JPH05346138A - Torque transmission device - Google Patents

Abstract

PURPOSE:To improve durability and to reduce cost by interposing a sealing member between an inner ring and an outer ring in a rolling bearing, and interposing the resin whose friction coefficient is relatively large between the rolling bearing and one of the flywheels in a condition with tightening margin. CONSTITUTION:A torque transmission device is provided with two flywheels 2, 3 supported by a rolling bearing 4 in a relatively rotatable manner, and a buffer mechanism 5 to suppress the relative rotation is interposed therebetween. The first flywheel 2 is fixed to the crankshaft of the engine, while a friction clutch is fixed to the second flywheel 3, and a clutch disc is interposed therebetween. A rolling bearing 4 constituted by interposing a sealing member 43 consisting of an annular rubber to seal the space between an inner ring 41 and an outer ring 42. The outer circumferential surface and the edge surface of the outer ring 42 are covered by a pair of heat-insulating covers 6 which are formed in L-shaped section respectively.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention has a first flywheel which can be fixedly connected to an output shaft of an internal combustion engine, and a friction surface for engaging a clutch disc, and a rolling bearing. Second flyable relative to the first flywheel
The present invention relates to a torque transmission device having a flywheel.

[0002]

2. Description of the Related Art Conventionally, in this type of torque transmission device, one race ring of the rolling bearing is fixedly directly connected to one flywheel and the other race ring is fixedly directly connected to the other flywheel. It was Therefore, when the clutch is slipping, the temperature of the rolling bearing is 25 degrees Celsius because of the heat transferred from the friction surface to the rolling bearing.
There were cases where the temperature was as high as 0 to 300 degrees. Under the influence of this high temperature, a large difference in thermal expansion is caused between the parts of the rolling bearing due to the temperature difference, so that the bearing play is lost, and the lubricant such as grease inside the bearing is deteriorated at an early stage. Therefore, there is a problem that the life of the rolling bearing is shortened.

On the other hand, a shock absorbing mechanism for suppressing relative rotation of both flywheels includes a viscous damper mechanism utilizing throttle resistance such as grease, and the damper grease is circulated by passing near the rolling bearing. There was also a problem that the damper grease would penetrate into the bearing. Therefore, as shown in FIG. 3, the outer ring 9 of the rolling bearing is
1 bends from the outer circumference to the shoulder of the end surface of the inner ring 92,
A pair of resin heat insulating covers 93 having an L-shaped cross section are provided to improve heat insulating properties of the bearing, and the leg portions 93 of the heat insulating cover 93 are also provided.
There is provided a torque transmission device in which a is pressed against the end surface shoulder portion of the inner ring 92 by the disc spring 94 to seal the inside of the rolling bearing (JP-A-2-85).
31). In this torque transmission device, in order to absorb the shock when the clutch is operated and prevent the damper grease from entering the inside of the bearing, the outer ring 91
O-rings 95 are attached to annular steps formed on both shoulders.

[0004]

In the above torque transmission device, since the heat insulating cover 93 is in sliding contact with one end surface of the inner ring 92, the heat insulating cover 93 has a sliding property in addition to the heat insulating property. It is required to have excellent properties. Therefore, an expensive material such as PEEK resin has to be used as the material of the heat insulating cover. In addition, since the disc spring 94 and the O-ring 95 are required, the number of parts is large, and therefore, the number of assembling steps is large, and the material cost of the heat insulating cover 93 is high, and the manufacturing cost is high.

Further, the heat insulation cover 9 is provided by the disc spring 94.
3 has a structure in which it is sealed by the contact surface pressure of the inner ring 92 pressed against the end surface of the inner ring 92, so the sealing performance deteriorates due to the effect of rattling in the axial direction. For this reason, there is a problem that the grease inside the bearing flows out and the air invades, which causes oxidative wear due to microvibration and shortens the life of the bearing.

Furthermore, since the heat insulating cover 93 is required to have excellent slidability, a material having a low friction coefficient has been used. Therefore, in order to obtain the fixed holding force of the outer ring 91 of the rolling bearing, it is necessary to set the tightening margin to be high, and therefore, the radial gap of the bearing becomes small, which is a cause of premature seizure. This invention is
It is an object of the present invention to solve the above technical problems and to realize a torque transmission device which can improve the durability of a rolling bearing and is low in manufacturing cost.

[0007]

In order to achieve the above object, a torque transmission device according to a first aspect of the present invention is rotatably supported relative to each other via a rolling bearing and relatively opposed via a buffer mechanism. First and second flywheels whose rotation is suppressed are provided, and the first flywheel includes:
In a torque transmission device, which is fixedly connectable to an output shaft of an internal combustion engine, the second flywheel comprises a friction surface for engagement with a clutch disc of a friction clutch, the rolling bearing comprising: A rolling member and a flywheel having a friction coefficient between the rolling bearing and the second flywheel are provided which are provided between the inner ring and the outer ring and seal between the inner ring and the outer ring. It is characterized in that a resin, which is larger than the metal constituting the above, is interposed in the state of having a tightening margin.

[0008]

[Operation] Since the rolling bearing is a so-called sealed type,
The inside of the bearing is highly sealed, and the outflow of the lubricant from the inside of the bearing and the intrusion of air into the inside of the bearing are prevented. Therefore, it is possible to prevent the occurrence of oxidative wear due to slight vibration. Further, since the sealing property of the rolling bearing is secured by the above-mentioned seal member, it is not necessary to slide the heat insulating cover on the end face of the bearing ring to seal as in the conventional case. It is not necessary to use an expensive material that also has sliding contact properties, the selection range of the material of the heat insulating cover is wide, it is possible to select one with low cost, and it is easy to fix and hold the bearing outer ring You can

Further, since the seal member interposed between the inner and outer rings buffers the impact between them and suppresses the generation of abrasion powder, the durability of the rolling bearing is improved in combination with the prevention of the above-mentioned oxidative abrasion. You can

[0010]

Embodiments will be described in detail below with reference to the accompanying drawings showing embodiments. FIG. 1 shows a torque transmission device according to an embodiment of the present invention. Referring to FIG. 1, the torque transmission device 1 includes first and second flywheels 2 and 3 rotatably supported by a rolling bearing 4.
And a cushioning mechanism 5 interposed between the flywheels 2 and 3 to suppress relative rotation between the flywheels 2 and 3.

The first flywheel 2 is fixed to a crankshaft 7 of an engine (not shown) via fixing screws 8. A friction clutch 9 is fixed to the second flywheel 3 by means not shown. Between the pressure plate 10 of the friction clutch 9 and the second flywheel 3,
A clutch disc 11 is provided, and the clutch disc 11 is attached to an input shaft 12 of a transmission device (not shown). A friction surface 3 a against which the clutch disc 11 is pressed is provided on the right side surface of the second flywheel 3.

The cushioning mechanism 5 includes the first flywheel 2
And a ring-shaped seal plate 52 that is non-rotatably connected to each other by a stud pin 51. Inner peripheral flange portion of the seal plate 52 and the boss portion 3a of the second flywheel 3
The outer periphery of the base end is sealed with a seal 59. An O-ring 60 seals between the first flywheel 2 and the outer peripheral side surface of the seal plate 52. The buffer space K sealed by the seal 59 and the O-ring 60 is filled with grease for providing a viscous damping action.

The buffer mechanism 5 is spline-coupled to the outer periphery of the boss portion 3a of the second flywheel 3 and a slider 53 which is allowed to rotate relative to the first flywheel 2 within a predetermined angle range. , Two drive plates 54 and 55 arranged on both sides of the slider 53 and integrally rotatably coupled by the first flywheel 2 and the stud pin 51, and a plurality of drive plates housed in a recess provided in the slider 53. Coil type torsion spring 56 for power storage
A spring seat 57 attached to the drive plates 54, 55 to receive one winding end of the torsion spring 56, and a driven plate 58 attached to the slider 53 to receive the other winding end of the torsion spring 56. It has and. The rotation of the slider 53 is restricted by the stud pin 51 and the slide stopper 61.
It is performed by abutting on.

When the flywheels 2 and 3 are twisted relative to each other, the torsion spring 56 is bent and the volume of the buffer space K is contracted so that the buffer space K is filled. The grease moves to the rolling bearing 4 side with a predetermined outflow resistance, and then returns to the buffer space K side again by centrifugal force. With reference to FIG. 1 and FIG. 2, the rolling bearing 4 has an inner ring 4
1, a hermetically sealed type having a pair of seal members 43 interposed between the outer ring 42, the balls 43, and the inner and outer rings 41, 42 to seal the inside of the bearing. The outer circumference 41a and the end surface 41b of the outer ring 41 of the rolling bearing 4 are covered with a pair of heat insulating covers 6 having an L-shaped cross section. This insulation cover 6
Is for preventing frictional heat from the friction surface 3 a of the second flywheel 3 from being transmitted to the rolling bearing 4.

The outer ring 42 of the rolling bearing 4 is integrally rotatable with the second flywheel 3 through the heat insulating cover 6 at the inner peripheral step of the central boss portion of the second flywheel 3. It is attached in a state where movement in the direction is restricted by the snap ring 13. On the other hand, the inner ring 41
Is attached to the outer peripheral step portion of the boss portion 2a of the first flywheel 2 so as to be integrally rotatable and restricted in axial movement.

Annular recesses 42a are formed in the inner peripheral portion of the outer ring 42 at both axial ends thereof, respectively, and are cut out in a rectangular cross section. At the outer peripheral portions of the inner ring 41, both axial end portions thereof are formed. , Annular recesses 4 each having a circular cross section of 1/4
1a is formed. The seal member 44 is the outer ring 4
An annular outer peripheral seal portion 44a housed in the second annular recess 42a, a double lip annular inner peripheral seal portion 44 abutting on the outer peripheral surface of the inner ring 41 and the peripheral surface of the annular recess 41a.
b, a main body rubber portion 44c that connects the outer peripheral seal portion 44a and the inner peripheral seal portion 44b, and a metal plate having an L-shaped cross section that reinforces the seal member 44 along the main body rubber portion 44c and the outer peripheral seal portion 44a. Reinforcement plate 44d
It has and. Acrylic rubber or the like can be exemplified as the rubber forming the seal member 44.

As the material of the heat insulating cover 6, synthetic resin such as PPS resin, which is excellent in heat insulating property and inexpensive and has a friction coefficient larger than that of the metal forming the bearing 4 and the flywheel 3, can be exemplified. Radial portion 6a of heat insulating cover 6
The diameter of the inner peripheral portion is set such that a slight gap is formed between the inner peripheral portion and the end surface of the inner ring 41. This allows
The heat insulating cover 6 exhibits a so-called labyrinth effect with the end face edge portion of the inner ring 41, and the sealing performance is enhanced. In addition, the heat insulating cover 6 is P which has been used conventionally.
Since it has a larger friction coefficient than that of EEK resin, the second flywheel 3 and the outer ring 42 can be made with a slight interference.
Is intervened between.

According to this embodiment, since the rolling bearing 4 of the sealed type is used, the sealing performance inside the bearing is high, and it is possible to prevent the outflow of grease from the inside of the bearing and the intrusion of air into the inside of the bearing. Therefore, it is possible to prevent the occurrence of oxidative wear due to slight vibration. In addition, the rubber seal member 44 interposed between the inner and outer races 41 and 42 cushions the impact between the inner and outer races 41 and suppresses the generation of wear debris. The durability can be improved.

Further, unlike the conventional case, it is not necessary to slidably contact the end face of the bearing ring to seal the end face of the bearing ring, and therefore the heat insulating cover 6 which is cost effective without considering the slidable contact property.
The material can be selected, and the disc spring and the like which have been conventionally required are not required, and the number of parts and the number of assembling steps can be reduced, so that the manufacturing cost can be reduced. The present invention is not limited to the above embodiments, and various modifications can be made without changing the gist of the present invention.

[0020]

As described above, according to the torque transmission device of the present invention, since the sealed type rolling bearing is adopted, the outflow of the lubricant from the inside of the bearing and the intrusion of air into the inside of the bearing are prevented. As a result, it is possible to prevent the occurrence of oxidative wear due to slight vibration. Moreover, the seal member interposed between the inner and outer races buffers the impact between them and suppresses the generation of abrasion powder, so that the durability of the rolling bearing can be improved together with the prevention of the above-mentioned oxidative wear.

Further, unlike the conventional case, it is not necessary to slidably contact the end face of the bearing ring to seal it, so that the cost-effective material of the heat insulating cover can be selected without considering the slidability. Moreover, since it is possible to reduce the number of parts and the number of assembling steps by eliminating the need for a disc spring or the like, which has been conventionally required, there are various unique effects that the manufacturing cost can be reduced.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a main part of a torque transmission device as an embodiment of the present invention.

FIG. 2 is a vertical cross-sectional view of a torque transmission device.

FIG. 3 is a vertical sectional view of a main part of a conventional torque transmission device.

[Explanation of symbols]

 2 1st flywheel 3 2nd flywheel 4 Rolling bearing 41 Inner ring 42 Outer ring 44 Seal member 5 Buffer mechanism 6 Insulation cover 11 Clutch disc

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Mitsuhiko Takenaka 1-1 1-1 Kinomotomiya, Neyagawa City, Osaka Prefecture Daikin Co., Ltd.

Claims (1)

[Claims] 1. A first fly, which is provided with first and second flywheels which are rotatably supported relative to each other via a rolling bearing and whose relative rotation is suppressed via a buffer mechanism. The wheel is fixedly connectable to an output shaft of an internal combustion engine, and the second flywheel is a torque transmission device having a friction surface for engaging a clutch disc of a friction clutch. Is equipped with a pair of annular rubber sealing members that are interposed between the inner ring and the outer ring and seal between the inner ring and the outer ring. The rolling bearing having the coefficient of friction described above is provided between the rolling bearing and the second flywheel. Also, a torque transmission device is characterized in that a resin, which is larger than the metal constituting the flywheel, is interposed in a state having a tightening margin.