CN113557370B - Clutch driven disc and clutch - Google Patents
Clutch driven disc and clutch Download PDFInfo
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- CN113557370B CN113557370B CN201980093988.1A CN201980093988A CN113557370B CN 113557370 B CN113557370 B CN 113557370B CN 201980093988 A CN201980093988 A CN 201980093988A CN 113557370 B CN113557370 B CN 113557370B
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- 230000005540 biological transmission Effects 0.000 claims description 15
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- 238000007906 compression Methods 0.000 description 7
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 1
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- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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Classifications
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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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention provides a clutch driven plate and a clutch. The clutch driven plate includes two side plates, two hub flanges between the two side plates, and a plurality of primary damper springs. 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 corresponds only to the second hub flange such that the first main damper spring and the second main damper spring are configured in series during torque transfer from 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. In this way, the main damping springs of the clutch driven plate are arranged in series to realize two-stage main torsional rigidity, and the torsion angle of the main damping springs of the clutch driven plate is larger, so that the damping effect on torsional vibration is improved, and the damping effect is improved.
Description
Technical Field
The present invention relates to the field of clutches for automobiles, and more particularly to a clutch driven plate and a clutch including the same.
Background
In the prior art, friction clutches are commonly used for torque transfer 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, which has a disk shape as a whole, includes a friction buffer 10, a holding 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 10 includes friction plates assembled together by rivets and a cushioning portion fixed to the holding plate 20 by rivets. Both the holding plate 20 and the cover plate 30 are located radially inward of the friction cushioning portion 10. The holding plate 20 is fixed with the cover plate 30. In this way, torque from the friction cushioning portion 10 can be transmitted to both the holding plate 20 and the cover plate 30.
Hub flange 40 is interposed between retainer plate 20 and cover plate 30 in axial direction a, and is mounted in the space enclosed by retainer plate 20 and cover plate 30. The plurality of main damper springs 50 are uniformly arranged in the circumferential direction C at the main damper spring mounting portion formed by the holding plate 20 and the cover plate 30. When the holding plate 20 and the cover plate 30 are rotated by the torque from the friction cushioning member 10, the holding plate 20 and the cover plate 30 are rotated with respect to the hub flange 40 such that the plurality of main damper springs 50 are compressed, and the plurality of main damper springs 50 dampen the torsional vibration while performing the function of transmitting the 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 member 10 can be transmitted to a transmission shaft such as an input shaft of a transmission via the main damper springs 50, the hub flange 40 and the hub core 60.
In the clutch driven plate 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 retaining plate 20 and the cover plate 30. Therefore, the main damper spring 50 of the clutch driven plate cannot achieve multi-stage main torsional rigidity, and since the torsion angle of the main damper spring 50 is generally small, the damper effect is poor.
Disclosure of Invention
The present invention has been made in view of the above-mentioned drawbacks of the prior art. An object of the present invention is to provide a novel clutch driven plate which can improve the vibration reduction effect as compared with the existing clutch driven plate. Another object of the present invention is to provide a clutch comprising the clutch driven plate described above.
In order to achieve the above object, the present invention adopts the following technical scheme.
The present invention provides a clutch driven plate comprising:
a friction cushioning portion including friction plates arranged along a circumferential direction so as to be able to receive torque from the 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 rotatable in a predetermined range in a circumferential direction with respect to the first hub flange and for transmitting torque to the outside, the second hub flange being formed with a second through hole penetrating the second hub flange in an axial direction;
two side plates fixed to each other with the first hub flange and the second hub flange interposed therebetween, the two side plates being capable of performing a predetermined range of rotation in a circumferential direction with respect to the first hub flange and the second hub flange, respectively, and the two side plates forming a main damper spring mounting portion; and
a plurality of main damper springs distributed along a circumferential direction and respectively accommodated and mounted in the corresponding main damper spring mounting portions,
wherein the first through hole and the second through hole are completely staggered in the circumferential direction, and the length of the first through hole is approximately equal to the length of a first main damping spring of the plurality of main damping springs, and the length of the second through hole is approximately equal to the 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 the relative rotation angle of the first hub flange with respect to the second hub flange is equal to the sum of the relative rotation angle of the first hub flange with respect to the two side plates and the relative rotation 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 an axial direction, and a length of the third through hole is greater than a length of the second main damper spring and a length of the second through hole.
More preferably, the second hub flange includes a cutout region that avoids the first main damper spring and the first through hole.
More preferably, the clutch driven plate includes a plurality of stopper fixing pins passing through the third through hole and the cutout region to achieve a restriction between the first hub flange and the second hub flange,
the rotation angle of the first hub flange with respect to the side plate is defined by the circumferential side wall of the first hub flange for forming the third through hole cooperating with the stopper fixing pin, and the rotation angle of the second hub flange with respect to the side plate is defined by the circumferential side wall of the second hub flange cooperating with the stopper fixing pin.
More preferably, the main damping spring mounting portion includes windows corresponding to the respective main damping springs that penetrate the side plates in an axial direction, the windows having a length substantially equal to a length of the respective main damping springs so that positions of the respective main damping springs can be defined by peripheral edges of the windows.
More preferably, the clutch driven disc further includes a hub core formed with an internal spline and an external spline, the hub core being mounted to the central through hole of the second disc hub flange and capable of achieving spline transmission with the second disc hub flange through the external spline, and the hub core being capable of achieving spline transmission with a transmission shaft through the internal spline.
More preferably, the hub core is rotatable in a predetermined range with respect to the second hub flange in a circumferential direction, and
the clutch driven disc further includes a pre-damper spring retainer fixedly mounted to the hub core and a plurality of pre-damper springs mounted to the pre-damper spring retainer such that the pre-damper springs are compressible when the hub core rotates relative to the second disc hub flange.
More preferably, the pre-damper spring holder 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 axially between the first hub flange and the second hub flange.
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 comprises a first friction plate arranged between the first side plate and the first disc hub flange, a second friction plate arranged between the second side plate and the second disc hub flange, and a third friction plate arranged between the second side plate and the pre-damping spring retainer of the clutch driven plate, and
the clutch driven plate further comprises a first diaphragm spring, a second diaphragm spring and a third diaphragm spring, wherein one end of the first diaphragm spring is abutted against the first side plate, the other end of the first diaphragm spring is abutted against the first friction plate, one end of the second diaphragm spring is abutted against the second side plate, the other end of the second diaphragm spring is abutted against the second friction plate, and one end of the third diaphragm spring is abutted against the second side plate, and the other end of the third diaphragm spring is abutted against the third friction plate.
The invention provides a clutch which comprises a clutch driven plate according to any one of the technical schemes.
By adopting the technical scheme, the invention provides a novel clutch driven plate and a clutch comprising the clutch driven plate. The clutch driven plate comprises two side plates, two hub flanges between the two side plates and a plurality of main damping springs, wherein a friction buffer part is fixedly arranged on one hub flange, and the other hub flange can be in transmission connection with a transmission shaft such as an input shaft of a speed changer. 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 corresponds only to the second hub flange, such that the first main damper spring and the second main damper spring are configured in series during torque transfer from the clutch driven plate such that the total relative rotational angle of the two hub flanges is equal to the sum of the relative rotational angle of the first hub flange with respect to the side plate and the relative rotational angle of the side plate with respect to the second hub flange (also known as the sum of the compression angles of the two main damper springs in series).
In this way, on the one hand, the main damping springs of the clutch driven disc are arranged in series, so that two-stage main torsional rigidity can be realized, the damping effect on torsional vibration is further improved, and the damping effect is further improved. 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 plate is larger, so that the damping effect on torsion vibration is further improved, and the damping effect is further improved.
Drawings
FIG. 1a is a schematic front view showing a clutch driven plate half according to the prior art; FIG. 1b is a schematic cross-sectional view including a central axis taken along an axial direction showing the clutch driven plate of 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 schematic cross-sectional view including a central axis taken along line S-S showing the clutch driven plate of FIG. 2 a; fig. 2c is an enlarged schematic view showing the region S1 in fig. 2 b; fig. 2d is an enlarged schematic view showing the region S2 in fig. 2 b; fig. 2e is an enlarged schematic view showing the region S3 in fig. 2 b; fig. 2f is a schematic diagram showing an exploded structure of the clutch disc of fig. 2 a.
Fig. 3a to 3c are explanatory views for explaining various states of the clutch disc in fig. 2a, in which fig. 3a shows an initial state of the clutch disc, fig. 3b shows an operating state in which the clutch disc rotates toward a driving side, fig. 3c shows an operating state in which the clutch disc rotates toward a pulling side, and a part of components are omitted in fig. 3a to 3c for clarity of illustration.
Fig. 4 is a graph showing the rotational angle of the hub core of the clutch driven disc of fig. 2a relative to the first disc hub flange with the corresponding torque.
Description of the reference numerals
10. The friction buffer 20 keeps the plate 30 cover 40, the hub flange 50 and the main damping spring 60 hub core
1. Friction buffer part 11 friction plate rivet 13 first disc hub flange 21 first through hole 21h2 third disc hub flange 221 main body part 222 lug 22 second through hole 22 second window 32 first main damping spring 42 second main damping spring 5 disc main body 62 pre-damping spring 81 second friction disc 83 third diaphragm spring 91 first diaphragm spring 92 second diaphragm spring 93 second diaphragm spring
Rradial A axial C circumferential.
Description of the embodiments
Exemplary embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood that these specific illustrations are for the purpose of illustrating how one skilled in the art may practice the invention, and are not intended to be exhaustive of all of the possible ways of practicing the invention, nor to limit the scope of the invention.
In the present invention, unless otherwise indicated, axial, radial and circumferential refer to the axial, radial and circumferential directions of the clutch driven plate, respectively; axial one side refers to the left side in fig. 2b to 2e, and axial other side refers to the right side in fig. 2b to 2 e; the radially outer side refers to the side radially away from the central axis (upper side in fig. 2c to 2 d), and the radially inner side refers to the side radially close to the central axis (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 buffer 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 5, a pre-damper spring holder 6, a plurality of (two in the present embodiment) pre-damper springs 7, friction plates (a first friction plate 81, a second friction plate 82 and a third friction plate 83), and diaphragm springs (a first diaphragm spring 91, a second diaphragm spring 92 and a third diaphragm spring 93) which are assembled with each other.
Specifically, in the present embodiment, the friction cushioning portion 1 includes the friction plate 11 and the cushioning portion 13 assembled together by the friction plate rivet 12, and the cushioning portion 13 is fixed to the first hub flange 21 by the rivet. The buffer 13 may be, for example, a wave plate. In this way, torque from a drive source such as an engine can be smoothly transmitted to the first hub flange 21 via the friction buffer portion 1.
Further, in the present embodiment, both of the hub flanges are located radially inward of the friction cushioning portion 1 and include the first hub flange 21 and the second hub flange 22 spaced apart from each other in the axial direction a, and the second hub flange 22 is capable of performing a predetermined range of rotation in the circumferential direction C with respect to the first hub flange 21.
As shown in fig. 2f, the first hub flange 21 has a disc shape as a whole and is capable of receiving 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 lengths of the first through holes 21h1 are each substantially equal to the length of the first main damper springs 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.
The first hub flange 21 is further formed with two third through holes 21h2 that pass through the first hub flange 21 in the axial direction a corresponding to second through holes 22h1 of a second hub flange 22 described below. 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 and the first through hole 21h1 are located at substantially the same position in the radial direction R. Each of the third through holes 21h2 has an arc shape extending along the circumferential direction C and the length of the third through hole 21h2 is much longer than the length of the second main damper spring 42 and the length of the second through hole 22h1.
In this way, the first main damper spring 41 is compressed during rotation of the first hub flange 21 via the first main damper spring 41 to the two side plates 31, 32, 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 can ensure that the second hub flange 22 does not affect the rotation of the first hub flange 21 nor the compression of the first main damper 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, the two lugs 222 being 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 22h1. The two lugs 222 are symmetrically disposed about the central axis of the clutch disk.
Each of the lugs 222 is formed with a second through hole 22h1 penetrating 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 other than the first main damper spring 41 among the four main damper springs are respectively installed in the two second through holes 22h1.
In addition, 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 fitting with an external spline of the hub 5 is formed in the second hub flange 22 at the central through hole 22h 2.
As shown in fig. 3a, in the initial state after the clutch is mounted, the first through hole 21h1 and the second through hole 22h1 are completely offset in the circumferential direction C. In the initial state, the first main damper springs 41 and the first through holes 21h1 of the first hub flange 21 correspond to the cutout regions of the second hub flange 22, and the second main damper springs 42 and the second through holes 22h1 of the second hub flange 22 correspond to the third through holes 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 rotation angle of the hub core 5 with respect to the first hub flange 21 is made different in the course of rotation of the clutch driven plate toward the driving side and the pulling side.
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 pin 33 so that the two side plates 31, 32 can rotate together. The two side plates 31, 32 are integrally rotatable in a predetermined range in the circumferential direction C with respect to the first hub flange 21 and the second hub flange 22, respectively, and the two side plates 31, 32 form main damper spring mounting portions to define positions of the main damper springs 41, 42.
More specifically, the two side plates 31, 32 include a first side plate 31 on one side in the axial direction and a second side plate 32 on the other side in the axial direction. 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 the respective first windows 31h and the length of the respective second windows 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. In this way, the positions of the first main damper springs 41 in the axial direction a, the radial direction R, and the circumferential direction C can be defined by the cooperation of the main damper spring mounting portions with the first through holes 21h1, and the positions of the second main damper springs 42 in the axial direction a, the radial direction R, and the circumferential direction C can be defined by the cooperation of the main damper spring mounting portions with the second through holes 22h1.
The stopper fixing pin 33 passes through the third through hole 21h2 of the first hub flange 21 and the cutout region of the second hub flange 22 to fix the first hub flange 21 and the second hub flange 22. Furthermore, the position of the stopper fixing pin 33 provided in the circumferential direction C can satisfy the function of restricting the rotation angle of the first hub flange 21 and the second hub flange 22 in the circumferential direction C. Specifically, the rotation 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 being fitted with the stopper fixing pin 33, and the rotation 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 being fitted 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 housed in the corresponding main damper spring mounting portion. The first main damper springs 41 and the second main damper springs 42 are alternately arranged in the circumferential direction C.
Further, the hub 5 is formed with an internal spline through which the hub 5 can be spline-driven coupled with an internal spline of the second hub flange 22, and an external spline through which the hub 5 can be spline-driven coupled with a drive shaft such as an input shaft of a transmission. Via the hub 5, the second hub flange 22 can be coupled in a driving manner 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 capable of a predetermined range of rotation in the circumferential direction C with respect to the second hub flange 22, so that the pre-damper spring 7 performs a damper function during this relative rotation.
By adopting the above technical scheme, when the torque from the friction buffer portion 1 is transmitted 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, the first main damper spring 41 and the second main damper spring 42 being arranged in series during the above-described torque transmission, so that the total relative rotation angle of the two hub flanges 21, 22 is equal to the sum of the relative rotation angle of the first hub flange 21 with respect to the side plates 31, 32 and the relative rotation angle of the side plates 31, 32 with respect to the second hub flange 22 (also referred to as the sum of the compression angles of the two-part main damper springs 41, 42 in series) in the operating state shown in fig. 3b and 3 c. In this way, the vibration damping effect of the clutch disc can be further improved.
Further, in the present embodiment, the pre-damper spring holder 6 includes a disc-shaped body 61 and a pre-damper spring mounting portion 62 provided to the disc-shaped 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, so that the first hub flange 21 and the second hub flange 22 are restrained in the axial direction a. The two pre-damper spring mounting portions 62 are arranged 180 degrees apart in the circumferential direction C. The pre-damper spring holder 6 is fixedly mounted to the hub 5. The two predamper springs 7 are mounted to the two predamper spring mounting portions 62 of the predamper holder 6 and are located in the central through-hole 22h2 of the second hub flange 22 such that the predamper springs 7 are compressed by the circumferential side walls of the second hub flange 22 forming the central through-hole 22h2 when the second hub flange 22 is rotated relative to the hub core 5. Both pre-damper springs 7 are cylindrical helical 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 discs of the clutch driven disc include a first friction disc 81 provided between the first side plate 31 and the first hub flange 21, a second friction disc 82 provided between the second side plate 32 and the second hub flange 22, and a third friction disc 83 provided 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 plate 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 plate 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 plate 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 plate 81 is generally annular in shape and includes a first friction plate radial portion extending in the radial direction R and a first friction plate axial portion extending from a radially inner end of the first friction plate radial portion toward one side in the axial direction. The first friction disk radial portion is pressed against the first hub flange 21 from the axial one side via the first diaphragm spring 91. The first friction disk axial portion is disposed on the hub 5 from the radially outer side, and the first friction disk axial portion abuts on the first disk hub flange 21 from one axial side and abuts on the first side plate 31 from the other axial side.
The second friction plate 82 has an annular shape as a whole and extends in the radial direction R. The second friction disk 82 is pressed against the second hub flange 22 from the axial other side via the second diaphragm spring 92.
The third friction plate 83 is generally annular in shape and includes a third friction plate radial portion extending in the radial direction R and a third friction plate axial portion extending from a radially inner end of the third friction plate radial portion toward the other side in the axial direction. The third friction disk radial portion is pressed against the pre-damper spring holder 6 from the axial other side via the third diaphragm spring 93. The third friction disk axial portion is disposed 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 side in the axial direction and abuts on the second side plate 32 from one side in the axial direction.
Thus, by the first diaphragm spring 91, the second diaphragm spring 92, and the third diaphragm spring 93 being engaged with the first friction plate 81, the second friction plate 82, and the third friction plate 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 effect 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-described embodiments are merely exemplary and are not intended to limit the present invention. Those skilled in the art can make various modifications and changes to the above-described embodiments without departing from the scope of the present invention.
(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 disc-shaped as a whole, similarly to the formation of the third through hole 21h2 by the first hub flange 21, 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 greater 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 damper springs 41, 42 may also be six or the like.
The main damper springs 41, 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 the main damper springs 41, 42 are housed in the main damper spring mounting portion as described above so that the longitudinal direction thereof coincides with the direction of one tangential line of the clutch driven disc in the circumferential direction C; when the main damper springs 41, 42 are arc-shaped coil springs, it is preferable that each of the main damper springs 41, 42 is housed in the main damper spring mounting portion as described above so that the longitudinal direction thereof coincides with the circumferential direction C of the clutch driven plate.
Further, the first main damping spring 41 and the second main damping spring 42 may be different in type, size, and spring rate.
(iii) With respect to the initial state of the clutch disc shown in fig. 3a, fig. 3b shows the operating state after rotation of the first hub flange 21 relative to the hub core 5 in a counterclockwise direction (drive side/drive direction), wherein the first hub flange 21 is rotated by an angle α1 relative to the side plates 31, 32 (compression angle of the first main damper spring 41 on the drive side) and the side plates 31, 32 are rotated by an angle β1 relative to the second hub flange 22 (compression angle of the second main damper spring 42 on the drive side) in the direction indicated by the arcuate single arrow in fig. 3 b; fig. 3c shows a state after the first hub flange 21 is rotated in the clockwise direction (drag side/drag direction) with respect to the hub core 5, in which the first hub flange 21 is rotated by an angle α2 (compression angle of the first main damper spring 41 on the drag side) with respect to the side plates 31, 32 and the side plates 31, 32 are rotated by an angle β2 (compression angle of the second main damper spring 42 on the drag side) with respect to the second hub flange 22 in the direction indicated by the arc single arrow in fig. 3 c.
(iv) As shown in fig. 4, it is apparent that the predamper 7 can achieve a one-stage predamper stiffness on the drive side and the main damping springs 41, 42 can achieve a two-stage main damping spring stiffness on the drive side; the sum of the two-stage rotation angles of the main vibration reduction springs 41 and 42 on the driving side is 38 degrees, which is much larger than the rotation angle of the main vibration reduction spring of the clutch driven plate on the driving side in the prior art, so that the vibration reduction effect of the clutch driven plate is improved. Similarly, the clutch disk according to the invention also improves the damping effect on the drag side.
Claims (10)
1. A clutch driven plate, comprising:
a friction buffer section (1) that includes friction plates (11) arranged along a circumferential direction (C) so as to be able to receive torque from the outside;
a first hub flange (21) fixedly connected to the friction buffer portion (1) and formed with a first through hole (21 h 1) penetrating the first hub flange (21) in an axial direction (a);
a second hub flange (22) rotatable in a predetermined range in a circumferential direction (C) with respect to the first hub flange (21) and for transmitting torque to the outside, the second hub flange (22) being formed with a second through hole (22 h 1) penetrating 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 via the first hub flange (21) and the second hub flange (22), the two side plates (31, 32) being rotatable relative to the first hub flange (21) and the second hub flange (22), respectively, over a predetermined range in the circumferential direction (C), and the two side plates (31, 32) forming a main damper spring mounting portion; and
a plurality of main damper springs (41, 42), wherein the plurality of main damper springs (41, 42) are distributed along the circumferential direction (C) and are respectively accommodated and mounted in the corresponding main damper spring mounting parts,
wherein the first through hole (21 h 1) and the second through hole (22 h 1) are completely staggered in the circumferential direction (C), and the length of the first through hole (21 h 1) is approximately equal to the length of a first main damper spring (41) of the plurality of main damper springs, the length of the second through hole (22 h 1) is approximately equal to the length of a second main damper spring (42) of the plurality of main damper springs, the first main damper spring (41) is mounted to the first through hole (21 h 1) and the second main damper spring (42) is mounted to the second through hole (22 h 1) 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).
2. The clutch disk of claim 1 wherein,
the first hub flange (21) is further formed with a third through hole (21 h 2) corresponding to the second through hole (22 h 1) and penetrating through the first hub flange (21) in the axial direction (A), and the length of the third through hole (21 h 2) is greater than the length of the second main damping spring (42) and the length of the second through hole (22 h 1).
3. Clutch driven disc according to claim 2, characterized in that the second hub flange (22) comprises a cut-out area which avoids the first main damper spring (41) and the first through hole (21 h 1).
4. A clutch driven plate according to claim 3, characterized in that it comprises a plurality of stop fixing pins (33), said plurality of stop fixing pins (33) passing through said third through holes (21 h 2) and said cutout areas to achieve a limit between said first hub flange (21) and said second hub flange (22),
-defining the rotation angle of the first hub flange (21) with respect to the side plates (31, 32) by means of the cooperation of the circumferential side wall of the first hub flange (21) forming the third through hole (21 h 2) with the stop fixing pin (33), and-defining the rotation angle of the second hub flange (22) with respect to the side plates (31, 32) by means of the cooperation of the circumferential side wall of the second hub flange (22) with the stop fixing pin (33).
5. Clutch driven disc according to any one of claims 1 to 4, characterised in that the primary damping spring mounting comprises a window (31 h, 32 h) through the side plate (31, 32) in the axial direction (a) corresponding to each primary damping spring (41, 42), the length of the window (31 h, 32 h) being approximately equal to the length of the respective primary damping spring (41, 42) such that the position of the respective primary damping spring (41, 42) can be defined by the periphery of the window (31 h, 32 h).
6. Clutch driven disc according to any of claims 1 to 4, characterized in that it further comprises a hub core (5), said hub core (5) being formed with internal and external splines, said hub core (5) being mounted to a central through hole (22 h 2) of said second disc hub flange (22) and being capable of realizing a spline transmission with said second disc hub flange (22) by means of said external splines, said hub core (5) being capable of realizing a spline transmission with a transmission shaft by means of said internal splines.
7. Clutch-driven disc according to claim 6, characterized in that the hub (5) is rotatable in the circumferential direction (C) in relation to the second hub flange (22) to a predetermined extent, and
the clutch driven disc further comprises a pre-damping spring retainer (6) and a plurality of pre-damping springs (7), wherein the pre-damping spring retainer (6) is fixedly mounted on the hub core (5), and the plurality of pre-damping springs (7) are mounted on the pre-damping spring retainer (6) so that the pre-damping springs (7) can be compressed when the hub core (5) rotates relative to the second disc hub flange (22).
8. Clutch driven disc according to claim 7, characterized in that the pre-damper spring holder (6) comprises a disc-shaped body (61) and a pre-damper spring mounting (62) formed in 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).
9. Clutch driven disc according to any of claims 1 to 4, characterized in that the two side plates (31, 32) comprise a first side plate (31) on one axial side of the first hub flange (21) and a second side plate (32) on the other axial side of the second hub flange (22),
the clutch driven plate further comprises a first friction plate (81) arranged between the first side plate (31) and the first disc hub flange (21), a second friction plate (82) arranged between the second side plate (32) and the second disc hub flange (22), and a third friction plate (83) arranged between the second side plate (32) and the pre-vibration reduction spring retainer (6) of the clutch driven plate, and
the 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 plate (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 plate (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 plate (83).
10. A clutch comprising the clutch driven plate 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 CN113557370A (en) | 2021-10-26 |
| CN113557370B true 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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| Publication number | Publication date |
|---|---|
| CN113557370A (en) | 2021-10-26 |
| WO2021000223A1 (en) | 2021-01-07 |
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