JPS5926625A - Engaging disc device of friction type - Google Patents

Abstract

PURPOSE:To prevent a neutral or grave echo from occurring quite effecitvely by stabilizing further hysteresis in characteristic of torsion and torque, by forming a component constituting a face of a pressing device to be pressed in an identical quality with a compoent constituting a control component. CONSTITUTION:Friction plates 61 and 62 are pressed by placing among both sides of a coller member 13 and a control component 5 through a Belleville spring 64. The other frcition plates 71 and 72 are pressed by placing them among the control component 5, driving plate 2 and an auxiliary plate 3 by the force of a Belleville spring 74. A first pressing plate 63 and a second pressing plate 73 are to form the surfaces to be pressed of respective pressing device and the other pressing device, which are formed of a plate material identical in their quality and about identical in their surface roughness with control plate 51 and 52 and their friction coefficients become identical with each other at the time when they engage respectively with friction discs 61 and 62 and other friction discs 71 and 72. In use of the titled device for a long period of time, degree of progress of wears of the face to be pressed and that of the control plates 51 52 are about identical with each other.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a friction type engagement disc device which is connected to a friction type engagement disc device and is particularly used in vehicles and is equipped with a shock absorber capable of absorbing torsional vibrations occurring in a transmission shaft system. It is.

A friction-type engagement disc device for a vehicle is generally placed in a power train equipped with a gear-type transmission to appropriately transmit power from the engine to the wheels in order to drive the vehicle. It has the function of interrupting the power flow between the engine and the engine as necessary, and the function of damping the vibrations of the periodic rotational force of the engine.

The periodic rotational force vibrations of the engine, together with the play in the meshing gears of the gear transmission, cause 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 placed in a gear-type transmission, it generates so-called neutral noise, which is the rattling sound generated in the play area of the gears, and when the engine rotation speed is relatively high and the rotational force is relatively large, the gear-type transmission When it is placed in a high-speed stage (for example, in a direct connection state), it does not generate the above-mentioned neutral sound, but generates a caged sound caused by high-frequency vibrations.

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 resistance. However, this is of no use for the squealing noise that occurs when the engine rotational speed is relatively high and the rotational force is relatively large. To counter this noise, it is necessary to increase torsional rigidity and damping resistance.

In order to achieve both of these damping characteristics and absorb the above-mentioned vibrations, a shock absorber has 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 proposals have been made for friction type engagement disc devices equipped with
981 (Showa 56) Published on September 8, U.S. Patent No. 3
, No. 327゜820, patented June 27, 1967], the common structure of this device is that an elastic member is disposed over two members arranged so as to be able to rotate relative to each other. In addition, a frictional resistance member is provided that applies a predetermined resistance force to the relative rotation of both members, and control is performed to appropriately actuate the elastic member and the frictional resistance member in stages according to the angle of relative rotation of both members. It is equipped with members.

This device can absorb the above-mentioned vibrations to such an extent that there is no practical problem, and the applicant has confirmed this through various experiments.

While conducting various experiments, the applicant confirmed that the following problems occurred. That is, a control member for operating a frictional resistance member that imparts a relatively low frictional resistance force, which is arranged to absorb neutral sound, and a control member for operating a frictional resistance member that is arranged to absorb neutral sound, and two members that are arranged to be able to rotate relative to each other. Since the conditions of the surfaces that rub against the friction resistance member are different, the relatively low friction resistance force changes as a result, making it difficult to maintain a stable friction resistance force over a long period of time. Can not. That is, it is not possible to stabilize the so-called hysteresis that occurs in the torsion-to-rotation force characteristic of the friction type engagement disc device (which appears as a result of the action of frictional resistance force).

The present invention has been made in view of the above points, and includes a grain member connected to a transmission shaft, a flange member arranged to rotate integrally with the comparison member, and a flange member that is parallel to the flange member and relative to the comparison member. A drive plate member disposed to be relatively rotatable, a friction surface member fixed to the outer periphery of the drive plate member, and a drive plate member of the collar member that stands in parallel with the collar member and is rotatable integrally with the drive member. a sub-plate member disposed on the opposite side of the sub-plate member, the sub-plate member, the drive plate member, and the windows formed in each of the front and front flange members, and the flange member and the drive plate member; and a resilient member disposed between the auxiliary plate member and the auxiliary plate member to complete the resistance against relative rotation thereof; and a resilient member located between the flange member, the drive plate member, and the auxiliary plate member, respectively; A notch or a hole formed in the flange member straddles the flange member, and the driving plate is operated in one operating range of relative rotation between the flange member, the driving plate member, and the sub-plate member. The member is engaged with the drive plate member and the secondary plate member and can rotate relative to the collar member, and in other operating ranges of the relative rotation, the blade member is disengaged from the driving plate member and the secondary plate member and rotates relative to the collar member. a control member disposed to engage with the drive plate member and rotate relative to the auxiliary plate member; and a control member sandwiched between the control member and the flange member to exert a resistance force when these two members rotate relative to each other. a first resistance means that resists rising; a second resistance means that is sandwiched between the control member and the driving plate member and the sub-plate member and resists rising of the resistance force when these both rotate relative to each other; The resistance means includes friction discs disposed on both sides of the flange member, and a pressing means disposed to press the friction discs against the flange member, and the member constituting the pressing surface of the pressing means is controlled as described above Another friction disc is formed of the same material as the member constituting the member and is disposed as the second resistance means in frictional contact with the control member, and the other friction disc is arranged to press against the control member. A friction type engagement mechanism is provided in which the pressing surface of the separate pressing means is made of the same material as the member forming the control member, and the problems of the conventional friction type engagement can be solved. The present invention aims to provide a combined disc device.

In carrying out the present invention, it is preferable to carry out the following procedure.

+1. l The first resistance means is sandwiched between a first pressing plate coupled to the control member so as to be able to move relative to the control member in the axial direction, and a plate member and a collar member of one of the pressing plate and the control plate member. and a first resilient means elastically mounted between the control plate member and the first pressing plate, the first pressing plate and the first resilient means serving as pressing means. ing.

(2) The second resistance means includes a second pressing plate coupled to one of the driving plate and the sub-plate member so as to be relatively movable only in the axial direction, and the other of the driving plate and the sub-plate member and the pressing plate. and the control plate member, and a second elastic means elastically mounted between one of the driving plate and the sub-plate member and the second pressing plate. The second pressing plate and the second resilient means serve as separate pressing means.

(3) The control plate member is controlled by one elastic member that is elastically contracted within a predetermined range of the entire range of relative rotation between the collar member and the drive plate and sub-plate members to complete the resistance. It engages with this one resilient member in order to operate.

(4) The control member passes through two control plates arranged in parallel on both sides of the collar member through a notch formed inward in the radial direction of a resilient member housing window formed in the collar member. By forming the connecting portions so that they are connected to each other, the hysteresis in the torsion/rotation force characteristic can be further stabilized, and neutral noise or locking noise can be extremely effectively prevented.

Hereinafter, the present invention will be described with reference to the drawings.

The shell member 1 is slidably fitted to a transmission shaft (not shown) (usually serves as an input shaft of a gear transmission) by a sprunn 11 formed in its inner cylinder part, and its outer cylinder part (9) 12 has a sprunn 11 formed in the radial direction. A flange member 13 is integrally disposed so as to extend from the bottom. A drive member 2 and a sub-plate member 3 are arranged on both side surfaces of the collar member 13 so as to stand in parallel with the collar member 13 and to be rotatable relative to the collar member 13, and both members are formed on the outside of the collar member 13. It is fixed by a connecting pin 14a extending horizontally through the notch 14.

A bushing 21 rotatably and slidably supported on the outer cylindrical portion 12 of the shell member 1 is disposed on the inner diameter portion of the drive plate member 2 .
It is fixed to rotate together with the Further, an appropriate number of buffer spring plates 21 are fixed to the outer circumference by studs 21a, and friction surface members 22, 22 are fixed to both sides of the spring plates 21 by studs 22a.

Bushing 21 is a non-lubricant bearing material, bearing material (bronze alloy,
It is made of copper/lead alloy, aluminum alloy, overlay alloy) or synthetic resin material, and can rotate and slide relatively stably with respect to the outer cylinder.

Flange member 13. Drive plate member 2. Spring accommodation windows 13a, 2a, 3a, 13(10)b, 2b, 3b, 13c, 2c, and 3c are formed in each of the sub-plate members 3, respectively.

A coil spring SPI, which is one of the resilient members, is disposed in each of the housing windows 13a, 2a, and 3a, with its end seated on a washer 41 that can be commonly engaged at will. Similarly, a coil spring SP2, which is one of the resilient members, is arranged in the housing windows 13b, 2b, and 3b, with its end seated on a washer 42 that can be commonly engaged at will. Furthermore, the accommodation window 13
A coil spring SP3, which is one of the elastic members, is disposed on the springs c, 2c, and 3c. In the normal state as shown in the figure (Fig. 1), both ends of the coil spring SP3 It is seated on the circumferential surface of each window 2C13C of the plate member 3, and is spaced apart from the window 13C of the collar member 13 by a predetermined rotation angle. In normal conditions, the end of the coil spring SP3 is spaced apart from the window 13b of the collar member 13 by a predetermined rotation angle as shown in the drawing (FIG. 1).

Between the flange member 13, the driving plate member 2, and the sub-plate member 3, control plates 51, 5 (11) 2 are arranged in parallel with the flange member 13, respectively. Both of these control plates 51 and 52 are integrally connected by a connecting pin 53 that penetrates through notches 15 and 15 formed in the radial direction of the window of the collar member 13, 3b, and 13C, respectively, and serves as a horizontal connecting portion. As a result, a control member 5 having a shape in which the collar member 13 is straddled at the notches 15, 15 is formed.

Note that the portion through which the connecting pin 53 penetrates may be a hole (long hole in the circumferential direction) formed in another portion instead of the notch.

The control plates 51 and 52 are displaced in the axial direction by a predetermined amount (particularly to the right in the drawing with reference to FIG. 4) with respect to the friction surfaces 51a and 52a, for example, by half the plate thickness or the plate thickness. an ear portion 51b that is integrally formed and to which the connecting pin 53 is riveted;
52b, and an arm portion 5 that extends radially outward from the friction contact surfaces 51a and 52a and is engaged with an end portion of the coil spring SP3.
1c.

52c.

Friction surfaces 51a and 52a of control plates 51 and 52 and collar member 1
Friction discs 61 and 62 (12) are arranged between both sides of 3. Between the friction plate 61 and the control plate 51,
A first pressing plate 63 is connected to the connecting pin 53 and is movable only in the axial direction.
1a is the first bullet repelling means loaded between the ball and the bullet. Friction discs 61 , 62 are pressed between both sides of the collar member 13 and the control member 5 by, for example, disc springs 64 . The first resistance means 6 is composed of the friction plates 61 and 62, the first pressing plate 63, the first repelling means 64, and the like described above. Further, the first pressing plate 63 and the first repelling means 64 serve as pressing means.

The relationship between the control plates 51, 52, the first pressing plate 63, and the collar member 13 (in a normal state) is illustrated in FIG. 6.

Separate friction discs 71, 72 are arranged between the control plate 51, 52 and the drive plate part 2 and the auxiliary plate part 3, respectively. A protrusion 73 extending in the axial direction is provided between the friction disc 72 and the sub-plate member 3.
A is coupled to the engagement notch 31 of the sub-plate member 3 so as to be movable only in the axial direction, and a second pressing plate 73 is disposed. The control member 5, the drive plate, and the sub-plate member 2 are elastically connected between the control member 5, the drive plate, and the sub-plate member 2 by a resilient means, such as a disc spring 74 (13), which is elastically mounted between the pressing plate 73 and the sub-plate member 3.
Another friction disc 71, 72 is clamped between and 3. The second resistance means 7 is composed of the friction plates 71 and 72, the second suppression plate 73, the second repelling means 74, and the like described above. Further, the second pressing plate 73 and the second repelling means 74 serve as separate pressing means.

Thus, the first pressing plate 63. The second pressing plate 73 forms a pressing surface of a pressing means and another pressing means, respectively, and is formed from a plate material made of the same material as the control plates 51 and 52 and having the same surface roughness. , the friction coefficients when working together with the friction discs 61, 62 and another friction disc 71, 72 are the same, and the pressing means.

The members forming the respective pressing surfaces of the other pressing means are made of the same material as the member forming the control member 5.

Further, it is better if the friction disc 71 is fixed to the bushing 21 by a known fixing means so that the friction disc 71 and the control plate 51 only relatively slide by friction.

This results in a friction disc 61.6'2 and another friction disc 71.7.
2, the frictional resistance force is stabilized (14). Furthermore, since the wear of the pressing surface and the friction surfaces of the control plates 51 and 52 progresses at the same level during long-term use, there is no sudden change in the frictional resistance force, which is stable over a long period of time. .

Further, the repulsive forces of the first repelling means 64 and the second repelling means 74 of the first resisting means 6 and the second resisting means 7 are set so as not to repel the control plates 51 and 52. In addition, the control plates 51 and 52 are provided with a resilient member housing window (13b) of the collar member 13.
, 13b, 13d, 13d) are connected to each other by connecting pins 53 provided through the notches 15 formed inward in the radial direction, so that the thickness of the control plates 51 and 52 is constant. In this case, the rigidity of the control member 5 can be improved as much as possible. Thus, the thickness of the control plates 51 and 52 can be set appropriately, and the repulsive forces of the first and second repelling means 64 and 74 do not interfere with each other. That is, the respective resistance forces of the first resistance means 6 and the second resistance means 7 do not interfere with each other. Therefore, each resistance force is maintained stably.

(15) The first pressing plate 631, the disc spring 64, the second pressing plate 73, and the disc spring 74 are not limited to the positions shown in the fourth diagram, but may be arranged on opposite sides or in the same direction. It goes without saying that you can get it. The disc springs 64, 74 may be other spring members such as wave springs or conical coil springs.

In addition, what is indicated by heat resistance 6 in FIG. 5 is a weight for balance expropriation.

Next, the operation of the above-mentioned device will be explained.

Here, mainly the control member 5 and the first and second resistance means 6
and 7 will be explained in relation to the torsional rotational force characteristics. For convenience of explanation, the grain member 1 and the collar member 13 are fixed, for example, in the first illustrated state, and the drive plate member 2. Sub-plate member 3. A description will be given assuming that the assembled friction surface members 22, 22, etc. are rotationally displaced from the first illustrated state in the direction of arrow B (counterclockwise).

When the assembled body is rotationally displaced counterclockwise from the first illustrated state, the coil springs SPI and SPI are first elastically compressed, then one of the coil springs 5P2 (16) and SP2, and then the other. Elasticized,
Finally, coil spring SP3. As SP3 is elastically contracted and the torsion angle (rotational displacement) increases as shown in the first quadrant of FIG. 7, the elastic forces of the respective coil springs are sequentially added.
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 controls the coil spring SP3. SP3
Until it is elastically contracted, it is rotationally displaced integrally with the assembly side and rotationally displaced relative to the flange member 13, so the first resistance means 6 acts and causes hysteresis H1. Coil spring SP3. At the same time that SP3 begins to elastically contract, the connecting pin 53 abuts and engages with the circumferential surface of the notch 15, and the control member 5 is integrally connected with the collar member 13, and rotational displacement is stopped. 2 resistance means act to create hysteresis H2.

The above operational relationships are summarized as shown in Table 1. In Table 1, O indicates an operating state and x indicates a non-example state (17).

Table 1 (18) Next, the case in which the assembled body is rotationally displaced clockwise from the state shown in the first diagram will be omitted because it is easily understood from the above description.

Incidentally, the torsional one-rotation force characteristic is as shown in the third quadrant of FIG. 7.

As explained above in detail, according to the present invention, the control section +J is disposed between the flange member that rotates integrally with the shell member, the driving plate member, and the sub-plate member, and the control unit +J is provided between the control member and the flange member. A first resistance means is sandwiched between the control member and the drive plate member and the sub-plate member.
The control member is composed of friction discs disposed on both sides of the flange member as resistance means, and a pressing means disposed to press the friction discs against the flange member, and the member constituting the pressing surface of the pressing means constitutes the control member. Another friction disc is formed of the same material as the member to which the control member is applied, and is disposed as a second resistance means in frictional contact with the control member, and another friction disc is disposed to press the other friction disc against the control member. By forming the member constituting the pressing surface of this pressing means of the same material as the part 1 constituting the control member, it is possible to Even if it rubs and slides (the first resistance means)
The same resistance force can be imparted, and similarly, the same resistance force can be imparted (the second resistance means) no matter which side of the two sides of another friction disc it rubs against and slides on. I can do it. In addition, even during long-term use, the progress of wear between the pressing surface and the friction surface of the control plate is the same, so there is no sudden change in the frictional resistance, and the resistance of the first and second resistance means is reduced. can be stabilized over a long period of time.

From the above, the hysteresis in the torsional rotational force characteristic is stabilized, and the change in hysteresis over time is very small and is maintained stably over a long period of time, which is a great practical effect.

In addition, by increasing the rigidity of the control member and preventing the two resistance means from interfering with each other, the hysteresis can be maintained more stably over a long period of time in conjunction with the above-mentioned functions and effects. This has the effect of making it possible to

[Brief explanation of drawings]

Fig. 1 is a front view showing an embodiment of the friction type engagement disc device (20) according to the present invention, Fig. 2 is a sectional view taken along the line 4 is an enlarged view of part A in FIG. 3, FIG. 5 is a partial cross-sectional view along line V-V in FIG. 1,
FIG. 6 is a front view showing the relationship between the collar member, the control member, and the first pressing plate among the components shown in FIG. 1, and FIG. 7 is a torsional rotation of the friction type engagement disc device according to the present invention. FIG. 3 is a characteristic diagram showing force characteristics. Explanation of the attached number In the diagram, ■ is the shell member, I3 is the collar member, 2 is the drive plate member, 3 is the sub-plate member, SPI, SF3. SF3 is an elastic member, 15 is a notch formed in the elastic member housing window of the collar member, 5 is a control member, 6 is a first resistance means, 61.62 is a friction plate, (21) 63.64 is a presser 63 is a member constituting a pressing surface; 7 is a second resistance means; 71.72 is another friction disk; 73.74 is another pressing means; 73 is a member constituting a pressing surface. Patent applicant Aisin Seiki Co., Ltd. Representative Reio Nakai (22)

Claims (1)

[Claims] A grain member connected to a transmission shaft, a collar member arranged to rotate integrally with the grain member, a drive plate member arranged in parallel with the collar member and rotatable relative to the grain member, and the drive plate. a friction surface member fixed to the outer circumference of the member; a sub-plate member disposed on the side of the collar member opposite to the drive plate member so as to be parallel to the collar member and rotatable together with the drive plate member; Commonly accommodated in each window formed in each of the secondary plate member, the driving plate member, and the flange member, and arranged between the flange member, the driving plate member, and the auxiliary plate member. an elastic member that completes the resistance against the relative rotation of the flange, which is located between the flange member and the drive plate and the auxiliary plate member, and which is formed in the flange member with a notch or hole formed in the flange member; The members are straddled and engaged with the drive plate member and the sub-plate member in one operating range of relative rotation between the flange member, the drive plate member, and the sub-plate member, and rotated relative to the flange member. At the same time, in other operating ranges of the relative rotation, the drive plate member and the sub-plate member are disengaged and engaged with the flange member, and the movement is made relative to the drive plate member and the sub-plate member. A control member arranged to be rotatable, a first resistance means sandwiched between the control member and the collar member and applying a resistance force when these two members rotate relative to each other, and the control member and the drive plate. The second resistance means is sandwiched between the member and the sub-plate member and applies a resistance force when the two rotate relative to each other, and the first resistance means are respectively disposed on both sides of the collar member. a friction disc and a pressing means disposed to press the friction disc against the collar member, the member forming the pressing surface of the pressing means being made of the same material as the member forming the control member. The second resistance means includes another friction disc disposed in frictional contact with the control member, and another pressing means disposed to press the other friction disc against the control member. A friction type locking disk device, characterized in that a member constituting a pressing surface of another pressing means is made of the same material as a member constituting the control member.