阅读说明：本技术 离合器系统及包括该离合器系统的变速器 (Clutch system and transmission comprising same ) 是由 J·德特勒 C·坎普顿 M·坎贝尔 于 2019-05-29 设计创作，主要内容包括：一种离合器系统,包括离合器板和与离合器板联接的储存器。储存器构造成在离合器板旋转时接收从离合器提捞的过量流体。离合器系统还包括与离合器板和储存器流体联接的液压控制阀。第一流体流动路径在储存器和离合器板之间限定。此外,液压控制阀包括与储存器流体联接的孔口和构造成在关闭位置和打开位置之间移动的润滑油阀。另外,在液压控制阀中限定腔。最后,润滑油阀在打开位置和关闭位置之间移动是使用来自储存器的流体来控制的,来自储存器的流体流过孔口并流入腔中。(a clutch system includes clutch plates and a reservoir coupled to the clutch plates. The reservoir is configured to receive excess fluid scooped up from the clutch as the clutch plates rotate. The clutch system also includes a hydraulic control valve fluidly coupled to the clutch plate and the reservoir. A first fluid flow path is defined between the reservoir and the clutch plate. Further, the hydraulic control valve includes an orifice fluidly coupled with the reservoir and a lube valve configured to move between a closed position and an open position. Additionally, a cavity is defined in the hydraulic control valve. Finally, movement of the lube valve between the open and closed positions is controlled using fluid from the reservoir, which flows through the orifice and into the chamber.)

1. A clutch system operatively coupled to a vehicle engine, the clutch system comprising:

A clutch plate configured to rotate when the engine is started;

A reservoir coupled with the clutch plates, wherein the reservoir is configured to receive excess fluid scooped up from the clutch plates as the clutch plates rotate; and

A hydraulic control valve fluidly coupled with the clutch plates and the reservoir and defining a first fluid flow path therebetween, the hydraulic control valve comprising:

A protrusion defining an aperture fluidly coupled with the reservoir, an

a lubrication valve configured to move between a closed position in which the first fluid flow path is blocked and an open position in which the first fluid flow path is fully open; wherein a cavity is defined in the hydraulic control valve when the lube valve is in the closed position or between the closed position and the open position;

Wherein movement of the lube valve between the closed position and the open position is controlled using the fluid from the reservoir, the fluid from the reservoir configured to flow through the orifice and into the cavity.

2. The clutch system of claim 1, wherein the clutch system does not include a pump.

3. The clutch system of any of claims 1 or 2, wherein the clutch plate includes at least one protrusion extending from the clutch plate, wherein the at least one protrusion is configured to direct the excess fluid scooped up from the clutch toward the reservoir.

4. A clutch system as set forth in claim 3 wherein said at least one projection includes a plurality of radially extending projections spaced circumferentially about said clutch plate.

5. The clutch system of any of claims 1 or 2, wherein the lube valve moves between the closed position and the open position based on a mechanical or hydraulic input, wherein the input acts directly on an actuation piston moving the actuation piston between a first position and a second position that actuates the lube valve to move between the closed position and the open position.

6. The clutch system of any of claims 1 or 2, wherein the lube valve moves from the closed position to the open position based on driver input.

7. a clutch system according to any one of claims 1 or 2, wherein the clutch system is provided within a manual transmission.

8. A clutch system as claimed in any one of claims 1 or 2, wherein the clutch system is provided within a dual clutch transmission.

9. the clutch system of claim 5, wherein the lubrication valve is configured to move between the open position and the closed position independently of the actuation piston.

10. The clutch system of any one of claims 1 or 2, wherein the hydraulic control valve further comprises a check valve disposed at an outlet of the hydraulic control valve, the check valve configured to allow fluid to be removed from the cavity.

11. The clutch system of claim 7, wherein the clutch system is disposed within a funnel shaped cover.

12. A vehicle transmission system operatively coupled to a vehicle engine, the transmission comprising:

A vehicle transmission coupled to the vehicle engine and including a funnel shaped cover; and

The clutch system of claim 1 disposed within the funnel shaped cover.

13. a method of controlling a hydraulic control valve in a clutch system operably coupled to a vehicle engine and disposed within a funnel shaped shroud, the clutch system comprising a clutch plate configured to rotate when the engine is started; a reservoir coupled with the clutch plate and the hydraulic control valve fluidly coupled with the clutch plate and the reservoir and defining a first fluid flow path between the reservoir and the clutch plate, the hydraulic control valve including a protrusion defining an aperture fluidly coupled with the funnel; and a lube valve configured to move between a closed position in which the first fluid flow path is blocked and an open position in which the first fluid flow path is fully open; wherein a cavity is defined in the hydraulic control valve when the lube valve is in the closed position or between the closed position and the open position, the method comprising:

(ii) scooping excess fluid from the clutch plates into the reservoir as the clutch plates rotate;

moving the lube valve between the closed position and the open position such that fluid from the reservoir lubricates the clutch plates; and

Controlling the movement of the lube valve back to the closed position using fluid from the funnel shaped cap through the orifice into the cavity.

14. The method of claim 13, further comprising directing the excess fluid from the clutch plate into the reservoir using a plurality of protrusions disposed about the clutch plate as the clutch plate rotates.

15. The method of any of claims 13 or 14, wherein the clutch system does not include a pump.

Technical Field

the present invention generally relates to a clutch system including a bailing system for controlling fluid and a passive hydraulic control valve, and a method of controlling the hydraulic control valve.

background

Conventional vehicles include an engine operatively coupled with a clutch system. The clutch system generally includes a clutch plate, a valve, and a pump. The pump is configured to move fluid to the valve to provide lubrication to the clutch plates. In conventional clutch systems, the clutch plates rotate when started by the engine, and excess fluid falls into a sump.

Conventional vehicles may use a pump to move fluid from the sump back through the valve for lubricating the clutch plates. However, using a pump to reuse fluid that has fallen into the sump requires additional power usage and additional materials, which adds undesirable weight to the vehicle. Thus, there remains a need to reuse excess fluid from the clutch plates without the use of a pump or other electronics. In addition, there remains a need for a hydraulic control valve that passively allows fluid flow to the clutch after the clutch slips, without the use of electronics.

Disclosure of Invention

A clutch system operatively coupled to a vehicle engine is disclosed. The clutch system includes a clutch plate configured to rotate when the engine is started. The clutch system also includes a reservoir coupled with the clutch plate. The reservoir is configured to receive excess fluid lifted from the clutch plates as the clutch plates rotate. The clutch system also includes a hydraulic control valve fluidly coupled to the clutch plate and the reservoir. A first fluid flow path is defined between the clutch plate and the reservoir. Further, the hydraulic control valve includes a protrusion defining an orifice fluidly coupled with the reservoir and a lube valve configured to move between a closed position where the first fluid flow path is blocked and an open position where the first fluid flow path is fully open. Additionally, a cavity is defined in the hydraulic control valve when the lube valve is in a closed position or between the closed position and an open position. Finally, fluid from a reservoir configured to flow through the orifice and into the cavity is used to control movement of the lube valve between the closed position and the open position.

a clutch system is disclosed that is operatively coupled to a vehicle engine and disposed within a funnel shaped cover. The clutch system includes a clutch plate configured to rotate when the engine is started. The clutch system also includes a reservoir coupled with the clutch plate. The reservoir is configured to receive excess fluid lifted from the clutch plates as the clutch plates rotate. The clutch system also includes a hydraulic control valve fluidly coupled to the clutch plate and the reservoir. A first fluid flow path is defined between the clutch plate and the reservoir. Further, the hydraulic control valve includes a protrusion defining an aperture fluidly coupled with the funnel shaped cover and a lube valve configured to move between a closed position in which the first fluid flow path is blocked and an open position in which the first fluid flow path is fully open. Additionally, a cavity is defined in the hydraulic control valve when the lube valve is in a closed position or between the closed position and an open position. Finally, movement of the lube valve between the closed position and the open position is controlled using fluid from the funnel shaped cover configured to flow through the orifice and into the cavity.

A vehicle transmission system operatively coupled to a vehicle engine is disclosed. The transmission system includes a vehicle transmission coupled to a vehicle engine and includes a funnel shroud. Additionally, the vehicle transmission system includes a clutch system disposed within the funnel shaped cover. A method of controlling a hydraulic control valve in a clutch system is also disclosed.

The ability to provide lubrication to the clutch plates using a bailing system that includes the clutch plates and a reservoir provides all of the benefits of pumping excess fluid from the sump for lubricating the clutch without the added expense, energy usage, or space requirements of using the pump.

Drawings

Other advantages of the present invention will be readily appreciated, as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:

FIG. 1 is a cross-sectional view of a vehicle having a powertrain;

FIG. 2A is a schematic illustration of a clutch system;

FIG. 2B is a perspective view of an exemplary clutch plate of the clutch system;

FIG. 2C is a perspective view of the bailing system of the clutch system;

FIG. 3A is a perspective view of a housing of a portion of the clutch system;

FIG. 3B is a top view of the housing of the clutch system;

FIG. 4 is a cross-sectional view of the clutch system;

FIG. 5 is a cross-sectional view of the clutch system with the lube valve in the closed position;

FIG. 6 is a cross-sectional view of the clutch system with the lube valve in an open position;

FIG. 7 is a cross-sectional view of the clutch system with the lube valve between the closed and open positions;

FIG. 8 is a cross-sectional view of the clutch system with the lube valve returned to a closed position;

FIG. 9 is a cross-sectional view of a clutch system according to another embodiment;

FIG. 10 is a cross-sectional view of a clutch system according to yet another embodiment; and

FIG. 11 is a cross-sectional view of a clutch system according to yet another embodiment.

Detailed Description

referring now to the drawings, wherein like reference numerals are used to refer to like structures unless otherwise specified, a powertrain for a vehicle is schematically illustrated at 10 in the drawings. As shown in FIG. 1, the powertrain 10 includes an engine 12 in rotational communication with a transmission 14. The transmission 14 may be any type of transmission including a manual, automatic, or semi-automatic transmission as known to those of ordinary skill in the art. In one exemplary embodiment, the transmission 14 is a manual transmission; however, it is contemplated that transmission 14 may be any type of automatic or semi-automatic transmission including, but not limited to, a Dual Clutch Transmission (DCT). It should also be appreciated that the engine 12 and transmission 14 of FIG. 1 are of the type employed in conventional "transverse front wheel drive" powertrains. It should also be appreciated that the engine 12 and/or transmission 14 may be configured in any suitable manner sufficient to generate and convert rotational torque to drive the vehicle 10 without departing from the scope of the present invention.

the engine 12 generates rotational torque that is selectively converted to the transmission 14, which in turn, the transmission 14 converts the rotational torque to one or more wheels via the clutch system 16. Hydraulic fluid is typically used to control the transmission 14. To this end, a hydraulic control valve 22 is used to control the flow of fluid to the clutch system 16, and more specifically, to the clutch plates 20 of the clutch system 16.

still referring to the embodiment shown in fig. 1, clutch system 16 is fluidly coupled to powertrain system 10 and is configured to move hydraulic fluid to clutch plates 20 as needed for cooling and/or lubrication purposes. As best shown in fig. 1, the clutch system 16 is typically disposed in a funnel-shaped cover 24 of the transmission 14, which is generally disposed adjacent the engine 12 and adjacent the remainder of the transmission. The clutch system 16 is typically a wet clutch system, but may be any type of clutch system known to one of ordinary skill in the art, including, but not limited to, any type of friction clutch system.

the clutch system 16 includes a clutch having clutch plates 20. In the embodiment shown in fig. 2, the clutch plate 20 is a disc-shaped plate having a hole defined through the center. However, it is also contemplated that clutch plate 20 may be another shape, or may have any number of apertures, or may not have apertures, as desired by one of ordinary skill in the art. Further, as shown in fig. 2B, the top surface 26 of the clutch plate 20 includes at least one protrusion 28 extending therefrom. In the embodiment shown in FIG. 2B, the top surface is a flat surface of the clutch plate 20, however, it is contemplated that the top surface 26 may be any surface of the clutch plate 20, including but not limited to a flat surface or a curved surface of a disc-shaped clutch plate. In the embodiment shown in FIG. 2B, the top surface 26 of the clutch plate 20 includes a plurality of circumferentially spaced protrusions 28 disposed about the clutch plate 20. In the embodiment shown in fig. 2B, the protrusion 28 extends radially from the aperture toward the distal edge of the top surface 26 of the clutch plate 20. However, it is also contemplated that the protrusions 28 may be provided in another arrangement, including, but not limited to, an alternating protrusion arrangement, a triangular arrangement, or a quartered arrangement. Additionally, it is contemplated that the protrusion 28 may extend in a straight line from an aperture in the distal edge of the top surface 26 of the clutch plate 20, or the protrusion 28 may include one or more curved portions. Further, it is contemplated that the protrusion 28 does not extend all the way to the aperture and/or all the way to the distal edge of the top surface 26 of the clutch plate 20, but rather only a portion thereof. Additionally, it is contemplated that each of the plurality of protrusions may have the same shape, size, and/or configuration as one another, or each of the plurality of protrusions may have a different shape, size, and/or configuration as one another, or a combination thereof.

the protrusion 28 also has a height defined as the distance the protrusion 28 extends from the top surface 26 of the clutch plate 20. It is contemplated that the protrusion 28 may have a constant height, or may have a height that varies as the protrusion 28 extends toward the distal edge of the top surface 26 of the clutch plate 20. In the embodiment shown in fig. 2B, the height of the protrusion 28 increases as the protrusion 28 extends toward the distal edge of the top surface 26. However, it is also contemplated that the height of the protrusion 28 may decrease as the protrusion 28 extends toward the distal edge of the top surface 26. Further, it is contemplated that the height of the protrusion 28 may increase and then decrease as the protrusion 28 extends toward the distal edge of the top surface 26.

in addition, the protrusion 28 also has a thickness defined as the distance between a first sidewall 30 of the protrusion 28 and a second sidewall 32 of the protrusion 28. It is contemplated that the protrusion 28 may have a constant thickness, or may have a thickness that varies as the protrusion 28 extends toward the distal edge of the top surface 26 of the clutch plate 20. In the embodiment shown in fig. 2B, the thickness of the protrusion 28 decreases as the protrusion 28 extends toward the distal edge of the top surface 26. However, it is also contemplated that the thickness of the protrusion 28 may increase as the protrusion 28 extends toward the distal edge of the top surface 26. Further, it is contemplated that the thickness of the protrusion 28 may increase and then decrease as the protrusion 28 extends toward the distal edge of the top surface 26.

As described above, the clutch plate 20 is configured to rotate when the engine 12 is started. Further, when the clutch plate 20 rotates, the protrusions 28 on the clutch plate 20 are configured to direct the excess fluid toward a desired location using a centripetal force generated by the rotation of the clutch plate 20, so as to reuse the excess fluid. As such, it is contemplated that the projections 28 may be of any shape, size, configuration, and number desired by one of ordinary skill in the art to direct excess fluid to a desired location.

FIG. 2 schematically illustrates one embodiment of bailing system 34, including clutch plate 20 and reservoir 36. In another embodiment of bailing system 34, clutch plate 20 includes a bailing plate fixedly connected to the clutch plate such that when the engine starts clutch plate 20, the bailing plate also rotates. Further, in this embodiment, the bailing pan includes a protrusion 28, the protrusion 28 configured to direct excess fluid into the reservoir 36 when rotated. In the embodiment shown in fig. 2, the protrusions 28 of the clutch plates 20 are configured to direct excess fluid into the reservoir 36 as the clutch plates 20 rotate. It is contemplated that the reservoir 36 may receive excess fluid through one or more inlet holes defined in the reservoir 36, the closed tube, the open channel 38, or through another method known to those of ordinary skill in the art. In the embodiment shown in fig. 2C, the protrusion 28 is configured to direct excess fluid into the channel 38, and the channel 38 delivers the excess fluid into the reservoir 36. In the embodiment shown in fig. 2C, the passage 38 is a tube having an opening at one end to receive fluid from the clutch plate 20 and an opening at the other end to allow fluid to flow into the reservoir 36. It is also contemplated that the channel 38 may be an open channel such that excess fluid may be received into the channel 38 anywhere along the length of the channel 38. Further, as desired by one of ordinary skill in the art, it is contemplated that the protrusion 28 is configured to direct fluid directly into the reservoir 36 without the use of the channel 38. Additionally, it is contemplated that excess fluid may be simultaneously directed into the channel 38 and directly into the reservoir 36, as desired by one of ordinary skill in the art. Additionally, it is contemplated that the clutch system 30 may include a plurality of reservoirs 36 arranged in any arrangement that collect fluid from the rotating clutch plates 20.

As best shown in fig. 3A and 3B, the reservoir 36 and hydraulic control valve 22 are disposed in a housing 40. In the embodiment shown in fig. 3A and 3B, the housing 40 is a generally rectangular housing 40 having a plurality of apertures for coupling with other equipment. It is contemplated that housing 40 may have any number of apertures as desired by one of ordinary skill in the art. Additionally, it is contemplated that the housing 40 may be made of steel. However, it is also contemplated that the housing 40 may comprise any material including, but not limited to, stainless steel, aluminum, or a plastic polymer.

In the embodiment shown in FIG. 4, the reservoir 36 has a generally rectangular cross-section, however, it is contemplated that the reservoir 36 may be any size or shape desired by one of ordinary skill in the art. As shown in fig. 1, the reservoir 36 is generally disposed within the funnel shaped enclosure 24 such that the size and shape of the funnel shaped enclosure 24 may define the size and shape of the reservoir 36. However, it is also contemplated that the reservoir 36 may be disposed elsewhere in the power system. As also shown in fig. 4, the reservoir 36 includes a plurality of outlets. In the embodiment shown in FIG. 4, the reservoir 36 includes a first outlet 42 and a second outlet 44, however, any number of outlets may be included.

Referring now to fig. 4-9, the reservoir 36 is fluidly coupled to the hydraulic control valve 22. The hydraulic control valve 22 is fluidly coupled to both the clutch plates 20 and the reservoir 36, and is configured to control fluid flow from the reservoir 36 to the clutch plates 20. In the embodiment shown in fig. 5-9, the hydraulic control valve 22 includes first and second inlets 46, 48 and first and second outlets 50, 52. However, it is also contemplated that hydraulic control valve 22 may include any number of inlets and/or outlets as desired by one of ordinary skill in the art. The hydraulic control valve 22 also defines a first fluid flow path 54, the first fluid flow path 54 being configured to provide lubrication to the clutch from the reservoir 36 when needed. More specifically, the first fluid flow path 54 is a path in which fluid is configured to flow from the first outlet 42 of the reservoir 36, through the first inlet 46 of the hydraulic control valve 22, through the first outlet 50 of the hydraulic control valve 22, and to the clutch.

The hydraulic control valve 22 also includes a lube valve 60. The lube valve 60 may be a piston or other device configured to move between a closed position 62 and an open position 64. In the embodiment illustrated in fig. 4-9, when the lube valve 60 is in the closed position 62, as shown in fig. 6, the lube valve 60 fully blocks the first fluid path so that no fluid flows to the clutch. 4-9, when the lube valve 60 is in the open position 64, as shown in FIG. 7, the first fluid flow path 54 is fully open so that the lube valve 60 does not block the first fluid flow path 54. In the embodiment shown in FIG. 6, the lube valve 60 is generally cylindrical with a cut-out portion that aligns with the first fluid flow path 54 allowing fluid to flow therethrough when the lube valve 60 is in the open position 64. However, it is also contemplated that the lube valve 60 may have any other shape including, but not limited to, annular, conical, disc-shaped, or rectangular configured to block the first fluid path in the closed position 62 and allow fluid flow through the first fluid path in the open position 64. In the embodiment shown in fig. 4-9, lubrication valve 60 is composed of steel, however, it is also contemplated that lubrication valve 60 may be constructed of another material including, but not limited to, stainless steel, plastic polymer, or aluminum, as desired by one of ordinary skill in the art. In the embodiment shown in fig. 4-9, the lube valve 60 is a spring biased valve such that the lube valve 60 includes a spring 66. In one embodiment, the spring 66 allows the lube valve 60 to move from the closed position 62 to the open position 64.

As shown in fig. 4-9, the hydraulic valve assembly also includes an actuation valve 70. Actuation valve 70 is configured to move between a rest position and an actuated position 74. Further, the actuation valve 70 is configured to move the lubrication valve 60 from the closed position 62 to the open position 64. In the embodiment illustrated in fig. 4-9, the actuator valve 70 is generally cylindrical and is disposed adjacent the lube valve 60. It is also contemplated that actuation valve 70 may be any shape, including but not limited to conical, disk-shaped, or rectangular. In the embodiment shown in fig. 4-9, actuation valve 70 is made of steel, however, it is also contemplated that actuation valve 70 may be made of another material including, but not limited to, stainless steel, plastic polymer, or aluminum, as desired by one of ordinary skill in the art. In the embodiment shown in fig. 4-9, actuation valve 70 is a spring-biased valve such that actuation valve 70 includes a spring 76.

in one embodiment, the clutch input 80 acts on the spring 76 to move the actuation valve 70 from the rest position to the actuated position 74 such that movement of the lube valve 60 from the closed position 62 to the open position 64 is actuated by the clutch input 80. In one embodiment, the clutch input 80 is coupled to a clutch pedal that is actuated when the driver desires to shift gears. It is also contemplated that clutch input 80 may be any type of input 80 including, but not limited to, a hydraulic input, a mechanical input, or an electronic input. In the embodiment illustrated in fig. 5-9, clutch input 80 actuates actuation valve 70 to move from the rest position to actuation position 74, which moves lubrication valve 60 from closed position 62 to open position 64. More specifically, in the embodiment illustrated in fig. 5-9, the actuator valve 70 includes an actuator pin 82, and the actuator pin 82 is configured to engage the lube valve 60 to move the lube valve 60 from the closed position 62 to the open position 64. As best shown in fig. 6, it is contemplated that the lubrication valve 60 may include a notch 84 or other engagement element configured to allow the actuator pin 82 to engage the lubrication valve 60 and move the lubrication valve 60 from the closed position 62 to the open position 64. As shown in fig. 7, the actuator valve 70 may be independent of the lube valve 60 such that the actuator valve 70 may move from the actuated position 74 back to the rest position independent of the lube valve 60.

The hydraulic control valve 22 also defines a second fluid flow path 86. In the second fluid flow path 86, fluid is configured to flow from the second outlet 44 of the reservoir 36, through the second inlet 48 of the hydraulic control valve 22, and into a cavity 88 defined in the hydraulic control valve 22. A cavity 88 is defined in the hydraulic control wall between the lubrication valve 60 and the wall of the hydraulic control valve 22. In addition, the hydraulic control valve 22 includes an orifice 90 disposed between the second inlet 48 of the hydraulic control module and the cavity 88. The orifice 90 is sized and shaped to allow fluid to flow into the cavity 88 at a predetermined rate. In the embodiment shown in fig. 5-9, the aperture 90 is defined by a projection 91 extending into the second fluid flow path 86, the projection 91 having an aperture 90 defined therethrough to allow fluid to continue to flow into the cavity 88. The projection 91 may be generally U-shaped such that a portion of the projection is aligned with the inlet 48. The remainder of the tab 91 is generally flat with an aperture 90 defined therethrough. In the embodiment shown in fig. 5-9, the orifice is circular and centrally defined on the projection 91, however, it is also contemplated that the orifice may be any shape, size, or location that permits a desired flow rate of fluid into the cavity 88. It is also contemplated that the protrusion defining the aperture may be any shape and size desired by one of ordinary skill in the art. In some embodiments, it is additionally contemplated that the fluid flowing into the cavity is air or another gas without departing from the spirit of the present invention.

In another exemplary embodiment, the second fluid flow path 86 is defined as a fluid flow path from the funnel-shaped cover 24 through the second inlet 48 of the hydraulic control valve 22 and into a cavity 88 defined in the hydraulic control valve 22. In this embodiment, it is contemplated that the fluid may be the same liquid fluid as described above, or the fluid may be air, such that ambient air from funnel-shaped shroud 24 flows into cavity 88. In this embodiment, the orifice is fluidly coupled to the funnel shaped cover 24 and fluid from the funnel shaped cover 24 configured to flow through the orifice and into the cavity is used to control movement of the lube valve between the closed position and the position.

As shown in the embodiment illustrated in fig. 5-9, when the clutch input 80 is actuated and the lube valve 60 moves from the closed position 62 to the open position 64, the lube valve 60 pushes fluid in the cavity 88 toward the second outlet 52 of the hydraulic control valve 22. It is contemplated that the second outlet 52 of the hydraulic control valve 22 may include a check valve 96. In the embodiment illustrated in fig. 5-9, the check valve 96 is a ball check valve, however, it is contemplated that the check valve 96 may be any type of valve configured to prevent backflow. Further, it is contemplated that the second outlet 52 may be fluidly coupled to the fluid reservoir 36 such that fluid exiting the second outlet 52 flows to a sump. Additionally, it is also contemplated that the second outlet 52 is fluidly coupled to the sump such that when fluid exits the second outlet 52, the fluid moves to the sump.

when clutch input 80 is deactivated, actuation valve 70 moves back to the rest position. As described above, the actuation valve 70 is configured to move from the actuated position 74 back to the rest position independently of the lube valve 60. Thus, the lube valve 60 remains in the open position 64 that allows fluid to remain flowing to the clutch. However, movement of actuator valve 70 back to the rest position creates a vacuum force that forces fluid from reservoir 36, through second inlet 48 of hydraulic control valve 22, through orifice 90, and into chamber 88. As more fluid enters the cavity 88, the lube valve 60 slowly returns to the closed position 62. However, by not immediately returning to the closed position 62 when the clutch input 80 is deactivated, lubrication is supplied to the clutch after the clutch input 80 has been deactivated.

In operation, as shown in fig. 5-9, when the engine 12 is started, the clutch plate 20 begins to rotate. Rotating the clutch plates 20 uses the protrusions 28 to direct excess fluid from the clutch plates 20 into the reservoir 36. When the clutch input 80 is activated, i.e., by the driver depressing the clutch pedal, the actuation valve 70 moves from the rest position to the actuation position 74, which moves the lube valve 60 from the closed position 62 to the open position 64. When the lube valve 60 is in the open position 64, fluid is free to flow in the first fluid flow path 54 such that fluid from the reservoir 36 passes through the valve to the clutch. When clutch input 80 is deactivated, i.e., by the driver releasing the clutch pedal, actuation valve 70 moves from actuation position 74 back to the rest position. The actuated valve 70 moves back to the rest position causing fluid to flow through the second outlet 44 of the reservoir 36, through the orifice 90, and into the cavity 88. When the cavity 88 fills, the fluid pushes the lube valve 60 back to the closed position 62. The flow of fluid from the reservoir 36 to the cavity 88 is controlled by the orifice 90, slowing the movement of the lube valve 60 back to the closed position 62, which provides additional fluid to the clutch. This additional fluid allows for cooling of the clutch and reduced drag. When the clutch input 80 is again activated, the actuation valve 70 moves from the rest position to the actuation position 74, which moves the lube valve 60 from the closed position 62 to the open position 64. Movement of the lube valve 60 to the open position 64 forces fluid from the chamber 88 through the check valve 96 to the outlet. Allowing fluid to remain flowing to the clutch after clutch input 80 has been deactivated allows flow to the clutch to be passively metered and does not require additional electronics. In addition, the use of bailing system 34 to reuse excess fluid eliminates the need for a pump while still reusing excess fluid.

Referring now to fig. 9-11, various embodiments of the hydraulic control valves 122, 222, 322 are also contemplated. The hydraulic control valves 122, 222, 322 shown in fig. 9-11 may be used in place of the hydraulic control valve 22 described above. 9-11, various configurations of cavities 188, 288, 388, lube valves 160, 260, 360, and actuation valves 170, 270, 370, as well as various positions of orifices 190, 290, 390, have been contemplated.

More specifically, the embodiment shown in FIG. 9 includes a lube valve 160, an actuation valve 170, and a third valve 198. In the embodiment shown in fig. 9, the third valve 198 is independent of the lube valve 160 and the actuator valve 170, and the movement of the lube valve 160 and the actuator valve 170 are dependent on each other.

in the embodiment shown in FIG. 10, the hydraulic control valve 222 includes a lube valve 260 and an actuation valve 270 similar to the hydraulic control valve 22 described above. However, in the embodiment shown in FIG. 10, the orifice 290 and check valve 296 are defined/disposed within the lubrication valve. In the embodiment shown in fig. 10, the lube valve and the actuator valve 270 move interdependently. Additionally, the orifice 290 controls the movement of the lube valve back to the closed position 262 by fluid drawn into the cavity 288 due to forces from the movement of the lube valve and the actuator valve 270.

In the embodiment shown in FIG. 11, the hydraulic control valve 322 is similar to the embodiment shown in FIG. 10, having an orifice 390 defined/disposed within the lube valve 360 and a check valve 396. Additionally, the spring 376 of the actuator valve 370 is a separate spring 376 so that the actuator valve 370 can move independently of the lube valve 360. Also, in the embodiment shown in FIG. 11, orifice 390 controls the movement of lubrication valve 360 back to closed position 362 by fluid drawn into cavity 388 due to the force from the movement of lubrication valve 360.

in operation, the embodiment of the hydraulic control valves 122, 222, 322 shown in FIGS. 9-11 operate similarly to the embodiment of the hydraulic control valve 22 shown in FIGS. 5-9. More specifically, when the engine 12 is started, the clutch plate 20 starts to rotate. Rotating the clutch plates 20 uses the protrusions 28 to direct excess fluid from the clutch plates 20 into the reservoir 36. When the clutch input 80 is activated, i.e., by the driver depressing the clutch pedal, the actuation valves 170, 270, 370 move from the rest position to the actuated position, which moves the lubrication valves 160, 260, 360 from the closed position to the open position. When the lube valve 160, 260, 360 is in the open position 64, fluid is free to flow in the first fluid flow path 54 such that fluid from the reservoir 36 passes through the hydraulic control valve 122, 222, 322 to the clutch. When the clutch input 80 is deactivated, i.e., by the driver releasing the clutch pedal, at least the actuation valves 170, 270, 370 move from the actuated position back to the rest position. The cavity 188, 288, 388 is then filled with fluid from the reservoir 36, which flows through the orifice 190, 290, 390 before entering the cavity 188, 288, 388. The controlled fluid flow of the orifices 190, 290, 390 moves at least the lube valve 160, 260, 360 back to the closed position. Fluid flows from the reservoir 36 to the cavity 188, 288, 388, which is controlled by the orifices 190, 290, 390, slowing the movement of the lube valve 160, 260, 360 back to the closed position, which provides additional fluid to the clutch 20. This additional fluid allows for cooling of the clutch and reduced drag. When the clutch input 80 is again activated, the actuation valve 170, 270, 370 moves from the rest position to the actuated position, which moves the lube valve 160, 260, 360 from the closed position to the open position. The lube valve 160, 260, 360 moves to an open position, which pushes fluid from the cavity 188, 288, 388 through the check valve 196, 296, 396 to an outlet.

allowing fluid to remain flowing to the clutch after clutch input 80 has been deactivated allows flow to the clutch to be passively metered and does not require additional electronics. In addition, the use of bailing system 34 to reuse excess fluid eliminates the need for a pump while still reusing excess fluid.

The present invention has been described in an illustrative manner, and it is to be understood that the terminology used is intended to be in the nature of description rather than of limitation. Many modifications and variations of the present invention are possible in light of the above teachings, and the invention may be practiced otherwise than as specifically described.