JP2016070416A - Clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a clutch device that can be reduced in radial dimensions.SOLUTION: A support member 40 is coupled to a clutch member 50, and a rotary member 30 is rotated by a motor 20. The rotary member 30 is provided with a cam 32, and a contact piece 41 that is brought into contact with the cam 32 is supported by the support member 40. The contact piece 41 is brought into contact with the cam 32 to move the clutch member 50 to a first position or second position in an axial direction. As a result, urging force is built up in an urging member 60 to allow the clutch member 50 moved to the first position or the second position to switch between transmitting rotation and disengaging rotation. The rotary member 30 is formed in a cylindrical shape, and is arranged coaxially with a first shaft 11, a second shaft 12, and the clutch member 50 to enable a clutch device 10 to be reduced in radial directions.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a clutch device, and more particularly to a clutch device capable of reducing a dimension in a radial direction.

  2. Description of the Related Art Conventionally, a clutch device that transmits or cuts off rotation between a first shaft and a second shaft is known. For example, in Patent Document 1, a contact member (operation pin) is supported on a rotating member (operation shaft) rotated by a motor, and an urging force in the axial direction is applied to the support member (moving member) by an urging member (coil spring). A clutch device is disclosed in which a cam formed on a support member and a contact are pressed by being applied. In the technique disclosed in Patent Document 1, the support member moves in the axial direction according to the contour of the cam by rotating the rotating member and the contact by the motor. Accordingly, the clutch member (moving fork) supported by the support member moves in the axial direction, and the first shaft and the second shaft are connected or disconnected via the clutch member.

JP 2010-107039 A

  However, in the technique disclosed in Patent Document 1, since the clutch member (moving fork) reciprocates on a straight line different from the rotation axis of the rotating member (operation shaft), there is a problem in that the radial dimension of the clutch device cannot be reduced. is there.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a clutch device capable of reducing the radial dimension.

Means for Solving the Problems and Effects of the Invention

  In order to achieve this object, according to the clutch device of the first aspect, the first shaft and the second shaft are integrally connected to each other at the first position in the axial direction, while being connected to the first position. The first shaft and the second shaft are separated from each other at a second position separated in the axial direction. The clutch member is connected to the support member, and the rotating member is rotated by a motor. A cam is formed on one of the rotating member and the supporting member, and a contact that contacts the contour of the cam is supported on the other of the rotating member and the supporting member. Since the urging force is accumulated in the urging member by the contact between the contactor and the cam and the clutch member moving to the first position or the second position in the axial direction, the urging force of the cam and the urging member The clutch member moves between the first position and the second position in the axial direction. As a result, rotation is transmitted or blocked between the first shaft and the second shaft. Since the rotating member is formed in a cylindrical shape and is arranged coaxially with the first shaft, the second shaft, and the clutch member, there is an effect that the size in the radial direction of the clutch device can be reduced.

  In addition, since the rotation of the support member is restricted with respect to the case by the rotation restricting portion, the clutch device housed in the case can prevent the axial position of the support member from changing according to the contour of the cam. As a result, since it is possible to prevent the clutch member supported by the support member from moving in the axial direction, it is possible to improve the reliability of transmission or interruption of rotation between the first shaft and the second shaft by the clutch member. is there.

  According to the clutch device of the second aspect, the rotation restricting portion is formed with the groove portion extending in the axial direction in the case. The engaging portion is slidably engaged in the axial direction along the groove portion, and is integrally formed with the contactor or the support member. Since the rotation restricting portion can be made compact using the case, in addition to the effect of the first aspect, there is an effect that the clutch device can be miniaturized.

  According to the clutch device of the third aspect, the contact is such that the outer peripheral surface of the roller is in contact with the cam, and the roller is rotatably supported by the support member by the support shaft. The engaging portion projects from the axial end surface of the support shaft along the axial direction of the support shaft. Since the rotation restricting portion is provided using the contact, in addition to the effect of the second aspect, there is an effect that the number of parts can be reduced.

  According to the clutch device of the fourth aspect, the clutch member is rotatably supported with respect to the support member by the sliding portion provided in the support member, and is fixed so as not to move in the axial direction with respect to the support member. Is done. Since the support member and the clutch member are arranged coaxially, in addition to the effect of any one of claims 1 to 3, there is an effect that the radial dimension of the clutch device can be reduced.

  According to the clutch device of the fifth aspect, the reduction gear is interposed between the motor and the rotating member. The rotating member has an outer shape with teeth that mesh with the reduction gear. Therefore, in addition to the effect of any one of claims 1 to 4, there is an effect that the motor speed reduction mechanism for obtaining a driving force required for driving the cam can be reduced in size.

It is a skeleton figure of the vehicle by which the clutch apparatus in 1st Embodiment of this invention is mounted. It is an axial sectional view of a clutch device. It is the elements on larger scale of the clutch apparatus which expanded a part of FIG. It is an expanded view of a cam. It is a skeleton figure of the vehicle by which the clutch apparatus in 2nd Embodiment is mounted. It is an axial sectional view of a clutch device. It is an axial sectional view of a clutch device in a 3rd embodiment.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. First, a vehicle equipped with a clutch device according to a first embodiment of the present invention will be described with reference to FIG. FIG. 1 is a skeleton diagram of a vehicle 1 (automobile) on which a clutch device 10 according to the first embodiment is mounted.

  As shown in FIG. 1, the vehicle 1 includes a two-wheel drive state in which the front wheels 5 are driven by a clutch device 10 disposed on the axle 4 of the front wheel 5 and a four-wheel drive state in which the front wheels 5 and the rear wheels 8 are driven. It is a car that can be switched. In the four-wheel drive state, the driving force of the power unit 2 is transmitted to the axle 4 of the front wheel 5 via the differential device 3, and the rotation of the axle 4 is transmitted to the axle 7 of the rear wheel 8 via the clutch device and the drive shaft 6. Is done. In the two-wheel drive state, transmission of rotation of the driven front wheel 5 from the axle 4 to the drive shaft 6 is interrupted by the clutch device 10.

  Next, a schematic configuration of the clutch device 10 will be described with reference to FIG. FIG. 2 is an axial sectional view of the clutch device 10. In FIG. 2, a portion related to power transmission from the axle 4 to the drive shaft 6 is illustrated, and illustration of a part of the axle 4 and the drive shaft 6 is omitted.

  The clutch device 10 transmits or blocks rotation between the first shaft 11 that rotates integrally with the axle 4 of the front wheel 5 and the second shaft 12 that transmits rotation to the drive shaft 6 via the bevel gear 9. It is a device to perform. The clutch device 10 is housed in a case 13 that is disposed radially outside a part of the first shaft 11 and the second shaft 12. The first shaft 11 is a cylindrical member fitted on the outer periphery of the axle 4, and the second shaft 12 is a cylinder disposed coaxially with the first shaft 11 on the radially outer side of the first shaft 11. Shaped member. The first shaft 11 and the second shaft 12 are supported by the first bearing 14 and the bearing 15 fixed to the case 13 such that the first shaft 11 and the second shaft 12 can rotate relative to the case 13 and can rotate relative to each other. The first shaft 11 has a spline 11a formed on the outer periphery, and the second shaft 12 has a spline 12a formed on the inner periphery.

  The motor 20 is fixed to the case 13 with a drive shaft 21 disposed parallel to the first shaft 11 and the second shaft 12. As the motor 20, a stepping motor or a DC motor controlled by a position detection sensor is used. Both ends of a gear shaft 23 arranged in parallel with the drive shaft 21 of the motor 20 are rotatably supported by the case 13. The gear shaft 23 is fixed with a first reduction gear 24 and a second reduction gear 25 that rotate integrally with the gear shaft 23, and the first reduction gear 24 meshes with a gear 22 that rotates integrally with the drive shaft 21. .

  Next, the clutch device 10 will be described in detail with reference to FIG. FIG. 3 is a partially enlarged view of the clutch device 10 in which a part of FIG. 2 is enlarged. Arrows X1-X2 indicate the axial directions of the axle 4 and the clutch device 10. The clutch device 10 is a clutch connected to the support member 40 by rotating the rotary member 30 by the motor 20 and changing the position of the support member 40 linked to the rotary member 30 in the axial direction (arrow X1-X2 direction). The position of the member 50 in the axial direction is changed. By switching the engagement state between the clutch member 50 and the splines 11a and 12a formed on the first shaft 11 and the second shaft 12, respectively, rotation transmission or interruption is switched.

  The rotating member 30 is a cylindrical member disposed radially outside the first shaft 11 and inside the case 13, and has the same axis O as the first shaft 11, the second shaft 12, and the clutch member 50. Arranged. The rotating member 30 is disposed on the radially outer side of a virtual projection surface obtained by projecting the outer periphery of the first shaft 11, the support member 40, and the clutch member 50 in the axial direction. The rotating member 30 is rotatably supported with respect to the case 13 by fixing the second bearing 16 fixed to the case 13 to the inner periphery.

  The rotating member 30 is formed with teeth 31 that mesh with the second reduction gear 25 on the outer shape. As a result, when the motor 20 rotationally drives the drive shaft 21, the rotating member 30 is rotationally driven via the gear 22, the first reduction gear 24, the second reduction gear 25, and the teeth 31. The gear 22, the first reduction gear 24, the second reduction gear 25, and the teeth 31 constitute a gear train for reducing the rotation of the drive shaft 21 of the motor 20 to obtain a necessary driving force. The rotating member 30 has a cam 32 formed on an end face in the axial direction.

  The support member 40 is a cylindrical member that is supported by the clutch member 50 and is moved in the axial direction in accordance with the contour of the cam 32 formed on the rotating member 30. 4) is supported. In the present embodiment, the contact 41 includes a roller 42 whose outer peripheral surface is in contact with the cam 32, and a support shaft 43 that rotatably supports the roller 42 on the support member 40. Since a plurality of rollers (not shown) are arranged between the roller 42 and the support shaft 43, friction between the roller 42 and the support shaft 43 can be reduced. The support shaft 43 has an engaging portion 44 projecting from an end face in the axial direction along the axial direction of the support shaft 43. The engaging portion 44 is a portion that is formed on the inner peripheral surface of the case 13 and engages with a groove portion 13a that extends in the axial direction. By engaging the engaging portion 44 with the groove portion 13 a, the support member 40 is prevented from rotating around the axis O of the first shaft 11 and the second shaft 12 with respect to the case 13.

  The clutch member 50 is a cylindrical member disposed on the radially outer side of the first shaft 11 and on the radially inner side of the second shaft 12. The clutch member 50 is rotatably connected to the support member 40 by fixing the third bearing 17 (sliding portion) fixed to the support member 40 to the outer periphery, while being connected to the support member 40. Fixed so that it cannot move in the axial direction. That is, the clutch member 50 is moved in the axial direction integrally with the support member 40.

  The clutch member 50 has splines 51 and 52 formed on the inner periphery and the outer periphery, respectively. In the movable range in the axial direction of the clutch member 50, the spline 11a formed on the first shaft 11 and the spline 51 formed on the inner periphery of the clutch member 50 are always engaged. On the other hand, the position of the spline 52 formed on the outer periphery of the clutch member 50 is set so that it does not engage with the spline 12a formed on the second shaft 12 depending on the position of the clutch member 50 in the axial direction. ing. As a result, the clutch member 50 rotates along with the first shaft 11 by the spline 51, and the first position in the axial direction (arrow X1 side) where the spline 52 is engaged with the spline 12a formed on the second shaft 12. The spline 52 moves along the spline 11a between the second position in the axial direction (arrow X2 side) where the spline 52 is not engaged with the spline 12a.

  In the clutch member 50, the third bearing 17 is fixed to one end side in the axial direction, and an urging member 60 (coil spring) is disposed on the other end side in the axial direction opposite thereto. The urging member 60 is disposed on the radially outer side of the first shaft 11 and on the radially inner side of the second shaft 12, and the end surface of the clutch member 50 on the other end side in the axial direction (arrow X2 direction) and the first shaft 11. It arrange | positions in the compressed state between predetermined locations of the outer periphery of the. Thereby, the urging member 60 presses the clutch member 50 toward one end side in the axial direction (arrow X1 direction). The clutch member 50 and the support member 40 are urged toward one side in the axial direction (arrow X1 direction) by the urging force of the urging member 60, and the contact 41 (roller 42) is pressed against the cam 32.

  Here, the cam 32 (end face cam) will be described with reference to FIG. FIG. 4 is a development view of the cam 32 (a drawing in which 360 ° of the outer peripheral surface of the rotating member 30 is developed on a plane). As the drive shaft 21 is rotated by the motor 20 (see FIG. 3), the rotating member 30 rotates in the arrow R direction. The cam 31 is a flat first working surface 33 positioned at a low position (one axial end side, arrow X1 side) and from the terminal end of the first working surface 33 toward the other axial end side (arrow X2 side). There is a path having one cycle of a switching surface 34 having a rising and inclined gradient and a flat second working surface 35 positioned at a high level (the other end side in the axial direction, the arrow X2 side). The cam 32 has a path for two cycles formed on the end surface in the axial direction of the rotating member 30 corresponding to one rotation of the rotating member 30, and the end of the second operating surface 35 and the starting end of the first operating surface 33. Are connected by a plane perpendicular to the first working surface 33 and the second working surface 35.

  Since the contact 41 is urged to one side (arrow X1 side) in the axial direction by the urging member 60 (see FIG. 3), the first operating surface 33, the switching surface 34, and It is pressed against the second working surface 35. Therefore, when the contact 41 is in contact with the first working surface 33 of the rotating member 30, the support member 40 (see FIG. 3) and the clutch member 50 are located at the first position on one side (arrow X1 side) in the axial direction. . At this time, since the spline 52 of the clutch member 50 is engaged with the spline 12 a formed on the second shaft 12, the rotation of the first shaft 11 is transmitted to the second shaft 12 via the clutch member 50. Since the rotation of the second shaft 12 is transmitted to the drive shaft 6 via the bevel gear 9, the vehicle 1 (see FIG. 1) is in a four-wheel drive state.

  Further, when the contact 41 is in contact with the switching surface 34 of the rotating member 30, the supporting member 40 and the clutch member 50 are gradually moved to the other side (arrow X <b> 2 side) in the axial direction as the rotating member 30 rotates. The contact member 41 and the cam 32 interfere with each other and the clutch member 50 is moved toward the second position in the axial direction, whereby the urging member 60 is compressed and the urging force is accumulated in the urging member 60.

  When the contact 41 is in contact with the second operating surface 35 of the rotating member 30, the support member 40 and the clutch member 50 are located at the second position on the other side (arrow X2 side) in the axial direction. At this time, since the engagement between the spline 12a formed on the second shaft 12 and the spline 52 of the clutch member 50 is released, transmission of rotation to the second shaft 12 is interrupted. As a result, the vehicle 1 is in a two-wheel drive state in which only the first shaft 11 is rotationally driven.

  Since the end of the second working surface 35 of the cam 32 and the starting end of the first working surface 33 are connected by a surface perpendicular to the first working surface 33 and the second working surface 35, the rotation of the rotating member 30 is performed. Thus, the clutch member 50 can be instantaneously switched from the second position to the first position. Therefore, when the spline 12a formed on the second shaft 12 and the spline 52 of the clutch member 50 come to the meshing position, the spline 52 meshes with the spline 12a by the urging force accumulated in the urging member 60, and the contact 41 contacts the first working surface 33. Therefore, the clutch device 10 can be instantaneously switched from the two-wheel drive state to the four-wheel drive state.

  Thus, the contact 41 and the cam 32 are pressed by the urging force of the urging member 60, and when the contact 41 is positioned on the first operating surface 33, the clutch member 50 is on one side in the axial direction (arrow X1). Direction). Since these two functions are exhibited by the single urging member 60, the structure of the clutch device 10 can be simplified and the number of parts can be reduced.

  According to the clutch device 10, the cylindrical rotating member 30 is disposed coaxially with the first shaft 11, the second shaft 12, and the clutch member 50, so that the rotating member 30 is disposed radially inward of the clutch member 50. The rotation axis (axis O) can be positioned. Thereby, the dimension of the radial direction of the clutch apparatus 10 can be made small. In particular, since the clutch member 50 is disposed radially inside a virtual projection surface obtained by projecting the rotating member 30 in the axial direction, the clutch device is compared with a case where the clutch member 50 is provided radially outside the rotating member 30. 10 radial dimensions can be reduced. Therefore, the clutch device 10 can be reduced in size.

  Further, the groove 13a is formed in the case 13, and the engaging portion 44 that protrudes from the contact 41 and extends radially outward has a rotation restricting portion that engages with the groove 13a. Thus, the support member 40 is movable in the axial direction, while the rotation of the support member 40 is restricted with respect to the case 13. As a result, it is possible to prevent the axial position of the support member 40 from changing according to the contour of the cam 32.

  Here, when there is no rotation restricting portion that restricts the rotation of the support member 40 with respect to the case 13, the support member 40 rotates with respect to the case 13, so regardless of the rotation position of the rotation member 30. The support member 40 moves in the axial direction according to the contour of the cam 32. In this case, there is a problem that the axial position of the clutch member 50 cannot be controlled by the motor 20. On the other hand, the clutch device 10 can prevent the support member 40 from rotating around the axis O with respect to the case 13 by engaging the engaging portion 44 with the groove portion 13a. As a result, the clutch member 50 coupled to the support member 40 can be prevented from moving in the axial direction regardless of the rotation of the rotating member 30. Since the position of the clutch member 50 in the axial direction can be accurately controlled by the motor 20, it is possible to improve the reliability of transmission or interruption of rotation between the first shaft 11 and the second shaft 12 by the clutch member 50.

  Further, the groove 13a extending in the axial direction is formed in the case 13, and the engaging portion 44 is formed integrally with the contact 41, so that the engaging portion 44 can slide in the axial direction along the groove 13a. Is engaged. As a result, the rotation restricting portion can be made compact by utilizing the groove portion 13a formed on the inner surface of the case 13. Therefore, it can suppress that the radial direction dimension of the clutch apparatus 10 expands more than necessary. As a result, the clutch device 10 can be reduced in size.

  In addition, the contact 41 that the outer peripheral surface of the roller 42 is in contact with the cam 32 and the roller 42 is rotatably supported by the support member 40 by the support shaft 43 is an axis of the support shaft 43 along the axial direction of the support shaft 43. An engaging portion 44 projects from the direction end surface. Since the engaging portion 44 is formed using the contact 41, the number of parts can be reduced.

  Here, the clutch member 50 is rotatably supported with respect to the support member 40 by the third bearing 17 (sliding portion) disposed on the support member 40, but cannot move in the axial direction with respect to the support member 40. Fixed to. With this configuration, since the support member 40 and the clutch member 50 are coaxially arranged, the radial dimension of the clutch device 10 can be reduced. Therefore, the clutch device 10 can be reduced in size.

  A first reduction gear 24 and a second reduction gear 25 are interposed between the motor 20 and the rotating member 30. Since the rotating member 30 has teeth 31 that mesh with the second reduction gear 25 formed on its outer shape, it is possible to obtain the necessary driving force for driving the cam 32 by reducing the rotation of the drive shaft 21. Furthermore, since the speed reduction mechanism (gear train) is formed using the outer shape (tooth 31) of the rotating member 30, the speed reduction mechanism of the motor 20 for obtaining a driving force for driving the cam 32 can be reduced in size.

  The rotating member 30 is rotatably supported by the case 13 by the second bearing 16, and a cam 32 is formed on the rotating member 30. A contact 41 that contacts the contour of the cam 32 is supported by the support member 40, and a biasing force that presses the contact 41 against the cam 32 is applied to the support member 40 by the biasing member 60. Since the clutch member 50 is fixed at the first axial position (arrow X1 direction) by the biasing force of the biasing member 60, the reliability of fixing the clutch member 50 at the first position can be improved with a simple configuration. .

  Further, the cam 32 and the urging member 60 are set so that the clutch member 50 is fixed to the first position by the urging force applied to the support member 40. Therefore, it is possible to improve the reliability that the state in which the first shaft 11 and the second shaft 12 are rotatably connected integrally can be stably maintained by the clutch member 50 fixed to the first position by the biasing member 60. .

  Next, a second embodiment will be described with reference to FIGS. In the first embodiment, the clutch device 10 that switches between transmission and interruption of power between the first shaft 11 and the second shaft 12 disposed on the radially outer side of the first shaft 11 has been described. On the other hand, in the second embodiment, the transmission or cut-off of power between the first shaft (axle 103) and the second shaft (axle 104) which are arranged in a state where the axial end faces face each other is switched. The clutch device 110 will be described. In addition, about the part same as the part demonstrated in 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 5 is a skeleton diagram of a vehicle 101 (automobile) on which the clutch device 110 according to the second embodiment is mounted.

  As shown in FIG. 5, the vehicle 101 includes a two-wheel drive state in which the rear wheel 109 is driven by the clutch device 110 disposed on the axles 103 and 104 of the front wheel 105, and a four-wheel drive in which the front wheel 105 and the rear wheel 109 are driven. It is an automobile that can be switched between driving states. In the four-wheel drive state, the axles 103 and 104 of the front wheel 105 are connected by the clutch device 110, so that the driving force of the power unit 102 that drives the axle 108 of the rear wheel 109 via the transfer 107 and the drive shaft 106 is changed to the clutch. This is transmitted to the axles 103 and 104 of the front wheel 105 via the device 110. In the two-wheel drive state, the output of the transfer 107 is switched, and the clutch device 110 releases the connection between the axles 103 and 104 of the front wheel 105, thereby interrupting transmission of the driving force to the axles 103 and 104 of the front wheel 105.

  Next, the configuration of the clutch device 110 will be described with reference to FIG. FIG. 6 is a cross-sectional view of the clutch device 110 in the axial direction. 6 is a one-side cross-sectional view illustrating one side with respect to the axis O, and the illustration on the opposite side is omitted. The clutch device 110 is a device that transmits or blocks rotation between the left axle 103 (first shaft) of the front wheel 105 (see FIG. 5) and the right axle 104 (second shaft) of the front wheel 105. . The 1st axis | shaft 103 and the 2nd axis | shaft 104 are arrange | positioned in the state which made the end surface of the axial direction oppose each other. In the first shaft 103, a first member 111 having an outer diameter larger than the outer diameter of the first shaft 103 is formed integrally with the first shaft 103, and the second shaft 104 is an outer diameter of the second shaft 104. A second member 112 having a larger outer diameter is formed integrally with the second shaft 104. Splines 111a and 112a are respectively formed on the outer circumferences of the first member 111 and the second member 112. The splines 111a and 112a are arranged in parallel in the axial direction, and the outer diameter and inner diameter of the splines 111a and 112a are set to be the same. The

  The clutch device 110 is housed in a case 113 disposed on the radially outer side of part of the first member 111 and the second member 112. By the fourth bearing 114 and the fifth bearing 115 fixed to the case 113, the first member 111 and the second member 112 are supported so as to be rotatable with respect to the case 113 and relatively rotatable relative to each other. The clutch device 110 rotates the rotating member 30 by the motor 20 and changes the axial position of the supporting member 140 linked to the rotating member 30, whereby the axial position of the clutch member 150 coupled to the supporting member 140 is changed. It is a device that changes. By switching the engagement state between the clutch member 150 and the splines 111a and 112a formed on the first member 111 and the second member 112, transmission or blocking of rotation is switched.

  The support member 140 is an annular member that is coupled to the clutch member 150 and is moved in the axial direction in accordance with the contour of the cam 32 formed on the rotating member 30. The support member 140 has a contact 41 (such as a roller 42) disposed on one end side in the axial direction (in the direction of arrow X1), and between the end surface on the other end side in the axial direction (in the direction of arrow X2) opposite to the case 113. The biasing member 160 (coil spring) is disposed in a compressed state. The urging member 160 is disposed outside the first member 111 in the radial direction, and presses the end surface on the other end side in the axial direction of the support member 140 toward the one end side in the axial direction with respect to the case 113. The support member 140 is urged toward one side in the axial direction (in the direction of the arrow X1) by the urging force of the urging member 160, and the contact 41 (roller 42) is pressed against the cam 32.

  The clutch member 150 is a cylindrical member disposed on the radially outer side of the first member 111 and the second member 112. The clutch member 150 is formed with annular flanges 151 and 152 (sliding portions) projecting radially outward at both ends in the axial direction, and the inner peripheral portion of the support member 140 between the flanges 151 and 152. Is placed. Thus, the clutch member 150 is rotatably connected to the support member 140 while being fixed so as not to move in the axial direction with respect to the support member 140. That is, the clutch member 150 is moved in the axial direction integrally with the support member 140.

  The clutch member 150 has a spline 153 formed on the inner periphery. Within the movable range of the clutch member 150 in the axial direction, the spline 111a formed on the first member 111 and the spline 153 formed on the inner periphery of the clutch member 150 are always engaged. On the other hand, the position of the spline 112a formed on the second member 112 is set so that it does not engage or disengage depending on the axial position of the clutch member 150 set by the cam 32. The clutch member 150 rotates with the first member 111, and the first position in the axial direction (arrow X1 side) where the spline 153 engages with the spline 112a formed on the second member 112, and the spline 112a with the spline 112a. It moves along the spline 111a between the second position in the axial direction (arrow X2 side) where 153 is not engaged. In the first position, the clutch member 150 straddles the spline 111a of the first member 111 and the spline 112a of the second member 112.

  Next, the operation of the clutch device 150 will be described. The contact 41 (roller 42) is pressed against the first operating surface 33 (see FIG. 4), the switching surface 34, and the second operating surface 35 by the biasing member 160 as the rotating member 30 rotates. Therefore, when the contact 41 is in contact with the first working surface 33 of the rotating member 30, the support member 140 and the clutch member 150 are located at the first position on one side (arrow X1 side) in the axial direction. At this time, since the spline 153 of the clutch member 150 is engaged with the spline 112a formed on the second member 112, the first member 111 (first shaft 103) and the second member 112 (second shaft 104) are integrally formed. The vehicle 101 rotates and the vehicle 101 enters a four-wheel drive state.

  Further, when the contact 41 is in contact with the second operating surface 35 of the rotating member 30, the support member 140 and the clutch member 150 are located at the second position on the other side (arrow X2 side) in the axial direction. At this time, since the engagement between the spline 112a formed on the second member 112 and the spline 153 of the clutch member 150 is released, the first member 111 (first shaft 103) and the second member 112 (second shaft 104). ) And rotation are not linked. When the rotation drive of the first shaft 103 and the second shaft 104 is released by switching the output of the transfer 107, the vehicle 101 (see FIG. 5) enters a two-wheel drive state in which only the rear wheel 109 is rotated. According to the clutch device 110 in the second embodiment, the same operation and effect as the clutch device 10 in the first embodiment can be realized.

  Here, in order to maintain the engagement state between the clutch member 150 and the spline 112a, there is means for engaging the tooth traces by forming the tooth traces of the splines 112a and 153 in a reverse taper shape. However, it is complicated to form the tooth traces of the splines 112a and 153 in a reverse taper shape, and there is a problem that the manufacturing cost for processing the tooth traces increases. Further, due to external forces such as vibrations, the splines 112a and 153 are disengaged and the clutch member 150 may be displaced in the axial direction, resulting in a problem of lack of reliability.

  On the other hand, according to the present embodiment, the urging force that presses the contact 41 against the cam 32 is applied to the support member 140 by the urging member 160, and the urging force of the urging member 160 causes the clutch member 150 to move in the axial direction. The first spline 112a and 153 are kept engaged with each other. Therefore, the work of processing the tooth traces of the splines 112a and 153 into a reverse taper shape can be eliminated, and the reliability of fixing the clutch member 150 at the first position can be improved with a simple configuration.

  Further, the cam 32 and the urging member 160 are set so that the clutch member 150 is fixed to the first position by the urging force applied to the support member 140, and thus is fixed to the first position by the urging member 160. By the clutch member 150, it is possible to improve reliability in which the state in which the first shaft 103 and the second shaft 104 are connected so as to be integrally rotatable is stably maintained.

  Next, a third embodiment will be described. In the second embodiment, the case where the support member 140 is pressed by the biasing member 160 (coil spring) has been described. In contrast, in the third embodiment, a case where the clutch member 250 is pressed against the biasing member 160 will be described. In addition, about the part same as the part demonstrated in 1st Embodiment and 2nd Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 7 is an axial sectional view of the clutch device 210 according to the third embodiment. FIG. 7 is a one-side cross-sectional view illustrating one side with respect to the axis O, and the illustration on the opposite side is omitted. Further, the clutch device 210 in the third embodiment is mounted on the vehicle 101 (see FIG. 5) instead of the clutch device 110 described in the second embodiment.

  The support member 240 is an annular member connected to the clutch member 250, and a contact 41 (a roller 42 or the like) is disposed at the tip of an arm 241 that projects from the end surface toward one end side in the axial direction. . The clutch member 250 is a cylindrical member disposed on the radially outer side of the first member 111 and the second member 112, and has an annular flange 251 projecting radially outward at both ends in the axial direction. 252 (sliding portion) is formed. The inner peripheral portion of the support member 240 is disposed between the flanges 251 and 252. As a result, the clutch member 250 is rotatably connected to the support member 240 while being fixed so as not to move in the axial direction with respect to the support member 240.

  The flange 251 provided on the other end side (arrow X2 side) in the axial direction of the clutch member 250 has a larger outer diameter than the flange 252 provided on one end side (arrow X1 side) in the axial direction. ing. A biasing member 160 (coil spring) is disposed between the end face of the flange 251 and the case 113 in a compressed state. As a result, the urging member 160 presses the clutch member 250 against the case 113 toward one end side in the axial direction. The clutch member 250 and the support member 240 are urged toward one side in the axial direction (in the direction of the arrow X1) by the urging force of the urging member 160, and the contact 41 (roller 42) is pressed against the cam 32. According to this clutch device 210, the same operation and effect as the clutch devices 10 and 110 of the first and second embodiments can be realized.

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

  In each of the above-described embodiments, a case where the cam 32 is formed on the rotating member 30 rotated by the motor 20 and the contact 41 is provided on the support members 40, 140, 240 to which the clutch members 50, 150, 250 are connected will be described. However, it is not necessarily limited to this. On the contrary, it is naturally possible to provide the contact 41 on the rotating member 30 and form the cam 32 on the support members 40, 140 and 240. Since the rotating member 30 is rotated by the motor 20 and the contact 41 is rotated, the support members 40, 140, and 240 can be moved in the axial direction according to the contour of the cam 32 against which the contact 41 is pressed. It is. Also in this case, the urging force is accumulated in the urging members 60 and 160 by the movement of the support members 40, 140, and 240, and the clutch members 50, 150, and 250 are moved in the axial direction using the urging force. Can do.

  In each of the above embodiments, the case where the engaging portion 44 is provided on the support shaft 43 (contactor 41) that supports the roller 42 has been described. However, the present invention is not necessarily limited thereto. Of course, it is possible to project a part of the support members 40, 140, 240 outward in the radial direction and to use the projecting portion as the engaging portion 44 that engages with the groove 13a. This is also because the rotation of the support members 40, 140, and 240 can be restricted with respect to the cases 13 and 113 in this case.

10, 110, 210 Clutch device 11, 103 First shaft 12, 104 Second shaft 13, 113 Case 13a Groove (part of rotation restricting portion)
17 Third bearing (sliding part)
20 Motor 25 Second reduction gear (reduction gear)
Reference Signs List 30 Rotating member 31 Teeth 32 Cam 40, 140, 240 Support member 41 Contact 42 Roller 43 Support shaft 44 Engaging part (part of rotation restricting part)
50, 150, 250 Clutch member 151, 152, 251, 252 Flange (sliding part)
60,160 biasing member

Claims (5)

In the clutch device that is housed in the case and transmits or blocks rotation between the first shaft and the second shaft,
The first shaft and the second shaft are integrally connected rotatably at a first position in the axial direction, and the first shaft and the second shaft at a second position spaced apart in the axial direction with respect to the first position. A clutch member that separates the two shafts;
A support member coupled to the clutch member;
A cylindrical rotating member that is coaxially disposed with the first shaft, the second shaft, and the clutch member, and is rotated by a motor;
A cam formed on one of the rotating member or the support member;
A contact that contacts the contour of the cam and is supported by the other of the rotating member or the support member;
An urging member in which an urging force is accumulated by the contact between the contact and the cam and the clutch member being moved to the first position or the second position in the axial direction;
A clutch device, comprising: a rotation restricting portion that restricts rotation of the support member with respect to the case.   The rotation restricting portion is formed in the case and extends in the axial direction, and is slidably engaged in the axial direction along the groove portion, and is integrally formed with the contactor or the support member. The clutch device according to claim 1, further comprising an engaging portion. The contact includes a roller whose outer peripheral surface is in contact with the cam, and a support shaft that rotatably supports the roller on the support member,
3. The clutch device according to claim 2, wherein the engaging portion protrudes from an axial end surface of the support shaft along an axial direction of the support shaft.   The clutch member is rotatably supported with respect to the support member by a sliding portion provided on the support member, and is fixed so as not to move in the axial direction with respect to the support member. The clutch device according to any one of claims 1 to 3. Comprising a reduction gear interposed between the motor and the rotating member;
The clutch device according to any one of claims 1 to 4, wherein teeth of the rotating member that mesh with the reduction gear are formed on an outer shape.

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