JP2008057692A - Spring arrangement structure and clutch device using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a spring arrangement structure and a clutch device using this structure, capable of reducing cost, without using a washer spring. <P>SOLUTION: This spring arrangement structure has a cam ring 15 (a first member) and a side gear 17 (a second member) at least one of which can rotate around the axis, and a wave spring 1 (a spiral spring) having a pair of ends 19 and 21, continuing in the peripheral direction, having alternately a recessed part 3 and a projection part 5 toward one side in the axial direction and wound in a plurality so that the recessed part 3 of a first winding part 7 mutually abuts on the projection part 5 of a second winding part 9. The wave spring 1 is arranged in the axial direction between the cam ring 15 and the side gear 17 so that an axial relative position between the cam ring 15 and the side gear 17 can be displaced. In this case, the ends 19 and 21 are constituted so as not to contact with the cam ring 15 or the side gear 17 up to a displacement state from an arrangement initial state of the wave spring 1. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an arrangement structure of a spring arranged between members and a clutch device using the same.

Patent Document 1 describes an electromagnetically controlled differential limiting device in which a return spring is disposed between a side gear in which a dog clutch is formed and a clutch piston (a pair of fastening members). This return spring urges the side gear and the clutch piston in the dog clutch engagement release direction.
JP-A-2005-240861

  By the way, in the return spring as described above, a wave spring having a wave shape in the entire circumferential direction is used. Further, in the dog clutch as described above, the side gear and the clutch piston rotate relative to each other in the non-engaged state.

  In such a configuration, when the end of the wave spring directly contacts the side gear and the clutch piston, the end of the wave spring bites into the side gear or the clutch piston, and the wave spring is expanded to the outer diameter side or contracted to the inner diameter side. There is a possibility that one winding part may get over one adjacent winding part. For this reason, a washer spring is assembled to the cam ring so that the end of the wave spring does not slide relative to the side gear directly.

  However, since the washer spring is expensive, it is expensive. Moreover, it was necessary to give a groove to the cam ring to prevent the washer spring from rotating. Further, a space for providing a washer spring is required, and the peripheral parts thereof must be thinly configured, and the degree of freedom in layout of the entire apparatus is limited.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a spring arrangement structure and a clutch device using the same, which can reduce the cost without using a washer spring.

  The invention of claim 1 includes a first member and a second member, at least one of which is rotatable about an axis, a pair of ends, a recess that is continuous in the circumferential direction and toward one side in the axial direction. A spiral spring having a plurality of spiral portions wound alternately so that the concave portions of the first winding portion and the convex portions of the second winding portion are in contact with each other. A spring arrangement structure in which the spring is arranged between the first member and the second member so that an axial relative position between the first member and the second member can be displaced. Is not in contact with the first member or the second member from the initial arrangement state of the spring to the displaced state.

  According to a second aspect of the present invention, in the spring arrangement structure according to the first aspect, the end is cut near the bottom of the concave portion contacting the first member or the top of the convex portion contacting the second member. The contact with the first member or the second member is avoided.

  The invention according to claim 3 is the spring arrangement structure according to claim 1 or 2, wherein the distance between the end and the first member or the second member increases when the amount of deflection of the spring increases. It is characterized by.

  The invention of claim 4 includes a first member and a second member, at least one of which is rotatable about an axis, a pair of ends, a recess that is continuous in the circumferential direction and toward one side in the axial direction. A spiral spring having a plurality of spiral portions wound alternately so that the concave portions of the first winding portion and the convex portions of the second winding portion are in contact with each other. A spring arrangement structure in which the spring is arranged between the first member and the second member so that an axial relative position between the first member and the second member can be displaced. The first member and the second member have a height in the axial direction from the top of the convex portion to the bottom of the concave portion in one winding portion so as to face the first winding portion in the radial direction. An axial gap between the first member and the second member formed when the displacement of the relative position in the axial direction between them is maximum Characterized in that it is largely set Ri.

  The invention of claim 5 includes a first member and a second member, at least one of which is rotatable about an axis, a pair of ends, a recess that is continuous in the circumferential direction and toward one side in the axial direction. A spiral spring having a plurality of spiral portions wound alternately so that the concave portions of the first winding portion and the convex portions of the second winding portion are in contact with each other. A spring arrangement structure in which the spring is arranged between the first member and the second member so that an axial relative position between the first member and the second member can be displaced. Is disposed in a radial gap formed between the first member located on the outer diameter side and the second member located on the inner diameter side, and the radial gap of the radial gap is the spring It is characterized by being set to less than twice the thickness in the radial direction.

  A sixth aspect of the present invention is a clutch device using the spring arrangement structure according to any one of the first to fifth aspects, and is one clutch member that is rotatable and is operated to move in the axial direction and has an intermittent portion. And the other clutch member that is disposed opposite to the one clutch member and has an intermittent portion, and the one clutch member that is disposed between the one clutch member and the other clutch member toward the initial arrangement state. A return spring biased in an axial direction, wherein the first member is the one clutch member, the second member is the other clutch member, and the spring is the return spring. To do.

  In the spring arrangement structure according to claim 1, since the end of the spring does not contact the first member or the second member from the initial arrangement state of the spring to the displaced state, the end of the spring may bite into the first member or the second member. In addition, the spring does not spread or contract due to biting, and it is possible to prevent the spring from getting over. For this reason, it is not necessary to use a washer spring, the cost concerning a washer spring can be reduced, and cost reduction can be achieved.

  The arrangement structure of the spring according to claim 2 is such that the end of the spring is cut at the bottom of the concave portion that contacts the first member or near the top of the convex portion that contacts the second member, and contact with the first member or the second member is achieved. It has been avoided. For this reason, the end of the spring does not bite into the first member or the second member.

  In the spring arrangement structure according to the third aspect, the distance between the end and the first member or the second member increases when the amount of deflection of the spring increases. Therefore, the end of the spring becomes the first member or the second as the spring is bent. It does not bite into the parts.

  In the spring arrangement structure according to claim 4, the axial height from the top of the convex portion to the concave portion in the first winding portion is the largest in the displacement in the axial relative position between the first member and the second member. Since it is set to be larger than the axial gap between the first member and the second member that are sometimes formed, the first winding portion enters the axial gap between the first member and the second member. There is no. For this reason, there is no space for the first winding part to move, and the spring does not get over. Therefore, it is not necessary to use a washer spring, the cost applied to the washer spring can be reduced, and cost reduction can be achieved.

  In the spring arrangement structure according to claim 5, since the radial gap formed by the first member and the second member is set to be less than twice the radial thickness of the spring, Even if the part tries to get over the adjacent winding part, there is no gap for the winding part to enter, and the part cannot get over. For this reason, it is not necessary to use a washer spring, the cost concerning a washer spring can be reduced, and cost reduction can be achieved.

  The clutch device according to the sixth aspect employs a spring arrangement structure that does not require the use of a washer spring. Therefore, the cost applied to the washer spring can be reduced, and the overall cost of the clutch device can be reduced. it can.

  The embodiment will be described with reference to FIGS.

  The spring arrangement structure of this embodiment has a cam ring 15 (first member) and a side gear 17 (second member), at least one of which can rotate around an axis, and a pair of ends 19, 21 in the circumferential direction. The concave portions 3 and the convex portions 5 alternately toward the one side in the axial direction, and the concave portions 3 of the first winding portion 7 and the convex portions 5 of the second winding portion 9 are provided. A plurality of wave springs 1 (spiral springs) wound in contact with each other, and the axial direction between the cam ring 15 and the side gear 17 so that the axial relative position between the cam ring 15 and the side gear 17 can be displaced. A wave spring 1 is arranged between them. The end portions 19 and 21 are configured not to contact the cam ring 15 or the side gear 17 from the initial arrangement state of the wave spring 1 to the displaced state.

  Further, the ends 19 and 21 are cut in the vicinity of the bottom portion 25 of the concave portion 3 that contacts the cam ring 15 or the top portion 23 of the convex portion 5 that contacts the side gear 17, thereby avoiding contact with the cam ring 15 or the side gear 17.

  Further, when the deflection amount of the wave spring 1 increases, the separation distance between the ends 19 and 21 and the cam ring 15 or the side gear 17 increases.

  Further, the cam ring 15 and the side gear so that the axial height H from the top portion 23 of the convex portion 5 to the bottom portion 25 of the concave portion 3 in the first winding portion 7 faces the first winding portion 7 in the radial direction. 17 is set to be larger than the axial clearance W <b> 1 between the cam ring 15 and the side gear 17 formed when the displacement of the relative position in the axial direction between the cam ring 15 and the side gear 17 is maximum.

  Further, the wave spring 1 is disposed in a radial gap 113 formed between the cam ring 15 located on the outer diameter side and the side gear 17 located on the inner diameter side, and the radial gap W2 of this radial gap is It is set to less than twice the radial thickness D of the wave spring 1.

  First, the differential device 41 to which the clutch device 47 provided with the wave spring 1 is applied will be described.

  As shown in FIGS. 1 to 3, the differential device 41 includes a differential case 43, a differential mechanism 45, and a clutch device 47. The differential case 43 is rotatably supported by a differential carrier (not shown). A ring gear (not shown) is fixed to the differential case 43, and the driving force of the engine is transmitted by meshing with a gear of a power transmission system that transmits the driving force of the engine (driving source). 43 is driven to rotate, and the driving force is transmitted to the left and right axles via a differential mechanism 45 housed inside the differential case 43.

  The differential mechanism 45 includes a pinion shaft 49, a pinion gear 51 rotatably supported by the pinion shaft 49, and output side gears 17 and 53 that mesh with the pinion gear 51 and mesh with the left and right axles. Yes. The pinion shaft 49 is engaged with the differential case 43 at its end and is prevented from being detached from the differential case 43 by bolts 55, and is rotationally driven integrally with the differential case 43. The pinion gear 51 is supported by the pinion shaft 49 so as to transmit driving force from the engine to the left and right side gears 17 and 53 and to be rotationally driven when a differential rotation occurs between the meshed left and right side gears 17 and 53. Yes.

  The outer peripheral sides of the boss portions 57 and 59 of the side gears 17 and 53 are supported by support portions 61 and 63 formed on the differential case 43, and the side gears 17 and 55 are splined to the inner peripheral sides of the boss portions 57 and 59. It is connected to the left and right wheels through the axles. When the side gear 17 is connected to the differential case 43 by the clutch device 47, the differential is locked.

  The clutch device 47 includes an electromagnetic coil 65, a plunger 67, a cam mechanism 75 including a cam surface 71 formed on the opening 69 of the differential case 43 and a cam surface 73 formed on the cam ring 15, and a dog clutch 77. ing. The electromagnetic coil 65 is supported in the radial direction by a support portion 81 having a core 79 formed in the differential case 43. A circumferential groove 83 is formed in the core 79, a contact member 85 is brought into contact with the circumferential groove 83, the contact member 85 is fixed by a bolt 87, and the electromagnetic coil 65 is supported in the axial direction with respect to the differential case 43. is doing. Further, the electromagnetic coil 65 is provided with a non-rotating member (not shown), and the electromagnetic coil 65 is prevented from rotating in the rotational direction by engaging the non-rotating member with the differential carrier side. A plunger 67 is disposed on the inner diameter side of the electromagnetic coil 65, and the plunger 67 is moved in the axial direction by energizing the electromagnetic coil 65.

  The plunger 67 is made of a magnetic material, and a ring 89 made of a nonmagnetic material that prevents the magnetic flux of the electromagnetic coil 65 from leaking toward the differential case 43 is integrally fixed to the inner periphery of the plunger 67. The ring 89 and the plunger 67 are supported so as to be movable in the axial direction on the boss portion 91 of the differential case 43 and not rotatable relative to the differential case 43, and are relatively rotatable with respect to the electromagnetic coil 65. Further, the ring 89 is provided with a plurality of projections 93 fitted into the opening 69, and when the plunger 67 is moved in the axial direction, the projection 93 is formed on the convex portion 94 of the cam ring 15 of the cam mechanism 75. Press the end face.

  The cam mechanism 75 includes a rotation direction surface of the convex portion 94 of the cam ring 15 and a rotation direction side surface of the opening 69 of the differential case 43. The cam ring 15 is supported on the inner periphery of the boss portion 57 of the side gear 17 so as to be axially movable. The cam ring 15 is provided with three protrusions 94 protruding at equal intervals in the circumferential direction. The convex portion 94 is engaged with the opening 69 of the differential case 43 to prevent the cam ring 15 from rotating. Further, a cam surface 73 is formed on the convex portion 94 on the surface in the rotational direction. Further, a cam surface 71 having the same inclination angle as that of the cam surface 73 of the convex portion 94 is formed on the surface of the differential case 43 in the rotation direction, and the cam operates when a driving torque is applied. The cam ring 15 is moved in the meshing direction (rightward) of the dog clutch 77 by the movement of the plunger 67 in the axial direction and the cam thrust force of the cam mechanism 75, and the dog clutch 77 is fastened.

  The dog clutch 77 is composed of a meshing tooth 29 of the cam ring 15 and a meshing tooth 31 of the side gear 17. When the meshing teeth 29 of the cam ring 15 and the meshing teeth 31 of the side gear 17 mesh with each other, the differential case 43 and the side gear 17 are connected to limit the differential of the differential mechanism 45. The engagement of the dog clutch 77 is released because the cam ring 15 is strongly pressed in the engagement direction of the dog clutch 77 by the movement of the plunger 67 in the engagement direction of the dog clutch 77 and the cam thrust force of the cam mechanism 75. Stable without anything.

  Here, the cam ring 15 is biased by the wave spring 1 in the meshing release direction (leftward) of the dog clutch 77. The wave spring 1 is supported between a support portion 95 formed on the inner diameter side of the meshing teeth 29 of the cam ring 15 and a support portion 97 formed on the inner diameter side of the meshing teeth 31 of the side gear 17. The cam ring 15 is normally biased by the wave spring 1 in the meshing release direction of the dog clutch 77, and when the energization of the electromagnetic coil 65 is stopped, the cam spring 15 is forced by the wave spring 1 in the meshing release direction of the dog clutch 77. Moved.

  Further, the oil in the oil reservoir provided in the differential carrier flows in and out through openings such as the opening 69 formed in the differential case 43, and the meshing portions of each gear, the sliding surface between the pinion gear 51 and the spherical washer 99, and the like. Lubricated and cooled, and the bearings 61 and 63, washers 105 and 107, dog clutch 77, cam mechanism 75, and the like are lubricated and cooled by the oil flowing from the oil passages 101 and 103 of the differential case 43.

  In the differential device 41 configured as described above, when the electromagnetic coil 65 is excited, the plunger 67 is moved to the right by the magnetic flux of the electromagnetic coil 65, the dog clutch 77 is engaged, and the differential mechanism 45 performs differential operation. In this state, the cam mechanism 75 is actuated by receiving the driving torque and presses the cam ring 15 to the right, thereby preventing the dog clutch 77 from being inadvertently released due to vibration or the like. When the excitation of the electromagnetic coil 65 is stopped, the cam ring 15 and the plunger 67 are returned to the left by the wave spring 1, and the engagement of the dog clutch 77 and the differential lock are released.

  Next, the assembly structure of the wave spring 1 will be described.

  As shown in FIG. 4, the wave spring 1 has a pair of end portions 19 and 21 in which the concave portions 3 and the convex portions 5 are alternately formed continuously in the circumferential direction and toward one side in the axial direction. . Moreover, the surface 11 by the side of the 2nd winding part 9 which the recessed part 3 formed in the 1st winding part 7 in the circumferential direction adjoins, and the 1st winding part formed in the 2nd winding part 9 7 is in contact with the surface 13 of the convex portion 5 adjacent to the concave portion 3 on the first winding portion 7 side. In this contact, since the concave portions 3 and the convex portions 5 are alternately formed in the circumferential direction, the contact is alternately made in the circumferential direction. Such a wave spring 1 is wound in plural and is disposed between the support part 95 of the cam ring 15 and the support part 97 of the side gear 17.

  As shown in FIG. 5, the ends 19 and 21 of the wave spring 1 disposed between the support portion 95 of the cam ring 15 and the support portion 97 of the side gear 17 are inclined so as to be separated from the cam ring 15 and the side gear 17. Yes. In order to form such end portions 19 and 21, the end portions 19 and 21 of the wave spring 1 are cut in the vicinity of the bottom portion 25 of the concave portion 3 that contacts the cam ring 15 or the top portion 23 of the convex portion 5 that contacts the side gear 17. . This cutting is performed by cutting a portion slightly inclined from the top portion 23 toward the adjacent winding portion (a portion in the downward direction in FIG. 5 from the top portion 23) or a portion inclined from the bottom portion 25 toward the adjacent winding portion ( 5 is cut from the bottom 25. In addition, you may cut | disconnect according to the top part 23 or the bottom part 25 of the terminal | ends 19 and 21. FIG. The ends 19 and 21 may be bent so as to be separated from the cam ring 15 and the side gear 17. In this manner, contact between the end 19 and 21 of the wave spring 1 and the cam ring 15 and the side gear 17 is prevented, so that the end 19 and 21 do not bite into the cam ring 15 and the side gear 17 due to the rotation of the cam ring 15 and the side gear 17. The spread of the wave spring 1 is prevented.

  Further, by forming the ends 19 and 21 by cutting or bending as described above, the separation distance between the ends 19 and 21 and the cam ring 15 or the side gear 17 is increased when the deflection amount of the wave spring 1 is increased. It has become. Therefore, as the cam ring 15 and the side gear 17 move in the meshing direction, the ends 19 and 21 of the wave spring 1 are separated from the cam ring 15 and the side gear 17, and the ends 19 and 21 do not bite into the cam ring 15 and the side gear 17.

  Further, as shown in FIG. 6, in the first winding portion 7 of the wave spring 1, the axial height H from the top portion 23 of the convex portion 5 to the bottom portion 25 of the concave portion 3 is the first winding portion 7. The axial clearance W1 between the cam ring 15 and the side gear 17 that is formed when the displacement of the axial relative position between the cam ring 15 and the side gear 17 is maximum is set so as to be opposed to each other in the radial direction. The axial clearance W1 is the width between the tooth surfaces 109 and 111 of the meshing teeth 29 and 31 in the initial state of the cam ring 15 and the side gear 17. This setting is set by an inclination angle A ° from the tooth surface 111 of the side gear 17 that contacts the top 23 of the convex portion 5 to the bottom 25 of the concave portion 3. Thus, since the axial height H of the wave spring 1 is set to be larger than the axial gap W1 between the tooth surfaces 109 and 111, in the initial state of the cam ring 15 and the side gear 17, the wave spring 1 has the tooth surface 109, Cannot enter between 111. For this reason, the wave spring 1 cannot spread, and the wave spring 1 is not overtaken.

  As shown in FIG. 7, the wave spring 1 is disposed in a radial gap 113 formed between the cam ring 15 positioned on the outer diameter side and the side gear 17 positioned on the inner diameter side. The radial gap W2 of the radial gap 113 is set to be less than twice the radial thickness D of the wave spring 1. This is set so as to eliminate the space in which the winding part (for example, the first winding part 7) of the wave spring 1 can enter even if the wave spring 1 tries to get over. For example, when the radial gap W <b> 2 is equal to the radial thickness D, there is a space in which the winding portion of the wave spring 1 can enter. For this reason, the radial gap W2 may be about 1.8 times or less of the radial thickness D, but preferably less than 1.6 times. Thus, since the radial gap W2 is set so as to eliminate the space in which the winding portion of the wave spring 1 can enter, the wave spring 1 does not get over.

  In such an assembly structure of the spring, since the ends 19 and 21 of the wave spring 1 are in contact with the cam ring 15 or the side gear 17 from the initial arrangement state of the wave spring 1 to the displaced state, the ends 19 and 21 of the wave spring 1 are cam rings. 15 or the side gear 17 does not bite, and the wave spring 1 does not spread or contract due to the biting, and the wave spring 1 can be prevented from getting over. For this reason, it is not necessary to use a washer spring, the cost concerning a washer spring can be reduced, and cost reduction can be achieved.

  Further, the ends 19 and 21 of the wave spring 1 are cut in the vicinity of the bottom 25 of the concave portion 3 that contacts the cam ring 15 or the top portion 23 of the convex portion 5 that contacts the side gear 17, and contact with the cam ring 15 or the side gear 17 is avoided. Therefore, the ends 19 and 21 do not bite into the cam ring 15 and the side gear 17 due to the rotation of the cam ring 15 and the side gear 17, and the wave spring 1 is prevented from spreading.

  Further, when the deflection amount of the wave spring 1 increases, the separation distance between the ends 19 and 21 and the cam ring 15 or the side gear 17 increases. Therefore, the end 19 of the wave spring 1 increases as the cam ring 15 and the side gear 17 move in the meshing direction. 21 are separated from the cam ring 15 and the side gear 17, and the ends 19 and 21 do not bite into the cam ring 15 and the side gear 17.

  Further, since the axial height H of the wave spring 1 is set to be larger than the axial clearance W1 between the tooth surfaces 109 and 111, the wave spring 1 has the tooth surfaces 109 and 111 in the initial state of the cam ring 15 and the side gear 17. The wave spring 1 cannot be spread out, and the wave spring 1 is prevented from getting over.

  Further, since the radial clearance W2 is set to be less than twice the radial thickness D of the wave spring 1, there is no space for the winding portion of the wave spring 1 to enter, and the wave spring 1 is overcome. There is no.

  Further, since the clutch device 47 employs the spring arrangement structure that does not require the use of the washer spring as described above, the cost applied to the washer spring can be reduced, and the cost of the entire clutch device 47 can be reduced. Can be achieved.

It is sectional drawing of the non-locking state of a differential apparatus. It is sectional drawing of the locked state of a differential apparatus. (A) It is a front view of the cam surface side of a cam ring. (B) It is a side view of a cam ring. (C) It is a front view by the side of the meshing tooth of a cam ring. It is a perspective view of a wave spring. It is an enlarged view of the arrangement state of a wave spring. (A) It is an enlarged view of the arrangement state of a wave spring. (B) It is a Z arrow line view of Fig.6 (a). It is an enlarged view of the arrangement state of a wave spring.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Wave spring 3 ... Concave part 5 ... Convex part 7 ... 1st winding part 9 ... 2nd winding part 15 ... Cam ring 17 ... Side gear 19, 21 ... End 23 ... Top part 25 ... Bottom part 29, 31 ... Meshing tooth 41 ... Differential device 47 ... Clutch device 77 ... Dog clutch 95, 97 ... Support part 109, 111 ... Tooth surface D ... Radial thickness W1 ... Axial clearance W2 ... Radial clearance

Claims (6)

At least one of the first member and the second member that can rotate around the axial center, and a pair of ends, the recesses and protrusions are alternately provided continuously in the circumferential direction and toward one side in the axial direction. And a spiral spring wound in a plurality so that the concave portion of the first winding portion and the convex portion of the second winding portion are in contact with each other, the first member and the second A spring arrangement structure in which the spring is arranged between the first member and the second member so that an axial relative position between the members can be displaced,
The spring arrangement structure is characterized in that the end does not contact the first member or the second member from the initial arrangement state of the spring to the displaced state. The arrangement structure of the spring according to claim 1,
The end is cut at the bottom of the concave portion that contacts the first member or near the top of the convex portion that contacts the second member, so that contact with the first member or the second member is avoided. An arrangement structure of a spring characterized by A spring arrangement structure according to claim 1 or 2,
The spring disposition structure characterized in that when the amount of deflection of the spring increases, the distance between the end and the first member or the second member increases. At least one of the first member and the second member that can rotate around the axial center, and a pair of ends, the recesses and protrusions are alternately provided continuously in the circumferential direction and toward one side in the axial direction. And a spiral spring wound in a plurality so that the concave portion of the first winding portion and the convex portion of the second winding portion are in contact with each other, the first member and the second A spring arrangement structure in which the spring is arranged between the first member and the second member so that an axial relative position between the members can be displaced,
The first member and the second member so that the axial height from the top of the convex portion to the bottom of the concave portion in the first winding portion faces the first winding portion in the radial direction. The spring arrangement structure is set to be larger than the axial gap between the first member and the second member formed when the displacement in the axial relative position between the first member and the second member is maximum. At least one of the first member and the second member that can rotate around the axial center, and a pair of ends, the recesses and protrusions are alternately provided continuously in the circumferential direction and toward one side in the axial direction. And a spiral spring wound in a plurality so that the concave portion of the first winding portion and the convex portion of the second winding portion are in contact with each other, the first member and the second A spring arrangement structure in which the spring is arranged between the first member and the second member so that an axial relative position between the members can be displaced,
The spring is further disposed in a radial gap formed between the first member located on the outer diameter side and the second member located on the inner diameter side, and the radial gap of the radial gap is: The spring arrangement structure is set to be less than twice the radial thickness of the spring. A clutch device using the spring arrangement structure according to any one of claims 1 to 5,
One clutch member that is rotatable and operated in the axial direction and has an intermittent portion, the other clutch member that is disposed opposite to the one clutch member and has an intermittent portion, the one clutch member, and the other clutch member, A return spring that is arranged between the two clutch members and biases the one clutch member in the axial direction toward the initial arrangement state,
The clutch device, wherein the first member is the one clutch member, the second member is the other clutch member, and the spring is the return spring.

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