JPH0723851U - Lockup device for torque converter - Google Patents

Abstract

(57) [Abstract] [Purpose] In a lockup device having a frictional resistance generation mechanism, it does not interfere with the flow of fluid in the turbine. [Structure] A lockup device for a torque converter includes a disc-shaped piston 10, an elastic coupling mechanism, and a frictional resistance generating mechanism 12. The disk-shaped piston 10 is movably arranged between the front cover 2 and the turbine shell 4 a, and can be pressed against the front cover 2. The elastic connecting mechanism 12 connects the piston 10 and the turbine shell 4a in the circumferential direction. The frictional resistance generating mechanism includes a driven plate 16 that is engaged with the rivet 7 so as to rotate integrally and frictionally slides on the disk-shaped piston 10, and generates frictional resistance when the piston 10 and the turbine 4 rotate relative to each other. .

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a lockup device, and more particularly to a lockup device for mechanically connecting a front cover and a turbine of a torque converter.

[0002]

[Prior art]

 A torque converter is a device that has three types of impellers (impeller, turbine, stator) inside and transmits torque by the fluid inside. The impeller is integrally connected to the front cover that is connected to the input side member, and the turbine is connected to the output side member. When torque is input to the front cover and the impeller by the input side member, the turbine is rotated via the fluid, and the torque is transmitted to the output side member via the turbine hub.

Generally, a lock-up device for mechanically connecting the front cover and the turbine is arranged inside the torque converter between the front cover and the turbine. This lock-up device is composed of a disk-shaped piston that is in pressure contact with the front cover, and an elastic connection mechanism that connects the disk-shaped piston and the turbine in the circumferential direction. This elastic coupling mechanism includes a torsion spring and the like, and is for absorbing the shock when the piston is pressed against the front cover.

Further, as disclosed in Japanese Patent Laid-Open No. 2-118256, there is also provided a lockup device provided with a frictional resistance generating mechanism for the purpose of damping torsional vibration on the input side.

[0005]

[Problems to be solved by the device]

 In the frictional resistance generating mechanism provided in the conventional lockup device, some of the constituent members penetrate into the turbine shell. Therefore, protrusions are formed inside the turbine shell. These protrusions obstruct the hydraulic oil flowing in the turbine, and as a result, vortices are generated in the hydraulic oil and the performance of the torque converter deteriorates.

An object of the present invention is to prevent a fluid flow in a turbine from being obstructed in a lockup device having a frictional resistance generating mechanism.

[0007]

[Means for Solving the Problems]

 A lockup device for a torque converter according to the present invention is a turbine including a front cover connected to an input side member, a turbine hub connected to an output side member, and a turbine shell having an inner peripheral end fixed to a turbine hub by rivets. And a disk-shaped piston, an elastic coupling mechanism, and a frictional resistance generating mechanism.

The disk-shaped piston is movably arranged between the front cover and the turbine shell, and can be pressed against the front cover. The elastic coupling mechanism circumferentially couples the piston and the turbine shell. The frictional resistance generating mechanism includes a plate member that engages with the rivet so as to rotate integrally and frictionally slides on the disc-shaped piston, and generates frictional resistance when the piston and the turbine rotate relative to each other.

[0009]

[Action]

 In the lockup device of the torque converter according to the present invention, the disk-shaped piston is pressed against the front cover during the lockup operation. The torque transmitted from the input side member is directly transmitted to the output side member via the front cover, the lockup device, the turbine shell and the turbine hub. At this time, if torsional vibration occurs in the lockup device, the piston and the turbine relatively rotate via the elastic coupling mechanism. At the time of this relative rotation, the frictional resistance generating mechanism generates frictional resistance to reduce torsional vibration.

Here, the plate member of the frictional resistance generating mechanism is engaged with the rivet that fixes the turbine shell to the turbine hub so as to rotate integrally. Therefore, unlike the conventional example, it is not necessary to pierce and lock the member constituting the frictional resistance generating mechanism in the turbine shell. As a result, the fluid flows smoothly through the turbine.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment FIG. 1 shows a torque converter 1 which employs a lockup device according to an embodiment of the present invention. Here, O-O is the rotation center line of the torque converter 1, an engine (not shown) is arranged on the left side of the drawing, and a transmission is arranged on the right side.

In the torque converter 1, a front cover 2 and an impeller shell 3a fixed to an outer peripheral wall 2a of the front cover 2 form a hydraulic oil chamber. The inner peripheral end of the impeller shell 3a is fixed to the impeller hub 3c. The front cover 2 is connected to a crankshaft (not shown) on the engine side. A torque converter main body including an impeller 3, a turbine 4, and a stator 5 and a lockup device 30 are arranged in a hydraulic oil chamber in the torque converter 1. A plurality of impeller blades 3b are fixed inside the impeller shell 3a, and the impeller 3 is constituted by both of them. A turbine 4 is arranged at a position facing the impeller 3. The turbine 4 is mainly configured by a turbine shell 4 a, a plurality of turbine blades 4 b fixed to the inner peripheral wall of the turbine shell 4 a, and a turbine hub 6. The inner peripheral end of the turbine shell 4a is fixed to the outer peripheral flange 6a of the turbine hub 6 with rivets 7. The rivet 7 has a head portion 7a (FIG. 2) extending toward the front cover 2 side, and the head portion 7a is engaged with a part of a frictional resistance generating mechanism 12 described later. The turbine hub 6 has a spline hole 6b on its inner peripheral portion that engages with an output shaft (not shown).

A stator 5 is arranged between the inner peripheral portion of the impeller 3 and the inner peripheral portion of the turbine 4. The stator 5 adjusts the flow direction of the hydraulic oil returned from the turbine 4 to the impeller 3, and has an annular stator carrier 5a and a plurality of stator blades 5b formed on the outer peripheral surface of the stator carrier 5a. It consists of The stator 5 is supported by a stator shaft (not shown) via a one-way clutch mechanism 8 arranged on the inner peripheral side.

The lockup device 30 is arranged between the front cover 2 and the turbine shell 4 a, and mainly includes the disc-shaped piston 10, the elastic coupling mechanism 11, and the frictional resistance generating mechanism 12. It is configured. The disk-shaped piston 10 has a cylindrical outer peripheral wall 10a extending toward the transmission side (right side in FIG. 1) at the outer peripheral end, and a cylindrical outer wall 10a extending toward the transmission at the inner peripheral end. It has an inner peripheral wall 10b. The inner peripheral wall 10b is supported on the outer peripheral surface of the turbine hub 6 so as to be slidable in the axial direction and the circumferential direction. An annular friction member 35 is adhered to the outer peripheral portion of the piston 10 on the side facing the friction surface of the front cover 2.

The elastic coupling mechanism 11 is arranged inside the outer peripheral wall 10 a of the piston 10. The elastic coupling mechanism 11 includes a retaining plate 31, a plurality of torsion springs 32, and bending claws 33. The retaining plate 31 is fixed to the piston 10 by a plurality of rivets 34. The retaining plate 32 has a tubular portion extending in an annular shape, and accommodates a plurality of torsion springs 32 in the tubular portion. Both ends of each torsion spring 32 in the circumferential direction are supported by bending claws formed on the retaining plate 31. Further, bending claws 33 fixed to the outer peripheral portion of the turbine shell 4a are engaged with both ends of the torsion spring 32. As described above, the piston 10 and the turbine shell 4a are elastically connected in the circumferential direction by the elastic connecting mechanism 11 including the retaining plate 31, the torsion spring 32, and the bending claw 33. There is.

Next, the frictional resistance generating mechanism 12 will be described in detail with reference to FIG. The frictional resistance generating mechanism 12 includes a disk-shaped driven plate 16 having a facing 18 stretched on one side surface, a cone spring 17, a support plate 15, and a plurality of rivets 14. As shown in FIG. 3, the driven plate 16 is composed of a disc portion 16a and an outer peripheral portion 16b that extends conically from the outer peripheral portion of the disc portion 16a. A plurality of semicircular guide grooves 16c are formed at the outer peripheral end of the outer peripheral portion 16b. The guide groove 16c is engaged with the head portion 7a of the rivet 7. As a result, the driven rate 16 can move in the axial direction with respect to the rivet 7, but cannot rotate relative to the rivet 7. The cone spring 17 is arranged on the engine side (left side in FIG. 2) of the inner peripheral portion of the piston 10. The driven plate 16 and the ring-shaped support plate 15 are arranged in this order on the transmission side of the inner peripheral end of the piston 10. The facing 18 is in contact with the side surface of the inner peripheral end portion of the piston 10. The cone spring 17, the driven plate 16 and the support plate 15 are fixed to the inner peripheral end of the piston 10 by a plurality of rivets 14. The rivet 14 is attached to the inner peripheral end of the piston 10 so as to be movable in the axial direction.

The cone spring 17 biases the rivet 14 toward the engine. As a result, the head on the other end side of the rivet 14 biases the driven plate 16 to the inner peripheral end of the piston 10 via the support plate 15. The disk portion 16a and the facing 18a are provided with elongated holes 16d and 18a formed in the circumferential direction through which the body of the rivet 14 passes, respectively, and the driven plate 16 and the facing 18a are formed. Can rotate relative to the piston 10 within a predetermined angle range. The distance that the rivet 14 can move within the elongated hole 16d formed in the driven plate 16 is set shorter than the distance that the torsion spring 32 is compressed between the retaining plate 31 and the bending claw 33. The rivet 14 functions as a stopper.

In the structure described above, the driven plate 16 is conventionally engaged with the rivet 7 that connects the turbine hub 6 and the turbine shell 4a. As a result, unlike the conventional example, it is not necessary to form a hole in the turbine shell and fix the plate member of the frictional resistance generating mechanism. Therefore, no protrusion is formed inside the turbine shell 4a, that is, on the side where the turbine blade 4b is formed, and does not hinder the flow of hydraulic oil circulating in the flow path of the turbine 4.

Further, the cone spring 17 is arranged on the engine side of the inner peripheral end of the piston 10. Therefore, the space between the inner peripheral end of the piston 10 and the outer peripheral flange 6a of the turbine hub 6 can be shortened in the axial direction. Next, the operation of the above embodiment will be described. Torque from a crankshaft (not shown) is transmitted to the front cover 2. As the front cover 2 rotates, the impeller 3 also rotates, and this torque is transmitted to the turbine 4 via hydraulic oil. The torque of the turbine 4 is transmitted to the output shaft (not shown) via the turbine hub 6.

When the output shaft (not shown) reaches a certain rotational speed, the hydraulic pressure of the working oil chamber in the torque converter 1 is increased and the hydraulic oil between the front cover 2 and the piston 10 is drained. As a result, the piston 10 is pressed against the front cover 2 side. Then, the friction member 35 of the piston 10 is pressed against the friction surface of the front cover 2. As a result, the torque of the front cover 2 is transmitted from the piston 10 to the turbine 4 via the elastic coupling mechanism 11. That is, the torque of the front cover 2 is mechanically transmitted to the output shaft (not shown) via the lockup device 30 and the turbine 4. Therefore, it is possible to obtain a good fuel economy state with less energy loss.

When torsional vibration occurs in the lockup device 30 during the lockup operation, the piston 10 and the turbine 4 repeat relative rotation via the elastic coupling mechanism 11. At this time, the torsion spring 32 expands and contracts between them, and further frictional resistance is generated between the facing 18 and the inner peripheral end portion of the piston 10, thereby attenuating the energy of torsional vibration. Second Embodiment The frictional resistance generating mechanism 12 shown in FIG. 4 is arranged between the inner peripheral end of the piston 10 and the outer peripheral flange 6a of the turbine hub 6. The frictional resistance generating mechanism 12 mainly includes a disk-shaped driven plate 26, a pressure plate 25, and a cone spring 27 from the piston 10 side. As is clear from FIG. 5, the driven plate 26 includes a disc portion 26a and a conical outer peripheral portion 26b protruding toward the transmission side on the outer periphery of the disc portion 26a. Facings 28 and 29 are attached to both surfaces of the disk portion 26a. A plurality of semicircular guide grooves 26c are formed at the outer peripheral end of the outer peripheral portion 26b. The guide groove 26c engages with the head portion 7a of the rivet 7 fixed to the outer peripheral flange 6a of the turbine hub 6. As a result, the driven plate 26 is movable in the axial direction with respect to the turbine 4, but is integrally rotated in the circumferential direction. As shown in FIG. 6, the pressure plate 25 is a ring-shaped plate, and has an annular protrusion 25a protruding toward the transmission side. The cone spring 27 has an inner peripheral end supported by a snap ring 30 that engages with a ring groove 10d of an inner peripheral wall 10b of the piston 10, and an outer peripheral end urges a protrusion 25a portion of the pressure plate 25 toward the engine. . A snap ring guide 31 shown in FIG. 8 is arranged on the outer circumference of the snap ring 30, and the snap ring guide 31 prevents the snap ring 30 from floating from the ring groove 10d due to the centrifugal force.

On the inner peripheral portion of the piston 10, a plurality of push-out portions 10c protruding toward the transmission side are formed. As is clear from FIG. 5, elongated holes 26c, 28a and 29a extending in the circumferential direction are formed in the disk portion 26a of the driven plate 26 and the facing portions 28 and 29 corresponding to the push-out portion 10c. It That is, the piston 10 can rotate relative to the driven plate 26 within a predetermined angle range. The distance by which the pushing portion 10c can move in the circumferential elongated hole 26c formed in the driven plate 26 or the like is greater than the distance by which the torsion spring 32 is compressed between the retaining plate 31 and the bending claw 33. It is set short. That is, the pushing portion 10c functions as a stopper.

Also in this embodiment, the driven plate 26 is engaged with the head portion 7a of the rivet 7 which is a member for fixing the turbine shell 4a to the outer peripheral flange of the turbine hub 6 in the related art. As a result, unlike the conventional example, it is not necessary to form a hole in the turbine shell and fix the plate member of the frictional resistance generating mechanism. Therefore, no protrusion is formed on the inner side of the turbine shell 4a on the side where the turbine blade 4b is formed, and the flow of hydraulic oil circulating in the flow path of the turbine 4 is not hindered.

Further, in this embodiment, since both side surfaces of the disk portion 26a of the driven plate 26 function as friction sliding surfaces, it is possible to generate twice the frictional resistance as compared with the above embodiment. . Third Embodiment The frictional resistance generating mechanism 12 shown in FIG. 9 is arranged between the inner peripheral end of the piston 10 and the outer peripheral flange 6a of the turbine hub 6. The frictional resistance generating mechanism 12 mainly includes a driven plate 46, a wave spring 47, and a support plate 45 in order from the piston 10 side. All of these members are Kanigen plated. As shown in FIG. 10, the driven plate 46 is a disc-shaped member, and includes a disc portion 46a and a conical outer peripheral portion 46b extending from the outer peripheral end of the disc portion 46a toward the transmission. A plurality of semicircular guide grooves 46c are formed at the outer peripheral end of the outer peripheral portion 46b. Each guide groove 46c is engaged with the head 7a of the rivet 7 fixed to the outer peripheral flange 6a. That is, the driven plate 46 is movable in the axial direction with respect to the turbine 4, but is incapable of relative rotation.

The transmission side of the wave spring 47 is supported by the support plate 45, and the engine side of the wave spring 47 urges the disc portion 46 a of the driven plate 46 to the side surface of the inner peripheral end of the piston 10. As shown in FIG. 11, the support plate 45 is a ring-shaped member and has a plurality of projections 45a extending in the circumferential direction on the transmission side. The transmission side of the inner peripheral end of the support plate 45 is supported by a snap ring 40 fixed to the inner peripheral wall 10b of the piston 10. The projection 45a of the pressure plate 45 prevents the snap ring 40 from being lifted up from the inner peripheral wall 10b of the piston 10 by the centrifugal force.

Also in this embodiment, the same effect as that of the first embodiment can be obtained.

[0027]

[Effect of device]

 In the lockup device for a torque converter according to the present invention, the plate member of the frictional resistance generating mechanism is engaged with the rivet that fixes the turbine shell to the turbine hub so as to rotate integrally therewith. Therefore, unlike the conventional example, it is not necessary to pierce and lock the member constituting the frictional resistance generating mechanism in the turbine shell. As a result, the fluid flows smoothly through the turbine.

[Brief description of drawings]

FIG. 1 is a schematic vertical sectional view of a torque converter to which a first embodiment of the present invention is applied.

FIG. 2 is a partially enlarged view of FIG.

FIG. 3 is a perspective partial view of a driven plate.

FIG. 4 is a diagram corresponding to FIG. 2 in the second embodiment.

FIG. 5 is a diagram corresponding to FIG. 3 in the second embodiment.

FIG. 6 is a partial perspective view of a pressure plate.

FIG. 7 is a partial vertical cross-sectional view of the snap ring guide.

FIG. 8 is a partial vertical sectional view of the piston.

FIG. 9 is a diagram corresponding to FIG. 2 in the third embodiment.

FIG. 10 is a diagram corresponding to FIG. 3 in the third embodiment.

FIG. 11 is a diagram corresponding to FIG. 6 in the third embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Torque converter 2 Front cover 4 Turbine 4a Turbine shell 6 Turbine hub 10 Disc-shaped piston 11 Elastic coupling mechanism 12 Friction resistance generating mechanism 16, 26, 36 Driven plate 30 Lockup device

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Creator Kunihiro Tokuda 1-1-1 Kinomotomiya, Neyagawa City Daikin Co., Ltd.

Claims (1)

[Scope of utility model registration request] 1. A torque converter including a front cover connected to an input member, a turbine hub connected to an output member, and a turbine including a turbine shell having an inner peripheral end fixed to the turbine hub by rivets. A lock-up device of the above, which is movably disposed between the front cover and the turbine shell, and has a disc-shaped piston that can be pressed into contact with the front cover, and the piston and the turbine shell in a circumferential direction. An elastic coupling mechanism for coupling, and a plate member that engages with the rivet so as to rotate integrally and frictionally slides on the disc-shaped piston, and generate frictional resistance when the piston and the turbine rotate relative to each other. A lockup device for a torque converter that includes a frictional resistance generating mechanism that causes