WO2010150771A1 - クラッチ及びモータ - Google Patents
クラッチ及びモータ Download PDFInfo
- Publication number
- WO2010150771A1 WO2010150771A1 PCT/JP2010/060532 JP2010060532W WO2010150771A1 WO 2010150771 A1 WO2010150771 A1 WO 2010150771A1 JP 2010060532 W JP2010060532 W JP 2010060532W WO 2010150771 A1 WO2010150771 A1 WO 2010150771A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- driven
- drive
- rotating body
- clutch
- shaft
- Prior art date
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 46
- 230000005540 biological transmission Effects 0.000 claims description 135
- 230000009467 reduction Effects 0.000 claims description 17
- 230000009471 action Effects 0.000 claims description 5
- 230000013011 mating Effects 0.000 claims 1
- 210000000078 claw Anatomy 0.000 description 21
- 230000007246 mechanism Effects 0.000 description 16
- 238000003825 pressing Methods 0.000 description 15
- 238000004519 manufacturing process Methods 0.000 description 8
- 239000000463 material Substances 0.000 description 7
- 238000005096 rolling process Methods 0.000 description 7
- 239000011347 resin Substances 0.000 description 6
- 229920005989 resin Polymers 0.000 description 6
- 239000005357 flat glass Substances 0.000 description 5
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 230000004323 axial length Effects 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- BGPVFRJUHWVFKM-UHFFFAOYSA-N N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] Chemical compound N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] BGPVFRJUHWVFKM-UHFFFAOYSA-N 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Images
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
-
- 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
- F16D13/00—Friction clutches
- F16D13/02—Friction clutches disengaged by the contact of a part mounted on the clutch with a stationarily-mounted member
-
- 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
- F16D41/00—Freewheels or freewheel clutches
- F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
- F16D41/063—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by moving along the inner and the outer surface without pivoting or rolling, e.g. sliding wedges
-
- 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
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
-
- 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
- F16D51/10—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as exclusively radially-movable brake-shoes
- F16D51/12—Brakes with outwardly-movable braking members co-operating with the inner surface of a drum or the like shaped as exclusively radially-movable 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
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/102—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction brakes
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/108—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
- E05F11/00—Man-operated mechanisms for operating wings, including those which also operate the fastening
- E05F11/38—Man-operated mechanisms for operating wings, including those which also operate the fastening for sliding windows, e.g. vehicle windows, to be opened or closed by vertical movement
- E05F11/50—Crank gear with clutches or retaining brakes, for operating window mechanisms
- E05F11/505—Crank gear with clutches or retaining brakes, for operating window mechanisms for vehicle windows
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
- E05Y2900/00—Application of doors, windows, wings or fittings thereof
- E05Y2900/50—Application of doors, windows, wings or fittings thereof for vehicles
- E05Y2900/53—Type of wing
- E05Y2900/55—Windows
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
- H02K7/1163—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion
- H02K7/1166—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion comprising worm and worm-wheel
Definitions
- the present invention includes a clutch that operates to transmit the rotational driving force of the drive shaft to the driven shaft while not transmitting the rotational force from the driven shaft to the drive shaft, and the drive shaft of the motor unit and the speed reduction mechanism of the speed reduction unit.
- the present invention relates to a motor connected via the clutch.
- a motor used as a drive source such as a power window device includes a motor unit that generates a rotational drive force that rotates a rotary shaft (drive shaft), and an output shaft that is connected to a load by reducing the rotational speed of the rotary shaft. Some have a speed reduction unit that outputs a rotational driving force.
- the rotation shaft provided in the motor unit and the worm shaft (output shaft) of the reduction mechanism provided in the reduction unit transmit the rotational driving force of the rotation shaft to the worm shaft, while rotating the rotational force from the worm shaft. It is connected via a clutch that operates so as not to transmit to the shaft.
- the rotating shaft and the worm shaft are connected via a mechanical clutch.
- the clutch includes a driving side rotating body that rotates integrally with the rotating shaft, a driven side rotating that rotates together with the worm shaft, and a plurality of parts for connecting the driving side rotating body and the driven side rotating body.
- the driving side rotating body and the driven side rotating body are arranged to face each other in the axial direction inside the cylindrical collar.
- a ball that receives a thrust load is disposed between the rotating shaft and the driven rotating body.
- three cylindrical rolling elements extending in the axial direction are arranged at equal angular intervals in the circumferential direction. These rolling elements are supported by a support member. Further, the support member supports the rolling element so as to face the drive side rotating body in the circumferential direction inside the collar. Further, the collar and the support member are fixed to a gear housing that houses the speed reduction mechanism by a stopper made of a metal plate material.
- the driving side rotating body and the driven side rotating body are engaged with each other in the rotation direction to rotate integrally. Therefore, the rotational driving force of the rotating shaft is transmitted to the worm shaft via the driving side rotating body and the driven side rotating body, and is decelerated and output by the speed reduction mechanism.
- the support member also engages with the drive side rotator in the rotation direction, whereby the support member rotates integrally with the drive side rotator together with the three rolling elements.
- a rotational force is applied to the worm shaft when the motor unit is stopped, the rolling member is sandwiched between the driven side rotating body and the collar and the rotation of the driven side rotating body is prevented. Transmission to the rotating shaft is prevented.
- the clutch described in Patent Document 1 including a driving side rotating body, a driven side rotating body, a collar, a ball, three rolling elements, a support member, and a stopper has a large number of parts and a complicated mechanism. . Therefore, facilities for manufacturing many parts are required, or the assembly process is complicated and the assembly process takes time, resulting in an increase in manufacturing cost.
- An object of the present invention is to provide a mechanical clutch having a simplified mechanism and a motor including the clutch.
- a clutch including a drive shaft, a drive side rotating body, a driven shaft, a driven side rotating body, a clutch housing, and a lock member.
- the drive-side rotator can rotate integrally with the drive shaft.
- the driven shaft is arranged coaxially with the drive shaft.
- the driven-side rotator can rotate integrally with the driven shaft.
- the lock member is disposed between the driving side rotating body and the driven side rotating body inside the clutch housing.
- the lock member includes a contact portion and a lock member. The abutting portion contacts and separates from the inner peripheral surface of the clutch housing.
- the lock member has a drive-side cam surface with which the drive-side rotator is brought into contact with the rotation direction.
- the lock member is pressed by the driven-side rotator and moved radially outward when the driven-side rotator is rotated. Abuts on the inner surface. As a result, the lock member is sandwiched between the clutch housing and the driven-side rotator to prevent further rotation of the driven-side rotator.
- the driving side rotating body presses the driving side cam surface in the rotating direction, and the action of the driving side cam surface causes the lock member to move radially inward to move the driven side Pressed against the rotating body.
- the lock member is interposed between the drive side rotary body and the driven side rotary body so that the drive side rotary body and the driven side rotary body are coupled to each other so as to be integrally rotatable via the lock member. Sandwiched between.
- FIG. 1 is a partial cross-sectional view of a motor according to the present invention.
- the partial expanded sectional view of the motor of FIG. 1 is an exploded perspective view of a clutch according to a first embodiment of the present invention.
- (A) And (b) is an exploded side view of the clutch of FIG. 4, respectively.
- (A) is a cross-sectional view of the clutch when the motor is stopped in the first embodiment (cross-sectional view taken along the line 6a-6a in FIG. 3), and
- FIG. (Sectional view taken along line 6b-6b in FIG. 3).
- FIG. (A) is a cross-sectional view of the clutch when driving the motor in the first embodiment (cross-sectional view taken along line 6a-6a in FIG. 3), and (b) is a cross-sectional view of the clutch when driving the motor in the first embodiment.
- the side view of the clutch of 2nd Embodiment which concerns on this invention.
- the disassembled perspective view of the clutch of FIG. (A) And (b) is sectional drawing of the clutch at the time of the motor stop in 2nd Embodiment, respectively (sectional drawing in alignment with line 10-10 in FIG. 8).
- (A) And (b) is sectional drawing of the clutch at the time of the motor drive in 2nd Embodiment, respectively (sectional drawing in alignment with line 10-10 in FIG. 8).
- FIG. 1 is a partial cross-sectional view of a motor of this embodiment used as a drive source for a power window device.
- This motor includes a motor unit 1, a speed reduction unit 2, and a clutch 3.
- the motor unit 1 has a bottomed cylindrical yoke housing 4, and a pair of magnets 5 are fixed to the inner peripheral surface thereof so as to face each other.
- an armature 6 is disposed inside the magnet 5 in the radial direction.
- the armature 6 has a rotating shaft 7 that extends along the axial direction at the radial center of the yoke housing 4, that is, a drive shaft.
- a bearing 8 is provided at the center of the bottom of the yoke housing 4, and the bearing 8 rotatably supports the base end of the rotating shaft 7.
- a cylindrical commutator 9 is fixed to a portion near the tip of the rotating shaft 7.
- a connecting portion 7 a having a pair of planes extending in parallel to each other is formed on the outer peripheral portion of the tip portion of the rotating shaft 7.
- a flange portion 4 a extending outward in the radial direction is formed in the opening of the yoke housing 4, and a brush holder 10 is fitted in the opening of the yoke housing 4.
- the brush holder 10 is formed by integrally forming a holder main body 10 a formed so as to close the opening of the yoke housing 4 and a connector portion 10 b protruding outward in the radial direction of the yoke housing 4.
- the holder body 10a is connected to the connector portion 10b by wiring.
- the holder body 10 a holds a pair of brushes 11 that are in sliding contact with the commutator 9.
- a bearing 12 is provided at the center of the holder body 10a, and the bearing 12 rotatably supports a portion of the rotating shaft 7 between the commutator 9 and the connecting portion 7a. Then, the external power source supplied to the brush 11 via the connector portion 10b is supplied to the coil winding of the armature 6 via the commutator 9, whereby the armature 6 (rotating shaft 7) rotates, that is, the motor portion 1 It is designed to rotate.
- the speed reduction unit 2 includes a gear housing 21 and a speed reduction mechanism 22 accommodated in the gear housing 21.
- the gear housing 21 is made of resin, and includes a fixing portion 21a for fixing the gear housing 21 to the motor portion 1 at a portion facing the motor portion 1 in the axial direction (the upper end portion in FIG. 1). Yes.
- the fixed portion 21 a has an outer shape similar to the outer shape of the flange portion 4 a of the yoke housing 4.
- a fitting recess 21b that opens toward the inside of the yoke housing 4 is formed in the fixed portion 21a.
- the gear housing 21 has a clutch housing recess 21c extending in the axial direction of the rotary shaft 7 at the bottom center of the fitting recess 21b, and a worm shaft housing portion extending in the axial direction of the rotary shaft 7 from the bottom center of the clutch housing recess 21c. 21d.
- the gear housing 21 also includes a wheel housing portion 21e on the side of the worm shaft housing portion 21d. The wheel housing portion 21e and the worm shaft housing portion 21d are connected at the central portion in the axial direction (longitudinal direction) of the worm shaft housing portion 21d.
- the substantially worm shaft 24 is accommodated in the worm shaft accommodating portion 21d.
- the worm shaft 24 is made of a metal material, and has a substantially cylindrical worm shaft main body 24a and a base end portion of the worm shaft main body 24a (that is, an end portion on the motor unit 1 side, an upper end portion in FIG. 1). And a driven side rotating body 24b formed integrally therewith.
- a screw tooth portion 24c is formed at the axial central portion of the worm shaft main body 24a. Both end portions in the axial direction of the worm shaft main body 24a are rotatably supported by a pair of metal bearings 25a and 25b which are arranged at both end portions in the axial direction of the worm shaft housing portion 21d. As shown in FIG.
- the worm shaft main body 24a in the worm shaft accommodating portion 21d is coaxial with the rotary shaft 7, that is, the central axis L1 of the rotary shaft 7 and the central axis of the worm shaft main body 24a. It arrange
- the driven-side rotator 24b extends along the axial direction from the base end surface of the worm shaft main body 24a.
- the shape of the cross section orthogonal to the axial direction is an elliptical shape, and is a columnar shape as a whole.
- an arc-shaped side surface that intersects the minor axis of the elliptical shape of the driven-side rotating body 24b is denoted by reference numeral “24e”.
- the center axis L3 of the driven side rotating body 24b coincides with the center axis L2 of the worm shaft main body 24a.
- the driven-side rotator 24b protrudes from the worm shaft housing portion 21d into the clutch housing recess 21c.
- the wheel accommodating portion 21e accommodates a disc-shaped worm wheel 26 that meshes with the screw tooth portion 24c of the worm shaft 24.
- the worm wheel 26 constitutes the speed reduction mechanism 22 together with the worm shaft 24.
- the worm wheel 26 is rotatable about an axis extending in a direction perpendicular to the central axis of the worm shaft main body 24a (a direction perpendicular to the paper surface in FIG. 1) at the radial central portion, and at the radial central portion.
- An output shaft 27 that rotates integrally with the worm wheel 26 is provided.
- a known window regulator (not shown) for raising and lowering the window glass of the vehicle is drivingly connected to the output shaft 27.
- the clutch housing recess 21c has a circular shape when viewed from the axial direction of the worm shaft 24, and the clutch 3 for connecting the rotary shaft 7 and the worm shaft 24 is housed therein.
- the clutch 3 includes a clutch housing 31, a driving side rotating body 32, a support member 33, a pair of locking members 34, and the driven side rotating body 24b.
- the clutch housing 31 is made of metal and has a cylindrical shape. As shown in FIG. 2, the outer diameter of the clutch housing 31 is formed to be substantially equal to the inner diameter of the clutch housing recess 21c, and the axial length of the clutch housing 31 is substantially equal to the depth of the clutch housing recess 21c. Are equally formed.
- the clutch housing 31 is housed in the clutch housing recess 21c in a state in which the outer circumferential surface of the clutch housing 31 is in contact with the inner circumferential surface of the clutch housing recess 21c and cannot rotate with respect to the gear housing 21. .
- the driving side rotating body 32 disposed inside the clutch housing 31 is made of a resin material, and is connected to the driving connecting portion 32 a to which the connecting portion 7 a of the rotating shaft 7 is connected.
- the part 32b and the pair of drive transmission parts 32c are integrally formed.
- the drive connecting portion 32a has a pair of flat surfaces extending in parallel with each other at the outer peripheral portion thereof.
- a support portion 32b is formed integrally with one end portion of the drive connecting portion 32a in the axial direction (the lower end portion in FIG. 4).
- the support portion 32b has a pair of flat surfaces extending in parallel with each other at the outer peripheral portion thereof. That is, the outer peripheral shape of the support portion 32b is the same as that of the drive connecting portion 32a, but is slightly larger in the radial direction than the drive connecting portion 32a. As shown in FIGS. 5A and 5B, the central axis L4 of the support portion 32b and the central axis L5 of the drive connecting portion 32a coincide with each other.
- the maximum dimension of the support portion 32b in the direction orthogonal to the central axis L4 is slightly smaller than the inner diameter of the clutch housing 31.
- a connecting hole that penetrates the drive connecting portion 32 a and the support portion 32 b in the directions of the central axes L ⁇ b> 4 and L ⁇ b> 5 is formed in the radial center portion of each of the drive connecting portion 32 a and the support portion 32 b.
- 32d is formed.
- the connecting hole 32d is a hole having a shape corresponding to the connecting portion 7a provided at the tip of the rotating shaft 7.
- a pair of drive transmission portions 32c extend along the axial direction from the end surface in the axial direction of the support portion 32b and from the end surface opposite to the drive coupling portion 32a (the lower end surface in FIG. 4).
- a pair of drive transmission part 32c is extended in the other side of the drive connection part 32a along the axial direction from the both sides of the support part 32b.
- the pair of drive transmission portions 32c extend from the two locations that are equiangularly spaced in the circumferential direction of the support portion 32b to the opposite side of the drive connecting portion 32a along the axial direction.
- the length from the proximal end to the distal end of the drive transmission portion 32 c is longer than the axial length of the clutch housing 31.
- the pair of drive transmission portions 32c are separated from each other in the direction orthogonal to the central axis L4. As shown in FIG. 3, the pair of drive transmission portions 32 c are inserted into the clutch housing 31.
- each drive transmission portion 32c has an arc shape along the inner peripheral surface of the clutch housing 31, and has diameters at both ends in the circumferential direction.
- a pair of transmitting portions 32e having a shape slightly bent toward the inner side in the direction is provided.
- Each transmission part 32e inclines so that it may approach the center part of the radial direction of the clutch housing 31 as it distances from the center part of the circumferential direction of the drive transmission part 32c.
- a pair of lock members 34 supported by a support member 33 so as to be movable in the radial direction (the radial direction of the rotary shaft 7 and the same as the radial direction of the clutch housing 31) are disposed between the pair of drive transmission portions 32c. Has been.
- the support member 33 disposed in the clutch housing 31 is formed of a resin material and has a rectangular tube shape.
- the support member 33 has holes extending along the radial direction of the clutch housing 31, and both ends of the holes form a pair of openings that open in opposite directions.
- the length between the openings ie, the length of the hole along the radial direction of the clutch housing 31
- the length between the openings is the length between the tips of the pair of transmission portions 32e in each drive transmission portion 32c (ie, the drive transmission portion 32c). Is shorter than the length between both ends in the circumferential direction) and longer than the length between the base end portions of the pair of transmission portions 32e in each drive transmission portion 32c. As shown in FIG.
- the support member 33 when the support member 33 is viewed from the axial direction of the clutch housing 31, the four corners of the support member 33 are chamfered. As shown in FIG. 4, the support member 33 has a pair of end walls facing each other in the axial direction of the rotating shaft 7, and a circular through hole 33 a is formed in the end wall. The inner diameter of the through hole 33a is slightly larger than the diameter of the portion of the worm shaft main body 24a excluding the screw tooth portion 24c.
- each lock member 34 has the same shape and size as each other, and are arranged symmetrically with respect to the central axis L6 of the clutch housing 31 inside the clutch housing 31. Yes. In addition, the length of each lock member 34 along the diameter direction of the clutch housing 31 is shorter than the half of the inner diameter of the clutch housing 31.
- Each lock member 34 is made of a resin material and has a substantially rectangular parallelepiped pressing portion 34a, an intermediate transmission portion 34b integrally formed on the radially outer side of the pressing portion 34a, and a radial direction of the intermediate transmission portion 34b. And an abutting portion 34c integrally formed on the outside.
- the pressing portion 34 a has a substantially rectangular plate shape corresponding to the inner peripheral surface of the support member 33, and the outer peripheral surface thereof is slidable on the inner peripheral surface of the support member 33. It is disposed inside the support member 33 in a contact state.
- a driven cam surface 34d that is recessed toward the contact portion 34c is formed on the side surface of the pressing portion 34a opposite to the contact portion 34c and on the side surface of the clutch housing 31 on the center axis L6 side (that is, the inner peripheral side). Is provided.
- the driven cam surface 34d extends from one end of the pressing portion 34a to the other end along the axial direction.
- Each driven cam surface 34d is symmetric with respect to a virtual plane (not shown) that passes through the center in the circumferential direction of the pressing portion 34a and extends in the radial direction. Further, the curvature of the driven cam surface 34d is smaller than the curvature of the pair of arcuate side surfaces 24e in the driven rotating body 24b, and has a gentle arc shape.
- An intermediate transmission portion 34b is integrally formed at an end portion of each pressing portion 34a opposite to the driven cam surface 34d, that is, an outer peripheral end portion.
- the intermediate transmission part 34b is formed so that the width in the circumferential direction gradually decreases from the proximal end on the pressing part 34a side toward the distal end on the outer peripheral side.
- the cross-sectional shape along the direction orthogonal to the axial direction has a trapezoidal shape.
- a pair of drive-side cam surfaces 34e that are inclined with respect to the radial direction (the radial direction of the rotary shaft 7 and the radial direction of the clutch housing 31) are formed at both ends in the circumferential direction of each intermediate transmission portion 34b. Has been.
- the pair of drive-side cam surfaces 34e are symmetric with respect to a virtual plane (not shown) that passes through the center in the circumferential direction of the contact portion 34c and extends in the radial direction, and the distance between each pair decreases as it goes radially outward. It extends to.
- Each drive side cam surface 34e extends from one end of the intermediate transmission portion 34b to the other end along the axial direction.
- the lock member 34 having the drive side cam surface 34e and the drive side rotating body 32 (drive transmission portion 32c) constitute a drive side cam mechanism.
- Each contact portion 34c extends linearly from one end of the intermediate transmission portion 34b to the other end along the axial direction, and forms a ridge toward the radially outer side.
- Each intermediate transmission portion 34b has a semicircular cross-sectional shape along a direction orthogonal to the axial direction.
- the pair of lock members 34 as described above are arranged inside the clutch housing 31 and between the pair of drive transmission portions 32 c of the drive side rotating body 32. ing. Specifically, the pair of lock members 34 are inserted into the support members 33 from the pair of openings of the support member 33 so that the driven cam surfaces 34d face each other. And in the clutch housing 31, the support member 33 in which a pair of lock member 34 was inserted is arrange
- the contact part 34c and the intermediate transmission part 34b that protrude radially outward from the opening of the support member 33 are the transmission part 32e of one drive transmission part 32c adjacent to the circumferential direction and the transmission part 32e of the other drive transmission part 32c.
- the pair of drive-side cam surfaces 34e in each lock member 34 is disposed so as to be able to contact the pair of transmission portions 32e and the drive-side rotator 32 in the rotational direction.
- the lock member 34 is movable along the radial direction of the rotary shaft 7 (that is, the same as the radial direction of the clutch housing 31) while being guided by the support member 33. When the lock member 34 moves to the radially outer end, The contact portion 34 c comes into contact with the inner peripheral surface of the support member 33.
- the distance between the driven cam surfaces 34d facing each other is set to be a shorter value.
- the driven-side rotating body 24b passes between the pair of driven cam surfaces 34d that are radially opposed to each other inside the clutch housing 31 so as to be sandwiched between the pair of lock members 34 through the pair of through holes 33a of the support member 33. Is arranged.
- the driven side rotating body 24b has a pair of side surfaces 24e facing the driven side cam surface 34d in the diameter direction of the clutch housing 31 (facing in the radial direction of the rotating shaft 7).
- the driven side rotating mechanism 24b and the pair of locking members 34 each having a driven side cam surface 34d constitute a driven side cam mechanism.
- the worm shaft 24 having the rotating shaft 7, the clutch housing 31, the driving side rotating body 32, and the driven side rotating body 24b is coaxial, that is, respectively.
- the central axis of each other is located on the same straight line.
- the cross section of the driven side rotating body 24b is elliptical
- a pair of arc-shaped side surfaces intersecting with the major axis of the elliptical shape are driven sides of the pair of lock members 34.
- the cam surface 34d is pressed radially outward (see arrow Y in FIG. 6B).
- the pair of lock members 34 pressed outward in the radial direction by the driven-side rotating body 24 b move toward the radially outer side of the clutch housing 31 while being guided by the pair of support members 33, and contact the lock member 34.
- the portion 34 c comes into contact with the inner peripheral surface of the clutch housing 31.
- the lock member 34 When the abutting portion 34c abuts on the inner peripheral surface of the clutch housing 31, the lock member 34 is prevented from moving further outward in the radial direction, so that the lock member 34 is connected to the clutch housing 31 and the driven side rotating body 24b. It is sandwiched between (intervened). Therefore, the lock member 34 sandwiched between the clutch housing 31 and the driven side rotating body 24b prevents further rotation of the driven side rotating body 24b. That is, a frictional force is generated between the contact portion 34 c of the lock member 34 and the inner peripheral surface of the clutch housing 31 so as to prevent the driven side rotating body 24 b from rotating. As a result, rotation of the worm shaft 24 is prevented and transmission of rotational driving force from the worm shaft 24 to the rotating shaft 7 is prevented.
- the two lock members 34 are separated from each other.
- the two drive side cam surfaces 34e facing the two transmission portions 32e in each drive transmission portion 32c are separated from each other along the diameter direction of the clutch housing 31.
- the two drive transmission portions 32c of the drive side rotating body 32 are arranged at neutral positions that are the central portions in the circumferential direction between the two lock members 34, respectively.
- the transmission unit 32e of the drive side rotating body 32 is connected to the drive side cam surface 34e. Can be immediately pressed in the direction of rotation.
- the contact portion 34c of the lock member 34 moves radially inward from the inner peripheral surface of the clutch housing 31 (see arrow ⁇ ).
- the pair of lock members 34 move toward the radially inner side of the clutch housing 31 while being guided by the pair of support members 33.
- the driven cam surfaces 34d of the pair of lock members 34 come into contact with the pair of arcuate side surfaces 24e of the driven side rotating body 24b from the radially outer side of the clutch housing 31.
- the pair of lock members 34 are pressed toward the driven-side rotator 24b by the component force F1, and sandwich the driven-side rotator 24b.
- the pair of lock members 34 sandwiching the driven-side rotator 24b, together with the driven-side rotator 24b, is driven around the central axis L1 of the rotating shaft 7 by the circumferential component force F2 of the pressing force F. It rotates integrally with the rotating body 32 (see arrow ⁇ ). That is, the driving side rotating body 32 and the driven side rotating body 24b are connected via the lock member 34 sandwiched between the driving side rotating body 32 and the driven side rotating body 24b, and rotate integrally. At this time, the support member 33 rotates integrally with the driving side rotating body 32 and the driven side rotating body 24 b via the lock member 34.
- the rotational driving force of the rotating shaft 7 is transmitted to the driven side rotating body 24 b via the driving side rotating body 32 and the lock member 34. Then, the worm shaft 24 rotates, and the worm wheel 26 and the output shaft 27 rotate according to the rotation. Accordingly, the window regulator that is drivingly connected to the output shaft 27 is operated, and the window glass is opened / closed (lifted / lowered). Even when the rotary shaft 7 is rotationally driven (that is, reversely rotated) in the direction opposite to the example shown in FIGS. 7A and 7B, the rotational driving force is similarly applied to the worm shaft 24. Is transmitted to.
- the clutch 3 includes six parts including a clutch housing 31, a driving side rotating body 32, a support member 33, a pair of locking members 34, and a driven side rotating body 24b. Therefore, the number of parts is reduced as compared with the prior art. Therefore, the mechanism of the clutch 3 is simplified.
- the pair of lock members 34 are pressed by the driven-side rotator 24b to which the rotational force is applied when the drive-side rotator 32 is not rotated, and move toward the outer side in the radial direction. At the time of rotation, the drive-side rotator 32 is pressed from the rotation direction, moved toward the driven-side rotator 24b, and pressed against the driven-side rotator 24b.
- the clutch 3 can transmit the rotational driving force of the rotating shaft 7 to the worm shaft 24 with a simple configuration using a cam mechanism, and can prevent the rotation from the worm shaft 24 from being transmitted to the rotating shaft 7.
- the clutch 3 with a reduced number of parts and a simplified mechanism requires less equipment for manufacturing and can reduce the time required for the assembly process, resulting in a reduction in manufacturing cost. be able to. As a result, the manufacturing cost of the motor having the clutch 3 can be reduced.
- the drive-side cam surfaces 34e that are in contact with the transmission portion 32e of the drive-side rotator 32 from the rotational direction are provided on both sides of the contact portion 34c in the circumferential direction. Accordingly, in both cases of forward rotation and reverse rotation of the drive side rotator 32 due to normal rotation and reverse rotation of the rotary shaft 7, the transmission portion 32e of the drive side rotator 32 is brought into contact with the drive side cam surface 34e to The lock member 34 can be moved radially inward.
- the pair of drive side cam surfaces 34e in each lock member 34 are provided symmetrically on both sides in the circumferential direction of the contact portion 34c, the drive side rotating body 32 can be rotated forward or backward. The radial movement of the lock member 34 is performed in the same manner.
- the pair of lock members 34 are arranged so as to sandwich the driven-side rotating body 24b, and the lock members 34 move along the radial direction of the rotating shaft 7. Therefore, when the driving side rotating body 32 is not rotating, the contact portions 34c of the pair of lock members 34 that are moved radially outward so as to be separated from each other by the rotation of the driven side rotating body 24b are formed on the inner peripheral surface of the clutch housing 31. Each abuts. And since a pair of lock member 34 is interposed between the driven side rotary body 24b and the clutch housing 31, the further rotation of the driven side rotary body 24b is prevented more stably.
- the pair of lock members 34 moved radially inward so as to approach each other press the side surface 24e of the driven side rotator 24b.
- the rotational driving force can be transmitted to the driven side rotating body 24b.
- a support member 33 is attached to the pair of lock members 34, and the support member 33 moves the lock member 34 along the radial direction as the drive side rotating body 32 and the driven side rotating body 24b rotate. It is stabilized. Accordingly, the rotation driving force is transmitted to the driven side rotating body 24b via the lock member 34 when the driving side rotating body 32 rotates, and the rotation of the driven side rotating body 24b is prevented when the driving side rotating body 32 is not rotating. Is performed stably. Further, since the support member 33 rotates integrally with the driving side rotating body 32 and the driven side rotating body 24b via the lock member 34, the support member 33 can always support the lock member 34.
- the driven-side rotating body 24b has a columnar shape, and each of the pair of lock members 34 has a driven-side cam surface 34d that is radially opposed to the driven-side rotating body 24b on the side surface opposite to the contact portion 34c.
- each of the pair of lock members 34 has a driven-side cam surface 34d that is radially opposed to the driven-side rotating body 24b on the side surface opposite to the contact portion 34c.
- the driven-side rotator 24b When the driven-side rotator 24b is rotated while the drive-side rotator 32 is not rotating, the driven-side rotator 24b presses the driven-side cam surface 34d toward the radially outer side, and the lock member 34 has a diameter. Move outward in the direction. As described above, when the driving side rotating body 32 is not rotated, the lock member 34 easily moves radially outward by the action of the driven side rotating body 24b and the driven side cam surface 34d having a columnar shape.
- the clutch 3 includes a pair of locking members 34 arranged so as to sandwich the driven side rotating body 24b having a columnar shape.
- the pair of locking members 34 receives the rotational driving force of the driving side rotating body 32 to sandwich the driven side rotating body 24b having a columnar shape on the driven side cam surface 34d. Therefore, transmission of the rotational driving force via the lock member 34 is performed more stably.
- the driven-side rotator 24b is simply formed with an elliptical cross section, and is easy to form.
- the driven-side rotating body 24b provided in the metallic worm shaft 24 can be easily formed by cutting.
- the driven-side rotating body 24b having an elliptical cross section can easily press the lock member 34 radially outward in accordance with the rotation.
- Each driven-side cam surface 34d has an arc shape that can sandwich the side surface 24e of the driven-side rotating body 24b when viewed from the axial direction. Therefore, when the driving side rotating body 32 rotates, the pair of lock members 34 can sandwich the driven side rotating body 24b more stably. Further, when the drive side rotator 32 is not driven, the lock member 34 is smoothly moved radially outward along with the rotation of the driven side rotator 24b.
- the driven-side rotating body 24b Since the driven-side rotating body 24b has a columnar shape with an elliptical cross section, the driven-side rotating body 24b can be downsized in the radial direction as compared with the conventional driven-side rotating body and has a simple shape. Accordingly, it is possible to reduce the mold cost, material cost and processing cost for forming the driven side rotating body 24b.
- the conventional clutch is configured to prevent the rotation of the driven side rotating body by utilizing the wedge effect caused by the rolling body being sandwiched between the driven side rotating body and the collar when the rotating shaft is driven. Therefore, high component accuracy may be required for the components of the clutch.
- the clutch 3 of the present embodiment is configured to prevent the rotation of the driven-side rotating body 24b by using the frictional force between the lock member 34 and the clutch housing 31, and therefore, the components of the clutch 3 are the conventional components. It does not have to be as accurate as the clutch. Therefore, the manufacturing cost of the clutch 3 can be reduced.
- the clutch 51 of the present embodiment includes a clutch housing 31, a driving side rotating body 52, a support member 53, a pair of locking members 34, a driven side rotating body 54, and a steel ball 55.
- the driving side rotating body 52 disposed inside the clutch housing 31 is made of a resin material, and the driving connecting portion 32a, the supporting portion 32b, and the pair of driving transmission portions 32c are integrally formed. Being done.
- a pair of transmission convex portions 52a are formed on the inner peripheral surface of the connection hole 32d that penetrates the central portions of the drive connection portion 32a and the support portion 32b in the direction of the central axis L4. Is formed.
- the pair of transmission convex portions 52a are integrally provided on a pair of flat surface portions 32f extending in parallel with each other on the inner peripheral surface of the support portion 32b that defines the coupling hole 32d.
- each transmission convex part 52a protrudes toward the center of the coupling hole 32d.
- each transmission convex part 52a is the circumferential direction as the shape seen from the center axis line L4 direction of the support part 32b goes to the front-end
- both end surfaces in the circumferential direction of each transmission convex portion 52a are drive side transmission surfaces 52b and 52c extending in parallel with the central axis L4.
- the pair of transmission convex portions 52a of the present embodiment includes a drive side transmission surface 52b on the clockwise direction side when viewed from the drive connecting portion 32a side (that is, the state shown in FIG. 10A), and is counterclockwise.
- a drive-side transmission surface 52c is provided on the circumferential direction side.
- a pair of engagement claws extending along the central axis L4 of the support portion 32b at the center portion in the circumferential direction at the axial front ends of the pair of drive transmission portions 32c. 56 is formed.
- the pair of engaging claws 56 are formed 180 degrees apart from each other in the circumferential direction in the driving side rotating body 52.
- Each engagement claw 56 includes a square columnar engagement shaft portion 56a extending along the axial direction of the rotation shaft 7 from the distal end surface of the drive-side rotator 52, and radially inward from the distal end portion of the engagement shaft portion 56a. And a protruding engaging projection 56b.
- each engagement claw 56 the radially outer side surface of the engagement shaft portion 56a is flush with the radially outer side surface of the drive transmission portion 32c, and the radially inner side of the engagement shaft portion 56a. This side surface is located on the radially outer side than the radially inner side surface of the drive transmission portion 32c.
- Each engaging claw 56 can tilt in the radial direction of the rotating shaft 7 by elastic deformation.
- the support member 53 disposed between the pair of drive transmission portions 32c is formed of a resin material in the same manner as the support member 33 of the first embodiment, and has a rectangular cylindrical shape. I am doing.
- the support main body 53a constituting the support member 53 has the same shape as the support member 33 of the first embodiment. That is, the support member 53 has a pair of end walls facing each other in the axial direction of the rotary shaft 7, and a circular through hole 33 a is formed in the end wall.
- a substantially annular base portion 53b that extends radially outward is integrally formed at the lower end portion of the support main body portion 53a.
- the base portion 53b extends perpendicularly to the axial direction of the rotary shaft 7, and its outer diameter is slightly larger than the outer diameter of the entire pair of drive transmission portions 32c in the drive-side rotating body 52 and the clutch housing 31. It is formed slightly smaller than the inner diameter.
- the thickness of the base portion 53b is substantially equal to the length of the portion of the engaging claw 56 excluding the engaging convex portion 56b, that is, the axial length of the engaging shaft portion 56a.
- each pair of the restriction portions 53c corresponds to each drive transmission portion 32c of the drive side rotating body 52.
- the other pair of restricting portions 53c is formed at a position 180 degrees away from the one pair of restricting portions 53c in the circumferential direction.
- Each restricting portion 53c extends along the axial direction of the rotating shaft 7 so that the tip thereof faces upward (on the driving side rotating body 52 side).
- An interval T between the pair of restricting portions 53 c is formed to be larger than a circumferential width t of the engaging claw 56.
- the curvature of the regulating surface 53d which is the inner circumferential surface of each regulating portion 53c, is formed to be equal to the curvature of the outer circumferential surface of the portion between the transmission portions 32e in the drive transmission portion 32c (see FIG. 10B).
- the restricting surfaces 53d of all restricting portions 53c are located on the same circle (not shown) centered on the center of the base portion 53b, and the diameters of the circles passing through the restricting surfaces 53d of all restricting portions 53c are: It is equal to the outer diameter of the entire pair of drive transmission portions 32c in the drive side rotating body 52.
- the outer diameter of the base portion 53b including the restricting portion 53c is slightly smaller than the inner diameter of the clutch housing 31.
- an engagement recess 53e is formed between the restriction portions 53c that make a pair in the base portion 53b. These two engaging recesses 53e are for engaging the two engaging claws 56 of the driving side rotating body 52 in order to integrate the driving side rotating body 52 and the support member 53.
- Each engaging recess 53e is formed so as to be recessed radially inward from the outer peripheral edge of the base portion 53b. As shown in FIG. 8, in the base portion 53b, the radial length at the two engaging recesses 53e is equal to the interval between the engaging shaft portions 56a of the pair of engaging claws 56.
- the circumferential width of each engaging recess 53e is formed to be equal to the interval T between the pair of restricting portions 53c.
- the support member 53 is disposed with respect to the drive-side rotating body 52 so that the support main body 53a having the pair of lock members 34 disposed therein is disposed between the pair of drive transmission portions 32c.
- the engaging claw 56 provided at the tip of each drive transmission portion 32c is engaged with the corresponding engaging recess 53e so as to be integrated with the driving side rotating body 52.
- the support member 53 inserts the support main body portion 53 a between the pair of drive transmission portions 32 c from the distal end side of the pair of drive transmission portions 32 c and also forms a pair of engagement recesses. It arrange
- the base portion 53b (engagement recess 53e) and the engagement claw 56 are snap-fit engaged by moving the base portion 53b over the engagement projection 56b of the engagement claw 56 from the support main body portion 53a side.
- the support member 53 and the drive side rotating body 52 are assembled together.
- the pair of restricting portions 53c are disposed on the radially outer side of the outer peripheral surface of each drive transmitting portion 32c.
- the restricting surfaces 53d of the pair of restricting portions 53c are in contact with the outer peripheral surfaces at the distal end portions of the respective drive transmitting portions 32c. Therefore, the movement of each drive transmission portion 32c in the radial direction is restricted by the restriction portion 53c.
- the drive side rotating body 52 is within the range of the interval T between the restricting portions 53c.
- the support member 53 can be rotated in the circumferential direction.
- the driven side rotating body 54 extends along the axial direction from the base end surface of the worm shaft main body 24a and has an elliptical cross-sectional shape orthogonal to the axial direction. It has a columnar shape.
- the center axis L7 of the driven side rotating body 54 coincides with the center axis L2 of the worm shaft main body 24a.
- the driven-side rotating body 54 passes through the pair of through-holes 33a of the support member 53 and is interposed between the two driven-side cam surfaces 34d that are radially opposed to each other inside the clutch housing 31 so as to be sandwiched between the pair of lock members 34. Is arranged.
- the distal end portion of the driven-side rotator 54 is inserted into the coupling hole 32d of the support portion 32b, and between the distal end surface of the rotating shaft 7 and the distal end surface of the driven-side rotator 54, A steel ball 55 that receives the thrust load of the worm shaft 24 is disposed.
- a pair of transmission recesses 54a is formed at the distal end of the driven-side rotator 54, and in the pair of transmission recesses 54a, the drive-side rotator 52 is provided.
- the tip portions of the pair of transmission convex portions 52a provided in the are respectively inserted.
- the pair of transmission recesses 54 a are opened outward in the radial direction in the cross-sectional short direction of the drive-side rotator 52. Further, the pair of transmission recesses 54a are open toward the distal end side (the upper side in FIG. 9) of the drive side rotating body 52.
- Each of the transmission recesses 54a has a shape as viewed from the direction of the central axis L7 of the driven-side rotator 54, and the width in the circumferential direction becomes narrower from the radially outer opening toward the radially inner bottom surface. It has a shape. Further, the inner side surfaces of both ends in the circumferential direction of each transmission recess 54 a form driven side transmission surfaces 54 b and 54 c that are parallel to the central axis L 7 of the driven side rotating body 54.
- Each transmission recess 54a of the present embodiment includes a driven-side transmission surface 54b in the clockwise direction when viewed from the front end side of the driven-side rotator 54, that is, in the state shown in FIG. A driven side transmission surface 54c is provided.
- the transmission convex portions 52a arranged in the respective transmission concave portions 54a have a clockwise driving side transmission surface 52b as viewed from the distal end side of the driven side rotating body 54.
- the counterclockwise drive-side transmission surface 52c faces the counterclockwise driven-side transmission surface 54c of the transmission recess 54a in the circumferential direction.
- the driving-side transmission surface 52b and the driven-side transmission surface 54b facing each other, and the driving-side transmission surface 52c and the driven-side transmission surface 54c face each other when a rotational force is applied from the driving-side rotating body 52 side.
- the inclination angle and the like are set so that the surfaces facing each other are not in contact with each other. For this reason, when a rotational force is applied from the driving side rotating body 52 side, the driving side transmission surface 52b and the driven side transmission surface 54b facing each other, and the driving side transmission surface 52c and the driven side transmission surface 54c contact each other. In contact therewith, the rotational driving force is transmitted from the driving side transmission surfaces 52b and 52c to the driven side rotating body 54 via the driven side transmission surfaces 54b and 54c.
- both ends in the major axis direction of the elliptical shape have the diameter of the driven-side cam surface 34d of the pair of lock members 34. Press toward the outside in the direction. Then, the pair of lock members 34 pressed outward in the radial direction by the driven-side rotator 54 move toward the radially outer side of the clutch housing 31 while being guided by the pair of support main body portions 53a.
- the contact portion 34 c contacts the inner peripheral surface of the clutch housing 31.
- the lock member 34 When the abutting portion 34 c abuts on the inner peripheral surface of the clutch housing 31, the lock member 34 is prevented from moving further outward in the radial direction. It is sandwiched between (intervened). Therefore, the lock member 34 sandwiched between the clutch housing 31 and the driven side rotating body 54 prevents further rotation of the driven side rotating body 54. That is, a frictional force is generated between the contact portion 34 c of the lock member 34 and the inner peripheral surface of the clutch housing 31 so as to prevent the driven side rotating body 54 from rotating. As a result, rotation of the worm shaft 24 is prevented and transmission of rotational driving force from the worm shaft 24 to the rotating shaft 7 is prevented.
- the frictional force at this time is the frictional force T1 in the radial direction of the pressing force T applied from the driven side rotating body 54 to the locking member 34 (the component force in the direction along the moving direction of the locking member 34 at the pressing force T) and the friction.
- ⁇ the coefficient in the direction along the moving direction of the locking member 34 at the pressing force T
- ⁇ ⁇ T1 the coefficient in the radial direction of the pressing force T applied from the driven side rotating body 54 to the locking member 34
- ⁇ ⁇ T1 the frictional force in the radial direction of the pressing force T applied from the driven side rotating body 54 to the locking member 34 (the component force in the direction along the moving direction of the locking member 34 at the pressing force T) and the friction.
- ⁇ ⁇ T1 the coefficient in the radial direction of the pressing force T applied from the driven side rotating body 54 to the locking member 34 (the component force in the direction along the moving direction of the locking member 34 at the pressing force T) and the friction.
- ⁇ ⁇ T1 the coefficient in
- the driven-side rotating body 54 is about to rotate from the output shaft 27 (see FIG. 1) side in the opposite direction to the example shown in FIGS. 10 (a) and 10 (b). Even in this case, the rotation is similarly prevented.
- the drive side cam surface 34e is inclined with respect to the radial direction. Due to the radial component force P2 of the pressing force P of the transmission portion 32e, the contact portion 34c of the lock member 34 moves in a direction away from the inner peripheral surface of the clutch housing 31 (see arrow ⁇ 2). At this time, the pair of lock members 34 move toward the radially inner side of the clutch housing 31 while being guided by the pair of support members 53. The driven cam surfaces 34 d of the pair of lock members 34 come into contact with the pair of arcuate side surfaces 24 e of the driven side rotating body 54 from the radially outer side of the clutch housing 31.
- the pair of driven-side cam surfaces 34d abut the driven-side rotating body 54 along the elliptical short axis direction of the driven-side rotating body 54. Further, the pair of lock members 34 are pressed toward the driven-side rotator 54 by the component force P ⁇ b> 2 and sandwich the driven-side rotator 54.
- the drive-side rotator 52 (see arrow ⁇ 2). That is, the driving side rotating body 52 and the driven side rotating body 54 are further connected to the driving side transmitting surface 52b and the driven side via the lock member 34 sandwiched between the driving side rotating body 52 and the driven side rotating body 54. It is connected via the transmission surface 54b and rotates integrally.
- the support member 53 rotates integrally with the driving side rotating body 52 and the driven side rotating body 54 via the lock member 34.
- the rotational driving force of the rotating shaft 7 is transmitted to the driven side rotating body 54 via the driving side rotating body 52 and the lock member 34. Then, the worm shaft 24 rotates, and the worm wheel 26 and the output shaft 27 rotate according to the rotation. Accordingly, the window regulator that is drivingly connected to the output shaft 27 is operated, and the window glass is opened / closed (lifted / lowered). Even when the rotary shaft 7 is rotationally driven (that is, reversely rotated) in the opposite direction to the example shown in FIGS. 11A and 11B, the rotational driving force is similarly applied to the worm shaft 24. Is transmitted to.
- This embodiment has the following advantages in addition to the advantages described in (1) to (11) of the first embodiment. (12)
- the movement of the pair of drive transmission portions 32c to the outside in the radial direction is restricted by the restriction portions 53c provided on the support member 53. Therefore, when the drive side rotator 52 rotates, the drive transmission portion 32 c can efficiently press the drive side cam surface 34 e in the rotation direction of the drive side rotator 52 with the rotation of the drive side rotator 52.
- the drive-side transmission surfaces 52 b and 52 c provided on the drive-side rotator 52 and the driven-side transmission surfaces 54 b and 54 c provided on the driven-side rotator 54 are the same drive side when the drive-side rotator 52 rotates. By abutting each other in the rotation direction of the rotating body 52, the rotational driving force of the driving side rotating body 52 can be efficiently transmitted to the driven side rotating body 54. Further, rotation transmission from the driving side rotating body 52 to the driven side rotating body 54 can be performed using the driving side transmitting surfaces 52b and 52c and the driven side transmitting surfaces 54b and 54c.
- the rotation transmission from the driving side rotating body 32 to the driven side rotating body 24b is performed by a pair of the lock member 34 and the driven side rotating body 24b.
- the dimensional accuracy of each member can be relaxed, and noise and vibration can be reduced.
- each embodiment of the present invention may be modified as follows.
- the present invention has been described by taking the motor used as the drive source of the power window device as an example.
- the present invention may be applied to a motor including the part 1 and the speed reduction part 2 having the worm shaft 24.
- the clutches 3 and 51 may be used in an apparatus including a drive shaft that is rotationally driven and a driven shaft to which the rotational drive force of the drive shaft is transmitted.
- the pair of locking members 34 when the driving side rotating body 32 is not rotating, the pair of locking members 34 are sandwiched between the driven side rotating body 24 b and the inner peripheral surface of the clutch housing 31, It may be formed so as to allow rotation of the driven rotary body 24b relative to the pair of lock members 34 in a state where a desired frictional force is generated between the contact portion 34c and the inner peripheral surface of the clutch housing 31. That is, when the driven side rotating body 24 b is rotated when the driving side rotating body 32 is not rotating, the driven side rotating body 24 b is rotated by the frictional force generated between the contact portion 34 c and the inner peripheral surface of the clutch housing 31. This makes it difficult to rotate the pair of lock members 34 relative to the clutch housing 31.
- the clutch 3 can be easily designed because the pair of lock members 34 and the driven-side rotator 24b are simply formed in a shape suitable for generating a desired frictional force. As a result, the manufacturing cost of the clutch 3 can be further reduced. The same applies to the clutch 51 of the second embodiment.
- the pair of lock members 34 are sandwiched between the driven-side rotating body 24b and the inner peripheral surface of the clutch housing 31, and the abutment of the lock member 34 is performed.
- the driven side rotating body 24b is allowed to rotate with respect to the pair of lock members 34 in a state where a desired frictional force is generated between the portion 34c and the inner peripheral surface of the clutch housing 31, and is driven and connected to the worm wheel 26.
- the rotational force from the output shaft 27 is applied to at least the meshing load between the worm wheel 26 and the screw tooth portion 24c of the worm shaft main body 24a, and the friction between the worm shaft main body 24a and the bearings 25a and 25b that support the worm shaft main body 24a. It may be configured to prevent transmission to the rotating shaft 7 due to the load and the rotational load of the clutch 3.
- the rotational load of the clutch 3 means a frictional force (friction load) generated inside the clutch 3. In this way, the rotational driving force of the rotary shaft 7 is transmitted to the output shaft 27 via the clutch 3, the worm shaft main body 24a having the screw teeth 24c and the worm wheel 26, while the rotational force from the output shaft 27 is transmitted.
- the loads that prevent the rotational force from the output shaft 27 from being transmitted to the rotating shaft 7 include the meshing load between the worm wheel 26 and the screw tooth portion 24c, and the friction load between the worm shaft main body 24a and the bearings 25a and 25b.
- it may include a friction load of other sliding portions in the motor. The same applies to the motor provided with the clutch 51 of the second embodiment.
- the cross section orthogonal to the axial direction of the driven side rotating bodies 24b and 54 has an elliptical shape, and the driven side rotating bodies 24b and 54 have a columnar shape as a whole.
- the cross-sectional shape orthogonal to the axial direction of the driven-side rotating bodies 24b and 54 may be flat as long as the lock member 34 has a shape that can be pressed radially outward with its own rotation.
- the cross section orthogonal to the axial direction may be rectangular, and the driven side rotating bodies 24b and 54 may be columnar as a whole.
- the driven cam surface 34d is formed in an arc shape, but may be in a planar shape parallel to the axial direction.
- the clutch 3 includes a pair of lock members 34, but may include a single lock member 34. In this case, at the time of rotation of the driving side rotating body 32, one locking member 34 pressed against the driving side rotating body 32 is pressed against the driven side rotating body 24b, so that the rotational driving force of the driving side rotating body 32 is locked. 34 to the driven rotating body 24b.
- the clutch 3 may be configured to include three lock members 34. In this case, three drive transmission portions 32 c are provided in the drive side rotating body 32 according to the number of the lock members 34. The same applies to the clutch 51 of the second embodiment.
- the pair of engaging claws 56 that engage and integrate the driving side rotating body 52 and the support member 53 in the axial direction are provided on the driving side rotating body 52.
- the pair of engaging claws 56 may be provided on the support member 53 so as to be able to engage with the driving side rotating body 52 in the axial direction.
- the pair of engaging claws 56 and the pair of engaging recesses 53e may be formed in at least one of the driving side rotating body 52 and the support member 53, and the shape thereof is not limited to the shape of the second embodiment. .
- the pair of engaging claws 56 and the pair of engaging recesses 53e allow the drive-side rotating body 52 and the support member 53 to be pivoted while allowing the relative rotation of the support member 53 and the driving-side rotating body 52 in the circumferential direction. It is formed to engage in the direction.
- the support member 53 includes two restricting portions 53c corresponding to the drive transmission portions 32c.
- one restriction portion 53c may be provided corresponding to each drive transmission portion 32c, or three or more restriction portions 53c may be provided corresponding to each drive transmission portion 32c.
- the lock member 34 is supported by the support member 33. However, the lock member 34 moves along the radial direction as the driving side rotating body 32 and the driven side rotating body 24b rotate. If possible, the support member 33 may be omitted. Further, in the clutch 51 of the second embodiment, if the lock member 34 can move along the radial direction along with the rotation of the driving side rotating body 52 and the driven side rotating body 54, the support member 53. May be omitted.
- each lock member 34 includes a pair of drive-side cam surfaces 34e.
- each lock member 34 may be configured to include one drive-side cam surface 34e.
- the motor unit 1 is configured to rotate the rotating shaft 7 only in one direction, and the drive-side cam surface 34e is formed to be positioned forward of the rotating shaft 7 in the rotation direction with respect to the drive transmission unit 32c. Is done.
- the driven-side rotators 24b and 54 may be formed separately from the worm shaft main body 24a.
- the driven-side rotators 24b and 54 and the worm shaft main body 24a are formed so as to be integrally rotatable (engaged in the rotational direction).
- the drive side rotating bodies 32 and 52 may be formed integrally with the rotating shaft 7.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Engineering (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Mechanical Operated Clutches (AREA)
- Gear Transmission (AREA)
Abstract
Description
図1は、パワーウインド装置の駆動源として用いられる本実施形態のモータの部分断面図である。このモータは、モータ部1、減速部2及びクラッチ3を備えている。
図6(a)及び図6(b)に示すように、モータ部1の停止時、即ち回転軸7の非回転駆動時であって駆動側回転体32の非回転時に、負荷、即ちウインドガラスから出力軸27に荷重がかかると、その荷重により従動側回転体24b(ウォーム軸24)が回転しようとする。そして、従動側回転体24bが、一対のロック部材34の間で矢印X方向に回転すると、従動側カム機構の作用により、一対のロック部材34が径方向外側に向かって相反する方向に移動する。詳しくは、従動側回転体24bの断面は楕円形状をなすため、従動側回転体24bが回転すると、その楕円形状の長軸と交差する円弧状の一対の側面が一対のロック部材34の従動側カム面34dを径方向外側に向かって押圧する(図6(b)において矢印Y参照)。そして、従動側回転体24bによって径方向外側に押圧された一対のロック部材34は、一対のサポート部材33に案内されながらクラッチハウジング31の径方向外側に向かって移動し、ロック部材34の当接部34cがクラッチハウジング31の内周面に当接する。当接部34cがクラッチハウジング31の内周面に当接すると、ロック部材34はそれ以上の径方向外側への移動が阻止されるため、ロック部材34はクラッチハウジング31と従動側回転体24bとの間に挟まれる(介在される)。従って、クラッチハウジング31と従動側回転体24bとの間に挟まれたロック部材34によって、同従動側回転体24bのそれ以上の回転が阻止される。つまり、ロック部材34の当接部34cとクラッチハウジング31の内周面との間に、従動側回転体24bの回転を妨げるような摩擦力が生じる。その結果、ウォーム軸24の回転が阻止されるとともにウォーム軸24から回転軸7への回転駆動力の伝達が阻止される。
(1)クラッチ3は、クラッチハウジング31、駆動側回転体32、サポート部材33、一対のロック部材34及び従動側回転体24bの6個の部品から構成されている。従って、従来に比べて部品点数が減少されている。従って、クラッチ3の機構が簡略化されている。また、一対のロック部材34は、駆動側回転体32の非回転時には回転力が加わった従動側回転体24bに押圧されて径方向外側に向かって移動するものであり、駆動側回転体32の回転時には駆動側回転体32に回転方向から押圧されて従動側回転体24bの方へ移動されて同従動側回転体24bに押し付けられるものである。即ち、クラッチ3は、カム機構を利用した簡易な構成で、回転軸7の回転駆動力をウォーム軸24に伝達し、ウォーム軸24からの回転が回転軸7に伝達されることを阻止できる。このように、部品点数が減少されて機構が簡略化されたクラッチ3は、製造するための設備が少なくてすむとともに、組付け工程にかかる時間を短縮できるため、結果的に製造コストを低減することができる。そして、ひいては該クラッチ3を有するモータの製造コストを低減することができる。
図10(a)及び図10(b)に示すように、回転軸7の非駆動時であって駆動側回転体52の非回転時に、負荷、即ちウインドガラス側から出力軸27に荷重がかかると、その荷重により従動側回転体54(ウォーム軸24)が回転しようとする。そして、従動側回転体54が、一対のロック部材34の間で矢印X2方向に回転すると、従動側カム機構の作用により、一対のロック部材34が径方向外側に向かって相反する方向(図10(b)において矢印Y2参照)に移動する。詳しくは、従動側回転体24bの断面は楕円形状をなすため、従動側回転体54が回転すると、その楕円形状の長軸方向の両端部が一対のロック部材34の従動側カム面34dを径方向外側に向かって押圧する。そして、従動側回転体54によって径方向外側に押圧された一対のロック部材34は、一対のサポート本体部53aに案内されながらクラッチハウジング31の径方向外側に向かって移動し、ロック部材34の当接部34cがクラッチハウジング31の内周面に当接する。当接部34cがクラッチハウジング31の内周面に当接すると、ロック部材34はそれ以上の径方向外側への移動が阻止されるため、ロック部材34はクラッチハウジング31と従動側回転体54との間に挟まれる(介在される)。従って、クラッチハウジング31と従動側回転体54との間に挟まれたロック部材34によって、同従動側回転体54のそれ以上の回転が阻止される。つまり、ロック部材34の当接部34cとクラッチハウジング31の内周面との間に、従動側回転体54の回転を妨げるような摩擦力が生じる。その結果、ウォーム軸24の回転が阻止されるとともにウォーム軸24から回転軸7への回転駆動力の伝達が阻止される。このときの摩擦力は、従動側回転体54からロック部材34に加えられる押圧力Tの径方向の分力T1(押圧力Tにおけるロック部材34の移動方向に沿った方向の分力)と摩擦係数μとを用いて、μ・T1と表わされる。またこのとき、従動側回転体54の回転方向に互いに対向する駆動側伝達面52bと従動側伝達面54b、及び、駆動側伝達面52cと従動側伝達面54cは、それぞれ非接触状態に保たれるため、従動側回転体54から駆動側回転体52に回転力を直接付与することがない。
(12)サポート部材53に設けられた規制部53cによって一対の駆動伝達部32cが径方向外側へ移動することが規制される。そのため、駆動側回転体52の回転時に、該駆動側回転体52の回転に伴って駆動伝達部32cが駆動側カム面34eを駆動側回転体52の回転方向に効率良く押圧することができる。
上記第1及び第2の実施形態では、パワーウインド装置の駆動源として用いられるモータを例に本発明を説明したが、パワーウインド装置の駆動源として用いられるモータ以外に、回転軸7を有するモータ部1とウォーム軸24を有する減速部2とを備えたモータに本発明を適用してもよい。また、クラッチ3,51は、モータ以外に、回転駆動される駆動軸と、該駆動軸の回転駆動力が伝達される従動軸とを備えた装置に利用してもよい。
上記第1の実施形態では、クラッチ3は、一対のロック部材34を備えているが、1つのロック部材34を備えた構成でもよい。この場合、駆動側回転体32の回転時には、駆動側回転体32に押圧された1つのロック部材34が従動側回転体24bに押し付けられることにより、駆動側回転体32の回転駆動力がロック部材34を介して従動側回転体24bに伝達される。また、クラッチ3は、3つのロック部材34を備えた構成であってもよい。この場合、ロック部材34の数に応じて駆動側回転体32に3つ駆動伝達部32cが備えられる。このことは、上記第2の実施形態のクラッチ51においても同様である。
Claims (15)
- 駆動軸と、
前記駆動軸と一体回転可能な駆動側回転体と、
前記駆動軸と同軸上に配置される従動軸と、
前記従動軸と一体回転可能な従動側回転体と、
前記駆動側回転体及び前記従動側回転体を内部に配置可能なクラッチハウジングと、
前記クラッチハウジングの内部において前記駆動側回転体と前記従動側回転体との間に配置されるロック部材であって、前記クラッチハウジングの内周面に接離する当接部、及び前記駆動側回転体が回転方向から当接される駆動側カム面を有するロック部材と
を備え、
前記駆動側回転体の非回転時には、前記ロック部材は、前記従動側回転体が回転されると該従動側回転体に押圧されて径方向外側に移動して前記当接部が前記クラッチハウジングの内周面に当接し、それによって前記クラッチハウジングと前記従動側回転体との間に挟まれてそれ以上の従動側回転体の回転を阻止し、
前記駆動側回転体の回転時には、前記駆動側回転体が前記駆動側カム面を回転方向に押圧するとともに、前記駆動側カム面の作用により前記ロック部材が径方向内側に移動して前記従動側回転体に押し付けられ、それによって前記ロック部材は、同ロック部材を介して前記駆動側回転体と前記従動側回転体とが一体回転可能に連結されるよう、前記駆動側回転体と前記従動側回転体との間に挟まれる、クラッチ。 - 請求項1に記載のクラッチにおいて、前記駆動側カム面は、同駆動側カム面が前記駆動側回転体によって回転方向に押圧されると前記ロック部材が前記駆動軸の径方向に移動されるように、前記駆動軸の径方向に対して傾斜している、クラッチ。
- 請求項2に記載のクラッチにおいて、前記ロック部材は一対の前記駆動側カム面を有し、該一対の駆動側カム面は、前記当接部の周方向両側に対称に設けられている、クラッチ。
- 請求項1乃至請求項3の何れか1項に記載のクラッチにおいて、
前記ロック部材は前記従動側回転体を径方向において挟むように一対配置され、前記一対のロック部材は、前記駆動軸の径方向に沿って相反する方向に移動可能である、クラッチ。 - 請求項1乃至請求項4の何れか1項に記載のクラッチはさらに、 前記ロック部材を前記駆動軸の径方向に移動可能に支持するとともに前記ロック部材を介して前記駆動側回転体及び前記従動側回転体と一体回転するサポート部材を有する、クラッチ。
- 請求項5に記載のクラッチにおいて、
前記駆動側回転体は、前記駆動軸の軸方向に延びかつ前記駆動軸の径方向に対向する一対の駆動伝達部を備え、該一対の駆動伝達部は、前記駆動側回転体の回転に伴って前記駆動側カム面を前記駆動側回転体の回転方向に押圧するように構成され、
前記サポート部材は、前記一対の駆動伝達部間に配置されるとともに、前記駆動伝達部の径方向外側への広がりを規制する規制部を有する、クラッチ。 - 請求項5又は請求項6に記載のクラッチにおいて、前記駆動側回転体及び前記サポート部材の少なくとも一方は、前記駆動側回転体及び前記サポート部材を一体的に係合すべく互いを軸方向に係合する係合部を有する、クラッチ。
- 請求項1乃至請求項7の何れか1項に記載のクラッチにおいて、
前記従動側回転体はカム軸を有し、
前記ロック部材は、前記当接部と反対側の側面に前記カム軸と径方向に対向する従動側カム面を有し、
前記駆動側回転体の非回転時において前記従動側回転体が回転すると、前記カム軸に前記従動側カム面が押圧されて前記ロック部材が径方向外側に移動する、クラッチ。 - 請求項8に記載のクラッチにおいて、
前記ロック部材は前記カム軸を挟むように一対配置され、前記一対のロック部材は、前記駆動軸の径方向に沿って相反する方向に移動可能であり、
前記駆動側回転体の回転時において径方向内側に移動された前記一対のロック部材の前記従動側カム面にて前記カム軸が挟持されて前記駆動側回転体から前記従動側回転体に前記ロック部材を介して回転駆動力が伝達される、クラッチ。 - 請求項8又は請求項9に記載のクラッチにおいて、前記カム軸は断面楕円形状の柱状をなす、クラッチ。
- 請求項10に記載のクラッチにおいて、前記従動側カム面は、その軸方向から見た形状が前記カム軸の短軸方向の両側面から前記カム軸を挟持可能な円弧状をなしている、クラッチ。
- 請求項1乃至請求項11の何れか1項に記載のクラッチにおいて、前記駆動側回転体及び前記従動側回転体は、前記駆動側回転体の回転時に前記駆動側回転体の回転方向に互いに当接する伝達面をそれぞれ有する、クラッチ。
- 請求項1乃至請求項12の何れか1項に記載のクラッチにおいて、前記駆動側回転体の非回転時において、前記ロック部材を前記従動側回転体と前記クラッチハウジングの内周面とで挟持し、前記当接部と前記クラッチハウジングの内周面との間で所望の摩擦力を発生させた状態で前記ロック部材に対する前記従動側回転体の回転を許容する、クラッチ。
- 駆動軸を有するモータ部と、
前記駆動軸と同軸上に配置され前記駆動軸の回転駆動力が伝達される従動軸を有する減速部であって、前記従動軸に伝達された回転駆動力を減速して出力する減速部と、
前記駆動軸と前記従動軸との間に設けられた請求項1乃至請求項13の何れか1項に記載のクラッチと
を備える、モータ。 - 請求項14に記載のモータにおいて、
前記減速部は、前記従動側回転体と一体回転可能に設けられ、軸受にて回転可能に支持されかつ螺子歯部を有する従動軸と、前記螺子歯部と噛合するウォームホイールと、該ウォームホイールに駆動連結された出力軸とを備え、
前記駆動軸の非回転時において、前記ロック部材を前記従動側回転体と前記クラッチハウジングの内周面とで挟持し、前記当接部と前記クラッチハウジングの内周面との間で所望の摩擦力を発生させた状態で前記従動側回転体の回転を許容するとともに、前記出力軸からの回転力を、少なくとも前記ウォームホイールと前記螺子歯部との噛み合い負荷と、前記従動軸と前記軸受との摩擦負荷と、前記クラッチの回転負荷とにより、前記駆動軸に伝達することを阻止する、モータ。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201080028828.8A CN102803773B (zh) | 2009-06-23 | 2010-06-22 | 离合器以及电动机 |
US13/379,935 US9455607B2 (en) | 2009-06-23 | 2010-06-22 | Clutch and motor |
DE112010002683T DE112010002683T5 (de) | 2009-06-23 | 2010-06-22 | Kupplung und Motor |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2009-148937 | 2009-06-23 | ||
JP2009148937 | 2009-06-23 | ||
JP2009285246A JP5297993B2 (ja) | 2009-06-23 | 2009-12-16 | クラッチ及びモータ |
JP2009-285246 | 2009-12-16 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010150771A1 true WO2010150771A1 (ja) | 2010-12-29 |
Family
ID=43386540
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2010/060532 WO2010150771A1 (ja) | 2009-06-23 | 2010-06-22 | クラッチ及びモータ |
Country Status (6)
Country | Link |
---|---|
US (1) | US9455607B2 (ja) |
JP (1) | JP5297993B2 (ja) |
KR (1) | KR101594975B1 (ja) |
CN (1) | CN102803773B (ja) |
DE (1) | DE112010002683T5 (ja) |
WO (1) | WO2010150771A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190093415A1 (en) * | 2016-03-17 | 2019-03-28 | Denso Corporation | Clutch, motor, and power window device |
Families Citing this family (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL1039622C2 (nl) * | 2012-05-23 | 2013-11-26 | Forest Group Nederland Bv | Vrijloop-koppeling. |
CN103206468B (zh) * | 2013-03-25 | 2016-05-25 | 湖州巨宏电机有限公司 | 内置式离合器及其带有此离合器的组合电机 |
JP6163074B2 (ja) * | 2013-09-27 | 2017-07-12 | テイ・エス テック株式会社 | ブレーキ装置 |
CN105337439B (zh) * | 2014-06-09 | 2019-03-15 | 德昌电机(深圳)有限公司 | 驱动装置及其电机 |
CN112769286B (zh) * | 2015-07-28 | 2023-12-15 | 德沃康科技集团有限公司 | 一种用于电驱动马达的制动装置 |
US20170130503A1 (en) * | 2015-11-09 | 2017-05-11 | Inteva Products, Llc | Apparatus and method for securing a case to a component |
CN106533050A (zh) * | 2016-11-18 | 2017-03-22 | 温州兴机电器有限公司 | 一种离合电机 |
JP2018204785A (ja) | 2017-01-11 | 2018-12-27 | キヤノン株式会社 | クラッチ、駆動伝達装置、および画像形成装置 |
CN108980230A (zh) * | 2017-06-01 | 2018-12-11 | 余姚市云仪智能科技有限公司 | 可自锁离合装置 |
EP4001686A1 (en) * | 2017-08-01 | 2022-05-25 | NSK Ltd. | Reverse input shutoff clutch, electric valve timing adjustment device, variable compression ratio device, and electric power steering device |
CA3089470A1 (en) | 2018-01-23 | 2019-08-01 | Wedgerock Llc | Anti-backdrive lock |
JP7052529B2 (ja) * | 2018-04-24 | 2022-04-12 | 日本精工株式会社 | アクチュエータ及びステアバイワイヤ式操舵装置 |
EP3792516B1 (en) * | 2018-05-07 | 2023-12-20 | Nsk Ltd. | Reverse input blocking clutch and actuator |
JP7219948B2 (ja) * | 2018-06-11 | 2023-02-09 | 下西技研工業株式会社 | ワンウェイクラッチおよびワンウェイクラッチ付き回転ダンパ装置 |
EP3851694A4 (en) * | 2018-09-12 | 2022-06-01 | NSK Ltd. | ELECTRIC MOTOR FEATURES REVERSE INPUT CUT-OFF CLUTCH |
EP3981997B1 (en) * | 2020-01-29 | 2023-06-28 | NSK Ltd. | Reverse input cutoff clutch |
EP4098900A4 (en) * | 2020-08-31 | 2023-08-16 | NSK Ltd. | ROTARY TRANSMISSION STATE SWITCHING DEVICE |
EP4123192A4 (en) * | 2021-01-28 | 2023-11-29 | NSK Ltd. | ELECTRIC MOTOR WITH LOCKING CLUTCH FOR REVERSE GEAR |
WO2022190323A1 (ja) * | 2021-03-11 | 2022-09-15 | 株式会社アイトロニクス | 変速機構 |
US11982325B2 (en) | 2021-11-15 | 2024-05-14 | Nsk Ltd. | Reverse input blocking clutch |
CN114162210B (zh) * | 2021-12-22 | 2024-03-22 | 中汽创智科技有限公司 | 一种传动轴连接装置及转向*** |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01317408A (ja) * | 1987-10-09 | 1989-12-22 | Yokota:Kk | カーテン開閉装置の両方向クラッチ |
JP2001289265A (ja) * | 2000-02-02 | 2001-10-19 | Asmo Co Ltd | クラッチ、及びモータ |
JP2007525628A (ja) * | 2004-02-26 | 2007-09-06 | シーメンス ヴィディーオー オートモティヴ コーポレイション | 電気モータ用の二方向摩擦クラッチアセンブリ |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3051282A (en) * | 1959-12-15 | 1962-08-28 | Whitney E Greene | Self-locking rotary transmission |
US3335831A (en) * | 1965-10-23 | 1967-08-15 | Formsprag Co | Bi-directional no-back drive device |
US3587796A (en) * | 1969-09-15 | 1971-06-28 | Duff Norton Co | Self-locking transmission mechanism |
US3603577A (en) * | 1969-09-23 | 1971-09-07 | Robert G Deraad | Buffer device with torsion bar actuated brakeshoes |
US4591029A (en) | 1984-08-17 | 1986-05-27 | Da Foe John P | Load actuating braking apparatus |
US6288464B1 (en) * | 1999-07-13 | 2001-09-11 | Asmo Co., Ltd. | Motor having worm gear mechanism |
US6382384B2 (en) * | 2000-02-02 | 2002-05-07 | Asmo Co., Ltd. | Clutch having reduced noise level and motor including such clutch |
US6257388B1 (en) * | 2000-04-24 | 2001-07-10 | Warner Electric Technology, Inc. | Anti-slip insert for a backstopping clutch |
JP3993010B2 (ja) | 2001-04-25 | 2007-10-17 | アスモ株式会社 | モータ |
US7163097B2 (en) | 2004-02-26 | 2007-01-16 | Siemens Vdo Automotive Corporation | Bi-directional friction clutch assembly for electric motors to prevent backdrive |
US7353930B2 (en) * | 2005-02-10 | 2008-04-08 | Continental Automotive Systems Us, Inc. | Bi-directional friction clutch or brake assembly for transmissions |
-
2009
- 2009-12-16 JP JP2009285246A patent/JP5297993B2/ja active Active
-
2010
- 2010-06-22 CN CN201080028828.8A patent/CN102803773B/zh active Active
- 2010-06-22 US US13/379,935 patent/US9455607B2/en active Active
- 2010-06-22 KR KR1020127000347A patent/KR101594975B1/ko active IP Right Grant
- 2010-06-22 WO PCT/JP2010/060532 patent/WO2010150771A1/ja active Application Filing
- 2010-06-22 DE DE112010002683T patent/DE112010002683T5/de active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01317408A (ja) * | 1987-10-09 | 1989-12-22 | Yokota:Kk | カーテン開閉装置の両方向クラッチ |
JP2001289265A (ja) * | 2000-02-02 | 2001-10-19 | Asmo Co Ltd | クラッチ、及びモータ |
JP2007525628A (ja) * | 2004-02-26 | 2007-09-06 | シーメンス ヴィディーオー オートモティヴ コーポレイション | 電気モータ用の二方向摩擦クラッチアセンブリ |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20190093415A1 (en) * | 2016-03-17 | 2019-03-28 | Denso Corporation | Clutch, motor, and power window device |
US10597926B2 (en) * | 2016-03-17 | 2020-03-24 | Denso Corporation | Clutch, motor, and power window device |
Also Published As
Publication number | Publication date |
---|---|
CN102803773A (zh) | 2012-11-28 |
JP5297993B2 (ja) | 2013-09-25 |
DE112010002683T5 (de) | 2012-11-22 |
US20120098367A1 (en) | 2012-04-26 |
US9455607B2 (en) | 2016-09-27 |
JP2011027252A (ja) | 2011-02-10 |
KR20120110080A (ko) | 2012-10-09 |
KR101594975B1 (ko) | 2016-02-17 |
CN102803773B (zh) | 2015-04-01 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2010150771A1 (ja) | クラッチ及びモータ | |
JP5885959B2 (ja) | モータ | |
JP6428867B2 (ja) | モータ | |
JP2001218420A (ja) | モータ、及びその製造方法 | |
JP6536015B2 (ja) | ジョイント構造、クラッチ及びモータ | |
JP6583075B2 (ja) | クラッチ、モータ及びパワーウインド装置 | |
US11047433B2 (en) | Clutch and motor | |
JP2010096313A (ja) | 電動モータ | |
JP6838513B2 (ja) | クラッチ及びモータ | |
JP4896635B2 (ja) | クラッチ、モータ及び車両用ドア開閉装置 | |
JP2010230153A (ja) | クラッチ機構、および減速機付モータ | |
WO2020022043A1 (ja) | クラッチ、及びモータ | |
JP2000211537A (ja) | 電動式パワ―ステアリング装置 | |
JP4137866B2 (ja) | モータ | |
JP6674998B1 (ja) | コイルばねを利用したロックタイプ双方向クラッチ | |
JP2001028863A (ja) | モータ | |
JP6828537B2 (ja) | クラッチ及びモータ | |
JP2001214945A (ja) | クラッチ及びモータ | |
JP5480080B2 (ja) | クラッチ及びモータ | |
JP2001028864A (ja) | モータ | |
JP2001289265A (ja) | クラッチ、及びモータ | |
JP2010223404A (ja) | クラッチ機構、および減速機付モータ | |
JP7215374B2 (ja) | モータ | |
WO2023153200A1 (ja) | クラッチユニット | |
WO2018061802A1 (ja) | クラッチ及びモータ |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201080028828.8 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 10792089 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13379935 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120100026831 Country of ref document: DE Ref document number: 112010002683 Country of ref document: DE |
|
ENP | Entry into the national phase |
Ref document number: 20127000347 Country of ref document: KR Kind code of ref document: A |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 10792089 Country of ref document: EP Kind code of ref document: A1 |