JP2021021417A - Rotation transmission device - Google Patents

Abstract

To prevent an erroneous lock of a two-way clutch caused by the loading of an idling radial load, in a rotation transmission device for transmitting rotation by using the two-way clutch and an electromagnetic clutch, and blocking the transmission.SOLUTION: When idling an input shaft 1 by carrying electricity to an electromagnetic coil 53a of an electromagnetic clutch 50, control for increasing and decreasing an electricity-carrying amount to the electromagnetic coil 53a is performed in conjunction with an increase/decrease of a value of torque which is detected by torque meters arranged at an input shaft 1 and an output shaft 2. By this control, even if a large radial load is loaded in idling, a suction force with respect to an armature 51 which is integrated with a control cage 16A out of a cage 16 is increased, a roller holding force exceeding a drag force which is received by rollers 15 by the radial load is imparted to the cage 16, each of the rollers 15 is held in an engagement release position, and an erroneous lock of a two-way clutch 10 can be thereby prevented.SELECTED DRAWING: Figure 1

Description

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

As a rotation transmission device that transmits and shuts off rotation from the input shaft to the output shaft, it has been conventionally known that a two-way clutch is provided and the engagement and disengagement of the two-way clutch is controlled by an electromagnetic clutch. (See, for example, Patent Document 1).

The rotation transmission device described in Patent Document 1 is a two-way clutch, which is an outer ring provided at the shaft end of the output shaft and an inner ring provided at the shaft end of the input shaft and arranged inside the outer ring in the radial direction. It has a control cage and a rotation cage that are rotatably and axially movable on the input shaft, and between the inner circumference of the outer ring and the outer circumference of the inner ring, the pillar portion of the control cage and the rotation cage. A pair of rollers (engagers) incorporated in pockets formed between adjacent pillars are urged by coil springs (elastic members) in a direction in which the pillars are alternately arranged in the circumferential direction. Then, the cylinder surface formed on the inner circumference of the outer ring and the cam surface formed on the outer circumference of the inner ring are put on standby at a position where they are engaged with each other. When the inner ring rotates in one direction, one of the pair of rollers is placed on the cylindrical surface of the outer ring. The one that transmits the rotation of the inner ring to the outer ring while engaged with the cam surface of the inner ring is adopted.

Then, by energizing the electromagnetic coil (electromagnet) of the electromagnetic clutch provided on the input shaft, magnetic attraction is applied to the armature connected to the control cage at a position facing the rotor fixed to the input shaft, and the armature And the width of the circumference of the pocket by the action of the torque cam (motion conversion mechanism) provided between the disc portion of the control cage and the disc portion of the rotation cage by moving the control cage in the axial direction. The control cage and the rotation cage are relatively rotated in the direction in which is smaller, and a pair of rollers are moved to the disengaged position (neutral position where the engagement is disengaged) at the pillar portion of each cage, and from the inner ring. The rotation transmission to the outer ring is cut off.

Further, when the energization of the electromagnetic coil of the electromagnetic clutch is released, the coil spring presses the pillar portion of the control cage and the rotation cage via the roller, so that the control cage and the rotation cage have the circumferential width of the pocket. Is relatively rotated in the direction of increasing, and the standby state in which the pair of rollers engages with the cylindrical surface and the cam surface is maintained.

Japanese Unexamined Patent Publication No. 2014-25483

By the way, in the rotation transmission device as described above, when the electromagnetic coil of the electromagnetic clutch is energized, the control cage and the rotation cage of the two-way clutch engage each roller at each pillar portion at the disengagement position (with the outer ring). It is held in a position where there is a gap between the two wheels), which blocks the transmission of rotation from the inner ring to the outer ring and causes the input shaft to idle. However, it is momentarily or dynamically radial from the outside due to vibration or the like. When a load is applied, the rotation of the input shaft may be transmitted to the output shaft even while the electromagnetic coil is energized (idling).

That is, when a radial load is applied while the electromagnetic coil is energized, as shown in FIG. 10A, if the radial load P is small, the cylindrical surface 72 on the inner circumference of the outer ring 71 and the outer periphery of the inner ring 73. A pair of rollers 75 (only one shown) incorporated into the wedge-shaped space between the cam surface 74 resists the elastic force of the coil spring 77 by the control cage and the column portion 76 of the rotary cage (only one shown). The inner ring 73 and the input shaft (not shown) slip smoothly because they are pushed out to the vast side of the wedge-shaped space and held in a state where they do not come into contact with the outer ring 71 (at the disengaged position). However, as shown in FIG. 10B, when the radial load P becomes large, a part of the outer ring 71 in which the elastic deformation becomes large comes into contact with the roller 75, and the roller 75 has a frictional force with the outer ring 71 (hereinafter, hereinafter, The inner ring 73 and the input shaft are in a state of receiving the drag force (referred to as “dragging force”), and idle while receiving the resistance of the drag force. Then, as shown in FIG. 10 (c), the radial load P becomes even larger, and the drag force acting on the roller 75 is the force that the control cage and the rotation cage hold the roller 75 at the disengagement position ( When the roller holding force (hereinafter referred to as "roller holding force") is exceeded, the roller 75 on the rear side in the rotation direction of the pair of rollers 75 moves relatively to the narrow side of the wedge-shaped space, and the cylindrical surface 72 of the outer ring 71 and the cylindrical surface 72. A phenomenon of unintentionally engaging with the cam surface 74 of the inner ring 73 (hereinafter referred to as “mislock”) occurs, and the rotation is transmitted to the outer ring 71 and the output shaft (not shown). ..

Therefore, an object of the present invention is to prevent mislocking of a two-way clutch due to a radial load during idling in a rotation transmission device that transmits and shuts off rotation by using a two-way clutch and an electromagnetic clutch. ..

In order to solve the above problems, the inventors of the present invention apply a radial load to a rotation transmission device having the above-described configuration in a state where the electromagnetic coil of the electromagnetic clutch is energized and the input shaft is idled. An experiment was conducted to investigate the behavior of the idling torque (torque due to dragging force) acting on the output shaft at that time. The results of this experiment are shown in FIG.

From FIG. 11, when the radial load is below a certain lower limit value, the idling torque does not act on the output shaft (state in FIG. 10A), and when the radial load becomes larger than the lower limit value, it is almost the same as the increase in the radial load. The idling torque also increases linearly (state in FIG. 10 (b)), and when the radial load reaches a certain upper limit value, the state in FIG. 10 (c) occurs, mislocking of the two-way clutch occurs, and the output shaft It can be seen that the rotation is transmitted to the output shaft (a constant rotational torque acts on the output shaft). At this time, the torque acting on the input shaft was also measured at the same time, and it was confirmed that the behavior showed the same tendency as in FIG.

From the above findings, in order to prevent mislocking of the two-way clutch, the inventors increase the amount of current (current value) of the electromagnetic clutch to the electromagnetic coil when the idling torque tends to increase. I came up with the idea that the roller holding force should be increased.

That is, the present invention relates to an input shaft, an output shaft arranged coaxially with the input shaft, a two-way clutch that transmits and shuts off rotation from the input shaft to the output shaft, and on the input shaft. It has an electromagnetic clutch provided to control engagement and disengagement of the two-way clutch, and the two-way clutch is provided at the outer ring provided at the shaft end portion of the output shaft and at the shaft end portion of the input shaft. The inner ring is arranged radially inside the outer ring, and the control cage and the rotation cage are supported by the input shaft so as to be rotatable and axially movable, and the inner circumference of the outer ring and the outer circumference of the inner ring. Pillars provided in each of the control cage and the rotary cage are alternately arranged in the circumferential direction between the two, and a pair of engagers and their engaging elements are placed in a pocket formed between the adjacent pillars. It incorporates an elastic member that urges a pair of engaging elements in a direction away from each other to stand by at a position where they engage with the inner circumference of the outer ring and the outer circumference of the inner ring, and the electromagnetic clutch is the control cage. It has an armature connected to, a rotor fixed to the input shaft and facing the armature in the axial direction, and an electric magnet arranged to face the rotor, and the control cage is moved in the axial direction by energizing the electric magnet. , The axial movement of the control cage is converted into a relative rotational motion of the control cage and the rotation cage in the direction in which the circumferential width of the pocket becomes smaller by the motion conversion mechanism, and the pair of engagers are disengaged. In the rotation transmission device, the torque detecting means is provided on at least one of the input shaft and the output shaft, and the value of the torque detected by the torque detecting means is increased or decreased while the electromagnetic clutch is energized. By controlling the amount of energization of the electromagnet in conjunction with this, even if a radial load is applied during idling, a roller holding force that exceeds the drag force received by the rollers due to the radial load is applied to each roller. Is held in the disengagement position to prevent mislocking of the two-way clutch.

Here, as the torque detecting means, a twist detecting type torque meter can be adopted. Further, a strain gauge can be used as the twist detecting means of the torque meter.

As described above, the rotation transmission device of the present invention measures the torque detected by the torque detecting means provided on at least one of the input shaft and the output shaft when the electromagnet of the electromagnetic clutch is energized and the input shaft is idled. Since the amount of electricity applied to the electromagnet is increased or decreased in conjunction with the increase or decrease in the value, even when a large radial load is applied, the corresponding roller holding force is applied to mislock the two-way clutch. Can be prevented. Further, when the radial load is small, the amount of electricity supplied to the electromagnet is also small, so that there is no possibility that the power consumption will increase more than necessary.

Front sectional view of the rotation transmission device according to the embodiment of the present invention. Sectional view taken along line II-II of FIG. Cross-sectional view showing the engaged state of the rollers corresponding to FIG. Sectional view taken along line IV-IV of FIG. Sectional view taken along the line VV of FIG. Sectional view along the VI-VI line of FIG. (A) is a cross-sectional view taken along the line VII-VII of FIG. 6, and (b) is a cross-sectional view for explaining the operation of the torque cam corresponding to (a). (A) and (b) are explanatory views of operation when a radial load is applied while energizing the electromagnet, (a) is a schematic cross-sectional view at the time of performing control, and (b) is performing control. Schematic cross-sectional view without Conceptual diagram of the usage state of the rotation transmission device of the embodiment (A) to (c) are explanatory views of the generation mechanism of the mislock of the two-way clutch, respectively. Graph showing the relationship between radial load and idling torque while the electromagnet is energized

Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 9. The basic configuration of the rotation transmission device of this embodiment is the same as that of the conventional one described above. That is, as shown in FIG. 1, this rotation transmission device has a cylindrical shape that covers the input shaft 1, the output shaft 2 arranged coaxially with the input shaft 1, and the shaft ends of both shafts 1 and 2. And the electromagnetic clutch that controls the engagement and disengagement of the two-way clutch 10 and the two-way clutch 10 that are incorporated in the housing 3 and transmit and shut off the rotation from the input shaft 1 to the output shaft 2. It consists of 50.

As shown in FIGS. 1 and 2, the two-way clutch 10 has a cylindrical surface 12 formed on the inner circumference of the outer ring 11 provided at the shaft end of the output shaft 2, and is provided at the shaft end of the input shaft 1. A plurality of cam surfaces 14 (inclined surfaces 14a and 14b) are formed on the outer periphery of the inner ring 13 at equal intervals in the circumferential direction, and a roller 15 as a pair of engagers is formed between each cam surface 14 and the cylindrical surface 12. A coil spring 20 as an elastic member is incorporated, and a roller 15 thereof is held by a cage 16 (control cage 16A and rotation cage 16B). Then, when the inner ring 13 rotates in one direction, the rotation of the inner ring 13 is transmitted to the outer ring 11 in a state where one of the pair of rollers 15 is engaged with the cylindrical surface 12 and the cam surface 14, and the inner ring 13 is rotated in the other direction. At the time of rotation, the rotation of the inner ring 13 is transmitted to the outer ring 11 in a state where the other roller 15 is engaged with the cylindrical surface 12 and the cam surface 14.

Here, the outer ring 11 is integrally formed with the output shaft 2, and the shaft end portion of the input shaft 1 can be rotated in a small-diameter recess 17 provided on the inner circumference of one end side (closed end side) thereof. A bearing 18 to support is incorporated. A portion of the output shaft 2 adjacent to the outer ring 11 is rotatably supported by a bearing cylinder 5 having a small diameter formed at one end of the housing 3 via a bearing 4. Further, a sealing seal 6 that seals between the output shaft 2 and the housing 3 is press-fitted into the inner circumference of the bearing cylinder 5 on the outer side in the axial direction from the bearing 4.

On the other hand, the inner ring 13 is formed integrally with the input shaft 1. The cam surface 14 of the inner ring 13 is composed of a pair of inclined surfaces 14a and 14b inclined in opposite directions, and one side or the other side in the circumferential direction between the inclined surfaces 14a and 14b and the cylindrical surface 12 of the outer ring 11. A wedge-shaped space that becomes narrow is formed. Further, a flat spring support surface 19 facing in the tangential direction of the inner ring 13 is provided between the pair of inclined surfaces 14a and 14b of the inner ring 13, and the coil spring 20 is supported by the spring support surface 19.

The coil spring 20 is arranged between the pair of rollers 15 and urges the rollers 15 in a direction away from each other. As a result, each roller 15 is arranged at a standby position (position shown in FIG. 3) that engages with the cylindrical surface 12 and the cam surface 14, and the engagement between the standby position and the cylindrical surface 12 and the cam surface 14 is released. It is possible to move in the circumferential direction from the disengagement position (position shown in FIG. 2). Then, the spring holding piece 47 formed on the outer peripheral side of the spring holder 45 fixed to the input shaft 1 is held between the pair of rollers 15 in a state where the movement to the outer peripheral side is restricted (FIGS. 4 and 4). 5).

The cage 16 includes a control cage 16A and a rotation cage 16B. Among them, the control cage 16A is provided with the same number of pillars 22 as the cam surface 14 on one side of the annular disc 21 at equal intervals in the circumferential direction, and an arcuate elongated hole is provided between the adjacent pillars 22. 23 is formed (see FIG. 6), and a tubular portion 24 is provided on the outer periphery in the direction opposite to the pillar portion 22. On the other hand, the rotation cage 16B has a configuration in which the same number of pillar portions 26 as the cam surface 14 are provided on one side of the annular disc portion 25 at equal intervals in the circumferential direction.

The control cage 16A and the rotary cage 16B have a combination in which the pillar portion 26 of the rotary cage 16B is inserted into the elongated hole 23 of the control cage 16A, and the pillar portions 22 and 26 are arranged alternately in the circumferential direction. Has been done. Then, in the combined state, the tip portions of the pillar portions 22 and 26 are arranged between the outer ring 11 and the inner ring 13, and the disc portions 21 and 25 are fitted to the outer circumference of the input shaft 1. It is said to be built-in located between 28 and the outer ring 11.

By incorporating the respective cages 16A and 16B as described above, as shown in FIG. 2, between the pillar portion 22 of the control cage 16A and the pillar portion 26 of the rotation cage 16B, the cam surface 14 of the inner ring 13 and the cam surface 14 The pockets 27 facing each other in the radial direction are formed, and a pair of rollers 15 and a coil spring 20 are incorporated in each pocket 27.

Further, the disc portions 21 and 25 of the cages 16A and 16B are slidably (moved in the axial direction) along the slide guide surface 29 formed on the outer circumference of the input shaft 1 and are supported by the rotary cage 16B. A thrust bearing 30 is incorporated between the disk portion 25 and the support ring 28 fitted to the input shaft 1. The thrust bearing 30 rotatably supports the rotary cage 16B in a state of preventing the rotary cage 16B from moving to the electromagnetic clutch 50 side.

Then, between the disc portion 21 of the control cage 16A and the disc portion 25 of the rotation cage 16B, the axial movement of the control cage 16A is performed relative to the control cage 16A and the rotation cage 16B. A torque cam 40 is provided as a motion conversion mechanism for converting the rotational motion into a vertical motion.

As shown in FIGS. 6 and 7 (a) and 7 (b), the torque cam 40 is located on the opposite surfaces of the disk portion 21 of the control cage 16A and the disk portion 25 of the rotary cage 16B in the circumferential direction. A pair of facing cam grooves 41, 42 that gradually become shallower toward both ends are provided in the central portion, and a ball 43 is incorporated between the pair of facing cam grooves 41, 42. Although the cam grooves 41 and 42 show a substantially V-shaped groove here, they may be arc-shaped grooves.

Then, from the state shown in FIG. 7B, when the control cage 16A moves in the axial direction in the direction in which the disc portion 21 of the control cage 16A approaches the disc portion 25 of the rotation cage 16B, FIG. 7 As shown in (a), the ball 43 rolls and moves toward the deepest position of the groove depths of the cam grooves 41 and 42, and the control cage 16A and the rotation cage 16B reduce the circumferential width of the pocket 27. It is designed to rotate relative to the direction.

Here, as shown in FIGS. 4 and 5, in the input shaft 1, the spring holder 45 cannot rotate relative to the holder fitting surface 44 formed on the other end side of the inner ring 13 and cannot move in the axial direction. It is fitted, and a plurality of detent pieces 46 arranged between the pillar portion 22 of the control cage 16A and the pillar portion 26 of the rotation cage 16B are formed on the outer periphery of the spring holder 45. When the control cage 16A and the rotation cage 16B rotate relative to each other in the direction of reducing the circumferential width of the pocket 27, the plurality of detent pieces 46 hold the pillar portions 22 and 26 of the cages 16A and 16B. The pair of rollers 15 are held in a neutral position by receiving them at both edges to regulate the relative rotation amount. Therefore, the coil spring 20 does not contract more than necessary, and even if expansion and contraction are repeated, the coil spring 20 is not damaged by fatigue.

On the other hand, as shown in FIG. 1, the electromagnetic clutch 50 includes an armature 51 axially facing the end surface of the tubular portion 24 of the control cage 16A, a rotor 52 axially facing the armature 51, and the rotor 52. Has an electromagnet 53 facing in the axial direction.

The armature 51 is rotatably and slidably fitted to the outer peripheral cylindrical surface 54 of the support ring 28, and the cylinder portion 24 of the control cage 16A is located on the inner circumference of the connecting cylinder 55 provided on one side of the outer peripheral portion thereof. It is press-fitted and connected and integrated with the control cage 16A. As a result, the armature 51 is provided to be slidable at two positions in the axial direction of the outer peripheral cylindrical surface 54 of the support ring 28 and the outer peripheral slide guide surface 29 of the input shaft 1. Here, the support ring 28 is positioned in the axial direction by a step portion formed on the other side of the slide guide surface 29 of the input shaft 1 in the axial direction.

The rotor 52 is fitted on the outer circumference of the input shaft 1, is positioned axially by a shim 56 incorporated between the rotor 52 and the support ring 28, and is prevented from rotating with respect to the input shaft 1.

The electromagnet 53 includes an electromagnetic coil 53a and a yoke 53b that supports the electromagnetic coil 53a. The yoke 53b is fitted to the inner circumference of the other end side (opening side) of the housing 3 and is retained by a retaining ring 7, and is made rotatable relative to the input shaft 1 via a bearing 57. ing. By incorporating the electromagnet 53, the opening of the housing 3 is closed to prevent foreign matter from entering the housing 3.

In this rotation transmission device, a torque meter (not shown) as a torque detecting means is provided on the input shaft 1 and the output shaft 2, and the conventional point is that the torque meter is used to perform the control described later. Is different. The torque meter is a twist detection type using a strain gauge, and when this rotation transmission device is used for a vehicle steering device (steering system), it is conventionally incorporated in the vehicle steering device. Things can be diverted.

This rotation transmission device has the above configuration, and when the energization of the electromagnetic clutch 50 to the electromagnetic coil 53a is cut off, as shown in FIG. 3, the roller 15 of the two-way clutch 10 has the cylindrical surface 12 of the outer ring 11. And is in a state of engaging with the cam surface 14 of the inner ring 13. Therefore, when the input shaft 1 rotates in one direction, the rotation is transmitted from the inner ring 13 to the outer ring 11 via one of the pair of rollers 15, and the output shaft 2 rotates in the same direction as the input shaft 1. Further, when the input shaft 1 rotates in the opposite direction, the rotation is transmitted from the inner ring 13 to the outer ring 11 and the output shaft 2 via the other roller 15.

On the other hand, when the electromagnetic coil 53a of the electromagnetic clutch 50 is energized while the two-way clutch 10 is engaged, an attractive force acts on the armature 51, and the armature 51 moves in the axial direction and is attracted to the rotor 52. At this time, since the armature 51 and the control cage 16A are connected and integrated by fitting the connecting cylinder 55 and the cylinder portion 24, the control cage 16A is a disk thereof as the armature 51 moves in the axial direction. The portion 21 moves in a direction approaching the disk portion 25 of the rotation cage 16B.

Due to the axial relative movement of the control cage 16A and the rotation cage 16B, the ball 43 of the torque cam 40 rolls and moves toward the deepest position of the groove depths of the cam grooves 41 and 42 (FIG. 7B). From the state to the state of FIG. 7A), the control cage 16A and the rotation cage 16B rotate relative to each other in the direction in which the circumferential width of the pocket 27 becomes smaller. Due to the relative rotation of the control cage 16A and the rotation cage 16B, the roller 15 of the two-way clutch 10 is pushed by the pillar portion 22 of the control cage 16A and the pillar portion 26 of the rotation cage 16B and moves in a direction approaching each other. To do.

As a result, as shown in FIG. 2, the roller 15 is displaced to the neutral position where the roller 15 is disengaged from the cylindrical surface 12 and the cam surface 14, and the two-way clutch 10 is put into the disengaged state.

Then, when the input shaft 1 is rotated in one direction in the disengaged state of the two-way clutch 10, the detent piece 46 formed on the spring holder 45 becomes the pillar portion 22 of the control cage 16A and the rotation cage 16B. Since one of the pillars 26 is pressed, the control cage 16A and the rotation cage 16B rotate together with the input shaft 1.

At this time, if no radial load is applied, each roller 15 of the two-way clutch 10 is held at the disengagement position by the roller holding force of the cage 16 (control cage 16A and rotation cage 16B). , The rotation of the input shaft 1 and the inner ring 13 is not transmitted to the outer ring 11 and the output shaft 2, and the input shaft 1 idles. However, when a radial load is applied from the outside, the rotation of the input shaft 1 is transmitted to the output shaft 2. It may end up.

That is, when a large radial load is applied and the drag force acting on the roller 15 exceeds the roller holding force of the cage 16, the control cage 16A is integrally rotated with the armature 51 as shown in FIG. 8 (b). The roller 15 on the rear side in the rotation direction is relatively narrow on the narrow side of the wedge-shaped space by rotating relative to the rotation cage 16B in the direction in which the pocket 27 expands while moving away from the rotation cage 16B and the rotation cage 16B. Move to and a mislock occurs.

Therefore, in this embodiment, when the electromagnetic coil 53a of the electromagnetic clutch 50 is energized and the input shaft 1 is idled, the value of the torque detected by the torque meters provided on the input shaft 1 and the output shaft 2 is increased or decreased. In conjunction with this, control is performed to increase or decrease the amount of electricity supplied to the electromagnetic coil 53a.

According to this control, when the torques of the input shaft 1 and the output shaft 2 tend to increase while the electromagnetic coil 53a is energized, the energization amount of the electromagnetic coil 53a is increased, which is shown in FIG. 8A. As described above, even if the drag force generated by the load of the radial load becomes large, the suction force with respect to the armature 51 is increased and the roller holding force exceeding the drag force is applied to the cage 16 to rotate with the control cage 16A. It is possible to prevent the relative movement with the cage 16B and hold each roller 15 in the disengaged position to prevent the two-way clutch 10 from being mislocked.

Further, when the torques of the input shaft 1 and the output shaft 2 tend to decrease from the above state, it is considered that the drag force is small, so the amount of electricity supplied to the electromagnetic coil 53a should be reduced accordingly. As a result, power consumption can be suppressed while imparting a roller holding force that exceeds the drag force.

Here, the method of changing the amount of energization of the electromagnetic coil 53a may be gradually increased or decreased according to the torque value of the torque meter, or may be changed stepwise (for example, when the torque value is low). It may be switched in two steps, the normal mode and the strong holding mode when the torque value is high).

Then, when the energization of the electromagnetic coil 53a is released while the input shaft 1 is idling by this control, the armature 51 is released from adsorption and becomes rotatable, and the control cage 16A and the rotation cage 16B are coil springs 20. Rotates relative to each other in the direction in which the circumferential width of the pocket 27 increases due to the pressing force of the roller 15, and returns to the standby state (state in FIG. The rotation of the input shaft 1 is transmitted to the output shaft 2 via the shaft 1. Then, when the input shaft 1 is temporarily stopped in this state and the rotation direction thereof is switched, the rotation of the input shaft 1 is transmitted to the output shaft 2 via the other roller 15.

As described above, this rotation transmission device is strong against the radial load and is dynamic because the two-way clutch 10 does not mislock even if a large radial load is applied while the input shaft 1 is idling. It is highly reliable. Further, when the radial load is small, the amount of electricity supplied to the electromagnetic coil 53a is also small, so that there is no possibility that the power consumption will increase more than necessary.

FIG. 9 conceptually shows the usage state of the rotation transmission device described above. That is, in this used state, an input side torque meter is provided on the input shaft connected to the drive motor, an output side torque meter is provided on the output shaft connected to the drive object, and the torque of the input shaft detected by the input side torque meter is provided. Based on the torque of the output shaft detected by the torque meter on the output side, the electromagnetic clutch control device controls the amount of electricity applied to the electromagnetic clutch built in the rotation transmission device main body.

It should be considered that the embodiments disclosed this time are exemplary in all respects and not restrictive. The scope of the present invention is shown not by the above description but by the scope of claims, and it is intended that all modifications within the meaning and scope equivalent to the scope of claims are included.

For example, in the embodiment, a torque meter as a torque detecting means for control is provided on both the input shaft and the output shaft, but the torque detecting means is not limited to the torque meter and is provided on at least one of the input shaft and the output shaft. You just have to.

1 Input shaft 2 Output shaft 3 Housing 10 Two-way clutch 11 Outer ring 12 Cylindrical surface 13 Inner ring 14 Cam surface 15 Roller (engager)
16A Control cage 16B Rotation cage 20 Coil spring (elastic member)
22 Pillar part (control cage side)
26 Pillar part (rotary cage side)
27 Pocket 40 Torque cam (motion conversion mechanism)
50 Electromagnetic clutch 51 Armature 52 Rotor 53 Electromagnet

Claims (3)

An input shaft, an output shaft arranged coaxially with the input shaft, a two-way clutch for transmitting and blocking rotation from the input shaft to the output shaft, and a two-way clutch provided on the input shaft. Has an electromagnetic clutch that controls the engagement and disengagement of
The two-way clutch is rotatable around the outer ring provided at the shaft end of the output shaft, the inner ring provided at the shaft end of the input shaft and arranged radially inside the outer ring, and the input shaft. A pillar portion provided in each of the control cage and the rotation cage, which has a control cage and a rotation cage that are supported so as to be movable in the axial direction, and is provided between the inner circumference of the outer ring and the outer circumference of the inner ring. Are alternately arranged in the circumferential direction, and a pair of engaging elements and the pair of engaging elements are urged in a direction separated from each other in a pocket formed between adjacent pillars to form an inner circumference of the outer ring. And it incorporates an elastic member that stands by at a position that engages with the outer circumference of the inner ring.
The electromagnetic clutch has an armature connected to the control cage, a rotor fixed to the input shaft and facing the armature in the axial direction, and an electromagnet arranged to face the rotor, and by energizing the electromagnet. The control cage is moved in the axial direction, and the axial movement of the control cage is converted into the relative rotational motion of the control cage and the rotation cage in the direction in which the circumferential width of the pocket becomes smaller by the motion conversion mechanism. In a rotation transmission device that disengages the pair of engagers.
A torque detecting means is provided on at least one of the input shaft and the output shaft, and the amount of electricity applied to the electromagnet is linked to an increase or decrease in the torque value detected by the torque detecting means while the electromagnetic clutch is energized. A rotation transmission device characterized by performing control to increase or decrease the torque. The rotation transmission device according to claim 1, wherein the torque detecting means is a twist detection type torque meter. The rotation transmission device according to claim 2, wherein the twist detecting means of the torque meter is a strain gauge.

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