JP2008019898A - Power transmission mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmission mechanism which can suppress dispersion of a release torque while miniaturizing the configuration. <P>SOLUTION: A power transmission mechanism PT of a refrigerant compressor connects a pulley 64 rotatably supported on a front housing 12 through a bearing 60 with a hub 67 coupled to a rotary shaft so as to be power-transmittable. The power transmission mechanism PT is equipped with a one-way clutch 70, wherein an inside clutch member of the one-way clutch 70 is formed of the outer ring 63 of the bearing 60. The outer ring 63 is integrally rotatably coupled to the pulley 64 by a coupling part 63a of the front housing 12 rather than by a portion taken as the inside clutch member in the outer ring 63. The inner peripheral surface 71B of an outside clutch member 71 is integrally rotatably coupled with the hub 67. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a power transmission mechanism that includes a one-way clutch and that functions as a torque limiter.

  Generally, a refrigerant compressor used in a vehicle air conditioner uses a rotational power of a crankshaft of a vehicle engine as a drive source, and the rotational power of the crankshaft is transmitted to a rotating shaft of the refrigerant compressor via a belt and a pulley. For this reason, the rotation fluctuation of the crankshaft which fluctuates according to the combustion control of the engine is transmitted to the rotation shaft of the refrigerant compressor via the belt and the pulley. When the rotational fluctuation of the crankshaft becomes large, the belt slips with respect to the pulley, and abnormal noise is generated or the belt is damaged.

  For this reason, a one-way clutch as a power transmission mechanism is interposed on the power transmission path between the pulley and the rotation shaft in order to prevent the rotation fluctuation of the crankshaft from being transmitted to the rotation shaft of the refrigerant compressor. (See Patent Document 1). As shown in FIG. 6, a pulley 101 is rotatably supported by a radial bearing 102 in the refrigerant compressor housing 100. The inner ring 104 of the one-way clutch 103 is substituted for the outer ring of the radial bearing 102, and the one-way clutch 103 and the radial bearing 102 are integrally provided, thereby reducing the size of the power transmission mechanism. . In addition, flat cam surfaces (not shown) are provided at a plurality of locations on the outer peripheral surface of the inner ring 104, and recesses (not shown) are provided. Further, the inner ring 104 is press-fitted into the pulley 101 on the housing 100 side, and the inner ring 104 is coupled to the pulley 101 so as to be integrally rotatable.

  The outer ring 105 of the one-way clutch 103 is provided on the outer peripheral side of the inner ring 104. The outer ring 105 is press-fitted (fitted) and fixed to the inner periphery of a cylindrical member 110 fixed to the shaft end of the rotary shaft 107 of the refrigerant compressor. A wedge-shaped space that narrows toward one direction in the circumferential direction of the outer ring 105 is formed at a portion where the cam surface of the inner ring 104 and the inner peripheral surface of the outer ring 105 face each other. A roller 106 is disposed between the inner ring 104 and the outer ring 105.

  In the refrigerant compressor, when the rotational speed of the pulley 101 (inner ring 104) becomes relatively faster than that of the rotating shaft 107, the rotation of the inner ring 104 causes the rollers 106 to roll to the narrow side of the wedge-shaped space and The outer ring 105 is locked. As a result, the rotating shaft 107 rotates synchronously with the pulley 101 via the outer ring 105 and the cylindrical member 110, that is, the one-way clutch 103. On the other hand, when the rotational speed of the pulley 101 (inner ring 104) is relatively slower than that of the rotating shaft 107, the roller 106 is rolled to the wide side of the wedge-shaped space, and the outer ring 105 becomes free with respect to the inner ring 104. Power transmission from 101 to the rotating shaft 107 is interrupted.

The one-way clutch 103 also has a function as a torque limiter that cuts off power transmission from the pulley 101 to the rotating shaft 107 when the refrigerant compressor is locked. That is, when the refrigerant compressor is locked and an excessive transmission torque (release torque) of a predetermined value or more acts on the rotary shaft 107 via the one-way clutch 103, the roller 106 is further moved from the narrow side of the wedge-shaped space by the rotation of the inner ring 104. Rolled into the recess. Then, the outer ring 105 is in a free state with respect to the inner ring 104, and power transmission from the pulley 101 to the rotating shaft 107 is cut off.
JP 2002-106608 A

  However, as disclosed in Patent Document 1, in the one-way clutch 103 having a torque limiter function, the outer ring 105 can be integrally rotated with the rotary shaft 107 by being press-fitted (fitted) to the inner periphery of the cylindrical member 110. It is connected to. For this reason, when the outer ring 105 is fitted to the inner periphery of the cylindrical member 110, a force that presses the outer ring 105 inward in the radial direction acts, and the inner diameter of the outer ring 105 may change. . If the inner diameter of the outer ring 105 changes, the width of the wedge-shaped space formed by the inner peripheral surface of the outer ring 105 and the cam surface of the inner ring 104 may change. For example, if the width of the wedge-shaped space is narrower than a predetermined width, when the one-way clutch 103 functions as a torque limiter, the roller 106 does not leave the wedge-shaped space even if a release torque greater than a predetermined value is applied. Will occur. Therefore, if the width of the wedge-shaped space changes, the timing at which the one-way clutch 103 functions as a torque limiter differs from a predetermined timing, resulting in a problem that the release torque in the torque limiter varies.

  An object of the present invention is to provide a power transmission mechanism that can suppress variations in release torque while reducing the size of the physique.

  In order to solve the above problems, the invention according to claim 1 is directed to a first rotating body rotatably supported by a housing of a rotating machine via a bearing and driven by an external driving source, and rotation of the rotating machine. A power transmission mechanism coupled to a shaft and coupled to a second rotating body disposed coaxially with the first rotating body so as to be capable of transmitting power, comprising an inner clutch member and a roller on an outer peripheral side of the inner clutch member An outer clutch member opposed to each other, and the roller is engaged with a wedge-shaped space formed between the opposing circumferential surfaces of both members, and the second rotating body is synchronously rotated with respect to the first rotating body. A one-way clutch that can be switched between a locked state to be released and a free state in which the roller is removed from the wedge-shaped space and the second rotating body is rotated relative to the first rotating body. When the torque transmitted to the second rotating body becomes excessive, the roller is detached from the wedge-shaped space and functions as a torque limiter that blocks power transmission from the first rotating body to the second rotating body. The outer ring is connected to the first rotating body so as to be integrally rotatable with a connecting portion on the housing side of the outer ring, which is the inner clutch member, and the outer clutch member and the second rotating body are connected to each other. The outer clutch member and the second rotating body were connected by the engagement of the protrusion and the recess formed between the two.

  According to this configuration, the outer ring of the bearing is integrally provided with the inner clutch member, and the bearing and the one-way clutch are integrated. For this reason, for example, the number of parts can be reduced as compared with the case where the bearing for supporting the first rotating body and the one-way clutch are provided separately in the power transmission mechanism, and the physique of the power transmission mechanism can be reduced. It can be downsized. Further, an inner clutch member of the one-way clutch is formed by the outer ring of the bearing. Further, in the outer ring, the connecting portion on the housing side than the portion forming the inner clutch member is connected to the first rotating body, and the outer ring and the first rotating body are Integral rotation is possible. Further, the second rotating body is coupled to the outer clutch member so as to be integrally rotatable by a concave-convex engagement relationship. For this reason, in the power transmission mechanism, the pressing force from each rotating body does not act on the outer clutch member and the inner clutch member of the one-way clutch in the connected state with the first rotating body and the second rotating body. It is possible to prevent the interval (width) between the opposing peripheral surfaces from changing. Therefore, in the one-way clutch, the width of the wedge-shaped space formed between the peripheral surfaces of both members can be maintained at a predetermined size, and variation in the release torque of the torque limiter can be suppressed.

  In addition, a clearance is formed between the end face of the projecting portion facing the radial direction of the rotating shaft and the inner bottom surface of the recessed portion, and the outer clutch member side along the axial direction of the rotating shaft in the projecting portion. A clearance may be formed between the end surface of the recess and the inner surface of the recess facing the end surface.

  According to this structure, in the connection part of a 2nd rotary body and an outer side clutch member, it is prevented that it mutually contacts in the radial direction and axial direction of a rotating shaft. Therefore, a pressing force other than the rotational power does not act on the outer clutch member, the width of the wedge-shaped space can be maintained at a predetermined size, and the variation in release torque can be more reliably suppressed.

  According to a third aspect of the present invention, the first rotating body is rotatably supported by a housing of the rotating machine via a bearing, and is driven by an external drive source. The first rotating body is coupled to a rotating shaft of the rotating machine, and the first rotation. A power transmission mechanism for coupling a second rotating body disposed coaxially with the body so as to be able to transmit power, an inner clutch member, and an outer clutch member opposed to an outer peripheral side of the inner clutch member via a roller And a locked state in which the roller is engaged with a wedge-shaped space formed between the opposing circumferential surfaces of the two members and the second rotating body is rotated synchronously with the first rotating body, and the roller is moved from the wedge-shaped space. A one-way clutch that can be switched to a free state in which the second rotating body is rotated relative to the first rotating body is provided, and transmission torque from the first rotating body to the second rotating body is excessive in the locked state. And the outer clutch member is formed by a part of the outer ring of the bearing, functioning as a torque limiter that separates the roller from the wedge-shaped space and interrupts power transmission from the first rotating body to the second rotating body. A protrusion and a recess formed between the inner clutch member and the second rotating body, wherein the outer ring is connected to the first rotating body so as to be integrally rotatable with a connecting portion on the housing side of the outer ring in the outer ring. The inner clutch member and the second rotating body were connected by the engagement.

  According to this configuration, the outer ring of the bearing is integrally provided with the outer clutch member, and the bearing and the one-way clutch are integrated. For this reason, for example, the number of parts can be reduced as compared with the case where the bearing for supporting the first rotating body and the one-way clutch are provided separately in the power transmission mechanism, and the physique of the power transmission mechanism can be reduced. It can be downsized. Further, an outer clutch member of the one-way clutch is formed by the outer ring of the bearing. Further, in the outer ring, a connecting portion on the housing side with respect to a portion forming the outer clutch member is connected to the first rotating body, and the outer ring and the first rotating body are connected. Integral rotation is possible. Moreover, the 2nd rotary body is connected with the inner side clutch member by the uneven | corrugated engagement relationship so that integral rotation is possible. For this reason, in the power transmission mechanism, the pressing force from each rotating body does not act on the outer clutch member and the inner clutch member of the one-way clutch in the connected state with the first rotating body and the second rotating body. It is possible to prevent the interval (width) between the opposing peripheral surfaces from changing. Therefore, in the one-way clutch, the width of the wedge-shaped space formed between the peripheral surfaces of both members can be maintained at a predetermined size, and variation in the release torque of the torque limiter can be suppressed.

  In addition, a clearance is formed between the end face of the projecting portion facing the radial direction of the rotating shaft and the inner bottom surface of the recessed portion, and the inner clutch member side along the axial direction of the rotating shaft in the projecting portion. A clearance may be formed between the end surface of the recess and the inner surface of the recess facing the end surface.

  According to this structure, in the connection part of a 2nd rotary body and an inner side clutch member, it is prevented that it mutually contacts in the radial direction and axial direction of a rotating shaft. Therefore, a pressing force other than rotational power does not act on the inner clutch member, the width of the wedge-shaped space can be maintained at a predetermined size, and variation in release torque can be more reliably suppressed.

  The bearing includes a plurality of rows of rolling elements in the axial direction of the bearing between the outer ring and an inner ring disposed at a predetermined interval on the inner peripheral side of the outer ring. At least one row of rolling elements is accommodated at a position corresponding to the connecting portion, and the outer ring and the first rotating body are connected by press-fitting the connecting portion inside the first rotating body, The inner diameter of the connecting portion may be set so that the interval between the connecting portion and the inner ring before press-fitting into the first rotating body is wider than the predetermined interval.

  According to this configuration, when the connecting portion is press-fitted inside the first rotating body, the connecting portion is reduced in diameter, the interval between the connecting portion and the inner ring is narrowed, and the interval between the connecting portion and the inner ring is set to a predetermined interval. can do. Note that the predetermined interval between the connecting portion and the inner ring means that the rolling element can be brought into contact with the connecting portion and the inner ring, and the rolling element can be reliably rolled between the connecting portion and the inner ring, and the first interval is set by the bearing. It is an interval that allows one rotating body to be rotated.

  According to the present invention, variation in release torque can be suppressed while reducing the size of the physique.

(First embodiment)
Hereinafter, a first embodiment in which the present invention is embodied in a power transmission mechanism PT used in a refrigerant compressor of a vehicle air conditioner will be described with reference to FIGS. In the following description, for the “front” and “rear” of the refrigerant compressor 10, the direction of the arrow Y shown in FIG.

  As shown in FIG. 1, the housing of the refrigerant compressor 10 as a rotating machine includes a cylinder block 11, a front housing 12 joined and fixed to the front end thereof, and a rear housing 14 joined and fixed to the rear end of the cylinder block 11. It consists of and. An intake valve forming plate 36, a valve plate 13, a discharge valve forming plate 28, and a retainer 33 are interposed between the cylinder block 11 and the rear housing 14 from the cylinder block 11 side to the rear housing 14 side. ing.

  A control pressure chamber 15 is defined between the cylinder block 11 and the front housing 12, and a rotating shaft 16 can rotate in the cylinder block 11 and the front housing 12 so as to penetrate the control pressure chamber 15. It is supported by. A support cylinder portion 12 a is formed at the front end portion of the front housing 12 so as to surround the front side of the rotating shaft 16. The front end portion of the rotating shaft 16 protrudes from the support cylinder portion 12a to the outside of the housing, and a power transmission mechanism PT is interposed between the front end portion of the rotating shaft 16 and the engine E of the vehicle as an external drive source. Has been. The rotation shaft 16 is rotated by connecting the engine E and the rotation shaft 16 by the power transmission mechanism PT.

  The rotary shaft 16 is rotatably supported on the front housing 12 by a radial bearing 18 on the front side. In the front housing 12, a shaft seal chamber 20 is formed between the front peripheral surface of the rotary shaft 16 and the inner peripheral surface of the front housing 12 facing the peripheral surface. A shaft seal member 21 that seals between the peripheral surface of the rotary shaft 16 and the peripheral surface of the shaft seal chamber 20 is provided in the shaft seal chamber 20. The rear side of the rotating shaft 16 is inserted into a shaft hole 11 b formed in the cylinder block 11 and is rotatably supported by the shaft hole 11 b by a radial bearing 19. Therefore, the rotating shaft 16 is rotatably supported by the housing (the cylinder block 11 and the front housing 12).

  In the control pressure chamber 15, a rotary support 22 is fixed to the rotary shaft 16, and the rotary support 22 is fixed to the rotary shaft 16 so as to be integrally rotatable. A thrust bearing 23 is provided between the rotary support 22 and the inner wall surface of the front housing 12. A swash plate 24 is accommodated in the control pressure chamber 15. An insertion hole 24a is formed in the center of the swash plate 24, and the rotary shaft 16 is inserted through the insertion hole 24a. A hinge mechanism 25 is interposed between the rotary support 22 and the swash plate 24. The swash plate 24 can be rotated synchronously with the rotary shaft 16 and the rotary support 22 by the hinge connection with the rotary support 22 via the hinge mechanism 25 and the support of the rotary shaft 16 via the insertion hole 24a. In addition, the tilt angle can be changed with respect to the rotation shaft 16 while being slid in the axial direction along the central axis L of the rotation shaft 16.

  In the cylinder block 11, a plurality of cylinder bores 26 (only one cylinder bore 26 is shown in FIG. 1) are formed through the rotation shaft 16 in the front-rear direction at equal angular intervals. A single-headed piston 27 is accommodated in the cylinder bore 26 so as to be movable in the front-rear direction. The front and rear openings of the cylinder bore 26 are closed by the valve plate 13 and the piston 27, and a compression chamber 37 whose volume changes in accordance with the movement of the piston 27 in the front and rear direction is defined in the cylinder bore 26. The piston 27 is anchored to the outer peripheral portion of the swash plate 24 via a pair of shoes 29, and moves in the cylinder bore 26 in the front-rear direction based on the rotation of the rotary shaft 16.

  A suction chamber 30 and a discharge chamber 31 are defined in the rear housing 14 so as to face the valve plate 13. Specifically, the suction chamber 30 is provided in the center of the rear housing 14, and the discharge chamber 31 is provided on the outer peripheral side of the suction chamber 30. In the valve plate 13, suction ports 32 are formed radially inward of the valve plate 13 and discharge ports 34 are formed radially outward of the valve plate 13 at positions facing the respective cylinder bores 26. .

  The suction valve forming plate 36 is formed with a suction valve 36 a that opens and closes the suction port 32 at a position corresponding to the suction port 32. Further, the suction valve forming plate 36 is formed with a discharge hole 36 b at a position corresponding to the discharge port 34. The discharge valve forming plate 28 is formed with a discharge valve 28 a that opens and closes the discharge port 34 at a position corresponding to the discharge port 34. The discharge valve forming plate 28 is formed with a suction hole 28 b at a position corresponding to the suction port 32. The opening position of the discharge valve 28a is regulated by the retainer 33. A capacity control valve 52 composed of an electromagnetic valve is assembled in the rear housing 14.

  In the refrigerant compressor 10, as the piston 27 moves, the refrigerant gas that passes through the suction hole 28b and the suction port 32, pushes away the suction valve 36a, and is sucked into the compression chamber 37 from the suction chamber 30 passes through the piston 27. Is compressed in the compression chamber 37. Further, the high-pressure refrigerant gas that passes through the discharge hole 36b and the discharge port 34 from the compression chamber 37 as the piston 27 moves and pushes out the discharge valve 28a and is discharged into the discharge chamber 31 is an external refrigerant circuit (not shown). Is derived. The return gas from the external refrigerant circuit is drawn into the suction chamber 30, and the refrigerant compressor 10 of this embodiment forms a refrigerant circulation circuit with the external refrigerant circuit. The cylinder block 11 (cylinder bore 26), the rotary shaft 16, the rotary support 22, the swash plate 24, the hinge mechanism 25, the piston 27, and the shoe 29 constitute a compression mechanism in the refrigerant compressor 10, and the compression mechanism rotates. It is driven based on the rotation of the shaft 16.

  The refrigerant compressor 10 is connected to a discharge chamber 31 serving as a discharge pressure region and the control pressure chamber 15, and a supply passage 54 for supplying the refrigerant gas in the discharge chamber 31 to the control pressure chamber 15 as a control gas. Is provided. The capacity control valve 52 is provided on the supply passage 54. The refrigerant compressor 10 is also provided with a discharge passage 53 that allows the control pressure chamber 15 to communicate with the suction chamber 30 serving as a suction pressure region and discharges the refrigerant gas in the control pressure chamber 15 to the suction chamber 30 serving as a control gas. It has been. The refrigerant gas discharged into the discharge chamber 31 passes through the supply passage 54 and is supplied to the control pressure chamber 15. The capacity control valve 52 adjusts the amount of refrigerant gas that passes through the supply passage 54 and is supplied to the control pressure chamber 15.

  The refrigerant gas in the control pressure chamber 15 is discharged to the suction chamber 30 through the discharge passage 53. The balance between the refrigerant gas supply amount to the control pressure chamber 15 via the supply passage 54 and the refrigerant gas discharge amount from the control pressure chamber 15 via the discharge passage 53 is controlled to determine the pressure of the control pressure chamber 15. (The control pressure chamber 15 is regulated). When the pressure in the control pressure chamber 15 is changed, the differential pressure between the control pressure chamber 15 and the cylinder bore 26 via the piston 27 is changed, and the inclination angle of the swash plate 24 is changed. As a result, the stroke of the piston 27 (the discharge capacity of the refrigerant compressor 10) is adjusted.

  Next, the power transmission mechanism PT will be described in detail. The power transmission mechanism PT is rotatably supported by a front housing 12 of the refrigerant compressor 10 via a bearing 60, is driven by the engine E, and is disposed coaxially with the pulley 64. And a hub 67 connected to each other. That is, the power transmission mechanism PT connects the pulley 64 as the first rotating body and the hub 67 as the second rotating body so as to transmit power. In the refrigerant compressor 10, the bearing 60 is mounted on the outer periphery of the support cylinder portion 12 a at the front end of the front housing 12. The bearing 60 includes an annular inner ring 61 mounted on the outer periphery of the support cylinder portion 12a, and an annular outer ring 63 disposed to face the outer periphery of the inner ring 61 via a ball 62 as a rolling element. Has been. The balls 62 are provided in a plurality of rows in the axial direction of the bearing 60.

  The pulley 64 is formed of a synthetic resin material in a cylindrical shape, and substantially the entire outer peripheral surface forms a belt hooking portion 64a, and a rib belt 65 from the engine E is hung on the belt hooking portion 64a. In the pulley 64, a cylindrical metal ring 66 is integrated with the inner peripheral surface on the front housing 12 side, and the metal ring 66 is integrally formed when the pulley 64 is formed. A part of the outer ring 63 on the front housing 12 side is press-fitted inside the metal ring 66, whereby the pulley 64 and the outer ring 63 are integrated with each other through the metal ring 66. That is, the pulley 64 is rotatably supported by the bearing 60. Therefore, the rotational power from the engine E is transmitted to the pulley 64 via the rib belt 65, and the pulley 64 rotates integrally with the outer ring 63 in the bearing 60.

  As shown in FIG. 3 (b), if the portion of the outer ring 63 that is press-fitted (connected) to the pulley 64 is a connecting portion 63 a, the inner ring 63 can be connected to the inner ring 63 when the connecting portion 63 a is press-fitted inside the pulley 64. The interval between the peripheral surface 63B and the outer peripheral surface 61A of the inner ring 61 is a predetermined interval α. The predetermined interval α is an interval in the bearing 60 that allows the balls 62 to roll between the peripheral surfaces 61A and 63B while bringing the balls 62 into contact with the outer peripheral surface 61A of the inner ring 61 and the inner peripheral surface 63B of the outer ring 63. It is.

  As shown in FIG. 3A, in a state before the connecting portion 63a is press-fitted inside the pulley 64, between the inner peripheral surface 63B of the outer ring 63 and the outer peripheral surface 61A of the inner ring 61 in the connecting portion 63a. Is set to be wider than the predetermined interval α formed after the connecting portion 63a is press-fitted. That is, the inner diameter of the connecting portion 63a is set so as to be wider than that after press-fitting so as to allow the interval β before press-fitting into the pulley 64. In the outer ring 63, the portion excluding the connecting portion 63a is not enlarged in diameter, and the interval between the inner peripheral surface 63B other than the connecting portion 63a and the outer peripheral surface 61A of the inner ring 61 is the predetermined interval α. Yes. As shown in FIG. 3B, when the connecting portion 63a is press-fitted inside the pulley 64, the connecting portion 63a is pressed against the inner peripheral surface of the pulley 64 (the inner peripheral surface of the metal ring 66) to reduce the diameter. As a result, a predetermined distance α is formed between the inner peripheral surface 63B of the outer ring 63 and the outer peripheral surface 61A of the inner ring 61 in the connecting portion 63a.

  As shown in FIG. 1, the hub 67 is fixed to the front end portion of the rotating shaft 16. The hub 67 is connected and fixed to the front end portion of the rotary shaft 16 so as to be integrally rotatable, and is disposed at a position coaxial with the pulley 64. The hub 67 includes a cylindrical portion 68 and an extending portion that extends from the front end portion of the cylindrical portion 68 in a direction orthogonal to the axial direction of the cylindrical portion 68 (the central axis L direction of the rotation shaft 16). 69 is integrally formed. Although not shown, the cylindrical portion 68 of the hub 67 and the rotary shaft 16 are abutted and engaged in the rotational direction of the rotary shaft 16 by spline engagement, a key structure, or the like. A damper accommodating portion 69a is formed in the extended portion 69, and a rubber damper D as an elastic member (buffer member) is accommodated in the damper accommodating portion 69a.

  A one-way clutch 70 is interposed between the pulley 64 and the hub 67 on the power transmission path between the pulley 64 and the hub 67. As shown in FIG. 3 (b), the one-way clutch 70 is disposed opposite to the inner clutch portion 63b formed integrally with the outer ring 63 of the bearing 60 with an interval on the outer peripheral side of the inner clutch portion 63b. And an outer clutch member 71. Further, the one-way clutch 70 includes a roller 72 interposed between the outer peripheral surface 63A of the inner clutch portion 63b and the inner peripheral surface 71B of the outer clutch member 71. That is, the inner clutch member in the one-way clutch 70 is formed by a part of the outer ring 63 (inner clutch portion 63 b), and the outer ring 63 is used in combination with the bearing 60 and the one-way clutch 70.

  In the outer ring 63, the inner clutch portion 63b is positioned in front of the connecting portion 63a and has an annular shape. Further, the connecting portion 63a and the inner clutch portion 63b are connected along the axial direction of the outer ring 63 (the axial direction of the rotary shaft 16), and in this axial direction, the connecting portion 63a is closer to the front housing 12 than the inner clutch portion 63b. While being offset to the side, the connecting portion 63a is located on the inner side of the inner clutch portion 63b in the radial direction of the outer ring 63. For this reason, the bearing 60 is located at a position offset toward the front housing 12 with respect to the one-way clutch 70 and is located closer to the rotating shaft 16 side. Therefore, a space with the bearing 60 as a bottom is formed on the inner peripheral side of the one-way clutch 70 (inner clutch portion 63b), and the rubber damper D of the hub 67 is accommodated in the space.

  Further, as shown in FIG. 1, the inner clutch portion 63 b and the outer clutch member 71 constituting the one-way clutch 70 are housed inside the pulley 64, and the outer peripheral surface 71 </ b> A of the outer clutch member 71 and the pulley 64. The outer clutch member 71 is separated from the inner peripheral surface 64 </ b> B, and the outer clutch member 71 is free from the pulley 64. The outer clutch member 71 has an annular shape, and the outer clutch member 71 is connected to the extending portion 69 of the hub 67 on the inner peripheral surface of the front end portion thereof.

  As shown in FIG. 4, a plurality of engaging recesses 711 are formed at equal intervals in the circumferential direction of the outer clutch member 71 on the inner peripheral surface 71 </ b> B at the front end portion of the outer clutch member 71. On the other hand, a plurality of engaging protrusions 691 are provided on the outer peripheral surface 69 </ b> A of the extending part 69 of the hub 67. Then, the engagement protrusions 691 of the hub 67 are engaged with the engagement recesses 711 of the outer clutch member 71, whereby the hub 67 and the outer clutch member 71 are connected, and the rotational power of the outer clutch member 71 is supplied to the hub. 67 can be transmitted.

  Further, as shown in the enlarged view of FIG. 4, a clearance CL <b> 1 is formed between the inner bottom surface 712 of the engaging recess 711 and the end surface 692 of the engaging protrusion 691 that face each other along the radial direction of the rotating shaft 16. Has been. For this reason, the outer clutch member 71 is not pressed outward by the hub 67 in the engaged state of the engagement recess 711 and the engagement protrusion 691. Further, as shown in FIG. 3B, in the engagement protrusion 691, the end surface 691b on the outer clutch member 71 side along the axial direction of the rotating shaft 16 and the inner surface of the engagement recess 711 facing the end surface 691b. A clearance CL <b> 2 is formed between 711 b and 711 b. For this reason, the outer clutch member 71 is not pressed by the hub 67 in the engaged state between the engagement recess 711 and the engagement protrusion 691.

  As shown in FIG. 2A, a plurality of support protrusions 71 a are provided on the inner peripheral surface 71 </ b> B of the outer clutch member 71 at regular intervals in the circumferential direction of the outer clutch member 71. A plurality of receiving recesses 73 defined by the support protrusions 71a are formed between the inner peripheral surface 71B of the outer clutch member 71 and the outer peripheral surface 63A of the inner clutch portion 63b. The rollers 72 are accommodated one by one.

  Further, on the inner peripheral surface 71 </ b> B of the outer clutch member 71, a wedge surface 71 b made of a flat surface is formed at a position located in each receiving recess 73. Further, a first concave surface 71c is formed on the inner peripheral surface 71B of the outer clutch member 71 on one side (front side) with respect to the wedge surface 71b in the rotational direction R of the outer clutch member 71. A second concave surface 71d is recessed on the other side (rear side) of 71b. And in each accommodation recessed part 73, the wedge-shaped space S which can set the predetermined width H and can clamp the roller 72 is formed in the opposing part of the wedge surface 71b and the outer peripheral surface 63A of the inner side clutch part 63b. ing. In the one-way clutch 70, when the roller 72 is engaged with the wedge-shaped space S, the hub 67 is synchronously rotated with respect to the pulley 64.

  On the other hand, in the one-way clutch 70, when the rotational speed of the pulley 64 (outer ring 63) becomes relatively slower than the rotational speed of the rotating shaft 16, the roller 72 moves from the wedge surface 71b side to the second concave surface 71d side in the wedge-shaped space S. It is moved and enters the second concave surface 71d. When the roller 72 enters the second concave surface 71d, the roller 72 is not sandwiched between the wedge-shaped spaces S. That is, the one-way clutch 70 is switched from the locked state to the free state in which the hub 67 is rotated relative to the pulley 64.

  Further, as shown in FIG. 2B, in the one-way clutch 70, when a predetermined transmission torque is applied from the pulley 64 to the rotating shaft 16, the roller 72 is detached from the locked position in the wedge-shaped space S by the inner clutch portion 63b. Then, it moves toward the first concave surface 71c and enters the first concave surface 71c. When the roller 72 enters the first concave surface 71 c, the roller 72 is not sandwiched by the wedge-shaped space S, and the hub 67 is rotated relative to the pulley 64. That is, the one-way clutch 70 prevents a transmission torque exceeding a predetermined value from acting on the rotating shaft 16, and the one-way clutch 70 functions as a torque limiter for interrupting power transmission from the pulley 64 to the hub 67. It has become. Then, the transmission torque of the predetermined value is set as a release torque that switches the one-way clutch 70 from the locked state to the free state and activates the torque limiter function.

  In the adjacent support protrusions 71a, roller support springs 74 are provided on the support protrusions 71a on the rear side in the rotation direction R so as to extend toward the front side in the rotation direction R. The roller urging spring 74 urges the roller 72 from the second concave surface 71d toward the wedge surface 71b. Further, the space between the inner peripheral surface 71B of the outer clutch member 71 and the outer peripheral surface 63A of the inner clutch portion 63b and in front of the roller 72 is between the outer clutch member 71 and the inner clutch portion 63b. Is provided with a ball 77 for maintaining the concentricity (see FIG. 3).

  In the power transmission mechanism PT having the above configuration, as shown in FIG. 2A, the pulley 64 is rotated by the power transmission from the engine E, and the outer ring 63 (inner clutch portion 63 b) integrated with the pulley 64 is provided. It is assumed that the rotation speed of the pulley 64 is relatively faster than that of the rotation shaft 16 in a state where the rotation is in the rotation direction R. Then, the roller 72 is moved from the second concave surface 71d toward the wedge surface 71b by the biasing force of the roller biasing spring 74. Then, the roller 72 enters between the wedge surface 71b and the outer peripheral surface 63A of the inner clutch portion 63b, that is, the wedge-shaped space S, and the roller 72 is clamped in the wedge-shaped space S.

  Then, the outer clutch member 71 is rotated in the same direction as the inner clutch portion 63b (outer ring 63) by the wedge action. That is, the one-way clutch 70 is in a locked state in which the hub 67 is synchronously rotated with respect to the pulley 64. The rotation of the outer clutch member 71 causes the rotation shaft 16 to rotate through the hub 67 connected to the outer clutch member 71. That is, the rotational power of the engine E is transmitted to the rotating shaft 16 by the power transmission mechanism PT, and the compression mechanism in the refrigerant compressor 10 is driven based on the rotation of the rotating shaft 16.

  On the other hand, it is assumed that the rotational speed of the pulley 64 is relatively slower than the rotational speed of the rotary shaft 16 due to the rotational fluctuation of the pulley 64 that fluctuates according to the combustion control of the engine E. Then, the roller 72 is moved from the wedge surface 71b side to the second concave surface 71d side in the wedge-shaped space S, that is, the roller 72 is detached from the wedge-shaped space S, and the roller 72 is in a free state with respect to the outer clutch member 71. Thus, the pulley 64 is idled. As a result, power transmission from the pulley 64 to the rotary shaft 16 via the hub 67 is interrupted, and a free state in which the rotary shaft 16 is relatively rotated is set. Therefore, the rotation variation of the pulley 64 is not transmitted to the rotating shaft 16 by the power transmission mechanism PT, and the rib belt 65 slips with respect to the pulley 64, noise is generated, or the rib belt 65 is damaged. Is prevented.

  Further, when the one-way clutch 70 is in the locked state and the rotating shaft 16 is rotating, the refrigerant compressor 10 is locked due to a failure of the refrigerant compressor 10 or the like, and an excessive transmission torque from the pulley 64 to the rotating shaft 16 is caused. , And the transmission torque reaches the release torque. Then, as shown in FIG. 2B, the roller 72 is moved from the lock position in the wedge-shaped space S toward the first concave surface 71c by the inner clutch portion 63b, and enters the first concave surface 71c. Then, the roller 72 is in a free state with respect to the inner peripheral surface 71B of the outer clutch member 71, and only the pulley 64 rotates. That is, power transmission from the pulley 64 to the rotating shaft 16 is cut off, and the torque limiter functions. Therefore, an excessive load is prevented from acting on the refrigerant compressor 10.

According to the above embodiment, the following effects can be obtained.
(1) In the power transmission mechanism PT having a torque limiter function, the connecting portion 63a of the outer ring 63 is press-fitted inside the pulley 64 to connect the pulley 64 and the outer ring 63 so as to be integrally rotatable, and the outer ring 63 (inner clutch An inner clutch member of the one-way clutch 70 is configured by the portion 63b). Further, the hub 67 is connected to the inner peripheral surface 71B of the outer clutch member 71 so as to be able to transmit power by the engagement relationship between the engagement protrusion 691 of the hub 67 and the engagement recess 711 of the outer clutch member 71. For this reason, in the one-way clutch 70, the outer clutch member 71 and the inner clutch portion 63b do not have a portion pressed to connect the pulley 64 and the hub 67, and the width H of the wedge-shaped space S is increased by the pressing force. It is prevented from changing. Therefore, the width H of the wedge-shaped space S can be maintained at a predetermined width, and the roller 72 can be detached from the wedge-shaped space S at a timing when a predetermined transmission torque (release torque) is applied. Therefore, the change in the width H of the wedge-shaped space S eliminates the problem that the roller 72 does not separate from the wedge-shaped space S even when the release torque is applied, and as a result, the variation in the release torque in the one-way clutch 70 can be suppressed. it can.

  (2) In the connecting portion between the hub 67 and the outer clutch member 71, a clearance CL1 is provided between the inner bottom surface 712 of the engagement recess 711 facing the radial direction of the rotating shaft 16 and the end surface 692 of the engagement protrusion 691. Is formed. Further, in the engagement protrusion 691, a clearance CL2 is formed between the end surface 691b on the outer clutch member 71 side along the axial direction of the rotating shaft 16 and the inner surface 711b of the engagement recess 711 facing the end surface 691b. Has been. For this reason, pressing force other than rotational power does not act on the outer clutch member 71, and the width H of the wedge-shaped space S can be maintained at a predetermined width, and variation in release torque can be more reliably suppressed. Can do.

  (3) In the power transmission mechanism PT, the outer ring 63 of the bearing 60 is integrally provided with the inner clutch portion 63b, and the outer ring 63 is used in combination with the bearing 60 and the one-way clutch 70, so the bearing 60 and the one-way clutch 70 are integrated. It has become. For this reason, for example, the number of parts can be reduced compared with the case where the bearing 60 for supporting the pulley 64 and the one-way clutch 70 are provided separately in the power transmission mechanism PT, and the power transmission mechanism PT The size in the radial direction can be reduced.

  (4) The inner diameter of the connecting portion 63a of the outer ring 63 is larger than the inner diameter of the connecting portion 63a after being press-fitted into the pulley 64. For this reason, when the connecting portion 63 a is press-fitted inside the pulley 64, the connecting portion 63 a is pressed against the inner peripheral surface 64 </ b> B of the pulley 64 and is reduced in diameter. Due to this reduced diameter, the distance between the inner peripheral surface 63B of the outer ring 63 and the outer peripheral surface 61A of the inner ring 61 in the connecting portion 63a is such that the inner peripheral surface 63B of the outer ring 63 and the outer peripheral surface of the inner ring 61 in the inner clutch portion 63b. The distance between the outer ring 63 and the inner ring 61 is the predetermined distance α. Therefore, in the bearing 60, the ball 62 can be reliably rolled between both the peripheral surfaces 61A and 63B while being in contact with the outer peripheral surface 61A of the inner ring 61 and the inner peripheral surface 63B of the outer ring 63.

  (5) In the power transmission mechanism PT, the bearing 60 is located inside the one-way clutch 70 and is offset to the front housing 12 side. And by accommodating the rubber damper D in the space formed by offsetting the bearing 60, the rubber damper D does not protrude from the power transmission mechanism PT, and the enlargement of the power transmission mechanism PT can be suppressed.

  (6) When the outer clutch member 71 and the hub 67 are connected, the end surface 692 of the engagement protrusion 691 does not press the inner bottom surface 712 of the engagement recess 711. For this reason, since the outer clutch member 71 is not pressed outward by the connection between the hub 67 and the outer clutch member 71, the width of the wedge-shaped space S is not changed by the pressing, and the wedge-shaped space The width H of S can be maintained at a predetermined size. As a result, variation in the width H of the wedge-shaped space S can be a cause, and it is possible to suppress variation in the timing at which the roller 72 is detached from the wedge-shaped space S when functioning as a torque limiter. Therefore, variation in release torque in the one-way clutch 70 can be suppressed.

  (7) Since variation in release torque in the one-way clutch 70 can be suppressed, when the refrigerant compressor 10 is locked by using the power transmission mechanism PT of the present embodiment, excessive transmission torque acts on the rotary shaft 16. This can be reliably prevented.

(Second Embodiment)
Next, a second embodiment in which the present invention is embodied in a power transmission mechanism PT used in a refrigerant compressor of a vehicle air conditioner will be described with reference to FIG. Note that in the second embodiment described below, the same components as those in the first embodiment described above are denoted by the same reference numerals, and redundant description thereof is omitted or simplified.

  As shown in FIG. 5, a bearing 80 is attached to the support cylinder portion 12 a of the front housing 12. The bearing 80 includes an annular inner ring 81 mounted on the outer periphery of the support cylinder portion 12a, and an annular outer ring 83 disposed opposite to the outer peripheral side of the inner ring 81 via a ball 82 as a rolling element. Has been. Then, a connecting portion 83 a as a part of the outer ring 83 on the front housing 12 side is press-fitted inside the metal ring 66, whereby the pulley 64 and the outer ring 83 are integrated via the metal ring 66. . Note that the space formed between the inner peripheral surface 83B of the outer ring 83 and the outer peripheral surface 81A of the inner ring 81 in the connecting portion 83a in a state before the connecting portion 83a of the outer ring 83 is press-fitted inside the pulley 64. β (not shown) is set to be wider than the predetermined interval α formed after the connecting portion 83a is press-fitted.

  A one-way clutch 85 is interposed between the pulley 64 and the hub 67 on the power transmission path between the pulley 64 and the hub 67. The one-way clutch 85 includes an outer clutch portion 83b that is integrally formed with the outer ring 83 of the bearing 80, an inner clutch member 86 that is opposed to the inner peripheral side of the outer clutch portion 83b with a space therebetween, and an outer clutch portion. The roller 88 is interposed between the inner peripheral surface 83B of the outer ring 83 and the outer peripheral surface 86A of the inner clutch member 86 at 83b. The outer clutch member in the one-way clutch 85 is formed by a part of the outer ring 83 (outer clutch part 83 b), and the outer ring 83 is used in combination with the bearing 80 and the one-way clutch 85.

  The outer clutch portion 83b and the inner clutch member 86 are in a position protruding forward from the pulley 64, and the outer peripheral surface 83A of the outer clutch portion 83b and the inner peripheral surface 64B of the pulley 64 are separated from each other. The outer clutch portion 83b is in a free state with respect to the pulley 64. The inner clutch member 86 has an annular shape, and is connected to the extending portion 69 of the hub 67 on the inner peripheral surface thereof so that it can rotate integrally with the hub 67.

  On the inner peripheral surface 86B of the inner clutch member 86, a plurality of engaging recesses 861 are formed at equal intervals in the circumferential direction of the inner clutch member 86. The engagement protrusions 691 of the hub 67 are engaged with the engagement recesses 861 of the inner clutch member 86, whereby the hub 67 and the inner clutch member 86 are connected. 67 can be transmitted.

  In addition, a clearance (not shown) is provided between the inner bottom surface (not shown) of the engaging recess 861 facing the radial direction of the rotating shaft 16 and the end face (not shown) of the engaging protrusion 691. Is formed. For this reason, the inner clutch member 86 is not pressed outward by the hub 67 in the engaged state of the engagement recess 861 and the engagement protrusion 691. Further, in the engagement protrusion 691, a clearance CL2 is formed between the end surface 691b on the inner clutch member 86 side along the axial direction of the rotating shaft 16 and the inner surface 861b of the engagement recess 861 facing the end surface 691b. Has been. For this reason, the inner clutch member 86 is not pressed by the hub 67 in the engaged state between the engagement recess 861 and the engagement protrusion 691. That is, the inner clutch member 86 is not subjected to a pressing force other than the rotational power, and the width of the wedge-shaped space (not shown) can be maintained at a predetermined size, and the variation in release torque can be more reliably performed. Can be suppressed.

  Although not shown, the one-way clutch 85 of the second embodiment includes a support protrusion, a receiving recess, a wedge surface, a roller biasing spring, a first concave surface, a second concave surface, and a wedge-shaped space, as in the first embodiment. ing. The one-way clutch 85 is in a locked state in which the hub 67 is synchronously rotated with respect to the pulley 64, and in a free state in which power transmission from the pulley 64 to the front housing 12 via the hub 67 is interrupted and the hub 67 is relatively rotated. Can be taken. The one-way clutch 85 functions as a torque limiter that interrupts power transmission from the pulley 64 to the rotary shaft 16 when the transmission torque from the pulley 64 to the rotary shaft 16 reaches the release torque.

  Therefore, in the second embodiment, in the power transmission mechanism PT having a torque limiter function, the connecting portion 83a of the outer ring 83 is press-fitted inside the pulley 64 to connect the pulley 64 and the outer ring 83 so as to be integrally rotatable. At the same time, an outer clutch member of the one-way clutch 85 is constituted by the outer ring 83 (outer clutch portion 83b). Further, the hub 67 is connected to the inner peripheral surface 86B of the inner clutch member 86 so as to be able to transmit power by the engagement relationship between the engagement protrusion 691 of the hub 67 and the engagement recess 861 of the inner clutch member 86. For this reason, in the one-way clutch 85, the outer clutch portion 83b and the inner clutch member 86 do not have a portion pressed for the connection between the pulley 64 and the hub 67, and the wedge-shaped space (not shown) is pressed by the pressing force. It is possible to prevent the area from changing. Therefore, the width of the wedge-shaped space can be maintained at a predetermined width, and the timing of the separation of the roller 88 from the wedge-shaped space when functioning as a torque limiter is caused by the variation in the width of the wedge-shaped space. Can be prevented from different. Therefore, variation in release torque in the one-way clutch 85 can be suppressed.

Each embodiment may be changed as follows.
○ The engagement relationship between the hub 67 and the outer clutch member 71 in the first embodiment is related to the engagement recess provided on the outer peripheral surface 69 </ b> A of the hub 67 and the inner peripheral surface 71 </ b> B of the outer clutch member 71. You may form by a protrusion. Further, the engaging relationship between the hub 67 and the inner clutch member 86 in the second embodiment is provided on the engaging recess provided on the outer peripheral surface 69 </ b> A of the hub 67 and the inner peripheral surface 86 </ b> B of the inner clutch member 86. You may form by an engaging protrusion.

In each embodiment, the outer rings 63 and 83 and the pulley 64 (metal ring 66) may be connected by spline engagement, a key structure, or the like.
○ The refrigerant compressor 10 is not a single-sided compressor that causes the single-headed piston 27 to perform the compressing operation, but the double-headed piston is compressed in the cylinder bores 26 provided on both front and rear sides of the control pressure chamber 15. A double-sided compressor may be used.

  The refrigerant compressor 10 is replaced with a configuration in which the swash plate 24 rotates integrally with the rotating shaft 16, and the swash plate 24 is supported so as to be rotatable relative to the rotating shaft 16. It may be a wobble) type compressor.

The refrigerant compressor 10 may be a fixed capacity type in which the stroke of the piston 27 cannot be changed.
As a rotary machine, the piston type refrigerant compressor 10 in which the piston 27 reciprocates is embodied, but any rotary machine in which power is transmitted from an external drive source by the power transmission mechanism PT can be used. You may apply.

Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.
(1) A rotary machine having a rotary shaft and having a power transmission mechanism for transmitting power from an external drive source connected to the rotary shaft, wherein the power transmission mechanism is as follows: A rotating machine provided with the power transmission mechanism according to any one of the preceding claims.

The longitudinal section showing the refrigerant compressor of a 1st embodiment. (A) is sectional drawing which shows a one-way clutch, (b) is sectional drawing which shows the state which the torque limiter of the one-way clutch functioned. (A) is a partial expanded sectional view which shows before press-fitting of a connection part, (b) is a partial expanded sectional view which shows the state which press-fitted the connection part inside the pulley. The front view which shows the connection state of a hub and an outer side clutch member. The expanded sectional view which shows the power transmission mechanism of 2nd Embodiment. The expanded sectional view which shows the power transmission mechanism of background art.

Explanation of symbols

  α ... predetermined intervals, CL1, CL2 ... clearance, E ... engine as an external drive source, S ... wedge-like space, PT ... power transmission mechanism, 10 ... refrigerant compressor as rotating machine, 11 ... cylinder block constituting the housing, DESCRIPTION OF SYMBOLS 12 ... Front housing which comprises a housing, 14 ... Rear housing which comprises a housing, 16 ... Rotating shaft, 60, 80 ... Bearing, 61, 81 ... Inner ring, 62, 82 ... Ball as rolling element, 63, 83 ... Outer ring 63A, outer peripheral surface of the inner clutch portion, 63a, 83a, a connecting portion, 63b, an inner clutch portion forming an inner clutch member, 64, a pulley as a first rotating body, 67, a hub as a second rotating body, 691. ... engaging protrusion as a protrusion, 691b ... end face, 692 ... end face, 70, 85 ... one-way clutch, 71 ... outer clutch member 71A: Inner peripheral surface of outer clutch member, 711: Engaging recess as recess, 711b ... Inner surface, 712 ... Inner bottom surface, 72, 88 ... Roller, 83B ... Inner peripheral surface of outer clutch portion, 83b ... Outer clutch member Outer clutch portion to be formed, 86 ... inner clutch member, 86A ... outer peripheral surface of inner clutch member, 861 ... engagement recess as a recess, 861b ... inner surface.

Claims (5)

A first rotating body rotatably supported by a housing of the rotating machine via a bearing and driven by an external drive source, and a first rotating body connected to a rotating shaft of the rotating machine and disposed coaxially with the first rotating body. A power transmission mechanism that couples two rotators so that power can be transmitted,
An inner clutch member and an outer clutch member opposed to the outer peripheral side of the inner clutch member via a roller are engaged with the roller in a wedge-shaped space formed between the opposed peripheral surfaces of both members. A one-way clutch that can be switched between a locked state in which the second rotating body is synchronously rotated with respect to the first rotating body and a free state in which the roller is removed from the wedge-shaped space and the second rotating body is relatively rotated with respect to the first rotating body. And when the transmission torque from the first rotating body to the second rotating body becomes excessive in the locked state, the roller is detached from the wedge-shaped space and the power transmission from the first rotating body to the second rotating body is cut off. The inner clutch member is formed by a part of the outer ring of the bearing, and the housing is more than the portion that becomes the inner clutch member in the outer ring. The outer ring is connected to the first rotating body by the connecting portion on the side so as to be rotatable integrally with the first rotating body, and the outer clutch member and the second rotating body are engaged by engagement of a protrusion and a recess formed between the outer clutch member and the second rotating body. And power transmission mechanism. A clearance is formed between an end surface of the projecting portion facing the radial direction of the rotating shaft and an inner bottom surface of the recessed portion, and an end surface on the outer clutch member side along the axial direction of the rotating shaft in the projecting portion. The power transmission mechanism according to claim 1, wherein a clearance is formed between the inner surface of the concave portion facing the end surface. A first rotating body rotatably supported by a housing of the rotating machine via a bearing and driven by an external drive source, and a first rotating body connected to a rotating shaft of the rotating machine and disposed coaxially with the first rotating body. There is a power transmission mechanism that connects the two rotating bodies so that power transmission is possible,
An inner clutch member and an outer clutch member opposed to the outer peripheral side of the inner clutch member via a roller are engaged with the roller in a wedge-shaped space formed between the opposed peripheral surfaces of both members. A one-way clutch that can be switched between a locked state in which the second rotating body is synchronously rotated with respect to the first rotating body and a free state in which the roller is removed from the wedge-shaped space and the second rotating body is relatively rotated with respect to the first rotating body. And when the transmission torque from the first rotating body to the second rotating body becomes excessive in the locked state, the roller is detached from the wedge-shaped space and the power transmission from the first rotating body to the second rotating body is cut off. The outer clutch member is formed by a part of the outer ring of the bearing, and the housing is more than the portion that becomes the outer clutch member in the outer ring. The outer ring is connected to the first rotating body by the connecting portion on the side so as to be rotatable integrally with the first rotating body, and the inner clutch member and the second rotating body are engaged by engagement of a protrusion and a recess formed between the inner clutch member and the second rotating body. And power transmission mechanism. A clearance is formed between the end surface of the projecting portion facing the radial direction of the rotating shaft and the inner bottom surface of the recess, and the end surface on the inner clutch member side along the axial direction of the rotating shaft in the projecting portion The power transmission mechanism according to claim 3, wherein a clearance is formed between the inner surface of the concave portion facing the end surface. The bearing accommodates a plurality of rows of rolling elements in the axial direction of the bearing between the outer ring and an inner ring disposed at a predetermined interval on the inner peripheral side of the outer ring, and the connecting portion And at least one row of rolling elements is housed in the position corresponding to the outer ring and the first rotating body are connected by press-fitting the connecting portion inside the first rotating body, and the connecting portion 5. The motive power according to claim 1, wherein an inner diameter of the power source is set such that a distance between the connecting portion and the inner ring before press-fitting into the first rotating body is larger than the predetermined distance. Transmission mechanism.

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