CN112833111B - Clutch driven disc and clutch - Google Patents
Clutch driven disc and clutch Download PDFInfo
- Publication number
- CN112833111B CN112833111B CN201911153242.3A CN201911153242A CN112833111B CN 112833111 B CN112833111 B CN 112833111B CN 201911153242 A CN201911153242 A CN 201911153242A CN 112833111 B CN112833111 B CN 112833111B
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- main damper
- side plates
- hub
- flange
- springs
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- 238000013016 damping Methods 0.000 claims abstract description 29
- 230000006835 compression Effects 0.000 claims abstract description 13
- 238000007906 compression Methods 0.000 claims abstract description 13
- 230000005540 biological transmission Effects 0.000 claims description 12
- 230000000149 penetrating effect Effects 0.000 claims description 5
- 230000000694 effects Effects 0.000 abstract description 8
- 125000006850 spacer group Chemical group 0.000 description 4
- 230000000670 limiting effect Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
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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- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/12306—Radially mounted springs
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/1232—Wound springs characterised by the spring mounting
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention provides a clutch driven plate and a clutch comprising the same. The clutch driven plate includes two side plates, a hub flange between the two side plates and a plurality of primary damper springs. The plurality of primary damping springs are divided into a plurality of groups, each group of primary damping springs including at least two primary damping springs in series with each other such that the maximum torsion angle at which the two side plates rotate relative to the hub flange is equal to the total compression angle of the group of primary damping springs (i.e., equal to the sum of the compression angles of the series of primary damping springs in the group of primary damping springs). In this way, the main damping springs in each group of main damping springs of the clutch driven disc are arranged in series, so that a larger torsion angle and smaller torsion rigidity can be realized, the damping effect on torsion 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 controllable torque transfer between a power source (e.g., an engine) and a transmission of an automobile.
As shown in fig. 1a and 1b, one clutch driven plate of the 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 is coupled with the hub flange 40 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 retainer plate 20 and the cover plate 30, the main damper springs 50, the hub flange 40, the hub core 60, and the like.
In the clutch driven plate having the structure as described above, all of the main damper springs 50 are linear cylindrical coil springs and the torsion angle of the hub flange 40 with respect to the retainer plate 20 and the cover plate 30 is equal to the compression angle of one of the main damper springs 50, in which case the torsion angle of the relative rotation between the hub flange 40 and the retainer plate 20 and the cover plate 30 depends on the compression angle of one of the main damper springs 50. Since the torsion angle is small due to the restriction of the operation principle of the clutch driven plate in the length of one main damping spring 50 in the case that the main damping spring 50 is a cylindrical coil spring, the damping effect of the clutch driven plate 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 having an axial direction, a radial direction and a circumferential direction and comprising:
two side plates that are spaced apart in the axial direction and fixed to each other, between which a plurality of main damper spring mounting portions are formed, and one of which is for receiving torque from the outside of the clutch driven plate;
a hub flange located between the two side plates in the axial direction, the two side plates being rotatable relative to the hub flange in the circumferential direction by a predetermined range, the hub flange being for transmitting torque to the outside of the clutch driven plate; and
the main vibration damper comprises a plurality of main vibration damper springs, wherein the main vibration damper springs are divided into a plurality of groups, each group of main vibration damper springs comprises at least two main vibration damper springs which are connected in series, each group of main vibration damper springs are respectively arranged on one main vibration damper spring installation part, so that in the process that the two side plates transmit torque to the hub flange through the main vibration damper springs, the maximum torsion angle of the two side plates relative to the hub flange is equal to the sum of compression angles of the main vibration damper springs in one group of main vibration damper springs.
Preferably, the clutch driven plate further includes a connection flange disposed between adjacent two of the main damper springs in each set, the connection flange connecting the adjacent two main damper springs in series.
More preferably, the connection flange includes a flange body and protrusions protruding from the flange body toward both circumferential sides, the protrusions protruding into turns of the main damper spring located at both sides of the connection flange, respectively.
More preferably, the clutch disc further includes guide pins mounted to the two side plates so as to pass through the connection flanges, and
the two side plates are formed with guide holes corresponding to the guide pins and extending in the circumferential direction, and both ends of the guide pins are installed in the guide holes to be slidable along the guide holes, thereby defining a movement locus of the connection flange.
More preferably, the hub flange is formed with an abutment surface for abutment with an end portion of the main damper spring during torque transmission, the abutment surface being substantially orthogonal to a central axis of the corresponding main damper spring.
More preferably, the two side plates respectively include windows extending along the circumferential direction and facing each other, the windows of the two side plates form the main damper spring mounting portion such that the main damper spring can be mounted between the two side plates, and the hub flange is formed with a cutout portion avoiding the main damper spring.
More preferably, the clutch driven plate further includes:
a friction cushioning portion fixed to the one side plate and including a friction plate arranged along the circumferential direction so as to be able to receive torque from the outside therethrough; and
and a hub core mounted to the radially inner sides of the two side plates and the hub flange and drivingly coupled with the hub flange so as to be capable of transmitting torque to the outside through the hub core.
More preferably, the hub flange is rotatable in the circumferential direction by a predetermined range with respect to the hub core, and
the clutch driven disc further includes a plurality of pre-damper springs mounted between the hub core and the hub flange such that the pre-damper springs can be compressed to dampen vibrations when the hub flange rotates relative to the hub core.
More preferably, the clutch driven disc further comprises a plurality of friction discs/sleeves disposed between the two side plates and the hub flange and the hub core.
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 includes two side plates, a hub flange between the two side plates and a plurality of primary damper springs. The plurality of main damper springs are divided into a plurality of groups, each group including at least two main damper springs connected in series with each other, such that a maximum torsion angle at which the two side plates are rotated with respect to the hub flange is equal to a total compression angle of one group of main damper springs (that is, equal to a sum of compression angles of the series of main damper springs in one group of main damper springs). In this way, the main damper springs of each set of main damper springs of the clutch disc according to the present invention are arranged in series, and thus the hub flange and the side plate of the clutch disc according to the present invention can achieve a larger relative torsion angle and a smaller torsion stiffness than those of the clutch disc according to the related art described in the above-mentioned background art, thereby improving the damping effect on torsional vibration and the damping effect.
Drawings
FIG. 1a is a schematic front view showing a clutch driven plate half; 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 showing a clutch driven plate according to an embodiment of the present invention, wherein a partial structure of the clutch driven plate is omitted in order to show its internal configuration; FIG. 2b is a schematic diagram showing an exploded construction of the clutch driven plate of FIG. 2 a; FIG. 2c is a partial cross-sectional schematic view including a central axis taken along line L1-L1 showing the clutch driven plate of FIG. 2 a; FIG. 2d is a partial cross-sectional schematic view including a central axis taken along line L2-L2 showing the clutch driven plate of FIG. 2 a; FIG. 2e is a partial cross-sectional schematic view including a central axis taken along line L3-L3 showing the clutch driven plate of FIG. 2 a.
Description of the reference numerals
10 Friction buffer 20 holding plate 30 cover plate 40 hub flange 50 main damping spring 60 hub core
1 Friction buffer 11 friction plate 12 friction plate rivet 13 buffer
21 first side plate 21h1 first window 21h2 first guide hole 22 second side plate 22h1 second window 22h2 second guide hole 23 connector
3-disc hub flange 31 flange body 32 wing 32s abutting surface
4 main damping spring
51 connecting flange 52 guiding pin 53 spacer
61 first friction disc 62 first friction sleeve 63 second friction disc 64 second friction sleeve
71 first diaphragm spring 72 second diaphragm spring
8 hub core
9 pre-damping spring
Rradial A axial C circumferential.
Detailed Description
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, the axial direction, the radial direction and the circumferential direction refer to the axial direction, the radial direction and the circumferential direction of the clutch driven plate, respectively. Axial one side refers to the left side in fig. 2c to 2e, e.g. the side on which the engine is located; the other axial side refers to the right side in fig. 2c to 2e, e.g. the side on which the transmission is located. The radially outer side refers to the side radially away from the central axis (upper side in fig. 2c to 2 e), and the radially inner side refers to the side radially close to the central axis (lower side in fig. 2c to 2 e). In addition, "drive coupling" refers to the ability to directly or indirectly transfer drive force and torque between two components/members.
The structure of a clutch driven plate according to an embodiment of the present invention will be described below with reference to the drawings.
As shown in fig. 2a to 2e, the clutch driven plate according to an embodiment of the present invention has a disk shape as a whole and includes a friction buffer portion 1, two side plates (a first side plate 21 and a second side plate 22), a plurality of connection pieces 23, a plate hub flange 3, a plurality of (four in this embodiment) main damper springs 4, a connection flange 51, a guide pin 52, a spacer 53, a plurality of friction plates/friction sleeves (a first friction plate 61, a first friction sleeve 62, a second friction plate 63, a second friction sleeve 64), a plurality of diaphragm springs (a first diaphragm spring 71, a second diaphragm spring 72), a hub core 8, and a plurality of (two in this embodiment) pre-damper springs 9, 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 side plate 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 side plate 21 via the friction cushioning member 1.
Further, in the present embodiment, the two side plates 21, 22 include a first side plate 21 located on one side in the axial direction and a second side plate 22 located on the other side in the axial direction. The two side plates 21, 22 are fixedly connected to one another coaxially via the hub flange 3 by means of four connecting elements 23. The torque from the friction cushioning portion 1 can drive the two side plates 21, 22 to rotate together, the two side plates 21, 22 are integrally rotatable in a predetermined range in the circumferential direction C with respect to the hub flange 3, and the two side plates 21, 22 form a main damper spring mounting portion to define the positions of the respective main damper springs 4.
The first side plate 21 includes two first windows 21h1 corresponding to the main damper springs 4 penetrating the first side plate 21 in the axial direction a, and the second side plate 22 includes two second windows 22h1 corresponding to the main damper springs 4 penetrating the second side plate 22 in the axial direction a. The first window 21h1 and the second window 22h1 are disposed opposite to each other in the axial direction a and the first window 21h1 and the second window 22h1 each extend a predetermined length along the circumferential direction C, and the positions of the respective main damper springs 4 can be defined by the peripheral edge of the first window 21h1 and the peripheral edge of the second window 22h1, thereby forming a main damper spring mounting portion. In this way, the positions of the main damper springs 4 in the axial direction a, the radial direction R, and the circumferential direction C can be defined by the main damper spring mounting portions.
The first side plate 21 further includes two first guide holes 21h2 corresponding to the guide pins 52 penetrating the first side plate 21 in the axial direction a, and the second side plate 22 further includes two second guide holes 22h2 corresponding to the guide pins 52 penetrating the second side plate 22 in the axial direction a. The first guide hole 21h2 and the second guide hole 22h2 are provided opposite to each other in the axial direction a and both the first guide hole 21h2 and the second guide hole 22h2 extend along the circumferential direction C. The circumferential length of the first guide hole 21h2 is smaller than the circumferential length of the first window 21h1, and the circumferential length of the second guide hole 22h2 is smaller than the circumferential length of the second window 22h1. The two first guide holes 21h2 are located radially inward of the corresponding first windows 21h1, respectively, and spaced apart from the first windows 21h1, and the circumferential center lines of the two first guide holes 21h2 are aligned with the circumferential center lines of the corresponding first windows 21h1, respectively. The two second guide holes 22h2 are respectively located radially inward of the corresponding second windows 22h1 and spaced apart from the second windows 22h1, and the circumferential center lines of the two second guide holes 22h2 are respectively aligned with the circumferential center lines of the corresponding second windows 22h1.
Further, in the present embodiment, the hub flange 3 is located between the two side plates 21, 22 in the axial direction a, and the two side plates 21, 22 are rotatable relative to the hub flange 3 in the circumferential direction C by a predetermined range. The hub flange 3 includes a flange body 31 at the center and two wing portions 32 protruding from the flange body 31 toward both sides. The circumferential both sides of the two wing portions 32 are formed as abutment surfaces 32s for abutting against the end portions of the main damper springs 4 during torque transmission, the abutment surfaces 32s being substantially orthogonal to the central axis of the corresponding main damper spring 4 in the form of a cylindrical coil spring. When the clutch disc is mounted, it is necessary that the two wing portions 32 and the two sets of main damper springs 4 are alternately arranged in the circumferential direction C, and therefore the hub flange 3 is formed with the cutout portions that avoid the main damper spring mounting portions, and the two cutout portions and the two wing portions 32 are alternately arranged in the circumferential direction C. In addition, the central through hole of the flange body 31 is formed with an internal spline for engagement with the external spline of the hub core 8.
Further, in the present embodiment, each of the four main damper springs 4 is a linear cylindrical coil spring. The four main damper springs 4 are divided into two groups, each group of main damper springs 4 including two main damper springs 4 connected in series with each other by a connecting flange 51. Each set of main damper springs 4 is mounted to one main damper spring mounting portion, respectively, such that the maximum torsion angle at which the two side plates 21, 22 rotate relative to the hub flange 3 during torque transmission from the two side plates 21, 22 to the hub flange 3 via the main damper springs 4 is equal to the total compression angle of one set of main damper springs 4 (i.e., the sum of the compression angles of the two main damper springs 4).
Further, in the present embodiment, one connecting flange 51 is provided between two adjacent main damper springs 4 in each set of main damper springs 4. The connection flange 51 includes a flange body and two convex portions protruding from the flange body toward both sides in the circumferential direction, the two convex portions protruding into turns of the main damper spring 4 located on both sides of the connection flange 51, respectively. Thus, first, the connecting flange 51 enables the adjacent two main damper springs 4 to be arranged in series; secondly, the connecting flange 51 can realize a certain radial limiting effect on the main damping springs 4 positioned at two sides of the connecting flange so as to inhibit the compressed main damping springs 4 from radial play possibly occurring under the action of centrifugal force in the main damping spring mounting part formed by the first windows 21h1 and the second windows 22h1 of the two side plates 21 and 22; again, the two protrusions of the connection flange 51 are formed to have a predetermined angle, thus causing the two main damper springs 4 of the set of main damper springs 4 to be arranged in the main damper spring mounting portion in such a manner that their central axes form a predetermined angle, thereby avoiding interference that may occur between the two main damper springs 4 directly in series and maximally avoiding deformation of the main damper springs 4 during compression from interference that may occur with the two side plates 21, 22.
Further, in the present embodiment, the guide pin 52 is attached to the two side plates 21, 22 so as to pass through the connection flange 51. The connection flange 51 is rotatable with respect to the guide pin 52, and both ends of the guide pin 52 are fitted into the guide holes 21h2, 22h2 of the two side plates 21, 22 so as to be slidable along the guide holes 21h2, 22h2. In this way, the guide pin 52 and the guide holes 21h2, 22h2 can guide the movement of the connection flange 51 when the two main damper springs 4 connected by the connection flange 51 are compressed, thereby defining the movement locus of the connection flange 51, and further maximally avoiding the interference of the main damper springs 4 with the two side plates 21, 22 during the compression.
Further, in the present embodiment, two spacers 53 are sleeved on the guide pin 52, the two spacers 53 being located on both sides of the connection flange 51 and between the connection flange 51 and the two side plates 21, 22, so that the guide pin 52 is prevented from moving in the axial direction a while defining the relative positions of the connection flange 51 and the two side plates 21, 22 in the axial direction a.
Further, in the present embodiment, in order to provide an appropriate damping effect while restraining the hub flange 3, the hub core 8, and the two side plates 21, 22 in the axial direction a, two friction disks 61 and 63, two friction sleeves 62 and 64, and two diaphragm springs 71 and 72 are provided.
Specifically, the first friction disk 61 extends in the radial direction R and is disposed between the first side plate 21 and the hub flange 3 in the axial direction a.
The first diaphragm spring 71 is fixed to the first side plate 21 and abuts against the first friction plate 61 from the axial side so that the first friction plate 61 abuts against the hub flange 3.
A radial portion of the first friction sleeve 62 extending in the radial direction R is provided between the first side plate 21 and the hub 8 in the axial direction a, and an axial portion of the first friction sleeve 62 extending in the axial direction a is provided between the first side plate 21 and the hub 8 in the radial direction R, against which the first side plate 21 abuts from the radially outer side and against which the axial portion abuts from the radially outer side against the hub 8.
The second diaphragm spring 72 is fixed to the first side plate 21 and abuts against a radial portion of the first friction sleeve 62 from the axial side so that the radial portion abuts against the hub core 8.
The second friction plate 63 extends in the radial direction R and is disposed between the hub flange 3 and the second side plate 22 in the axial direction a, and the second friction plate 63 abuts against the hub flange 3 and the second side plate 22 by the spring force of the first diaphragm spring 71.
The second friction sleeve 64 includes an annular main body portion and an extension portion extending from the main body portion toward one axial side. The main body part is located between the hub core 8 and the second side plate 22 in the axial direction A and is abutted against the hub core 8 and the second side plate 22, and the protruding part extends through the external spline of the hub core 8 and is mainly used for axially limiting and circumferentially limiting the pre-damping spring 9.
Further, in the present embodiment, the hub core 8 is formed with internal and external splines. The hub core 8 can be splined with the internal splines of the hub flange 3 by means of its external splines, and the hub core 8 can be splined with a drive shaft, such as an input shaft of a transmission. Via the hub core 8, the hub flange 3 can be coupled in a drive manner with a drive shaft, for example an input shaft of a transmission. In addition, in the initial state shown in fig. 2a (neither the main damper spring 4 nor the pre-damper spring 9 is compressed), the hub flange 3 is able to perform a predetermined range of rotation in the circumferential direction C with respect to the hub core 8, so that the pre-damper spring 9 is compressed to exert a damper function during this relative rotation.
Further, in the present embodiment, both the pre-damper springs 9 are linear cylindrical coil springs. The two predamper springs 9 are arranged 180 degrees apart in the circumferential direction C at predamper mounting portions formed between the hub core 8 and the hub flange 3 such that the predamper springs 9 are compressed during a relative rotation of the hub flange 3 with respect to the hub core 8.
By adopting the above-described technical means, the torque from the friction cushioning member 1 is transmitted in the following order: the friction damper 1→the two side plates 21, 22→the main damper spring 4→the hub flange 3, and then transmitted to the hub 8 via the pre-damper spring 9 or directly to the hub 8. The main damper springs 4 of each set of main damper springs 4, which are implemented in a series arrangement, are compressed together during the above-described torque transmission such that the relative rotation angle of the two side plates 21, 22 with respect to the hub flange 3 is equal to the sum of the compression angles of the main damper springs 4 in series. In this way, the vibration damping effect of the clutch disc can be improved.
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. In addition, the following supplementary explanation is entered.
(i) Although in the above embodiment, the pre-damper springs 9 and the main damper springs 4 connected in series to each other are each linear cylindrical coil springs, the present invention is not limited thereto. For example, the pre-damper springs 9 and the main damper springs 4 may also be arc-shaped helical springs; but also a rubber spring or a combination or combination of a coil spring and a rubber spring.
(ii) Although not illustrated in the above embodiments, it is understood that, in order to ensure the trajectory of the main damper spring 4 when compressed by the hub flange 3 and further suppress the radial play that may occur in the main damper spring mounting portion of the compressed main damper spring 4, the abutment surface 32s of the hub flange 3 may also form a protrusion that protrudes into the turns of the main damper spring 4.
(iii) Although the total number of the main damper springs 4 is four in the above embodiment, the present invention is not limited thereto. The total number of main damper springs 4 may also be six or the like. The number of the set of main damper springs 4 is not limited to two, and may be three or more, and one connecting flange 51 is provided between adjacent main damper springs 4 of the set of main damper springs 4.
Although not explicitly described in the above embodiment, each main damper spring 4 in the form of a cylindrical coil spring should be housed in the main damper spring mounting portion as described above so that its longitudinal direction coincides with the direction of one tangential line of the clutch driven disc in the circumferential direction C.
(iv) In addition, the main damping spring in the clutch driven plate according to the present invention employs cylindrical coil springs connected in series with each other, so that the clutch driven plate according to the present invention not only achieves substantially the same relative torsion angle as the clutch driven plate employing the long arc-shaped coil spring, but also saves costs.
Claims (7)
1. A clutch driven disc having an axial direction (a), a radial direction (R) and a circumferential direction (C) and comprising:
-two side plates (21, 22), the two side plates (21, 22) being spaced apart in the axial direction (a) and fixed to each other, a plurality of main damper spring mounting portions being formed between the two side plates (21, 22), and one side plate (21) of the two side plates (21, 22) being for receiving torque from the outside of the clutch driven plate;
-a hub flange (3), said hub flange (3) being located between said two side plates (21, 22) in said axial direction (a), said two side plates (21, 22) being rotatable relative to said hub flange (3) over a predetermined range of rotation in said circumferential direction (C), said hub flange (3) being adapted to transmit torque to the outside of said clutch driven disc; and
-a plurality of main damper springs (4), said plurality of main damper springs (4) being divided into a plurality of groups, each group of said main damper springs (4) comprising at least two of said main damper springs (4) connected in series with each other, -each group of said main damper springs (4) being mounted to one of said main damper spring mounting portions, respectively, such that during torque transfer of said two side plates (21, 22) to said hub flange (3) via said plurality of main damper springs (4), the maximum torsion angle of rotation of said two side plates (21, 22) with respect to said hub flange (3) is equal to the sum of the compression angles of a plurality of main damper springs (4) of a group of said main damper springs (4), -said clutch driven disc further comprises a connecting flange (51), said connecting flange (51) being arranged between adjacent two main damper springs (4) of each group of said main damper springs (4), such that said connecting flange (51) enables said adjacent two main damper springs (4) to achieve a rotational torque transfer, said connecting flange bodies (51) comprising a series connection of said protruding flange bodies (51) and a plurality of said protruding flange turns (51) located on opposite sides of said main flange rings (4) respectively,
the clutch driven plate further comprises a guide pin (52), the guide pin (52) is mounted on the two side plates (21, 22) in a manner of penetrating the connecting flange (51), and
the two side plates (21, 22) are formed with guide holes (21 h2, 22h 2) corresponding to the guide pins (52) and extending along the circumferential direction (C), and both ends of the guide pins (52) are mounted in the guide holes (21 h2, 22h 2) so as to be slidable along the guide holes (21 h2, 22h 2) to define a movement locus of the connecting flange (51).
2. Clutch driven disc according to claim 1, characterized in that the hub flange (3) is formed with an abutment surface (32 s) for abutment with an end of the main damper spring (4) during torque transmission, which abutment surface (32 s) is substantially orthogonal to the central axis of the corresponding main damper spring (4).
3. Clutch driven disc according to claim 1, characterized in that the two side plates (21, 22) each comprise windows (21 h1, 22h 1) extending along the circumferential direction (C) and facing each other, the windows (21 h1, 22h 1) of the two side plates (21, 22) forming the main damper spring mounting part such that the main damper spring (4) can be mounted between the two side plates (21, 22), and the hub flange (3) being formed with a cutout avoiding the main damper spring (4).
4. The clutch driven plate of claim 1, further comprising:
a friction cushioning portion (1), the friction cushioning portion (1) being fixed to the one side plate (21) and including a friction plate arranged along the circumferential direction (C) so as to be able to receive torque from the outside therethrough; and
-a hub (8), said hub (8) being mounted radially inside said two side plates (21, 22) and said hub flange (3) and being in driving connection with said hub flange (3) so as to be able to transmit torque to the outside through the hub (8).
5. Clutch-driven disc according to claim 4, characterized in that the hub flange (3) is rotatable in the circumferential direction (C) over a predetermined range with respect to the hub core (8) and in that
The clutch driven disc further comprises a plurality of pre-damping springs (9), wherein the pre-damping springs (9) are arranged between the hub core (8) and the disc hub flange (3), so that the pre-damping springs (9) can be compressed to realize damping when the disc hub flange (3) rotates relative to the hub core (8).
6. Clutch driven disc according to claim 4 or 5, characterized in that it further comprises a plurality of friction discs/friction sleeves (61, 62, 63, 64) arranged between the two side plates (21, 22) and the hub flange (3) and the hub core (8).
7. A clutch comprising the clutch driven plate of any one of claims 1 to 6.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911153242.3A CN112833111B (en) | 2019-11-22 | 2019-11-22 | Clutch driven disc and clutch |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911153242.3A CN112833111B (en) | 2019-11-22 | 2019-11-22 | Clutch driven disc and clutch |
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| CN112833111A CN112833111A (en) | 2021-05-25 |
| CN112833111B true CN112833111B (en) | 2024-03-12 |
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| CN201911153242.3A Active CN112833111B (en) | 2019-11-22 | 2019-11-22 | Clutch driven disc and clutch |
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| CN (1) | CN112833111B (en) |
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| JPH0893791A (en) * | 1994-09-29 | 1996-04-09 | Exedy Corp | Damper disk assembly |
| JPH11336843A (en) * | 1998-05-28 | 1999-12-07 | Unisia Jecs Corp | Torque transmission device |
| DE102008039630A1 (en) * | 2007-09-17 | 2009-03-26 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | torsional vibration dampers |
| DE102010047446A1 (en) * | 2009-10-29 | 2011-05-05 | Schaeffler Technologies Gmbh & Co. Kg | Clutch disk for friction clutch, has bolts attached at driver disk and are distributed over extent, where bolts are reached through in recesses at height of twisting angle in counter disk |
| DE102012215829A1 (en) * | 2011-09-29 | 2013-04-04 | Schaeffler Technologies AG & Co. KG | Serial torsional vibration damper has input flange for connection with drive motor, intermediate flange and spring system for elastic coupling of input flange with intermediate flange |
| DE102012221216A1 (en) * | 2011-12-07 | 2013-06-13 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper for attenuating torsional vibration in powertrain of e.g. passenger car, has bow spring and compression spring that are arranged around the rotational axis |
| DE102014226596A1 (en) * | 2014-01-17 | 2015-07-23 | Schaeffler Technologies AG & Co. KG | Damping plates for a clutch hub, a clutch hub and a clutch |
| DE102016203042A1 (en) * | 2016-02-26 | 2017-08-31 | Schaeffler Technologies AG & Co. KG | torsional vibration dampers |
| DE102016211220A1 (en) * | 2016-06-23 | 2017-12-28 | Schaeffler Technologies AG & Co. KG | Clutch disc and friction clutch device |
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2019
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Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0893791A (en) * | 1994-09-29 | 1996-04-09 | Exedy Corp | Damper disk assembly |
| JPH11336843A (en) * | 1998-05-28 | 1999-12-07 | Unisia Jecs Corp | Torque transmission device |
| DE102008039630A1 (en) * | 2007-09-17 | 2009-03-26 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | torsional vibration dampers |
| DE102010047446A1 (en) * | 2009-10-29 | 2011-05-05 | Schaeffler Technologies Gmbh & Co. Kg | Clutch disk for friction clutch, has bolts attached at driver disk and are distributed over extent, where bolts are reached through in recesses at height of twisting angle in counter disk |
| DE102012215829A1 (en) * | 2011-09-29 | 2013-04-04 | Schaeffler Technologies AG & Co. KG | Serial torsional vibration damper has input flange for connection with drive motor, intermediate flange and spring system for elastic coupling of input flange with intermediate flange |
| DE102012221216A1 (en) * | 2011-12-07 | 2013-06-13 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper for attenuating torsional vibration in powertrain of e.g. passenger car, has bow spring and compression spring that are arranged around the rotational axis |
| DE102014226596A1 (en) * | 2014-01-17 | 2015-07-23 | Schaeffler Technologies AG & Co. KG | Damping plates for a clutch hub, a clutch hub and a clutch |
| DE102016203042A1 (en) * | 2016-02-26 | 2017-08-31 | Schaeffler Technologies AG & Co. KG | torsional vibration dampers |
| DE102016211220A1 (en) * | 2016-06-23 | 2017-12-28 | Schaeffler Technologies AG & Co. KG | Clutch disc and friction clutch device |
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| Publication number | Publication date |
|---|---|
| CN112833111A (en) | 2021-05-25 |
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