KR100191866B1 - Damper disk assembly - Google Patents

Abstract

In the clutch disc assembly 1, a small coil spring 6 is arranged to be compressed in a relative rotation between the flange 2b of the hub 2 and the auxiliary pin 5.

The float rubber 31 is disposed in the small coil spring 6 described above and has both ends spaced apart from the flange 2b and the auxiliary plate 5.

The large coil spring 7 is arranged to be compressible by the rotation of the plates 3, 4 with respect to the auxiliary plate 5, and has a stronger rigidity than that of the small coil spring 6 described above.

Description

Damper disc assembly

The present invention relates to a damper disk assembly, and more particularly to a damper disk assembly having a cushioning characteristic.

For example, a clutch disc assembly for use in clutches of a vehicle may be a circular or annular input plate, an output hub with integrally radial flanges, and between the flange and the input plate to allow their relative rotation within a limited range. It includes elastic members disposed.

In addition, the hub disc type clutch disc assembly has been proposed in which the traditional flange is separated from the hub, and the separated flange and the hub are joined by a soft elastic member.

The clutch disc assembly of the hub separation type is also equipped with a friction generating mechanism for generating hysteresis torque when relative rotation occurs between the input plate and the hub.

The friction generating mechanism generates low hysteresis torque in the first stage and high hysteresis torque in the second stage.

In the damper disc assembly mentioned above, the maximum relative torsion angle between the input plate and the hub is large and the assembly exhibits low and high rigidity torsional characteristics.

When the torsion angle is small, the input plate rotates with the intermediate disc member, and these members rotate relative to the output hub.

In this action, the soft elastic member, in other words, low rigidity, the member is compressed, and the friction generating mechanism generates a low hysteresis torque.

When the torsion angle is large, the intermediate disc member rotates with the output hub and these members rotate relative to the input plate.

In this action, the strong elastic member, in other words the high rigid member, is compressed, and therefore the friction generating mechanism generates a high hysteresis torque.

When the conventional damper disc assembly is subjected to torsional vibration while the engine is idling, relative rotation occurs periodically within the range of the first stage.

Relative rotation occurs periodically within the range of the first to second steps described above.

When the characteristic changes temporarily from the first step to the second step, the protrusion of the hub collides with the protrusion of the separated flange, and thus a jumping phenomenon occurs.

This jumping phenomenon causes a friction sound of the gear in the transmission, and the equivalent sound is felt by the driver and the passenger in a vehicle equipped with a damper disc.

The object of the present invention is, for example, to have two characteristics in the second stage, and to absorb shocks caused by the collision of components in the damper disc due to the deflection of the torsional characteristic between the first and second stages. It is to provide a damper disk assembly.

In view of the invention, the damper disc assembly comprises a first rotating member, a second rotating member relatively rotatable relative to the first rotating member, and a coil compressed at a relative rotation between the first and second rotating members. It includes a spring.

The elastic body is disposed in the coil spring with both end portions spaced apart from the first and second rotary members.

The third rotating member rotatable relative to the second rotating member is disposed adjacent to the first and second rotating members.

The elastic member is disposed between the second rotary member and the third rotary member and is compressed by relative rotation therebetween.

The elastic member has a stronger rigidity than the coryl spring. The elastic body is formed with a cylindrical columnar portion.

In addition, the elastic body forms a sheet portion fixed to both sides of the body and an inertia deformable body.

Preferably the body is made of rubber. Furthermore, the auxiliary plate is disposed radially outward of the first rotating member, and the first and second rotating members are correspondingly coupled to form gears extending in the radial direction.

Preferably, the first and second rotating members are provided with grooves into which the coil spring and the elastic sea are correspondingly inserted.

The damper disk assembly includes sheet members disposed at both ends of the coil spring, and both ends of the elastic body are spaced apart from the sheet members.

The damper disc assembly includes a fourth rotating member, wherein the third and fourth rotating members are disposed on both sides of the first and second rotating members to be fixed to either one and are limited in rotation relative to the first and second rotating members. It is formed for displacement.

The damper disc assembly includes a hysteresis friction generating device disposed between the third and fourth rotating members and is engageable with the first and second rotating members, wherein the friction generating device is disposed between the first and second rotating members. Corresponding to the relative rotational displacement in the frictional cause, the friction generating mechanism causes friction in response to the relative rotational displacement between the second and third rotating member and the frictional generating device is the first and second rotation Friction is caused in response to relative rotational displacements between the members.

When the third rotating member rotates, it transmits torque to the first rotating member via the elastic member, the second rotating member and the coil spring.

When the torsional vibration is delivered to the third rotating member, relative rotation occurs periodically between the second rotating member and the first rotating member.

Regarding the torsional characteristics, the third rotating member rotates integrally with the second rotating member when the torsion angle is small, and thus the first rotating member rotates relatively with the second and third rotating members.

In this action, the coil spring is compressed until it exhibits a soft characteristic at the rotational displacement of the first stage.

When the torsion angle increases, the second and first rotating members rotate integrally, and the third rotating member rotates relative to the first and second rotating members.

In this action, the elastic member is compressed until it exhibits hard properties in the second step.

In the range between the first and second steps, the elastic body is compressed between the second and first rotating members.

The shock caused by the transition between the first and second steps is thereby absorbed.

The above and other objects, features, aspects and advantages of the present invention will become more apparent from the following detailed description when read in conjunction with the accompanying drawings.

1 is a longitudinal cross-sectional schematic view of a clutch disc assembly having a hub and other components in accordance with one embodiment of the present invention.

2 is a partial cutaway cross-sectional view of the clutch disc assembly as seen in the direction of arrow II in FIG.

3 is a front view of the hub shown separately from the clutch disk assembly depicted in FIGS. 1 and 2.

4 is a cross-sectional view of the hub cut along the line IV-IV in FIG.

FIG. 5 is a cross-sectional view of the hub, first and second friction washers, and first and second conical springs in an enlarged manner in the clutch disk assembly shown in FIG.

6 is a plan view of the first friction washer removed from the clutch disc assembly.

FIG. 7 is a cross sectional view of the first friction washer taken along line VIII-VIII in FIG.

8 is a plan view of a second friction washer from the clutch disc assembly.

FIG. 9 is a cross sectional view of the second friction washer taken along line VIII-VIII in FIG.

FIG. 10 is a cross sectional view of the second friction asher taken along line VIII-VIII in FIG.

11 is a top view of the first conical spring removed from the clutch disc assembly.

12 is a top view of a second conical coil spring removed from the clutch disc assembly.

FIG. 13 is an enlarged end of a portion of the hub and associated components of the clutch disc assembly depicted in FIG.

14 is a graph showing the torsional vibration characteristics of the clutch disc assembly in the first step.

The clutch disc assembly 1 according to the embodiment of the present invention shown in FIG. 1 selectively transmits torque from an engine (not shown) disposed on the left side in FIG. 1 to a transmission (not shown) disposed on the right side. It is provided to cut off.

In FIG. 1, 0-0 represents the axis of rotation of the clutch disc assembly 1.

In essence, the clutch disc assembly 1 is provided with a hub 2 provided as an output member, ie a first rotating member, a clutch plate 3 provided with an input member ie a second rotating member, and a fourth rotating member. Retaining plate 4, intermediate member ie subplate 5 provided as second rotating member, small coil springs disposed between subplate 5 and hub 2 to allow limited relative rotation therebetween (6), large coil springs (7) disposed between plates (3) (4) to allow limited relative rotation between them, and between hub (2) and plates (3) (4) A frictional resistance issuing mechanism (8) provided as a hysteresis friction generating device for generating a predetermined hysteresis torque when relative rotation occurs.

The hub 2 is disposed in the center of the clutch disc assembly 1, and can be combined with a shaft (not shown) of the transmission.

The hub 2 is formed with a cylindrical boss 2a extending in the axial direction, and a flange 2b integrally extending radially outward from the boss 2a.

The plurality of protrusions 2c are formed around the outer side of the flange 2b and are spaced apart from each other at uniform intervals.

As shown in FIG. 3 and FIG. 4, the opposite end of the small coil spring 6 demonstrated below to the two sides of the said flange 2b (in other words, opposite in the circumferential direction) A groove 2d is provided for receiving the end.

The boss 2a is provided with a spline hole 2e for engaging the shaft (not shown) of the transmission.

Said auxiliary plate 5 is arranged radially outward of the flange 2b of the hub 2.

Said auxiliary plate 5 is annular and has four protruding protrusions 5a extending radially outward as shown in FIG.

Each protruding protrusion 5a is provided with a window 5b extending in the circumferential direction of the disk.

Outer grooves 5c are formed between the protruding protrusions 5a. The inner periphery of the auxiliary plate 5 is provided with inner protrusions 5d located between the protrusions 2c of the hub 2.

Since the constant circumferential cap S (see FIG. 13) is held between the protrusions 2c and the inner protrusion 5d, the hub 2 and the auxiliary plate 5 are subjected to relative rotation within a constant displacement angle. .

The inner peripheral portion of the auxiliary plate 5 is provided with two inner grooves 5e corresponding to the grooves 2d of the hub 2, respectively, as shown in FIG.

These grooves 2d and inner grooves 5e receive a small coil spring 6.

The sheet members 30 are arranged at each opposite end of the small coil spring 6 and contact the circumferential opposite ends of the inner groove 5e and the side edges of the groove 2d.

The rubber flow 31 is arrange | positioned inside 6 of each coil spring as shown in FIG.

The rubber float 31 is made of a rubber body 3la and a hard material such as synthetic resin and has a site portion 3lb fixed to both ends of the sea.

The sheet portion 3lb described above has a diameter larger than that of the body 3la. The sheet portions 3lb and the corresponding sheet members 30, respectively, are spaced apart by a constant distance G as shown in FIG.

The distance G and the distances S are about two distances G which are somewhat smaller than one distance S.

In other words, when a relative displacement occurs between the hub 2 and the auxiliary plate 5, the distance G will be removed one before the spacing S is removed, as will be explained in more detail below.

In the neutral state shown in FIG. 2, each of the protrusions 2c moves in the direction R2 with respect to the inner protrusion 5d.

The clutch plate 3 and the retaining plate 4 are arranged on both sides of the auxiliary plate 5.

The clutch plate 3 and the reducing plate 4, which are mated with each other and have a substantially annular disk shape, are rotatably arranged around the boss 2a of the hub 2.

The contact of the clutch plate 3 and the retaining plate 4 pins 11 is fixed together in their radially outer part.

The contact pins 11 extend through the outer groove 5c formed in the auxiliary plate 5.

Each of the contact pins 11 is circumferentially spaced from the edge of the outer groove 5c at a constant distance so that the plates 3 and 4 are rotatable independently of the subplate 5.

The friction coupling 10 is arranged in the radially outer portion of the clutch disc 3. The friction coupling 10 includes an annular buffer plate 12 and a friction facing 13.

It has an annular part 12a fixed to the clutch plate 3 by the above-mentioned buffer plate 12 and the contact pin 11.

A plurality of shock absorbing portions 12b are provided in the radially wound portion of the shock absorbing plate 12.

The friction facings 13 are fixed to the opposite surface of the buffer 12b. The flywheel (not shown) of the engine is arranged on the left side of the friction facing 13.

When the friction facings 13 are pressed against the flywheel by the front plate (not shown), the torque of the engine is supplied to the clutch disc assembly 1.

The clutch plate 3 and the retaining plate 4 are provided with windows 3a and 4a located at positions corresponding to the windows 5b of the auxiliary plate 5.

Said second coil springs 7 are arranged in these windows 3a and 4a. The radially inner and outer edges of the windows 3a and 4a are provided with supports 3b and 4b which are bent axially outwardly and partially cut.

The large springs 7 described above are typically four in total, and comprise two first spring assemblies 7a and two second spring assemblies 7b.

The first spring assemblies 7a are arranged in the openings 5b of the auxiliary plate 5 opposite to each other.

Each of the first spring assemblies 7a forms a large diameter coil spring, and a small diameter coil spring is disposed inside the large diameter coil spring.

Each end of the first spring assembly 7a facing in the circumferential direction has an edge of the opening 5b of the auxiliary plate 5 facing in the circumferential direction, and a window 3a of the clutch plate 3 facing in the circumferential direction. ) And the edge of the window 4a of the retaining plate 4 facing in the circumferential direction.

The second spring assemblies 7a are coil springs. The coil spring ends of the circumferentially facing second spring assembly 7b are in contact with the circumferentially facing windows 5a, 3a, 4a.

The axial movement of the large coil springs 7 mentioned above is limited by the support 4b of the retaining plate 4 and the support 3b of the clutch plate 3.

In the inner periphery of the clutch and retaining plates (3) (4) described above, four holes (3c) which are evenly spaced in the circumferential direction while being engaged with the part of the frictional resistance generating mechanism (8) as mentioned below. 4c is provided.

The friction resistance generating mechanism 8 described above is now described.

The friction resistance generating mechanisms 8 are annularly formed members, which extend around the bosses 2a and are arranged in radially inner portions of the clutch and retaining plates 3 and 4.

The members forming the frictional resistance generating mechanism 8 include the first friction washer 14, the second friction washer 15, the first conical spring 16, the second conical spring 17 and the third friction washer. (18).

The first friction washer 14 is an annular plate made of synthetic resin.

As shown in Figs. 5 to 7, the first friction washer 14 has an inner periphery close to the boss 2a, and the projections 2c and the flange 2b of the hub 2 are guided to the transmission side. ) Has one side in contact with the surface.

The first friction washer 14 has an annular plate portion 14a and an annular projection portion 14b that projects into the annular plate portion and protrudes to the transmission side.

The annular groove 14c is provided at a position close to the protruding annular projection 14a.

The outer periphery of the annular plate portion 14a is provided with four projections 14d projecting outward in the radial direction.

The first conical spring 16 is disposed axially between the first friction washer 14 and the retaining plate 4.

The first conical spring 16 has an outer periphery supported by the retaining plate 4 and has an annular groove 14c formed in the annular protrusion 14b protruding from the first friction washer 14. Has an inner periphery in contact with it.

In the combined state, the first conical spring 16 is compressed by the force of the first friction washer 14 which resists the flange 2b and the projections 2c of the hub 2.

The outer periphery of the first conical spring 16 is provided with a plurality of grooves 16a as shown in FIG.

The purpose of these grooves 16a is to reduce the change in the elastic force of the first conical spring 16 which may be caused by the change of the position of the first conical spring 16 due to the wear of the first friction washer 14. .

The second friction washer 15 is an annular plate member as shown in FIGS. 8 to 10 and is located concentrically around the first friction washer 14.

The second friction washer 15 is made of the same material as the first friction washer 14 and has the same coefficient of friction.

The second friction washer 15 is composed of an annular plate portion 15a and an annular protrusion 15b protruding from the inner peripheral portion of the annular plate portion 15a toward the transmission side.

The annular plate end surface facing toward the engine is in contact with the inner periphery of the end surface of the auxiliary plate 5.

The annular projection 15b facing the transmission side is provided with four cutout grooves 15e at equal intervals in the circumferential direction on its end surface.

The cutout groove 15e is coupled with the protrusion 14b of the first friction washer 14 to allow relative movement in the axial direction but to prevent relative rotation in the circumferential direction.

A constant gap is maintained in the axial direction between the protrusion 14d and the groove 15e,

The annular projection 15b has four projections projecting through the groove 15e toward the transmission side.

These projections are composed of two snap projections 15c and two rod-shaped projections 15d.

Projections of the same type are arranged in opposite positions. Each snap protrusion 15c is divided into two parts by an axial slit, and its free end is provided with a hooked portion for snap engagement.

The snap protrusion 15c is inserted into the hole 4c formed in the retaining plate 4.

The snap portion formed in the snap protrusion 15c restricts or prevents axial separation of the second friction washer 15 from the retaining plate 4.

The rod-shaped protrusion 15d is inserted into the other hole 4c in the retaining plate 4.

The second conical spring 17 is arranged axially between the second friction washer 15 and the retaining plate 4.

The inner periphery of this second conical spring 17 is provided with a plurality of grooves 17a as shown in FIG.

The purpose of these grooves 17a is to reduce the change in the pressing force of the second coil spring 17 where the position of the second conical spring 17 can be changed due to the wear of the second friction washer 15.

When the conical spring 17 is compressed in the assembled state, its outer periphery contacts the retaining plate 4, and its inner periphery is in other words a projection 17b facing the transmission side. The lateral surface of the annular protrusion 15b of the friction washer 15 is in contact with it.

In this way, the second conical spring 17 presses the second friction washer 15 toward the side surface of the auxiliary plate 5 extending toward the transmission side.

In this state, the second conical spring 17 has a larger pressing force than the elastic force of the first conical spring 16.

The grooves 17a of the second conical spring 17 correspond to the snap protrusion 15a, the rod-like protrusion 15d, and the groove 15e of the second friction washer 15, so that these portions do not interfere.

The third friction washer 18 is arranged axially between the inner periphery of the clutch plate 3 on the one hand and between the flange 2b of the hub 2 and the inner periphery of the auxiliary plate 5 on the other hand. Is placed.

The third friction washer 18 is made of the same material as the first and second friction washers 14, 15, and generally has the same coefficient of friction.

The side surface of this third friction washer 18 extending toward the transmission side is in contact with the side surface of the flange 2b and the inner peripheral side surface of the auxiliary plate 5, and the side surface extending toward the engine with respect to It is in contact with the clutch plate 3.

The outer periphery of this third friction washer 18 extending axially towards the engine is provided with a snap projection 18a, which is engaged into a hole 3c formed in the clutch plate 3.

Each snap protrusion 18a has the same shape as the snap protrusion 15c of the second friction washer 15 mentioned previously.

An inner periphery of the upper and third friction washers 18 is provided with an annular projection 18b extending axially toward the engine.

The annular protrusion outer peripheral portion is in contact with the inner peripheral portion of the clutch plate 3. The operation of the clutch disc assembly 1 described above will be described below.

When the friction facing 13 hits the flywheel (not shown) of the engine and is compressed, the torque of the engine is transmitted from the flywheel to the clutch plate 3, the retaining plate 4.

This torque is transmitted to the hub 2 via the large coil spring 7, the auxiliary pipe 5 and the small coil spring 6, and even more to the shaft of the transmission.

When a torsional vibration is transmitted from the flywheel of the engine to the clutch disc assembly 1, relative rotation occurs periodically between the clutch and retaining plate (3) (4) and the subplate (5) and the hub (2).

As a result, the frictional resistance generating mechanism 8 generates hysteretic torque as the small torque sprinkle and the large coil springs 6 and 7 are compressed.

Torsional characteristics will be described.

Within a small torsion angle range, the clutch plate 3 and the retaining plate 4 rotate with the subplate 5 and these clutch plate 3 and retaining plate 4 rotate relative to the hub 2. Done.

In this action, the small coil spring 6 is circumferentially compressed, and the first and third friction washers 14 and 18 slide on the flange 2b and the projection 2c of the hub 2. .

When the torsion angle increases, both opposite ends of each of the float rubbers 31 make contact with the sheet members 6a, after which the float rubber 31 is compressed.

Then, the protrusion 2c and the inner protrusion 5d are brought into contact with each other, after which the auxiliary plate 5 and the hub 2 cause relative rotation with respect to the clutch plate 3 and the retaining plate 4. Rotate integrally

In this action, the large coil spring 7 is compressed and the first friction washer 14 slides on the flange 2b of the hub 2.

At the same time, the second friction washer 15 slides radially on the inner surface of the auxiliary plate 5, and the third friction washer 18 slides on the flange 2b of the hub 2 extending towards the flywheel. And slide on the surface in the radially inner portion of the auxiliary plate 5 extending towards the flywheel.

High hysteresis torque occurs when the pressing force of the second conical spring 17 is greater than that of the first conical spring 16.

If a slight torsional vibration is transmitted to the clutch disc assembly 1 while the engine is idling, the torsion angle changes in a first stage region spanning from the neutral position to the opposite side.

The first step area is defined as the rotation angle displacement between the hub 2 and the auxiliary plate 5.

When the projection 2c makes contact with the inner projection 5d, the displacement angle enters the region defined by the second step.

The float rubber 31 having the body 31a and the sheet portion 3lb is of the same size as the distance G that is removed before one of the gaps S is removed.

In other words, the sheet portion 3lb is in contact with the sheet member 30 before contact is made between the protrusion 2c and the inner protrusion 5d.

Therefore, the contact between the float rubber 31 and the sheet portion 3lb of the sheet member 30 reduces the collision force between the projection 2c and the inner projection 5d.

Simultaneously with this contact, the impact due to collision between the dolly portion 2c and the inner protrusion 5d is absorbed by the compression of the float rubber 31.

As a result, as shown in the torsion characteristic graph shown in FIG. 14, the torsional stiffness smoothly changes parabola.

According to the damper disc assembly of the present invention, when torsional vibration is transmitted, relative rotation occurs periodically between the rotating members.

According to the torsion characteristic, the clutch plate and the auxiliary plate rotate integrally, and thus rotate relative to the hub when the torsion angle is small.

In this action, the coil spring is compact and exhibits low stiffness, ie properties in the first stage.

When the torsion angle increases, the auxiliary plate and the hub rotate integrally and therefore rotate relative to the clutch plate.

In this action, the elastic member is compressed to exhibit high rigidity, that is to say a characteristic in the second stage.

At the boundary of the first and second stages, the elastic body is compressed between the subplate and the hubs.

This absorbs the impact caused by the transfer between the first and second stages.

Various implementations of the invention will vary without departing from the spirit or scope of the invention.

The description of the preceding embodiments of the present invention is provided solely for the purpose of illustration and is not intended to limit the invention as defined by the appended claims and their equivalents.

Claims (9)

A first rotating member; A second rotating member rotating relative to the first rotating member; A coil spring compressed by relative rotation between the first and second rotational members; An elastic body having both end portions spaced apart from the first rotating member and the second rotating member and disposed in the coil spring; A third rotating member rotating relative to the second rotating member; And an elastic member having greater rigidity than the coil spring and being compressed at a relative rotation between the second and third rotary members. The damper disk assembly of claim 1, wherein the elastic body has a cylindrical shape. The damper disk assembly of claim 2, wherein the elastic body includes an elastically deformable body and a sheet portion to which both ends of the body are fixed. 4. The damper disc assembly of claim 3 wherein the body is made of rubber. The damper disk assembly of claim 1, wherein the second rotating member is disposed radially outward of the first rotating member, and the first rotating member and the second rotating member are correspondingly engaged with these radially extending gears. The damper disk assembly of claim 1, wherein the second rotating member is disposed radially outward of the first rotating member, and the first rotating member and the second rotating member are correspondingly engaged with these radially extending gears. The damper disc assembly of claim 1 wherein the disc assembly further comprises sheet members arranged at both ends of the coil spring and at both ends of the elastic body spaced apart from the sheet member. The disk assembly of claim 1, wherein the disk assembly includes a pair of fourth rotating members disposed on one side of the first and second rotating members while the third rotating member is disposed on both sides of the first and second rotating members. And the third and fourth rotating members are fixed to each other for limited rotational displacement with respect to the first and second rotating members. The hysteresis friction assembly according to claim 8, wherein the disc assembly further comprises a hysteresis friction assembly coupled with the first and second rotation members and disposed between the third and fourth rotation members. Causing friction in response to the relative rotational displacement between the first rotational member and the third rotational member, causing friction in response to the relative rotational displacement between the second and the third rotational members; Damper disc assembly causing friction in response to relative rotational displacement between members.