Damper disk assembly having integral retaining plate connecting means

Abstract: A clutch disk assembly includes axially opposed clutch and retaining plates 3 and 4. A flange having a plurality of circumferentially long recesses is arranged between clutch and retaining plates. A plate coupling portion 30 extends through a recess at the flange and connects the clutch and retaining plates 3 and 4 together.

Description: BACKGROUND OF THE INVENTION A. Field of the Invention The present invention relates to a damper disk assembly. B. Description of Related Art A clutch disk assembly used in a clutch for an automotive vehicle typically includes a pair of input plates opposed to each other, an output hub formed with a radial flange, and coil springs disposed between the flange and the input plates for elastically coupling the paired input plates to the flange but allowing limited relative rotary displacement therebetween. The paired input plates are fixed together at their radially outer portions by a plurality of stop pins for integral rotation. The stop pins extend through recesses formed near the outer periphery of the flange, respectively. The input plates are rotatable relative to the flange through a predetermined angle. When the stop pins are brought into contact with edges of the recesses, the input plates stop its rotation relative to the flange. The conventional clutch disk assembly described above uses the stop pins as members for restricting relative rotation between the input plates and the flange. Each stop pin requires a minimum diameter, and for structural strength must be located radially inside the outer periphery of the input plates. Due to the limiting conditions associated with the arrangement of the stop pins, the torsion angle within which relative rotation between the paired input plates and the flange occurs cannot be easily increased. This means that, even if hard coil springs are used, the capacity or properties of the coil springs cannot be fully utilized, because the relative torsion angle cannot be increased sufficiently. US 4,570,775 describes a clutch plate assembly comprising two coaxial parts mounted for relative rotation within a predetermined range of angular displacement against the action of springs. One coaxial part comprises a hub flange and the other coaxial part comprises two annular guide members. An axial ring is fixed to the first annular guide member and circumferentially spaced tenons secure the second annular guide member to the axial ring through notches in the latter. The hub flange has circumferentially spaced radial lugs received with clearance in recesses in the axial ring. The recesses and notches in the axial ring are circumferentially offset relative to one another. The free edge of the axial ring axially closes off the recesses. DE 44 38 468 A1 describes a damper disk assembly having a plate portion extending axially. According to this document a first circular plate is connected via a plug-in connection to a second circular plate. DE 83 09 592 U1 further discloses a damper disk assembly having a first and second circular plate. Both circular plates have radially outwardly extending portions which are fixed to each other by rivets. SUMMARY OF THE INVENTION An object of the invention is to provide a damper disk assembly with a construction which overcomes the disadvantages associated with the necessary configuration of stop pins in the prior art, and to provide the damper disk assembly with a sufficient increase in a relative torsion angle between an input member and an output member, as compared with the prior art. According to the invention, the object is solved by the combination of features of claim 1. The sub-claims contain further preferred developments of the invention. The foregoing and other objects, features, aspects and advantages of the present invention will become more apparent from the following detailed description, when taken in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross sectional side view of a clutch disk assembly in accordance with a first embodiment of the present invention taken along the line I-I in Fig. 2; Fig. 2 is a partial cutaway, part cross section and part elevational view of the clutch disk assembly shown in Fig. 1; Fig. 3 is a fragmentary, cross sectional view of a portion of the clutch disk assembly depicted in Fig. 1, on a slightly enlarged scale; Fig. 4 is a fragmentary, elevational view of a portion of the clutch disk assembly depicted in Figs. 1 and 2, on a slightly enlarged scale; Fig. 5 is a perspective view of a portion of the clutch disk assembly depicted in Figs. 1 and 2, showing a plate coupling portion of the clutch disk assembly; Fig. 6 is a cross sectional side view similar to Fig. 1, showing a clutch disk assembly in accordance with a second embodiment of the present invention taken along the line VI-VI in Fig. 7; Fig. 7 is a plan of the clutch disk assembly of the second embodiment; DESCRIPTION OF THE PREFERRED EMBODIMENTS First Embodiment A clutch disk assembly 1 shown in Figs. 1 and 2 is provided for selectively transmitting torque from a flywheel (not shown) of an engine to a transmission (not shown). In Fig. 1, line O-O represents a rotation axis of the clutch disk assembly 1. When installed in an automotive vehicle, the clutch disk assembly 1 is configured for installation with the engine (not shown) positioned to the left side of Fig. 1 and the transmission (not shown) positioned to the right side of Fig. 1. For convenience, henceforth the left side of Fig. 1 will be referred to as the engine side and the right side of Fig. 1 will be referred to as the transmission side. The clutch disk assembly 1 includes, as major components, a frictional coupling portion 2, input plates which are specifically a clutch plate 3 and a retaining plate 4, coil springs 5, first and second intermediate plates 6 and 7, and a spline hub 8. The frictional coupling portion 2 is adapted to be pressed against the flywheel (not shown). The frictional coupling portion 2 includes a cushioning plate 16, and first and second friction facings 17 and 18. The cushioning plate 16 is formed with an annular portion 16a and a plurality of cushioning portions 16b which are formed at the outer periphery of the annular portion 16a and are arranged in the circumferential direction. The annular portion 16a is fixed to the clutch and retaining plates 3 and 4 by four fixing rivets 21, as will be described in greater detail below. The first friction facing 17 at the engine side and the second friction facing 18 at the transmission side are fixed to the opposite surfaces of the cushioning portions 16b of the cushioning plate 16 by rivets 19, respectively. The clutch and retaining plates 3 and 4 are annular plate members, and are axially spaced from each other by a predetermined distance. The retaining plate 4 is provided at its outer periphery with four plate coupling portions 30 which are generally equally circumferentially spaced from each other, as shown in Figs. 3 to 5. Each plate coupling portion 30 is generally formed with an extension 31 and a claw or tongue 32. Each extension 31 is formed unitarily with the retaining plate 4 as a single element, the extension 31 being bent at an outer periphery of the retaining plate 4 toward the clutch plate 3. The extension 31 has a predetermined circumferential width. The claw 32 extends radially inwardly from the extension 31, being bent radially inward from the extension 31. The claw 32 is in contact with the annular portion 16a of the cushioning plate 16. The claw 32 is provided with an aperture 32a into which the fixing rivet 21 is inserted. The claw 32 has a smaller circumferential width than the extension 31. Each of the fixing rivets 21 extend through a corresponding aperture formed in the clutch plate 3, a corresponding aperture formed in the annular portion 16a of the cushioning plate 16 and one aperture 32a thus fixing the clutch plate 3, cushioning plate 16 and the claws 32 of the retaining plate 4 together. The retaining plate 4 is provided with caulking apertures 33 at positions corresponding to the claws 32 to allow for insertion and deformation of the rivets 21 during assembly, as is described in greater detail below. Each of the clutch and retaining plates 3 and plate 4 is provided at its radially outer portion with circumferentially equally spaced four openings or windows 3a or 4a. Each of the windows 3a and 4a is provided at its radially inner and outer edges with cut and bent portions 3b or 4b. The spline hub 8 is arranged coaxially with the plates 3 and 4. The spline hub 8 includes an axially extending cylindrical boss 8 and a radial flange 10 extending integrally from the boss 9. The boss 9 is provided at its inner periphery with a spline aperture 9a fitted to a shaft (not shown) which extends from the transmission (not shown). The flange 10 has openings or windows 10a at positions corresponding to the windows 3a and 4a. The flange 10 is also provided at its outer periphery with four recesses 10b corresponding to the plate coupling portions 30. The flange 10 also has circumferentially extending contact concavities 10c which are located at circumferentially opposite portions of each recess 10b. The above described configuration is such that, compared to the prior art, allows for an increase in the maximum value of the relative rotation angle of the plates 3 and 4 with respect to the flange 10. The first intermediate plate 6 is arranged between the clutch plate 3 and the flange 10. The second intermediate plate 7 is arranged between the flange 10 and the retaining plate 4. These plates 6 and 7 have outer diameters generally equal to those of the clutch and retaining plates 3 and 4, but have inner diameters larger than the inner diameter of the plates 3 and 4, as can be seen in Fig. 1. The first and second intermediate plates 6 and 7 have openings 6a and 7a at positions corresponding to the openings 3a, 4a and 10a, respectively. The openings 6a and 7a are circumferentially shorter than the openings 3a, 4a and 10a. The coil springs 5 are arranged in the windows 3a, 4a, 6a, 7a and 10a. As can be seen from the figure, each coil spring 5 is actually defined by two coaxially arranged springs, one large coil spring and small coil springs. Each pair of coaxial coil springs will herein after be referred to as the coil spring 5 for simplicity. Circumferentially opposite ends of each coil spring 5 are in contact with the edges of the windows 3a and 4a and the edges of the windows 6a and 7a. In Fig. 2, the four coil springs 5 are shown, one in a lower position, one on the engine side or left side, one in an upper position and one on the transmission or right side. The configuration of the coil springs 5 on the left and lower sides will now be described. It should be appreciated that the coil springs 5 in the upper and right sides are configured generally the same as the coil springs 5 in the lower and left sides. The left coil spring 5 is arranged such that the end at the R2 side, i.e., the end forming the forward end in the direction R2, is in contact with the edges of the windows 3a, 4a and 10a, and the end at the R1 side, i.e., the end forming the forward end in the direction R1, is spaced by a predetermined distance from the edges of the windows 3a, 4a and 10a. The lower coil spring 5 is arranged such that the end at the R1 side is in contact with the edges of the windows 3a, 4a and 10a, and the end at the R2 side is spaced by a predetermined distance from the edge of the windows 3a, 4a and 10a. Thus, the end of the coil spring 5 in the left position adjacent to the coil spring 5 in the lower position of is spaced from the edges of the windows 3a, 4a and 10a. Opposite ends of each coil spring 5 are in contact with the edges of the windows 6a and 7a of the first and second intermediate plates 6 and 7. In this manner, the left and lower coil springs 5 are arranged in series to couple the plates 3 and 4 to the flange 10 via the intermediate plates 6 and 7. The other set of the two coil springs 5 at the upper and right positions in Fig. 2 are arranged similarly to the above. A first friction washer 11 is arranged between radially inner portions of the flange 10 and the retaining plate 4. The first friction washer 11 has an annular or circular potion which is in contact with the surface of the flange 10 facing the transmission side. The first friction washer 11 has engagement projections 11a for snap-fit. The engagement projections 11a are axially movable with respect to the first friction washer 11 but are engaged with apertures formed at a radially inner portion of the retaining plate 4 such that the first friction washer 11 cannot rotate with respect to the retaining plate 4. A conical spring 12 is arranged between the circular portion of the first friction washer 11 and the retaining plate 4. The conical spring 12 thus arranged is axially compressed so that it axially biases the first friction washer 11 and the retaining plate 4 away from each other. The second friction washer 13 is arranged between the radially inner portions of the clutch plate 3 and the flange 10. The second washer 13 is in contact with the flange 10 and the outer periphery of the boss 9. The second friction washer 13 has axially projected engagement projections 13a for snap-fit, which are axially movably with respect to the clutch plate 3 but are engaged in apertures formed at the radially inner portion of the clutch plate 3 such that the second friction washer 13 cannot rotate with respect to the clutch plate 3. Operation of the clutch disk assembly 1 will be described below. When the friction coupling portion 2 is coupled to the flywheel (not shown), a torque is transmitted from the flywheel to the spline hub 8 via the friction coupling portion 2, clutch and retaining plates 3 and 4, coil springs 5, first and second intermediate plates 6 and 7, and coil springs 5. The torque is further transmitted from the spline hub 8 to the shaft (not shown) extending from the transmission (not shown). When a torsional vibration due to, e.g., variation in combustion of the engine is transmitted to the clutch disk assembly 1, the respective plates perform periodical relative rotation, so that the coil springs 5 are compressed, and the first and second friction washers 11 and 13 slide on the flange 10 to generate a hysteresis torque by producing friction. Torsion characteristics will be described below. In the following description, it is assumed that the spline hub 8 is fixed to an appropriate stationary member, and the clutch and retaining plates 3 and 4 are rotated relatively to the spline hub 8. With respect to the operation of the coil springs 5, the following description will be given only on one set of the left and lower coil springs 5. In Fig. 2, the plates 3 and 4 are shown in a torsion free state. When the plates 3 and 4 are rotated in the direction R1 from the torsion free state, the edges of the windows 3a and 4a in the plates 3 and 4 push the left coil spring 5, which in turn pushes the lower coil spring 5 via the intermediate plates 6 and 7. The left coil spring 5 is compressed between the plates 3 and 4 and the intermediate plates 6 and 7. The lower coil spring 5 is compressed·between the intermediate plates 6 and 7 and the flange 10. Thus, the left and lower coil springs 5 act in series. Simultaneously, the right and upper coil springs 5 act in series in a similar manner. This results in low-rigidity characteristics. When the torsion angle increases, the end at the R1 side of the left coil spring 5 is brought into contact with the edge of the left window 10a in the flange 10, and the edges of the lower windows 3a and 4a are brought into contact with the end at the R2 side of the lower coil spring 5. Consequently, both the coil springs 5 are compressed in parallel between the edges of the windows 3a and 4a in the clutch and retaining plates 3 and 4 and the edge of the window 10a in the flange 10. This provides high-rigidity characteristics. During this operation, the first and second intermediate plates 6 and 7 do not make relative rotation. When the torsion angle further increases to a predetermined amount, the extensions 31 of the plate coupling portions 30 are brought into contact with the contact concavities 10c of the recesses 10b formed at the flange 10. This stops relative rotation of the clutch and retaining plates 3 and 4 with respect to 'the spline hub 8. The first embodiment described above and shown in Figs. 1 through 5 does not employ conventional stop pins. Rather, present invention provides a structure in which the plate coupling portions 30 couple the clutch and retaining plates 3 and 4 together and restrict relative rotation of the plates 3 and 4 with respect to the flange 10. Therefore, the maximum relative torsion angle can be larger than that in the prior art where stop pins are employed. In particular, the extension 31 can be circumferentially shorter than the conventional stop pin, which can further increase the maximum relative torsion angle. An assembly operation of the clutch disk assembly 1 will be described below. First, the spline hub 9, cushioning plate 16, first and second intermediate plates 6 and 7 and others are arranged on the clutch plate 3, and the retaining plate 4 is arranged with respect to them on the clutch plate 3. In this operation, the apertures 32a in the claws 32 of the retaining plate 4 are aligned to the apertures in the clutch plate 3 and the retaining plate 16. In this state, the fixing rivets 21 are inserted into the connection apertures from the clutch plate side. Dies for rivet caulking are inserted into caulking apertures 33 formed at the retaining plate 4 and the recesses 10b at the flange 10, and heads of the fixing rivets 21 are deformed. In this manner, the clutch and retaining plates 3 and 4 are coupled together, and the cushioning plate 16 is fixed to the radially outer portion of the plates 3 and 4. The plate coupling portion described above is formed with an extension and claw extend integrally from the clutch plate. Alternatively, the plate coupling portion may be made of a separate member, independent of the clutch and retaining plates. Second Embodiment In the first embodiment described above, the boss of the spline hub is integral with the flange. In contrast to the first embodiment, a second embodiment is also within the scope of the present invention. The second embodiment has virtually all of the elements of the first embodiment above except that a spline hub is formed as a separate member from a flange. Further, an elastic member arrange between the spline hub and the flange. This structure further increases the maximum value of the total torsion displacement angle, and can provide lower-rigidity characteristics at the first stage in the relative rotation operation. Below, only the structure and operation of the second embodiment which differs from the first embodiment will be described below, and similar structure and operation will not be described below. The boss 9 is an axially extending cylindrical member, and has a spline aperture 9a fitted to the shaft extending from the unillustrated transmission. The boss 9 is integrally provided at its outer periphery with a flange 9b. The flange 9b has a plurality of outer teeth 9c projected radially outward. The separate flange 10 is provided at its inner periphery with a plurality of inner teeth 10d, each of which is located between the adjacent outer teeth 9c. A circumferential space is defined between the teeth 10d and 9c neighboring to each other. The flange 9b is provided with a circumferentially long recess 9d, and a recess 10e is formed at the position in the separate flange 10 corresponding to the recess 9d. A small coil spring 41 is arranged in the recesses 9d and 10e. A first friction washer 51 and a first conical spring 52 are arranged between the flange 9b and a radially inner portion of the retaining plate 4. The first friction washer 51 is in contact with the flange 9b, and the first conical spring 52 is axially compressed between the first friction washer 51 and the retaining plate 4. A second friction washer 53 and a second conical spring 54 are arranged between the separate flange 10 and the retaining plate 4. The second friction washer 53 is in contact with the separate flange 10, and the second conical spring 54 is axially compressed between the second friction washer 53 and the retaining plate 4. The second friction washer 53 has a plurality of engagement projections 53a for snap-fit projected toward the transmission. The engagement projections 53a are axially movable with respect to the retaining plate 4 but due to engagement with apertures formed at the radially inner portion of the retaining plate 4, the second friction washer 53 cannot rotate with respect to the retaining plate 4. Similarly, the first friction washer 51 is axially movable but is engaged with the second friction washer 53 so that the first and second friction washers 51 and 53 rotate together with the retaining plate 4. A third friction washer 55 is arranged between the flange 9b and the radially inner portion of the clutch plate 3. A fourth friction washer 56 is arranged between radially inner portions of the separate flange 10 and the clutch plate 3. The third friction washer 55 is in contact with the flange 9b, and is engaged with the clutch plate 3 such that it may not rotate with respect thereto. The fourth friction washer 56 is in contact with the separate flange 10 and the clutch plate 3. The fourth friction washer 56 is provided with a plurality of engagement projections 56a projected toward the engine. The engagement projections 56a are axially movably but are engaged with the clutch plate 3 such that the forth friction washer 56 may not rotate with respect to the clutch plate 3. The third and fourth friction washers 55 and 56 are engaged with each other such that they may not rotate with respect to one another. In this embodiment, only the small coil spring 41 having the lowest rigidity is compressed when the torsion angle is small. In this operation, only the first and third friction washers 51 and 55 frictionally slide on the flange 9b, so that a low hysteresis torque is generated. According to the damper disk assembly of the invention, a conventional stop pin is eliminated, and the plurality of plate coupling portions are employed for coupling the paired first circular plates together and restricting relative rotation between the first and second circular plates. Since the plate coupling portion can have a smaller circumferential width than a stop pin, the maximum relative torsion angle can be larger than that in the prior art. various details of the present invention may be changed without departing from its scope. Furthermore, the foregoing description of the embodiments according to the present invention are provided for illustration only, and not for the purpose of limiting the invention as defined by the appended claims.

Claims: A damper disk assembly comprising: - a pair of first circular plates (3, 4) axially opposed to each other; - a second circular plate (10) arranged between said paired first circular plates (3, 4) for rotation relative to the same; - an elastic member (5) being adapted to be compressed in response to relative rotation between said paired first circular plates and said second circular plate; and - plate portions (30) extending from the outer periphery of one of said paired first circular plates to the outer periphery of the other of said paired first circular plates and fixed to the other of said paired first circular plates; - said second circular plate (10) is formed with a plurality of long recesses (10c) arranged in the circumferential direction, and said plate portions (30) are composed of a plurality of axially extending plates circumferentially spaced from each other and extending in said plurality of recesses (10c), - wherein each of said axially extending plates can move in the circumferential direction within the respective recess (10c) to a certain degree to make a stopper for said paired first circular plates (3, 4) and said second circular plate (10), - said first circular plates are a pair of first annular plates (3, 4), - said second circular plate is a second annular plate (10) arranged between said first annular plates (3, 4), said second annular plate being formed with at least one circumferentially extending recess (10c) on an outer circumferential portion thereof; and the damper disk assembly further comprises: - said elastic member (5) disposed between said first annular plates; - wherein at least one of said axially extending plates extends through said recess connecting said first annular plates together - said plate portions comprise : - an extension (31) homogeneously formed with one of said paired first annular plates and axially extending from a radially outer portion thereof; and - a claw (32) formed on said extension, said claw extending radially inwardly, said claw being fixed to the other of said first annular plates, wherein said claw (32) is fixed to said other of said first annular plates by a rivet (21) which extends through said other of said first annular plates and said claw. A damper disk assembly according to claim 1, further comprising: - a third rotary circular plate (9b) being adjacent to said second circular plate (10) and having a circumferentially long recess (9d); and - a second elastic member (41) adapted to be circumferentially compressed by relative rotation between said second and third circular plates (9, 10), - wherein when the relative torsion angle between said first and third circular plates is small, said first of said first and second elastic members acting in series is compressed, and when said relative torsion angle is large, said first circular plates is in contact with and compresses said first elastic member. The damper disk assembly according to claim 1, further comprising a cushion plate (16) having a plurality of friction surfaces fixed thereto, said cushion plate being fixed to said claw and said other of said first annular plates. The damper disk assembly according to claim 1, further comprising first and second friction plates (11, 13), said first friction plate disposed between one of said first annular plates and said second annular plate, said second friction plate disposed between the other of said first annular plates and said second annular plate, said first and second friction plates for generating friction in response to relative rotation between said first annular plates and said second annular plate. The damper disk assembly according to claim 1, further comprising a hub (8) disposed radially inward from said second annular plate, said hub and said second annular plate being configured for limited rotary displacement with respect to one another. The damper disk assembly according to claim 5, further comprising first, second and third friction plates (51, 53, 55), said first friction plate disposed between one of said first annular plates and said second annular plate, said second friction plate disposed between the other of said first annular plates and said second annular plate, and said third friction plate disposed between said other of said first annular plates and said hub, said first and second friction plates for generating friction in response to relative rotation between said first annular plates and said second annular plate, and said third friction plate for generating friction in response to relative rotation between said first annular plates and said hub.

Inventors: MIZUKAMI HIROSHI, UENOHARA NORIHISA, MIZUKAMI, HIROSHI, UENOHARA, NORIHISA
Applicants: EXEDY CORP, EXEDY CORPORATION
Application year: 1997
Main classification: F16F15
IPC codes: F16F15, F16D13, F16D3