WO2017149829A1 - Cam mechanism and clutch device using said cam mechanism - Google Patents

Cam mechanism and clutch device using said cam mechanism Download PDF

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Publication number
WO2017149829A1
WO2017149829A1 PCT/JP2016/080462 JP2016080462W WO2017149829A1 WO 2017149829 A1 WO2017149829 A1 WO 2017149829A1 JP 2016080462 W JP2016080462 W JP 2016080462W WO 2017149829 A1 WO2017149829 A1 WO 2017149829A1
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WO
WIPO (PCT)
Prior art keywords
cam
ring
pressure ring
cam mechanism
wall portion
Prior art date
Application number
PCT/JP2016/080462
Other languages
French (fr)
Japanese (ja)
Inventor
功 廣田
学 遠藤
豊史 丸山
Original Assignee
Ｇｋｎ ドライブライン ジャパン株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2016158619A external-priority patent/JP6735180B2/en
Application filed by Ｇｋｎ ドライブライン ジャパン株式会社 filed Critical Ｇｋｎ ドライブライン ジャパン株式会社
Priority to EP16892665.7A priority Critical patent/EP3425239A4/en
Priority to CN201680062027.0A priority patent/CN108138922B/en
Publication of WO2017149829A1 publication Critical patent/WO2017149829A1/en
Priority to US15/950,237 priority patent/US10704612B2/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
    • F16D27/108—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/08—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion
    • F16H25/12—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms

Definitions

  • the following disclosure relates to a cam mechanism applied to a vehicle and a clutch device using the cam mechanism.
  • a clutch may be interposed between two shafts for the purpose of switching between a two-wheel drive (2WD) mode and a four-wheel drive (4WD) mode, and an actuator may control connection / disconnection of the clutch. Since it is difficult to generate a sufficient thrust force by a single means, a cam mechanism may be combined to increase the output.
  • Patent Document 1 is advantageous in generating a large thrust force, but the burden on the actuator is rather increased. Even if the roll can roll without friction at a certain point on the contact line facing in the radial direction, the cam surface has a circumferential speed difference with respect to the roll at the inner side or the outer side in the radial direction from that point. Friction inevitably occurs between the cam surface and the roll. The inventors have discovered that when bearing large thrust forces, such friction can cause significant resistance or damage the cam surface and roll.
  • the cam mechanism has an annular shape around an axis, is arranged in a circumferential direction on one surface of the annular ring facing in the axial direction, and each of the cam mechanisms is perpendicular to the axis.
  • a cam ring provided with a plurality of cam surfaces inclined in the circumferential direction, and adjacent to the surface of the cam ring in the axial direction and facing the surface of the cam ring and symmetrical with the cam surfaces of the cam ring
  • a pressure ring provided with a plurality of cam surfaces and rotatable relative to the cam ring around the shaft; and a plurality of taper rollers interposed between the cam ring and the pressure ring, each of which is in a radial direction
  • a tapered roller having a conical surface tapered inwardly and capable of rolling on the cam surface.
  • the first rotating member and the second rotating member that can rotate independently around the shaft, the cam mechanism described above, and the cam ring are drivably coupled to each other.
  • FIG. 1 is a cross-sectional view of the clutch device according to the first embodiment.
  • FIG. 2 is a perspective view of the cam ring and the cam member of the cam mechanism according to the first embodiment.
  • FIG. 3 is an exploded perspective view of the cam mechanism according to the first embodiment.
  • FIG. 4 is an exploded perspective view when the cam member of the cam mechanism according to the first embodiment is arranged on the pressure ring.
  • FIG. 5A is a perspective view when the cam ring and the pressure ring of the cam mechanism according to the first embodiment are not relatively rotated.
  • FIG. 5B is a side view of the cam ring and pressure ring corresponding to FIG. 5A.
  • FIG. 6A is a plan view of the cam ring and pressure ring corresponding to FIG. 5A.
  • FIG. 6B is a cross-sectional view taken along line VIB-VIB of FIG. 6A.
  • FIG. 7A is a perspective view when the cam ring and the pressure ring of the cam mechanism according to the first embodiment rotate relative to each other.
  • FIG. 7B is a side view of the cam ring and pressure ring corresponding to FIG. 7A.
  • FIG. 8A is a plan view of the cam ring and pressure ring corresponding to FIG. 7A.
  • 8B is a cross-sectional view taken from line VIIIB-VIIIB in FIG. 8A. It is a perspective view of the cam mechanism which concerns on 2nd Embodiment. It is sectional drawing of the cam mechanism which concerns on 2nd Embodiment.
  • the axis means the rotating shaft of the rotating member, and the radial direction means the direction orthogonal to this.
  • Such a rotation axis usually coincides with the central axis of the cam mechanism.
  • a cam mechanism is used in combination with, for example, a clutch device, an example of which is a multi-plate clutch.
  • a clutch device an example of which is a multi-plate clutch.
  • the combination with the multi-plate clutch is advantageous in that the torque to be transmitted can be controlled continuously in a quantitative manner, but is not necessarily limited to this.
  • an appropriate friction clutch or other spline, dog, synchro cone, etc. Can be combined with a type clutch.
  • the clutch device 101 includes an outer rotating member 103 and an inner rotating member 105 as a pair of rotating members that can rotate independently around an axis, and the outer rotating member 103 and the inner rotating member 105.
  • An intermittent portion 107 that is arranged between the outer rotating member 103 and the inner rotating member 105 by axial movement, an actuator 109 that operates the intermittent portion 107, and an intermittent portion that is operated by the actuator 109.
  • the cam mechanism 1 which operates 107 is provided.
  • the pair of rotating members are not necessarily arranged on the inner side and the outer side, respectively.
  • an independent intermittent part intervenes between these, and a rotating member may also serve as a clutch plate, respectively.
  • the actuator 109 is connected to the cam ring 5 in a driving manner and rotates relative to the pressure ring 9 to cause a cam action, thereby connecting the clutch.
  • the outer rotating member 103 is rotatably supported by a carrier 113 as a stationary member via a bearing 111, and includes a rotor 115 and a housing 117.
  • the rotor 115 is made of a magnetic material, and is arranged such that one side extending portions 119 and 121 and a wall portion 123 that extend to the electromagnet 167 side of the actuator 109 in the axial direction cover the periphery of the electromagnet 167. 123 is arranged between the electromagnet 167 and the pilot clutch 163 of the actuator 109 in the axial direction.
  • a member 125 made of a nonmagnetic material is integrally provided on the wall portion 123 by a fixing means such as welding. That is, since the nonmagnetic member 125 cuts the wall portion 123, the magnetic flux is guided to the armature 165 described later so as to bypass the member 125.
  • the core 175 surrounding the electromagnet 167, the extended portions 119 and 121, the wall portion 123, and the armature 165 constitute a magnetic path that guides a closed magnetic flux loop. When the electromagnet 167 is excited, the magnetic flux attracts the armature 165 toward the wall portion 123.
  • the rotor 115 is provided with an air gap that is opposed to the core 175 of the electromagnet 167 with a small gap therebetween, so that magnetic flux can be transferred from the core 175 of the electromagnet 167 to the rotor 115. .
  • the pilot clutch 163 side of the rotor 115 is an other-side extension portion 127 extending in the axial direction, and a spline-shaped connection portion 129 is provided on the inner periphery of the other-side extension portion 127. It has been.
  • the housing 117 is coupled to the coupling portion 129 so as to be integrally rotatable, and the axial position of the rotor 115 is positioned by abutment of the convex portion 131 provided on the housing 117 with the end portion, and fixing such as welding is performed. By means, it is fixed so as to be rotatable together with the housing 117.
  • the housing 117 is made of a nonmagnetic material and has a bottomed cylindrical shape.
  • a seal member 133 is provided between the housing 117 and the rotor 115 in the radial direction to partition the inside of the outer rotating member 103 from the outside.
  • the bottom wall 135 of the housing 117 is provided with an injection hole 137 for allowing the lubricating oil to flow into the outer rotating member 103. After the lubricating oil is injected, the housing 117 is closed by the lid member 139.
  • a spline-shaped engaging portion 141 is formed on the cylindrical inner periphery of the housing 117, and the outer clutch plate of the intermittent portion 107 is engaged.
  • an engaging portion 143 having a concavo-convex shape in the circumferential direction is formed extending toward the rotor 115 in the axial direction.
  • An outer plate is engaged with the recess.
  • the engaging portion 143 is located on the inner peripheral side of the other extending portion 127 of the rotor 115, and the magnetic flux is transmitted to the other extending portion 127 by disposing the engaging portion 143 made of a nonmagnetic material. It has a difficult structure.
  • a connecting member 145 such as a stud bolt is fixed to the bottom wall portion 135 of the housing 117, and one rotating member (not shown) of the input / output members is provided via the connecting member 145, for example.
  • the outer rotating member 103 is connected to be rotatable together.
  • a seal member 147 that partitions the inside and outside of the carrier 113 is disposed between the outer rotating member 103 and the carrier 113, and a dust cover 149 is disposed so as to cover the periphery of the seal member 147. Yes.
  • the inner rotating member 105 is disposed on the rotational axis of the outer rotating member 103 so as to be rotatable relative to the outer rotating member 103.
  • the inner rotating member 105 is formed in a hollow shape, and is rotatably supported by the outer rotating member 103 via an X ring 151, a sliding bush 153, and a bearing 155 on the outer periphery.
  • the X ring 151 is a sealing means for partitioning the outside with respect to the outside after the lubricating oil is sealed inside the outer rotating member 103.
  • a spline-shaped engaging portion 157 is formed on the outer periphery of the inner rotating member 105, and the inner clutch plate of the intermittent portion 107 and the pressure ring 9 of the cam mechanism 1 are engaged.
  • a partition wall 159 is provided as a single member continuous with the inner rotation member 105 at the central portion on the axial center side of the inner rotation member 105, and partitions the inside and the outside of the outer rotation member 103.
  • a spline-shaped connecting portion 161 is formed on the inner periphery of the inner rotating member 105.
  • the other rotating member (not shown) of the input / output members is connected to the inner rotating member 105 so as to be integrally rotatable.
  • the driving torque transmitted between the inner rotating member 105 and the outer rotating member 103 is interrupted by the interrupting portion 107.
  • the intermittent portion 107 is disposed in the outer rotating member 103 and includes a plurality of outer clutch plates and a plurality of inner clutch plates.
  • the plurality of outer clutch plates are engaged with an engaging portion 141 formed on the inner periphery of the housing 117 so as to be axially movable and integrally rotatable with the outer rotating member 103.
  • the plurality of inner clutch plates are alternately arranged in the axial direction with respect to the plurality of outer clutch plates, and can be moved in the axial direction to an engaging portion 157 formed on the outer periphery of the inner rotating member 105 and rotate integrally with the inner rotating member 105. Engaged as possible.
  • the intermittent portion 107 is a multi-plate clutch composed of a plurality of outer clutch plates and a plurality of inner clutch plates, and is a control type friction clutch capable of intermediate control of transmission torque with sliding friction.
  • Such an interrupting portion 107 is interrupted by the operation of the actuator 109, and interrupts the driving torque transmitted between the outer rotating member 103 and the inner rotating member 105.
  • the actuator 109 includes a pilot clutch 163, an armature 165, an electromagnet 167, and the like.
  • the pilot clutch 163 is arranged between the rotor 115 and the armature 165 in the axial direction in the outer rotating member 103.
  • the pilot clutch 163 includes a plurality of outer plates that are axially movable to the engaging portion 143 of the housing 117 and are connected to the outer rotating member 103 so as to be integrally rotatable, and a plurality of outer plates on the outer periphery of the cam ring 5 of the cam mechanism 1.
  • it is composed of a plurality of inner plates which are alternately arranged in the axial direction and are movable in the axial direction and connected to the cam ring 5 so as to be integrally rotatable.
  • Such a pilot clutch 163 is connected by the armature 165 being attracted and moved by the excitation of the electromagnet 167.
  • the armature 165 is made of a magnetic material, is formed in an annular shape, is disposed to face the rotor 115 with the pilot clutch 163 interposed therebetween in the axial direction, and is disposed in the outer rotating member 103 so as to be movable in the axial direction.
  • the armature 165 is attracted and moved to the rotor 115 side by a magnetic flux loop formed when the electromagnet 167 is excited, and the pilot clutch 163 is connected.
  • the electromagnet 167 is disposed outside the outer rotating member 103 via the bearing 169 in the rotor 115 and is prevented from rotating by the carrier 113 by the rotation preventing member 171 and includes an electromagnetic coil 173 and a core 175.
  • the electromagnetic coil 173 is annularly molded with a predetermined number of turns and molded with resin.
  • a lead wire 177 is connected to the electromagnetic coil 173, and is connected to a controller (not shown) that controls energization via the lead wire 177.
  • a core 175 is disposed around the electromagnetic coil 173.
  • the core 175 is made of a magnetic material so that a magnetic field is formed by energization of the electromagnetic coil 173, has a predetermined magnetic path cross-sectional area, and is disposed between the electromagnetic coil 173 and the rotor 115 in the radial direction.
  • the magnetic flux is transmitted along with 115 to form a magnetic flux loop.
  • the electromagnet 167 is energized to the electromagnetic coil 173 so as to generate the necessary friction torque at the intermittent portion 107 under the control of the controller, the pilot clutch 163 is connected, and the thrust force is generated by the cam mechanism 1.
  • the cam mechanism 1 is composed of a cam ring 5, a pressure ring 9, and a cam member 11.
  • the cam mechanism 1 is adjacent to the clutch device 101, and in particular, the pressure ring 9 is adjacent to the intermittence portion 107. Therefore, the pressure ring 9 can exert a pressing force on the intermittence portion 107 to connect the clutch.
  • the cam ring 5 is disposed on the outer periphery of the inner rotating member 105 so as to be movable in the axial direction, and a plurality of inner plates of the pilot clutch 163 can be rotated integrally with an uneven engagement portion 21 formed on the outer diameter portion of the cam ring 5. It is connected. That is, the cam ring 5 forms a ring around the axis.
  • a thrust bearing 179 that receives a thrust reaction force generated in the cam mechanism 1 is disposed.
  • the pressure ring 9 is axially movable to the engaging portion 157 of the inner rotating member 105 and is disposed so as to be rotatable integrally with the inner rotating member 105.
  • the pressure ring 9 is axially connected to the intermittent portion 107 so as to be able to contact the clutch plate of the intermittent portion 107. Adjacent to each other.
  • the pressure ring 9 is axially moved in the connecting direction of the intermittent portion 107 by the thrust force generated by the cam mechanism 1, and the annular pressing portion 23 formed on the outer peripheral side applies a pressing force to the plurality of clutch plates of the intermittent portion 107. Grant and connect.
  • a plurality of cam surfaces 3 and 7 are formed in the circumferential direction on the axially opposed surfaces of the pressure ring 9 and the cam ring 5, respectively.
  • a cam member 11 is interposed between the seven members.
  • This cam member 11 causes the pressure ring 9 to be connected to the intermittent portion 107 side with a strength corresponding to the friction torque generated in the pilot clutch 163 when a differential rotation occurs between the cam ring 5 and the pressure ring 9 due to the connection of the pilot clutch 163. Generates a cam thrust force that moves in the axial direction.
  • the electromagnet 167 when the electromagnet 167 is energized, the magnetic lines of force are circulated through the core 175, the one-side extending portions 119 and 121 of the rotor 115, the wall portion 123, and the armature 165, thereby forming a magnetic flux loop.
  • the armature 165 is attracted and moved to the electromagnet 167 side, and the pilot clutch 163 is fastened.
  • the fastening torque of the pilot clutch 163 is converted into axial thrust through the cam mechanism 1, and the pressing portion 23 of the pressure ring 9 presses the plurality of clutch plates of the intermittent portion 107 to connect the intermittent portion 107.
  • connection of the intermittent portion 107 connects the outer rotating member 103 and the inner rotating member 105, and for example, it is possible to transmit driving torque between the input / output members.
  • the cam mechanism 1 includes a cam ring 5 having a plurality of cam surfaces 3 formed in the circumferential direction, and is rotatable relative to the cam ring 5 in the axial direction. And a pressure ring 9 formed with a plurality of cam surfaces 7 facing the cam surface 3 of the cam ring 5 in the circumferential direction, and between the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9, the cam ring 5 and the pressure A plurality of cam members 11 that move relative to the circumferential direction between the cam surfaces 3 and 7 by the relative rotation with the ring 9 and move the pressure ring 9 in the axial direction are provided.
  • the cam member 11 is a tapered roller that tapers inward in the radial direction.
  • the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 are in relative movement with respect to the cam surfaces 3 and 7 of the cam member 11.
  • the inclination is set so that the center position on the inner diameter side of the cam member 11 and the center position on the outer diameter side of the cam member 11 are the same in the radial direction.
  • cam ring 5 and the pressure ring 9 include an inner diameter wall portion 13 that restricts the movement of the cam member 11 toward the inner diameter side, and an outer diameter wall portion 15 that restricts the movement of the cam member 11 toward the outer diameter side. Is provided.
  • the inner diameter wall portion 13 and the outer diameter wall portion 15 have a circular shape capable of simultaneously regulating the plurality of cam members 11.
  • the inner end peripheral wall 17 and the outer end peripheral wall 19 of the taper roller in the cam member 11 are formed in curved shapes 20 and 22.
  • the cam member 11 is formed of a material having higher strength than the cam surfaces 3 and 7.
  • Each cam member 11 is a tapered roller formed in a truncated cone shape and tapering inward in the radial direction. That is, each cam member 11 has a conical surface that tapers inward in the radial direction. This alleviates the peripheral speed difference with respect to the cam surfaces 3 and 7 and reduces friction.
  • Each taper roller is dimensioned so that the conical surface bus converges in the axis, preferably to minimize the peripheral speed difference, i.e. the friction.
  • a plurality of cam members 11 are arranged at equal intervals in the circumferential direction of the cam ring 5 and the pressure ring 9 between the cam surfaces 3 and 7 formed on the opposing surfaces of the cam ring 5 and the pressure ring 9 facing each other in the axial direction. ing.
  • the cam ring 5 and the pressure ring 9 rotate relative to each other due to a rotation difference between the cam ring 5 and the pressure ring 9 by controlling the rotation of the cam ring 5 by fastening the pilot clutch 163.
  • the cam member 11 which is a taper roller rolls on the cam surfaces 3 and 7 by the relative rotation of the cam ring 5 and the pressure ring 9, and also moves the pressure ring 9 in the axial direction as described later.
  • the cam ring 5 generally has an annular shape, and the plurality of cam surfaces 3 are arranged in the circumferential direction on one surface of the annular ring facing in the axial direction.
  • the cam surface 3 of the cam ring 5 is formed of two inclined surfaces that are inclined upward on both sides in the circumferential direction, which is both sides of the moving direction of the cam member 11, with respect to one cam member 11.
  • a plurality of crests and troughs are continuously formed at equal intervals in the circumferential direction with respect to each cam member 11 as a set. That is, each cam surface 3 is inclined in the circumferential direction with respect to the circumferential surface orthogonal to the axis.
  • each cam surface 3 of the cam ring 5 is inclined so that the two inclined surfaces expand from the inner diameter side toward the outer diameter side, and therefore, while the cam members 11 roll, Maintain contact. That is, each cam surface 3 is inclined not only in the circumferential direction but also in a direction in which the surface is directed outward in the radial direction, and is in line contact with the conical surface of each cam member 11. This also helps to hold each cam member 11 radially.
  • each cam surface 3 is an inclined surface dimensioned to direct the cam member 11 such that the generatrix of the conical surface always intersects the axis, an example of which is a helical surface centered on the axis . In such a combination, each cam member 11 does not cause skew (inclination) with respect to the radial direction and does not cause a difference in peripheral speed, so that it can roll on each cam surface 3 without friction.
  • the cam surface 7 of the pressure ring 9 is disposed opposite to the cam surface 3 of the cam ring 5 in the axial direction.
  • the pressure ring 9 is also generally ring-shaped and includes a plurality of cam surfaces 7 corresponding to the plurality of cam surfaces 3.
  • the cam surface 7 of the pressure ring 9 has the same inclination angle and the same shape as the cam surface 3 of the cam ring 5, and is at an initial position where no rotational difference is generated between the cam ring 5 and the pressure ring 9.
  • the cam ring 5 is arranged symmetrically facing the cam surface 3 in the axial direction.
  • the movement distance on the outer diameter side of the cam member 11 can be determined in the circumferential movement of the cam surfaces 3 and 7 of the cam member 11.
  • the moving distance on the inner diameter side of the member 11 can be made larger, and blurring of the rotational axis in the circumferential direction of the cam ring 5 and the pressure ring 9 of the cam member 11 can be prevented.
  • cam members 11 each composed of a plurality of tapered rollers are arranged in the valleys between the cam surfaces 3 and 7, respectively.
  • the cam ring 5 and the pressure ring 9 are closest to each other in the axial direction.
  • the pressing portion 23 of the pressure ring 9 presses the plurality of clutch plates of the intermittent portion 107, and the intermittent portion 107 is connected.
  • the cam member 11 is formed of a taper roller, and the cam surfaces 3 and 7 are inclined so as to expand from the inner diameter side toward the outer diameter side. Even if the cam member 11 moves to any position on the cam surfaces 3 and 7, the center position on the inner diameter side of the cam member 11 and the center position on the outer diameter side of the cam member 11 can be made the same in the radial direction. .
  • the design accuracy of the cam mechanism 1 can be improved, the setting of the fastening torque of the pilot clutch 163 in the actuator 109 of the clutch device 101 can be easily changed, and the intermittent portion 107 of the clutch device 101 can be changed.
  • the intermittent characteristics in can be improved.
  • the cam ring 5 and the pressure ring 9 include an inner diameter wall portion 13 positioned on the inner diameter side of each of the cam surfaces 3 and 7, and an outer diameter wall portion 15 positioned on the outer diameter side of the cam surfaces 3 and 7. Is provided.
  • the inner diameter wall portion 13 and the outer diameter wall portion 15 regulate the movement of the cam member 11 toward the inner diameter side in the circumferential movement of the cam surfaces 3 and 7 of the cam member 11, and the outer diameter The wall portion 15 restricts the movement of the cam member 11 toward the outer diameter side.
  • the inner diameter wall portion 13 and the outer diameter wall portion 15 are formed on the opposing surfaces of the cam ring 5 and the pressure ring 9 so as to face each other in the same shape, and have an inner diameter with respect to the plurality of cam members 11. The movement to the side and the movement to the outer diameter side can be restricted.
  • the cam member 11 can be stably moved in the circumferential direction of the cam surfaces 3 and 7, and the axial movement of the pressure ring 9 can be stabilized.
  • the inner diameter wall portion 13 and the outer diameter wall portion 15 have a circular shape that is continuously formed in an annular shape in the circumferential direction so that the plurality of cam members 11 can be simultaneously regulated.
  • the inner diameter wall portion 13 and the outer diameter wall portion 15 have a circular shape, the circumferential movement of all the cam surfaces 3 and 7 of the plurality of cam members 11 can be stably performed.
  • the axial movement of the pressure ring 9 can be stabilized.
  • the inner diameter wall portion 13 and the outer diameter wall portion 15 are provided so that the inner wall surface in contact with the cam member 11 is perpendicular to the end surfaces of the cam ring 5 and the pressure ring 9.
  • the inner end peripheral wall 17 and the outer end peripheral wall 19 of the cam member 11 sliding with the inner wall surfaces of the inner diameter wall portion 13 and the outer diameter wall portion 15 are formed in curved surfaces 20 and 22.
  • the cam member 11 can smoothly move along the curved surfaces of the inner end peripheral wall 17 and the outer end peripheral wall 19.
  • the cam surfaces 3 and 7 can be moved.
  • the cam member 11 is formed of a material having higher material strength than the cam surfaces 3 and 7, that is, the cam ring 5 and the pressure ring 9.
  • the cam member 11 is composed of a taper roller, the contact between the cam member 11 and the cam surfaces 3 and 7 is a line contact, and the contact pressure is higher than the point contact when a ball is used for the cam member 11. Has been lowered.
  • cam member 11 When a ball is used for the cam member 11, if the material strength of the cam member 11 is higher than the material strength of the cam surfaces 3 and 7, stress concentrates on the contact portion of the cam surfaces 3 and 7 with the cam member 11, The cam surfaces 3 and 7 may be damaged.
  • the cam member 11 may be deformed by the contact pressure with the cam surfaces 3 and 7.
  • the cam member 11 made of a taper roller has a reduced contact pressure with the cam surfaces 3 and 7, so even if the material strength of the cam member 11 is higher than that of the cam surfaces 3 and 7, the cam surface 3 , 7 and deformation of the cam member 11 can be prevented.
  • the clutch device 101 it is possible to increase the fastening force of the pilot clutch 163 and increase the moving stroke in the axial direction of the pressure ring 9 without increasing costs due to design changes or design changes.
  • the intermittent characteristics of the part 107 can be improved.
  • the cam member 11 is composed of a tapered roller whose rotation diameter increases from the inner diameter side toward the outer diameter side, and the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 are cams of the cam member 11.
  • the center position on the inner diameter side of the cam member 11 and the center position on the outer diameter side of the cam member 11 in the relative movement with respect to the surfaces 3 and 7 are set so as to be the same in the radial direction.
  • the axial movement of the pressure ring 9 can be designed without considering the frictional resistance caused by the sliding of the cam member 11 on the cam surfaces 3 and 7. Accuracy can be improved.
  • the cam ring 5 and the pressure ring 9 include an inner diameter wall portion 13 that restricts the movement of the cam member 11 toward the inner diameter side, and an outer diameter wall portion 15 that restricts the movement of the cam member 11 toward the outer diameter side. Since it is provided, the cam member 11 can be stably moved in the circumferential direction of the cam surfaces 3 and 7, and the axial movement of the pressure ring 9 can be stabilized.
  • the inner diameter wall portion 13 and the outer diameter wall portion 15 have a circular shape capable of simultaneously regulating the plurality of cam members 11, the circumferential direction of all the cam surfaces 3, 7 of the plurality of cam members 11 is provided. The movement can be stably performed, and the axial movement of the pressure ring 9 can be stabilized.
  • the cam member 11 follows the curved surface of the inner end peripheral wall 17 and the outer end peripheral wall 19.
  • the cam surfaces 3 and 7 can be moved smoothly.
  • the cam member 11 is formed of a material having a material strength higher than that of the cam surfaces 3 and 7, the cam member 11 can be prevented from being deformed and a high cam thrust force of the cam mechanism 1 can be obtained.
  • the design accuracy of the cam mechanism 1 can be improved, so that an accurate design according to the characteristics of the interrupting portion 107 can be performed. Intermittent characteristics can be improved.
  • the outer end surface 203 of the tapered roller in the cam member 11 includes a convex portion that is convex outward in the radial direction, and the convex portion is an appropriate curved surface, for example, a spherical surface.
  • the curvature radius R1 of the curved surface is set smaller than the radius R2 of the inner peripheral surface 205 of the outer diameter wall portion 15.
  • the outer diameter wall portion 15 may be provided on only one of the cam ring 5 and the pressure ring 9.
  • cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 are a first cam surface 207 where the cam member 11 is relatively moved from the initial position to the first operation position, and the cam member is operated second from the first operation position.
  • the first cam surface 207 is set to have a larger inclination angle than the second cam surface 209.
  • the outer diameter wall portion 15 is formed in a circular shape, that is, in a cylindrical shape, so that the inner peripheral surface of the outer diameter wall portion 15 is formed.
  • 205 (see FIG. 13) will have at least two contact points.
  • outer diameter wall portion 15 is provided on each of the cam ring 5 and the pressure ring 9, the outer end surface 203 and the inner peripheral surface 205 of the outer diameter wall portion 15 come into contact at least at four points. .
  • the outer end surface 203 of the tapered roller in the cam member 11 includes a convex portion that is convex outward in the radial direction, and the convex portion is an appropriate curved surface, for example, a spherical surface.
  • the radius of curvature R1 of the outer end surface 203 of the tapered roller is set to be smaller than the radius R2 of the inner peripheral surface 205 of the outer diameter wall portion 15.
  • the outer end surface 203 of the taper roller is convex outward in the radial direction and has a radius of curvature R1 smaller than the radius R2 of the inner peripheral surface 205, it slides in point contact with the inner peripheral surface 205 of the outer peripheral wall portion 15. To do.
  • the radius of curvature R1 of the outer end surface 203 of the taper roller is the same as the definition based on normal technical common sense, and is defined as the radius of the curved surface of the outer end surface 203 as understood with reference to FIG.
  • the curvature radius R1 of the outer end surface 203 is made smaller than the radius R2 of the inner peripheral surface 205 of the outer diameter wall portion 15 in this way, so that the cam member 11 is connected to the cam ring 5.
  • the pressure ring 9 relative to each other between the cam surfaces 3 and 7, the contact point between the outer end surface 203 and the inner peripheral surface 205 of the outer diameter wall portion 15 is one point, and the outer diameter wall portion 15 is connected to the cam ring 5.
  • the pressure ring 9 is provided on each of the pressure rings 9, two contact points between the outer end surface 203 and the inner peripheral surface 205 of the outer diameter wall portion 15 can be provided.
  • the outer diameter wall portion 15 is provided only on the cam ring 5 or only on the pressure ring 9 as shown in FIGS.
  • the inner diameter wall 13 is also provided only on the cam ring 5 or only on the pressure ring 9.
  • the contact point between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15 is set to 1. It can be a point, and the frictional resistance can be further reduced.
  • cam surfaces 3 and 5 of the cam ring 5 and the pressure ring 9 include a first cam surface 207 and a second cam surface 209.
  • the first cam surface 207 moves relative to a certain extent between the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 from the initial position from the valleys of the cam surfaces 3 and 7 positioned at the initial position of the cam member 11. It is provided in the range up to the first operating position when That is, the first cam surface 207 is continuously inclined from the trough, and the trough calms the cam member 11 to the initial position, but when the cam member 11 rolls on the first cam surface 207, the first cam surface 207 Move axially to the operating position.
  • the axial stroke of the pressure ring 9 with respect to the rotational phase between the cam ring 5 and the pressure ring 9 can be increased.
  • the second cam surface 209 is formed at the peak portion of the cam surfaces 3 and 7 where the cam member 11 completes the relative movement between the cam surfaces 5 and 7 between the cam ring 5 and the pressure ring 9 from the first operation position. It is provided in the range up to the second operating position which is the top. That is, the first cam surface 207 to the second cam surface 209 are continuously inclined, and when the cam member 11 rolls on the second cam surface 209, it moves in the axial direction to the second operating position.
  • the rotational phase of the cam ring 5 and the pressure ring 9 is made larger than that of the first cam surface 207, and the displacement ratio of the axial stroke of the pressure ring 9 to this is made smaller.
  • the thrust force of the pressure ring 9 is increased.
  • the first cam surface 207 and the second cam surface 209 are set such that the inclination angle of the first cam surface 207 is larger than the inclination angle of the second cam surface 209.
  • the cam member 11 moves on the second cam surface 209, that is, when the cam member 11 moves from the first operation position to the second operation position, the cam member 11 is positioned on the first cam surface 207.
  • the fastening force of the intermittent portion 107 can be accurately controlled, and the intermittent characteristic of the intermittent portion 107 is improved. Can do.
  • the outer end surface 203 of the taper roller in the cam member 11 is formed in a spherical shape, and the radius of curvature R1 of the outer end surface 203 of the taper roller is larger than the radius R2 of the inner peripheral surface 205 of the outer diameter wall portion 15. Since it is set to be small, the contact between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15 in the relative movement between the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 of the cam member 11. The points can be reduced, and the frictional resistance can be reduced.
  • outer diameter wall portion 15 is provided only on one of the cam ring 5 and the pressure ring 9, the contact between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15. A point can be made into one point, and also frictional resistance can be reduced.
  • first cam surface 207 is set to have an inclination angle larger than that of the second cam surface 209, the first cam surface 207 can improve the responsiveness from the initial position of the cam member 11, and second The cam surface 209 can accurately control the axial movement of the pressure ring 9.
  • the cam ring and the pressure ring are provided with the inner diameter wall portion and the outer diameter wall portion.
  • the present invention is not limited thereto, and at least one of the cam ring and the pressure ring includes an inner diameter wall portion and What is necessary is just to provide an outer-diameter wall part.
  • the inner end peripheral wall and the outer end peripheral wall are formed in a curved shape.
  • the present invention is not limited thereto, and one of the inner end peripheral wall and the outer end peripheral wall is formed in a curved shape. May be.
  • the contact point between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15 is set to 1.
  • the outer end surface 203 of the cam member 11 is not formed into a spherical shape with a radius of curvature R1 as described above, a convex portion (protrusion or the like) is formed in the vicinity of the axial center of the outer end surface 203 of the cam member 11. May be provided so as to abut and slide on the outer diameter wall portion. Also in this case, a curved surface or a flat surface may be formed so that the front end of the convex portion or the edge portion of the front end does not come into contact with the outer diameter wall portion.
  • the actuator is an electromagnetic actuator.
  • the present invention is not limited to this, for example, an actuator that causes relative rotation between the cam ring and the pressure ring, such as a motor, gear, and cam mechanism. Any actuator may be used.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

A cam mechanism (1), which is used in combination with a clutch (107) for transmitting torque between a first rotating member and a second rotating member, is provided with: a cam ring (5), which forms an annulus around a shaft and in which one surface of the annulus that faces the axial direction is provided with multiple cam surfaces (3), which are side-by-side in the circumferential direction and each of which is inclined in the circumferential direction with respect to a circumferential plane that is orthogonal to the shaft; a pressure ring (9), which is adjacent to said surface of the cam ring (5) in the axial direction, is provided with multiple cam surfaces (7) that face said surface of the cam ring (5) and are symmetric with the multiple cam surfaces (3) of the cam ring (5), and is capable of rotating relative to the cam ring (5) around the shaft; and multiple tapered rollers (11), which are interposed between the cam ring (5) and the pressure ring (9), have respective conical surfaces that taper inward in the radial direction, and are capable of rolling on the cam surfaces (3,7).

Description

カム機構及びこのカム機構を用いたクラッチ装置。A cam mechanism and a clutch device using the cam mechanism.
　以下の開示は、車両に適用されるカム機構及びこのカム機構を用いたクラッチ装置に関する。 The following disclosure relates to a cam mechanism applied to a vehicle and a clutch device using the cam mechanism.
　一般に車両は幾つかのクラッチを利用する。例えば二輪駆動（２ＷＤ）モードと四輪駆動（４ＷＤ）モードとを切り替える目的で、２つのシャフトの間にクラッチが介在し、その連結－脱連結をアクチュエータが制御することがある。単独の手段によって十分なスラスト力を発生することは難しいので、その出力を増大するために、カム機構を組み合わせることがある。 Generally, vehicles use several clutches. For example, a clutch may be interposed between two shafts for the purpose of switching between a two-wheel drive (2WD) mode and a four-wheel drive (4WD) mode, and an actuator may control connection / disconnection of the clutch. Since it is difficult to generate a sufficient thrust force by a single means, a cam mechanism may be combined to increase the output.
　カム機構を滑らかに作動させる目的で、カム部材の間にボールを介在させることがある。相対的に回転するカム面の間でボールが転動することにより、ボールは摺動抵抗を著しく減ずる。これはアクチュエータの負担を軽減するが、カム面とボールとは点接触するに過ぎないので、大きなスラスト力をカム機構に負担させるには問題がある。ボールに代えて線接触が可能なロールを利用することは、かかる問題を解決する手段の一であろう。特許文献１は、関連する技術を開示する。 ∙ Balls may be interposed between cam members for the purpose of smoothly operating the cam mechanism. As the ball rolls between the relatively rotating cam surfaces, the ball significantly reduces sliding resistance. This reduces the burden on the actuator, but the cam surface and the ball are only in point contact, and there is a problem in placing a large thrust force on the cam mechanism. Using a roll capable of line contact instead of a ball would be one means for solving such a problem. Patent Document 1 discloses a related technique.
特開２００５－２０１２８８号公報JP 2005-201288 A
　本発明者らが検討したところによれば、特許文献１に開示された構造は、大きなスラスト力を発生するに有利だが、アクチュエータの負担はむしろ増大することが明らかになった。径方向に向いた接触線上のある点においてロールが摩擦なしに転動できるとしても、その点より径方向に内寄りまたは外寄りでは、カム面はロールに対して周速差を有するために、カム面とロールとの間に不可避的に摩擦が生じてしまう。大きなスラスト力を負担するとき、かかる摩擦が著しい抵抗を生じ、あるいはカム面およびロールを損傷しかねないことを、本発明者らは発見した。 According to a study by the present inventors, it has been clarified that the structure disclosed in Patent Document 1 is advantageous in generating a large thrust force, but the burden on the actuator is rather increased. Even if the roll can roll without friction at a certain point on the contact line facing in the radial direction, the cam surface has a circumferential speed difference with respect to the roll at the inner side or the outer side in the radial direction from that point. Friction inevitably occurs between the cam surface and the roll. The inventors have discovered that when bearing large thrust forces, such friction can cause significant resistance or damage the cam surface and roll.
　下記の装置は、上述のごとき問題の要因の発見に基づき、線接触の利点を享受しながら摩擦抵抗を低減して滑らかな作動を可能にすることを目的として創出された。 The following devices were created for the purpose of enabling smooth operation by reducing the frictional resistance while enjoying the advantages of line contact based on the discovery of the above-mentioned problem factors.
　第１の局面によれば、カム機構は、軸の周りに円環をなし、軸方向に向いた前記円環の一の面上に周方向に並び、それぞれ前記軸に直交する周面に対して周方向に傾斜した複数のカム面を備えた、カムリングと、前記カムリングの前記面に軸方向に隣接し、前記カムリングの前記面に対向して前記カムリングの前記複数のカム面に対称的な複数のカム面を備え、前記軸の周りに前記カムリングに対して相対的に回転可能な、プレッシャリングと、前記カムリングと前記プレッシャリングとの間に介在した複数のテーパローラであって、それぞれ径方向に内方に向かって先細になる円錐面を備えて前記カム面上を転動可能なテーパローラと、を備える。 According to the first aspect, the cam mechanism has an annular shape around an axis, is arranged in a circumferential direction on one surface of the annular ring facing in the axial direction, and each of the cam mechanisms is perpendicular to the axis. A cam ring provided with a plurality of cam surfaces inclined in the circumferential direction, and adjacent to the surface of the cam ring in the axial direction and facing the surface of the cam ring and symmetrical with the cam surfaces of the cam ring A pressure ring provided with a plurality of cam surfaces and rotatable relative to the cam ring around the shaft; and a plurality of taper rollers interposed between the cam ring and the pressure ring, each of which is in a radial direction And a tapered roller having a conical surface tapered inwardly and capable of rolling on the cam surface.
　第２の局面によれば、それぞれ前記軸の周りに独立して回転可能な第１の回転部材および第２の回転部材と、上述のカム機構と、前記カムリングに駆動的に結合してこれを回転せしめるアクチュエータと、前記プレッシャリングに隣接し、前記プレッシャリングから押圧力を受けて脱連結可能に連結して前記第１の回転部材と前記第２の回転部材との間でトルクを伝達するクラッチと、を備える。 According to the second aspect, the first rotating member and the second rotating member that can rotate independently around the shaft, the cam mechanism described above, and the cam ring are drivably coupled to each other. An actuator that rotates, and a clutch that is adjacent to the pressure ring and receives a pressing force from the pressure ring and is detachably connected to transmit torque between the first rotating member and the second rotating member. And comprising.
図１は、第１実施形態に係るクラッチ装置の断面図である。FIG. 1 is a cross-sectional view of the clutch device according to the first embodiment. 図２は、第１実施形態に係るカム機構のカムリングとカム部材との斜視図である。FIG. 2 is a perspective view of the cam ring and the cam member of the cam mechanism according to the first embodiment. 図３は、第１実施形態に係るカム機構の分解斜視図である。FIG. 3 is an exploded perspective view of the cam mechanism according to the first embodiment. 図４は、第１実施形態に係るカム機構のカム部材をプレッシャリングに配置させたときの分解斜視図である。FIG. 4 is an exploded perspective view when the cam member of the cam mechanism according to the first embodiment is arranged on the pressure ring. 図５Ａは第１実施形態に係るカム機構のカムリングとプレッシャリングとが相対回転していないときの斜視図である。FIG. 5A is a perspective view when the cam ring and the pressure ring of the cam mechanism according to the first embodiment are not relatively rotated. 図５Ｂは、図５Ａに対応するカムリングとプレッシャリングの側面図である。FIG. 5B is a side view of the cam ring and pressure ring corresponding to FIG. 5A. 図６Ａは図５Ａに対応するカムリングとプレッシャリングの平面図である。FIG. 6A is a plan view of the cam ring and pressure ring corresponding to FIG. 5A. 図６Ｂは図６ＡのＶＩＢ－ＶＩＢ線から取られた断面図である。6B is a cross-sectional view taken along line VIB-VIB of FIG. 6A. 図７Ａは第１実施形態に係るカム機構のカムリングとプレッシャリングとが相対回転したときの斜視図である。FIG. 7A is a perspective view when the cam ring and the pressure ring of the cam mechanism according to the first embodiment rotate relative to each other. 図７Ｂは、図７Ａに対応するカムリングとプレッシャリングの側面図である。FIG. 7B is a side view of the cam ring and pressure ring corresponding to FIG. 7A. 図８Ａは図７Ａに対応するカムリングとプレッシャリングの平面図である。FIG. 8A is a plan view of the cam ring and pressure ring corresponding to FIG. 7A. 図８Ｂは、図８ＡのＶＩＩＩＢ－ＶＩＩＩＢ線から取られた断面図である。8B is a cross-sectional view taken from line VIIIB-VIIIB in FIG. 8A. 第２実施形態に係るカム機構の斜視図である。It is a perspective view of the cam mechanism which concerns on 2nd Embodiment. 第２実施形態に係るカム機構の断面図である。It is sectional drawing of the cam mechanism which concerns on 2nd Embodiment. 第２実施形態に係るカム機構の断面図である。It is sectional drawing of the cam mechanism which concerns on 2nd Embodiment. 第２実施形態に係るカム機構のカム部材の側面図である。It is a side view of the cam member of the cam mechanism which concerns on 2nd Embodiment. 第２実施形態に係るカム機構のカムリングの正面図である。It is a front view of the cam ring of the cam mechanism which concerns on 2nd Embodiment. 第２実施形態に係るカム機構の他例を示す断面図である。It is sectional drawing which shows the other example of the cam mechanism which concerns on 2nd Embodiment.
　添付の図面を参照して以下に幾つかの例示的な実施形態を説明する。以下の説明および請求の範囲を通じて、特段の説明がなければ、軸は回転部材の回転軸の意味であり、また径方向はこれに直交する方向を意味する。かかる回転軸は、通常にはカム機構の中心軸とも一致する。 Several exemplary embodiments are described below with reference to the accompanying drawings. Throughout the following description and claims, unless otherwise specified, the axis means the rotating shaft of the rotating member, and the radial direction means the direction orthogonal to this. Such a rotation axis usually coincides with the central axis of the cam mechanism.
　まず、図１を参照するに、カム機構は例えばクラッチ装置と組み合わせて使用され、その一例は多板クラッチである。多板クラッチとの組み合わせは、伝達するトルクを量的に連続的に制御できる点で利点があるが、必ずしもこれに限られず、例えば適宜の摩擦クラッチ、ないしスプライン、ドッグ、シンクロコーン等の他の形式のクラッチと組み合わせることができる。 First, referring to FIG. 1, a cam mechanism is used in combination with, for example, a clutch device, an example of which is a multi-plate clutch. The combination with the multi-plate clutch is advantageous in that the torque to be transmitted can be controlled continuously in a quantitative manner, but is not necessarily limited to this. For example, an appropriate friction clutch or other spline, dog, synchro cone, etc. Can be combined with a type clutch.
　本実施の形態に係るクラッチ装置１０１は、軸の周りに独立して回転可能な一対の回転部材としての外側回転部材１０３と内側回転部材１０５と、この外側回転部材１０３と内側回転部材１０５との間に配置され軸方向移動によって外側回転部材１０３と内側回転部材１０５との間の動力伝達を断続する断続部１０７と、この断続部１０７を作動させるアクチュエータ１０９と、このアクチュエータ１０９の作動により断続部１０７を操作するカム機構１とを備えている。なお他の形式のクラッチにおいては、一対の回転部材がそれぞれ内側と外側に配置されるとは限られない。また独立した断続部がこれらの間に介在するとは限られず、回転部材がそれぞれクラッチ板を兼ねることがありうる。アクチュエータ１０９は、後述の通り、カムリング５に駆動的に結合してこれをプレッシャリング９に対して相対回転せしめてカム作用を引き起こし、以ってクラッチを連結せしめる。 The clutch device 101 according to the present embodiment includes an outer rotating member 103 and an inner rotating member 105 as a pair of rotating members that can rotate independently around an axis, and the outer rotating member 103 and the inner rotating member 105. An intermittent portion 107 that is arranged between the outer rotating member 103 and the inner rotating member 105 by axial movement, an actuator 109 that operates the intermittent portion 107, and an intermittent portion that is operated by the actuator 109. The cam mechanism 1 which operates 107 is provided. In other types of clutches, the pair of rotating members are not necessarily arranged on the inner side and the outer side, respectively. Moreover, it is not necessarily that an independent intermittent part intervenes between these, and a rotating member may also serve as a clutch plate, respectively. As will be described later, the actuator 109 is connected to the cam ring 5 in a driving manner and rotates relative to the pressure ring 9 to cause a cam action, thereby connecting the clutch.
　外側回転部材１０３は、ベアリング１１１を介して静止系部材としてのキャリア１１３に回転可能に支持され、ロータ１１５と、ハウジング１１７とから構成されている。 The outer rotating member 103 is rotatably supported by a carrier 113 as a stationary member via a bearing 111, and includes a rotor 115 and a housing 117.
　ロータ１１５は、磁性材料からなり、軸方向のアクチュエータ１０９の電磁石１６７側に延設された一側延設部１１９，１２１と壁部１２３とが電磁石１６７の周囲を覆うように配置され、壁部１２３が電磁石１６７とアクチュエータ１０９のパイロットクラッチ１６３との軸方向間に配置されている。 The rotor 115 is made of a magnetic material, and is arranged such that one side extending portions 119 and 121 and a wall portion 123 that extend to the electromagnet 167 side of the actuator 109 in the axial direction cover the periphery of the electromagnet 167. 123 is arranged between the electromagnet 167 and the pilot clutch 163 of the actuator 109 in the axial direction.
　また、壁部１２３には、非磁性材料からなる部材１２５が溶接などの固定手段によって壁部１２３と一体的に設けられている。すなわち、非磁性の部材１２５が壁部１２３を切断しているので、磁束は部材１２５を迂回するように後述のアーマチャ１６５へ導かれる。電磁石１６７を囲むコア１７５、延設部１１９，１２１、壁部１２３、およびアーマチャ１６５は、閉じた磁束ループを導く磁路を構成する。電磁石１６７が励磁されると、磁束はアーマチャ１６５を壁部１２３に向かって吸引する。 Further, a member 125 made of a nonmagnetic material is integrally provided on the wall portion 123 by a fixing means such as welding. That is, since the nonmagnetic member 125 cuts the wall portion 123, the magnetic flux is guided to the armature 165 described later so as to bypass the member 125. The core 175 surrounding the electromagnet 167, the extended portions 119 and 121, the wall portion 123, and the armature 165 constitute a magnetic path that guides a closed magnetic flux loop. When the electromagnet 167 is excited, the magnetic flux attracts the armature 165 toward the wall portion 123.
　このロータ１１５は、電磁石１６７のコア１７５との径方向間に微小隙間を持って対向するエアギャップが設けられており、電磁石１６７のコア１７５からロータ１１５への磁束の受け渡しが可能となっている。 The rotor 115 is provided with an air gap that is opposed to the core 175 of the electromagnet 167 with a small gap therebetween, so that magnetic flux can be transferred from the core 175 of the electromagnet 167 to the rotor 115. .
　このようなロータ１１５のパイロットクラッチ１６３側は、軸方向に延設された他側延設部１２７となっており、この他側延設部１２７の内周にはスプライン形状の連結部１２９が設けられている。 The pilot clutch 163 side of the rotor 115 is an other-side extension portion 127 extending in the axial direction, and a spline-shaped connection portion 129 is provided on the inner periphery of the other-side extension portion 127. It has been.
　この連結部１２９には、ハウジング１１７が一体回転可能に連結されると共に、ハウジング１１７に設けられた凸部１３１と端部が当接することによってロータ１１５の軸方向位置が位置決めされ、溶接などの固定手段によってハウジング１１７と一体回転可能に固定される。 The housing 117 is coupled to the coupling portion 129 so as to be integrally rotatable, and the axial position of the rotor 115 is positioned by abutment of the convex portion 131 provided on the housing 117 with the end portion, and fixing such as welding is performed. By means, it is fixed so as to be rotatable together with the housing 117.
　ハウジング１１７は、非磁性材料からなり、有底の筒状に形成されている。また、ハウジング１１７とロータ１１５との径方向間には、外側回転部材１０３の内部を外部から区画するシール部材１３３が設けられている。 The housing 117 is made of a nonmagnetic material and has a bottomed cylindrical shape. A seal member 133 is provided between the housing 117 and the rotor 115 in the radial direction to partition the inside of the outer rotating member 103 from the outside.
　なお、ハウジング１１７の底壁部１３５には、外側回転部材１０３内に潤滑油を流入させる注入孔１３７が設けられ、潤滑油を注入させた後、蓋部材１３９によって閉塞される。 The bottom wall 135 of the housing 117 is provided with an injection hole 137 for allowing the lubricating oil to flow into the outer rotating member 103. After the lubricating oil is injected, the housing 117 is closed by the lid member 139.
　このハウジング１１７の筒状の内周には、スプライン形状の係合部１４１が形成され、断続部１０７の外側クラッチ板が係合されている。 A spline-shaped engaging portion 141 is formed on the cylindrical inner periphery of the housing 117, and the outer clutch plate of the intermittent portion 107 is engaged.
　また、係合部１４１と軸方向に隣り合うハウジング１１７の端部には、軸方向のロータ１１５側に向けて延設され周方向に凹凸形状の係合部１４３が形成され、パイロットクラッチ１６３の外側プレートが凹部に係合されている。 Further, at the end of the housing 117 adjacent to the engaging portion 141 in the axial direction, an engaging portion 143 having a concavo-convex shape in the circumferential direction is formed extending toward the rotor 115 in the axial direction. An outer plate is engaged with the recess.
　この係合部１４３は、ロータ１１５の他側延設部１２７の内周側に位置されており、非磁性材料の係合部１４３を配置させることによって他側延設部１２７に磁束が透過し難い構造となっている。 The engaging portion 143 is located on the inner peripheral side of the other extending portion 127 of the rotor 115, and the magnetic flux is transmitted to the other extending portion 127 by disposing the engaging portion 143 made of a nonmagnetic material. It has a difficult structure.
　このようなハウジング１１７の底壁部１３５には、スタッドボルトなどの連結部材１４５が固定され、この連結部材１４５を介して、例えば、入出力部材のうちいずれか一方の回転部材（不図示）が外側回転部材１０３と一体回転可能に連結される。 A connecting member 145 such as a stud bolt is fixed to the bottom wall portion 135 of the housing 117, and one rotating member (not shown) of the input / output members is provided via the connecting member 145, for example. The outer rotating member 103 is connected to be rotatable together.
　なお、外側回転部材１０３とキャリア１１３との間には、キャリア１１３の内部と外部とを区画するシール部材１４７が配置されると共に、シール部材１４７の周囲を覆うようにダストカバー１４９が配置されている。 A seal member 147 that partitions the inside and outside of the carrier 113 is disposed between the outer rotating member 103 and the carrier 113, and a dust cover 149 is disposed so as to cover the periphery of the seal member 147. Yes.
　このような外側回転部材１０３の回転軸心部には、内側回転部材１０５が外側回転部材１０３と相対回転可能に配置されている。 The inner rotating member 105 is disposed on the rotational axis of the outer rotating member 103 so as to be rotatable relative to the outer rotating member 103.
　内側回転部材１０５は、中空状に形成され、外周でＸリング１５１、摺動ブッシュ１５３、ベアリング１５５を介して外側回転部材１０３に回転可能に支持されている。 The inner rotating member 105 is formed in a hollow shape, and is rotatably supported by the outer rotating member 103 via an X ring 151, a sliding bush 153, and a bearing 155 on the outer periphery.
　なお、Ｘリング１５１は、外側回転部材１０３の内部に潤滑油を封入した後、外部に対して区画するシール手段となっている。 Note that the X ring 151 is a sealing means for partitioning the outside with respect to the outside after the lubricating oil is sealed inside the outer rotating member 103.
　この内側回転部材１０５の外周には、スプライン形状の係合部１５７が形成され、断続部１０７の内側クラッチ板と、カム機構１のプレッシャリング９とが係合されている。 A spline-shaped engaging portion 157 is formed on the outer periphery of the inner rotating member 105, and the inner clutch plate of the intermittent portion 107 and the pressure ring 9 of the cam mechanism 1 are engaged.
　また、内側回転部材１０５の軸心側の中央部には、区画壁１５９が内側回転部材１０５と連続する一部材で設けられ、外側回転部材１０３の内部と外部とを区画している。 Further, a partition wall 159 is provided as a single member continuous with the inner rotation member 105 at the central portion on the axial center side of the inner rotation member 105, and partitions the inside and the outside of the outer rotation member 103.
　このような内側回転部材１０５の内周には、スプライン形状の連結部１６１が形成され、例えば、入出力部材のうち他方の回転部材（不図示）が内側回転部材１０５と一体回転可能に連結される。 A spline-shaped connecting portion 161 is formed on the inner periphery of the inner rotating member 105. For example, the other rotating member (not shown) of the input / output members is connected to the inner rotating member 105 so as to be integrally rotatable. The
　このような内側回転部材１０５と外側回転部材１０３との間に伝達される駆動トルクは、断続部１０７によって断続される。 The driving torque transmitted between the inner rotating member 105 and the outer rotating member 103 is interrupted by the interrupting portion 107.
　断続部１０７は、外側回転部材１０３内に配置され、複数の外側クラッチ板と、複数の内側クラッチ板とを備えている。 The intermittent portion 107 is disposed in the outer rotating member 103 and includes a plurality of outer clutch plates and a plurality of inner clutch plates.
　複数の外側クラッチ板は、ハウジング１１７の内周に形成された係合部１４１に軸方向移動可能で外側回転部材１０３と一体回転可能に係合されている。 The plurality of outer clutch plates are engaged with an engaging portion 141 formed on the inner periphery of the housing 117 so as to be axially movable and integrally rotatable with the outer rotating member 103.
　複数の内側クラッチ板は、複数の外側クラッチ板に対して軸方向に交互に配置され、内側回転部材１０５の外周に形成された係合部１５７に軸方向移動可能で内側回転部材１０５と一体回転可能に係合されている。 The plurality of inner clutch plates are alternately arranged in the axial direction with respect to the plurality of outer clutch plates, and can be moved in the axial direction to an engaging portion 157 formed on the outer periphery of the inner rotating member 105 and rotate integrally with the inner rotating member 105. Engaged as possible.
　この断続部１０７は、複数の外側クラッチ板と複数の内側クラッチ板とで構成された多板クラッチであり、滑り摩擦を伴い伝達トルクを中間制御可能な制御型の摩擦クラッチとなっている。 The intermittent portion 107 is a multi-plate clutch composed of a plurality of outer clutch plates and a plurality of inner clutch plates, and is a control type friction clutch capable of intermediate control of transmission torque with sliding friction.
　このような断続部１０７は、アクチュエータ１０９の作動によって断続され、外側回転部材１０３と内側回転部材１０５との間に伝達される駆動トルクを断続する。 Such an interrupting portion 107 is interrupted by the operation of the actuator 109, and interrupts the driving torque transmitted between the outer rotating member 103 and the inner rotating member 105.
　アクチュエータ１０９は、パイロットクラッチ１６３と、アーマチャ１６５と、電磁石１６７などから構成されている。 The actuator 109 includes a pilot clutch 163, an armature 165, an electromagnet 167, and the like.
　パイロットクラッチ１６３は、外側回転部材１０３内でロータ１１５とアーマチャ１６５との軸方向間に配置されている。 The pilot clutch 163 is arranged between the rotor 115 and the armature 165 in the axial direction in the outer rotating member 103.
　このパイロットクラッチ１６３は、ハウジング１１７の係合部１４３に軸方向移動可能で外側回転部材１０３と一体回転可能に連結する複数の外側プレートと、カム機構１のカムリング５の外周に複数の外側プレートに対して軸方向間に交互に配置され軸方向移動可能でカムリング５と一体回転可能に連結する複数の内側プレートとで構成されている。 The pilot clutch 163 includes a plurality of outer plates that are axially movable to the engaging portion 143 of the housing 117 and are connected to the outer rotating member 103 so as to be integrally rotatable, and a plurality of outer plates on the outer periphery of the cam ring 5 of the cam mechanism 1. On the other hand, it is composed of a plurality of inner plates which are alternately arranged in the axial direction and are movable in the axial direction and connected to the cam ring 5 so as to be integrally rotatable.
　このようなパイロットクラッチ１６３は、アーマチャ１６５が電磁石１６７の励磁によって吸引移動されることにより接続される。 Such a pilot clutch 163 is connected by the armature 165 being attracted and moved by the excitation of the electromagnet 167.
　アーマチャ１６５は、磁性材料からなり、環状に形成され、軸方向にパイロットクラッチ１６３を挟んでロータ１１５と対向配置され、外側回転部材１０３内に軸方向移動可能に配置されている。 The armature 165 is made of a magnetic material, is formed in an annular shape, is disposed to face the rotor 115 with the pilot clutch 163 interposed therebetween in the axial direction, and is disposed in the outer rotating member 103 so as to be movable in the axial direction.
　このアーマチャ１６５は、電磁石１６７が励磁されたときに形成される磁束ループによってロータ１１５側に吸引移動され、パイロットクラッチ１６３を接続させる。 The armature 165 is attracted and moved to the rotor 115 side by a magnetic flux loop formed when the electromagnet 167 is excited, and the pilot clutch 163 is connected.
　電磁石１６７は、ロータ１１５内でベアリング１６９を介して外側回転部材１０３の外部に配置されると共に、回り止め部材１７１によってキャリア１１３に回り止めされ、電磁コイル１７３とコア１７５とを備えている。 The electromagnet 167 is disposed outside the outer rotating member 103 via the bearing 169 in the rotor 115 and is prevented from rotating by the carrier 113 by the rotation preventing member 171 and includes an electromagnetic coil 173 and a core 175.
　電磁コイル１７３は、環状に所定巻き数巻回されて樹脂でモールド成形されている。また、電磁コイル１７３には、リード線１７７が接続され、このリード線１７７を介して通電を制御するコントローラ（不図示）に接続されている。この電磁コイル１７３の周囲には、コア１７５が配置されている。 The electromagnetic coil 173 is annularly molded with a predetermined number of turns and molded with resin. In addition, a lead wire 177 is connected to the electromagnetic coil 173, and is connected to a controller (not shown) that controls energization via the lead wire 177. A core 175 is disposed around the electromagnetic coil 173.
　コア１７５は、電磁コイル１７３への通電により磁界が形成されるように磁性材料から形成され、所定の磁路断面積を有し、電磁コイル１７３とロータ１１５との径方向間に配置されてロータ１１５と共に磁束を透過して磁束ループを形成させる。 The core 175 is made of a magnetic material so that a magnetic field is formed by energization of the electromagnetic coil 173, has a predetermined magnetic path cross-sectional area, and is disposed between the electromagnetic coil 173 and the rotor 115 in the radial direction. The magnetic flux is transmitted along with 115 to form a magnetic flux loop.
　この電磁石１６７は、コントローラによる制御によって断続部１０７で必要な摩擦トルクを生じさせるように電磁コイル１７３に通電され、パイロットクラッチ１６３が接続されてカム機構１でスラスト力が発生される。 The electromagnet 167 is energized to the electromagnetic coil 173 so as to generate the necessary friction torque at the intermittent portion 107 under the control of the controller, the pilot clutch 163 is connected, and the thrust force is generated by the cam mechanism 1.
　カム機構１は、カムリング５と、プレッシャリング９と、カム部材１１とから構成されている。カム機構１はクラッチ装置１０１に隣接し、特にプレッシャリング９は断続部１０７に隣接しており、以ってプレッシャリング９は押圧力を断続部１０７に及ぼしてクラッチを連結せしめることができる。 The cam mechanism 1 is composed of a cam ring 5, a pressure ring 9, and a cam member 11. The cam mechanism 1 is adjacent to the clutch device 101, and in particular, the pressure ring 9 is adjacent to the intermittence portion 107. Therefore, the pressure ring 9 can exert a pressing force on the intermittence portion 107 to connect the clutch.
　カムリング５は、内側回転部材１０５の外周に軸方向移動可能に配置され、カムリング５の外径部に形成された凹凸状の係合部２１にパイロットクラッチ１６３の複数の内側プレートが一体回転可能に連結されている。すなわちカムリング５は、軸の周りに円環をなしている。 The cam ring 5 is disposed on the outer periphery of the inner rotating member 105 so as to be movable in the axial direction, and a plurality of inner plates of the pilot clutch 163 can be rotated integrally with an uneven engagement portion 21 formed on the outer diameter portion of the cam ring 5. It is connected. That is, the cam ring 5 forms a ring around the axis.
　このカムリング５とロータ１１５の軸方向間には、カム機構１で生じるスラスト反力を受けるスラストベアリング１７９が配置されている。 Between the cam ring 5 and the rotor 115 in the axial direction, a thrust bearing 179 that receives a thrust reaction force generated in the cam mechanism 1 is disposed.
　このようなカムリング５は、パイロットクラッチ１６３の接続により回転が制御され、プレッシャリング９との間に差回転を生じる。 Rotation of such a cam ring 5 is controlled by the connection of the pilot clutch 163, and differential rotation occurs between the cam ring 5 and the pressure ring 9.
　プレッシャリング９は、内側回転部材１０５の係合部１５７に軸方向移動可能で内側回転部材１０５と一体回転可能に配置され、断続部１０７のクラッチ板と当接可能に断続部１０７と軸方向に隣接配置されている。 The pressure ring 9 is axially movable to the engaging portion 157 of the inner rotating member 105 and is disposed so as to be rotatable integrally with the inner rotating member 105. The pressure ring 9 is axially connected to the intermittent portion 107 so as to be able to contact the clutch plate of the intermittent portion 107. Adjacent to each other.
　このプレッシャリング９は、カム機構１で生じるスラスト力によって断続部１０７の接続方向に軸方向移動され、外周側に形成された環状の押圧部２３で断続部１０７の複数のクラッチ板に押圧力を付与して接続させる。 The pressure ring 9 is axially moved in the connecting direction of the intermittent portion 107 by the thrust force generated by the cam mechanism 1, and the annular pressing portion 23 formed on the outer peripheral side applies a pressing force to the plurality of clutch plates of the intermittent portion 107. Grant and connect.
　このようなプレッシャリング９とカムリング５との軸方向の対向面には、それぞれ複数のカム面３，７（図２，図３参照）が周方向に形成されており、これらのカム面３，７間にカム部材１１が介在されている。 A plurality of cam surfaces 3 and 7 (refer to FIGS. 2 and 3) are formed in the circumferential direction on the axially opposed surfaces of the pressure ring 9 and the cam ring 5, respectively. A cam member 11 is interposed between the seven members.
　このカム部材１１は、パイロットクラッチ１６３の接続によってカムリング５とプレッシャリング９との間に差回転が生じることにより、パイロットクラッチ１６３に生じる摩擦トルクに応じた強さでプレッシャリング９を断続部１０７側へ軸方向押圧移動させるカムスラスト力を発生させる。 This cam member 11 causes the pressure ring 9 to be connected to the intermittent portion 107 side with a strength corresponding to the friction torque generated in the pilot clutch 163 when a differential rotation occurs between the cam ring 5 and the pressure ring 9 due to the connection of the pilot clutch 163. Generates a cam thrust force that moves in the axial direction.
　このように構成されたクラッチ装置１０１では、電磁石１６７への通電により、コア１７５、ロータ１１５の一側延設部１１９，１２１及び壁部１２３、アーマチャ１６５を介した磁力線が循環されて磁束ループが形成され、アーマチャ１６５が電磁石１６７側に吸引移動されてパイロットクラッチ１６３が締結される。 In the clutch device 101 configured as described above, when the electromagnet 167 is energized, the magnetic lines of force are circulated through the core 175, the one- side extending portions 119 and 121 of the rotor 115, the wall portion 123, and the armature 165, thereby forming a magnetic flux loop. The armature 165 is attracted and moved to the electromagnet 167 side, and the pilot clutch 163 is fastened.
　このパイロットクラッチ１６３の締結トルクは、カム機構１を介して軸方向推力に変換され、プレッシャリング９の押圧部２３が断続部１０７の複数のクラッチ板を押圧して断続部１０７が接続される。 The fastening torque of the pilot clutch 163 is converted into axial thrust through the cam mechanism 1, and the pressing portion 23 of the pressure ring 9 presses the plurality of clutch plates of the intermittent portion 107 to connect the intermittent portion 107.
　この断続部１０７の接続により、外側回転部材１０３と内側回転部材１０５とが接続され、例えば、入出力部材間の駆動トルクの伝達が可能となる。 The connection of the intermittent portion 107 connects the outer rotating member 103 and the inner rotating member 105, and for example, it is possible to transmit driving torque between the input / output members.
　例えば図２から図４を参照するに、本実施の形態に係るカム機構１は、周方向に複数のカム面３が形成されたカムリング５と、このカムリング５と相対回転可能で軸方向移動可能に配置され周方向にカムリング５のカム面３と対向する複数のカム面７が形成されたプレッシャリング９と、カムリング５とプレッシャリング９とのカム面３，７間に配置されカムリング５とプレッシャリング９との相対回転によりカム面３，７間で周方向に相対移動してプレッシャリング９を軸方向に移動させる複数のカム部材１１とを備えている。 For example, referring to FIG. 2 to FIG. 4, the cam mechanism 1 according to the present embodiment includes a cam ring 5 having a plurality of cam surfaces 3 formed in the circumferential direction, and is rotatable relative to the cam ring 5 in the axial direction. And a pressure ring 9 formed with a plurality of cam surfaces 7 facing the cam surface 3 of the cam ring 5 in the circumferential direction, and between the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9, the cam ring 5 and the pressure A plurality of cam members 11 that move relative to the circumferential direction between the cam surfaces 3 and 7 by the relative rotation with the ring 9 and move the pressure ring 9 in the axial direction are provided.
　そして、カム部材１１は、径方向に内方に向かって先細になるテーパローラであり、カムリング５とプレッシャリング９とのカム面３，７は、カム部材１１のカム面３，７に対する相対移動におけるカム部材１１の内径側の中心位置とカム部材１１の外径側の中心位置とを径方向に同一とさせる傾斜に設定されている。 The cam member 11 is a tapered roller that tapers inward in the radial direction. The cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 are in relative movement with respect to the cam surfaces 3 and 7 of the cam member 11. The inclination is set so that the center position on the inner diameter side of the cam member 11 and the center position on the outer diameter side of the cam member 11 are the same in the radial direction.
　また、カムリング５とプレッシャリング９とには、カム部材１１の内径側への移動を規制する内径壁部１３と、カム部材１１の外径側への移動を規制する外径壁部１５とが設けられている。 In addition, the cam ring 5 and the pressure ring 9 include an inner diameter wall portion 13 that restricts the movement of the cam member 11 toward the inner diameter side, and an outer diameter wall portion 15 that restricts the movement of the cam member 11 toward the outer diameter side. Is provided.
　さらに、内径壁部１３と外径壁部１５とは、複数のカム部材１１を同時に規制可能な周回形状を備えている。 Furthermore, the inner diameter wall portion 13 and the outer diameter wall portion 15 have a circular shape capable of simultaneously regulating the plurality of cam members 11.
　また、カム部材１１におけるテーパローラの内端周壁１７と外端周壁１９とは、曲面状２０，２２に形成されている。 Further, the inner end peripheral wall 17 and the outer end peripheral wall 19 of the taper roller in the cam member 11 are formed in curved shapes 20 and 22.
　さらに、カム部材１１は、カム面３，７より強度が高い材料で形成されている。 Furthermore, the cam member 11 is formed of a material having higher strength than the cam surfaces 3 and 7.
　各カム部材１１は、円錐台状に形成され、径方向に内方に向かって先細になるテーパローラである。すなわち各カム部材１１は径方向に内方に向かって先細になる円錐面を備える。これは各カム面３，７に対する周速差を緩和して摩擦を軽減する。好ましくは周速差を、すなわち摩擦を、極小化するべく、かかる円錐面の母線が軸において収斂するように、各テーパローラは寸法づけられる。カムリング５とプレッシャリング９との軸方向に対向するそれぞれの対向面に形成されたカム面３，７間に、カムリング５及びプレッシャリング９の周方向に等間隔に複数のカム部材１１が配置されている。 Each cam member 11 is a tapered roller formed in a truncated cone shape and tapering inward in the radial direction. That is, each cam member 11 has a conical surface that tapers inward in the radial direction. This alleviates the peripheral speed difference with respect to the cam surfaces 3 and 7 and reduces friction. Each taper roller is dimensioned so that the conical surface bus converges in the axis, preferably to minimize the peripheral speed difference, i.e. the friction. A plurality of cam members 11 are arranged at equal intervals in the circumferential direction of the cam ring 5 and the pressure ring 9 between the cam surfaces 3 and 7 formed on the opposing surfaces of the cam ring 5 and the pressure ring 9 facing each other in the axial direction. ing.
　このカムリング５とプレッシャリング９とは、上述したように、パイロットクラッチ１６３の締結によるカムリング５の回転の制御により、カムリング５とプレッシャリング９との間に回転差が生じて相対回転する。 As described above, the cam ring 5 and the pressure ring 9 rotate relative to each other due to a rotation difference between the cam ring 5 and the pressure ring 9 by controlling the rotation of the cam ring 5 by fastening the pilot clutch 163.
　このとき、テーパローラであるカム部材１１は、カムリング５とプレッシャリング９との相対回転により、カム面３，７上を転動し、また後述のごとくプレッシャリング９を軸方向に移動させる。 At this time, the cam member 11 which is a taper roller rolls on the cam surfaces 3 and 7 by the relative rotation of the cam ring 5 and the pressure ring 9, and also moves the pressure ring 9 in the axial direction as described later.
　カムリング５は、概して円環をなしており、複数のカム面３は軸方向に向いた円環の一の面上に、周方向に並んでいる。 The cam ring 5 generally has an annular shape, and the plurality of cam surfaces 3 are arranged in the circumferential direction on one surface of the annular ring facing in the axial direction.
　カムリング５のカム面３は、１つのカム部材１１に対してカム部材１１の移動方向の両側である周方向の両側に上り傾斜となる２つの傾斜面で形成され、この２つの傾斜面を１組としてそれぞれのカム部材１１に対して周方向等間隔に山部と谷部とを連続して複数形成されている。すなわち、各カム面３は、軸に直交する周面に対してそれぞれ周方向に傾斜している。 The cam surface 3 of the cam ring 5 is formed of two inclined surfaces that are inclined upward on both sides in the circumferential direction, which is both sides of the moving direction of the cam member 11, with respect to one cam member 11. A plurality of crests and troughs are continuously formed at equal intervals in the circumferential direction with respect to each cam member 11 as a set. That is, each cam surface 3 is inclined in the circumferential direction with respect to the circumferential surface orthogonal to the axis.
　このカムリング５のカム面３は、２つの傾斜面がそれぞれ内径側から外径側に向けて拡がるように傾斜されており、以って各カム部材１１が転動する間、その円錐面と線接触を維持する。すなわち、各カム面３は、周方向のみならず、径方向に外方に面を向ける向きに傾斜し、各カム部材１１の円錐面と線接触する。これはまた、各カム部材１１を径方向に向けて保持するのに役立つ。好ましくは、各カム面３は、円錐面の母線が常に軸に交わるようにカム部材１１を向けさせるように寸法づけられた傾斜面であり、その一例は、軸を中心とした螺旋面である。かかる組み合わせにおいては、各カム部材１１は径方向に対してスキュー（傾き）を生ずることがなく、また周速差が生じないので各カム面３上を摩擦なく転動することができる。 The cam surface 3 of the cam ring 5 is inclined so that the two inclined surfaces expand from the inner diameter side toward the outer diameter side, and therefore, while the cam members 11 roll, Maintain contact. That is, each cam surface 3 is inclined not only in the circumferential direction but also in a direction in which the surface is directed outward in the radial direction, and is in line contact with the conical surface of each cam member 11. This also helps to hold each cam member 11 radially. Preferably, each cam surface 3 is an inclined surface dimensioned to direct the cam member 11 such that the generatrix of the conical surface always intersects the axis, an example of which is a helical surface centered on the axis . In such a combination, each cam member 11 does not cause skew (inclination) with respect to the radial direction and does not cause a difference in peripheral speed, so that it can roll on each cam surface 3 without friction.
　このようなカムリング５のカム面３には、軸方向にプレッシャリング９のカム面７が対向して配置されている。 The cam surface 7 of the pressure ring 9 is disposed opposite to the cam surface 3 of the cam ring 5 in the axial direction.
　プレッシャリング９も、概して円環をなしており、複数のカム面３に対応する複数のカム面７を備える。プレッシャリング９のカム面７は、カムリング５のカム面３と同一の傾斜角度及び同一の形状を有しており、カムリング５とプレッシャリング９との間に回転差が生じていない初期位置で、カムリング５のカム面３と軸方向に対向して対称に配置される。 The pressure ring 9 is also generally ring-shaped and includes a plurality of cam surfaces 7 corresponding to the plurality of cam surfaces 3. The cam surface 7 of the pressure ring 9 has the same inclination angle and the same shape as the cam surface 3 of the cam ring 5, and is at an initial position where no rotational difference is generated between the cam ring 5 and the pressure ring 9. The cam ring 5 is arranged symmetrically facing the cam surface 3 in the axial direction.
　このようにカムリング５とプレッシャリング９とのカム面３，７を形成することにより、カム部材１１のカム面３，７の周方向の移動において、カム部材１１の外径側の移動距離をカム部材１１の内径側の移動距離より大きくすることができ、カム部材１１のカムリング５及びプレッシャリング９の周方向における回転軸心のブレを防止することができる。 By forming the cam surfaces 3 and 7 between the cam ring 5 and the pressure ring 9 in this way, the movement distance on the outer diameter side of the cam member 11 can be determined in the circumferential movement of the cam surfaces 3 and 7 of the cam member 11. The moving distance on the inner diameter side of the member 11 can be made larger, and blurring of the rotational axis in the circumferential direction of the cam ring 5 and the pressure ring 9 of the cam member 11 can be prevented.
　このようなカムリング５とプレッシャリング９との初期位置では、図４，図６Ｂに示すように、互いのカム面３，７間の谷部にそれぞれ複数のテーパローラからなるカム部材１１が配置され、このとき図５Ａ，５Ｂ，６Ａに示すように、カムリング５とプレッシャリング９とが軸方向に最も近接した状態となる。 In the initial positions of the cam ring 5 and the pressure ring 9 as shown in FIGS. 4 and 6B, cam members 11 each composed of a plurality of tapered rollers are arranged in the valleys between the cam surfaces 3 and 7, respectively. At this time, as shown in FIGS. 5A, 5B, and 6A, the cam ring 5 and the pressure ring 9 are closest to each other in the axial direction.
　この状態からカムリング５とプレッシャリング９とに回転差が生じると、図８Ｂに示すように、複数のカム部材１１がそれぞれカム面３，７上を周方向に転動し、図７Ａ，７Ｂ，８Ａに示すように、プレッシャリング９を軸方向に断続部１０７に向けて移動させる。 When a difference in rotation occurs between the cam ring 5 and the pressure ring 9 from this state, as shown in FIG. 8B, the plurality of cam members 11 roll in the circumferential direction on the cam surfaces 3 and 7, respectively. As shown to 8A, the pressure ring 9 is moved toward the intermittent part 107 to an axial direction.
　このプレッシャリング９の軸方向移動により、プレッシャリング９の押圧部２３が断続部１０７の複数のクラッチ板を押圧し、断続部１０７が接続される。 By the movement of the pressure ring 9 in the axial direction, the pressing portion 23 of the pressure ring 9 presses the plurality of clutch plates of the intermittent portion 107, and the intermittent portion 107 is connected.
　このようなカム部材１１のカム面３，７の周方向の移動において、カム部材１１がテーパローラからなり、カム面３，７が内径側から外径側に向けて拡がるように傾斜されているので、カム部材１１がカム面３，７のどの位置に移動しても、カム部材１１の内径側の中心位置とカム部材１１の外径側の中心位置とを径方向に同一とさせることができる。 In such circumferential movement of the cam surfaces 11 and 7 of the cam member 11, the cam member 11 is formed of a taper roller, and the cam surfaces 3 and 7 are inclined so as to expand from the inner diameter side toward the outer diameter side. Even if the cam member 11 moves to any position on the cam surfaces 3 and 7, the center position on the inner diameter side of the cam member 11 and the center position on the outer diameter side of the cam member 11 can be made the same in the radial direction. .
　このため、カム部材１１のカム面３，７の周方向の移動におけるカム部材１１の回転軸心のブレを防止することができ、カム部材１１が、特に、カム部材１１の外径側がカム面３，７上を滑りながら移動することがない。 For this reason, it is possible to prevent blurring of the rotational axis of the cam member 11 during the circumferential movement of the cam surfaces 3 and 7 of the cam member 11, and the cam member 11, particularly, the outer diameter side of the cam member 11 is the cam surface. It does not move while sliding on 3 and 7.
　従って、例えば、プレッシャリング９の軸方向の移動ストロークの設計において、カム面３，７におけるカム部材１１の滑りによって生じる摩擦抵抗など、複雑な条件を考慮する必要がなく、純粋なカム部材１１とカム面３，７との設定で正確な設計を行うことができる。 Therefore, for example, in the design of the movement stroke in the axial direction of the pressure ring 9, it is not necessary to consider complicated conditions such as frictional resistance caused by the sliding of the cam member 11 on the cam surfaces 3 and 7, and the pure cam member 11 and An accurate design can be performed by setting with the cam surfaces 3 and 7.
　特に、カム機構１の設計の正確性を向上することができることにより、クラッチ装置１０１のアクチュエータ１０９におけるパイロットクラッチ１６３の締結トルクの設定などを容易に変更することができ、クラッチ装置１０１の断続部１０７における断続特性を向上することができる。 In particular, since the design accuracy of the cam mechanism 1 can be improved, the setting of the fastening torque of the pilot clutch 163 in the actuator 109 of the clutch device 101 can be easily changed, and the intermittent portion 107 of the clutch device 101 can be changed. The intermittent characteristics in can be improved.
　ここで、カムリング５とプレッシャリング９とには、それぞれのカム面３，７の内径側に位置する内径壁部１３と、カム面３，７の外径側に位置する外径壁部１５とが設けられている。 Here, the cam ring 5 and the pressure ring 9 include an inner diameter wall portion 13 positioned on the inner diameter side of each of the cam surfaces 3 and 7, and an outer diameter wall portion 15 positioned on the outer diameter side of the cam surfaces 3 and 7. Is provided.
　この内径壁部１３と外径壁部１５とは、カム部材１１のカム面３，７の周方向の移動において、内径壁部１３がカム部材１１の内径側への移動を規制し、外径壁部１５がカム部材１１の外径側への移動を規制する。 The inner diameter wall portion 13 and the outer diameter wall portion 15 regulate the movement of the cam member 11 toward the inner diameter side in the circumferential movement of the cam surfaces 3 and 7 of the cam member 11, and the outer diameter The wall portion 15 restricts the movement of the cam member 11 toward the outer diameter side.
　このような内径壁部１３と外径壁部１５とは、カムリング５とプレッシャリング９とのそれぞれの対向面に、同様の形状で対向するように形成され、複数のカム部材１１に対して内径側への移動と、外径側への移動とを規制することができる。 The inner diameter wall portion 13 and the outer diameter wall portion 15 are formed on the opposing surfaces of the cam ring 5 and the pressure ring 9 so as to face each other in the same shape, and have an inner diameter with respect to the plurality of cam members 11. The movement to the side and the movement to the outer diameter side can be restricted.
　このように内径壁部１３と外径壁部１５とを設けることにより、カム部材１１を安定してカム面３，７の周方向に移動させることができ、プレッシャリング９の軸方向移動を安定化することができる。 By providing the inner diameter wall portion 13 and the outer diameter wall portion 15 in this way, the cam member 11 can be stably moved in the circumferential direction of the cam surfaces 3 and 7, and the axial movement of the pressure ring 9 can be stabilized. Can be
　加えて、内径壁部１３と外径壁部１５とは、複数のカム部材１１を同時に規制可能なように、周方向に連続して環状に形成された周回形状をなしている。 In addition, the inner diameter wall portion 13 and the outer diameter wall portion 15 have a circular shape that is continuously formed in an annular shape in the circumferential direction so that the plurality of cam members 11 can be simultaneously regulated.
　このように内径壁部１３と外径壁部１５とを周回形状とすることにより、複数のカム部材１１の全てのカム面３，７の周方向の移動を安定して行うことができ、さらにプレッシャリング９の軸方向移動を安定化することができる。 Thus, by making the inner diameter wall portion 13 and the outer diameter wall portion 15 have a circular shape, the circumferential movement of all the cam surfaces 3 and 7 of the plurality of cam members 11 can be stably performed. The axial movement of the pressure ring 9 can be stabilized.
　ここで、内径壁部１３と外径壁部１５とは、カム部材１１と当接する内壁面が、カムリング５及びプレッシャリング９の端面から垂直となるように突設されている。 Here, the inner diameter wall portion 13 and the outer diameter wall portion 15 are provided so that the inner wall surface in contact with the cam member 11 is perpendicular to the end surfaces of the cam ring 5 and the pressure ring 9.
　このように内径壁部１３と外径壁部１５との内壁面を垂直に設けることにより、内径壁部１３と外径壁部１５との内壁面とカム部材１１の内端周壁１７と外端周壁１９とが摺動したときに、内壁面に沿ってカム部材１１の内径側や外径側が浮き上がることを防止でき、カム部材１１のカム面３，７の周方向における移動を安定化することができる。 Thus, by providing the inner wall surfaces of the inner diameter wall portion 13 and the outer diameter wall portion 15 vertically, the inner wall surfaces of the inner diameter wall portion 13 and the outer diameter wall portion 15, the inner end peripheral wall 17 and the outer end of the cam member 11. When the peripheral wall 19 slides, the inner diameter side and the outer diameter side of the cam member 11 can be prevented from floating along the inner wall surface, and the movement of the cam surfaces 3 and 7 of the cam member 11 in the circumferential direction can be stabilized. Can do.
　この内径壁部１３と外径壁部１５との内壁面と摺動するカム部材１１の内端周壁１７と外端周壁１９とは、曲面状２０，２２に形成されている。 The inner end peripheral wall 17 and the outer end peripheral wall 19 of the cam member 11 sliding with the inner wall surfaces of the inner diameter wall portion 13 and the outer diameter wall portion 15 are formed in curved surfaces 20 and 22.
　このようにカム部材１１の内端周壁１７と外端周壁１９とを曲面状２０，２２に形成することにより、カム部材１１が内端周壁１７と外端周壁１９との曲面に沿ってスムーズにカム面３，７を移動することができる。 In this way, by forming the inner end peripheral wall 17 and the outer end peripheral wall 19 of the cam member 11 in curved shapes 20 and 22, the cam member 11 can smoothly move along the curved surfaces of the inner end peripheral wall 17 and the outer end peripheral wall 19. The cam surfaces 3 and 7 can be moved.
　加えて、カム部材１１は、カム面３，７、すなわちカムリング５及びプレッシャリング９より材料強度が高い材料で形成されている。 In addition, the cam member 11 is formed of a material having higher material strength than the cam surfaces 3 and 7, that is, the cam ring 5 and the pressure ring 9.
　ここで、カム部材１１は、テーパローラからなるので、カム部材１１とカム面３，７との接触が線接触となっており、カム部材１１にボールを使用したときの点接触よりも、接触圧力が低下されている。 Here, since the cam member 11 is composed of a taper roller, the contact between the cam member 11 and the cam surfaces 3 and 7 is a line contact, and the contact pressure is higher than the point contact when a ball is used for the cam member 11. Has been lowered.
　カム部材１１にボールを使用した場合には、カム部材１１の材料強度がカム面３，７の材料強度より高いと、カム面３，７のカム部材１１との接触部分に応力が集中し、カム面３，７に損傷が生じる恐れがあった。 When a ball is used for the cam member 11, if the material strength of the cam member 11 is higher than the material strength of the cam surfaces 3 and 7, stress concentrates on the contact portion of the cam surfaces 3 and 7 with the cam member 11, The cam surfaces 3 and 7 may be damaged.
　このため、カム部材１１にボールを使用した場合には、クラッチ装置１０１において、パイロットクラッチ１６３の締結力を上げて、プレッシャリング９の軸方向の移動ストロークを上げるような場合、カム面３，７の材料強度をさらに高くする必要があり、設計変更や設計変更による高コスト化を引き起こしていた。 For this reason, when a ball is used for the cam member 11, in the clutch device 101, when the fastening force of the pilot clutch 163 is increased to increase the axial movement stroke of the pressure ring 9, the cam surfaces 3, 7 It was necessary to further increase the material strength of the material, which caused a cost increase due to a design change and a design change.
　加えて、カム面３，７の材料強度を高くした場合には、カム面３，７との接触圧力によりカム部材１１に変形が生じる恐れがあった。 In addition, when the material strength of the cam surfaces 3 and 7 is increased, the cam member 11 may be deformed by the contact pressure with the cam surfaces 3 and 7.
　これに対して、テーパローラからなるカム部材１１は、カム面３，７との接触圧力が低下されているので、カム部材１１の材料強度をカム面３，７より高くしても、カム面３，７の損傷やカム部材１１の変形を防止することができる。 On the other hand, the cam member 11 made of a taper roller has a reduced contact pressure with the cam surfaces 3 and 7, so even if the material strength of the cam member 11 is higher than that of the cam surfaces 3 and 7, the cam surface 3 , 7 and deformation of the cam member 11 can be prevented.
　このため、クラッチ装置１０１においては、設計変更や設計変更による高コスト化を伴うことなく、パイロットクラッチ１６３の締結力を上げて、プレッシャリング９の軸方向の移動ストロークを上げることができるなど、断続部１０７の断続特性を向上することができる。 For this reason, in the clutch device 101, it is possible to increase the fastening force of the pilot clutch 163 and increase the moving stroke in the axial direction of the pressure ring 9 without increasing costs due to design changes or design changes. The intermittent characteristics of the part 107 can be improved.
　このようなカム機構１では、カム部材１１が、内径側から外径側に向けて回転径が拡がるテーパローラからなり、カムリング５とプレッシャリング９とのカム面３，７が、カム部材１１のカム面３，７に対する相対移動におけるカム部材１１の内径側の中心位置とカム部材１１の外径側の中心位置とを径方向に同一とさせる傾斜に設定されている。 In such a cam mechanism 1, the cam member 11 is composed of a tapered roller whose rotation diameter increases from the inner diameter side toward the outer diameter side, and the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 are cams of the cam member 11. The center position on the inner diameter side of the cam member 11 and the center position on the outer diameter side of the cam member 11 in the relative movement with respect to the surfaces 3 and 7 are set so as to be the same in the radial direction.
　このため、カム部材１１は、カムリング５とプレッシャリング９とのカム面３，７間で周方向に相対移動するとき、内径側の移動距離と外径側の移動距離との差を吸収しながら回転軸心がブレることがなく、カム部材１１の外径側がカム面３，７上を滑りながら移動することがない。 For this reason, when the cam member 11 relatively moves in the circumferential direction between the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9, it absorbs the difference between the moving distance on the inner diameter side and the moving distance on the outer diameter side. The rotation axis does not move, and the outer diameter side of the cam member 11 does not move while sliding on the cam surfaces 3 and 7.
　従って、このようなカム機構１では、カム面３，７におけるカム部材１１の滑りによって生じる摩擦抵抗などを考慮することなく、プレッシャリング９の軸方向の移動などを設計することができ、設計の正確性を向上することができる。 Therefore, in such a cam mechanism 1, the axial movement of the pressure ring 9 can be designed without considering the frictional resistance caused by the sliding of the cam member 11 on the cam surfaces 3 and 7. Accuracy can be improved.
　また、カムリング５とプレッシャリング９とには、カム部材１１の内径側への移動を規制する内径壁部１３と、カム部材１１の外径側への移動を規制する外径壁部１５とが設けられているので、カム部材１１を安定してカム面３，７の周方向に移動させることができ、プレッシャリング９の軸方向移動を安定化することができる。 In addition, the cam ring 5 and the pressure ring 9 include an inner diameter wall portion 13 that restricts the movement of the cam member 11 toward the inner diameter side, and an outer diameter wall portion 15 that restricts the movement of the cam member 11 toward the outer diameter side. Since it is provided, the cam member 11 can be stably moved in the circumferential direction of the cam surfaces 3 and 7, and the axial movement of the pressure ring 9 can be stabilized.
　さらに、内径壁部１３と外径壁部１５とは、複数のカム部材１１を同時に規制可能な周回形状を備えているので、複数のカム部材１１の全てのカム面３，７の周方向の移動を安定して行うことができ、さらにプレッシャリング９の軸方向移動を安定化することができる。 Further, since the inner diameter wall portion 13 and the outer diameter wall portion 15 have a circular shape capable of simultaneously regulating the plurality of cam members 11, the circumferential direction of all the cam surfaces 3, 7 of the plurality of cam members 11 is provided. The movement can be stably performed, and the axial movement of the pressure ring 9 can be stabilized.
　また、カム部材１１におけるテーパローラの内端周壁１７と外端周壁１９とは、曲面状２０，２２に形成されているので、カム部材１１が内端周壁１７と外端周壁１９との曲面に沿ってスムーズにカム面３，７を移動することができる。 Further, since the inner end peripheral wall 17 and the outer end peripheral wall 19 of the taper roller in the cam member 11 are formed in curved surfaces 20 and 22, the cam member 11 follows the curved surface of the inner end peripheral wall 17 and the outer end peripheral wall 19. The cam surfaces 3 and 7 can be moved smoothly.
　さらに、カム部材１１は、カム面３，７より材料強度が高い材料で形成されているので、カム部材１１の変形を防止して、カム機構１の高いカムスラスト力を得ることができる。 Furthermore, since the cam member 11 is formed of a material having a material strength higher than that of the cam surfaces 3 and 7, the cam member 11 can be prevented from being deformed and a high cam thrust force of the cam mechanism 1 can be obtained.
　また、カム機構１を用いたクラッチ装置１０１では、カム機構１の設計の正確性を向上することができるので、断続部１０７の特性に応じた的確な設計を行うことができ、断続部１０７の断続特性を向上することができる。 Further, in the clutch device 101 using the cam mechanism 1, the design accuracy of the cam mechanism 1 can be improved, so that an accurate design according to the characteristics of the interrupting portion 107 can be performed. Intermittent characteristics can be improved.
　上述の実施形態には幾つかの変形がありうるが、例えば図９～１４に示すごとく変形することができる。 The above-described embodiment can have several modifications, but can be modified as shown in FIGS. 9 to 14, for example.
　本実施の形態に係るカム機構２０１は、カム部材１１におけるテーパローラの外端面２０３は、径方向に外方向に凸である凸部を含み、凸部は適宜の曲面であって例えば球面である。かかる曲面の曲率半径Ｒ１は、外径壁部１５の内周面２０５の半径Ｒ２より小さく設定されている。 In the cam mechanism 201 according to the present embodiment, the outer end surface 203 of the tapered roller in the cam member 11 includes a convex portion that is convex outward in the radial direction, and the convex portion is an appropriate curved surface, for example, a spherical surface. The curvature radius R1 of the curved surface is set smaller than the radius R2 of the inner peripheral surface 205 of the outer diameter wall portion 15.
　図１０，１４に例示されるごとく、外径壁部１５は、カムリング５とプレッシャリング９とのうちいずれか一方にのみ設けられていてもよい。 As illustrated in FIGS. 10 and 14, the outer diameter wall portion 15 may be provided on only one of the cam ring 5 and the pressure ring 9.
　さらに、カムリング５とプレッシャリング９とのカム面３，７は、カム部材１１が初期位置から第１作動位置まで相対移動する第１カム面２０７と、カム部材が第１作動位置から第２作動位置まで相対移動する第２カム面２０９とを有し、第１カム面２０７は、第２カム面２０９より傾斜角度が大きく設定されている。 Further, the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 are a first cam surface 207 where the cam member 11 is relatively moved from the initial position to the first operation position, and the cam member is operated second from the first operation position. The first cam surface 207 is set to have a larger inclination angle than the second cam surface 209.
　なお、第１実施形態と同一の構成には、同一の記号を記して構成及び機能説明は第１実施形態を参照するものとし省略するが、第１実施形態と同一の構成であるので、得られる効果は同一である。 The same components as those of the first embodiment are denoted by the same reference numerals, and the description of the configuration and functions will be omitted with reference to the first embodiment. However, the configuration is the same as that of the first embodiment. The effect achieved is the same.
　ここで、図１～図８に示すカム部材１１には、カムリング５とプレッシャリング９とのカム面３，７間を相対移動するとき、外端面２０３（図１２参照）側が径方向外側に向けて移動するように外力が加わる。 Here, when the cam member 11 shown in FIGS. 1 to 8 is relatively moved between the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9, the outer end surface 203 (see FIG. 12) side faces radially outward. External force is applied to move.
　このため、カム部材１１におけるテーパローラの外端面２０３は、カムリング５とプレッシャリング９とに設けられた外径壁部１５，１５と摺動することになる。 Therefore, the outer end surface 203 of the taper roller in the cam member 11 slides with the outer diameter wall portions 15 and 15 provided on the cam ring 5 and the pressure ring 9.
　このとき、外端面２０３が平面または平面に近い形状で形成されている場合には、外径壁部１５が周回形状、すなわち円筒状に形成されているので、外径壁部１５の内周面２０５（図１３参照）に対して少なくとも２点の接触点を有することになる。 At this time, when the outer end surface 203 is formed in a flat shape or a shape close to a flat surface, the outer diameter wall portion 15 is formed in a circular shape, that is, in a cylindrical shape, so that the inner peripheral surface of the outer diameter wall portion 15 is formed. 205 (see FIG. 13) will have at least two contact points.
　加えて、外径壁部１５は、カムリング５とプレッシャリング９とにそれぞれ設けられているので、外端面２０３と外径壁部１５の内周面２０５とが少なくとも４点で接触することになる。 In addition, since the outer diameter wall portion 15 is provided on each of the cam ring 5 and the pressure ring 9, the outer end surface 203 and the inner peripheral surface 205 of the outer diameter wall portion 15 come into contact at least at four points. .
　このようにカム部材１１のカムリング５とプレッシャリング９とのカム面３，７間の相対移動におけるカム部材１１の外端面２０３と外径壁部１５の内周面２０５との接触点が多いと、摩擦抵抗が増大してしまう。 Thus, when there are many contact points between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15 in the relative movement between the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 of the cam member 11. The frictional resistance will increase.
　そこで、図９～図１４に示すように、カム部材１１におけるテーパローラの外端面２０３は、径方向に外方向に凸である凸部を含み、凸部は適宜の曲面であって例えば球面である。テーパローラの外端面２０３の曲率半径Ｒ１は、外径壁部１５の内周面２０５の半径Ｒ２より小さく設定されている。 Therefore, as shown in FIGS. 9 to 14, the outer end surface 203 of the tapered roller in the cam member 11 includes a convex portion that is convex outward in the radial direction, and the convex portion is an appropriate curved surface, for example, a spherical surface. . The radius of curvature R1 of the outer end surface 203 of the tapered roller is set to be smaller than the radius R2 of the inner peripheral surface 205 of the outer diameter wall portion 15.
　テーパローラの外端面２０３は、径方向に外方向に凸であってその曲率半径Ｒ１が内周面２０５の半径Ｒ２より小さいため、外径壁部１５の内周面２０５に点接触して摺動する。 Since the outer end surface 203 of the taper roller is convex outward in the radial direction and has a radius of curvature R1 smaller than the radius R2 of the inner peripheral surface 205, it slides in point contact with the inner peripheral surface 205 of the outer peripheral wall portion 15. To do.
　ここで、テーパローラの外端面２０３の曲率半径Ｒ１とは、通常の技術常識に基づく定義と同じであり、図１２を参照して理解される通り、外端面２０３の曲面の半径と定義される。 Here, the radius of curvature R1 of the outer end surface 203 of the taper roller is the same as the definition based on normal technical common sense, and is defined as the radius of the curved surface of the outer end surface 203 as understood with reference to FIG.
　図１１，１３を図１２と組み合わせて参照するに、このように外端面２０３の曲率半径Ｒ１を外径壁部１５の内周面２０５の半径Ｒ２より小さくすることにより、カム部材１１がカムリング５とプレッシャリング９とのカム面３，７間を相対移動したとき、外端面２０３と外径壁部１５の内周面２０５との接触点を１点とし、外径壁部１５がカムリング５とプレッシャリング９とにそれぞれ設けられている場合には、外端面２０３と外径壁部１５の内周面２０５との接触点を２点とすることができる。 Referring to FIGS. 11 and 13 in combination with FIG. 12, the curvature radius R1 of the outer end surface 203 is made smaller than the radius R2 of the inner peripheral surface 205 of the outer diameter wall portion 15 in this way, so that the cam member 11 is connected to the cam ring 5. And the pressure ring 9 relative to each other between the cam surfaces 3 and 7, the contact point between the outer end surface 203 and the inner peripheral surface 205 of the outer diameter wall portion 15 is one point, and the outer diameter wall portion 15 is connected to the cam ring 5. When the pressure ring 9 is provided on each of the pressure rings 9, two contact points between the outer end surface 203 and the inner peripheral surface 205 of the outer diameter wall portion 15 can be provided.
　このため、カム部材１１の外端面２０３と外径壁部１５の内周面２０５との摩擦抵抗を低減することができ、カム機構２０１の設計への影響を抑制することができる。 Therefore, the frictional resistance between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15 can be reduced, and the influence on the design of the cam mechanism 201 can be suppressed.
　ここで、外径壁部１５は、図１０，図１４に示すように、カムリング５のみ、或いはプレッシャリング９のみに設けられている。なお、内径壁部１３も、カムリング５のみ、或いはプレッシャリング９のみに設けられている。 Here, the outer diameter wall portion 15 is provided only on the cam ring 5 or only on the pressure ring 9 as shown in FIGS. The inner diameter wall 13 is also provided only on the cam ring 5 or only on the pressure ring 9.
　このように外径壁部１５をカムリング５とプレッシャリング９とうちいずれか一方にのみ設けることにより、カム部材１１の外端面２０３と外径壁部１５の内周面２０５との接触点を１点とすることができ、さらに摩擦抵抗を低減することができる。 Thus, by providing the outer diameter wall portion 15 only on one of the cam ring 5 and the pressure ring 9, the contact point between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15 is set to 1. It can be a point, and the frictional resistance can be further reduced.
　一方、カムリング５とプレッシャリング９とのカム面３，５は、第１カム面２０７と第２カム面２０９とを備えている。 On the other hand, the cam surfaces 3 and 5 of the cam ring 5 and the pressure ring 9 include a first cam surface 207 and a second cam surface 209.
　第１カム面２０７は、カム部材１１の初期位置で位置するカム面３，７の谷部からカム部材１１が初期位置からカムリング５とプレッシャリング９とのカム面３，７間をある程度相対移動するときの第１作動位置までの範囲に設けられている。すなわち、谷部から第１カム面２０７は連続して傾斜しており、谷部はカム部材１１を初期位置に落ち着かせるが、カム部材１１が第１カム面２０７上を転動すると、第１作動位置まで軸方向に移動する。 The first cam surface 207 moves relative to a certain extent between the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 from the initial position from the valleys of the cam surfaces 3 and 7 positioned at the initial position of the cam member 11. It is provided in the range up to the first operating position when That is, the first cam surface 207 is continuously inclined from the trough, and the trough calms the cam member 11 to the initial position, but when the cam member 11 rolls on the first cam surface 207, the first cam surface 207 Move axially to the operating position.
　すなわち、第１カム面２０７によれば第２カム面２０９と異なり、カムリング５とプレッシャリング９との回転位相に対するプレッシャリング９の軸方向ストロークが大きくとれる。 That is, according to the first cam surface 207, unlike the second cam surface 209, the axial stroke of the pressure ring 9 with respect to the rotational phase between the cam ring 5 and the pressure ring 9 can be increased.
　第２カム面２０９は、第１作動位置からカム部材１１が第１作動位置からカムリング５とプレッシャリング９とのカム面３，７間の相対移動を完了するカム面３，７の山部の頂部である第２作動位置までの範囲に設けられている。すなわち、第１カム面２０７から第２カム面２０９は連続して傾斜しており、カム部材１１が第２カム面２０９上を転動すると、第２作動位置まで軸方向に移動する。 The second cam surface 209 is formed at the peak portion of the cam surfaces 3 and 7 where the cam member 11 completes the relative movement between the cam surfaces 5 and 7 between the cam ring 5 and the pressure ring 9 from the first operation position. It is provided in the range up to the second operating position which is the top. That is, the first cam surface 207 to the second cam surface 209 are continuously inclined, and when the cam member 11 rolls on the second cam surface 209, it moves in the axial direction to the second operating position.
　すなわち、第２カム面２０９によれば第１カム面２０７よりも、カムリング５とプレッシャリング９との回転位相を大きくして、これに対するプレッシャリング９の軸方向ストロークの変位割合を小さくすることで、プレッシャリング９のスラスト力を増大させている。 That is, according to the second cam surface 209, the rotational phase of the cam ring 5 and the pressure ring 9 is made larger than that of the first cam surface 207, and the displacement ratio of the axial stroke of the pressure ring 9 to this is made smaller. The thrust force of the pressure ring 9 is increased.
　このような第１カム面２０７と第２カム面２０９とは、第１カム面２０７の傾斜角度が第２カム面２０９の傾斜角度より大きくなるように設定されている。 The first cam surface 207 and the second cam surface 209 are set such that the inclination angle of the first cam surface 207 is larger than the inclination angle of the second cam surface 209.
　このように第１カム面２０７と第２カム面２０９との傾斜角度を設定することにより、カム部材１１が第１カム面２０７を移動するとき、すなわちカム部材１１が初期位置から第１作動位置に移動するとき、カムリング５の少ない回転で大きなプレッシャリング９の軸方向移動距離を得ることができ、プレッシャリング９の初期の応答性を向上することができる。 Thus, by setting the inclination angle between the first cam surface 207 and the second cam surface 209, when the cam member 11 moves on the first cam surface 207, that is, the cam member 11 is moved from the initial position to the first operating position. When moving to a large angle, a large axial movement distance of the pressure ring 9 can be obtained with a small rotation of the cam ring 5, and the initial responsiveness of the pressure ring 9 can be improved.
　これに対して、カム部材１１が第２カム面２０９を移動するとき、すなわちカム部材１１が第１作動位置から第２作動位置に移動するとき、カム部材１１が第１カム面２０７に位置するときよりもカムリング５の多い回転でプレッシャリング９を軸方向移動させることで、断続部１０７（図１参照）の締結力を的確に制御することができ、断続部１０７の断続特性を向上することができる。 On the other hand, when the cam member 11 moves on the second cam surface 209, that is, when the cam member 11 moves from the first operation position to the second operation position, the cam member 11 is positioned on the first cam surface 207. By moving the pressure ring 9 in the axial direction with more rotation of the cam ring 5 than in the case, the fastening force of the intermittent portion 107 (see FIG. 1) can be accurately controlled, and the intermittent characteristic of the intermittent portion 107 is improved. Can do.
　このようなカム機構２０１では、カム部材１１におけるテーパローラの外端面２０３が、球面状に形成され、テーパローラの外端面２０３の曲率半径Ｒ１が、外径壁部１５の内周面２０５の半径Ｒ２より小さく設定されているので、カム部材１１のカムリング５とプレッシャリング９とのカム面３，７間の相対移動におけるカム部材１１の外端面２０３と外径壁部１５の内周面２０５との接触点を低減でき、摩擦抵抗を低減することができる。 In such a cam mechanism 201, the outer end surface 203 of the taper roller in the cam member 11 is formed in a spherical shape, and the radius of curvature R1 of the outer end surface 203 of the taper roller is larger than the radius R2 of the inner peripheral surface 205 of the outer diameter wall portion 15. Since it is set to be small, the contact between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15 in the relative movement between the cam surfaces 3 and 7 of the cam ring 5 and the pressure ring 9 of the cam member 11. The points can be reduced, and the frictional resistance can be reduced.
　また、外径壁部１５は、カムリング５とプレッシャリング９とのうちいずれか一方にのみ設けられているので、カム部材１１の外端面２０３と外径壁部１５の内周面２０５との接触点を１点とすることができ、さらに摩擦抵抗を低減することができる。 Further, since the outer diameter wall portion 15 is provided only on one of the cam ring 5 and the pressure ring 9, the contact between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15. A point can be made into one point, and also frictional resistance can be reduced.
　さらに、第１カム面２０７は、第２カム面２０９より傾斜角度が大きく設定されているので、第１カム面２０７によってカム部材１１の初期位置からの応答性を向上することができ、第２カム面２０９によってプレッシャリング９の軸方向移動を的確に制御することができる。 Furthermore, since the first cam surface 207 is set to have an inclination angle larger than that of the second cam surface 209, the first cam surface 207 can improve the responsiveness from the initial position of the cam member 11, and second The cam surface 209 can accurately control the axial movement of the pressure ring 9.
　なお、上述のカム機構では、カムリングとプレッシャリングとに内径壁部と外径壁部とが設けられているが、これに限らず、カムリングとプレッシャリングとのうち少なくとも一方に、内径壁部と外径壁部とを設ければよい。 In the above cam mechanism, the cam ring and the pressure ring are provided with the inner diameter wall portion and the outer diameter wall portion. However, the present invention is not limited thereto, and at least one of the cam ring and the pressure ring includes an inner diameter wall portion and What is necessary is just to provide an outer-diameter wall part.
　また、カム部材におけるテーパローラでは、内端周壁と外端周壁とが曲面状に形成されているが、これに限らず、内端周壁と外端周壁とのうちいずれか一方を曲面状に形成してもよい。 Further, in the taper roller in the cam member, the inner end peripheral wall and the outer end peripheral wall are formed in a curved shape. However, the present invention is not limited thereto, and one of the inner end peripheral wall and the outer end peripheral wall is formed in a curved shape. May be.
　また、外径壁部１５をカムリング５とプレッシャリング９とのうちいずれか一方にのみ設ければ、カム部材１１の外端面２０３と外径壁部１５の内周面２０５との接触点を１点とすることが可能だが、カム部材１１の外端面２０３は上述したように曲率半径Ｒ１の球面状に形成せずとも、カム部材１１の外端面２０３の軸心部近傍に凸部（突起などを含む）を設けて、外径壁部と当接・摺動するようにしてもよい。この場合にも、凸部の先端や先端の縁部分が外径壁部に対して片当たりをしないように、曲面取り又は平面取りなどを形成してもよい。 Further, if the outer diameter wall portion 15 is provided only on one of the cam ring 5 and the pressure ring 9, the contact point between the outer end surface 203 of the cam member 11 and the inner peripheral surface 205 of the outer diameter wall portion 15 is set to 1. Although the outer end surface 203 of the cam member 11 is not formed into a spherical shape with a radius of curvature R1 as described above, a convex portion (protrusion or the like) is formed in the vicinity of the axial center of the outer end surface 203 of the cam member 11. May be provided so as to abut and slide on the outer diameter wall portion. Also in this case, a curved surface or a flat surface may be formed so that the front end of the convex portion or the edge portion of the front end does not come into contact with the outer diameter wall portion.
　さらに、上述のクラッチ装置では、アクチュエータが電磁式アクチュエータとなっているが、これに限らず、例えば、モータ・ギヤ・カム機構など、カムリングとプレッシャリングとの間に相対回転を生じさせるアクチュエータであれば、どのようなアクチュエータであってもよい。 Further, in the clutch device described above, the actuator is an electromagnetic actuator. However, the present invention is not limited to this, for example, an actuator that causes relative rotation between the cam ring and the pressure ring, such as a motor, gear, and cam mechanism. Any actuator may be used.
　幾つかの実施形態を説明したが、上記開示内容に基づいて実施形態の修正ないし変形をすることが可能である。 Although several embodiments have been described, the embodiments can be modified or modified based on the above disclosure.

Claims (10)

  1. 　軸の周りに円環をなし、軸方向に向いた前記円環の一の面上に周方向に並び、それぞれ前記軸に直交する周面に対して周方向に傾斜した複数のカム面を備えた、カムリングと、
    　前記カムリングの前記面に軸方向に隣接し、前記カムリングの前記面に対向して前記カムリングの前記複数のカム面に対称的な複数のカム面を備え、前記軸の周りに前記カムリングに対して相対的に回転可能な、プレッシャリングと、
    　前記カムリングと前記プレッシャリングとの間に介在した複数のテーパローラであって、それぞれ径方向に内方に向かって先細になる円錐面を備えて前記カム面上を転動可能なテーパローラと、
    　を備えたカム機構。     A plurality of cam surfaces are formed around the shaft, arranged in a circumferential direction on one surface of the annular ring facing in the axial direction, and inclined in the circumferential direction with respect to the circumferential surface orthogonal to the axis. With cam ring,
    A plurality of cam surfaces that are axially adjacent to the surface of the cam ring and that are opposed to the surface of the cam ring and that are symmetrical with respect to the plurality of cam surfaces of the cam ring, Relatively rotatable pressure ring,
    A plurality of tapered rollers interposed between the cam ring and the pressure ring, each having a conical surface tapering inward in the radial direction and capable of rolling on the cam surface;
    Cam mechanism with
  2. 　請求項１のカム機構であって、
    　前記複数のテーパローラを径方向に内方に規制する内径壁部、または、前記複数のテーパローラを径方向に外方に規制する外径壁部、
    　をさらに備えたカム機構。     The cam mechanism according to claim 1,
    An inner diameter wall portion for restricting the plurality of taper rollers radially inward, or an outer diameter wall portion for restricting the plurality of taper rollers outward in a radial direction;
    A cam mechanism further comprising:
  3. 　請求項２のカム機構であって、
    　前記内径壁部及び前記外径壁部の一方または両方は、周方向に連続している、カム機構。     The cam mechanism according to claim 2,
    One or both of the inner diameter wall portion and the outer diameter wall portion is a cam mechanism that is continuous in the circumferential direction.
  4. 　請求項３のカム機構であって、
    　前記複数のテーパローラは、それぞれ、径方向に外方向に凸である凸部を含む外端面を備え、以って前記外径壁部の内周面に点接触して摺動する、カム機構。     The cam mechanism according to claim 3,
    Each of the plurality of tapered rollers includes an outer end surface including a convex portion that is convex outward in the radial direction, and thus slides in point contact with the inner peripheral surface of the outer diameter wall portion.
  5. 　請求項４のカム機構であって、
    　前記凸部は、球面であって、
    　前記凸部の曲率半径は、前記外径壁部の前記内周面の半径より小さい、カム機構。     The cam mechanism according to claim 4,
    The convex portion is a spherical surface,
    A cam mechanism in which a radius of curvature of the convex portion is smaller than a radius of the inner peripheral surface of the outer diameter wall portion.
  6. 　請求項４のカム機構であって、
    　前記外径壁部は、前記カムリングと前記プレッシャリングのいずれかと一体である、カム機構。     The cam mechanism according to claim 4,
    The outer diameter wall portion is a cam mechanism integrated with either the cam ring or the pressure ring.
  7. 　請求項１のカム機構であって、
    　前記円錐面の母線が前記軸において収斂するよう、前記テーパローラは寸法づけられており、
    　前記カムリングの各カム面および前記プレッシャリングの各カム面は、前記円錐面に線接触するべく径方向に外方に傾斜した螺旋面である、カム機構。     The cam mechanism according to claim 1,
    The tapered roller is dimensioned so that the generatrix of the conical surface converges at the axis;
    Each cam surface of the cam ring and each cam surface of the pressure ring are helical surfaces inclined outward in the radial direction so as to be in line contact with the conical surface.
  8. 　請求項１乃至７のいずれか１項のカム機構であって、
    　前記カムリングおよび前記プレッシャリングの各カム面は、前記テーパローラを初期位置に落ち着かせる谷部と、前記テーパローラを前記初期位置から第１の位置へ軸方向に移動せしめるべく前記谷部から連続して傾斜した第１カム面と、前記第１カム面から連続しており、前記テーパローラを前記第１の位置から第２の位置へ軸方向に移動せしめるべく前記周面に対して前記第１カム面より小さな角度で傾斜した第２カム面と、を含む、カム機構。     The cam mechanism according to any one of claims 1 to 7,
    Each cam surface of the cam ring and the pressure ring is inclined continuously from the trough so as to cause the tapered roller to settle to an initial position and to move the taper roller from the initial position to the first position in the axial direction. The first cam surface is continuous with the first cam surface, and the taper roller is moved from the first position to the second position in the axial direction from the first cam surface with respect to the circumferential surface. And a second cam surface inclined at a small angle.
  9. 　請求項１乃至７のいずれか１項に記載のカム機構であって、
    　前記テーパローラは、曲面よりなる内端面または外端面を備える、カム機構。     The cam mechanism according to any one of claims 1 to 7,
    The taper roller is a cam mechanism having an inner end surface or an outer end surface made of a curved surface.
  10. 　それぞれ前記軸の周りに独立して回転可能な第１の回転部材および第２の回転部材と、
    　請求項１のカム機構と、
    　前記カムリングに駆動的に結合してこれを回転せしめるアクチュエータと、
    　前記プレッシャリングに隣接し、前記プレッシャリングから押圧力を受けて脱連結可能に連結して前記第１の回転部材と前記第２の回転部材との間でトルクを伝達するクラッチと、
    　を備えたクラッチ装置。     A first rotating member and a second rotating member, each independently rotatable about the axis;
    A cam mechanism according to claim 1;
    An actuator for drivingly coupling to and rotating the cam ring;
    A clutch that is adjacent to the pressure ring, receives a pressing force from the pressure ring and is detachably connected to transmit torque between the first rotating member and the second rotating member;
    A clutch device comprising:
PCT/JP2016/080462 2016-03-04 2016-10-14 Cam mechanism and clutch device using said cam mechanism WO2017149829A1 (en)

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EP16892665.7A EP3425239A4 (en) 2016-03-04 2016-10-14 Cam mechanism and clutch device using said cam mechanism
CN201680062027.0A CN108138922B (en) 2016-03-04 2016-10-14 Cam mechanism and clutch device using the same
US15/950,237 US10704612B2 (en) 2016-03-04 2018-04-11 Cam mechanism and clutch device with the same

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JP2016-041787 2016-03-04
JP2016041787 2016-03-04
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JP2016158619A JP6735180B2 (en) 2016-03-04 2016-08-12 A cam mechanism and a clutch device using this cam mechanism.

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WO2019171459A1 (en) * 2018-03-06 2019-09-12 Ｇｋｎ ドライブライン ジャパン株式会社 Low-hysteresis cam mechanism provided with tapered rollers
WO2019244268A1 (en) * 2018-06-20 2019-12-26 Ｇｋｎ ドライブライン ジャパン株式会社 Low hysteresis cam mechanism equipped with tapered roller
WO2020008507A1 (en) * 2018-07-02 2020-01-09 Ｇｋｎ ドライブライン ジャパン株式会社 Friction clutch device
CN110821981A (en) * 2019-11-28 2020-02-21 河北艾斯特车桥有限公司 Full-disc brake for heavy vehicle
CN112334675A (en) * 2018-07-06 2021-02-05 株式会社电装 Clutch device
US11773919B2 (en) 2019-03-26 2023-10-03 Gkn Automotive Limited Disconnectable coupling with lubrication control

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019171459A1 (en) * 2018-03-06 2019-09-12 Ｇｋｎ ドライブライン ジャパン株式会社 Low-hysteresis cam mechanism provided with tapered rollers
CN112334679B (en) * 2018-06-20 2023-09-15 吉凯恩汽车有限公司 Low hysteresis cam mechanism with tapered roller
WO2019244268A1 (en) * 2018-06-20 2019-12-26 Ｇｋｎ ドライブライン ジャパン株式会社 Low hysteresis cam mechanism equipped with tapered roller
CN112334679A (en) * 2018-06-20 2021-02-05 吉凯恩汽车有限公司 Low-hysteresis cam mechanism with tapered roller
JPWO2019244268A1 (en) * 2018-06-20 2021-05-13 ジーケーエヌ オートモーティブ リミテッド Low hysteresis cam mechanism with tapered rollers
WO2020008507A1 (en) * 2018-07-02 2020-01-09 Ｇｋｎ ドライブライン ジャパン株式会社 Friction clutch device
CN112352114A (en) * 2018-07-02 2021-02-09 吉凯恩汽车有限公司 Friction clutch device
JPWO2020008507A1 (en) * 2018-07-02 2021-05-13 ジーケーエヌ オートモーティブ リミテッド Friction clutch device
CN112352114B (en) * 2018-07-02 2022-02-15 吉凯恩汽车有限公司 Friction clutch device
JP7065189B2 (en) 2018-07-02 2022-05-11 ジーケーエヌ オートモーティブ リミテッド Friction clutch device
CN112334675A (en) * 2018-07-06 2021-02-05 株式会社电装 Clutch device
US11773919B2 (en) 2019-03-26 2023-10-03 Gkn Automotive Limited Disconnectable coupling with lubrication control
CN110821981A (en) * 2019-11-28 2020-02-21 河北艾斯特车桥有限公司 Full-disc brake for heavy vehicle
CN110821981B (en) * 2019-11-28 2021-10-01 河北埃克斯福动力科技有限公司 Full-disc brake for heavy vehicle

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