JPH0356675Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Purpose of the Invention] (Field of Industrial Application) The present invention consists of a drive plate fixed to a drive shaft, and a drive plate disposed coaxially with the drive plate so as to be able to rotate relative to the drive plate. The supported flywheel constitutes an inertial body, a torque limit mechanism and a damper mechanism are interposed between the drive plate and the flywheel, and the rotational torque of the drive shaft is transmitted through the drive plate and both mechanisms. The present invention relates to a rotational torque transmission device that transmits rotational torque to the flywheel, and is used as an automobile engine vibration absorption device.

(Prior Art) There is a prior art related to the present invention as shown in FIG.

This includes a drive plate 32 fixed to a drive shaft 31 and a flywheel 33 disposed coaxially with the drive plate 32 and supported on the drive plate 32 so as to be relatively rotatable. A torque limit mechanism 34 and a damper mechanism 35 are interposed between the plate 32 and the flywheel 33, and the rotational torque of the drive shaft 31 is transferred to the flywheel 33 via the drive plate 32 and both mechanisms 34 and 35.
The flywheel 33 is supported on the drive plate 32 by a bearing 36, and the bearing 3
A snap spring 37 is used to prevent the drive plate 6 from coming off from the drive plate 32.

(Problem that the idea aims to solve) This prior art has the following problems.

In other words, the axial length becomes longer because the snap spring prevents the bearing from coming off. In addition, it is necessary to manage the machining of stop grooves, etc.

Therefore, the technical objective of the present invention is to eliminate the slip-off prevention using a snap spring and solve the above-mentioned problems.

(Means for solving the problem) The technical means taken to solve the above technical problem is to support the flywheel to the drive plate via a bearing, and to fix the bearing to the drive plate to prevent it from coming off. In this case, the end of the inner race of the bearing interposed between the drive plate and the flywheel is tightened and fixed with bolts.

(Function) By taking the above technical measures, it is possible to prevent the bearing from coming off with a bolt. Therefore, since a snap spring is not required, the axial length can be shortened and machining of a retaining groove is not required.

(Specific Effects) The bearing of the present invention supports the weight of the flywheel. For this reason, the load of the flywheel always acts on the bearing, which poses a problem in bearing durability. Comparing the inner race and outer race of a bearing, the inner race is located closer to the drive shaft than the outer race, so the temperature due to heat transfer from the engine is higher, and the inner race has a higher temperature than the outer race. It is more prone to wear than lace. In order to improve the durability of the bearing as much as possible to overcome these problems, the present invention fixes the end of the inner race of the bearing by tightening it with bolts to prevent the inner race from slipping out or rattling.
Therefore, slight vibrations in the axial direction of the inner race can be stopped, and the life of the bearing can be extended.

(Example) Hereinafter, an example showing the above technical means will be described based on the drawings.

In FIG. 2, the rotational torque transmission device 1 is composed of two divided inertia bodies: a drive plate that is a rotating member and a flywheel that is a stator member.

The drive plate, which is a rotating member, includes a drive plate 7, an annular protrusion 10, and a ring gear 11.
The drive shaft 2 is connected and fixed to the drive shaft 2 with a bolt 8.

The flywheel, which is a stator member, is integrally composed of a flywheel 9 and a driven plate 16 that are connected and fixed to each other by bolts 17. A clutch cover 4 is positioned and fixed to the flywheel 9 by a pin 13. A pressure plate 6 is disposed within the clutch cover 4, a facing 5 of a clutch disk D is disposed between the pressure plate 6 and the flywheel 9, and a facing 5 of a clutch disk D is disposed between the pressure plate 6 and the flywheel 9. A driven shaft 3, which is an input member of a transmission (not shown), is connected to the shaft.

A damper mechanism A and a torque limit mechanism B are interposed between the drive plates 7, 10, 11 and the flywheels 9, 16.

The damper mechanism A includes a coil spring 26 and is held within a window 12 formed in the drive plate 7. The main body of the torque limit mechanism B is housed between the flywheel 7 and the driven plate 16, and includes, from the left in the drawing, a friction material 24, a drive disk 20, a disc spring 23, a drive disk 20,
The friction material 24 is arranged in this order, and the drive disk 2
0 and 20 extend to the position of the damper mechanism A in the radial direction. In this case, drive disk 2
A predetermined play is provided between the damper mechanism A and the damper mechanism A in the circumferential direction.

Further, a hysteresis mechanism C for absorbing torque vibration is interposed between the drive plate 7 and the driven plate 16 on the inner periphery of the rotational torque transmission device 1.

The flywheels 9, 16 are supported on the drive plates 7, 10, 11 through bearings 19. And bearing 19
Drive plates 7, 10, 11 and flywheels 9, 16 serve as axial fixing means to prevent them from coming off.
The end of the inner race 19a of the bearing 19 interposed between the two is tightened and fixed with the bolt 8. As a result, unlike the conventional case, a snap spring is not required, so the axial length can be shortened and machining of a stopper groove becomes unnecessary.

The operation based on the above configuration will be explained below.

In response to the rotation of the drive shaft 2, the drive plates 7, 10, 11, which are rotating members, move in the circumferential direction between the drive disks 20, 20 and the damper mechanism A, relative to the flywheels 9, 16, which are stator members. It rotates relatively by a predetermined amount of play. As a result, hysteresis torque is generated by the operation of the hysteresis mechanism C. When the relative rotation increases, the drive disks 20, 20 come into contact with the damper mechanism A, causing the coil spring 26 to elastically contract.

On the other hand, the flywheels 9 and 16 are operated by the friction material of the hysteresis mechanism C and the drive disks 20 and 20 of the torque limit mechanism B and the friction material 2.
It is rotationally driven by frictional action with 4 and 24.
Therefore, torque vibrations from the engine are absorbed by the operation of the damper mechanism A, the torque limit mechanism B, and the hysteresis mechanism C. In addition, if excessive torque vibration occurs, the drive disks 20, 20 of the torque limit mechanism A and the friction material 2
Because relative slippage occurs between 4 and 24,
Relative rotation occurs between the drive plates 7, 10, 11 and the flywheels 9, 16, and excessive torque vibrations are eliminated.

In this way, the bearing 19 not only supports the load in the axial direction and the load accompanying the relative displacement in the rotational direction between the drive plates 7, 10, 11 and the flywheels 9, 16 from the engine, but also supports the load in the axial direction of the flywheels 9, 16. Because it constantly supports the weight of
The durability of the bearing 19 becomes a problem. Also, when comparing the inner race 19a and outer race 19b of the bearing 19, the inner race 19
Since the inner race 19a is disposed closer to the drive shaft than the outer race 19b, the temperature due to heat transfer from the engine is higher, and the inner race 19a is more likely to wear than the outer race 19b.
In order to improve the durability of the bearing 19 as much as possible against such problems, the present invention fixes the end of the inner race 19a of the bearing 19 by tightening it with the bolt 8.
Eliminates the relief or looseness of a. Therefore, the slight axial vibration of the inner race 19a can be stopped, and the life of the bearing 19 can be extended.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a prior art rotary torque transmission device of the present invention, and FIG. 2 is a sectional view of an embodiment of the present invention. Explanation of symbols, 1...Rotary torque transmission device, 2...
... Drive shaft, 7, 10, 11 ... Drive plate, 9, 16 ... Flywheel, A ... Damper mechanism, B ... Torque limit mechanism, 8 ... Bolt, 19 ... Bearing, 19a ... Inner race, 19b...Outer lace.

Claims (1)

[Scope of utility model registration request] An inertial body is constituted by a drive plate fixed to the drive shaft and a flywheel arranged coaxially with the drive plate and supported by the drive plate so as to be relatively rotatable, and between the drive plate and the flywheel. In a rotational torque transmission device that includes a torque limit mechanism and a damper mechanism and transmits rotational torque of the drive shaft to the flywheel via the drive plate and both mechanisms, the flywheel is supported on the drive plate. A rotary torque transmission device that uses bolts to tighten and fix an end of an inner race of the bearing interposed between the drive plate and the flywheel through a bearing and as a means for fixing the bearing to the drive plate to prevent it from coming off. .