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WO2012026020A1 - Dispositif d'embrayage - Google Patents

Dispositif d'embrayage Download PDF

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Publication number
WO2012026020A1
WO2012026020A1 PCT/JP2010/064478 JP2010064478W WO2012026020A1 WO 2012026020 A1 WO2012026020 A1 WO 2012026020A1 JP 2010064478 W JP2010064478 W JP 2010064478W WO 2012026020 A1 WO2012026020 A1 WO 2012026020A1
Authority
WO
WIPO (PCT)
Prior art keywords
peripheral surface
cage
sprag
cam groove
ring
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/JP2010/064478
Other languages
English (en)
Japanese (ja)
Inventor
忠彦 加藤
幹典 松井
剛央 山田
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.)
Univance Corp
Original Assignee
Univance Corp
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 Univance Corp filed Critical Univance Corp
Priority to JP2012530484A priority Critical patent/JP5618449B2/ja
Priority to PCT/JP2010/064478 priority patent/WO2012026020A1/fr
Publication of WO2012026020A1 publication Critical patent/WO2012026020A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16D41/069—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags
    • F16D41/07—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags between two cylindrical surfaces

Definitions

  • the present invention relates to a clutch device that transmits rotation in a fixed direction, and more particularly, to a clutch device that can ensure the degree of freedom in design related to the material of a member and the arrangement of components and can improve the reliability of rotation transmission and switching. Is.
  • a clutch device that transmits rotation in a certain direction for example, in Patent Document 1, a cylindrical surface is formed on the outer periphery of the inner ring and the inner periphery of the outer ring, and two cages (inner cages) having different diameters between the cylindrical surfaces. And a clutch device that holds the sprags with these cages.
  • a plurality of first magnetic pole teeth formed at equal intervals in the circumferential direction of the end of one of the cages, and the phase is shifted in the circumferential direction with respect to the first magnetic pole teeth.
  • a second magnetic pole tooth formed on one of the outer ring and the inner ring, and an electromagnet that applies a magnetic attraction force between the first and second magnetic pole teeth by energization of the electromagnetic coil.
  • the electromagnetic coil When the electromagnetic coil is energized, the first and second magnetic pole teeth are magnetized by the electromagnet, and a magnetic attractive force is applied between the first and second magnetic pole teeth, and the first and second magnets are applied to the two cages.
  • a relative rotational force is applied in the direction in which the phases between the magnetic pole teeth of the magnetic poles are equal.
  • JP 2006-46612 A (paragraphs 0014, 0015, etc.)
  • the present invention has been made to solve the above-described problems, and is a clutch capable of ensuring the degree of freedom in design related to the material of the member and the arrangement of the parts, and improving the reliability of rotation transmission and switching.
  • the object is to provide a device.
  • the outer ring side portion of the sprag is held by the outer cage disposed in the housing space between the outer circumferential surface of the inner ring and the inner circumferential surface of the outer ring, and the housing space has A portion of the sprag on the inner ring side is held by the arranged inner cage. Since the sprag is tiltably held by the inner cage and the outer cage, the inner cage and the outer cage can be moved relative to each other around the shaft center so that the outer race surface of the inner ring and the inner circumference surface of the outer ring and the sprag can be moved. The engagement and disengagement with the engagement surface can be switched.
  • the first rotating part and the second rotating part are connected to the inner holder and the outer holder, and are arranged outside the housing space so as to be rotatable in conjunction with the rotation of the inner holder and the outer holder. Therefore, a contact load is applied to the first rotating part and the second rotating part by the load applying device, and the inner cage and the outer cage are moved relative to each other around the axis in conjunction with the contact load. it can.
  • the load applying device applies a contact load to the first rotating unit and the second rotating unit, and the inner cage and the outer cage are moved relative to each other around the axis in conjunction with the contact load.
  • the inner and outer cages are moved relative to each other around the axis without contact by magnetic force, it is less likely to be subject to restrictions on the material of the member and the arrangement of the parts.
  • the inner retainer and the outer retainer can be reliably moved around the axis, and the reliability of rotation transmission and switching can be improved.
  • a cam groove formed on at least one peripheral surface of the first rotating part or the second rotating part, and a surface that is engaged with the cam groove and intersects the axis.
  • an engagement element configured to reciprocate in the axial direction by the load applying device while being configured to be rotatable inside, when the inner and outer cages are rotated around the axis,
  • the first rotating part and the second rotating part are relatively moved around the axis center in a state where the engaging element is engaged with the cam groove.
  • the engagement and disengagement of the sprags with respect to the outer peripheral surface and the inner peripheral surface are switched.
  • the apparatus configuration can be simplified.
  • the engaging element is engaged with the cam groove formed in at least one of the first rotating part or the second rotating part, the movement of the engaging element is restricted by the cam groove.
  • a load is applied to the inner cage and the outer cage via the first pinion and the second pinion that are arranged on axes different from the axis of the inner ring and the outer ring.
  • the relative positions of the cage and the outer cage are displaced.
  • the rotation radius of the 1st rotation part and the 2nd rotation part which are formed integrally with the 1st pinion and the 2nd pinion can be made small.
  • the clutch device can be downsized.
  • since the rotation radii of the first rotating part and the second rotating part can be reduced, there is an effect that the friction due to the sliding contact between the first rotating part and the second rotating part can be reduced.
  • the first rotating part and the second rotating part have portions that overlap each other along the axial direction, and the first cam groove and the second cam that are formed in the overlapping portions.
  • a groove is provided, and at least one of the first cam groove or the second cam groove is penetrated into the first rotating part or the second rotating part. Since the engaging element is inserted into one of the first cam groove or the second cam groove and engaged with the other of the first cam groove or the second cam groove, it is held outside by the reciprocating movement of one engaging element.
  • the cage and the inner cage can be relatively moved around the axis. Thereby, in addition to the effect of Claim 2 or 3, there exists an effect which can further simplify an apparatus structure.
  • At least one of the inner cage and the outer cage is urged by the urging member, and the direction of the urging is determined by the load applied by the load applying device. Since the direction of movement of the outer cage is opposite to the relative movement direction, when the load applying device is not driven, the urging member is used to engage or disengage the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring and the engaging surface of the sprag. Either state can be maintained. Further, the engagement or disengagement of the outer peripheral surface and the inner peripheral surface with the engagement surface of the sprag can be switched by driving the load applying device and applying a contact load against the urging force of the urging member. it can.
  • the load applying device only needs to be driven when switching the engagement or disengagement between the outer peripheral surface and the inner peripheral surface and the engagement surface of the sprag, thereby reducing the time for driving the load applying device.
  • the urging force is applied by the urging member in the direction in which the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring and the engagement surface of the sprag are engaged or disengaged. Therefore, by driving the load applying device, the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring and the engagement surface of the sprag can be quickly engaged or disengaged.
  • the effect of the fifth aspect there is an effect that power transmission and interruption can be quickly switched without time loss.
  • the sprags come into contact with each other when the sprags are tilted by releasing the engagement between at least one of the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring and the engaging surface of the sprags. Since further tilting is restricted, when the sprags come into contact with each other, further relative movement of the inner and outer cages holding the sprags is also regulated. Therefore, there is no need to provide a positioning member or the like for regulating the relative movement amount of the inner cage and the outer cage, and in addition to the effect of any one of claims 1 to 6, there is an effect that the apparatus configuration can be simplified.
  • FIG. 1 It is a schematic diagram of a part of the clutch device according to the first embodiment. It is an axial sectional view of a clutch device.
  • A is a partial exploded view of the clutch device
  • (b) is a schematic view showing the positional relationship between the first cam groove and the second cam groove and the engaging element
  • (c) is the engaging element.
  • It is a schematic diagram which shows the relationship between reciprocation and the relative movement of a 1st cam groove and a 2nd cam groove.
  • A is a schematic diagram of the clutch device in which the inner ring and the outer ring and the sprag are engaged
  • (b) is a schematic diagram of the clutch device in which the engagement between the inner ring and the outer ring and the sprag is released
  • FIG. 3 is a schematic view of a main part of a clutch device in which engagement between an inner ring and an outer ring and a sprag is released.
  • (A) is a schematic diagram which shows the state which an inner ring
  • (b) is the state by which engagement with the inner ring
  • (A) is a principal part schematic diagram of the clutch apparatus in 4th Embodiment
  • (b) is a principal part schematic diagram of 5th Embodiment
  • (c) is in 6th Embodiment.
  • (d) is a principal part schematic diagram of the clutch apparatus in 7th Embodiment.
  • FIG. 1 is a schematic diagram of a part of the clutch device 1 according to the first embodiment of the present invention.
  • the clutch device 1 includes an inner ring 2, an outer ring 3 surrounding the outer periphery of the inner ring 2, a plurality of sprags 4 disposed between the inner ring 2 and the outer ring 3, and the sprags 4.
  • the inner retainer 5 and the outer retainer 6 are configured to retain the inner ring 2 side portion and the outer ring 3 side portion, respectively.
  • Pockets 5 a and 6 a are formed in the inner cage 5 and the outer cage 6, respectively.
  • FIG. 2 is an axial sectional view of the clutch device 1.
  • the inner ring 2 includes an outer peripheral surface 2 a having a circular cross section, and is configured to be rotatable around an axis O.
  • the inner ring 2 in the present embodiment is supported on a central shaft 7 formed in a columnar shape via a roller bearing B1. Since the inner ring 2 is provided with a gear 2b that rotates about the axis O in the axial direction (right side in FIG. 2), the rotation can be transmitted to the inner ring 2 via the gear 2b, and the rotation of the inner ring 2 causes the gear 2b to rotate. Is output via.
  • the outer ring 3 includes an inner peripheral surface 3 a having a circular cross section facing the outer peripheral surface 2 a of the inner ring 2, and is configured to be rotatable around the axis O in the same manner as the inner ring 2.
  • the outer ring 3 in the present embodiment is formed in a substantially annular shape and, as shown in FIG. 2, is supported by the case C through the ball bearing B2, and is supported by the central shaft 7 through the roller bearing B3. .
  • the sprag 4 is a member that bears a function for restricting the relative rotation between the inner ring 2 and the outer ring 3, and includes engagement surfaces 4a and 4b (see FIG. 1) that are in contact with the outer peripheral surface 2a and the inner peripheral surface 3a, respectively.
  • engagement surfaces 4a and 4b in contact with the outer peripheral surface 2a and the inner peripheral surface 3a, respectively.
  • a plurality are arranged at equal intervals in the circumferential direction.
  • the inner cage 5 is a cylindrical member that holds a portion of the sprag 4 on the inner ring 2 side, and is supported on the axis O side of the first disk portion 8.
  • the first disk portion 8 is a member formed in a disk shape that intersects with the direction of the axis O, and is disposed on the outer peripheral side of the inner ring 2 outside the accommodation space g.
  • the first rotating portion 9 is a member formed in a cylindrical shape coaxial with the inner ring 2, extends in a direction parallel to the axis O from the outer periphery of the first disc portion 8, and is integrated with the inner cage 5. It is configured to be rotatable. In the present embodiment, the first rotating portion 9 is disposed to face the outer peripheral surface 2 a of the inner ring 2. Thereby, the length of the inner ring 2 and the first rotating part 9 in the axis O direction can be shortened, and the clutch device 1 can be downsized.
  • the outer cage 6 is a cylindrical member that holds a portion of the sprag 4 on the outer ring 3 side, and is supported on the axis O side of the second disc portion 10 disposed facing the first disc portion 8.
  • the second disk portion 10 is a member formed in a disk shape that intersects the direction of the axis O, and is disposed outside the accommodation space g.
  • the second rotating part 11 is a member formed in a cylindrical shape coaxial with the inner ring 2, is located between the outer peripheral surface 3 a of the outer ring 3 and the first rotating part 9, and is pivoted from the outer periphery of the second disk part 10. It extends in a direction parallel to the center O and is configured to be rotatable integrally with the outer cage 6.
  • the 1st cam groove 9a and the 2nd cam groove 11a are penetrated by the surrounding surface in alignment with the axial center O direction, respectively.
  • the first rotating portion 9 and the second rotating portion 11 have portions that overlap each other along the direction of the axis O, and the first cam groove 9a and the second cam groove 11a are formed in the overlapping portions. Are formed obliquely.
  • the load applying device 20 includes an actuator 21 and a reciprocating unit 22.
  • the actuator 21 is a power source that generates a load to be applied to the inner cage 5 and the outer cage 6, and is fixed to the case C.
  • the reciprocating part 22 is a part for transmitting the power of the actuator 21 to the inner holder 5 and the outer holder 6, and is arranged in parallel with the axis O. By driving the actuator 21, Reciprocated in parallel.
  • the annular member 12 is an annular member disposed along the peripheral surface 9b of the first rotating portion 9, and the first engaging portion 12a formed in a series of grooves in the circumferential direction of the outer peripheral surface. And is configured to be rotatable along the peripheral surface 9b of the first rotating portion 9.
  • the first engaging portion 12a is a portion where the second engaging portion 22a protruding in the axial direction from the tip of the reciprocating portion 22 formed in an arm shape is engaged so as to be slidable in the circumferential direction.
  • the annular member 12 includes an engagement element 13 that protrudes in the direction of the axis O.
  • the engaging element 13 is inserted into the first cam groove 9 a that penetrates the first rotating part 9 and is engaged with the second cam groove 11 a that penetrates the second rotating part 11.
  • a groove 3c is formed on the outer peripheral surface 3b of the outer ring 3 in parallel with the axis O, and the engaging element 13 is inserted into the first cam groove 9a and the second cam groove 11a while the tip is a groove. 3c is engaged.
  • the engaging element 13 is engaged with the groove 3c, the first cam groove 9a, and the second cam groove 11a, so that when the outer ring 3 rotates around the axis O, it is formed on the outer peripheral surface 3b of the outer ring 3.
  • the engaging element 13 and the annular member 12 engaged with the groove 3c are rotated around the axis O. Accordingly, the first rotating portion 9 and the second rotating portion 11 in which the engagement element 13 is inserted in the first cam groove 9a and the second cam groove 11a are also rotated around the axis O, and the first rotating portion 9 and the second rotating portion 9
  • the inner cage 5 and the outer cage 6 that are integrated with the two rotating portions 11 and the sprags 4 held by these are rotated in the circumferential direction.
  • FIG. 3A is a partial exploded view of the clutch device 1
  • FIG. 3B is a schematic diagram showing the positional relationship between the first cam groove 9a and the second cam groove 11a and the engaging element 13.
  • FIG. 3C is a schematic diagram showing the relationship between the reciprocation of the engagement element 13 and the relative movement of the first cam groove 9a and the second cam groove 11a.
  • the first cam groove 9a and the second cam groove 11a are formed in different shapes on the peripheral surfaces of the first rotating part 9 and the second rotating part 11, respectively.
  • each of the first cam groove 9a and the second cam groove 11a obliquely intersects a straight line L parallel to the axis O, and the actuator 21 (see FIG. 2).
  • the actuator 21 are formed apart from each other (downward in FIG. 3B).
  • the annular member 12 is moved in the direction away from the actuator 21 along the peripheral surface 9b of the first rotating portion 9, and the engaging element 13 protruding from the annular member 12 has the first cam groove 9a and the first 2 The cam groove 11a is moved away from the actuator 21.
  • the first cam groove 9a and the second cam groove 11a are formed so as to be separated from each other as the distance from the actuator 21 (see FIG. 2) increases with respect to the straight line L parallel to the axis O.
  • the engaging element 13 moves through the first cam groove 9a and the second cam groove 11a in the direction away from the first cam groove 9a (downward in FIG. 3B), as shown in FIG.
  • the portion 11 is relatively moved in the circumferential direction around the axis O (the arrow direction shown in FIG. 3C).
  • the actuator 21 is driven from this state and the engaging element 13 moves in the first cam groove 9a and the second cam groove 11a in a direction approaching the actuator 21 (upward in FIG.
  • the rotating part 11 is relatively moved in the opposite direction (counter arrow direction shown in FIG. 3C). Since the inner cage 5 and the outer cage 6 are connected to the first rotating unit 9 and the second rotating unit 11, the inner cage 5 and the outer holding unit are moved as the first rotating unit 9 and the second rotating unit 11 move relative to each other. The vessel 6 is moved relative.
  • a biasing member 14 (see FIGS. 2 and 3A) that biases the first disk portion 8 and the second disk portion 10 in the circumferential direction around the axis O is provided.
  • the urging member 14 is formed of an annular torsion coil spring, and is disposed between the first disk portion 8 and the second disk portion 10 along the first disk portion 8 and the second disk portion 10. At the same time, both ends are respectively engaged with the first disk portion 8 and the second disk portion 10.
  • the first rotating portion 9 and the second rotating portion 11 are set so as to be urged by the urging member 14 in the direction opposite to the relative movement direction when the engagement element 13 moves in the direction away from the actuator 21. ing.
  • the engaging element 13 when the engaging element 13 is located near the actuator 21, the first rotating part 9 and the second rotating part 11 are maintained at predetermined positions by the urging force of the urging member 14 without driving the actuator 21. it can. Since the load applying device 20 only needs to be driven when the first rotating unit 9 and the second rotating unit 11 are relatively moved from this position, energy consumption required to drive the load applying device 20 can be suppressed.
  • the inner cage 5 is fixed by inserting a distal end portion 5 b into a locking hole 8 a formed on the axial center side of the first disc portion 8. Thereby, the assembly of the inner cage 5 can be facilitated. Further, after one end of the sprag 4 is inserted into the pocket 6a of the outer cage 6, the other end of the sprag 4 is inserted into the pocket 5a of the inner cage 5, and the tip 5b of the inner cage 5 is locked into the locking hole. By inserting in 8a, the holding
  • the width W1 (see FIG. 1) of the sprag 4 in the rotation direction on the outer ring 3 side is set to be narrower than the width W2 of the pocket 5a formed in the inner cage 5 in the rotation direction. Therefore, when the clutch device 1 is assembled by inserting the sprag 4 into the pockets 5a and 6a after the inner cage 5 and the outer cage 6 are arranged, the width of the sprag 4 on the outer ring 3 side from the pocket 5a of the inner cage 5 is assembled.
  • the end of W1 (see FIG. 1) can be inserted, and the end can be inserted into the pocket 6a of the outer cage 6 to hold the sprag 4 in the inner cage 5 and the outer cage 6. Thereby, the assembly operation
  • FIG. 4A is a schematic view of the clutch device 1 in which the inner ring 2 and the outer ring 3 are engaged with the sprag 4
  • FIG. 4B is a diagram in which the engagement between the inner ring 2 and the outer ring 3 and the sprag 4 is released
  • FIG. 4C is a schematic view of the main part of the clutch device 2 in which the engagement between the inner ring 2 and the outer ring 3 and the sprag 4 is released.
  • the clutch device 1 does not drive the actuator 21 and does not drive the first rotating portion 9. And the 2nd rotation part 11 is maintained in a predetermined position with the urging
  • FIG. 4A the inner retainer 5 and the outer retainer are held at positions where the engagement surfaces 4a and 4b of the sprag 4 are in contact with the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3. The positional relationship between the pockets 5a and 6a of the container 6 is determined.
  • first cam groove 9a and the second cam groove 11a have a groove length (vertical direction in FIGS. 3B and 3C) and a width (FIG. 3B and FIG. Since a margin is provided in FIG. 3 (c), the sprag 4 is moved in the self-locking direction by the urging force of the urging member 14 (arrow B in FIG. 4 (a)) as shown in FIG. 4 (a). Tilt in the direction of arrow S in FIG. 4 (a), the outer peripheral surface 2a of the inner ring 2, the inner peripheral surface 3a of the outer ring 3, and the engaging surfaces 4a and 4b of the sprag 4 are engaged.
  • the urging member 14 is applied by the load applying device 20 (see FIG. 2).
  • the inner cage 5 and the outer cage 6 are relatively moved by applying a load (arrow L in FIG. 4 (b)) against the urging force, and the sprags 4 inserted into the pockets 5a and 6a are anti-self-locked. Tilt in the direction (counter arrow direction in FIG. 4A).
  • the distance l2 between the engagement surfaces 4a and 4b of the sprag 4 in the radial direction of the outer ring 3 is smaller than the distance l1 between the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3, and A gap is formed between the surface 2 a and the inner peripheral surface 3 a of the outer ring 3 and the engagement surfaces 4 a and 4 b of the sprag 4.
  • a gap is formed between the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3 and the engagement surfaces 4a and 4b of the sprag 4 so that the inner ring 2 is locked (direction Ri in FIG. 4 (b)). ), The contact between the outer peripheral surface 2a of the inner ring 2 and the engagement surface 4a of the sprag 4 is reliably prevented, and transmission of power by the sprag 4 can be reliably interrupted.
  • a contact load is applied to the first rotating portion 9 and the second rotating portion 11 by the load applying device 20 and is interlocked with the contact load. Since the inner cage 5 and the outer cage 6 are relatively moved around the axis O, the material of the member and the like are compared with those in which the cage is relatively moved around the axis without contact by magnetic force as in the prior art. It is possible to make it difficult to receive restrictions on the arrangement of parts, to ensure the degree of design freedom, and to reliably move the inner cage 5 and the outer cage 6 around the axis O, and to transmit rotation and The certainty of the switching of the interruption can be improved.
  • first cam groove 9a and the second cam groove 11a formed on the peripheral surfaces of the first rotating portion 9 and the second rotating portion 11 are engaged with the first cam groove 9a and the second cam groove 11a.
  • the engaging element 13 is configured to be rotatable in a plane intersecting the axis O, when the inner holder 5 and the outer holder 6 are rotated around the axis O, the engaging element 13 is interlocked.
  • the first rotating portion 9 and the second rotating portion 11 are rotated about the axis O in a state where the engaging element 13 is engaged with the first cam groove 9a and the second cam groove 11a.
  • the engaging element 13 is engaged with the first cam groove 9a and the second cam groove 11a formed in the first rotating part 9 and the second rotating part 11, the first cam groove 9a and the second cam groove The movement of the engagement element 13 is restricted by 11a. As a result, even when the first rotating part 9 and the second rotating part 11 rotate at high speed, it is possible to follow the relative movement of the outer retainer 5 and the inner retainer 6 with the back and forth movement of the engagement element 13, and quick switching. Is possible.
  • FIG. 4A when the inner cage 5 and the outer cage 6 are relatively moved by the biasing force of the biasing member 14 (arrow B in FIG. 4A), the sprag 4 is moved to the inner ring 2. And the outer ring 3 is engaged, and further relative movement of the inner cage 5 and the outer cage 6 is restricted.
  • FIG. 4B the inner cage 5 and the outer cage 6 are relatively moved by the load of the load applying device 20 (arrow L in FIG. 4B), and the inner ring 2, the outer ring 3 and the sprag 4 are moved.
  • the engagement with is released, the sprags 4 come into contact with each other at the contact point P, and further relative movement of the inner cage 5 and the outer cage 6 is restricted.
  • retainer 6 is also determined by the engagement or contact
  • FIG. Therefore, it is possible to eliminate the need for accuracy such as positioning with respect to the engaging element 13 that relatively moves the first rotating part 9 and the second rotating part 11. Since the engagement element 13 may be a mechanism that applies a load to the first rotation unit 9 and the second rotation unit 11 by reciprocating, the device configuration can be simplified.
  • first rotating portion 9 and the second rotating portion 11 have portions that overlap each other along the direction of the axis O, and the first cam groove 9a and the second cam groove 11a are formed at the portions, and the first The first cam groove 9 a and the second cam groove 11 a are penetrated by the first rotating part 9 and the second rotating part 11. Since the engagement element 13 is inserted into the first cam groove 9a and the second cam groove 11a, the inner cage 5 and the outer cage 6 are relatively moved around the axis O by the reciprocation of one engagement element 13. Can be made. Thereby, the apparatus configuration can be further simplified.
  • the urging member 14 urges the inner cage 5 and the outer cage 6 in one direction, but the sprag 4 itself is in a self-locking direction (the direction of arrow S in FIG. 4A) or anti-self.
  • the case where the urging member for urging in the locking direction (the counter arrow S direction in FIG. 4A) is not provided has been described.
  • a biasing member 114 that biases the sprag 4 in the self-locking direction or the anti-self-locking direction is provided.
  • FIG. 5A is a schematic diagram showing a state where the inner ring 2 and the outer ring 3 are engaged with the sprag 4 in the clutch device 101 according to the second embodiment
  • FIG. 5B is a diagram showing the inner ring 2 and the outer ring 3. It is a schematic diagram which shows the state by which engagement with the sprags 4 was cancelled
  • symbol is attached
  • a load applying device 20 (see FIG.
  • the urging member 114 is a member that is engaged with a predetermined portion of the sprag 4 and urges the sprag 4 itself in a self-locking direction or an anti-self-locking direction.
  • the urging member 114 is constituted by a ribbon spring, and the sprag 4 is engaged with the outer peripheral surface 2 a of the inner ring 2 and the inner peripheral surface 3 a of the outer ring 3 so that the engaging surfaces 4 a and 4 b of the sprag 4 are engaged. Energize. As a result, when the engaging element 13 is positioned near the actuator 21 (see FIG. 2) (see FIG.
  • the sprag 4 does not drive the actuator 21, but the sprag 4 can 5 (a) is tilted in the self-locking direction according to arrow B), and the outer peripheral surface 2a of the inner ring 2, the inner peripheral surface 3a of the outer ring 3, and the engaging surfaces 4a and 4b of the sprag 4 are engaged.
  • the urging member 114 is applied by the load applying device 20 (see FIG. 2).
  • the inner cage 5 and the outer cage 6 are moved relative to each other, and the sprag 4 is made anti-self.
  • the engagement between the outer peripheral surface 2 a of the inner ring 2, the inner peripheral surface 3 a of the outer ring 3 and the engaging surfaces 4 a and 4 b of the sprag 4 can be released as shown in FIG.
  • the load applying device 20 applies the urging force ( By applying a load (arrow L in FIG. 5 (b)) that opposes FIG. 5 (a), the inner cage 5 and the outer cage 6 are moved relative to each other, and the sprag 4 is tilted in the anti-self-lock direction.
  • a load arrow L in FIG. 5 (b)
  • the inner cage 5 and the outer cage 6 are moved relative to each other, and the sprag 4 is tilted in the anti-self-lock direction.
  • the engagement between the outer peripheral surface 2 a of the inner ring 2, the inner peripheral surface 3 a of the outer ring 3, and the engagement surfaces 4 a and 4 b of the sprag 4 can be released.
  • the urging member 114 that is engaged with a predetermined portion of the sprag 4 is provided, and the sprag 4 is urged in the self-locking direction.
  • the outer peripheral surface 2a of the inner ring 2 and The engagement surfaces 4 a and 4 b of the sprag 4 can be reliably engaged with the inner peripheral surface 3 a of the outer ring 3 by the urging force of the urging member 114.
  • the dimensional tolerance of the pockets 5a and 6a and the sprags 4 of the inner cage 5 and the outer cage 6 can be relaxed.
  • FIG. 6 is an axial sectional view of the clutch device 201 according to the third embodiment
  • FIG. 7 is a partial exploded view of the clutch device 201. Note that the same parts as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
  • the inner cage 205 is a cylindrical member that holds a portion of the sprag 4 on the inner ring 2 side, and protrudes in a direction parallel to the axis O from the axis O side of the first disk portion 208 as shown in FIG. It is installed.
  • the pocket 205a formed in the inner holder 205 has one edge (left side in FIG. 7) removed. Thereby, when the clutch device 201 is assembled, the sprag 4 can be inserted into the inner holder 205 from the removed edge, so that the assembly can be facilitated.
  • the first disk portion 208 has a pinion 208a formed on the outer periphery. Further, since the first disk portion 208 is restricted from rotating relative to the inner ring 2 by a pin (not shown), the inner cage 205 is rotated as the inner ring 2 rotates.
  • the outer cage 206 is a cylindrical member that holds a portion of the sprag 4 on the outer ring 3 side, and protrudes in a direction parallel to the axis O from the axis O side of the second disk portion 210 as shown in FIG. It is installed.
  • the second disk portion 210 is disposed facing the first disk portion 208, and a pinion 210a is formed on the outer periphery. Further, the first disk part 208 and the second disk part 210 are engaged with a biasing member 214 composed of a torsion coil spring, and a biasing force is applied so as to move the first disk part 208 and the second disk part 210 relative to each other. Is granted.
  • the first pinion 231 and the second pinion 241 that mesh with the pinions 208a and 210a are rotatably supported by a parallel shaft 230 disposed in parallel with the central shaft 7.
  • the first pinion 231 is integrally formed with a first rotating portion 232 that protrudes toward the second pinion 241 along the parallel axis 230.
  • the first rotating portion 232 is formed in a cylindrical shape, and a notch 232a is penetrated from the end portion to the peripheral surface in parallel with the parallel shaft 230.
  • the second pinion 241 is integrally formed with a second rotating portion 242 that protrudes on the opposite side of the first pinion 231 along the parallel axis 230.
  • the second rotating part 242 is formed in a cylindrical shape having a larger diameter than the first rotating part 232, and a cam groove 242 a that obliquely intersects the parallel shaft 230 is penetrated from the end part to the peripheral surface.
  • the 1st rotation part 232 and the 2nd rotation part 242 have a site
  • the load applying device 220 includes an actuator 221 and a reciprocating part 222.
  • the actuator 221 is a power source that generates a load to be applied to the inner cage 205 and the outer cage 206, and is configured to be rotatable with respect to the parallel shaft 230 while being restricted from moving along the parallel shaft 230.
  • the reciprocating unit 222 is a member for transmitting the power of the actuator 221 to the inner holder 205 and the outer holder 206, and is configured to be rotatable and reciprocating with respect to the parallel shaft 230, and drives the actuator 221. By this, it is reciprocated in parallel with the parallel shaft 230.
  • the actuator 221 is composed of a solenoid, and the reciprocating part 222 is fixed to the tip of the plunger 223 that is reciprocated.
  • An opening spring 224 that urges the reciprocating part 222 toward the first rotating part 232 and the second rotating part 242 is disposed between the actuator 221 and the reciprocating part 222. Accordingly, when the actuator 221 is energized, the plunger 223 is pulled in, the reciprocating part 222 approaches the actuator 221, and when the energization is released, the reciprocating part 222 is moved away from the actuator 221 by the release spring 224.
  • the engaging element 213 is a part protruding from the reciprocating part 222 in the axial center Op direction of the parallel shaft 230, and penetrates the cam groove 242a and is engaged with the notch part 232a.
  • the rotation is transmitted to the first pinion 231 that meshes with the pinion 208a. Since the engaging element 213 is engaged with the cam groove 242a and the notch 232a, the rotation of the first pinion 231 is transmitted to the second pinion 241 via the engaging element 213, and the pinion 210a meshes with the second pinion 241.
  • the outer cage 206 When transmitted, the outer cage 206 rotates at the same speed as the inner cage 205. Accordingly, the inner holder 205 and the outer holder 206 and the sprags 4 held by the inner holder 205 and the outer holder 206 are rotated in the circumferential direction together with the inner ring 3.
  • the cam groove 242 a is formed so as to be oblique to the parallel shaft 230, and the notch 232 a is formed in a direction parallel to the parallel shaft 230. Accordingly, when the engagement element 213 reciprocates along the parallel axis 230 in parallel with the parallel axis 230, the second rotating part 242 in which the cam groove 242 a is formed moves around the parallel axis 230 with respect to the first rotating part 232. It is moved relative. Along with this relative movement, the phases of the inner holder 205 and the outer holder 206 are displaced.
  • the phase (relative position) between the inner holder 205 and the outer holder 206 is such that the energization of the actuator 221 of the load applying device 220 is released and the reciprocating unit 222 is actuated by the release spring 224.
  • the engagement surfaces 4 a and 4 b of the sprag 4 are engaged with the outer peripheral surface 2 a of the inner ring 2 and the inner peripheral surface 3 a of the outer ring 3 by the relative movement of the second rotating unit 242 with respect to the first rotating unit 232.
  • the urging force by the urging member 214 is set so as to assist the relative movement of the second rotating part 242 with respect to the first rotating part 232 when the engaging element 213 (reciprocating part 222) moves away from the actuator 221. ing.
  • the spurs are applied to the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3 by the biasing force of the biasing member 214.
  • the four engaging surfaces 4a and 4b are engaged.
  • a load is applied to the pinions 208a and 210a via the first rotating portion 232 and the second rotating portion 242 disposed on the parallel shaft 230. Then, since the relative positions of the inner holder 205 and the outer holder 206 are displaced, the rotation radii of the first rotating part 232 and the second rotating part 242 are made smaller than those in the first and second embodiments. be able to. As a result, the clutch device 201 can be reduced in size. In addition, since the rotation radii of the first rotation unit 232 and the second rotation unit 242 can be reduced, friction caused by sliding contact between the first rotation unit 232 and the second rotation unit 242 can also be reduced.
  • the fourth to seventh embodiments will be described with reference to FIG.
  • the sprag 4 when the sprag 4 is tilted to disengage the inner ring 2 and the outer ring 3 from the sprag 4, the sprags 4 come into contact with each other, and the sprag 4 is further tilted. The case where it is regulated was explained.
  • the sprags when the sprags are tilted to disengage the inner ring 2 and the outer ring 3 from the sprags, the sprags are held between the inner cage and the outer cage. The case where the tilting of the sprag is further restricted will be described.
  • FIG. 8A is a schematic diagram of the main part of the clutch device 301 in the fourth embodiment
  • FIG. 8B is a schematic diagram of the main part of the clutch device 401 in the fifth embodiment.
  • FIG. 8D is a schematic diagram of a main part of the clutch device 601 in the seventh embodiment.
  • symbol is attached
  • the sprag 304 is tilted by the inner holders 305a and 305b and the outer holders 306a and 306b, and the engagement surfaces 304a and 304b of the sprag 304 are
  • the engagement between the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3 is released, the sprag 304 contacts the outer retainer 306a at the contact P1, and contacts the inner retainer 305b at the contact P2.
  • the sprag 304 is clamped by the inner holder 305b and the outer holder 306a, and further tilting is restricted.
  • the sprag 404 is tilted by the inner cages 405a and 405b and the outer cages 406a and 406b, and the engagement surfaces 404a and 404b of the sprag 404
  • the sprag 404 contacts the outer cages 406a and 406b at the contacts P1 and P2, and contacts the inner cage 405b at the contact P3.
  • the sprag 404 is held between the inner holder 405b and the outer holders 406a and 406b, and further tilting is restricted.
  • the sprag 504 is tilted by the inner cages 505a and 505b and the outer cages 506a and 506b, and the engagement surfaces 504a and 504b of the sprag 504
  • the sprag 504 contacts the outer cage 506a at the contact P1, and contacts the inner cage 505b at the contact P2.
  • the sprag 504 is held between the inner holder 505b and the outer holder 506a, and further tilting is restricted.
  • the sprag 604 is tilted by the inner cages 605a and 605b and the outer cages 606a and 606b, and the engagement surfaces 604a and 604b of the sprag 604 and
  • the sprag 604 contacts the outer retainer 606a at the contact P1, and contacts the inner retainers 605a and 605b at the contacts P2 and P3. .
  • the sprag 604 is held between the inner holders 605a and 605b and the outer holder 606a, and further tilting is restricted.
  • the sprag is sandwiched between the inner cage and the outer cage, and further tilting is restricted, so that as described in the first embodiment, It is not necessary to provide a positioning member or the like for restricting the relative movement amount of the cage and the outer cage, the first rotating parts 9 and 232, and the second rotating parts 11 and 242, and the apparatus configuration can be simplified.
  • the biasing force is applied so that the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3 and the engagement surfaces 4a, 4b of the sprag 4 are engaged by the biasing members 14, 114, 214.
  • the present invention is not necessarily limited to this, and the engagement between the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface 3a of the outer ring 3 and the engagement surfaces 4a and 4b of the sprag 4 is released. It is also possible to apply an urging force as described above. Also in this case, it is possible to switch between power transmission and transmission cancellation by applying a load against the urging force of the urging members 14, 114, 214 by the load applying devices 20, 220.
  • the load applying devices 20, 220 are driven to switch the direction in which the load is applied, so that the inner retainers 5, 205 and the outer retainers 6, 206 are switched. It is possible to switch between power transmission and transmission cancellation by changing the relative positions.
  • the actuator 221 is configured by a solenoid.
  • the present invention is not necessarily limited to this, and it is naturally possible to employ another power source.
  • Examples of other power sources include a pneumatic cylinder and a hydraulic cylinder.
  • the urging member 114 is constituted by a ribbon spring.
  • the urging member 114 is not necessarily limited to this, and other urging members can naturally be employed.
  • other urging members include a coil spring.
  • the case where the urging members 14 and 214 are constituted by torsion coil springs has been described.
  • the present invention is not necessarily limited to this, and other urging members may naturally be employed. Is possible. Examples of other urging members include a torsion bar.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)

Abstract

L'invention concerne un dispositif d'embrayage qui peut accroître la fiabilité de la commutation entre la transmission et l'isolation de la rotation et assurer un degré de liberté de conception par rapport à la disposition de composants et de matériel d'éléments. A l'aide d'un dispositif d'application de charge (20), une charge de contact est appliquée à une première section de rotation (9) reliée à un support interne (5) et à une seconde section de rotation (11) reliée à un support externe (6). Parallèlement à la charge de contact, le support interne (5) et le support externe (6) sont amenés à se déplacer relativement autour d'un axe (0), et la transmission et l'isolation de rotation d'une roue interne (2) et d'une roue externe (3) sont commutées. Il en résulte qu'il est possible d'accroître la fiabilité de la commutation entre la transmission et l'isolation de rotation comme il est possible d'assurer un degré de liberté de conception et de ne pas être susceptible à des contraintes sur la disposition de composants et du matériel d'éléments en comparaison avec les dispositifs qui entraînent un déplacement relatif sans contact au moyen d'une force magnétique.
PCT/JP2010/064478 2010-08-26 2010-08-26 Dispositif d'embrayage Ceased WO2012026020A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2012530484A JP5618449B2 (ja) 2010-08-26 2010-08-26 クラッチ装置
PCT/JP2010/064478 WO2012026020A1 (fr) 2010-08-26 2010-08-26 Dispositif d'embrayage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/064478 WO2012026020A1 (fr) 2010-08-26 2010-08-26 Dispositif d'embrayage

Publications (1)

Publication Number Publication Date
WO2012026020A1 true WO2012026020A1 (fr) 2012-03-01

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PCT/JP2010/064478 Ceased WO2012026020A1 (fr) 2010-08-26 2010-08-26 Dispositif d'embrayage

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JP (1) JP5618449B2 (fr)
WO (1) WO2012026020A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017214950A (ja) * 2016-05-30 2017-12-07 株式会社豊田中央研究所 オーバーランニングクラッチ
JP2020051536A (ja) * 2018-09-27 2020-04-02 Ntn株式会社 回転伝達装置
JP7417155B1 (ja) 2022-12-21 2024-01-18 株式会社椿本チエイン カムクラッチ
WO2024203105A1 (fr) * 2023-03-29 2024-10-03 株式会社椿本チエイン Embrayage sélectionnable

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS495129B1 (fr) * 1970-05-04 1974-02-05
JPH01122326U (fr) * 1988-02-08 1989-08-18
JPH05509147A (ja) * 1990-08-02 1993-12-16 イナ　ベルツラーゲル　シエツフレル　コマンデイトゲゼルシヤフト 切換え可能なスプラグ式フリーホイール装置
JPH0596570U (ja) * 1992-06-01 1993-12-27 株式会社フジユニバンス 一方向クラッチ
JPH07502799A (ja) * 1992-01-20 1995-03-23 シユタイル‐ダイムレル‐プーフ　アクチエンゲゼルシヤフト 選択的なフリーホイール作用を持つ両回転方向用クラツチ
WO2010087446A1 (fr) * 2009-01-30 2010-08-05 株式会社ユニバンス Embrayage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS495129B1 (fr) * 1970-05-04 1974-02-05
JPH01122326U (fr) * 1988-02-08 1989-08-18
JPH05509147A (ja) * 1990-08-02 1993-12-16 イナ　ベルツラーゲル　シエツフレル　コマンデイトゲゼルシヤフト 切換え可能なスプラグ式フリーホイール装置
JPH07502799A (ja) * 1992-01-20 1995-03-23 シユタイル‐ダイムレル‐プーフ　アクチエンゲゼルシヤフト 選択的なフリーホイール作用を持つ両回転方向用クラツチ
JPH0596570U (ja) * 1992-06-01 1993-12-27 株式会社フジユニバンス 一方向クラッチ
WO2010087446A1 (fr) * 2009-01-30 2010-08-05 株式会社ユニバンス Embrayage

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017214950A (ja) * 2016-05-30 2017-12-07 株式会社豊田中央研究所 オーバーランニングクラッチ
JP2020051536A (ja) * 2018-09-27 2020-04-02 Ntn株式会社 回転伝達装置
JP7085446B2 (ja) 2018-09-27 2022-06-16 Ntn株式会社 回転伝達装置
JP7417155B1 (ja) 2022-12-21 2024-01-18 株式会社椿本チエイン カムクラッチ
WO2024135499A1 (fr) * 2022-12-21 2024-06-27 株式会社椿本チエイン Embrayage à came
WO2024135027A1 (fr) * 2022-12-21 2024-06-27 株式会社椿本チエイン Embrayage à came
JP2024089323A (ja) * 2022-12-21 2024-07-03 株式会社椿本チエイン カムクラッチ
WO2024203105A1 (fr) * 2023-03-29 2024-10-03 株式会社椿本チエイン Embrayage sélectionnable

Also Published As

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JPWO2012026020A1 (ja) 2013-10-28
JP5618449B2 (ja) 2014-11-05

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