JP2019157966A - Rotation transmission device - Google Patents

Abstract

To prevent abrasion of a roller or cylindrical surface due to high-speed rotation with respect to the cylindrical surface of an output side member together with an input side member and a holder in a state where the roller of a clutch mechanism is at a neutral position.SOLUTION: A holder 18 has a pocket surface 24 that can contact with a roller 17 in a circumferential direction. The value of the arithmetic average roughness Ra of the pocket surface 24 is equal to or less than the value of the arithmetic average roughness Ra of a cylindrical surface 15 of an output side member 2. Consequently, when an input side member 1 idles in a state where the roller 17 is in a neutral position, the roller 17 pressed against the cylindrical surface 15 by the centrifugal force easily autorotates.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a rotation transmission device used for switching between transmission and interruption of power in a power transmission path.

  Conventionally, as a rotation transmission device, an input side member, an output side member having an inner peripheral portion arranged outside the input side member, and transmission and interruption of rotational torque between the input side member and the output side member are performed. What is provided with the clutch mechanism to perform is known. The clutch mechanism includes a cylindrical surface provided on the inner peripheral portion of the output side member, a cam surface provided on the input side member and forming a wedge space between the cylindrical surface, and a space between the cylindrical surface and the cam surface. And a retainer for holding the roller. The cage has a pocket surface that can contact the roller in the circumferential direction. The roller is disposed so as to be movable between an engagement position where the roller is engaged with the cylindrical surface and the cam surface by a relative rotation of the cage with respect to the cam surface, and a neutral position where the engagement is released. An electromagnetic actuator is used as a means for controlling the relative rotation between the cage and the cam surface.

  For example, rotation transmission devices such as Patent Documents 1 and 2 include a switch spring, an electromagnet, a rotor, and an armature. The switch spring is elastically deformed by the relative rotation of the cage with respect to the input side member, and the cage is returned and rotated by the restoring elasticity so that the roller moves to the neutral position. The armature is supported so as to be movable in the axial direction, and is prevented from rotating with respect to the cage by energizing the electromagnetic coil of the electromagnet. The rotor is prevented from rotating by the output side member. When the armature is attracted to the rotor by the energization described above, the cage is connected to the output side member via the armature and the rotor, and the roller is rotated by the relative rotation of the cage and the input side member. It is engaged with the cylindrical surface and the cam surface of the input side member, and rotational torque is transmitted between the input side member and the output side member. When the energization described above is released, the cage is returned and rotated by the spring force of the switch spring, the roller pushed in the circumferential direction on the pocket surface of the cage is moved to the neutral position, and the roller against the cylindrical surface and the cam surface is moved. The engagement is released.

JP 2007-247713 A JP-A-2005-90678

  In the clutch mechanism as described above, when the input side member rotates at a high speed while the roller is in the neutral position, the rollers held on the cam surface of the input side member and the pocket surface of the cage are the input side member and Rotates at high speed with the cage. For this reason, since the roller is pressed against the cylindrical surface of the output side member by the centrifugal force acting on the roller and keeps rotating at a high speed relative to the cylindrical surface together with the input side member and the cage in this state, the cylindrical surface and the roller There is a possibility that the drag torque increases at the contact portion, and the roller and the cylindrical surface wear.

  Therefore, the problem to be solved by the present invention is to wear the roller and the cylindrical surface by rotating at high speed with respect to the cylindrical surface of the output side member together with the input side member and the cage while the roller of the clutch mechanism is in the neutral position. Is to prevent.

  In order to achieve the above object, a first solving means according to the present invention includes: an input side member; an output side member having an inner peripheral portion disposed outside the input side member; and the input side member. A clutch mechanism that transmits and shuts off rotational torque between the output side members, and the clutch mechanism is provided on a cylindrical surface provided on the inner peripheral portion of the output side member, and on the input side member. A cam surface that forms a wedge space between the cylindrical surface, a roller disposed between the cylindrical surface and the cam surface, and a retainer that retains the roller. A pocket surface that can contact the roller in a direction, and the roller engages with the cylindrical surface and the cam surface by relative rotation of the retainer with respect to the cam surface, and the engagement. It is arranged to be movable between the neutral position to be released In the rotation transmitting device, the value of the arithmetic average roughness Ra of said pocket surface, is to employ the arithmetic mean is the value of the roughness Ra following arrangement of said cylindrical surface. Here, arithmetic mean roughness Ra means arithmetic mean roughness Ra prescribed | regulated by Japanese Industrial Standard (JIS) B0601: 2013.

  According to the configuration of the first solution means, since the value of the arithmetic average roughness Ra of the pocket surface of the cage is equal to or less than the value of the arithmetic average roughness Ra of the cylindrical surface of the output side member, the roller in the neutral position is When rotating together with the input side member and the cage, the friction coefficient between the pocket surface and the roller is reduced to the same level or less with respect to the friction coefficient between the cylindrical surface and the roller. For this reason, since the roller is easily rotated by the frictional resistance force between the roller and the cylindrical surface, the drag torque between the roller and the cylindrical surface is reduced, and thus wear of the roller and the cylindrical surface can be prevented.

  Specifically, the pocket surface may be formed of a surface treatment unit applied to a metal material forming the cage. In this way, the pocket surface can be modified to have a low-friction surface property with respect to the surface of the metal material processed into a cage shape.

  For example, the surface treatment is plating. By plating, the value of the arithmetic average roughness Ra of the pocket surface can be made smaller than the surface of the metal material that is the cage material.

  For example, the surface treatment is shot blasting. By shot blasting, the value of the arithmetic average roughness Ra of the pocket surface can be reduced as compared with the surface of the metal material that is the cage material.

  For example, the surface treatment is chemical polishing. By chemical polishing, the value of the arithmetic average roughness Ra of the pocket surface can be made smaller than the surface of the metal material that is the cage material. Chemical polishing is a preferred surface treatment means in that it can be performed at a relatively low cost compared to plating and shot blasting.

  In order to achieve the above object, the second solution means according to the present invention includes an input side member, an output side member having an inner peripheral portion arranged outside the input side member, and the input side member. A clutch mechanism that transmits and shuts off rotational torque between the output side members, and the clutch mechanism is provided on a cylindrical surface provided on the inner peripheral portion of the output side member, and on the input side member. A cam surface that forms a wedge space between the cylindrical surface, a roller disposed between the cylindrical surface and the cam surface, and a retainer that retains the roller. A pocket surface that can contact the roller in a direction, and the roller engages with the cylindrical surface and the cam surface by relative rotation of the retainer with respect to the cam surface, and the engagement. It is arranged to be movable between the neutral position to be released In the rotation transmission device, the retainer has a plurality of pocket groove portions having a depth from the pocket surface at positions facing the rollers in the circumferential direction, and the pocket groove portions are provided on both sides in the axial direction of the pocket groove portion. It is to adopt a configuration having a shape for guiding oil from the groove end toward the axial center of the pocket groove portion in the rotation direction of the roller.

  According to the configuration of the second solution means, when the roller in the neutral position rotates at a high speed together with the input side member and the cage, the roller pressed against the cylindrical surface by the centrifugal force is rotated and the oil for lubricating the clutch mechanism is supplied. Pull into the pocket groove. The oil drawn into the pocket groove is dragged by the roller that rotates, advances from both axial sides of the pocket groove to the axial center, and eventually merges at the axial center of the pocket groove. Since the oil pressure is increased and an oil film is formed between the roller and the pocket surface at this junction, the friction coefficient between the roller and the pocket surface is reduced. As a result, the roller is easily rotated by the frictional resistance between the cylindrical surface and the drag torque between the roller and the cylindrical surface is reduced, so that wear of the roller and the cylindrical surface can be prevented.

  The output-side member may have an outer groove portion that forms a gap that has a depth from the cylindrical surface and gradually narrows in the circumferential direction between the output-side member and the roller. If it does in this way, if a roller will rotate at high speed toward the narrow side of a clearance gap with an input side member and a holder | retainer, oil will also rotate simultaneously. For this reason, a wedge effect is generated between the roller and the outer groove portion, where oil is dragged from the deep side of the outer groove portion toward the shallow side to increase the hydraulic pressure, and an oil film is formed between the roller and the cylindrical surface. Is done. Thereby, the friction coefficient between a roller and a cylindrical surface can be reduced.

  As described above, when the roller of the clutch mechanism is rotated at a high speed with respect to the cylindrical surface of the output side member together with the input side member and the cage while the roller of the clutch mechanism is in a neutral position, Since the friction coefficient is reduced and the rotation of the roller is facilitated, the drag torque between the roller and the cylindrical surface is reduced, thereby preventing the roller and the cylindrical surface from being worn.

Sectional drawing which shows the contact aspect of the roller in the rotation transmission apparatus of 1st embodiment of this invention Sectional drawing which shows the whole structure of the rotation transmission apparatus of FIG. Sectional view taken along line III-III in FIG. Sectional drawing which shows the whole structure of the rotation transmission apparatus which concerns on 2nd embodiment of this invention Sectional view taken along line VV in FIG. 4 is a perspective view of the cage of FIG. Sectional view of the cage of FIG. Sectional drawing which shows the whole structure of the rotation transmission apparatus which concerns on 3rd embodiment of this invention Sectional view taken along line IX-IX in FIG.

  1st Embodiment as an example which concerns on the said 1st solution means of this invention is described based on FIGS. 1-3. As shown in FIG. 2, the rotation transmission device according to the first embodiment includes an input side member 1, an output side member 2 disposed coaxially with the input side member 1, and the input side member 1 and the output side member 2. A clutch mechanism 3 that transmits and blocks rotation from the input side member 1 to the output side member 2 is provided.

  Hereinafter, the direction along the axis (rotation center line) of the input side member 1 and the output side member 2 is referred to as “axial direction”. A direction orthogonal to the axial direction is referred to as a “radial direction”. The circumferential direction around the axis is referred to as “circumferential direction”.

  The clutch mechanism 3 is covered with a cylindrical housing 4.

  The input side member 1 is a shaft that is a component of the power transmission path. The input side member 1 is formed in a hollow shaft shape. An input shaft S that transmits rotational torque from the outside is connected to the inner peripheral side of the input side member 1. The input shaft S is inserted through the opening 5 on one axial side of the housing 4 (left side in FIG. 2). A seal or bearing 6 is provided between the opening 5 of the housing 4 and the input shaft S. In the case of the seal 6, it is for sealing between the shaft S and the housing 4. In the case of the bearing 6, it is for supporting the input shaft S rotatably with respect to the housing 4, and a rolling bearing with a seal may be adopted to serve also as a seal.

  The output side member 2 is a shaft that is a component of the power transmission path, and is a member to which rotational torque is transmitted from the clutch mechanism 3. The output side member 2 has an inner peripheral portion 7 disposed outside the input side member 1 and a shaft portion 8 extending outward from the other axial side of the housing 4 (the right side in FIG. 2). A bearing 9 is provided between the outer periphery of the output side member 2 and the inner periphery of the housing 4. The bearing 9 is for supporting the output side member 2 so as to be rotatable with respect to the housing 4 and non-movable in the axial direction. The shaft portion 8 is connected to other components of the power transmission path.

  Although an example in which the inner peripheral portion 7 and the shaft portion 8 are formed as an integral member as the output side member 2 is shown, the shaft portion is not essential for the output side member, and another shaft is connected to the output side member. You may make it do. Moreover, although what was connected with the input shaft S as the input side member 1 was illustrated, you may make it form a shaft part integrally in an input side member, and may connect the shaft part to another component. These connecting means are not particularly limited, and examples thereof include serration fitting, spline fitting, and key connection.

  A seal 10 is provided between the outer periphery of the output side member 2 and the other axial side of the housing 4. The seal 10 is for preventing foreign matter from entering from the outside and leakage of the fluid lubricant from the inside of the housing 4 to the outside.

  The input side member 1 includes a cam ring portion 11 protruding radially at an axial intermediate position of the input side member 1, a first end portion 12 positioned on one side in the axial direction with respect to the cam ring portion 11, and a cam ring portion 11. On the other hand, it has the 2nd end part 13 located in the other axial direction side. A bearing 14 is provided between the outer periphery of the second end 13 and the inner periphery 7 of the output side member 2. The bearing 14 is for rotatably supporting the input side member 1 with respect to the output side member 2.

  As shown in FIGS. 2 and 3, the clutch mechanism 3 includes a cylindrical surface 15 provided on the inner peripheral portion 7 of the output side member 2 and a cam surface 16 provided on the outer periphery of the cam ring portion 11 of the input side member 1. A roller 17 disposed between the cylindrical surface 15 and the cam surface 16, a retainer 18 that retains the roller 17, a switch spring 19 that retains the phase of the retainer 18 with a spring force, and the clutch mechanism 3. And an electromagnetic actuator 20 that controls engagement and release.

  The cylindrical surface 15 is continuous over the entire circumference in the circumferential direction. The overall shape of the output side member 2 is formed by forging, for example. The cylindrical surface 15 is finished by, for example, grinding for a forged product. In this case, the arithmetic average roughness Ra of the cylindrical surface 15 can be set to 0.8 to 1.0, for example.

  The cam surface 16 forms a wedge space with the cylindrical surface 15. The wedge space gradually narrows from the circumferential center of the cam surface 16 toward both circumferential ends. That is, the radial distance between the cam surface 16 and the cylindrical surface 15 is one direction in the circumferential direction (counterclockwise in FIG. 3) from the position of the roller 17 in FIG. It gradually becomes smaller and gradually becomes smaller from the position of the roller 17 toward the other circumferential direction (clockwise in FIG. 3). In addition, although the example which comprised the cam surface 16 by the single plane was shown, the cam surface may be comprised by a some surface and it can also be comprised by a single curved surface.

  A plurality of cam surfaces 16 are formed on the outer periphery of the input side member 1 at intervals in the circumferential direction. That is, a plurality of wedge spaces are formed, and the roller 17 is disposed in each wedge space.

  The roller 17 is formed in a cylindrical roller shape. The roller 17 is between the engagement position where the roller 18 is engaged with the cylindrical surface 15 and the cam surface 16 by the relative rotation of the cage 18 with respect to the cam surface 16 and the neutral position where the engagement between the cylindrical surface 15 and the cam surface 16 is released. Is arranged to be movable. When the cage 18 rotates relative to the input side member 1, the roller 17 engages with the cylindrical surface 15 and the cam surface 16 and transmits rotational torque between the input side member 1 and the output side member 2.

  The cage 18 includes a plurality of column portions 21 arranged in the circumferential direction, a first part 22 continuous on one axial side of the column portions 21, and a second ring continuous on the other axial side of the column portions 21. Part 23. A space between the column portions 21 adjacent to each other in the circumferential direction is a space for accommodating the roller 17.

  As shown in FIGS. 1 and 3, the column portion 21 has a pocket surface 24 that can contact the roller 17 in the circumferential direction. The pocket surfaces 24 are formed on both sides of each column portion 21 in the circumferential direction. The pocket surface 24 is a flat surface along a virtual axial plane (a plane including the aforementioned axis) that bisects the space between the column portions 21 adjacent in the circumferential direction in the circumferential direction. The roller 17 is restricted in circumferential position relative to the cam surface 16 due to contact with the pocket surface 24 facing in the circumferential direction, and is forcedly rotated together with the cage 18.

  The value of the arithmetic average roughness Ra of the pocket surface 24 is equal to or less than the value of the arithmetic average roughness Ra of the cylindrical surface 15.

  As shown in FIG. 2, the second ring portion 23 of the cage 18 has an inward flange. The second ring portion 23 is rotatably fitted to the outer periphery of the second end portion 13 of the input side member 1 on the inner periphery of the flange. The cage 18 is positioned in the axial direction by the cam ring portion 11 and the retaining ring 25 at the flange of the second ring portion 23. The retaining ring 25 is attached to a retaining ring groove formed in the second end portion 13.

  The overall shape of the cage 18 is formed by pressing, for example, using a metal material as a raw material. In this case, each column portion 21 shown in FIG. 3 is formed by punching the metal material. An example of the metal material is a steel plate. In a workpiece in which the column portion is punched by press working, the arithmetic average roughness Ra of the portion having the pocket surface shape is about 2.0. By subjecting the pocket shape portion of the workpiece to surface treatment, a pocket surface 24 composed of a surface treatment portion can be obtained.

  Examples of the surface treatment include parker treatment, plating, solid lubricating film treatment, shot blasting, and chemical polishing.

  The aforementioned Parker treatment is a phosphate film treatment in which an insoluble phosphate film is grown on the surface of a workpiece using a phosphate solution.

The above-described plating is a treatment for depositing a metal film on the surface of the workpiece by electrons released by oxidation of the reducing agent contained in the plating solution, and includes, for example, electroless nickel plating. In the case of plating, the wear resistance and self-lubricating property of the pocket surface 24 can be improved by adopting composite plating in which fine particles are mixed in the plating bath and co-deposited with the metal. For example, when importance is attached to wear resistance, silicon carbide, aluminum oxide, diamond, or the like may be co-deposited. Further, when emphasizing self-lubricating properties, polytetrafluoroethylene (PTFE), fluorinated graphite or the like may be co-deposited. When both wear resistance and self-lubricating property are emphasized, SiC + BN, Si ₃ N ₄ + BN, Si ₃ N ₄ + CaF _{2 and the} like may be co-deposited.

  The above-described solid lubricating film treatment is, for example, a treatment in which fine particles are dispersed alone or in combination in a paint and coated on the surface of a workpiece, and is also referred to as Pallube treatment. Examples of the fine particles include fluorine, graphite, and molybdenum disulfide.

  The above-described shot blasting is a process in which a granular projection material collides with a workpiece and the surface of the workpiece is ground. In the case of shot blasting, for example, the surface of the workpiece may be coated by transferring a projection material excellent in self-lubricating properties such as molybdenum disulfide particles to the workpiece.

  The above-described chemical polishing is a process in which the surface of the workpiece is melted and polished by bringing the surface of the workpiece into contact with an acidic chemical polishing solution without using electricity. According to the chemical polishing, for example, the workpiece surface having an arithmetic average roughness Ra value of about 2.0 and a maximum height roughness Rz value of about 0.9 is uniformly polished, and the arithmetic operation of the pocket surface 24 is performed. The value of the average roughness Ra can be modified to 1.0 or less, and the value of the maximum height roughness Rz can be modified to 0.4 or less. A pocket surface 24 that is smoother than the cylindrical surface 15 can be obtained. The aforementioned maximum height roughness Rz is also defined by Japanese Industrial Standard (JIS) B0601: 2013.

  The switch spring 19 shown in FIG. 2 elastically holds the cage 18 so that the roller 17 is in the neutral position. The switch spring 19 is disposed on the first end portion 12 of the input side member 1. The clutch mechanism 3 has a spring retaining ring 26 that keeps the switch spring 19 on the first end portion 12.

  The switch spring 19 is made of a metal spring in which a pair of engagement pieces 27 are formed outward at both ends of a C-shaped ring portion. The ring portion of the switch spring 19 is passed through the outer periphery of the first end portion 12 and is fitted in a recess 28 formed in the input side member 1. The concave portion 28 has a certain depth in the axial direction on the end surface of the cam ring portion 11. The pair of engaging pieces 27 of the switch spring 19 are inserted into a notch 29 formed in the first part 22 of the retainer 18 from a notch formed in the outer wall of the recess 28. The pair of engaging pieces 27 of the switch spring 19 presses the notch portion of the recess 28 and the notch portion 29 of the cage 18 in opposite directions in the circumferential direction. By the pressing, the cage 18 is held in a phase where the roller 17 is in a neutral position.

  The spring holding ring 26 is fitted to the outer periphery of the first end 12 of the input side member 1 and the inner periphery of the first part 22 of the cage 18. The spring retaining ring 26 is prevented from moving in one axial direction by a retaining ring 30 attached to the outer periphery of the first end portion 12. For this reason, escape of the switch spring 19 from the recess 28 is prevented by the spring holding ring 26.

  The electromagnetic actuator 20 includes an armature 31 that faces the first part 22 of the cage 18 in the axial direction, a rotor 32 that faces the armature 31 in the axial direction, an electromagnet 33 that faces the rotor 32 in the axial direction, and an armature 31. And a separation spring 34 that presses in the direction away from the rotor 32.

  The armature 31 is slidably fitted to the outer periphery of the first end portion 12 of the input side member 1. The armature 31 is prevented from rotating with respect to the cage 18. The armature 31 has an engagement hole 43 for preventing rotation. The cage 18 has a projecting piece 44 that extends from the first part 22 into the engagement hole 43. The protruding piece 44 can engage with the engaging hole 43 in the circumferential direction over the entire range of the stroke of the armature 31. By the engagement, the armature 31 is prevented from rotating in a state in which it can move in the axial direction with respect to the retainer 18. In addition, you may make it the structure which interposes a connecting plate like patent document 2 for the rotation prevention of an armature and a holder | retainer.

  The rotor 32 has an inner cylindrical part and an outer cylindrical part located outside the inner cylindrical part. The rotor 32 is press-fitted into the rotor guide 45 at the outer periphery of the outer cylindrical portion. The rotor guide 45 is attached to the outer peripheral end of the output side member 2. The rotor 32 is prevented from rotating with respect to the output side member 2 via the rotor guide 45. For this reason, the rotor 32 can rotate integrally with the output side member 2. The rotor guide 45 is made of a nonmagnetic material.

  A bearing 46 is provided between the inner periphery of the inner cylindrical portion of the rotor 32 and the outer periphery of the input shaft S. The bearing 46 is for rotatably supporting the rotor 32 with respect to the input shaft S.

  The electromagnet 33 includes a field core 47 and an electromagnetic coil 48 supported by the field core 47. The electromagnet 33 is disposed in a space between the inner cylindrical portion and the outer cylindrical portion of the rotor 32. The field core 47 is supported on the closed end of the housing 4 in a non-rotatable state.

  The separation spring 34 is interposed between the facing surfaces of the armature 31 and the rotor 32. The amount by which the armature 31 is separated from the rotor 32 in the axial direction is limited by the retaining ring 30. The retaining ring 30 is also used for regulating the spring retaining ring 26, but may be provided separately.

  The operation of the rotation transmission device according to the first embodiment will be described (refer to FIGS. 2 and 3 as appropriate). First, in a state where the energization of the electromagnetic coil 48 of the electromagnetic actuator 20 is interrupted, the roller 17 is in the neutral position, and the cage 18 causes the roller 17 to move against the cam surface 16 by the spring force of the switch spring 19. The phase is maintained in a neutral position. Therefore, regardless of whether the input shaft S rotates counterclockwise or clockwise in FIG. 3, the rotational torque of the input side member 1 that rotates integrally with the input shaft S is not transmitted to the output side member 2, and output The input side member 1 rotates idly (free rotation) with respect to the side member 2. That is, the clutch mechanism 3 is in a disengaged state in which transmission of rotational torque from the input side member 1 to the output side member 2 is cut off.

  In the disengaged state, the rotation of the input side member 1 is transmitted to the cage 18 via the switch spring 19, and the cage 18 and the roller 17 rotate together. Further, since the armature 31 is prevented from rotating by the cage 18, the armature 31 also rotates together.

  When the electromagnetic coil 48 is energized while the input side member 1 is rotating, an attractive force is applied to the armature 3 1. For this reason, the armature 31 moves against the elasticity of the separation spring 34 and is attracted to the rotor 32.

  The frictional resistance acting on the attracting surfaces of the rotor 32 and the armature 31 becomes the rotational resistance of the cage 18. The frictional resistance is set in advance to a value larger than the spring force of the switch spring 19. For this reason, the switch spring 19 is elastically deformed, and the cage 18 rotates relative to the input side member 1. By the relative rotation, the roller 17 is pushed into the narrow portion of the wedge space between the cylindrical surface 15 and the cam surface 16 and engages with the cylindrical surface 15 and the cam surface 16. For this reason, the rotational torque of the input side member 1 is transmitted to the output side member 2 via the roller 17. That is, the clutch mechanism 3 is in an engaged state in which rotational torque is transmitted from the input side member 1 to the output side member 2.

  In this engaged state, when the energization to the electromagnetic coil 48 is interrupted, the armature 31 moves away from the rotor 32 to a position where it comes into contact with the retaining ring 30 by the pressing of the separation spring 34. Further, when the armature 31 is separated from the rotor 32, the retainer 18 rotates in the reverse direction when engaged with the input side member 1 by the spring force of the switch spring 19 and is pushed by the pocket surface 24 of the column portion 21. The roller 17 returns to the neutral position. For this reason, the clutch mechanism 3 returns to the disengaged state.

  For example, as shown in FIG. 1, when the clutch mechanism 3 is in the disengaged state and the input side member 1 rotates clockwise (in the direction of arrow A), the input side member 1 and the cage 18 are connected to the switch spring 19. Therefore, both the input side member 1 and the cage 18 rotate clockwise. The roller 17 in contact with the pocket surface 24 of the column portion 21 of the cage 18 also rotates clockwise together with the cage 18 and the like.

For this reason, when the input side member 1 idles clockwise at high speed, the roller 17 moves radially outward due to centrifugal force and contacts the cylindrical surface 15. A drag torque that drags the roller 17 and the cage 18 against the cylindrical surface 15 is generated by the frictional resistance force μ ₁ · N acting on the contact portion. The drag torque tries to rotate the roller 17 and acts against the spring force of the switch spring 19 to rotate the cage 18 relative to the input side member 1. At this time, the roller 17 comes into contact with the pocket surface 24 of the column portion 21 on the left side in the drawing that is the rear side in the rotation direction in the clockwise rotation. The frictional resistance force μ ₂ · F acting on the contact portion generates a brake torque that inhibits the rotation of the roller 17.

Here, since the value of the arithmetic average roughness Ra of the pocket surface 24 is smaller than the value of the arithmetic average roughness Ra of the cylindrical surface 15, the friction coefficient μ _{2 at} the contact portion between the pocket surface 24 and the roller 17 is a cylinder. becomes smaller than the friction coefficient mu ₁ at the contact portion of the surface 15 and the roller 17, the frictional resistance force mu ₁ · N is greater than the frictional resistance μ ₂ · F. For this reason, the roller 17 easily rotates and easily rolls the cylindrical surface 15. Accordingly, since the roller 17 is easily rotated by the frictional resistance force μ ₁ · N between the cylindrical surface 15 and the drag torque described above, the wear of the roller 17 and the cylindrical surface 15 is prevented.

  As described above, the rotation transmission device shown in FIGS. 1 to 3 operates at a high speed with respect to the cylindrical surface 15 of the output side member 2 together with the input side member 1 and the cage 18 with the roller 17 of the clutch mechanism 3 in the neutral position. When rotating, since the drag torque described above is reduced, wear of the roller 17 and the cylindrical surface 15 can be prevented. In addition, as a secondary effect by reducing the drag torque described above, the rotation transmission device according to the first embodiment prevents improper rotation of the cage 18 with respect to the input side member 1, and prevents the clutch mechanism 3 from being misengaged. Occurrence can also be prevented.

  A second embodiment of the present invention will be described with reference to FIGS. In the following, only differences from the first embodiment will be described.

  FIG. 4 shows an example in which the rotation transmission device 100 is applied as a part of a power transmission path of a machine including an oil pump in a lubricating oil circulation path. The rotation transmission device 100 is attached to a partition wall W of the machine. Rotational torque is transmitted to the input side member 101 from an output shaft (not shown) provided in the machine.

  A clutch mechanism 104 is disposed inside the inner peripheral portion 103 of the output side member 102. The electromagnet 105 is attached around the opening of the partition wall W in the field core. The rotor 106 is attached to the output side member 102 by press-fitting the inner side portion 103 of the output side member 102.

  The first end portion 107 of the input side member 101 includes a shaft portion that extends inward of the electromagnet 105 through the rotor 106 and the electromagnet 105. The first end 107 is inserted through the opening of the partition wall W at the shaft portion, and is connected to the output shaft of the machine. A bearing 108 is disposed between the outer periphery of the first end 107 and the inner periphery of the rotor 106.

  A bearing 110 between the second end portion 109 of the input side member 101 and the inner peripheral portion 103 of the output side member 102 is in axial contact with the second ring portion 112 of the cage 111, and the other axial side of the cage 111. Restrict movement to

  The retainer 111 and the armature 113 are prevented from rotating via a connecting plate 114. The connecting plate 114 also serves as a spring holding ring that regulates the switch spring 115. The connecting plate 114 is inserted into the notch of the first part 116 and the engagement hole (not shown) of the armature 113 while being fitted to the inner periphery of the first part 116 of the cage 111. .

  As described above, the rotation transmission device 100 regulates the housing of the first embodiment, the bearing between the inner periphery of the housing and the outer periphery of the output side member, the bearing between the input shaft and the rotor, and the second ring portion of the cage. It has a simple structure with no retaining ring.

  As shown in FIGS. 4 and 5, the input side member 101 has an oil supply path that guides the oil fed by the oil pump (not shown) to the roller 117 through the inside of the input side member 101. That is, the input side member 101 includes a central path 119 that passes through the inside of the first end 107 and reaches the inside of the roller 117 and the cam surface 118, and an outlet path 120 that branches from the central path 119 and faces the roller 117. Have The outlet passage 120 extends in the radial direction corresponding to each roller 117. The oil flows from the central path 119 to the outlet path 120 and flows out from the outlet path 120 toward the corresponding roller 117. This oil is continuously sent to the central path 119 during the operation of the oil pump.

  As shown in FIGS. 5 to 7, the column part 121 of the cage 111 includes a plurality of first pocket groove parts 123 having a depth in the circumferential direction from the pocket surface 122 at positions facing the rollers 117 in the circumferential direction. A second pocket groove 124 is provided.

  The first pocket groove 123 has a V shape that is sharpened toward the inner diameter side of the cage 111. The second pocket groove portion 124 has an inverted V shape that is sharpened toward the outer diameter side of the cage 111.

  Here, when the cage 111 and the cam surface 118 rotate clockwise in FIG. 5 (arrow A direction), the rotation direction of the roller 117 is counterclockwise. In this case, the first pocket groove portion 123 has an axial center portion (V-shaped tip) of the pocket groove portion 123 toward the rotation direction of the roller 117 from the groove end (V-shaped both ends) on both sides in the axial direction of the pocket groove portion 123. It will have a shape that guides the oil.

  On the other hand, when the cage 111 and the cam surface 118 rotate counterclockwise in FIG. 5, the rotation direction of the roller 117 is clockwise. In this case, the second pocket groove portion 124 has an axial center portion (inverted V shape) of the pocket groove portion 124 toward the rotation direction of the roller 117 from the groove end (both ends of the inverted V shape) on both axial sides of the pocket groove portion 124. It has a shape that guides oil to the tip.

  The first pocket grooves 123 are distributed over substantially the entire range where the pocket surface 122 is formed. This distribution is arranged so that two or more first pocket grooves 123 are arranged in the axial direction and the radial direction. The second pocket groove portion 124 is also arranged in the same manner as the first pocket groove portion 123. Further, the first pocket groove portions 123 and the second pocket groove portions 124 are arranged so as to be alternately arranged in the axial direction.

  The shallow groove portions such as the first and second pocket groove portions 123 and 124 may be formed by an appropriate method such as etching processing or surface pressing processing on the column portion 121.

  When the clutch mechanism 104 shown in FIG. 4 is in the disengaged state, for example, when the cage 111 rotates clockwise in FIG. 5 together with the input side member 101, the roller 117 in the neutral position pressed against the cylindrical surface 125 by centrifugal force. Is rotated, and oil flowing out from the outlet passage 120 is drawn into the first and second pocket grooves 123 and 124. Here, the oil drawn into each first pocket groove portion 123 is dragged by the rotating roller 117 and advances from both axial sides of the first pocket groove portion 123 to the axial central portion side, and eventually the first pocket groove portion 123 is dragged. The pocket grooves 123 meet at the central portion in the axial direction. Since the oil pressure is increased at this joining portion and an oil film is formed between the roller 117 and the pocket surface 122, the friction coefficient between the roller 117 and the pocket surface 122 is reduced. As a result, the roller 117 is easily rotated by the frictional resistance between the roller surface 117 and the cylindrical surface 125, so that the drag torque between the roller 117 and the cylindrical surface 125 is reduced, thereby preventing the roller 117 and the cylindrical surface 125 from being worn. Is done. Note that when the retainer 111 rotates counterclockwise in FIG. 5 together with the cam surface 118, the hydraulic pressure increases at the joining portion of the second pocket groove portion 124, the friction coefficient between the roller 117 and the pocket surface 122 is reduced, and wear is also caused. Is prevented.

  As described above, when the rotation transmission device 100 rotates at high speed with respect to the cylindrical surface 125 of the output side member 102 together with the input side member 101 and the retainer 111 in a state where the roller 117 of the clutch mechanism 104 is in the neutral position, the rotation transmission device 100 described above. Since the drag torque is reduced, wear of the roller 117 and the cylindrical surface 125 can be prevented. Further, as a secondary effect by reducing the drag torque described above, the rotation transmission device 100 prevents the cage 111 from rotating illegally with respect to the input side member 101 and prevents the clutch mechanism 104 from being misengaged. You can also.

  In addition, although V shape and reverse V shape were illustrated as the 1st and 2nd pocket groove parts 123 and 124, you may change into other shapes, such as U shape and arrow line shape. In short, oil dragging by roller rotation is used to join the oil from the end of the groove on both sides in the axial direction to the center of the groove to increase oil pressure, thereby promoting oil film formation between the roller and the pocket surface. It only needs to be possible.

  Further, reducing the value of the arithmetic average roughness Ra of the pocket surface 122 is advantageous for forming an oil film between the roller 117 and the pocket surface 122. For this reason, also in the second embodiment, the value of the arithmetic average roughness Ra of the pocket surface 122 is preferably equal to or less than the value of the arithmetic average roughness Ra of the cylindrical surface 125.

  When the pocket groove portions 123 and 124 are formed, the friction coefficient at the contact portion between the pocket surface 122 and the roller 117 can be reduced by promoting the formation of an oil film. You may make larger than the value of arithmetic mean roughness Ra of the surface 125. FIG. That is, friction reduction by the pocket groove is a technique that can be adopted regardless of the magnitude relationship of the calculated average roughness Ra between the pocket surface and the cylindrical surface.

  A third embodiment of the present invention will be described with reference to FIGS. In addition, since 3rd embodiment changes only the shape of the output side member in 2nd embodiment, below, only a difference with 2nd embodiment is described.

  The output side member 130 shown in FIGS. 8 and 9 has a plurality of outer grooves 132 extending from the cylindrical surface 131 in the circumferential direction with a depth in the radial direction. The outer groove 132 is at a position facing the roller 117 in the radial direction. The outer groove 132 has a deepest portion on the groove end side on one circumferential side, and gradually becomes shallower from the deepest portion to the groove end on the other circumferential side. That is, the outer groove portion 132 forms a wedge-shaped space that gradually becomes narrower from one side in the circumferential direction to the other side (in the direction of the arrow A in the circumferential direction in FIG. 9).

  The outer groove portion 132 is formed only at a position facing the axial central portion of the roller 117 in the radial direction. This is because both sides of the roller 117 in the axial direction can be uniformly engaged with the cylindrical surface 131.

  The plurality of outer grooves 132 are continuously formed on the entire circumference in the circumferential direction. A groove end on one side in the circumferential direction of a certain outer groove 132 is continuous with a groove end on the other side in the circumferential direction of the adjacent outer groove 132. For this reason, the roller 117 forms the above-mentioned wedge-shaped gap between any one of the outer groove portions 132 at most positions in the circumferential direction.

  When the clutch mechanism 104 shown in FIG. 8 is in the disengaged state, when the retainer 111 rotates clockwise in FIG. The column part 121 pushes the roller 117, and the roller 117 revolves clockwise. That is, the roller 117 rotates at a high speed toward the narrow side of the wedge-shaped gap formed between the outer groove 132 and the roller 117, and the oil flowing out from the outlet passage 120 also rotates in the same direction at the same time. It will be. For this reason, a wedge effect is generated between the roller 117 and the outer groove portion 132 so that the oil pressure is dragged from the deep side of the outer groove portion 132 toward the shallow side. An oil film is formed between them. As a result, the coefficient of friction between the roller 117 and the cylindrical surface 131 can be reduced, and as a result, wear of the roller 117 and the cylindrical surface 131 can be further prevented.

  In the examples shown in FIGS. 8 and 9, only the outer groove portion 132 effective when the input side member 101 rotates in one direction in the disengaged state is employed. You may add a groove part (namely, the outward groove part which forms the clearance gap which narrows toward one side from the other side of a circumferential direction between rollers). In the case of changing to two directions, the outer groove portions having different depth changing directions may be alternately formed in the circumferential direction at the same axial position, or may be separately formed at different positions in the axial direction.

  Further, the outer groove portion does not need to be continuously formed on the entire circumference. For example, the outer groove portion may be formed at a plurality of locations in the circumferential direction with a pitch equal to or less than the pitch of the roller.

  As in the third embodiment, the rotation transmission device having only the outward groove portion corresponding to one direction has a shorter time for rotating in the other direction than the time for the input side member to rotate in one direction when in the disengaged state. Suitable for cases.

  Each embodiment disclosed this time should be considered as illustrative in all points and not restrictive. Accordingly, the scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

1,101 Input side member 2,102,130 Output side member 3,104 Clutch mechanism 7,103 Inner periphery 15,125,131 Cylindrical surface 16,118 Cam surface 17,117 Roller 18,111 Cage 24,122 Pocket Surface 100 Rotation transmission device 123, 124 Pocket groove 132 Outer groove

Claims (7)

An input side member (1, 101), an output side member (2, 102, 130) having an inner periphery (7, 103) disposed outside the input side member (1, 101), and the input A clutch mechanism (3, 104) for transmitting and interrupting rotational torque between the side member (1, 101) and the output side member (2, 102, 130);
The clutch mechanism (3, 104) includes a cylindrical surface (15, 125, 131) provided on the inner peripheral portion (7, 103) of the output side member (2, 102, 130), and the input side member. A cam surface (16, 118) provided on (1, 101) and forming a wedge space between the cylindrical surface (15, 125, 131), the cylindrical surface (15, 125, 131) and the cam surface. A roller (17, 117) disposed between (16, 118) and a holder (18, 111) for holding the roller (17, 117),
The retainer (18, 111) has a pocket surface (24, 122) that can contact the roller (17, 117) in the circumferential direction, and the roller (17, 117) is a cam surface (16 , 118) and the engagement position where the retainer (18, 111) is engaged with the cylindrical surface (15, 125, 131) and the cam surface (16, 118) by the relative rotation of the retainer (18, 111) and the engagement is released. In the rotation transmission device arranged to be movable between the neutral position,
The rotation transmission device according to claim 1, wherein a value of the arithmetic average roughness Ra of the pocket surface (24, 122) is equal to or less than a value of the arithmetic average roughness Ra of the cylindrical surface (15, 125, 131).   The rotation transmission device according to claim 1, wherein the pocket surface (24, 122) includes a surface treatment portion applied to a metal material forming the cage (18, 111).   The rotation transmission device according to claim 2, wherein the surface treatment is plating.   The rotation transmission device according to claim 2, wherein the surface treatment is shot blasting.   The rotation transmission device according to claim 2, wherein the surface treatment is chemical polishing. An input side member (101), an output side member (102, 130) having an inner peripheral portion (103) disposed outside the input side member (101), the input side member (101) and the output A clutch mechanism (104) for transmitting and interrupting rotational torque between the side members (102, 130),
The clutch mechanism (104) is provided on the cylindrical surface (125, 131) provided on the inner peripheral portion (103) of the output side member (102, 130) and the cylinder provided on the input side member (101). A cam surface (118) forming a wedge space with the surface (125, 131), a roller (117) disposed between the cylindrical surface (125, 131) and the cam surface (118), A holder (111) for holding the roller (117);
The cage (111) has a pocket surface (122) that can contact the roller (117) in the circumferential direction, and the roller (117) is configured to support the cam surface (118). Transmission device arranged to be movable between an engagement position engaging with the cylindrical surface (125, 131) and the cam surface (118) and a neutral position for releasing the engagement by relative rotation of In
The cage (111) has a plurality of pocket groove portions (123, 124) having a depth from the pocket surface (122) at a position facing the roller (117) in the circumferential direction, and the pocket groove portion ( 123, 124) guides oil from the groove end on both axial sides of the pocket groove (123, 124) toward the axial center of the pocket groove (123, 124) in the direction of rotation of the roller (117). A rotation transmission device having a shape.   The output side member (130) has an outer groove portion (132) that forms a gap that has a depth from the cylindrical surface (131) and gradually narrows in the circumferential direction between the output side member (130) and the roller (117). The rotation transmission device according to claim 6.

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