Dual clutch pack dual operating clutch and method for adjusting same

Abstract

A dual automatic mechanically actuated wet clutch device, for operation within a fluid tight housing, for a dual input shaft transmission that includes tightly specified average spacing between friction plate surfaces where the average spacing is selected from between about 0.05 mm to about 0.25 mm in an open position. The clutch has at least first and second independently actuatable clutch portions, and at least one clutch pack in the first or second clutch portion; and mechanical apparatus provided to move friction plates in at least one of the clutch portions toward each other so that they engage. The invention also includes apparatus and methods for adjusting and maintaining the spacing between the friction plate surfaces.

Description

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

FIG. 1 is an upper half cross sectional side view of a first preferred embodiment of a dual output clutch in accordance with the invention.

FIG. 2 is an upper half cross sectional side view of a second preferred embodiment of a dual output clutch in accordance with the invention.

FIG. 3 is an upper half cross sectional side view of a third preferred embodiment of a dual output clutch in accordance with the invention.

FIG. 4 is an upper half cross sectional side view of a fourth preferred embodiment of a dual output clutch in accordance with the invention.

FIG. 5 is an upper half cross sectional side view of a fifth preferred embodiment of a dual output clutch in accordance with the invention.

FIG. 6 is an upper half cross sectional side view of a sixth preferred embodiment of a dual output clutch in accordance with the invention.

FIG. 7 is an upper half cross sectional disassembled side view of a seventh preferred embodiment of a dual output clutch in accordance with the invention.

FIG. 8 is an upper half cross sectional side view of the assembled preferred embodiment of FIG. 7.

FIG. 9 is an upper half cross sectional side view of an eighth preferred embodiment of a dual output clutch in accordance with the invention.

Claims

1. A clutch, for at least partial operation within a fluid tight housing containing fluid, said clutch comprising first and second independently actuatable first and second clutch portions a) said first clutch portion including: a first clutch portion clutch pack including: i) a first clutch pack first series of coaxial friction plates engaged with a first drive ring and being axially movable in relation thereto, said first drive ring acting as at least a portion of a support housing for the clutch, said first drive ring being directly or indirectly connectable to the drive shaft of an engine; andii) a first clutch pack second series of coaxial friction plates engaged with a first driven ring and being axially movable in relation thereto, said driven ring being directly or indirectly connectable to a first input shaft to a transmission,the friction plates of the second series of friction plates being in alternating relationship and coaxial with the friction plates of the first series of friction plates to form a friction plate set, the friction plates of the first series being normally in a spaced relationship with the friction plates of the second series such that there is an average gap of from about 0.05 to about 0.25 mm between adjacent friction plates,said friction plates being movable toward each other along their respective drive and driven rings so as to engage each other on friction surfaces of the friction plates so as to enable the transfer of torque from the drive ring to the driven ring without significant slippage between adjacent friction plates; andb) mechanical apparatus provided to move said friction plates toward each other.

2. The clutch of claim 1 wherein a first mechanical apparatus is provided to move said friction plates toward each other along their respective drive and driven rings so as to engage each other on friction surfaces of the friction plates enabling the transfer of torque from the drive ring to the driven ring.

3. The clutch of claim 2 where the mechanical apparatus comprises at least one lever that, when activated, provides pressure through a fulcrum against an outer friction plate of the clutch pack to move said friction plates so as to engage each other on the friction surfaces enabling the transfer of torque from the drive ring to the driven ring and when deactivated permit return of the friction plates to their normally spaced relationship.

4. The clutch of claim 3 wherein a series of levers are provided such that, when activated, provide pressure against an outer friction plate of the clutch pack to move said friction plates so as to engage each other on the friction surfaces enabling the transfer of torque from the drive ring to the driven ring and when deactivated permit return of the friction plates to their normally spaced relationship.

5. The clutch of claim 1 wherein first and second clutch portions are provided having radially concentric first and second clutch packs respectively for operation within the fluid tight housing, one of said first and second clutch packs being an outer clutch pack having a larger inside diameter than an outside diameter of the other of said first and second clutch packs, said other clutch pack being an inner clutch pack, said second clutch pack comprising: i) a second clutch pack first series of coaxial friction plates engaged with a second drive ring and being axially movable in relation thereto, said second drive ring being directly or indirectly connectable to the drive shaft of an engine; andii) a second clutch pack second series of coaxial friction plates engaged with a second driven ring and being axially movable in relation thereto, said second driven ring being directly or indirectly connectable to a second input shaft to the transmission,the friction plates of the second clutch pack second series of friction plates being in alternating relationship and coaxial with the friction plates of the second clutch pack first series of friction plates to form a friction plate set, the friction plates of the second clutch pack first series being normally in a spaced relationship with the friction plates of the second clutch pack second series such that there is an average gap of from about 0.05 to about 0.25 mm between adjacent friction plates,said friction plates of said second clutch pack being movable toward each other along their respective drive and driven rings so as to engage each other on their surfaces so as to enable the transfer of torque from the second drive ring to the second driven ring without significant slippage between adjacent friction plates wherein a second apparatus is provided to move said friction plates of the second clutch pack toward each other.

6. The clutch of claim 5 wherein the first mechanical apparatus and second apparatus can operate independently of each other so as to engage and disengage the friction plates of the first and second clutch packs independently of each other.

7. The clutch of claim 6 where said first mechanical apparatus is entirely mechanical and said second apparatus comprises hydraulics.

8. The clutch of claim 6 where said second apparatus is mechanical.

9. The clutch of claim 1 wherein the first clutch pack comprises from about 3 to about 8 friction plates, 2 of which are exterior friction plates having a single inwardly facing friction surface and the balance of which are interior friction plates having dual friction surfaces on opposite sides.

10. The clutch of claim 9 wherein the second clutch pack comprises from about 3 to about 8 friction plates, 2 of which are exterior friction plates having a single inwardly facing friction surface and the balance of which are interior friction plates having dual friction surfaces on opposite sides.

11. The clutch of claim 1 wherein sufficient pressure to engage friction plate friction surfaces is provided to permit no more slippage between engaged friction surfaces than is required to dampen engine vibration or to assist in providing a gradual rotational speed transition from the engine to the transmission.

12. The clutch of claim 5 wherein sufficient pressure to engage friction plate friction surfaces is provided to permit no more slippage between engaged friction surfaces than is required to dampen engine vibration or to assist in providing a gradual rotational speed transition from the engine to the transmission.

13. The clutch of claim 6 wherein the first clutch portion is an outer clutch portion having an outer fulcrum that reacts against an outer lever spring and the outer fulcrum directly or indirectly transmits applied force to the outer clutch pack to engage the outer clutch pack friction surfaces, as a result of pressure applied to the fulcrum by the outer lever spring and the clutch is provided with a main clutch bearing permitting clutch rotation and tolerance from the main clutch bearing to a touch point between the outer fulcrum and the outer lever spring is adjusted to permit an average normally open spacing between friction surfaces of between about 0.05 and about 0.25 mm and to permit sufficient pressure on the friction surfaces during engagement to prevent significant slippage during torque transfer.

14. The clutch of claim 13 wherein the second clutch portion is an inner clutch portion having an inner fulcrum that reacts against an inner lever spring and the inner fulcrum directly or indirectly transmits applied force to the inner clutch pack to engage the inner clutch pack friction surfaces, as a result of pressure applied to the inner fulcrum by the inner lever spring and the clutch is provided with a main clutch bearing permitting clutch rotation and tolerance from the main clutch bearing to an inner touch point between the inner fulcrum and the inner lever spring is adjusted to permit an average normally open spacing between inner friction surfaces of between about 0.05 and about 0.25 mm and to permit sufficient pressure on the friction surfaces during engagement to prevent significant slippage during torque transfer.

15. The clutch of claim 13 wherein the adjustment is accomplished by machining a pivot force receiving end of the fulcrum to produce a desired distance from the bearing to the touch point.

16. The clutch of claim 15 wherein a radius approximating half the thickness of the fulcrum is machined at an end of the fulcrum at the touch point to maintain a more consistent lever ratio.

17. The clutch of claim 13 wherein an outer pusher is provided between the outer fulcrum and the outer clutch pack such that the outer fulcrum reacts against the outer lever spring and transmits applied force through the outer pusher to the outer clutch pack to engage the outer clutch pack friction surfaces and tolerance between the main clutch bearing and the outer touch point is adjusted using shims between the clutch plates and the outer pusher,

18. The clutch of claim 17 wherein the outer pusher incorporates an oil dam that prevents cooling oil flow from by-passing the outer clutch pack.

19. The clutch of claim 13 wherein tolerance from the main clutch bearing to the outer touch point between the outer fulcrum and the outer lever spring is adjusted by machining or shimming a push portion of the outer fulcrum.

20. The clutch of claim 13 wherein the outer fulcrum is bent at an inner diameter to increase fulcrum stiffness and to form a surface containing the touch point.

21. The clutch of claim 13 wherein the outer fulcrum is bent to form a surface at a push portion to distribute force over a larger surface area of the outer clutch pack.

22. The clutch of claim 13 wherein an outer lever spring preload is adjusted by machining the support housing at an outer support point for the outer lever spring to adjust support point distance from the clutch main bearing.

23. The clutch of claim 13 where an outer lever spring preload is adjusted by shims between the support housing of the clutch and an outer support point for the outer lever spring.

24. The clutch of claim 13 wherein the clutch support housing for use within a fluid tight housing, comprises an outer plate and an outer carrier and the outer lever spring is assembled to the outer carrier and outer lever spring support point distance from the clutch main bearing is adjusted by connecting the outer carrier to the outer plate to obtain a desired outer lever spring preload.

25. The clutch of claim 14 wherein tolerance from the main clutch bearing to the inner touch point between the inner fulcrum and the inner lever spring is adjusted by machining or shimming a push portion of the inner fulcrum or by machining the pivot portion of the inner fulcrum.

26. The clutch of claim 1 where the first clutch portion first drive ring is provided with interiorly extending slides and the first clutch pack first series of friction plates are provided with grooves that ride on the first drive ring slides.

27. The clutch of claim 1 where the first clutch portion is provided with a series of spaced fingers and the first clutch pack first series of friction plates are provided with tabs that ride in gaps between the fingers.

28. The clutch of claim 1 where the first clutch portion first driven ring is provided with exteriorly extending slides and the first clutch pack second series of friction plates are provided with grooves that ride on the second driven ring slides.

29. The clutch of claim 5 where the second clutch portion second drive ring is provided with interiorly extending slides and the second clutch pack first series of friction plates are provided with grooves that ride on the second drive ring slides.

30. The clutch of claim 5 where the second clutch portion second driven ring is provided with interiorly extending slides and the second clutch pack second series of friction plates are provided with grooves that ride on the second driven ring slides.

31. The clutch of claim 14 wherein the outer drive ring and inner drive ring are interconnected by a support flange having a support point for the outer spring and preload of the outer spring is adjusted by machining the flange at the support point to control the outer spring support position relative to the main clutch bearing.

32. The clutch of claim 31 where a pivot point for the outer spring is located on an outer support housing comprising the outer drive ring and the outer support housing is machined to control the location of the pivot point relative to the main clutch bearing.

33. A method for adjusting a clutch for use within a fluid tight housing wherein the clutch comprises first and second independently actuatable clutch portions each having radially concentric first and second clutch packs respectively, one of said first and second clutch packs being an outer clutch pack having a larger inside diameter than an outside diameter of the other of said first and second clutch packs, said other clutch pack being an inner clutch pack, a) said first clutch portion clutch pack including: i) a first clutch pack first series of coaxial friction plates engaged with a first drive ring and being axially movable in relation thereto, said first drive ring forming at least a portion of an outer support housing for the clutch, and being directly or indirectly connectable to the drive shaft of an engine; andii) a first clutch pack second series of coaxial friction plates engaged with a first driven ring and being axially movable in relation thereto, said driven ring being directly or indirectly connectable to a first input shaft to a transmission,the friction plates of the first clutch pack second series of friction plates being in alternating relationship and coaxial with the friction plates of the first clutch pack first series of friction plates to form a friction plate set, the friction plates of the first series being normally in a spaced relationship with the friction plates of the second series such that there is an average gap of from about 0.05 to about 0.25 mm between adjacent friction plates,said friction plates being movable toward each other along their respective drive and driven rings so as to engage each other on friction surfaces of the friction plates of the first clutch pack so as to enable the transfer of torque from the drive ring to the driven ring without significant slippage between adjacent friction plates; andfirst mechanical apparatus provided to move said friction plates toward each other; andsaid second clutch pack comprising: i) a second clutch pack first series of coaxial friction plates engaged with a second drive ring and being axially movable in relation thereto, said second drive ring being directly or indirectly connectable to the drive shaft of an engine; andii) a second clutch pack second series of coaxial friction plates engaged with a second driven ring and being axially movable in relation thereto, said second driven ring being directly or indirectly connectable to a second input shaft to a transmission,the friction plates of the second clutch pack second series of friction plates being in alternating relationship and coaxial with the friction plates of the second clutch pack first series of friction plates to form a friction plate set, the friction plates of the second clutch pack first series being normally in a spaced relationship with the friction plates of the second clutch pack second series such that there is an average gap of from about 0.05 to about 0.25 mm between adjacent friction plates,said friction plates of said second clutch pack being movable toward each other along their respective drive and driven rings so as to engage each other on their surfaces so as to enable the transfer of torque from the second drive ring to the second driven ring without significant slippage between adjacent friction plates; andsecond mechanical apparatus provided to move said second clutch pack friction plates toward each other;wherein the first clutch portion is an outer clutch portion having an outer fulcrum that reacts against an outer lever spring and the outer fulcrum directly or indirectly transmits applied force to the outer clutch pack to engage the outer clutch pack friction surfaces, as a result of pressure applied to the fulcrum by the outer lever spring;wherein the second clutch portion is an inner clutch portion has an inner fulcrum that reacts against an inner lever spring and the inner fulcrum directly or indirectly transmits applied force to the inner clutch pack to engage the inner clutch pack friction surfaces, as a result of pressure applied to the inner fulcrum by the inner lever spring and the clutch is provided with a main clutch bearing permitting clutch rotation; andwherein the clutch is provided with a main clutch bearing permitting clutch rotation;said method comprising:adjusting tolerance from the main clutch bearing to a touch point between the outer fulcrum and the outer lever spring to permit an average normally open spacing between friction surfaces of between about 0.05 and about 0.25 mm and to permit sufficient pressure on the friction surfaces during engagement to prevent significant slippage during torque transfer; andadjusting tolerance from the main clutch bearing to an inner touch point between the inner fulcrum and the inner lever spring to permit an average normally open spacing between inner friction surfaces of between about 0.05 and about 0.25 mm and to permit sufficient pressure on the friction surfaces during engagement to prevent significant slippage during torque transfer.

34. The method of claim 33 wherein tolerance from the main clutch bearing to the outer touch point between the outer fulcrum and the outer lever spring is adjusted by machining or shimming a push portion of the outer fulcrum or by machining or shimming at the outer pivot portion of the outer fulcrum.

35. The method of claim 33 wherein tolerance from the main clutch bearing to the inner touch point between the inner fulcrum and the inner lever spring is adjusted by machining or shimming a push portion of the inner fulcrum or by machining the pivot portion of the inner fulcrum.

36. The method of claim 33 wherein an outer lever spring preload is adjusted by machining an outer drive ring of the clutch where an outer support point of the lever spring is located to adjust support point distance from the clutch main bearing.

37. The method of claim 33 where an outer lever spring preload is adjusted by shims between an outer drive ring of the clutch and an outer support point for the outer lever spring.

38. The method of claim 33 wherein the clutch outer support housing comprises an outer plate and an outer carrier and an outer lever support point distance from the clutch main bearing is adjusted by connecting the outer carrier to the outer plate based on an outer lever spring preload.

39. The method of claim 33 wherein an outer lever spring preload is adjusted by machining or shimming an outer drive ring of the clutch at an outer lever spring support point.

40. The method of claim 33 wherein an end of at least one fulcrum of at least one of the clutch portions is machined to obtain a radius approximating half of fulcrum thickness of its fulcrum at an end of the fulcrum at the touch point to maintain a more consistent lever ratio.

41. The method of claim 33 wherein a pusher is provided in at least one of the clutch portions between its fulcrum and its clutch pack such that its fulcrum reacts against its lever spring and transmits applied force through the pusher to the clutch pack to engage the clutch pack friction surfaces and tolerance between the main clutch bearing and the touch point is adjusted using shims between the clutch plates and the pusher where the shims are selected according to thickness to adjust distance from the main clutch bearing to the touch point of the clutch portion.

42. The method of claim 33 wherein tolerance from the main clutch bearing to a touch point for at least one of the clutch portions is adjusted by determining distance from a hub bearing surface of the clutch bearing to the clutch portion touch point on the fulcrum on a line parallel to a rotational axis of the drive ring and then machining a pivot end or push end of the fulcrum to produce the desired distance from the bearing to the touch point

43. The method of claim 33 wherein a fulcrum of at least one of the clutch portions is bent down at an inner diameter to improve stiffness of the fulcrum.

44. The method of claim 33 wherein a fulcrum of at least one of the clutch portions is bent inwardly to provide a centrally protruding larger surface area portion to distribute applied force over a larger area of a pusher and tolerance is adjusted by machining or shimming at the larger surface area.

45. The method of claim 33 wherein preload, of at least one of the lever springs of the first and second clutch portions, is adjusted by machining the top of the lever spring, drive ring, or a spring holder attached to the outer housing, at a lever spring support point to obtain a desired distance from the support point to the main clutch bearing to provide the correct preload of the outer lever spring.

46. The method of claim 33 wherein preload, of at least one of the lever springs of the first and second clutch portions, is adjusted by measuring the distance from a support point at a top portion of the outer lever spring at the outer support housing to a main bearing surface of the main clutch bearing and inserting a shim between the outer support housing and the lever spring to obtain a correct distance to obtain the desired preload.

47. The method of claim 33 wherein the support housing is divided into an outer plate and outer carrier and the outer lever spring is assembled to the outer carrier and outer clutch portion tolerance is adjusted by determining the distance of the outer touch point from a clutch bearing surface and connecting the outer carrier to the outer plate at the desired distance to meet tolerance.

48. The method of claim 47 wherein outer spring preload is adjusted by adjusting outer spring support point distance from the clutch bearing by controlling position where the outer carrier is connected to the outer plate and the outer support point and an outer pivot point are both located at parts of the outer carrier and location of the outer support point relative to the main clutch bearing is controlled by sliding the outer carrier into the outer carrier to control preload on the spring relative to an interconnected release bearing.

49. The method of claim 48 wherein at least one of inner spring tolerance and inner spring preload are controlled by adjusting distance from an inner spring pivot point to the outer spring pivot point by stamping tolerance or machining.

50. The method of claim 33 wherein the outer drive ring and inner drive ring are interconnected by a support flange having a support point for the outer spring and preload of the outer spring is adjusted by machining the flange at the support point to control the outer spring support position relative to the main clutch bearing.

51. The method of claim 50 where a pivot point for the outer spring is located on an outer support housing comprising the outer drive ring and the outer support housing is machined to control the location of the pivot point relative to the main clutch bearing.

52. The method of claim 50 comprising: machining the outer support housing outer spring pivot point relative to the main clutch bearing to adjust an outer touch point between the outer spring and outer fulcrum,machining the support flange outer spring support point relative to the main bearing to adjust outer spring preload,machining the support flange at an inner spring pivot point to adjust the inner spring pivot point relative to the outer spring pivot point,assembling the inner clutch pack and inner fulcrum into an inner support housing comprising the inner drive ring while shimming to adjust the inner spring touch point at the inner fulcrum relative to the inner spring support point,assembling the inner spring,securing the inner support housing to the flange,assembling the outer clutch pack while shimming or machining to adjust the outer spring touch point relative to the outer spring support point,assembling the flange within the outer support housing, andinstalling the outer fulcrum and outer spring.