US20040214678A1 - Pressure control valve for hydraulic actuation assembly - Google Patents
Pressure control valve for hydraulic actuation assembly Download PDFInfo
- Publication number
- US20040214678A1 US20040214678A1 US10/106,225 US10622502A US2004214678A1 US 20040214678 A1 US20040214678 A1 US 20040214678A1 US 10622502 A US10622502 A US 10622502A US 2004214678 A1 US2004214678 A1 US 2004214678A1
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- US
- United States
- Prior art keywords
- blind hole
- spring
- valve assembly
- area
- groove
- 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.)
- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0406—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/045—Compensating for variations in viscosity or temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/02—Check valves with guided rigid valve members
- F16K15/04—Check valves with guided rigid valve members shaped as balls
- F16K15/044—Check valves with guided rigid valve members shaped as balls spring-loaded
- F16K15/046—Check valves with guided rigid valve members shaped as balls spring-loaded by a spring other than a helicoidal spring
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/04—Control of fluid pressure without auxiliary power
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0221—Valves for clutch control systems; Details thereof
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7904—Reciprocating valves
- Y10T137/7922—Spring biased
- Y10T137/7927—Ball valves
Definitions
- This invention relates to a pressure control valve arrangement in a hydraulically-actuated differential or torque coupling device for use with a vehicle drive train, for example, a speed sensitive limited slip differential; and more particularly is directed to a multi-control valve assembly for a hydraulically actuated clutch pack in a torque coupling device.
- Limited slip differentials and torque coupling devices are well known in the art.
- a hydraulically actuated friction clutch pack is actuated to retard relative rotation of at least one of the rotating component, e.g., at least on side gears relative to the differential case.
- hydraulic pressure is directly increased in response to an increase in rotational speed differential of the axle components.
- One common way to provide the hydraulic pressure is to include an internal pump, or gerotor pump, within a differential case.
- a pressure relief valve to provide relief from pressure build up in the limited slip device. In other words, once the hydraulic pressure reaches a predetermined level, the pressure relief valve relieves that pressure.
- FIG. 7 A ball is simply provided in a ball seat on the external surface of the differential case.
- the ball seat is in communication with hydraulic fluid of the limiting device.
- the ball is retained in the seat by a leaf spring secured to the outer surface of the differential case. As hydraulic pressure in the limiting device increased, the ball is forced against the leaf spring. If sufficient pressure exists, the leaf spring opens and fluid is allowed to flow out of the differential case. Otherwise, the valve remains closed.
- the present invention provides an improved pressure control valve for use in a limited slip differential or torque coupling device.
- a pressure control valve assembly is disposed in the hydraulic flow path of a differential assembly and is connected to a passageway leading to a limited slip device within the differential case to establish fluid communication there between.
- the invention includes a machined or formed blind hole, a groove which partially intersects the blind hole, a ball member seated in the blind hole, and a spring resiliently acting on the ball to apply a force biasing the ball into the blind hole.
- an area, which is not sealed by the ball is formed that provides a controlled leakage path for the hydraulic fluid.
- the hydraulic pressure of the fluid on the pressure side increases which increases the force on the ball acting against the spring.
- the resultant forces on the ball deflect the spring to increase the bleed area and increase the fluid bled proportionally to the fluid pressure. Therefore, a pressure control mechanism is provided.
- the pressure control valve controls the pressure flow in a manner that can be controlled by changing the dimensions of the hole, groove and ball. Hydraulic flow leakage and pressure control can vary with the force of the spring.
- a temperature sensitive spring is used (e.g., as a bimetallic member) to allow the force on the ball to vary with temperature to either decrease upper pressure values at higher temperature or increase upper pressure with increase in temperature, or to provide compensation for change in fluid viscosity with temperature.
- FIG. 1 is a sectional view of a limited slip differential employing the pressure control valve assembly of the present invention.
- FIG. 2 is an enlarged sectional view of the pressure control valve assembly shown in FIG. 1;
- FIG. 3 a is a partial cross section view of the pressure control valve according to a first embodiment of this invention.
- FIG. 3 b is a sectional view of the pressure control valve assembly of FIG. 3 a taken along line IIIb-IIIb.
- FIG. 4 represents a curve of pressure versus flow for the control valve of this invention.
- FIG. 5 shows as alternate application of the control valve system of this invention in a torque transfer mechanism.
- FIG. 6 is an enlarged sectional view of the pressure control valve assembly shown in FIG. 5 and embodying an alternate structural arrangement for the valve assembly.
- FIG. 7 is a sectional view of a related art pressure relief valve.
- FIG. 1 is a cross sectional view of a limited slip differential employing the pressure control valve of the present invention.
- a differential case 1 driven by a ring gear houses a pair of side gears 3 a , 3 b a pair of pinion gears 5 a , 5 b and a pinion shaft 7 to allow speed differential between a pair of opposite output shafts 4 a , 4 b as is commonly known in the art.
- a limited slip device in the form of a clutch pack 9 is disposed between the side gear 3 b and the differential case 1 .
- a plurality of friction discs is alternately splined onto the side gear 3 b and differential case 1 .
- a hydraulically actuated piston 11 disposed within a piston chamber serves to compress the clutch pack 9 and retard any speed differential between the side gear 3 b and differential case 1 . This results in a retardation of any speed differential between the shafts 4 a , 4 b .
- a gerotor pump 12 is employed to provide pressurized hydraulic fluid to actuate the piston 11 and engage the clutch pack.
- a self-contained pressure control valve assembly is disposed within the differential case 11 .
- FIG. 2 depicts one arrangement of the pressure control valve assembly according to the present invention.
- FIG. 2 is an enlarged view of area A of FIG. 1.
- the pressure control valve of the present invention includes a spring shown in the form of a cantilever beam 20 in FIG. 2 mounted to the differential case 1 for resiliently acting on a ball member 24 disposed in blind hole 1 a .
- a groove 1 b is formed on the pressure side of the hydraulic actuation system, and the groove 1 b partially 1 ; intersects the hole 1 a.
- FIGS. 3 a and 3 b schematically show the control valve assembly of FIG. 2 whereby the cantilevered beam 20 acts on the ball 24 to seat the ball in the blind hole 1 a while the leakage path (see arrows ‘A’) remains at least partially open at the intersection of the hole 1 a and groove 1 b where there is formed a fluid bleed area 28 .
- FIG. 3 b shows a cross sectional view of FIG. 3 a taken along line IIIb-IIIb whereby the groove is formed as an elongated notch along line x-x with a groove width ‘w’.
- the ball contact area of the ball 24 is shown by reference numeral 26 .
- FIGS. 2-3 b controls the pressure flow in a manner that can be controlled by changing the dimensions of the hole 1 a , groove 1 b and ball 24 . Hydraulic flow leakage and pressure control can vary with the force of the spring 20 .
- FIG. 4 represents a curve of pressure versus flow for the control valve of this invention. It is noted however that the spring force may be selected to provide a variety of maximum pressures with respect to FIG. 4 and the invention may employ the use of non-linear springs.
- FIG. 5 shows as alternate application of the control valve system described above with respect to FIGS. 2-4, whereby the control valve system is disposed on an actuation piston 201 for a torque transfer system that couples the outer case member 215 and ring gear (not shown) to an inner differential case 217 .
- a gerotor pump assembly 210 and clutch 212 is disposed between the outer case member 215 and inner case 217 .
- FIG. 6 is an enlarged view of area B of FIG. 5.
- the pressure control valve of the present invention includes a spring shown in the form of a coil spring 220 mounted to the actuation piston 201 for resiliently acting on a ball member 224 disposed in blind hole 201 a .
- a groove 201 b is formed on the pressure side of the hydraulic actuation system, and the groove 201 b partially intersects the hole 201 a .
- a screw or plug member 230 retains the ball 224 and spring 220 within the blind hole 201 a via any suitable manner such as threads, friction fit, adhesive, welding etc.
- the screw or plug member 230 is formed with a suitable passageway 232 formed therein for permitting fluid flow therethrough.
- an area, which is not sealed by the ball 224 is formed that provides a controlled leakage path for the hydraulic fluid.
- the hydraulic pressure of the fluid on the pressure side increases which increases the force on the ball 224 acting against the spring 220 .
- the resultant forces on the ball deflect the spring 220 to increase the bleed area and increase the fluid bled proportionally to the fluid pressure. Therefore, a pressure control mechanism is provided.
- a temperature sensitive spring is used (e.g., as a bimetallic member) to allow the force on the ball to vary with temperature to either decrease upper pressure values at higher temperature or increase upper pressure with increase in temperature, or to provide compensation for change in fluid viscosity with temperature.
- valve system of this invention can be an assembly and installed in a component as a modular assembly, it can be separately mounted, or it can be integrated to a component as part of its design.
- the present invention may be used in a direct torque coupling arrangement where speed sensitive coupling between the shafts 4 a , and 4 b are desired.
- the surface forming the seating component for the ball may be formed on an insert piece that is threaded into a tap hole, whereby the ball is seated on the insert piece and resiliently held in place by a suitable spring member.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Retarders (AREA)
- Safety Valves (AREA)
Abstract
Description
- a) Field of the Invention
- This invention relates to a pressure control valve arrangement in a hydraulically-actuated differential or torque coupling device for use with a vehicle drive train, for example, a speed sensitive limited slip differential; and more particularly is directed to a multi-control valve assembly for a hydraulically actuated clutch pack in a torque coupling device.
- b) Background of Related Art
- Limited slip differentials and torque coupling devices are well known in the art. In such devices, a hydraulically actuated friction clutch pack is actuated to retard relative rotation of at least one of the rotating component, e.g., at least on side gears relative to the differential case. Normally, hydraulic pressure is directly increased in response to an increase in rotational speed differential of the axle components. One common way to provide the hydraulic pressure is to include an internal pump, or gerotor pump, within a differential case. As hydraulic pressure increases as a result of the increased speed of the pump (increased speed differential), there is a need to provide a pressure relief valve to provide relief from pressure build up in the limited slip device. In other words, once the hydraulic pressure reaches a predetermined level, the pressure relief valve relieves that pressure.
- One such pressure relief valve of the related art is shown in FIG. 7. A ball is simply provided in a ball seat on the external surface of the differential case. The ball seat is in communication with hydraulic fluid of the limiting device. The ball is retained in the seat by a leaf spring secured to the outer surface of the differential case. As hydraulic pressure in the limiting device increased, the ball is forced against the leaf spring. If sufficient pressure exists, the leaf spring opens and fluid is allowed to flow out of the differential case. Otherwise, the valve remains closed.
- It is also known to provide a hydraulic valve assembly including a bleed passage to control how the hydraulic pressure in the hydraulic system rises with increased flow. However, the prior art fails to adequately provide variable pressure control, linear and non-linear as well as thermo-sensitive compensation for changes in fluid viscosity with temperature.
- The need therefore exists for an improved differential control valve that is simple in design, easy to assembly and opens and closes in a predictable and consistent manner, while integrating two distinct hydraulic flow and pressure mechanisms into a single assembly.
- The present invention provides an improved pressure control valve for use in a limited slip differential or torque coupling device. A pressure control valve assembly is disposed in the hydraulic flow path of a differential assembly and is connected to a passageway leading to a limited slip device within the differential case to establish fluid communication there between.
- In the preferred embodiment, the invention includes a machined or formed blind hole, a groove which partially intersects the blind hole, a ball member seated in the blind hole, and a spring resiliently acting on the ball to apply a force biasing the ball into the blind hole. At the intersection of the blind hole and groove, an area, which is not sealed by the ball, is formed that provides a controlled leakage path for the hydraulic fluid. As the hydraulic fluid flow increases, the hydraulic pressure of the fluid on the pressure side increases which increases the force on the ball acting against the spring. As the pressure increases further, the resultant forces on the ball deflect the spring to increase the bleed area and increase the fluid bled proportionally to the fluid pressure. Therefore, a pressure control mechanism is provided.
- The pressure control valve controls the pressure flow in a manner that can be controlled by changing the dimensions of the hole, groove and ball. Hydraulic flow leakage and pressure control can vary with the force of the spring.
- In a modified embodiment of this invention, a temperature sensitive spring is used (e.g., as a bimetallic member) to allow the force on the ball to vary with temperature to either decrease upper pressure values at higher temperature or increase upper pressure with increase in temperature, or to provide compensation for change in fluid viscosity with temperature.
- The objects, features and advantages of the present invention are readily apparent from the following detailed description of the best modes for carrying out the invention when taken in connection with the accompanying drawings.
- FIG. 1 is a sectional view of a limited slip differential employing the pressure control valve assembly of the present invention.
- FIG. 2 is an enlarged sectional view of the pressure control valve assembly shown in FIG. 1;
- FIG. 3a is a partial cross section view of the pressure control valve according to a first embodiment of this invention.
- FIG. 3b is a sectional view of the pressure control valve assembly of FIG. 3a taken along line IIIb-IIIb.
- FIG. 4 represents a curve of pressure versus flow for the control valve of this invention.
- FIG. 5 shows as alternate application of the control valve system of this invention in a torque transfer mechanism.
- FIG. 6 is an enlarged sectional view of the pressure control valve assembly shown in FIG. 5 and embodying an alternate structural arrangement for the valve assembly.
- FIG. 7 is a sectional view of a related art pressure relief valve.
- FIG. 1 is a cross sectional view of a limited slip differential employing the pressure control valve of the present invention. However, it is to be understood that while the present invention is described in relation to a speed sensitive limited slip differential, the present invention is equally suitable for use in a variety of torque coupling mechanisms using hydraulic pump systems, as well as other hydraulic couplings for a drive-train. A
differential case 1 driven by a ring gear (not shown) houses a pair ofside gears pinion gears pinion shaft 7 to allow speed differential between a pair ofopposite output shafts clutch pack 9 is disposed between theside gear 3 b and thedifferential case 1. A plurality of friction discs is alternately splined onto theside gear 3 b anddifferential case 1. A hydraulically actuatedpiston 11 disposed within a piston chamber serves to compress theclutch pack 9 and retard any speed differential between theside gear 3 b anddifferential case 1. This results in a retardation of any speed differential between theshafts gerotor pump 12 is employed to provide pressurized hydraulic fluid to actuate thepiston 11 and engage the clutch pack. In such an arrangement, as the relative speed between theoutput shafts differential case 11. - FIG. 2 depicts one arrangement of the pressure control valve assembly according to the present invention.
- FIG. 2 is an enlarged view of area A of FIG. 1. The pressure control valve of the present invention includes a spring shown in the form of a
cantilever beam 20 in FIG. 2 mounted to thedifferential case 1 for resiliently acting on aball member 24 disposed inblind hole 1 a. Agroove 1 b is formed on the pressure side of the hydraulic actuation system, and thegroove 1 b partially 1; intersects thehole 1 a. - At the intersection of the
blind hole 1 a andgroove 1 b, an area, which is not sealed by theball 24, is formed that provides a controlled leakage path ‘P’ for the hydraulic fluid. As the hydraulic fluid flow increases, the hydraulic pressure of the fluid on the pressure side increases which increases the force on theball 24 acting against thespring 20. As the pressure increases further, the resultant forces on the ball deflect thespring 20 to increase the bleed area and increase the fluid bled proportionally to the fluid pressure. Therefore, a pressure control mechanism is provided. - FIGS. 3a and 3 b schematically show the control valve assembly of FIG. 2 whereby the cantilevered
beam 20 acts on theball 24 to seat the ball in theblind hole 1 a while the leakage path (see arrows ‘A’) remains at least partially open at the intersection of thehole 1 a andgroove 1 b where there is formed afluid bleed area 28. FIG. 3b shows a cross sectional view of FIG. 3a taken along line IIIb-IIIb whereby the groove is formed as an elongated notch along line x-x with a groove width ‘w’. The ball contact area of theball 24 is shown byreference numeral 26. - The pressure control valve shown in FIGS. 2-3b controls the pressure flow in a manner that can be controlled by changing the dimensions of the
hole 1 a,groove 1 b andball 24. Hydraulic flow leakage and pressure control can vary with the force of thespring 20. FIG. 4 represents a curve of pressure versus flow for the control valve of this invention. It is noted however that the spring force may be selected to provide a variety of maximum pressures with respect to FIG. 4 and the invention may employ the use of non-linear springs. - FIG. 5 shows as alternate application of the control valve system described above with respect to FIGS. 2-4, whereby the control valve system is disposed on an
actuation piston 201 for a torque transfer system that couples theouter case member 215 and ring gear (not shown) to an innerdifferential case 217. Agerotor pump assembly 210 and clutch 212 is disposed between theouter case member 215 andinner case 217. - FIG. 6 is an enlarged view of area B of FIG. 5. The pressure control valve of the present invention includes a spring shown in the form of a
coil spring 220 mounted to theactuation piston 201 for resiliently acting on aball member 224 disposed inblind hole 201 a. Agroove 201 b is formed on the pressure side of the hydraulic actuation system, and thegroove 201 b partially intersects thehole 201 a. A screw or plugmember 230 retains theball 224 andspring 220 within theblind hole 201 a via any suitable manner such as threads, friction fit, adhesive, welding etc. The screw or plugmember 230 is formed with asuitable passageway 232 formed therein for permitting fluid flow therethrough. - As with the embodiment of FIGS. 2-4, at the intersection of the
blind hole 201 a andgroove 201 b, an area, which is not sealed by theball 224, is formed that provides a controlled leakage path for the hydraulic fluid. As the hydraulic fluid flow increases, the hydraulic pressure of the fluid on the pressure side increases which increases the force on theball 224 acting against thespring 220. As the pressure increases further, the resultant forces on the ball deflect thespring 220 to increase the bleed area and increase the fluid bled proportionally to the fluid pressure. Therefore, a pressure control mechanism is provided. - In a modified embodiment of this invention, a temperature sensitive spring is used (e.g., as a bimetallic member) to allow the force on the ball to vary with temperature to either decrease upper pressure values at higher temperature or increase upper pressure with increase in temperature, or to provide compensation for change in fluid viscosity with temperature.
- As apparent from the foregoing description, the valve system of this invention can be an assembly and installed in a component as a modular assembly, it can be separately mounted, or it can be integrated to a component as part of its design.
- While the present invention has been shown and described with reference to specific embodiments forming the best mode, various changes in form and detail may be made without departing from the spirit and scope of the invention. While the best modes for carrying out the invention have been described in detail, those familiar with the art to which this invention relates will recognize various alternatives, designs and embodiments for practicing the present invention as defined by the following claims. For example, the present invention may be used in a direct torque coupling arrangement where speed sensitive coupling between the
shafts
Claims (20)
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
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US10/106,225 US6802791B1 (en) | 2002-03-27 | 2002-03-27 | Pressure control valve for hydraulic actuation assembly |
CNA038070693A CN1701187A (en) | 2002-03-27 | 2003-01-27 | Pressure control valve for hydraulic actuation assembly |
AU2003258435A AU2003258435A1 (en) | 2002-03-27 | 2003-01-27 | Pressure control valve for hydraulic actuation assembly |
BR0308657A BR0308657A (en) | 2002-03-27 | 2003-01-27 | Pressure Control Valve Assembly |
EP03745508A EP1490604A1 (en) | 2002-03-27 | 2003-01-27 | Pressure control valve for hydraulic actuation assembly |
PCT/US2003/002205 WO2003083321A1 (en) | 2002-03-27 | 2003-01-27 | Pressure control valve for hydraulic actuation assembly |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/106,225 US6802791B1 (en) | 2002-03-27 | 2002-03-27 | Pressure control valve for hydraulic actuation assembly |
Publications (2)
Publication Number | Publication Date |
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US6802791B1 US6802791B1 (en) | 2004-10-12 |
US20040214678A1 true US20040214678A1 (en) | 2004-10-28 |
Family
ID=28673543
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US10/106,225 Expired - Lifetime US6802791B1 (en) | 2002-03-27 | 2002-03-27 | Pressure control valve for hydraulic actuation assembly |
Country Status (6)
Country | Link |
---|---|
US (1) | US6802791B1 (en) |
EP (1) | EP1490604A1 (en) |
CN (1) | CN1701187A (en) |
AU (1) | AU2003258435A1 (en) |
BR (1) | BR0308657A (en) |
WO (1) | WO2003083321A1 (en) |
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DE10224682A1 (en) * | 2002-06-04 | 2003-12-18 | Bosch Gmbh Robert | Pressure regulator for a fuel supply system of an internal combustion engine |
DE10309351A1 (en) * | 2003-03-03 | 2004-09-16 | Robert Bosch Gmbh | pressure regulator |
US7051857B2 (en) * | 2004-03-08 | 2006-05-30 | Eaton Corporation | Coupling device and improved method of controlling torque transmission |
US7318511B2 (en) * | 2005-06-27 | 2008-01-15 | Eaton Corporation | Coupling device independent of differential speed |
GB0907607D0 (en) * | 2009-05-01 | 2009-06-10 | Wabco Automotive Uk Ltd | Vacuum pump |
WO2013155138A1 (en) * | 2012-04-13 | 2013-10-17 | Eaton Corporation | Limited-slip driveline apparatus |
US9074671B2 (en) | 2012-10-10 | 2015-07-07 | Eaton Corporation | Limited slip differential |
US9382954B2 (en) * | 2014-05-22 | 2016-07-05 | Gm Global Technology Operations, Llc | Temperature compensated torque limiting valve |
US9435173B2 (en) * | 2014-06-26 | 2016-09-06 | Woods Petroleum Llc | Production string pressure relief system |
US10227998B2 (en) | 2015-12-31 | 2019-03-12 | Cnh Industrial America Llc | System for controlling the supply of hydraulic fluid to a work vehicle implement |
US10104826B2 (en) | 2016-01-29 | 2018-10-23 | Cnh Industrial America Llc | System for controlling the supply of hydraulic fluid to a work vehicle implement |
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-
2002
- 2002-03-27 US US10/106,225 patent/US6802791B1/en not_active Expired - Lifetime
-
2003
- 2003-01-27 CN CNA038070693A patent/CN1701187A/en active Pending
- 2003-01-27 EP EP03745508A patent/EP1490604A1/en not_active Withdrawn
- 2003-01-27 AU AU2003258435A patent/AU2003258435A1/en not_active Abandoned
- 2003-01-27 WO PCT/US2003/002205 patent/WO2003083321A1/en not_active Application Discontinuation
- 2003-01-27 BR BR0308657A patent/BR0308657A/en not_active IP Right Cessation
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Also Published As
Publication number | Publication date |
---|---|
BR0308657A (en) | 2005-02-09 |
WO2003083321A8 (en) | 2004-01-22 |
US6802791B1 (en) | 2004-10-12 |
EP1490604A1 (en) | 2004-12-29 |
WO2003083321A1 (en) | 2003-10-09 |
CN1701187A (en) | 2005-11-23 |
AU2003258435A1 (en) | 2003-10-13 |
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