently, A.A.R. is considering whether to issue a specification that requires a commercially available quick connect type accessory to be used to access the pressure inside the brake cylinder. However, the disadvantage of this accessory is that it only provides a single valve with which it is contained at the pressure to be measured. That is, while a connection or accessory is not being used to access the pressure, it offers only one valve to avoid the pressure leaks it is supposed to contain. Unless the attachment or connection is routinely covered to protect the valve when the accessory is not being used to access the valve.
P1448 / 98MX the brake cylinder pressure, the valve is exposed to dust, dirt and / or other potential contaminants. Of course, it is important that said connection or accessory avoid pressure leakage from the brake cylinder, otherwise the operation of the brakes may be adversely affected. It should be noted that the above background information is provided to assist the reader in understanding the present invention. In accordance with this, it is not intended that any terms used be limited to any particular narrow interpretation unless specifically stated otherwise in this document.
OBJECTIVES OF THE INVENTION Therefore, it is a primary objective of the present invention to provide an extremely reliable accessory that allows the pressure inside a brake cylinder of a railway car to be measured quickly. Another goal is to make the pressure inside the brake cylinder measurable quickly with an accessory that has two valves, so that if one valve leaks, the other valve will prevent the leakage of air that is supposed to contain the fitting. P1448 / 98MX Another objective is to design a dual valve accessory with a protruding end in which a female coupler of the quick connect device can be connected, so that the pressure inside the brake cylinder can be measured quickly by coupling the accessory with its corresponding coupler female, that at its other end has a pressure measuring device connected. A further objective of the invention is to provide a dual valve fitting that allows rapid pressure measurement within any type of pipe or container capable of containing air or other suitable fluid under pressure. In addition to the objects and advantages listed above, various other objects and advantages of the invention will be more readily apparent to those skilled in the relevant art from reading the section of the detailed description of this document. The other objects and advantages will be particularly evident when the detailed description is considered together with the accompanying drawings and the appended claims.
SUMMARY OF THE INVENTION In a first currently preferred embodiment, the invention provides a dual valve accessory forP1448 / 98MX allow rapid measurement of the pressure contained within a housing. The dual valve fitting includes a valve body, a valve retainer, first and second sealing rings and a mechanism for pushing the valve retainer into a flow conduit defined by the valve body. The valve body at its protruding end is shaped to mate with a female coupler of a quick connection device and at its threaded end is designed to be screwed into a threaded bore of said housing. The valve retainer defines, around it, first and second annular recesses, each of which is separate from the other to coincide with the separation of the external and internal annular seats of the valve formed in the flow conduit. By forming the first valve, the first sealing ring retains in the first annular recess so that it can settle against the external annular seat of the valve. By forming a second valve, the second sealing ring retains in the second annular recess so that it can settle against the internal annular seat of the valve. The thrust mechanism acts on the valve retainer, so that the first and second sealing rings settle against the outer and inner annular seats of the valve, respectively. This normally makes the first and second valves closed.
P1448 / 98MX When coupled to the protruding end of the fitting, the female coupler causes the valve retainer to move inward against the push mechanism to open both the first and second valves, thereby allowing flow from the valve. housing through the flow conduit and into the female coupler. In a second embodiment, the dual valve accessory includes first and second valve bodies. The first valve body defines a flow conduit from its threaded end to its protruding end; the protruding end is shaped to mate with a female coupler of a quick connect device. Located in the flow conduit, a first valve has a rod-like head at the upper end of a valve stem that can be seated against an external annular valve seat formed in the flow conduit. A first pushing mechanism drives the rod-type head against the external annular valve seat, so that the first valve closes normally. The second valve body defines a flow auger from its upper threaded end towards its lower threaded end which communicates with the flow conduit of the first valve body. The upper threaded end connects to the threaded end of the first valve body, while the lower threaded endP1448 / 98MX is designed to be screwed into a threaded hole in the housing. Located in the flow hole, a second valve has a retainer defining at its upper end a recess that retains a retention-type valve that can seat against an internal annular valve seat formed in the flow bore. A second thrust mechanism acts on the retainer, so that the retention-type valve sits therein against the internal annular valve seat thereby normally closing the second valve. A shank extension is disposed between the lower end of the valve stem and an upper side of the retention type valve. When coupled with the protruding end of the fitting, the female coupler causes translation of the valve stem, the shank extension and the retainer thereby opening both the first and the second valve. This allows flow from the housing through the flow bore and the flow conduit and into the female coupler. In a third and a fourth embodiment of the invention, the dual valve accessory also includes first and second valve bodies. The first valve body together with the first valve and the first pushing mechanism that it houses, are in general identical to those of the second embodiment. The second bodyP1448 / 98MX valve defines a flow orifice from its upper threaded end towards its lower threaded end which communicates with the flow conduit of the first valve body. The upper threaded end is connected to the threaded end of the first valve body, while the lower threaded end is designed to be screwed into a threaded bore of the housing. Located in the flow orifice, a second valve has a piston whose upper end is disposed opposite to the lower end of the valve stem with a dead space preferably provided in the middle. Around the lower end of the plunger an annular groove is defined which retains a sealing mechanism which can seat against the inner annular seat of the valve formed in the flow orifice. A second thrust mechanism acts on the plunger, so that the sealing mechanism sits against the internal annular valve seat thus normally closing the second valve. When the female coupler is coupled with the protruding end of the fitting, this female coupler causes translation of the valve stem and the plunger thereby opening both the first and the second valve. This allows the flow from the housing through the flow orifice and the flow conduit to the female coupler.
P1 48 / 98MX In an aspect related to the third and fourth embodiments, the invention provides an auxiliary valve unit for use with a male plug of the quick connect device. The plug includes (i) a first valve body defining a flow conduit from its protruding end to its threaded end, the protruding end is shaped to engage a female coupler of the quick connect device; (ii) a first valve located in the flow conduit, the first valve includes a rod type head at the upper end of a valve stem that can seat against an external annular valve seat formed in the flow conduit at the end protuberant; and (ii) a first means for pushing the rod type head against the external annular seat of the valve, so that the first valve closes normally. The auxiliary valve unit includes a second valve body in which a second valve is housed. The second valve body defines a flow orifice from its upper threaded end to its lower threaded end which communicates with the flow conduit of the first valve body. The upper threaded end is connected to the threaded end of this first valve body, while the lower threaded end is designed to be screwed into a threaded bore of the housing.
P1448 / 98MX Located in the flow orifice, a second valve has a piston whose upper end is arranged opposite to the lower end of the valve stem with a dead space preferably provided in the middle. An annular groove is defined around a lower end of the plunger which retains a sealing mechanism that can seat against an annular internal valve seat formed in the flow bore. A second thrust mechanism acts on the plunger, so that the sealing mechanism sits against the internal annular valve seat thus normally closing the second valve. When the female coupler is coupled with the protruding end, the female coupler causes translation of the valve stem and the plunger, thus opening both the first valve and the second valve. This allows the flow from the housing through the flow orifice and the flow conduit to the female coupler. In a fifth embodiment of the invention, the dual valve accessory includes a single valve body defining a flow conduit from its threaded end to its protruding end. The protruding end is shaped to mate with a female coupler of a quick connect device. The threaded end is designed to be screwed into a threaded hole of aP1448 / 98MX hosting. Located in the upper section of the flow conduit, a first valve has a rod head at the upper end of a valve stem. The rod head can be seated against an external annular valve seat formed in the protruding end of the flow conduit. A first pushing mechanism urges or pushes the rod head against the external annular valve seat, so that the first valve is normally closed. Located in a lower section of the flow conduit, a second valve has a retainer. The retainer defines at its upper end a recess which retains therein the retention-type valve for seating against an internal annular valve seat formed in the flow conduit. A second thrust mechanism acts on the retainer, so that its retention-type valve seats against the annular inner valve seat thereby normally closing the second valve. The lower end of the valve stem is spaced a dead space from the upper side of the retention type valve. When the female coupler is coupled with the protruding end, the valve stem moves inward with its rod-like head without seating on the outer annular valve seat and its upper end moves through the dead space and pushes against settle to the retention type valve. This allows the flowP1448 / 98MX from the housing through the flow conduit to the female coupler. In a sixth embodiment of the invention, the dual valve fitting also has a single valve body defining a flow conduit from its threaded end to its protruding end. The upper section of the flow conduit and the first valve located therein is similar to that described in connection with the fifth embodiment. Located in a lower section of the flow conduit, a second valve has a seat part and a valve retainer. At its outer periphery, the seat part carries a selvedge by means of which the seat part is sealably secured within the flow conduit adjacent to the first push mechanism. Formed at its lower end, the seat part has an internal annular valve seat. Between its ends, the seat piece defines an inner bore. The upper end of the valve retainer is extendable through this internal bore to a point of a dead space separated from a lower end of the valve stem. Around its lower end, the valve retainer carries an annular retention type valve which can seat against the internal annular valve seat. A second thrust mechanism acts on the valve retainer, so that its retention-type valve sits against the internal annular seat of the valve.
P1448 / 98MX valve, thus making the second valve normally closed. When the female coupler is coupled to its protruding end, the valve stem moves inward with its rod-like head without seating on the outer annular valve seat and its lower end moves through the dead space and pushes against the upper end of the valve retainer to remove the retention type valve from its seat. This allows flow from the housing through the flow conduit to the female coupler.
BRIEF DESCRIPTION OF THE DRAWINGS OR FIGURES Figure 1 is a schematic diagram of the air brake equipment for a typical freight railway wagon that includes an S-1 load sensing valve. Figure 2 is a side view of the load sensing valve S-1 shown schematically in Figure 1. Figure 3a is a front view of a dual valve fitting in accordance with a first embodiment of the invention, the rear view or Rear of this will be the same as the front or front view. Figure 3b is a cross-sectional view of a dual valve fitting shown in Figure 3a. Figures 3c-d are partial section views of theP1448 / 98MX dual valve accessory shown in Figure 3a. Figure 3e is a bottom view of the dual valve fitting shown in Figure 3a. Figure 3f is an exploded perspective view of the dual valve fitting shown in Figure 3. Figure 3g is a cross-sectional view of a protective cap that can be used to protect the invention against contaminants. Figure 3h is a cross-sectional view of the dual valve fitting showing therein housed an arrow projecting from the lower end of a valve retainer. Figure 4 is a cross-sectional view of the dual valve fitting in accordance with a second embodiment of the invention. Figure 5 is a cross-sectional view of the dual valve fitting according to a third embodiment of the invention. Figure 6 is a cross-sectional view of the dual valve fitting in accordance with a fourth embodiment of the invention. Figure 7 is a cross-sectional view of the dual valve fitting according to a fifth embodiment of the invention.
P1448 / 98MX Figure 8 is a cross-sectional view of the dual valve fitting according to a sixth embodiment of the invention.
DBSCRIPTION »nKTftT.T.A. OF THE INVENTION Before describing the invention in detail, the reader is cautioned that, for reasons of security and understanding, the identical components that have identical functions in each of the accompanying drawings, have been marked, as far as possible, with the same reference number, in each of the Figures provided in this document. Figures 1 and 2 each illustrate a housing 701 of a load sensing valve S-1 700. The housing 701 defines an internal chamber or conduit 702 communicating with a brake cylinder 800 of a rail car. Typically, an interconnect tube 801 connects the chamber 702 to the brake cylinder 800. The housing 701 also defines a threaded bore / pipe socket 703 that communicates with the chamber 702, as best seen in Figure 2. Al Removing the tube plug 704 from the tube socket 703 provides direct access to the chamber 702. The tube socket 703 can then be used as an access port through which the pressure in the cylinder is accessed. of brakes of theP1448 / 98MX load sensing valve S-1. Figures 3a-h and 4-6 illustrate the essential details of the various embodiments of the present invention, namely, a dual valve accessory. The dual valve accessory in each of these modes allows rapid measurement of the brake cylinder pressure inside the housing of a load sensing valve or load-sensing valves of type S-1 or ELX type manufactured by various manufacturers of railway equipment. It should be apparent from the reading of this document that the dual valve fitting described and claimed herein may be applied, of course, to any other type of housing, pipe or container capable of containing air or other fluid under pressure. In a first currently preferred embodiment shown in Figures 3a-f, the dual valve fitting 1 basically includes a valve body 2, a valve retainer 3, first and second seal rings 4 and 5 and a means 6 for pushing the valve retainer 3 within a flow conduit 7 defined by the valve body 2. The valve body 2 has a protruding end 20 which is shaped to mate with a female coupler of a quick connect device. The valve body 2 also has a threaded end 21 which is designed to be screwed into the threaded bore 703 of anyP1448 / 98MX suitable housing such as that of the load sensing valve S-1 700. The valve retainer 3 defines around the same first and second annular recesses 31 and 32. These annular recesses 31 and 32 are spaced apart from each other. yes so as to coincide with the separation of the external and internal annular valve seats 71 and 72 formed in the flow conduit 7. By forming a first valve, the first seal ring 4 is adjusted or adapted in the first annular recess 31 to settle against the external annular valve seat 71 when the first valve is closed. By forming a second valve, the second seal ring 5 is housed in the second annular recess 32 to settle against the annular inner valve seat 72 when the second valve is closed. Seal rings 4 and 5 may be composed of rubber or any other suitable sealing material. The pushing means 6 acts on the valve retainer 3 so that the first and second seal rings 4 and 5 are seated against the external and internal annular valve seats 71 and 72, respectively. The pushing means 6 thus normally closes the first and second valves. It is in this normally closed position that these valves are shown in Figure 3b. Figures 3c-d show the valvesP1448 / 98MX first and second in the open position. The valve retainer 3 is designed so that the first annular recess 31 has a smaller diameter than the second annular recess 32. The first and second seal rings 4 and 5 must, of course, have their internal diameters dimensioned in accordance with , so that each seal ring is properly retained within its respective recess. Similarly, the flow conduit 7 is shaped so that the outer annular valve seat 71 has an internal diameter that is smaller than that of the annular internal valve seat 72. It is this arrangement that provides the first valve with an effective diameter smaller than that of the second valve. The first and second valves thus receive in their normally closed positions by virtue of the action of the pushing means 6 on the valve retainer 3. When in the closed position, the first and second valves thus avoid each air pressure leakage from the housing 701. The pushing means 6 preferably includes a retaining ring 60 and a spring 62, as best seen in FIG. Figure 3f, although it may take the form of various other types of mechanical devices. The retaining ring 60 is wedged securely in an annular groove 25 which is formed in the flow conduit 7 nearP1448 / 98MX of the lower part of the threaded end 21 of the valve body 2. The spring 62 is disposed between the retainer ring 60 and a lower end of the valve retainer 3. The spring 62 thus compresses the first and second seal rings 4 and 5 in the outer and inner annular seats 71 and 72 of the valve. The retaining ring 60 may also include a washer 61 to additionally support the lower portion of the spring 62 within the flow conduit 7 of the valve body 2. The valve body 2 also includes a hexagonal external portion 24 between the protruding and threaded ends 20 and 21 to accept a key with which it is securely screwed to the fitting 1 in the threaded bore 703 of the housing 701. Arranged within a groove formed adjacent a lower side of the hexagonal external portion 24 adjacent to the threaded end 21 of the valve body 2 is a selvedge. When the threaded end 21 of the dual valve fitting is screwed into the threaded bore 703, it is with this o-ring that the valve body 2 is sealed against the housing. Alternatively, this seal can be implemented using a pipe socket arrangement. The coupling of this female coupler of the quick connect device with the protruding end 20 of the dual valve accessory 1 causes the retainer 3Valve P1448 / 98MX is moved inward, against spring 62. This displaces the first and second valves away from the external and internal valve seats 71 and 72. When the first and second valves are opened, air is allowed to flow from the housing to the threaded end 21 of the flow conduit 7. The air continues to flow past the spring 62 around the valve retainer 3 until it emerges or emerges from the protruding end 20 of the flow conduit 7. Finally, the air current passes to the female coupler. By using the pressure measuring device connected to the opposite end of the female coupler, the pressure of the air contained within the housing can thus be read quickly. Referring to Figure 3f, the valve retainer 3 may also have an arrow 33, cylindrical or in some other way, around which the spring 62 may be concentrically positioned to further stabilize the pushing means 6. As shown in the Figure 3h, this arrow 33 can be made long enough to project from the threaded end 21 when the dual valve fitting 1 is coupled with a female coupler. When it is used to access the pressure in certain housings that still have a third valve located at the bottom of theP1448 / 98MX threaded hole, the dual valve accessory by arrow 33 can be used to not seat this third valve. It is also preferred that the external and internal valve seats 71 and 72 be formed within the flow conduit 7, so that the first valve opens before and closes after the second valve. With this closing sequence, the dual valve accessory 1 protects against leaks, dust, dirt or other contaminants, preventing the first external valve from closing completely. As best seen in Figure 3c, it is also preferred that the upper end of the valve retainer 3 never leave the upper section 17 of the flow conduit 7 when both the first and second valves are fully open. In a second embodiment shown in Figure 4, the dual valve fitting 100 includes a first and a second valve body 101 and 201. The first valve body 101 has a protruding end 120 which is shaped to mate with a female coupler of a quick connect device. The first valve body 102 also has a threaded end 121 which is designed to be screwed into the second valve body 201, as provided below. Defined inside the first valve body between its ends there isP1448 / 98MX a flow conduit 107. An outer annular valve seat 102 is formed within the flow conduit 107 at or near the protruding end opening 120. Located in the flow conduit 107, a first valve has a rod-like head 115 at the upper end of a valve. valve stem 110 The rod type head 115 may be composed of rubber or any other suitable seal material. A first pushing means 130 urges the rod-like head 115 against the outer annular valve seat 112. The first thrust means preferably includes a first retaining ring 131 and a first spring 132, although it can take the form of various other types of mechanical devices. The retaining ring 131 is secured within an annular groove 108 formed within the flow conduit 107 of the first valve body 101. The first spring 132 is arranged concentrically around the valve stem 110 between the first retainer ring 131 and the underside of the rod-like head 115. It is this first spring 132 that pushes the stem head forcibly. 115 against the external valve seat 112, so that the first valve is normally kept closed. The second valve body 201 has an internally threaded upper end 220 which is designed forP1448 / 98MX admit to the threaded end 121 of the first valve body 101. The second valve body also has a lower threaded end 221 that is screwed into the threaded bore 703 of any suitable housing, such as that of the load sensing valve S-1 700. Defined within the second valve body between its ends there is a flow orifice 207 communicating with the flow conduit 107 of the first valve body 101. Located in the flow orifice 207, a second valve has a retainer 209 which defines a recess 252 at its upper end. Retained in this recess is a retention-type valve 253 whose upper side can be seated against an internal annular valve seat 245 formed in the flow hole 207. The retention type valve may be composed of rubber or any other suitable sealing material. A second pushing means 230 acts on the retainer 209, so that the holding-type valve 253 sits against the inner annular valve seat 245. The second pushing means 230 preferably includes a second retaining ring 231 and a second spring 232, although it can take the form of various other types of mechanical apparatus. The second retaining ring is retained within an annular groove 208 formed within the flow hole 207 in the lower threaded end 221 of the second body 201 ofP1448 / 98MX valve. The second spring 232 is located between the second retaining ring 231 and the lower end of the retainer 209. The lower end of the retainer 209 may have an arrow, cylindrical or in some other way, around which the second may be concentrically located. spring 232 to additionally stabilize the second thrust means 230. This second spring 232 is the one that forcibly pushes the holding type valve 253 in the retainer 209 against the inner annular valve seat 245, so that the second valve is normally maintained closed. The dual valve fitting 100 also includes a shank extension 264 disposed between a lower end of the valve shank 110 and the upper side of the holding type valve 253. The shank extension in its upper part preferably defines a cavity in the that the lower end of the valve stem 110 projects even when the first valve is closed. Preferably, a dead space 266 is provided between the bottom end of the valve shank 110 and the upper part of the shank extension 264 within this cavity. By virtue of the dead space 266, the rod-type head 115 may not be seated in the outer annular valve seat 112 while the holding-type valve 253 remains seated in the annular seat.
P1448 / 98MX internal valve 245. When the first valve is opened in this manner, the integrity of the second valve can be tested in this way when the dual valve fitting 100 is connected to a pressure carrying housing such as the load sensing valve S-1 700. The first valve body 101 may also include an external hexagonal portion 124 between the protruding and threaded ends, 120 and 121, to accept a mechanical wrench with which the first valve body 101 is screwed into the upper threaded end 220 of the second body 201 of valve. Arranged within a groove formed adjacent the underside of the external hexagonal portion 124 adjacent the threaded end 121 is a hoop. When the threaded end 121 of the first valve body 101 is screwed into the upper threaded end 220, it is with this collar that the first valve body 101 is sealed against the second valve body 201. Instead, this seal can be implemented using a pipe socket arrangement. The second valve body 201 also defines an annular groove formed on its outer surface above its lower threaded end 221. A hoop 228 fits securely in this groove. It is with this arosello 228 that the second valve body 201 is sealed against the housing 701 when the threaded endP1448 / 98MX lower 201 is screwed into the threaded bore 703 of the housing. This seal, too, can be implemented using a pipe socket arrangement. By coupling the female coupler of the quick connect device to the protruding end 120 of the dual valve fitting 100, the rod 110 of the valve is caused to move inwardly against the first spring 132. By means of this movement, the bottom end of the shank 110 of the valve moves through and beyond the dead space 266 and towards the upper part of the shank extension 264. The lower part of the shank extension 264, in turn, drives the retention type valve 253 outside the annular inner valve seat 245 as the detent 209 moves inwardly against the second spring 232. With both the first and second valves open, air is allowed to flow from the housing toward the lower threaded end 221 of the orifice 207 of the valve. flow. The air flow continues beyond the second spring 232 around the retainer 209 and the extension of the cane 264 to the flow conduit 107 of the first valve body 101. Flowing past the first retaining ring 131, the first spring 132 and the rod-type head 115, the air emerges from the protruding end 120 of the flow conduit 107. Finally, the air stream passes to the female coupler.
P1448 / 98MX Using a pressure measuring device connected to the opposite end of the female coupler, the air pressure contained within the housing can thus be read quickly. In a third and a fourth embodiment shown in Figures 5 and 6, respectively, the dual valve fitting also includes first and second valve bodies. The first valve body together with the first valve and the first thrust means it generally admits are identical to those of the second embodiment. The second valve body has an internally threaded upper end 320 which is designed to admit the threaded end 121 of the first valve body 101. The second valve body also has a threaded lower end 321 that is screwed into the threaded bore 703 of any suitable housing, such as that of the load sensing valve S-1 700. Defined within the second valve body between its ends there is a flow auger 307 communicating with the flow conduit 107 of the first valve body 101. Located in the flow orifice 307, a second valve has a plunger whose upper end is disposed opposite the lower end of the valve shank 110. The bottom end of the plunger defines an annular groove in which a means ofP1448 / 98MX sealed. This sealing means is designed to settle against an internal annular valve seat formed in the flow orifice 307. The sealing means may be composed of rubber or any other suitable material. A second thrust means acts on the plunger, so that the sealing means sits against the internal annular valve seat. In the third embodiment of the invention shown in Figure 5, located in the flow orifice 307 proximate its threaded lower end 321, there is an annular flange 310 on whose underside the inner annular valve seat 311 is formed. The seal means 330 that can be seated against this internal valve seat 311 is a selvedge 331. Shaped on the upper side of the annular flange 310 is a lower annular spring seat 312. Formed in the plunger 309 near its upper end there is an upper annular spring seat 313. The spring seat 313 may also be comprised of an annular groove defined within the plunger 309 in which a retaining ring is retained to serve as the spring seat 313. Together with the lower and upper spring seats 312 and 313, the second thrust means 340 includes a second spring 342 arranged concentrically around the plunger 309 between the spring seats. The spring 342 compresses a seal 331 against theP1448 / 98MX internal annular valve seat 311, to keep the second valve normally closed. The second thrust means 340 may also take the form of various other types of mechanical apparatus. In the fourth embodiment of the invention illustrated in Figure 6, the seal means 345 preferably takes the form of an annular retention-type valve 346 that is molded in an annular groove 347 disposed about the bottom or interior end of the plunger 319. The second thrust means 350 preferably includes a second retaining ring 351 and a second spring 352, although it can take the form of various other types of mechanical apparatus. The second retaining ring 351 is retained within an annular groove 353 formed in the threaded lower end 321 of the flow orifice 307. The second spring 352 is disposed between this second retainer ring and the bottom or inner end of the plunger 319. The spring 352 compresses a check valve 346 against the annular inner valve seat 361, to keep the second valve normally closed. Referring to both the third and fourth embodiments of the invention, a dead space 366 is preferably provided between the lower end of the valve stem 110 and the upper end of the plunger. Under theP1448 / 98MX dead space 366, the rod type head 115 may not be seated in the outer annular valve seat 112 while the second valve remains closed. With the first valve opened in this manner, the integrity of the second valve can thus be tested when the dual valve fitting is connected to a pressure carrying housing such as the load detecting valve S-1 700. As with the second valve In this embodiment, the second valve body of both the third and fourth embodiments may also define an annular groove formed on its outer surface above its threaded lower end. An arosello 228 fits securely within this groove. It is with this annular groove / ring arrangement or with a pipe socket arrangement that the second valve body can seal against the housing 701 when its threaded lower end 321 is screwed into the threaded bore 703 of the bearing housing. Considering the operation of the third and fourth modes of the dual valve fitting, the coupling of the female coupler of the quick connect device with the protruding end 120 of the first valve body 101 causes the valve stem 110 to move inwardly against the first spring 132. By means of this movement, the lower end of the valve stem 110 moves through and beyond the spaceP1448 / 98MX dead 366 and towards the top of the plunger. The lower part of the plunger, in turn, pushes the sealing means out of the internal annular valve seat as the plunger moves inwardly against the second spring. With both valves open, the first and the second, air is allowed to flow from the housing to the threaded lower end 321 of the flow orifice 307. The air flow continues beyond the second spring around the plunger to the flow conduit 107 of the first valve body 101. Flowing past the first retaining ring 131, the first spring 132 and the rod-like head 115, air emerges from the protruding end 120 of the flow conduit 107. Finally, the air current passes to the female coupler. By using a pressure measuring device connected to the opposite end of the female coupler, the air pressure contained within the housing can thus be read quickly. In an aspect related to the third and fourth embodiments, the invention also provides an auxiliary valve unit. The auxiliary valve unit preferably adopts the shape of the second valve body of the third and fourth embodiments and is intended to be implemented in conjunction with a male plug of a quick connection device. Of course, in theP1448 / 98MX market there are a variety of quick connect devices available in commercial form. The male plug of a normal quick connect device, available commercially, would only need to be modified to work with the auxiliary valve unit to constitute the dual valve accessory in its third and fourth modes. For example, the male plug of a standard coupling would have to be modified to engage and interact with the second valve body and its associated components, such as its threaded upper end and the plunger. In a fifth embodiment shown in Figure 7, the dual valve fitting only has a valve body 401. The valve body 401 has the protruding end 120 and the threaded end 121 between which a flow conduit 407 is defined. The threaded end 121 is screwed into the threaded bore 703 of any suitable housing, such as that of the load sensing valve S-1 700. The outer annular valve seat 112 is formed within the flow conduit 407. Located in the upper section of the flow conduit 407, the first valve has the rod type head 115 at the upper end of the valve stem 110. The first pushing means 130 drives or compels the rod head 115 against the outer seat 112 ofP1448 / 98MX valve. Although it may take the form of various other types of mechanical apparatus, the first pushing means preferably includes the first spring 132 and an annular flange 410 on the upper side of which a spring upper seat 431 is formed. The first spring 132 is arranged concentrically around the valve stem 110 between the seat 431 and the underside of the rod head 115. The first spring 132 forcibly pushes the rod head 115 against the external valve seat 112, so that the first valve is normally kept closed. Located in the lower section of the flow conduit 407, a second valve has a retainer 409 defining at its upper end a recess 452. Retained in this recess is a retention-type valve 453 whose upper side can be seated against an inner annular seat 445 valve formed on the underside of the annular flange 410. Although it may be implemented in other forms, the second thrust means 230 preferably includes a retaining ring 231 and a second spring 232. The second retaining ring is retained within a groove annular 208 formed within the flow conduit 407 at the threaded end 121 of the valve body 401. The second spring 232 is disposed between the retaining ring 231 and the lower end of the retainer 409. It is thisP1448 / 98MX second spring 232 which pushes the check valve 453 in the detent 409 against the inner annular valve seat 445, so that the second valve is normally kept closed. In this fifth embodiment, the dead space 266 is preferably provided between the lower end of the valve stem 110 and the upper side of the check valve 453. The dead space 266 allows the rod head 115 not to be seated in the seat external valve 112 while the check valve 453 remains seated in the internal valve seat 445. With the first valve opened in this way, the integrity of the second valve can then conveniently and quickly be tested. The valve body 401 also preferably includes the external hexagonal portion 124 between its protruding and threaded ends to accept a mechanical key with which it is screwed to the valve body 401 in a suitable housing. Arranged within a groove formed adjacent a lower side of the external hexagonal portion is an arosello 419. It is with this arosello 419 or with a pipe making arrangement that the valve body 401 seals against said housing when the threaded end 121 is screw into threaded bore 703 of a bearing housing.
P1448 / 98MX The retainer 409, as part of its lower end, may also have an arrow 433, cylindrical or in some other way, around which the spring 232 may be arranged in a concentric manner to additionally stabilize the pushing means 230. As shown in Figure 7, this arrow 433 can be made long enough to project from the threaded end 121 when the dual valve fitting is coupled with a female coupler. When used to access pressure in certain housings which still have a third valve located in the bottom or bottom of the threaded bore, the dual valve accessory, by means of arrow 433 can be used to not seat this third valve. In a sixth embodiment shown in Figure 8, the dual valve accessory also has only one valve body 501. The valve body 501 has its protruding end 120 and the threaded end 121 between which a flow conduit 507 is defined. The threaded end 121 is screwed into the threaded bore 703 of any suitable housing, such as that of the load sensing valve S-1 700. The outer annular valve seat 112 is formed within the flow conduit 507. Located in the upper section of the flow conduit 507, the first valve presents the head of typeP1448 / 98MX rod 115 at the upper end of the valve stem 110. The first pushing means 130 drives or compels the rod head 115 against the outer valve seat 112. Although it can be implemented using other types of apparatus, the first pushing means preferably includes a spring stop 131 and a first spring 132. The spring stop 131 can be held in place by a protruding ring or ring that can be secured within a groove annular defined in the flow conduit 507. The first spring 132 is arranged concentrically about the valve stem 110 between the stop 131 and the underside of the rod head 115. The first spring 132 thus pushes the first valve in the closed position A cylindrical seat member 540 has an annular groove around its circumference in which it retains a ring 542. It is with this o-ring 542 that the seat part 540 is sealed in the conduit 507 The lower end 545 of the seat part 540 is formed as an internal annular valve seat and its opposite end 546 is located adjacent to the seat. e to the spring stop 131. Along its longitudinal axis, the seat part 540 also defines through it an internal bore 548. Extending through this internal bore 548 from the sectionP1448 / 98MX upper to the lower section of the flow conduit 507, there is a valve retainer 550. Located in the lower section of the flow conduit 507, a second valve includes a valve retainer 550 and the annular inner valve seat 545 of the seat part 540. The upper end of the valve retainer 550 is extendable through the inner bore. 548 of the seat part 540 to a point preferably the dead space 266 separated from the lower end of the stem 110 of the valve. Around its lower end, the valve retainer 550 carries an annular retention-type valve 553. In this sixth embodiment of the invention, the second pushing means 230 acts on the valve retainer 550, so that the retention-type valve 553 e sits thereon against the inner annular valve seat 545. Although it can be implemented in alternative ways, the second thrust means 230 preferably and essentially includes the same structure as that described for the fifth embodiment of the invention. Accordingly, this second spring 232 is the one that forcibly pushes the retainer-type valve 553 of the detent 550 against the annular inner valve seat 545 so that the second valve is normally kept closed. Of course, dead space 266 will allow theP1448 / 98MX first valve opens, so that the integrity of the second valve can be tested quickly. In the dual valve accessory of this sixth embodiment it likewise preferably includes other features previously described. This includes features such as a hexagonal portion 124 together with either the hoop / groove arrangement or the pipe socket arrangement with which the valve body 501 seals against the bearing housing. The dual valve fitting may also have an arrow 533 formed as part of the lower end of the valve retainer 550. The arrow 533 is preferably made long enough to project or protrude from the threaded end 121, when the dual valve fitting is coupled with a female coupler. When used to access pressure in certain housings that still have a third valve located in the bottom or bottom of the threaded bore, arrow 533 allows the dual valve fitting not to seat in this third valve. Referring to all embodiments of the invention, the position of the first valve makes it more exposed to dust, dirt and other potential contaminants. The second valve thus serves as a backrest to the first valve if the first valve succumbs to saidP1 48 / 98MX pollutants or is degraded in some other way. Conversely, if the second valve is degraded, the first valve acts as the backup valve to prevent leakage of air or other fluid from any bearing housing to which the invention is connected. A protective cap can be used to cover the protruding end of the invention and protect it from contaminants when it is not used. As shown in Figure 3g, in the context of the first embodiment, although applicable to all other embodiments, the protective cap 8 has a cover 81, a washer 82 and a belt 83. The belt 83 is used to connect the cover 81 with washer 82 to reduce the likelihood of loss or misplacing the protective cap 8. Washer 82 has an internal diameter that allows it to be securely wrapped in a corresponding annular recess 23 carried by valve body 2 , as shown in Figures 3a, to hold or hold the protective cap 8 over the dual valve fitting. The cover 81 is dimensioned so that it can clamp tightly to the protruding end 20, and still detach and easily catch on the dual valve fitting. The dual valve fitting described and claimed in this document can, of course, be applied to many types of housings, tubes or containers capable of containing orP1448 / 98MX keep air or other suitable fluid under pressure. The presently preferred and alternative embodiments and related aspects for carrying out the invention have been set forth in detail in accordance with the Patent Law. Those of ordinary skill in the art to which this invention pertains may nevertheless recognize various alternative ways to practice the invention without deviating from the spirit and scope of the appended claims. Those having experience will also recognize that the foregoing description is illustrative only and is not intended to limit any of the following claims to any particular narrow interpretation. In accordance with the foregoing, to promote the progress of science and useful techniques, we ensure for ourselves through the Patent Title the exclusive rights to all matter covered by the following claims during the time prescribed by the Patent Law.
P1448 / 98MX