JPH042811B2 - - Google Patents

Description

[Detailed description of the invention]

(Objective of the Invention) (Industrial Application Field) The present invention relates to a friction type engagement disc device, and particularly relates to a friction type engagement disc device used in vehicles etc. and equipped with a shock absorber capable of absorbing torsional vibrations occurring in a transmission shaft system. disk device. (Prior Art) A friction type engagement disc device for a vehicle is generally placed in a power train equipped with a gear type transmission device to appropriately transmit power from an engine for driving the vehicle to the wheels. It has the function of intermittent power transmission between the engine and the gear type transmission as necessary, and the function of damping the periodic vibrations of the engine's rotational force. The periodic rotational force vibration of the engine, together with the play of the meshing gears of the gear transmission, causes the gear transmission to be in a neutral state when the engine rotational speed is relatively low and the rotational force is relatively small. When the engine is rotating, it generates so-called neutral noise, which is the rattling noise that occurs in the idle part of the gear, and when the engine rotational speed is relatively high and the rotational force is relatively large, the gear type transmission When it is placed in the high-speed stage (for example, in a direct connection state), it does not generate the above-mentioned neutral sound, but other high-frequency vibrations cause it and generate a shuffling sound. In order to absorb such vibrations, it is necessary to provide a shock absorber that has mutually contradictory damping characteristics. That is, in order to absorb neutral sound, it is sufficient to reduce torsional rigidity and damping characteristics. However, this is useless against the squealing noise that occurs when the engine rotational speed is relatively high and the rotational force is relatively large. To deal with this squealing sound, it is necessary to increase torsional rigidity and damping characteristics. In order to achieve both of these damping characteristics and absorb the above-mentioned vibrations, a shock absorber is provided that includes an elastic member, a friction resistance member, and a mechanism for appropriately operating these members in order to damp the vibrations of the periodic rotational force of the engine. Various types of friction-type engagement disc devices have been proposed (Japanese Patent Application Laid-open No. 113845/1984, US Pat. No. 3,327,820). The common structure of the above devices is that an elastic member is disposed across two members arranged so as to be able to rotate relative to each other, and a friction member is provided that provides a predetermined resistance force against the relative rotation of both members. The friction plate is provided with a control plate for operating the elastic member and the friction plate in appropriate steps according to the angle of relative rotation of both members. (Problems with Prior Art) However, while conducting various experiments, the applicant confirmed that the following problems occurred. That is, a control plate for operating a friction plate that provides a relatively low frictional resistance force, which is arranged to absorb neutral sound, and a control plate for operating a friction plate, which is arranged to absorb neutral sound, and a friction plate for each of two members arranged to be able to rotate relative to each other. Since the conditions of the surfaces that come into contact with the friction plates are different, the relatively low frictional resistance force changes as a result, making it impossible to maintain the frictional resistance force stably over a long period of time. That is, it is not possible to stabilize the so-called hysteresis that occurs in the torsion-per-rotation force characteristic of the friction type engagement disc device (which appears as a result of the action of frictional resistance force). (Means for Solving the Problems) The present invention has been made in view of the following points, and the control plate and the first and second thrust plates are made of the same material, thereby achieving friction that can eliminate the conventional problems. It is an object of the present invention to provide an engaging disk device. (Function) The first and second friction plates of the first and second thrust mechanisms can apply the same frictional resistance force no matter which side surface they rub against each other. Furthermore, even during long-term use, the progress of wear between the pressing surface and the frictional surface of the control plate is at the same level, so there is no sudden change in the frictional resistance force. As a result, hysteresis can be stabilized over a long period of time. (Example) Hereinafter, the present invention will be described with reference to the drawings. The hub member 1 is connected to a transmission shaft (not shown) (usually serves as an input shaft of a gear transmission) by a spline 11 formed in an inner cylindrical portion thereof, and has a spline 11 extending in the radial direction in an outer cylindrical portion 12 thereof. Flange member 13
are arranged integrally. A disk plate 2 and a sub-plate 3 are arranged on both sides of the flange member 13 in parallel with the flange member 13 and rotatable relative to the flange member 13, and both of these members are formed outside of the flange member 13. It is fixed by a connecting pin 14a extending horizontally through the notch 14. A hub member 1 is attached to the inner diameter portion of the disc plate 2.
A bushing 25 rotatably and slidably supported is fixed on the outer cylindrical portion 12 of. Further, an appropriate number of buffer spring plates 21 are fixed to the outer peripheral portion by studs 21a, and facings 22 are fixed to both sides of the spring plates 21 by studs 22a. The bush 25 is formed of a non-lubricant bearing material, a bearing material (bronze alloy, copper/lead alloy, aluminum alloy, overlay alloy), synthetic resin material, etc., and is relatively stable with respect to the outer circumference of the hub member 1. It can rotate and slide. A spring accommodation window 13 is provided in each of the flange member 13, the disk plate 2, and the sub-plate 3.
a, 2a, 3a, 13b, 2b, 3b, 13c,
2c and 3c are formed respectively. A coil spring SP1, which is one of the resilient members, is disposed in each of the accommodation windows 13a, 2a, and 3a, with its end seated on a washer 41 that can be commonly engaged with the windows. Similarly, each of the housing windows 13b, 2b, and 3b has a coil spring, which is one of the elastic members, with its end seated on a washer 42 that can be commonly engaged with the window.
SP2 is installed. Furthermore, the accommodation window 13c,
A coil spring SP3, which is one of the elastic members, is installed in 2c and 3c, as shown in the diagram (Fig. 1).
In the normal state, both ends of the coil spring SP3 are seated on the circumferential surface of each window 2c, 3c of the disk plate 2 and sub-plate 3, and are rotated by a predetermined rotation angle from the window 13c of the flange member 13. They are separated. In normal conditions, the end of the coil spring SP2 is spaced apart from the window 13b of the flange member 13 by a predetermined rotation angle, as shown in the first figure. Control plates 51 and 52 are arranged between the flange member 13 and the disk plate 2 and sub-plate 3, respectively, in parallel to the flange member 13. Both control plates 5
1 and 52 are windows 13b and 13 of the flange member 13
They are integrally connected by connecting pins 53 that pass through notches 15 formed inwardly in the radial direction of c and serve as horizontal connecting portions, and as a result, the notches 15 span the flange member 13. Shape control member 5
is formed. The control plates 51 and 52 have frictional surfaces 51a and 52a and an axial direction (particularly a fourth
With reference to the figure, ears 51b, 5 which are integrally formed and displaced by half the plate thickness (to the right in the figure) and to which the connecting pin 53, which is a connecting member, is riveted.
2b, and arm portions 51c and 52c that extend radially outward from the friction surfaces 51a and 52a and are engaged with the ends of the coil spring SP3. First friction plates 61, 62 are disposed between the friction surfaces 51a, 52a of the control plates 51, 52 described above and both side surfaces of the flange member 13. First friction plate 61
A first thrust plate 63 is disposed between the connecting pin 53 and the control plate 51 so as to be movable only in the axial direction. The first resilient member loaded with bullets, for example, a disc spring 64
As a result, the first friction plates 61 and 62 are pinched between both sides of the flange member 13 and the control plates 51 and 52. The first thrust mechanism 6 is composed of the first friction plates 61, 62, the first thrust plate 63, the disc spring 64, etc. described above. The relationship between the control plates 51, 52, the first thrust plate 63, and the flange member 13 (in normal state) is illustrated in FIG. 6. Separate second friction plates 71 and 72 are arranged between the control plates 51 and 52 and the disk plate 2 and sub-plate 3, respectively. A second thrust plate 73 is disposed between the second friction plate 72 and the sub-plate 3, with an axially extending protrusion 73a coupled to the engagement notch 31 of the sub-plate 3 so as to be movable only in the axial direction. The control plates 51, 52, the disk plate 2, and the sub-plate 3 are provided with a second resilient member, for example, another disc spring 74, which is elastically loaded between the second thrust plate 73 and the sub-plate 3. The second friction plates 71 and 72 are pressed between the plate 3 and the second friction plates 71 and 72. The second thrust mechanism 7 is composed of the second friction plates 71, 72, the second thrust plate 73, another disc spring 74, etc., which have been explained above. The first and second thrust plates 63, 73 are
The first and second friction plates 61 and 6 are made of the same material as the control plates 51 and 52 and have the same surface roughness.
The coefficient of friction when working together with 2, 71, and 72 is the same. Further, one side 71 of the second friction plate is fixed to the bushing 23 by well-known fixing means, and the second
It is even more effective to cause relative frictional sliding only between one side of the friction plate 71 and one side of the control plate 51. As a result, the frictional resistance by the first and second friction plates 61, 62, 71, 72 is stabilized. Furthermore, since the wear of the friction surfaces of the control plates 51 and 52 progresses at the same level even during long-term use, there is no sudden change in the frictional resistance force, and the hysteresis remains stable over a long period of time. The resiliency of each of the disc springs 64 and another disc spring 74 of the first thrust mechanism 6 and the second thrust mechanism 7 is set so as not to elastically deflect the control plates 51 and 52. In addition, the control plates 51 and 52 have elastic member housing windows (13b, 13b, and 13d, 13d) of the flange member 13.
The control plates 51 and 52 are connected to each other near the first and second thrust mechanisms 6 and 7 because the control plates 51 and 52 are connected to each other by connecting pins 53 that are disposed through respective notches 15 formed inwardly in the radial direction. The control plates 51, 52
becomes more rigid. Furthermore, since a notch for passing the connecting pin of the control plate between each window of the flange member 13 is not required, each window can be made larger without reducing the strength of the flange member 13, and the torsion angle can be set larger. . The first thrust plate 63, the disc spring 64, the second thrust plate 73, and the other disc spring 74 are not limited to the positions shown in the fourth diagram, for example.
It goes without saying that they can be arranged on opposite sides or in the same direction. The disc springs 64, 74 may be other spring members such as wave springs or conical coil springs. In addition, what is indicated by number 8 in FIG. 5 is a weight for balancing. Next, the operation of the above-mentioned device will be explained. Here, the control member 5 and the first and second thrust mechanisms 6 and 7 will be mainly explained in relation to the torsional rotational force characteristics. For convenience of explanation, the hub member 1 and flange member 13 are fixed, for example, in the first illustrated state, and the disk plate 2, sub-plate 3, facing 22, etc. are assembled from the first illustrated state to B. An explanation will be given assuming that the rotational displacement is performed in the direction of the arrow (counterclockwise). When the assembled body is rotationally displaced counterclockwise from the state shown in the first diagram, first the coil springs SP1 and SP
1 is elastically compressed, then coil spring SP2,
One of SP2 is elastically compressed, then the other is elastically compressed, and finally, coil springs SP3 and SP3 are elastically compressed, and as the torsion angle (rotational displacement) increases, each coil The elastic forces of the springs are added sequentially, and the resulting rotational force changes. Moreover, when it is turned back clockwise, it acts in the opposite direction and the elastic force is sequentially subtracted. In this operation, the control member 5 is rotationally displaced integrally with the assembly side and rotationally displaced relative to the flange member 13 until the coil springs SP3, SP3 are elastically compressed. 6 acts and hysteresis H
1. Coil spring SP3, SP3
When the second The thrust mechanism acts to generate hysteresis H2. The above operational relationships are summarized as shown in Table 1. In Table 1, ○ indicates an operating state, and × indicates a non-operating state. Next, the case where the assembled body is rotationally displaced clockwise from the state shown in the first figure will be omitted because it is easily understood from the above description. Incidentally, the torsional force characteristic is as shown in the third quadrant of FIG. 7.

[Table] (Effects) As explained in detail above, according to the present invention, the first and second friction plates of the first and second thrust mechanisms can slide against each other on either side thereof. Can provide the same frictional resistance. Furthermore, even during long-term use, the progress of wear between the pressing surface and the frictional surface of the control plate is at the same level, so there is no sudden change in the frictional resistance force. As a result, the hysteresis can be stabilized over a long period of time, which has a great effect in reducing the vibrations that occur in the transmission shaft system in response to engine rotation, as well as the neutral noise and shuffling noise caused by these vibrations. be.

[Brief explanation of drawings]

FIG. 1 is a front view showing an embodiment of a friction type engagement disc device according to the present invention, and FIG. 2 is a line taken along the line of FIG.
3 is a sectional view along the line in FIG. 1, FIG. 4 is an enlarged view of part A in FIG. 3, FIG. 5 is a partial cross-sectional view along the line in FIG. FIG. 7 is a front view showing the relationship between the flange member, the control plate, and the first pressing plate among the component parts of FIG. It is a diagram. Explanation of the main parts of the diagram, 1... hub member, 2...
Disc plate, 3...Sub plate, 6...
First thrust mechanism, 7...Second thrust mechanism, 1
3...Flange member, 22...Facing, 2
3... Bush, 51, 52... Control plate, 61, 62... First friction plate, 63... First thrust plate, 64... Belleville spring (first elastic member), 71, 72... Second friction plate, 73...Second thrust plate, 74...Another disc spring (second bullet repellent member), SP
1, SP2, SP3...Coil spring (elastic member).

Claims (1)

[Scope of Claims] 1. A hub member connected to a transmission shaft; a flange member disposed to rotate integrally with the hub member; and a flange member disposed in parallel with the flange member so as to be rotatable relative to the hub member. a facing fixed to the outer periphery of the disk plate; a sub-plate disposed parallel to the flange member and rotatable together with the disk plate with the flange member in between; the sub-plate; an elastic member commonly housed in each window formed in each of the disc plate and the flange member, a connecting member disposed between the hub member and the disc plate, and the hub member and the sub-plate, respectively; a first friction plate disposed between an inner surface of the control plate and both sides of the flange member, and one of the first friction plate and the control plate; a first thrust plate disposed between the first thrust plate and the inner surface of the control plate; and a first friction plate elastically mounted between the first thrust plate and the inner surface of the control plate. a first thrust mechanism having a first elastic member pinched therebetween; a second friction plate disposed between the outer surface of the control plate and the disk plate and the sub-plate; a second thrust plate disposed between one of the thrust plates and the disk plate and the sub-plate; and a second thrust plate disposed between the second thrust plate and the disk plate or the sub-plate. a second thrust mechanism having a second elastic member that is elastically loaded and presses the second friction plate between the disk plate, the sub-plate, and the control plate; a control plate and the first and second
A friction type engagement disc device characterized in that thrust plates are made of the same material.