JPWO2010087446A1 - Clutch device - Google Patents

Abstract

To provide a small clutch device capable of quickly switching between rotation transmission and interruption in a certain direction and preventing an impact during rotation transmission. According to a clutch device (1), a load is applied to a sprag (4) against a biasing force of a ribbon spring (6) by a load applying device (10), and the sprag (4) is anti-locked. By tilting to the right, the engagement of the sprag (4) with the inner ring (2) and the outer ring (3) is released, and the inner ring (2) and the outer ring (3) rotate relative to each other in both rotational directions. Therefore, since the sprag (4) is tilted to transmit the rotation in a certain direction and the switching is cut off, the switching can be quickly performed as compared with the case where the switching is performed by moving the sprag (4). In addition, since the switching can be performed quickly, the inner ring (2) and the outer ring (3) do not idle during the period from when the rotation is blocked until the rotation is transmitted. Can be prevented. [Selection] Figure 2

Description

  The present invention relates to a clutch device that transmits rotation only in a certain direction, and more particularly, to a small clutch device that can quickly switch between rotation and blocking in a certain direction and prevent an impact during rotation transmission. It is.

  As a clutch device that transmits rotation only in a certain direction, for example, Patent Document 1 discloses that the sprag is disengaged from the inner ring and the outer ring by applying a biasing force to the sprag during low and medium speed rotation. The outer ring and the outer ring rotate relative to each other, and at the time of high-speed rotation, centrifugal force is applied to the sprag against the biasing force, so that the sprag is engaged with the inner ring and the outer ring, and the relative rotation between the inner ring and the outer ring is restricted. A sprag type one-way clutch is disclosed.

  However, the sprag type one-way clutch disclosed in Patent Document 1 cannot transmit rotation during low and medium speed rotations, and always transmits rotation in a fixed direction during high speed rotations. Switching between transmission and disconnection cannot be performed as required.

  On the other hand, in Patent Document 2, a wedge-shaped space is formed between the inner ring and the outer ring facing each other, and the retainer is pressed by a switch spring to hold the engaging element at the neutral position of the wedge-shaped space. The engagement of the engagement element with the outer ring is released and the inner ring and the outer ring rotate relative to each other, and a load greater than the holding force by the switch spring is applied to the cage to move the engagement element from the neutral position of the wedge-shaped space in the rotation direction. A rotation transmission device is disclosed in which an engagement element is engaged with an inner ring and an outer ring and relative rotation between the inner ring and the outer ring is restricted by being moved.

  Further, in Patent Document 3, a gap in which the facing interval changes is provided between the input shaft and the output shaft, and the retainer is pressed by a spring to hold the friction element at a portion having a large gap. The engagement of the friction element with the output shaft is released, the input shaft and the output shaft rotate relative to each other, and a load greater than the holding force by the spring is applied to the retainer to move the friction element to a portion with a small clearance in the rotational direction. Thus, there is disclosed a friction type one-way clutch on / off device in which a friction element engages with an input shaft and an output shaft to restrict relative rotation between the input shaft and the output shaft.

  According to these apparatuses disclosed in Patent Documents 2 and 3, rotation is transmitted in a certain direction and switching between interruption is performed by applying a load to the engagement element or the friction element and moving the engagement element or the friction element. be able to.

Japanese Utility Model Sho 62-151440 JP-A-2005-30443 JP-A-5-149351

  However, in the apparatuses disclosed in Patent Documents 2 and 3, in order to transmit rotation in a certain direction and switch between interruptions, it is necessary to move the engagement element or the friction element in the rotation direction. There is a problem that it takes time to move the friction element and time is required for switching.

  In addition, since switching takes time, the inner ring or the input shaft and the outer ring or the output shaft run idle until the rotation is transmitted from the state where the rotation is interrupted, and an impact is generated when the rotation is transmitted. was there.

  Furthermore, in order to move the engagement element or the friction element, it is necessary to apply a load more than the holding force by the spring to the cage or the retainer, which causes a problem that the apparatus is increased in size. Moreover, the energy loss for giving a load was also large.

  The present invention has been made to solve the above-described problems, and is a compact clutch device capable of quickly switching between rotation transmission and interruption in a certain direction and preventing an impact during rotation transmission. It is intended to provide.

Means for Solving the Problems and Effects of the Invention

  According to the clutch device of claim 1, a biasing force is applied to the sprag by the biasing member, and the sprag is tilted in the self-locking direction so that the engagement surface is in contact with the outer peripheral surface and the inner peripheral surface. A frictional force is generated at the contact point of the engagement surface with the inner peripheral surface, and a sprag is engaged with the inner ring and the outer ring by the self-locking angle, thereby restricting relative rotation between the inner ring and the outer ring in a constant rotation direction. On the other hand, a load is applied to the sprag against the urging force of the urging member by the load applying device, and the sprag is tilted in the anti-self-locking direction, so that the engagement of the sprag with the inner ring and the outer ring is released. The outer ring rotates relative to both rotation directions.

  As described above, according to the present invention, the sprag is tilted to transmit the rotation in a certain direction and the switching of the cutoff is performed, so that the switching is performed as compared with the case where the switching is performed by moving the sprag as in the prior art. Time can be shortened and switching can be performed quickly.

  In addition, since switching can be performed quickly, the inner ring and the outer ring do not run idle until the rotation is transmitted from the state where the rotation is interrupted as in the conventional case, preventing the shock during rotation transmission. There is an effect that can be done.

  Further, since the sprag is tilted to transmit rotation in a fixed direction and switch between cutoffs, the clutch device can be reduced in size without increasing the size of the device as in the prior art. is there.

  According to the clutch device of the second aspect, in addition to the effect produced by the clutch device of the first aspect, the load applying device is a load in which the rotational moment around the contact acting on the sprag by the biasing force of the biasing member becomes zero. In addition, since a load is applied to the sprag that causes the reaction force acting on the sprags in the normal direction of the outer peripheral surface and the inner peripheral surface to be 0 or less at the contact, a load larger than the biasing force of the biasing member is applied to the sprag. Without this, the engagement of the sprags with the inner ring and the outer ring can be released. Therefore, it is possible to reduce the necessary load to be applied to the sprags, and accordingly, there is an effect that the load applying device can be reduced in size.

  Further, in the case of a configuration in which a load larger than the urging force of the urging member is applied to the sprag, the load applying device increases in size and causes an increase in the size of the clutch device, so that the load applying device can be reduced in size. There is an effect that the clutch device can be miniaturized.

  According to the clutch device of the third aspect, in addition to the effect produced by the clutch device of the first or second aspect, the load applying device is configured such that the sprag is engaged with the inner ring and the outer ring and the shaft is rotated along with the rotation of the inner ring and the outer ring. In the state of revolving around the center, the sprag is a load where the sum of the rotational moment around the contact acting on the sprag due to centrifugal force and the rotational moment around the contact acting on the sprag due to the biasing force of the biasing member is zero. Therefore, there is an effect that the sprags can be reliably released from the inner ring and the outer ring even when the clutch device is transmitting rotation.

  According to the clutch device of the fourth aspect, in addition to the effect produced by the clutch device according to any one of the first to third aspects, the cage includes a holding portion that extends in the axial direction and holds the sprag, and a shaft. A load transmitting portion that extends in a direction that intersects the center direction and that transmits a load from the load applying device, and the load applying device applies a load to the sprags via the cage, so that a plurality of sprags are applied to the sprags at a time. The load can be applied, and there is an effect that the load can be efficiently applied to the sprag.

  In addition, since the load transmission part extends in the direction intersecting the axial direction, the dimension of the cage in the axial direction can be shortened compared to the case where the load transmission part extends in the axial direction. There is an effect that the clutch device can be miniaturized.

  According to the clutch device of the fifth aspect, in addition to the effect achieved by the clutch device of the fourth aspect, the load transmitting portion is formed in a gear shape, and the load is transmitted from the load applying device via the gear mechanism. The energy loss generated in the load transmission path from the load applying device to the cage can be reduced, and the load can be efficiently transmitted to the cage.

  According to the clutch device of the sixth aspect, the load transmitting portion is formed in a circular shape, and is pressed and braked by the operation of the load applying device. By braking the load transmitting portion and the cage, the sprag is prevented from tilting in the self-locking direction, and the engagement of the sprag to the inner ring and the outer ring is prevented. In this way, the sprag can be disengaged by braking the cage that is to rotate with the outer ring or the inner ring, so that the apparatus configuration can be simplified. Moreover, the energy loss which arises in the transmission path of the load from a load provision apparatus to a holder | retainer can be made small, and there exists an effect which can transmit a load to a holder | retainer efficiently.

  According to the clutch device of the seventh aspect, in addition to the effect exerted by the clutch device according to any one of the first to sixth aspects, the load applying device is constituted by an electric motor. Compared with the case of using a solenoid or the like, there is an effect that the structure of the load applying device can be simplified and the load applying device can be downsized.

  In addition, when the structure of the load applying device is complicated, the load applying device is enlarged and the size of the clutch device is increased. Therefore, the structure of the load applying device can be simplified and the load applying device can be downsized. If possible, the clutch device can be reduced in size.

  In addition, when the load applying device is configured to apply a load to the sprags via the cage, the cage rotates around the axis along with the rotation of the inner ring and the outer ring when the clutch device transmits the rotation. Therefore, the load applying device serves as the rotational resistance of the cage, but by configuring the load applying device with an electric motor, the rotational resistance of the cage can be reduced, and the inner ring and the outer ring can be rotated at high speed. On the other hand, since the cage does not rotate in a state where the rotation of the clutch device is interrupted, it is possible to apply a load to the sprag with a small drive energy by configuring the load applying device with an electric motor.

  According to the clutch device of the eighth aspect, in addition to the effect achieved by the clutch device of the seventh aspect, the load applying device is configured such that the inner ring and the outer ring apply load while the inner ring or the outer ring rotates in a self-locking direction with respect to the sprag. When the device rotates in the direction opposite to the direction in which the load is applied to the sprag by the device, it acts as a generator and is configured to be able to regenerate the generated electric power, so that the load applying device can save energy. .

  According to the clutch device of claim 9, in addition to the effect of the clutch device of claim 8, when the load applying device acts as a generator, the rotational moment around the contact acting on the sprag becomes zero. Since the load is applied to the sprag by the braking force of the load applying device, after applying the load to the sprag by the load applying device and rotating the inner ring and the outer ring relatively, by causing the load applying device to act as a generator, Even if the load applying device is not continuously driven, the state where the engagement of the sprags with the inner ring and the outer ring is released can be maintained. Therefore, there is an effect that further energy saving of the load applying device can be achieved.

It is the schematic diagram which showed typically the vehicle by which the clutch apparatus in one embodiment of this invention is mounted. It is the fragmentary sectional view which showed a part of power transmission device as sectional drawing. It is sectional drawing of the power transmission device in the III-III line of FIG. It is the elements on larger scale of the power transmission device which expanded and showed the part shown by IV of FIG. It is a graph which shows the electric power energy of the load provision apparatus in 2nd Embodiment. It is the fragmentary sectional view which showed a part of power transmission device in 3rd Embodiment as sectional drawing. It is the disassembled perspective view which showed the press part and the axial part as a perspective view. It is sectional drawing of the power transmission device in the VIII-VIII line of FIG. It is the elements on larger scale of the power transmission device which expanded and showed the part shown by IX of FIG.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings. First, a first embodiment will be described with reference to FIGS. FIG. 1 is a schematic diagram schematically showing a vehicle 100 on which a clutch device 1 according to an embodiment of the present invention is mounted. Note that arrows FB and LR in FIG. 1 indicate the front-rear direction and the left-right direction of the vehicle 100, respectively.

  First, a schematic configuration of the vehicle 100 will be described. As shown in FIG. 1, the vehicle 100 drives a front unit 110 that drives a front wheel 101 (left front wheel 101FL and right front wheel 101FR) and a rear wheel 102 (left rear wheel 102BL and right rear wheel 102BR). The rear unit 120 is configured to be able to drive the front wheel 101 and the rear wheel 102 independently of each other.

  The front unit 110 mainly includes an engine 111 and a motor 112 as a power source, and a power transmission device 113 that transmits the power of the engine 111 and the motor 112 to the front wheels 101. The front unit 110 supplies two powers of the engine 111 and the motor 112. The front wheel 101 can be driven by properly using it.

  The rear unit 120 mainly includes a motor 121 as a power source and a power transmission device 122 that transmits the power of the motor 121 to the rear wheel 102, and the motor 121 is controlled according to the driving torque of the front wheel 101. Thus, the rear wheels 102 can be driven so that the driving torques of the front wheels 101 and the rear wheels 102 can be distributed appropriately according to the traveling state of the vehicle 100.

  In addition, the power transmission device 122 of the rear unit 120 incorporates the clutch device 1 (see FIGS. 2 and 3) according to an embodiment of the present invention, and a motor 121 according to the traveling state of the vehicle 100. The power transmission path from the rear wheel 102 to the rear wheel 102 can be cut off.

  Next, the detailed configuration of the clutch device 1 will be described with reference to FIGS. 2 and 3. 2 is a partial cross-sectional view showing a part of the power transmission device 122 as a cross-sectional view, and FIG. 3 is a cross-sectional view of the power transmission device 122 taken along line III-III in FIG.

  As shown in FIGS. 2 and 3, the clutch device 1 includes an inner ring 2, an outer ring 3 surrounding the outer periphery of the inner ring 2, a plurality of sprags 4 disposed between the inner ring 2 and the outer ring 3, The retainer 5 that holds the sprags 4 is mainly provided so that the power of the motor 121 (see FIG. 1) can be transmitted to the rear wheel 102 (see FIG. 1) via the inner ring 2 and the outer ring 3.

  In the present embodiment, the power of the motor 121 is input to the outer ring 3, and the power of the motor 121 input to the outer ring 3 is transmitted to the rear wheel 102 via the inner ring 2. However, the present invention is not necessarily limited to this, and is configured such that the power of the motor 121 is input to the inner ring 2 and the power of the motor 121 input to the inner ring 2 is transmitted to the rear wheel 102 via the outer ring 3. Also good.

  The inner ring 2 is a member having a function of transmitting the power of the motor 121 to the rear wheel 102. As shown in FIGS. 2 and 3, the inner ring 2 includes an outer peripheral surface 2a having a circular cross section and rotates around the axis O. It is configured to be possible. The inner ring 2 in the present embodiment is formed in a substantially cylindrical shape, and is supported by a case 122a that forms an outline of the power transmission device 122 via a ball bearing B1, as shown in FIG.

  The outer ring 3 is a member responsible for the function of transmitting the power of the motor 121 to the rear wheel 102 together with the inner ring 2, and has a circular cross section facing the outer peripheral surface 2a of the inner ring 2 as shown in FIGS. An inner peripheral surface 3 a is provided, and the inner ring 2 is configured to be rotatable around the axis O similarly to the inner ring 2. In addition, the outer ring | wheel 3a in this Embodiment is formed in a substantially annular shape, and as shown in FIG. 2, it is supported by the inner ring | wheel 2 via the roller bearing B2.

  The sprag 4 is a member that bears a function for restricting the relative rotation between the inner ring 2 and the outer ring 3, and includes engagement surfaces 4a and 4b (see FIG. 4) that are in contact with the outer peripheral surface 2a and the inner peripheral surface 3a, respectively. As shown in FIG. 3, a plurality of elements are arranged at equal intervals in the circumferential direction between the outer peripheral surface 2a and the inner peripheral surface 3a.

  The sprag 4 is urged in the circumferential direction of the outer peripheral surface 2a and the inner peripheral surface 3a by a ribbon spring 6 (see FIG. 4). Here, the ribbon spring 6 will be described with reference to FIG. FIG. 4 is a partially enlarged cross-sectional view of the power transmission device 122 in which a portion indicated by IV in FIG. 3 is enlarged.

  The ribbon spring 6 applies a biasing force to the sprag 4 so that the sprag 4 is in the directions of arrows Si and So in FIG. 4 (hereinafter referred to as “self-locking direction”) so that the engagement surfaces 4a and 4b are in contact with the outer peripheral surface 2a and the inner peripheral surface 3a. 4), and is formed by applying a wave-like bending process to a metal material, and can apply a load P as an urging force to the sprag 4 using its elasticity. It is configured. However, the ribbon spring 6 may be constituted by a coil spring.

  By applying a load P to the sprag 4 by the ribbon spring 6, the sprag 4 tilts in the self-locking direction, and as a result, the engagement surfaces 4a and 4b come into contact with the outer peripheral surface 2a and the inner peripheral surface 3a. As shown in FIG. 4, frictional force is generated at the contact point A between the inner peripheral surface 3a and the engagement surface 4b and the contact point B between the outer peripheral surface 2a and the engagement surface 4a, and between the outer peripheral surface 2a and the inner peripheral surface 3a. Due to the displacement of the contacts A and B in the circumferential direction, the sprag 4 engages with the inner ring 2 and the outer ring 3 in a constant rotation direction, and the relative rotation between the inner ring 2 and the outer ring 3 is restricted.

  In the state where the engagement surfaces 4a and 4b are in contact with the outer peripheral surface 2a and the inner peripheral surface 3a, as shown in FIG. 4, each imaginary line connecting the contacts A and B and the axis O is at a predetermined angle. (Hereinafter referred to as “self-lock angle α”), and the condition for the sprag 4 to engage the inner ring 2 and the outer ring 3 is μ> tan α. However, the friction coefficient of each contact A and B is μ.

  Returning to FIG. 2 and FIG. The cage 5 is a member that holds the sprag 4 so as to be tiltable in the circumferential direction of the outer peripheral surface 2a and the inner peripheral surface 3a. As shown in FIGS. 2 and 3, the retainer 5a, the load transmitting portion 5b, It is configured with. The holding part 5 a is a part that holds the sprag 4 and extends in the direction of the axis O as shown in FIGS. 2 and 3 and holds the upper end side of the sprag 4.

  The load transmitting portion 5b is a portion to which a load is transmitted from a load applying device 10 described later, and is extended in a direction intersecting with the direction of the axis O as shown in FIG. Thereby, compared with the case where the load transmission part 5b is extended in the axial center O direction, the dimension of the axial direction O of the holder | retainer 5 can be shortened, and size reduction of the clutch apparatus 1 can be achieved.

  Further, as shown in FIG. 3, the load transmitting portion 5b is formed in a gear shape so that the load is transmitted from the load applying device 10 via a gear mechanism configured between the pinion 12 and the pinion 12 described later. It is configured. Thereby, the energy loss produced in the load transmission path from the load applying device 10 to the cage 5 can be reduced, and the load can be efficiently transmitted to the cage 5.

  According to the clutch device 1 configured as described above, a biasing force is applied to the sprag 4 by the ribbon spring 6, so that the sprag 4 is engaged with the inner ring 2 and the outer ring 3, and the inner ring 2 and the outer ring 3 are engaged. Relative rotation in a constant rotation direction is restricted. On the other hand, the engagement of the sprag 4 with the inner ring 2 and the outer ring 3 is released, so that the inner ring 2 and the outer ring 3 rotate relative to each other in both rotation directions. Thereby, rotation transmission in a fixed direction and switching between cutoffs can be performed.

  However, normally, since the urging force is applied to the sprag 4 by the ribbon spring 6 and the sprag 4 is engaged with the inner ring 2 and the outer ring 3, in order to release the engagement of the sprag 4 with the inner ring 2 and the outer ring 3. Needs to apply an external force to the sprag 4 against the urging force of the ribbon spring 6.

  Therefore, in order to forcibly release the engagement of the sprags 4 with the inner ring 2 and the outer ring 3, the clutch device 1 applies a load to the sprags 4 against the urging force of the ribbon spring 6 to attach the sprags 4. A load applying device 10 for tilting in the anti-self-locking direction (counter arrow Si, So direction in FIG. 4) is provided.

  As described above, the load applying device 10 is a device for applying a load to the sprag 4 against the urging force of the ribbon spring 6 and tilting the sprag 4 in the anti-self-locking direction. As shown, the actuator 11 and the pinion 12 are provided.

  The actuator 11 is a power source that generates a load to be applied to the sprag 4 and is configured by an electric motor (an AC motor or a DC motor) and is configured to be drivable by electric power supplied from a power source (not shown).

  Thus, since the load application apparatus 10 (actuator 11) is comprised with the electric motor, compared with the case where the load application apparatus 10 (actuator 11) comprises a cylinder, a solenoid, etc., for example, the load application apparatus 10 is comprised. In addition to simplifying the structure, the load applying device 10 can be downsized.

  In addition, when the structure of the load applying device 10 is complicated, the load applying device 10 is enlarged and the clutch device 1 is increased in size. However, the structure of the load applying device 10 is simplified and the load applying device 10 is small. If the size can be reduced, the clutch device 1 can be reduced in size.

  Further, in a state where the clutch device 1 is transmitting rotation, the cage 5 rotates around the axis O along with the rotation of the inner ring 2 and the outer ring 3, so that the load applying device 10 becomes the rotational resistance of the cage 5. However, by configuring the load applying device 10 (actuator 11) with an electric motor, the rotational resistance of the cage 5 can be reduced, and the inner ring 2 and the outer ring 3 can be rotated at high speed. On the other hand, in a state where the clutch device 1 is not rotating, the cage 5 does not rotate, so that the load applying device 10 (actuator 11) is configured by an electric motor to apply a load to the sprag 4 with a small drive energy. be able to.

  The pinion 12 is a member for transmitting the power of the actuator 11 to the cage 5, and is formed in a gear shape that meshes with the load transmission portion 5b of the cage 5, as shown in FIG. A gear mechanism is formed between them.

  When the power of the actuator 11 is transmitted to the cage 5 by the pinion 12, a load is applied to the sprag 4 via the cage 5. As described above, since the load applying device 10 applies a load to the sprags 4 via the cage 5, it is possible to apply a load to the plurality of sprags 4 at a time, and to efficiently apply a load to the sprags 4. Can do.

  According to the load applying device 10 configured as described above, by applying a load to the sprag 4 against the urging force of the ribbon spring 6, the sprag 4 is tilted in the anti-self-lock direction, and the inner ring 2 and The engagement of the sprag 4 with the outer ring 3 can be forcibly released.

Next, the load R applied to the sprag 4 by the load applying device 10 will be described with reference to FIG. As shown in FIG. 4, when the sprag 4 is engaged with the inner ring 2 and the outer ring 3, the sprag 4 is moved in a self-locking direction (counterclockwise in FIG. 4) by the load P applied to the sprag 4 by the ribbon spring 6. A rotation moment that tilts to) is generated. Accordingly, a pressing load acts on the contact A and the contact B. As a reaction force against the sprags 4, together with the reaction force F _A to the normal direction of the inner peripheral surface 3a acts at the contact A, acting reaction force F _B to the normal direction of the outer peripheral surface 2a at the contact B .

  Further, when the sprag 4 engages with the inner ring 2 and the outer ring 3 and revolves around the axis O along with the rotation of the inner ring 2 and the outer ring 3, centrifugal force K acts on the sprag 4. Since the straight line connecting the contact A and the contact B passes between the center of gravity of the sprag 4 (the point of action of the centrifugal force K) and the point of action of the load P, the centrifugal force K acts on the sprag 4 in the anti-self-locking direction. A rotational moment (clockwise in FIG. 4) is generated, and the pressing load of the sprag 4 due to the load P at the contact A and the contact B is reduced.

Here, considering a contact point B around the rotation moment _{M B} acting on the sprags 4, the load P in the sprag 4, load R, since the reaction force _{F A} and the centrifugal force K is _acting, M B = -lp · P + Lr · R + Ls · sinβ · F a -Lk · K ( hereinafter referred to as "formula (1)") and a. However, in the formula (1), the horizontal distance from the contact B to the point of application of load P Lp, the vertical distance from the contact B to the point of application of the load R Lr, the contact point B to the point of application of the reaction force F _A The straight line distance is Ls, the horizontal distance from the contact point B to the center of gravity of the sprag 4 is Lk, the angle formed by the virtual line connecting the contact points A and B and the virtual line connecting the contact point A and the axis O is β, In FIG. 4, the clockwise rotational moment around the contact point B is positive.

Moreover, given the contact A around a rotational moment _{M A} acting on the sprags 4, the load P in the sprag 4, load R, since the reaction force _{F B} and the centrifugal force K is _acting, M A = - (Lp -Ls · sinβ) · P- (Ls · cosβ-Lr) · R + Ls · sinβ · F B · cosα + Ls · cosβ · F B · sinα + (Ls · sinβ-Lk) · K = - (Lp-Ls · sinβ) · P- (Ls.cos.beta.-Lr) .R + Ls.Fp.sin (.alpha. +. Beta.) + (Ls.sin.beta.-Lk) .K (hereinafter referred to as "Expression (2)"). However, in Equation (2), the clockwise rotational moment around the contact A in FIG.

Here, if the rotational moment M _A ≧ 0 or the rotational moment M _B ≧ 0 and the reaction force F _A ≦ 0 or the reaction force F _B ≦ 0, the outer peripheral surface 2a of the inner ring 2 or the inner peripheral surface of the outer ring 3 3a and the sprag 4 do not come into contact with each other. As a result, μ≈0, and the engagement of the sprag 4 with the inner ring 2 and the outer ring 3 is released.

Therefore, the load R applied to the sprag 4 by the load applying device 10 in order to release the engagement between the outer peripheral surface 2a of the inner ring 2 and the sprag 4 at the contact B is M _B = 0 and F in the equation (1). It is obtained by calculating R that satisfies _A ≦ 0. Substituting these into equation (1) results in Lr · R ≧ Lp · P + Lk · K. Thereby, R ≧ (Lp · P + Lk · K) / Lr (hereinafter referred to as “Expression (3)”).

  As described above, the centrifugal force K causes the sprag 4 to generate a rotational moment in the anti-self-locking direction (clockwise in FIG. 4) to reduce the pressing load of the sprag 4 due to the load P at the contact B. R is required when centrifugal force K = 0. Substituting K = 0 into equation (3), R ≧ Lp / Lr · P. If Lp <Lr, then Lp / Lr <1. That is, the load R ≧ Lp / Lr · P <P, and the sprag 4 is disengaged from the inner ring 2 without applying a load larger than the urging force (load P) of the ribbon spring 6 to the sprag 4. be able to.

In addition, at the contact A, the load R applied to the sprag 4 by the load applying device 10 to release the engagement between the inner peripheral surface 3a of the outer ring 3 and the sprag 4 is M _A = 0 and It is obtained by calculating R such that F _B ≦ 0. Substituting these into equation (2) results in (Ls · cosβ−Lr) · R ≦ (Ls · sinβ−Lk) · K− (Lp−Ls · sinβ) · P. Accordingly, R ≧ {(Lp−Ls · sinβ) · P− (Ls · sinβ−Lk) · K} / (Ls · cosβ−Lr) (hereinafter referred to as “Expression (4)”).

  As described above, the centrifugal force K causes the sprag 4 to generate a rotational moment in the anti-self-locking direction (clockwise in FIG. 4) to reduce the pressing load of the sprag 4 due to the load P at the contact A. R is required when centrifugal force K = 0. Substituting K = 0 into Equation (4), R ≧ (Lp−Ls · sinβ) / (Ls · cosβ−Lr) · P. If (Lp−Ls · sinβ) <(Ls · cosβ−Lr), then (Lp−Ls · sinβ) / (Ls · cosβ−Lr) <1. That is, the load R ≧ (Lp−Ls · sinβ) / (Ls · cosβ−Lr) · P <P, and even if a load larger than the urging force (load P) of the ribbon spring 6 is not applied to the sprag 4, The engagement of the sprag 4 with the outer ring 3 can be released.

  In the load application device 10 according to the present embodiment, either the engagement of the inner ring 2 and the sprag 4 or the engagement of the outer ring 3 and the sprag 4 is released, that is, as shown in Expression (3). Load R ≧ (Lp · P + Lk · K) / Lr or load R ≧ {(Lp−Ls · sinβ) · P− (Ls · sinβ−Lk) · K} / (Ls · cosβ shown in Expression (4) -Lr) is applied to the sprag 4.

  Accordingly, the sprag 4 can be disengaged from the inner ring 2 and the outer ring 3 without applying a load larger than the urging force of the ribbon spring 6 to the sprag 4. The load R can be reduced, and the load applying device 10 can be downsized accordingly. As a result, the size of the clutch device 1 can be reduced.

  Further, in the load application device 10 in the present embodiment, the load R is applied to the sprag 4 so that the rotational moment M considering the centrifugal force K is 0, so that the clutch device 1 is in a state of transmitting the rotation. Also, the engagement of the sprag 4 with the inner ring 2 and the outer ring 3 can be reliably released.

  As described above, according to the clutch device 1, the sprag 4 is tilted to transmit the rotation in a certain direction and the switching is cut off. Therefore, the switching is performed in comparison with the case where the switching is performed by moving the sprag 4. Time can be shortened and switching can be performed quickly.

  Further, since the switching can be performed quickly, the inner ring 2 and the outer ring 3 do not idle during the period from when the rotation is blocked until the rotation is transmitted, and it is possible to prevent an impact during rotation transmission. it can.

  Furthermore, since the sprag 4 is tilted to transmit rotation in a fixed direction and switch between cutoffs, the clutch device 1 can be reduced in size without increasing the size of the device.

  Next, a second embodiment will be described with reference to FIG. The load application device 10 according to the second embodiment is configured such that an actuator 11 constituted by an electric motor acts as a generator and can regenerate electric power generated by the actuator 11. FIG. 5 is a graph showing the power energy of the load application device 10 according to the second embodiment. In FIG. 5, the horizontal axis indicates the rotational speed N (rotational speed) of the lower rotational speed compared with the inner ring 2 and the outer ring 3, and the vertical axis indicates the power energy of the load applying device 10 applied to the sprag 4. W (electric power) is shown. Hereinafter, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  In the load application device 10 according to the second embodiment, the inner ring 2 or the outer ring 3 rotates in the self-locking direction with respect to the sprag 4 while the inner ring 2 and the outer ring 3 are opposite to the load application direction to the sprag 4 by the load application device 10. When rotating in the direction, the actuator 11 acts as a generator, and the generated power can be regenerated. Thereby, energy saving of the load application apparatus 10 can be achieved.

  Specifically, as shown in FIG. 5, in a state where the rotational speed N is 0 to Na, the actuator 11 acts as an electric motor and applies electric power energy Wa to the sprag 4, while the rotational speed N is Na to Nmax ( In the state of the maximum number of revolutions), the application of power energy to the sprag 4 is stopped and the actuator 11 acts as a generator so that the brake energy Wa can be regenerated.

  In addition, since the structure for regenerating the electric power generated by the actuator 11 to a power source (not shown) is well known (for example, Japanese Patent Laid-Open No. 2000-217371), the description and illustration are omitted.

  Further, in the load applying device 10 in the second embodiment, when the actuator 11 acts as a generator, the load giving the rotational moment around the contact B acting on the sprag 4 becomes zero. 11) is configured to be applied to the sprag 4 by the brake force.

  Therefore, after the load is applied to the sprag 4 by the load applying device 10 and the inner ring 2 and the outer ring 3 are relatively rotated, the load applying device 10 (actuator 11) is caused to act as a power generator, so that the load applying device 10 is Even if the driving is not continued, the state where the engagement of the sprags 4 with the inner ring 2 and the outer ring 3 is released can be maintained. Therefore, further energy saving of the load applying device 10 can be achieved.

  Next, a third embodiment will be described with reference to FIGS. In the clutch device 201 according to the third embodiment, the load transmitting unit 205b is formed in a circular shape, and the load transmitting unit 205b is pressed and braked by the operation of the load applying device 210. Hereinafter, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. FIG. 6 is a partial cross-sectional view showing a part of the power transmission device 210 as a cross-sectional view, and FIG. 7 is an exploded perspective view showing the pressing part 220 and the shaft part 211 as a perspective view.

  The cage 205 is a member that holds the sprag 4 so as to be tiltable in the circumferential direction of the outer peripheral surface 2a and the inner peripheral surface 3a, and includes a holding portion 5a that holds the sprag 4 and a load transmitting portion 205b. ing. The holding part 5 a extends in the direction of the axis O and holds the upper end side of the sprag 4.

  The load transmitting portion 205b is a portion that is pressed and braked by the operation of a load applying device 210 described later, and extends from the holding portion 5a in a direction crossing the direction of the axis O as shown in FIG. It is formed in a shape. The outer peripheral edge part of the load transmission part 205b is provided with the taper part 205c formed in the taper shape toward the edge over the perimeter.

  The load applying device 210 is a device for applying a load to the sprag 4 against the urging force of the ribbon spring 6 and tilting the sprag 4 in the anti-self-locking direction. As shown in FIG. (Not shown), a shaft portion 211 rotated by an actuator, and a pressing portion 220 that is coaxially connected to the shaft portion 211 and presses the load transmitting portion 205b from both sides.

  The shaft portion 211 is a member configured to be rotatable by an actuator (not shown), one end (left side in FIG. 6) is connected to the actuator, and the other end is fixed to the housing 212 to be rotatable. . The actuator is constituted by an electric motor (AC motor or DC motor), and is configured to be drivable by electric power supplied from a power source (not shown). By driving the actuator, the shaft portion 211 is rotated, and the pressing portion 220 disposed on the shaft portion 211 is rotated. The pressing portion 220 is a portion that presses the load transmitting portion 205b from both sides and brakes the rotating load transmitting portion 205b, and is disposed on the other end side of the shaft portion 211.

  Hereinafter, the detailed configuration of the pressing portion 220 will be described with reference to FIG. The pressing portion 220 is formed in a disk shape, and the first pressing portion 230 in which the shaft portion 211 is inserted into the through hole 233, and the shaft portion 211 is inserted into the through hole 243 and slides in the axial direction of the shaft portion 211. It is configured to include a second pressing portion 240 that can be configured.

  The first pressing portion 230 is formed on one end surface 231 configured to face one end side (left side in FIG. 7) of the shaft portion 211 and the housing 212 (see FIG. 6). The other end surface 232 in contact with each other and a through hole 233 that penetrates the one end surface 231 and the other end surface 232 are configured.

  The second pressing portion 240 has an outer diameter substantially the same as that of the first pressing portion 230 and is configured to be able to contact one end surface 231 of the first pressing portion 230 and one end of the shaft portion 211. A cylindrical portion 242 extending from the contact portion 241 in the axial direction toward the side (left side in FIG. 7), and a through hole 243 penetrating the contact portion 241 and the cylindrical portion 242 are configured. .

  The cylindrical part 242 of the second pressing part 240 includes a notch part 244 formed in a substantially rectangular shape by notching a part in the circumferential direction on one end side (left side in FIG. 7). The notch portion 244 has a first receiving portion 244a and a second receiving portion 244b formed in the circumferential direction, and a third receiving portion 244c formed in the axial direction. On the other hand, the shaft portion 211 has a protrusion 213 formed in a direction intersecting the axial direction, and the protrusion 213 is provided in the notch 244.

  Here, since the second pressing portion 240 is configured to be slidable with respect to the shaft portion 211, when the shaft portion 211 is rotated in the direction of the arrow L and the protrusion 213 contacts the first receiving portion 244a. The first receiving portion 244a is pressed by the protrusion 213, and the second pressing portion 240 rotates in the arrow L direction. Further, when the shaft portion 211 is rotated in the arrow R direction and the projection 213 comes into contact with the second receiving portion 244b, the second receiving portion 244b is pushed by the projection 213, and the second pressing portion 240 is moved in the arrow R direction. Rotate. Further, since a gap is provided between the third receiving portion 244c of the notch portion 244 and the protrusion 213, the second pressing portion 240 is configured to be movable to one end side (left side in FIG. 7) of the shaft portion 211. However, when the third receiving portion 244c abuts against the protrusion 213, the further movement is restricted.

  The contact portion 241 of the second pressing portion 240 is formed such that a part of the outer peripheral edge portion on the one end surface 231 side of the first pressing portion 230 is formed in a belt shape having a predetermined width and is inclined in the length direction. The inclined surface 245 is provided. The inclined surface 245 is a portion that is pressed against one side surface of the load transmitting portion 205b. The inclined surface 245 extends from the one end 245a (the lower side in FIG. 7) to the other end 245b (the upper side in FIG. 7) along the circumferential direction of the contact portion 241 as viewed from the other end side (the right side in FIG. 7) of the shaft portion 211. It is configured so as to gradually descend and incline toward one end side (left side in FIG. 7) of the portion 211. Therefore, the distance between the one end surface 231 and the inclined surface 245 of the first pressing portion 230 is gradually increased from one end 245a (lower side in FIG. 7) to the other end 245b (upper side in FIG. 7). Compared with the thickness of the load transmitting portion 205b, the interval is narrow on the one end 245a side (lower side in FIG. 7) of the inclined surface 245 and wider on the other end 245b side (upper side in FIG. 7). Yes.

  Further, the inclined surface 245 corresponds to the shape of the tapered portion 205c of the load transmitting portion 205b (see FIG. 6) and extends from the center side to the outer edge of the contact portion 241 at one end side (left side in FIG. 7) of the shaft portion 211. It is formed so as to be gradually inclined toward the. Accordingly, a wide part of the inclined surface 245 can be pressed against the tapered portion 205c.

  Communication holes 246 and 234 are formed in the contact portion 241 and the first pressing portion 230 of the second pressing portion 240, respectively. The torsion coil spring 214 (see FIG. 6) has one end inserted and fixed in the communication holes 246 and 234 and the other end fixed to the housing 212. Since one end of the torsion coil spring 214 is inserted and fixed in the communication holes 246 and 234, when the second pressing portion 240 is rotated by rotating the shaft portion 211, the torsion coil inserted in the communication holes 246 and 234 The first pressing portion 230 is also rotated in the same direction by the spring 214. The torsion coil spring 214 is attached to the housing 212 and the pressing portion 220 so as to apply a biasing force that rotates the first pressing portion 230 and the second pressing portion 240 about the axis. The direction of the biasing force is the arrow T direction (the same direction as the arrow R direction).

  As a result, in the state where the rotation of the shaft portion 211 is restricted and the projection 213 is in contact with the first receiving portion 244a, the first pressing portion 230 and the urging force in the direction of the arrow T are applied. The second pressing part 240 cannot rotate in the direction of arrow R. However, as shown in FIG. 7, when the shaft portion 211 is rotated in the direction of arrow R to release the contact between the protrusion 213 and the first receiving portion 244a, the protrusion 213 is not pressed against the second receiving portion 244b. In addition, the first pressing portion 230 and the second pressing portion 240 are rotated in the arrow R direction by the biasing force in the arrow T direction of the torsion coil spring 214 (see FIG. 6). Further, when the shaft portion 211 is rotated in the direction of the arrow R and the protrusion 213 is pressed against the second receiving portion 244b, the first pressing portion 230 and the second pressing portion can be pressed without the biasing force of the torsion coil spring 214 in the arrow T direction. Part 240 is rotated in the direction of arrow R.

  Returning to FIG. The shaft portion 211 is provided with a compression coil spring 215 having one end fixed to one end side (left side in FIG. 6) of the shaft portion 211. The other end side (the right side in FIG. 6) of the compression coil spring 215 presses the end surface of the cylindrical portion 242 (see FIG. 7) of the second pressing portion 240, and the second pressing portion 240 becomes the first pressing portion 230. It is energized (in the direction of arrow S shown in FIG. 7).

  Next, with reference to FIG. 8, the relationship between the holder | retainer 205 and the press part 220 is demonstrated. 8 is a cross-sectional view of the power transmission device 122 taken along line VIII-VIII in FIG. As described above, the second pressing portion 240 has the inclined surface 245, and the distance between the inclined surface 245 and the one end surface 231 (see FIG. 7) of the first pressing portion 230 is compared with the thickness of the load transmitting portion 205b. The inclined surface 245 is wide at the one end 245a side and narrow at the other end 245b side. In addition, as shown in FIG. 8, the pressing portion 220 is disposed so that the tapered portion 205 c of the load transmitting portion 205 b is positioned on the inclined surface 245. Therefore, when the shaft portion 211 is rotated in the arrow R direction, the one end 245a side of the inclined surface 245 is pressed against the tapered portion 205c of the load transmitting portion 205b. Further, when the shaft portion 211 is rotated in the arrow L direction, the inclined surface 245 is separated from the tapered portion 205c of the load transmitting portion 205b.

  Here, when the sprag 4 is engaged with the inner ring 2 and the outer ring 3, power is transmitted to the inner ring 2 and the outer ring 3, and the outer ring 3 and the sprag 4 are rotated in the direction of the arrow (counterclockwise in FIG. 8). The holder 205 is also rotated in the direction of the arrow (counterclockwise in FIG. 8) with the rotation thereof. In such a state, by rotating the shaft portion 211 in the arrow L direction so that the inclined surface 245 is separated from the tapered portion 205c of the load transmitting portion 205b, the load transmitting portion 205b (the retainer 205) is free. Therefore, power is transmitted to the inner ring 2 and the outer ring 3.

  On the other hand, when the shaft portion 211 is rotated in the arrow R direction, the one end 245a side of the inclined surface 245 is pressed against the tapered portion 205c of the load transmitting portion 205b, and the inclined surface 245 and the one end surface 231 of the first pressing portion 230 (see FIG. 7), the tapered portion 205c of the load transmitting portion 205b is pressed. Thereby, the rotating load transmission part 205b (cage 205) is braked. In this case, the load R (see FIG. 4) is applied to the sprag 4 from the holding portion 5a (the holder 205) using the inertial force in a relative relationship with the outer ring 3. Accordingly, the sprag 4 tilts in the anti-self-lock direction (clockwise in FIG. 4), and the transmission of power by the sprag 4 is interrupted.

  Next, during the operation in which power is transmitted by engaging the sprag 4 with the inner ring 2 and the outer ring 3, the inner ring 2 and the outer ring 3 are stopped without using the inertia force to brake the cage 205. A description will be given of a case where the cage 205 is braked (inhibiting rotation) during starting. FIG. 9 is a partially enlarged cross-sectional view of the power transmission device 122 in which the portion indicated by IX in FIG. 8 is enlarged.

  As shown in FIG. 9, the holding portion 5 a (the holder 205) that holds the upper end side of the sprag 4 has a slight gap G between the sprag 4. Since there is a gap G, the sprag 4 held by the holding portion 5a can tilt in the self-lock direction (arrow Lo direction) and the anti-self-lock direction (arrow Fr direction). Therefore, as shown in FIG. 9 (a), when a gap is formed between the action point 4a of the load R (see FIG. 4) in the sprag 4 and the holding portion 5a, the outer ring 3 rotates counterclockwise at the start. Then (or when the inner ring 2 rotates clockwise), even if it is desired to interrupt the transmission of power by the sprag 4, the sprag 4 is engaged with the outer peripheral surface 2a and the inner peripheral surface 3a, and the power is transmitted by the sprag 4. Problem arises.

  In contrast, in the present embodiment, the second pressing portion 240 is provided with the notch portion 244 (see FIG. 7), and the first pressing portion 230 and the second pressing portion 240 are provided by the torsion coil spring 214 (see FIG. 6). An urging force in the direction of arrow T (see FIGS. 7 and 8) is generated. Furthermore, the urging | biasing force of the arrow S direction (refer FIG. 7) is produced in the 2nd press part 240 by the compression coil spring 215 (refer FIG. 6).

  Thereby, at the time of starting, first, the shaft portion 211 is slightly rotated in the direction of arrow R (see FIG. 8) to release the contact between the first receiving portion 244a of the notch portion 244 and the protrusion 213 (see FIG. 7). Then, even if the protrusion 213 is not pressed against the second receiving portion 244b, the first pressing portion 230 and the second pressing portion 240 are moved in the arrow R direction by the biasing force in the arrow T direction of the torsion coil spring 214 (see FIG. 6). Is rotated. As a result, the one end 245a of the inclined surface 245 gradually approaches the tapered portion 205c of the load transmitting portion 205b, and finally the tapered portion 205c of the load transmitting portion 205b is connected to the inclined surface 245 of the second pressing portion 240 and the first pressing portion 230. It is sandwiched between one end surface 231.

  Further, since the urging force in the direction of arrow S (see FIG. 7) is generated in the second pressing portion 240 by the compression coil spring 215 (see FIG. 6), the tapered portion 205c and the second pressing portion 240 of the load transmitting portion 205b. Friction occurs between As described above, the urging force in the direction of arrow T (see FIG. 8) by the torsion coil spring 214 (see FIG. 6) causes the load transmitting portion 205b (the retainer 205) to move in the direction of the arrow in FIG. As shown in FIG. 9B, the gap G between the action point 4a of the sprag 4 and the holding portion 5a (the holder 205) can be eliminated.

  Further, by rotating the shaft portion 211 and pressing the protrusion 213 against the second receiving portion 244b, even if the outer ring 3 rotates counterclockwise (or the inner ring 2 rotates clockwise), the sprag Since the holding portion 5a is pressed against the fourth action point 4a, the sprag 4 cannot be tilted in the self-locking direction (arrow Lo direction). As a result, the sprag 4 is prevented from engaging with the outer peripheral surface 2a and the inner peripheral surface 3a at the time of starting, and transmission of power by the sprag 4 can be reliably interrupted.

  The present invention has been described above based on the embodiments. However, the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed.

  For example, the numerical values given in the above embodiment are merely examples, and other numerical values can naturally be adopted.

  In the above embodiment, the case where the clutch device 1 is incorporated in the power transmission device 122 of the vehicle 100 has been described. However, the present invention is not necessarily limited to this. For example, other vehicles (locomotives, passenger cars, freight cars, Naturally, it can be incorporated into a power transmission device such as a traveling device, a working device, and a machine tool of a special vehicle.

  In the first embodiment, the case where the actuator 11 is configured by an electric motor (AC motor or DC motor) has been described. However, the present invention is not necessarily limited to this, and other power sources can naturally be employed. is there. Examples of other power sources include a hydraulic motor, a pneumatic cylinder, a hydraulic cylinder, an AC solenoid, and a DC solenoid.

  Here, when the actuator 11 is configured by a solenoid, the actuator 11 is not limited to the case where a load is applied to the sprag 4 by a gear mechanism or the like. For example, the actuator 11 is configured to apply a load to the sprag 4 using an electromagnetic force. Also good.

1,201 Clutch device 2 Inner ring 2a Outer peripheral surface 3 Outer ring 3a Inner peripheral surface 4 Sprags 4a, 4b Engagement surface 5, 205 Cage 5a Holding unit 5b, 205b Load transmitting unit 6 Ribbon spring (biasing member)
10,210 Load applying device 11 Actuator (part of load applying device, electric motor)
A, B Contact O Axis center α Self-locking angle

Claims (9)

An inner ring having an outer peripheral surface having a circular cross section and configured to be rotatable around an axis, and an inner ring having a circular cross section facing the outer peripheral surface of the inner ring and configured to be rotatable about the axis Each of the imaginary lines connecting the respective contact points of the engaging surface to the outer peripheral surface and the inner peripheral surface and the shaft center. A plurality of sprags arranged in the circumferential direction between the outer peripheral surface and the inner peripheral surface so that the angle formed is a constant self-locking angle, and the sprags are arranged around the outer peripheral surface and the inner peripheral surface. A retainer that can be tilted in a direction, and a biasing force applied to the sprag so that the sprag is tilted in the circumferential self-locking direction so that the engagement surface is in contact with the outer peripheral surface and the inner peripheral surface. An urging member for causing the urging member to The sprag is tilted in the self-lock direction so that a biasing force is applied to the plug so that the engagement surface is in contact with the outer peripheral surface and the inner peripheral surface, thereby generating a frictional force at the contact and the self-lock angle. In the clutch device in which the sprag is engaged with the inner ring and the outer ring to restrict relative rotation of the inner ring and the outer ring in a constant rotation direction.
A load applying device that applies a load to the sprags against the urging force of the urging member to tilt the sprags in a direction opposite to the self-locking direction and in a circumferential anti-self-locking direction; ,
A load is applied to the sprag against the urging force of the urging member by the load applying device, and the sprag is tilted in the anti-self-locking direction, so that the sprag is engaged with the inner ring and the outer ring. The clutch device, wherein the clutch is released and the inner ring and the outer ring rotate relative to each other in both rotation directions.   The load applying device is a load in which a rotational moment around the contact acting on the sprag by the urging force of the urging member becomes zero, and the outer peripheral surface and the inner peripheral surface are applied to the sprag at the contact. The clutch device according to claim 1, wherein a load is applied to the sprags so that a reaction force acting in a linear direction is 0 or less.   In the state in which the sprag is engaged with the inner ring and the outer ring and revolves around the axis with the rotation of the inner ring and the outer ring, the load applying device acts on the sprag by centrifugal force. 3. The load according to claim 1, wherein a load is applied to the sprags, wherein a sum of a rotational moment around the rotation moment and a rotation moment around the contact acting on the sprag by the biasing force of the biasing member is zero. The clutch device as described. The retainer includes a holding portion that extends in the axial direction and holds the sprag, and a load transmission portion that extends in a direction intersecting the axial direction and transmits a load from the load applying device. ,
The clutch device according to any one of claims 1 to 3, wherein the load applying device applies a load to the sprags via the cage.   The clutch device according to claim 4, wherein the load transmitting portion is formed in a gear shape, and a load is transmitted from the load applying device by a gear mechanism.   The clutch device according to claim 4, wherein the load transmitting portion is formed in a circular shape and is pressed and braked by the operation of the load applying device.   The clutch device according to claim 1, wherein the load applying device is configured by an electric motor.   The load applying device is configured such that the inner ring and the outer ring rotate in the self-locking direction with respect to the sprag while the inner ring and the outer ring rotate in a direction opposite to the load applying direction to the sprag by the load applying device. The clutch device according to claim 7, wherein the clutch device is configured to be capable of regenerating electric power generated while acting as a generator.   When the load applying device acts as a generator, a load with a rotational moment around the contact acting on the sprag being zero is applied to the sprag by the braking force of the load applying device. The clutch device according to claim 8.

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