JP2016109251A - Rotation transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotation transmission device in which a preload is easily managed and which is easily assembled.SOLUTION: A two-way clutch 10 which is assembled between opposing ends of an input shaft Sand an output shaft S, and transmits and blocks the rotation from the input shaft Sto the output shaft S, and an electromagnetic clutch 50 which is arranged on the input shaft S, and oppositely arranged at the two-way clutch 10 are each covered with a housing 1. A positioning part 5 for axially positioning a built-in component composed of the two-way clutch 10 and the electromagnetic clutch 50 is arranged in a bearing cylinder 2 which is arranged at one end of the housing 1, a spiral screw part 59 is arranged in an opening end of the other end of the housing 1, a male screw 58 arranged at an external periphery of a flange 57 of a flanged cylinder body 56 as a pressurization member is engaged with the spiral screw part 59, the built-in component is pressed toward the positioning part 5 by the screwing of the flanged cylinder body 56 to impart a preload to the built-in component.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a rotation transmission device used for switching between transmission and cutoff of rotation from an input shaft to an output shaft.

  As a rotation transmission device for transmitting and interrupting rotation from an input shaft to an output shaft, a two-way clutch for coupling and releasing the input shaft and the output shaft is provided, and the engagement and release of the two-way clutch are electromagnetic clutches What is controlled by this is conventionally known.

  In the rotation transmission device described in Patent Document 1, a plurality of column portions provided in the control holder and a plurality of column portions provided in the rotation holder are provided between the outer ring and the inner ring incorporated inside the outer ring. Incorporating to be alternately arranged in the circumferential direction, incorporating a pair of opposed rollers in a pocket formed between adjacent pillars, and separating the pair of rollers with an elastic member incorporated between the opposed portions And is put on standby at a position where it engages with a cylindrical surface formed on the inner periphery of the outer ring and a cam surface formed on the outer periphery of the inner ring. The rotation of the inner ring is transmitted to the outer ring by engaging with the cam surface.

  Also, an electromagnetic clutch is provided on the input shaft connected to the inner ring, and a magnetic attractive force is applied to the armature disposed opposite to the rotor by energizing the electromagnet of the electromagnetic clutch, and the armature and the control holding connected to the armature. The control cage and the rotary cage are moved in the direction in which the circumferential width of the pocket is reduced by the action of a torque cam provided between the opposing faces of the flange of the control cage and the flange of the rotary cage. Are rotated relative to each other, and the pair of rollers are moved to the disengagement position at the pillar portion of each cage, so that the rotation transmission from the inner ring to the outer ring is blocked.

  In the rotation transmission device, each of the two-way clutch formed by the outer ring, the inner ring, the pair of rollers and the cage and the electromagnetic clutch for controlling the two-way clutch is covered with the housing. If the two-way clutch and the electromagnetic clutch are rattled when the electromagnetic clutch is incorporated in the housing, the two-way clutch cannot be functioned accurately and reliably.

  In order to eliminate such inconvenience, the rotation transmission device described in Patent Document 1 is selected according to the radial length and the axial length of various parts and housings constituting the two-way clutch and electromagnetic clutch. By incorporating an elastic member made of a spacer or a wave spring, a preload is applied to a built-in component composed of a two-way clutch and an electromagnetic clutch to remove backlash.

JP 2012-149746 A

  By the way, applying preload by incorporating spacers and elastic members makes it difficult to manage preload due to large variations in spring reaction force due to the combination of spacers and elastic members, and measures the dimensions of various parts and housings. Since it is necessary to select and assemble spacers and elastic members of appropriate sizes, it is very time-consuming to assemble the rotation transmission device, and the number of parts increases and the cost increases. There were still points to be improved in order to improve the cost and reduce the cost.

  An object of the present invention is to provide a rotation transmission device that can easily manage and assemble preload.

  In order to solve the above-described problems, in the present invention, a two-way clutch that is incorporated between opposed ends of an input shaft and an output shaft and transmits and blocks rotation from the input shaft to the output shaft, and the input shaft An electromagnetic clutch provided on the two-way clutch and disposed opposite to the two-way clutch; and a housing that covers the two-way clutch and the electromagnetic clutch, wherein the electromagnetic clutch is incorporated in one end opening of the housing. The two-way clutch is disengaged by energization of the electromagnet, and the housing has a bearing cylinder that covers an end portion of the output shaft on the side where the outer ring is continuously provided at the other end portion. And a rotation transmission device in which a bearing that rotatably supports the output shaft is incorporated in the bearing cylinder, the front end of the housing and one of the bearing cylinders A positioning part for axially positioning a built-in component consisting of a two-way clutch and the electromagnetic clutch is provided, and a helical screw part is provided on the other side, and the built-in part is pressed against the positioning part toward the helical screw part. A configuration in which the pressure member is screw-engaged is employed.

  In the rotation transmission device having the above-described configuration, when the pressure member is screwed, the built-in component including the two-way clutch and the electromagnetic clutch can be pushed toward the positioning portion by the pressure member, and is built in by contact with the positioning portion. A preload can be applied to the built-in component by further applying a pushing force while the component is stopped. By adjusting the screwing amount of the pressure member, it is possible to apply an appropriate preload to the built-in component, and it is easy to manage the preload.

  Here, as the pressurizing member, a flanged cylinder provided on the outer end surface of the electromagnet or a cylindrical U-shaped cap provided with a cylindrical portion facing in the same direction on the outer periphery and inner periphery of the annular plate portion, or A screw ring in which a male screw is formed on the outer periphery can be employed.

  When a flanged cylinder is used as a pressure member, a male thread is formed on the outer periphery of the flange provided on the cylinder, and the male thread is formed on a spiral thread formed on the inner circumference of the opening end of the housing. The electromagnet is pressed in the axial direction by screw engagement.

  When a U-shaped cap is used as a pressure member, a female thread is formed on the inner periphery of the outer cylindrical portion, and the female screw is engaged with a helical thread formed on the outer periphery of the opening end of the housing. Then, the electromagnet is pressed in the axial direction at the inner peripheral cylindrical portion, or the female screw is screw-engaged with the helical thread portion provided on the outer periphery of the bearing tube, and the inner peripheral cylindrical portion is inserted into the bearing tube. Press the outer ring of the built-in bearing.

  When a screw ring is used as a pressure member, the male screw formed on the outer periphery of the screw ring is screw-engaged with a helical thread portion provided on the inner periphery of the bearing tube, and is incorporated into the bearing tube. The outer ring of the bearing is pressed in the axial direction.

  By providing a loosening prevention means for preventing the pressure member from loosening at the preload adjusting position, it is possible to suppress the occurrence of rattling and maintain the state where the two-way clutch and the electromagnetic clutch function reliably over a long period of time.

  When the pressurizing member is screwed into the open end of the housing as the loosening prevention means, the open end is caulked inward and the inward caulking projection is formed on the outer end surface of the pressurizing member. It is possible to employ a method for engaging, a method in which a lock ring having a male thread formed on the outer periphery is screwed into a helical thread portion and pressed against a pressure member, and the lock ring functions as a lock nut.

  A method of driving a pin into a radial pin hole formed in a bearing cylinder to engage with an outer end face of the pressure member as a loosening prevention means when the pressure member is screw-engaged in the bearing cylinder, a bearing A method in which the opening end of the cylinder is crimped inward and the inward crimping protrusion is engaged with the outer end face of the pressure member, and an oil seal is press-fitted into the opening end of the bearing cylinder, and the outer end face of the pressure member It is possible to employ a method of press-contacting.

  In the present invention, as described above, by screwing the pressure member, the built-in component consisting of the two-way clutch and the electromagnetic clutch can be pushed toward the positioning portion with the pressure member. Appropriate preload can be reliably applied, and preload management is easy.

  Further, since preload is applied by screwing the pressure member, it is not necessary to incorporate a spacer or an elastic member, and the number of parts can be reduced to facilitate the assembly of the rotation transmission device and reduce the cost. it can.

A longitudinal sectional view showing an embodiment of a rotation transmission device according to the present invention Sectional drawing which expands and shows the electromagnetic clutch part of FIG. Sectional view along line III-III in FIG. Sectional drawing which shows the disengagement state of the roller shown in FIG. Sectional view along line V-V in FIG. Sectional view along line VI-VI in FIG. Sectional view along line VII-VII in FIG. (A) is sectional drawing which followed the VIII-VIII line of FIG. 7, (b) is sectional drawing which shows an operation state. Sectional drawing which shows an example of the locking means which stops a pressurization member Sectional drawing which shows the other example of the locking means which stops a pressurization member Sectional drawing which shows the other example of a pressurization member A longitudinal sectional view showing another embodiment of the rotation transmission device according to the present invention Sectional drawing which expands and shows a part of FIG. Sectional drawing which shows an example of the locking means which stops a pressurization member Sectional drawing which shows the other example of the locking means which stops a pressurization member Sectional drawing which shows the further another example of the locking means which locks a pressurizing member. Sectional drawing which shows the further another example of the locking means which locks a pressurizing member. Sectional drawing which shows the other example of a pressurization member

Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows an embodiment of a rotation transmission device according to the present invention. As shown in the figure, the rotation transmission device includes an input shaft S ₁ , an output shaft S ₂ arranged coaxially with the input shaft S ₁ , a housing 1 covering the shaft ends of both shafts, and the housing 1. engagement of two-way clutch 10 and a two-way clutch 10 that is incorporated into the inner performing an interrupting a transmission of rotation from the input shaft S ₁ to the output shaft S _2, an electromagnetic clutch 50 for controlling the release.

The housing 1 has a cylindrical shape, and a small-diameter bearing cylinder 2 is provided at one end thereof, and an end opening on the outer end side of the bearing cylinder 2 is sealed by incorporating a seal member 3. A bearing 4 that rotatably supports the output shaft S ₂ is incorporated inside the bearing cylinder 2, and an outer ring 4 a of the bearing 4 is positioned in the axial direction by a positioning portion 5 provided on the inner diameter surface of the bearing cylinder 2. Thus, movement toward the outer end side of the bearing tube 2 is prevented.

  In FIG. 1, the annular protrusion integrally provided on the inner diameter surface of the bearing cylinder 2 is used as the positioning portion 5, but the positioning portion 5 is not limited to the annular protrusion. For example, an annular groove may be provided on the inner diameter surface of the bearing cylinder, and a retaining ring attached to the annular groove may be used as the positioning portion.

As shown in FIGS. 1 to 3, two-way clutch 10, a cylindrical surface 12 provided on the inner periphery of the outer ring 11 provided on the shaft end of the output shaft S _2, provided on the shaft end of the input shaft S ₁ A plurality of cam surfaces 14 are formed in the circumferential direction on the outer circumference of the inner ring 13, and a pair of rollers 15 and an elastic member 16 are assembled between each of the plurality of cam surfaces 14 and the cylindrical surface 12. The roller 15 is held by a cage 20, and the rotation of the inner ring 13 is transmitted to the outer ring 11 by engaging one of the pair of rollers 15 with the cylindrical surface 12 and the cam surface 14 by rotating the inner ring 13 in one direction. Further, when the inner ring 13 rotates in the other direction, the other roller 15 is engaged with the cylindrical surface 12 and the cam surface 14 to transmit the rotation of the inner ring 13 to the outer ring 11.

Here, a small-diameter concave portion 17 is formed on the inner surface side of the closed end portion of the outer ring 11, and the shaft end portion of the input shaft S ₁ is rotatably supported by a bearing 18 incorporated in the concave portion 17.

The inner ring 13 is formed integrally with the input shaft S _1. As shown in FIG. 3, the cam surface 14 formed on the outer periphery of the inner ring 13 is inclined in opposite directions to form a wedge-shaped space with the cylindrical surface 12 of the outer ring 11, 14b and a flat surface 14c provided between the pair of inclined surfaces 14a, 14b, and the elastic member 16 is supported by the flat surface 14c.

  The elastic member 16 consists of a coil spring. The elastic member 16 is incorporated between the pair of rollers 15, and the elastic member 16 biases the pair of rollers 15 away from each other so as to engage with the cylindrical surface 12 and the cam surface 14. Is arranged.

  As shown in FIG. 2, the cage 20 includes a control cage 20A and a rotary cage 20B. As shown in FIG. 2 and FIG. 7, the control retainer 20 </ b> A is provided with the same number of column portions 22 as the cam surface 14 a at equal intervals in the circumferential direction on one outer peripheral portion of the annular flange 21. An arc-shaped long hole 23 is formed on the outer periphery, and a cylindrical portion 24 is provided on the outer periphery in a direction opposite to the column portion 22.

  On the other hand, the rotary cage 20B has a configuration in which the same number of column portions 26 as the cam surface 14b are provided on the outer periphery of the annular flange 25 at equal intervals in the circumferential direction.

The control retainer 20A and the rotation retainer 20B are a combination in which the column portions 26 of the rotation retainer 20B are inserted into the elongated holes 23 of the control retainer 20A, and the column portions 22 and 26 are alternately arranged in the circumferential direction. The Then, the distal end portion of the pillar portion 22 and 26 is disposed between the outer ring 11 and inner ring 13 in the combination state, the flange 25 of the flange 21 and the rotary cage 20B of the control retainer 20A is fitted on the outer periphery of the input shaft _{S 1} The support ring 28 and the open end face of the outer ring 11 are incorporated.

  By incorporating the cages 20A and 20B as described above, as shown in FIGS. 3 and 4, a pocket 27 is formed between the column portion 22 of the control cage 20A and the column portion 26 of the rotary cage 20B. The pocket 27 faces the cam surface 14 of the inner ring 13 in the radial direction, and a roller 15 and an elastic member 16 as a pair of opposed engaging members are incorporated in each pocket 27.

As shown in FIGS. 1 and 2, the flange 21 of the control retainer 20A is slidably supported along the slide guide face 29 formed on the outer periphery of the input shaft S _1. On the other hand, the rotation retainer 20B is rotatably supported by a thrust bearing 30 which is backed up by the flanges 25 and the input shaft S ₁ to the mated above the support ring 28.

Here, the support ring 28 that backs up the thrust bearing 30 is press-fitted to the input shaft S ₁ , and is positioned in the axial direction by a step portion 31 provided at an end portion of the slide guide surface 29.

  Between the flange 21 of the control holder 20A and the flange 25 of the rotary holder 20B, the movement of the control holder 20A in the axial direction is converted into a relative rotational movement of the control holder 20A and the rotary holder 20B. A torque cam 40 is provided as a motion conversion mechanism.

  As shown in FIG. 2, FIG. 7 and FIG. 8 (a), the torque cam 40 reaches both ends deeply at the center in the circumferential direction on the opposing surfaces of the flange 21 of the control holder 20A and the flange 25 of the rotary holder 20B. Accordingly, a pair of opposed cam grooves 41, 42 that gradually become shallower are provided, and a ball 43 is incorporated between one end of the cam groove 41 and the other end of the other cam groove 42.

  Here, the cam grooves 41 and 42 are grooves having a circular cross section, but may be V-shaped grooves.

  When the control holder 20A moves in the axial direction in the direction in which the flange 21 of the control holder 20A approaches the flange 25 of the rotary holder 20B, the torque cam 40 has a ball 43 as shown in FIG. Rolls toward the deepest groove depth of the cam grooves 41 and 42, and the control holder 20A and the rotary holder 20B are relatively rotated in the direction in which the circumferential width of the pocket 27 is reduced. .

As shown in FIG. 6, the inner ring 13, the end of the slide guide face 29 side formed in the input shaft S _1, the large diameter of the holder fitting surface 44 from the slide guide face 29 is formed, the holder An annular spring holder 45 that prevents the roller 15 and the elastic member 16 from falling off in the axial direction is fitted to the fitting surface 44.

  The spring holder 45 is positioned in the axial direction so as to abut against the axial end surface of the inner ring 13. As shown in FIGS. 5 and 6, a plurality of braking pieces 46 are formed on the outer periphery of the spring holder 45 between the column portion 22 of the control holder 20 </ b> A and the column portion 26 of the rotation holder 20 </ b> B.

  When the control retainer 20A and the rotation retainer 20B rotate relative to each other in the direction of reducing the circumferential width of the pocket 27, the plurality of braking pieces 46 are aligned with the column portion 22 of the control retainer 20A and the columns of the rotation retainer 20B. The part 26 is received at both side edges and is held in a neutral position where the pair of opposed rollers 15 are disengaged.

  A holding piece 47 that extends in the axial direction and extends outside the elastic member 16 is formed on the outer peripheral portion of the spring holder 45, and the holding piece 47 prevents the elastic member 16 from falling off between the pair of rollers 15. ing.

  As shown in FIGS. 1 and 2, the electromagnetic clutch 50 includes an armature 51 that faces the end face of the cylindrical portion 24 formed in the control holder 20 </ b> A in the axial direction, and a rotor 52 that faces the armature 51 in the axial direction. The rotor 52 has an electromagnet 53 facing in the axial direction.

The armature 51 is supported to be freely rotatable and slidably by the input shaft S aforementioned support ring 28 provided on _1. A connecting cylinder 54 is provided on the outer periphery of the armature 51, and the cylinder 24 of the control holder 20A is press-fitted into the inner diameter surface of the connecting cylinder 54 so that the control holder 20A and the armature 51 are connected and integrated. Armature 51 by the Linking is the support of the slidable in two places in the axial direction of the outer peripheral of the input shaft the outer circumference of the slide guide face 29 of the S ₁ of the support ring 28.

The rotor 52 has an outer cylindrical portion 52a and the inner cylinder portion 52b, the inner cylindrical portion 52b is press-fitted to the input shaft _{S 1.} The rotor 52 is positioned in the axial direction by a shim 55 incorporated between the rotor 52 and the support ring 28.

  The electromagnet 53 has an electromagnetic coil 53a and a core 53b that supports the electromagnetic coil 53a. The core 53b is incorporated between the outer cylinder part 52a and the inner cylinder part 52b of the rotor 52, and the outer periphery of the end part is supported by the inner diameter surface of the housing 1 as a stationary member and is prevented from rotating.

  As shown in FIGS. 1 and 2, a flanged cylinder 56 is provided as a pressure member on the outer end side of the core 53b. A male screw 58 is provided on the outer periphery of the flange 57 provided at the end portion of the cylindrical body 56, and the male screw 58 is screwed to a helical screw portion 59 formed on the inner periphery of the opening end portion of the other end of the housing 1. Are combined.

  The flanged cylinder 56 is screw-engaged with the helical thread portion 59 with the flange 57 as the front side, and a built-in component including the two-way clutch 10 and the electromagnetic clutch 50 is positioned by the flange 57 abutted against the outer end surface of the electromagnet 53. It is pressed toward the part 5 to apply a preload to the built-in component, and the built-in component is assembled without backlash.

Inside the flanged tubular body 56 bearing 60 for rotatably supporting the input shaft S ₁ is being built. The bearing 60 is secured by a retaining ring 61 attached to the inner periphery of the cylindrical body 56.

  The rotation transmission device shown in the embodiment has the above structure, and FIG. 3 shows a state in which the roller 15 of the two-way clutch 10 is engaged with the cylindrical surface 12 and the cam surface 14. When the electromagnetic coil 53a of the electromagnetic clutch 50 is energized with the two-way clutch 10 engaged, a magnetic attractive force acts on the armature 51, and the armature 51 moves in the axial direction and is attracted to the rotor 52.

  Here, since the armature 51 is connected and integrated with the control holder 20A, the flange 21 of the control holder 20A approaches the flange 25 of the rotary holder 20B as the armature 51 moves in the axial direction. Move in the direction.

  At this time, as shown in FIG. 8B, the ball 43 in the torque cam 40 rolls and moves toward the deepest groove depth of the cam grooves 41 and 42, and the control holder 20A and the rotary holder 20B 4 rotates in a direction in which the circumferential width of the roller 27 becomes smaller, and the pair of opposed rollers 15 shown in FIG. 4 are pushed by the column portion 22 of the control holder 20A and the column portion 26 of the rotation holder 20B so as to approach each other. Moving.

  Therefore, as shown in FIG. 4, the roller 15 is displaced to the neutral position where the engagement with the cylindrical surface 12 and the cam surface 14 is released, and the two-way clutch 10 is disengaged.

In the disengaged state of the two-way clutch 10, the input shaft rotates the inner ring 13 in one direction by inputting the rotational torque into S _1, the column portion 22 of the braking members 46 formed on the spring holder 45 is controlled retainer 20A In order to press one of the column parts 26 of the rotary cage 20B, the control cage 20A and the rotary cage 20B rotate together with the inner ring 13. At this time, since the pair of opposed rollers 15 is held in the neutral position where the engagement is released, the rotation of the inner ring 13 is not transmitted to the outer ring 11 and the inner ring 13 rotates freely.

  When the energization of the electromagnetic coil 53a is released in the free rotation state of the inner ring 13, the armature 51 is released from the suction and becomes rotatable and slidable. By releasing the suction, the control holder 20A and the rotary holder 20B are relatively rotated in the direction in which the circumferential width of the pocket 27 is increased by the pressing of the elastic member 16 incorporated between the pair of rollers 15, and the pair of opposed rollers 15. As shown in FIG. 3, each of them is in a standby state in which it engages with the cylindrical surface 12 and the cam surface 14, and is unidirectional between the inner ring 13 and the outer ring 11 via one of the pair of opposed rollers 15. Rotational torque is transmitted.

Here, when the input shaft S ₁ is stopped and the rotation direction of the input shaft S ₁ is switched, the rotation of the inner ring 13 is transmitted to the outer ring 11 via the other roller 15.

  As described above, when the energization of the electromagnetic coil 53a is interrupted, the control holder 20A and the rotary holder 20B are relatively rotated in the direction in which the circumferential width of the pocket 27 is increased, and each of the pair of opposed rollers 15 is cylindrical surface 12. Further, since the standby state in which the cam surface 14 is immediately engaged is set, the rotation direction play is small, and the rotation of the inner ring 13 can be immediately transmitted to the outer ring 11.

  Here, if the two-way clutch 10 and the electromagnetic clutch 50 are assembled with a backlash with respect to the housing 1, each of the two-way clutch 10 and the electromagnetic clutch 50 cannot be operated accurately and reliably. For this reason, it is necessary to apply an appropriate preload to each of the two-way clutch 10 and the electromagnetic clutch 50.

  When preload is applied to the built-in components including the two-way clutch 10 and the electromagnetic clutch 50, the flanged cylinder 56 shown in FIGS. 1 and 2 is rotated. At this time, since the male screw 58 formed on the outer periphery of the flange 57 of the cylindrical body 56 is screw-engaged with the helical thread portion 59 formed on the inner periphery of the opening end of the housing 1, the rotation of the cylindrical body 56 is performed. The cylindrical body 56 is screwed by the operation, and the built-in components including the two-way clutch 10 and the electromagnetic clutch 50 are pushed toward the positioning portion 5 by the cylindrical body 56 to apply preload.

  In this way, the preload can be applied to the built-in component by a simple operation of rotating the cylinder 56, and an appropriate preload can be applied to the built-in component by adjusting the screwing amount of the cylinder 56. And preload control is easy.

  In the case of applying a preload by screw engagement between the male screw 58 formed on the outer periphery of the flange 57 and the helical screw portion 59 provided on the inner periphery of the opening end of the housing 1, the load of disturbance such as vibration is applied. If the thread portion is loosened by the above, there is a possibility that the two-way clutch 10 cannot be functioned reliably. In order to prevent the occurrence of such inconvenience, it is preferable to provide a locking means for locking the cylinder 56 at the preload adjustment position.

  9 and 10 show examples of the loosening prevention means 70 for preventing the cylindrical body 56 from loosening. In the example shown in FIG. 9, the opening end of the housing 1 is crimped inward, and the inward crimping protrusion 71 is engaged with the outer end surface of the flange 57 in the cylindrical body 56.

  In the example shown in FIG. 10, the male screw 73 formed on the outer periphery of the lock ring 72 is screw-engaged with the helical screw portion 59 and is pressed against the flange 57 by tightening the male screw 73 so that the lock ring 72 functions as a lock nut. I try to show it.

  1, 9, and 10, the pressure member is composed of the flanged cylinder 56, but the pressure member is not limited to this. In FIG. 11, cylindrical portions 64, 65 facing in the same direction are provided on the outer periphery and inner periphery of the annular plate portion 63, and a U-shaped cap 62 having a female screw 66 formed on the inner periphery of the outer peripheral cylindrical portion 64. Is used as a pressure material.

In the cap 62 as the pressurizing member, the female screw 66 formed on the outer peripheral cylindrical portion 64 is screw-engaged and tightened to the helical screw portion 67 formed on the outer periphery of the opening end portion of the housing 1. presses the bearing 60 at the peripheral cylindrical portion 65 within which is provided, along with pushed toward the positioning portion 5 showing the electromagnet 53 in Fig. 1 with the outer ring 60a of the bearing 60, the shaft of the input shaft S ₁ in the inner ring 60b of the bearing 60 The preload is applied to the two-way clutch 10 and the electromagnetic clutch 50 by pushing in the direction.

  In FIG. 1, a positioning portion 5 is provided in a bearing tube 2 provided at one end portion of a housing 1, and a flanged tube as a pressurizing member is provided on a helical thread portion 59 formed at the other end opening portion of the housing 1. Although the body 56 is screw-engaged, the position where the positioning portion is formed and the position where the pressure member is assembled are not limited thereto.

  12 and 13 show another embodiment of the rotation transmission device according to the present invention. In this embodiment, a ring groove 6 is provided on the inner periphery of the open end at the other end of the housing 1, and a retaining ring 7 attached to the ring groove 6 is used as a positioning portion.

  Further, a spiral threaded portion 8 is formed on the inner periphery of the opening end portion of the bearing cylinder 2 in the housing 1, and a male screw 81 formed on the outer periphery of a screw ring 80 as a pressurizing member is screwed into the spiral threaded portion 8. It is different from the rotation transmission device shown in FIG. 1 in that it is engaged. For this reason, the same parts as those shown in FIG.

  12 and 13, by tightening the screw ring 80, the built-in component comprising the housing 1, the two-way clutch 10 and the electromagnetic clutch 50 is pushed in the opposite direction to apply a preload to the built-in component.

  As shown in FIG. 12 and FIG. 13, it is preferable that the screw ring 80 is prevented from loosening by providing a means for preventing loosening when the preload is applied by tightening the screw ring 80. 14 to 17 show examples of the loosening prevention means 70. FIG.

  In the loosening prevention means 70 shown in FIG. 14, a radial pin hole 73 is formed in the bearing cylinder 2, the pin 74 is driven into the pin hole 73, and the screw 74 is engaged by the engagement of the pin 74 with the outer end surface of the screw ring 80. It has 80 slack stops.

  In the loosening prevention means 70 shown in FIG. 15, the open end portion of the bearing cylinder 2 is caulked inward, and the caulking projection 75 is engaged with the outer end surface of the screw ring 80 to prevent the screw ring 80 from loosening. .

  In the loosening prevention means 70 shown in FIG. 16, a male screw 77 formed on the outer periphery of the lock ring 76 is screw-engaged with the helical thread portion 8 formed on the inner periphery of the bearing cylinder 2, and the lock ring 76 is screwed. The screw ring 80 is prevented from loosening by being brought into pressure contact with the outer surface of the ring 80.

  In the loosening prevention means 70 shown in FIG. 17, the seal member 3 made of an oil seal is press-fitted into the opening of the bearing cylinder 2, and the seal member 3 is pressed against the outer surface of the screw ring 80 to prevent the looseness of the screw ring 80. It is said.

  As shown in FIGS. 14 to 17, the screw ring 80 is prevented from loosening by the loosening prevention means 70, so that an appropriate preload state for a built-in component composed of the two-way clutch 10 and the electromagnetic clutch 50 is maintained over a long period of time. Can be held.

  12 to 17, the screw ring 80 is a pressure member, but the pressure member is not limited to this. In FIG. 18, cylindrical portions 92, 93 facing in the same direction are provided on the outer periphery and inner periphery of the annular plate portion 91, and a U-shaped cap 90 in which a female screw 94 is formed on the inner periphery of the outer peripheral cylindrical portion 92. Is a pressure member.

  In the cap 90 as the pressurizing member, the female screw 94 formed on the outer peripheral cylindrical portion 92 is screw-engaged with the helical screw portion 95 formed on the outer periphery of the bearing tube 2 and tightened to be provided on the cap 90. The bearing 4 is pressed by the inner circumferential cylindrical portion 93 to apply preload to the two-way clutch 10 and the electromagnetic clutch 50 shown in FIG.

S ₁ Input shaft S ₂ Output shaft 1 Housing 2 Bearing cylinder 3 Seal member (oil seal)
DESCRIPTION OF SYMBOLS 4 Bearing 5 Positioning part 7 Retaining ring 8 Helical thread part 10 Two-way clutch 50 Electromagnetic clutch 53 Electromagnet 56 Flange cylinder (pressure member)
57 Flange 58 Male thread 59 Spiral thread 62 Cap (Pressure member)
63 Annular plate portion 64 Cylindrical portion 65 Cylindrical portion 66 Male screw 67 Helical screw portion 70 Loosening prevention means 72 Lock ring 73 Male screw 74 Pin 76 Lock ring 77 Male screw 80 Screw ring (pressure member)
81 male screw 90 cap 91 annular plate portion 92 cylindrical portion 93 cylindrical portion 94 female screw 95 helical screw portion

Claims (11)

Input shaft (S ₁₎ and the output shaft (S ₂₎ 2-way clutch which performs the blocking and transmission of rotation to the output shaft (S ₂₎ from the incorporated between opposed ends the input shaft (S ₁₎ of (10 ), An electromagnetic clutch (50) provided on the input shaft (S ₁ ) and disposed opposite to the two-way clutch (10), and the two-way clutch (10) and the electromagnetic clutch (50). A housing (1),
The electromagnetic clutch (50) includes an electromagnet (53) incorporated in one end opening of the housing (1), and the two-way clutch (10) is disengaged by energizing the electromagnet (53). And
The housing (1) has a bearing cylinder (2) covering the end of the output shaft (S ₂ ) on the side where the outer ring (11) is connected to the other end, and the bearing cylinder (2). In the rotation transmission device in which the bearing (4) for rotatably supporting the output shaft (S ₂ ) is incorporated,
A positioning part (5,) for axially positioning a built-in component consisting of the two-way clutch (10) and the electromagnetic clutch (50) in either one of the open end of the housing (1) and the bearing cylinder (2). 7), and the other side is provided with a helical screw portion (8, 59, 67), and the built-in component is pressed toward the positioning portion (5, 7) on the helical screw portion (8, 59, 67). A rotation transmission device characterized in that a pressure member (56, 62, 80, 90) to be screwed is engaged.   The pressurizing member (56) comprises a flanged cylinder provided on the outer end surface of the electromagnet (53), and a male screw (58) formed on the outer periphery of the flange (57) of the cylinder (56) The rotation according to claim 1, wherein the electromagnet (53) is pressed in the axial direction by being screw-engaged with a helical thread portion (59) formed on the inner periphery of the opening end of the housing (1). Transmission device.   The rotation transmission device according to claim 2, further comprising a locking means (70) for locking the pressure member (56) at a preload adjustment position.   The rotation transmission device according to claim 3, wherein the loosening prevention means (70) is formed by inward caulking at an open end of the housing (1).   The rotation transmission device according to claim 3, wherein the loosening prevention means (70) is formed by screwing a lock ring (72) having a male screw (73) formed on an outer periphery thereof into the helical thread portion (59).   The pressure member (62) is provided with cylindrical portions (64, 65) facing in the same direction on the outer periphery and inner periphery of the annular plate portion (63), and the female screw (66) is provided on the inner periphery of the outer peripheral cylindrical portion (64). And a female screw (66) of the cap (62) is screwed to a helical screw portion (67) formed on the outer periphery of the open end of the housing (1). The rotation transmission device according to claim 1, wherein the electromagnet (53) is pressed by an inner peripheral cylindrical portion.   The pressure member (80) comprises a screw ring having a male screw (81) formed on the outer periphery, and the male screw (81) of the screw ring (80) is provided on the inner periphery of the bearing cylinder (2). The rotation transmission device according to claim 1, wherein the bearing (4) is pressed by being screw-engaged with the threaded portion (8).   The rotation transmission device according to claim 7, wherein the pressurizing member (80) is loosened at a preload adjusting position by driving a pin (74) penetrating the bearing cylinder (2) in the radial direction.   The rotation transmission device according to claim 7, wherein the pressurizing member (80) is prevented from loosening at a preload adjusting position by inward caulking of the opening end of the bearing cylinder (2).   The rotation transmission device according to claim 7, wherein the pressure member (80) is prevented from being loosened at a preload adjustment position by press-fitting an oil seal (3) into the opening end of the bearing cylinder (2).   The pressure member (90) is provided with cylindrical portions (92, 93) facing in the same direction on the outer periphery and inner periphery of the annular plate portion (91), and the female screw (94) is provided on the inner periphery of the outer peripheral cylindrical portion (92). And a female thread (94) of the cap (90) is screw-engaged with a helical thread portion (95) provided on the outer periphery of the bearing cylinder (2). The rotation transmission device according to claim 1, wherein the outer ring of the bearing (4) is pressed by the inner circumferential cylindrical portion (93).

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