Source: http://www.google.com/patents/US6251018?ie=ISO-8859-1
Timestamp: 2014-03-10 15:04:56
Document Index: 198942347

Matched Legal Cases: ['arts 51', 'arts 51', 'arts 51', 'arts 51', 'arts 51', 'arts 35', 'arts 76', 'art 91', 'art 91', 'art 91', 'arts 99', 'art 96', 'art 97', 'art 37', 'art 59', 'art 36', 'arts 37', 'arts 37', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'arts 36', 'arts 36', 'art 36', 'art 37', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36', 'art 36']

Patent US6251018 - Dampening disk assembly with spring retaining plate - Google PatentsSearch Images Maps Play YouTube News Gmail Drive More »Sign inAdvanced Patent SearchPatentsA clutch disk assembly (1) is provided between an input shaft and an output shaft to selectively transmit rotation therebetween. The clutch disk assembly (1) is provided with a dampening mechanism (4) to provide smooth transition during engagement and disengagement of the clutch disk assembly. The dampening...http://www.google.com/patents/US6251018?utm_source=gb-gplus-sharePatent US6251018 - Dampening disk assembly with spring retaining plateAdvanced Patent SearchPublication numberUS6251018 B1Publication typeGrantApplication numberUS 09/291,968Publication dateJun 26, 2001Filing dateApr 15, 1999Priority dateApr 17, 1998Fee statusLapsedAlso published asDE19917307A1, DE19917307B4Publication number09291968, 291968, US 6251018 B1, US 6251018B1, US-B1-6251018, US6251018 B1, US6251018B1InventorsHideki Hashimoto, Takeshi Noguchi, Naohiko TakahashiOriginal AssigneeExedy CorporationExport CitationBiBTeX, EndNote, RefManPatent Citations (19), Referenced by (1), Classifications (11), Legal Events (4) External Links: USPTO, USPTO Assignment, EspacenetDampening disk assembly with spring retaining plateUS 6251018 B1Abstract A clutch disk assembly (1) is provided between an input shaft and an output shaft to selectively transmit rotation therebetween. The clutch disk assembly (1) is provided with a dampening mechanism (4) to provide smooth transition during engagement and disengagement of the clutch disk assembly. The dampening mechanism (4) has a more durable second retaining plate (32) with a rectangular window portion for transmitting torque. This second retaining plate (32) has a second receptacle (36) to support a first spring (16). The second retaining plate (32) includes a disk-like plate main body. The second receptacle (36) is formed from that plate main body. The second receptacle (36) projects in an axial direction from the plate main body. The second receptacle (36) includes an axially supporting part (36 a) and a circular supporting part (36 b). The axially supporting part (36 a) supports an axially outside part of the first spring (16) and continues in a radial direction. The circular supporting part (36 b) supports both end parts of the first spring (16), and is formed on both circular ends of the axially supporting part (36 a). A second hole (36 f) is formed at both corners of an inner circumferential side of the axially supporting part (36 a). The second holes (36 f) are elongated holes that extend in a radial direction.
What is claimed is: 1. A spring retaining plate for use with a dampening disk assembly to support at least one coil spring, said spring retaining plate comprising:
a plate main body having a disk shaper, a spring supporting portion including an axially supporting part, said axially supporting part continuously projecting from said plate main body in an axial direction, continuing in a radial direction to form a spring seat for supporting an axially outside part of the coil spring, said axially supporting part having a pair of end portions with inner and outer circumferential sides extending between said end portions; and an elongated hole being formed at radially inner circumferential corners of said axially supporting parts, said elongated hole being formed in a portion where said axially supporting part and said plate body. 2. A spring retaining plate as set forth in claim 1, wherein each of said elongated holes extends over said axially supporting part and said plate main body.
3. A spring retaining plate as set forth in claims 1, wherein said elongated holes extend in substantially in a radial direction.
4. A spring retaining plate as set forth in claim 2, wherein said elongated holes extend in substantially in a radial direction.
5. A spring retaining plate as set forth in claim 2, wherein said elongated holes have an oval shape.
6. A spring retaining plate as set forth in claim 3, wherein said elongated holes have an oval shape.
7. A spring retaining plate as set forth in claim 1, wherein
several of said spring supporting portions are formed in said plate main body with each of said spring supporting portions having said axially supporting part, said end portions and said elongated holes. 8. A spring retaining plate as set forth in claim 7, wherein said spring supporting portions are arranged in a circular pattern.
9. A spring retaining plate as set forth in claim 8, wherein each of said elongated holes extends over said axially supporting part and said plate main body.
10. A spring retaining plate as set forth in claim 9, wherein each of said elongated holes extends in a substantially radial direction.
11. A spring retaining plate as set forth in claim 10, wherein said elongated holes have an oval shape.
12. A spring retaining plate as set forth in claim 10, further comprising additional holes extending over said axially supporting parts and said plate main body.
13. A spring retaining plate as set forth in claim 12, wherein said additional holes are radially elongated.
14. A spring retaining plate as set forth in claim 1, wherein said elongated holes extend radially from said inner circumferential side to said outer circumferential side.
15. A spring retaining plate as set forth in claim 14, wherein each of said elongated holes has an inner radial end, a middle radial section and an outer radial end with said inner and outer radial ends being wider than said middle radial section.
16. A spring retaining plate as set forth in claim 15, wherein each of said elongated holes extends over said axially supporting part and said plate main body at said inner circumferential side.
17. A spring retaining plate as set forth in claim 14, wherein several of said spring supporting portions are formed in said plate main body with each of said spring supporting portions having said axially supporting parts.
18. A spring retaining plate as set forth in claim 17, wherein
each of said elongated holes has an inner radial end, a middle radial section and an outer radial end with said inner and outer radial ends being wider than said middle radial section. 19. A spring retaining plate as set forth in claim 18, wherein each of said elongated holes extends over said axially supporting part and said plate main body at said inner circumferential side.
20. A spring retaining plate as set forth in claim 17, wherein said spring supporting portions are arranged in a circular pattern.
21. A dampening disk assembly comprising:
a pair of spring retaining plates fixedly coupled to each other to form a coil spring receiving space therebetween, with each of said spring retaining plates having a plate main body with a disk shape, a centrally located attachment portion formed in said plate main body and at least one spring supporting portion formed in said plate main body which is radially spaced from said centrally located attachment portion; a central hub located between said spring retaining plates and rotatably coupled to said centrally located attachment portions of said spring retaining plates; and at least one coil spring having a pair of circular ends supported by said spring supporting portions of said spring retaining plates and said hub to elastically couple said spring retaining plates to said hub in a rotary direction, said at least one spring supporting portion of at least one of said spring retaining plates including an axially supporting part and an end supporting part, said axially supporting part continuously projecting from said plate main body in an axial direction, continuing in a radial direction to form a spring seat for supporting an axially outside part of the coil spring, said axially supporting part having a pair of end portions with inner and outer circumferential sides extending between said end portions; and an elongated hole being formed at inner circumferential corners of said axially supporting parts, said elongated hole being formed in a portion where said axially supporting part projects axially from said plate body and a radial boarder between said axially supporting part and said plate body. 22. A dampening disk assembly as set forth in claim 21, wherein each of said elongated holes extends over said axially supporting part and said plate main body.
23. A dampening disk assembly as set forth in claim 21, wherein each of said elongated holes extends along a direction which is substantially the same direction of said end portions.
24. A dampening disk assembly as set forth in claim 21, wherein said elongated holes extend in a substantially radial direction.
25. A dampening disk assembly as set forth in claim 24, wherein said holes have an oval shape.
26. A dampening disk assembly as set forth in claim 21, wherein
several of said spring supporting portions are formed in said plate main body with each of said spring supporting portions having said axially supporting parts, said end portions and said elongated holes. 27. A dampening disk assembly as set forth in claim 26, wherein said spring supporting portions are arranged in a circular pattern.
28. A dampening disk assembly as set forth in claim 27, wherein each of said elongated holes extends over said axially supporting part and said plate main body.
29. A dampening disk assembly as set forth in claim 28, wherein each of said elongated holes extends in a substantially radial direction.
30. A dampening disk assembly as set forth in claim 29, wherein said elongated holes have an oval shape.
31. A dampening disk assembly as set forth in claim 29, further comprising
additional holes extending over said axially supporting parts and said plate main body. 32. A dampening disk assembly as set forth in claim 31, wherein said additional holes are radially elongated.
33. A dampening disk assembly as set forth in claim 21, wherein
said elongated holes extend radially from said inner circumferential side to said outer circumferential side. 34. A dampening disk assembly as set forth in claim 33, wherein each of said elongated holes has an inner radial end, a middle radial section and an outer radial end with said inner and outer radial ends being wider than said middle radial section.
35. A dampening disk assembly as set forth in claim 34, wherein
each of said elongated holes extends over said axially supporting part and said plate main body at said inner circumferential side.
This invention generally relates to the retaining plates of a dampening disk assembly, which is used in a clutch of a motorized vehicle. More specifically, the present invention relates to the holes formed in plates, which are located adjacent, the rectangular windows such that these holes reduce wear and increase life span of the plate.
In general, a clutch disk assembly or dampening disk assembly is used in a clutch of a vehicle. The dampening disk assembly includes an input portion connected with a flywheel on an engine side, and a spline hub connected with a shaft extending from a transmission. The input portion and the spline hub are coupled in a circular direction by a dampening mechanism. The dampening mechanism includes a plurality of coil springs. The input portion includes a friction facing pressed by a flywheel and a pair of disk like plates. The spline hub includes a boss part in which the shaft from the transmission is inlayed, and a flange extending to an outer circumferential side of the boss part. Window holes are formed in the flange, and within each window hole is an elastic portion such as a coil spring. The two plates have rectangular windows (spring supporting part), which are formed by punching and cut and lift in an axial direction, at locations corresponding to the coil springs. These rectangular windows have convex shapes, which are formed by a drawing method. Both circular end parts of the rectangular windows touch both end parts of the coil springs, and operate as a connecting part for transmitting torque therebetween. In addition, the rectangular windows operate as spring casings to seat the coil springs and regulate the coil springs movements in both axial and radial directions.
As the coil spring seated in the rectangular window gets larger, both the axially projecting amount of the rectangular window from the plate main body and the cut and lift angle of the rectangular window get larger.
In the conventional clutch disk assembly mentioned above, the rectangular windows of the retaining plates have round theft holes at the radially inside part on both sides of the rectangular window in a circular direction. Since the theft hole reduces stress, a crack in the retaining plate occurs less often.
However, these prior art plates with these round theft holes do not extend far enough to enable lifting of the rectangular window. Therefore, during the forming of the rectangular window, a crack is easily caused.
An object of the present invention is to make it more difficult to break the rectangular window in the plate used for the dampening disk assembly.
A plate is used for a dampening disk assembly, and supports a coil spring. The plate includes a disk like plate main body and a spring supporting part that is formed at the plate main body. The spring supporting part projects in an axial direction from the plate main body so as to be able to seat the coil spring. The spring supporting part includes an axially supporting part which continues in a radial direction and supports an axially outside part of the coil spring. It also includes a circular supporting part which is formed on both circular side parts of the axially supporting part and supports both ends of the coil spring. A hole which is long in one direction is formed around both corners of its inner circumferential side of the axially supporting part.
The lifted parts of the spring supporting parts have a large angle. Nonetheless, owing to the radially long hole, its amount to extend during forming the window is sufficiently secure, thereby reducing the possibility of cracking.
This long hole is formed to stretch over the axially supporting part, and the plate main body. The hole extends along the same direction as the circular supporting part extends, and has an oval shape. These features result in less cracks being caused during formation of the rectangular window.
The plate includes a disk-like plate main body and a spring supporting part, which is formed at the plate main body. The spring supporting part includes an axially supporting part which projects from the plate main body in an axial direction so as to be able to seat the coil spring, and continues in a radial direction and supports an axially outside part of the coil spring. The spring supporting part also includes a circular supporting part, which is formed on both circular side parts of the axially supporting part and supports both ends of the coil spring. A hole which extends from the radially inside part to the radially outside part is formed on both circular side parts of the axially supporting part.
A dampening disk assembly includes two plates, a hub and a coil spring, where the two plates are fixed to each other. The hub is disposed on a central side of the two plates. Both circular end parts of the coil spring are supported by the spring supporting parts and the coil spring couples the two plates and the hub elastically in a rotary direction.
These and other objects, features, aspects and advantages of the present invention will become apparent to those skilled in the art from the following detailed description, which, taken in conjunction with the drawings, discloses preferred embodiments of the present invention.
FIG. 1 is a partial side elevational view of a clutch disk assembly in accordance with an embodiment of the present invention with portions broken away for purposes illustration;
FIG. 7 shows a torsion characteristic curve of the clutch disk assembly in accordance present invention;
FIG. 11 is a partial edge elevational view of a part of the fixing plate illustrated FIG. 8 as viewed along an arrow XI of FIG. 8;
FIG. 14 is a cross sectional view of the bushing illustrated in FIG. 12 as viewed along section line XIV�XIV in FIG. 12;
FIG. 21 is a cross sectional view of the friction bushing illustrated in FIG. 20 as viewed song section line XXI�XXI of FIG. 20;
FIG. 25 is a partial cross sectional view when a clutch disk assembly is used for a twin clutch; FIG. 26 is a partial plan view showing a radially outside supporting part of a second receptacle;
FIG. 27 is a partial plan view showing advanced abrasion of the radially outside supporting part of the second receptacle illustrated in FIG. 26.
The structure of the clutch disk assembly I will now be described in more detail with reference to FIG. 3 The input rotary portion 2 includes a first retaining plate (clutch plate) 31, a second retaining plate 32 and a clutch disk 33 coupled to the outer periphery of the first retaining plate 31. The first retaining plate 31 and the second retaining plate 32 are disk-shaped members which form annular plate portions that are disposed in an axial direction apart from each other by a predetermined distance. The first retaining plate 31 is disposed on the first axis side, and the second retaining plate 32 is disposed on the second axis side. The outer circumferential parts of the first retaining plate 31 and the second retaining plate 32 are fixedly coupled to each other by a plurality of stop pins 40 disposed in a circular direction side by side as seen in FIGS. 1 and 5. Consequently, the distance in an axial direction between the first retaining plate 31 and the second retaining plate 32 is determined by pins 40. Both plates 31 and 32 rotate together in a body. A cushioning plate 41 of the clutch disk 33 is fixedly coupled to the outer circumferential part of the first retaining plate 31 by a plurality of rivets 43 as seen in FIGS. 1, 3 and 4. An annular friction facing 42 is fixedly coupled to both sides of the cushioning plate 41.
As seen in FIG. 3, several first receptacles 34 are formed in each of the first retaining plate 31 and the second retaining plate 32 in equal intervals in a circular direction. The first receptacle 34 is a portion, which swells slightly in an axial direction. Each of the first receptacles 34 has a first supporting portion 35 on its both sides in a circular direction. The first supporting portions 35 oppose each other in a circular direction. As seen in FIG. 4, several second receptacles 36 are formed in each of the first retaining plate 31 and the second retaining plate 32 in equal intervals in a circular direction. The second receptacles 36 are disposed adjacent to the R1 side of each of the first receptacles 34. Each of the second receptacles 36 has a second supporting portion 37 on its both sides in a circular direction. Each second receptacle 36 is longer than the first receptacle 34 in both a radial and circular directions as seen in FIG. 1.
As seen in FIGS. 4 and 5, at an outer circumferential edge of the second retaining plate 32, a plurality of bent parts 51 that are bent toward the second axis side are formed. The bent parts 51 are formed adjacent to the stop pins 40. The bent parts 51 increase the strength of the circumference of the stop pin 40 over the stop pin 40 by itself Therefore, the stop pins 40 can be disposed at the most radially outer sides of the first retaining plate 31 and the second retaining plate 32, resulting in a high stopping torque. Since the bent parts 51 do not lengthen the second retaining plate 32 in a radial direction, the length of the second retaining plate 32 can be smaller in a radial direction compared with that of the conventional one with the same strength. When the length of the second retaining plate 32 in a radial direction is the same with that of the conventional one, the stop pins 40 can be disposed at the more radially outer side compared with the conventional one. Since the bent parts 51 are formed partially around the second retaining plate 32, the amount of metal plate material is reduced.
As seen in FIG. 3-5, the hub flange 18 is disposed in an axial direction between the first retaining plate 31 and the second retaining plate 32. The hub flange 18 operates as an intermediate portion between the input rotary portion 2 and the hub 3. The hub flange 18 is a disk-shaped member or annular portion that is thicker than the plates 31 and 32. At the hub flange 18, several first window holes 57 are formed corresponding to the first receptacles 34. The first window holes 57 are formed for the first receptacles 34. The circular angle of each of the first window holes 57 is smaller than the circular angles between the first supporting portions 35 of the first receptacles 34. The centers of a rotary direction of the first window holes 57 coincide approximately with that of the first receptacles 34. Therefore, as seen in FIG. 1, a gap of a torsion angle θ2 is formed at both sides in a circular direction between the circular ends of the first window holes 57 and the first supporting portions 35 of the first receptacles 34. The springs 17 are installed within the first window holes 57. The springs 17 are coil springs with their circular ends touching the circular ends of the first window holes 57. In this condition, gaps with torsion angles θ2 exist between both circular ends of the springs 17 and the first supporting parts 35 of the first receptacles 34 as seen in FIG. 1.
As seen in FIGS. 2-5, a spacer 80 is disposed between the first disk-shaped portion 71 of the fixing plate 20 and the hub flange 18. The spacer 80 connects the fixing plate 20 with the hub flange 18 in a rotary direction, and plays a role to receive a force which is applied from the fixing plate 20 to the hub flange 18. The spacer 80 is an annular resin portion, and has many lightening portions to decrease the weight. The spacer 80 includes an annular portion and a plurality of protrusions 82 projecting from the annular portion 81 outward in a radial direction as seen in FIG. 2. Two cutouts 83 are formed at the outer circumferential edge of each of the protrusions 82. A projection 84 extends from each of the protrusions 82 toward the first axis side as seen in FIG. 3. Projections 84 are inserted in connecting holes 58, which are formed in the hub flange 18. The projections 84 are connected with the connecting holes 58 such that they are slightly movably in a radial direction and relatively unmovably in a rotary direction.
A friction portion 86 is molded to or bonded to the fixing plate 20 side of the annular portion 85. The friction portion 86 is a portion that is designed to increase a friction coefficient between the first friction washer 48 and the fixing plate 20, and extends in an annular or disk-like shape. The annular portion 85 has a plurality of rotationally connecting portions 87 extending toward the second axis side. These connecting portions 87 are formed at the inner circumference of the annular portion 85. The rotationally connecting portions 87 are inserted in a plurality of cutouts 53 which are formed in a center hole 52 (inner circumferential edge) of the second retaining plate 32. In this way, the first friction washer 48 is connected with the second retaining plate 32 relatively non-rotatable manner, but in an axially movable manner. In addition, in the annular portion 85, connecting portions 88, which extend outward in a radial direction from the outer circumferential edge and then extend toward the second axis side. The connecting portions 88 are relatively thin and have a tab or detent portion at the end. The connecting portions 88 are inserted in holes 54, which are formed at the second retaining plate 32, and its tab or detent portions of connecting portions 88 are connected with the second retaining plate 32. The connecting portions 88 urge itself outward in a radial direction when it is connected, and press itself against the holes 54. Therefore, after partially assembling (subassembling), the first friction washer 48 is difficult to remove from the second retaining plate 32. In this way, at the first friction washer 48, the rotationally connecting portions 87 transmit a torque and the connecting portions 88 connect temporarily a portion of first friction washer 85 with the second retaining plate 32. The connecting portions 88 are thin and able to bend. Since the connecting portions 88 have a low rigidity, it will not typically break during sub-assembling. Therefore, since a force is not applied to the rotationally connecting portions 87 during subassembling, the first friction washer 48 is less likely to be broken than the conventional resin friction washer which have a tab or detent portion of radially connecting portions 88 to connect a second retaining plate 32. In addition, since a press fitting machine is not necessary during sub-assembling, an equipment cost can be reduced.
The first cone spring 49 is disposed between the first friction washer 48 and the inner circumference of the second retaining plate 32. The first cone spring 49 is compressed in an axial direction between the second retaining plate 32 and the first friction washer 48. The outer circumferential edge of the first cone spring 49 is supported by the second retaining plate 32, while the inner circumferential edge of the first cone spring 49 contacts the annular portion 85 of the first friction washer 48. As seen in FIG. 2, the first cone spring 49 has a plurality of cutouts 49 a formed on its inner circumferential side. It can be thought that the cutouts 49 a at the inner circumferential edge form a plurality of projections on the inner circumferential edge of first cone spring 49. Projection parts tat are formed on the outer circumferential side of the rotationally connecting portions 87 of the first friction washer 48 are inserted in the cutouts 49 a. In this way, the first cone spring 49 is connected with the first friction washer 48 relatively non-rotatable manner.
A bushing 19 operates as an output portion in the second dampening mechanism 6. The bushing 19 is connected with the hub 3 in a relatively non-rotatable manner. In particular, the bushing 19 is an annular resin portion, which is disposed on the second axis side of both the internal teeth 61 of the hub flange 18 and the external teeth 65 of the hub 3. The bushing 19 is also located on the inner circumferential side of the cylinder-shaped portion 72 of the fixing plate 20, and in a space on the outer circumferential side of the second axis side part of the boss 62. The bushing 19 includes mainly an annular portion 89 with a plurality of spring receptacles 90, as shown in FIG. 12 to 19. The spring receptacles 90 are formed at equal intervals in a circular direction at the side face of the second axis side of the annular portion 89. The spring receptacles 90 are formed at locations corresponding to the cut and lift parts 76 or the cutout parts of the fixing plate 20. The spring receptacles 90 are concave parts that are formed at the side face of the bushing 19 on the second axis side. The concave parts, as shown in FIG. 14 and 15, are formed smoothly so that its cross section forms a part of a circle. In addition, a hole is formed that penetrates in an axial direction each spring receptacle 90 at its center in both radial and circular directions. At the inner circumference of the annular portion 89, an inner circumferential supporting part 91 is formed with a cylinder like shape. The supporting part 91 extends toward the second axis side from the annular portion 89. An inner circumferential face 91 a of the bushing 19 is formed by the inner circumferential supporting part 91. This inner face 91 a touches or is close to the outer circumferential face of the boss 62. A side face 89 a is formed on the second axis side of the annular portion 89 of the bushing 19. This side face 89 a touches the side face of the first axis side of the second disk-shaped portion 73 of the fixing plate 20.
A second cone spring 78 is an urging portion in the second friction mechanism to urge the second disk-shaped portion 73 and the annular portion 89 towards each other in an axial direction. The second cone spring 78 is disposed in an axial direction between the bushing 19 and the external teeth 65 of the hub 3 and the internal teeth 61 of the flange 18. The inner circumference of the second cone spring 78 is supported by the flange 64 of the hub 3, while the outer circumference of the second cone spring 78 touches the annular portion 89 of the bushing 19. The second cone spring 78 is compressed in an axial direction, and urges the bushing 19 toward the second axis side. As a result, the side face 89 a of the second axis side of the annular portion 89 of the bushing 19 and the side face of the first axis side of the second disk-shaped portion 73 of the fixing plate 20 are urged towards each other in an axial direction by a predetermined force. The second cone spring 78 has an inner and outer diameters smaller than those of the first cone spring 49. The second cone spring 78 also has a thickness that is much smaller than that of the first cone spring 49. Thus, an urging force of the second cone spring 78 is much smaller than that of the first cone spring 49. At an inner circumferential edge the second cone spring 78 has a plurality of cutouts formed at an inner circumferential edge of the second cone spring 78. It can be thought that the cutouts of the cone spring 78 form a plurality of projections at the inner circumferential edge. The connecting parts 99 mentioned above extend within the cutouts of the cone spring 78.
As described above, the fixing plate 20 operates in the second dampening mechanism 6 as an input portion to connect with the second springs 21, as a portion included in the second friction mechanism 10, and as a portion included in the first friction mechanism 8. An advantage for the use of the fixing plate 20 is described as follows. The fixing plate 20, as described above, operates in the second dampening mechanism 6 as an supporting portion to support both ends of the second springs 21 in a circular direction and as an portion included in the second friction mechanism 11. Thus, one portion has two functions, resulting in a small number of parts. In addition, the fixing plate 20 supports the outside in an axial direction of the second spring 21. Furthermore, the fixing plate 20 includes friction faces both for the second friction mechanism 10 to generate a friction by rubbing at the first step of the torsion characteristic and for the first friction mechanism 8 to generate a friction by rubbing at the second step of the torsion characteristic. Thus, one portion has two friction faces, resulting in an easy adjustment and control of the friction characteristic of both friction faces. In other words, rubbing faces for both a flange of a boss and a hub flange are not necessary to be controlled, being different from that of the conventional dampening mechanism. Particularly, since the fixing plate 20 has a small size and a simple structure, being different from the conventional hub or hub flange, it is easy to control its friction face. Since the fixing plate 20 mentioned above is made of a metal plate, the fixing plate 20 with a desired shape can be obtained easily by press working, resulting in a low cost of the fixing plate 20.
Referring to FIGS. 3-5 and 20-22, a bushing 93, which forms a part of a third dampening mechanism, will now be described in more detail. The bushing 93 is disposed at the inner circumference of the first retaining plate 31 and touches the outer circumferential face of the hub 3, the end face of the flange 64, the external teeth 65, the cylinder-shaped portion 59 of the hub flange 18 and the internal teeth 61.
Functions of the bushing 93 includes dampening vibrations in a rotary direction by generating a friction, locating the first retaining plate 31 for the hub 3 in a radial direction, and locating the hub flange 18 for the hub 3 in a radial direction. The bushing 93, as shown in FIG. 20 to 22, includes mainly an annular resin portion 94. The annular portion 94 is a disk-shaped portion that has a predetermined width in a radial direction and a small thickness in an axial direction. The annular portion 94 is disposed between the inner circumference of the first retaining plate 31 and that of the hub flange 18 in an axial direction. An annular friction portion 95 is molded to, bonded to, or simply disposed at the annular portion 94 on the second axis side. The friction portion 95 has an annular shape, with a disk-shaped portion, which has a predetermined width in a radial direction and a small thickness in an axial direction. The friction portion 95 is made of a material with a high friction coefficient, for example, a rubber type material, a glass type mixed fiber spinning or impregnated compact or a ceramic. The friction portion 95 gives a characteristic of a high friction coefficient to the bushing 93. The magnitude of its friction can be adjusted by selecting the material of friction portion 95.
As shown in a plan view of FIG. 20, the inner and outer diameters of the annular portion 94 and the friction portion 95 are circular. The friction portion 95 can be thought to be disposed so as to touch the side face of the annular portion 94 on the second axis side, or thought to be disposed within a channel, which is formed at the side face of the annular portion 94 on the second axis side. In other words, a cylinder 30 shaped part 96 extends toward the second axis side, and is formed at the inner circumferential edge of the annular portion 94, with a cylinder-shaped part 97 extending toward the second axis side at its outer circumferential edge. An annular space surrounded by the cylinder-shaped portions 96 and 97 forms a channel of the annular portion 94. An inner and outer diameters of the channel are circular, and the friction portion 95 is disposed within the channel.
Several holes 95 a are formed side by side in a circular direction at the friction portion 95, and projections 94 a of the annular portion 94 are inserted in the holes 95 a. In this way, a whirl stop between the annular portion 94 and the friction portion 95 is performed. Particularly, since the friction portion 95 has a circular shape, such a whirl stop plays an important role. In the conventional friction portion, when it has a circular shape, there is a possibility to cause a problem concerning its strength, such as a peeling by adhering to a backboard made of SPCC. Therefore, in the conventional friction portion, a whirl stop is performed by using a friction portion with a square shape. While the friction portion 95 in accordance with the present invention has a simple structure with a circular shape, it does not have a problem such as a peeling. Particularly, it is easy to form the holes 95i a l of the friction portion 95 and to form the projections 94i a l of the annular resin portion 94, resulting in a reduction of a cost.
In the present embodiment, since the friction portion 95 is not fixedly coupled to the annular portion 94, the friction portion 95 can come off in an axial direction.
Therefore, a working such as a bonding is not necessary. However, in this embodiment in accordance with the present invention, the friction portion 95 may be bonded to the annual portion 94.
Pluralities of cutouts 97 a are formed at the cylinder-shaped portion 97. The internal side face of the cylinder-shaped portion 97 in a radial direction touches the outer circumferential face on the first axis side of the cylinder-shaped portion 59 of 30 the hub flange 18. In other words, the hub flange 18 is positioned by the cylinder-shaped portion 97 of the bushing 93 in a radial direction against the hub 3, the first retaining plate 31 and the second retaining plate 32.
When the hub 3 is twisted in a R2 direction against the input rotary portion 2, mainly the second dampening mechanism 6 operates within a range of a torsion angle θ1. In other words, the second springs 21 are compressed in a rotary direction, causing a rubbing in the second friction mechanism 10. In this case, since a rubbing is not caused in the first friction mechanism 8, a characteristic of a high hysteresis torque can not be obtained. As, a result, a characteristic of the first step of a low rigidity and low hysteresis torque is obtained. When the torsion angle is over the torsion angle θ1, the second stopper 12 touches, resulting in a stop of a relative rotation between the hub 3 and the hub flange 18. In other words, the second dampening mechanism 6 does not operate when the torsion angle is over θ1. Thus, the second springs 21 are not compressed when the torsion angle is over θ1. Therefore, the second springs 21 are not likely to be broken. In addition, it is not necessary to consider the strengths of the second springs 21, which leads to an easy design. The first dampening mechanism 5 operates at the second step of a torsion characteristic. In other words, the first springs 16 are compressed in a rotary direction between the hub flange 18 and the input rotary portion 2, resulting in a rubbing in the first friction mechanism 8. As a result, a characteristic of the second step of a high rigidity and high hysteresis torque is obtained. When the torsion angle is over θ1+θ2, .the end part of the springs 17 in a circular direction touches the second supporting part 37 of the second receptacle 36. In other words, in the second dampening mechanism 6, the first springs 16 and the springs 17 are compressed in parallel. As a result, a rigidity of the third step is higher than that of the second step. When the torsion angle is θ1+θ2+θ3, the first stopper 11 touches, resulting in a stop of a relative rotation between the input rotary portion 2 and the hub 3.
In the present invention, however, the first cone spring 49 urges the fixing plate 20 toward the first axis side, and its urging force is applied to the hub flange 18 and the bushing 93. Therefore, when an amount of abrasion in the second friction mechanism 10 corresponds to or coincides with an amount of abrasion at a friction face between the bushing 93 and the hub flange 18, the following results can be obtained. When a part (the friction portion 95) of the bushing 93 corresponding to the cylinder-shaped part 59 of the hub flange 18 abrades, the hub flange 18, the spacer 80, the fixing plate 20 and the first friction washer 48 all move toward the first axis side corresponding to an amount of the abrasion. As a result, at the friction face in the second friction mechanism 10, the second disk-shaped portion 73 moves toward the first axis side. The location of the bushing 19 against the hub 3 in an axial direction hardly changes. Therefore, a posture of the second cone spring 78 which is disposed between the flange 64 and the bushing 19 hardly changes. Thus, an abrasion following mechanism using the hub flange 18 and the first friction mechanism 8 keeps a posture of the second cone spring 78 constant, regardless of an abrasion at the friction face of the second friction mechanism 10, resulting in a stable generation of a hysteresis torque in the second friction mechanism 10. As a result, a hysteresis torque that shows a small change with the passage of time can be obtained, leading to an improved sound and vibration performance. In addition, since it is not necessary to consider an abrasion margin of the second cone spring 78, the degree of freedom to design the second cone spring 78 increases. In particular, it is possible to design the second cone spring 78 with a low stress and a high load. A set load of the second cone spring 78 is set to be approximately a peak of a load characteristic in a cone spring. When an amount of abrasion in the bushing 19 is kept to be equal to that in the bushing 93, the load of the second cone spring 78 is kept to be approximately a maximum. When an amount of abrasion in the bushing 19 is different from that in the bushing 93, the set load shifts slightly from a peak of a load characteristic to both its side. In this case, an amount of variation of a set load is set so as to be a minimum, in addition its amount is predictable.
In the machine circuit in FIG. 6, some other elastic portion or a spring may be disposed at the location of a spacer 80. In the present embodiment, the phrases �connect so as to rotate in a body� and �connect relatively unrotatably� mean that both portions are able to transmit torque in a circular direction. This embodiment also contains a condition in which a gap is formed in a rotary direction between the two portions. Within a predetermined angle, a torque is not transmitted between the two portions.
A hole 36 b is formed at the radially central part of the axially supporting part 36 a. The hole 36 b has an approximately trapezoid-like shape in which its radially outside part has a length in a circular direction smaller than that of its radially inside part.
Both circular end parts of the second receptacles 36 are cut and lifted in an axial direction. In other words, the second receptacles 36 are set off from the main body of the first retaining plate 31 or the second retaining plate 32. As a result, openings 36 e and 36 f are formed in the rotational direction on both sides of the second receptacle 36. The end faces of the second receptacles 36 of the plate main body form a pair of second supporting parts 37. The second supporting parts 37 touch both ends of the first spring 16 in a circular direction. The reason why both ends of the second receptacle 36 are cut off from the plate main body is to have a large �cut and lift� angle from the plate main body. This large angle exists in order to seat the first spring 16 with a large diameter in the second receptacle 36. When the coil spring 16 has a relatively small diameter, both ends of the second receptacle 36 do not need to be cut off. Rather, the axially supporting part 36 a can be connected continuously with the plate main body. For this reason, the part that supports both circular end parts of the coil spring 16 can be larger in the rectangular windows formed by the second receptacles 36.
As shown in FIG. 24, in the axially supporting part 36 a, the thickness of the portion of the axially supporting part 36 a that projects the most outwardly in an axial direction is smaller than that of other portions of the plate main body. Specifically, the thickness of the outer portion of the axially supporting part 36 a is smaller by distance �t� than the thickness of a conventional plate. The axially outside portion of the axially supporting part 36 a has a flat surface 36 c formed along this thinner portion.
Since the outer portion of the axially supporting parts 36 a of the second retaining plate 32 do not project outwardly in an axial direction as far as conventional supporting parts, axially supporting parts 36 a do not interfere with other portions of the clutch. This is particularly the case in a twin clutch in which two clutch disk assemblies IA and lB are disposed in an axial direction as shown in FIG. 25. The gap �T� between adjacent second receptacles 36 in an axial direction can be larger than the gap of a conventional twin clutch. As a result, even if an abrasion of the friction facing occurs, the clutch disk assemblies IA and IB will not interfere with each other.
Each of the second holes 36 f has its long axis extending in a radial direction. More specifically, the second holes 36 f extend longitudinally in the same direction as the circular end part of the axially supporting part 36 a or the second supporting part 37 extends.
A method of forming the second receptacles 36 (rectangular window) will now be described in more detail. The holes 36 b, and first and second holes 36i e l and 36 f are formed in the plate main body of the second retaining plate 32 before bending of the plate main body of the retaining plate. The axially supporting part 36 a is formed to project outwardly from the plate main body in an axial direction by a conventional pressing or lifting method. The inner circumferential portion of the axially supporting part 36 a is bent further out of the plane of the plate main body than the outer circumferential portion of the axially supporting part 36 a. Thus, a larger lift angle is formed at the inner angle lifted from the circumference such that more material is needed to sufficiently extend the second receptacle 36. In the present embodiment, the second holes 36 f are formed at the inner circumferential corners of the rectangular window or second receptacle 36. In addition, the second holes 36 f extend radially to allow a large lift angle of the axially supporting part 36 a at its inner circumferential portion. The result is that, during manufacture of the rectangular window of the second receptacle 36, cracking seldom occurs. Also, during use of the device, when torque is applied to the rectangular window of the second receptacle, cracking seldom occurs.
Referring now to FIG. 29, the structure of another embodiment of second retaining plate 32 will now be discussed. In this embodiment, a large hole 36 g is formed at each end of the second receptacle 36. The holes 36 g extend longitudinally in a radial direction. In other words, holes 36 g are formed at both circular end parts of the axially supporting part 36 a. The holes 36 g extend completely over the axially supporting part 36 a in a radial direction. Both radial end parts of the holes 36 g have a round shape, which is larger than the rest of hole 36 g. The hole 36 g has a cutout shape in which both circular side parts are open. The radial inside end of the hole 36 g further extends from the axially supporting part 36 a to the inside in a radial direction, and is formed as a part of the plate main body. This cutout of hole 36 g leads to a similar effect to that obtained in the second receptacle 36 in FIG. 28.
As shown in FIG. 26, the radial outside of axially supporting part 36 a is supporting part 36 d, which supports the radial outside of the first spring 16. A gap is formed in a radial direction between the radially outside supporting part 36 d and the radially outside part of the first spring 16. The radially outside supporting part 36 d includes an intermediate part 36 h located at the intermediate section in a circular direction, and a circular end part 36 i which is formed at both sides of the intermediate part 36 h in a circular direction. The intermediate part 36 h extends in an arc like shape along an orbit �A� which is formed when the first spring 16 is compressed. The circular end part 36 i is formed so as to project outwardly in a radial direction from the intermediate part 36 h. In other words, the circular end part 36 i is located outwardly in a radial direction from the orbit �A� of the first spring 16. The circular end part 36 i is formed corresponding to an end turn 16 a (one turn at both circular end parts) of the first spring 16, and is radially spaced apart from the outside part of the end turn 16 a In the structure mentioned above, when the first spring 16 is compressed, the first spring 16 rubs the second receptacle 36. At that time, a centrifugal force moves the first spring 16 outwardly in a radial direction, the first spring 16 rubs the radially outside supporting part 36 d. In particular, the first spring 16 mainly rubs the intermediate part 36 h, resulting in an abrasion thereof. For example, the first spring 16 rubs against a shaded part B as shown in FIG. 27. However, since the first spring 16 does not rub the circular side part 36 i, the thickness of the radially outside corner part of the second receptacle 36 does not change. In other words, the strength of the radially outside corner part of the second receptacle 36 is maintained. For this reason, the corner part of the second receptacle 36 is less likely to form cracks. The result is that the life span of the plates 31 and 32 can be extended.
In a plate used for a dampening disk assembly relating to the present invention, both circular end parts of a second supporting part to support a radially outside part of a coil spring is located outward in a radial direction from a circular intermediate part. Therefore, when the coil spring operates, the coil spring barely rubs both circular end parts. As a result, the thickness of both circular end parts of the second supporting part is secured, resulting in maintaining its strength.
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