阅读说明：本技术 离合器和从动盘总成 (Clutch and driven plate assembly ) 是由 叶鉴申 段茂林 于 2019-03-28 设计创作，主要内容包括：提供了一种从动盘总成,其包括减振盘、盘毂和减振弹簧,所述减振弹簧为涡卷弹簧,所述涡卷弹簧的一端安装于所述盘毂,所述涡卷弹簧的另一端安装于所述减振盘,所述涡卷弹簧与所述盘毂同轴安装,所述涡卷弹簧能够在所述减振盘和所述盘毂之间传递扭矩。涡卷弹簧与传统的柱形螺旋弹簧相比,具有更小的弹簧刚度,在传递扭矩的过程中,涡卷弹簧能够获得更大的旋转角度,从而使从动盘总成具有更高的减振效率和更好的减振效果。零部件数目更少,从而使从动盘总成的质量减小、惯性降低。这样的从动盘总成几乎可以获得类似于双质量飞轮的较大的旋转角度和较小的弹簧刚度,从而获得类似于双质量飞轮的减振性能。(The driven disc assembly comprises a vibration reduction disc, a disc hub and a vibration reduction spring, wherein the vibration reduction spring is a spiral spring, one end of the spiral spring is installed on the disc hub, the other end of the spiral spring is installed on the vibration reduction disc, the spiral spring and the disc hub are coaxially installed, and the spiral spring can transmit torque between the vibration reduction disc and the disc hub. Compared with the traditional cylindrical spiral spring, the spiral spring has smaller spring stiffness, and can obtain larger rotating angle in the process of transmitting torque, so that the driven disc assembly has higher vibration reduction efficiency and better vibration reduction effect. The number of parts is reduced, so that the mass of the driven disk assembly is reduced and the inertia is reduced. Such a driven disk assembly can almost achieve a larger rotation angle and a smaller spring rate similar to those of a dual mass flywheel, thereby achieving a damping performance similar to that of the dual mass flywheel.)

1. A driven disc assembly comprising a damping disc, a hub (50) and a damping spring, characterised in that the damping spring is a spiral spring (40), one end of the spiral spring (40) is mounted to the hub (50), the other end of the spiral spring (40) is mounted to the damping disc, the spiral spring (40) is mounted coaxially with the hub (50), the spiral spring (40) is capable of transmitting torque between the damping disc and the hub (50).

2. A driven disc assembly according to claim 1, wherein the hub (50) comprises a hub disc (51) and a hub core (52), the hub disc (51) being non-rotatably connected to or integrally formed with the hub core (52), one end of the spiral spring (40) being mounted to the hub core (52) and the other end of the spiral spring (40) being mounted to a radially outer portion of the damper disc.

3. A driven disc assembly according to claim 1, wherein the disc hub (50) comprises a disc hub disc (51) and a disc hub core (52), the disc hub disc (51) being non-rotatably connected or integrally formed with the disc hub core (52), the damper disc comprising:

a first damper disc (31), the first damper disc (31) being located on one axial side of the hub disc (51) in the axial direction of the driven disc assembly; and

a second damper disk (32), the second damper disk (32) being located on the other axial side of the hub disk (51) in the axial direction of the driven disk assembly,

in the axial direction of the driven disc assembly, the spiral spring (40) is located between the damper disc and the hub disc (51).

4. The driven plate assembly of claim 3,

in the axial direction of the driven plate assembly, the spiral spring (40) is located between the first damping plate (31) and the hub plate (51).

5. The driven plate assembly according to claim 4, wherein the hub (50) further includes a stopper pin (61), the stopper pin (61) projecting from the hub plate (51) to the other axial side, the second damping plate (32) having an arc-shaped stopper groove (62) extending along a circumferential direction thereof, the stopper pin (61) protruding into the arc-shaped stopper groove (62) and being rotatable within a predetermined range in the circumferential direction within the arc-shaped stopper groove (62).

6. A driven disk assembly according to claim 5 wherein the predetermined range does not exceed 40 degrees.

7. A driven plate assembly according to claim 3, wherein the first damping plate (31) and the second damping plate (32) are integrally mounted by a damping plate rivet (30a), an axis of the damping plate rivet (30a) extending in the axial direction, and the other end of the spiral spring (40) is mounted to a portion of the damping plate rivet (30a) between the first damping plate (31) and the second damping plate (32).

8. A driven disc assembly according to claim 1, wherein the hub (50) comprises a hub disc (51) and a hub core (52), the hub disc (51) being non-rotatably connected to or integrally formed with the hub core (52), one end of the spiral spring (40) being mounted to the hub disc (51) and the other end of the spiral spring (40) being mounted to a radially outer portion of the damper disc.

9. The driven disc assembly according to claim 1, wherein the number of the spiral springs (40) is two to four, the spiral springs (40) are arranged along the axial direction of the driven disc assembly, one ends of the spiral springs (40) are uniformly arranged along the circumferential direction of the disc hub (50), and the other ends of the spiral springs (40) are uniformly arranged along the circumferential direction of the damping disc.

10. A clutch, characterized by comprising a driven plate assembly according to any one of claims 1 to 9.

Technical Field

The invention relates to the technical field of vehicles, in particular to a clutch and driven plate assembly.

Background

The driven plate assembly generally includes a friction plate, a damper spring mounted to the damper plate, a hub core, a plate hub fixedly mounted to the hub core, and the like.

In a conventional clutch, the damper spring is typically a cylindrical coil spring. The disk surface of the damping disk has a mounting window in which the axis of the cylindrical coil spring is mounted substantially tangentially to the circumferential direction of the damping disk. The vibration damping disc plays a role in power transmission in the driven disc assembly, and the friction plate receives torque transmitted from the engine end and transmits the torque to the vibration damping disc. The damper disc rotates relative to the hub disc, the damper spring is compressed, and torque is transmitted in sequence to the damper spring and hub in the driven disc assembly. Finally, the hub outputs power to the gearbox.

In such a driven disk assembly, the rotational angle of the damper disk is usually not more than about 20 degrees, the spring rate is higher than that of the arc spring of the dual mass flywheel, and the damping efficiency and the damping effect are poor.

Disclosure of Invention

The present invention has been made in view of the state of the art described above. The invention aims to provide a clutch and driven plate assembly which has a good vibration reduction effect and high vibration reduction efficiency.

The driven disc assembly comprises a vibration reduction disc, a disc hub and a vibration reduction spring, wherein the vibration reduction spring is a spiral spring, one end of the spiral spring is installed on the disc hub, the other end of the spiral spring is installed on the vibration reduction disc, the spiral spring and the disc hub are installed coaxially, and the spiral spring can transmit torque between the vibration reduction disc and the disc hub.

In at least one embodiment, the hub comprises a hub disc and a hub core, the hub disc being non-rotatably connected to or integrally formed with the hub core, one end of the spiral spring being mounted to the hub core and the other end of the spiral spring being mounted to a radially outer portion of the damper disc.

In at least one embodiment, the hub comprises a hub disc and a hub core, the hub disc being non-rotatably connected or integrally formed with the hub core, the damper disc comprising:

a first damper disc located on one axial side of the hub disc in an axial direction of the driven disc assembly; and

a second damper disc located on the other axial side of the hub disc in the axial direction of the driven disc assembly,

in the axial direction of the driven disc assembly, the spiral spring is located between the damper disc and the hub disc.

In at least one embodiment, the wrap spring is located between the first damper disc and the hub disc in an axial direction of the driven disc assembly.

In at least one embodiment, the hub further includes a stopper pin protruding from the hub disc toward the other axial side, and the second damping disc has an arc-shaped stopper groove extending along a circumferential direction thereof, and the stopper pin protrudes into the arc-shaped stopper groove and is rotatable within a predetermined range in the circumferential direction within the arc-shaped stopper groove.

In at least one embodiment, the predetermined range does not exceed 40 degrees.

In at least one embodiment, the first damping plate and the second damping plate are integrally mounted by a damping plate rivet, an axis of which extends in the axial direction, and the other end of the spiral spring is mounted to a portion of the damping plate rivet between the first damping plate and the second damping plate.

In at least one embodiment, the hub comprises a hub disc and a hub core, the hub disc being non-rotatably connected to or integrally formed with the hub core, one end of the spiral spring being mounted to the hub disc and the other end of the spiral spring being mounted to a radially outer portion of the damper disc.

In at least one embodiment, the number of the spiral springs is two to four, the spiral springs are arranged along the axial direction of the driven disc assembly, one ends of the spiral springs are evenly arranged along the circumferential direction of the disc hub, and the other ends of the spiral springs are evenly arranged along the circumferential direction of the damping disc.

There is provided a clutch including a driven plate assembly according to any one of the preceding claims.

The driven plate assembly and the clutch adopting the technical scheme can at least obtain the following beneficial effects:

compared with the traditional cylindrical spiral spring, the spiral spring has smaller spring stiffness, and can obtain larger rotating angle in the process of transmitting torque, so that the driven disc assembly has higher vibration reduction efficiency and better vibration reduction effect.

The number of parts is reduced, so that the mass of the driven disk assembly is reduced and the inertia is reduced.

Such a driven disk assembly can almost achieve a larger rotation angle and a smaller spring rate similar to those of a dual mass flywheel, thereby achieving a damping performance similar to that of the dual mass flywheel.

Drawings

FIG. 1 is a front view of one embodiment of a driven disk assembly provided by the present invention.

Fig. 2 is an axial cross-sectional view of the driven disk assembly of fig. 1.

FIG. 3 is an exploded view of the driven disk assembly of FIG. 1.

FIG. 4 is a front view of the driven disc assembly of FIG. 1 with the second damping disc removed.

Fig. 5 is a front view of a second damping disc of the driven disc assembly of fig. 1.

FIG. 6 is a front view of the hub of the driven disk assembly of FIG. 1.

FIG. 7 is an elevation view of another embodiment of a driven disk assembly provided by the present invention.

FIG. 8 is a graph of torque versus deflection of a flat spiral spring in a driven disk assembly according to the present invention.

Description of reference numerals:

the vibration damping disc comprises a driven disc assembly 1, a first friction plate 11, a second friction plate 12, a friction plate rivet 10a, a corrugated plate 20, a corrugated plate rivet 20a, a first vibration damping disc 31, a second vibration damping disc 32, a vibration damping disc rivet 30a, a vibration damping disc rivet hole 30b, a flat spiral spring 40, a disc hub 50, a disc hub 51, a disc hub core 52, a limiting pin 61, an arc limiting groove 62 and a support ring 70.

Detailed Description

Exemplary embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood that the detailed description is intended only to teach one skilled in the art how to practice the invention, and is not intended to be exhaustive or to limit the scope of the invention.

Referring to fig. 1 to 3, the present invention provides a driven plate assembly 1 of a clutch. In this embodiment, driven disc assembly 1 may include first friction plate 11, second friction plate 12, corrugated plate 20, first damping disc 31, two flat spiral springs 40, hub 50, support ring 70, and second damping disc 32. The hub 50 has a hub disc 51 and a hub core 52 which are connected in a rotationally fixed manner or are formed integrally, the hub disc 51 being fitted to the hub core 52 outside the hub core 52.

The "axial direction" of the driven disk assembly 1 is a direction extending from the flywheel of the engine to the transmission, such as a direction perpendicular to the drawing in fig. 1, and a left-right direction in fig. 2.

It is defined here that one axial side of the driven disk assembly 1 is the side closer to the flywheel of the engine, and the other axial side of the driven disk assembly 1 is the side closer to the transmission. .

The driven disk assembly 1 has, in order from one axial side to the other axial side: first damping disk 31, flat spiral spring 40, hub disk 51 of hub 50 and second damping disk 32. Hub core 52 extends through first damper disc 31, flat spiral spring 40 and second damper disc 32. Hub 50, first damping disk 31, second damping disk 32 and flat spiral spring 40 are coaxially arranged.

Flat spiral spring 40 may be located on one axial side of hub plate 51, flat spiral spring 40 having a radially inner end and a radially outer end, the radially inner end (one end) of flat spiral spring 40 being mounted to hub 50. The radially outer end of the spiral spring 40 is mounted to a damping disc, such as the portion of the first damping disc 31 near the outer periphery.

Thus, when the damping plate and the hub 50 rotate relatively, the spiral spring 40 is elastically deformed in a plane thereof by a torque, so that the torque is transmitted between the damping plate (first damping plate 31) and the hub 50.

As defined herein, the first damping disk 31 has an inner portion and an outer portion in the radial direction thereof, the radially inner portion of the first damping disk 31 includes a portion from the inner periphery in the radial direction up to the center of the outer periphery and the inner periphery, and the radially outer portion of the first damping disk 31 includes a portion from the center of the outer periphery and the inner periphery in the radial direction up to the outer periphery.

It should be understood that the radially outer end of the spiral spring 40 may also be located at other positions on the radially outer portion of the first damping plate 31, and such spiral spring 40 may also serve to stabilize the load torque.

As shown in fig. 3 and 4, a plurality of corrugated sheets 20 are fixed to a first damping plate 31 by corrugated sheet rivets 20a to form a corrugated sheet ensemble, the corrugated sheets are integrally installed between a first friction plate 11 and a second friction plate 12, and the first friction plate 11 and the second friction plate 12 are formed into a friction plate ensemble by friction plate rivets 10 a.

When spiral spring 40 is installed between first damper disk 31 and hub plate 51, torque transmitted from the flywheel of the engine is transmitted to spiral spring 40 through the entire friction plate and first damper disk 31 in sequence, the transmission path is short, and the transmission efficiency is high.

As shown in fig. 6, the hub 50 may further include a limit pin 61, and the limit pin 61 is located on the hub plate 51, for example, the limit pin 61 is integrally formed with the hub plate 51. The stopper pin 61 may protrude from the hub plate 51 to the other axial side in the axial direction of the driven plate assembly 1, that is, the stopper pin 61 is located between the hub plate 51 and the second damping plate 32. In the axial direction of driven disk assembly 1, stopper pin 61 and spiral spring 40 are located on both sides of hub plate 51.

As shown in fig. 5, the second damping disk 32 may further be provided with an arc-shaped limiting groove 62, and the arc-shaped limiting groove 62 extends along the circumferential direction of the second damping disk 32. The stopper pin 61 can be inserted into the arc-shaped stopper groove 62 in the axial direction of the driven disc assembly 1, and moves within a predetermined range in the circumferential direction of the second damping disc 32 in the arc-shaped stopper groove 62.

Thus, the flat spiral spring 40 is prevented from being excessively deformed due to an excessively large torque transmitted thereto, thereby protecting the flat spiral spring 40 from being damaged.

The number of the limiting pins 61 may be at least two, preferably two or three, and the number of the arc-shaped limiting grooves 62 is the same as that of the limiting pins 61.

The arc-shaped stopper groove 62 may provide the stopper pin 61 with the above-described predetermined range of rotational span in two opposite directions, for example, along the circumferential direction of the second damping plate 32, thereby protecting the spiral spring 40 in the case of transmitting torque in two directions.

Specifically, referring to fig. 1, taking as an example the case where the damping disk as a whole (described later) rotates counterclockwise (when viewed from the transmission side toward the engine side) with respect to the hub 50 when torque is transmitted, when the spiral spring 40 does not transmit torque (i.e., is in a natural state), the arc-shaped stopper groove 62 allows the damping disk as a whole to rotate counterclockwise (forward) by, for example, 32 degrees with respect to the hub 50 (i.e., the stopper pin 61) and clockwise (reverse) by, for example, 8 degrees, with a rotational span in the counterclockwise direction that is greater than that in the clockwise direction.

The rotational span of the damping disc as a whole in the counterclockwise direction serves for damping when torque is transmitted between the damping disc as a whole and the hub 50.

The stopper pins 61 and the arc-shaped stopper grooves 62 may be uniformly distributed in the circumferential direction of the disc hub 51 and the circumferential direction of the second damping disc 32, respectively.

The predetermined range may be, for example, not more than 40 degrees.

As shown in fig. 2 and 3, the first damper disk 31 and the second damper disk 32 may be mounted as a damper disk unit by a damper disk rivet 30a, and the axis of the damper disk rivet 30a may be in the axial direction of the driven disk assembly 1. A mounting space is formed between the first damping disk 31 and the second damping disk 32 in the axial direction of the driven disk assembly 1, and both the spiral spring 40 and the hub disk 51 of the hub 50 can be mounted in this mounting space.

Specifically, in the axial direction of the driven disk assembly 1, there may be mounted in this mounting space in this order: spiral spring 40, hub 51 and support ring 70. Support ring 70 supports hub plate 51 to second damping plate 32, and spiral spring 40 occupies the entire space between one axial side of hub plate 51 and the other axial side of first damping plate 31 in the axial direction of driven plate assembly 1, i.e., spiral spring 40 is supported on one axial side of hub plate 51 and the other axial side of first damping plate 31.

Therefore, the driven disc assembly 1 is high in axial space utilization rate and good in compactness.

The radially outer end (the other end) of the spiral spring 40 may be mounted to a portion of the damper disc rivet 30a between the first damper disc 31 and the second damper disc 32, and particularly, may be a portion between the first damper disc 31 and the hub 51.

Preferably, the radially outer end of the spiral spring 40 may be hooked to the damper disc rivet 30a by a V-hook.

In the present embodiment, the number of the spiral springs 40 may be two, and the two spiral springs 40 are arranged along the axial direction of the driven plate assembly 1. The number of the damping disk rivets 30a may be two, the first and second damping disks 31 and 32 may each have two damping disk rivet holes 30b, and the two damping disk rivet holes 30b are arranged at an interval of 180 degrees in the circumferential direction of the first and second damping disks 31 and 32.

The two spiral springs 40 are mounted at their radially outer ends to the two damping plate rivets 30a, respectively, i.e., the two spiral springs 40 are distributed at 180 degrees apart along the circumferential direction of the hub 50/the circumferential direction of the first damping plate 31, and the two spiral springs 40 can uniformly bear torque without occupying excessive axial space.

In another embodiment, as shown in fig. 7, the number of spiral springs 40 may be three, and three spiral springs 40 are arranged along the axial direction of driven disk assembly 1. The number of the damping disk rivets 30a may be three, the first and second damping disks 31 and 32 may each have three damping disk rivet holes 30b, and the three damping disk rivet holes 30b are arranged at intervals of 120 degrees in the circumferential direction of the first and second damping disks 31 and 32.

The radially outer ends of the three flat spiral springs 40 are respectively mounted to the three damping plate rivets 30a, i.e., the three flat spiral springs 40 are uniformly distributed along the circumferential direction of the hub 50/the circumferential direction of the first damping plate 31.

It should be understood that fig. 7 is primarily intended to schematically illustrate the arrangement of the three flat spiral springs 40, thereby omitting details of other components.

As shown in fig. 8, the torque T of the spiral spring 40 is proportional to the deformation P.

The following beneficial effects can be obtained by adopting the driven disc assembly 1 provided by the invention:

the spiral spring 40 has a smaller spring rate than a conventional cylindrical coil spring, and the spiral spring 40 can obtain a larger rotation angle in the process of transmitting torque, so that the driven plate assembly 1 has higher vibration damping efficiency and better vibration damping effect.

The driven disk assembly 1 has a smaller number of parts, and the driven disk assembly 1 has a reduced mass and a reduced inertia.

Such a driven disk assembly 1 can almost obtain a large rotation angle and a small spring rate similar to those of a dual mass flywheel, thereby obtaining a damping performance similar to that of the dual mass flywheel.

The invention also provides a clutch with the driven plate assembly 1.

It should be understood that the above embodiments are only exemplary and are not intended to limit the present invention. Various modifications and alterations of the above-described embodiments may be made by those skilled in the art in light of the teachings of the present invention without departing from the scope thereof.

(1) It should be understood that when there are a plurality of flat spiral springs 40, the plurality of flat spiral springs 40 should be mounted in a pattern that enables torque to be transmitted between the damping plate and the hub 50.

(2) The spiral spring 40 may also be mounted on the other axial side of the hub core 52 for transmitting torque between the second damping plate 32 and the hub 50, and of course, the spiral spring 40 may also be mounted on both axial sides of the hub core 52 for transmitting torque between the second damping plate 32 and the hub 50, and between the first damping plate 31 and the hub 50.

(3) The spiral springs 40 may be four, and when the spiral springs 40 are two to four, each spiral spring 40 can uniformly bear the torque without occupying too much axial space.

(4) The spiral spring 40 may be a heat-treated I-stage steel strip, and the spiral spring 40 has a thickness direction along its radial direction and a width direction along its axial direction.

(5) The spiral spring 40 may have a thickness of, for example, 3mm, a width of, for example, 10mm, and a tensile strength of, for example, 1600N/mm²。

(6) In other embodiments of the present invention, other types of wrap springs may be used instead of flat wrap springs, such as frusto-conical wrap springs.

(7) In other embodiments of the present invention, one end of the spiral spring 40 may be mounted to the hub 51 and the other end may be mounted to the damper disc.