Patent Application
20080136075
The present invention relates to coned disc springs that are used to absorb shocks occurring during the engaging of a clutch of a multiplate clutch structure of a transporting machine. Specifically, the present invention relates to improvement in a coned disc spring comprising teeth for inhibiting relative rotation with respect to a clutch drum.
A wet-type multiplate clutch structure is used as a clutch structure in a transmission of a transporting machine. The wet-type multiplate clutch structure comprises a coned disc spring used for absorbing shocks occurring during the engaging of a clutch.
Driven plates 103 and driving plates 104 are alternately arranged with predetermined spaces between the clutch drum 101 and the clutch hub 102. The driven plate 103 is closely fitted to the spline groove 101A of the clutch drum 101, and the driving plate 104 is closely fitted to the spline groove 101A of the clutch hub 102, and they can move in the axial direction. A piston 105, which is movable in the axial direction, is provided at the bottom side of the clutch drum 101. An oil pressure space 106 is provided between the piston 105 and the clutch drum 101.
A coned disc spring 200 having a hole in the center and a circular dish shape is provided between the driven plate 103, which is on the bottom side of the clutch drum 101, and the piston 105. The coned disc spring 200 is supported by the driven plate 103 at the surface of the outer periphery, and by the piston 105 at the back of the inner periphery.
In the above multiplate clutch structure 100, when operating oil is supplied to the oil pressure space 106, the piston 105 driven by oil pressure presses the driven plate 103, which is on the bottom side of the clutch drum 101, through the coned disc spring 200. Then, the driven plate 103 on the bottom side of the clutch drum 101 moves to the opening of the clutch drum 101, and friction surfaces of the driven plate 103 and the driving plate 104, which are placed oppositely to each other, engage, whereby they are clutched. In this case, the coned disc spring 200 elastically deforms from the dish shape to become flattened, thereby absorbing shocks that occur during the engaging of the clutch.
The above coned disc spring 200 has a circular shape, whereby it tends to relatively rotate with respect to the clutch drum 101 during rotation of the clutch structure 100. Therefore, the coned disc spring 200 frequently hits the inside wall of the clutch drum 101, which may cause a problem of wear on the inside of the wall of the clutch drum 101.
In order to solve the above problem, a coned disc spring 300 has been proposed (for example, see Japanese Unexamined Patent Application Publications Nos. 2001-295860 and H9-329155). As shown in
When the above coned disc spring 300 is elastically deformed during the engaging of a clutch, a concentration of stress occurs at the base of the teeth 311. Therefore, there has been a problem in that the durability of the coned disc spring 300 is greatly decreased.
In order to reduce the stress that may occur at the base of the teeth 311, a radius of curvature R of a circular arc portion 311A at the base of the teeth 311 may be enlarged. In this case, the circular arc portion 311A at the base of the teeth 311 extends in the circumferential direction and projects to the radial outer side. Therefore, if a corner portion of the spline groove 101A of the clutch drum 101 is sharp, the base of the tooth 311 heavily interferes with the spline groove 101A during rotation of the clutch drum 101. Accordingly, wear of the spline groove 101A caused by the tooth 311 increases. Moreover, a length L of a straight portion 311B on the side of the teeth 311 is shortened, and the area in which the tooth 311 and the spline groove 101A are closely fitted is decreased. Therefore, a contact pressure due to the tooth 311 at the spline groove 101A is increased, and the wear of the spline groove 101A caused by the tooth 311 is increased. Specifically, in order to ensure that the display of the correct mileage of an automobile, which has been increasing recently, the coned disc spring 300 is required to be highly durable. Accordingly, the above problems need to be solved.
An object of the present invention is to provide a coned disc spring by which a stress occurring at a base of a tooth during the engaging of a clutch is decreased, and by which wear of a spline groove caused by the tooth is decreased.
The present invention provides a coned disc spring arranged between a second and a third component provided inside a tubular first component and which is movable in an axial direction. The coned disc spring comprises a body having a circular dish shape, teeth, and a stress relaxation portion. The tooth closely fits into a spline groove formed on an inner peripheral surface of the first component, and it projects to a radial outer side on an outer periphery of the body. The stress relaxation portion is formed by notching a base of the tooth in approximately circular arc shape in a direction of at least one of a circumferential direction and a radial direction of the body.
The coned disc spring of the present invention comprises a stress relaxation portion formed by notching the base of a tooth in approximately a circular arc shape in a direction of at least one of a circumferential direction and a radial direction. Therefore, the base of the tooth may have a large radius of curvature R without projecting to the radial outer side. Accordingly, when the above coned disc spring is arranged between a driven plate and a piston in a clutch structure of a transporting machine, the stress relaxation portion can reduce stress occurring at the base of the tooth during the engaging of the clutch. Moreover, even if a corner portion of a spline groove of a clutch drum is sharp, the base of the tooth does not interfere with the spline groove during rotation of the clutch drum, whereby wear of the spline groove caused by tooth can be reduced. Therefore, the coned disc spring may be highly durable, thereby ensuring proper display of recently increasing automobile mileage.
Various shapes of the coned disc spring of the present invention are explained with reference to
When the radius of curvature R of the base of a tooth of the conventional coned disc spring “a” is enlarged, the stress occurring thereat is decreased. In this case, the circular arc portion of the base of the tooth extends along the circumferential direction and projects to the radial outer side. Therefore, as mentioned above, if a corner portion of the spline groove of the clutch drum is sharp, the base of the tooth heavily interferes with the spline groove. Accordingly, wear of the spline groove caused by the tooth is increased. Moreover, the length of a straight portion at the side of the tooth is shortened, whereby an area in which the tooth and the spline groove are closely fitted is decreased. Therefore, a contact pressure occurring due to the tooth at the spline groove is increased, and wear of the spline groove caused by the tooth is increased. Accordingly, if the radius of curvature R of the base of the tooth is set to be larger than the value of point P on the curve (a), the durability of the coned disc spring is greatly reduced. As a result, the radius of curvature R cannot be set to be larger than the value of point P.
On the other hand, the coned disc spring “b” of the present invention comprises a stress relaxation portion formed by notching the base of a tooth in approximately a circular arc shape in the radial direction. Therefore, if a corner portion of the spline groove of the clutch drum is sharp, even if the radius of curvature R of the base of the tooth is set to be larger than that of the conventional coned disc spring “a”, the tooth does not interfere with the spline groove. Accordingly, when the coned disc spring “b” of the present invention is compared to a conventional coned disc spring “a”, it may be set to have a large radius of curvature R at the base of the tooth, such as the value of point Q, whereby stress occurring at the base of the tooth during the engaging of the clutch is reduced.
The coned disc spring “c” of the present invention comprises a stress relaxation portion formed by notching the base of a tooth in approximately a circular arc shape along the circumferential direction. Therefor, even if the coned disc spring “c” is set to have a larger radius of curvature R at the base of the tooth than that of a conventional coned disc spring “a”, the tooth does not interfere with the spline groove, as in the case of the coned disc spring “b” of the present invention. Accordingly, when the coned disc spring “c” of the present invention is compared to the conventional coned disc spring “a”, it may be set to have a large radius of curvature R at the base of the tooth such as the value of point R. In this case, when the coned disc spring “c” of the present invention has a similar degree of radius of curvature R at the base of the tooth with respect to the coned disc spring “b”, stress occurring thereat is very small. Therefore, when the coned disc spring “c” is compared to the coned disc spring “b” of the present invention, stress occurring at the base of the tooth thereof is further reduced.
The coned disc spring “b” of the present invention has a longer straight portion at the side of the tooth than that of the coned disc spring “c” of the present invention. Therefore, the area in which the tooth and the spline groove are closely fitted is large, and the contact pressure thereat can be reduced. Thus, when the coned disc spring “b” is compared to the coned disc spring “c”, wear of the spline groove caused by the tooth during rotation of the clutch drum is further reduced.
The coned disc spring “d” comprises a stress relaxation portion of which the shape is formed by combining the relaxation portions of the coned disc springs “b” and “c”. Therefore, as shown by the curve “d” in
The coned disc springs “b”, “c”, and “d” of the present invention may have various compositions so as to improve the characteristics thereof. For example, the stress relaxation portion of the above coned disc spring “b” may comprise a first circular arc portion and a second circular arc portion. The first circular arc portion has opposite first and second ends and is formed in a circular arc shape, and the first end is smoothly connected to the outer periphery of the body. The second circular arc portion has opposite first and second ends and is formed in a circular arc shape, and the first end is smoothly connected to the second end of the first circular arc portion, and the second end is smoothly connected to a side of the tooth. In this case, the first circular arc portion may have a larger radius of curvature than that of the second circular arc portion. According to this aspect, the second circular arc portion, which has a smaller radius of curvature R than that of the first arc portion, smoothly connects the first arc portion, which is connected to the outer periphery of the body, and a boundary between the stress relaxation portion and the side of the tooth. Therefore, the side of the tooth of the stress relaxation portion may have a longer straight portion than that of the tooth comprising a stress relaxation portion composed of one circular arc portion. Accordingly, wear of the spline groove caused by the tooth during rotation of the clutch drum is further reduced.
The above coned disc spring “c” may comprise a third circular arc portion, a straight portion, and a fourth circular arc portion. The third circular arc portion has opposite first and second ends and is formed in a circular arc shape, and the first end is smoothly connected to the outer periphery of the body. The straight portion has opposite first and second ends and extends to an approximately radial inner side of the body, and the first end is smoothly connected to the second end of the third circular arc portion. The fourth circular arc portion has opposite first and second ends and is formed in a circular arc shape, and the first end is smoothly connected to the second end of the straight portion, and the second end is smoothly connected to a side of the tooth. According to this aspect, when a coned disc spring is pressed in manufacturing, components of a die corresponding to the base of the tooth may have an improved durability.
The coned disc spring of the present invention comprises a stress relaxation portion at the base of the tooth. For example, when it is arranged between a driven plate (a second component) and a piston (a third component) at the inside of a clutch drum (a first component) of a clutch structure, the stress relaxation portion can reduce stress occurring at the base of the tooth during the engaging of the clutch. Moreover, even if a corner portion of the spline groove of the clutch drum is sharp, the tooth does not interfere with the spline groove during rotation of the clutch drum, whereby wear of the spline groove caused by the tooth may be reduced.
1 to 4 denote coned disc springs, 10 denotes a body, 11 denotes a tooth, 12, 22, 32, and 42 denote stress relaxation portions, 12A to 12C, 22A, 22B, 32A, 32C, 42A, and 42B denote circular arc portions, 32B denotes a straight portion, 101 denotes a clutch drum (a first component), 103 denotes a driven plate (a second component), 101A denotes a spline groove (a groove), and 105 denotes a piston (a third component).
A first embodiment of the present invention is explained with reference to the drawings.
The base of the teeth 11 is notched in approximately a circular arc shape along the circumferential direction to form a stress relaxation portion 12. For example, when the stress relaxation portion 12 is provided to the following clutch structure 100, it relaxes the stress concentrated at the base of the teeth 11 during the engaging of the clutch. The stress relaxation portion 12 comprises circular arc portions 12A to 12C that have a circular arc shape and are formed from the outer periphery of the body 10 toward the side of the teeth 11, in that order. The circular arc portion 12A (a first circular arc portion) has opposite first and second ends, and the first end is smoothly connected to the outer periphery of the body 10. The circular arc portion 12B (a second circular arc portion) has opposite first and second ends, and the first end is smoothly connected to the second end of the circular arc portion 12A. The circular arc portion 12C has opposite first and second ends, and the first end is smoothly connected to the second end of the circular arc portion 12B, and the second end is smoothly connected to the side of the teeth 11. In this case, the circular arc portion 12A has a radius of curvature R, which is, for example, twice as large as that of the circular arc portion 12B.
The above coned disc spring 1 may be applied to a clutch structure 100 shown in
The clutch structure 100, for example, is a wet-type multiplate clutch structure used for automatic cars. The clutch structure 100 comprises a cylindrical clutch drum 101 (a first component) having a bottom. Plural spline grooves 101A, extending in the axial direction, are formed along the circumferential direction on the inner peripheral surface of the clutch drum 101. A tubular clutch hub 102 is provided to the clutch drum 101 and has a common rotation axis with respect to the clutch drum 101. Plural spline grooves 102A, extending in the axial direction, are formed at equal intervals along the circumferential direction on the outer periphery of the clutch hub 102.
A driven plate 103 (a second component) and a driving plate 104, which have a circular disc shape and are each formed with a hole in the center, are alternately arranged at predetermined intervals between the clutch drum 101 and the clutch hub 102. The driven plate 103 is formed with plural teeth on the outer periphery thereof at equal intervals along the circumferential direction, and the teeth are closely fitted to the spline grooves 101A. Therefore, the driven plate 103 cannot relatively rotate with respect to the clutch drum 101, but it can move in the axial direction. The driving plate 104 is formed with plural teeth on the inner periphery thereof at equal intervals along the circumferential direction, and the teeth are closely fitted to the spline grooves 102A. Therefore, the driving plate 104 cannot relatively rotate with respect to the clutch hub 102, but it can move in the axial direction.
A piston 105 (a third component), which is movable in the axial direction, is provided at the bottom side of the clutch drum 101. An oil pressure space 106, to which operating oil is supplied, is provided between the bottom of the clutch drum 101 and the piston 105. The piston 105 is driven by the operating oil supplied to the oil pressure space 106 in the axial direction. A return spring 107 is fixed by an end thereof on the surface of the piston 105 at the opening side of the clutch drum 101. The return spring 107 expands and contracts by pressure loaded thereon. The return spring 107 is fixed to a spring retainer 108 by another end thereof. The return spring 107 biases the piston 105 to the bottom of the clutch drum 101.
The above coned disc spring 1 is arranged between the driven plate 103, which is on the bottom side of the clutch drum 101, and the piston 105. In this case, in the coned disc spring 1, the teeth 11 are splined to the spline grooves 101A, the body 10 is supported by the driven plate 103 at the surface of the outer periphery thereof, and the body 10 is simultaneously supported by the piston 105 at the back of the inner periphery thereof. Therefore, the coned disc spring 1 cannot relatively rotate with respect to the clutch drum 101, but it can move in the axial direction.
In the clutch drum 101, in order that the driven plate 103 and the driving plate 104 do not move beyond a predetermined position, a retaining plate 109 is arranged at the opening side thereof. The retaining plate 109 is formed with plural teeth on the outer periphery thereof at equal intervals along the circumferential direction, and the teeth are closely fitted to the spline groove 101A. Therefore, the retaining plate 109 cannot relatively rotate with respect to the clutch drum 101, but it can move in the axial direction. A snap ring 110 is arranged on the surface of the retaining plate 109 at the opening side of the clutch drum 101, so that the retaining plate 109 does not go off to the outside. The snap ring 110 is latched together with a ring groove formed on an end of the opening side of the clutch drum 101.
The operation of the clutch structure 100 provided with the coned disc spring 1 will be explained with reference to
When an operating oil is supplied to the oil pressure space 106, the piston 105 is driven by the oil pressure, and it moves toward the opening side of the clutch drum 101 along the axis line with respect to the bias power of the return spring 107. The piston 105 presses the driven plate 103, which is on the bottom side of the clutch drum 101, through the coned disc spring 101. Then, the driven plate 103 and the driving plate 104, which are alternately arranged, and the retaining plate 109 move to the opening side of the clutch drum 101 along the axis line. Thus, when the retaining plate 109 is pushed by the snap ring 110, the friction surfaces of the driven plate 103 and the driving plate 104 which oppose each other, are engaged and are clutched. Therefore, torque can be transmitted from the clutch drum 101 to the clutch hub 102.
In this case, the coned disc spring 1 is elastically deformed from the dish shape to flattish shape, whereby it absorbs the shocks occurring during the engaging of the clutch. When the coned disc spring 1 is elastically deformed, stress occurring at the base of the teeth 11 is reduced by the stress relaxation portion 12. The stress relaxation portion 12 does not project to the radial outer side, whereby the tooth 11 does not interfere with the spline groove 101A during rotation of the clutch drum 101.
When the supply of the operating oil to the oil pressure space 106 is stopped, the piston 105 is pushed back to the bottom side of the clutch drum 101 by the bias power of the return spring 107. Then, the friction surfaces of the driven plate 103 and the driving plate 104 are disengaged and are unclutched, and the coned disc spring 1 simultaneously returns to the former shape.
In the above first embodiment, the coned disc spring 1 comprises a stress relaxation portion 12 formed by notching the base of the tooth 11 in an approximately circular arc shape, whereby the base of the tooth 11 can have a large radius of curvature R without projecting to the radial outer side. Therefore, when the above coned disc spring 1 is arranged between the driven plate 103 and the piston 105 in the clutch structure 100 of a transporting machine, the stress relaxation portion 12 can reduce the stress occurring at the base of the teeth 11 during the engaging of the clutch. Furthermore, even if a corner portion of the spline groove 101A of the clutch drum 101 is sharp, the tooth 11 does not interfere with the spline groove 101A during rotation of the clutch drum 101, whereby wear of the spline groove 101A caused by the tooth 11 may be reduced. Accordingly, the coned disc spring 1 may be highly durable, thereby ensuring the accurate displays of the recently increasing mileage of automobiles.
Specifically, in the stress relaxation portion 12, a circular arc portion 12B, which has a smaller radius of curvature R than that of a circular arc portion 12A, smoothly connects the circular arc portion 12A, which is connected to the outer periphery of a body 10, and a boundary between the stress relaxation portion 12 and the side of the teeth. Therefore, the side of the teeth 11 of the stress relaxation portion may have a longer straight portion than that of the teeth comprising a stress relaxation portion composed of one circular arc portion. Accordingly, wear of the spline groove 101A caused by the teeth 11 during the engaging of the clutch drum 101 is further reduced.
A second embodiment of the present invention is explained with reference to
In a coned disc spring 2 of the second embodiment, a stress relaxation portion 12 is not formed by notching the base of the teeth 11 in circular arc shape along the circumferential direction, unlike the first embodiment. The stress relaxation portion 22 is formed by notching the base of the teeth in approximately a circular arc shape in a radial direction, which is shown in
A third embodiment of the present invention is explained with reference to
In a coned disc spring 3 of the third embodiment, a stress relaxation portion 22, comprising circular arc portions 22A and 22B, is not formed by notching in radial direction at the base of the tooth 11, which is shown in the second embodiment. As shown in
A fourth embodiment of the present invention is explained with reference to
In the coned disc spring 4 of the fourth embodiment, as shown in
The present invention is explained with reference to the first to fourth embodiment, but this is not limited to the first to the fourth embodiment, and various compositions are possible. For example, in the first to fourth embodiment, a coned disc spring of the present invention is used for a wet-type multiplate clutch for automatic cars, but this is not limited thereto. For example, the coned disc spring of the present invention may be used for a multiplate clutch structure of a construction machine and a transporting machine such as two-wheeled motor vehicles.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2005-035247 | Feb 2005 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2006/302348 | 2/10/2006 | WO | 00 | 9/4/2007 |
