WO2019216280A1 - 逆入力遮断クラッチ及びアクチュエータ - Google Patents

逆入力遮断クラッチ及びアクチュエータ Download PDF

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Publication number
WO2019216280A1
WO2019216280A1 PCT/JP2019/018027 JP2019018027W WO2019216280A1 WO 2019216280 A1 WO2019216280 A1 WO 2019216280A1 JP 2019018027 W JP2019018027 W JP 2019018027W WO 2019216280 A1 WO2019216280 A1 WO 2019216280A1
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WO
WIPO (PCT)
Prior art keywords
input
engagement
output
pressed
engaging
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2019/018027
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
優也 大黒
寛孝 岸田
大輝 橋口
豊田　俊郎
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
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
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to JP2020518282A priority Critical patent/JP7380552B2/ja
Priority to CN201980031049.4A priority patent/CN112189100B/zh
Priority to EP19799519.4A priority patent/EP3792516B1/en
Priority to US17/053,902 priority patent/US11428278B2/en
Publication of WO2019216280A1 publication Critical patent/WO2019216280A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • 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
    • F16D45/00—Freewheels or freewheel clutches combined with automatic clutches
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D43/18—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with friction 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D51/00—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like
    • F16D51/16—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis
    • F16D51/18—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis with two brake-shoes
    • F16D51/20—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis with two brake-shoes extending in opposite directions from their pivots
    • F16D51/22—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as brake-shoes pivoted on a fixed or nearly-fixed axis with two brake-shoes extending in opposite directions from their pivots mechanically actuated
    • 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
    • F16D51/00—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like
    • F16D51/46—Self-tightening brakes with pivoted brake shoes, i.e. the braked member increases the braking action
    • F16D51/48—Self-tightening brakes with pivoted brake shoes, i.e. the braked member increases the braking action with two linked or directly-interacting brake shoes
    • F16D51/50—Self-tightening brakes with pivoted brake shoes, i.e. the braked member increases the braking action with two linked or directly-interacting brake shoes mechanically actuated
    • 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
    • F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
    • F16D67/02—Clutch-brake combinations
    • 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
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2247—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers
    • F16H25/2252—Planetary rollers between nut and screw
    • 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
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2247—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers
    • F16H25/2266—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers arranged substantially in parallel to the screw shaft axis
    • 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
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
    • F16H25/2454—Brakes; Rotational locks
    • 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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/084—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate coupling members wedging by pivoting or rocking
    • 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
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/2062—Arrangements for driving the actuator
    • F16H2025/2081—Parallel arrangement of drive motor to screw axis

Definitions

  • the rotational torque input to the input member is transmitted to the output member, whereas the rotational torque reversely input to the output member is completely cut off and not transmitted to the input member or only a part thereof is input.
  • the present invention relates to a reverse input cutoff clutch that transmits to a member and blocks the remaining portion.
  • the present invention also relates to an actuator including the reverse input cutoff clutch.
  • the reverse input cutoff clutch includes an input member connected to an input side mechanism such as a drive source and an output member connected to an output side mechanism such as a speed reduction mechanism, and rotational torque input to the input member is an output member. Rotational torque that is reversely input to the output member is completely cut off and not transmitted to the input member, or only part of it is transmitted to the input member and the rest is cut off. Yes.
  • the reverse input cutoff clutch is roughly classified into a lock type and a free type according to the difference in the mechanism for blocking the rotational torque that is reversely input to the output member.
  • the lock-type reverse input cutoff clutch includes a mechanism that prevents or suppresses rotation of the output member when rotational torque is reversely input to the output member.
  • the free-type reverse input cutoff clutch includes a mechanism that causes the output member to idle when a rotational torque is input to the output member. Which one of the lock type reverse input cutoff clutch and the free type reverse input cutoff clutch is used is appropriately determined depending on the use of the device incorporating the reverse input cutoff clutch.
  • JP-A-2004-084918, JP-A-2007-232095, and the like describe a lock-type reverse input cutoff clutch.
  • the reverse input shut-off clutch described in these publications is a wedge-shaped rolling element disposed in a wedge-shaped space between the inner member and the outer member when rotational torque is reversely input to the output member.
  • a mechanism for preventing rotation of the output member is provided by moving the space to the narrower side in the radial direction and stretching the space between the inner member and the outer member.
  • actuators using an electric motor as a power source are used in industrial winches, hoists, cranes, various positioning devices, and the like.
  • transmission of rotational torque from the input member to the output member is efficiently performed, so that the electric motor can be reduced in size and the output member can be reduced. Since transmission of reversely inputted rotational torque can be interrupted by the reverse input cutoff clutch, there is an advantage that the power consumption of the electric motor can be reduced.
  • An actuator having a reverse input cutoff clutch is disclosed in, for example, Japanese Patent Application Laid-Open No. 2004-144124.
  • An object of the present invention is to provide a reverse input cutoff clutch that can easily release the state in which the rotation of the output member is prevented or suppressed, and an actuator including such a reverse input cutoff clutch.
  • the 1st aspect of this invention is related with the actuator provided with the reverse input interruption
  • the actuator according to the first aspect includes a rotation / linear motion conversion mechanism and a reverse input cutoff clutch having a lock mechanism.
  • the rotation / linear motion conversion mechanism includes a screw shaft having a male engagement portion on an outer peripheral surface, and a nut having a female engagement portion on an inner peripheral surface, and the male engagement portion and the female side
  • the engaging portion is engaged directly or via a plurality of intermediate engaging members
  • the lock mechanism includes a pressed member, an input engagement portion, an output engagement portion, and an engagement element.
  • the pressed member has a cylindrical pressed surface on the inner peripheral surface
  • the input engagement portion has a rotation center axis that is coaxial with the center axis of the pressed surface, and is arranged on the radially inner side of the pressed surface
  • the output engagement portion has a rotation center axis that is coaxial with the center axis of the pressed surface, and is disposed radially inward of the pressed surface and radially inward of the input engagement portion.
  • the engaging element is disposed on the radially inner side of the pressed surface, and when a rotational torque is input to the input engaging portion, the pressed member is based on the engagement with the input engaging portion.
  • the rotational torque input to the input engagement portion is transmitted to the output engagement portion based on the engagement with the output engagement portion.
  • rotational torque When rotational torque is reversely input, it moves in a direction approaching the pressed surface based on the engagement with the output engaging portion, and is reversely input to the output engaging portion by being pressed against the pressed surface.
  • the transmitted rotational torque is not transmitted to the input engaging portion, or a part of the rotational torque reversely input to the output engaging portion is transmitted to the input engaging portion based on the engagement with the input engaging portion.
  • the lock mechanism is disposed at a portion where the output engagement portion is connected to the nut so as to be able to transmit torque and is axially disengaged from the female engagement portion around the screw shaft. ,as well as,
  • the inner diameter dimension of the output engagement part is smaller than the outer diameter dimension of the axial range in which the female side engagement part exists in the nut. It is characterized by that.
  • the engagement element is constituted by a pair of engagement elements, and the output engagement portion is disposed so as to be sandwiched from both sides in the radial direction by the pair of engagement elements.
  • the engagement element has a pressing surface pressed against the pressed surface, and the pressing surface has a smaller radius of curvature than the pressed surface and is provided in a pair spaced apart in the circumferential direction. It is preferable to be configured by an arcuate convex surface.
  • the actuator according to the first aspect may further include a speed reduction mechanism for increasing the rotational torque input to the input engagement portion.
  • the output portion of the speed reduction mechanism is connected to the input engagement portion so that torque can be transmitted, and the speed reduction mechanism and the lock mechanism are adjacent to each other in the axial direction around the screw shaft. It is preferable that they are arranged.
  • the actuator according to the first aspect may further include an electric motor serving as a generation source of the rotational torque input to the input engagement portion.
  • the actuator of the first aspect is The rotation / linear motion conversion mechanism is a ball screw mechanism;
  • the male engagement portion is a male spiral groove;
  • the female side engaging portion is a female side spiral groove,
  • Each of the intermediate engaging members is a ball, By arranging each of the balls between the male side spiral groove and the female side spiral groove, the male side spiral groove and the female side spiral groove are engaged via each of the balls. Yes, A configuration can be employed.
  • the actuator of the first aspect is
  • the rotation / linear motion conversion mechanism is a planetary roller screw mechanism
  • the male engagement portion is a male screw portion
  • the female engagement portion is a female screw portion
  • Each of the intermediate engagement members is a planetary roller having a roller screw portion on the outer peripheral surface, The male screw portion and the female screw portion are engaged with each other through the planetary rollers by engaging the roller screw portions of the planetary roller with both the male screw portion and the female screw portion.
  • a configuration can be employed.
  • a second aspect of the present invention relates to a reverse input cutoff clutch.
  • the reverse input cutoff clutch of the second aspect is A pressed member having a cylindrical concave pressed surface having a central axis;
  • An input member having an input engagement portion disposed radially inward of the pressed surface, and having a rotation center axis coaxial with the central axis of the pressed surface;
  • An output member having an output engaging portion disposed radially inward of the pressed surface and radially inward of the input engaging portion, and having a rotation center axis coaxial with the pressed surface;
  • a first portion disposed at a position sandwiched between the input engagement portion and the output engagement portion with respect to the radial direction on the radially inner side of the pressed surface, and the input engagement portion with respect to the radial direction
  • An engagement element having a pair of second portions disposed at positions deviated on both sides in the circumferential direction from a position sandwiched between the output engagement part; Is provided.
  • the engagement element is separated from the pressed surface when the input engagement portion engages with the first portion when rotational torque is input to the input member.
  • the rotational torque input to the input member is transmitted to the output member, and the rotational torque is reversely input to the output member.
  • the output engaging portion engages with the first portion, the output engaging portion moves in a direction approaching the pressed surface, and the pair of second portions is pressed against the pressed surface, The rotational torque reversely input to the output member is not transmitted to the input member, or a part of the rotational torque reversely input to the output member is transmitted to the input member and the remainder is blocked.
  • the pair of contact portions where the pair of second portions and the pressed surface are in contact with each other With respect to the direction of the bisector of the tangent line of the pressed surface at each of the contact portions of the pair of contact portions, it is positioned closer to the central axis of the pressed surface than a predetermined portion
  • the predetermined portion is a portion of the first portion that is engaged with the input engagement portion when rotational torque is input to the input member.
  • the predetermined contact portion is a portion of the first portion that is engaged with the output engaging portion when a rotational torque is reversely input to the output member. It is preferable to be positioned closer to the central axis.
  • the engagement element may have a structure that does not have a portion arranged on the radially outer side of the input engagement portion on the radially inner side of the pressed surface.
  • the pressed surface has a diametrical direction
  • the input engaging portion is constituted by a pair of input engaging portions disposed at two positions opposite to the diametrical direction of the pressed surface.
  • the coupling is constituted by a pair of engagement elements
  • the output engagement part is disposed so as to be sandwiched from both sides in the radial direction by the pair of input engagement parts and the pair of engagement elements. .
  • Each of the pair of second portions has a pressing surface pressed against the pressed surface, and the pressing surface is configured by an arcuate convex surface having a smaller radius of curvature than the pressed surface. It is preferable.
  • the intermediate member is disposed at least in any part between the two parts.
  • the intermediate member may be formed of a gap adjusting material having the pressed surface, which is disposed in a portion between the pair of second portions and the pressed member and is held by the pressed member.
  • the intermediate member may be formed of a gap adjusting member that is disposed in a portion between the pair of second portions and the pressed member and is held by the pair of second portions of the engagement element.
  • the gap adjusting material also includes a friction material adhered or bonded to the engagement element.
  • the intermediate member is disposed in at least one of a portion between the input engagement portion and the first portion of the engagement member and a portion between the output engagement portion and the first portion of the engagement member. Further, it can be made of a gap adjusting material.
  • the gap adjusting member can be held by any of the input engagement portion, the output engagement portion, and the engagement element.
  • the reverse input cutoff clutch of the second aspect further includes a guide member for guiding the displacement of the engagement element, and the gap adjusting member can be held by the guide member.
  • the gap adjusting material may be a coiled spring.
  • the gap adjusting material can be made of at least one material selected from metal, ceramics, synthetic resin, and rubber.
  • the gap adjusting material can be composed of a coating material.
  • the intermediate member is disposed in a portion between the pair of second portions and the pressed member, and is made of a lubricant that lubricates a contact portion between the pressed surface and the pair of second portions. it can.
  • the lubricant is preferably made of traction oil or traction grease.
  • At least one of the pressed surface and the pressed surface has a fine uneven shape.
  • the reverse input cutoff clutch of the third aspect and the fourth aspect is A pressed member having a pressed surface; An input member having a rotation center axis and at least one input engagement portion; An output member having a rotation center axis coaxial with the rotation center axis of the input member, and an output engagement portion; At least one pressing surface facing the pressed surface, an engagement-side input engagement portion that engages with the input engagement portion, and an engagement-side output engagement portion that engages with the output engagement portion Having at least one engagement element.
  • the engaging element separates the pressing surface from the pressed surface based on the engagement between the input engaging part and the engaging element side input engaging part. And the engagement side output engagement portion is engaged with the output engagement portion to transmit the rotational torque input to the input member to the output member and to the output member.
  • the pressing surface is displaced so as to press the pressing surface against the pressed surface based on the engagement between the output engaging portion and the engagement member side output engaging portion. Is frictionally engaged with the pressed surface.
  • a portion between the engaging element and the pressed member, a portion between the input engaging portion and the engaging side input engaging portion, and An intermediate member is disposed in at least one of the portions between the output engagement portion and the engagement element side output engagement portion.
  • a gap adjusting material As the intermediate member, a gap adjusting material, a lubricant that lubricates a contact portion between the pressed surface and the pressing surface, in particular, traction oil or traction grease, a convex portion provided on a radially outer portion of the engagement element And an elastic body made of rollers or balls.
  • the intermediate member is disposed at a portion between the pressing surface and the pressed member, and is held by the pressed member. It can consist of clearance gap adjustment material which has.
  • the intermediate member may be formed of a gap adjusting material that is disposed in a portion between the engagement element and the pressed surface and is held by the engagement element and having the pressing surface.
  • the intermediate member is disposed in at least one of a portion between the input engagement portion and the engagement element side input engagement portion and a portion between the output engagement portion and the engagement element side output engagement portion. Further, it can be made of a gap adjusting material. In this case, the gap adjusting member can be held by any one of the input engagement portion, the output engagement portion, and the engagement element.
  • the reverse input cut-off clutch of the third aspect can further include a guide member that guides the displacement of the engagement element, and in this case, the gap adjusting material can be held by the guide member.
  • the gap adjusting member is disposed in at least one of a portion between the input engagement portion and the engagement element side input engagement portion and a portion between the output engagement portion and the engagement element side output engagement portion. It can consist of a coiled spring.
  • the gap adjusting material can be made of at least one material selected from metal, ceramics, synthetic resin, and rubber.
  • the gap adjusting material can be made of a coating material.
  • the intermediate member is disposed at a portion between the engagement element and the pressed member, and is made of a lubricant that lubricates a contact portion between the pressed surface and the pressed surface. be able to.
  • the lubricant is preferably made of traction oil or traction grease.
  • the pressed member has an inner circumferential surface having a circular shape when viewed from the axial direction, the pressed surface is provided on the inner circumferential surface, and the engagement element.
  • the pressed member Preferably has a radially outer portion facing the inner peripheral surface, and the pressing surface is provided on the radially outer portion.
  • the engaging element has a convex portion that protrudes radially outward as compared to a portion adjacent in the circumferential direction at least in one circumferential direction of the radially outer portion, and has a radially outer surface, and
  • the pressing surface may be provided on the radially outer surface.
  • the pressing surface is formed by a convex surface having an arc shape when viewed from the axial direction, and the radius of curvature of the pressing surface is preferably smaller than the radius of curvature of the pressed surface.
  • the pressing surface may have a crowning shape.
  • the pressed member has an inner circumferential surface having a circular shape when viewed from the axial direction, and the pressed surface is provided on the inner circumferential surface
  • the engagement element includes an engagement element main body having the engagement element side input engagement part and the engagement element side output engagement part, and at least one pressing body, and the pressing surface includes the at least one pressing surface.
  • the engagement body has a radially outer portion facing the inner peripheral surface, and a holding recess provided at at least one location in the circumferential direction of the radially outer portion and opening radially outward. The pressing body is held in the holding recess, A configuration can also be adopted.
  • the engagement body may be provided with a groove extending over the entire length in the axial direction in the radially outer portion, and the holding recess may be constituted by the groove.
  • the pressed member includes a guide groove extending over the entire circumference on the inner peripheral surface, and the pressed surface is configured by an inner surface of the guide groove, and is radially outward from the holding recess of the pressing body.
  • a protruding portion may be disposed inside the guide groove.
  • the pressing body can be made of rollers or balls.
  • a part of the roller or ball that is more than half of the roller or ball is disposed inside the holding recess, and an opening on the radially outer side of the holding recess
  • the width is preferably smaller than the diameter of the roller or ball.
  • the pressed member may have a ridge over the entire circumference in a part of the inner peripheral surface in the axial direction, and the pressed surface may be constituted by the radially inner side surface of the ridge.
  • the pressed surface may be a convex surface having a circular arc cross-sectional shape.
  • At least one of the pressed surface and the pressing surface can have a fine uneven shape.
  • the reverse input cutoff clutch of the fourth aspect is
  • the pressed member has an inner circumferential surface having a circular shape when viewed from the axial direction, and the pressed surface is provided on the inner circumferential surface
  • the engaging element has a radially outer portion facing the inner peripheral surface, and the pressing surface is provided on the radially outer portion
  • the intermediate member is provided in at least one place in the circumferential direction of the radially outer portion, protrudes radially outward as compared to a portion adjacent in the circumferential direction, and includes a convex portion having a radially outer surface; and ,
  • the pressing surface is provided on the radially outer surface
  • the pressing surface may be a convex surface having an arc shape when viewed from the axial direction.
  • the radius of curvature of the pressing surface is preferably smaller than the radius of curvature of the pressed surface.
  • the pressing surface has a crowning shape.
  • the reverse input cutoff clutch of the fourth aspect is
  • the pressed member has an inner circumferential surface having a circular shape when viewed from the axial direction, and the pressed surface is provided on the inner circumferential surface
  • the engagement body has a radially outer portion facing the inner peripheral surface, and a holding recess provided at at least one location in the circumferential direction of the radially outer portion and opening radially outward.
  • the intermediate member is constituted by at least one pressing body held in the holding recess, and The pressing surface is provided on the at least one pressing body. A configuration can also be adopted.
  • the engagement element may include a groove extending in the radial outer portion over the entire length in the axial direction, and the holding recess may be constituted by the groove.
  • the pressed member includes a guide groove extending over the entire circumference on the inner peripheral surface, and the pressed surface is configured by an inner surface of the guide groove, and the diameter of the pressed body from the holding recess is increased. A portion protruding outward in the direction may be disposed inside the guide groove.
  • the pressing body can be made of rollers or balls.
  • a part of the roller or ball that is more than half of the roller or ball is disposed inside the holding recess, and an opening on the radially outer side of the holding recess
  • the width is preferably smaller than the diameter of the roller or ball.
  • the pressed member has a ridge over the entire circumference in a part of the axial direction of the inner peripheral surface, and the pressed surface can be constituted by a radially inner surface of the ridge.
  • the pressed surface is constituted by a convex surface having a circular cross section.
  • the reverse input cutoff clutch of the second aspect, the third aspect, and the fourth aspect can also be applied to the actuator. That is, the actuator of the present invention is an actuator provided with a rotation / linear motion conversion mechanism and a reverse input cutoff clutch, and the reverse input cutoff clutch has the second mode, the third mode, and the fourth mode. An actuator constituted by any one of the reverse input cutoff clutches is also included.
  • the rotation / linear motion conversion mechanism includes a screw shaft having a male engagement portion on an outer peripheral surface, and a nut having a female engagement portion on an inner peripheral surface, and the male engagement portion
  • the female engaging portion is engaged directly or via a plurality of intermediate engaging members.
  • the output engagement portion is connected to the nut so as to be able to transmit torque, and is disposed at a portion that is axially disengaged from the female engagement portion around the screw shaft.
  • the inner diameter dimension of the output engagement portion is smaller than the outer diameter dimension in the axial range of the nut where the female engagement portion exists.
  • the actuator may further include a speed reduction mechanism for increasing the rotational torque input to the input engagement portion.
  • the output part of the speed reduction mechanism is connected to the input engagement part so that torque can be transmitted, and the speed reduction mechanism and the reverse input cutoff clutch are adjacent to each other in the axial direction around the screw shaft. Can be arranged.
  • the actuator may further include an electric motor serving as a generation source of rotational torque input to the input engagement portion.
  • the actuator is The rotation / linear motion conversion mechanism is a ball screw mechanism;
  • the male engagement portion is a male spiral groove;
  • the female side engaging portion is a female side spiral groove,
  • Each of the intermediate engaging members is a ball, By arranging each of the balls between the male side spiral groove and the female side spiral groove, the male side spiral groove and the female side spiral groove are engaged via each of the balls. Yes, The configuration can be taken.
  • the actuator is The rotation / linear motion conversion mechanism is a planetary roller screw mechanism
  • the male engagement portion is a male screw portion
  • the female engagement portion is a female screw portion
  • Each of the intermediate engagement members is a planetary roller having a roller screw portion on the outer peripheral surface, The male screw portion and the female screw portion are engaged with each other through the planetary rollers by engaging the roller screw portions of the planetary roller with both the male screw portion and the female screw portion.
  • the configuration can be taken.
  • the state in which the rotation of the output engagement portion that is the output member is prevented or suppressed can be easily released.
  • FIG. 1 is a cross-sectional view of an actuator according to a first example of an embodiment of the first aspect of the present invention.
  • FIG. 2 is an enlarged view of the central portion of FIG. 1 except for the housing.
  • FIG. 3 is a perspective view showing the actuator according to the first example of the embodiment of the first aspect with the housing omitted.
  • FIG. 4 is an exploded perspective view of the ball screw mechanism and the reverse input cutoff clutch that constitute the actuator according to the first example of the embodiment of the first aspect.
  • FIG. 5 is a cross-sectional view taken along the line AA in FIG.
  • FIG. 6 is a diagram illustrating a state in which rotational torque is input to the input member with respect to the reverse input cutoff clutch according to the first example of the embodiment of the first aspect.
  • FIG. 7 is a diagram illustrating a state in which the rotational torque is reversely input to the output member with respect to the reverse input cutoff clutch according to the first example of the embodiment of the first aspect.
  • FIG. 8 is a diagram illustrating the relationship between the force that acts on the engagement member from the output member when the rotational torque is reversely input to the output member with respect to the reverse input cutoff clutch according to the first example of the embodiment of the first aspect.
  • FIG. FIG. 9 is a diagram for explaining a condition in which the output member is locked when the rotational torque is reversely input to the output member with respect to the reverse input cutoff clutch according to the first example of the embodiment of the first aspect. .
  • FIG. 10 is a perspective view showing an input member constituting the reverse input cutoff clutch according to the first example of the embodiment of the first aspect.
  • FIG. 11 is a perspective view showing an output member constituting the reverse input cutoff clutch according to the first example of the embodiment of the first aspect.
  • FIG. 12 is a partial cross-sectional view of the actuator relating to the second example of the embodiment of the first aspect.
  • FIG. 13 is a partial cross-sectional view of the actuator according to the third example of the embodiment of the first aspect.
  • FIG. 14 is a partial cross-sectional view regarding a fourth example of the embodiment of the first aspect.
  • FIG. 15 is a diagram corresponding to FIG. 5 with respect to a fifth example of the embodiment of the first aspect.
  • FIG. 16 is a perspective view of the reverse input cutoff clutch according to the first example of the embodiment of the second mode.
  • FIG. 17 is an exploded perspective view of the ball screw mechanism and the reverse input cutoff clutch that constitute the actuator according to the first example of the embodiment of the second mode.
  • FIG. 18 is a diagram corresponding to FIG. 5 regarding the first example of the embodiment of the second mode.
  • FIG. 19 is a diagram illustrating a state in which rotational torque is input to the input member with respect to the reverse input cutoff clutch according to the first example of the embodiment of the second mode.
  • FIG. 20 is a diagram illustrating a state in which the rotational torque is reversely input to the output member with respect to the reverse input cutoff clutch according to the first example of the embodiment of the second aspect.
  • FIG. 21 shows the reverse input shut-off clutch related to the first example of the embodiment of the second mode in order to explain the condition that the output member is locked or semi-locked when the rotational torque is reversely input to the output member.
  • FIG. FIG. 22 is a diagram corresponding to FIG. 21 relating to the structure of the reference example for explaining the operation and effect of the first example of the embodiment of the second mode.
  • FIG. 23 is a cross-sectional view of the reverse input cutoff clutch according to the second example of the embodiment of the second mode.
  • FIG. 24 is a perspective view of the reverse input cutoff clutch according to the second example of the embodiment of the second mode.
  • 25 is a cross-sectional view taken along the line BB in FIG. FIG.
  • FIG. 26 is a perspective view showing an input member constituting the reverse input cutoff clutch according to the second example of the embodiment of the second mode.
  • FIG. 27 is a perspective view showing an output member constituting the reverse input cutoff clutch according to the second example of the embodiment of the second mode.
  • FIG. 28 is a perspective view showing a pair of engaging elements constituting a reverse input cutoff clutch according to the second example of the embodiment of the second mode.
  • FIG. 29 is a perspective view showing the pressed member constituting the reverse input cutoff clutch according to the second example of the embodiment of the second mode.
  • FIG. 30 is a cross-sectional view of the reverse input cutoff clutch of the first example of the embodiment of the third aspect. 31 is a cross-sectional view taken along the line ⁇ - ⁇ in FIG. FIG.
  • FIG. 32 is a perspective view showing a part of the input member constituting the reverse input cutoff clutch of the first example of the embodiment of the third mode.
  • FIG. 33 is a perspective view showing a part of an output member constituting the reverse input cutoff clutch of the first example of the embodiment of the third mode.
  • FIG. 34 is a partial cross-sectional view showing an example of a method for fixing the gap adjusting material to the pressed member with respect to the reverse input cutoff clutch of the first example of the embodiment of the third mode.
  • FIG. 35 is a diagram illustrating a state in which rotational torque is input to the input member with respect to the reverse input cutoff clutch of the first example of the embodiment of the third aspect.
  • FIG. 36 is a diagram illustrating a state in which the rotational torque is reversely input to the output member with respect to the reverse input cutoff clutch of the first example of the embodiment of the third aspect.
  • FIG. 37 is a diagram showing the relationship between the force that acts on the engagement member from the output member when the rotational torque is reversely input to the output member, with respect to the reverse input cutoff clutch of the first example of the third embodiment. It is an enlarged view of the center part of 35.
  • FIG. 38 is a diagram illustrating a reverse input cutoff clutch according to a second example of the embodiment of the third aspect.
  • FIG. 39 is a diagram illustrating a reverse input cutoff clutch according to a third example of the embodiment of the third aspect.
  • FIG. 40 is a diagram illustrating a reverse input cutoff clutch according to a fourth example of the embodiment of the third aspect.
  • FIG. 41 is a diagram illustrating a reverse input cutoff clutch according to a fifth example of the embodiment of the third aspect.
  • FIG. 42 is a diagram illustrating a reverse input cutoff clutch of a sixth example of the embodiment of the third aspect.
  • FIG. 43 is a diagram illustrating a reverse input cutoff clutch according to a seventh example of the embodiment of the third aspect.
  • FIG. 44 is a diagram illustrating a reverse input cutoff clutch of an eighth example of the embodiment of the third aspect.
  • FIG. 45 is a diagram illustrating a reverse input cutoff clutch according to a ninth example of the embodiment of the third aspect.
  • FIG. 41 is a diagram illustrating a reverse input cutoff clutch according to a fifth example of the embodiment of the third aspect.
  • FIG. 42 is a diagram illustrating a reverse input cutoff clutch of a sixth example of the embodiment of the third aspect.
  • FIG. 46 is a perspective view of a gap adjusting member (plate spring) incorporated in the reverse input cutoff clutch of the ninth example of the embodiment of the third aspect.
  • FIG. 47 is a diagram illustrating a reverse input cutoff clutch according to a tenth example of the embodiment of the third aspect.
  • FIG. 48 is a cross-sectional view showing the variable compression ratio device of the eleventh example of the embodiment of the third aspect.
  • FIG. 49 is an exploded perspective view showing the main part of the variable compression ratio device of the eleventh example of the embodiment of the third aspect.
  • FIG. 50 is a diagram illustrating a reverse input cutoff clutch according to a first example of the embodiment of the fourth aspect. 51 is a cross-sectional view taken along line X1-X1 of FIG. FIG.
  • FIG. 52 is a perspective view of the reverse input cutoff clutch of the first example of the embodiment of the fourth aspect.
  • FIG. 53 is a perspective view showing a part of the input member taken out from the reverse input cutoff clutch of the first example of the embodiment of the fourth mode.
  • FIG. 54 is a perspective view showing a part of the output member taken out from the reverse input cutoff clutch of the first example of the embodiment of the fourth mode.
  • FIG. 55 is a diagram illustrating a state in which rotational torque is input to the input member with respect to the reverse input cutoff clutch according to the first example of the embodiment of the fourth aspect.
  • FIG. 56 is a diagram illustrating a state in which the rotational torque is reversely input to the output member with respect to the reverse input cutoff clutch of the first example of the embodiment of the fourth aspect.
  • FIG. 57 is a partially enlarged view of FIG. 56 showing the relationship of the force that acts on the engagement element from the output member when the rotational torque is reversely input to the output member.
  • FIG. 58 is a diagram for explaining a condition in which the output member is locked or semi-locked when the rotational torque is reversely input to the output member.
  • FIG. 59 is a diagram illustrating a reverse input cutoff clutch according to a second example of the embodiment of the fourth aspect.
  • FIG. 60 is a perspective view showing only one engaging member extracted from the reverse input cutoff clutch of the second example of the embodiment of the fourth aspect.
  • FIG. 61 is a diagram illustrating a relationship of forces acting when a rotational torque is reversely input to the output member in the reverse input cutoff clutch of the second example of the embodiment of the fourth aspect.
  • FIG. 62 is a diagram illustrating a reverse input cutoff clutch of a third example of the embodiment of the fourth aspect.
  • 63 is a partially enlarged view of FIG.
  • FIG. 64 is a diagram showing a reverse input cutoff clutch of a fourth example of the embodiment of the fourth aspect.
  • FIG. 65 is a diagram showing a reverse input cutoff clutch according to a fifth example of the embodiment of the fourth aspect.
  • 66 is a cross-sectional view taken along line X2-X2 of FIG. FIG.
  • FIG. 67 is a diagram illustrating a reverse input cutoff clutch according to a sixth example of the embodiment of the fourth aspect.
  • FIG. 68 is a diagram corresponding to FIG. 66 regarding the seventh example of the embodiment of the fourth aspect.
  • FIG. 69 is a cross-sectional view showing the holding recesses and rollers (or balls) of the engaging elements and their peripheral parts that constitute the reverse input cutoff clutch of the eighth example of the embodiment of the fourth aspect.
  • FIG. 70 is a diagram corresponding to FIG. 69 regarding the ninth example of the embodiment of the fourth aspect.
  • FIG. 71 is a diagram corresponding to FIG. 51 relating to a tenth example of embodiment of the fourth aspect.
  • FIG. 72 is a perspective view showing a part of the pressed member constituting the reverse input cutoff clutch of the tenth example of the fourth embodiment.
  • the actuator 1 of the first example of the embodiment of the first aspect includes a ball screw mechanism 6 that is a rotation / linear motion conversion mechanism, and a reverse input cutoff clutch 5 having a lock mechanism 52.
  • the rotary straight path mechanism (ball screw mechanism 6) has a screw shaft (ball) having a male side engaging portion (male side spiral groove 10) on the outer peripheral surface.
  • the intermediate engagement members are engaged.
  • the lock mechanism 52 includes the pressed member 16, the input engagement portion 20, the output engagement portion 26, and the engagement element 17.
  • the pressed member 16 has a cylindrical pressed surface 28 on the inner peripheral surface.
  • the input engagement portion 20 has a rotation center axis O that is coaxial with the center axis O of the pressed surface 28, and is disposed on the radially inner side of the pressed surface 28.
  • the output engaging portion 26 has a rotation center axis O that is coaxial with the central axis O of the pressed surface 28, and is disposed radially inward of the pressed surface 28 and inward of the input engaging portion 20. ing.
  • the engaging element 17 is disposed on the radially inner side of the pressed surface 28, and when a rotational torque is input to the input engaging portion 20, the pressed surface is based on the engagement with the input engaging portion 20. 28, the rotational torque input to the input engagement portion 20 is transmitted to the output engagement portion 26 based on the engagement with the output engagement portion 26, whereas the output engagement portion 26 When the rotational torque is reversely input, it moves in the direction approaching the pressed surface 28 based on the engagement with the output engaging portion 26, and is reversely input to the output engaging portion 26 by being pressed against the pressed surface 28. The transmitted rotational torque is not transmitted to the input engagement portion 20 or a part of the rotational torque reversely input to the output engagement portion 26 is transmitted to the input engagement portion 20 based on the engagement with the input engagement portion 20. The remainder is cut off.
  • the lock mechanism 52 is connected to the output engaging portion 26 so as to be able to transmit torque to the nut 8, and the axial range in which the female-side spiral groove 11 exists around the screw shaft 7 (male-side engaging portion). It is arrange
  • the inner diameter dimension of the output engagement portion 26 is smaller than the outer diameter dimension of the axial range where the female spiral groove 11 is present in the nut 8.
  • the actuator 1 of this example includes a housing 2, an electric motor 3 that is a drive source supported by the housing 2, a speed reduction mechanism 4 that is housed inside the housing 2, a reverse input cutoff clutch 5, and a ball screw. And a mechanism 6.
  • the actuator 1 decelerates (increases) the rotational motion of the electric motor 3 by the speed reduction mechanism 4 and then transmits the rotational motion to the ball screw mechanism 6 via the reverse input shut-off clutch 5, and the rotational motion is linearly moved by the ball screw mechanism 6. It is configured to output after converting to.
  • the reverse input shut-off clutch 5 is a lock-type reverse input shut-off clutch.
  • the rotational torque input to the input portion on the electric motor 3 side is transmitted to the output portion on the ball screw mechanism 6 side.
  • the rotational torque that is reversely input to the output unit has a reverse input blocking function that does not transmit to the input unit or transmits only part of the torque and blocks the remaining part.
  • the axial direction of the actuator 1 is the axial direction of the ball screw mechanism 6, that is, the left-right direction in FIGS. Moreover, one side in the axial direction is the right side in FIGS. 1 and 2, and the other side in the axial direction is the left side in FIGS. 1 and 2.
  • the axial direction of the reverse input cutoff clutch 5 coincides with the axial direction of the ball screw mechanism 6. Further, the radial direction and the circumferential direction mean the radial direction and the circumferential direction of the reverse input cutoff clutch 5.
  • the ball screw mechanism 6 includes a screw shaft (ball screw shaft) 7, a nut (ball nut) 8, and a plurality of balls 9.
  • the screw shaft 7 has a male spiral groove 10 formed in a spiral shape on the outer peripheral surface.
  • the nut 8 is arranged around the screw shaft 7 coaxially with the screw shaft 7 and has a female-side spiral groove 11 formed in a spiral shape on the inner peripheral surface.
  • the plurality of balls 9 are spirally disposed between the male spiral groove 10 and the female spiral groove 11. Further, in the portion of the nut 8 that overlaps the radially outer side of the female side spiral groove 11, when the screw shaft 7 and the nut 8 are relatively rotated, the male side spiral groove 10 and the female side spiral groove 11 are A circulation path 12 (see FIG.
  • the circulation path 12 may be formed directly on the nut 8 or may be formed using another member such as a circulation tube.
  • the ball screw mechanism 6 can convert the relative rotational motion between the screw shaft 7 and the nut 8 into the relative linear motion (the axial relative motion) between the screw shaft 7 and the nut 8. It is configured.
  • the screw shaft 7 is disposed on the inner side of the housing 2, and both end portions in the axial direction protrude outside the housing 2. Further, the screw shaft 7 is slidably supported with respect to the housing 2 by a support body 53 such as a sliding bearing held inside each of both axial sides of the housing 2. It should be noted that the outer peripheral surface of the portion of the screw shaft 7 that is slidably supported by the support body 53 can be constituted by a simple cylindrical surface on which the male spiral groove 10 is not formed. The installation of the support 53 can be omitted.
  • the nut 8 is supported inside the housing 2 by the first bearing 13 so as to be able to rotate only.
  • the reverse input shut-off clutch 5 includes an input member 14 that is an input portion, an output member 15 that is an output portion, a pressed member 16, and a pair of engaging members 17, and inside the housing 2.
  • the screw shaft 7 and the nut 8 are arranged coaxially with the screw shaft 7 and the nut 8.
  • the reverse input cutoff clutch 5 has a lock mechanism 52 in a part thereof, and the lock mechanism 52 is arranged at a portion disengaged from the nut 8 on one side in the axial direction.
  • the axial direction, the radial direction, and the circumferential direction of the input member 14, the output member 15, and the pressed member 16 are the axial direction, the radial direction, and the reverse input cutoff clutch 5 unless otherwise specified. Match with the circumferential direction.
  • the input member 14 includes an input cylinder portion 18 that is an input connection portion, an input ring portion 19, and a pair of input engagement portions 20.
  • the input cylinder part 18 has a cylindrical shape.
  • the input annular portion 19 has an annular shape, is disposed coaxially with the input cylinder portion 18, and has a radially intermediate portion coupled to one end portion in the axial direction of the input cylinder portion 18.
  • Each of the pair of input engagement portions 20 has a substantially elliptical column shape, and extends from two positions on the radially inner side of the input ring portion 19 toward the one side in the axial direction.
  • the pair of input engagement portions 20 are arranged in a portion of the input ring portion 19 that is radially outward from the rotation center axis O so as to be separated from each other in the radial direction.
  • the radially outer surface of the input engagement portion 20 has a partial cylindrical surface shape centering on the rotation center axis O, and the radially inner side surface of the input engagement portion 20 is a pair of input engagement portions 20. It has a flat surface shape orthogonal to the diametrical direction which is the separation direction.
  • the output member 15 is configured in a cylindrical shape, and is disposed coaxially with the input member 14 on the radially inner side of the input member 14.
  • the output member 15 includes an output cylinder portion 21 that constitutes a half portion on the other side in the axial direction, and an offset cylinder portion 22 that constitutes a half portion on the one side in the axial direction.
  • the output cylinder portion 21 has a large-diameter inner peripheral surface portion 23 that is a cylindrical surface on the inner peripheral surface.
  • the offset cylindrical portion 22 has a small-diameter inner peripheral surface portion 24 that is a cylindrical surface having a smaller diameter than the large-diameter inner peripheral surface portion 23 on the inner peripheral surface.
  • the offset cylindrical portion 22 has a small-diameter cylindrical portion 25 having a smaller outer diameter than the other axial side portion on one axial side.
  • the small diameter cylindrical portion 25 has an output engaging portion 26 at an axially intermediate portion.
  • the output engaging portion 26 has flat cam surfaces 27 that are parallel to each other at two positions on the radially opposite side of the outer peripheral surface.
  • the other axial side of the offset cylindrical portion 22 is disposed on the radially inner side of the input cylindrical portion 18, and the output engaging portion 26 is disposed between the pair of input engaging portions 20.
  • a second bearing 33 is installed between the inner peripheral surface of the input cylinder portion 18 and the outer peripheral surface of the other side portion in the axial direction of the offset cylinder portion 22.
  • the second bearing 33 ensures the coaxiality between the input member 14 and the output member 15 and allows the relative rotation between the input member 14 and the output member 15.
  • a rolling bearing such as a cylindrical sliding bearing or a radial needle bearing can be used.
  • the 2nd bearing 33 is abbreviate
  • the pressed member 16 has an L-shaped cross-sectional shape and is configured in an annular shape as a whole.
  • the pressed member 16 is disposed coaxially with the input member 14 and the output member 15 and around the pair of input engagement portions 20 and output engagement portions 26.
  • the pressed member 16 has a pressed surface 28 that is a cylindrical concave surface on the inner peripheral surface that surrounds the pair of the input engaging portion 20 and the output engaging portion 26.
  • Each of the engaging members 17 constituting the pair of engaging members 17 has a substantially arcuate plate shape (bow plate shape) and is arranged on the radially inner side of the pressed member 16.
  • the pair of engagement elements 17 are arranged in a radial direction that is a direction in which the output engagement portion 26 is separated from the pair of cam surfaces 27 between the pressed surface 28 and the outer peripheral surface of the output engagement portion 26. It arrange
  • Each engagement element 17 is composed of the same parts made in the same shape and size.
  • Each engaging element 17 has a pressing surface 29 that is a cylindrical convex surface on the radially outer surface (outer peripheral surface) facing the pressed surface 28, and is provided on the cam surface 27 of the output engaging portion 26.
  • An output engagement surface 30 that can be engaged with the cam surface 27 is provided at the center portion in the circumferential direction of the opposed radially inner side surface.
  • the output engagement surface 30 has a flat surface shape orthogonal to the separation direction (vertical direction in FIG. 5) of the pair of engagement elements 17.
  • a portion between the pressed surface 28 and the pressing surface 29 or a portion between the cam surface 27 and the output engaging surface 30 in a state where the pair of engaging elements 17 is disposed on the radially inner side of the pressed member 16, a portion between the pressed surface 28 and the pressing surface 29 or a portion between the cam surface 27 and the output engaging surface 30.
  • the inner diameter dimension of the pressed member 16 and the radial dimension of the engagement element 17 are regulated so that there is a gap in the inner diameter.
  • Each of the engagement elements 17 has an input engagement hole 31 in a circumferential central portion of the radial intermediate portion.
  • the input engagement hole 31 is a substantially rectangular axial through-hole extending in the width direction of each engagement element 17 and has a size that allows the input engagement portion 20 to be inserted loosely.
  • the surface located radially inward is an input engagement surface 32 that can be engaged with the input engagement portion 20.
  • the input engagement surface 32 has a flat surface shape parallel to the output engagement surface 30.
  • each engagement element 17 is a direction (left and right in FIG. 5) orthogonal to the separation direction or perspective direction (vertical direction in FIG. 5) of the pair of engagement elements 17 in a virtual plane orthogonal to the axial direction. Direction).
  • the pressing surface 29 of each engaging element 17 has a surface property having a larger friction coefficient than the other portions, and the radius of curvature thereof is the same as or slightly smaller than the radius of curvature of the pressed surface 28. .
  • the pressing surface 29 can be configured directly by the surface of each engaging element 17 or can be configured by an intermediate member such as a friction material fixed to each engaging element 17 by sticking or bonding.
  • an intermediate member such as a gap adjusting material may be disposed between the pressed surface 28 and the pressing surface 29, and the pressed surface 28 may be provided on the inner surface of the gap adjusting material.
  • each engaging element 17 moves in a radial direction relative to the pressed surface 28 in a portion between the pressed surface 28 and the pressed surface 29.
  • the backlash can be suppressed to be small even when there is a variation in the clearance provided for the purpose, that is, the backlash in the rotational direction between the input member 14 and the output member 15.
  • a lubricant such as traction oil, traction grease, or other lubricating oil for lubricating the contact portion between the pressed surface 28 and the pressing surface 29 is disposed between the pressed surface 28 and the pressing surface 29. You can also As a result, the friction coefficient ⁇ between the pressed surface 28 and the pressing surface 29 is increased to improve the brake torque, or the finishing process and the heat treatment applied to the pressing surface 29 of the engagement element can be locally limited. An effect is obtained.
  • Both side surfaces in the circumferential direction of each engagement element 17 are flat surfaces orthogonal to the perspective direction. As shown in FIG. 6, the output engagement surfaces 30 of the respective engagement elements 17 face each other in a state where they are in surface contact with the cam surface 27, that is, in a state where the pair of engagement elements 17 are closest to each other in the perspective direction.
  • Each circumferential direction of the pair of engagement elements 17 is such that the circumferential side surfaces of the pair of engagement elements 17 do not contact each other, or even if they contact, the surface pressure of the contact portion is substantially zero. Dimensions are regulated.
  • the reverse input shut-off clutch 5 includes a pair of input engagement portions 20, an output engagement portion 26, a pressed member 16, and a pair of engagement elements 17 that are arranged so as to overlap each other in the radial direction.
  • a configured lock mechanism 52 is provided.
  • the lock mechanism 52 is disposed at a portion disengaged from the nut 8 on one side in the axial direction.
  • the output member 15 is externally fitted and fixed so that the output cylinder portion 21 can transmit torque to the nut 8.
  • the large-diameter inner peripheral surface portion 23 of the output cylinder portion 21 is externally fitted to the outer peripheral surface of the nut 8 on the one axial end portion and the intermediate portion without radial backlash.
  • the end surface on the other side in the axial direction of the output cylinder portion 21 is in contact with the flange portion 34 having an outward flange shape provided at the other end in the axial direction of the nut 8, so Positioning is achieved.
  • the output cylinder portion 21 is fixed to the nut 8 using a plurality of bolts 35.
  • axial through holes 36 are provided at a plurality of circumferential locations (six locations in the illustrated example) of the flange portion 34, and the through holes 36 are provided at the other axial end portion of the output cylinder portion 21.
  • a screw hole 37 is provided at a position matching each of the screw holes 37.
  • a bolt 35 inserted through each of the through holes 36 is screwed into each of the screw holes 37.
  • methods such as press fitting, spline fitting, key engagement, welding, brazing, etc. may be employed as a method for externally fixing the output cylinder portion 21 so that torque can be transmitted to the nut 8. it can.
  • the small diameter inner peripheral surface portion 24 of the offset cylindrical portion 22 is in close proximity to the outer peripheral surface of the screw shaft 7 in a state where the output cylindrical portion 21 is fitted and fixed to the nut 8.
  • the output member 15 is supported inside the housing 2 together with the nut 8 by the first bearing 13 so that only the rotation is possible.
  • a deep groove ball bearing which is a kind of rolling bearing capable of supporting a radial load and an axial load, is used as the first bearing 13.
  • the inner ring 38 of the first bearing 13 is externally fitted (press-fit externally fitted) to the output cylinder portion 21 with an interference fit. Further, the inner ring 38 has its axial end on the other side in contact with an outward flange-shaped flange 40 provided at the other end in the axial direction of the output cylinder 21, so that the axial direction relative to the output cylinder 21 Is positioned.
  • the outer ring 39 of the first bearing 13 is fitted into the housing 2 with an interference fit (press fit fit).
  • the outer ring 39 includes a stepped surface 41 provided in a portion adjacent to the other axial side of the outer ring 39 on the inner peripheral surface of the housing 2, and an axial direction one side of the outer ring 39 on the inner peripheral surface of the housing 2. Positioning in the axial direction with respect to the housing 2 is achieved by being clamped in the axial direction between the retaining rings 42 locked to adjacent portions.
  • the first bearing is provided to support the nut and the output member so as to be rotatable only with respect to the housing.
  • the type and the installation location are not limited, but the bearing is configured to support a radial load and an axial load in both directions. It is preferred that As the first bearing, a multipoint contact ball bearing, a double-row angular ball bearing, or the like is used.
  • the first bearing is installed so as to directly support the nut with respect to the housing or to support another member (a member other than the output member) that rotates together with the nut with respect to the housing.
  • wheel of a 1st bearing can also be integrally formed with respect to the member adjacent to a 1st bearing.
  • the output gear 50 constituting the speed reduction mechanism 4 is externally fitted and fixed to the input cylinder portion 18 of the input member 14 so that torque can be transmitted.
  • the output gear 50 is externally fitted and fixed to the input cylinder portion 18 so as to be able to transmit torque by a method such as press fitting, spline fitting, key engagement, welding, or brazing.
  • the output gear 50 is positioned in the axial direction with respect to the input member 14 by bringing the axially one side surface of the radially inner end portion into contact with the input ring portion 19.
  • the annular first spacer 43 is sandwiched in the axial direction between the input member 14 and the output gear 50 and the inner ring 38 of the first bearing 13, whereby the input member 14 and the output gear with respect to the output member 15. 50 axial positionings are achieved.
  • the input cylinder portion 18 can be integrally formed with the output gear 50.
  • An annular second spacer 44 is locked together with a retaining ring 45 on the outer peripheral surface of one end portion in the axial direction of the small diameter cylindrical portion 25 constituting the output member 15. Whether the second spacer 44 is opposed to the one end face in the axial direction of the pair of input engagement portions 20 and the one side face in the axial direction of the pair of engagement elements 17 in the axial direction with a minute gap therebetween. Or lightly touching. Thereby, the axial positioning of the input member 14 and the pair of engagement elements 17 with respect to the output member 15 is achieved, and the relative rotation between the input member 14, the output member 15 and the pair of engagement elements 17, and A radial displacement of the pair of engagement elements 17 is allowed.
  • the pressed member 16 is fixed to the housing 2 using a plurality of bolts 46. Specifically, axial through holes 47 are provided at a plurality of circumferential locations (four locations in the illustrated example) of the pressed member 16, and the housing 2 is aligned with each of the through holes 47. A screw hole 48 is provided. Bolts 46 inserted through the respective through holes 47 are screwed into the respective screw holes 48. As a method for fixing the pressed member 16 to the housing 2, methods such as press fitting, spline fitting, key engagement, welding, brazing, and the like can be employed. Further, the pressed member can be formed integrally with the housing.
  • the speed reduction mechanism 4 is a parallel shaft gear mechanism composed of a plurality of gears in which the respective rotation center axes are arranged in parallel to each other.
  • the speed reduction mechanism 4 includes an input gear 49 that is an input unit and an output gear 50 that is an output unit.
  • the input gear 49 torques the tip of the drive shaft 51 of the electric motor 3 arranged in parallel with the screw shaft 7 by a method such as press fitting, spline fitting, key engagement, welding, brazing, or the like. It is fixed so that it can be transmitted.
  • the drive shaft 51 of the electric motor 3 can be driven to rotate in both directions.
  • the tooth portions provided on the outer peripheral portions of the input gear 49 and the output gear 50 mesh with each other.
  • the second bearing 33 also plays a role of supporting a gear reaction force applied from the input gear 49 to the output gear 50.
  • a reduction mechanism in addition to a parallel shaft gear mechanism, a planetary gear mechanism, a bevel gear mechanism, a wave gear mechanism, a cycloid reduction mechanism, a belt drive type reduction mechanism, a chain drive type reduction mechanism, a wedge roller type traction drive reduction mechanism, these Various reduction mechanisms such as combinations can be employed.
  • the rotational torque of the drive shaft 51 of the electric motor 3 is decelerated (increased) by the speed reduction mechanism 4 and then input to the input member 14 of the reverse input cutoff clutch 5.
  • the reverse input cutoff clutch 5 transmits all of the rotational torque input to the input member 14 to the output member 15 via a pair of engagement elements 17.
  • the rotational torque transmitted to the output member 15 is transmitted to the nut 8 and the nut 8 rotates.
  • the rotation of the nut 8 is converted into a linear motion of the screw shaft 7 via a plurality of balls 9. Therefore, for example, if the screw shaft 7 is coupled to the driven portions of various mechanical devices, the driven portion can be driven by the linear motion of the screw shaft 7.
  • Each engaging element 17 is radially inward so as to approach each other in the perspective direction based on the engagement between the input engaging surface 32 and the input engaging portion 20 (the engaging element 17 positioned on the upper side in FIG. Next, the engaging member 17 located on the lower side of FIG. 6 is moved upward).
  • the output engagement surfaces 30 of the pair of engagement elements 17 sandwich the output engagement portions 26 of the output member 15 from both sides in the radial direction and engage with the pair of cam surfaces 27 of the output member 15 without rattling (surfaces). Contact.
  • the rotational torque input to the input member 14 is transmitted to the output member 15 via the pair of engaging members 17 and output from the output member 15.
  • the transmission of the rotational torque from the input member 14 to the output member 15 is performed regardless of the rotation direction of the input member 14.
  • the engaging member 17 located on the lower side is moved downward).
  • the pressing surfaces 29 of the pair of engagement elements 17 are pressed against the pressed surface 28.
  • the pressing surface 29 and the pressed surface 28 are in contact with each other over the entire range or a part (for example, the central portion) of the pressing surface 29 in the circumferential direction.
  • the rotational torque reversely input to the output member 15 is prevented from being transmitted to the input member 14, or only a part thereof is transmitted and the remaining portion is blocked.
  • Such a blocking function is realized regardless of the rotation direction of the output member 15.
  • the pair of engaging members 17 is configured so that the pressing surface 29 does not slide (relatively rotate) with respect to the pressed surface 28. Is stretched between the output engaging portion 26 and the pressed member 16 to lock the output member 15. On the other hand, in order to transmit only a part of the rotational torque reversely input to the output member 15 to the input member 14 and to block the remaining portion, the pressing surface 29 slides against the pressed surface 28.
  • the pair of engaging members 17 are stretched between the output engaging portion 26 and the pressed member 16 so as to move, and the output member 15 is half-locked.
  • a reaction force is applied to the driven parts of various mechanical devices coupled to the screw shaft 7, whereby an axial load is reversely input to the screw shaft 7, and the output member 15 of the reverse input cutoff clutch 5.
  • the reverse input cutoff clutch 5 prevents the output member 15 from rotating (locks the output member 15), and the rotational torque reversely input to the output member 15 is transmitted to the input member 14.
  • the rotation of the output member 15 is suppressed (the output member 15 is half-locked), and only a part of the rotational torque reversely input to the output member 15 is transmitted to the input member 14 and the remainder is cut off.
  • the electric motor 3 Even if the electric motor 3 is not energized, when the output member 15 is locked, the position of the driven portion can be held, and when the output member 15 is half-locked, It is possible to prevent the position from changing suddenly. In short, the electric motor 3 generates a force for holding the position of the driven part or preventing the position of the driven part from changing suddenly against the reaction force applied to the driven part. There is no need. Therefore, the power consumption of the electric motor 3 can be reduced accordingly.
  • the amount of rotation torque that is reversely input to the output member 15 is appropriately set according to the application of the actuator 1. Is set.
  • the housing 2 is fixed to the vehicle body with the axial direction of the screw shaft 7 aligned with the vehicle width direction. And the base end part of the tie rod connected with a steered wheel is couple
  • a reaction force that is, a restoring force is applied to the steered wheels from the road surface so as to return the steered angle to a straight traveling state.
  • a reaction force that is, a restoring force is applied to the steered wheels from the road surface so as to return the steered angle to a straight traveling state.
  • the first advantage is less likely to be obtained as the amount of rotation torque that is reversely input to the output member 15 is increased
  • the second advantage is that the amount of rotation torque that is reversely input to the output member 15 is reduced.
  • the amount of torque cutoff is preferably 80% or less, and more preferably 20% or less.
  • the cutoff amount of the rotational torque reversely input to the output member 15 is preferably 20% or more, and more preferably 80% or more. From the viewpoint of obtaining both the first advantage and the second advantage, it is preferable that the shutoff amount of the rotational torque reversely input to the output member 15 is within a range of 20% to 80%.
  • the reverse input cutoff clutch 5 of this example the function of transmitting the rotational torque input to the input member 14 to the output member 15 to the engagement member 17 and the function of blocking the rotational torque reversely input to the output member 15 (output) And the function of locking or semi-locking the member 15). For this reason, the number of parts of the reverse input cutoff clutch 5 can be suppressed, and the operation can be stabilized as compared with the case where both functions are provided in different members.
  • the timing for releasing the interruption of rotational torque reversely input to the output member, and the rotational torque from the input member to the output member There is a possibility that the timing of starting the transmission of the signal will be shifted.
  • the rotational torque is reversely input to the output member between the release of the rotational torque interruption and the start of transmission of the rotational torque to the output member, the output member is locked again.
  • the engaging member 17 has both a function of transmitting the rotational torque input to the input member 14 to the output member 15 and a function of blocking the rotational torque reversely input to the output member 15. Therefore, it is possible to prevent such inconvenience from occurring.
  • the lock mechanism 52 of the reverse input cut-off clutch 5 is disposed at a portion disengaged from the nut 8 on one side in the axial direction. Further, the inner diameter dimension of the output engagement portion 26 constituting the lock mechanism 52 (the inner diameter dimension of the small-diameter inner peripheral surface portion 24) is larger than the outer diameter dimension in the axial range of the nut 8 where the female-side spiral groove 11 exists. It is getting smaller. For this reason, the diameter dimension of the lock mechanism 52 can be made small.
  • the circulation path 12 is provided on the radially outer side of the female spiral groove 11 in the axial range of the nut 8 where the female spiral groove 11 exists, the axial direction The outer diameter of the range tends to be large. Further, the output engaging portion 26 constituting the lock mechanism 52 needs to ensure a predetermined thickness or more in the radial direction in order to ensure its strength. For this reason, if the output engagement part which comprises a locking mechanism is arrange
  • the output engagement portion 26 constituting the lock mechanism 52 is disposed in a portion that is axially disengaged from the nut 8, and the inner diameter dimension of the output engagement portion 26 is the nut 8.
  • the outer diameter dimension of the output engagement part 26 is set. Can be small. Therefore, the diameter dimension of the lock mechanism 52 can be reduced correspondingly, and the actuator 1 can be reduced in the radial direction.
  • the speed reduction mechanism 4 and the lock mechanism 52 are arranged adjacent to each other in the axial direction without the first bearing 13 being sandwiched between the speed reduction mechanism 4 and the lock mechanism 52 in the axial direction. For this reason, the structure which spans the input member 14 between the output gear 50 and the lock mechanism 52 which comprise the deceleration mechanism 4 can be simplified.
  • the speed reduction mechanism 4 is provided between the electric motor 3 and the reverse input cutoff clutch 5. For this reason, at least a part of the rotational torque reversely input from the ball screw mechanism 6 side is interrupted by the reverse input interrupting clutch 5 before being transmitted to the speed reduction mechanism 4. Therefore, the speed reduction mechanism 4 is protected from the rotational torque that is reversely input. Specifically, fretting in the engagement between the input gear 49 and the output gear 50 is prevented or suppressed.
  • a ball screw mechanism is adopted as the rotation straight path conversion mechanism.
  • a sliding screw mechanism can be alternatively applied as the rotation linear motion conversion mechanism. That is, the male side engaging portion existing on the outer peripheral surface of the screw shaft is a male screw portion, the female side engaging portion existing on the inner peripheral surface of the nut is a female screw portion, and the male screw portion and the female screw portion are screwed together. Thus, the male screw portion and the female screw portion can be directly engaged.
  • an actuator drive source an engine, a water wheel, a windmill, etc. can be applied in addition to an electric motor.
  • the drive source of an actuator can also be a human power.
  • the rotation / linear motion converting mechanism such as the ball screw mechanism and the planetary roller screw mechanism has a function of decelerating the output of the drive source, the decelerating mechanism can be omitted.
  • the materials of the input member, the output member, the pressed member, and the engagement member constituting the reverse input cutoff clutch are not particularly limited.
  • these materials in addition to metals such as iron alloys, copper alloys, and aluminum alloys, synthetic resins mixed with reinforcing fibers as necessary can be applied.
  • the input member, the output member, the pressed member, and the engagement element can be made of the same material, or can be made of different materials.
  • the hardness, elasticity, and the like can be made different between the input member, the output member, and the pressed member and the engaging element.
  • the traction oil is applied to the portion where the input member, the output member, the pressed member, and the engagement element are in contact with each other as long as the output member is locked or semi-locked.
  • a lubricant such as traction grease or normal lubricating oil can be arranged.
  • at least one member among the input member, the output member, the pressed member, and the engagement member can be made of oil-impregnated metal.
  • the actuator of the present invention can be applied not only to automobiles but also to steer-by-wire steering devices mounted on various transportation equipment such as construction machines and ships.
  • the reverse input cutoff clutch according to the first aspect can be applied to various mechanical devices such as a variable compression ratio device, an electric door device, a power window device, a steering device, and a jack in addition to the actuator.
  • the number of engagement elements constituting the reverse input cutoff clutch of the first aspect is not limited to two, and may be one or three or more.
  • the output member 15a constituting the reverse input cutoff clutch 5a is integrally formed with the nut 8a constituting the ball screw mechanism 6a.
  • the number of parts can be reduced by integrally forming the output member 15a with the nut 8a.
  • the nut 8a and the output member 15a can be combined into one component, or a plurality of bolts 35 (see FIGS. 1 and 2) used as a coupling member can be omitted.
  • a plurality of bolts 35 used as a coupling member can be omitted.
  • the inertial force of the rotating body including the nut 8a can be reduced, and the power consumption of the electric motor 3 (see FIG. 1) serving as a drive source can be reduced.
  • Other configurations and operations are the same as those of the first example of the first embodiment.
  • the positional relationship in the axial direction between the speed reduction mechanism 4a and the lock mechanism 52a constituting the reverse input cutoff clutch 5b is reversed from that in the first example of the first embodiment. That is, in this example, the lock mechanism 52a is disposed between the first bearing 13 and the speed reduction mechanism 4a in the axial direction.
  • An output engaging portion 26 is provided on the other axial side of the offset cylindrical portion 22a constituting the output member 15b, and the pressed members 16 and 1 constituting the lock mechanism 52a are provided on the radially outer side of the output engaging portion 26.
  • a pair of engagement elements 17 and a pair of input engagement portions 20 and 20 are disposed.
  • the speed reduction mechanism 4a, the input cylinder part 18, and the 2nd bearing 33 are arrange
  • Other configurations and operations are the same as those of the first example of the first embodiment.
  • This example differs from the first example of the first embodiment in that a planetary roller screw mechanism 54 is employed as the rotation / linear motion conversion mechanism instead of the ball screw mechanism 6 (see FIG. 1). ing.
  • the planetary roller screw mechanism 54 includes a screw shaft 55, a nut 56, a plurality of planetary rollers 57, two ring gears 58, and two cages 59.
  • the screw shaft 55 has a male screw portion 60 on the outer peripheral surface.
  • the nut 56 has a female thread portion 61 on the inner circumferential surface in the axial direction intermediate portion, and is arranged around the screw shaft 55 coaxially with the screw shaft 55.
  • Each of the planetary rollers 57 has a roller screw portion 62 on the outer circumferential surface in the axial direction and a gear portion 63 on each outer circumferential surface near the both ends in the axial direction.
  • the plurality of planetary rollers 57 are arranged in parallel with the screw shaft 55, and are arranged at equal intervals in the circumferential direction between the outer peripheral surface of the screw shaft 55 and the inner peripheral surface of the nut 56.
  • the roller screw portion 62 of each planetary roller 57 meshes with both the male screw portion 60 and the female screw portion 61.
  • Each of the two ring gears 58 has an annular shape and has a gear portion 64 on the inner peripheral surface.
  • the ring gears 58 are fitted and fixed one by one to both ends of the nut 56 in the axial direction.
  • Each gear portion 64 of the ring gear 58 meshes with a gear portion 63 that is present near each axial end of each planetary roller 57.
  • Each of the two cages 59 has an annular shape and has axial support holes 65 at a plurality of locations that are equally spaced in the circumferential direction.
  • One cage 59 is disposed between the outer peripheral surface of the screw shaft 55 and the inner peripheral surfaces of both end portions in the axial direction of the nut 56.
  • Both end portions in the axial direction of the planetary roller 57 are rotatably inserted into the respective support holes 65 of the cage 59.
  • Each of the cages 59 is freely rotatable with respect to both the screw shaft 55 and the nut 56 and is prevented from being displaced in the axial direction with respect to the nut 56.
  • Such a planetary roller screw mechanism 54 is based on the fact that the planetary roller 57 rotates and revolves between the screw shaft 55 and the nut 56 when the screw shaft 55 and the nut 56 rotate relative to each other. 55 and the nut 56 perform relative linear motion.
  • the screw shaft 55 is disposed inside the housing 2 (see FIG. 1), and the nut 8 ( In place of (see FIG. 1), the output cylinder portion 21 of the output member 15 is externally fixed to the nut 56.
  • the lock mechanism 52 (see FIG. 1) of the reverse input shut-off clutch 5 is disposed at a portion disengaged from the nut 56 on one side in the axial direction, and constitutes the lock mechanism 52.
  • a configuration is adopted in which the inner diameter dimension of the output engagement portion 26 (see FIG. 1) is smaller than the outer diameter dimension in the axial range of the nut 56 where the female thread portion 61 exists. For this reason, the diameter dimension of the lock mechanism 52 can be made small.
  • Other configurations and operations are the same as those of the first example of the first embodiment.
  • the structure of the lock mechanism 52b constituting the reverse input cutoff clutch 5c is different from the first example of the first embodiment.
  • the perspective outer side surfaces of the pair of engaging members 17a are two portions separated in the circumferential direction, which are pressing surfaces 29a pressed against the pressed surface 28.
  • a circumferential intermediate portion sandwiched between the pressing surfaces 29a is a portion that is not pressed against the pressed surface 28, that is, a portion that is retracted radially inward from the pressing surface 29a.
  • Each of the pressing surfaces 29 a is a cylindrical convex surface having a radius of curvature smaller than the radius of curvature of the pressed surface 28.
  • the reverse input cutoff clutch 5d of the first example of the embodiment of the second aspect is: A pressed member 16 having a cylindrical concave pressed surface 28 having a central axis; An input member 14 that includes the input engagement portion 20 disposed on the radially inner side of the pressed surface 28 and has a rotation center axis that is coaxial with the central axis of the pressed surface 28; An output member 15 having an output engagement portion 26 disposed radially inside the input engagement portion 20 on the radially inner side of the pressed surface 28 and having a rotation center axis coaxial with the pressed surface 28; A first portion 68 disposed at a position sandwiched between the input engagement portion 20 and the output engagement portion 26 with respect to the radial direction inside the pressed surface 28 in the radial direction, and the input engagement portion 20 with respect to the radial direction. And an engagement member 17b having a pair of second portions 69 disposed at positions deviated on both sides in the circumferential direction from a position sandwiched between the first engagement portion
  • the engagement member 17b is engaged with the first portion 68 when the rotational torque is input to the input member 14.
  • the first portion 68 is engaged with the output engagement portion 26 so that the rotational torque input to the input member 14 is transmitted to the output member 15, and the first portion 68 is engaged with the output engagement portion 26.
  • the output engaging portion 26 engages with the first portion 68, so that the output member 15 moves in a direction approaching the pressed surface 28 and a pair of second portions 69.
  • the pair of second portions 69 and the pressed surface 28 are in contact with each other.
  • the pair of contact portions M1 and M2 in contact with each other is a predetermined portion with respect to the direction of the bisector Z of the tangent line X1 and X2 of the pressed surface 28 at each contact portion of the pair of contact portions M1 and M2. Is located closer to the center axis O of the pressed surface 28, and the predetermined portion is the input engagement portion 20 when rotational torque is input to the input member 14 of the first portion 68. It is a portion to be engaged (a chain line L1 in FIG. 21).
  • the predetermined portion is a portion of the first portion 68 that is engaged with the output engagement portion 26 when a rotational torque is reversely input to the output member 15 (a chain line L2 in FIG. 21).
  • the portions M1 and M2 are preferably positioned closer to the center axis O of the pressed surface 28.
  • each of the engagement elements 17b constituting the pair of engagement elements 17b has a substantially arcuate plate shape (bow plate shape) and is disposed on the radially inner side of the pressed member 16. ing.
  • the pair of engaging elements 17b is arranged such that the output engaging portion 26 is arranged in the radial direction, which is the separation direction of the pair of cam surfaces 27, between the pressed surface 28 and the outer peripheral surface of the output engaging portion 26. It arrange
  • each of the pair of engaging elements 17b is a first portion arranged at a position sandwiched between the input engaging portion 20 and the output engaging portion 26 with respect to the radial direction inside the pressed surface 28 in the radial direction.
  • 68, and a pair of second portions 69 disposed at positions deviated on both sides in the circumferential direction from a position sandwiched between the input engagement portion 20 and the output engagement portion 26 in the radial direction.
  • a chain line ⁇ 1 is a virtual line indicating the boundary between the first portion 68 and the second portion 69.
  • none of the engaging elements 17 b has a portion arranged on the radially outer side of the input engaging portion 20 on the radially inner side of the pressed surface 28.
  • Each engaging element 17b is composed of the same parts made in the same shape and size.
  • Each engaging element 17b has a cylindrical convex pressing surface 29 on a radially outer surface on both sides in the circumferential direction opposite to the pressed surface 28, that is, on each radially outer surface of the pair of second portions 69. Have. Further, each engagement element 17b is camped on the radially inner side surface of the circumferential intermediate portion facing the cam surface 27 of the output engagement portion 26, that is, on the radially inner side surface of the circumferential intermediate portion of the first portion 68. An output engagement surface 30 that can be engaged with the surface 27 is provided. The output engagement surface 30 has a flat surface shape orthogonal to the separation direction (vertical direction in FIG. 6) of the pair of engagement elements 17b.
  • Each engaging element 17b is engaged with the input engaging portion 20 on the radially outer surface of the circumferential intermediate portion facing the radially inner surface of the input engaging portion 20, that is, on the radially outer surface of the first portion 68. It has a mating input engaging surface 32.
  • the input engagement surface 32 has a flat surface shape parallel to the output engagement surface 30. There are gaps between the pressed surface 28 and the input engagement surface 32 in the circumferential direction and in the separation direction of the pair of engagement elements 17b. For this reason, the input engagement portion 20 can move relative to the rotation direction of the input member 14 with respect to the pair of engagement members 17b, and each engagement member 17b has one pair with respect to the input engagement portion 20. The relative movement of the engaging element 17b in the separating direction is possible.
  • Each of the pair of pressing surfaces 29 has a friction coefficient larger than the friction coefficient of the other portion of each engaging element 17b, and has a curvature radius Cr ′ smaller than the curvature radius Cr of the pressed surface 28. (Cr ′ ⁇ Cr).
  • the input engagement portion 20 rotates in the rotational direction of the input member 14 (clockwise in the example of FIG. 19). Rotate to. Then, the input engagement portion 20 presses the input engagement surface 32 inward in the radial direction, and moves the pair of engagement elements 17b in directions away from the pressed surface 28, respectively.
  • Each of the engagement elements 17b is arranged on the radially inner side (the engagement element 17b located on the upper side in FIG. 19) so as to approach each other in the separation direction based on the engagement between the input engagement surface 32 and the input engagement portion 20.
  • the engaging member 17b located on the lower side of FIG. 19 is moved downward).
  • the output engagement surface 30 of the pair of engagement elements 17b sandwiches the output engagement portion 26 from both sides in the radial direction and engages (surface contact) with the pair of cam surfaces 27 without rattling.
  • the rotational torque input to the input member 14 is transmitted to the output member 15 via the pair of engaging members 17b and output from the output member 15.
  • the pair of pressing surfaces 29 included in the pair of engagement elements 17 b are pressed against two locations separated in the circumferential direction of the pressed surface 28.
  • the radius of curvature Cr ′ of the pressing surface 29 is smaller than the radius of curvature Cr of the pressed surface 28, each pressing surface 29 and the pressed surface 28 are in line contact or point contact at one point. Therefore, each engaging element 17b having a pair of pressing surfaces 29 and the pressed surface 28 come into contact with each other at a total of two points.
  • the reverse input cutoff clutch 5d of this example prevents the rotational torque reversely input to the output member 15 from being transmitted to the input member 14, or only a part thereof is transmitted and the remaining portion is blocked. To function.
  • the normal force P corresponding to the normal force Fc acts on the contact portions M ⁇ b> 1 and M ⁇ b> 2 between the respective pressing surfaces 29 and the pressed surfaces 28.
  • the wedge angle between the tangents X1 and X2 at the respective contact portions M1 and M2 is 2 ⁇ and the friction coefficient between the pressing surface 29 and the pressed surface 28 is ⁇ ′, the respective contact portions.
  • the normal force P acting on M1 and M2 is expressed by the following equation (10).
  • P Fc / 2 (sin ⁇ + ⁇ ′ ⁇ cos ⁇ ) (10)
  • the friction coefficient ⁇ ′, the distance R, and the normal force Fc should be increased.
  • the wedge angle ⁇ should be made as small as possible in order to increase the brake torque T ′ by utilizing the wedge effect.
  • the respective contact portions M1 and M2 are arranged as much as possible with the central axis of the pressed surface 28. It can be seen that it should be close to O.
  • each of the contact portions M1 and M2 is input to the bisector Z.
  • the input engagement surface 32 is a portion of the first portion 68 of each engagement member 17 that is engaged with the input engagement portion 20 when rotational torque is input to the input member 14.
  • the output engagement surface 30 is a portion of the first portion 68 of each engagement element 17b where the output engagement portion 26 engages when the rotational torque is reversely input to the output member 15.
  • the brake torque T ′ must satisfy the relationship of the formula (8): T> T ′ shown in the first example of the first mode.
  • the friction coefficient ⁇ between the output engagement portion 26 and the output engagement surface 30, the friction coefficient ⁇ ′ between the pressing surface 29 and the pressed surface 28, the rotation center axis The distance r from O to the contact portion X, the distance R from the rotation center axis O to the contact portions M1 and M2, and the wedge angle ⁇ between the direction of the line of action of the tangential force Ft and the output engagement surface 30 are respectively shown.
  • the output member 15 can be semi-locked.
  • the brake torque T ′ is applied to the contact portion M1 between the pressing surface 29 and the pressed surface 28 from the rotation center axis O of the output member 15.
  • the size is proportional to the distance R to M2.
  • the wedge angle ⁇ should be made as small as possible, that is, the contact portions M1 and M2 between the pressed surface 28 and the engaging element 17 are determined. It can be seen that the direction of the bisector Z (vertical direction in FIG. 21) should be as close to the central axis O of the pressed surface 28 as possible.
  • the contact portions M1 and M2 are closer to the center axis O of the pressed surface 28 than the input engagement surface 32 with respect to the direction of the bisector Z (lower than the chain line L1 in FIG. 21). Furthermore, it is positioned closer to the center axis O of the pressed surface 28 than the output engagement surface 30 (lower than the chain line L2 in FIG. 21).
  • the wedge angle ⁇ is made sufficiently small to easily obtain a large brake torque T ′.
  • the contact portions M1 and M2 are farther from the center axis O than the input engagement surface 32 in the direction of the bisector Z (the chain line L1 in FIG. 22).
  • the distance R required to obtain the brake torque T ′ having a predetermined magnitude is reduced, that is, the diameter of the lock mechanism 52c is reduced. be able to.
  • the distance R is the same as the structure of the reference example, a larger brake torque T ′ than that of the structure of the reference example can be obtained.
  • the safety factor against slipping of the pressing surface 28 and the pressing surface 29 can be increased.
  • each of the engagement elements 17b of the pair of engagement elements 17b constituting the reverse input cutoff clutch 5d is a portion disposed on the radially inner side of the pressed surface 28 and on the radially outer side of the input engagement portion 20. Does not have. For this reason, as in the structure of the reference example shown in FIG. 22, the engaging element 17 z has a portion disposed on the radially inner side of the pressed surface 28 and on the radially outer side of the input engaging portion 20. Compared to the case, it is easy to reduce the weight and facilitate the manufacture.
  • the contact portions M1 and M2 are closer to the center axis O of the pressed surface 28 than the output engagement surface 30 with respect to the direction of the bisector Z (lower than the chain line L2 in FIG. 21). Is located. However, when the present invention is implemented, the contact portions M1 and M2 are closer to the center axis O of the pressed surface 28 than the input engagement surface 32 in the direction of the bisector Z (in FIG. 21). (The lower side of the chain line L1) and farther from the center axis O of the pressed surface 28 than the output engagement surface 30 (the upper side of the chain line L2 in FIG. 21), or the output engagement surface It can also be located at the same position as 30 (on the chain line L2 in FIG. 21). Such a configuration is also included in the scope of the present invention.
  • the pressing surface 29 of each engaging element 17b has a cylindrical convex shape.
  • the pressing surface of the engagement element can be configured by a non-cylindrical convex shape such as an elliptical cylindrical convex surface.
  • the reverse input cutoff clutch of the second aspect can be applied to various mechanical devices such as a variable compression ratio device, an electric door device, a power window device, a steering device, and a jack in addition to the actuator.
  • the number of engaging elements constituting the reverse input cutoff clutch of the second aspect is not limited to two, and may be one or three or more.
  • This example is an example of the reverse input cutoff clutch 5e that can be used by being incorporated in various mechanical devices.
  • the reverse input cutoff clutch 5e of the present example is the same as the first example of the embodiment of the second mode in terms of the basic structure and basic operation of the lock mechanism 52d, but the input member 14a, the output member 15c, Each specific structure of the pressing member 16a and the pair of engaging members 17c is different from the first example of the second embodiment.
  • the input member 14a and the output member 15c each have a solid shaft shape, and are arranged in series and coaxial with each other in the axial direction.
  • the input member 14a is disposed on one side in the axial direction with respect to the output member 15c, and has an input shaft portion 66 in addition to the pair of input engagement portions 20a constituting the lock mechanism 52d.
  • the input shaft portion 66 has a stepped columnar shape and has a rotation center axis that is coaxial with the center axis of the pressed surface 28 constituting the lock mechanism 52d.
  • the pair of input engaging portions 20 a extends in the axial direction from two positions on the opposite side in the radial direction of the end surface on the other axial side of the input shaft portion 66.
  • the radially inner side surface of the input engagement portion 20a is formed by a convex surface having a mountain shape that inclines in a direction toward the radially inner side from the circumferential direction both sides toward the circumferential direction central side.
  • the input shaft portion 66 is connected to an output portion of an input side mechanism constituting various mechanical devices so as to be able to transmit torque by any means.
  • the output member 15c has an output shaft portion 67 in addition to the output engagement portion 26a constituting the lock mechanism 52d.
  • the output shaft portion 67 is cylindrical and has a rotation center axis that is coaxial with the center axis O of the pressed surface 28.
  • the output engagement portion 26 a has an elliptical column shape, and extends in the axial direction from the central portion of the end surface on one axial side of the output shaft portion 67.
  • the output shaft portion 67 is connected to an input portion of the output side mechanism that constitutes various mechanical devices so as to transmit torque by any means.
  • the pressed member 16a is formed in an annular shape as a whole and has a pressed surface 28 on the inner peripheral surface, but has a rectangular cross-sectional shape.
  • the pressed member 16a is fixed to a housing or the like that constitutes various mechanical devices by any means.
  • each of the pair of engaging parts 17c constituting the locking mechanism 52d is disposed on the radially outer side of the input engaging part 20a. It has the 3rd part 70 which is a part.
  • the third portion 70 connects the pair of second portions 69 to each other on the radially outer side of the input engagement portion 20a.
  • a chain line ⁇ ⁇ b> 1 is a virtual line indicating the boundary between the first portion 68 and the second portion 69
  • a chain line ⁇ ⁇ b> 2 is a virtual line indicating the boundary between the second portion 69 and the third portion 70.
  • Each engagement element 17 c has an input engagement hole 31 in a radial intermediate portion of the circumferential intermediate portion, that is, a portion sandwiched between the first portion 68 and the third portion 70.
  • the input engagement hole 31 is a substantially rectangular axial through-hole extending in a direction (left-right direction in FIG. 24) orthogonal to the separation direction and the axial direction of the pair of engagement elements 17c.
  • the input engagement portion 20a is loosely inserted. That is, there are gaps between the inner surface of the input engagement hole 31 and the input engagement portion 20a in the circumferential direction and in the separation direction of the pair of engagement elements 17c.
  • each input engagement part 20a can be moved relative to the respective engagement element 17c in the rotational direction of the input member 14a, and each engagement element 17c can be moved relative to each input engagement part 20a.
  • Relative movement of the pair of engaging elements 17c in the separating direction is possible.
  • each of the engaging elements 17c is easy to ensure rigidity because the third part 70 connects the pair of second parts 69 to each other on the outside in the radial direction of each input engaging part 20a.
  • Other configurations and operations are the same as those of the first example of the first embodiment and the first example of the first embodiment.
  • the reverse input cutoff clutch 5f of the first example of the embodiment of the third aspect is A pressed member 16b having a pressed surface 28a; An input member 14b having a rotation center axis O and at least one input engagement portion 20b; An output member 15d having a rotation center axis O coaxial with the rotation center axis O of the input member 14b, and an output engaging portion 26b; At least one pressing surface 29 that opposes the pressed surface 28a, an engaging side input engaging portion 74 that engages with the input engaging portion 20b, and an engaging side output engagement that engages with the output engaging portion 26b. And at least one engaging member 17d having a portion 72.
  • the engaging member 17d when the rotational torque is input to the input member 14b, the engaging member 17d is connected to the input engaging portion 20b and the engaging member side input engaging portion 74. Based on the engagement, the pressing surface 29 is displaced so as to be separated from the pressed surface 28a, and the engaging member side output engaging portion 72 is engaged with the output engaging portion 26b.
  • the portion between the engaging member 17d and the pressed member 16b, the input engaging portion 20b, and the engaging member side input engaging portion 74 are arranged.
  • An intermediate member is arranged in at least one of the intermediate portion and the intermediate portion between the output engagement portion 26b and the engagement element side output engagement portion 72.
  • a gap adjusting material 75 is used as the intermediate member.
  • the reverse input cutoff clutch 5f of the first example of the embodiment of the third aspect will be described in detail.
  • the reverse input cutoff clutch 5f of this example is a lock type reverse input cutoff clutch, and includes an input member 14b, an output member 15d, a pressed member 16b, and a pair of engagement elements 17d.
  • the input member 14b is connected to an input side mechanism such as an electric motor, and receives rotational torque.
  • the input member 14b includes a rotation center axis O and a pair of input engagement portions 20b arranged at positions radially away from the rotation center axis O.
  • the input member 14b is formed so as to protrude in the axial direction from two positions opposite to the radial direction of the distal end surface of the input shaft portion 66a having a stepped columnar shape and the large diameter portion of the input shaft portion 66a. And a pair of input engaging portions 20b.
  • the input shaft portion 66a has a small-diameter portion connected to the output portion of the input-side mechanism so as to be able to transmit torque, or is formed integrally with the output portion of the input-side mechanism.
  • the pair of input engaging portions 20b have a substantially elliptical column shape and are separated from each other in the radial direction of the input member 14b.
  • Each of the input engaging portions 20b is a flat surface that is perpendicular to the radially outer surface on the same cylindrical surface as the outer peripheral surface of the large-diameter portion of the input shaft portion 66a, and the separation direction of the pair of input engaging portions 20b. And a radially inner side surface.
  • the output member 15d is connected to an output side mechanism such as a speed reduction mechanism, and outputs rotational torque.
  • the output member 15d includes a rotation center axis O that is coaxial with the rotation center axis O of the input member 14b, and an output engagement portion 26b that is disposed on the rotation center axis O.
  • the output member 15d includes an output shaft portion 67a having a cylindrical shape, and an output engagement portion 26b formed so as to protrude in the axial direction from the center portion of the distal end surface of the output shaft portion 67a.
  • the output shaft portion 67a is connected to the input portion of the output side mechanism so that torque can be transmitted, or is formed integrally with the input portion of the output side mechanism.
  • the output engagement portion 26b has a cam function. That is, the distance from the rotation center axis O of the output member 15d to the outer peripheral surface of the output engagement portion 26b is not constant in the circumferential direction.
  • the output engagement portion 26b has a substantially rectangular column shape.
  • the outer peripheral surface of the output engaging portion 26b is mutually connected with a pair of first flat surfaces parallel to each other in the longitudinal direction (left and right direction in FIG. 31) and in the short direction (up and down direction in FIG. 31). It consists of a pair of parallel second flat surfaces and a partial cylindrical surface connecting the first flat surface and the second flat surface.
  • the output engagement portion 26b is disposed between the radially inner side surfaces of the pair of input engagement portions 20b.
  • the pressed member 16b is fixed to another member (not shown) such as a housing and its rotation is restricted.
  • the pressed member 16b has a central axis O that is coaxial with the rotation center axis O of the input member 14b, and has a pressed surface 28a that is a cylindrical concave surface on the inner peripheral surface that is centered on the central axis.
  • the pressed member 16 b is configured by combining the pressed member main body 108 and the gap adjusting material 75.
  • the pressed member main body 108 is formed in an annular shape and has an inner peripheral surface that is a cylindrical concave surface.
  • the gap adjusting member 75 is made of a metal plate such as a steel plate, has a short cylindrical shape, and has a pressed surface 28a on the inner peripheral surface.
  • the gap adjusting member 75 is fixed to the pressed member main body 108 in a state of being fitted into the inner peripheral surface of the pressed member main body 108 without any radial play.
  • the gap adjusting member 75 is fixed to the pressed member main body 108 by bonding its outer peripheral surface to the inner peripheral surface of the pressed member main body 108 with an adhesive.
  • the method of fixing the gap adjusting member 75 to the pressed member main body 108 is not limited to adhesion.
  • any means such as fixing means as shown in FIG. 34 may be used.
  • any means such as fixing means as shown in FIG. 34 may be used.
  • a pair of bent pieces 109 bent outward in the radial direction are formed from both axial sides of the gap adjusting member 75, and the pressed member main body 108 is formed by the pair of bent pieces 109. It is clamped from both sides in the axial direction.
  • the gap adjusting member 75 includes a fixing portion such as a pair of bent pieces 109, the fixing portion is bonded, welded, screwed, and riveted to the pressed member main body 108.
  • the pressed member 16b is disposed radially outside the input member 14b and the output member 15d. Specifically, in the assembled state of the reverse input cutoff clutch 5f, the pair of input engagement portions 20b and output engagement portions 26b are disposed on the radially inner side of the pressed member 16b.
  • Each of the engaging members 17d constituting the pair of engaging members 17d includes a pressing surface 29 that opposes the pressed surface 28a, an engaging member side input engaging portion 74 that engages with the input engaging portion 20b, and an output engagement. And an engaging member side output engaging portion 72 that engages with the portion 26b.
  • each engaging element 17d has a substantially semicircular plate shape, and is disposed on the radially inner side of the pressed member 16b.
  • Each engaging element 17d has a pressing surface 29 on the radially outer surface of the outer peripheral surface, and a bottom surface 71 that is a flat surface on the radially inner surface of the outer peripheral surface and the engaging side output. And an engaging portion 72.
  • Each engaging element 17 d has a side surface 73 which is a flat surface perpendicular to the bottom surface 71 at a portion connecting the both ends in the circumferential direction of the pressing surface 29 and both ends of the bottom surface 71 of the outer peripheral surface.
  • the radial direction with respect to the engaging element 17d means a direction perpendicular to the bottom surface 71 indicated by an arrow A in FIG.
  • the width direction with respect to the engagement element 17d refers to a direction parallel to the bottom surface 71 indicated by an arrow B in FIG.
  • the pressing surface 29 is a partially cylindrical convex surface and has a radius of curvature equal to or less than the radius of curvature of the pressed surface 28a.
  • the pressing surfaces 29 of the respective engagement elements 17d are directed to the opposite side in the radial direction, and the bottom surfaces 71 of the respective engagement elements 17d are opposed to each other.
  • the inner diameter dimension of the pressed member 16b and the radial dimension of each engagement element 17d are restricted.
  • Each engaging element 17d has an engaging-element-side input engaging part 74 that is a substantially rectangular long hole that penetrates the radial intermediate part in the axial direction and extends in the width direction.
  • the portion located radially inward is a flat surface perpendicular to the radial direction.
  • the engagement element side input engagement portion 74 has a size capable of loosely inserting the input engagement portion 20b of the input member 14b. Specifically, when the input engagement portion 20 b is inserted inside the engagement element side input engagement portion 74, the engagement element is interposed between the input engagement portion 20 b and the inner surface of the engagement element side input engagement portion 74.
  • the input engagement portion 20b can move in the distance (displacement) with respect to the pressed surface 28a on the inner side of the engagement member side input engagement portion 74, and can move relative to the rotation direction of the input member 14b. Is engaged.
  • Each engagement element 17d has an engagement element side output engagement part 72 which is a substantially rectangular recess formed so as to be recessed outwardly with respect to the radial direction of the engagement element 17d from the center part in the width direction of the bottom surface 71.
  • the engagement element-side output engagement part 72 has a size and a shape that allow a half of the output engagement part 26b of the output member 15d to be loosely arranged inside the engagement element-side output engagement part 72.
  • the engagement element side output engagement portion 72 has an opening width that is slightly larger than the dimension in the longitudinal direction of the output engagement portion 26b, and has a dimension in the short direction of the output engagement portion 26b. It has a radial depth slightly smaller than 1/2.
  • the bottom part of the engagement element side output engagement part 72 is a flat surface orthogonal to the radial direction.
  • the pair of input engaging portions 20b of the input member 14b disposed on one side in the axial direction are respectively engaged with the engagement side input engagement of the pair of engagement elements 17d.
  • the output engagement portion 26b of the output member 15d that is inserted in the portion 74 in the axial direction and disposed on the other side in the axial direction is inserted between the pair of engagement member side output engagement portions 72 in the axial direction.
  • the pair of engaging elements 17d are arranged so as to sandwich the output engaging part 26b from the radially outer side by the respective engaging element side output engaging parts 72.
  • the axial dimension of the input engaging part 20b, the axial dimension of the output engaging part 26b, the axial dimension of the pressed member 16b, and the axial dimension of the engaging element 17d are substantially the same. ing.
  • FIGS. 35 to 37 The operation and the operation of the reverse input cutoff clutch 5f of this example are shown in FIGS. 35 to 37. Basically, the operation and the operation of the reverse input cutoff clutch 5 in the first example of the embodiment of the first mode are shown. The description here is omitted.
  • the size of the gap between the constituent members is adjusted so that the operation of locking or semi-locking the output member 15d is possible.
  • the backlash in the rotational direction between the input member 14b and the output member 15d can be suppressed to be small.
  • the reverse input cutoff clutch 5f of this example in order to enable a switching operation between a state where the output member 15d is locked or semi-locked and a state where the output member 15d is locked or semi-locked,
  • the portion between the input engagement portion 20b and the inner surface of the engagement element side input engagement portion 74, the portion between the output engagement portion 26b and the bottom portion of the engagement element side output engagement portion 72, the pressed surface 28a and the pressure A gap for allowing each of the engaging elements 17d to move in the radial direction relative to the pressed surface 28a, that is, between the input member 14b and the output member 15d, between the surface 29 and the portion between the input member 14d and the output member 15d. Need to provide rotational backlash. Such backlash is also necessary to enable the assembly of the reverse input cutoff clutch 5f.
  • the backlash in the rotational direction between the input member 14b and the output member 15d increases.
  • the positional relationship in the rotational direction between the input member 14b and the output member 15d varies greatly depending on whether the input member 14b rotates in the forward direction or the reverse direction, and the output depends on the rotational position of the input member 14b. It becomes difficult to control the rotational position of the member 15d with high accuracy. Further, the response time from when the rotation direction of the input member 14b is reversed to when the rotation direction of the output member 15d is reversed, or until the output member 15d is locked or semi-locked after the rotation torque is reversely input to the output member 15d.
  • the response time becomes longer. And if the former response time becomes long, the responsiveness of the control by the mechanical device incorporating the reverse input cutoff clutch 5f becomes low. Further, if the latter response time becomes long, for example, in the application of locking the output member 15d, it is difficult to meet the request even when it is desired to minimize the reverse input rotation of the output member 15d. Furthermore, abnormal noise and fretting due to collision and rubbing are likely to occur between the members constituting the reverse input cutoff clutch 5f. From the viewpoint of avoiding such inconvenience, the backlash is desirably kept as small as possible.
  • the backlash varies due to accumulation of dimensional tolerances of the input member 14b, the output member 15d, the pressed member 16c, and the engaging member 17d. For this reason, the said backlash may become large unintentionally. Such inconvenience can be avoided by reducing the dimensional tolerance. However, in general, it is not easy to reduce the dimensional tolerance. Such a workaround also causes a cost increase.
  • the reverse input cutoff clutch 5f of this example has an appropriate thickness dimension as the gap adjusting member 75 that constitutes the pressed member 16b when the reverse input cutoff clutch 5f is assembled without reducing the dimensional tolerance.
  • the backlash can be kept small. Specifically, for example, when assembling the reverse input cutoff clutch 5f, first, the backlash is measured in a state where the members other than the gap adjusting member 75 are assembled. Next, based on the size of the backlash measured in this way, a gap adjusting member 75 having an appropriate thickness dimension capable of suppressing the backlash is selected. By assembling the reverse input cutoff clutch 5f including the gap adjusting material 75 selected in this way, the backlash can be suppressed to be small.
  • the backlash can be suppressed to be small, so that the backlash in the rotational direction between the input member 14b and the output member 15d can be suppressed to be small.
  • the following effects can be obtained. That is, the positional relationship in the rotational direction between the input member 14b and the output member 15d is substantially equal between the case where the input member 14b rotates in the forward direction and the case where the input member 14b rotates in the reverse direction (the positional relationship of the two cases). The difference can be made sufficiently small). For this reason, the rotational position of the output member 15d can be accurately controlled by the rotational position of the input member 14b.
  • the response time can be shortened.
  • By shortening the former response time it is possible to increase the responsiveness of control by the mechanical device incorporating the reverse input cutoff clutch 5f.
  • By shortening the latter response time for example, in the application where the output member 15d is locked, the reverse input rotation of the output member 15d can be minimized.
  • the reverse input cutoff clutch of the third aspect can be used by being incorporated between an electric motor and a driven part driven by the electric motor, for example, in an actuator using an electric motor as a driving source.
  • the driven part can be driven with high efficiency by the electric motor
  • the electric motor is set by locking the reverse input cutoff clutch.
  • the position of the driven part can be held without requiring the power consumption. Therefore, an actuator with high efficiency and low power consumption can be realized.
  • the reverse input cutoff clutch of the third aspect can be applied to various mechanical devices such as a variable compression ratio device, an electric door device, a power window device, a steering device, and a jack. And the backlash between the input member and output member of a reverse input interruption
  • blocking clutch can be suppressed small, and the positioning of the movable part of various machine apparatuses can be performed with sufficient precision.
  • the number of engagement elements constituting the reverse input cutoff clutch of the present invention is not limited to two, but may be one or three or more.
  • the input member, the output member, the pressed member, the engagement member, and the gap adjusting material are in contact with each other as long as the output member is locked or semi-locked.
  • Lubricants such as traction oil, traction grease and other normal lubricating oils can also be arranged.
  • at least one of the input member, the output member, the pressed member, the engagement element, and the gap adjusting material can be made of oil-impregnated metal.
  • the material of the gap adjusting material may be ceramics or rubber. Further, the gap adjusting material is formed on at least one surface of the input member, the output member, the pressed member, and the engaging member, such as plating such as nickel chrome plating, thermal spray coating, resin coating, It can also be constituted by various coating materials.
  • each of the pair of engaging members 17e has a guide hole 76 extending radially in the radially inner portion of the intermediate portion in the width direction. Both end portions in the axial direction of the guide hole 76 are open to the bottom portion of the engagement element side output engagement portion 72 and the portion located on the radially inner side of the inner surface of the engagement element side input engagement portion 74.
  • the output engagement portion 26c of the output member 15e has an insertion hole 77 that is orthogonal to the center of the output engagement portion 26c and penetrates the output engagement portion 26c in the lateral direction.
  • Both end portions in the axial direction of the guide shaft 78 which is a guide member, do not rattle in the radial direction of the guide shaft 78 and can move in the axial direction of the guide shaft 78 in the guide holes 76 of the respective engagement elements 17e.
  • An intermediate portion in the axial direction of the guide shaft 78 is loosely inserted into the insertion hole 77 of the output engagement portion 26c.
  • the engagement mechanisms 17e move relative to each other in the width direction by the guide mechanism constituted by the guide hole 76 and the guide shaft 78 of each engagement element 17e.
  • the respective engagement elements 17e are prevented from being inclined with respect to each other so that the bottom surfaces 71 of the engagement elements 17e are not parallel to each other, and each engagement element 17e is only allowed to move in the radial direction.
  • each engagement element 17e has two cylindrical guide recesses 79 that are recessed in the width direction of the bottom surface 71 in the direction perpendicular to the bottom surface 71.
  • they are elastic so as to be bridged between the respective guide recesses 79 inside the two sets of guide recesses 79 arranged on the same straight line.
  • a coiled spring 80 as a member is disposed.
  • Each of the pair of engaging members 17e is biased toward the pressed surface 28a by the elasticity of the pair of springs 80 disposed in the two sets of guide recesses 79.
  • This example is a modification of the second example (see FIG. 38) of the embodiment of the third aspect.
  • the radially outer surfaces of the pair of engaging elements 17f are pressing surfaces 29b in which two portions separated in the circumferential direction are pressed against the pressed surface 28a.
  • the circumferential intermediate portion sandwiched between the pressing surfaces 29b is a flat surface that cannot be pressed against the pressed surface 28a.
  • Each of the pressing surfaces 29b is a cylindrical convex surface having a radius of curvature smaller than the radius of curvature of the pressed surface 28a.
  • This example is a modification of the second example (see FIG. 38) of the embodiment of the third aspect.
  • the pressed member 16c is configured only by the pressed member main body 108a, and the pressed surface 28 is provided on the inner peripheral surface of the pressed member main body 108a.
  • each of the engagement elements 17g constituting the pair of engagement elements 17g is configured by combining the engagement element main body 110 and the gap adjusting member 75a.
  • the engagement body 110 has the same configuration as the engagement element 17e of the second example of the embodiment of the third aspect, but is a radially outer surface that is a partially cylindrical convex surface that is the pressing surface 29 in the engagement element 17e. Does not function as a pressing surface.
  • the gap adjusting member 75 a has a substantially semi-cylindrical shape that can cover a continuous range between the radially outer surface and the radially outer portion of the pair of side surfaces 73 on the outer peripheral surface of the engagement body 110.
  • the gap adjusting member 75a is fixed to the engaging member main body 110 in a state of covering the range.
  • the fixing method of the clearance adjustment material 75a with respect to the engaging element main body 110 can employ
  • the gap adjusting member 75 a includes a pressing surface 29 c having a radius of curvature equal to or smaller than the radius of curvature of the pressed surface 28 on the radially outer surface of the portion covering the radially outer surface of the engagement body 110.
  • each engaging element 17g has a gap adjusting member 75a, the gap between each engaging element 17g and the pressed member 16b, which is a counterpart member, and the input member 14b are individually provided. And the output member 15e can be adjusted. Therefore, the backlash in the rotational direction between the input member 14b and the output member 15e can be further reduced as compared with the first to third examples of the embodiment of the third aspect.
  • Other configurations and operations are the same as those of the second example of the embodiment of the third aspect.
  • each of the engagement elements 17h constituting the pair of engagement elements 17h is configured by combining the engagement element main body 110a and the pair of gap adjusting members 75b.
  • the engaging element main body 110a has the same configuration as the engaging element 17f of the third example (see FIG. 39) of the embodiment of the third aspect, but is a pressing surface 29b in the engaging element 17f. Two portions separated in the circumferential direction do not function as a pressing surface.
  • Each of the pair of gap adjusting members 75b has a substantially semi-cylindrical shape capable of covering two portions separated in the circumferential direction of the radially outer side surface of the engagement body 110a.
  • the pair of gap adjusting members 75b is fixed to the engaging member main body 110a in a state of covering the two portions.
  • the pair of gap adjusting members 75b includes a pressing surface 29d having a radius of curvature smaller than the radius of curvature of the pressed surface 28 on the radially outer surface.
  • Other configurations and operations are the same as those of the third example and the fourth example of the embodiment of the third aspect.
  • This example is a modification of the third example (see FIG. 39) of the embodiment of the third aspect.
  • the pressed member 16c is configured only by the pressed member main body 108a, and the pressed surface 28 is provided on the inner peripheral surface of the pressed member main body 108a.
  • the gap adjustment is performed at a position sandwiched between the inner surface of the engagement element side input engagement part 74 and the input engagement part 20b.
  • the gap adjusting material 75d is disposed at a position where the material 75c is disposed and is sandwiched between the inner surface of the engagement-side output engagement portion 72 and the output engagement portion 26c.
  • the gap adjusting member 75c has a U-shaped plate shape that can cover a continuous range of the radially inner side surface of the input engaging portion 20b of the input member 14b and the radially inner side portions of both circumferential side surfaces.
  • the gap adjusting member 75c is fixed to the input engaging portion 20b in a state of covering this range.
  • the fixing means for the gap adjusting material 75c with respect to the input engagement portion 20b the same means as the fixing means for the gap adjusting material 75 described in the first example of the embodiment of the third aspect can be adopted.
  • the gap adjusting member 75d covers the outer surface of the short side half of the output engagement portion 26c of the output member 15e, that is, the continuous range of the short side surface and the short side half of both long side surfaces. It has a U-shaped plate shape.
  • the gap adjusting member 75d is fixed to the output engagement portion 26c while covering this range. In this state, the gap adjusting member 75 d has a through hole 81 at a position aligned with the opening of the insertion hole 77.
  • a guide shaft 78 is loosely inserted into the through hole 81.
  • each of the engaging members 17f engages the input engaging portion 20b and the inner surface of the engaging member side input engaging portion 74 via the gap adjusting member 75c. Then, it moves inward in the radial direction and engages the input member 14b by engaging the bottom of the output side engaging part 72 with the output engaging part 26b via the gap adjusting member 75d. The rotational torque thus transmitted is transmitted to the output member 15e. Further, when the rotational torque is reversely input to the output member 15e, each of the engagement elements 17f engages the output engagement part 26c and the engagement element side output engagement part 72 via the gap adjusting member 75d. Based on this, the pressing surface 29b is frictionally engaged with the pressed surface 28 by moving outward in the radial direction.
  • the gap adjusting member 75c is disposed between the inner surface of the engagement element side input engagement part 74 and the input engagement part 20b, and the engagement element side output engagement part 72 A gap adjusting member 75d is disposed between the inner surface and the output engagement portion 26c.
  • the gap between the inner surface of the engagement element side input engagement part 74 and the input engagement part 20b, and the inner surface of the engagement element side output engagement part 72 and the output engagement part 26c. Can be individually adjusted. Therefore, the backlash in the rotational direction between the input member 14b and the output member 15e can be further reduced as compared with the first to fifth examples of the embodiment of the third aspect.
  • the gap adjusting member 75d disposed between the output engaging portion 26c and the output engaging portion 26c may be configured to include only one of them. Such a configuration is also included in the scope of the present invention. Other configurations and operations are the same as those of the third example of the third embodiment.
  • This example is a modification of the sixth example (see FIG. 42) of the embodiment of the third aspect.
  • the guide shaft 78 is disposed at the center.
  • cylindrical guide shafts 78a are arranged on both sides in the width direction of the pair of engaging elements 17i. That is, in each of the both sides in the width direction of the pair of engaging elements 17i, both axial sides of the guide shaft 78a are swayed in the radial direction inside the pair of guide recesses 79 arranged on the same straight line. And is inserted so as to be movable in the axial direction.
  • the spring 80 is disposed on the radially inner side of the guide shaft 78a.
  • the gap adjusting member 75e disposed between the input engagement portion 20b and the inner surface of the engagement member side input engagement portion 74a is fixed to each engagement member 17i.
  • Each engaging element 17i has a holding recess 82 recessed inward in the radial direction at the intermediate portion in the width direction of the inner surface of the engaging side input engaging portion 74a.
  • the bottom of the holding recess 82 is a flat surface perpendicular to the radial direction of each engagement element 17i.
  • the gap adjusting member 75e is formed in a flat plate shape, and is fixed to each engaging element 17i in a state in which a half portion in the thickness direction is held inside the holding recess 82 without a gap.
  • the fixing means for the gap adjusting member 75e with respect to each engaging element 17i can be the same means as the fixing means for the gap adjusting member 75 described in the first example of the embodiment of the third mode.
  • the gap adjusting member 75f disposed between the output engagement portion 26b and the inner surface of the engagement element side output engagement portion 72a is fixed to each engagement element 17i.
  • Each of the engaging members 17i has a holding recessed portion 83 that is recessed radially outward in the intermediate portion in the width direction of the bottom portion of the engaging-side output engaging portion 72a.
  • the bottom of the holding recess 83 is a flat surface perpendicular to the radial direction of each engagement element 17i.
  • the gap adjusting member 75f is formed in a flat plate shape, and is fixed to each engaging element 17i in a state where a half part in the thickness direction is held inside the holding recess 83 without a gap.
  • the fixing means for the gap adjusting member 75f with respect to each engaging element 17i the same means as the fixing means for the gap adjusting material 75 described in the first example of the embodiment of the third aspect can be adopted.
  • the gap adjustment can be performed with fewer steps compared to the sixth example of the third embodiment. That is, in the sixth example of the embodiment of the third aspect, a total of 2 steps including a step of fixing the gap adjustment member 75c to the input engagement portion 20b and a step of fixing the gap adjustment member 75d to the output engagement portion 26c. It is necessary to adjust the gap in the process. On the other hand, in this example, the gap adjustment can be performed by only one step of fixing the gap adjusting members 75e and 75f to the engaging element 17i. Other configurations and operations are the same as in the sixth example of the embodiment of the third aspect.
  • This example is a modification of the sixth example (see FIG. 42) of the embodiment of the third aspect.
  • the gap adjusting member 75g disposed between the input engagement portion 20b and the inner surface of the engagement member side input engagement portion 74 is held by the guide shaft 78. That is, the gap adjusting member 75g is formed in a flat plate shape, and is between the radially inner side surface of the input engagement portion 20b and the portion located on the radially inner side of the inner surface of the engagement member side input engagement portion 74. Is arranged.
  • the gap adjusting member 75g has a through hole 84 in the thickness direction at the center.
  • an axial end portion of the guide shaft 78 is inserted so as not to rattle in the radial direction of the guide shaft 78 and to be movable in the axial direction of the guide shaft 78.
  • the gap adjusting member 75g is engaged with the axial end of the guide shaft 78 in the through hole 84, and the radially inner side surface of the input engagement portion 20b and the engagement element side input engagement portion 74. It is held by the guide shaft 78 so as not to drop out from between the inner surface of the guide shaft 78 and the inner surface.
  • the gap adjusting member 75 h disposed between the output engagement portion 26 c and the inner surface of the engagement element side output engagement portion 72 is held by the guide shaft 78.
  • the gap adjusting member 75h is formed in a flat plate shape, and is disposed between the lateral side surface of the output engagement portion 26c and the bottom portion of the engagement element side output engagement portion 72.
  • the gap adjusting member 75h has a through hole 85 in the thickness direction at the center. Inside the through hole 85, an intermediate portion in the axial direction of the guide shaft 78 is inserted so as not to rattle in the radial direction of the guide shaft 78 and to be movable in the axial direction of the guide shaft 78.
  • the gap adjusting member 75h is formed by engaging the axially intermediate portion of the guide shaft 78 with the through-hole 85, and the side surface in the short direction of the output engaging portion 26c and the engaging-side output engaging portion. It is held by the guide shaft 78 so as not to drop out from between the bottom portion of 72.
  • the gap adjusting members 75g and 75h can be held on the guide shaft 78 by inserting the guide shaft 78 into the respective through holes 84 and 85. For this reason, the installation work of the gap adjusting members 75g and 75h can be easily performed.
  • Other configurations and operations are the same as in the sixth example of the embodiment of the third aspect.
  • the gap adjusting member 75i disposed between the input engagement portion 20b and the inner surface of the engagement member side input engagement portion 74 is a plate spring made of steel.
  • the gap adjusting member 75i is in contact with each other with respect to the thickness direction of the contact plate 86 from both sides of the flat contact plate 86 and the width direction of the contact plate 86 (horizontal direction in FIGS. 45 and 46).
  • a pair of fixing plate portions 87 formed so as to be bent at right angles in the same direction.
  • the gap adjusting member 75i fits the pair of fixed plate portions 87 into the holding recesses 82 of the respective engagement elements 17i without rattling in the width direction, and the pair of fixed plate portions 87 and the contact plate portions 86. And the bottom part of the holding recess 82 are fixed to the respective engagement elements 17i in a state where a space 88 is a part surrounded by the four sides.
  • the gap adjusting member 75j disposed between the output engaging portion 26b and the inner surface of the engagement member side output engaging portion 72a is also a steel plate spring having the same configuration as the gap adjusting member 75i. is there.
  • the gap adjusting member 75j is in contact with each other with respect to the thickness direction of the contact plate portion 86a from both sides of the flat contact plate portion 86a and the width direction of the contact plate portion 86a (left and right direction in FIGS. 45 and 46).
  • a pair of fixed plate portions 87a formed so as to be bent at right angles in the same direction.
  • the gap adjusting member 75j fits the pair of fixed plate portions 87a into the holding recesses 83 of the respective engagement elements 17i without rattling in the width direction, and the pair of fixed plate portions 87a and the contact plate portions 86a. And the bottom part of the holding recess 83 are fixed to the respective engagement elements 17i in a state where a space 88a is a part surrounded by the four sides.
  • the input engaging portion 20b presses the contact plate portion 86 of the gap adjusting material 75i, and the output engaging portion 26b is set to the gap adjusting material 75j. Is pressed by the contact plate portion 86a.
  • the contact plate portions 86 and 86a are elastically bent toward the space portions 88 and 88a, the impact acting between the input engagement portion 20b and the output engagement portion 26c and the respective engagement elements 17i. Can be relaxed.
  • the output engagement portion 26b presses the contact plate portion 86a of the gap adjusting member 75j.
  • the contact plate portion 86a is elastically bent toward the space portion 88a, so that the impact acting between the output engagement portion 26c and the pressed member 16b and the respective engagement elements 17i can be reduced. Can do.
  • Other configurations and operations are the same as those of the seventh example of the third embodiment.
  • the gap adjusting member 75k disposed between the input engagement portion 20b and the inner surface of the engagement member side input engagement portion 74 is configured by a coiled spring.
  • one gap adjusting member 75k is disposed on each side of the input engagement portion 20b in the circumferential direction.
  • each gap adjusting member 75k is disposed so as to span between the circumferential side surface of the input engagement portion 20b and the circumferential end portion of the inner surface of the engagement member side input engagement portion 74.
  • the gap adjusting member 75m disposed between the output engagement portion 26c and the inner surface of the engagement element side output engagement portion 72 is also configured by a coiled spring.
  • one gap adjusting member 75m is arranged on each side in the longitudinal direction of the half in the short direction of the output engagement part 26c. Specifically, each gap adjustment member 75m is bridged between the longitudinal side surface of the half in the short direction of the output engagement portion 26c and the inner side surface constituting the inner surface of the engagement element side output engagement portion 72. Has been placed.
  • the input member 14b and the output member 15e are not loaded with rotational torque, and are not loaded between the input engagement portion 20b and the inner surface of the engagement member side input engagement portion 74. Due to the elasticity of the arranged gap adjusting member 75k, it is possible to suppress the rattling in the rotational direction between the input engagement portion 20b and each engagement element 17f. Further, in the no-load state, the output engaging portion 26c and each of the engaging members 17f are caused by the elasticity of the gap adjusting member 75m disposed between the output engaging portion 26c and the inner surface of the engaging side output engaging portion 72. Shaking of the rotation direction between and can be suppressed. Furthermore, in the no-load state, the positional relationship in the rotational direction between the input member 14b and the output member 15e can be returned to the neutral position by the elasticity of the gap adjusting members 75k and 75m.
  • the radially inner side surface of the input engaging portion 20b and the engaging element side input engaging portion 74 are input.
  • the gap adjusting member 75k is strongly sandwiched between the inner surface of the inner surface of the output member and the portion positioned on the radially inner side, or the gap is adjusted between the corner portion of the output engaging portion 26c and the bottom portion of the engaging member side output engaging portion 72.
  • the material 75m is not strongly clamped. For this reason, the backlash between the input member 14b and the output member 15e does not change over time due to wear of the gap adjusting members 75k and 75m.
  • the gap adjusting members 75k and 75m bend elastically, so the input engagement portion 20b and the output engagement portion 26c and the respective engagement elements 17f. The impact acting between the two can be reduced. Further, when the rotational torque is reversely input to the output member 15e, the gap adjusting member 75m is elastically bent, and thus acts between the output engaging portion 26c and the pressed member 16b and the respective engaging elements 17f. Impact can be mitigated. In this example, the load on the gap adjusting members 75k and 75m is only the stress caused by the elastic deflection. For this reason, the strength of the gap adjusting materials 75k and 75m may be determined in consideration of only this stress, and the gap adjusting materials 75k and 75m are highly durable. Other configurations and operations are the same as in the sixth example of the embodiment of the third aspect.
  • variable compression ratio device 89 is incorporated in the internal combustion engine (engine) 90, and can change the engine compression ratio by changing the top dead center position and the bottom dead center position of the piston 91.
  • the variable compression ratio device 89 of this example includes the link mechanism 92, the control shaft 93, the electric motor 94, the speed reduction mechanism 4b, and the reverse input cutoff clutch 5f described in the first example of the third embodiment. Prepare.
  • the link mechanism 92 is connected to a piston 91 disposed in the cylinder 95 of the internal combustion engine 90, and moves the piston 91 in the vertical direction, and includes an upper link 96, a lower link 97, and a control link 98.
  • the upper link 96 is connected to the piston 91 via the piston pin 99 and is connected to the lower link 97 via the first connection pin 100a.
  • the lower link 97 is rotatably attached to the crankpin 102 of the crankshaft 101, and is connected to the control link 98 via the second connecting pin 100b.
  • the control link 98 is supported by an eccentric shaft portion 103 provided on the control shaft 93.
  • the posture of the link mechanism 92 having such a configuration is changed by rotating the control shaft 93 to change the top dead center position and the bottom dead center position of the piston 91.
  • the number of the upper links 96, the lower links 97, and the control links 98 of the link mechanism 92 is the same as the number of the cylinders 95.
  • the control shaft 93 is arranged in parallel with the crankshaft 101 and is rotatably supported by a bearing (not shown).
  • the control shaft 93 is rotationally driven by the electric motor 94, and changes the top dead center position and the bottom dead center position of the piston 91 by changing the rotation phase thereof.
  • the speed reduction mechanism 4b and the reverse input cutoff clutch 5f are arranged between the electric motor 94 and the control shaft 93.
  • the speed reduction mechanism 4b is a high-efficiency parallel shaft gear reducer, and includes a plurality (eight in the illustrated example) of gears 104a to 104h that decelerate and output the rotation of the electric motor 94.
  • the speed reduction mechanism 4b includes a first gear 104a that is an input gear, a second gear 104b that is an intermediate gear, a third gear 104c, a fourth gear 104d, a fifth gear 104e, a sixth gear 104f, and A seventh gear 104g and an eighth gear 104h as an output gear are provided.
  • the first gear 104a to the seventh gear 104g are external gears having tooth portions on the outer peripheral surface
  • the eighth gear 104h is an internal gear having tooth portions on the inner peripheral surface.
  • the first gear 104a which is an input gear, is provided at the tip of the output shaft 105 of the electric motor 94.
  • the second gear 104 b and the third gear 104 c are provided on a first intermediate shaft 106 a that is disposed in parallel with the output shaft 105 of the electric motor 94.
  • the fourth gear 104d and the fifth gear 104e are provided on a second intermediate shaft 106b disposed coaxially with the output shaft 105 of the electric motor 94.
  • the sixth gear 104f and the seventh gear 104g are provided on a third intermediate shaft 106c disposed in parallel with the output shaft 105 of the electric motor 94.
  • the eighth gear 104 h is disposed coaxially with the output shaft 105 of the electric motor 94.
  • the reduction mechanism 4b meshes the first gear 104a and the second gear 104b, the third gear 104c and the fourth gear 104d, the fifth gear 104e and the sixth gear 104f, and the seventh gear 104g and the eighth gear 104h, respectively.
  • the rotational movement of the output shaft 105 of the electric motor 94 is decelerated in four stages.
  • the reduction mechanism 4b can have a large reduction ratio, the electric motor 94 used in combination with the reduction mechanism 4b can be reduced in size.
  • the reverse input cutoff clutch 5f is arranged between the speed reduction mechanism 4b connected to the electric motor 94 and the control shaft 93.
  • the basic configuration of the reverse input cut-off clutch 5f is the same as that of the first example of the third embodiment.
  • the input member 14b of the reverse input cutoff clutch 5f is fixed coaxially to the eighth gear 104h that is the output gear of the speed reduction mechanism 4b.
  • the input member 14b is arranged coaxially with the output shaft 105 of the electric motor 94, and rotates in synchronization with the eighth gear 104h.
  • the output member 15 d of the reverse input cutoff clutch 5 f is formed integrally with the control shaft 93.
  • An output engagement portion 26 b is provided at the base end portion of the control shaft 93.
  • the annular pressed member 16b of the reverse input cutoff clutch 5f is constrained from rotating via a support bracket 107 arranged around the periphery.
  • a pair of engaging elements 17d is provided so as to sandwich the output engaging portion 26b from both sides in the radial direction.
  • an input engagement portion 20b provided at a tip portion of the input member 14b is loosely inserted inside an engagement portion side input engagement portion 74 formed at a radial intermediate portion of each engagement portion 17d.
  • variable compression ratio device 89 of this example decelerates the rotation of the electric motor 94 by the speed reduction mechanism 4b and transmits it to the input member 14b of the reverse input cutoff clutch 5f. At this time, the output of the electric motor 94 is amplified by the speed reduction mechanism 4b.
  • the pair of engaging elements 17d are radially inward so as to approach each other based on the engagement between the engaging element side input engaging part 74 and the input engaging part 20b.
  • By moving and engaging the output engagement portion 26b and the pair of engagement element side output engagement portions 72 almost all of the rotational torque input to the input member 14b is transferred to the control shaft 93 (output member 15d). introduce.
  • the posture of the link mechanism 92 is changed to a posture corresponding to the rotational phase of the control shaft 93.
  • the rotational phase of the control shaft 93 can be finely controlled, and the attitude of the link mechanism 92 can be finely adjusted. it can.
  • variable compression ratio device 89 of this example when the rotational torque is reversely input from the control shaft 93 to the reverse input cutoff clutch 5f, only a part of the reversely input rotational torque is supplied to the input member 14b and the speed reduction mechanism 4b. To the electric motor 94, and the remainder is cut off. That is, the remainder of the rotational torque is consumed by sliding the pressing surface 29 against the pressed surface 28a. For this reason, energy consumption (electric energy) required for the electric motor 94 is reduced as compared with the case where the rotational torque reversely input from the control shaft 93 is held only by the electric motor 94 without providing the reverse input cutoff clutch 5f. can do. Therefore, the operating cost of the variable compression ratio device 89 can be reduced.
  • the reverse input cutoff clutch 5f incorporated in the variable compression ratio device 89 of this example, the backlash between the input member 14b and the output member 15d is suppressed to be small by the gap adjusting member 75 constituting the pressed member 16b. Yes.
  • the reverse input cut-off clutch 5 f can transmit the reversing operation in the rotation direction of the electric motor 94 to the control shaft 93 with high responsiveness. For this reason, the control of the rotation phase of the control shaft 93, that is, the control of changing the engine compression ratio can be performed with high responsiveness.
  • the speed reduction mechanism 4b is not limited to such a parallel shaft gear speed reducer.
  • various known structures such as a planetary gear reducer, a cycloid reducer, and a harmonic drive (registered trademark) reducer can be used. If there is a margin in the output torque (output power) of the electric motor 94, the speed reduction mechanism 4b may be omitted and the electric motor 94 and the reverse input cutoff clutch 5f may be directly connected.
  • the reverse input cutoff clutch 5p of the first example of the embodiment of the fourth aspect of the present invention is: A pressed member 16d having a pressed surface 28b; An input member 14c having a rotation center axis O and at least one input engagement portion 20c; An output member 15f having a rotation center axis O coaxial with the rotation center axis O of the input member 14c, and an output engaging portion 26d; At least one pressing surface 29 that opposes the pressed surface 28b, an engaging side input engaging portion 74 that engages with the input engaging portion 20c, and an engaging side output engagement that engages with the output engaging portion 26d. And at least one engaging member 17j having a portion 72.
  • the portion between the engaging member 17j and the pressed member 16d, the input engaging portion 20c and the engaging-side input engaging portion 74 are arranged.
  • An intermediate member is arranged in at least one of the intermediate portion and the intermediate portion between the output engagement portion 26d and the engagement element side output engagement portion 72.
  • a lubricant that lubricates the contact portion between the pressed surface 28b and the pressing surface 29, particularly traction oil or traction grease, is used as an intermediate member. It has been.
  • the reverse input cutoff clutch 5p of the first example of the embodiment of the fourth aspect will be described in detail.
  • the reverse input cutoff clutch 5p of this example is a lock type reverse input cutoff clutch, and includes an input member 14c, an output member 15f, a pressed member 16d, and a pair of engaging members 17j.
  • the input member 14c is connected to an input side mechanism such as an electric motor, and receives rotational torque. As shown in FIGS. 51 and 53, the input member 14c has an input shaft portion 66b and a pair of input engagement portions 20c.
  • the input shaft portion 66b has a stepped columnar shape, and its base end portion is connected to the output portion of the input side mechanism so as to be able to transmit torque, or is provided integrally with the output portion of the input side mechanism.
  • the pair of input engagement portions 20c are substantially elliptical cylinders, and are constituted by convex portions extending in the axial direction from two positions on the diametrically opposite side of the distal end surface of the input shaft portion 66b.
  • the input engagement portions 20c of the pair of input engagement portions 20c are separated from each other in the diameter direction of the input member 14c.
  • Each input engagement portion 20c is disposed at a portion of the distal end surface of the input shaft portion 66b that is radially outward from the rotation center axis O.
  • Each of the input engaging portions 20c has an outer surface in the radial direction that has the same cylindrical surface shape as the outer peripheral surface of the distal end portion of the input shaft portion 66b, and the inner surface in the radial direction has a circumferential direction.
  • the center part is comprised by the circular-arc-shaped convex surface which protruded to radial inside.
  • the output member 15f is connected to an output side mechanism such as a speed reduction mechanism, and outputs rotational torque.
  • the output member 15f is disposed coaxially with the input member 14c, and has an output shaft portion 67b and an output engagement portion 26d as shown in FIGS.
  • the output shaft portion 67b has a cylindrical shape, and a tip portion thereof is connected to the input portion of the output side mechanism so as to be able to transmit torque, or is provided integrally with the input portion of the output side mechanism.
  • the output engaging portion 26d has a cam function. For this reason, the distance from the rotation center axis
  • the output engagement portion 26d has a substantially long cylindrical shape and extends in the axial direction from the center portion of the base end surface of the output shaft portion 67b.
  • the outer peripheral surface of the output engaging portion 26d is composed of a pair of flat surfaces parallel to each other and a pair of arcuate convex surfaces. For this reason, the distance from the rotation center axis O of the output engagement portion 26d to the outer peripheral surface is not constant over the circumferential direction.
  • the output engagement portion 26d is disposed at a portion between the pair of input engagement portions 20c.
  • the pressed member 16d is formed in a thin annular shape, and is fixed to another member (not shown) such as a housing and its rotation is restricted.
  • the pressed member 16d is disposed coaxially with the input member 14c and the output member 15f and radially outside the input member 14c and the output member 15f.
  • the pair of input engagement portions 20c and the output engagement portion 26d are arranged on the radially inner side of the pressed member 16d in the assembled state of the reverse input cutoff clutch 5p.
  • the pressed member 16d has a pressed surface 28b which is a cylindrical concave surface on the inner peripheral surface thereof.
  • the pair of engaging elements 17j are formed in a substantially semicircular plate shape, and are arranged on the radially inner side of the pressed member 16d.
  • the radially outer surface pressed against the pressed surface 28b is a pressing surface 29 that is a cylindrical convex surface
  • the radially inner surface is The portion other than the portion where the engagement element side output engagement portion 72 is formed is constituted by a bottom surface 71 having a flat surface shape.
  • Both sides in the width direction of each engaging element 17j are constituted by flat side surfaces 73 perpendicular to the bottom surface 71.
  • the radial direction with respect to the engagement element 17j means a direction perpendicular to the bottom surface 71 indicated by an arrow A in FIG.
  • the radius of curvature of the pressing surface 29 is equal to or less than the radius of curvature of the pressed surface 28b.
  • the pressing surface 29 has a surface property having a large friction coefficient compared to the other portions of the engaging element 17j.
  • the pressing surface 29 can be configured directly by the surface of the engaging element 17j, or can be configured by a friction material fixed to the engaging element 17j by sticking or bonding.
  • the pressing surfaces 29 of the respective engaging members 17j are directed to the opposite side in the radial direction of the pressed member 16d, and the bottom surfaces 71 of the respective engaging members 17j are opposed to each other.
  • the inner diameter dimension of the pressed member 16d and the radial dimension of each engagement element 17j are restricted.
  • the engagement element 17j has an engagement element side input engagement part 74 and an engagement element side output engagement part 72.
  • the engagement element side input engagement portion 74 is configured by a through hole that is a rectangular long hole that penetrates the radial intermediate portion of the engagement element 17j in the axial direction and is long in the width direction.
  • the engagement element side input engagement portion 74 has a size capable of loosely inserting the input engagement portion 20c. Specifically, in a state where the input engagement portion 20 c of the input member 14 c is inserted inside the engagement element side input engagement portion 74, between the input engagement portion 20 c and the inner surface of the engagement element side input engagement portion 74. There are gaps in the width direction and the radial direction of the engaging element 17j.
  • the input engagement portion 20c can be displaced with respect to the rotation direction of the input member 14c with respect to the engagement member side input engagement portion 74 (engagement member 17j).
  • the engagement element 17j can be displaced in the radial direction with respect to the engagement part 20c.
  • the engagement element-side output engagement part 72 is configured by a substantially rectangular recess that is recessed radially outward from the center in the width direction of the bottom surface 71 of each of the pair of engagement elements 17j.
  • the engagement element side output engagement portion 72 has a size and a shape that allows the first half portion in the short axis direction of the output engagement portion 26d of the output member 15f to be disposed on the inner side without rattling.
  • the opening width of the engagement element side output engagement portion 72 is substantially the same as the dimension of the output engagement portion 26d in the major axis direction (same or slightly larger), and its radial direction.
  • the depth is slightly smaller than 1 ⁇ 2 of the dimension of the output engagement portion 26d in the minor axis direction.
  • the bottom portion of the engagement element side output engagement portion 72 is a flat surface parallel to the bottom surface 71.
  • the pair of input engagement portions 20c of the input member 14c disposed on one side in the axial direction is the engagement portion side input engagement portion of the pair of engagement members 17j.
  • the output engaging portion 26d of the output member 15f which is inserted in the axial direction 74 and disposed on the other axial side, is inserted between the pair of engaging member side output engaging portions 72 in the axial direction. That is, the pair of engaging elements 17j is arranged so that the output engaging part 26d is sandwiched from the radially outer side by the engaging element side output engaging part 72 of each engaging element 17j.
  • the axial dimension of the input engaging part 20c, the axial dimension of the output engaging part 26d, the axial dimension of the pressed member 16d, and the axial dimension of the engaging element 17j are substantially the same. .
  • traction oil or traction grease is used as a lubricant for the reverse input cutoff clutch 5p.
  • Traction grease is grease using traction oil as a base oil. Therefore, the mutual contact portions of the input member 14c, the output member 15e, the pressed member 16d, and the pair of engaging members 17j are contact portions through an oil film of traction oil.
  • a traction oil having a traction coefficient of 0.1 or more is preferably used, and examples thereof include naphthenic lubricating oil and paraffinic lubricating oil.
  • FIGS. 55 to 58 The operation and operation of the reverse input cut-off clutch 5p of this example are shown in FIGS. 55 to 58. Basically, the operation and operation of the reverse input cut-off clutch 5 in the first example of the embodiment of the first mode are shown. The description here is omitted.
  • traction oil or traction grease is used as a lubricant for the reverse input cutoff clutch 5p.
  • Traction oil base oil of traction grease
  • the viscosity when the contact pressure between the members (oil film pressure) is high is higher than that of normal lubricating oil. For this reason, when rotational torque is input to the input member 14c, the contact portion between the input engagement portion 20c and the engagement member side input engagement portion 74, and the engagement engagement portion side output engagement portion 72 with the output engagement.
  • a thick oil film of traction oil is formed at the contact portion with the portion 26d.
  • the friction coefficient ⁇ ′ between the pressing surface 29 and the pressed surface 28b when the output member 15f is locked or half-locked is a traction oil that is not easily affected by temperature or deterioration. Traction coefficient. Therefore, the switching operation between the locked or semi-locked state and the locked or semi-locked state can be performed more stably.
  • traction oil or traction grease is used as the lubricant, and therefore, compared with the case where normal lubricating oil is used as the lubricant, there is a difference between the pressing surface 29 and the pressed surface 28b.
  • the friction coefficient ⁇ ′ can be increased. Therefore, if the distance R is the same, a larger brake torque T ′ can be obtained than when ordinary lubricating oil is used as the lubricant.
  • the safety factor against slipping of the pressed surface 28b and the pressing surface 29a can be made larger than when ordinary lubricating oil is used as the lubricant.
  • the reverse input cut-off clutch 5p of this example can reduce the distance R necessary for obtaining the brake torque T 'having the same magnitude as that in the case of using ordinary lubricating oil as the lubricant.
  • the size can be reduced by 5p.
  • it is the same as that of the 1st example of embodiment of a 1st aspect, and the 1st example of embodiment of a 3rd aspect.
  • At least one of the pressed surface of the pressed member and the pressed surface of the engagement member is formed with a fine uneven shape (a number of fine grooves, dimples, etc.) (Texture processing section).
  • a fine uneven shape a number of fine grooves, dimples, etc.
  • the contact surface pressure between the pressed surface and the pressing surface can be increased.
  • a larger brake torque can be obtained by increasing the traction coefficient with the pressing surface.
  • the traction oil can be easily held in the concave portion of the concave and convex portion.
  • traction oil or traction grease is used as the lubricant, but the reverse input cutoff clutch of the present invention is implemented using a lubricant other than traction oil or traction grease, such as ordinary lubricating oil. Or can be carried out without using a lubricant.
  • the reverse input cutoff clutch of the fourth aspect can be used by being incorporated between an electric motor and a driven part driven by the electric motor, for example, in an actuator using an electric motor as a driving source.
  • the driven part can be driven with high efficiency by the electric motor
  • the electric motor is set by locking the reverse input cutoff clutch.
  • the position of the driven part can be held without requiring the power consumption. Therefore, an actuator with high efficiency and low power consumption can be realized.
  • the reverse input shut-off clutch of the present invention is used by being incorporated in a variable compression ratio device, an electric brake device, an electric door device, a steering device, etc., that change the piston process of an internal combustion engine of an automobile to make the engine compression ratio variable. Can do.
  • each of the engaging members 17k of the pair of engaging members 17k is a cylindrical guide recessed portion 79 that is recessed in both sides of the bottom surface 71a in the width direction in a direction perpendicular to the bottom surface 71a. (Not shown in FIG. 61). Then, in a state where the bottom surfaces 71a of the respective engagement elements 17k are opposed to each other, elastically so as to be bridged over the respective guide recesses 79 inside the two sets of guide recesses 79 existing on the same straight line.
  • a coil spring 80 (not shown in FIG. 61), which is a member, is disposed.
  • Each of the engagement elements 17k is biased toward the pressed surface 28b by the elastic force exerted by the pair of coiled springs 80. Thereby, the radial movement of each engagement element 17k can be accurately performed by stabilizing the posture of each engagement element 17k while synchronizing.
  • the radially inner side surface of the engagement element 17k is configured by a flat surface-like bottom surface 71a as a whole except for the location where the guide recess 79 is located, and the engagement element side output engagement part 72b is formed by a bottom surface. 71a is provided at the center in the width direction.
  • each engagement element 17k has a pressing surface 29a that is pressed against the pressed surface 28b at two positions spaced apart in the circumferential direction on the radially outer surface.
  • Each of the pressing surfaces 29a is a cylindrical convex surface having a curvature radius Cr ′ smaller than the curvature radius Cr of the pressed surface 28b.
  • each engagement element 17k is a flat front end surface that is not pressed against the pressed surface 28b at the circumferential intermediate portion that is a portion between the pair of pressing surfaces 29a among the radially outer surfaces. 111. That is, there is always a gap between the tip surface 111 and the pressed surface 28b.
  • the normal force P acting on M2 is expressed by the following equation (10).
  • P Fc / 2 (sin ⁇ + ⁇ ′ ⁇ cos ⁇ ) (10)
  • the magnitude of the brake torque T ′ is the friction coefficient ⁇ ′, the distance R (clutch size), the normal force Fc, and the wedge angle ⁇ . And is expressed by the following equation (17).
  • T ′ ⁇ ′RFc / (sin ⁇ + ⁇ ′ ⁇ cos ⁇ ) (17)
  • the friction coefficient ⁇ ′ is 0.1
  • the distance R is 15 mm
  • the wedge angle ⁇ is 25 degrees
  • the normal force Fc is 1000 N.
  • the brake torque T ′ obtained by the reverse input cutoff clutch 5p of the first example of the fourth embodiment is 1.5 Nm
  • the reverse input cutoff clutch 5q of this example is 2.9 Nm.
  • the reverse input cutoff clutch 5q of this example can obtain a brake torque T 'approximately twice as large as the reverse input cutoff clutch 5p by utilizing the wedge effect. That is, the reverse input cut-off clutch 5q of this example can be obtained even when the brake torque T 'having the same magnitude as the reverse input cut-off clutch 5p and the distance R is halved.
  • the reverse input cutoff clutch 5q of this example can obtain a larger brake torque T ′ than the structure of the first example of the fourth embodiment.
  • the brake torque T ′ is the same, the distance R can be made smaller than the structure of the first example of the embodiment of the fourth aspect, and the size can be reduced.
  • the 1st example of embodiment of a 4th aspect is the same as that of the 1st example of embodiment of a 4th aspect.
  • FIG. 62 A third example of the embodiment of the fourth aspect of the present invention will be described with reference to FIGS. 62 and 63.
  • FIG. 62 A third example of the embodiment of the fourth aspect of the present invention will be described with reference to FIGS. 62 and 63.
  • a convex portion 112 that protrudes outward in the radial direction as an intermediate member at the center in the circumferential direction of the radially outer portion of each of the engagement elements 17l as compared with the portion adjacent to both sides in the circumferential direction.
  • the radially outer surface of the convex 112 constitutes a pressing surface 29e that is pressed against the pressed surface 28b.
  • the pressing surface 29e is configured by a cylindrical convex surface having an arc shape when viewed from the axial direction. Therefore, in this example, the contact between the pressed surface 28b and the pressing surface 29e is a line contact.
  • the radius of curvature Cra of the pressing surface 29e is smaller than the radius of curvature of the pressing surface 29 of the structure of the first example (see FIG. 50) of the fourth embodiment.
  • the curvature radius Cra of the pressing surface 29e is 30% or less, preferably 20% or less, more preferably 10% or less of the curvature radius Cr of the pressed surface 28b.
  • a portion that is circumferentially removed from the convex portion 112 (pressing surface 29e) is configured by a cylindrical convex surface that is not pressed against the pressed surface 28b. Has been. That is, there is always a gap between the pressed surface 28b and the portion of the radially outer surface of each engagement element 17l that is deviated in the circumferential direction from the convex portion 112 (pressing surface 29e). Yes.
  • the convex portion 112 is arranged on a part (central portion) in the circumferential direction of the radially outer portion of each engagement element 17l, and the radially outer surface of the convex portion 112 is used as the pressing surface 29e, thereby pressing
  • the curvature radius Cra of the surface 29e is made sufficiently smaller than the curvature radius of the pressing surface 29 of the structure of the first example of the fourth embodiment. For this reason, in the structure of this example, compared with the structure of the 1st example of embodiment of the 4th aspect, the contact area of the to-be-pressed surface 28b and the pressing surface 29e can be made smaller.
  • the contact surface pressure between the pressed surface 28b and the pressing surface 29e when the rotational torque is reversely input to the output member 15f can be further increased.
  • the viscosity of the traction oil existing between the pressed surface 28b and the pressing surface 29e can be increased, and the friction coefficient (traction coefficient) ⁇ ′ between the pressed surface 28b and the pressing surface 29e can be increased. it can.
  • the brake torque T ′ larger than the structure of the first example of the embodiment of the fourth aspect can be obtained.
  • the distance R can be made smaller than the structure of the first example of the embodiment of the fourth aspect, and the size can be reduced.
  • the bus bar shape of the pressing surface which is the radially outer surface of the convex portion of each engaging element, is changed to a crowning shape such as a convex arc shape so that the pressing surface and the covered surface are covered.
  • traction oil or traction grease is used as the lubricant, but the reverse input cutoff clutch of this example is implemented using a lubricant other than traction oil or traction grease, such as ordinary lubricating oil. Or can be carried out without using a lubricant. Even in this case, it is possible to obtain an advantageous effect that it is only necessary to locally perform the finishing process or the heat treatment applied to each engagement element.
  • both the lubricant made of traction oil or traction grease and the convex 112 are provided as the intermediate member, but only the convex 112 can be provided as the intermediate member. Are also included within the scope of the present invention.
  • the circumferential position of the convex portion 112 arranged on the radially outer side of each engagement element 17l is one place in the circumferential center.
  • the circumferential position of the convex portion 112 formed on the radially outer side of each engagement element 17m is set at two locations separated in the circumferential direction.
  • the respective curvature radii Cra of the two pressing surfaces 29e separated in the circumferential direction are larger than the curvature radius Cr ′ of the pressing surface 29a of the structure of the second example of the fourth embodiment. And is sufficiently smaller than the radius of curvature Cr of the pressed surface 28b.
  • a larger brake torque T ′ is obtained compared to the structure of the second example of the embodiment of the fourth aspect.
  • the brake torque T ′ is the same, the distance R can be made smaller than the structure of the second example of the embodiment of the fourth aspect, and the size can be reduced.
  • Other configurations and operational effects are the same as those of the second and third examples of the fourth embodiment.
  • FIG. 65 A fifth example of the embodiment of the fourth aspect of the present invention will be described with reference to FIGS. 65 and 66.
  • FIG. 65 A fifth example of the embodiment of the fourth aspect of the present invention will be described with reference to FIGS. 65 and 66.
  • each of the engaging elements 17n includes an engaging element main body 110b having an engaging element side input engaging part 74 and an engaging element side output engaging part 72, and a pressing surface 29f as an intermediate member.
  • one roller 114 which is a pressing body having The engaging element body 110b has a holding recess 113 that opens radially outward at one place in the center in the circumferential direction of the radially outer part. The rollers 114 are held in the holding recess 113.
  • the holding recess 113 is a V-shaped groove (V groove) viewed from the axial direction, and is formed over the entire axial length of the radially outer portion of the engaging element main body 110b.
  • the roller 114 is the whole columnar shape, and the outer peripheral surface of the roller 114 comprises the cylindrical pressing surface 29f.
  • the radius of curvature of the pressing surface 29f is sufficiently smaller than the radius of curvature of the pressing surface 29 of the structure (see FIG. 50) of the first example of the fourth embodiment.
  • the diameter of the roller 114 (the diameter of the pressing surface 29f) is larger than the depth of the holding recess 113, and the axial dimension of the roller 114 is smaller than the axial dimension of the engagement body 110b.
  • the roller 114 In a state where the roller 114 is held in the holding recess 113, the roller 114 is arranged in the holding recess 113 only in the inner portion in the radial direction of the engagement body 110b, and the outer portion in the radial direction of the engagement body 110b in the holding recess 113. It is arranged outside 113.
  • the pressed member 16e has a guide groove 115 having a rectangular cross-sectional shape over the entire circumference on the inner peripheral surface of the intermediate portion in the axial direction.
  • the outer side portion of the roller 114 in the radial direction of the engagement body 110b is disposed in the guide groove 115.
  • the bottom surface of the guide groove 115 constitutes a pressed surface 28c having a cylindrical surface shape. Therefore, in this example, the contact between the pressed surface 28c and the pressing surface 29f is a line contact.
  • the pressing surface 29f made of the outer peripheral surface of the roller 114 is pressed against the pressed surface 28c that is the bottom surface of the guide groove 115. That is, the pressing surface 29f and the inner surface of the holding recess 113 are in strong contact via an oil film of traction oil, and the pressing surface 29f and the pressed surface 28c are in strong contact via an oil film of traction oil. As a result, the viscosity of these oil films increases, and a brake torque T ′ is generated at the contact portion between the pressing surface 29f and the pressed surface 28c.
  • the radius of curvature of the pressing surface 29f is sufficiently smaller than the radius of curvature of the pressing surface 29 of the structure of the first example of the fourth embodiment.
  • the contact area between the pressed surface 28c and the pressing surface 29f can be made smaller, and the pressed surface 28c and the pressing surface 29f The contact surface pressure can be made higher.
  • the viscosity of the traction oil existing between the pressed surface 28c and the pressing surface 29f is increased, and the friction coefficient (traction coefficient) ⁇ ′ between the pressed surface 28c and the pressing surface 29f can be increased. it can.
  • the distance R is the same, the brake torque T ′ larger than the structure of the first example of the embodiment of the fourth aspect can be obtained.
  • the distance R can be made smaller than the structure of the first example of the embodiment of the fourth aspect, and the size can be reduced.
  • rotational torque is input to the input member 14c, and when the input member 14c, the output member 15f, and the pair of engaging members 17n rotate in synchronism with the pressed member 16e, Even when a misalignment occurs between the pressing member 16e) and the rotation side (the input member 14c, the output member 15f, and the pair of engaging members 17n), the pressing of the outer peripheral surface of the roller 114 against the pressed surface 28c.
  • the rotation on the rotating side can be stabilized by bringing the surface 29f into rolling contact and / or sliding contact.
  • the internal gap of the reverse input cutoff clutch 5t when assembling the reverse input cutoff clutch 5t, by selecting the size of the roller 114, the internal gap of the reverse input cutoff clutch 5t can be adjusted, and the internal gap can be within an appropriate range.
  • each of the engaging members 17n is divided into two parts including the engaging member main body 110b and 114, and the outer peripheral surface of the roller 114 forms a pressing surface 29f. For this reason, it is not necessary to perform finishing or heat treatment on the radially outer portion of the engagement body 110b. Therefore, the manufacturing cost can be suppressed.
  • the engagement element 17n is constituted by the engagement element main body 110b and the roller 114.
  • the engagement element main body 110b may be interpreted as an engagement element
  • the roller 114 may be interpreted as an intermediate member. Is possible.
  • both the lubricant made of traction oil or traction grease and the roller 114 are provided as the intermediate member, but only the pressing body made of the roller 114 can be provided as the intermediate member, This configuration is also included in the scope of the present invention.
  • rollers 114 for example, mass-produced products for bearings (hardness HRC 61 to 67) can be used. Specifically, cylindrical rollers having a diameter of 3 mm to 40 mm and an axial length of 3 mm to 65 mm, and a diameter of 5. A rod-shaped roller having a length of 5 mm to 15 mm and an axial length of 18 mm to 90 mm, a needle roller having a diameter of 1 mm to 5 mm, and an axial length of 5.8 mm to 49.8 mm can be used.
  • the size of the roller 114 is determined in consideration of the relationship with the size of surrounding members. Other configurations and operational effects are the same as those of the first example of the fourth embodiment.
  • the circumferential position of the holding recess 113 holding the roller 114 in the radially outer part of the engaging body 110b constituting the engaging 17n. Is one place in the center in the circumferential direction.
  • the circumferential position of the holding recess 113 holding the roller 114 among the radially outer portions of the engaging body 110c constituting each engaging member 17o is Two locations separated in the direction.
  • the pressing surface 29f which is the outer peripheral surface of the two rollers 114 separated in the circumferential direction, is pressed against the pressed surface 28c.
  • the radius of curvature of the pressing surface 29f that is the outer peripheral surface of the roller 114 is smaller than the radius of curvature Cr ′ of the pressing surface 29a of the structure of the second example of the fourth embodiment.
  • a larger brake torque T ′ is obtained compared to the structure of the second example of the embodiment of the fourth aspect.
  • the brake torque T ′ is the same, the distance R can be made smaller than the structure of the second example of the embodiment of the fourth aspect, and the size can be reduced.
  • Other configurations and operational effects are the same as those of the second and fifth examples of the fourth embodiment.
  • the rollers 114 are used as the pressing bodies constituting the respective engagement elements 17n and 17o.
  • the balls 116 are used as the pressing bodies that constitute the respective engagement elements 17p.
  • the surface of the ball 116 constitutes a pressing surface 29g.
  • the cross-sectional shape of the pressed surface 28d which is the inner surface of the guide groove 115a formed on the inner peripheral surface of the pressed member 16f, is a circle whose curvature radius is larger than the curvature radius of the pressing surface 29g, which is the surface of the ball 116. It has an arc shape.
  • the contact between the pressing surface 29g, which is the surface of the ball 116, the inner surface of the holding recess 113, and the pressed surface 28d is a point contact, so that the contact area between these surfaces is further increased.
  • the contact surface pressure between these surfaces can be further increased. Therefore, the friction coefficient (traction coefficient) ⁇ ′ between these surfaces can be further increased.
  • the distance R is the same, it is possible to obtain a larger brake torque T ′ than the structures of the fifth example and the sixth example of the fourth embodiment. In other words, if the brake torque T ′ is the same, the distance R can be made smaller than the structures of the fifth example and the sixth example of the embodiment of the fourth aspect, and the size can be reduced.
  • the balls 116 for example, mass-produced products for bearings (hardness HRC of about 61 to 67, diameter of 0.3 mm to 101.6 mm) can be used. However, the size of the ball 116 is determined in consideration of the relationship with the size of surrounding members. Other configurations and operational effects are the same as those of the fifth and sixth examples of the fourth embodiment.
  • the holding recess for holding the roller 114 is not limited to the V groove, but an R groove, a circular arc groove, a gothic arc groove having an arc shape when viewed from the axial direction.
  • Various shapes of grooves such as can be employed. If an R groove, a circular arc groove, or a Gothic arc groove is used as the holding recess, the contact surface pressure with the inner surface 114 of the holding recess or the outer peripheral surface of 114 (or the surface of the ball 116) can be reduced, thereby suppressing wear. Can do.
  • the impact resistance performance with the inner surface 114 of the holding recess and the outer peripheral surface (or the surface of the ball 116) can be improved.
  • Such impact resistance performance is higher for gothic arc grooves than for circular arc grooves.
  • the holding recess for holding the roller 114 may be closed without opening both ends in the axial direction.
  • the rollers 114 (or balls 116) can be prevented from coming out of the holding recess in the axial direction, so that the guide groove formed on the inner peripheral surface of the pressed member can be omitted.
  • both axial ends of the holding recess holding the roller 114 (or ball 116) are opened in the axial direction, for example, by a member disposed adjacent to the holding recess in the axial direction, when it is possible to prevent the roller 114 (or the ball 116) from coming out of the holding recess in the axial direction, the guide groove formed on the inner peripheral surface of the pressed member can be omitted.
  • the holding recess 113a of the engaging element main body 110c constituting each engaging element 17q has a single arc shape and a C-shaped R groove as viewed from the axial direction. .
  • both axial end portions of the holding recess 113a are open in the axial direction.
  • a part of the roller 114 (or the ball 116) that is more than half of the roller 114 (or the ball 116) is disposed inside the holding recess 113a.
  • the opening width on the outer side in the radial direction of the holding recess 113a is made smaller than the diameter of the roller 114 (or the ball 116).
  • the roller 114 (or the ball 116) can be inserted into the holding recess 113a from the opening in the axial direction of the holding recess 113a.
  • the diameter of the roller 114 (or the ball 116) is slightly smaller than the inner diameter of the holding recess 113a, so that the pressing surface 29f (29g) formed by the outer peripheral surface of the roller 114 (or the surface of the ball 116). And a gap is provided between the inner surface of the holding recess 113a.
  • the bus bar shape of the pressing surface 29h provided on the side surface is a convex arc shape that is a crowning shape.
  • a protrusion 117 as an intermediate member is provided over the entire circumference in the axially intermediate portion of the inner peripheral surface of the pressed member 16g, and the pressed surface is pressed on the radially inner side surface of the protrusion 117.
  • a surface 28e is provided.
  • the pressed surface 28e is a convex surface having a circular cross section.
  • the pressed surface 28e and the pressed surface 29h when the rotational torque is reversely input to the output member 15f can be point contact, the pressed surface It is possible to obtain a larger brake torque T ′ by increasing the contact surface pressure between 28e and the pressing surface 29h.
  • Other configurations and operational effects are the same as those of the first example of the fourth embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Transmission Devices (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Mechanical Operated Clutches (AREA)
PCT/JP2019/018027 2018-05-07 2019-04-26 逆入力遮断クラッチ及びアクチュエータ Ceased WO2019216280A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2020518282A JP7380552B2 (ja) 2018-05-07 2019-04-26 逆入力遮断クラッチ及びアクチュエータ
CN201980031049.4A CN112189100B (zh) 2018-05-07 2019-04-26 逆向输入断开离合器以及促动器
EP19799519.4A EP3792516B1 (en) 2018-05-07 2019-04-26 Reverse input blocking clutch and actuator
US17/053,902 US11428278B2 (en) 2018-05-07 2019-04-26 Reverse input blocking clutch and actuator

Applications Claiming Priority (8)

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JP2018-089021 2018-05-07
JP2018089021 2018-05-07
JP2018-111199 2018-06-11
JP2018111199 2018-06-11
JP2018151015 2018-08-10
JP2018-151015 2018-08-10
JP2019008976 2019-01-23
JP2019-008976 2019-01-23

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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021107073A1 (ja) * 2019-11-29 2021-06-03 日本精工株式会社 逆入力遮断クラッチ
WO2021152980A1 (ja) * 2020-01-29 2021-08-05 日本精工株式会社 逆入力遮断クラッチ
JP2021153570A (ja) * 2019-12-17 2021-10-07 東都興業株式会社 回転伝達装置
JP2022026971A (ja) * 2020-07-31 2022-02-10 株式会社アイシン 逆入力遮断動力伝達装置
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WO2023085395A1 (ja) * 2021-11-15 2023-05-19 日本精工株式会社 逆入力遮断クラッチ
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JP7375989B1 (ja) * 2022-05-30 2023-11-08 日本精工株式会社 逆入力遮断クラッチ
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JP7509335B1 (ja) * 2023-05-29 2024-07-02 日本精工株式会社 逆入力遮断クラッチ
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Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2359010A (en) * 1942-05-04 1944-09-26 Skardon T Smith Multiple bar shaft lock
US3051282A (en) * 1959-12-15 1962-08-28 Whitney E Greene Self-locking rotary transmission
US3261437A (en) * 1964-07-27 1966-07-19 Carl H Kramm Overrunning clutch
US3435706A (en) * 1966-12-08 1969-04-01 Usm Corp Torque reactive wave generators
JPH03249435A (ja) * 1990-02-28 1991-11-07 Ntn Corp クラッチ
JP2004084918A (ja) 2002-02-20 2004-03-18 Nsk Ltd リニアアクチュエータ
JP2004144124A (ja) 2002-10-22 2004-05-20 Nsk Ltd アクチュエータ
JP2004182063A (ja) * 2002-12-03 2004-07-02 Ntn Corp 車輪操舵装置
JP2007232095A (ja) 2006-03-01 2007-09-13 Ntn Corp 逆入力防止クラッチ
JP2008075804A (ja) * 2006-09-22 2008-04-03 Nsk Ltd 遊星ローラねじ装置
JP2009108889A (ja) * 2007-10-26 2009-05-21 Origin Electric Co Ltd 双方向クラッチ
JP2011027252A (ja) * 2009-06-23 2011-02-10 Asmo Co Ltd クラッチ及びモータ
WO2013058278A1 (ja) * 2011-10-21 2013-04-25 株式会社ユニバンス ローラクラッチ装置
JP2013148118A (ja) * 2012-01-17 2013-08-01 Mitsuba Corp 逆転防止機構
JP2017020612A (ja) * 2015-07-14 2017-01-26 Ntn株式会社 逆入力遮断クラッチ
JP2017214943A (ja) * 2016-05-30 2017-12-07 Ntn株式会社 逆入力防止クラッチ

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1617745A (en) * 1927-02-15 Albert cotysinard
US1575038A (en) * 1924-11-07 1926-03-02 Clas Angelo Robert Window regulator
JPS6298018A (ja) * 1985-10-21 1987-05-07 Ikeda Bussan Co Ltd ロツク機構
JPH09303427A (ja) * 1996-05-09 1997-11-25 Ntn Corp ２ウェイクラッチユニット
JP3941512B2 (ja) * 2002-01-11 2007-07-04 日本精工株式会社 クラッチ機構付リニアアクチュエータ
JP5185209B2 (ja) * 2009-06-09 2013-04-17 オリジン電気株式会社 逆入力遮断クラッチ
JP2011089570A (ja) * 2009-10-21 2011-05-06 Ntn Corp 逆入力遮断クラッチ
CN103174774B (zh) * 2013-03-29 2016-04-27 合肥双擎动力科技有限公司 使用离心超越离合器的自动变速系统
JP2017040288A (ja) * 2015-08-18 2017-02-23 Ntn株式会社 逆入力遮断クラッチ
JP6583075B2 (ja) 2016-03-17 2019-10-02 株式会社デンソー クラッチ、モータ及びパワーウインド装置
CN107923491A (zh) * 2016-07-25 2018-04-17 马渊马达株式会社 防止逆转机构和带减速机的电机
CN110998119A (zh) * 2017-08-01 2020-04-10 日本精工株式会社 逆向输入断开离合器、电动配气正时调整装置、可变压缩比装置及电动助力转向装置

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2359010A (en) * 1942-05-04 1944-09-26 Skardon T Smith Multiple bar shaft lock
US3051282A (en) * 1959-12-15 1962-08-28 Whitney E Greene Self-locking rotary transmission
US3261437A (en) * 1964-07-27 1966-07-19 Carl H Kramm Overrunning clutch
US3435706A (en) * 1966-12-08 1969-04-01 Usm Corp Torque reactive wave generators
JPH03249435A (ja) * 1990-02-28 1991-11-07 Ntn Corp クラッチ
JP2004084918A (ja) 2002-02-20 2004-03-18 Nsk Ltd リニアアクチュエータ
JP2004144124A (ja) 2002-10-22 2004-05-20 Nsk Ltd アクチュエータ
JP2004182063A (ja) * 2002-12-03 2004-07-02 Ntn Corp 車輪操舵装置
JP2007232095A (ja) 2006-03-01 2007-09-13 Ntn Corp 逆入力防止クラッチ
JP2008075804A (ja) * 2006-09-22 2008-04-03 Nsk Ltd 遊星ローラねじ装置
JP2009108889A (ja) * 2007-10-26 2009-05-21 Origin Electric Co Ltd 双方向クラッチ
JP2011027252A (ja) * 2009-06-23 2011-02-10 Asmo Co Ltd クラッチ及びモータ
WO2013058278A1 (ja) * 2011-10-21 2013-04-25 株式会社ユニバンス ローラクラッチ装置
JP2013148118A (ja) * 2012-01-17 2013-08-01 Mitsuba Corp 逆転防止機構
JP2017020612A (ja) * 2015-07-14 2017-01-26 Ntn株式会社 逆入力遮断クラッチ
JP2017214943A (ja) * 2016-05-30 2017-12-07 Ntn株式会社 逆入力防止クラッチ

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021107073A1 (ja) * 2019-11-29 2021-06-03 日本精工株式会社 逆入力遮断クラッチ
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US11708870B2 (en) 2019-11-29 2023-07-25 Nsk, Ltd. Reverse-input blocking clutch
CN113748271B (zh) * 2019-11-29 2023-02-17 日本精工株式会社 反向输入切断离合器
EP4006371A4 (en) * 2019-11-29 2022-08-24 NSK Ltd. REVERSE ENTRY LOCKING CLUTCH
JP7591208B2 (ja) 2019-12-17 2024-11-28 東都興業株式会社 回転伝達装置
JP2021153570A (ja) * 2019-12-17 2021-10-07 東都興業株式会社 回転伝達装置
JP2024138013A (ja) * 2019-12-17 2024-10-07 東都興業株式会社 回転伝達装置
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US11506249B2 (en) 2020-01-29 2022-11-22 Nsk Ltd. Reverse input cutoff clutch
WO2021152980A1 (ja) * 2020-01-29 2021-08-05 日本精工株式会社 逆入力遮断クラッチ
JP6962510B1 (ja) * 2020-01-29 2021-11-05 日本精工株式会社 逆入力遮断クラッチ
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US12049931B2 (en) 2021-02-08 2024-07-30 Nsk Ltd. Reverse-input blocking clutch
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KR102869129B1 (ko) 2021-02-08 2025-10-14 닛본 세이고 가부시끼가이샤 역입력 차단 클러치
WO2022168466A1 (ja) * 2021-02-08 2022-08-11 日本精工株式会社 逆入力遮断クラッチ
JPWO2022168466A1 (https=) * 2021-02-08 2022-08-11
US11920644B2 (en) 2021-11-15 2024-03-05 Nsk Ltd. Reverse input cut-off clutch
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WO2023136149A1 (ja) * 2022-01-14 2023-07-20 日本精工株式会社 逆入力遮断クラッチおよびその組立方法
JP7375991B1 (ja) * 2022-01-14 2023-11-08 日本精工株式会社 逆入力遮断クラッチおよびその組立方法
US12259015B2 (en) 2022-01-14 2025-03-25 Nsk Ltd. Reverse-input blocking clutch and manufacturing method thereof
US11879508B2 (en) 2022-03-15 2024-01-23 Hyundai Motor Company Clutch for preventing backdrive
JP2024102289A (ja) * 2022-04-04 2024-07-30 日本精工株式会社 逆入力遮断クラッチ
WO2023233801A1 (ja) * 2022-05-30 2023-12-07 日本精工株式会社 逆入力遮断クラッチ
JP7375989B1 (ja) * 2022-05-30 2023-11-08 日本精工株式会社 逆入力遮断クラッチ
JP7509335B1 (ja) * 2023-05-29 2024-07-02 日本精工株式会社 逆入力遮断クラッチ
WO2024247372A1 (ja) * 2023-05-29 2024-12-05 日本精工株式会社 逆入力遮断クラッチ
WO2025243407A1 (ja) * 2024-05-21 2025-11-27 株式会社ジェイテクト ボールねじ装置
WO2025249035A1 (ja) * 2024-05-29 2025-12-04 Ntn株式会社 逆入力遮断クラッチ
WO2026053731A1 (ja) * 2024-09-05 2026-03-12 日本精工株式会社 逆入力遮断クラッチ

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US11428278B2 (en) 2022-08-30
US20210277964A1 (en) 2021-09-09
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JPWO2019216280A1 (ja) 2021-05-13
CN112189100A (zh) 2021-01-05
CN112189100B (zh) 2022-09-13
EP3792516A4 (en) 2021-12-22
JP7380552B2 (ja) 2023-11-15

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