Driveline clutch

Abstract: A first ball ramp actuator (5A) having a control ring (16) acting with an activation ring (18) to supply an axial clutch clamping force in a vehicle driving mode and a second ball ramp actuator (5B) using the activation ring (18) acting with a clutch pressure plate (12) to supply an axial clutch clamping force in a vehicle coast mode where one side of a one-way clutch (38) is attached to the activation ring (18) and another side is attached to a support bracket (37) that is frictionally coupled to the control ring (16) by an electromagnetic coil (30) to maintain an energized rotational relationship with the activation ring (18) when in the coast mode.

Description: Background of the Invention The present invention relates to a vehicle driveline clutch and more particularly, to a driveline clutch where a friction disc is clamped to an engine flywheel using a ball ramp actuator where a one-way clutch is used to provide drive and coast driveline clutch lock-up. Driveline clutches commonly use a plurality of springs to clamp a friction disc to an engine flywheel. The springs are disposed within a pressure plate assembly which is bolted to the flywheel. A mechanical linkage that controls the pressure plate spring mechanism is displaced by the operator to control the lock-up and release of the clutch. Efforts to automate the operation of the clutch using electronics are currently underway. It is known to use an electromechanical or hydraulic actuator connected to the mechanical linkage to, in essence, replace the operator for more accurate clutch operation during transmission shifting. Using such an actuator, the mechanical linkage is moved in response to an electrical control signal generated by a central microprocessor used to process a variety of vehicle sensor inputs and other operating conditions to determine when and in what manner the driveline clutch should be activated, or deactivated. The use of a ball ramp actuator to load a clutch pack in a vehicle driveline differential is known. U.S. Patent Nos. 5,092,825 and 4,805,486 disclose limited slip differentials where a clutch pack is loaded in response to the activation of a ball ramp actuator initiated by rotation of a servo motor or a solenoid driven brake shoe on an activating ring. The advantage of the ball ramp mechanism over other actuators is that it converts rotary motion into axial motion with a very high force amplification, often 100:1 or greater. A ball ramp actuator has also been utilized in a vehicle transmission to engage and disengage gearsets by loading a gear clutch pack in response to a signal as disclosed in U.S. Patent No. 5,078,249. In both of these applications, one side of the ball ramp actuator, commonly called a control ring, reacts against case ground through the force induced by an electromagnetic field generated by a coil or is rotated by an electric motor relative to case ground. To generate greater clamping forces, the electrical current supplied to the coil or motor is increased thereby increasing the reaction of the control ring to case ground which rotates the control ring relative to an activation ring thereby causing rolling elements to engage ramps in the control and activation ring which increase the axial movement and clamping force on the clutch pack. One problem with the use of a ball ramp actuator to supply the clutch clamping force is that the mechanics of prior art unidirectional ball ramp mechanisms result in a loss of clamping force when the vehicle is in a coast mode. Once the engine power is reduced and the driveline is actually over-running the engine (coast mode), the prior art ball ramp actuator with single ramp unidirectional actuation will disengage the clutch thereby eliminating the potential for engine braking of the vehicle. In other words, this type of prior art ball ramp actuated clutch using a ball ramp having only a single ramp angle, will cause the clutch to disengage when the engine is not supplying rotational energy into the transmission when the vehicle is coasting. When coasting, the flywheel is no longer supplying rotational energy to either the transmission or the ball ramp actuator. In this circumstance, the relative rotation of the activation ring and control ring has been reversed such that the ball ramp axial displacement is collapsed thereby allowing the pressure plate to pull away from the clutch disc. The result is that the engine is disengaged from the transmission and any engine braking effort is eliminated. The ball ramp actuator comprises a plurality of roller elements, a control ring and an opposed activation ring where the activation ring and the control ring define at least three opposed single ramp surfaces formed as circumferential semi-circular grooves, each pair of opposed grooves containing one roller element. A plurality of thrust balls (or other type of thrust bearing) are interposed between the control ring and a housing member, rotating with and connected to the input member such as a flywheel. An electromagnetic coil is disposed adjacent to one element of a control clutch so as to induce a magnetic field that loads the control clutch which in turn applies a force on the control ring of the ball ramp actuator. The control clutch can be similar to those commonly used for vehicle air conditioning compressors. A clutch for driving a refrigerating apparatus for a vehicle air conditioning compressor is disclosed in US-Patent No. 2 807 148. The clutch comprises a input portion which is formed by a pulley and a rotationally driven housing connected to the pulley, a ball ramp mechanism, and an output shaft connected to the ball ramp mechanism. A coil coaxially surrounding the output shaft is housed in a magnetic armature the magnetic field of which drags one disc of the ball ramp mechanism in frictionally engagement with the driven housing. The resulting relative movement between both discs of the ball ramp mechanism drives the discs of the mechanism apart and in frictionally engagement with the housing. The discs are axially expanded an clamped between apposing inner surfaces of the housing. Torque reserval from the engine to the compressor is not likely. Subsequently the clutch for coupling the refrigerating apparatus to the engine is not intended for use in apparatuses where torques in different directions occur. Summary of the Invention As an alternative, reference is made to an efficient, quick acting ball ramp clutch actuator. The ball ramp mechanism has dual angle ramps where the clutch is locked in both the drive and coast mode of vehicle operation. That invention also provides for a ball ramp actuator for an electronically controlled clutch such as might be used in a motor vehicle. The present invention uses a ball ramp actuator having single angle ramps which allow the outside diameter of the ball ramp actuator to be significantly reduced. The present invention is characterized by the features of claim 1 and especially by a flywheel and a transmission input shaft being coupled through a control ring having single direction variable depth grooves (ramps) and an activation ring having single direction variable depth grooves at least partially opposed to those of the control ring of a ball ramp actuator where the activation ring is prevented from counterrotating by a one-way clutch. An electromagnetic coil is used to activate a control clutch which frictionally couples the control ring to the transmission input shaft. The ball ramp actuator provides a clamping force on the clutch friction disc whose amplitude immediately increases with the differential speed between the input (flywheel) and output (transmission) shafts without complex electronic intervention using the coil. Upon lock-up between the flywheel and the transmission input shaft, the parasitic energy loss is minimized since there is no slippage in the control clutch which is connected to the transmission input shaft as opposed to case ground as found in prior art systems. One provision of the present invention is to prevent a ball ramp actuated clutch from disengaging when the input torque is reversed. Another provision of the present invention is to prevent a ball ramp actuated clutch from disengaging by locking the rotational orientation between a control ring and an activation ring using a one-way clutch when the driveline input is reversed. Still another provision of the present invention is to prevent a first ball ramp mechanism from disengaging when the driveline torque is reversed by locking the rotational orientation between a control ring and an activation ring and providing a ball ramp mechanism between the control ring and a pressure plate which energizes in a direction opposite to the first ball ramp mechanism. The present invention makes use of a one-way clutch defined for purposes of this application as any mechanism which permits rotation of an element in one direction and prevents substantial rotation in an opposite direction. The purpose of the one-way clutch as used in the ball ramp actuator of the present invention is to hold the actuation ring in a fixed position relative to the control ring so as to maintain the existing clamping force on the clutch plate when the input torque is reversed such as in a vehicle coast mode. Using a one-way clutch of the present invention allows a clutch having a unidirectional ball ramp actuator with single angle ramps (grooves) (which only applies a clamping load when the control ring is rotated in one direction relative to the activation ring) to apply a clutch clamping force when the engine is driving or being driven. A bidirectional ball ramp actuator has dual angle ramps which operate in either direction of rotation and a one-way clutch would not serve any meaningful purpose other than prevent a momentary clutch release upon a vehicle drive to coast transition. With the use of a one-way clutch acting essentially between a transmission input shaft and the actuation ring of a ball ramp actuator having single angle grooves, the clamping force of a clutch disc can be maintained as the input torque to the driveline clutch is reversed. A second ball ramp mechanism with reverse acting ramps can be used between the actuation ring and the pressure plate to provide an additional clamping force upon torque reversal. Brief Description of the Drawings Figure 1 is a partial cross-sectional view of the ball ramp actuator of the present invention mounted to input and output members; Figure 2 is a front sectional view taken along line II-II of Figure 1 of the activation ring, control ring and pressure plate of the ball ramp actuator of the present invention; Figure 3 is a sectional view of Figure 2 taken along line III-III of Figure 2 of the ball ramp actuator of the present invention with the actuator in a non-energized state; Figure 4 is a sectional view of Figure 2 taken along line III-III of Figure 3 of the ball ramp actuator of the present invention with the actuator in an energized state; and Figure 5 is a sectional view of Figure 2 taken along line III-III of Figure 3 of the ball ramp actuator of the present invention with both the first and second ball ramp mechanisms energized. Detailed Description of the Preferred Embodiment Referring now to the drawings, which are not intended to limit the present invention, Figure 1 is a partial cross-sectional view of the main driveline clutch assembly of the type in which the present invention is utilized to energize a driveline clutch by supplying an axial force to a pressure plate 12 which acts to clamp a clutch disc 9 to an engine flywheel 4. Most all of the elements herein described have circular peripheral edges and encircle the transmission input shaft 8 and rotate on a common axis of rotation 59. Figure 1 shows only a portion of the clutch assembly elements which are symmetrical around the axis of rotation 59. The engine flywheel 4 is rotatably driven by a prime mover (not shown) such as an internal combustion engine through its crankshaft (also not shown). The crankshaft rotates the flywheel 4 which is coupled to a transmission 3 through the driveline clutch assembly of the present invention by the clamping action of the pressure plate 12 to the clutch disc 9 having a first surface 10A and a second surface 10B, which rotatably drives the transmission input shaft 8. A pressure plate 12 is used to clamp the clutch disc 9 which is nonrotatably attached to the transmission input shaft 8 through engagement of a plurality of shaft splines 13 and mating clutch disc splines 11 through attached friction pads 10 to the flywheel 4 thereby transferring the rotational power from the engine to the transrnission 3 and subsequently to the rest of the vehicle driveline. The pressure plate 12 is typically forced toward the flywheel 4 using a reaction of a plurality of high spring rate clutch springs. When the operator wishes to disengage the clutch disc 9, a mechanical release mechanism is activated by movement of the operator's foot and leg thereby overcoming the force of the clutch springs and allowing the clutch disc to slip relative to the flywheel 4. It should be understood, that neither the clutch springs nor the mecnanical release mechanism are features of the present invention. Instead, a first ball ramp actuator mechanism 5A is used to axially force the pressure plate 12 toward the flywheel 4 which is controlled by clutch control electronics 15 which controls most all of the transmission 3 shifting sequences. The pressure plate 12 has a first surface 12A which frictionally engages the second surface 10B of the clutch disk 9. Ball ramp mechanisms are well known in the art and have been used to load transmission gear clutches as disclosed in U.S. Patent No. 5,078,249 and differential clutch packs as disclosed in U.S. Patent No. 5,092,825. In the prior art, the ball ramp control mechanism is energized through a reaction of a control ring against case ground by an electrical coil or motor. The detailed operation of the ball ramp actuator 5 is disclosed in U.S. Patent No. 5,078,249 and U.S. Patent No. 5,092,825. In essence, relative motion between a control ring 16 and an activation ring 18 being driven through the pressure plate 12 by the second ball ramp mechanism 5B which is locked by its geometry causes one or more rolling elements 20A (which can be spherically shaped or barrel shaped in addition to other designs) to roll along a like number of opposed ramps 22A and 23A formed in the control ring 16 and the activation ring 18. Figure 2 illustrates this geometry with more detail and precision, reference to which is made subsequently. Referring once again to Figure 1, the annular control ring 16 is axially loaded by the first ball ramp mechanism 5A and reacts against a thrust bearing 27 which is trapped between the control ring 16 and a mechanism support member 34 which is attached to the flywheel 4. The support bearing 27 provides for axial support of the control ring 16 while allowing for relative rotation with respect to the support member 34. The control ring 16 is frictionally coupled to the transmission input shaft 8 through the action of an energizing coil 30 which causes the control ring 16 to be axially loaded against a friction element 28 thereby completing the coupling arrangement to the transmission input shaft 8. The coil 30 is electrically energized using a clutch control unit 15 which in turn can be controlled by a vehicle system electronic control unit (not shown). The electrical current is introduced into the coil 30 by the clutch control unit 15 where the electrical current in the coil 30 creates a magnetic field 36 which flows through a narrow air gap 35 through the control support 37 (specifically the magnetic section 37B) through the locking ring 32 into the control ring 16 and then returning to the coil 30 in a circular manner. The coil 30 creates the magnetic field 36 which provides electromagnetic coupling of the control ring 16 to the locking ring 32 through the friction element 28 and control support magnetic section 37B and functions to frictionally couple the control ring 16 to the transmission input shaft 8. The coil 30 is mounted to case ground through support bracket 31 which is attached to the case of the transmission 3. The narrow air gap 35 exists between the coil 30 and the locking ring 32 since the coil 30 is grounded and the locking ring 32 rotates with the transmission input shaft 8. A control support extension section 37A (which is joined to the magnetic section 37B to form the control support 37) supports a first side 38A of a one-way clutch 38. A second side 38B of the one-way clutch 38 is mounted to the activation ring 18. The purpose of the one-way clutch 38 is to prevent relative rotation between the control ring 16 and the activation ring 18 so as to maintain the position of the first ball ramp mechanism 5A such that the coupling between the flywheel 4 and the transmission input shaft 8 is maintained in any vehicle operating mode such as drive or coast and in addition serves to drive the second ball ramp mechanism 5B in coast mode. In this manner, the engine can act as a brake to slow the vehicle when in a vehicle coast mode since the ball ramp actuator remains in the energized state by operation of the one-way clutch 38. In the prior art, the ball ramp clutch mechanism with a one-way ramp would disengage the clutch whenever the rotational torque is reversed such as in the vehicle coast mode. The one-way clutch 38 functions to lock the activation ring 18 to the control support extension 37A which is connected to the magnetic section 37B to form the control support 37 which is in turn nonrotatably connected to the transmission input shaft 8 through splines 13. Bushing 39 surrounds the transmission main shaft 8 and serves to rotatably support the control support 37 at the control support extension 37A. Thus, unless the coil 30 is energized, the control support 37 is free to rotate thereby allowing the one-way clutch to rotate with the control ring 16 so that the control ring 16 and the activation ring 18 are free to assume a non-energized rotational orientation. In normal operation, when the engine is powering the vehicle driveline through rotation of its flywheel 4 then through the ball ramp clutch assembly 2, the one-way clutch 38 is free to allow motion in one direction between the activation ring 18 and control ring 16 which further clamps the pressure plate 12. The one-way clutch 38 does not permit the relative rotation of the control ring 18 relative to the activation ring 16 so as to reduce the clamping force on the clutch disc 9 so long as the coil 30 is energized to magnetically connect the control support 37 through its magnetic section 37B to the transmission input shaft 8 through the locking ring 32. The clutch disc 9 is clamped between the pressure plate 12 and the flywheel 4 and is composed of a plurality of friction plates 10 and a spline 11 which slidingly and nonrotatably engages the transmission input shaft 8 through splines 13 thereby completing the torque transfer path. When the vehicle is in a coast mode, where the driveline is powering the engine, the one-way clutch 38 locks the activation ring 18 to the locking ring 32 through the control support extension 37A where the coil 30, if energized, is also functioning to frictionally lock the control ring 16 to the locking ring 32, and locking ring 32 is splined to input shaft 8 and in turn supplies coast torque to ball ramp mechanism 5B to activate and supply a clamping force to the clutch disc 9, thereby maintaining the relative rotational orientation between the control ring 16, the activation ring 18 and input shaft 8. The result is that the clamping force supplied by the control ring 18 and the activation ring 16 is maintained at its current level and additional clamping is provided whenever the vehicle goes into a coast mode such that the transmission input shaft 8 transfers power to the engine flywheel 4. To further clamp the clutch disc 9 between the flywheel 4 and the pressure plate 12 in the coast mode where the driveline is rotating the engine, the second ball ramp mechanism 5B is energized in the opposite rotational direction to the first ball ramp mechanism 5A. The second ball ramp mechanism 5B does not provide for relative movement between the activation ring 18 and the pressure plate 12 when the engine is powering the vehicle. When the torque transfer is reversed in the vehicle coast mode, the activation rings rotate through a small angle relative to the pressure plate 12 thereby causing a plurality of rolling elements 26A, 26B and 26C to travel along opposing ramps 24A and 25A, 24B and 25B, and 24C and 25C respectively which causes the second ball ramp mechanism 5B to expand axially thereby supply additional clamping force to the clutch disc 9. The pressure plate 12 is nonrotatably coupled to the engine flywheel 4 by way of a retaining bolt 40 where the pressure plate 12 is slidably connected to the retaining bolt 40 and is forced away from the flywheel 4 by the return spring 42. In this manner, when the first and second ball ramp mechanisms 5A and 5B are in a non-energized state, the return spring 42 forces the pressure plate 12 away from the flywheel 4 thereby releasing the clutch disc 9 so that the engine flywheel 4 can freely rotate relative to the transmission input shaft 8 and no torque is transferred through the clutch assembly. A housing 6 surrounds the flywheel 4 and the ball ramp clutch assembly 2 where it is common practice to bolt the transmission 3 to the bellhousing 6. Now referring to Figures 2, 3, 4 and 5, the control ring 16 is shaped in a disc configuration surrounding the transmission input shaft 8 and rotating about a common axis of rotation 59. The control ring 16 has a plurality of radial grooves 22A, 22B and 22C formed therein which vary in axial depth along their length. Grooves 22A, 22B and 22C are shown in more detail by reference to Figures 3, 4 and 5 and constrain spherical elements 20A, 20B and 20C. In a similar manner, activation ring 18 contains a like number and orientation of circumferentially extending (at a constant radius to the axis of rotation 59) grooves directly opposing the grooves in the control ring. Specifically, control ring groove 22A is partially opposed to activation ring groove 23A when the ball ramp mechanism 5 is in a non-energized state as shown in Figure 3 and directly opposes the activation ring groove 23A when in a fully energized state (not shown). Upon relative rotational motion between the control ring 16 and the activation ring 18, the spherical element 20A rolls relative to the control ring groove 22A and activation control ring groove 23A where the variable depth of the grooves 22A and 23A as shown in Figure 4 provide for an axial motion that tends to separate the control ring 16 from the activation ring 18. This axial motion is shown by reference to the separation gap 44. In the non-energized state as shown in Figure 3, the separation gap 44 is relatively narrow and after relative rotation of the control ring 16 and the activation ring 18 to the energized state shown in Figure 4, the separation gap is significantly wider as discussed infra. The axial motion supplied by the first and second ball ramp mechanisms 5A and 5B are used to axially move the pressure plate 12 toward the flywheel 4 thereby supplying a clamping force on the clutch disc 9. This motion is more clearly exemplified in Figures 3, 4 and 5 and reference thereto will now be made. Figures 3, 4 and 5 are sectional views of Figure 2 taken along line III-III of the control ring 16 and the activation ring 18 and the pressure plate 12 of the present invention. Figure 3 shows the first ball ramp mechanism 5A in a non-energized state where the spherical element 20A is located at the deepest depth of the control ring groove 22A and the deepest portion of the activation ring groove 23A thereby establishing a relatively narrow separation gap 44 between the control ring 16 and the activation ring 18. Also shown is the second ball ramp mechanism 5B between the activation ring 18 and the pressure plate 12 where spherical element 26A is located in the deepest portion of the activation ring groove 24A and the deepest portion of the pressure plate groove 25A thereby establishing a relatively narrow separation gap 46. Figure 4 illustrates the relationship between the control ring 16, the activation ring 18 and the pressure plate 12 when the first ball ramp mechanism 5A is energized by supplying electrical current to the coil 30 from the clutch control unit 15 and the engine is supplying torque to the driveline. The magnetic interaction between the coil 30, the locking ring 32, the control support 37 and the control ring 16 causes the friction element 28 to contact and frictionally connect the control ring 16 to the transmission input shaft 8. Thus, since the pressure plate 12 is rotating and attached to the engine flywheel 4, and ball ramp mechanism 5B cannot rotate in an engine drive direction, if there is relative rotational speed differences between the engine flywheel 4 and the transmission input shaft 8 there is relative rotational motion induced between the pressure plate 12 and the control ring 16. This relative rotational motion causes the control ring 16 to rotate relative to the activation ring 18 to establish a geometrical relationship as shown in Figure 4. The separation gap 44 is significantly increased as compared to the non-energized state of Figure 3 while the separation gap 46 remains the same as in the non-energized state in Figure 3 since the second ball ramp mechanism 5B is locked until the torque is reversed. The spherical element 20A has rolled along both the control ring groove 22A and the activation ring groove 23A to an intermediate depth of the grooves 22A and 23A thereby further separating the control ring 16 from the activation ring 18 and providing axial movement from the support member 34 as shown by the increase in the separation gap 44 which is transferred to the pressure plate 12 for clamping of the clutch disc 9 to the flywheel 4. To provide engine braking effect in the vehicle coast operating mode, the coil 30 remains energized and the one-way clutch 38 operates against the control support 37 to prevent the first ball ramp mechanism 5A from releasing. The second ball ramp mechanism 5B has a reversed direction ramp orientation between the activation ring 18 and the pressure plate 12 so that reverse torque transfer results in activation of the second ball ramp actuator 5B thereby increasing the clamping force of the pressure plate 12 on the clutch disc 9. Referring to Figure 5, spherical element 26A has rolled along activation ring groove 24A and pressure plate groove 25A (also referred to as plate grooves) to an intermediate depth of the grooves 24A and 25A thereby increasing the separation gap 46 as compared to that shown in Figures 3 and 4. The result is that additional axial motion is applied to the pressure plate 12 relative to the engine flywheel 4 and the support member 34 which clamps the clutch disc 9 between the pressure plate 12 and the engine flywheel 4 thereby frictionally connecting the flywheel 4 to the transmission input shaft 8. According to the present invention, once the clutch assembly 2 is engaged by action of the first ball ramp actuator 5A the engine can supply power to the vehicle driveline thereby propelling the vehicle. When it is no longer desirable to increase the speed of the vehicle by supplying power from the engine to the driveline, the engine power is decreased and the engine can act as a brake to the vehicle by reversing the flow of rotational power from the engine to the driveline to one flowing from the driveline to the engine. The one-way clutch 38 serves to maintain the relative rotational position of the activation ring 18 relative to the control ring 16 and the pressure plate 12 thereby maintaining the clamping force between the pressure plate 12 and the flywheel 4 to maintain the frictional coupling between the transmission input shaft 8 and the flywheel 4 so that the drive line can supply rotational power to the engine which, if the engine throttle is closed, will tend to brake the vehicle. An additional clamping force can be supplied by a second ball ramp mechanism 5B placed between the activation ring 18 and the pressure plate 12 designed to energize when the torque flow reverses as during vehicle coasting. This invention has been described in great detail, sufficient to enable one skilled in the art to make and use the same.

Claims: A driveline clutch having a flywheel (4) rotated about an axis of rotation (59) by a prime mover, a driveline transmission (3) having an input shaft (8) and a housing (6), a clutch disc (9) splined to said input shaft (8), said clutch disc (9) radially extending from said input shaft (8) and having friction material cn a first surface (10A) and on a second surface (10B) where said first surface (10A) frictionally engages said flywheel (4), a pressure plate (12) encircling said input shaft (8) having a first surface (12A) for frictionally engaging said second surface (10B) of said clutch disc (9), a first ball ramp mechanism (5A) for mcving said pressure plate (12) toward said clutch disc (9) and said flywheel (4) thereby causing said clutch disc (9) to be clamped therebetween, said first ball ramp mechanism (5A) having an activation ring (18) encircling said input shaft (8), said activation ring (18) being axially connected to said pressure plate (12) where axial movement of said activation ring (18) results in axial movement of said pressure plate (12), a control ring (16) encircling said input shaft (8) and disposed adjacent to said activation ring (18), said control ring (16) and said activation ring (18) having opposed faces provided with circumferentially extending grooves (22A, 22B, 22C 23A, 23B, 23C) arranged in at least three partially opposed pairs, said grooves (22A, 22B, 22C, 23A, 23B, 23C) having portions of varying depth, and rolling members (20A, 20B, 20C) disposed one in each opposed pair of grooves (22A, 23A; 22B, 23B; 22C, 23C), the grooves (22A, 22B, 22C, 23A, 23B, 23C) on said activation ring (18) and said adjacent control ring (16) being arranged so that relative angular movement of said activation ring (18) and said control ring (16) in a drive direction, from a starting position thereof causes axial movement of said activation ring (18) away from said control ring (16) operating to axially displace said adjacent pressure plate (12), and a coil (30) for inducing a magnetic field in said control ring (16), the improvement comprising: a second ball ramp mechanism (5B) for moving said pressure plate (12) toward said clutch disc (9) and said flywheel (4) thereby causing said clutch disc (9) to be clamped therebetween disposed between said pressure plate (12) and said activation ring (18), said pressure plate (12) and said activation ring (18) having cpposed faces provided with circumferentially extending grooves (24A,24B,24C,25A,25B,25C) arranged in at least three partially opposed pairs, said grooves (24A,248,24C,25A,258,25C) having portions of varying depth; and rolling members (26A,26B,26C) disposed one in each opposed pair of grooves (24A,25A,24B,25B,24C,25C), the grooves (24A,25A,24B,25B,24C,25C) on said pressure plate (12) and said adjacent activation ring (18) being arranged so that relative angular movement of said activation (18) and said pressure plate (12) in an opposite drive direction, from a starting position thereof, cause axial movement of said pressure plate (12) toward said clutch disc (9); bearing means (27) operative to absorb axial thrust loads from said control ring (16) said bearing means (27) reacting against said flywheel (4) through a support member (34) ; a control clutch (33) having a friction element (28) and locking ring 32 nonrotably attached to said input shaft (8) where upon application, said control clutch (33) frictionally couples said control ring (16) to said locking ring 32 and said input shaft (8); a one-way clutch (38) having a first side (38a) attached to said activation ring (18) and a second side (38b) attached to said control support (37) oriented to prevent said activation ring (18) from rotating with respect to said control ring (16) in a direction to release said ball ramp mechanism (5a); and a control support (37) having a magnetic section (37b) disposed between said control ring (16) and said locking ring (32), said control support (37) having a control support extension (37a) section rotatably supported by said input shaft (8) and attached to said one-way clutch (38), said control support (37) and said locking ring (32) magnetically coupling said control ring (16) to said transmission input shaft (8) when said coil (30) is energized. The driveline clutch of claim 1, wherein said control support (37) is provided with the friction element (28) attached to said magnetic section (37B) disposed to frictionally engage said control ring (18) upon energization of said coil (30). The driveline clutch of claim 1, wherein said rolling members (26A, 26B, 26C) are spherical. The driveline clutch of claim 1, wherein said coil (30) is attached to said housing (6). The driveline clutch of claim 1, wherein said coil (30) is electrically controlled by clutch control unit (15).

Inventors: JANSON DAVID ALLEN, ORGANEK GREGORY JOSEPH, PRESTON DAVID MICHAEL, JANSON, DAVID ALLEN, ORGANEK, GREGORY JOSEPH, PRESTON, DAVID MICHAEL
Applicants: EATON CORP, EATON CORPORATION
Application year: 1995
Main classification: F16D27
IPC codes: F16D23, F16D28, F16D47, F16D27, F16D13