WO2017188265A1 - Embrayage à prévention d'entrée inverse - Google Patents

Embrayage à prévention d'entrée inverse Download PDF

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Publication number
WO2017188265A1
WO2017188265A1 PCT/JP2017/016414 JP2017016414W WO2017188265A1 WO 2017188265 A1 WO2017188265 A1 WO 2017188265A1 JP 2017016414 W JP2017016414 W JP 2017016414W WO 2017188265 A1 WO2017188265 A1 WO 2017188265A1
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WO
WIPO (PCT)
Prior art keywords
side member
output side
clutch
reverse input
lubricating oil
Prior art date
Application number
PCT/JP2017/016414
Other languages
English (en)
Japanese (ja)
Inventor
糸見　正二
高田　声一
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2016090586A external-priority patent/JP2017198301A/ja
Priority claimed from JP2016097730A external-priority patent/JP2017207082A/ja
Priority claimed from JP2016101285A external-priority patent/JP2017207172A/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2017188265A1 publication Critical patent/WO2017188265A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • 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
    • F16D41/10—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action with self-actuated reversing
    • 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
    • F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
    • 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
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake

Definitions

  • the present invention relates to a reverse input prevention clutch that transmits rotation of an input side member to an output side member when input torque is applied and prevents the input side member from rotating in response to reverse input torque.
  • the reverse input prevention clutch transmits its rotation to the output side member when input torque is applied to the input side member, and prevents the input side member from rotating when reverse input torque is applied to the output side member. It is to make.
  • this reverse input prevention clutch there is a type of locking the output side member against the reverse input torque (hereinafter, this type is referred to as “lock type”) (for example, see Patent Document 1 below).
  • the lock-type reverse input prevention clutch described in Patent Document 1 is configured such that the input side member rotates with a slight angle delay between the input side member and the output side member that rotate about the same axis.
  • Torque transmission means for transmitting to the member is provided, a fixing member is arranged on the radially outer side of the output side member, a plurality of cam surfaces are provided on the outer peripheral surface of the output side member, and the inner peripheral cylindrical surface of the fixing member and the output side member
  • a wedge-shaped space that gradually narrows in the circumferential direction is formed between the cam surfaces of each of the cam surfaces, and a pair of rollers that serve as lock engaging members and springs that push the rollers into the narrow portion of the wedge-shaped space are incorporated in each wedge-shaped space.
  • pillar portions of the cage that rotate integrally with the input side member are inserted.
  • each roller is pushed into the narrow part of the wedge-shaped space by the elasticity of the spring. Therefore, even if reverse input torque is applied to the output side member, the roller on the rear side in the rotational direction is fixed to the fixed member and the output. By engaging with the side member, the output side member is locked with the fixed member, and rotation is not transmitted to the input side member.
  • both axial ends of the annular space between the outer peripheral surface of the output side member and the inner peripheral surface of the fixing member are covered with the fixing member, and the inner side of the fixing member Lubricant such as grease is enclosed in (inside the clutch) to lubricate between the roller and the inner peripheral cylindrical surface of the fixed member and the cam surface of the output side member. It is inevitable that when the rotation is transmitted from the input side member to the output side member, it gradually leaks out of the clutch and gradually decreases.
  • an object of the present invention is to prevent poor lubrication in a lock-type reverse input prevention clutch used in a lubricating oil immersion environment by replacing the lubricating oil inside and outside the clutch.
  • the present invention provides an input side member and an output side member that are arranged in a state of rotating around the same axis, and a fixing member that is arranged on the radially outer side of the output side member. And a plurality of lock engaging members arranged between the outer peripheral surface of the output side member and the inner peripheral surface of the fixing member with respect to the reverse input torque applied to the output side member.
  • an inflow port through which the lubricating oil flows from the outside to the inside of the fixed member, and the lubricating oil from the inside to the outside of the fixed member at a radially outer side than the inflow port And a path through which the lubricating oil flowing from the inlet to the inside of the fixing member reaches the outlet through the annular space is adopted.
  • the lubricating oil inside the clutch flows out from the outlet to the outside of the clutch due to the centrifugal force acting with the rotation of the output side member. Since the lubricant flows into the clutch and the lubricant is exchanged between the inside and outside of the clutch, it is difficult for the lubricant inside the clutch to deteriorate early and the temperature to rise, preventing poor lubrication and problems caused by it for a longer period of time than before. Can do.
  • the bearing may be provided with the inlet.
  • the bearing is a sintered bearing
  • the sintered bearing is configured so that the inflow port penetrates in the axial direction.
  • the bearing is a rolling bearing without a seal structure
  • the space between the rolling elements adjacent in the circumferential direction of the rolling bearing can be configured as the inflow port.
  • a radial groove is provided in the output side member to guide the lubricating oil from a position facing the inflow port in the axial direction to the annular space. It is good to have the structure which is made. And when the radial direction groove
  • the reverse input prevention clutch according to the present invention is provided with a lubricating oil inlet and outlet, and a path from the inlet to the outlet through the annular space inside the clutch. Since the lubricating oil is exchanged between the inside and outside of the cylinder, even when operating under high speed rotation and high torque conditions, lubrication failure inside the clutch is unlikely to occur and lubrication failure due to temperature rise is unlikely to occur. Can be used stably for a long time.
  • FIG. 1 Vertical front view of reverse input prevention clutch of embodiment
  • FIG. 16 is a longitudinal front view of the main part showing a first modification of the reverse input prevention clutch of FIG. 20 is an external perspective view of the spring of FIG.
  • FIG. 16 is a longitudinal front view of the main part showing a second modification of the reverse input preventing clutch of FIG. 22 is an external perspective view of the spring of FIG.
  • the reverse input prevention clutch includes an input shaft 1 as an input side member, an output side member 4 in which an output shaft 2 and an inner ring 3 are integrally formed, and a radially outer side of the inner ring 3.
  • the retainer 8, the roller (lock engagement element) 9 and the coil spring 10 incorporated between the inner ring 3 and the outer ring 5, and the inner periphery of the small diameter portion at the other end of the housing 6 are rotatably supported.
  • the sintered bearing 11 is used in a lubricating oil immersion environment.
  • the coil spring 10 can be replaced with another elastic member such as a leaf spring.
  • the housing 6 is formed with a plurality of notches 6a on the outer peripheral edge of the flange at one end, and a claw 7a formed on the outer peripheral edge of the presser lid 7 is fitted into these notches 6a and bent. It is integrated with the lid 7.
  • the presser lid 7 is provided with attachment holes 7b in three tongue-shaped projecting portions projecting from the outer periphery thereof.
  • the housing 6 and the presser lid 7 serve as a fixing member 12 that is integrally fixed to an external member (not shown) through an attachment hole 7 b of the presser lid 7.
  • the input shaft 1 includes an engaging portion 1a having a two-sided width (two engaging surfaces parallel to the shaft center and parallel to each other) on the outer periphery, and a small-diameter cylindrical portion 1b protruding from an end surface of the engaging portion 1a.
  • the distal end portion of the engaging portion 1a is inserted into an engaging hole 3a provided in the center of the inner ring 3, and the small diameter cylindrical portion 1b is output from the bottom of the engaging hole 3a of the inner ring 3 to the output shaft.
  • 2 is fitted in the circular hole 2a and rotates around the same axis as the output side member 4 (the output shaft 2 and the inner ring 3).
  • the engagement hole 3a of the inner ring 3 has a cross section substantially the same shape as the engagement portion 1a of the input shaft 1, and a slight rotational clearance is generated when the engagement portion 1a of the input shaft 1 is inserted.
  • torque transmitting means is configured to transmit the input torque applied to the input shaft 1 to the output side member 4 with a slight angular delay.
  • the cylindrical portion 8b of the cage 8 is fitted into the axially central portion of the engaging portion 1a of the input shaft 1 so that the input shaft 1 and the cage 8 rotate integrally.
  • An input torque is applied to the input shaft 1 from a drive source (not shown) such as a motor, and the output shaft 2 is a rotation transmission member (such as an output gear) attached to an engaging portion 2b having a two-sided width formed on the outer periphery. Torque is output in the illustration (not shown).
  • the inner circumference of the outer ring 5 is a cylindrical surface, and a plurality of cam surfaces 3 b are provided in the circumferential direction on the outer circumference of the inner ring 3, and between the inner circumferential cylindrical surface of the outer ring 5 and each cam surface 3 b of the inner ring 3.
  • a wedge-shaped space 13 that is gradually narrowed on both sides in the circumferential direction is formed.
  • a pair of rollers 9 is incorporated in each wedge-shaped space 13, and the coil spring 10 is assembled so as to be sandwiched between the pair of rollers 9, and each roller 9 is pushed into a narrow portion of the wedge-shaped space 13. Yes.
  • a locking means is configured to lock the inner ring 3 that is a part of the output side member 4 and the outer ring 5 that is a part of the fixing member 12 against the reverse input torque applied to the output side member 4. .
  • the fixing member 12 (housing 6 and presser lid 7) covers both axial ends of an annular space (including the wedge-shaped space 13) between the outer peripheral surface of the inner ring 3 and the inner peripheral surface of the outer ring 5.
  • Lubricating oil flows from the outside of the fixed member 12 to the inside (from the outside of the clutch to the inside of the clutch) on the outer circumferential surface of the sintered bearing 11 fitted to the inner circumference of the small diameter portion, penetrating in the axial direction with a semicircular cross section.
  • a plurality of inflow ports 11a are provided in the circumferential direction, and the lubricating oil flows out from the inside of the clutch to the outside of the clutch at a position facing the annular space on the presser lid 7 radially outside the inflow port 11a of the sintered bearing 11.
  • a plurality of outlets 7c are provided in the circumferential direction.
  • a radial groove 3c is provided on one end face of the inner ring 3 to guide the lubricating oil from a position facing each inlet 11a of the sintered bearing 11 in the axial direction to a position of the wedge-shaped space 13 in the annular space.
  • a path is formed in which the lubricating oil flowing into the clutch from each inlet 11a reaches the outlet 7c via the annular space.
  • the lubricating oil immersed in the entire clutch also enters the inside of the clutch, and lubrication is performed between the roller 9 and the inner peripheral cylindrical surface of the outer ring 5 and the cam surface 3b of the inner ring 3. .
  • This reverse input prevention clutch has the above-described configuration, and each roller 9 is pushed into the narrow portion of the wedge-shaped space 13 by the elasticity of the coil spring 10, so that even if reverse input torque is applied to the output side member 4,
  • the output side member 4 is locked to the fixing member 12 by engaging the roller 9 on the rear side in the rotation direction with the outer ring 5 which is a part of the fixing member 12 and the inner ring 3 which is a part of the output side member 4. No rotation is transmitted to 1.
  • each outlet 7c of the presser lid 7 is caused by the centrifugal force in which the lubricating oil inside the clutch acts as the inner ring 3 rotates.
  • the lubricating oil outside the clutch flows into the clutch from each inlet 11a of the sintered bearing 11, and the lubricating oil flowing from the inlet 11a is guided to the radial groove 3c of the inner ring 3.
  • the position of the wedge-shaped space 13 in the annular space between the inner and outer rings 3 and 5 is reached.
  • FIGS. 4 and 5 show modifications in which the position of the lubricant outlet is changed.
  • the outlet 7c of the presser lid 7 of the embodiment shown in FIGS. 1 to 3 is eliminated, and instead of the plurality of notches 6a formed on the flange at one end of the housing 6, the presser lid 7 and A lubricant oil outlet 6b is formed by forming what is not used for the integration (not fitted with the claw 7a) so as to enter one end of the outer ring 5 formed integrally with the housing 6.
  • the lubricating oil inside the clutch easily flows out of the clutch due to centrifugal force, and the lubricating oil inside and outside the clutch can be replaced more smoothly.
  • FIG. 6 shows a modification in which a circumferential groove 3d is provided between the radial grooves 3c of the inner ring 3 of the embodiment shown in FIGS. If it does in this way, it will become easy for the lubricating oil which flowed into the inside of a clutch from each inflow port 11a of the sintered bearing 11 to flow into the said annular space, and the exchange of the lubricating oil inside and outside a clutch will become smoother.
  • the radial groove 3c of the inner ring 3 is formed so as to open at a position facing the wedge-shaped space 13 between the inner and outer rings 3, 5, but the example of FIG. As in the modification shown in FIG. 7, the opening can be made at a position facing the column portion 8 a of the cage 8. Moreover, it replaces with the sintered bearing 11 which has the inlet 11a of an Example and each modification, uses the rolling bearing which does not have a seal structure, and makes the space between the rolling elements adjacent in the circumferential direction into an inlet. You can also.
  • unlocking means is not limited to the cage that rotates integrally with the input side member as in the above-described embodiments and modifications, but when input torque is applied to the input side member, Can be pushed out to the wide part of the wedge-shaped space against the elasticity of an elastic member such as a coil spring.
  • this invention is a lock type thing other than the reverse input prevention clutch which used the roller as a lock engagement element like embodiment, for example, between the outer peripheral cylindrical surface of an inner ring, and the inner peripheral cylindrical surface of a fixing member,
  • the present invention can also be applied to a reverse input prevention clutch in which a sprag as a lock engagement element is arranged to constitute a lock means.
  • the output side member rotates and outputs.
  • the rollers and springs arranged on the radially outer side of the cam surface of the side member also rotate, and torque loss occurs due to friction between the rollers and the fixed member.
  • torque loss it is effective to reduce the elasticity of the spring that presses the roller.
  • the spring that receives centrifugal force during rotation transmission is radially outward. To the inner peripheral cylindrical surface of the fixing member. In particular, when the engine is operated at a high speed, the centrifugal force acting on the spring increases, and the spring easily moves radially outward.
  • the output side member will not be locked with the fixed member when reverse input torque is applied, and the output side member There is a possibility that rotation is transmitted to the input side member. Further, if the spring continues to rotate while being in contact with the inner peripheral cylindrical surface of the fixing member when the input torque is applied, problems such as wear and breakage of the spring occur.
  • the spring that normally pushes the roller into the narrow portion of the wedge-shaped space contacts the roller at two axial positions in the case of a coil spring, and in the case of a leaf spring, the roller. Since the rollers are in line contact with each other in the axial direction, when the output side member locks against the fixed member against the reverse input torque, the rollers are always in the same posture (the posture in which the axial direction of the rollers and the output side member substantially coincides). It will engage with the same position of the cam surface of the output side member. For this reason, by repeatedly locking the output side member and releasing the locked state during use, wear and fatigue of the engagement position of the output side member with the roller are likely to proceed faster than other parts.
  • FIGS. 8 and 9 show a reverse input prevention clutch incorporating a single spring 14 formed integrally as described later, instead of the plurality of coil springs 10 of the reverse input prevention clutch shown in FIGS. 1 and 2 described above. Indicates.
  • this reverse input prevention clutch an input shaft 1 as an input side member, an output side member 4 in which an output shaft 2 and an inner ring 3 are integrally formed, and an outer ring 5 disposed on the radially outer side of the inner ring 3 are integrally formed.
  • a sintered bearing 11 to be configured.
  • the members other than the spring 14 are not provided with the inlet 11a of the sintered bearing 11, the outlet 7c of the presser lid 7 and the radial groove 3c of the inner ring 3 for replacing the lubricating oil inside and outside the clutch. Is the same as that shown in FIG. 1 and FIG.
  • the spring 14 is formed by integrally forming a plurality of pressing portions 14a and an annular mounting portion 14b using a metal plate as a material.
  • Each pressing portion 14a is composed of a pair of pressing pieces formed in a shape that curves convexly toward the roller 9 by cutting and raising the outer peripheral portion of the metal plate.
  • the mounting portion 14b is fitted on the outer periphery of the output shaft 2 at the outer side in the axial direction of the arrangement of the rollers 9, specifically, at a position adjacent to the inner ring 3 in the axial direction.
  • the pressing portion 14a is inserted between the pair of rollers 9 in each wedge-shaped space 13 from the mounting portion 14b, and the pair of pressing pieces of each pressing portion 14a are respectively connected to the rollers 9 facing each other in the circumferential direction. It is pressed at the center position in the direction and pushed into the narrow part of the wedge-shaped space 13.
  • each pressing portion 14a does not move radially outward.
  • the mounting portion 14b of the spring 14 is sandwiched between the other end surface of the inner ring 3 and the inner surface of the stepped portion of the housing 6 in the axial direction, so that the spring 14 is also restricted from moving in the axial direction. The center position in the direction is pressed.
  • This reverse input prevention clutch has the above-described configuration, and the basic operation is the same as that of the reverse input prevention clutch shown in FIGS. That is, since each roller 9 is pushed into the narrow portion of the wedge-shaped space 13 by the elasticity of the pressing portion 14a of the spring 14, even if a reverse input torque is applied to the output side member 4, the roller 9 on the rear side in the rotation direction By engaging the outer ring 5 which is a part of the fixing member 12 and the inner ring 3 which is a part of the output side member 4, the output side member 4 is locked to the fixing member 12 and is not transmitted to the input shaft 1.
  • the spring 14 rotates integrally with the output side member 4 and receives a centrifugal force. Since it is fitted on the outer periphery of the output shaft 2, the pressing force 14a does not move outward in the radial direction to reduce the elasticity of pressing the rollers 9, nor does it come into contact with the inner peripheral cylindrical surface of the outer ring 5. .
  • the spring 14 that presses the roller 9 is restricted from moving radially outward, so that the output side member 4 is not properly locked when the reverse input torque is applied, or the rotation is transmitted.
  • each roller 9 is pressed at its axial center by the pressing portion 14a of the spring 14, when the reverse input torque is applied and the output side member 4 is locked with the fixing member 12 as described above,
  • the roller 9 on the rear side in the rotation direction is slightly rotated around the axial center position, and is inclined to the axial direction of the output side member 4 on the inner peripheral cylindrical surface of the outer ring 5 and the cam surface 3b of the inner ring 3. Engage more often.
  • the rotation angle of the roller 9 varies depending on the frictional state between the roller 9 and the inner and outer rings 3 and 5 when the output side member 4 is locked.
  • the degree of freedom of the engagement position can be increased (the range in which the roller 9 engages with the cam surface 3b of the inner ring 3 is wider than in the past), so that the progress of wear and fatigue of the engagement position is suppressed, It can be used stably for a long time.
  • the roller 9 is made of steel, and the output side member 4 including the inner ring 3 is formed of ceramic or cemented carbide, or the cam surface 3b is coated with DLC (diamond-like carbon) or hard chrome plating. Just do it.
  • Each of the springs 15 is formed by integrally forming a pressing portion 15a composed of a pair of pressing pieces having the same shape as shown in FIGS. 8 to 12B and a columnar mounting portion 15b, using a metal plate as a material. .
  • the pressing portion 15a is inserted between the pair of rollers 9 in the wedge-shaped space 13 as in the example of FIGS. 8 to 12B, and both end portions in the longitudinal direction of the mounting portion 15b are arranged in the arrangement of the rollers 9.
  • the outer side is fitted into a recess 8c formed on the inner peripheral side of the column part 8a of the cage 8.
  • each spring 15 is restrained from moving radially outward and axially, and is held in a state where the pair of pressing pieces of the pressing portion 15a presses the axial center position of the rollers 9 opposed in the circumferential direction. It is attached to the input shaft 1 via a device 8.
  • the means for attaching the spring mounting portion to the input side member or the output side member in the axially outer side of the arrangement of the rollers in a state in which movement to the outer side in the radial direction is restricted is not limited to the above-described example. Things can be adopted.
  • FIGS. 16 to 19 incorporate the same number of springs 16 as the wedge-shaped spaces 13 as in the examples of FIGS. 13 to 15.
  • each of the springs 16 includes a pressing portion 16 a made up of a pair of pressing pieces each having a U-shaped cross section and a mounting portion 16 b having a C-shaped vertical cross section, each of which is made of a metal plate. It is integrally formed, and the pressing pieces of the pressing portion 16a extend radially outward from both peripheral ends of the mounting portion 16b.
  • each spring 16 is fitted in a recess 3 e provided in the center portion in the circumferential direction of the cam surface 3 b of the inner ring 3 to restrict the radially outward movement.
  • the recess 3e of the inner ring 3 is formed such that the back side of the radial cross section is formed in a circular shape along the outer shape of the mounting portion 16b of the spring 16, and the opening is narrower than the back side and widens outward in the radial direction. And extends from the axial center of the inner ring 3 to the other end surface.
  • a stopper plug 17 having substantially the same cross-sectional shape as the recess 3e is fitted from the other end surface of the inner ring 3, so that the spring 16 is prevented from coming off and is positioned in the axial direction. Accordingly, as shown in FIG. 19, the pressing portion 16a of the spring 16 is inserted between the pair of rollers 9 in the wedge-shaped space 13, and the pair of pressing pieces of the pressing portion 16a are opposed to each other in the circumferential direction. The center position of 9 in the axial direction is pressed.
  • the springs 18 and 19 of each of the above-described modifications are obtained by plastically deforming the metal wires so as to have substantially the same shape as the longitudinal cross-sectional shape of the spring 16 shown in FIGS. 19a and mounting portions 18b and 19b are formed.
  • the mounting portion 18b of the spring 18 of the first modification is C-shaped, but the mounting portion 19b of the spring 19 of the second modification is formed in a spiral shape.
  • the spring 19 can push the roller 9 into the narrow portion of the wedge-shaped space 13 with a stronger elasticity than the spring 18 of the first modification, and the locking operation is more stable than in the first modification. It can be carried out.
  • the springs 15, 16, 18, and 19 are restricted from moving radially outward. There is no risk of malfunction due to locking failure or contact between the springs 15, 16, 18, 19 and the outer ring 5, and it can be used stably for a long period of time even under high-speed rotation operating conditions, and torque loss can be reduced. it can.
  • the position where the spring presses the roller is not limited to the strict sense of the axial center of the roller (see, for example, FIG. 22), and the roller presses against the spring. It is only necessary to be able to rotate a substantially equal distance on both sides in the axial direction with the position to be centered.
  • ⁇ Appendix> An input side member and an output side member arranged in a state of rotating around the same axis, a fixed member arranged on a radially outer side of the output side member, and a reverse input torque applied to the output side member
  • the lock means for locking the output side member and the fixing member with respect to the above, the lock release means for releasing the lock state by the lock means for the input torque applied to the input side member, and the lock state released Torque transmitting means for transmitting an input torque applied to the input side member to the output side member when in a state;
  • the locking means is provided with a cylindrical surface on the inner periphery of the fixed member, and a plurality of cam surfaces are provided on the outer periphery of the output side member, and the inner peripheral cylindrical surface of the fixed member and each cam surface of the output side member A wedge-shaped space gradually narrowing on both sides in the circumferential direction is formed, and a pair of rollers are incorporated in each wedge-
  • a reverse input prevention clutch characterized in that it is attached in a state of being caught.
  • the spring is characterized in that the mounting portion is formed in an annular shape and is fitted on the outer periphery of the output side member, and the pressing portion is inserted between the pair of rollers in each wedge-shaped space from the mounting portion.
  • the reverse input preventing clutch according to appendix 1.
  • the unlocking means has a pillar portion inserted on both sides in the circumferential direction of each wedge-shaped space, and is a cage attached to the input side member so as to rotate integrally with the input side member,
  • the springs are incorporated in the same number as the wedge-shaped space, each of the pressing portions is inserted between a pair of rollers in the wedge-shaped space, and the attachment portion is attached to the input side member via the cage.
  • the reverse input preventing clutch according to Supplementary Note 1.
  • the lock means for locking the output side member and the fixing member with respect to the above, the lock release means for releasing the lock state by the lock means for the input torque applied to the input side member, and the lock state released Torque transmitting means for transmitting an input torque applied to the input side member to the output side member when in a state;
  • the locking means is provided with a cylindrical surface on the inner periphery of the fixed member, and a plurality of cam surfaces are provided on the outer periphery of the output side member, and the inner peripheral cylindrical surface of the fixed member and each cam surface of the output side member A wedge-shaped space gradually narrowing on both sides in the circumferential direction is formed, and a pair of rollers are incorporated in each wedge-shaped space, and each of the rollers is pushed into a narrow portion of
  • the reverse input prevention clutch characterized by the above-mentioned. (Appendix 5)
  • the spring is characterized in that the mounting portion is formed in an annular shape and is fitted on the outer periphery of the output side member, and the pressing portion is inserted between the pair of rollers in each wedge-shaped space from the mounting portion.
  • the reverse input preventing clutch according to appendix 4.
  • the unlocking means has a pillar portion inserted on both sides in the circumferential direction of each wedge-shaped space, and is a cage attached to the input side member so as to rotate integrally with the input side member,
  • the springs are incorporated in the same number as the wedge-shaped space, each of the pressing portions is inserted between a pair of rollers in the wedge-shaped space, and the attachment portion is attached to the input side member via the cage.
  • the reverse input prevention clutch according to appendix 4. (Appendix 7) The same number of springs are incorporated in the wedge-shaped space, the pressing portions are inserted between a pair of rollers in the wedge-shaped space, and the mounting portion is fitted in a recess provided on the cam surface of the output side member.
  • the reverse input preventing clutch according to appendix 4, wherein (Appendix 8) The reverse input preventing clutch according to any one of appendices 4 to 7, wherein the cam surface of the output side member has a hardness higher than that of the roller.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

L'invention concerne un embrayage de prévention d'entrée inverse comprenant : une entrée d'écoulement (11a) par laquelle de l'huile de lubrification située à extérieur d'un embrayage s'écoule à l'intérieur de l'embrayage ; une sortie d'écoulement (7c) par laquelle l'huile de lubrification située à l'intérieur de l'embrayage s'écoule vers l'extérieur de l'embrayage ; et un passage ménagé de l'entrée d'écoulement (11a) à la sortie d'écoulement (7c) en passant par un espace annulaire situé entre une bague intérieure et une bague extérieure et comprenant un espace en forme de coin (13). En raison de cette configuration, de l'huile de lubrification est échangée entre l'intérieur et l'extérieur de l'embrayage en fonction de la rotation de la bague intérieure (3) pendant le fonctionnement et des défauts de lubrification en raison d'une détérioration précoce ou à des augmentations de température de l'huile de lubrification à l'intérieur de l'embrayage sont évités.
PCT/JP2017/016414 2016-04-28 2017-04-25 Embrayage à prévention d'entrée inverse WO2017188265A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2016090586A JP2017198301A (ja) 2016-04-28 2016-04-28 逆入力防止クラッチ
JP2016-090586 2016-04-28
JP2016-097730 2016-05-16
JP2016097730A JP2017207082A (ja) 2016-05-16 2016-05-16 逆入力防止クラッチ
JP2016-101285 2016-05-20
JP2016101285A JP2017207172A (ja) 2016-05-20 2016-05-20 逆入力防止クラッチ

Publications (1)

Publication Number Publication Date
WO2017188265A1 true WO2017188265A1 (fr) 2017-11-02

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5474152A (en) * 1995-04-12 1995-12-12 Teledyne Industries, Inc. Lubrication system for a starter clutch assembly
JP2001295866A (ja) * 2000-02-07 2001-10-26 Nsk Warner Kk ワンウェイクラッチ装置
JP2005249003A (ja) * 2004-03-02 2005-09-15 Ntn Corp 回転伝達装置
JP2015161393A (ja) * 2014-02-28 2015-09-07 Ntn株式会社 逆入力防止クラッチ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5474152A (en) * 1995-04-12 1995-12-12 Teledyne Industries, Inc. Lubrication system for a starter clutch assembly
JP2001295866A (ja) * 2000-02-07 2001-10-26 Nsk Warner Kk ワンウェイクラッチ装置
JP2005249003A (ja) * 2004-03-02 2005-09-15 Ntn Corp 回転伝達装置
JP2015161393A (ja) * 2014-02-28 2015-09-07 Ntn株式会社 逆入力防止クラッチ

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