CN113557370A - Clutch driven plate and clutch - Google Patents
Clutch driven plate and clutch Download PDFInfo
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- CN113557370A CN113557370A CN201980093988.1A CN201980093988A CN113557370A CN 113557370 A CN113557370 A CN 113557370A CN 201980093988 A CN201980093988 A CN 201980093988A CN 113557370 A CN113557370 A CN 113557370A
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- 238000013016 damping Methods 0.000 claims abstract description 54
- 230000000149 penetrating effect Effects 0.000 claims description 9
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 11
- 230000005540 biological transmission Effects 0.000 description 13
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention provides a clutch driven disc and a clutch. The clutch driven disc includes two side plates and two hub flanges and a plurality of main damper springs between the two side plates. A first main damping spring of the plurality of main damping springs corresponds only to the first hub flange and a second main damping spring of the plurality of main damping springs corresponds only to the second hub flange such that the first main damping spring and the second main damping spring achieve a series configuration during torque transfer of the clutch driven plate such that a total relative rotational angle of the two hub flanges is equal to a sum of a relative rotational angle of the first hub flange with respect to the side plate and a relative rotational angle of the side plate with respect to the second hub flange. Therefore, the main damping springs of the clutch driven disc are arranged in series to realize two-stage main torsional rigidity, and the main damping springs of the clutch driven disc have larger torsional angle, so that the damping effect on torsional vibration is improved, and the damping effect is improved.
Description
The invention relates to the field of clutches of automobiles, in particular to a clutch driven disc and a clutch comprising the same.
In the prior art, a friction clutch is generally used for torque transmission between a power source (e.g., an engine) and a transmission of an automobile.
As shown in fig. 1a and 1b, a clutch driven plate of a conventional friction clutch has an overall disc shape, and includes a friction cushioning portion 10, a retaining plate 20, a cover plate 30, a hub flange 40, a plurality of main damper springs 50, and a hub core 60.
The friction cushioning portion 10 includes a friction plate and a cushioning portion assembled together by rivets, and the cushioning portion is fixed to the retaining plate 20 by rivets. Both the retainer plate 20 and the cover plate 30 are located radially inward of the friction cushioning portion 10. The retainer plate 20 is fixed with the cover plate 30. In this way, the torque from the friction cushioning portion 10 can be transmitted to both the retainer plate 20 and the cover plate 30.
The hub flange 40 is interposed between the retainer plate 20 and the cover plate 30 in the axial direction a, and is mounted in a space surrounded by the retainer plate 20 and the cover plate 30. A plurality of main damper springs 50 are arranged evenly in the circumferential direction C on a main damper spring mounting portion formed by the retainer plate 20 and the cover plate 30. When the retainer plate 20 and the cover plate 30 are rotated by torque from the friction cushioning portion 10, the retainer plate 20 and the cover plate 30 are rotated relative to the hub flange 40 such that the plurality of main damper springs 50 are compressed, and the plurality of main damper springs 50 damp torsional vibration while performing a function of transmitting torque to the hub flange 40.
The hub core 60 is disposed in the central through hole of the hub flange 40, and the hub core 60 and the hub flange 40 are coupled via spline transmission, so that torque from the friction cushioning portion 10 can be transmitted to a transmission shaft, such as an input shaft of a transmission, via the main damper spring 50, the hub flange 40, and the hub core 60.
In the clutch driven disk having the structure as described above, all the main damper springs 50 are arranged in parallel, and the torsion angle of the main damper springs 50 depends on the rotation angle between the hub flange 40 and the retainer plate 20 and the cover plate 30. Therefore, the main damper spring 50 of the clutch driven disc cannot achieve multi-stage main torsional rigidity, and a poor damping effect is caused because the torsion angle of the main damper spring 50 is generally small.
Disclosure of Invention
The present invention has been made in view of the above-mentioned drawbacks of the prior art. It is an object of the present invention to provide a novel clutch driven plate which enables an improved damping effect compared to existing clutch driven plates. It is another object of the present invention to provide a clutch including the clutch disk described above.
In order to achieve the above object, the present invention adopts the following technical solutions.
The present invention provides a clutch driven disc comprising:
a friction cushioning portion including friction plates arranged along a circumferential direction to be able to receive torque from outside;
a first hub flange fixedly connected to the friction buffer portion and formed with a first through hole penetrating the first hub flange in an axial direction;
a second hub flange that is rotatable in a circumferential direction by a predetermined range with respect to the first hub flange and transmits torque to the outside, the second hub flange being formed with a second through hole that penetrates the second hub flange in an axial direction;
two side plates that are fixed to each other across the first hub flange and the second hub flange, that are rotatable in a circumferential direction by a predetermined range with respect to the first hub flange and the second hub flange, respectively, and that form a main damper spring mounting portion; and
a plurality of main damper springs that are distributed along a circumferential direction and are respectively received and mounted in the corresponding main damper spring mounting portions,
wherein the first through hole and the second through hole are completely staggered in a circumferential direction, and a length of the first through hole is substantially equal to a length of a first main damping spring of the plurality of main damping springs, and a length of the second through hole is substantially equal to a length of a second main damping spring of the plurality of main damping springs, the first main damping spring being mounted to the first through hole and the second main damping spring being mounted to the second through hole such that a relative rotational angle of the first hub flange with respect to the second hub flange is equal to a sum of a relative rotational angle of the first hub flange with respect to the two side plates and a relative rotational angle of the two side plates with respect to the second hub flange.
Preferably, the first hub flange is further formed with a third through hole corresponding to the second through hole and penetrating the first hub flange in the axial direction, and a length of the third through hole is greater than a length of the second main damping spring and a length of the second through hole.
More preferably, the second hub flange includes a cutaway area that avoids the first main damping spring and the first through hole.
More preferably, the clutch driven plate includes a plurality of stopper fixing pins passing through the third through holes and the cutout regions to achieve a spacing between the first hub flange and the second hub flange,
a rotation angle of the first hub flange with respect to the side plate is defined by a circumferential side wall of the first hub flange for forming the third through hole cooperating with the stopper fixing pin, and a rotation angle of the second hub flange with respect to the side plate is defined by a circumferential side wall of the second hub flange cooperating with the stopper fixing pin.
More preferably, the main damper spring mounting portion includes a window hole corresponding to each of the main damper springs, which penetrates the side plate in the axial direction, and the length of the window hole is substantially equal to the length of the corresponding main damper spring, so that the position of the corresponding main damper spring can be defined by the peripheral edge of the window hole.
More preferably, the clutch driven plate further includes a hub core formed with an inner spline and an outer spline, the hub core being mounted to the central through hole of the second hub flange and capable of spline-transmitting with the second hub flange via the outer spline, and the hub core capable of spline-transmitting with a transmission shaft via the inner spline.
More preferably, the hub core is rotatable relative to the second hub flange in a circumferential direction for a predetermined range, and
the clutch driven plate further includes a pre-damper spring holder fixedly mounted to the hub core and a plurality of pre-damper springs mounted to the pre-damper spring holder such that the pre-damper springs are compressible when the hub core rotates relative to the second hub flange.
More preferably, the pre-damper spring retainer includes a disc-shaped body and a pre-damper spring mounting portion formed on the disc-shaped body, a portion of the disc-shaped body being interposed between the first hub flange and the second hub flange in the axial direction.
More preferably, the two side plates include a first side plate located on one axial side of the first hub flange and a second side plate located on the other axial side of the second hub flange,
the clutch driven plate further includes a first friction disk disposed between the first side plate and the first hub flange, a second friction disk disposed between the second side plate and the second hub flange, and a third friction disk disposed between the second side plate and a pre-damper spring retainer of the clutch driven plate, and
the clutch driven disc further comprises a first diaphragm spring, one end of the first diaphragm spring abuts against the first side plate, the other end of the first diaphragm spring abuts against the first friction disc, one end of the second diaphragm spring abuts against the second side plate, the other end of the second diaphragm spring abuts against the second friction disc, and one end of the third diaphragm spring abuts against the second side plate, and the other end of the third diaphragm spring abuts against the third friction disc.
The invention provides a clutch comprising a clutch driven plate according to any one of the above technical aspects.
By adopting the technical scheme, the invention provides a novel clutch driven disc and a clutch comprising the same. The clutch driven disc comprises two side plates, two disc hub flanges and a plurality of main damping springs, wherein the two disc hub flanges are arranged between the two side plates, the friction buffering part is fixedly arranged on one disc hub flange, and the other disc hub flange can be in transmission connection with a transmission shaft such as an input shaft of a transmission. A first main damper spring of the plurality of main damper springs corresponds only to the first hub flange and a second main damper spring of the plurality of main damper springs corresponds only to the second hub flange, such that the first main damper spring and the second main damper spring realize a series arrangement during torque transmission of the clutch disk, such that a total relative rotational angle of the two hub flanges is equal to a sum of a relative rotational angle of the first hub flange with respect to the side plate and a relative rotational angle of the side plate with respect to the second hub flange (which may also be said to be a sum of compression angles of two portions of the main damper springs in series).
Thus, on the one hand, the main damping springs of the clutch driven disc according to the present invention are arranged in series, so that two stages of main torsional rigidity can be achieved, and further, the damping effect on torsional vibration is improved, thereby improving the damping effect. On the other hand, compared with the torsion angle of the main damping spring in the prior art, the torsion angle of the main damping spring of the clutch driven disc is larger, so that the damping effect on torsional vibration is further improved, and the damping effect is further improved.
FIG. 1a is a schematic front view showing halves of a clutch driven plate according to the prior art; fig. 1b is a cross-sectional schematic view including a center axis, taken in an axial direction, showing the clutch driven plate in fig. 1 a.
FIG. 2a is a schematic front view illustrating a clutch driven plate according to an embodiment of the present invention; FIG. 2b is a cross-sectional schematic view including a central axis taken along line S-S showing the clutch driven disk in FIG. 2 a; FIG. 2c is an enlarged schematic view illustrating the region S1 in FIG. 2 b; FIG. 2d is an enlarged schematic view illustrating the region S2 in FIG. 2 b; FIG. 2e is an enlarged schematic view illustrating the region S3 in FIG. 2 b; fig. 2f is a schematic diagram showing an exploded construction of the clutch driven plate of fig. 2 a.
Fig. 3a to 3c are explanatory diagrams for explaining various states of the clutch driven plate in fig. 2a, in which fig. 3a shows an initial state of the clutch driven plate, fig. 3b shows an operation state in which the clutch driven plate rotates toward a driving side, fig. 3c shows an operation state in which the clutch driven plate rotates toward a dragging side, and some components are omitted in fig. 3a to 3c for clarity of illustration.
Fig. 4 is a graph showing the angle of rotation of the hub core of the clutch driven disc in fig. 2a relative to the first disc hub flange and the corresponding torque.
Description of the reference numerals
10 friction cushioning portion 20 retaining plate 30 cover plate 40 hub flange 50 main damper spring 60 hub core
1 friction buffer 11 friction plate 12 friction plate rivet 13 buffer 21 first hub flange 21h1 first through hole 21h2 third through hole 22 second hub flange 221 body 222 lug 22h1 second through hole 22h2 center through hole 31 first side plate 31h first window 32 second side plate 32h second window 33 stop fixed pin 41 first main damping spring 42 second main damping spring 5 hub core 6 predamperometric spring holder 61 plate body 62 predamperometric spring holder 7 predamperometric spring 81 first friction plate 82 second friction plate 83 third friction plate 91 first diaphragm spring 92 second diaphragm spring 93 third diaphragm spring 93
R is radial A to axial C.
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.
In the present invention, axial, radial and circumferential refer to axial, radial and circumferential directions of the clutch driven plate, respectively, unless otherwise specified; one axial side refers to the left side in fig. 2b to 2e, the other axial side refers to the right side in fig. 2b to 2 e; the radially outer side refers to a side distant from the central axis in the radial direction (upper side in fig. 2c to 2 d), and the radially inner side refers to a side close to the central axis in the radial direction (lower side in fig. 2c to 2 d).
As shown in fig. 2a to 2f, the clutch driven plate according to the embodiment of the present invention has a disk shape as a whole and includes one friction cushioning portion 1, two hub flanges (a first hub flange 21 and a second hub flange 22), two side plates (a first side plate 31 and a second side plate 32), a stopper fixing pin 33, a plurality of (four in the present embodiment) main damper springs 41 and 42, a hub core 5, a pre-damper spring holder 6, a plurality of (two in the present embodiment) pre-damper springs 7, friction disks (a first friction disk 81, a second friction disk 82, and a third friction disk 83), and diaphragm springs (a first diaphragm spring 91, a second diaphragm spring 92, and a third diaphragm spring 93) assembled to each other.
Specifically, in the present embodiment, the friction cushioning portion 1 includes a friction plate 11 and a cushioning portion 13 assembled together by friction plate rivets 12, and the cushioning portion 13 is fixed to the first hub flange 21 by rivets. The buffer 13 may be, for example, a corrugated sheet. Thus, torque from a drive source such as an engine can be smoothly transmitted to the first hub flange 21 via the friction cushioning portion 1.
Further, in the present embodiment, both hub flanges are located radially inward of the friction cushioning portion 1 and include a first hub flange 21 and a second hub flange 22 spaced apart from each other in the axial direction a, the second hub flange 22 being rotatable relative to the first hub flange 21 in the circumferential direction C over a predetermined range.
As shown in fig. 2f, the first hub flange 21 has a disk shape as a whole and can receive torque from the friction cushioning portion 1. The first hub flange 21 is formed with two first through holes 21h1 penetrating the first hub flange 21 in the axial direction a, and the length of each of the first through holes 21h1 is substantially equal to the length of the first main damper spring 41. After the clutch is mounted, two first main damper springs 41 among the four main damper springs are mounted in the two first through holes 21h1, respectively.
In addition, the first hub flange 21 is also formed with two third through holes 21h2 that correspond to the second through holes 22h1 of the second hub flange 22 described below and penetrate the first hub flange 21 in the axial direction a. In the circumferential direction C, the third through holes 21h2 are alternately arranged with the first through holes 21h 1; the third through hole 21h2 is located at substantially the same position as the first through hole 21h1 in the radial direction R. Each of the third through holes 21h2 has an arc shape extending in the circumferential direction C and the length of the third through hole 21h2 is much greater than the length of the second main damper spring 42 and the length of the second through hole 22h 1.
Thus, the first main damping spring 41 is compressed during the rotation of the first hub flange 21 with the two side plates 31, 32 via the first main damping spring 41, and the first hub flange 21 is relatively rotated with respect to the two side plates 31, 32. In this process, the third through hole 21h2 ensures that the second hub flange 22 does not affect the rotation of the first hub flange 21 and the compression of the first main damping spring 41.
As shown in fig. 2f, the second hub flange 22 includes a main body portion 221 and two lugs 222 protruding radially outward from the main body portion 221, and the two lugs 222 are formed integrally with the main body portion 221. Further, in the circumferential direction C, a cutout region is formed in a region around the main body portion 221 between the two lugs 222, the cutout region corresponding to the first main damper spring 41 and the first through hole 22h 1. The two lugs 222 are arranged symmetrically with respect to the central axis of the clutch driven plate.
Each of the lugs 222 is formed with a second through hole 22h1 passing through the second hub flange 22 in the axial direction a. The length of the second through hole 22h1 is substantially equal to the length of the second main damper spring 42, and two second main damper springs 42, excluding the first main damper spring 41, of the four main damper springs are respectively fitted into the two second through holes 22h 1.
Further, a central through hole 22h2 penetrating the second hub flange 22 in the axial direction a is formed in a central portion of the second hub flange 22, and an internal spline for mating with an external spline of the hub core 5 is formed in the central through hole 22h2 of the second hub flange 22.
As shown in fig. 3a, in the initial state after the clutch is completely mounted, the first through hole 21h1 is completely displaced from the second through hole 22h1 in the circumferential direction C. In the initial state, the first main damper spring 41 and the first through hole 21h1 of the first hub flange 21 correspond to the cutaway region of the second hub flange 22, and the second main damper spring 42 and the second through hole 22h1 of the second hub flange 22 correspond to the third through hole 21h2 of the first hub flange 21. In addition, since both the first through holes 21h1 and the second through holes 22h1 are unevenly distributed in the circumferential direction C as a whole, the rotational angle of the hub core 5 with respect to the first disc hub flange 21 during rotation of the clutch driven disc toward the driving side and the trailing side is different.
Further, in the present embodiment, the two side plates 31, 32 are fixed to each other via the first hub flange 21 and the second hub flange 22 by the stopper fixing pins 33 so that the two side plates 31, 32 can rotate together. The two side plates 31, 32 are integrally rotatable in the circumferential direction C by a predetermined range with respect to the first and second hub flanges 21, 22, respectively, and the two side plates 31, 32 form a main damper spring mounting portion to define the positions of the main damper springs 41, 42.
More specifically, the two side plates 31, 32 include a first side plate 31 on one axial side and a second side plate 32 on the other axial side. The first side plate 31 includes four first windows 31h corresponding to the respective main damper springs 41, 42 penetrating the first side plate 31 in the axial direction a, the second side plate 32 includes four second windows 32h corresponding to the respective main damper springs 41, 42 penetrating the second side plate 32 in the axial direction a, and the length of each first window 31h and the length of each second window 32h are substantially equal to the length of the main damper springs 41, 42, so that the positions of the respective main damper springs 41, 42 can be defined by the peripheral edges of the first windows 31h and the peripheral edges of the second windows 32 h. Thus, the position of the first main damper spring 41 in the axial direction a, the radial direction R, and the circumferential direction C can be defined by the main damper spring mounting portion in cooperation with the first through hole 21h1, and the position of the second main damper spring 42 in the axial direction a, the radial direction R, and the circumferential direction C can be defined by the main damper spring mounting portion in cooperation with the second through hole 22h 1.
The stopper fixing pins 33 pass through the third through holes 21h2 of the first hub flange 21 and the cutaway regions of the second hub flange 22 to fix the first hub flange 21 and the second hub flange 22. Further, the stopper fixing pin 33 is provided at a position in the circumferential direction C that satisfies a function of limiting the rotation angle of the first and second hub flanges 21 and 22 in the circumferential direction C. Specifically, the rotational angle of the first hub flange 21 with respect to the side plates 31, 32 is defined by the circumferential side wall of the first hub flange 21 for forming the third through hole 21h2 cooperating with the stopper fixing pin 33, and the rotational angle of the side plates 31, 32 with respect to the second hub flange 22 is defined by the circumferential side wall of the second hub flange 22 cooperating with the stopper fixing pin 33.
Further, in the present embodiment, all the main damper springs 41, 42 are linear cylindrical coil springs and may have different spring rates. As described above, the four main damper springs 41, 42 are unevenly distributed along the circumferential direction C, but are each accommodated in the corresponding main damper spring mounting portion. The first main damper spring 41 and the second main damper spring 42 are alternately arranged in the circumferential direction C.
Further, the hub core 5 is formed with an internal spline and an external spline, the hub core 5 can be spline-drive coupled with the internal spline of the second hub flange 22 by the external spline thereof, and the hub core 5 can be spline-drive coupled with a drive shaft such as an input shaft of a transmission by the internal spline thereof. Via the hub core 5, the second hub flange 22 can be drivingly coupled with a drive shaft, for example an input shaft of a transmission. In addition, in the initial state shown in fig. 3a, the hub core 5 is able to rotate in the circumferential direction C for a predetermined range relative to the second hub flange 22, so that the pre-damper spring 7 performs a damping function during this relative rotation.
By adopting the above technical solution, in the process of transmitting the torque from the friction cushioning portion 1 in the following order: the friction cushioning portion 1 → the first hub flange 21 → the first main damper spring 41 → the side plates 31, 32 → the second main damper spring 42 → the second hub flange 22 → the hub core 5, and the first main damper spring 41 and the second main damper spring 42 are arranged in series in the above-described torque transmission process, so that in the operating state shown in fig. 3b and 3c, the total relative rotational angle of the two hub flanges 21, 22 is equal to the sum of the relative rotational angle of the first hub flange 21 with respect to the side plates 31, 32 and the relative rotational angle of the side plates 31, 32 with respect to the second hub flange 22 (which can also be said to be the sum of the compression angles of the two portions of the main damper springs 41, 42 in series). Thus, the vibration damping effect of the clutch driven plate can be further improved.
Further, in the present embodiment, the pre-damper spring holder 6 includes a disc-shaped main body 61 and a pre-damper spring mounting portion 62 provided to the disc-shaped main body 61. The radially outer portion of the disc-shaped body 61 is interposed between the first hub flange 21 and the second hub flange 22 in the axial direction a, thereby restraining the first hub flange 21 and the second hub flange 22 in the axial direction a. Two pre-damper spring mounts 62 are arranged 180 degrees apart in the circumferential direction C. The pre-damper spring holder 6 is fixedly mounted to the hub core 5. Two pre-damper springs 7 are mounted to the two pre-damper spring mounts 62 of the pre-damper spring holder 6 and are located in the central through hole 22h2 of the second hub flange 22 such that the pre-damper springs 7 are compressed by the circumferential side wall of the second hub flange 22 forming the central through hole 22h2 when the second hub flange 22 rotates relative to the hub core 5. Both pre-damper springs 7 are cylindrical coil springs, and the spring rate of the pre-damper springs 7 is smaller than that of the main damper springs 41, 42.
Further, in the present embodiment, the friction disks of the clutch driven disk include a first friction disk 81 disposed between the first side plate 31 and the first hub flange 21, a second friction disk 82 disposed between the second side plate 32 and the second hub flange 22, and a third friction disk 83 disposed between the second side plate 32 and the pre-damper spring holder 6. The corresponding diaphragm springs include a first diaphragm spring 91 having one end abutting against the first side plate 31 and the other end abutting against the first friction disk 81, a second diaphragm spring 92 having one end abutting against the second side plate 32 and the other end abutting against the second friction disk 82, and a third diaphragm spring 93 having one end abutting against the second side plate 32 and the other end abutting against the third friction disk 83. Thus, the first diaphragm spring 91 presses the first friction disk 81 against the first hub flange 21, the second diaphragm spring 92 presses the second friction disk 82 against the second hub flange 22, and the third diaphragm spring 93 presses the third friction disk 83 against the pre-damper spring holder 6.
More specifically, the first friction disk 81 is annular in shape as a whole and includes a first friction disk radial portion extending in the radial direction R and a first friction disk axial portion extending from a radially inner end of the first friction disk radial portion toward one axial side. The first friction disc radial portion is pressed against the first hub flange 21 from the axial one side via the first diaphragm spring 91. A first friction disc axial portion is disposed on the hub core 5 from the radially outer side, and the first friction disc axial portion abuts against the first hub flange 21 from one axial side and the first side plate 31 from the other axial side.
The second friction disk 82 is annular in shape overall and extends in the radial direction R. The second friction disk 82 is pressed against the second hub flange 22 from the other axial side via the second diaphragm spring 92.
The third friction disk 83 is annular in shape as a whole and includes a third friction disk radial portion extending in the radial direction R and a third friction disk axial portion extending from a radially inner end of the third friction disk radial portion toward the other axial side. The third friction disk radial portion is pressed against the pre-damper spring holder 6 from the other axial side via the third diaphragm spring 93. A third friction disk axial portion is placed on the hub 5 from the radially outer side, and the third friction disk axial portion abuts on the pre-damper spring holder 6 from the other axial side and abuts on the second side plate 32 from the one axial side.
In this way, by the first, second, and third diaphragm springs 91, 92, and 93 engaging with the first, second, and third friction disks 81, 82, and 83, respectively, not only the axial positions of the two side plates 31 and 32, the two hub flanges 21 and 22, and the pre-damper spring holder 6 can be ensured, but also a damping action can be provided.
In addition to providing the clutch driven plate having the above-described structure, the present invention also provides a clutch including the clutch driven plate.
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.
(i) Although it is described in the above embodiment that the first hub flange 21 forms the first through hole 21h1 and the third through hole 21h2 and the second hub flange 22 forms the second through hole 22h1, the present invention is not limited thereto. In the case where the second hub flange 22 is formed in a disc shape as a whole, similarly to the case where the first hub flange 21 is formed with the third through hole 21h2, it is also possible to form the second hub flange 22 with a fourth through hole corresponding to the first through hole 21h1 and penetrating the second hub flange 22 in the axial direction a, the length of the fourth through hole being larger than the length of the first main damper spring 41.
(ii) Although the total number of the main damper springs 41, 42 is four in the above embodiment, the present invention is not limited thereto. The total number of main damping springs 41, 42 may also be six, etc.
The main damper springs 41 and 42 may be not only linear coil springs as described above but also arc-shaped coil springs.
When the main damper springs 41, 42 are linear coil springs, it is preferable that each of the main damper springs 41, 42 be housed in the main 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 clutch driven plate; when the main damper springs 41, 42 are arc-shaped coil springs, it is preferable that the main damper springs 41, 42 be accommodated in the main damper spring mounting portion as described above such that the longitudinal direction thereof coincides with the circumferential direction C of the clutch driven plate.
Further, the first main damper spring 41 and the second main damper spring 42 may be different in each of type, size, and spring rate.
(iii) Fig. 3b shows an operating state after the first hub flange 21 has rotated in a counterclockwise direction (driving side/driving direction) with respect to the hub core 5 with respect to the initial state of the clutch driven disc shown in fig. 3a, in which the first hub flange 21 has rotated by an angle α 1 (compression angle of the first main damping spring 41 on the driving side) with respect to the side plates 31, 32 and the side plates 31, 32 have rotated by an angle β 1 (compression angle of the second main damping spring 42 on the driving side) with respect to the second hub flange 22 in a direction indicated by an arc-shaped single arrow in fig. 3 b; fig. 3c shows a state after the first hub flange 21 is rotated in the clockwise direction (trailing side/trailing direction) with respect to the hub core 5, in which the first hub flange 21 is rotated by an angle α 2 (compression angle on the trailing side of the first main damper spring 41) with respect to the side plates 31, 32, and the side plates 31, 32 are rotated by an angle β 2 (compression angle on the trailing side of the second main damper spring 42) with respect to the second hub flange 22, in the direction indicated by the arc-shaped single arrows in fig. 3 c.
(iv) As shown in fig. 4, it is apparent that the pre-damper spring 7 can achieve one stage of pre-damper spring stiffness on the drive side, and the main damper springs 41, 42 can achieve two stages of main damper spring stiffness on the drive side; and the sum of the two-stage rotation angles of the main damping springs 41 and 42 on the driving side is 38 deg., which is much larger than the rotation angle of the main damping spring on the driving side of the clutch driven plate of the prior art, thereby improving the damping effect of the clutch driven plate. Similarly, the clutch disk according to the invention also improves the damping effect on the trailing side.
Claims (10)
- A clutch driven plate, comprising:a friction cushioning portion (1) including friction plates (11) arranged along a circumferential direction (C) to be able to receive torque from outside;a first hub flange (21) fixedly connected to the friction cushioning portion (1) and formed with a first through hole (21h1) penetrating the first hub flange (21) in an axial direction (A);a second hub flange (22) that is rotatable in a circumferential direction (C) for a predetermined range relative to the first hub flange (21) and that transmits torque to the outside, the second hub flange (22) being formed with a second through hole (22h1) that penetrates the second hub flange (22) in an axial direction (A);two side plates (31, 32), the two side plates (31, 32) being fixed to each other across the first hub flange (21) and the second hub flange (22), the two side plates (31, 32) being rotatable in a circumferential direction (C) by a predetermined range with respect to the first hub flange (21) and the second hub flange (22), respectively, and the two side plates (31, 32) forming a main damper spring mounting portion; anda plurality of main damper springs (41, 42), the plurality of main damper springs (41, 42) being distributed along a circumferential direction (C) and being respectively received and mounted in the corresponding main damper spring mounting portions,wherein the first through hole (21h1) and the second through hole (22h1) are completely staggered in the circumferential direction (C), and a length of the first through hole (21h1) is substantially equal to a length of a first main damping spring (41) of the plurality of main damping springs, a length of the second through hole (22h1) is substantially equal to a length of a second main damping spring (42) of the plurality of main damping springs, the first main damping spring (41) is mounted to the first through hole (21h1) and the second main damping spring (42) is mounted to the second through hole (22h1), such that the relative rotation angle of the first hub flange (21) with respect to the second hub flange (22) is equal to the sum of the relative rotation angle of the first hub flange (21) with respect to the two side plates (31, 32) and the relative rotation angle of the two side plates (31, 32) with respect to the second hub flange (22).
- The clutch driven disk according to claim 1,the first hub flange (21) is further formed with a third through hole (21h2) corresponding to the second through hole (22h1) and penetrating the first hub flange (21) in an axial direction (a), and a length of the third through hole (21h2) is greater than a length of the second main damping spring (42) and a length of the second through hole (22h 1).
- The clutch driven disc according to claim 1 or 2, characterized in that the second hub flange (22) includes a cutout region that avoids the first main damper spring (41) and the first through hole (21h 1).
- The clutch driven disc according to claim 3, characterized in that the clutch driven disc includes a plurality of stopper fixing pins (33), the plurality of stopper fixing pins (33) passing through the third through holes (21h2) and the cutaway region to achieve a limit between the first hub flange (21) and the second hub flange (22),the rotational angle of the first hub flange (21) with respect to the side plates (31, 32) is defined by the circumferential side wall of the first hub flange (21) for forming the third through hole (21h2) cooperating with the stopper fixing pin (33), and the rotational angle of the second hub flange (22) with respect to the side plates (31, 32) is defined by the circumferential side wall of the second hub flange (22) cooperating with the stopper fixing pin (33).
- A clutch driven disc according to any one of claims 1 to 4, characterized in that the main damping spring mounting portion comprises a window (31h, 32h) corresponding to each main damping spring (41, 42) passing through the side plate (31, 32) in the axial direction (A), the length of the window (31h, 32h) being substantially equal to the length of the corresponding main damping spring (41, 42), so that the position of the corresponding main damping spring (41, 42) can be defined by the peripheral edge of the window (31h, 32 h).
- The clutch driven disc according to any one of claims 1 to 5, characterized in that the clutch driven disc further comprises a hub core (5), the hub core (5) being formed with an internal spline and an external spline, the hub core (5) being mounted to a central through hole (22h2) of the second hub flange (22) and being spline-drivable with the second hub flange (22) by the external spline, the hub core (5) being spline-drivable with a drive shaft by the internal spline.
- A clutch driven disc according to claim 6, characterized in that the hub core (5) is rotatable in the circumferential direction (C) for a predetermined range relative to the second disc hub flange (22), andthe clutch driven plate further comprises a pre-damper spring holder (6) and a plurality of pre-damper springs (7), the pre-damper spring holder (6) is fixedly mounted to the hub core (5), and the plurality of pre-damper springs (7) are mounted to the pre-damper spring holder (6) such that the pre-damper springs (7) can be compressed when the hub core (5) rotates relative to the second hub flange (22).
- The clutch driven disc according to claim 7, characterized in that the pre-damper spring retainer (6) includes a disc-shaped body (61) and a pre-damper spring mounting portion (62) formed at the disc-shaped body (61), a portion of the disc-shaped body (61) being interposed between the first hub flange (21) and the second hub flange (22) in the axial direction (A).
- The clutch driven disc according to any one of claims 1 to 8, characterized in that the two side plates (31, 32) include a first side plate (31) located on one axial side of the first hub flange (21) and a second side plate (32) located on the other axial side of the second hub flange (22),the clutch driven disc further comprises a first friction disc (81) arranged between the first side plate (31) and the first hub flange (21), a second friction disc (82) arranged between the second side plate (32) and the second hub flange (22), and a third friction disc (83) arranged between the second side plate (32) and a pre-damper spring retainer (6) of the clutch driven disc, andthe clutch driven plate further comprises a first diaphragm spring (91) with one end abutting against the first side plate (31) and the other end abutting against the first friction disc (81), a second diaphragm spring (92) with one end abutting against the second side plate (32) and the other end abutting against the second friction disc (82), and a third diaphragm spring (93) with one end abutting against the second side plate (32) and the other end abutting against the third friction disc (83).
- A clutch comprising the clutch disk of any one of claims 1 to 9.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/CN2019/094215 WO2021000223A1 (en) | 2019-07-01 | 2019-07-01 | Clutch driven disc and clutch |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113557370A true CN113557370A (en) | 2021-10-26 |
| CN113557370B CN113557370B (en) | 2023-07-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980093988.1A Active CN113557370B (en) | 2019-07-01 | 2019-07-01 | Clutch driven disc and clutch |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN113557370B (en) |
| WO (1) | WO2021000223A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113969945B (en) * | 2021-12-28 | 2022-04-22 | 浙江铁流离合器股份有限公司 | Four-stage vibration damping clutch |
| CN114932390B (en) * | 2022-04-27 | 2024-03-29 | 浙江华弈汽车零部件科技有限公司 | Intelligent assembly equipment for automobile clutch spring |
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| WO2021000223A1 (en) | 2021-01-07 |
| CN113557370B (en) | 2023-07-18 |
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