JP2017203539A - Driving force transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a driving force transmission device capable of smoothly switching transmission of torque between a first shaft and a second shaft, and properly keeping steering feeling without complicating an assembling process of the driving force transmission device.SOLUTION: When a relative position of cages 40, 41 is changed from a first position P1 to a second position P2, rollers 39a, 39b are moved in a direction to approach each other against elastic energization force of an elastic body 42, so that the rollers 39a, 39b are kept in an off-state of forming clearances S1, S2 without being engaged with a cam face 43 or an inner peripheral face portion 44. When the relative position of the cages 40, 41 is changed from the first position P1 to the second position P2, the rollers 39a, 39b are moved in a direction to be separated from each other by elastic energization force, the roller at a downstream side, of the rollers 39a, 39b is tightly engaged with the cam face 43 and the inner peripheral face portion 44, and the roller at the upstream side is kept in an on-state of forming the clearances S1, S2 with respect to the cam face 43 or the inner peripheral face portion 44.SELECTED DRAWING: Figure 9

Description

  The present invention relates to a driving force transmission device that switches on / off of transmission of rotational force between a first shaft and a second shaft that are provided coaxially with each other.

  The rotation transmission device described in the following Patent Document 1 includes a two-way clutch and an electromagnetic clutch for engaging and disengaging the two-way clutch. The two-way clutch includes an outer ring and an inner ring, a pair of rollers incorporated between the outer ring and the inner ring, and a control holder and a rotation holder that hold the pair of rollers. The control holder and the rotation holder define the circumferential width of the pair of rollers.

  When the electromagnetic coil provided in the electromagnetic clutch is not energized, the circumferential width of the pair of rollers is set to be relatively wide. In this state, both of the pair of rollers are pushed away from each other by the elastic member disposed between the pair of rollers, and the pair of rollers are not spaced on both the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring. Engage. Thereby, the two-way clutch is in the connected state.

  On the other hand, when the electromagnetic coil provided in the electromagnetic clutch is energized, a force is applied to the control holder, and the control holder and the rotary holder are relatively rotated by this force. The direction width becomes narrower. Therefore, the pair of rollers are pushed by the control retainer and the rotation retainer to move toward each other, and the engagement with the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring is released. As a result, the two-way clutch is disengaged.

JP2013-092191A

  In the rotation transmission device described in Patent Document 1, in a connected state of the two-way clutch, both of the pair of rollers are engaged with (i.e., meshed) the inner ring and the outer ring without a gap, so that the rotational torque is generated inside the two-way clutch. May remain. When this residual rotational torque is large, when the control cage is relatively rotated to switch the two-way clutch from the connected state to the disconnected state, at least one of the pair of rollers and the first shaft (inner ring) or the second shaft There is a possibility that the engagement with the (outer ring) is not released. In this case, the two-way clutch may not be smoothly switched from the connected state to the disconnected state. In other words, there is a possibility that the transmission of the rotational force between the first shaft and the second shaft cannot be smoothly switched from the on state to the off state. Therefore, a driving force transmission device that can smoothly switch the transmission of the rotational force between the first shaft and the second shaft from the on state to the off state is desired.

  Further, the inventors of the present invention interpose a separator in the circumferential direction between the pair of holding members, and change the relative position in the circumferential direction of the pair of holding members as the separator is displaced in the axial direction. ing. In order to maintain a good steering feeling, it is necessary to accurately define the circumferential relative positions of the pair of holding members in the on state. By using a part of the separator as a circumferential spacer, it may be possible to define the circumferential relative position of the pair of holding members in the ON state. In this case, however, the optimum circumferential relative position of the holding member It is necessary to repeat the selection of the separator in order to obtain the above, and as a result, the assembly process of the driving force transmission device may be complicated.

  Therefore, the present invention can smoothly switch the transmission of the rotational force between the first shaft and the second shaft, and can improve the steering feeling without complicating the assembly process of the driving force transmission device. It is an object of the present invention to provide a driving force transmission device that can be maintained at a low level.

In order to achieve the above object, the invention according to claim 1 is provided between a first shaft (25) and a second shaft (26) provided coaxially with each other, and the first shaft is provided. Driving force transmission device (1) for switching on / off of transmission of rotational force between the second shaft and the second shaft, wherein the first shaft includes an outer peripheral surface portion (43), and the second shaft The shaft includes an inner peripheral surface portion (44) facing the outer peripheral surface portion, and at least one wedge space (38) is formed between the outer peripheral surface portion and the inner peripheral surface portion, and the inside of the wedge space A pair of rollers (39a, 39b) arranged on the side, an elastic body (42) that elastically biases the pair of rollers in a direction away from each other in the circumferential direction, and the pair of rollers are held in the wedge space A pair of holding members (40, 41) that are relative to each other in the circumferential direction. A pair of holding members movably provided and defining a circumferential width of the pair of rollers; a shaft portion (58); and a wedge portion (59) bulging in a circumferential direction from a part of the shaft portion. And a separator (SP) provided so as to be displaceable in the axial direction of the first shaft and the second shaft, and in accordance with the displacement in the axial direction, the circumference of the pair of holding members A separator that changes the relative position in the direction, and when the relative position in the circumferential direction of the pair of holding members changes from the first position (P1) to the second position (P2), the pair of rollers is It is moved off in the direction close to the circumferential direction against the elastic urging force of the elastic body, and the pair of rollers are not engaged with the outer peripheral surface portion or the inner peripheral surface portion, and a gap (S1, S2) is generated. The state is realized, and the circumferential direction relative of the pair of holding members When the position is changed from the second position to the first position, the pair of rollers are moved away from each other by the elastic biasing force, and the roller on the downstream side in the rotation direction of the pair of rollers is moved. Is engaged with the outer peripheral surface portion and the inner peripheral surface portion without a gap, and the roller on the upstream side in the rotational direction is in an ON state in which a gap (S3, S4) is generated between the outer peripheral surface portion or the inner peripheral surface portion. The first position of the pair of holding members is defined by the pair of holding members sandwiching the wedge portions in the circumferential direction abutting against the side surfaces of the wedge portions, respectively. In the state in the first position,
The driving force transmission device further includes a spacer (75) for adjusting an axial position of the separator with respect to the second shaft.

The invention according to claim 2 further includes a bearing that supports the first shaft and the second shaft so as to be relatively rotatable, and the spacer is interposed between the second shaft and the bearing. The driving force transmission device according to claim 1, wherein the driving force transmission device is mounted.
The invention according to claim 3 is the driving force transmission apparatus according to claim 1 or 2, wherein the spacer is interposed between the second shaft and the separator.

  According to a fourth aspect of the present invention, a plurality of the separators are provided side by side in the circumferential direction, the spacer is ring-shaped, and is interposed between the second shaft and the plurality of separators. The driving force transmission device according to claim 3.

  According to the configuration of the first aspect, in the ON state, the roller on the downstream side in the rotation direction is engaged with the outer peripheral surface portion and the inner peripheral surface portion without a gap, and therefore, between the first shaft and the second shaft. Rotational force can be transmitted in a good manner. In the ON state, the roller on the upstream side in the rotation direction has a gap between the outer peripheral surface portion or the inner peripheral surface portion. In other words, in the ON state, only one of the pair of rollers is engaged with the outer peripheral surface portion and the inner peripheral surface portion, so that no rotational torque remains between the roller and the outer peripheral surface portion or the inner peripheral surface portion. Even then, only a small rotational torque remains. Accordingly, when the transmission of the rotational force between the first shaft and the second shaft is switched from the on state to the off state, the engagement between the roller and the outer peripheral surface portion and the inner peripheral surface portion can be smoothly performed. . Therefore, transmission of the rotational force between the first shaft and the second shaft can be switched smoothly.

Further, the axial position of the separator with respect to the second shaft is adjusted using a spacer. Further, in the on state, the first positions of the pair of holding members are defined by the pair of holding members abutting against the side surfaces of the wedge portions.
By selecting a spacer of just the right size and adjusting the axial position of the separator with respect to the second axis with high precision, the axial position of the separator with respect to the holding member can be adjusted with high precision. The first position of the member can be defined with high accuracy.

In addition, since the axial position of the separator is adjusted by selecting the spacer, it is not necessary to remove the separator when adjusting the first position. Thereby, complication of the assembly process of a driving force transmission device can be prevented.
As described above, the transmission of the rotational force between the first shaft and the second shaft can be smoothly switched, and the steering feeling can be kept good without complicating the assembly process of the driving force transmission device. Can do.

  According to the configuration of the second aspect, since the spacer is interposed between the second shaft and the bearing, the spacer is fixed to the second shaft. As the pair of holding members are displaced from the first position to the second position, the separator is also displaced in the axial direction. However, since the spacer is fixed to the second shaft, the separator is not displaced. The spacer can be held in the desired position. This can reliably prevent the spacer from falling off.

According to the configuration of the third aspect, the spacer is interposed between the second shaft and the separator. Therefore, the axial position of the separator with respect to the second axis can be directly adjusted.
According to the structure of Claim 4, the spacer is ring-shaped and is interposed between the second shaft and the plurality of separators. With the displacement of the pair of holding members from the first position to the second position, the separator is detached from the second shaft or the separator, but the spacer is ring-shaped, so the second shaft and the separator The spacer is stopped in the space between. This can reliably prevent the spacer from falling off.

FIG. 1 is a diagram showing a schematic configuration of a steering device equipped with a clutch unit as a driving force transmission device according to an embodiment of the present invention. FIG. 2 is a cross-sectional view of the clutch unit. FIG. 3 is a cross-sectional view taken along section line III-III in FIG. FIG. 4 is a perspective view showing a configuration of a two-way clutch included in the clutch unit. FIG. 5 is an exploded perspective view showing the configuration of the two-way clutch. FIG. 6 is a cross-sectional view taken along section line VI-VI in FIG. 3 and is a schematic view showing an off state of the clutch unit. FIG. 7 is a schematic view showing an off state of the clutch unit. FIG. 8 is a schematic view showing an ON state of the clutch unit. FIG. 9 is a schematic diagram illustrating an ON state of the clutch unit. FIG. 9A illustrates a state in which the output shaft rotates in the C1 direction with respect to the input shaft. FIG. 9B illustrates an output shaft with respect to the input shaft. Shows a state of rotating in the C2 direction. FIG. 10 is a schematic view showing an on state of a clutch unit as a driving force transmission device according to another embodiment of the present invention. FIG. 11 is a schematic view showing an off state of a clutch unit as a driving force transmission device according to another embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
FIG. 1 is a diagram showing a schematic configuration of a steering device 2 on which a clutch unit 1 as an example of a driving force transmission device according to an embodiment of the present invention is mounted.
The steering device 2 is a so-called steer in which the mechanical connection between the steering mechanism A for steering the steered wheels 3 and the steering mechanism B including the steering member 4 such as a steering wheel and the steering shaft 5 is released. It is a by-wire system. And in order to implement | achieve the mechanical fail safe mechanism of a steer-by-wire system, the clutch unit 1 is interposed between the steering shaft 5 and the pinion shaft 9 provided in the steering mechanism A, and it rotates by the clutch unit 1. Force transmission is switched on (connected) / off (disconnected).

The steering device 2 includes a steering mechanism A and a steering mechanism B.
The turning mechanism A includes a turning shaft 10, a turning actuator 11, a pair of tie rods 12, and a pair of knuckle arms 13. Each tie rod 12 has one end connected to the corresponding end of the steered shaft 10 and the other end connected to the corresponding steered wheel 3 via the corresponding knuckle arm 13. As the steered shaft 10 moves in the axial direction (vehicle width direction), the steered angle of the steered wheels 3 changes. The turning actuator 11 includes a motor (not shown) and a motion conversion mechanism (not shown) such as a ball screw device that converts the driving force of the motor into movement of the turning shaft 10 in the axial direction.

The steering device 2 further includes a rack housing 15 that accommodates a portion of the pinion shaft 9 where the pinion 9 a is formed and the steered shaft 10. The rack housing 15 is fixed to the vehicle body 14.
The steering mechanism B includes a steering angle sensor 16 for detecting the steering angle of the steering member 4 and a rotational torque sensor 17 for detecting the steering rotational torque applied to the steering member 4. The steering mechanism B includes a turning angle sensor 21 for detecting the turning angle of the turning wheel 3 and a vehicle speed sensor 18 for detecting the vehicle speed. Each detection signal of various sensors including the steering angle sensor 16, the rotational torque sensor 17, the turning angle sensor 21, and the vehicle speed sensor 18 is input to a control unit 20 configured by an ECU (Electronic Control Unit). It has come to be.

  When the steering member 4 is operated and the steering shaft 5 is rotated, the control unit 20 sets the target turning angle based on the steering angle detected by the steering angle sensor 16 and the vehicle speed detected by the vehicle speed sensor 18. Set. The control unit 20 drives and controls the turning actuator 11 based on the deviation between the target turning angle and the turning angle detected by the turning angle sensor 21. Thereby, operation of the steering mechanism A by the steering member 4 is enabled.

Further, the control unit 20 applies an appropriate reaction force to the steering member 4 based on the detection signal output from the rotational torque sensor 17, the steering angle sensor 16, etc., in the direction opposite to the direction in which the steering member 4 is steered. Thus, the motor 23 is driven and controlled. The output rotation of the motor 23 is decelerated (amplified) by the speed reducer 24 and transmitted to the steering member 4 via the steering shaft 5.
As described above, the clutch unit 1 to which the driving force transmission device according to the embodiment of the present invention is applied is interposed between the steering shaft 5 and the pinion shaft 9. A mechanism for fail-safe of the steering device 2 is realized.

  The clutch unit 1 is interposed in the middle portion of the intermediate shaft 6 including an input shaft 25 as a first shaft and an output shaft 26 as a second shaft. One end of the intermediate shaft 6 is connected to the steering shaft 5 via a universal joint 7, and the other end of the intermediate shaft 6 is connected to one end of a pinion shaft 9 via a universal joint 8. The pinion shaft 9 has a pinion 9a at the other end. The rack 10a of the steered shaft 10 is meshed with the pinion 9a.

The intermediate shaft 6 includes an input shaft 25 connected to the steering shaft 5 and an output shaft 26 connected to the pinion shaft 9. The input shaft 25 and the output shaft 26 are arranged coaxially with each other.
The clutch unit 1 is interposed between the input shaft 25 and the output shaft 26. The clutch unit 1 is a device that can switch on / off the transmission of rotational force between the input shaft 25 and the output shaft 26.

  During normal operation of the vehicle, the control unit 20 mechanically disconnects the steering member 4 and the steering mechanism A with the clutch unit 1 in the released state. On the other hand, when the vehicle is in the ignition-off state or when an abnormality occurs such as a malfunction in the steer-by-wire system, the control unit 20 turns the clutch unit 1 into the engaged state and turns the steering member 4 The mechanism A is mechanically coupled.

  In this state, when the steering member 4 and the steering shaft 5 rotate according to the driver's operation of the steering member 4, the steering rotational torque is transmitted from the steering member 4 to the steering shaft 5. The steering rotation torque is transmitted to the pinion shaft 9 via the steering shaft 5 and the intermediate shaft 6, and the pinion shaft 9 rotates. The rotation of the pinion shaft 9 is converted into an axial movement of the steered shaft 10. The turning angle of the steered wheels 3 changes due to the axial movement of the steered shaft 10. Thereby, direct operation of the steering mechanism A by the steering member 4 is enabled.

The clutch unit 1 can be applied not only to the intermediate shaft 6 of the steering device 2 but also to other shafts of the steering device. The clutch unit 1 can also be applied to shafts used for devices other than the steering device (for example, a main shaft of a machine tool, a shaft to which a propeller for wind power generation is attached, an axle of a train, etc.). it can.
FIG. 2 is a cross-sectional view of the clutch unit 1.

  In the following description, the axial direction of the input shaft 25 and the output shaft 26 is referred to as an axial direction X. Also, in the axial direction X, the direction from the output shaft 26 side to the input shaft 25 side (the right side of the drawing in FIG. 2) is defined as the first direction X1, and the direction from the input shaft 25 side to the output shaft 26 side (see FIG. 2) is the second direction X2. The second direction X2 is the reverse direction of the first direction X1. A radial direction R is defined as the radial direction of the input shaft 25 and the output shaft 26. The circumferential direction of the input shaft 25 and the output shaft 26 is a circumferential direction C. Further, in the circumferential direction C, the clockwise direction when the input shaft 25 is viewed from the output shaft 26 side is defined as the C1 direction (see FIG. 3), and it is opposite when the input shaft 25 is viewed from the output shaft 26 side. A clockwise direction is defined as a C2 direction (see FIG. 3).

The input shaft 25 includes an inner shaft 27 that extends in the axial direction X, and an inner ring 28 that is coaxially connected to an end portion of the inner shaft 27 on the second direction X2 side. The output shaft 26 includes a shaft portion 29 that extends in the axial direction X, and an outer ring 30 that is coaxially connected to an end portion of the shaft portion 29 on the first direction X1 side.
The clutch unit 1 includes a two-way clutch 31 that turns on (connects) / off (disconnects) transmission of torque between the inner ring 28 and the outer ring 30, an electromagnetic suction unit 32 that drives the two-way clutch 31, and a two-way clutch. And a housing 33 for housing the clutch 31 and the electromagnetic suction part 32.

The housing 33 has a cylindrical shape, and a bearing cylinder 34 is formed at the end in the second direction X2. A first rolling bearing 35 is disposed between the inner peripheral surface of the bearing cylinder 34 and the outer peripheral surface of the shaft portion 29 of the output shaft 26. The output shaft 26 is supported by the housing 33 through the first rolling bearing 35 so as to be rotatable and immovable in the axial direction X.
The inner ring 28 is formed using, for example, a steel material, and the outer ring 30 is formed in a cylindrical shape with one end in the axial direction X being a closed end, and is formed using a steel material. An annular step 36a that narrows the inner diameter of the outer ring 30 and a bottom surface 36b that continues to the annular step 36a are formed at the bottom of the outer ring 30. The annular step portion 36a has a cylindrical shape, and the inner diameter of the outer ring 30 is narrowed. The bottom surface 36b is a plane perpendicular to the axial direction X. A second rolling bearing (bearing) 37 is fixed between the inner periphery of the annular step portion 36 of the outer ring 30 and the outer periphery of the end portion of the inner ring 28 on the second direction X2 side. A shim ring (spacer) 75 is inserted between the second rolling bearing 37 and the bottom surface 36b. The shim ring 75 has an annular shape and is formed using a steel material. The main surface (the left and right surfaces in FIG. 2) of the shim ring 75 is in close contact with both the outer ring 37a and the bottom surface 36b of the second rolling bearing 37. Therefore, the relative position of the input shaft 25 and the output shaft 26 in the axial direction X is adjusted by changing the thickness of the shim ring 75 inserted between the second rolling bearing 37 and the bottom surface 36b. Thus, the inner ring 28 is supported so as to be rotatable with respect to the outer ring 30 and immovable in the axial direction X.

FIG. 3 is a cross-sectional view taken along section line III-III in FIG. FIG. 4 is a perspective view showing the configuration of the two-way clutch 31. FIG. 5 is an exploded perspective view showing the configuration of the two-way clutch 31.
The two-way clutch 31 is provided in each of one or a plurality of (for example, three in this embodiment) wedge spaces 38 formed by the inner ring 28, the outer ring 30, and the outer periphery of the inner ring 28 and the inner periphery of the outer ring 30. A pair of rollers 39a, 39b arranged side by side in direction C, a first retainer (holding member) 40 that is rotatably provided around the inner shaft 27 and holds the pair of rollers 39a, 39b, and an inner shaft 27 is provided in a rotatable manner around a second retainer (holding member) 41 that holds a pair of rollers 39a and 39b, and a wedge space 38, and the first and second rollers 39a and 39b The elastic body 42 elastically pressing in the circumferential direction C that is separated from each other, and the first retainer 40 and the second retainer 41 are engaged with each other, and the first retainer 40 and the second retainer 41 are engaged. relative position (In this embodiment three) more switching comprising a separator SP, and a back plate BP which displaceably supported a separator SP in the axial direction X.

The inner ring 28 has an outer peripheral surface portion including a plurality of (for example, three) cam surfaces (outer peripheral surface portions) 43. Further, in this embodiment, the inner ring 28 and the inner shaft 27 are integrally provided, but the inner ring 28 and the inner shaft 27 may be configured by separate members. The outer ring 30 has a cylindrical inner peripheral surface portion 44.
As shown in FIG. 3, each wedge space 38 is partitioned by an inner peripheral surface portion 44 of the outer ring 30 and each cam surface 43 of the inner ring 28. Each wedge space 38 becomes narrower toward both ends in the circumferential direction C. In each wedge space 38, an elastic body 42 is disposed between the first roller 39a and the second roller 39b. An example of the elastic body 42 is a coil spring. The elastic body 42 is supported by a main surface 45 described below. The plurality of elastic bodies 42 are held by the inner ring 28 by fitting an elastic body holder SH (see FIG. 4) that collectively supports the elastic bodies 42 to the inner ring 28.

  The cam surfaces 43 are provided at equal intervals in the circumferential direction C. Each cam surface 43 is continuous with both the flat main surface 45 orthogonal to the radial direction R and the circumferential direction C of the main surface 45, and a pair of flat surfaces that are inclined with respect to the main surface 45 with respect to the circumferential direction C. And inclined surfaces 46a and 46b. The inclined surfaces 46 a and 46 b connect the end portion of the main surface 45 and the outer peripheral cylindrical surface of the inner ring 28, and are inclined in opposite directions along the circumferential direction C.

  As shown in FIGS. 4 and 5, the first and second cages 40 and 41 are rotatable relative to each other. The first cage 40 includes a columnar first width defining portion 47 and an annular first support portion 48 that collectively supports the first width defining portion 47. The first support portion 48 supports, for example, a plurality of first width defining portions 47. The first retainer 40 is rotatable relative to the inner ring 28 and the outer ring 30 so that the first support portion 48 is coaxial with the inner ring 28 and the outer ring 30. The first width defining portions 47 are the same number as the pair of rollers 39a and 39b (three in this embodiment), are columnar shapes extending in the axial direction X, and are arranged at equal intervals in the circumferential direction C. The first cage 40 is formed using a resin material.

More specifically, the annular first support portion 48 includes a flat plate annular first annular portion 49a and a circle disposed coaxially with respect to the first annular portion 49a and on the first direction X1 side. And an annular second annular portion 49b. Further, in this embodiment, the first width defining portion 47 connects the first annular portion 49a and the second annular portion 49b in the axial direction X.
As shown in FIGS. 4 and 5, each first width defining portion 47 has a columnar shape extending along the axial direction X. Each first width defining portion 47 is disposed between the corresponding separator SP and the first roller 39a. Each first width defining portion 47 includes a first restricting protrusion 50 that protrudes from the second annular portion 49b toward the first direction X1. A first pressing surface 51 that can be pressed against the first roller 39a is formed on the side surface of each first width defining portion 47 on the circumferential direction C2 side.

As shown in FIGS. 3 and 5, a first slidable contact surface 52 slidably contactable with the separator SP is formed on the side surface of each first width defining portion 47 on the circumferential direction C1 side. The first slidable contact surface 52 is formed in an inclined surface that goes toward the circumferential direction C1 as it goes in the first direction X1.
As shown in FIG. 5, the second retainer 40 includes a flat plate-shaped third annular portion 53 and a plurality of second retainers 40 that protrude from the inner peripheral portion of the third annular portion 53 toward the second direction X <b> 2. And a second width defining portion 54. The third annular portion 53 is disposed so as to surround the outer periphery of the second annular portion 49b. The second width defining portions 54 are provided in the same number (three in this example) as the number of rollers 39a and 39b, and are arranged at equal intervals in the circumferential direction C. Each second width defining portion 54 is disposed between the corresponding separator SP and the second roller 39b.

Since the third annular portion 53 surrounds the outer periphery of the second annular portion 49b of the first retainer 40, the first retainer 40 can be called an inner retainer, and the second retainer 41 can be referred to as an outer cage.
A second pressing surface 55 that can contact (press) the second roller 39b is formed on the side surface of each second width defining portion 54 on the circumferential direction C1 side. A second slidable contact surface 56 slidable with the separator SP is formed on the side surface of each second width defining portion 54 on the circumferential direction C2 side. The second slidable contact surface 56 is formed as an inclined surface that goes in the circumferential direction C2 as it goes in the first direction X1.

The third annular portion 53 is provided with a second restricting protrusion 57 (only one is shown in FIG. 5) protruding in the first direction X1 at the same position as each second width defining portion 54. It has been. The second cage 41 is formed using a resin material.
As shown in FIG. 3, the wedge space 38 includes a pair of rollers 39 a by a first pressing surface 51 of the first width defining portion 47 and a second pressing surface 55 of the second width defining portion 54. , 39b are partitioned in a state of being arranged in the circumferential direction C. The pocket P is a space that is long in the circumferential direction C, and is a region in which the pair of rollers 39a and 39b accommodated in the pocket P can move in the circumferential direction C. By switching the relative positions in the circumferential direction C of the first width defining portion 47 and the second width defining portion 54, the width of the pocket P, that is, the circumferential width W of the pair of rollers 39a and 39b can be changed. .

Each separator SP includes a shaft portion 58 that extends in the axial direction X, and a wedge portion 59 that is provided at an end portion 58a of the shaft portion 58 on the second direction X2 side and that becomes wider in the second direction X2.
The wedge portion 59 includes a first sliding contact surface (side surface) 60 provided on the side surface on the circumferential direction C2 side and a second sliding contact surface (side surface) 61 provided on the side surface on the circumferential direction C1 side. .
The first sliding contact surface 60 is an inclined surface that extends in the circumferential direction C1 as it goes in the first direction X1. In this embodiment, the first sliding contact surface 60 is formed into a curved surface such as a part of a spherical surface. The second slidable contact surface 61 is an inclined surface that goes in the circumferential direction C2 as it goes in the first direction X1. In this embodiment, the second sliding contact surface 61 is formed in a curved surface such as a part of a spherical surface. In addition, the 1st sliding contact surface 60 and the 2nd sliding contact surface 61 may be formed in the flat inclined surface.

  As shown in FIGS. 2 and 5, the back plate BP has a flat plate shape and is fitted to the inner shaft 27 of the input shaft 25 so as not to move in the axial direction X. The back plate BP is formed using a steel material, for example. A surface of the back plate BP on the second direction X2 side is in sliding contact with the second annular portion 49b and the third annular portion 53, respectively. In the back plate BP, a plurality of (three in this example) long holes 62 penetrating the back plate BP in the axial direction X are formed at equal intervals in the circumferential direction C. The first restriction protrusions 50, the second restriction protrusions 57, and the separators SP are inserted through the long holes 62.

As shown in FIG. 2, the electromagnetic attraction unit 32 includes an armature 63 provided on a plurality of separators SP so as to be movable in the axial direction X, an annular rotor 64 facing the armature 63 from the first direction X1, And an electromagnet 65 disposed on the rotor 64 in the first direction X1 side.
In this embodiment, the armature 63 is provided in a disk shape. The armature 63 is formed using a magnetic material. In the energized state of the electromagnet 65 of the electromagnetic attraction unit 32, the armature 63 is drawn toward the first direction X1.

  The rotor 64 is fixed to the inner shaft 27 while being fitted to the inner shaft 27 of the input shaft 25. The electromagnet 65 includes an annular electromagnetic coil 65a and an annular core 65b that supports the electromagnetic coil 65a. The core 65 b is fixed to a lid member 66 fixed to the opening side of the housing 33. A third rolling bearing 68 is disposed between the cylindrical bearing support portion 67 extending from the lid member 66 in the first direction X1 and the inner shaft 27 of the input shaft 25. The end portion of the inner shaft 27 of the input shaft 25 in the second direction X2 is supported by the housing 33 through the third rolling bearing 68 and the lid member 66 so as to be relatively rotatable and not relatively movable in the axial direction X. Yes.

  As shown in FIG. 2, the clutch unit 1 further rotates the first and second width defining portions 47 and 54 as the output shaft 26 in accordance with the rotation of the output shaft 26 when the two-way clutch 31 is on. It further includes a swivel structure 69 that moves in the direction. The suspension structure 69 includes, for example, an elastic member 71 disposed between the armature 63 and the rotor 64. The elastic member 71 is, for example, a coil spring that can expand and contract in the axial direction X, and a plurality of elastic members 71 are arranged in the circumferential direction C at equal intervals. The elastic member 71 is compressed between the armature 63 and the rotor 64. Therefore, the separator SP is elastically pressed toward the output shaft 26 by the elastic member 71.

Each separator SP is coupled to the armature 63 in such a posture that the wedge portion 59 is along the circumferential direction when viewed from the axial direction X. Depending on the mounting accuracy of each separator SP to the armature 63, the rotational direction posture of the wedge portion 59 around the shaft portion 58 may be inclined from the intended posture in each separator SP.
FIG. 6 is a cross-sectional view taken along the cutting plane line VI-VI in FIG. 3 and is a schematic diagram showing the clutch unit 1 in an off state. FIG. 7 is a schematic diagram showing an off state of the clutch unit 1. 8 and 9A and 9B are schematic views showing the ON state of the clutch unit 1. 9A shows a state where the output shaft 26 is rotated in the C1 direction with respect to the input shaft 25, and FIG. 9B shows a state where the output shaft 26 is rotated in the C2 direction with respect to the input shaft 25.

By changing the relative positions of the first and second cages 40 and 41, the two-way clutch 31 (clutch unit 1) can be switched between an on state and an off state. The relative positions of the first and second cages 40 and 41 are switched by moving the separator SP in the axial direction X.
The separator SP has a predetermined cutting position (the position of the separator SP shown in FIG. 6) drawn in the first direction X1 side and a connection position (FIG. 9) located on the second direction X2 side from the cutting position. The position of the separator SP shown in FIG.

When the separator SP is in the connection position, the relative positions of the first and second cages 40, 41 are the first position P1 (the first and second cages 40, shown in FIGS. 5, 9A, and 9B). 41 relative position). At this time, the circumferential width W of the pair of rollers 39a and 39b defined by the first width defining portion 47 and the second width defining portion 54 is set to be relatively narrow.
When the electromagnet 65 (see FIG. 2) is energized with the separator SP in the connected position, the electromagnet 65 attracts the armature 63. As a result, the plurality of separators SP connected to the armature 63 are drawn toward the first direction X1. By this pull-in, the plurality of separators SP are displaced in the first direction X1 and disposed at the cutting position (the position of the separator SP shown in FIG. 6).

  5 and 6, when each separator SP is displaced toward the first direction X1, the first sliding contact surface 60 of the separator SP presses the first width defining portion 47 toward the circumferential direction C2. While sliding on the first sliding contact surface 52 of the first width defining portion 47. Therefore, the first width defining portion 47 moves to the circumferential direction C2 side. Further, when each separator SP is displaced toward the first direction X1, the second sliding surface 61 of the separator SP presses the second width defining portion 54 toward the circumferential direction C1, and the second width defining is performed. The second sliding contact surface 56 of the portion 54 slides. Therefore, the second width defining portion 54 moves to the circumferential direction C1 side. That is, when each separator SP is displaced toward the first direction X1, the first width defining portion 47 and the second width defining portion 54 adjacent to each other in the circumferential direction C1 move in a direction away from each other. To do. Therefore, due to the displacement of each separator SP in the first direction X1 side, the circumferential width W of the pair of rollers 39a and 39b defined by the first and second width defining portions 47 and 54 is narrowed. At this time, the first holder 40 rotates in the circumferential direction C2 with respect to the separator SP, and the second holder 41 rotates in the circumferential direction C1 with respect to the separator SP. At this time, the first restricting protrusion 50 is engaged with the end of the long hole 62 of the back plate BP on the first direction X1 side, and the movement of the first width defining portion 47 is restricted, and the The movement of the second width defining portion 54 is restricted by engaging the second restricting protrusion 57 with the end portion in the direction X2 of the second direction.

  When the separator SP is disposed at the cutting position, that is, the relative position of the first and second cages 40 and 41 is the second position P2 (the first and second cages 40 and 40 shown in FIG. 6). When the first width defining portion 47 is moved to the circumferential direction C2, the first pressing surface 51 of each first width defining portion 47 is moved to the corresponding first roller. Since 39 a is pressed toward the circumferential direction C <b> 2, each first roller 39 a is moved toward the circumferential direction C <b> 2 against the elastic biasing force of the elastic body 42. As a result, as shown in FIG. 7, each first roller 39a moves from the main surface 45 to the inclined surface 46a, and a gap S1 is formed between each first roller 39a and the inner peripheral surface portion 44 of the outer ring 30. Is formed. That is, the engagement of the first roller 39a with the cam surface 43 of the inner ring 28 and the inner peripheral surface portion 44 of the outer ring 30 is released.

  Further, as a result of the movement of the second width defining portion 54 toward the circumferential direction C1, the second pressing surface 55 of each second width defining portion 54 moves the corresponding second roller 39b toward the circumferential direction C1. Therefore, each second roller 39b is moved toward the circumferential direction C1 against the elastic biasing force of the elastic body 42. As a result, as shown in FIG. 7, each second roller 39 b moves from the main surface 45 to the inclined surface 46 b, and there is a gap between each second roller 39 b and the inner peripheral surface portion 44 of the outer ring 30. S1 is formed. That is, the engagement of each second roller 39b with the cam surface 43 of the inner ring 28 and the inner peripheral surface portion 44 of the outer ring 30 is released.

In a state in which the relative position of the first and second cages 40 and 41 is changed to the second position P2, the two-way clutch 31 has the pair of rollers 39a and 39b not engaged with the inner peripheral surface portion 44 in the wedge space 38. In this state, the gaps S1 and S2 are generated.
Although the clearance S1 and the clearance S2 are described as being formed between the rollers 39a and 39b and the inner peripheral surface portion 44 of the outer ring 30, they are formed between the rollers 39a and 39b and the cam surface 43 of the inner ring 28. May be.

  On the other hand, when energization to the electromagnet 65 (see FIG. 2) is released, the armature 63 is not attracted by the electromagnet 65. When the armature 63 is not sucked, the first sliding contact surface 60 of the separator SP is moved from the first sliding contact surface 52 by receiving the elastic biasing force of the elastic body 42 through the pair of rollers 39a and 39b. The second slidable contact surface 61 of the separator SP is displaced from the second slidable contact surface 56 to the second direction X2 side. Therefore, the first width defining portion 47 moves to the circumferential direction C1 side, and the second width defining portion 54 moves to the circumferential direction C2 side. As a result, the first width defining portion 47 and the second width defining portion 54 corresponding to the common separator SP approach each other and abut on the outer peripheral surface 58b of the shaft portion 58 of the separator SP in the circumferential direction C, respectively. Accordingly, the relative movement of the first and second cages 40 and 41 is restricted, and the first and second cages 40 and 41 are defined at the first position P1. As a result, the separator SP is again arranged at the connection position (the position of the separator SP shown in FIG. 8).

  Further, with the displacement of the separator SP in the second direction X2, the pressing by the first width defining portion 47 and the second width defining portion 54 is released. For this reason, the pair of rollers 39a and 39b are moved away from each other by the elastic biasing force of the elastic body 42. The first roller 39a is moved to the circumferential direction C1 side, and the second roller 39b is moved to the circumferential direction C2 side. Accordingly, the rollers 39a and 39b are moved from the main surface 45 to the inclined surfaces 46a and 46b, and the two-way clutch 31 is turned on so that the rollers 39a and 39b can engage with the inner peripheral surface portion 44.

When the two-way clutch 31 is on, the input shaft 25 and the output shaft 26 basically rotate together. However, the input shaft 25 and the output shaft 26 may rotate relative to each other until either of the rollers 39a and 39b is engaged with the cam surface 43 and the inner peripheral surface portion 44.
In the ON state of the two-way clutch 31, as shown in FIG. 6, the end portion 59a on the second direction X2 side of the wedge portion 59 of the separator SP is in contact with the annular step portion 36 (side surface thereof). The separator SP is elastically pressed toward the output shaft 26 by the elastic member 71 of the swirling structure 69, whereby friction is generated between the separator SP and the output shaft 26. In this state, as the output shaft 26 rotates, the first and second width defining portions 47 and 54 move in the same rotational direction as the output shaft 26 (ie, rotate) in the separator SP.

  As shown in FIG. 8, when the two-way clutch 31 is in the ON state, the pair of width defining portions 47 and 54 sandwiching the separator SP in the circumferential direction C are respectively connected to the first sliding contact surface 60 and the second sliding surface of the wedge portion 59. It is in contact with the contact surface 61. Therefore, in this state, the distance L between the pair of width defining portions 47 and 54 depends on the axial position of the wedge portion 59 with respect to the first and second cages 40 and 41. That is, the relative position of the first and second cages 40 and 41 can be defined as the first position P1 by controlling the axial position of the wedge portion 59 with high accuracy.

  As shown in FIG. 3, when the two-way clutch 31 is on, that is, when the first and second cages 40 and 41 are at the first position P1, the circumferential width W of the pair of rollers 39a and 39b is A relatively narrow interval is set. The circumferential width W is an interval at which it is impossible for both the pair of rollers 39a and 39b to engage the cam surface 43 and the inner peripheral surface portion 44 without a gap in the free state of the elastic body 42. In other words, the circumferential width W is such that one of the pair of rollers 39a and 39b can be engaged with the cam surface 43 and the inner peripheral surface portion 44 without any gap. In this case, the other of the pair of rollers 39a and 39b is the cam The gaps S <b> 3 and S <b> 4 (see the enlarged views of FIGS. 9A and 9B) are formed between the surface 43 and the inner peripheral surface portion 44.

  The circumferential width W of the pair of rollers 39a and 39b is determined by the distance L between the pair of width defining portions 47 and 54. Since the width defining portions 47 and 54 and the wedge portion 59 are in contact with each other in the circumferential direction C when the two-way clutch 31 is in an on state, a pair of separators SP having poor dimensional accuracy or mounting accuracy of each separator SP to the armature 63 The distance L between the width defining portions 47 and 54 cannot be maintained at the desired size (the relative position of the first and second cages 40 and 41 is the desired position (first position P1)). As a result, the circumferential width W of the pair of rollers 39a and 39b may vary from one unit to another. In this case, it is assumed that the gaps S3 and S4 between the roller on the upstream side in the rotation direction and the cam surface 43 and the inner peripheral surface portion 44 become too wide. In this case, the play of the steering member 4 (see FIG. 1) is caused. There is a possibility that the steering feeling becomes worse.

  For this reason, in this embodiment, a shim ring 75 of just the right size is selected for each unit 1 and interposed between the output shaft 26 and the second rolling bearing 37. Thereby, the axial position of the separator SP with respect to the output shaft 26 is adjusted. The axial positions of the first and second cages 40 and 41 are positioned by a back plate BP coupled to the input shaft 25 so as not to move in the axial direction X. Therefore, the axial position of the separator SP relative to the cages 40 and 41 can be adjusted with high accuracy by selecting the shim ring 75 from a plurality of types having different thicknesses.

The operator selects the shim ring 75 having the right size selected from a plurality of types after assembling the two-way clutch 31.
For example, let us consider a case where the distance L between the pair of width defining portions 47 and 54 is defined as a desired size by utilizing a part (for example, the head) of the separator SP as a spacer in the circumferential direction C. In this case, a plurality of separators SP having different circumferential widths of the head are prepared, and a separator SP having an optimum circumferential width is selected for each unit 1. In this case, it is necessary to disassemble the two-way clutch 31 every time the separator SP is replaced, and the assembly process of the two-way clutch 31 may be very complicated.

In this embodiment, since the position of the separator SP in the axial direction is adjusted by selecting the shim ring 75 (the thickness of the shim ring 75 is selected optimal), it is not necessary to remove the separator SP when adjusting the first position P1. . Thereby, complication of the assembly process of the clutch unit 1 can be prevented.
As shown in FIG. 9A, in the ON state of the two-way clutch 31, that is, in the state where the relative positions of the first and second cages 40 and 41 are at the first position P1, the output shaft 26 is in relation to the input shaft 25. When rotating, the first and second width defining portions 47 and 54 move in the same rotational direction as the output shaft 26 by the action of the hanging structure 69.

  When the two-way clutch 31 is in the ON state, the output shaft 26 rotates relative to the input shaft 25, for example, in the circumferential direction C1 due to the operation of the steering member 4 (see FIG. 1) or the reverse input from the steered wheels 3 (see FIG. 1). In this case (when rotational torque is generated on the output shaft 26 in the circumferential direction C1 side), as shown in FIG. 9A, the second of the rollers 39a and 39b on the upstream side in the rotational direction (circumferential direction C2 side). The roller 39b is moved to a state in which a gap S3 is formed between the roller 39b and the cam surface 43 or the inner peripheral surface portion 44, and the second roller 39b is connected to the first downstream side (circumferential direction C1 side) via the elastic body 42. The roller 39a is moved so as to engage with the cam surface 43 and the inner peripheral surface portion 44 without a gap. Thereby, it is possible to transmit the rotational force between the input shaft 25 and the output shaft 26.

  Conversely, when the output shaft 26 rotates in the circumferential direction C2 side with respect to the input shaft 25 (when rotational torque in the circumferential direction C2 side is generated in the output shaft 26), as shown in FIG. The first roller 39a on the upstream side (circumferential direction C1 side) in the rotational direction of 39a, 39b is moved to a state in which a gap S4 is generated between the cam surface 43 or the inner peripheral surface portion 44, and the first roller 39a Moves the second roller 39b on the downstream side (circumferential direction C2 side) through the elastic body 42 so as to engage the cam surface 43 and the inner peripheral surface portion 44 without any gap. Thereby, it is possible to transmit the rotational force between the input shaft 25 and the output shaft 26.

  As described above, according to this embodiment, in the ON state of the two-way clutch 31, the roller (roller 39a or 39b) on the downstream side in the rotational direction is engaged with the cam surface 43 and the inner peripheral surface portion 44 without a gap. Therefore, it is possible to satisfactorily transmit the rotational force between the input shaft 25 and the output shaft 26 when the two-way clutch 31 is on. Further, when the two-way clutch 31 is in the ON state, the rollers (rollers 39a or 39b) on the upstream side in the rotation direction have gaps S3 and S4 between the cam surface 43 and the inner peripheral surface portion 44. That is, in the on state of the two-way clutch 31, only one of the pair of rollers 39a and 39b is engaged with the cam surface 43 and the inner peripheral surface portion 44. Even if the rotational torque does not remain between them or remains, the rotational torque is small. Therefore, when the transmission of the rotational force between the input shaft 25 and the output shaft 26 is switched from the on state to the off state, the engagement between the pair of rollers 39a and 39b and the cam surface 43 and the inner peripheral surface portion 44 is released. It can be done smoothly. Therefore, transmission of rotational force between the input shaft 25 and the output shaft 26 can be switched smoothly.

The shim ring 75 having the right size is selected and the axial position of the wedge portion 58 with respect to the output shaft 26 is adjusted with high accuracy. Thereby, the axial direction position of the separator SP with respect to the cages 40 and 41 can be adjusted with high accuracy. Therefore, the first position P1 of the first and second cages 40 and 41 is defined with high accuracy. be able to.
In addition, since the axial position of the separator SP is adjusted by selecting the shim ring 75, it is not necessary to remove the separator SP when adjusting the first position P1. Thereby, complication of the assembly process of the clutch unit 1 can be prevented.

As described above, the transmission of the rotational force between the input shaft 25 and the output shaft 26 can be switched smoothly, and the steering feeling can be maintained well without complicating the assembly process of the clutch unit 1.
Further, since the shim ring 75 is interposed between the output shaft 26 and the second rolling bearing 37, the shim ring 75 is fixed to the output shaft 26. As the first and second cages 40 and 41 are displaced from the first position P1 to the second position P2, the separator SP is also displaced in the axial direction X, but the shim ring 75 is fixed to the output shaft 26. Therefore, the shim ring 75 can be held at the intended position regardless of the displacement of the separator SP. Thereby, it is possible to reliably prevent the shim ring 75 from falling off.

FIG. 10 is a schematic diagram showing an on state of a clutch unit 201 as a driving force transmission device according to another embodiment of the present invention. FIG. 11 is a schematic diagram showing an off state of the clutch unit 201.
This embodiment is different from the embodiment of FIGS. 1 to 9 in that a shim ring (spacer) is replaced with a shim ring 202 (spacer) instead of a configuration in which the output shaft 26 and the second rolling bearing 37 are interposed. ) Between the output shaft 26 and the separator SP.

  Specifically, the shim ring 202 has an annular shape and is formed using a steel material. The shim ring 202 is inserted (interposed) between the annular step portion 36 (the side surface) of the output shaft 26 and the end portion 59a on the second direction X2 side of the wedge portion 59 of the separator SP. The shim ring 202 is inserted (interposed) between the output shaft 26 and a plurality (three in this embodiment) of separators SP.

  In the ON state of the two-way clutch 31, as shown in FIG. 10, the end portion 59a on the second direction X2 side of the wedge portion 59 of the separator SP is in contact with the annular step portion 36 (side surface thereof). The main surface (the left and right surfaces in FIG. 10) of the shim ring 202 is in close contact with both the annular step portion 36 and the end portion 59 a of the wedge portion 59. Therefore, the axial position of the separator SP with respect to the output shaft 26 can be directly adjusted by changing the thickness of the shim ring 202 inserted between the annular step portion 36 and the wedge portion 59.

  In the OFF state of the two-way clutch 31, as shown in FIG. 11, the end portion 59a on the second direction X2 side of the wedge portion 59 of the separator SP is separated from the shim ring 202 in the axial direction X. At this time, the shim ring 202 is detached from the annular step portion 36 and the wedge portion 59. However, since the shim ring 202 has a ring shape, the shim ring 202 is formed in a space between the annular step portion 36 and the end portion 59a of the wedge portion 59. It can be stopped. Thereby, it is possible to reliably prevent the shim ring 202 from falling off.

As mentioned above, although two embodiment of this invention was described, this invention can also be implemented with another form.
For example, the shim ring 75 may not be ring-shaped but may be divided in the circumferential direction C.
In addition, the present invention can be variously modified within the scope of the claims.

DESCRIPTION OF SYMBOLS 1 ... Clutch unit (driving force transmission device), 25 ... Input shaft (first shaft), 26 ... Output shaft (second shaft), 37 ... Second rolling bearing (bearing), 38 ... Wedge space, 39a , 39b ... roller, 42 ... elastic body, 40 ... first cage (holding member), 41 ... second cage (holding member), 43 ... cam surface (outer peripheral surface portion), 44 ... inner peripheral surface portion, SP DESCRIPTION OF SYMBOLS ... Separator 59 ... Wedge part 60 ... 1st sliding contact surface (side surface) 61 ... 2nd sliding contact surface (side surface), 75 ... Shim ring (spacer), 201 ... Clutch unit (driving force transmission device), 202 ... Shim ring (spacer), P1 ... first position, P2 ... second position, S1 ... gap, S2 ... gap, S3 ... gap, S4 ... gap, W ... circumferential width

Claims (4)

Driving force transmission provided between a first shaft and a second shaft provided coaxially with each other and for switching on / off of transmission of rotational force between the first shaft and the second shaft. A device,
The first shaft includes an outer peripheral surface portion, the second shaft includes an inner peripheral surface portion facing the outer peripheral surface portion, and at least one wedge space is provided between the outer peripheral surface portion and the inner peripheral surface portion. Is formed,
A pair of rollers arranged in the wedge space;
An elastic body that elastically biases the pair of rollers in a direction away from each other in the circumferential direction;
A pair of holding members for holding each of the pair of rollers in the wedge space, the pair of holding members provided so as to be relatively movable in the circumferential direction and defining a circumferential width of the pair of rollers;
A separator having a shaft portion and a wedge portion bulging in a circumferential direction from a part of the shaft portion, the separator being provided to be displaceable in the axial direction of the first shaft and the second shaft, A separator that changes a relative position in the circumferential direction of the pair of holding members in accordance with the displacement in the axial direction;
When the relative position in the circumferential direction of the pair of holding members changes from the first position to the second position, the pair of rollers is moved in a direction approaching the circumferential direction against the elastic biasing force of the elastic body. An off-state is realized in which the pair of rollers are not engaged with the outer peripheral surface portion or the inner peripheral surface portion to create a gap,
When the relative position in the circumferential direction of the pair of width defining members changes from the second position to the first position, the pair of rollers are moved away from each other by the elastic biasing force, and the pair of width defining members Of the rollers, the roller on the downstream side in the rotational direction engages the outer peripheral surface portion and the inner peripheral surface portion without a gap, and the upstream roller in the rotational direction has a gap between the outer peripheral surface portion or the inner peripheral surface portion. The on-state that produces
The first position of the pair of holding members is defined by the pair of holding members sandwiching the wedge portions in the circumferential direction abutting against the side surfaces of the wedge portions, respectively.
The driving force transmission device further includes a spacer that adjusts an axial position of the separator with respect to the second shaft in a state where the pair of holding members are in the first position. A bearing further supporting the first shaft and the second shaft so as to be relatively rotatable;
The driving force transmission device according to claim 1, wherein the spacer is interposed between the second shaft and the bearing.   The driving force transmission device according to claim 1, wherein the spacer is interposed between the second shaft and the separator. A plurality of the separators are provided side by side in the circumferential direction,
The driving force transmission device according to claim 3, wherein the spacer has a ring shape and is interposed between the second shaft and the plurality of separators.

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