JP6010996B2 - Driving force transmission device - Google Patents

Description

  The present invention relates to a driving force transmission device.

  In a driving force transmission device using a friction clutch plate, the clutch plates may slide and rotate due to drag torque when not engaged, that is, when two wheels are driven. For this reason, turning performance is deteriorated and fuel consumption is deteriorated. Therefore, Japanese Patent Laid-Open No. 4-92126 (Cited Document 1) describes that relative rotation does not occur between clutch plates when not engaged.

JP-A-4-92126

  An object of the present invention is to provide a driving force transmission device that prevents relative rotation from occurring between clutch plates when not engaged, by a configuration different from the conventional one.

(Claim 1) A driving force transmission device according to this means includes a cylindrical outer rotating member, an inner rotating member coaxially disposed in the outer rotating member so as to be relatively rotatable, the outer rotating member, and the An intermediate rotating member arranged coaxially so as to be rotatable relative to the inner rotating member in a radial direction; a friction main clutch plate that transmits torque between the outer rotating member and the intermediate rotating member; A two-way clutch disposed between the rotating member and the inner rotating member and having a roller and a retainer for holding the roller, and a pilot capable of transmitting the torque of the outer rotating member by attracting the armature to the yoke side by magnetic force an electromagnetic clutch device comprising a clutch plate, is provided between the pilot clutch plate and the friction main clutch plate, via the pilot clutch plate The phase difference between the rotation of the outer rotating member transmitted and the rotation of the cage of the two-way clutch restricted by the moving cam member is converted into an axial pressing force, and the moving cam member is moved in the axial direction. And a cam mechanism that presses the friction-type main clutch plate by being moved.
The movable cam member of the cam mechanism is restricted in rotation with respect to the cage of the two-way clutch, and when the cage of the two-way clutch is positioned at a neutral position, When the cage of the two-way clutch deviates from the neutral position in the circumferential direction, the two-way clutch rotates together with the intermediate rotation member.

(Claim 2) In addition, the two-way clutch includes a plurality of circumferential biasing member that biases said retainer against said inner rotary member in the circumferential direction of the neutral position, while toward the neutral position in each of the rotational direction and opposite rotational direction to the neutral position, the plurality of circumferential direction biasing members each may be urged to so that the plurality of locations in the circumferential direction of the retainer.

(Claim 3) Further, the cage is provided so as to be movable in the axial direction with respect to the inner rotating member, and the two-way clutch moves the cage toward the moving cam member with respect to the inner rotating member. An axial biasing member for biasing, and a pin provided on the inner rotating member, wherein the retainer is formed with an engagement hole, and the engagement hole is formed on the movable cam member. When the cage is not pressed in the axial direction, the cage is biased by the axial biasing member to engage the pin to hold the cage in a neutral position in the circumferential direction, and the cage When the pin is pressed in the axial direction by the moving cam member against the axial urging member, the engagement with the pin is released to allow the cage to move in the circumferential direction from the neutral position. It may be.

  (Claim 1) According to the driving force transmission device according to the present means, the torque transmission state and the torque non-transmission state are switched between the intermediate rotation member and the inner rotation member by the two-way clutch. Here, when the cage of the two-way clutch is located at the neutral position, the intermediate rotating member and the inner rotating member can be relatively rotated. On the other hand, when the cage rotates relative to the intermediate rotating member and the inner rotating member, the cage moves in the circumferential direction from the neutral position, and the intermediate rotating member and the inner rotating member are locked via the roller. The

  In this means, when the torque is not transmitted between the outer rotating member and the inner rotating member, the following operation is performed. The electromagnetic clutch device is deenergized and the pilot clutch plate is disengaged. That is, the cam mechanism, the cage and the roller are in a free state (unregulated state) with respect to the outer rotating member. Therefore, the roller is positioned at the neutral position, and the intermediate rotating member and the inner rotating member are in a state of being relatively rotatable.

  Here, since the friction type main clutch plates are not pressed by the moving cam member, the main clutch plates are not frictionally engaged with each other. However, when a drag torque between adjacent main clutch plates is generated, the intermediate rotating member generates a force that rotates together with the outer rotating member. However, since the intermediate rotating member is in a state of being rotatable relative to the inner rotating member, even if the intermediate rotating member rotates together with the outer rotating member, the torque is not transmitted to the inner rotating member. Thus, even if drag torque is generated in the friction main clutch plate, torque is not transmitted between the outer rotating member and the inner rotating member. Therefore, deterioration of fuel consumption can be suppressed without lowering turning performance.

  On the other hand, when the torque is transmitted between the outer rotating member and the inner rotating member, the following operation is performed. The electromagnetic clutch device is energized and the pilot clutch plate is engaged. Then, the rotational phases of the inner rotating member and the moving cam member are shifted, and as a result, the rotational phases of the inner rotating member and the two-way clutch cage are shifted. If it does so, a two-way clutch will be in an engagement state and will be in a torque transmission state between an intermediate | middle rotation member and an inner side rotation member. Furthermore, when the moving cam member presses the friction type main clutch plate, the main clutch plates are engaged with each other. As a result, the torque of the outer rotating member is transmitted to the intermediate rotating member via the main clutch plate, and the torque of the intermediate rotating member is transmitted to the inner rotating member via the two-way clutch. Therefore, when the electromagnetic clutch device is energized, the differential between the outer rotating member and the inner rotating member is suppressed.

  (Claim 2) The two-way clutch can be reliably returned to the neutral position by the circumferential urging member. Accordingly, relative rotation between the intermediate rotation member and the inner rotation member can be allowed in the neutral position.

  (Claim 3) In order to position the retainer in the neutral position, the engagement between the engagement hole formed in the retainer and the pin is utilized, and the axial direction of the retainer by the axial biasing member is used. I use travel. As described above, since the pin and the engagement hole are physically positioned, even if a force that causes the moving cam member to rotate relative to the inner rotating member due to inertia occurs, the cage is in the neutral position. Can continue to maintain.

  Further, the engagement between the pin and the engagement hole is released by the movement of the movable cam member in the axial direction. As the movable cam member moves in the axial direction in this way, the friction main clutch plate is engaged and the two-way clutch is also engaged. Therefore, when the electromagnetic clutch device is energized, torque is transmitted between the outer rotating member and the inner rotating member.

1st embodiment: It is an axial sectional view of a driving force transmission device. FIG. 2 is an enlarged view of a periphery of a two-way clutch constituting the device when the electromagnetic coil of the driving force transmission device in FIG. 1 is in a non-energized state. FIG. 2 is a radial cross-sectional view of a two-way clutch constituting the driving force transmission device of FIG. 1 in a non-engaged state. It is the figure which looked at the holder | retainer which comprises the two-way clutch of FIG. 2 from radial direction. It is the figure which looked at the holder | retainer of FIG. 5 from the axial direction of the right side. It is the figure which looked at the assembly | attachment state of the roller which comprises the two-way clutch of FIG. 2, a holder | retainer, a bush, and the circumferential direction biasing member from radial direction. It is the figure which looked at the assembly | attachment state of FIG. 6 from the axial direction of the right side. FIG. 2 is an enlarged view around a two-way clutch when an electromagnetic coil of the driving force transmission device in FIG. 1 is energized. It is radial direction sectional drawing in the engagement state of the two-way clutch of FIG. 2nd embodiment: It is an axial sectional view of a driving force transmission device. It is an enlarged view of the periphery of the two-way clutch which comprises the said apparatus, when the electromagnetic coil of the driving force transmission apparatus of FIG. It is the figure which looked at the assembly state of the roller which comprises the two-way clutch of FIG. 11, a holder | retainer, and a bush from radial direction. FIG. 11 is an enlarged view of the periphery of a two-way clutch constituting the device when the electromagnetic coil of the driving force transmission device of FIG. 10 is energized. It is the figure which looked at the assembly state of the roller which comprises the two-way clutch of FIG. 13, a holder | retainer, and a bush from radial direction.

<First embodiment>
(Configuration of driving force transmission device)
The driving force transmission device 1 according to the first embodiment will be described with reference to FIGS. The driving force transmission device 1 is applied to, for example, a driving force transmission system to an auxiliary driving wheel side in which a driving force is transmitted according to a traveling state of a vehicle in a four-wheel drive vehicle. More specifically, in a four-wheel drive vehicle, the driving force transmission device 1 includes, for example, a propeller shaft to which engine driving force is transmitted and a rear differential as an auxiliary driving wheel, or a rear differential and a drive shaft. It is connected between. In the following description, the former case will be described as an example. The driving force transmission device 1 transmits the driving force transmitted from the propeller shaft to the auxiliary driving wheel while changing the transmission ratio. The driving force transmission device 1 acts to reduce the rotation difference when, for example, a rotation difference between the front wheels and the rear wheels occurs.

  The driving force transmission device 1 includes a so-called electronic control coupling. As shown in FIG. 1, the driving force transmission device 1 includes an outer rotating member 10, an inner rotating member 20, an intermediate rotating member 30, a friction main clutch plate 40, a two-way clutch 50, and a pilot clutch plate mechanism. The electromagnetic clutch apparatus 60 which comprises these, and the cam mechanism 70 are provided.

  The outer rotating member 10 is supported on the inner peripheral side of the cylindrical hole cover 2 so as to be rotatable with respect to the hole cover 2. The outer rotating member 10 is formed in a cylindrical shape as a whole, and is formed by a front housing 11 disposed on the vehicle front side and a rear housing 12 disposed on the vehicle rear side.

  The front housing 11 is formed of, for example, an aluminum alloy made of a nonmagnetic material mainly composed of aluminum, and has a bottomed cylindrical shape. The outer peripheral surface of the cylindrical portion of the front housing 11 is rotatably supported on the inner peripheral surface of the hole cover 2 via a bearing. Further, the bottom of the front housing 11 is connected to the vehicle rear end side of a propeller shaft (not shown). That is, the bottomed cylindrical opening side of the front housing 11 is disposed so as to face the vehicle rear side. A female spline 11a is formed in the axially central portion of the inner peripheral surface of the front housing 11, and a female screw is formed near the opening of the inner peripheral surface.

  The rear housing 12 is formed in an annular shape, and is disposed integrally with the front housing 11 on the radially inner side on the opening side of the front housing 11. On the vehicle rear side of the rear housing 12, an annular groove is formed that opens in the axial direction over the entire circumference. A part of the bottom of the annular groove (left side in FIG. 1) of the rear housing 12 is provided with an annular member 12a formed of, for example, stainless steel as a nonmagnetic material. Parts of the rear housing 12 other than the annular member 12a are made of a material containing iron as a main component (hereinafter referred to as “iron-based material”), which is a ferromagnetic material, in order to form a magnetic circuit. A male screw is formed on the outer peripheral surface of the rear housing 12, and the male screw is screwed to the female screw of the front housing 11. The front housing 11 and the rear housing 12 are fixed by tightening the female screw of the front housing 11 to the male screw of the rear housing and bringing the end surface of the front side of the front housing 11 into contact with the end surface of the stepped portion of the rear housing.

  The inner rotating member 20 is formed in a cylindrical shape, and a female spline 20a is formed on the inner peripheral surface thereof. The inner rotating member 20 passes through a central through hole of the rear housing 12 in a liquid-tight manner, and is coaxially disposed in the outer rotating member 10 so as to be relatively rotatable. Further, the drive pinion gear 4 is inserted inside the inner rotating member 20, and the male spline of the drive pinion gear 4 is fitted to the female spline 20 a of the inner rotating member 20. The inner rotating member 20 is rotatably supported by the front housing 11 and the rear housing 12 via a bearing in a state where the axial position is restricted with respect to the front housing 11 and the rear housing 12. The space that is liquid-tightly partitioned by the outer rotating member 10 and the inner rotating member 20 is filled with lubricating oil at a predetermined filling rate.

  The intermediate rotation member 30 is formed in a cylindrical shape, and is coaxially disposed so as to be relatively rotatable between the outer rotation member 10 and the inner rotation member 20 in the radial direction. A male spline 30 a is formed on the outer peripheral surface of the intermediate rotating member 30.

  The friction main clutch plate 40 transmits torque between the outer rotating member 10 and the intermediate rotating member 30. The friction type main clutch plate 40 is a wet multi-plate type friction clutch formed of an iron-based material. The main clutch plate 40 is disposed between the inner peripheral surface of the cylindrical portion of the front housing 11 and the outer peripheral surface of the intermediate rotating member 30. The main clutch plate 40 includes a plurality of inner main clutch plates 41 and a plurality of outer main clutch plates 42, which are alternately arranged in the axial direction. Each inner main clutch plate 41 has a female spline 41 a formed on the inner peripheral side, and is fitted to the male spline 30 a of the intermediate rotating member 30. Each outer main clutch plate 42 has a male spline 42 a formed on the outer peripheral side, and is fitted to the female spline 11 a of the front housing 11.

  The two-way clutch 50 is disposed between the inner rotating member 20 and the intermediate rotating member 30. That is, the two-way clutch 50 can switch between a torque non-transmission state, a one-way torque transmission state, and a torque transmission state in the other direction between the intermediate rotation member 30 and the inner rotation member 20.

  As shown in FIGS. 1 and 2, the two-way clutch 50 includes a cylindrical inner peripheral surface 51 formed on the inner peripheral surface of the intermediate rotating member 30 and a polygon outer peripheral surface 52 ( In this embodiment, a 12-sided outer peripheral surface), a plurality of rollers 53, a cage 54, a bush 55, and a circumferential urging member 56 are provided.

  As shown in FIG. 3, the cylindrical inner peripheral surface 51 of the intermediate rotating member 30 and the polygonal outer peripheral surface 52 of the inner rotating member 20 face each other in the radial direction. Accordingly, the radial distance between the cylindrical inner peripheral surface 51 and the polygonal outer peripheral surface 52 varies depending on the circumferential position. That is, the radial distance between the apex of the polygonal outer peripheral surface 52 and the cylindrical inner peripheral surface 51 is the shortest, and the radial distance between the center of the polygon outer peripheral surface 52 and the cylindrical inner peripheral surface 51 is the longest. Here, the latter position is the neutral position of the two-way clutch 50.

  The plurality of rollers 53 are arranged one by one on each side of the polygonal outer peripheral surface 52, and are arranged between the polygonal outer peripheral surface 52 and the cylindrical inner peripheral surface 51 in the radial direction. When the roller 53 is positioned at the neutral position, the roller 53 can be rotated relative to the cylindrical inner peripheral surface 51. That is, when the roller 53 is positioned at the neutral position, relative rotation between the inner rotating member 20 and the intermediate rotating member 30 is allowed. On the other hand, when the roller 53 moves in the circumferential direction from the neutral position on the polygonal outer peripheral surface 52, the roller 53 restricts relative rotation with respect to the inner rotating member 20 and the intermediate rotating member 30 by the wedge effect.

  As shown in FIGS. 4 and 5, the retainer 54 has an annular portion 54a in which a plurality of window portions 54b are formed in the circumferential direction, and extends in the axial direction from one axial end of the annular portion 54a and further has a diameter. A plurality of claw portions 54c extending outward in the direction. As shown in FIGS. 1 and 2, the retainer 54 is in a state where the rollers 53 are held by the respective window portions 54b, and the claw portions 54c are on the side opposite to the bottom surface of the outer rotating member 10 (FIGS. 1 and 2). Between the cylindrical inner peripheral surface 51 and the polygonal outer peripheral surface 52 so as to be located on the right side of FIG.

  The bush 55 is formed in an annular shape, and is fixed to the polygonal outer peripheral surface 52 by press-fitting as shown in FIGS. 1 and 2. The bush 55 is disposed adjacent to the claw portion 54 c side of the annular portion 54 a of the cage 54. Furthermore, a plurality of recesses 55a are formed on the outer peripheral side of the bush 55 in the circumferential direction so as not to interfere with the claw portion 54c.

  The circumferential urging members 56 are disposed between the wall portions on both sides in the circumferential direction of the recess 55a and the wall portions on both sides in the circumferential direction of the claw portion 54c. The circumferential urging member 56 is formed, for example, in a U shape, and urges the claw 54 c in the circumferential direction toward the bush 55 in a direction in which the claw 54 c returns to the neutral position.

  The electromagnetic clutch device 60 engages the pilot clutch plates 64 by pulling the armature 63 toward the yoke 61 by magnetic force. That is, the electromagnetic clutch device 60 transmits the torque of the outer rotating member 10 to the support cam member 71 constituting the cam mechanism 70. As shown in FIG. 1, the electromagnetic clutch device 60 includes a yoke 61, an electromagnetic coil 62, an armature 63, and a pilot clutch plate 64.

  The yoke 61 is formed in an annular shape and is accommodated in an annular groove of the rear housing 12 through a gap so as to be rotatable relative to the rear housing 12. The yoke 61 is fixed to the rear cover 3. The electromagnetic coil 62 is formed in an annular shape by winding a winding, and is fixed to the yoke 61.

  The armature 63 is formed of, for example, a ferromagnetic material that is an iron-based material, and is formed in an annular shape including a male spline on the outer peripheral side. The armature 63 is disposed between the friction main clutch plate 40 and the rear housing 12 in the axial direction. Then, the outer peripheral side of the armature 63 is fitted to the female spline 11a of the front housing 11. That is, the armature 63 is provided such that it cannot rotate relative to the outer rotating member 10 and can move in the axial direction. When a current is supplied to the electromagnetic coil 62, the armature 63 acts so as to be drawn toward the yoke 61 by a magnetic force.

  The pilot clutch plate 64 transmits torque between the outer rotating member 10 and the support cam member 71. The pilot clutch plate 64 is made of an iron-based material. The pilot clutch plate 64 is disposed between the inner peripheral surface of the cylindrical portion of the front housing 11 and the outer peripheral surface of the support cam member 71. Further, the pilot clutch plate 64 is disposed between the armature 63 and the rear housing 12. The pilot clutch plate 64 includes an inner pilot clutch plate 64a and an outer pilot clutch plate 64b, and is alternately arranged in the axial direction. The inner pilot clutch plate 64 a has a female spline formed on the inner peripheral side, and is fitted to the male spline of the support cam member 71. The outer pilot clutch plate 64 b has a male spline formed on the outer peripheral side, and is fitted to the female spline 11 a of the front housing 11.

  When current is supplied to the electromagnetic coil 62, the yoke 61, the outer peripheral side of the rear housing 12, the outer peripheral side of the pilot clutch plate 64, the armature 63, the inner peripheral side of the pilot clutch plate 64, and the inner peripheral side of the rear housing 12 A magnetic circuit passing through the yoke 61 is formed. Then, the armature 63 is drawn toward the yoke 61, and the inner pilot clutch plate 64a and the outer pilot clutch plate 64b are frictionally engaged. Then, the torque of the outer rotating member 10 is transmitted to the support cam member 71. On the other hand, when the current supply to the electromagnetic coil 62 is interrupted, the attractive force to the armature 63 is lost, and the frictional engagement between the inner pilot clutch plate 64a and the outer pilot clutch plate 64b is released.

  The cam mechanism 70 is provided between the main clutch plate 40 and the pilot clutch plate 64, and torque based on the rotational difference between the outer rotating member 10 and the cage 54 of the two-way clutch 50 transmitted via the pilot clutch plate 64. Is converted into an axial pressing force to press the main clutch plate 40. The cam mechanism 70 includes a support cam member 71, a moving cam member 72, and a cam follower 73.

  The support cam member 71 is formed in an annular shape having a male spline on the outer peripheral side. A cam groove is formed on the end surface of the support cam member 71 in the axial direction. The support cam member 71 is provided via a gap with respect to the outer peripheral surface of the inner rotary member 20 and is supported on the vehicle front end surface of the rear housing 12 via a thrust bearing. That is, the support cam member 71 is relatively rotatable with respect to the inner rotation member 20 and the rear housing 12, and is provided to be regulated with respect to the axial direction. Further, the male spline of the support cam member 71 is fitted to the female spline of the inner pilot clutch plate 64a.

  Most of the moving cam member 72 is formed in an annular shape from an iron-based material. A cam groove is formed on the end surface of the moving cam member 72 in the axial direction so as to face the cam groove of the support cam member 71 in the axial direction. A plurality of recesses 72a that restrict the claw portion 54c of the retainer 54 in the circumferential direction and allow axial movement are formed on the opposite surface in the axial direction with respect to the cam groove of the moving cam member 72. Accordingly, the moving cam member 72 rotates together with the cage 54. Furthermore, when the moving cam member 72 moves to the main clutch plate 40 side, it presses the inner main clutch plate 41 and frictionally engages the main clutch plates 40.

  The cam follower 73 is formed in a ball shape and is interposed in cam grooves facing each other of the support cam member 71 and the moving cam member 72. That is, when the cam follower 73 and the respective cam grooves act to cause a rotation difference between the support cam member 71 and the moving cam member 72, the moving cam member 72 is separated from the support cam member 71 in the axial direction. Move to. The axial separation amount of the moving cam member 72 with respect to the support cam member 71 increases as the rotational phase shift between the support cam member 71 and the moving cam member 72 increases.

(Basic operation of the driving force transmission device)
Next, the basic operation of the driving force transmission device 1 having the above-described configuration will be described with reference to FIGS. 2 to 3 and FIGS. 8 to 9. A description will be given of the torque non-transmission state and the torque transmission state between the outer rotation member 10 and the inner rotation member 20.

  As shown in FIG. 2, when a torque non-transmission state is set between the outer rotating member 10 and the inner rotating member 20, the following is performed. The electromagnetic coil 62 is turned off and the pilot clutch plate 64 is turned off. Accordingly, the support cam member 71 can rotate relative to the outer rotating member 10. Here, the moving cam member 72, the retainer 54, and the roller 53 are restricted in the circumferential direction by the engagement between the claw portion 54 c of the retainer 54 and the recess 72 a of the moving cam member 72. Therefore, when the support cam member 71 is not restricted by the pilot clutch plate 64, the support cam member 71, the moving cam member 72, the roller 53, and the cage 54 are in a free state (regulation) with respect to the outer rotating member 10. State).

  Therefore, as shown in FIG. 3, the retainer 54 does not cause a rotational phase shift with respect to the inner rotating member 20, and the roller 53 is positioned at the neutral position of the polygonal outer peripheral surface 52. That is, the support cam member 71, the moving cam member 72, the roller 53, the retainer 54, and the inner rotating member 20 are in a state of rotating integrally. Therefore, the moving cam member 72 does not press the main clutch plate 40 without moving in the axial direction toward the main clutch plate 40 with respect to the support cam member 71.

  Thus, since the main clutch plate 40 is not pressed by the moving cam member 72, the main clutch plates 40 are not frictionally engaged with each other. Since the roller 53 of the two-way clutch 50 is located at the neutral position, the torque is not transmitted between the intermediate rotating member 30 and the inner rotating member 20. Therefore, the inner main clutch plate 41 and the intermediate rotating member 30 are in a state of being rotatable relative to the outer rotating member 10 and the inner rotating member 20.

  However, a drag torque between adjacent main clutch plates 40 may be generated. In this case, the intermediate rotating member 30 generates a force that rotates together with the outer rotating member 10. However, since the intermediate rotating member 30 is in a state of being rotatable relative to the inner rotating member 20, even if the intermediate rotating member 30 rotates with the outer rotating member 10, the torque is transmitted to the inner rotating member 20. There is nothing. Thus, even if drag torque is generated in the main clutch plate 40, torque is not transmitted between the outer rotating member 10 and the inner rotating member 20. Therefore, deterioration of fuel consumption can be suppressed without lowering turning performance.

  Next, a case where a torque transmission state is established between the outer rotating member 10 and the inner rotating member 20 will be described. The torque transmission state between the two members is a case where there is a rotational difference between the outer rotating member 10 and the inner rotating member 20 and operates for the purpose of reducing the rotational difference.

  In this case, a current is supplied to the electromagnetic coil 62. Then, a magnetic circuit that circulates through the yoke 61, the rear housing 12, and the armature 63 with the electromagnetic coil 62 as a base point is formed. By forming the magnetic circuit, the armature 63 is drawn toward the yoke 61 side. As a result, as shown in FIG. 8, the armature 63 presses the pilot clutch plate 64, and the inner pilot clutch plate 64a and the outer pilot clutch plate 64b are frictionally engaged. Then, the rotational torque of the outer rotating member 10 is transmitted to the support cam member 71 via the pilot clutch plate 64, and the support cam member 71 rotates together with the outer rotating member 10.

  Here, the movable cam member 72 rotates together with the inner rotating member 20 via the cage 54 and the roller 53. However, since the torque of the support cam member 71 is transmitted to the moving cam member 72 via the cam follower 73, the moving cam member 72 operates so that the rotational phase is shifted with respect to the inner rotating member 20. Then, as shown in FIG. 9, the rotational phases of the inner rotating member 20 and the cage 54 of the two-way clutch 50 are shifted. As a result, the two-way clutch 50 is engaged, that is, the roller 53 is wedge-engaged with the cylindrical inner peripheral surface 51 and the polygonal outer peripheral surface 52, and torque is transmitted between the intermediate rotating member 30 and the inner rotating member 20. It becomes a state.

  At this time, the rotation of the movable cam member 72 is restricted with respect to the cage 54, so that the movable cam member 72 tries to rotate together with the cage 54, the intermediate rotating member 30 and the inner rotating member 20. As a result, a rotational phase shift occurs between the support cam member 71 and the movable cam member 72. The movable cam member 72 moves in the axial direction with respect to the support cam member 71 by the action of the cam follower 73 and each cam groove. The moving cam member 72 presses the main clutch plate 40, and the main clutch plates 40 are frictionally engaged with each other. As a result, the torque of the outer rotating member 10 is transmitted to the intermediate rotating member 30 via the main clutch plate 40, and the torque of the intermediate rotating member 30 is transmitted to the inner rotating member 20 via the two-way clutch 50. Therefore, when the electromagnetic coil 62 is energized, the differential between the outer rotating member 10 and the inner rotating member 20 is suppressed.

  Incidentally, as described above, after the roller 53 is wedge-engaged with the cylindrical inner peripheral surface 51 and the polygon outer peripheral surface 52, the movable cam member 72 moves in the axial direction. The recess 72a of the moving cam member 72 and the claw portion 54c of the retainer 54 restrict circumferential movement and allow axial movement. Therefore, in a state where the roller 53 is engaged with the intermediate rotation member 30 and the inner rotation member 20, the movable cam member 72 presses the main clutch plate 40 without affecting the engagement of the roller 53. be able to.

  When the electromagnetic coil 62 is switched from the energized state to the non-energized state, the moving cam member 72 moves to the support cam member 71 side, and the pressing of the main clutch plate 40 by the moving cam member 72 is released. Then, the frictional engagement of the main clutch plate 40 is released. Accordingly, the force of relative rotation between the inner rotating member 20 and the cage 54 does not act, and the cage 54 returns to the neutral position by the biasing force of the circumferential biasing member 56. As a result, the roller 53 moves to the neutral position, and the inner rotating member 20 and the intermediate rotating member 30 are allowed to rotate relative to each other, and even if the drag torque of the main clutch plate 40 is generated, the rotation of the intermediate rotating member 30 is performed. Is not transmitted to the inner rotating member 20.

<Second embodiment>
The driving force transmission apparatus 100 of 2nd embodiment is demonstrated with reference to FIGS. Here, the driving force transmission apparatus 100 of this embodiment differs in the two-way clutch 150 from the driving force transmission apparatus 1 of the first embodiment. Hereinafter, the two-way clutch 150 will be described. In addition, about the same structure as 1st embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted.

  As shown in FIGS. 10 and 11, the two-way clutch 150 includes a cylindrical inner peripheral surface 51 formed on the inner peripheral surface of the intermediate rotating member 30, a polygon outer peripheral surface 52 formed on the outer peripheral surface of the inner rotating member 20, A plurality of rollers 53, a cage 154, a bush 155, and an axial biasing member 156 are provided.

  As shown in FIGS. 11 and 12, the retainer 154 includes an annular portion 154a in which a plurality of window portions 154b are formed in the circumferential direction, and extends in the axial direction from one axial end of the annular portion 154a and further has a diameter. And a plurality of claw portions 154c extending outward in the direction. The axial length of the window 154b is longer than the axial length of the roller 53 so as to allow axial movement of the cage 154 described below.

  Further, an engagement hole 154d is formed in the claw portion 154c of the cage 154 at an axial position where the bush 155 is disposed. The engagement hole 154d is formed in a shape approximate to a home base type. The top shape of the home base type in the engagement hole 154d is formed in an arc shape on the annular portion 154a side and in the center in the circumferential direction. Further, the engagement hole 154d is formed to be inclined so as to escape to the opposite side of the annular portion 154a from the top of the arc shape toward both sides in the circumferential direction. Further, the end portion in the axial direction of the claw portion 154c of the cage 154 is always in contact with the recess 72a of the movable cam member 72 as shown in FIG.

  The bush 155 is formed in an annular shape, and is fixed to the polygonal outer peripheral surface 52 by press-fitting as shown in FIG. The bush 155 is disposed adjacent to the claw portion 154c side of the annular portion 154a of the retainer 154 at the axial position of the engagement hole 154d. Further, a plurality of recesses 155a are formed on the outer peripheral side of the bush 155 in the circumferential direction so as not to interfere with the claw portion 154c. Further, a pin 155b protruding outward in the radial direction is fixed to the recess 155a. The pin 155b is inserted into the engagement hole 154d and can move within the engagement hole 154d. Here, in FIG. 12, the pin 155b is fitted into the top of the arcuate shape of the engagement hole 154d.

  The axial urging member 156 is disposed between the end surface of the inner rotating member 20 and the end surface of the retainer 154 (opposite side of the claw portion 154c), and moves the retainer 154 relative to the inner rotating member 20 to the moving cam member 72. Energized to the side.

  Below, operation | movement of the driving force transmission apparatus 100 of this embodiment is demonstrated. When the electromagnetic coil 62 is not energized, it operates as follows. The axial biasing member 156 biases the cage 154 toward the moving cam member 72 side. At this time, the cage 154 does not generate a force against the biasing force of the axial biasing member 156 by the moving cam member 72. Then, the pin 155b fits into the arcuate top of the engagement hole 154d, and the relative rotation between the cage 154 and the bush 155 is restricted. That is, the relative rotation between the cage 154 and the inner rotation member 20 is restricted.

  The state in which the pin 155b is fitted into the top of the arcuate shape of the engagement hole 154d is a state in which the retainer 154 is positioned at the neutral position. Therefore, the retainer 154 is neutralized by the pin 155b and the engagement hole 154d. Can be held in position. Even if the moving cam member 72 generates a force relative to the inner rotating member 20 due to inertia, the retainer 154 continues to be maintained in the neutral position. Therefore, if the pin 155b is fitted into the top of the arcuate shape of the engagement hole 154d, the intermediate rotation member 30 and the inner rotation member 20 can be reliably rotated relative to each other.

  Subsequently, when the electromagnetic coil 62 is energized, the moving cam member 72 is restricted from moving in the circumferential direction by the cage 154, and the cage 154 is restricted from moving in the circumferential direction by the inner rotating member 20 via the pin 155b. Accordingly, a rotational phase shift occurs between the support cam member 71 and the movable cam member 72, and the movable cam member 72 moves in the axial direction toward the main clutch plate 40 with respect to the support cam member 71.

  As the moving cam member 72 moves in the axial direction, the retainer 154 moves toward the axial biasing member 156 against the biasing force of the axial biasing member 156. As a result, the engagement between the pin 155b and the arcuate top of the engagement hole 154d is released, and the pin 155b is allowed to move in the circumferential direction at the engagement hole 154d. That is, the cage 154 can move from the neutral position in the circumferential direction.

  Then, at that time, the cage 154 regulated by the movable cam member 72 has a rotational phase shift with respect to the inner rotary member 20, so that the two-way clutch 150 is engaged, that is, the roller 53 is cylindrical. The inner circumferential surface 51 and the polygonal outer circumferential surface 52 are wedge-engaged, and the torque is transmitted between the intermediate rotating member 30 and the inner rotating member 20.

  Thereafter, the moving cam member 72 further moves in the axial direction, the moving cam member 72 presses the main clutch plate 40, and the main clutch plates 40 are frictionally engaged with each other. As a result, the torque of the outer rotating member 10 is transmitted to the intermediate rotating member 30 via the main clutch plate 40, and the torque of the intermediate rotating member 30 is transmitted to the inner rotating member 20 via the two-way clutch 150. Therefore, when the electromagnetic coil 62 is energized, the differential between the outer rotating member 10 and the inner rotating member 20 is suppressed.

1, 100: Driving force transmission device, 10: Outer rotating member, 20: Inner rotating member, 30: Intermediate rotating member, 40: Friction-type main clutch plate, 50, 150: Two-way clutch, 51: Cylindrical inner peripheral surface, 52 : Polygonal outer surface, 53: Roller, 54, 154: Cage, 55, 155: Bush, 56: Circumferential biasing member, 60: Electromagnetic clutch device, 64: Pilot clutch plate, 70: Cam mechanism, 71: Support cam member 72: Moving cam member 155b: Pin 156: Axial biasing member

Claims (3)

A cylindrical outer rotating member;
An inner rotating member disposed coaxially within the outer rotating member so as to be relatively rotatable;
An intermediate rotating member arranged coaxially so as to be relatively rotatable between the outer rotating member and the inner rotating member in a radial direction;
A friction main clutch plate that transmits torque between the outer rotating member and the intermediate rotating member;
A two-way clutch disposed between the intermediate rotating member and the inner rotating member and having a roller and a retainer for holding the roller;
An electromagnetic clutch device comprising a pilot clutch plate capable of transmitting the torque of the outer rotating member by attracting the armature to the yoke side by magnetic force;
The retainer of the two-way clutch provided between the friction type main clutch plate and the pilot clutch plate and restricted by the rotation of the outer rotating member and the moving cam member transmitted through the pilot clutch plate. A cam mechanism for converting the phase difference from the rotation of the shaft into an axial pressing force and pressing the friction main clutch plate by moving the movable cam member in the axial direction;
Equipped with a,
The moving cam member of the cam mechanism is
Rotation is restricted with respect to the cage of the two-way clutch,
When the cage of the two-way clutch is located in a neutral position, it can rotate relative to the intermediate rotation member,
A driving force transmission device that rotates together with the intermediate rotation member when the cage of the two-way clutch is displaced in the circumferential direction from a neutral position . The two-way clutch includes a plurality of circumferential urging members that urge the cage toward the neutral position in the circumferential direction with respect to the inner rotation member ,
In each the other rotational direction to the neutral position while the rotational direction and the neutral position of towards, the plurality of circumferential biasing member, you urge the respective plurality of locations in the circumferential direction of said retainer, The driving force transmission device according to claim 1. The cage is provided so as to be movable in the axial direction with respect to the inner rotating member,
The two-way clutch is
An axial biasing member that biases the cage toward the movable cam member with respect to the inner rotation member;
A pin provided on the inner rotating member;
With
An engagement hole is formed in the cage,
The engagement hole is
When the retainer is not pressed in the axial direction by the movable cam member, the retainer is biased by the axial biasing member to engage with the pin, thereby causing the retainer to be neutral in the circumferential direction. Hold in position,
When the cage is pressed in the axial direction by the moving cam member against the axial biasing member, the engagement with the pin is released and the cage moves in the circumferential direction from the neutral position. The driving force transmission device according to claim 1, wherein the driving force transmission device is allowed.

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