JPH0652090B2 - Rotational vibration absorber Transmission device - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a transmission device equipped with a rotary vibration absorber, for example, vibrationally absorbs the rotation of an internal combustion engine of a vehicle or the like to smoothly transmit power. Therefore, the present invention relates to a transmission device applied to a power transmission system.

[Conventional technology]

Absorbing the rotational vibration of the internal combustion engine is caused by a tapping sound generated in a rotational gap in the power transmission path, for example, a tooth surface gap of a meshing gear of a gear type transmission of a vehicle or a propulsion shaft. It has been known for a long time that the resonance of the rotating inertial body and the like and, as a result, the effect of suppressing various noises propagated to and generated in the vehicle body are effective, and various devices have been proposed.

One of them is a device provided with a plurality of rotary inertia bodies opposed to each other on a rotary shaft, and provided with a damping means for imparting resistance to relative rotation of both rotary inertia bodies (for example, Japanese Patent Laid-Open Publication No. Sho. Fifty
-25907).
Further, based on such a device, a device in consideration of application of a clutch device for appropriately connecting and disconnecting a transmission state between an internal combustion engine of a vehicle and a gear type transmission (for example, Japanese Patent Laid-Open No. 54-700).
No. 8 or an apparatus as disclosed in Japanese Patent Laid-Open No. 55-20964) is also known.

When arranging two rotary inertia bodies, for example, one of the rotary inertia bodies is fixed to the output shaft of the internal combustion engine such as a wheel, and the other of the rotary inertia bodies is fixed to the driven shaft. In the case of disposing the clutch device, the other of the rotary inertia bodies cannot be directly fixed to the driven shaft. Therefore, it is conceivable to mount the two rotary inertia bodies on the output shaft side of the internal combustion engine. In this case, it is necessary to mount the bearing between the two rotary inertia bodies in consideration of receiving the axial direction when the clutch device is released and taking into consideration the rotation between the two rotary inertia bodies.

Further, in the case where the whole device is to be made compact, a sliding bearing is considered as the bearing, and in consideration of the above points, the flanged bearing is suitable, and a conventionally known device (for example, JP-A- 54-7008 or JP-A-55.
It is also used in the apparatus disclosed in Japanese Patent Publication No. 20964).

When the flanged bearing is mounted between the two rotary inertia bodies, the tubular portion holds the concentricity of the two rotary inertia bodies and receives the axial force at the flange portion. Also, since the power transmission system of the vehicle is arranged to extend in the horizontal direction,
A radial force corresponding to the weight of either one of the two rotary inertia bodies and the majority of the weight of the clutch device is applied to the tubular portion of the flanged bearing. On the other hand, when the two rotary inertia bodies rotate relative to each other, the sliding speed differs between the tubular portion and the flange portion of the flanged bearing. Therefore, it is necessary to satisfy different usage conditions with one bearing, and it is difficult to perform the optimum design in consideration of uniform wear in both parts.
In addition, there is a similar problem when selecting the bearing material, and the cost becomes higher in terms of manufacturability due to the collar, and there is still room for consideration when it is put to practical use.

The present invention has been made in view of the above points, and it is an object of the present invention to provide a rotary vibration absorbing device-attached transmission device that satisfies different usage conditions and can maintain stable vibration absorbing characteristics for a long period of time.

[Means for solving problems]

The present invention relates to a first rotating member connected to an output shaft of an internal combustion engine, a second rotating member arranged on the first rotating member and connected to an input shaft of a transmission through a clutch mechanism, First
The rotary vibration absorber installed between the rotary member and the second rotary member, and the first rotary member disposed between the first rotary member and the second rotary member in the radial direction. The rolling bearing that positions the rotary member and the second rotary member concentrically and allows the rotation of both rotary members, and the first rotary member and the second rotary member in the axial direction. A thrust member arranged to restrict axial displacement of the rolling bearing toward the first rotating member and allow the respective rotating members to rotate, and the rolling bearing to the first rotating member. And a retaining ring provided so as to restrict axial displacement of the second rotary member toward the second rotary member.

〔Example〕

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a cross-sectional view showing an example of a transmission device with a rotary vibration absorber according to the present invention, showing an output shaft 1 of an internal combustion engine and an input shaft 2 of a transmission arranged in a transmission system such as wheels. This is an example of the arrangement. The transmission device with a rotary vibration absorber (hereinafter simply referred to as “transmission device”) 3 is a first transmission device mainly connected to the output shaft 1.
The rotating member 10 and the second rotating member 2 connected to the input shaft 2.
0 and a rotary vibration absorbing device 30 arranged between the rotary members 10 and 20. A clutch device is provided between the transmission device 3 and the input shaft 2 so as to intermittently connect and disconnect the transmission state.

The drive plate 11 is fastened to the output shaft 1 of the internal combustion engine by bolts 18, a sleeve 12 is formed at an inner portion in the radial direction so as to extend in the axial direction, and an outer portion than the sleeve 12 portion is formed. A sliding surface 13 is formed on the. An annular member 15 having a ring gear is fixed to the outer peripheral portion of the drive plate 11 with bolts 19. The annular member 15 includes a frictional contact portion 16 extending inward in the radial direction. The contact surface 14 is also formed on the portion of the drive plate 11 facing the contact portion 16.
Thus, these members present a rotary inertial body, and
It serves as the rotating member 10.

A driven plate 23 having an approximately L-shaped cross section and an auxiliary plate 24 are fixedly fastened by bolts 28 to the inner peripheral portion of the driven plate 21, and these members exhibit a rotational inertial body, and the second rotation. It becomes the member 20. A disc spring 33 is sandwiched between the driven plate 23 and the auxiliary plate 24.
The friction plates 32, 32 are pressed against the friction contact surface 14 of the drive plate 11 and the friction contact portion 16 of the annular member 15 by the force of
The drive plates 31, 31 frictionally engaged with the rotating member 10 are the second
The auxiliary plate 24 serving as the rotating member 20 and the driven plate 23 are arranged so as to be rotatable relative to each other.

The driven plate 23, the auxiliary plate 24, and the drive plates 31, 31 are formed with rectangular windows or notches at positions corresponding to the axial direction, and the windows or notches have elastic members (for example, as shown in the drawing). A coil spring) 35 is mounted. The driven plate 23, the auxiliary plate 24, and the drive plate 3 are interposed via the elastic member 35.
1, 31 and the elastic member 3
By elastically contracting 5, the driven plate 23, the auxiliary plate 24, and the drive plates 31, 31 can rotate relative to each other. Drive plates 31, 31
A friction plate 36 is inserted between one of them and the auxiliary plate 24, and is pressed by a pressing plate 38 and a disc spring 37 that are in contact with the driven plate 23. As a result, a resistance force is applied to the relative rotation of the driven plate 23, the auxiliary plate 24, and the drive plates 31, 31. Thus, at least these members serve as the rotary vibration absorbing device 30 that establishes an absorptive transmission relationship between the first rotating member 10 and the second rotating member 20.

The inner peripheral portion 25 of the driven plate 23 is supported by a rolling bearing (in this example, a double-row type ball bearing) 41 fitted in the sleeve 12 portion of the drive plate 11 and prevented from coming off by the retaining ring 17. There is. As a result, the first rotating member 10 and the second rotating member 20 are positioned concentrically, and relative rotation of both rotating members 10.20 is allowed smoothly.

Between the sliding surface 13 of the drive plate 11 and the sliding surface 26 of the driven plate 23, a resin-made thrust member 42 having a low friction coefficient and wear resistance is provided. This makes the first
The axial displacement of the second rotary member 20 relative to the rotary member 10 (in this example, the displacement in the left direction in the drawing) is restricted.

The clutch device 5 is a so-called diaphragm spring type clutch, and a clutch plate 51 fixed to a right surface of the driven plate 21 in the drawing by a bolt 29 is engaged with the pressure plate 5 that is displaceable only in the axial direction.
2, the pivot rings 54, 54 and the set rivet 5 to press the pressure plate 52 to the left in the drawing.
A diaphragm spring 53 supported by 5 is provided. Between the frictional contact surface 27 of the driven plate 21 and the pressure plate 52, friction facings 57, 57 fixed to the outer peripheral portion of the clutch disk 58 tacked to the hub 59 that is splined with the driven shaft 2. Is pinched. The illustrated state shows the clutch engagement state, and power can be transmitted from the driven freight 21 to the driven shaft 2 (or vice versa). Reference numeral 56 is a clutch release member for operating the engagement and disengagement of the clutch device 5.

Next, the operation of the above component device will be described. When the internal combustion engine is activated, rotational power is transmitted from the output shaft 1 to the first rotating member 1
From 0 to the second rotation member 2 via the rotary vibration absorber 30.
It is transmitted to 0. If the clutch device 5 is in the engaged state (state shown in the figure), power is transmitted to the input shaft 2 via the clutch device 5. In such a transmission operation, the rotational vibration from the internal combustion engine is absorbed by the elastic member 35 and the friction plate 36. Further, in the case where a sudden rotation vibration more than the permissible level occurs in the power transmission system and an abnormal rotation torque is generated, the load of the disc spring 33 and the friction plates 32, 32
When the torque is equal to or more than the transmission allowable rotational torque value determined by the friction coefficient of No. 1 or the like, slippage occurs between the drive plates 31 and 31 and the friction plates 32 and 32, or between the friction plates 32 and 32 and the friction surfaces 14 and 16. Occurs, and torque transmission is limited.

When the elastic member 35, the friction plate 36, and the like perform a vibration absorbing action, the first rotating member 10 and the second rotating member 20 rotate relative to each other, but both rotating members 10 and 20 are rolling bearings 4.
Since the bearing relationship is maintained by No. 1, the vibration absorption characteristics are also stable. Further, the resin-made thrust member 42 having a low friction coefficient and abundant wear resistance is attached to the first rotating member 10
Since it is arranged so as to contact the inner surface of the rolling bearing 41 and the first rotating member 10 side of the rolling bearing 41, smooth relative rotation between the first rotating member 10 and the second rotating member 20 can be obtained, and vibration absorption can be achieved. The characteristics are stable. In the power transmission state, the second rotary member 20 is supported on the first rotary member 10 by the rolling bearing 41 on the one hand, and is supported on the input shaft 2 via the clutch device 5 on the other hand. Therefore, no eccentric force acts on the rolling bearing 41. Further, a large thrust force does not act on the thrust member 42, so that the product of the load on the sliding surface and the peripheral speed is low.

To release the clutch device, the clutch release member 56 may be displaced leftward from the illustrated state and the inner peripheral portion of the diaphragm spring 53 may be pressed. As a result, due to the action of the diaphragm spring 53, the pressure fret 52 is separated rightward, and the friction facing 5
The pinching force applied to 7, 57 is released, and the transmission path between the second rotating member 20 and the input shaft 2 is blocked. At this time, the thrust force of the clutch release member 56 is received by the thrust member 42.

In the clutch released state, the second rotating member 20 is supported by the first rotating member 10 by the rolling bearing 41, but is pressed to the left in the drawing for the clutch releasing action, and the power is transmitted. The eccentric force does not act because it does not act. Furthermore, the first rotating member 10 and the second
Since the rotary member 20 often rotates integrally with the rotary member 20, the thrust member 42 receives a large load, but the peripheral speed is low, and as a result, the product of the load and the peripheral speed is low. .

The thrust member 42 is required to have a low friction coefficient and a high wear resistance, but it is used in the vicinity of an internal combustion engine, and heat generation in a vibration absorber or a clutch device.
Further, in consideration of heat generation of the thrust member, a heat resistant resin is preferable. Generally, phenolic resins are considered to be suitable. As suitable for the device according to the present invention, when confirmed by various tests, phenol resin 20 to 60% by weight, graphite 15 to 60% by weight, reinforcing materials 10 such as asbestos, carbon fiber and glass fiber 10
The compounding ratio is 25% by weight and the other 5 to 15% by weight. The most preferable mixing ratio is 30% by weight of phenol resin, 40% by weight of graphite, 10% by weight of asbestos, 10% by weight of carbon fiber, and 10% by weight of curing agent / blocking inhibitor.

In addition, with the above-mentioned resin material (hereinafter referred to as an example),
The thrust 42 member is molded and the test results are shown together with the comparative example as follows.

The mixing ratios of Comparative Examples 1 and 2 are as follows.

[Comparative Example 1] Phenolic resin 30% by weight Graphite 50% by weight Carbon fiber 15% by weight Curing agent / blocking inhibitor 5% by weight [Comparative Example 2] Phenolic resin 45% by weight Graphite 10% by weight Asbestos 30% by weight Curing agent / block Inhibitor 10% by weight Further, the test was conducted at an ambient temperature of 25 ° C to 100 ° C.

As the rolling bearing 41, an outer roller bearing such as a ball bearing or a needle roller bearing can be used.

〔The invention's effect〕

According to the present invention, the two parts of the rolling bearing, in which the respective portions of the first rotating member and the second rotating member that allow rotation, are arranged in the radial direction and the specified thrust member provided in the axial direction are separate members. Since it is composed of the members, it is possible to easily and inexpensively optimize each of them according to the usage conditions. As a result, it is possible to obtain a stable vibration absorption characteristic as compared with the conventional one while maintaining the relative rotation between the first rotating member and the second rotating member. Further, the thrust member is arranged so as to regulate the axial displacement of the rolling bearing toward the first rotating member side, and the retaining ring regulates the axial displacement of the rolling bearing toward the second rotating member side. Since the thrust member and the retaining ring are provided, most of the moving force due to the pressing force and the vibration when the clutch device is released can be provided. Thus, the axial movement of the second rotating member with respect to the first rotating member can be restricted by the thrust member and the retaining ring, and as a result, the pressing force and the moving force carried by the rolling bearings are alleviated and the rolling motion is reduced. The durability of the dynamic bearing can be greatly improved.

The present invention is not limited to the examples, for example,
It goes without saying that the present invention can be applied to a transmission device having a damper device incorporated in a clutch disc or a damper device incorporated in a fluid coupling (for example, a direct coupling clutch portion of a torque converter).

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view showing an example of a transmission device with a rotary vibration absorber according to the present invention. DESCRIPTION OF SYMBOLS In the drawings, 1 is an output shaft of an internal combustion engine, 2 is an input shaft of a transmission, 3 is a transmission device with a rotary vibration absorbing device, 10 is a first rotating member, 17 is a retaining ring, 20 Is a second rotary member, 30 is a rotary vibration absorber, 41 is a rolling bearing, and 42 is a thrust member.

 ─────────────────────────────────────────────────── ─── Continuation of front page (56) Reference JP-A-55-20964 (JP, A) JP-A-53-116633 (JP, A) JP-B 41-12689 (JP, B1) JP-B 44- 17247 (JP, B1)

Claims (1)

[Claims] 1. A first rotating member connected to an output shaft of an internal combustion engine, and a second rotating member arranged on the first rotating member and connected to an input shaft of a transmission through a clutch mechanism. A rotary vibration absorbing device that is installed between the first rotating member and the second rotating member, and is arranged between the first rotating member and the second rotating member in the radial direction. A rolling bearing that positions the first rotating member and the second rotating member concentrically and allows the respective rotating members to rotate, and the first rotating member and the second rotating member in the axial direction. A thrust member disposed between the rolling member and the first rotating member so as to restrict axial displacement of the rolling bearing toward the first rotating member and allow the respective rotating members to rotate. In order to regulate the axial displacement of the rolling bearing toward the second rotating member side. Rotational vibration device Supplementary transmission having an eclipse was snap ring.