JP4725243B2 - Roller clutch - Google Patents

Description

  The present invention relates to an improvement in a roller clutch that is used by being incorporated in, for example, a reel for fishing gear, a business machine such as a printer or a copying machine.

  For example, as described in Patent Documents 1 and 2, a roller clutch has been conventionally incorporated into a reel for fishing gear. That is, a structure has been conventionally known in which a roller clutch is provided between a handle shaft that fixes a handle for winding a fishing line at an end thereof and a part of a cover of a reel and only allows rotation in a predetermined direction. And has been implemented. Specifically, when the handle is rotated to wind up the fishing line, the roller clutch is idled (overrun), so that the fishing line can be wound up. On the other hand, when the fishing line tends to be fed out by pulling the fish or the like, the roller clutch is locked to prevent the fishing line from being fed out.

  Further, as described in Patent Document 3, for example, a structure in which a one-way clutch such as a roller clutch is incorporated in a printer is also known. In the case of the structure described in Patent Document 3, the above-described one-way clutch is incorporated in a roller for fixing toner to paper, and this roller is driven even when the rotational force is hardly transmitted to this roller. The paper can be discharged. As a roller clutch used in various devices such as a printer such as a printer or a fishing gear reel as described above, there are various structures as described in Patent Documents 4 to 7, for example. Are known. 5-7 has shown the shell type roller clutch described in patent document 4 among these.

The basic structure and operation of the roller clutch will be described with reference to the shell-type roller clutch 1 . The roller clutch 1 includes an outer ring 2, a plurality of rollers 3 and 3, a cage 4, and a plurality of springs 5 and 5. Out of these, the outer rings 2 are each formed in a cylindrical shape by a hard metal plate material such as bearing steel. In use, for example, it is internally fitted and fixed to a partial inner peripheral surface of a housing such as a reel cover. The inner peripheral surface of such an outer ring 2 is a cam surface 6 that is uneven in the circumferential direction. That is, a plurality of recesses 7, 7 each called a ramp portion are formed on the inner peripheral surface of the outer ring 2 at equal intervals in the circumferential direction, and the inner peripheral surface of the outer ring 2 is used as the cam surface 6. . Further, at both axial ends of the outer ring 2, a pair of flanges 8a and 8b each having an inward flange shape and different thickness dimensions are provided, and a metal plate constituting the outer ring 2 is directed inward in the diameter direction. It is formed by bending. The plurality of rollers 3, 3, the cage 4, and the plurality of springs 5, 5 are provided inside the outer ring 2 in the diameter direction as described above.

  Among these, the cage 4 is formed integrally with a bowl-shaped cylindrical shape using a synthetic resin (for example, a synthetic resin such as polyamide 46 mixed with about 20% glass fiber), and each pair is a ring. Rim portions 9, 9 and column portions 10, 10 that connect the inner side surfaces of both rim portions 9, 9. Such a retainer 4 is configured to rotate relative to the outer ring 2 by engaging convex portions formed on the outer peripheral surfaces of the rim portions 9 and 9 with the concave portions 7 and 7 constituting the cam surface 6. Is blocked. Further, between the cage 4 and the rollers 3 and 3, the rollers 3 and 3 are directed to the shallow side of the recesses 7 and 7 in the same direction with respect to the circumferential direction (the left direction in FIG. 7). The above-mentioned springs 5 and 5 are provided to press the

  The roller clutch 1 configured as described above has the outer ring 2 fitted and fixed to the housing, and the inner side of the plurality of rollers 3 and 3, for example, a rotary shaft 11 such as a handle shaft of a reel, and the like. And assembled in a state where the relative rotating member is inserted. In this assembled state, a cylindrical space 12 is formed between the inner peripheral surface of the outer ring 2 and the outer peripheral surface of the rotating shaft 11. The width dimension of the cylindrical space 12 with respect to the diameter direction of the outer ring 2 (vertical direction in FIGS. 5 and 7) is larger than the outer diameter of the rollers 3 and 3 in the portions corresponding to the recesses 7 and 7, In the part which remove | deviated from these each recessed parts 7 and 7, it is smaller than the outer diameter of these each rollers 3 and 3.

  In the state where the roller clutch 1 configured as described above is provided between the outer peripheral surface of the rotating shaft 11 and the inner peripheral surface of the housing, the roller clutch 1 includes a housing in which the outer ring 2 is fitted and fixed. Only the relative rotation of the rotating shaft 11 in a predetermined direction is transmitted. That is, when the rotating shaft 11 rotates with respect to the outer ring 2 in the same direction as the pressing direction of the rollers 3 and 3 by the springs 5 and 5, the outer peripheral surface of the rotating shaft 11 is configured. A force in the same direction as the pressing direction acts on the rollers 3 and 3 from the cylindrical surface 13. As a result, each of these rollers 3 and 3 is displaced toward a portion having a narrow width in the radial direction of the cylindrical space 12 and bites into the portion in a wedge shape. As a result, the outer ring 2 and the rotating shaft 11 are locked, and the rotating shaft 11 cannot rotate relative to the outer ring 2.

  On the other hand, when the rotating shaft 11 rotates in the direction opposite to the pressing direction with respect to the outer ring 2, a force in the direction opposite to the pressing direction is applied from the cylindrical surface 13 to the rollers 3 and 3. Works. As a result, each of the rollers 3 and 3 tends to be displaced toward a wide portion in the radial direction of the cylindrical space 12. At this time, the rollers 3 and 3 bend (elastically compress) the springs 5 and 5. As described above, each of the rollers 3 and 3 displaced toward the wide portion can freely roll and slightly displace at the portion. As a result, an overrun state occurs between the outer ring 2 and the rotating shaft 11, and the rotating shaft 11 can rotate with respect to the outer ring 2.

  In FIGS. 6 and 7, the springs 5 and 5 are schematically shown. In general, as a spring incorporated into the roller clutch 1, a plate spring formed by bending a plate material is used. There are many. FIG. 8 shows an example of a structure using a leaf spring as a spring incorporated in the roller clutch. The spring 5a shown in FIG. 8 is formed by bending a plate material such as stainless steel so that the base 14 and one end portion (right end portion in FIG. 8) of the base portion 14 extend in the thickness direction of the base portion 14 (FIG. 8). And a pressing piece 15 bent in the vertical direction). The pressing piece 15 has a tip portion extending to the other end portion (left end portion in FIG. 8) of the base portion 14, and an intermediate portion or a tip portion in a free state substantially in the axial direction (left and right direction in FIG. 8). They are parallel. The cage 4a incorporating such a spring 5a is disposed in the cylindrical space 12 in a state in which relative rotation with respect to the outer ring 2 having the cam surface 6 shown in FIGS. (See FIGS. 6 and 7). And between each pillar part 10 formed in the circumferential direction several places, each roller 3 is hold | maintained so that some displacement regarding rolling and the circumferential direction is possible. Further, the end side support plate portions 16 and 16 and the intermediate side support plate portion 17 are provided on the outer peripheral surface of each column portion 10 so as to lock the base portion 14 of the spring 5a at both ends and the intermediate portion in the axial direction. Are formed in a state protruding outward in the radial direction.

  In order to lock the spring 5 a to the retainer 4 a, the base portion 14 is disposed between the both end side support plate portions 16 and 16 and the intermediate side support plate portion 17. Then, the intermediate part one side surface (upper surface in FIG. 8) of the base portion 14 is brought into contact with the other circumferential side surface (lower surface in FIG. 8) of the intermediate support plate portion 17. At the same time, the other side surfaces of the both end portions of the base portion 14 are brought into contact with a portion closer to the intermediate portion in the axial direction (left-right direction in FIG. 8) on one side surface in the circumferential direction of the both end side support plate portions 16 and 16. Thus, the base portion 14 is locked between the support plate portions 16 and 17. Further, both end portions of the base portion 14 are brought into contact with or in close proximity to the stepped surfaces 18 of the both end side support plate portions 16, 16 so as to position the spring 5a in the axial direction. In this manner, the pressing piece 15 constituting the spring 5a is elastically brought into contact with the rollers 3 in a state where the base portion 14 is locked between the support plate portions 16 and 17. These rollers 3 are pressed in the same direction with respect to the circumferential direction toward a portion where the radial width of the cylindrical space 12 is narrow. The pressing piece 15 has an intermediate part or a tip part substantially parallel to the axial direction in a free state, that is, substantially parallel to an arrangement direction of the rollers 3, and the intermediate part or the tip part is set to the rollers. 3 is brought into contact with the rolling surface. Therefore, when each of the rollers 3 is pressed by the pressing piece 15, it is difficult for the rollers 3 to be skewed.

The outer ring 2 constituting the shell type roller clutch 1 shown in FIGS. 5 to 7 is fitted and fixed to a partial inner peripheral surface of a housing such as a reel cover. That is, as shown in FIG. 9, an outer ring 2a formed by pressing a metal plate is fitted and fixed to a housing 20 formed of a light alloy such as an aluminum alloy or a magnesium alloy or a synthetic resin. Since the housing 20 and the outer ring 2a that are fitted and fixed in this manner are made of different materials, the fitting strength may be reduced due to a temperature change during use. For example, when the housing 20 is made of synthetic resin and the outer ring 2a is made of carbon steel such as S12C, the linear expansion coefficient of the housing 20 is larger than that of the outer ring 2a. The housing 20 expands more than the outer ring 2a. For this reason, the fitting strength between the housing 20 and the outer ring 2a is lowered. Accordingly, if no measures are taken between the housing 20 and the outer ring 2a, a creep phenomenon may occur in which the housing 20 and the outer ring 2a rotate relative to each other due to a decrease in the fitting strength.

  In order to prevent such a creep phenomenon, protrusions 21 and 21 are formed in the axial direction at a plurality of circumferential positions on the inner circumferential surface of the housing 20, and the circumference of the outer circumferential surface of the outer ring 2a. Concave grooves 22 and 22 are formed from the insertion side end to the housing 20 to the axially intermediate portion at positions aligned with the protrusions 21 and 21 at a plurality of positions in the direction. In addition, the height of each said protrusion 21, 21 or the depth of each said concave groove 22, 22 does not change over an axial direction, respectively. When the outer ring 2 a is fitted and fixed in the housing 20, the protrusions 21 and 21 are engaged with the concave grooves 22 and 22. Thereby, the relative rotation of the housing 20 and the outer ring 2a can be prevented regardless of the temperature rise during use. However, since the fitting of the outer ring 2a into the housing 20 is usually performed by an interference fit, the structure in which the protrusions 21 and 21 and the concave grooves 22 and 22 are engaged as described above. In this case, it is difficult to perform the fitting operation between the housing 20 and the outer ring 2a. For this reason, there is a possibility that damage such as peeling may occur on the surfaces of the protrusions 21 and 21 or the concave grooves 22 and 22 at the time of insertion.

JP 2000-116923 A JP 2001-17042 A JP 2000-242126 A JP-A-11-117954 JP 2002-89591 A Japanese Utility Model Publication No. 6-4434 JP 2004-156631 A

The present invention has been invented in order to realize a structure in which a roller clutch can be easily inserted into a housing in view of the circumstances as described above.

The roller clutch of the present invention includes an outer ring, a cam surface, a pair of flanges, a plurality of rollers, a cage, and a plurality of springs.
Of these, the outer ring is fitted and fixed inside the housing having an inner circumferential surface as a cylindrical surface.
Further, the cam surface is an unevenness extending in the circumferential direction formed on the inner peripheral surface of the outer ring.
Further, the both flange portions are formed in a state where they are bent radially inward from both axial end portions of the outer ring, and each has an inward flange shape and different thickness dimensions .
Each roller is provided in a cylindrical space between the cam surface and a cylindrical surface provided on an outer peripheral surface of a member inserted inside the outer ring.
The retainer is supported on the inner side of the outer ring in a state in which relative rotation with respect to the outer ring is prevented, and holds the rollers so as to be slightly displaceable in the rolling and circumferential directions.
The springs are provided between the cage and the rollers, and press the rollers in the same direction with respect to the circumferential direction.
Furthermore, concave grooves are provided in a plurality of locations on the outer peripheral surface of the outer ring in the axial direction from the end portion on the insertion side to the housing. Then, in a state where the outer ring is fitted and fixed to the housing, the protrusions formed in the axial direction at a plurality of circumferential positions on the inner peripheral surface of the housing are engaged with the concave grooves. This prevents relative rotation (creep) between the housing and the outer ring.

In particular, in the roller clutch according to the present invention, the outer peripheral surface of the outer ring on the side where the outer ring is inserted into the housing and on the side provided with a flange having a large thickness among the both flanges. In addition, an inclined surface portion that is inclined in a radially inward direction is formed only at the end portion of each of the concave grooves toward the distal end side that is the outer surface side of the flange portion having a large thickness dimension .

In the roller clutch of the present invention configured as described above, the inclined surface portion formed at least at the end of each concave groove in the outer peripheral surface of the insertion side end of the outer ring serves as a guide surface, and the roller clutch can be easily inserted into the housing. it can. Moreover, the strength reduction of a collar part based on forming the said inclined surface part in the insertion side edge part among the said outer rings can be suppressed.

FIG. 1 shows a first example of a reference example related to the present invention . It should be noted that the feature of this reference example is that the end side support plate is used to prevent the spring 5a from being excessively bent at the time of overrun and causing the bent portion 19 to fatigue early or to be crushed by the rollers 3. A part of the parts 16a, 16a protrudes in the circumferential direction from the bent part 19. The basic structure and operation of the roller clutch are the same as the contents described in the conventional structure shown in FIGS. 5 to 7 and the structure shown in FIG. Therefore, in regard to portions overlapping with the contents described in these figures 5 to 8, and omitted or simplified illustration and description, it will be mainly described below characteristic portions of the present embodiment.

In the case of the roller clutch of the present reference example, the end side support plates formed respectively at both ends in the axial direction (left and right direction in FIG. 1) of the outer peripheral surface of the column portion 10 provided at a plurality of locations in the circumferential direction of the cage 4b. Protruding portions 23 are formed on the portions 16a and 16a, respectively. That is, of the circumferential direction one side surface (upper surface in FIG. 1) of the both end side support plate portions 16a and 16a on the side pressing each of the rollers 3, than the portion where the base portion 14 of the spring 5a is in contact. A portion closer to the end in the axial direction is projected from the bent portion 19 toward the side pressing the rollers 3 (upper side in FIG. 1) with respect to the circumferential direction as the projecting portion 23. The bent portion 19 is a continuous portion of the base 14 and the pressing piece 15 constituting the spring 5a, and is a portion that is curved (folded back) in a substantially U shape. Therefore, the protruding portion 23 only has to protrude beyond the curved portion. On the other hand, of the circumferential side single side surfaces of the both end side support plate portions 16a, 16a, the portion closer to the middle in the axial direction is opposite to the side pressing the rollers 3 in the circumferential direction (lower side in FIG. 1). Are stepped 24 respectively. Further, both end portions in the axial direction of the base portion 14 of each of the springs 5a are brought into contact with the step portions 24, 24.

In the case of this reference example configured as described above, even if the roller clutch overrun speed is high and the amount of displacement of each roller 3 in the direction in which each spring 5a is bent tends to increase, each roller 3 However, it abuts against the projecting portions 23 formed at the portions near the both ends in the axial direction of the both end side support plate portions 16a, 16a. For this reason, it is possible to prevent the springs 5a from being excessively bent and the stress acting on the bent portion 19 from becoming too large, or the rollers 3 from interfering with the bent portion 19. As a result, the bent portion 19 can be prevented from being fatigued or crushed early, and the normal operation of the roller clutch can be ensured. Note that the protruding portion 23 only has to protrude to the side that presses each roller 3 with respect to the bent portion 19. However, when the protruding portion 23 is excessively protruded, the respective rollers 3 are recessed 7 (see FIGS. 6 to 7). ) May not move sufficiently, and the overrun torque may increase. For this reason, the amount of protrusion of the protrusion 23 is restricted in consideration of this point.

Incidentally, in order to restrict the movement of the circumferential direction of each roller 3 at the time of overrun, but a portion of the intermediate side support plate part 17 it is considered also to project in the circumferential direction, like to the shape of the reference example In the case of the spring 5 a, the pressing piece 15 constituting the spring 5 a exists between the intermediate support plate portion 17 and the rollers 3. For this reason, in the structure of this reference example , if a part of the intermediate support plate portion 17 is protruded in the circumferential direction so as to restrict the movement of the rollers 3 in the circumferential direction, the elasticity of the pressing piece 15 is increased. The amount of deformation is small (too little). For this reason, the structure which makes this intermediate side support plate part 17 protrude cannot be employ | adopted.

2 to 3 show an embodiment of the present invention. The feature of this embodiment is that at least a plurality of circumferential directions of the outer circumferential surface of the outer ring 2c are arranged at least on the outer circumferential surface of the insertion side end so that the outer ring 2c can be easily fitted and fixed to the housing 20 (see FIG. 9). The inclined surface portion 25 is formed at the end portion of the concave groove 22a formed at the location. The basic structure and operation of the roller clutch are the same as those described in the conventional structure shown in FIGS. 5 to 7 and the structure shown in FIG. For this reason, illustrations and explanations are omitted or simplified with respect to the parts overlapping with those described in FIGS. 5 to 7 and 9, and hereinafter, the characteristic parts of the present embodiment will be mainly described.

In the case of the present embodiment, inclined surface portions 25 are respectively formed at the insertion side end portions (left end portions in FIG. 2) of the respective concave grooves 22a formed on the outer peripheral surface of the outer ring 2c. As shown in detail in FIG. 3, the inclined surface portion 25 is a tapered surface that is inclined inward in the radial direction toward the tip by pressing the end of the groove 22 a. In the illustrated example, the inclination angle θ of the inclined surface portion 25 with respect to the axial direction (left-right direction in FIG. 2) is 15 °.

As is well known, the thickness of one flange portion 8b is made thin so that it is easy to bend the one flange portion 8b after incorporating a roller or the like on the inner diameter side of the outer ring 2c.

In the case of the present embodiment configured as described above, when the roller clutch having the outer ring 2c is inserted into the housing 20, the inclined surface portions 25 respectively formed at the insertion side end portions of the concave grooves 22a are provided with the concave portions. It serves as a guide for engagement between the groove 22a and the protrusions 21 and 21 (see FIG. 9) formed on the inner peripheral surface of the housing 20. Therefore, it is possible to smoothly engage the concave grooves 22a and the protrusions 21 and 21 .

  For this reason, when the roller clutch is inserted into the housing 20, the assembling work is facilitated, and the surface of each of the protrusions 21, 21 or the concave grooves 22a is less likely to be damaged. Further, since the force required for assembly is small, for example, the circumferential phases of the ridges 21, 21 and the concave grooves 22a are different (the ridges 21, 21 and the concave grooves 22a are different from each other). Are not matched), the degree to which the force required for assembly becomes larger than that in the case of regular assembly becomes significant. Therefore, it can be easily determined that the assembly is wrong. For this reason, it is possible to prevent erroneous assembly of the housing 20 and the roller clutch.

  As described above, when the housing 20 and the roller clutch are assembled in a state where the phases of the protrusions 21 and 21 and the concave grooves 22a are different from each other, the protrusions 21 and 21 are connected to the outer periphery of the outer ring 2c. The outer ring 2c is compressed by pressing a portion of the surface that is out of the concave grooves 22a. Then, the radial gap in the cylindrical space existing between the inner peripheral surface of the outer ring 2c and the outer peripheral surface of the rotating shaft, for example, becomes smaller than a predetermined value. As described above, when the radial gap in the cylindrical space is reduced, the function of the roller clutch may be deteriorated, such as malfunction. Therefore, if the erroneous assembly of the housing 20 and the roller clutch can be prevented as in the present embodiment, such a decrease in the function of the roller clutch can be prevented.

FIG. 4 shows a second example of a reference example relating to the present invention . The outer ring 2d of the roller clutch 1b that is the object of this reference example is formed by changing the thickness of the outer ring 2d with respect to the circumferential direction so as to increase the depth of the recesses 7a, 7a constituting the cam surface 6a. It is thickened at the part outside 7a. In other words, of the inner peripheral surface of the outer ring 2d, the inner diameter dimension of the portion removed from each of the recesses 7a and 7a is reduced to increase the radial depth of the recesses 7a and 7a. In the case of this reference example , the maximum radial depth (hanging margin) δ of each of the recesses 7a, 7a is set to be the thickness of the outer ring 2d at a position away from the recesses 7a, 7a in the circumferential direction. 27% of the total. In FIG. 4, the cage for holding the rollers 3 and 3 is omitted.

  In the case of the roller clutch 1b having the outer ring 2d configured as described above, the roller clutch 1b is externally fitted, for example, due to insufficient rigidity of the housing 20a made of a light alloy such as synthetic resin or aluminum alloy, or used. It is possible to prevent the malfunction of the roller clutch 1b due to the temperature rise. That is, due to temperature rise during use and insufficient rigidity of the housing 20a, the radial dimension of the cylindrical space 12 existing between the cam surface 6a and the cylindrical surface 13 of the rotary shaft 11 becomes larger than an appropriate value. There is a case. Even in such a case, since the depth in the radial direction of each of the recesses 7a and 7a is increased, the rollers 3 and 3 are circumferentially moved from the recesses 7a and 7a when locked or overrun. It is possible to prevent climbing into (dive into) the detached part.

In particular, in the case of this reference example , the hanging allowance δ of each of the recesses 7a and 7a is 27% of the thickness of the portion of the outer ring 2d outside the recesses 7a and 7a. It is possible to more effectively prevent the rollers 3 and 3 from getting on (submitting). In other words, in the case of the conventional structure, the contact amount of the concave portion constituting the cam surface is usually about 6 to 18%. For this reason, there is a possibility that the rollers may run up or sink due to insufficient rigidity of the housing or an increase in the radial dimension of the cylindrical space due to a temperature rise during use. On the other hand, as in the structure of the present reference example , when the above-mentioned allowance δ is 27%, even when the radial dimension of the cylindrical space 12 increases, the rollers 3 and 3 can sufficiently run and sink. Can be prevented. As a result, it is possible to prevent malfunction of the roller clutch 1b due to insufficient rigidity of the housing 20 or a temperature increase during use. Note that the take allowance [delta], in consideration of the usage and the like, preferably, 20-40% of the wall thickness of the recesses 7a, the portion deviating from 7a of the outer ring 2d, more preferably from 25% to 35% .

In order to manufacture the outer ring 2d as described above, it is difficult to perform press working that has been conventionally employed as a method for manufacturing an outer ring of a roller clutch. That is, since the thickness of the outer ring 2d is increased, it is difficult to ensure the shape accuracy when processed by press working. For this reason, in the present reference example , the outer ring 2d is formed by drawing. Specifically, by performing a drawing process on a carbon steel pipe such as STKM10, which is a material of the outer ring 2d, a plurality of recesses are provided in the circumferential direction at equal intervals on the inner peripheral surface over the entire axial direction. Use intermediate material. Next, the intermediate material is cut into a predetermined length and then subjected to a predetermined finishing process such as cutting and polishing. As a result, the outer ring 2d having the cam surface 6a having a large radial depth of the recesses 7a, 7a as described above is obtained on the inner peripheral surface.

If comprised in this way, the outer ring | wheel 2d which enlarged the depth of each recessed part 7a and 7a by enlarging thickness can be obtained easily and accurately. In the case of this reference example , since the thickness of the portion of the outer ring 2d where the recesses 7a and 7a are not formed is considerably increased, it is more difficult to manufacture the outer ring 2d with high precision by press working. For this reason, as described above, the manufacturing method of the present reference example , in which the steel pipe that is the material of the outer ring 2d is subjected to a drawing process, and the concave portions corresponding to the concave portions 7a and 7a are formed on the inner peripheral surface of the steel pipe. It is more effective to adopt the outer ring 2d having excellent shape accuracy.

  The roller clutch according to the present invention is used for driving an auxiliary machine for an idling stop car, an alternator and a compressor for an automobile auxiliary machine, a starter motor constituting an automobile starting device, in addition to a reel for fishing gear and an office machine such as a printer. It can also be used by being incorporated in a roller clutch built-in pulley device that is used by being fixed to the end of a rotating shaft such as a motor.

The figure which shows the 1st example of the reference example regarding this invention in the state which took out the holder | retainer, the spring, and the roller, and looked at the one part from radial direction outer side. The fragmentary sectional view which shows the outer ring | wheel integrated in the structure of the Example of this invention. The perspective view which expands and shows the inclined surface part of FIG. The half part sectional view which abbreviate | omits and shows the 2nd example of the reference example regarding this invention in the state which fitted in the housing. Sectional drawing which shows an example of a conventional structure. II sectional drawing of FIG. The B section enlarged view of FIG. The figure similar to FIG. 1 which shows an example of the conventional structure which incorporated the leaf | plate spring as a spring which presses a roller. The perspective view which shows an example of the structure which fits a roller clutch to a housing.

1, 1b Roller clutch 2, 2a, 2c, 2d Outer ring 3 Roller 4, 4a, 4b Cage 5, 5a Spring 6, 6a Cam surface 7, 7a Recess
8a, 8b collar portion 9 rim portion 10 column portion 11 rotating shaft 12 cylindrical space 13 cylindrical surface 14 base portion 15 pressing piece 16, 16a end portion side support plate portion 17 intermediate side support plate portion 18 step surface 19 bent portion 20, 20a Housing 21 Projection strip 22, 22a Groove 23 Projection 24 Step
25 Inclined surface

Claims (2)

An outer ring fitted inside and fixed to the inside of the housing having an inner peripheral surface as a cylindrical surface, a cam surface formed on the inner peripheral surface of the outer ring and having irregularities extending in the circumferential direction, and both axial ends of the outer ring A pair of flanges each formed in an inward flange shape and having different thickness dimensions, and an outer peripheral surface of a member inserted inside the cam surface and the outer ring. A plurality of rollers provided in a cylindrical space between the provided cylindrical surfaces and supported on the inner side of the outer ring in a state in which relative rotation with respect to the outer ring is prevented. A retainer that is held so as to be slightly displaceable with respect to the direction, and a plurality of springs that are provided between the retainer and the rollers and press the rollers in the same direction with respect to the circumferential direction. Above several places on the outer circumference A concave groove is provided in the axial direction from the end on the insertion side to the housing, and the outer ring is fitted and fixed to the housing in the axial direction at a plurality of circumferential positions on the inner peripheral surface of the housing. In the roller clutch that prevents the relative rotation between the housing and the outer ring by engaging the protrusion formed with the concave grooves, at the end of the outer ring inserted into the housing , Out of the outer peripheral surface of the end portion on the side where the thickness portion having a large thickness is provided among the both flange portions , only the end portion of each of the concave grooves is the outer surface side of the flange portion having a large thickness dimension. A roller clutch characterized in that an inclined surface portion that is inclined in a radially inward direction toward the tip end side is formed. The roller clutch according to claim 1, wherein an inclination angle of the inclined surface portion with respect to the axial direction of the outer ring is 10 to 30 degrees.

Images