CN114585822A

CN114585822A - Vibration reduction structure with two-stage damping, vehicle vibration reducer and clutch driven disc

Info

Publication number: CN114585822A
Application number: CN201980101339.1A
Authority: CN
Inventors: 肖荣亭
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2019-12-04
Filing date: 2019-12-04
Publication date: 2022-06-03
Also published as: WO2021109014A1; DE112019007946T5

Abstract

A vibration damping structure with two-stage damping and a vibration damper and a clutch driven plate for a vehicle, the vibration damping structure includes a hub flange (1), two side plates (21,22) and a plurality of vibration damping springs (3), annular friction members (41,42) and an elastic member (5) are provided between the hub flange (1) and the side plates (21,22), the annular friction members (41,42) have different coefficients of friction with the surfaces of the side plates (21,22) and the hub flange (1) in abutment, the annular friction members (41,42) utilizing different coefficients of friction can rotate relative to the hub flange (1) during operation of the vibration damping structure, the annular friction members (41,42) rotate synchronously with the hub flange (1) after the annular friction members (41,42) are engaged with the hub flange (1), so that the annular friction members (41,42) the damping device generates friction damping with a hub flange (1), and the annular friction components (41,42) and the side plate (21) generate friction damping in the synchronous rotation process, so that two-stage damping effect is realized, different damping effects can be generated in the normal working state and the idling working state of the engine, and the damping effect on torsional vibration is improved.

Description

Vibration reduction structure with two-stage damping, vehicle vibration reducer and clutch driven disc

Technical Field

The present invention relates to a vibration damping structure with two-stage damping for a vehicle, and a vehicle damper and a clutch driven plate including the vibration damping structure.

Background

In the prior art, a flywheel serving as a vehicle damper is generally installed between an engine crankshaft of a vehicle and an input shaft of a transmission, and is used for transmitting torque of the engine crankshaft to the input shaft of the transmission while effectively attenuating torsional vibration of the engine crankshaft, so as to reduce the influence of the torsional vibration of the engine crankshaft on the transmission. To achieve the above, prior art flywheels typically include, in addition to the flywheel mass, side plates, a hub flange and damper springs, a friction sleeve/disc and a diaphragm spring between the side plates and the hub flange. These friction sleeves/discs and diaphragm springs not only axially limit the side plates and hub flange, but also provide a corresponding damping effect during operation of the vehicle shock absorber. However, the conventional flywheel including one hub flange can realize only one-stage damping action, and cannot simultaneously achieve vibration damping in both a normal operating state and an idling operating state of the engine.

Similarly, similar problems exist in the existing clutch driven disc for a vehicle.

Disclosure of Invention

Based on the above-mentioned drawbacks of the prior art, it is an object of the present invention to overcome or at least alleviate the above-mentioned disadvantages of the prior art. Therefore, the invention provides a novel vibration damping structure with two-stage damping, which realizes different damping effects aiming at two states of a normal working state and an idling working state of an engine. The invention also provides a vehicle damper and a clutch driven disc comprising the damping structure.

In order to achieve the above object, the present invention adopts the following technical solutions.

The invention provides a vibration damping structure with two-stage damping, which comprises:

a first side plate and a second side plate that are fixed together in a spaced-apart manner in an axial direction of the vibration damping structure;

a flange that is located between the first side plate and the second side plate and that is capable of rotating relative to the first side plate and the second side plate in a circumferential direction of the vibration damping structure for a predetermined range;

a plurality of damper springs each mounted to a damper spring mounting portion formed by the first side plate, the second side plate, and the flange, so that torsional vibration can be attenuated while torque can be transmitted between the first side plate and the flange via the plurality of damper springs; and

an annular friction member that is located between the first side plate and the flange and that abuts against the first side plate and the flange by an elastic force of the elastic member, and an elastic member, a friction coefficient of a surface of the annular friction member that abuts against the first side plate and a friction coefficient of a surface of the annular friction member that abuts against the flange being different, so that: during operation of the vibration damping structure, the annular friction assembly is enabled to perform a predetermined range of relative rotation with respect to the flange along with the side plate due to the difference in the coefficients of friction and to generate frictional damping between the annular friction assembly and the flange, and both rotate in synchronization after the annular friction assembly and the flange are engaged and generate frictional damping between the annular friction assembly and the first side plate.

Preferably, the flange may be a hub flange to which a hub is connected on the radially inner side.

Preferably, the annular friction assembly includes a first annular friction member and a second annular friction member that are not rotatable relative to each other, the first annular friction member abuts against the hub flange and is made of a first material, and the second annular friction member abuts against the first side plate and is made of a second material having a different friction coefficient from the first material.

More preferably, the first material is a non-metallic material and the second material is a metallic material.

More preferably, the first annular friction member includes an annular friction portion and a plurality of first projecting portions projecting from the annular friction portion toward the hub flange, the annular friction portion abuts against the hub flange, the plurality of first projecting portions project into the hub flange in the axial direction, and

the hub flange is formed with a plurality of arc-shaped through holes distributed in the circumferential direction, each of the first projecting portions projects into the corresponding arc-shaped through hole in the axial direction, and the dimension of each of the first projecting portions in the circumferential direction is smaller than the dimension of the corresponding arc-shaped through hole in the circumferential direction, so that the first projecting portions can be engaged with the hub flange after the first annular friction member is relatively rotated in the circumferential direction with respect to the hub flange for a predetermined range.

More preferably, a dimension of the first projecting portion in the axial direction is smaller than a dimension of the hub flange in the axial direction.

More preferably, the first annular friction member further includes a plurality of second projecting portions projecting from the annular friction portion toward the first side plate, and

the second annular friction member is provided with a plurality of fixing holes which are distributed in the circumferential direction and correspond to the plurality of second extending parts, and each second extending part extends into the corresponding fixing hole, so that the first annular friction member and the second annular friction member cannot rotate relatively at least in the circumferential direction.

More preferably, the dimension of the second projecting portion in the axial direction is smaller than the dimension of the second annular friction member in the axial direction.

More preferably, the vibration damping structure further includes a third annular friction member located between the hub flange and the second side plate, and the elastic member is fixed to the second side plate in a relatively non-rotatable manner and abuts against the third annular friction member, so that the third annular friction member abuts against the hub flange.

The present invention also provides a shock absorber for a vehicle, including:

the vibration damping structure according to any one of the above technical solutions; and

a flywheel mass fixed to one of a hub flange and a side plate of the vibration reduction structure for receiving a torque from the outside, the other of the hub flange and the side plate for transmitting the torque to the outside.

The present invention also provides a clutch driven plate including:

a friction damper mechanism provided radially outside one of a hub flange and a side plate of the vibration damping structure and fixed to the one for receiving a torque from the outside, the other one of the hub flange and the side plate for transmitting the torque to the outside.

By adopting the technical scheme, the invention provides a novel vibration damping structure with two-stage damping, and a vehicle vibration damper and a clutch driven disc comprising the vibration damping structure. The damping structure comprises a hub flange, two side plates and a plurality of damping springs, wherein an annular friction assembly and an elastic piece are arranged between the hub flange and the side plates, and the friction coefficient of the surface of the annular friction assembly abutted against one side plate and the hub flange is different. Therefore, in the working process of the vibration damping structure, the annular friction assembly can rotate relative to the disk hub flange by utilizing the difference of the friction coefficients, and the annular friction assembly and the disk hub flange rotate synchronously after the annular friction assembly is jointed with the disk hub flange, so that the annular friction assembly and the disk hub flange generate friction damping in the relative rotation process and the annular friction assembly and the side plate generate friction damping in the synchronous rotation process, and further two-stage damping effect is realized.

Therefore, the vibration damping structure can realize two-stage damping action under the condition of only comprising one hub flange, can generate different damping actions under the two states of the normal working state and the idling working state of the engine, gives consideration to vibration damping under the two states, and improves the damping effect on torsional vibration.

Drawings

FIG. 1a is a schematic front view of a vibration damping structure with two-stage damping according to an embodiment of the present invention, wherein a part of the structure is omitted to show the internal construction thereof; FIG. 1b is an exploded schematic view of the vibration dampening structure of FIG. 1 a; FIG. 1c is a cross-sectional schematic view of the vibration damping structure of FIG. 1a taken along line L1-L1 including a central axis O; fig. 1d is an enlarged schematic view of region M in fig. 1 c.

FIG. 2a is a schematic perspective view of a first annular friction member of the vibration damping structure of FIG. 1 a; fig. 2b is another perspective view of the first annular friction member of the vibration damping structure of fig. 1 a.

Description of the reference numerals

1 hub flange 1h1 mounting hole 1h2 first arc through hole 1h3 second arc through hole

21 first side plate 21h first window 22 second side plate 22h second window 23 connector

3 damping spring

41 first annular Friction element 411 annular Friction portion 412 first extension 413 second extension 42 second annular Friction element 42 securing hole 43 third annular Friction element FP1 first Friction Pair FP2 second Friction Pair FP3 third Friction Pair FP4 fourth Friction Pair

5 diaphragm spring

R radial A axial C circumferential O central axis.

Detailed Description

The following describes specific embodiments of the present invention with reference to the drawings. In the drawings, axial, radial and circumferential directions refer to axial, radial and circumferential directions, respectively, of the vibration damping structure according to the present invention, unless otherwise specified; the axial side refers to the left side in fig. 1c and 1d, such as the side where the engine is located; the other axial side refers to the right side in fig. 1c and 1d, for example, the side on which the transmission is located; the radially outer side refers to a side (upper side in fig. 1 d) away from the central axis O in the radial direction, and the radially inner side refers to a side (lower side in fig. 1 d) close to the central axis O in the radial direction.

The construction and operation of the vibration damping structure with two-stage damping according to an embodiment of the present invention will be first described with reference to the accompanying drawings.

(vibration damping structure with two-stage damping according to an embodiment of the present invention)

As shown in fig. 1a to 1d, the vibration damping structure with two-stage damping according to an embodiment of the present invention has a disk shape as a whole and includes one hub flange 1, two side plates (a first side plate 21 and a second side plate 22), a plurality of (four in the present embodiment) connecting members 23, a plurality of (four in the present embodiment) vibration damping springs 3, a plurality of (three in the present embodiment)

annular friction members

41,42, 43 (wherein the first annular friction member 41 and the second annular friction member 42 constitute an annular friction assembly), and a diaphragm spring 5, which are assembled with each other.

Specifically, in the present embodiment, the hub flange 1 has a circular plate shape, and the hub flange 1 is located between the two

side plates

21,22 in the axial direction a and is rotatable in the circumferential direction C within a predetermined range with respect to the two

side plates

21,22 after the entire vibration damping structure is mounted.

Further, the hub flange 1 is formed with a mounting hole 1h1, a first arc through hole 1h2, and a second arc through hole 1h3 penetrating in the axial direction a. The mounting hole 1h1 is used for mounting the damper spring 3, the first arc through hole 1h2 is used for the first protrusion 412 of the first annular friction member 41 described below to protrude into, and the second arc through hole 1h3 is used for the engagement with the connecting member 23.

Specifically, the number of the mounting holes 1h1 is the same as the number of the damper springs 3, and four mounting holes 1h1 are evenly distributed in the circumferential direction C. The length of the mounting hole 1h1 may substantially coincide with the initial length of the damper spring 3 when uncompressed.

The first arc-shaped through hole 1h2 extends a predetermined length in the circumferential direction C. The number of the first arc-shaped through holes 1h2 is the same as the number of the first protruding parts 412 of the first annular friction member 41. The length of the first arc-shaped through hole 1h2 in the circumferential direction C is larger than the length of the corresponding first protruding portion 412 in the circumferential direction C. The maximum range of rotation of the first annular friction member 41 in the circumferential direction C with respect to the hub flange 1 is defined by the first arc-shaped through hole 1h2 in cooperation with the first protruding portion 412.

In the illustrated non-limiting example, the number of the plurality of first arc-shaped through holes 1h2 and the number of the plurality of first protruding parts 412 are each eight. The four first arc-shaped through holes 1h2 are respectively located radially inward of the corresponding mounting holes 1h1 and spaced apart from the corresponding mounting holes 1h1, and the other four first arc-shaped through holes 1h2 are respectively located radially inward of the corresponding second arc-shaped through holes 1h3 and spaced apart from the corresponding second arc-shaped through holes 1h 3.

The second arc-shaped through hole 1h3 extends a predetermined length in the circumferential direction C. The number of the second arc-shaped through holes 1h3 is the same as that of the connecting pieces 23, four second arc-shaped through holes 1h3 are uniformly distributed in the circumferential direction C, and four second arc-shaped through holes 1h3 and four mounting holes 1h1 are alternately arranged in the circumferential direction C. The maximum extent to which the hub flange 1 can be rotated in the circumferential direction C relative to the two

side plates

21,22 is defined by the second arcuate through-holes 1h3 in cooperation with the connecting piece 23.

In the present embodiment, the first side plate 21 and the second side plate 22 are provided to face each other with the hub flange 1 interposed therebetween in the axial direction a, the first side plate 21 is positioned on one axial side of the hub flange 1, and the second side plate 22 is positioned on the other axial side of the hub flange 1. The first side plate 21 and the second side plate 22 are fixedly connected together by four connecting pieces 23 evenly distributed in the circumferential direction C, so that the two

side plates

21,22 can operate as a whole.

Specifically, the first side plate 21 is formed with a first window 21h for mounting the damper spring 3. The number of the first windows 21h is the same as the number of the damper springs 3, and the four first windows 21h are evenly distributed in the circumferential direction C. The length of the first window 21h in the circumferential direction C may be substantially equal to the initial length of the damper spring 3 when uncompressed. The second side plate 22 is formed with a second window 22h for mounting the damper spring 3. The number of the second windows 22h is the same as the number of the damper springs 3, and the four second windows 22h are evenly distributed in the circumferential direction C. The length of the second window 22h in the circumferential direction C may be substantially equal to the initial length of the damper spring 3 when uncompressed.

When the first side plate 21 and the second side plate 22 are fixedly coupled together, the first window 21h and the second window 22h are opposed to each other in the axial direction a, and the paired first window 21h and second window 22h correspond to one mounting hole 1h1 to form one damper spring mounting portion. When the damper spring 3 is mounted in this damper spring mounting portion, the damper spring 3 is restrained in all of the radial direction R, the axial direction a, and the circumferential direction C.

In the present embodiment, the damper springs 3 may be cylindrical coil springs and have the same size. The four damper springs 3 are respectively mounted in the corresponding damper spring mounting portions such that the damper springs 3 are compressed when the first and

second side plates

21,22 rotate relative to the hub flange 1, thereby enabling the damper springs 3 to function to damp torsional vibration when torque is transmitted between the first and

second side plates

21,22 and the hub flange 1 via the damper springs 3.

In the present embodiment, the damping structure of the vibration damping structure according to an embodiment of the present invention includes three

annular friction members

41,42, 43 and the diaphragm spring 5, wherein the first annular friction member 41 and the second annular friction member 42 are relatively fixed to constitute an annular friction assembly. In the present application, the phrase "the first annular friction member 41 and the second annular friction member 42 are relatively fixed" means that they cannot rotate relatively at least in the circumferential direction C, and more preferably, they cannot move relatively in the radial direction R at the same time, but they may not be easily separated in the axial direction a.

Specifically, the first annular friction member 41 is annular as a whole and made of a non-metallic material such as plastic, and the first annular friction member 41 is located between the first side plate 21 and the hub flange 1 and is capable of rotating in the circumferential direction C relative to the hub flange 1 for a predetermined range. As shown in fig. 2a and 2b, the first annular friction member 41 includes an annular friction portion 411, a plurality of first protruding portions 412 protruding from the annular friction portion 411 toward the other side in the axial direction, and a plurality of second protruding portions 413 protruding from the annular friction portion 411 toward the one side in the axial direction. The annular friction portion 411 of the first annular friction member 41 is located between the first side plate 21 and the hub flange 1 in the axial direction a. The plurality of first projecting portions 412 are evenly distributed in the circumferential direction C and the first projecting portions 412 project in the axial direction a into the first arc-shaped through hole 1h2 of the hub flange 1. The plurality of second protrusions 413 are evenly distributed in the circumferential direction C and the second protrusions 413 protrude into the mounting hole 42h of the second annular friction member 42 in the axial direction a.

Assuming that the first projecting portion 412 is located at the center position of the first arc-shaped through hole 1h2 (as shown in fig. 1 a) in the initial state in which the damper spring 3 is uncompressed, the angle of the central angle corresponding to the arc between the circumferential end portion of the first projecting portion 412 and the corresponding circumferential end portion of the first arc-shaped through hole 1h2 is α. Thus, when the hub flange 1 is rotated by an angle smaller than α with respect to the

side plates

21,22 from the initial state (when the damper spring 3 is uncompressed), the first annular friction member 41 is also rotated by the same angle with respect to the hub flange 1 by the difference in frictional force between the

annular friction members

41,42 and the hub flange 1 and the second side plate 22 described below; as the first projecting portion 412 engages with the hub flange 1 after the hub flange 1 has rotated relative to the

side plates

21,22 by an angle equal to α, the first annular friction member 41 will rotate synchronously with the hub flange 1 without relative rotation therebetween.

It should be understood that reference in this application to the first protrusion 412, the first annular friction member 41 or the annular friction member engaging the hub flange 1 means that they are not rotatable relative to each other in at least one circumferential direction (clockwise or counterclockwise). After the first protruding portion 412, the first annular friction member 41, or the annular friction member is engaged with the hub flange 1, the engaged state can be released and re-established due to the rotation of the side plate 41 relative to the hub flange 1.

In addition, it is preferable that a reset member (not shown) be provided so that the first protrusion 412 can return to the central position of the first arc-shaped through hole 1h2 after the operation of the vibration damping structure is completed; alternatively, the maximum relative rotational angle of the hub flange 1 with respect to the two

side plates

21,22, which is defined by the connection piece 23 and the second arc-shaped through hole 1h3, and the central angle corresponding to the maximum compression of the damper spring 3 may be greater than 2 α. Thus, the vibration damping structure can be ensured to normally play a two-stage damping role.

Further, the second annular friction member 42 is annular as a whole and made of a metal material, and the second annular friction member 42 is located between the first side plate 21 and the hub flange 1 in the axial direction a. The second annular friction member 42 is formed with a plurality of fixing holes 42h corresponding to the second protruding portion 413 of the first annular friction member 41, which are evenly distributed in the circumferential direction C, and the shape and size of the fixing holes 42h match those of the second protruding portion 413.

Further, the third annular friction member 43 is annular as a whole and made of a non-metallic material. The third annular friction element 43 is located in the axial direction a between the hub flange 1 and the second side plate 22.

In the present embodiment, the diaphragm spring 5 is fixed to the second side plate 22 (cannot rotate relative to the second side plate 22). The diaphragm spring 5 presses against the third annular friction member 43, so that the third annular friction member 43 abuts against the hub flange 1, the hub flange 1 abuts against the annular friction portion 411 of the first annular friction member 41, and the second annular friction member 42 abuts against the first side plate 21.

It should be further noted that the dimension in the axial direction a of the first protruding portion 412 of the first annular friction member 41 is preferably smaller than the dimension in the axial direction a of the hub flange 1, and the dimension in the axial direction a of the second protruding portion 413 of the first annular friction member 41 is preferably smaller than the dimension in the axial direction a of the second annular friction member 42. Therefore, in the axial direction a, the first projecting portion 412 of the first annular friction member 41 does not contact the third annular friction member 43, the diaphragm spring 5, and the second side plate 22, and the second projecting portion 413 of the first annular friction member 41 does not contact the first side plate 21.

The construction of the vibration damping structure according to the present invention is explained above, and the operation principle of the vibration damping structure according to the present invention will be explained below.

Because the friction coefficients of the first annular friction member 41 made of a non-metallic material and the second annular friction member 42 made of a metallic material are different, in the case where the first side plate 21 and the hub flange 1 are made of the same kind of material (e.g., metal) under the spring force of the same diaphragm spring 5, the (static) friction force between the second annular friction member 42 and the first side plate 21 is larger than the (static) friction force between the first annular friction member 41 and the hub flange 1. In this way, when the vibration damping structure according to the present invention is in the initial state as shown in fig. 1a, due to the relationship between the above-described frictional forces, at the initial stage of the rotation of the hub flange 1 with respect to the two

side plates

21,22 from the initial state, the annular friction member assembly of the first annular friction member 41 and the second annular friction member 42 can rotate with the two

side plates

21,22 instead of with the hub flange 1, and thus the annular friction member assembly generates relative rotation with respect to the hub flange 1. Only when the first protruding portion 412 of the first annular friction member 41 abuts the circumferential end portion of the first arc-shaped through hole 1h2 of the hub flange 1, that is, the first protruding portion 412 engages with the hub flange 1, the annular friction member rotates synchronously with the hub flange 1, and at this time, the annular friction member rotates relative to the side plate 21. During both the above-mentioned relative rotation and the synchronous rotation, the different friction pairs described below act, thus producing a two-stage damping effect.

Based on the above structural design, as shown in fig. 1d, during the operation of the vibration damping structure according to the present invention, the following four friction pairs can be realized.

Name(s)	Component part
First friction pair FP1	Annular friction part 411 of first annular friction member 41 and hub flange 1

Second friction pair FP2	Third annular friction member 43 and diaphragm spring 5
Third friction pair FP3	Third annular friction element 43 and hub flange 1
Fourth friction pair FP4	Second annular friction member 42 and first side plate 21

In this way, during the rotation of the hub flange 1 from the initial state (when the damper springs 3 are not compressed) relative to the two

side plates

21,22 by an angle smaller than α, the annular friction assembly of the first annular friction member 41 and the second annular friction member 42 rotates with the

side plates

21,22, so that the first friction acts as a damping action on the FP1 on one axial side of the hub flange 1; on the other axial side of the hub flange 1, the second friction pair FP2 or the third friction pair FP3 is damped depending on whether the third annular friction member 43 is fixed to the hub flange 1 or to the second side plate 22. The damping action described above acts primarily in the idle state of the engine.

After the hub flange 1 rotates by an angle equal to α relative to the two

side plates

21,22 from the initial state (when the damper spring 3 is uncompressed), the annular friction assembly of the first annular friction member 41 and the second annular friction member 42 rotates with the hub flange 1, so that the fourth friction member has a damping effect on FP4 on one axial side of the hub flange 1; on the other axial side of the hub flange 1, the second friction pair FP2 or the third friction pair FP3 damps depending on whether the third annular friction member 43 is fixed to the hub flange 1 or to the second side plate 22. The damping effect mainly plays a role in the normal working state of the engine.

Thus, the vibration damping structure can give consideration to both the idling state and the normal working state of the engine and play a two-stage damping role.

The construction and the operation principle of the vibration damping structure with two-stage damping according to an embodiment of the present invention have been explained above, and the construction of the vehicular damper and the clutch driven plate according to the present invention including the vibration damping structure will be explained below.

(damper for vehicle according to the invention)

The present invention also provides a shock absorber for a vehicle that may include a flywheel mass, a hub core, and a centrifugal pendulum unit in addition to the shock absorbing structure having the above-described configuration. Specifically, the hub flange 1 or the first side plate 21 of the vibration damping structure is fixedly connected with both the flywheel mass and the engine crankshaft of the vehicle for receiving torque from the engine; the second side plate 22 of the vibration damping structure or the hub flange 1 is fixedly connected to a hub core, which is in driving connection with a transmission input shaft of a vehicle for transmitting torque to the transmission input shaft. The transmission may be a dual clutch transmission, a manual automatic transmission, or any other type of transmission. In addition, a plurality of centrifugal pendulum units may be located radially outward of the hub flange and mounted to the first and

second side plates

21,22 for further damping torsional vibrations from the engine.

(Clutch driven plate according to the invention)

The present invention also provides a clutch driven plate that may include a friction damping mechanism and a hub core in addition to the vibration damping structure having the above-described configuration. The friction buffer mechanism may be disposed radially outside the hub flange 1 and fixedly connected to the hub flange 1, the friction buffer mechanism is configured to receive torque from an outside of the clutch driven disc, and the hub core is fixed to the first side plate 21 or the second side plate 22 of the vibration damping structure and configured to transmit torque to the outside of the clutch driven disc.

The specific technical solutions of the present invention are explained in detail above, and further supplementary descriptions will be provided below.

(i) Although the number of the damper springs 3 is four in the above embodiment, other numbers of the damper springs 3 may be adopted. The damper spring 3 may be not only a linear cylindrical coil spring as described above but also an arc-shaped coil spring.

When the damper springs 3 are linear cylindrical coil springs, it is preferable that each damper spring 3 is housed in the damper spring mounting portion as described above such that the longitudinal direction thereof coincides with the direction of one tangent line of the circumferential direction C of the damper structure; when the damper springs 3 are arc-shaped coil springs, it is preferable that each damper spring 3 is housed in the damper spring mounting portion as described above so that the longitudinal direction thereof coincides with the circumferential direction C of the damper structure.

(ii) In order to avoid interference of the linear damper springs 3 with the hub flange 1 when the hub flange 1 rotates relative to the

side plates

21 and 22, the radially outer edge of the mounting hole 1h of the hub flange 1 may be formed with an arcuate contour that is convex radially outward.

(iii) In the damper structure according to the present invention, the

annular friction members

41,42, 43 and the diaphragm spring 5 may be disposed radially inside or radially outside the damper spring mounting portion.

(iv) Although not specifically described in the above embodiment, it is to be understood that the first annular friction member 41 and the second annular friction member 42 may be formed integrally; or the first annular friction member 41 and the second annular friction member 42 may be fixed together by other connecting members.

(v) When the vibration damping structure of the present invention is applied to a damper or a clutch disc for a vehicle, the damper or the clutch disc for a vehicle further includes a torque limiter, and the torque limiter may be provided at an input end of torque and/or an output end of torque of the damper or the clutch disc for a vehicle, or at another position of the damper or the clutch disc for a vehicle. For example, in one non-limiting embodiment of a vehicle damper, a torque limiter may be disposed between the flywheel mass and the flange as the input member, or between the side plate as the output member and the output shaft.

Claims

A vibration damping structure with two-stage damping, the vibration damping structure comprising:

a first side plate (21) and a second side plate (22), the first side plate (21) and the second side plate (22) being fixed together in an axial direction (A) of the vibration damping structure, spaced apart from each other;

a flange (1), wherein the flange (1) is positioned between the first side plate (21) and the second side plate (22) and can rotate relative to the first side plate (21) and the second side plate (22) in a preset range in the circumferential direction (C) of the vibration damping structure;

an annular friction assembly (41,42) and an elastic member (5), the annular friction assembly (41,42) being located between the first side plate (21) and the flange (1) and abutting against the first side plate (21) and the flange (1) under the elastic force of the elastic member (5), a friction coefficient of a surface of the annular friction assembly (41,42) abutting against the first side plate (21) and a friction coefficient of a surface of the annular friction assembly (41,42) abutting against the flange (1) being different, so that: during the operation of the vibration damping structure, the annular friction assemblies (41,42) can rotate relative to the flanges (1) for a predetermined range along with the side plates (21,22) and generate friction damping between the annular friction assemblies (41,42) and the flanges (1) due to the difference of the friction coefficients, and the annular friction assemblies (41,42) rotate synchronously with the flanges (1) after being engaged and generate friction damping between the annular friction assemblies (41,42) and the first side plates (21).
The vibration damping arrangement according to claim 1, characterized in that the annular friction member (41,42) comprises a first annular friction member (41) and a second annular friction member (42) which are non-rotatable relative to each other, the first annular friction member (41) abutting the flange (1) and being made of a first material, the second annular friction member (42) abutting the first side plate (21) and being made of a second material having a different coefficient of friction from the first material.
The vibration damping structure according to claim 2, characterized in that the first material is a non-metallic material and the second material is a metallic material.
The vibration damping structure according to claim 2 or 3,

the first annular friction member (41) includes an annular friction portion (411) and a plurality of first projecting portions (412) projecting from the annular friction portion (411) toward the flange (1), the annular friction portion (411) abuts on the flange (1), the plurality of first projecting portions (412) project into the flange (1) in the axial direction (A), and

the flange (1) is formed with a plurality of arc-shaped through holes (1h2) distributed in the circumferential direction (C), each of the first projecting portions (412) projects into the corresponding arc-shaped through hole (1h2) in the axial direction (A), and the dimension of each of the first projecting portions (412) in the circumferential direction (C) is smaller than the dimension of the corresponding arc-shaped through hole (1h2) in the circumferential direction (C), so that the first projecting portion (412) is engaged with the flange (1) after the first annular friction member (41) is relatively rotatable with respect to the flange (1) in the circumferential direction (C) for a predetermined range.
The vibration damping structure according to claim 4,

the first annular friction member (41) further includes a plurality of second projecting portions (413) projecting from the annular friction portion (411) toward the first side plate (21), and

the second annular friction member (42) is formed with a plurality of fixing holes (42h) corresponding to the plurality of second protruding portions (413) distributed in the circumferential direction (C), and each of the second protruding portions (413) protrudes into the corresponding fixing hole (42h), so that the first annular friction member (41) and the second annular friction member (42) cannot rotate relative to each other at least in the circumferential direction (C).
The vibration damping structure according to any one of claims 1 to 5, characterized in that the vibration damping structure further comprises a third annular friction member (43), the third annular friction member (43) being located between the flange (1) and the second side plate (22), the elastic member (5) being relatively non-rotatably fixed to the second side plate (22) and abutting against the third annular friction member (43) such that the third annular friction member (43) abuts against the flange (1).
A shock absorber for a vehicle, comprising:

the vibration damping structure according to any one of claims 1 to 6; and

a flywheel mass fixed to one of a flange (1) and a side plate (21,22) of the vibration damping structure for receiving torque from outside, the other of the flange (1) and the side plate (21,22) for transmitting torque to outside.
The vehicle shock absorber as set forth in claim 7, further comprising a torque limiter.
A clutch driven plate, comprising:

the vibration damping structure according to any one of claims 1 to 6; and

the clutch driven disk receives torque from the outside via one of a flange (1) and side plates (21,22) of the vibration damping structure, and the clutch driven disk is used for transmitting torque to the outside via the other of the flange (1) and side plates (21, 22).
The clutch driven disc of claim 9, further comprising a torque limiter.