JPH02225860A - Direct-coupled clutch for hydraulic power transmission - Google Patents

Abstract

PURPOSE:To reduce the abrasion of each forming member of a damper mechanism by having a tubulous part extendable in the axial direction at the radial inside of a second driven plate, and providing a centering part for abutting to that tubulous part in the radial direction at the inner peripheral end of a first driven plate. CONSTITUTION:A flange part 18g at the inner peripheral end of a disc 18 is supported by a peripheral wall 20e surface of a second driven plate 20b to secure the centering of a first driven plate. Namely, the flange part 18g is formed with a centering part. Consequently, the first and the second driven plates 19, 20 are hardly inclined each other to reduce the bearing of contact surfaces between them. The abrasion of both plates 19, 29 is thereby restrained to greatly improve the abrasion resistance of a damper mechanism 15.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a fluid transmission device that transmits torque through fluid, and in particular, to a fluid transmission device that directly transmits torque mechanically. This relates to a direct clutch in the device.

[Prior Art] Conventionally, this type of direct coupling clutch is provided with a damper mechanism for absorbing and mitigating shocks and vibrations generated when the direct coupling clutch is connected.

As this damper mechanism, one disclosed in Japanese Patent Laid-Open No. 61-252964 is known.

As shown in FIGS. 4 and 5, the damper mechanism 01 shown in this publication is installed in a torque converter as a fluid transmission device. The first buffer member 04 is arranged on the side and consists of a large number of compression coil springs.
A first driven plate 05 is connected to the first driven plate 05 so as to be relatively slidable in the circumferential direction via the first driven plate 05, and a plurality of first driven plates 05 are arranged on the inner peripheral side and have a larger spring constant than the first buffer member 04. A second driven plate 08 is connected to the turbine hub 07 so as to be relatively slidable in the circumferential direction via a second buffer member 06 .

Drive plate 03 and second driven plate 08
are a pair of ring-shaped disks 03a, 03a;
08a, 08a, and the first driven plate 05 and the first buffer member 04 are sandwiched between a pair of disks 03a, 03a.

Further, the first driven plate 05 and the second buffer member 06 are sandwiched between another pair of disks 08a, 08a, and these disks are connected by rivets 09.010, respectively.

In the damper mechanism 01 configured in this way, the torque from the lock-up piston 02 is transmitted to the drive plate 03, the first buffer member 04, and the like. Since it comes to be transmitted in series to the turbine hub t-button 07 via the first driven play 1-05, the second slack member 06, and the second driven plate 08, there is no need to increase the diameter of the damper mechanism 01. , the torque capacity that can be absorbed can be increased.

[Problems to be Solved by the Invention] Incidentally, in such a damper mechanism 01, for example, in order to connect the first and second driven plates 05, 08 so as to be able to slide relative to each other, a cylindrical spacer 01 is provided at the connecting portion.
1 is disposed, and a rivet 010 is passed through this spacer 011 to connect them.

However, in such a damper mechanism 01.

A second driven plate 08 is attached to the turbine hub 07 by being fitted into the turbine hub 07. 1st driven plate 0
5 and the second driven plate 08 rotate, due to the unbalance in the circumferential direction of the first driven plate o5, the first
The center of rotation of the driven plate 05 tends to deviate from that of the second driven plate 08. At this time, since the surface pressure of the contact surface of the spacer 011 with the first driven plate 05 increases, the first driven plate 05 and the spacer 01
1 is worn out, and when the spacer 011 is worn out, the second buffer member is sandwiched between the first driven plate 05 and the second driven plate 08 due to the eccentricity of the first driven plate 05 and the second driven plate 08. It is also possible that it may wear out.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a direct coupling clutch in a fluid transmission device that can reduce wear on each component of a damper mechanism.

[Means for Solving the Problems] In order to solve such problems, the present invention provides a lock-up piston that is provided in a fluid transmission device that transmits driving torque from an input member to an output member via fluid. In a direct coupling clutch that directly connects the input member and the output member and includes a damper mechanism that absorbs and alleviates impact applied to the lock-up piston, an outer peripheral end of the damper mechanism is spline-fitted to the lock-up piston. a first drive plate connected to the drive plate via a first buffer member so as to be relatively rotatable;
The drive plate includes a driven plate, and a second driven plate connected to the driven plate through a second buffer member so as to be relatively rotatable, and whose inner peripheral end is connected to the output member, and the second driven plate has a cylindrical part extending axially inwardly in the radial direction, and a centering part that contacts the cylindrical part in the radial direction is provided at the inner circumferential end of the first driven play 1. It is said that

[Operation and Effects of the Invention] In the direct coupling clutch in the fluid transmission device of the present invention configured as described above, the damper mechanism includes a drive plate whose outer peripheral end is spline-fitted to the lock-up piston, and a drive plate connected to the drive plate. a first driven plate that is relatively rotatably connected via a first buffer member;
The second driven plate is connected to the driven plate via a second buffer member so as to be relatively rotatable, and has an inner peripheral end connected to the output member, and the second driven plate is connected to the second driven plate through a second buffer member.
The driven plate has a cylindrical portion extending axially inwardly in the radial direction, and the inner peripheral end of the first driven plate is provided with a centering portion that abuts the cylindrical portion in the radial direction. The protruding portion prevents the first driven plate and the second driven plate from coming into contact with each other in the radial direction. Therefore, even if the first driven plate tries to eccentrically due to an unbalance in the circumferential direction, the centering portion allows the first and second driven plates to
Since the driven plates are positioned, the second buffer member does not wear out.

[Example code] Hereinafter, the present invention will be explained in detail using the drawings.

FIG. 1 is an overall sectional view of an automatic transmission equipped with a torque converter to which an embodiment of the present invention is applied, and FIG. 2 is a sectional view of the torque converter.

As shown in FIG. 1, an automatic transmission 100 ii includes a torque converter 101 , a planetary speed change gear mechanism 102 , and a hydraulic control mechanism 103 .

The driving torque from the engine is increased by the torque converter 101 at low speeds and input to the planetary speed change gear mechanism 102. The planetary speed change gear mechanism 102 automatically changes its rotation speed by being controlled by the hydraulic control mechanism 103. , is output from the output shaft 104.

As shown in FIG. 2, this torque converter 101 is
A drive plate 3 is connected to the output shaft of a power source such as an engine via a connecting member 2. A pump impeller 4 is connected to this drive plate 3.

A space 5 formed by the drive plate 3 and the pump impeller 4 is filled with a working fluid such as oil. Further, a turbine impeller 6 is arranged to face the pump impeller 4, and the turbine impeller 6 is connected to a turbine hub 8 spline-fitted to an input shaft 7 of an automatic transmission 100. ing. (Additional) Pump impeller 4
A stator impeller 9 is disposed between the turbine impeller 6 and the turbine impeller 6 . The stator impeller 9 is rotatably supported in only one direction by a stator shaft 11 fixed to a housing (not shown) of the transmission via a one-way clutch 10.

Further, a lock-up mechanism 12 consisting of a direct clutch is attached to the turbine hub 8.

This lock-up mechanism 12 includes a lock-up piston 14 to which a clutch friction material 13 is fixed, and a damper mechanism 15.
For example, when the vehicle speed exceeds a predetermined speed, the lock-up piston 14 operates and the friction material 13 frictionally engages with the drive plate 3, thereby directly transmitting torque mechanically. It is meant to be. In addition, the damper mechanism 15 absorbs and alleviates shocks and vibrations that occur when the friction material 13 frictionally engages with the drive plate 3.

As shown in FIGS. 2 and 3, the damper mechanism 15 includes a drive plate 16 formed from a ring-shaped disk.
A first formed from a pair of ring-shaped discs 17 and 18.
It includes a driven plate 19 and a second driven plate 20 formed from a ring-shaped disk.

The drive plate 16 has a predetermined number of splines m 16 a formed on its outer peripheral edge at approximately equal intervals in the circumferential direction, as well as a predetermined number of first windows in the radial intermediate portion. 16b is bored.

Also, a pair of disks 17 of the first driven plate 19.
18, a predetermined number of first and second bulges 17a, 17b and third and fourth bulges 18a, 18b are formed on the outer peripheral end side and the inner peripheral end side, respectively, protruding to one side. These bulges 17a, 17b, 18
a, 18 b have second and third windows 17, respectively.
c, 17d, and fourth and fifth windows 18c, 18d, respectively, are bored in the circumferential direction. Furthermore, a pair of disks 1
A predetermined number of protrusions 17e extending radially outward are provided at the outer peripheral end of 7.18.

18e is formed. Protrusion 17e on disk 17 side
is arranged to face the groove bottom 14b formed between the teeth 14d of the lock-up piston 14.

Further, the disk 17 has a bent portion 17f continuous to the second bulging portion 17b. The height of this bent portion 17f is set to approximately the thickness of the second driven plate 20. Then, the first and second bulges 17a, 1
7b and the bent portion 17f, the disk 17 has a ribbed shape, and its rigidity is extremely high. Similarly, the third m! on disk 18! Tabe 1
A bent portion 18f is formed continuously from 8a. The height of this bent portion 18f is set to the thickness of the horizontal drive plate 16. Further, a flange portion 18g extending in the axial direction is formed at the inner peripheral end of the disk 18. and third and fourth bulges 18a.

18b, the bent portion 18f, and the flange portion 18g, the disk 18 has a rib shape, and its rigidity is extremely high.

A predetermined number of windows 20a are formed in the second driven plate 20, the same number as the windows 17d and 18d. Further, the center portion of the second driven plate 20 is formed with an axial bulge 20b that protrudes to one side.
A relatively large hole 20c in b and around this hole 20c,
A predetermined number of rivet holes 20d, 20d, . . . are bored.

The drive plate 16 has a groove 1 at its outer peripheral end.
The lock-up piston 14 is spline-fitted by fitting the teeth 14a of the lock-up piston 14 into the lock-up piston 6a. Further, the pair of disks 17 and 18 of the first driven plate 19 are arranged so as to sandwich the drive plate 16 on the outer circumference side and the second driven plate 20 on the inner circumference side. .18 is connected between the drive plate 16 and the second driven plate 20 by a predetermined number of rivets 21. In that case, the first buffer member 22 made of a compression coil spring is housed in the first window 16b and the first and third bulging parts 17a, 18a, and the second and fourth bulging parts 17b .

A second buffer member 23 made of a compression coil spring is housed in the recessed fitting portion 18b and the recessed fitting portion 20a. Also 2 cars disc 1
Since 7.18 does not undergo relative sliding at t/X, a spacer is not required. In this way, similarly to the damper mechanism described in the above-mentioned publication, the first driven plate 19 is connected to the drive plate 16 via the first buffer member 22 so as to be slidable relative to the first driven plate 19 in the circumferential direction. A second driven plate 20 is coupled via a second buffer member 23 so as to be relatively movable in the circumferential direction. Further, the inner peripheral end of the second driven plate 20 is fixed to the flange portion 8a of the turbine hub 8 by a rivet 24 so as to be collinear with the turbine impeller 6.

In that case, the second driven plate 20 is positioned in the axial direction by the flange portion 8a.

Thus plate 16. 19. In the assembled state of 20, the bulging portion 20b of the second driven plate 20
The inner peripheral flange portion 18g of the disk 18 is attached to the peripheral wall 20e of the disc 18.
comes to be abutted and supported, thereby performing centering.

Next, the operation of this embodiment will be explained.

When the drive plate 3 rotates due to the drive torque from the engine, the pump impeller 4 rotates.

The rotation of the pump impeller 4 causes the working fluid to be discharged toward the turbine impeller 6. The discharged working fluid causes the turbine impeller 6 to rotate. This rotation of the turbine impeller 6 is transmitted to the input shaft 7 via the turbine hub 8, causing the input shaft 7 to rotate. In that case, the flow direction of the working fluid flowing out from the turbine impeller 6 is not changed by the stator blade rlL9, and the transmitted torque increases. Furthermore, when the rotational speed exceeds a predetermined number, the stator impeller 9 also begins to rotate, so the torque to be transmitted does not increase, and the torque converter 1 functions simply as a fluid coupling.

For example, when the vehicle speed exceeds a predetermined value, the lock-up piston 14 of the lock-up mechanism 12 operates, and the friction material 13 comes into frictional engagement with the drive plate 3. That is, the torque converter 1 enters a lock-up state. As a result, the drive plate 3 and the turbine hub 8 are directly connected, and torque is directly transmitted mechanically to the turbine hub 8 without using fluid.

When the friction material 13 frictionally engages with the drive plate 3, there is a difference between the torque of the drive plate 3 and the torque of the turbine hub 8, so that shock and vibration are generated in the lock-up piston 14. In that case, the torque is - the first drive plate 16, the first buffer member 22, the first driven plate 19 consisting of two disks, the second buffer member 23,
The signal is transmitted to the second driven plate 20 in this order. therefore.

Since the torque is received and stopped in series by the first and second buffer members 22, 23, the shocks and vibrations thereof are effectively absorbed and alleviated.

By the way, the flange portion 18g at the inner peripheral end of the disk 18 is connected to the *wall 2O of the bulge portion 20b of the second driven plate 20.
Since it is supported on the e-plane, the centering of the first driven plate 19 is reliably performed. That is, the flange portion 18g forms a centering portion6. Therefore, the first and second driven plates 19, 20 are hardly inclined toward each other.

The contact pressure between them is reduced. This suppresses the wear of both the plates 19 and 20, making it possible to significantly improve the wear resistance of the damper mechanism.

Furthermore, during operation of the torque converter 101, centrifugal force due to rotation acts on the first and second buffer members 22,23. The centrifugal force causes the first and second buffer members 22.
23 attempts to deform the pair of disks 17 and 18.

However, since the disks 17, 18 are rib-shaped and their rigidity is large enough to withstand the force of pushing them open, deformation of these disks 17, 18 is reliably prevented.

Furthermore, the torque from the lock-up piston 14 is transmitted in series to the drive plate 16, the first buffer member 22, the first driven plate 1, the second buffer member 23, and the second driven plate 2o. The torque capacity that can be absorbed can be increased without increasing the diameter of the mechanism 15.

Furthermore, since the pair of discs 17 and 18 are only connected between the first buffer member 22 and the second buffer member 23, the number of rivets and presses used to form each disc are significantly lower than in conventional damper mechanisms. Not only is there one less molded product, but there is no need for a spacer. Therefore, the number of parts can be reduced.

Furthermore, since spacers and rivets are no longer provided between the second buffer members 23, it is possible to increase the axial length of the second buffer members 23, and it is possible to obtain a damper mechanism with high torque and high torsion angle. become able to.

Note that the present invention is not limited to the above-mentioned embodiments,
Various design changes are possible.

For example, in the above-mentioned embodiment, the flange portion 18g is provided at the inner peripheral end of the disk 18, but the flange portion may be provided at the outer peripheral end of the disk 17. In that case, the flange portion is provided on the lock-up piston. It is supported on the inner circumferential surface of the axial flange portion in which 14 teeth 14a are formed.

Further, in the above embodiment, the first and second buffer members 22.
Although a compression coil spring is used for 23, other cushioning members such as rubber may also be used.

Further, in the embodiments described above, rivets are used as fasteners to connect the pair of disks, but other fasteners such as screws and bolts may also be used.

Furthermore, in the above embodiments, the present invention is explained using a torque converter as a fluid transmission device, but a fluid coupling (
It can also be applied to other fluid transmission devices such as fluid couplings).

[Brief explanation of the drawing]

FIG. 1 is a schematic overall sectional view of an automatic transmission equipped with a torque converter to which an embodiment of a direct coupling clutch in a fluid transmission device according to the present invention is applied, FIG. 2 is a sectional view of the torque converter, and FIG. FIG. 4 is a cross-sectional view of a damper mechanism in the torque converter, FIG. 4 is a cross-sectional view of a conventional torque converter, and FIG. 5 is a diagram showing a conventional damper mechanism used in the torque converter. 1... Torque converter (fluid transmission device), 12.
...Lockup machine i14...Lockup piston 15...Damper mechanism 16...Drive plate,
17.18...Disk length 18g...Flange part (
Centering part), 19... 1st driven plate, 20...
...Second driven plate, 20b...Axial expansion center 20e...Peripheral wall, 22...First buffer member, 23
...Second shock absorbing member patent applicant Aisin ADA Co., Ltd. (
(1 other person) Representative Patent Attorney Kenji Aoki (6 others) Figure 3

Claims (1)

[Claims] (1) Provided in a fluid transmission device that transmits driving torque from an input member to an output member via fluid, the lock-up piston directly connects the input member and the output member, and the impact is applied to the lock-up piston. In a direct coupling clutch equipped with a damper mechanism that absorbs and alleviates a first driven plate connected to the driven plate; and a second driven plate connected to the driven plate through a second buffer member so as to be relatively rotatable, and whose inner peripheral end is connected to the output member; The second driven plate has a cylindrical portion extending axially inwardly in the radial direction, and the inner peripheral end of the first driven plate is provided with a centering portion that abuts the cylindrical portion in the radial direction. A direct coupling clutch in a fluid transmission device characterized by: