JP2011231828A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission device whose construction can be simplified by reducing the number of part items and whose switching mechanism and control can also be simplified.SOLUTION: First sprags 11 and second sprags 21 are retained by a retainer 30 movably in the circumferential direction of an inner ring 2 and an outer ring 3. The first sprags 11 are biased by a first biasing member in the circumferential anti-locking direction. Also, the first sprags 11 are moved in a locking direction by being provided with a load by a load providing device 40, resulting in the engagement surfaces respectively engaged with the inner ring 2 and the outer ring 3, while the engagements between the engagement surfaces of the second sprags 21 and the inner ring 2 and the outer ring 3 are released. Switching the first sprags 11 from an idle state to a locked state can correctively be carried out by providing the retainer 30 with a load by a load transmission device 40, whereby the constitution of the device can be simplified by reducing the number of the part items and the switching mechanism and control can be simplified.

Description

  The present invention relates to a power transmission device that can reduce the number of parts, simplify the device configuration, and simplify the switching mechanism and control.

  As a clutch device (power transmission device) configured to include a pair of one-way clutches and capable of switching the transmission direction of power, for example, one disclosed in Patent Document 1 is known. In the clutch device (power transmission device) disclosed in Patent Document 1, the relative rotation between the outer ring and the shaft is locked by an engagement element constituting a one-way clutch. The lock state of the relative rotation is released by operating the operation lever and moving the engagement / disengagement operation member holding the engagement element, and is switched to the idling state.

Japanese Patent Laid-Open No. 10-323257

  However, in the clutch device (power transmission device) disclosed in Patent Document 1, the engagement / disengagement operation member and the operation lever are provided for each one-way clutch, and two engagement / disengagement operation members are arranged in parallel between the outer ring and the shaft. It had been. Therefore, an operation lever is also provided for each engaging / disengaging operation member. As described above, since the engagement / disengagement operation member and the operation lever are provided for each one-way clutch, there is a problem that the number of parts is increased and the apparatus configuration is complicated.

  Further, when switching between the locked state and the idling state, it has been necessary to operate the operation lever separately for each one-way clutch to move the engagement / disengagement operation member separately. When operating the operation levers separately, it is necessary to prevent the pair of one-way clutches from being double-engaged, which complicates the control of the switching mechanism and the operation lever.

  The present invention has been made to solve the above-described problems, and an object thereof is to provide a power transmission device that can reduce the number of parts, simplify the device configuration, and simplify the switching mechanism and control. .

Means for Solving the Problems and Effects of the Invention

  According to the power transmission device of the first aspect, the first clutch transmits the power from one of the second member or the first member to the second member or the other of the first member so as to be cut off, while the second member or the first member. Transmission of power from the other one member to one of the second member or the first member is interrupted, and power is transmitted from the second member or the other of the first member to one of the second member or the first member by the second clutch. On the other hand, power transmission from one of the second member or the first member to the other of the second member or the first member is interrupted. The first engaging element and the second engaging element are held by the retainers of the first clutch and the second clutch so as to be movable in the circumferential direction of the predetermined surface and the opposing surface. The first urging member is urged in the circumferential anti-lock direction. Further, the first engaging element is engaged with the predetermined surface and the opposing surface by being applied with a load by the load applying device and being moved in the locking direction. At this time, since the engagement between the engagement surface of the second engagement element and the predetermined surface and the opposing surface is released, the relative rotation between the first member and the second member is restricted by the first engagement element. . That is, the first engagement element is switched from the idling state to the locked state, and the rotation is transmitted from the first member to the second member via the first engagement element.

  Thus, since the retainer collectively holds the first engagement element and the second engagement element, it is not necessary to provide a retainer for each clutch, and there is an effect that the number of parts can be reduced. In addition, since the first engagement element can be switched from the idling state to the locked state collectively by applying a load to one cage by the load transmission device, the device configuration is simplified and the switching is performed. There is an effect that the mechanism and control can be simplified.

  According to the power transmission device of the second aspect, one of the first member and the second member includes an inner ring that has an outer peripheral surface having a circular cross section and is configured to be rotatable about an axis. The other of the second members includes an outer ring that has an inner peripheral surface with a circular cross section facing the outer peripheral surface of the inner ring and is configured to be rotatable about the axis. There is an effect that the cross-sectional shape can be simplified to a circular shape. Further, since the first engaging element and the second engaging element are constituted by sprags whose engaging surfaces can be engaged with the outer peripheral surface and the inner peripheral surface, the sprags (first engaging member and second engaging member) are moved. (Tilting) can be used to transmit rotation in a certain direction and switch between cutoffs.

  Here, when the second engagement element is engaged with the inner ring and the outer ring and power is transmitted via the second engagement element, the inner ring and the outer ring are elastically deformed by the second engagement element engaged with the inner ring and the outer ring. And the distance between the inner ring and the outer ring may be slightly increased. However, since the first engagement element is biased in the anti-lock direction, the first engagement element can be prevented from being caught in the inner ring and the outer ring.

  On the other hand, the first engagement element can be engaged with the inner ring and the outer ring by moving (tilting) the first engagement element in the locking direction by the load applying device. As a result, when the first engagement element is engaged with the inner ring and the outer ring and power is transmitted through the first engagement element, the inner engagement and the outer ring are elastically deformed by the first engagement element engaged with the inner ring and the outer ring. And the distance between the inner ring and the outer ring may be slightly increased. In this case, when the second engagement element is urged in the anti-lock direction by the second urging member, the second engagement element is prevented from being caught in the inner ring and the outer ring.

  However, when the second engagement element is urged in the locking direction by the second urging member, the second engagement element may be caught in the inner ring and the outer ring. When the second engagement element is engaged with the inner ring and the outer ring, the distance between the inner ring and the outer ring is widened by the second engagement element engaged with the inner ring and the outer ring when power is transmitted through the second engagement element. . When this interval becomes equal to or greater than the interval between the inner ring and the outer ring when the first engagement element is engaged, the first sprag is biased in the anti-lock direction, so that the first engagement element is bitten. Move (tilt) in the opposite direction. As a result, the first engagement element can be prevented from being bitten by the inner ring and the outer ring. As described above, in addition to the effect of the first aspect, it is possible to prevent the first engagement element and the second engagement element from being bitten by the inner ring and the outer ring, and to prevent the switching of the transmission direction of power.

  According to the power transmission device of the third aspect, the first biasing member biases the first engagement element so that a gap is formed between one of the outer peripheral surface or the inner peripheral surface and one of the engagement surfaces. Therefore, friction between the outer peripheral surface or the inner peripheral surface and the engagement surface of the first sprag can be eliminated. Thereby, in addition to the effect of Claim 2, there exists an effect which can suppress the energy loss by friction.

  According to the power transmission device of the fourth aspect, the reaction force acting on the first engaging element from the other of the outer peripheral surface or the inner peripheral surface at the contact point where the other of the outer peripheral surface or the inner peripheral surface is in contact with the other of the engaging surface is: Since the direction of the component force component in the load direction acting on the first engagement element by the load application device is the same direction as the locking direction of the first engagement element, when a load is applied to the first engagement element by the load application device, The engagement surface is prevented from slipping on the outer peripheral surface or the inner peripheral surface, and the first engagement element can be reliably moved (tilted) around that. Thereby, in addition to the effect of Claim 2 or 3, it is possible to reliably engage the two engagement surfaces of the first engagement element with the outer peripheral surface and the inner peripheral surface by applying a load from the load applying device. It is possible to transmit power with certainty.

  According to the power transmission device of the fifth aspect, the first engaging elements are disposed at equal intervals between the outer peripheral surface and the inner peripheral surface and are in contact with each other by being tilted in the anti-lock direction. When the first engagement element is tilted to the abutting position, the first engagement elements restrain each other. By tilting the first engagement element until they are constrained to each other, a sufficient gap can be secured between one of the outer peripheral surface or the inner peripheral surface and one of the engagement surfaces. As a result, in addition to the effect of any one of claims 2 to 4, when the inner ring and the outer ring rotate relative to each other, one of the outer peripheral surface or the inner peripheral surface and one of the engaging surfaces comes into contact with each other. Therefore, it is possible to prevent the first engagement element from being engaged and the relative rotation from being restricted.

  Further, since the first engaging elements biased in the anti-locking direction are restrained when tilted to a position where they are brought into contact with each other, the first engaging elements are prevented from being inclined more than a predetermined angle. By setting the predetermined angle within a range in which the first engagement element can be moved by the retainer, the first engagement element can be moved by the retainer without employing a member for regulating the position of the retainer. The number of parts can be reduced, and the apparatus configuration can be simplified.

  According to the power transmission device of claim 6, since the load applying device is constituted by an electric motor, in addition to the effect of any one of claims 1 to 5, the load applying device is constituted by a cylinder, a solenoid or the like. In comparison, the structure of the load applying device can be simplified, and the load applying device can be reduced in size, and the power transmission device can be reduced in size.

  Further, in the case where the load applying device is configured to apply a load to the first engagement element via the cage, in a state where the power transmission device is transmitting rotation, the cage is rotated along with the rotation of the inner ring and the outer ring. Since it rotates around the center, the load applying device becomes 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 power transmission device is interrupted, a load can be applied to the first engagement element with an electric motor having a small driving energy, energy loss can be suppressed, and the power transmission device can be suppressed. There is an effect that can be reduced in size.

It is the schematic diagram which showed typically the internal structure of the vehicle by which the power transmission device in 1st Embodiment of this invention is mounted. It is the schematic diagram which showed typically the internal structure of the transmission device with which the power transmission device was integrated. It is the axial direction sectional view which showed a part of transmission device as sectional drawing. It is sectional drawing of the power transmission device in the IV-IV line of FIG. (A) is a schematic diagram of the first clutch in which the first sprag is tilted in the anti-lock direction, and (b) is a schematic diagram of the first clutch in which the first sprag is tilted in the lock direction. It is sectional drawing of the power transmission device in the VI-VI line of FIG. It is a partial exploded three-dimensional view of a power transmission device. It is a schematic diagram of the 1st sprag tilted to the antilock direction. (A) is the schematic diagram which showed typically the internal structure of the power transmission device at the time of normal driving | running | working, (b) is the schematic diagram which showed typically the internal structure of the power transmission device at the time of up-shifting is there. (A) is the schematic diagram which showed typically the internal structure of the power transmission device at the time of coast driving | running | working, (b) is the schematic diagram which showed typically the internal structure of the power transmission device at the time of downshifting is there. It is the schematic diagram which showed typically the internal structure of the vehicle by which the power transmission device in 2nd Embodiment is mounted. (A) is the schematic diagram which showed typically the internal structure of the power transmission device at the time of normal driving | running | working, (b) is the schematic diagram which showed typically the internal structure of the power transmission device at the time of coast driving | running | working. is there. It is the schematic diagram which showed typically the internal structure of the vehicle by which the power transmission device in 3rd Embodiment is mounted. (A) is the schematic diagram which showed typically the internal structure of the power transmission device at the time of normal driving | running | working, (b) is the internal structure of the power transmission device at the time of reducing the rotation speed of an input shaft in normal driving | running | working. It is the schematic diagram which showed typically. (A) is the schematic diagram which showed typically the internal structure of the power transmission device at the time of reverse drive, (b) typically shows the internal structure of the power transmission device at the time of reducing the rotation speed of the input shaft at the time of reverse drive. It is the schematic diagram shown. (A) is the schematic diagram which showed typically the internal structure of the power transmission device in the comparative example in which motive power is input into the outer ring and output from the inner ring, and (b) is the outer ring when the motive power is input to the inner ring. It is the schematic diagram which showed typically the internal structure of the power transmission device output from.

  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 the internal structure of a vehicle 100 on which the power transmission device 1 according to the first embodiment of the present invention is mounted. As shown in FIG. 1, the vehicle 100 includes a front wheel 101 (left front wheel 101FL and right front wheel 101FR), a rear wheel 102 (left rear wheel 102BL and right rear wheel 102BR), and an engine 103 as a power source. The motor 104 and the engine 103 and the transmission device 110 that transmits the power of the motor 104 to the rear wheel 102 are mainly provided, and the rear wheel 102 can be driven by the power of the engine 103 and the motor 104. The transmission device 110 includes a power transmission device 1 configured to be able to switch the power of the engine 103 and the motor 104, and a transmission device 111 that outputs the power input from the power transmission device 1 at a predetermined gear ratio (see FIG. 2). ) And is mainly configured.

  Next, the detailed configuration of the power transmission device 1 will be described with reference to FIGS. FIG. 2 is a schematic view schematically showing the internal structure of the transmission device 110, and FIG. 3 is an axial sectional view showing a part of the transmission device 110 as a cross-sectional view. 4 is a cross-sectional view of the power transmission device 1 (first clutch 10) taken along line IVb-IVb of FIG. 3, and FIG. 5 (a) shows the first clutch 10 in which the first sprag 11 is tilted in the anti-lock direction. FIG. 5B is a schematic diagram of the first clutch 10 in which the first sprag 11 is tilted in the locking direction. 6 is a cross-sectional view of the power transmission device 1 (second clutch 20) taken along the line Va-Va in FIG. 3, and FIG. 7 is a partial exploded view of the power transmission device 1. In FIG. 6, for the sake of simplification of the drawing, the illustration of the first clutch (the back side in FIG. 6) provided in parallel with the second clutch 20 is omitted.

  As shown in FIG. 2, the power transmission device 1 includes an inner ring 2, an outer ring 3 that surrounds the outer periphery of the inner ring 2, a first clutch 10 and a second clutch 20 that switch transmission of power between the outer ring 3 and the inner ring 2. It is configured with.

  The inner ring 2 is a member that functions as a first member for transmitting the driving force from the engine 103 and the motor 104 to the rear wheel 102, and has a circular cross section as shown in FIGS. The outer peripheral surface 2a (predetermined surface) is provided so as to be rotatable around the axis O. Note that the inner ring 2 in the present embodiment is formed in a substantially cylindrical shape, and is supported by a case 110a that forms an outline of the transmission device 110 via a ball bearing B1, as shown in FIG. The driving force from the engine 103 and the motor 104 is input to the inner ring 2 from the input shaft 112 via the main clutch 113 (see FIG. 2).

  The outer ring 3 is a member having a function as a second member for transmitting the driving force to the rear wheel 102 (see FIG. 2) together with the inner ring 2, and as shown in FIGS. 4 and 6, the outer peripheral surface of the inner ring 2 An inner peripheral surface 3 a (opposing surface) having a circular cross section facing 2 a is provided, and is configured to be rotatable around an axis O in the same manner as the inner ring 2. Note that the outer ring 3 in the present embodiment is formed in a substantially annular shape, and is supported by the inner ring 2 via a roller bearing B2, as shown in FIG. The outer ring 3 is connected to an output shaft 114 (see FIG. 2), and the rotation of the outer ring 3 is transmitted to the transmission 111.

  As shown in FIG. 2, the transmission 111 is composed of a plurality of gear pairs, and in this embodiment, is configured as a part of a dog clutch type automatic control type manual transmission (AMT). The power transmitted to the transmission 111 is configured to be transmitted to the rear wheel 102 (drive wheel) via the differential device 115.

  The first clutch 10 of the power transmission device 1 is a device that transmits power from the inner ring 2 to the outer ring 3 so as to be cut off, while interrupting transmission of power from the outer ring 3 to the inner ring 2, as shown in FIGS. 2 and 3. In addition, a first sprag 11 serving as a first engagement element that engages with the inner ring 2 and the outer ring 3 is provided. The second clutch 20 is a device that transmits power from the outer ring 3 to the inner ring 2 while interrupting transmission of power from the inner ring 2 to the outer ring 3. As shown in FIGS. 2 and 3, the second clutch 20 is connected to the inner ring 2 and the outer ring 3. A second sprag 21 as a second engaging element to be engaged is provided.

  First, the first clutch 10 will be described. The first sprags 11 are members that have a function of regulating the relative rotation between the inner ring 2 and the outer ring 3, and are respectively provided on the outer peripheral surface 2 a of the inner ring 2 and the inner peripheral surface 3 a of the outer ring 3 as shown in FIG. 4. Engaging surfaces 11a and 11b are in contact with each other, and a plurality of them are arranged at equal intervals in the circumferential direction between the outer peripheral surface 2a and the inner peripheral surface 3a. Further, the first sprag 11 has a groove portion 11d formed on two side surfaces 11c (see FIG. 7) connecting the two engagement surfaces 11a and 11b. The groove 11d is a part where a first urging member 12 described later is mounted.

  The retainer 30 is a member that holds the first sprag 11 and the second sprag 21 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. A holding portion 31 that is annularly extended in the direction and a load transmission portion 32 that extends from the holding portion 31 in a direction that intersects the direction of the axis O are configured.

  The holding portion 31 is a portion that holds the first sprag 11 and the second sprag 21, and is disposed around the outer peripheral surface 2 a of the inner ring 2 as shown in FIGS. 3 and 4. Moreover, as shown in FIG. 7, the holding | maintenance part 31 is provided with two or more hole parts 31a formed at equal intervals over the circumferential direction. A portion of the first sprag 11 (engagement surface 11a side) located on the inner ring 2 side is inserted into the hole 31a, and the two front and rear surfaces 11e and the hole communicating the two engagement surfaces 11a and 11b of the first sprag 11 A gap of an appropriate size is formed between the portion 31a. Thereby, the 1st sprag 11 is hold | maintained by the holding | maintenance part 31 between opposition of the outer peripheral surface 2a and the internal peripheral surface 3a so that it can tilt largely in the circumferential direction.

  The load transmitting portion 32 is a portion to which a load is transmitted from a load applying device 40 described later, and extends in a direction intersecting with the direction of the axis O as shown in FIGS. Thereby, compared with the case where the load transmission part 32 is extended in the axial center O direction, the dimension of the axial direction O of the holder | retainer 30 can be shortened, and size reduction of the power transmission device 1 can be achieved.

  Further, as shown in FIG. 4, the load transmission unit 32 is formed in a gear shape, and a load is transmitted from the load applying device 40 via a gear mechanism configured between the pinion 42 and the pinion 42 described later. It is configured. Thereby, the energy loss which arises in the transmission path of the load from the load application apparatus 40 to the holder | retainer 30 can be made small, and a load can be transmitted to the holder | retainer 30 efficiently.

  As shown in FIG. 4, the first urging member 12 is a member that is formed by an annular coil spring and applies an urging force in the direction of expanding the diameter. Here, the first sprag 11 urged by the urging member 12 will be described with reference to FIG. In addition, the outer ring | wheel 3 shall rotate in the arrow T direction (counterclockwise) of FIG.

  As shown in FIG. 5A, the first biasing member 12 is mounted in the groove portion 11d of the first sprag 11, and the first sprag 11 is engaged by applying a biasing force in the direction of expanding the diameter. The first sprag 11 is tilted in the direction of arrow S by using the frictional force generated on the surface 11b and the inner peripheral surface 3a of the outer ring 3. As a result, the engagement surface 11a of the first sprag 11 is tilted in the counter arrow Li direction in FIG. 5 (hereinafter referred to as “anti-lock direction”). As a result, as shown in FIG. 5, a gap is generated between the outer peripheral surface 2a and the engaging surface 11a. Thereby, the inner ring 2 and the outer ring 3 can be rotated relative to each other, and the transmission of power from the outer ring 3 to the inner ring 2 is interrupted. Further, since a gap is generated between the outer peripheral surface 2a and the engagement surface 11a, friction between the outer peripheral surface 2a and the engagement surface 11a of the first sprag 11 can be eliminated, and energy loss due to friction can be suppressed.

  Further, there is an appropriate size between the two front and rear surfaces 11e (see FIG. 7) connecting the two engaging surfaces 11a and 11b of the first sprag 11 and the hole 31a formed in the holding portion 31. Since a gap is formed, as shown in FIG. 5A, the first sprags 11 abut against each other by being largely tilted in the anti-lock direction. When the first sprags 11 are tilted to positions where they abut against each other, the first sprags 11 are restrained from each other. Thereby, the clearance gap between the outer peripheral surface 2a and the engagement surface 11a is fully securable. As a result, when the inner ring 2 and the outer ring 3 rotate relative to each other, the outer peripheral surface 2a and the engaging surface 11a come into contact with each other, and the first sprag 11 is unintentionally engaged with the outer peripheral surface 2a and the inner peripheral surface 3a. In combination, the relative rotation of the inner ring 2 and the outer ring 3 can be prevented from being restricted.

  Further, when the first sprags 11 urged in the anti-lock direction by the first urging member 12 are tilted to a position where they abut against each other, they restrain each other, and the first sprags 11 are tilted more than the angle at which they abut each other. It is prevented. By setting the angle within a range in which the first sprag 11 can be moved by the holding unit 31 (the holding unit 30), the first holding unit 30 does not employ a member or the like that restricts the position of the holding unit 30. The sprag 11 can be moved. As a result, the number of parts can be reduced and the apparatus configuration can be simplified.

  Moreover, the groove part 11d is each formed in the two side surfaces 11c (refer FIG. 7) which connects the two engaging surfaces 11a and 11b of the 1st sprag 11, and the 1st biasing member 12 is mounted | worn with these groove parts 11d. Therefore, the first sprag 11 can be tilted in the anti-lock direction with a good balance by the biasing force of the first biasing member 12.

  According to the first clutch 10 described above, in order to engage the first sprag 11 with the inner ring 2 and the outer ring 3, it is necessary to apply an external force to the first sprag 11 against the urging force of the first urging member 12. There is. Therefore, the first clutch 10 is provided with a load applying device 40 (see FIGS. 2 to 4).

  The load applying device 40 applies a load to the first sprag 11 against the urging force of the first urging member 12, and the first sprag 11 is in the direction indicated by the arrow Li in FIG. 5 (hereinafter referred to as “lock direction”). As shown in FIGS. 2 to 4, the device includes an actuator 41 and a pinion 42. The actuator 41 is a power source that generates a load to be applied to the first sprag 11, is configured 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). .

  Thus, since the load applying device 40 (actuator 41) is configured by an electric motor, for example, the load applying device 40 is compared with a case where the load applying device 40 (actuator 41) is configured by a cylinder, a solenoid, or the like. In addition to simplifying the structure, the load applying device 40 can be reduced in size, and the power transmission device 1 can be reduced in size.

  Further, in a state where the first clutch 10 is transmitting rotation, the cage 30 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 40 has the rotational resistance of the cage 30. However, by configuring the load applying device 40 (actuator 41) with an electric motor, the rotational resistance of the cage 30 can be reduced, and the inner ring 2 and the outer ring 3 can be rotated at high speed. On the other hand, since the retainer 30 does not rotate when the first sprag 11 does not revolve, it is possible to apply a load to the first sprag 11 with a small drive energy by configuring the load applying device 40 (actuator 41) with an electric motor. it can.

  The pinion 42 is a member for transmitting the power of the actuator 41 to the cage 30, and is formed in a gear shape that meshes with the load transmission portion 32 of the cage 30, as shown in FIG. A gear mechanism is formed between them. When the power of the actuator 41 is transmitted to the cage 30 by the pinion 42, a load is applied to the first sprag 11 via the cage 30. Thus, since the load application device 40 applies a load to the first sprags 11 via the retainer 30, it is possible to apply a load to the plurality of first sprags 11 at a time, and the first sprags 11 can be efficiently applied. A load can be applied to the.

  According to the load applying device 40 configured as described above, as shown in FIG. 5B, the first sprag 11 is applied to the first sprag 11 via the retainer 30 against the urging force of the first urging member 12. By applying a load R in the locking direction (direction of arrow Li in FIG. 5), the engagement surface 11b of the first sprag 11 can be rolled to the inner peripheral surface 3a, and the first sprag 11 can be tilted in the locking direction. . As a result, the engaging surfaces 11a and 11b of the first sprag 11 are in contact with the outer peripheral surface 2a and the inner peripheral surface 3a, so that the contact between the inner peripheral surface 3a and the engaging surface 11b and the outer peripheral surface 2a and the engaging surface 11a Frictional force is generated at the contact points of the inner ring 2, and the first sprags 11 are engaged with the inner ring 2 and the outer ring 3 due to the displacement of the respective contact points in the circumferential direction of the outer peripheral surface 2 a and the inner peripheral surface 3 a, so Relative rotation is restricted. As a result, power is transmitted from the outer ring 3 to the inner ring 2, and the inner ring 2 rotates as the outer ring 3 rotates (in the direction of arrow T in FIG. 5).

  When the first sprag 11 is engaged with the inner ring 2 and the outer ring 3 and the relative rotation between the inner ring 2 and the outer ring 3 is restricted, the outer ring 3 is viewed from the inner ring 2 side by the relative rotation with the inner ring 2. When rotating in the Lo direction (hereinafter referred to as “lock direction”), even if the load application by the load applying device 40 is stopped, the first sprag 11 is tilted in the lock direction by the relative rotation of the outer ring 3, and the inner ring 2 The engagement between the outer ring 3 and the first sprag 11 is maintained. In addition, when the inner ring 2 rotates in the locking direction (in the direction of arrow Li in FIG. 5) as viewed from the outer ring 3 side relative to the outer ring 3, even when the load application by the load applying device 40 is stopped, The first sprag 11 is tilted in the locking direction by the relative rotation, and the engagement between the inner ring 2 and the outer ring 3 and the first sprag 11 is maintained.

  On the other hand, when the first sprag 11 is engaged with the inner ring 2 and the outer ring 3 and the relative rotation between the inner ring 2 and the outer ring 3 is restricted, the outer ring 3 is viewed from the inner ring 2 side by the relative rotation with the inner ring 2. 5 rotates in the counter-arrow Lo direction (hereinafter referred to as “anti-lock direction”) in FIG. 5, the load applying device 40 is stopped or the load applied by the load applying device 40 is reduced to reduce the first urging force. Due to the urging force of the member 12 (in the direction of arrow S in FIG. 5A), the first sprag 11 is tilted in the anti-lock direction. Thereby, the engagement between the inner ring 2 and the outer ring 3 and the first sprag 11 is released, and transmission of power from the outer ring 3 to the inner ring 2 is interrupted. Further, when the inner ring 2 rotates in the anti-lock direction (counter arrow Li direction in FIG. 5) relative to the outer ring 3 as viewed from the outer ring 3 side, the load applying device 40 is stopped or applied by the load applying device 40. By reducing the load, the first sprag 11 tilts in the anti-lock direction due to the urging force of the first urging member 12 (in the direction of arrow S in FIG. 5A). Thereby, the engagement between the inner ring 2 and the outer ring 3 and the first sprag 11 is released, and transmission of power from the outer ring 3 to the inner ring 2 is interrupted.

  According to the first clutch 10 configured as described above, a load is applied to the first sprag 11 by the power transmission device 40, whereby the first sprag 11 is engaged with the inner ring 2 and the outer ring 3, and the inner ring 2. Relative rotation between the outer ring 3 and the outer ring 3 in the constant rotation direction is restricted. On the other hand, when the application of the load by the power transmission device 40 is released, the urging force is applied to the first sprag 11 by the first urging member 12, and therefore the first sprag 11 to the inner ring 2 and the outer ring 3. Thus, the inner ring 2 and the outer ring 3 can be rotated relative to each other in both rotation directions. Thereby, rotation transmission in a fixed direction and switching between cutoffs can be performed.

Next, the relationship between the urging force and the load acting on the first sprag 11 will be described with reference to FIG. FIG. 8 is a schematic view of the first sprag 11 tilted in the anti-lock direction. As shown in FIG. 8, the first sprag 11 that is disengaged from the inner ring 2 and the outer ring 3 is brought into contact with the contact surface 11 b by the biasing force (load P) applied by the first biasing member 12. A rotational moment tilted in the anti-lock direction (clockwise in FIG. 8) is generated around the contact A with the inner peripheral surface 3a. Further, when the first sprag 11 is engaged 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 first sprag 11. Along with these, a pressing load acts on the contact A. As a reaction force, the first sprag 11, the reaction force F _A to the normal direction of the inner peripheral surface 3a acts at a contact point A. On the other hand, in order to tilt the first sprag 11 in the lock direction, the holding portion 31 applies a load R in the lock direction (direction of arrow Li in FIG. 8) to the contact C that contacts the first sprag 11.

Here, considering a contact point A about a rotational moment M _A acting on the first sprag 11, the load P in the first sprag 11, because the load R and the centrifugal force K acts, rotation moment M _A is the following It is represented by Formula (1).

M _A = Lp · P + Lk · K−Lr · R (1)
However, in Formula (1), Lp is a horizontal distance from the contact A to the application point of the load P (groove portion 11d), and Lk is from the contact A to the application point of the centrifugal force K (the center of gravity G of the first sprag 11). Lr is a vertical distance from the contact A to the point of application of the load R (contact C). The rotational moment M _A is positive in the clockwise direction around the contact A. Strictly speaking, the loads P, K and R need to take into account errors due to the horizontal and vertical components of the load, but the errors are significantly smaller than the magnitudes of the loads P, K and R. The loads P and K act in the vertical direction, and the load R acts in the horizontal direction.

Here, in order to engage the engaging surface 11a of the first sprag 11 with the outer peripheral surface 2a, the engaging surface 11b of the first sprag 11 does not slide on the inner peripheral surface 3a, and the first sprag 11 is not shown in FIG. It is necessary to be tilted counterclockwise. That is, it is necessary that M _A <0. In the state shown in FIG. 8, the engagement between the inner ring 2 and the outer ring 3 and the first sprag 11 is released, so that the outer ring 3 and the inner ring 2 can rotate around the axis O, but the outer ring 3 and the inner ring 2 With this driving force, the first sprag 11 cannot revolve around the axis O. Accordingly, the centrifugal force K does not act on the first sprag 11 (K = 0). From the above, the requirements to engage the engagement surface 11a of the first sprags 11 on the outer circumferential surface 2a of the formula (2) to by substituting _{M A <0, K = 0} , the following equation (2) It is represented by

R> Lp / Lr · P (2)
Here, if Lp <Lr, Lp / Lr <1. Therefore, the load R <P from Equation (2). Therefore, the load applying device 40 (see FIG. 3) does not apply a load larger than the urging force (load P) of the first urging member 12 to the first sprag 11, and the first sprag is applied to the outer ring 3 and the inner ring 2. 11 can be engaged. Thereby, while being able to miniaturize the load provision apparatus 40 and to apply | coat a small load, an energy loss can be suppressed. As a result, the power transmission device 1 can be reduced in size.

In FIG. 8, when the angle between the normal line at the contact A and the vertical direction is α, the magnitude of the horizontal component of the reaction force F _A acting on the first sprag 11 from the inner peripheral surface 3a is F _A · sin α, the direction of which is the same as the lock direction (the direction of arrow Lo in FIG. 8). Further, when the friction coefficient at the contact point A and mu, the magnitude of the frictional a μ · F _A · cosα, its orientation is the same direction as the locking direction (Figure 8 arrow Lo direction).

As described above, the reaction force F _A to the inner peripheral surface 3a acting from the inner peripheral surface 3a in the first sprag 11 at the contact point A in contact with the engaging surface 11b is first through the holding portion 31 by the load applying device 40 The direction of the component component of the load R acting on the sprag 11 (the horizontal direction and the left-right direction in FIG. 8) is the same as the lock direction. Therefore, when the load R is applied to the first sprag 11 by the load applying device 40, the engagement surface 11b is prevented from sliding on the inner peripheral surface 3a, and the first sprag 11 is reliably tilted in the locking direction. be able to. Thereby, by applying a load from the load applying device 40, the two engaging surfaces 11a and 11b of the first sprag 11 can be reliably engaged with the outer peripheral surface 2a and the inner peripheral surface 3a.

  As described above, according to the first clutch 10, the load applying device 40 can perform transmission of rotation in a certain direction and switching between cutoffs as necessary. Furthermore, by securing a distance to the extent that the first sprags 11 can be tilted by the cage 30, a plurality of first sprags 11 can be arranged at small intervals between the outer peripheral surface 2 a and the inner peripheral surface 3 a. it can. Thereby, even if the 1st clutch 10 (power transmission device 1) is small, transmission torque capacity can be enlarged.

  Returning to FIG. 3, the second clutch 20 will be described. The second sprag 21 is a member having a function for restricting relative rotation between the inner ring 2 and the outer ring 3, and engaging surfaces 21 a and 21 b (FIGS. 3 and 6) in contact with the outer peripheral surface 2 a and the inner peripheral surface 3 a, respectively. As shown in FIG. 6, a plurality of the outer peripheral surface 2a and the inner peripheral surface 3a are arranged at equal intervals in the circumferential direction. Further, as shown in FIG. 7, the second sprag 21 has a groove 21d formed between the side surfaces 21c from the engagement surface 21b toward the engagement surface 21a. The groove portion 21d is a portion where a second urging member 22 described later is mounted.

  As shown in FIG. 7, the holding portion 31 has hole portions 31 b formed at equal intervals in the circumferential direction in parallel with the hole portion 31 a. By inserting the portion of the second sprag 21 (on the engagement surface 21a side) located on the inner ring 2 side into the hole 31b, the second sprag 21 is held by the retainer 30 together with the first sprag 11 so as to be tiltable. . As shown in FIGS. 4 and 6, the first sprag 11 and the second sprag 21 are juxtaposed with the cage 30 so that the rotation lock direction is the reverse direction.

  As shown in FIG. 6, the second urging member 22 is formed by an annular coil spring, and is a member that applies an urging force in the direction of reducing the diameter. The second urging member 22 is attached to the groove portion 21d of the second sprag 21. By applying a urging force in the direction of reducing the diameter, the engagement surface 21b of the second sprag 21 and the inner peripheral surface of the outer ring 3 are provided. The second sprag 21 is tilted in the locking direction so that the engagement surface 21a and the outer peripheral surface 2a of the inner ring 2 are in contact with 3a. Thereby, the inner ring | wheel 2 and the outer ring | wheel 3 and the 2nd sprag 21 can be engaged.

  Further, since the second sprag 21 is held in the holder 30 together with the first sprag 11, a load can be applied together with the first sprag 11 by the load applying device 40. Thus, the second sprag 21 can be tilted in the anti-lock direction by applying an external force to the second sprag 21 via the retainer 30 against the urging force of the second urging member 21. Thereby, transmission of motive power can be interrupted.

  Further, the first sprag 11 and the second sprag 21 are held by a single holder 30, and the first sprag 11 and the second sprag 21 are connected to the first sprag 11 and the second sprag 21 via the holder 30 using a single load applying device 40. Since the load is applied, the load can be efficiently applied to the plurality of first sprags 11 and second sprags 21. Furthermore, compared with the case where the 1st sprag 11 and the 2nd sprag 21 are hold | maintained with a separate holder | retainer, while changing a number of parts and simplifying an apparatus structure, a switching mechanism and control can be simplified.

  Next, the operation of the power transmission device 1 configured as described above will be described with reference to FIGS. 9 and 10. 9 and 10, for easy understanding, the power transmission path is indicated by an arrow P, and the rotation direction and the rotation speed of the inner ring 2 and the outer ring 3 are indicated by the direction and size of the arrow T. . Further, the direction of the load applied to the holding portion 31 (cage 30) by operating the load application device 40 (see FIG. 2) is indicated by an arrow R. The direction in which the first sprag 11 and the second sprag 21 are urged by the first urging member 12 and the second urging member 22 is indicated by an arrow S. Further, relative to the first sprag 11 or the second sprag 21, the rotation in the locking direction of the inner ring 2 as viewed from the outer ring 3 side by the relative rotation with the outer ring 3 is indicated by the arrow Li, and the inner ring 2 side by the relative rotation with the inner ring 2. The rotation in the locking direction of the outer ring 3 as viewed from the side is indicated by an arrow Lo. Note that FIG. 12, FIG. 14 and FIG.

  First, the operation of the power transmission device 1 during normal travel will be described, and then the operation of the power transmission device 1 when shifting up the transmission 111 (see FIG. 2) will be described. FIG. 9A is a schematic diagram schematically showing the internal structure of the power transmission device 1 during normal traveling, and FIG. 9B is a schematic diagram of the internal structure of the power transmission device 1 during upshifting. It is the schematic diagram shown in. During normal travel, the load applying device 40 of the power transmission device 1 is deactivated while the main clutch 113 (see FIG. 2) is connected. As a result, as shown in FIG. 9A, in the first clutch 10, the first sprag 11 is tilted in the anti-lock direction, and a gap is generated between the outer peripheral surface 2 a and the engagement surface 11 a, and in the second clutch 20, The second sprag 21 is tilted in the locking direction.

  In this state, power is transmitted from the input shaft 112 to the inner ring 2. Assuming that the rotation direction of the inner ring 2 is the locking direction of the second sprag 20 (counterclockwise in FIG. 9), the rotation of the inner ring 2 in the first sprag 11 as viewed from the outer ring 3 side relative to the outer ring 3 It is the antilock direction (counter arrow Li direction), and the second sprag 21 is the lock direction (arrow Li direction). As a result, the power transmitted to the inner ring 2 is transmitted to the outer ring 3 via the second sprag 21. The power transmitted to the outer ring 3 drives the rear wheel 102 (see FIG. 2) via the output shaft 114.

  Next, when shifting up, it is desirable to reduce the rotational speed of the input shaft 112 (inner ring 2) in order to reduce shift shock in the transmission 111 (see FIG. 2). In the power transmission device 1, it is possible to reduce the rotation speed of the input shaft 112 using a known means while the main clutch 113 (see FIG. 2) is connected. That is, as shown in FIG. 9 (b), when the rotational speed of the inner ring 2 is made slower than the rotational speed of the outer ring 3, the rotational direction of the outer ring 3 is relative to the inner ring 2 as viewed from the inner ring 2 side. One sprag 11 is in the locking direction (arrow Lo direction), and the second sprag 21 is in the anti-locking direction (counter arrow Lo direction). However, since the first sprag 11 is tilted in the anti-lock direction, no power is transmitted through the first sprag 11. Therefore, the rotational speed of the input shaft 112 can be reduced without affecting the rotational speed of the output shaft 114. As a result, a series of operations can be performed while the main clutch 113 (see FIG. 2) is connected, so that the speed change operation time can be shortened.

  Similarly, when coasting with the accelerator pedal released, the rotational speed of the output shaft 114 decreases due to the inertia of the engine 103 (see FIG. 2), as shown in FIG. 9B. Can be prevented. Thus, the vehicle 100 (see FIG. 1) can be comfortably coasted without being decelerated by the engine brake.

  On the other hand, it is also possible to apply an engine brake. With reference to FIG. 10A, the operation of the power transmission device 1 during coasting will be described, and then the operation of the power transmission device 1 when the transmission 111 (see FIG. 2) is shifted down will be described. FIG. 10A is a schematic diagram schematically showing the internal structure of the power transmission device 1 during coasting, and FIG. 10B is a schematic diagram of the internal structure of the power transmission device 1 during downshifting. It is the schematic diagram shown in. In coasting where the accelerator pedal (not shown) is released and engine braking is applied, the load applying device 40 of the power transmission device 1 is operated with the main clutch 113 (see FIG. 2) connected, and FIG. As shown to (a), the holding | maintenance part 31 is rotated in the arrow R direction. As a result, in the first clutch 10, the first sprag 11 is tilted in the locking direction, and the outer peripheral surface 2a and the inner peripheral surface 3a can be engaged with the engaging surfaces 11a and 11b. The sprag 21 is tilted in the anti-lock direction.

  In coasting, no power is input from the input shaft 112 to the inner wheel 2, while power is input from the rotating rear wheel 102 (see FIG. 2) to the outer wheel 3 via the output shaft 114. Since the rotation direction of the outer ring 3 is counterclockwise in FIG. 10 as in FIG. 9, the rotation of the outer ring 3 is viewed from the inner ring 2 side relative to the inner ring 2 as shown in FIG. The first sprag 11 is in the lock direction (arrow Lo direction), and the second sprag 21 is in the anti-lock direction (counter arrow Lo direction). As a result, the power transmitted to the outer ring 3 is transmitted to the inner ring 2 via the first sprag 11. The power transmitted to the inner ring 2 is transmitted to the engine 103 (see FIG. 2) and the like via the input shaft 112. As a result, the rotational speed of the output shaft 112 decreases due to the inertia of the engine 103 and the like, and consequently the rotational speed of the rear wheel 102 (see FIG. 2) also decreases. That is, engine braking is applied.

  In addition, since the 1st sprag 11 and the 2nd sprag 21 are hold | maintained at the single holder | retainer 30, when the holding | maintenance part 31 is rotated in the arrow R direction by the action | operation of the load provision apparatus 40, FIG. ), The first sprag 11 is tilted in the locking direction, while the second sprag 21 is tilted in the anti-locking direction. However, in the second clutch 20, the rotation direction of the outer ring 3 to which power is input is the anti-lock direction (counter arrow Lo direction), so the second clutch 20 does not power regardless of whether the load applying device 40 is activated or not. I can't communicate.

  Next, when shifting down, it is desirable to increase the rotational speed of the input shaft 112 (inner ring 2) in order to reduce shift shock in the transmission 111 (see FIG. 2). In the power transmission device 1, it is possible to increase the rotation speed of the input shaft 112 using a known means while the main clutch 113 (see FIG. 2) is connected. That is, as shown in FIG. 10B, when the rotational speed of the inner ring 2 is made higher than the rotational speed of the outer ring 3, the rotation of the inner ring 2 is the first relative to the outer ring 3 as viewed from the outer ring 3 side. The sprag 11 is in the anti-lock direction (counter arrow Li direction), and the second sprag 21 is in the lock direction (arrow Li direction). However, since the second sprag 21 is tilted in the anti-lock direction (counter arrow S direction) by the operation of the load applying device 40, power is not transmitted through the second sprag 21. Therefore, the rotational speed of the input shaft 112 can be increased without affecting the rotational speed of the output shaft 114. As a result, a series of operations can be performed while the main clutch 113 (see FIG. 2) is connected, so that the speed change operation time can be shortened.

  In addition, since the 1st sprag 11 and the 2nd sprag 21 are hold | maintained at the single holder | retainer 30, when the holding | maintenance part 31 is rotated in the arrow R direction by the action | operation of the load provision apparatus 40, FIG. ), The second sprag 21 is tilted in the anti-lock direction (counter arrow S direction), while the first sprag 11 is tilted in the lock direction (counter arrow S direction). However, in the first clutch 11, the rotation direction of the inner ring 2 is the anti-lock direction (counter arrow Li direction) as viewed from the outer ring 3 side by relative rotation with the outer ring 3, so that even if the load applying device 40 is operated, the first clutch 10 cannot transmit power.

  Furthermore, the power transmission device 1 in the present embodiment will be described in comparison with the power transmission device 501 in the comparative example shown in FIG. First, the power transmission device 501 in the comparative example will be described. FIG. 16A is a schematic diagram schematically showing the internal structure of the power transmission device 501 in which power is input to the outer ring 503 and output from the inner ring 502, and FIG. FIG. 5 is a schematic diagram schematically showing the internal structure of a power transmission device 501 that is input and output from an outer ring 503. In FIG. 16, the power transmission path is indicated by an arrow P for easy understanding.

  As shown in FIG. 16, the power transmission device 501 has an inner ring 502 (shaft) configured to be rotatable and an inner peripheral surface 503 a facing the outer peripheral surface 502 a of the inner ring 502, and can rotate coaxially with the inner ring 502. An outer ring 503 configured to be configured, a first sprag 504 configured to be engageable with the outer ring 503 and the inner ring 502, a second sprag 505 whose locking direction is opposite to the first sprag 504, and the first sprags. 504 and the 2nd sprag 505 are each provided with the 1st holder | retainer 506 and the 2nd holder | retainer 507. The first sprag 504 and the second sprag 505 are juxtaposed in the axial direction with respect to the outer ring 503 and the inner ring 502 and are spring members (not shown) in the locking direction (direction of arrow S in FIG. 16) opposite to each other. Each is energized. Note that levers (not shown) are respectively extended from the first cage 506 and the second cage 507, and the first cage 506 and the second cage 507 are circularly operated by operating the levers separately. By rotating in the circumferential direction, the first sprag 504 or the second sprag 505 can be tilted to a free state (a state where power cannot be transmitted).

  In the power transmission device 501 configured as described above, the outer ring 503 is locked relative to the first sprag 504 or the second sprag 505 relative to the inner ring 502 as viewed from the inner ring 502 side (see arrow Lo in FIG. 16). When the first sprag 504 or the second sprag 505 is tilted in the rotation lock direction, the first sprag 504 or the second sprag 505 is engaged with the inner ring 502 and the outer ring 503. Thereby, power is transmitted from the outer ring 503 to the inner ring 502.

  On the other hand, when the outer ring 503 rotates relative to the first sprag 504 or the second sprag 505 in the anti-locking direction (in the direction of the arrow Lo in FIG. 16) as viewed from the inner ring 502 side, The first sprag 504 or the second sprag 505 is not engaged with the inner ring 502 and the outer ring 503, and the outer ring 503 is idled. As a result, transmission of power from the outer ring 503 to the inner ring 502 is interrupted.

  When the inner ring 502 rotates relative to the first sprag 504 or the second sprag 505 in the locking direction (direction of arrow Li in FIG. 16) as viewed from the outer ring 503 by relative rotation with the outer ring 503, the first The sprag 504 or the second sprag 505 tilts in the locking direction (the arrow S direction in FIG. 16), and the first sprag 504 or the second sprag 505 engages with the inner ring 502 and the outer ring 503. As a result, power is transmitted from the inner ring 502 to the outer ring 503.

  On the other hand, when the inner ring 502 rotates relative to the first sprag 504 or the second sprag 505 in the anti-lock direction (in the direction of the arrow Li in FIG. 16) when viewed from the outer ring 503 side relative to the outer ring 503, The first sprag 504 or the second sprag 505 is not engaged with the inner ring 502 and the outer ring 503, and the inner ring 502 rotates idle. As a result, transmission of power from the inner ring 502 to the outer ring 503 is interrupted.

  Further, even when the first sprag 504 or the second sprag 505 can be engaged with the inner ring 502 and the outer ring 503, the first retainer 506 and the second retainer can be operated by operating a lever (not shown). By rotating 507 in the circumferential direction, the first sprag 504 or the second sprag 505 can be brought into a free state (a state where power cannot be transmitted). By operating the lever in this way, power transmission can be forcibly interrupted.

  Since the power transmission device 501 is configured as described above, as shown in FIG. 16A, when power is input to the outer ring 503 and the outer ring 503 rotates (the rotation direction is counterclockwise in FIG. 16). The rotation of the outer ring 503 is in the anti-lock direction (the direction of the arrow Lo in FIG. 16) with respect to the first sprag 504, and in the lock direction (the direction of the arrow Lo in FIG. 16) with respect to the second sprag 505. In this case, the second sprag 505 is engaged with the inner ring 502 and the outer ring 503, and power is transmitted from the outer ring 503 to the inner ring 502.

  Also, as shown in FIG. 16 (b), when power is input to the inner ring 502 and the inner ring 502 rotates (the rotation direction is counterclockwise in FIG. 16), the rotation of the inner ring 502 is relative to the first sprag 504. Is the locking direction (direction of arrow Li in FIG. 16), and is anti-locking direction (direction of arrow Li in FIG. 16) with respect to the second sprag 505. In this case, the first sprag 505 is engaged with the inner ring 502 and the outer ring 503, and power is transmitted from the outer ring 503 to the inner ring 502.

  However, in the power transmission device 501 in the comparative example, when the second sprag 505 engages with the inner ring 502 and the outer ring 503 as shown in FIG. 16A, the second sprag 505 engaged with the inner ring 502 and the outer ring 503. As a result, the inner ring 502 and the outer ring 503 are elastically deformed, and the distance between the inner ring 502 and the outer ring 503 is slightly widened. Here, since the first sprag 504 is biased in the locking direction (the direction of arrow S in FIG. 16), when the interval between the inner ring 502 and the outer ring 503 is widened, the first sprag 504 is placed between the inner ring 502 and the outer ring 503 ( It is bitten like a wedge at a position indicated by a two-dot chain line in FIG.

  Thereafter, as shown in FIG. 16B, when the first sprag 504 engages with the inner ring 502 and the outer ring 503, the first sprag 504 engaged with the inner ring 502 and the outer ring 503 elastically acts on the inner ring 502 and the outer ring 503. Deformation occurs, and the distance between the inner ring 502 and the outer ring 503 is slightly increased. Here, since the second sprag 505 is also urged in the locking direction (the arrow L direction in FIG. 16), when the distance between the inner ring 502 and the outer ring 503 is widened, the second sprag 505 is also between the inner ring 502 and the outer ring 503 ( It is bitten like a wedge at a position indicated by a two-dot chain line in FIG.

  As described above, when either the first sprag 504 or the second sprag 505 is caught between the inner ring 502 and the outer ring 503, the first sprag 504 and the second sprag 505 are biased in the locking direction. Therefore, it is gradually bitten deeply in the locking direction. Finally, it becomes impossible to release the bite, and it becomes impossible to switch the transmission direction of the power, and the first sprag 504 and the second sprag 505 are brought into a free state (a state where the power cannot be transmitted) by operating the lever. Can not even. As described above, there is a problem that the first sprag 504 and the second sprag 505 are engaged between the inner ring 502 and the outer ring 503 so that the power transmission direction cannot be switched or the power transmission cannot be interrupted.

  On the other hand, according to the power transmission device 40 in the present embodiment, as shown in FIG. 9, the second sprag 21 is urged in the lock direction (arrow S direction) by the second urging member 22. The second sprag 21 can be engaged with the inner ring 2 and the outer ring 3 by this urging force. When the second sprag 21 is engaged with the inner ring 2 and the outer ring 3 and power is transmitted through the second sprag 21, the second sprag 21 is engaged with the inner ring 2 and the outer ring 3 by the second sprag 21 engaged with the inner ring 2 and the outer ring 3. Elastic deformation may occur, and the distance between the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3 may be slightly widened. However, since the first sprag 11 is tilted in the anti-locking direction (arrow S direction), the first sprag 11 is caught in the inner ring 2 and the outer ring 3 while power is transmitted through the second sprag 21. Can be prevented.

  On the other hand, the first sprag 11 can be engaged with the inner ring 2 and the outer ring 3 by tilting the first sprag 11 in the locking direction (in the direction of the arrow S in FIG. 9) against the urging force by the load applying device 40. . As a result, when the first sprag 11 is engaged with the inner ring 2 and the outer ring 3 and power is transmitted through the first sprag 11, the inner ring 2 and the outer ring 3 are elastically deformed by the first sprag 11, and the inner ring There is a possibility that the distance between the outer peripheral surface 2a of the two and the inner peripheral surface 3a of the outer ring 3 is slightly widened. In this case, since the second sprag 21 is biased in the locking direction (arrow S direction), the second sprag 21 may be caught in the inner ring 2 and the outer ring 3. When the second sprag 21 is bitten by the inner ring 2 and the outer ring 3, when power is transmitted through the second sprag 21, the second sprag 21 is bitten by the second sprag 21 bitten by the inner ring 2 and the outer ring 3. The space | interval of the outer peripheral surface 2a and the inner peripheral surface 3a of the outer ring | wheel 3 is expanded. However, since the first sprag 11 is tilted in the anti-locking direction (arrow S direction) by the first urging member 12, the distance between the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3 by the second sprag 21. Is slightly expanded, the first sprag 11 tilts in the direction opposite to the biting direction. Thereby, it is possible to prevent the first sprag 11 from being caught in the inner ring 2 and the outer ring 3. As described above, it is possible to prevent the first sprag 11 and the second sprag 21 from being bitten by the inner ring 2 and the outer ring 3 and to prevent the switching of the power transmission direction.

  Further, by preventing the first sprag 11 and the second sprag 21 from being caught in the inner ring 2 and the outer ring 3, the first biasing member 12 tilts the first sprag 11 in the anti-lock direction (arrow S direction). On the other hand, the first sprag 11 can be tilted in the lock direction (counter arrow S direction) by the load applying device 40. As a result, the transmission of power by the first clutch 10 can be interrupted by switching the operation of the load applying device 40 or not.

  Further, the first biasing member 12 biases the first sprag 11 so that a gap is formed between the outer peripheral surface 2a and the engagement surface 11a of the first sprag 11, and therefore the outer peripheral surface 2a and the engagement surface 11a. Friction can be eliminated, and energy loss due to friction can be suppressed. Further, by forming the gap, the first sprag 11 can be made more difficult to be bitten.

  Furthermore, since the second sprag 21 can be tilted in the anti-lock direction (counter arrow S direction) as required by the load applying device 40, the transmission of power by the second clutch 20 can be cut off and the power can be switched freely. Can be improved.

  Next, a second embodiment will be described with reference to FIGS. FIG. 11 is a schematic diagram schematically showing the internal structure of a vehicle on which the power transmission device 201 according to the second embodiment is mounted, and FIG. 12 (a) shows the inside of the power transmission device 201 during normal travel. It is the schematic diagram which showed the structure typically, and FIG.12 (b) is the schematic diagram which showed typically the internal structure of the power transmission device 201 at the time of coast driving | running | working. In the first embodiment, the power transmission device 1 is disposed in the power transmission path of the vehicle 100 using the rear wheel 102 as the driving wheel, and the driving force of the engine 103 or the like is input to the inner ring 2 of the power transmission device 1. Explained. On the other hand, in the second embodiment, a case will be described in which the power transmission device 201 is disposed in the power transmission path of a vehicle having the front wheels 101 as driving wheels, and the driving force of the engine 103 or the like is input to the outer wheels 3. Moreover, although 1st Embodiment demonstrated the case where a clearance gap was formed in the engaging surface 11a of the 1st sprag 11, and the outer peripheral surface 2a of the inner ring | wheel 2, in 2nd Embodiment, the 1st sprag 11 of the 1st sprag 11 was demonstrated. A case where a gap is formed between the engagement surface 11b and the inner peripheral surface 3a of the outer ring 3 will be described. In addition, the same code | symbol is attached | subjected about the part same as 1st Embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 11, the power transmission device 201 in the second embodiment is disposed in a power transmission path between the input shaft 112 and the transmission 121. The transmission 121 is configured as a part of a dog clutch type automatic control manual transmission (AMT), and the power of the engine 103 and the motor 104 is input via the input shaft 112 and the main clutch 113, and via the differential device 124. And is transmitted to the front wheel 101 (drive wheel).

  The first sprags 11 and the second sprags 21 constituting the first clutch 210 and the second clutch 220 are disposed between the inner ring 2 and the outer ring 3 facing each other, and as shown in FIG. The part located in is held. The holding portion 231 extends in the axial direction, and the load transmitting portion 232 extends from the holding portion 231 in a direction intersecting the axial direction. The load applying device 40 is configured to apply a load to the first sprag 11 and the second sprag 21 via a cage 230 including a holding portion 231 and a load transmission portion 232.

  As shown in FIG. 12A, when the load applying device 40 is in an inoperative state, the first sprag 11 is tilted in the anti-lock direction (arrow S direction) by a first biasing member (not shown). In addition, a gap is formed between the engagement surface 11 b of the first sprag 11 and the inner peripheral surface 3 a of the outer ring 3. On the other hand, the second sprag 21 is tilted in the locking direction (arrow S direction) by a second urging member (not shown) when the load applying device 40 is inactive, and the outer peripheral surface 2a of the inner ring 2 and The inner peripheral surface 3a of the outer ring 3 and the engaging surfaces 21a and 21b of the second sprag 21 are in contact with each other.

  Next, the operation of the power transmission device 201 configured as described above will be described with reference to FIG. First, the operation of the power transmission device 201 during normal travel will be described, and then the operation of the power transmission device 201 during coast travel will be described. During normal travel, the load applying device 40 of the power transmission device 201 is deactivated while the main clutch 113 (see FIG. 11) is connected. Accordingly, as shown in FIG. 12A, the first sprag 11 is tilted in the anti-lock direction (arrow S direction) in the first clutch 210, and the second sprag 21 is tilted in the lock direction in the second clutch 220. The

  In this state, power is transmitted from the input shaft 112 to the outer ring 3. Assuming that the rotation direction of the outer ring 3 is the locking direction of the second sprag 21 (the counterclockwise arrow T direction in FIG. 12), the rotation of the outer ring 3 is relative to the inner ring 2 as viewed from the inner ring 2 side. 1 sprag 11 is in the anti-lock direction (counter arrow Lo direction), and the second sprag 21 is in the lock direction (arrow Lo direction). As a result, the power transmitted to the outer ring 3 is transmitted to the inner ring 2 via the second sprag 21. Since the first sprag 11 is tilted in the anti-lock direction (arrow S direction), it can be prevented from being bitten by the inner ring 2 and the outer ring 3.

  In the coast running shown in FIG. 12B, the load applying device 40 of the power transmission device 201 is operated with the main clutch 113 (see FIG. 11) connected to apply a load in the arrow R direction to the holding portion 231. Give. As a result, in the first clutch 210, the first sprag 11 is tilted in the locking direction (counter arrow S direction), the outer peripheral surface 2a and the inner peripheral surface 3a are brought into contact with the engaging surfaces 11a and 11b, and can be engaged. In the two-clutch 220, the second sprag 21 is tilted in the anti-lock direction (counter arrow S direction).

  When an accelerator pedal (not shown) is released in this state and power is input from the rotating front wheel 101 (see FIG. 11) to the inner wheel 2 via the output shaft 114, the rotation direction of the inner wheel 2 is as shown in FIG. Since the rotation is counterclockwise, as shown in FIG. 12B, the rotation of the inner ring 2 is relative to the outer ring 3 and viewed from the outer ring 3 side, the first sprag 11 is in the locking direction (arrow Li direction). Yes, the second sprag 21 is in the anti-lock direction (counter arrow Li direction). As a result, the power transmitted to the inner ring 2 is transmitted to the outer ring 3 and the input shaft 112 via the first sprag 11. At this time, since the second sprag 21 is tilted in the anti-lock direction (counter arrow S direction) by the load applying device 40, it can be prevented from being bitten by the inner ring 2 and the outer ring 3. As described above, according to the power transmission device 201, it is possible to prevent the first sprag 11 and the second sprag 21 from being bitten by the inner ring 2 and the outer ring 3, and to prevent switching of the power transmission direction.

  Next, a third embodiment will be described with reference to FIGS. FIG. 13 is a schematic diagram schematically showing the internal structure of a vehicle on which the power transmission device 301 according to the third embodiment is mounted, and FIG. 14 (a) is a power transmission device during normal travel (forward). FIG. 14B is a schematic diagram schematically illustrating the internal structure of the power transmission device 301. FIG. 14B schematically illustrates the internal structure of the power transmission device 301 when the rotational speed of the input shaft 122 is reduced during normal travel (forward). FIG. 15A is a schematic diagram schematically illustrating the internal structure of the power transmission device 301 during reverse travel, and FIG. 15B illustrates the rotational speed of the input shaft 122 during reverse travel. It is the schematic diagram which showed typically the internal structure of the power transmission device 301 when making it fall.

  In the first embodiment, the power transmission device 1 is disposed in the power transmission path of the vehicle 100 using the rear wheel 102 as the driving wheel, and the driving force of the engine 103 or the like is input to the inner ring 2 of the power transmission device 1. Explained. On the other hand, in the third embodiment, a case will be described in which the power transmission device 301 is disposed in the power transmission path of a vehicle having the front wheels 101 as driving wheels, and the driving force of the engine 103 or the like is input to the outer wheels 3. In addition, the same code | symbol is attached | subjected about the part same as 1st Embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 13, the power transmission device 301 in the third embodiment is disposed in a power transmission path between the transmission 121 and the front wheel 101. The transmission 121 is configured as a part of a dog clutch type automatic control manual transmission (AMT), and the power of the engine 103 and the motor 104 is input via the input shaft 112 and the main clutch 113, and is input via the input shaft 122. Thus, power is output to the power transmission device 301. The power output from the power transmission device 301 is configured to be transmitted to the front wheels 101 (drive wheels) via a differential device 124 disposed on the output shaft 123.

  The first sprags 11 and the second sprags 21 constituting the first clutch 310 and the second clutch 320 are disposed between the inner ring 2 and the outer ring 3 facing each other, and as shown in FIG. The part located in is held. The holding portion 331 extends in the axial direction, and the load transmitting portion 332 extends from the holding portion 331 in a direction intersecting with the axial direction. The load applying device 40 is configured to apply a load to the first sprag 11 and the second sprag 21 via a cage 330 including a holding portion 331 and a load transmission portion 332.

  14A, the first sprag 11 is urged in the anti-lock direction (arrow S direction) by a first urging member (not shown), and the anti-lock direction (arrow S). In the state tilted in the direction), a gap is formed between the engagement surface 11 a of the first sprag 11 and the outer peripheral surface 2 a of the inner ring 2. On the other hand, as shown in FIG. 15A, the second sprag 21 is urged in the anti-lock direction (arrow S direction) by a second urging member (not shown) and the anti-lock direction (arrow S). In the state tilted in the direction), a gap is formed between the engagement surface 21 a of the second sprag 21 and the outer peripheral surface 2 a of the inner ring 2. As shown in FIGS. 14 and 15, the locking direction of the first sprag 11 is set to be opposite to the locking direction of the second sprag 21.

  Next, the operation of the power transmission device 301 configured as described above will be described with reference to FIGS. 14 and 15. First, with reference to FIG. 14, the operation of the power transmission device 301 during normal travel (forward) will be described. During normal travel (forward), the load applying device 40 of the power transmission device 301 is operated to apply a load in the direction of arrow R (counterclockwise in FIG. 14) to the holding portion 331. Accordingly, as shown in FIG. 14A, in the first clutch 310, the first sprag 11 is tilted in the anti-lock direction (arrow S direction) by the first urging member (not shown), and the second clutch In 320, the second sprag 21 is tilted in the locking direction (counter arrow S direction) by the holding portion 331. In the present embodiment, a gap is formed between the engagement surface 11 a of the first sprag 11 and the outer peripheral surface 2 a of the inner ring 2.

  Power is transmitted from the input shaft 122 to the outer ring 3, and the rotation direction of the outer ring 3 is assumed to be the locking direction of the second sprag 21 (the direction of the arrow T in FIG. 14 (a) counterclockwise in FIG. 14). The rotation of the outer ring 3 is relative to the inner ring 2 and viewed from the inner ring 2 side in the anti-lock direction (counter arrow Lo direction) in the first sprag 11 and in the lock direction (arrow Lo direction) in the second sprag 21. It is. As a result, the power transmitted to the outer ring 3 is transmitted to the inner ring 2 via the second sprag 21. Since the first sprag 11 is tilted in the anti-lock direction (arrow S direction), it can be prevented from being bitten by the inner ring 2 and the outer ring 3.

  In this state, when the rotational speed of the input shaft 122 is lowered due to, for example, an accelerator pedal (not shown) being released, the rotational speed of the outer ring 3 is reduced compared to the rotational speed of the inner ring 2. As a result, as shown in FIG. 14B, the rotation of the inner ring 2 (in the direction of arrow T in FIG. 14B) is relative to the outer ring 3 and viewed from the outer ring 3 side, the first sprag 11 is in the locking direction. (In the direction of arrow Li), and in the second sprag 21, it is in the anti-lock direction (in the direction of anti-arrow Li). However, since the load in the direction of arrow R is applied to the holding portion 331 by the operation of the load applying device 40 and the first sprag 11 is tilted in the anti-lock direction (arrow S direction), the first sprag 11 is connected to the inner ring 2 and The outer ring 3 cannot be engaged. As a result, transmission of power from the input shaft 122 to the output shaft 123 is interrupted.

  Next, the operation of the power transmission device 301 during reverse travel will be described with reference to FIG. During reverse travel, the load applying device 40 of the power transmission device 301 is operated to apply a load in the direction of arrow R (clockwise in FIG. 15) to the holding portion 331. As a result, as shown in FIG. 15A, in the first clutch 310, the first sprag 11 is tilted in the locking direction (counter arrow S direction) by the holding portion 331, and in the second clutch 320, the second urging force is applied. The second sprag 21 is tilted in the anti-lock direction (arrow S direction) by a member (not shown). In the present embodiment, a gap is formed between the engagement surface 21 a of the second sprag 21 and the outer peripheral surface 2 a of the inner ring 2.

  At the time of reverse travel, the rotation direction of the input shaft 122 is switched to the reverse direction (direction of counterclockwise arrow T in FIG. 15) with respect to the forward travel (see FIG. 14). When viewed from the inner ring 2 side by rotation, the first sprag 11 is in the lock direction (arrow Lo direction), and the second sprag 21 is in the anti-lock direction (counter arrow Lo direction). As a result, the power transmitted to the outer ring 3 is transmitted to the inner ring 2 via the first sprag 11. Since the second sprag 21 is tilted in the anti-locking direction (arrow S direction), it can be prevented from being bitten by the inner ring 2 and the outer ring 3.

  In this state, when the rotational speed of the input shaft 122 is lowered due to, for example, an accelerator pedal (not shown) being released, the rotational speed of the outer ring 3 is reduced compared to the rotational speed of the inner ring 2. As a result, as shown in FIG. 15B, the rotation of the inner ring 2 (in the direction of arrow T in FIG. 15B) is relative to the outer ring 3 and is anti-locked by the first sprag 11 when viewed from the outer ring 3 side. Direction (counter arrow Li direction), and the second sprag 21 is the lock direction (arrow Li direction). However, since the load in the direction of the arrow R is applied to the holding portion 331 by the operation of the load applying device 40 and the second sprag 21 is tilted in the anti-locking direction (the direction of the arrow S), the second sprag 21 has the inner ring 2 and The outer ring 3 cannot be engaged. As a result, transmission of power from the input shaft 122 to the output shaft 123 is interrupted.

  When the power transmission direction is switched from forward (see FIG. 14) to reverse (see FIG. 15), the rotation direction (arrow T direction) of the outer ring 3 is switched from the clockwise direction of FIG. 14 to the counterclockwise direction of FIG. . When the rotation direction of the outer ring 3 is counterclockwise in FIG. 14, the rotation of the outer ring 3 is relative to the inner ring 2 and is in the locking direction (arrow Lo direction) at the first sprag 11 when viewed from the inner ring 2 side. When the engagement surfaces 11a and 11b of the first sprag 11 are in contact with the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3, when the rotation of the outer ring 3 is in the locking direction (arrow Lo direction) The engagement surfaces 11 a and 11 b of the first sprag 11 may engage with the outer peripheral surface 2 a of the inner ring 2 and the inner peripheral surface 3 a of the outer ring 3. At this time, if the engaging surfaces 21a, 21b of the second sprag 21 are engaged with the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3, the first sprag 11 and the second sprag 21 are double-engaged. It becomes.

  However, as shown in FIG. 14A, when power is transmitted from the outer ring 3 to the inner ring 2 via the second sprag 21, the first sprag 11 is moved by the first biasing member (not shown). A gap is formed between the engagement surface 11 a and the outer peripheral surface 2 a of the inner ring 2. Thereby, it is prevented that the 1st sprag 11 is bitten by the inner ring | wheel 2 and the outer ring | wheel 3, and double meshing is prevented.

  Similarly, when the power transmission direction is switched from backward (see FIG. 15) to forward (see FIG. 14), the rotation direction of the outer ring 3 (arrow T direction) changes from counterclockwise to FIG. 15 clockwise in FIG. Switch. When the rotation direction of the outer ring 3 is clockwise in FIG. 15, the rotation of the outer ring 3 is the locking direction (arrow Lo direction) at the second sprag 21 when viewed from the inner ring 2 side relative to the inner ring 2. When the engagement surfaces 21a, 21b of the second sprag 21 are in contact with the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3, when the rotation of the outer ring 3 is in the locking direction (arrow Lo direction) The engagement surfaces 21 a and 21 b of the second sprag 21 may engage with the outer peripheral surface 2 a of the inner ring 2 and the inner peripheral surface 3 a of the outer ring 3. At this time, if the engaging surfaces 11a and 11b of the first sprag 11 are engaged with the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3, the first sprag 11 and the second sprag 21 are double-engaged. It becomes.

  However, as shown in FIG. 15A, when power is transmitted from the outer ring 3 to the inner ring 2 via the first sprags 11, the second sprag 21 is moved by the second urging member (not shown). A gap is formed between the engagement surface 21 a and the outer peripheral surface 2 a of the inner ring 2. As a result, the second sprag 21 is prevented from being bitten by the inner ring 2 and the outer ring 3, and double meshing is prevented.

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

  In the above-described embodiment, the case where the power transmission devices 1, 201, and 301 are incorporated in the vehicle 100 has been described. However, the present invention is not necessarily limited to this. For example, other vehicles (locomotives, passenger cars, cargoes) Naturally, it can be incorporated in a power transmission device such as a traveling device, a working device, and a machine tool of a car and a special vehicle.

  In the above embodiment, the case where the first engagement element and the second engagement element are configured by the first sprag 11 and the second sprag 21 has been described, but the present invention is not necessarily limited thereto. The first engagement element and the second engagement element can be rollers such as rollers and balls. In this case, the roller is urged by the urging member and held by the cage. A cylindrical surface is formed on one of the outer peripheral surface 2a and the inner peripheral surface 3a of the inner ring 2 and the outer ring 3 (predetermined surfaces and opposing surfaces of the first member and the second member), and a cam surface is formed on the other. A wedge-shaped space in which the rollers engage is formed between the cylindrical surface and the cam surface. Similar to the above-described embodiment, the load is applied to the rollers (first engaging element and second engaging element) via the cage by the load applying device, whereby the engagement between the cylindrical surface of the roller and the cam surface is performed. And release can be switched. Thereby, the same operation as in the above embodiment can be obtained.

  In the first embodiment, the case where the actuator 41 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 first sprag 11 and the second sprag 21 by a gear mechanism or the like. You may comprise so that a load may be provided to the 2nd sprag 21. FIG.

  In each of the above embodiments, the case where the first urging member 12 and the second urging member 22 are configured by coil springs has been described. However, the present invention is not necessarily limited to this, and other urging members are employed. Of course it is possible. The other urging member is formed, for example, by applying a wave-like bending process to a metal material, and is configured so that a load as an urging force can be applied to the first sprag 11 and the second sprag 21 using its elasticity. Ribbon springs.

  In each of the above-described embodiments, the case where the first spring 11 is urged by the urging force of the two first urging members 12 has been described. However, the present invention is not necessarily limited to this. In addition, it is naturally possible to use one urging member for urging.

  In each of the above-described embodiments, the case where the first sprags 11 tilted in the anti-lock direction contact each other and restrain each other is not necessarily limited to this, and depending on the shape of the first sprag 11 For example, the first sprag 11 tilted in the anti-lock direction may be brought into contact with the holding portions 31, 231, and 331 to naturally restrict further tilting. In this case, the same effect can be obtained.

  In each of the above embodiments, a gap is formed between the engagement surface 11a of the first sprag 11 tilted in the anti-lock direction and the outer peripheral surface 2a of the inner ring 2 or the inner peripheral surface 3a of the outer ring 3. The case where a gap is formed between the engagement surface 21a of the second sprag 21 (see FIG. 15) tilted in the anti-lock direction and the outer peripheral surface 2a of the inner ring 2 has been described. Absent. The first sprag 11 and the second sprag 21 are inclined between the inner ring 2 and the outer ring 3 by tilting the first sprag 11 and the second sprag 21 in the anti-lock direction by the first biasing member 12 and the second biasing member 22. This is because 21 can be prevented from being bitten.

1,201,301 Power transmission device 2 Inner ring (first member or second member)
2a Outer peripheral surface (predetermined surface or facing surface)
3 Outer ring (second member or first member)
3a Inner peripheral surface (opposite surface or predetermined surface)
10, 210, 310 First clutch 11 First sprag (first engagement element)
11a, 11b Engaging surface 12 First urging member 20, 220, 320 Second clutch 21 Second sprag (second engaging element)
21a, 21b Engagement surface 22 Second urging member 30, 230, 330 Cage 31, 231, 331 Holding unit 32, 232, 332 Load transmitting unit 40 Load applying device O Axis center

Claims (6)

A first member configured to be rotatable about an axis;
A second member having a facing surface facing a predetermined surface of the first member and configured to be rotatable about the axis;
One of the second member or the first member transmits power to the other of the second member or the first member so as to be cut off, while the second member or the other of the first member transmits the second member or the first member. A first clutch that blocks transmission of power to one of the first members;
While transmitting power from the other of the second member or the first member to one of the second member or the first member, the second member or the first from one of the second member or the first member. A second clutch that interrupts transmission of power to the other of the members,
The first clutch is
The engaging surface is in contact with the predetermined surface and the facing surface, the engaging surfaces are configured to be engageable with the predetermined surface and the facing surface, and between the facing of the predetermined surface and the facing surface A plurality of first engagement elements disposed in a circumferential direction;
A first biasing member that applies a biasing force to the first engagement element and biases the first engagement element in the circumferential anti-lock direction;
The second clutch is
The engaging surface is in contact with the predetermined surface and the facing surface, the engaging surfaces are configured to be engageable with the predetermined surface and the facing surface, and between the facing of the predetermined surface and the facing surface A plurality of second engagement elements disposed in a circumferential direction;
A second biasing member that biases the second engagement element in the circumferential direction by applying a biasing force to the second engagement element;
The first clutch and the second clutch are:
A cage that holds the first engagement element and the second engagement element movably in a circumferential direction of the predetermined surface and the opposing surface;
A load is applied to the retainer so that the engagement surface of the first engagement element is in contact with the predetermined surface and the opposing surface, respectively, in the lock direction opposite to the antilock direction in the circumferential direction. A load applying device for moving one engagement element;
The load is applied to the first engaging element against the urging force of the first urging member by the load applying device, and the first engaging element is moved in the locking direction, so that the predetermined surface and the opposing surface are opposed to each other. With the engagement between the surface and the engagement surface of the second engagement element released, the engagement surface of the first engagement element engages with the predetermined surface and the opposing surface, respectively, and the first member A power transmission device, wherein relative rotation with the second member is restricted. One of the first member or the second member includes an inner ring that has an outer peripheral surface having a circular cross section and is configured to be rotatable about an axis.
The other of the first member or the second member is configured to include an outer ring that has an inner peripheral surface having a circular cross section facing the outer peripheral surface of the inner ring and is configured to be rotatable about the axis.
The first engagement element and the second engagement element have two engagement surfaces in contact with the outer peripheral surface and the inner peripheral surface, respectively, and the engagement surfaces can be engaged with the outer peripheral surface and the inner peripheral surface. The power transmission device according to claim 1, comprising a sprag.   The first biasing member biases the first engagement element such that a gap is formed between one of the outer peripheral surface or the inner peripheral surface and one of the engagement surfaces. 2. The power transmission device according to 2.   The reaction force that acts on the first engaging element from the outer peripheral surface or the other of the inner peripheral surface at the contact point at which the other of the outer peripheral surface or the inner peripheral surface contacts the other of the engaging surfaces of the first engaging element, 4. The power transmission according to claim 2, wherein a direction of a component component in a load direction acting on the first engagement element by the load applying device is the same direction as a locking direction of the first engagement element. 5. apparatus.   5. The first engaging element according to claim 2, wherein the first engaging elements are arranged at equal intervals between the outer peripheral surface and the inner peripheral surface and are in contact with each other by being tilted in the anti-lock direction. The power transmission device according to any one of the above.   The power transmission device according to claim 1, wherein the load applying device is configured by an electric motor.

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