JP2004239311A - Friction clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve durability, and restrict generation of space between friction slide surfaces by enlarging sliding area. <P>SOLUTION: In a friction slide surface 65 of an outer clutch plate 63, a plurality of circumferential grooves 67 are provided in diametric directions to adjoin each other, so that torque is transmitted by friction engagement between the friction side surface 65 of the outer clutch plate 63 and a friction slide surface 83 of an inner clutch plate 81 in a pilot clutch 49. Protrusions are coupled in diametric directions to form a flat surface part 75 for composing the friction slide surface 65. Height of an edge part of the flat surface part 75 on the side of the groove 67 is set to be less than maximum height of a coarseness curve of the flat surface part 75 at less than 1 μm. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a friction clutch of a power transmission device mounted on a propeller shaft of an automobile or the like.
[0002]
[Prior art]
Conventional friction clutches include, for example, those shown in FIGS. FIG. 13 is a front view of a conventional clutch plate, and FIG.
[0003]
As shown in FIG. 13, the clutch plate 101 is provided with a large number of fine protrusions 105 extending in the circumferential direction on the friction engagement surface 103 in parallel at a fine interval.
[0004]
As shown in FIG. 14, the height _{h 1} from the frictional engagement surfaces 103 of the ridges 105 is formed above 1 [mu] m, distance _{h 2} in parallel is set to 600μm or less. Therefore, the ridge 105 remains even after long-term use, and the formation of an oil film between the inner and outer clutch plates can be prevented (for example, see Patent Document 1).
[0005]
[Patent Document 1]
Japanese Patent No. 3009382 [0006]
[Problems to be solved by the invention]
However, in the above-described friction clutch, the sliding area is reduced and the surface pressure is increased due to the presence of the ridge 105 on the friction engagement surface 103. Therefore, the wear of the clutch plate on the mating side that frictionally engages with the clutch plate 101 in FIG.
[0007]
Further, due to the presence of the ridge 105, a space is formed between the ridge 105 and the frictional engagement surface of the mating clutch plate. Therefore, when attempting to fasten such a clutch plate using electromagnetic force, the magnetic force is weakened by the presence of a large number of spaces between the friction engagement surfaces, so that a large electromagnet is required to obtain a predetermined fastening force, There is a possibility that the overall size and weight will increase.
[0008]
The present invention is directed to a friction clutch capable of increasing a sliding area, suppressing wear of a friction sliding surface, improving durability, and suppressing generation of a space between the friction sliding surfaces. Providing is an issue.
[0009]
[Means for Solving the Problems]
The invention according to claim 1 is provided with a plurality of circumferentially extending grooves on one side of the frictional sliding surface so as to be radially adjacent to each other. In the friction clutch which transmits torque by engaging, the gap between the grooves is a flat portion forming a friction sliding surface by connecting the protrusions in a radial direction.
[0010]
A second aspect of the present invention is the friction clutch according to the first aspect, wherein a height of an edge portion of the flat portion on the groove side is equal to or less than a maximum height of a roughness curve of the flat portion. Features.
[0011]
A third aspect of the present invention is the friction clutch according to the second aspect, wherein the height of the edge is set to less than 1 μm.
[0012]
A fourth aspect of the present invention is the friction clutch according to any one of the first to third aspects, wherein the width of the groove is set to be smaller than the radial width of the flat portion.
[0013]
According to a fifth aspect of the present invention, in the friction clutch according to any one of the first to fourth aspects, the friction sliding surface on the other side includes a groove intersecting the groove. And friction clutch.
[0014]
The invention of claim 6 is the friction clutch according to any one of claims 1 to 5, wherein the surface hardness of the one-side friction sliding surface is higher than the surface hardness of the mating friction sliding surface. It is characterized in that the height is set small.
[0015]
The invention of claim 7 is the friction clutch according to any one of claims 1 to 6, wherein the surface roughness of the one-side friction sliding surface is larger than the surface roughness of the mating friction sliding surface. It is characterized in that the height is set small.
[0016]
【The invention's effect】
According to the first aspect of the present invention, the friction sliding surface on one side is provided with a plurality of grooves along the circumferential direction so as to be radially adjacent to each other, and the friction between the friction sliding surface on the other side and the friction sliding surface on the one side is provided. Torque can be transmitted by the engagement. Then, when the friction sliding surfaces slide with each other, the grooves are along the sliding direction, so that the occurrence of vibration and the like can be suppressed.
[0017]
Since the ridges are radially connected to each other to form a friction sliding surface between the grooves, the formation of the ridges is suppressed, and a reduction in the sliding area can be suppressed. Therefore, the surface pressure can be reduced, and the durability is improved.
[0018]
Since the formation of the ridge is suppressed in the flat portion, it is possible to suppress the formation of a space between the flat portion and the frictional sliding surface on the other side. Therefore, for example, when used as an electromagnetic clutch, it is possible to suppress the formation of a space between the friction sliding surfaces, suppress the weakening of the magnetic force by the space, improve the fastening force by the magnetic force, Also, the size and weight of the electromagnet can be reduced.
[0019]
According to the invention of claim 2, in addition to the effect of the invention of claim 1, the height of the edge of the flat portion on the groove side is equal to or less than the maximum height of the roughness curve of the flat portion. A reduction in the sliding area with respect to the friction sliding surface on the other side can be reliably suppressed, and a space formed between the friction sliding surface on the other side can be more reliably suppressed.
[0020]
According to the third aspect of the invention, in addition to the effect of the second aspect, the height of the edge is set to less than 1 μm, so that a reduction in the sliding area with respect to the friction sliding surface on the other side is more reliably suppressed. And the formation of a space between the mating frictional sliding surface and the mating friction sliding surface can be suppressed more reliably.
[0021]
According to a fourth aspect of the present invention, in the friction clutch according to any one of the first to third aspects, the width of the groove is set to be smaller than the radial width of the flat portion. The area of the sliding surface can be increased, the surface pressure on the friction sliding surface on the mating side can be reduced, the wear of the friction sliding surface is suppressed, and the durability is improved.
[0022]
Further, when used as an electromagnetic clutch, the magnetic path area can be increased, the fastening force by magnetic force can be improved, and the magnet can be reduced in size.
[0023]
According to the fifth aspect of the invention, in addition to the effects of any one of the first to fourth aspects, the friction sliding surface on the other side includes a groove intersecting the groove, so that the frictional sliding surface on one side is provided. The surface roughness of the sliding surface can be formed and maintained by the intersecting grooves of the friction sliding surface on the mating side.
[0024]
In the invention of claim 6, in addition to the effect of any one of the inventions of claims 1 to 5, the surface hardness of the one-side friction sliding surface is made to be higher than the surface hardness of the mating friction sliding surface. Since the frictional sliding surface on one side is roughened by the frictional sliding surface on the other side, the surface roughness of the frictional sliding surface on the one side can be maintained for a long period of time and the mirror surface can be suppressed.
[0025]
In the invention of claim 7, in addition to the effect of any one of the inventions of claims 1 to 6, the surface roughness of the friction sliding surface on the one side is made larger than the surface roughness of the friction sliding surface on the other side. Because the surface of the friction sliding surface on one side is roughened by the surface of the friction sliding surface on the other side, the surface roughness of the friction sliding surface on the one side is maintained for a long period of time, and the mirror surface is suppressed because it is set small. can do.
[0026]
BEST MODE FOR CARRYING OUT THE INVENTION
FIG. 1 is a skeleton plan view of a four-wheel drive vehicle showing an assembled state of a power transmission device to which one embodiment of the present invention is applied, and FIG. 2 is a cross-sectional view of the power transmission device to which one embodiment is applied.
[0027]
As shown in FIG. 1, the torque transmission device 1 is interposed between a front propeller shaft 5 as an input-side rotating member of a four-wheel drive vehicle 3 and a rear propeller shaft 7 as an output-side rotating member. 5 and 7, respectively. Further, the torque transmission device 1 is elastically supported via mount members 11 and 13 on the lower surface side of the floor panel 9 which is the vehicle body side.
[0028]
Note that the torque transmission device 1 can be appropriately selected and arranged according to the mounted vehicle, such as inside the transfer 31, between the transfer 31 and the front propeller shaft 5, between the rear propeller shaft 7 and the rear differential 33, and the like.
[0029]
The output from the engine 15 via the transmission 17 is transmitted to the front wheels 25 and 27 via the front differential 19 and the axle shafts 21 and 23. On the other hand, the power is transmitted from the differential case 29 of the front differential 19 to the front propeller shaft 5 via the transfer 31. The torque transmitted to the front propeller shaft 5 is transmitted to the rear propeller shaft 7 via the torque transmission device 1, and further transmitted to the rear wheels 39, 41 via the rear differential 33 and the axle shafts 35, 37. .
[0030]
Details of the torque transmission device 1 are as shown in FIG. As shown in FIG. 2, the torque transmission device 1 includes a clutch housing 43 and a shaft 45, and is arranged coaxially and relatively rotatable. The clutch housing 43 is coupled to, for example, the front propeller shaft 5 side, and the shaft 45 is coupled to, for example, the rear propeller shaft 7 side. A main clutch 47, a pilot clutch 49, a cam plate 51, a pressing plate 53, and an armature 55 are arranged between the clutch housing 43 and the shaft 45. Outside the end plate member 57 of the clutch housing 43, an electromagnet 59 fixedly supported on the vehicle body side is provided.
[0031]
The main clutch 47 includes a pair of inner and outer clutch plates, is fastened by pressing by a pressing plate 53, and transmits torque between the clutch housing 43 and the shaft 45 by frictional engagement.
[0032]
The pilot clutch 49 includes an inner / outer clutch plate, which will be described later, and is provided between the clutch housing 43 and the cam plate 51. The outer clutch plate is engaged with the clutch housing 43, and the inner clutch plate is engaged with the cam plate 51. The armature 55 is moved by the magnetic force generated by controlling the energization of the electromagnet 59, and the pilot clutch 49 is engaged between the armature 55 and the end plate member 57.
[0033]
A ball 61 is interposed between the cam surfaces of the cam plate 51 and the pressing plate 53.
[0034]
Therefore, when the cam plate 51 is engaged with the clutch housing 43 by the engagement control of the pilot clutch 49, a positional displacement in the circumferential direction occurs between the cam plate 51 and the pressing plate 53, and the cam surface with respect to the ball 61. As a result, the pressing plate 53 moves in a direction along the rotation axis. By the movement of the pressing plate 53, the main clutch 47 is engaged, and the torque is transmitted from the clutch housing 43 to the shaft 45 as described above. By this torque transmission, torque is transmitted from the front propeller shaft 5 to the rear propeller shaft 7 via the torque transmission device 1.
[0035]
The inner clutch plate of the pilot clutch 49 is formed as a friction clutch according to one embodiment of the present invention as shown in FIGS. 3 is a front view of the outer clutch plate according to one embodiment, FIG. 4 is an enlarged cross-sectional view of a main part taken along the line SA-SA in FIG. 3, FIG. (B) is a cross-sectional view of the middle stage of the formation of the flat portion, and (c) is a cross-sectional view after the formation of the flat portion.
[0036]
As shown in FIG. 3, the outer clutch plate 63 as a friction clutch is formed of, for example, a donut-shaped iron plate. A groove 67 is provided on the friction sliding surface 65 of the outer clutch plate 63. The grooves 67 are formed on both surfaces of the outer clutch plate 63. However, it can be formed on only one side. The groove 67 is formed as a spiral groove centered on the center C of the outer clutch plate 63. Therefore, the groove 67 is formed along the circumferential direction of the outer clutch plate 63, and is a single groove as a whole, but is provided so as to be adjacent to each other in the radial direction. Although the gap 67 is widely shown in FIG. 3 as compared to the size of the outer clutch plate 63, it is conceptually shown, and the actual setting will be described later.
[0037]
The outer clutch plate 63 is provided with a large-diameter center hole 69, an outer spline 71, and a through hole 73. The center hole 69 is loosely fitted on the outer peripheral side of the cam plate 51. The outer spline 71 is spline-fitted to the clutch housing 43. The through hole 73 forms a magnetic field of the electromagnet 59 on both sides in the radial direction.
[0038]
The space between the grooves 67 is formed as a flat portion 75 constituting the friction sliding surface 65 as shown in FIG. The height of the edge 77 on the groove 67 side of the flat portion 75 is set to be equal to or less than the maximum height of the roughness curve of the flat portion 67. Here, the maximum height is extracted from the roughness curve by a reference length in the direction of the average line, and the interval between the top line and the bottom line of the extracted portion is measured in the direction of the longitudinal magnification of the roughness curve. The values are expressed in micrometers (μm).
[0039]
In the present embodiment, the height of the edge 77 is set to less than 1 μm from the bottom line. The height h ₃ seen from the bottom line of the groove 67 of the edge 77 is set to about 10 [mu] m. The pitch _{h 4} between the grooves 67 each other is set to about 100 m to 300 m. The width of the groove 67 is set smaller than the width of the flat portion 75. This width is a width on the radius of the clutch plate 63 in the present embodiment.
[0040]
As shown in FIG. 5 (c), the flat portion 75 between the grooves 67 is formed by connecting ridges 79 to each other in the radial direction, and forms the friction sliding surface 65. In the formation of the flat portion 75, as shown in FIGS. 5A and 5B, at the initial stage of the formation of the flat portion 75, the ridge 79a rises with respect to the formation of the groove 67a. In the middle part of the formation of the flat portion, the groove 67b becomes deep and the ridge 79b grows gradually as shown in FIG. After the formation of the flat portion 75, the result is as shown in FIG.
[0041]
The groove 67 is not limited to the spiral groove shown in FIG. 3, but may be formed as shown in FIGS. FIG. 6 is a front view of an outer clutch plate according to another embodiment, and FIG. 7 is a front view of an outer clutch plate according to still another embodiment.
[0042]
In the outer clutch plate 63A of FIG. 6, the groove 67A is formed as an eccentric groove in which a plurality of concentric circles are shifted from the center C. In the outer clutch plate 63B of FIG. It is formed by concentric grooves.
[0043]
The common features of the grooves 67, 67A, and 67B in FIGS. 3, 6, and 7 are as follows. That is, since the grooves 67, 67A, 67B are formed along the circumferential direction in any of the outer clutch plates 63, 63A, 63B, vibration or the like is generated when the outer clutch plates 63, 63A, 63B slide and rotate with the mating clutch plate. Can be suppressed.
[0044]
On the other hand, the functional differences between the grooves 67, 67A and 67B are as follows. That is, in the case of the spiral groove shown in FIG. 3, the groove 67 can slightly roughen the friction sliding surface of the mating clutch plate during the sliding rotation, and the mirror sliding of the friction sliding surface can be suppressed. In the case of the eccentric groove of FIG. 6, the groove 67A tends to roughen the friction sliding surface of the mating clutch plate during the sliding rotation as compared with the case of the groove 67. In the case of the concentric groove shown in FIG. 7, the groove 67B coincides with the rotating circle, and the emphasis is placed on suppressing the occurrence of vibration and the like.
[0045]
The friction sliding surface of the inner clutch plate of the pilot clutch 49, which is a mating clutch plate that can be frictionally engaged with the friction sliding surface 65 of the outer clutch plates 63, 63A, 63B as one side, as shown in FIG. It has become. FIG. 8 is a front view of the inner clutch plate 81.
[0046]
As shown in FIG. 8, the inner clutch plate 81 is also provided with a plurality of grooves 85 in the friction sliding surface 83. This groove 85 is also conceptually shown in FIG. 8, and the depth of the groove 85 and the interval between the grooves 85 can be set as appropriate, and are formed, for example, on the order of microns. The grooves 85 are formed on both surfaces of the inner clutch plate 81, but may be formed on only one surface. The inner clutch plate 81 is provided with an inner spline 87, and the outer periphery 89 is circular. In addition, the inner clutch plate 81 is provided with a through hole 91 which is arranged concentrically with the through hole 73 of the outer clutch plate 63 and formed in substantially the same size.
[0047]
The grooves 85 are so-called sunburst grooves, and are arranged so that a plurality of curves intersect in a lattice. That is, the inner clutch plate 81 in FIG. 8 has a configuration in which a groove 85 is provided so as to intersect with the groove 67 of the friction sliding surface 65 of the outer clutch plate 63.
[0048]
The surface hardness of the friction sliding surface 65 of the outer clutch plate 63 is set smaller than the surface hardness of the friction sliding surface 83 of the inner clutch plate 81. Further, the surface roughness of the friction sliding surface 65 of the outer clutch plate 63 is set smaller than the surface roughness of the friction sliding surface 83 of the inner clutch plate 81.
[0049]
Accordingly, when any of the outer clutch plates 63, 63A, 63B is used as the pilot clutch 49 in combination with the inner clutch plate 81 of FIG. 8, the following functions can be achieved.
[0050]
Torque can be transmitted by frictional engagement between the friction sliding surfaces 65 of the outer clutch plates 63, 63A, 63B and the friction sliding surfaces 83 of the inner clutch plate 81. Therefore, when the friction sliding surfaces 65 and 83 slide, the grooves 67, 67A and 67B are in the sliding direction, so that the occurrence of vibration and the like can be suppressed.
[0051]
Between the grooves 67, 67A, and 67B, the ridges 79 are radially connected to each other to form the flat portion 75 that forms the friction sliding surface 65. Therefore, the formation of the ridge on the flat portion 75 is suppressed, A reduction in the sliding area of the inner clutch plate 81 with respect to the friction sliding surface 83 can be suppressed. Therefore, the surface pressure can be reduced, and the durability is improved.
[0052]
Since the formation of the ridge is suppressed in the flat portion 75, the formation of a space between the flat portion 75 and the friction sliding surface 83 of the inner clutch plate 81 can be suppressed. Therefore, as shown in FIG. 2, when the electromagnetic clutch is used for the pilot clutch 49 which is fastened by moving the armature 55 by the magnetic force of the electromagnet 59, a space is formed between the friction sliding surfaces 65 and 83. This can suppress the electromagnetic force being weakened by the space, improve the operation responsiveness due to the magnetic force, and reduce the size and weight of the electromagnet 59.
[0053]
The height of the edge 77 on the side of each of the grooves 67, 67A, 67B of the flat portion 75 is equal to or less than the maximum height of the roughness curve of the flat portion 75. The reduction of the sliding area with respect to the inner clutch plate 81 can be suppressed reliably, and the space formed between the inner clutch plate 81 and the friction sliding surface 83 can be suppressed more reliably.
[0054]
Since the height of the edge 77 is set to less than 1 μm, a decrease in the sliding area of the inner clutch plate 81 with respect to the friction sliding surface 83 can be suppressed more reliably, and the frictional sliding of the inner clutch plate 81 can be suppressed. Formation of a space between the surface 83 and the surface 83 can be suppressed more reliably.
[0055]
Since the width of each of the grooves 67, 67A, 67B is set to be smaller than the radial width of the flat portion 75, the area of the friction sliding surface 65 formed by the flat portion 75 can be increased, and the inner clutch plate can be increased. It is possible to reduce the surface pressure of the friction sliding surface 81 against the friction sliding surface 83, and the durability is improved. When the electromagnetic clutch is used for the pilot clutch 49, for example, as described above, the magnetic path area can be increased, the fastening force due to the magnetic force can be improved, and the magnet can be reduced in size and weight. You can also.
[0056]
The surface roughness of the friction sliding surface 65 of the outer clutch plates 63, 63A, 63B is formed by the groove 85 of the friction sliding surface 83 of the inner clutch plate 81 intersecting the grooves 67, 67A, 67B. Can be maintained.
[0057]
Since the surface hardness of the friction sliding surface 65 of the outer clutch plates 63, 63A, 63B is set to be smaller than the surface hardness of the friction sliding surface 83 of the inner clutch plate 81, the outer clutch plates 63, 63A, 63B. While the friction sliding surface 65 of the outer clutch plates 81 is roughened by the friction sliding surface 83 of the inner clutch plate 81, the surface roughness of the friction sliding surface 65 of the outer clutch plates 63, 63A, 63B is maintained for a long time, and the mirror surface is suppressed. be able to.
[0058]
Since the surface roughness of the friction sliding surface 65 of the outer clutch plates 63, 63A, 63B is set to be smaller than the surface roughness of the friction sliding surface 83 of the inner clutch plate 81, the outer clutch plates 63, 63A, 63B. While the surface of the friction sliding surface 65 is roughened by the surface of the friction sliding surface 83 on the other side, the surface roughness of the friction sliding surface 65 of the outer clutch plates 63, 63A, 63B is maintained for a long time, and its mirror surface is maintained. Can be suppressed.
[0059]
Note that the inner clutch plate 81 may be configured as shown in FIGS.
[0060]
The groove 85A of the inner clutch plate 81A in FIG. 9 is formed as a so-called lattice groove.
[0061]
The groove 85B of the inner clutch plate 81B in FIG. 10 is formed by an eccentric radiation groove extending straight from the circumference 93 centered on the center C1 of the inner clutch plate 81B.
[0062]
The groove 85C of the inner clutch plate 81C in FIG. 11 is formed as a concentric radiation groove extending straight from the center C1 of the inner clutch plate 81C.
[0063]
The grooves of the inner clutch plate 81D shown in FIG. 12 are formed as grooves 85D1, 85D2, 85D3, and 85D4, each of which is an extension of a different length and extends through the center C1. The groove 85D1 is formed to be long over the entire friction sliding surface 83. The groove 85D2 is the second longest, the groove 85D3 is the third longest, and the groove 85D4 is short and formed on the outer peripheral side.
[0064]
A set of grooves 85D4, 85D3, 85D2, 85D3, and 85D4 circumferentially adjacent to each other on the friction sliding surface 83 is equally spaced in the circumferential direction at a constant angle. The longest grooves 85D1 are equally arranged at regular intervals in the circumferential direction, and a set of the grooves 85D4, 85D3, 85D2, 85D3, 85D4 is arranged between the grooves 85D1.
[0065]
The circumferential distance between the leading ends 93, 95, and 97 of the grooves 85D2, 85D3, and 85D4 and the groove 85D1 is constant.
[0066]
With such a groove setting, at a certain sliding rotation angle of the inner clutch plate 81D, any of the grooves 85D1, 85D2, 85D3, and 85D4 exists on the radius from the inner diameter to the outer diameter, and the electromagnet 59 Is turned off, the disconnection response of the pilot clutch 49 when the magnetic force disappears can be improved. At the same time, it is possible to secure a large magnetic flux transmission area and a large sliding area for friction sliding.
[0067]
Although the outer clutch plates 63, 63A, 63B and the inner clutch plates 81, 81A, 81B, 81C, 81D are used as the pilot clutch 49 of the torque transmitting device 1 in FIG. is there. Although the groove 67 is formed in the outer clutch plate 63 of the pilot clutch 49, the inner clutch plate 81 side has the configuration shown in FIGS. 3, 6, and 7, and the outer clutch plate 63 side has the configuration shown in FIGS. It is also possible.
[0068]
Further, the friction clutch is not limited to a clutch using a clutch plate, but can be applied to a cone clutch or the like. Further, the intersecting arrangement of the grooves, the relation of the groove width, the relation of the surface hardness, and the relation of the surface roughness can be appropriately selected and configured, and it is also possible to omit these relations. is there.
[0069]
The embodiment of the present invention can be applied to devices other than the torque transmission device 1, and can also be applied to a multi-plate clutch other than an electromagnetic clutch, a cone clutch, and the like.
[Brief description of the drawings]
FIG. 1 is a skeleton plan view of a four-wheel drive vehicle showing an assembled state of a torque transmission device to which an embodiment of the present invention is applied.
FIG. 2 is a sectional view of a torque transmission device to which an embodiment of the present invention is applied.
FIG. 3 is a front view of an outer clutch plate according to the embodiment.
FIG. 4 is an enlarged cross-sectional view of an essential part taken along line SA-SA of FIG. 3 according to the embodiment;
FIGS. 5A and 5B are cross-sectional views showing an initial stage of forming a flat portion, FIG. 5B is a cross-sectional view showing a middle stage of forming a flat portion, and FIG.
FIG. 6 is a front view of an outer clutch plate according to another embodiment of the present invention.
FIG. 7 is a front view of an outer clutch plate according to still another embodiment of the present invention.
FIG. 8 is a front view of the inner clutch plate according to the embodiment of the present invention.
FIG. 9 is a front view of an inner clutch plate according to another embodiment of the present invention.
FIG. 10 is a front view of an inner clutch plate according to still another embodiment of the present invention.
FIG. 11 is a front view of an inner clutch plate according to still another embodiment of the present invention.
FIG. 12 is a front view of an inner clutch plate according to still another embodiment of the present invention.
FIG. 13 is a front view of a clutch plate according to a conventional example.
FIG. 14 is an enlarged sectional view of a main part of the clutch plate.
[Explanation of symbols]
49 Pilot clutch (friction clutch)
63, 63A, 63B Outer clutch plate 65 Friction sliding surface 67, 67A, 67B Groove 75 Flat part 79 Ridge 81, 81A, 81B, 81C, 81D Inner clutch plate 83 Friction sliding surface 85, 85A, 85B, 85C, 85D groove

Claims (7)

A plurality of circumferentially extending grooves are provided on one side of the frictional sliding surface so as to be radially adjacent to each other, and the frictional sliding surface of the other side frictionally engages with the frictional sliding surface of the one side to transmit torque. The friction clutch
The friction clutch according to claim 1, wherein the groove is a flat portion that forms a friction sliding surface by connecting the ridges to each other in a radial direction. The friction clutch according to claim 1, wherein
A height of an edge portion of the flat portion on the groove side is equal to or less than a maximum height of a roughness curve of the flat portion. The friction clutch according to claim 2, wherein
The height of the edge is set to less than 1 μm. The friction clutch according to claim 1, wherein
The width of the groove is set smaller than the radial width of the flat portion. The friction clutch according to claim 1, wherein:
A friction clutch, wherein the friction sliding surface on the other side includes a groove intersecting the groove. The friction clutch according to claim 1, wherein:
A friction clutch, wherein the surface hardness of the one-side friction sliding surface is set smaller than the surface hardness of the mating-side friction sliding surface. The friction clutch according to any one of claims 1 to 6, wherein
A friction clutch, wherein the surface roughness of the one frictional sliding surface is set smaller than the surface roughness of the frictional sliding surface on the other side.

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