JP2008151327A - Rotation transmitting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To control change-over between the transmission and the interruption of rotating torque without using an electromagnetic clutch. <P>SOLUTION: This rotation transmitting device comprises first and second inner rings 10, 20, an outer ring 30 arranged outside the first and second inner rings 10, 20, a plurality of pairs of rollers 40a, 40b arranged in wedge spaces Ma, Mb between each of the first and second inner rings 10, 20 and the outer ring 30 in an engageable/disengageable manner, a cage connected to the second inner ring 20 and having pockets for storing the rollers 40a, 40b, a first spring 60 inserted between each of the pairs of rollers 40a, 40b for energizing the rollers 40a, 40b in the direction of engaging them in the wedge spaces Ma, Mb, and a second spring 70 for rotating the second inner ring 20 relative to the first inner ring 10 in one direction to energize the roller 40b laid between the second inner ring 20 and the outer ring 30 in the wedge space Mb in the direction of separating it. Herein, a switch 80 is provided for thrusting the second inner ring 20 against the elastic force of the second spring 70 to engage the roller 40b in the wedge space Mb and for separating the roller 40b in the wedge space Mb with one-directional rotation of the second inner ring 20 due to the elastic force of the second spring 70 during the operation of centrifugal force. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention is used in a simple system mounted on a hybrid car for the purpose of improving fuel efficiency, a so-called ISG (Integrated Starter Generator) system, and used for switching between transmission and cut-off of power, such as a generator pulley of a vehicle. The present invention relates to a transmission device.

  As this type of rotation transmission device, there is one having a structure in which switching of power transmission and switching is controlled by an electromagnetic clutch (for example, see Patent Document 1).

  The rotation transmission device disclosed in Patent Document 1 is incorporated between an inner member, an outer member provided outside the inner member, an inner periphery of the outer member, and an outer periphery of the inner member. An armature made of a magnetic material movable in the axial direction, a roller incorporated in the armature and engageable between the inner periphery of the outer member and the outer periphery of the inner member, and the roller being the outer periphery of the inner member A switch spring that elastically holds the armature in a neutral position that is disengaged from the inner periphery of the outer member, and a rotor that is fixed to the inner periphery of the outer member or the outer periphery of the inner member and faces the armature, It is composed of an electromagnet that faces the rotor and attracts the armature to the rotor by energization.

  In the rotation transmission device having the above-described configuration, the armature is separated from the rotor and the roller is moved between the inner periphery of the outer member and the outer periphery of the inner member by the elastic force of the switch spring when the electromagnet is cut off. It is held in the disengaged neutral position. As a result, even if rotational torque is input to the inner member and the inner member rotates, the rotation is not transmitted to the outer member, and only the inner member rotates freely.

  On the other hand, when the electromagnet is energized in the rotation state of the inner member, the armature is attracted to the rotor, and the armature is coupled to the outer member via the rotor. As a result, the inner member and the armature rotate relative to each other, and the roller engages between the inner periphery of the outer member and the outer periphery of the inner member by the relative rotation. For this reason, the rotation of the inner member is transmitted to the outer member via the roller, and the outer member rotates in the same direction as the inner member.

Further, when the inner member and the armature rotate relative to each other, the switch spring is elastically deformed. Therefore, when the electromagnet is de-energized, the armature is rotated by the elastic restoring force of the switch spring, and the roller returns to the neutral position where the engagement is released between the inner periphery of the outer member and the outer periphery of the inner member. Thus, torque transmission from the inner member to the outer member is interrupted.
JP 2006-248463 A

  By the way, in the conventional rotation transmission device described above, switching between power transmission and interruption is controlled by an electromagnetic clutch having an electromagnet that attracts the armature to the rotor by energization. For this reason, if the electromagnetic clutch is not energized continuously, the rotation torque cannot be continuously transmitted from the inner member to the outer member. Therefore, when this rotation transmission device is mainly used in the power transmission state There is a problem that power consumption increases.

  Further, in this rotation transmission device, when the rotation of the inner member and the outer member is switched in the forward and reverse directions in the power transmission state from the inner member to the outer member, that is, in the energized state of the electromagnetic clutch, Since the engagement state of the roller is switched between the inner periphery of the inner member and the outer periphery of the inner member, rattling occurs by switching the engagement state of the roller. There is a possibility.

  Therefore, the present invention has been proposed in view of the above-mentioned problems, and the object of the present invention is to control the switching between transmission and interruption of rotational torque by simple means without using an electromagnetic clutch. The object is to provide a rotation transmission device.

  As technical means for achieving the above-mentioned object, the present invention includes a first inner member and a second inner member which are coaxially arranged so as to be rotatable forward and backward, a first inner member, An outer member that is coaxially disposed on the outer side of the second inner member and that can rotate forward and backward, and a wedge formed between the outer peripheral surface of the first inner member and the inner peripheral surface of the outer member Arranged in a wedge space formed between the outer peripheral surface of one of the engaging elements and the second inner member and the inner peripheral surface of the outer member arranged in a state of being engaged in the space so as to be disengageable. A plurality of pairs of engagement elements comprising the other engagement elements, a cage connected to the second inner member, and having a pocket for accommodating each pair of engagement elements so as to be capable of rolling in the circumferential direction; Between each pair of engagement elements interposed between the outer peripheral surface of the outer member and the inner peripheral surface of the outer member and between the outer peripheral surface of the second inner member and the inner peripheral surface of the outer member. Inserted between the first elastic member and the first inner member and the second inner member that are biased in the direction in which each pair of engaging elements is engaged in the wedge space, The engagement member interposed between the outer peripheral surface of the second inner member and the inner peripheral surface of the outer member by rotating the second inner member in one direction with respect to the first inner member is a wedge space. And a second elastic member that urges the second inner member between the first inner member and the second inner member, and the second inner member is inserted into the second elastic member. By pressing against the elastic force of the second inner member, the engaging element interposed between the outer peripheral surface of the second inner member and the inner peripheral surface of the outer member is engaged in the wedge space, and the A switching member for separating the engagement element in the wedge space by unidirectional rotation of the second inner member by the elastic force of the second elastic member is provided.

  The rotation transmission device of the present invention includes a first inner member and a second inner member that are coaxially disposed so as to be rotatable in the forward and reverse directions, the first inner member and the second inner member, By pressing the second inner member against the elastic force of the second elastic member by the switching member inserted between the outer peripheral surface of the second inner member and the inner periphery of the outer member If the engagement element interposed between the two surfaces is engaged in the wedge space, a power transmission state is obtained by bi-directional rotation, and the second inner member is moved by the elastic force of the second elastic member when centrifugal force is applied. If the engagement element is separated from the wedge space by one-way rotation, a power transmission state is obtained by one-way rotation. As described above, by switching between transmission and interruption of the rotational torque with the centrifugal force, the electromagnetic clutch in the conventional rotational transmission device is not used and there is no power consumption.

  In addition, a plurality of pairs of engagement elements are arranged so as to be disengageable in a wedge space formed between the outer peripheral surface of the first inner member and the second inner member and the inner peripheral surface of the outer member. And a pair of members interposed between the outer peripheral surface of the first inner member and the inner peripheral surface of the outer member and between the outer peripheral surface of the second inner member and the inner peripheral surface of the outer member. The first elastic member is inserted between the couplings, and the first elastic member urges each pair of the engagement elements in the wedge space so that the input rotation direction is switched between forward and reverse. Even if it changes, since the engagement element is engaged in the wedge space in both the forward rotation side and the reverse rotation side, the engagement state of the engagement element is not switched and no play occurs.

  On the other hand, the switching member in the above-described configuration is provided between the first inner member and the second inner member so as to be movable in the radial direction, and between the pin and the cage. A third elastic member that biases the elastic force inward in the direction, and a weight that is attached to one end of the pin and moves the pin outward in the radial direction against the elastic force of the third elastic member by centrifugal force A structure is desirable.

  According to such a structure, when the pin is in the radially innermost position due to the elastic force of the third elastic member, a power transmission state is achieved by bi-directional rotation. On the other hand, when the pin moves radially outward against the elastic force of the third elastic member due to the centrifugal force, a power transmission state is achieved by one-way rotation.

  The switching member in the above-described configuration includes an eccentric cam that is rotatably inserted between the first inner member and the second inner member, the eccentric cam, and the first inner member. The eccentric cam includes a third elastic member that urges the second inner member in a direction to press the second inner member, and the eccentric cam resists the elastic force of the third elastic member by centrifugal force. A structure that allows rotation is desirable.

  According to such a structure, when the eccentric cam presses the second inner member by the elastic force of the third elastic member, a power transmission state is achieved by bi-directional rotation. On the other hand, when the eccentric cam is rotated against the elastic force of the third elastic member by centrifugal force, and the elastic force of the second elastic member becomes larger than the pressing force to the second inner member by the eccentric cam. The second inner member rotates in one direction by the second elastic member, and a power transmission state is obtained by the one-way rotation.

  According to the present invention, the first inner member is inserted between the second inner member and the second inner member is pressed against the elastic force of the second elastic member. An engagement element interposed between the outer peripheral surface of the second inner member and the inner peripheral surface of the outer member is engaged in the wedge space, and the second force due to the elastic force of the second elastic member is applied when centrifugal force is applied. By providing a switching member that disengages the engagement element in the wedge space by one-way rotation of the inner member, an inexpensive rotation transmission device that does not consume power without using an electromagnetic clutch in a conventional rotation transmission device is provided. It is possible to switch between a power transmission state by bi-directional rotation and a power transmission state by one-way rotation.

  A plurality of pairs of engaging elements disposed in a wedge space formed between the outer peripheral surface of the first inner member and the second inner member and the inner peripheral surface of the outer member; Inserted between each pair of engaging members interposed between the outer peripheral surface of the outer member and the inner peripheral surface of the outer member and between the outer peripheral surface of the second inner member and the inner peripheral surface of the outer member. In addition, since the first elastic member that urges each pair of the engagement elements in the direction to engage with each other in the wedge space, there is no backlash when the rotation direction is switched between forward and reverse in the power transmission state. Occurrence of abnormal noise can be prevented and the life of the rotation transmission device can be improved.

  Hereinafter, embodiments of the rotation transmission device according to the present invention will be described in detail. 1 and 2 show a first embodiment of the present invention. FIGS. 1 (a) and 1 (b) show a power transmission state by bi-directional rotation, and FIGS. 2 (a) and 2 (b) show a power transmission state by one-way rotation, respectively. Show. 3 and 4 show a second embodiment of the present invention. FIGS. 3 (a) and 3 (b) show a power transmission state by bi-directional rotation, and FIGS. 4 (a) and 4 (b) show a power transmission state by one-way rotation. Respectively. Further, FIG. 5 shows an example in which the rotation transmission device in the first embodiment is applied to an ISG system mounted on a hybrid car or the like.

  The rotation transmission device in the first embodiment shown in FIGS. 1A and 1B is a first inner ring 10 that is a first inner member that outputs a rotational torque, and a second inner member that is a second inner member. Inner ring 20, outer ring 30 that is an outer member to which rotational torque is input, rollers 40a and 40b that are a plurality of pairs (four pairs in the figure), retainers 50, and a first spring 60 that is a first elastic member. The main part is composed of the second spring 70 as the second elastic member and the switch 80 as the switching member.

  The first inner ring 10 and the second inner ring 20 are coaxially arranged so as to be rotatable relative to each other in the forward and reverse directions while being joined to each other in the axial direction. At the center of the first inner ring 10, there are an inner shaft part 13 projecting on the second inner ring side (left side in FIG. 1 (b)) and an outer shaft part 15 projecting on the opposite second inner ring side (right side in FIG. 1 (b)). It is provided integrally. The inner shaft portion 13 of the first inner ring 10 is inserted and disposed in a recess 23 formed at the center of the second inner ring 20. The outer shaft portion 15 of the first inner ring 10 is led out to the outside as an output shaft.

  The first inner ring 10 has a convex portion 12 that protrudes in the radial direction at equal circumferential intervals (90 ° intervals) and extends in the axial direction (left direction in FIG. 1B). The surface is a cam surface 14 that forms a wedge space Ma with which the roller 40 a can be engaged and disengaged with the inner peripheral surface 32 of the outer ring 30. Moreover, the 1st inner ring | wheel 10 has the notch part 16 which notched the part in V shape.

  On the other hand, the second inner ring 20 protrudes in the radial direction at equal circumferential intervals (90 ° intervals) and further extends in the axial direction opposite to the first inner ring 10 (right direction in FIG. 1B). The outer peripheral surface of the convex portion 22 is a cam surface 24 that forms a wedge space Mb between which the roller 40 b can be engaged and disengaged with the inner peripheral surface 32 of the outer ring 30. Moreover, the 2nd inner ring | wheel 20 has the notch part 26 which notched the part in V shape. Furthermore, the 2nd inner ring | wheel 20 has the axial part 28 which made the center site | part protrude in the axial direction [FIG.1 (b) left direction].

  The convex portion 22 of the second inner ring 20 is arranged in a state where the phase is shifted by a predetermined angle in the circumferential direction with respect to the convex portion 12 of the first inner ring 10. Further, a part of the notch 26 of the second inner ring 20 overlaps with a part of the notch 16 of the first inner ring 10, so that the notch 16 of the first inner ring 10 and the notch 26 of the second inner ring 20 are overlapped. It is arranged in a state of penetrating in the axial direction.

  The outer ring 30 is coaxially arranged outside the first inner ring 10 and the second inner ring 20 so as to be able to rotate forward and backward. That is, the outer ring 30 is integrally provided on the cylindrical large-diameter portion 34 that accommodates the first inner ring 10 and the second inner ring 20 described above, and one end side (left side in FIG. 1B) of the large-diameter portion 34. The small diameter portion 36 is rotatably supported on the shaft portion 28 of the second inner ring 20 via the rolling bearing 102. The rolling bearing 102 interposed between the small diameter portion 36 and the shaft portion 28 of the second inner ring 20 is prevented from coming off by a retaining ring 104 attached to the shaft portion 28 of the second inner ring 20.

  A plurality of pairs (four pairs in FIG. 1A) of rollers 40 a and 40 b are arranged at equal intervals (90 ° intervals) along the circumferential direction of the outer ring 30. Of each pair of rollers 40a, 40b, one roller 40a is engaged in a wedge space Ma formed between the cam surface 14 of the convex portion 12 of the first inner ring 10 and the cylindrical inner peripheral surface 32 of the outer ring 30. The other roller 40b can be engaged and disengaged in a wedge space Mb formed between the cam surface 24 of the convex portion 22 of the second inner ring 20 and the cylindrical inner peripheral surface 32 of the outer ring 30. It is arranged in.

  The cage 50 has a bottomed cylindrical shape with one end side (the right side in FIG. 1B) opened, and a hole 54 formed in the bottom portion 52 is fitted into the root portion of the shaft portion 28 of the second inner ring 20. The retaining ring 106 attached to the base portion is prevented from coming off. Pockets 56a and 56b for accommodating the rollers 40a and 40b in a rollable manner are formed in the cylindrical portion 58 that integrally extends in the axial direction from the bottom 52 of the cage 50. The plate 51 is fixed to the opening end of the cylindrical portion 58 of the cage 50 in a state of being joined to the first inner ring 10 in the axial direction so as to close the opening of the cage 50, and the outer shaft portion 15 of the first inner ring 10. The stopper ring 108 is attached to the stopper ring 108 to prevent it from coming off. Therefore, the cage 50 can rotate integrally with the first inner ring 10 via the plate 51.

  The first spring 60 is a wedge space Ma formed between each pair of rollers 40 a and 40 b, that is, between the cam surface 14 of the convex portion 12 of the first inner ring 10 and the cylindrical inner peripheral surface 32 of the outer ring 30. Engagement / disengagement is achieved by a wedge space Mb formed between one roller 40a disposed in an engaged state, the cam surface 24 of the convex portion 22 of the second inner ring 20 and the cylindrical inner peripheral surface 32 of the outer ring 30. It is interposed between the other roller 40b arranged as possible. The elastic force of the first spring 60 biases each pair of rollers 40a and 40b toward the narrow side of the wedge spaces Ma and Mb, thereby causing the cam surfaces 14 and 24 of the first inner ring 10 and the second inner ring 20 and the outer ring 30 to be biased. The inner peripheral surface 32 is engaged with each other. FIG. 1A shows the cam surfaces 14 and 24 of the first inner ring 10 and the second inner ring 20 on the narrow side of the wedge spaces Ma and Mb and the outer ring due to the elastic force of the first spring 60. The state which is engaging between 30 inner peripheral surfaces 32 is shown.

  The second spring 70 is interposed between the opposed end surfaces of the convex portion 12 of the first inner ring 10 and the convex portion 22 of the second inner ring 20. The elastic force of the second spring 70 is urged in the direction in which the second inner ring 20 is rotated clockwise with respect to the first inner ring 10 (see FIG. 1A). Thereby, the convex part 22 of the 2nd inner ring | wheel 20 which makes a pair with this with respect to the convex part 12 of the 1st inner ring | wheel 10 is spaced apart along the circumferential direction. As a result, the wedge angle formed by the cam surface 14 of the convex portion 12 of the first inner ring 10 with respect to the inner peripheral surface 32 of the outer ring 30 does not change, but the cam surface 24 of the convex portion 22 of the second inner ring 20 The wedge angle formed with respect to the inner peripheral surface 32 is increased. Of the pair of rollers 40a and 40b, one roller 40a is engaged in the wedge space Ma, and the other roller 40b is separated in the wedge space Mb. It will be. FIG. 2A shows that between the pair of rollers 40 a and 40 b, one roller 40 a is between the cam surface 14 of the first inner ring 10 and the inner peripheral surface 32 of the outer ring 30 due to the elastic force of the second spring 70. The other roller 40b is separated from between the cam surface 24 of the second inner ring 20 and the inner peripheral surface 32 of the outer ring 30, and a minute gap Sb is formed between the inner peripheral surface 32 of the outer ring 30 and the other roller 40b. It shows the state.

  The switch 80 constitutes a round bar-like pin 82 arranged in parallel along the axial direction, a weight 84 attached to one end of the pin 82, the vicinity of one end of the pin 82, and a part of the cage 50. And a third spring 86 that is a third elastic member stretched between the plate 51 and the plate 51. At the tip and the center of the pin 82, a part of the notch 26 of the second inner ring 20 overlaps with a part of the notch 16 of the first inner ring 10, and the notch 16 and the first inner ring 10 The two inner rings 20 are arranged in a portion penetrating in the axial direction at the notch portion 26 of the inner ring 20, and are in contact with the inclined surface 11 of the notch portion 16 of the first inner ring 10 and the inclined surface 21 of the notch portion 26 of the second inner ring 20. Yes. In the upper part of the plate 51, a long hole-like slit 53 is formed along the radial direction, and a pin 82 is accommodated in the slit 53 so as to be movable in the radial direction, and the third spring 86 accommodated in the slit 53 together with the pin 82. Thus, the pin 82 is urged radially inward. A weight 84 attached to one end of the pin 82 is disposed outside the plate 51. In this switch 80, when a centrifugal force acts on the weight 84 due to the rotation of the first inner ring 10, the pin 82 moves radially outward against the elastic force of the third spring 86.

  An operation example of the rotation transmission device of the first embodiment having the above-described configuration will be described in detail below.

  FIGS. 1A and 1B show a power transmission state (a state in which the first inner ring 10 is rotated clockwise and counterclockwise by rotational input from the outer ring 30) by bi-directional rotation. In this state, the switch 80 is disposed in the radially innermost position (the lowermost position in FIG. 1A) in the slit 53 with the elastic force of the pin 82 toward the radially inner side of the third spring 86. . At this time, the first inner ring 10 is pressed clockwise with respect to the second inner ring 20 by the elastic force of the second spring 70. The pin 82 is placed on the inclined surface 11 of the notched portion 16 of the first inner ring 10 and the inclined surface 21 of the notched portion 26 of the second inner ring 20 so as to position-control the rotation of the second inner ring 20 against this pressing force. Abutting and sandwiched between both inclined surfaces 11 and 21.

  On the other hand, due to the elastic force of the first spring 60, each pair of rollers 40a and 40b interposed between the first inner ring 10 and the second inner ring 20 and the outer ring 30 has one roller 40a and the other roller 40b circumferentially. It is pressed so as to be separated in the direction. Of each pair of rollers 40a, 40b, one roller 40a is directed to the narrow side of the wedge space Ma formed between the cam surface 14 of the convex portion 12 of the first inner ring 10 and the inner peripheral surface 32 of the outer ring 30. The other roller 40 b is urged to engage between the cam surface 14 of the first inner ring 10 and the inner peripheral surface 32 of the outer ring 30, and the other roller 40 b is connected to the cam surface 24 of the convex portion 22 of the second inner ring 20 and the outer ring 30. The wedge space Mb formed between the inner peripheral surface 32 and the inner peripheral surface 32 is biased toward the narrow side and engaged between the cam surface 24 of the second inner ring 20 and the inner peripheral surface 32 of the outer ring 30. .

  As a result, when rotational torque in either the forward or reverse direction is input to the outer ring 30, the first inner ring 10 and the second inner ring 20 are moved to the outer ring 30 via the rollers 40 a and 40 b by the elastic force of the first spring 60. Since it is engaged in both forward and reverse directions, the rotational torque from the outer ring 30 is transmitted to the first inner ring 10 and the second inner ring 20. That is, the second inner ring 20 is rotated in the forward or reverse direction by the rotational torque input from the outer ring 30. Thus, the power transmission device functions as a two-way clutch.

  At this time, of each pair of rollers 40a and 40b, one roller 40a is formed on the narrow side (counterclockwise side) of the wedge space Ma between the cam surface 14 of the first inner ring 10 and the inner peripheral surface 32 of the outer ring 30. ) Is engaged between the cam surface 14 of the first inner ring 10 and the inner peripheral surface 32 of the outer ring 30, and the other roller 40 b is connected to the cam surface 24 of the second inner ring 20 and the inner periphery of the outer ring 30. It is biased toward the narrow side (clockwise side) of the wedge space Mb between the surface 32 and is engaged between the cam surface 24 of the second inner ring 20 and the inner peripheral surface 32 of the outer ring 30. . That is, the rollers 40a and 40b are engaged in the wedge spaces Ma and Mb in both the counterclockwise direction and the clockwise direction. Thereby, even if the direction of the rotational torque input to the outer ring 30 is switched between the forward and reverse directions, the play does not occur because the engagement state of the rollers 40a and 40b is not switched.

  Next, FIGS. 2A and 2B show a state where the rotational speed of the power transmission device is increased from the power transmission state due to the bi-directional rotation shown in FIGS. 1A and 1B, that is, the power transmission state due to the one-way rotation ( A state in which the first inner ring 10 is rotated counterclockwise by rotational input from the outer ring 30 is shown. When the power transmission device shown in FIGS. 1 (a) and 1 (b) is changed from the low-speed rotation state to the high-speed rotation state of the power transmission device shown in FIGS. 2 (a) and 2 (b), a switch is indicated as indicated by an arrow in FIG. 2 (b). A centrifugal force acting radially outward acts on the weight 84 of the 80, and the pin 82 moves against the elastic force of the third spring 86 radially outward in the slit 51 by the centrifugal force, and the radially outermost position. It is arranged at [the uppermost position in FIG. 2 (a)]. That is, the pin 82 of the switch 80 is removed from the state in which it is in contact with the inclined surface 11 of the notched portion 16 of the first inner ring 10 and the inclined surface 21 of the notched portion 26 of the second inner ring 20.

  As a result, the second inner ring 20 rotates clockwise relative to the first inner ring 10 by the elastic force of the second spring 70. By this rotation, the convex portion 22 of the second inner ring 20 that is paired with the convex portion 12 of the first inner ring 10 is separated along the circumferential direction, and the convex portion 12 of the first inner ring 10 is separated. The wedge angle formed by the cam surface 14 with respect to the inner peripheral surface 32 of the outer ring 30 is increased. On the other hand, the wedge angle formed by the cam surface 24 of the convex portion 22 of the second inner ring 20 with respect to the inner peripheral surface 32 of the outer ring 30 does not change.

  As a result, of the pair of rollers 40a and 40b pressed so as to be separated from each other in the circumferential direction by the elastic force of the first spring 60, one of the rollers 40b has the pocket 56b of the cage 50 by the pressing force. Is pressed against the outer end surface of the outer periphery of the outer ring 30 and is released in the wedge space Mb, and a minute gap Sb is generated between the roller 40b and the inner peripheral surface 32 of the outer ring 30. On the other hand, the other roller 40 a maintains the engaged state in the wedge space Ma between the cam surface 14 of the first inner ring 10 and the inner peripheral surface 32 of the outer ring 30.

  As a result, the outer ring 30 and the rollers 40a and 40b can rotate in one counterclockwise direction. That is, the counterclockwise rotational torque from the outer ring 30 is transmitted to the first inner ring 10 and the second inner ring 20, and the second inner ring 20 is output and rotated counterclockwise by the rotational torque input from the outer ring 30. On the other hand, the clockwise rotational torque from the outer ring 30 is not transmitted to the first inner ring 10 and the second inner ring 20, and the outer ring 30 rotates idly. Thus, the power transmission device functions as a one-way clutch.

  When this power transmission device shifts from the high speed rotation state (see FIGS. 2 (a) and 2 (b)) to the low speed rotation state (see FIGS. 1 (a) and (b)), the centrifugal force is reversed. Does not act on the weight 84, and the pin 82 of the switch 80 moves radially inward by the elastic force of the third spring 86, so that the inclined surface 11 of the notch 16 of the first inner ring 10 and the second inner ring 20 are moved. It enters between the inclined surface 21 of the notch 26. Thereby, the pin 82 presses the inclined surface 21 of the notch 26 of the second inner ring 20, and the second inner ring 20 rotates counterclockwise with respect to the first inner ring 10. As a result, the other roller 40b is engaged with the wedge space Mb between the cam surface 24 of the second inner ring 20 and the inner peripheral surface 32 of the outer ring 30, and the rotational torque input from the outer ring 30 is prevented. Thus, the second inner ring 20 can be rotated in both the clockwise and counterclockwise directions. That is, the one-way clutch is shifted to the two-way clutch.

  In the first embodiment described above, the case where the switch 80 having the pin 82 is used as the switching member for switching between the two-way clutch function and the one-way clutch function has been described, but the present invention is limited to this. Instead, a switch 81 having an eccentric cam 83 can be used as a switching member as in the second embodiment shown in FIGS.

  FIGS. 3 (a) and 3 (b) correspond to FIGS. 1 (a) and 1 (b) in the first embodiment, and show a power transmission state by bi-directional rotation. FIGS. 4 (a) and 4 (b) show the first embodiment. It corresponds to FIGS. 2A and 2B in the embodiment, and shows a power transmission state by one-way rotation. Note that, in the following second embodiment, the same parts as those in the rotation transmission device in the first embodiment are denoted by the same reference numerals, and redundant description is omitted. The difference between the two embodiments is a switching member, which is only a switch 80 having a pin 82 and a switch 81 having an eccentric cam 83.

  The switch 80 in the first embodiment switches the two-way clutch function and the one-way clutch function by moving the pin 82 in the radial direction by centrifugal force by switching between the low speed rotation and the high speed rotation in the power transmission device. I have to. On the other hand, the switch 81 in the second embodiment has a two-way clutch function and a one-way clutch by rotating the eccentric cam 83 by centrifugal force by switching between low speed rotation and high speed rotation in the power transmission device. Switch between functions.

  That is, in the rotation transmission device according to the second embodiment, as shown in FIGS. 3A and 3B, the switch 81 rotates the water droplet-shaped eccentric cam 83 and the eccentric cam 83 at a position shifted from the center thereof. The shaft 85 is movably supported, and the third spring 87 is a third elastic member stretched between the convex portion 12 of the first inner ring 10 and the eccentric cam 83.

  The eccentric cam 83 of the switch 81 is configured such that a part of the notch portion 26 of the second inner ring 20 overlaps with a part of the notch part 16 of the first inner ring 10 and the second notch 16 of the first inner ring 10 and the second notch 16. The notch 26 of the inner ring 20 is disposed in a portion penetrating in the axial direction and is brought into contact with the inclined surface 11 of the notch 16 of the first inner ring 10 and the inclined surface 21 of the notch 26 of the second inner ring 20. Yes. Further, the shaft 85 of the switch 81 is arranged in parallel along the axial direction, and the base end thereof is fixed to the plate 51 that is integrated with the cage 50. The third spring 87 of the switch 81 presses the eccentric cam 83 counterclockwise (leftward in FIG. 3A) against the first inner ring 10.

  In this switch 81, the eccentric cam 83 is rotated by the centrifugal force acting by the rotation of the power transmission device, and its posture is changed between the first inner ring 10 and the second inner ring 20, so that power transmission by bi-directional rotation is achieved. The state and the power transmission state by one-way rotation are switched.

  That is, in the power transmission state by the bi-directional rotation shown in FIGS. 3A and 3B, the switch 81 causes the eccentric cam 83 to press the second inner ring 20 counterclockwise by the elastic force of the third spring 87. At this time, the pressing force of the eccentric cam 83 overcomes the elastic force of the second spring 70 that presses the second inner ring 20 clockwise against the first inner ring 10. Therefore, the eccentric cam 83 abuts on the inclined surface 21 of the notch portion 26 of the second inner ring 20 so as to position-control the rotation of the second inner ring 20 against the pressing force by the elastic force of the second spring 70. Yes.

  On the other hand, due to the elastic force of the first spring 60, each pair of rollers 40a and 40b interposed between the first inner ring 10 and the second inner ring 20 and the outer ring 30 has one roller 40a and the other roller 40b circumferentially. The one roller 40a is urged toward the narrow side of the wedge space Ma formed between the cam surface 14 of the first inner ring 10 and the inner peripheral surface 32 of the outer ring 30. The other roller 40b is in a state of being urged and engaged with the narrow side of the wedge space Mb formed between the cam surface 24 of the second inner ring 20 and the inner peripheral surface 32 of the outer ring 30. Yes.

  As a result, when rotational torque in either the forward or reverse direction is input to the outer ring 30, the first inner ring 10 and the second inner ring 20 are moved to the outer ring 30 via the rollers 40 a and 40 b by the elastic force of the first spring 60. Since it is engaged in both forward and reverse directions, the rotational torque from the outer ring 30 is transmitted to the first inner ring 10 and the second inner ring 20. That is, the second inner ring 20 is output and rotated in either the forward or reverse direction by the rotational torque input from the outer ring 30, and the power transmission device functions as a two-way clutch.

  At this time, as in the case of the first embodiment, since the rollers 40a and 40b are engaged in the wedge spaces Ma and Mb in both the counterclockwise direction and the clockwise direction, the rotational torque input to the outer ring 30 is reduced. Even if the direction is switched between forward and reverse, there is no backlash due to the absence of switching of the engagement state of the rollers 40a and 40b.

  Next, when the low-speed rotation state of the power transmission device shown in FIGS. 3A and 3B is changed to the high-speed rotation state of the power transmission device shown in FIGS. The centrifugal force toward the outside acts and the attitude of the eccentric cam 83 changes. That is, in the state shown in FIG. 3A, the attitude (center line L) of the eccentric cam 83 with respect to the rotation center (shaft 85) is slightly tilted from the radial direction, but in the state shown in FIG. The posture (center line L) with respect to the rotation center of the eccentric cam 83 changes so as to coincide with the radial direction.

  Due to the change in posture of the eccentric cam 83, the pressing force of the eccentric cam 83 that presses the second inner ring 20 by the third spring 87 is reduced, and the second inner ring 20 is pressed clockwise against the first inner ring 10. The elastic force of the spring 70 overcomes the pressing force of the eccentric cam 83. As a result, the second inner ring 20 rotates clockwise with the elastic force of the second spring 70. Due to this rotation, the convex portion 22 of the second inner ring 20 is separated from the convex portion 12 of the first inner ring 10 along the circumferential direction, and the cam surface 14 of the convex portion 12 of the first inner ring 10 becomes the outer ring. The wedge angle formed with respect to the inner peripheral surface 32 of 30 is increased. On the other hand, the wedge angle formed by the cam surface 24 of the second inner ring 20 with respect to the inner peripheral surface 32 of the outer ring 30 does not change.

  As a result, due to the elastic force of the first spring 60, one of the pair of rollers 40a and 40b is pressed against the outer end surface of the pocket 56b of the cage 50 by the pressing force, and is separated from the wedge space Mb. Thus, a minute gap Sb is generated between the roller 40b and the inner peripheral surface 32 of the outer ring 30. On the other hand, the other roller 40 a maintains the engaged state in the wedge space Ma between the cam surface 14 of the first inner ring 10 and the inner peripheral surface 32 of the outer ring 30.

  Therefore, the outer ring 30 and the rollers 40a and 40b can be rotated in one counterclockwise direction. That is, the counterclockwise rotational torque from the outer ring 30 is transmitted to the first inner ring 10 and the second inner ring 20, and the second inner ring 20 is output and rotated counterclockwise by the rotational torque input from the outer ring 30. On the other hand, the clockwise rotational torque from the outer ring 30 is not transmitted to the first inner ring 10 and the second inner ring 20, and the outer ring 30 rotates idly. Thus, the power transmission device functions as a one-way clutch.

  When this power transmission device shifts from the high speed rotation state (see FIGS. 4 (a) and (b)) to the low speed rotation state (see FIGS. 3 (a) and (b)), the centrifugal force is reversed. Does not act on the eccentric cam 83, the pressing force by which the eccentric cam 83 of the switch 81 presses the second inner ring 20 by the third spring 87 increases, and the second inner ring 20 rotates counterclockwise. As a result, the other roller 40b is engaged in the wedge space Mb between the cam surface 24 of the second inner ring 20 and the inner peripheral surface 32 of the outer ring 30, and the rotational torque input from the outer ring 30 is prevented. The second inner ring 20 rotates in both clockwise and counterclockwise directions. That is, the one-way clutch is shifted to the two-way clutch.

  By the way, the present invention can be applied to a simple system mounted on a hybrid car for the purpose of improving the fuel efficiency of an automobile, a so-called ISG (Integrated Starter Generator) system. FIG. 5 shows an application example in which the rotation transmission device 110 in the first embodiment is connected between the motor generator 120 (MG) and the pulley 130 in the generator pulley of the ISG system using both the engine and the electric motor. In this configuration example, the small diameter portion 36 of the outer ring 30 of the rotation transmission device 110 extends in the axial direction and is connected to the motor generator 120, and the outer shaft portion 15 of the first inner ring 10 extends in the axial direction to pull the pulley 130. The axis of rotation. The pulley 130 is wrapped around a belt (not shown), and is connected to an engine (not shown) via the belt.

  When the pulley 130 rotates at a high speed, the rotation transmission device 110 functions as a one-way clutch and enters a power transmission state of the one-way clutch, and the power from the engine is transmitted to the motor generator 120 via the rotation transmission device 110. The generator 120 is caused to generate power. At this time, when the pulley 130 shifts to a low speed rotation while the motor generator 120 maintains a high speed rotation due to the inertia of the motor generator 120, the rotation transmission device 110 enters a power cut-off state of the one-way clutch and the outer ring 30 It will be idle.

  Thus, even when the pulley 130 rotates at a low speed, the motor generator 120 can be ensured to rotate at a high speed, and the phenomenon that the motor generator 120 rotates at a low speed can be reduced. It becomes easy to improve the power generation efficiency. In addition, since the rotation transmission device 110 is in the power cutoff state of the one-way clutch, fluctuations in the tension of the belt wrapped around the pulley 130 can be reduced, so that the life of the belt can be extended.

  On the other hand, when motor generator 120 functions as a starter motor, rotation transmission device 110 functions as a two-way clutch, and the power of motor generator 120 can be transmitted to the engine via rotation transmission device 110.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the scope of the present invention. The scope of the present invention is not limited to patents. It includes the equivalent meanings recited in the claims, and the equivalent meanings recited in the claims, and all modifications within the scope.

In the power transmission state by the bi-directional rotation of the rotation transmission device according to the first embodiment of the present invention, (a) is a sectional view taken along line BB in (b), and (b) is line AA in (a). FIG. In the power transmission state by one-way rotation of the rotation transmission device according to the first embodiment of the present invention, (a) is a cross-sectional view taken along line DD of (b), and (b) is CC of (a). It is sectional drawing which follows a line. In the power transmission state by the bi-directional rotation of the rotation transmission device in the second embodiment of the present invention, (a) is a sectional view taken along line FF in (b), and (b) is line EE in (a). FIG. (A) is sectional drawing in alignment with the HH line of (b), (b) is GG of (a) in the power interruption state by one-way rotation of the rotation transmission apparatus in 2nd embodiment of this invention. It is sectional drawing which follows a line. It is a block diagram which shows the application example which connected the rotation transmission apparatus in 1st embodiment between the motor generator and the pulley.

Explanation of symbols

10 First inner member (first inner ring)
14 The outer peripheral surface (cam surface) of the first inner member
20 Second inner member (second inner ring)
24 The outer peripheral surface (cam surface) of the second inner member
30 Outer member (outer ring)
32 Inner peripheral surface 40a, 40b of outer member Engagement element (roller)
50 Cage 56a, 56b Pocket 60 First elastic member (first spring)
70 Second elastic member (second spring)
80, 81 switching member (switch)
82 Pin 83 Eccentric cam 84 Weight 86, 87 Third elastic member (third spring)
Ma, Mb wedge space

Claims (3)

A first inner member and a second inner member that are coaxially disposed so as to be rotatable forward and backward, and a positive member that is coaxially disposed on the outside of the first inner member and the second inner member. An outer member capable of rotating in reverse, one engagement element arranged in a state of being engaged in a wedge space formed between the outer peripheral surface of the first inner member and the inner peripheral surface of the outer member, and the first engaging member A plurality of pairs of engagement elements including the other engagement elements arranged to be disengageable in a wedge space formed between the outer peripheral surface of the two inner members and the inner peripheral surface of the outer member; A cage connected to the inner member and having a pocket for accommodating each pair of engaging members so as to roll in the circumferential direction, and between the outer peripheral surface of the first inner member and the inner peripheral surface of the outer member And a pair of engagement elements interposed between the outer peripheral surface of the second inner member and the inner peripheral surface of the outer member, respectively, and engaging both the engagement elements in the wedge space. The first elastic member to be urged, and the first inner member and the second inner member are inserted between the first inner member and the second inner member in one direction with respect to the first inner member. A second elastic member that rotates and urges the engaging element interposed between the outer peripheral surface of the second inner member and the inner peripheral surface of the outer member in a direction to disengage in the wedge space;
The second inner member is interposed between the first inner member and the second inner member and presses the second inner member against the elastic force of the second elastic member. An engagement element interposed between the outer peripheral surface of the member and the inner peripheral surface of the outer member is engaged in the wedge space, and one of the second inner members is caused by the elastic force of the second elastic member when centrifugal force is applied. A rotation transmission device comprising a switching member for detaching the engagement element in a wedge space by rotating in a direction.   The switching member is provided between the first inner member and the second inner member so as to be movable in the radial direction, and between the pin and the cage, and is elastic inward in the radial direction. 2. A third elastic member that urges a force, and a weight that is attached to one end of the pin and moves the pin radially outward against the elastic force of the third elastic member by centrifugal force. The rotation transmission device according to 1.   The switching member is provided between an eccentric cam rotatably inserted between the first inner member and the second inner member, and between the eccentric cam and the first inner member. The eccentric cam comprises a third elastic member that urges the second inner member in a pressing direction, and the eccentric cam is rotated against the elastic force of the third elastic member by centrifugal force. The rotation transmission device according to claim 1.

Images