Clutch and engine

Abstract

Coupling comprising: a drive shaft (7); a drive-side rotating body (32; 52) rotatable as a unit with the drive shaft (7); a driven shaft (24a) arranged coaxially with the drive shaft (7); a driven-side rotating body (24b; 54) rotatable as a unit with the driven shaft (24a); a coupling housing (31) suitable for arranging the drive-side rotating body (32; 52) and the driven-side rotating body (24b; 54); and a locking element (34) arranged between the drive-side rotating body and the driven-side rotating body (24b; 54) inside the coupling housing (31), wherein the locking element (34) has a contact section (34c) which comes into contact with and moves away from the inner circumferential surface of the coupling housing (31), and a drive-side cam surface (34a) on which the drive-side rotating body (32;52) from a direction of rotation, wherein when the output-side rotating body (24b; 54) is rotated in the non-rotating state of the input-side rotating body (32; 52), the locking element (34) is pushed by the output-side rotating body (24b; 54) and moved radially outwards, thereby bringing the contact section (34c) into contact with the inner circumferential surface of the coupling housing (31), so that the locking element (34) is located between the coupling housing (31) and the output-side rotating body (24b; 54) and prevents further rotation of the output-side rotating body (24b; 54); and in the rotating state of the input-side rotating body (32; 52), the input-side rotating body (32;52) the drive-side cam surface (34e) is moved in the direction of rotation, and the drive-side cam surface (34e) causes the locking element (34) to be moved radially inwards and the locking element (34) to be pushed against the driven-side rotating body (24b; 54), so that the locking element (34) is positioned between the drive-side rotating body (32; 52) and the driven-side rotating body (24b; 54), thereby coupling the drive-side rotating body (32; 52) and the driven-side rotating body (24b; 54) to the locking element (34), so that they can be rotated as a unit.;

Description

TECHNICAL AREA

[0001] The present invention relates to a coupling for transmitting a drive torque from a drive shaft to a driven shaft without transmitting a torque from the driven shaft to the drive shaft, and to a motor in which a drive shaft of a motor unit and a deceleration mechanism of a deceleration unit are coupled together by the coupling. REASONABLE STATE OF THE ART

[0002] A motor used as a drive source for a window regulator or the like comprises a motor unit that generates a drive torque to rotate a rotary shaft (drive shaft) and a deceleration unit that decelerates the rotational speed of the rotary shaft and outputs the drive torque from a load-bearing output shaft. The rotary shaft arranged in the motor unit and a worm shaft (output shaft) of the deceleration mechanism arranged in the deceleration unit are coupled by a clutch that causes the drive torque to be transmitted from the rotary shaft to the worm shaft without transmitting any torque from the worm shaft to the rotary shaft.

[0003] For example, in a motor described in patent document 1, a mechanical coupling connects the rotary shaft and the worm shaft. The coupling has an input-side rotating body that rotates as a unit with the rotary shaft, an output-side rotating body that rotates as a unit with the worm shaft, and a plurality of components that couple the input-side rotating body and the output-side rotating body to each other.

[0004] The drive-side and driven-side rotating bodies are arranged such that they face each other axially inside a cylindrical collar. A ball for absorbing a thrust load is located between the rotating shaft and the driven-side rotating body. Three cylindrical roller elements, extending axially, are arranged circumferentially at equal angular intervals between an inner circumferential wall of the collar and an outer circumferential wall of the driven-side rotating body. The roller elements are supported by a carrier element. The carrier element supports the roller elements such that they face the drive-side rotating body circumferentially within the collar. Furthermore, the collar and the carrier element are attached to a gearbox housing, which accommodates the deceleration mechanism with a stop formed by a metal plate.

[0005] When the motor unit is driven and the rotating shaft is turned, the drive-side and driven-side rotating bodies engage in the direction of rotation and rotate as a unit. The drive torque of the rotating shaft is thus transmitted from the drive-side and driven-side rotating bodies to the worm shaft, delayed by the deceleration mechanism, and then released. During this process, the support element also engages with the drive-side rotating body in the direction of rotation. The support element then rotates as a unit with the drive-side rotating body and the three roller elements. If torque is applied to the worm shaft when the motor unit is stopped, the roller elements are positioned between the driven-side rotating body and the collar, thus preventing rotation of the driven-side rotating body.This prevents the rotational force of the worm shaft from being transferred to the rotating shaft. DOCUMENTS OF THE STATE OF TECHNOLOGY Patent documents

[0006] Patent document 1: Japanese publication no. 2003-278784 SUMMARY OF THE INVENTION Problems to be solved by the invention

[0007] The coupling described in patent specification 1, however, comprises the drive-side rotating body, the driven-side rotating body, the collar, the ball, the three rolling elements, the support element, and the stop. Thus, the coupling has a large number of components and a complex operating mechanism. As a result, large production lines are required for each component, and the coupling of such components is laborious, thereby increasing assembly time and consequently resulting in high manufacturing costs.

[0008] It is an object of the present invention to provide a mechanical coupling with a simplified operating mechanism and a motor comprising such a coupling. Measures to solve the problem

[0009] To solve the aforementioned problem, the present invention provides a coupling comprising a drive shaft, a drive-side rotating body rotatable as a unit with the drive shaft, a driven shaft arranged coaxially with the drive shaft, an output-side rotating body rotatable as a unit with the driven shaft, a coupling housing suitable for arranging the drive-side and output-side rotating bodies, and a locking element arranged inside the coupling housing between the drive-side and output-side rotating bodies. The locking element has a contact section that engages with and retracts from the inner circumferential surface of the coupling housing, and a drive-side cam surface against which the drive-side rotating body engages when rotating in one direction.When the output-side rotating body is rotated while the input-side rotating body is not rotating, the locking element is pushed by the output-side rotating body and moved outwards in a radial direction, bringing the contact section into contact with the inner circumferential surface of the coupling housing, so that the locking element is positioned between the coupling housing and the output-side rotating body and prevents further rotation of the output-side rotating body.During rotation of the drive-side rotating body, the drive-side rotating body pushes the drive-side cam surface in the direction of rotation, whereby the drive-side cam surface then causes the locking element to move inwards in the radial direction and the locking element to be pushed against the driven-side rotating body, so that the locking element is located between the drive-side rotating body and the driven-side rotating body, thereby coupling the drive-side rotating body and the driven-side rotating body to the locking element, so that they can be rotated as a unit.

[0010] During rotation of the drive-side rotating body, the drive-side rotating body presses the drive-side cam surface in the direction of rotation, and the drive-side cam surface causes the locking element to move radially inwards and be pushed against the drive-side rotating body. As a result, the locking element is positioned between the drive-side and driven-side rotating bodies in such a way that it couples the drive-side and driven-side rotating bodies together, allowing them to rotate as a single unit. BRIEF DESCRIPTION OF THE DRAWING

[0011] They show:

[0012] Fig. 1 a partial cross-sectional view of a motor according to the present invention;

[0013] Fig. 2 a partially enlarged cross-sectional view of the engine of Fig. 1;

[0014] Fig. 3 A perspective view of a clutch located in the engine of Fig. 1 is arranged;

[0015] Fig. 4 a splayed perspective view of a coupling according to a first embodiment of the present invention;

[0016] Fig. 5(a) and Fig. 5(b) Distended side views of the coupling of Fig. 4;

[0017] Fig. 6(a) a cross-sectional view of the clutch with the engine stopped (cross-sectional view along line 6a-6a in Fig. 3) in the first embodiment, and Fig. 6(b) a cross-sectional view of the clutch with the engine stopped (cross-sectional view along line 6b-6b in Fig. 3) in the first embodiment;

[0018] Fig. 7(a) a cross-sectional view of the clutch in the driven state of the motor in the first embodiment (cross-sectional view along line 6a-6a in Fig. 3) Fig. 7(b) a cross-sectional view of the clutch in the driven state of the motor in the first embodiment (cross-sectional view along line 6b-6b in Fig. 3);

[0019] Fig. 8 a side view of a coupling according to a second embodiment of the present invention;

[0020] Fig. 9 a splayed perspective view of the coupling of Fig. 8;

[0021] Fig. 10(a) and Fig. 10(b) Cross-sectional views of the clutch in the stopped state of the engine in the second embodiment (cross-sectional view along line 10-10 in Fig. 8); and

[0022] Fig. 11(a) and Fig. 11(b) Cross-sectional views of the clutch in the driven state of the motor in the second embodiment (cross-sectional view along line 10-10 in Fig. 8). FORMS OF EXECUTION OF THE INVENTION

[0023] A first embodiment of the present invention will now be described with reference to the drawing.

[0024] Fig. Figure 1 is a partial cross-sectional view of a motor of the present embodiment, which is used as a drive source for a window lifting device. The motor comprises a motor unit. 1 , a delay unit 2 and a clutch 3 on.

[0025] The engine unit 1 features a tubular yoke housing 4 with a closed bottom. A pair of magnets 5 is located on the inner circumferential surface of the yoke housing. 4 secured so that they are opposite each other. An anchor 6 is on an inner side in a radial direction of the magnet 5 inside the yoke housing 4 arranged. The anchor 6 has a rotating shaft 7on, i.e. a drive shaft that extends along an axial direction in the center in the radial direction of the yoke housing 4 extends. A camp 8 is in the middle of the floor of the yoke housing 4 arranged. Through the warehouse 8 is a basal end of the rotating shaft 7 Rotatably mounted. A cylindrical collector. 9 is located on a section of the rotating shaft that is closer to a distal end 7 fastened. A drive coupling section 7a with a pair of flat surfaces extending parallel to each other, is located on the outer circumferential part of the distal end of the rotating shaft 7 trained.

[0026] A flange section 4a , which extends outwards in the radial direction, is in the opening of the yoke housing. 4 trained, and a brush holder 10 is at the opening of the yoke housing 4 attached. The brush holder 10is designed by the one-piece formation of a holder main body 10a , which is designed to open the yoke housing 4 closes, as well as a connector 10b , which in the radial direction of the yoke housing 4 protrudes outwards. The main holder body 10a is connected to the connector 10b connected by wiring. The main holder body 10a holds a pair of brushes 11 , sliding on the collector 9 concerns. A warehouse 12 is in the middle of the main holder body 10a arranged. Through the warehouse 12 is a section between the collector 9 and the drive coupling section 7a on the rotating shaft 7 Rotatably mounted. One via the connector 10b to the brush 11 The external power supply is connected via the collector 9 to a coil winding of the armature 6This leads to the anchor being moved. 6 (the rotating shaft 7 ) rotated, i.e. the motor unit 1 is powered.

[0027] The delay unit 2 a gearbox housing 21 as well as one in the gearbox housing 21 recorded delay mechanism 22 up. The gearbox housing 21 is made of resin and has a fastening section 21a on, which the gearbox housing 21 on the engine unit 1 at one section (upper end in Fig. 1) attached to the motor unit 1 axially opposite. The fastening section 21a It has an external shape that corresponds to the external shape of the flange section. 4a of the yoke housing 4 similar. One towards the interior of the yoke housing. 4 open mounting recess 21b is in the fastening section 21atrained. The fastening section 21a and the flange section 4a are through a screw 23 with the mounting recess 21b attached holder main body 10a of the brush holder 10 coupled, so that the gearbox housing 21 and the yoke 4 coupled and the motor unit 1 and the delay unit 2 are united with each other.

[0028] The gearbox housing 21 has a coupling mounting recess 21c on, which are in the axial direction of the rotating shaft 7 in the middle of the lower part of the mounting recess 21b extends, as well as a worm shaft receiving section 21d , which is aligned in one axial direction of the rotating shaft 7 from the center of the lower part of the coupling mounting recess 21c extends. The gearbox housing 21 also features a wheel mounting section 21eon the side of the worm shaft mounting section 21d on. The wheel mounting section 21e and the worm shaft intake section 21d are located on the central part in the axial direction (longitudinal direction) of the worm shaft receiving section. 21d interconnected.

[0029] The worm shaft intake section 21d takes on a worm shaft that is essentially circular and columnar in shape 24 up. The snail shaft 24 is made of a metallic material and has a worm shaft main body that is essentially circular and columnar. 24a on, as well as a driven-side rotating body 24b , located at the basal end of the snail shaft main body 24a (i.e., the end on the side of the motor unit, in Fig. 1 above) is formed in one piece. A screw tooth section 24c The central section is the axial direction of the worm shaft main body24a formed. Both axial ends of the worm shaft main body 24a are secured by a pair of metallic bearings 25a , 25b with a cylindrical shape, which extends at both ends in the axial direction of the worm shaft receiving section 21d are arranged, rotatably mounted. As in Fig. Figure 2 shows the main body of the worm shaft. 24a in the worm shaft intake section 21d arranged so that it is coaxial with the rotating shaft 7 is, i.e., such that a central axis L1 of the rotating shaft 7 and a central axis 12 of the worm shaft main body 24a extend along a straight line.

[0030] The output-side rotating body 24b extends along the axial direction from the basal end face of the worm shaft main body 24a As in Fig. As shown in section 4, the driven-side rotating body has 24bIn cross-section, it has an elliptical shape perpendicular to the axial direction and is rod-shaped overall. For the sake of simplicity, the arc-shaped side surface, which corresponds to the minor axis, is in the elliptical shape of the driven-side body of revolution. 24b cuts, with the reference sign “ 24e “As stated in Fig. As shown in 2, a central axis is formed. 13 of the output-side rotating body 24b with the central axis 12 of the worm shaft main body 24a together. The driven-side rotating body 24b protrudes from the worm shaft intake section 21d into the clutch mounting recess 21c before.

[0031] A worm gear 26 with the shape of a circular plate, which has a screw tooth section 24c the snail shaft 24 The engagement is located in the wheel mounting section 21e recorded. The worm gear 26together with the worm shaft 24 the delay mechanism 22 The worm gear 26 is rotatable about an axis that is aligned with the central axis of the worm shaft main body 24a orthogonal direction (direction perpendicular to the drawing plane in Fig. 1) extends radially in the central section and has an output shaft 27 , which rotates as a unit with the worm gear, in the central section in the radial direction. A window regulator known per se (not shown) for raising and lowering the window pane of a vehicle is driven by the output shaft. 27 coupled.

[0032] The coupling mounting recess 21c when viewed from the axial direction of the worm shaft 24 a circular shape and takes the coupling 3 on which the rotating shaft 7 and the snail shaft 24 coupled together. As in the Fig. 3 and Fig. As shown in section 4, the coupling 3 a clutch housing 31 , a drive-side rotating body 32 , a support element 33 , a pair of locking elements 34 and the output-side rotating body 24b on.

[0033] The clutch housing 31 It is made of metal and has a cylindrical shape. As in Fig. Figure 2 shows the outer diameter of the clutch housing. 31 designed so that it is essentially equal to the inner diameter of the coupling mounting recess 21c is, and the axial length of the clutch housing 31 is designed so that it is essentially equal to the depth of the coupling mounting recess. 21c is. The clutch housing 31 is in the clutch mounting recess 21c recorded in a state in which the inner circumferential surface of the coupling mounting recess 21cadjacent outer circumferential surface of the clutch housing 31 related to the gearbox housing 21 cannot be swivelled.

[0034] As in the Fig. 3 and Fig. As shown in section 4, this is the one in the clutch housing. 31 arranged drive-side rotating bodies 32 Made of resin. Furthermore, the drive-side rotating body is 32 one-piece with a drive coupling section 32a , with which the drive coupling section 7a the rotating shaft 7 is coupled, a support section 32b and a pair of drive transmission sections 32c trained.

[0035] The drive coupling section 32a It has a pair of flat surfaces that extend parallel to each other along its outer part. The support section 32b is at one axial end (lower end in Fig. 4) of the drive coupling section 32aformed in one piece. The support section 32b It has a pair of flat surfaces that extend parallel to each other along its outer part. That is, the shape of the outer circumference of the support section. 32b is the same as that of the drive coupling section 32a , however, is slightly larger in the radial direction than the drive coupling section 32a As in the Fig. 5(a) and Fig. As shown in 5(b), a central axis 14 of the support section 32b with a central axis 15 of the drive coupling section 32a together. The maximum dimension in relation to the central axis. 14 in the carrier section 32b The orthogonal direction is slightly smaller than the inner diameter of the clutch housing. 31 As in Fig. Figure 4 shows a coupling hole. 32d , which is the drive coupling section 32a and the carrier section 32bin the direction of the center axes 14 , 15 permeated, at the corresponding central part in the radial direction of the drive coupling section 32a and the carrier section 32b trained. The coupling hole 32d is a hole with a shape that corresponds to the distal end of the rotating shaft 7 arranged drive coupling section 7a corresponds to the drive coupling section. 7a is thus in the coupling hole 32d used so that the rotating shaft 7 and the drive-side rotating body 32 They are engaged with each other in the direction of rotation so that they can be rotated as a unit.

[0036] The pair of drive transmission sections 32c extends along the axial direction from the axial end face of the support section 32b The end face (lower end face in Fig. 4) lies on the drive coupling section 32opposite side. The pair of drive transmission sections 32c extends along the axial direction from two sides of the support section 32b to the opposite side of the drive coupling section 32a In other words, the pair of drive transmission sections extends 32c along the axial direction of two areas at equal angular intervals in the circumferential direction of the support section 32b to the opposite side of the drive coupling section 32a As in Fig. Figure 3 shows the length from the basal end to the distal end of the drive transmission section. 32c such that they are larger than the axial length of the clutch housing 31 is. As further explained in Fig. As shown in 5(b), the drive transmission sections are 32c in each pair in one direction relative to the central axis 14 spaced apart in an orthogonal direction. As in Fig. Figure 3 shows the pair of drive transmission sections. 32c into the clutch housing 31 used.

[0037] As in the Fig. 6(a) and Fig. As shown in 6(b), each drive transmission section has 32c , which has a circular arc shape and extends along the inner circumferential surface of the clutch housing 31 extends a pair of transmission parts 32e with a shape that curves slightly inwards radially at both ends of the circumference. Each transmission part 32e is with increasing distance of the circumferentially central part of the drive transmission section 32c on the radially central part of the clutch housing 31 inclined towards.

[0038] A pair of locking elements 34 , which is from the supporting element 33 is carried in such a way that it is in a radial direction (radial direction of the rotating shaft) 7and simultaneously radial direction of the clutch housing 31 ) is movable, is between the pair of drive transmission sections 32c arranged.

[0039] The one in the clutch housing 31 arranged support element 33 It is made of a resin material and has a hollow box shape. The support element 33 has a hole that runs along the radial direction of the clutch housing 31 The two ends of the hole form a pair of openings that open in opposite directions. The length between the openings (i.e., the length of the hole in the radial direction of the clutch housing) 31 ) is less than the length between the distal ends of the pair of transmission parts 32e in each drive transmission section 32c (i.e., the length between the circumferential ends of the drive transmission section) 32c) and greater than the length between the basal ends of the pair of transmission parts 32e in each drive transmission section 32c As in Fig. 6(a) shows the four corners of the support element. 33 when considering the support element 33 from the axial direction of the clutch housing 31 beveled. As in Fig. As shown in section 4, the support element 33 a pair of end walls that are aligned with each other in the axial direction of the rotating shaft 7 opposite each other. A circular through-hole. 33a is formed in each end wall, with the exception of the screw tooth section. 24c The corresponding part has an inner diameter of the through hole. 33a slightly larger than the diameter of the worm shaft main body 24a .

[0040] As in the Fig. 4 and Fig. As shown in 6(b), the pair of locking elements 34the same shape and size and is symmetrical with respect to a central axis 16 of the clutch housing 31 inside the clutch housing 31 arranged. The length runs along the direction of the clutch housing diameter. 31 in each locking element 34 is smaller than half the inner diameter of the clutch housing 31 Each of the locking elements 34 , which are made of a resin material, include a sliding section 34a on, which is essentially rectangular and block-shaped, an intermediate transmission section 34b , which as a unit with the radially outer side of the sliding section 34a is trained, and a contact section 34c , which forms a unit with the radially outer side of the intermediate transmission section 34b is trained.

[0041] In each locking element 34 is the sliding section 34awith the outer shape of an essentially square plate, which corresponds to the inner circumferential surface of the supporting element 33 corresponds to the support element 33 arranged in a state in which the outer circumferential surface is movable on the inner circumferential surface of the support element 33 is involved. One on the contact section 34c recessed output-side curve surface 34d is on the side surface on the contact section 34c opposite side in the sliding section 34a arranged. The side surface is closer to the central axis. 16 (i.e. inner circumferential side) of the clutch housing 31 The output-side curve surface 34d extends along the axial direction from one end to the other end of the sliding section 34a . Each output-side curved surface 34dis symmetrical with respect to an imaginary plane (not shown) that extends radially through the circumferential central part of the sliding section. 34a extends. The curvature of the driven-side curve surface 34d is weaker than the curvature of the pair of circular arc-shaped side surfaces 24e in the output-side rotating body 24b and therefore forms a gradual circular arc shape.

[0042] The intermediate transmission section 34b is as a unit with the curve surface on the output side 34d opposite end, i.e. the end on the outer circumference side in each sliding section 34a trained. The intermediate transmission section 34b is designed such that the width in the circumferential direction increases from the basal end, which is closer to the sliding section. 34a The distance between the end and the outer circumference gradually decreases. In the intermediate transfer section... 34bThe cross-sectional shape is trapezoidal along the axial direction, orthogonal to the surface. A pair of drive-side curved surfaces. 34e , which are related to the radial direction (radial direction of the rotating shaft) 7 , and same in radial direction of clutch housing 31 ) are inclined, at both ends of the circumference of each intermediate transfer section 34b formed. The pair of drive-side cam surfaces 34e is symmetrical with respect to an imaginary plane (not shown) that passes through the center in the circumferential direction of the contact section. 34c and extends in the radial direction. Furthermore, the drive-side cam surfaces extend 34e so that they approach each other radially outwards. Each drive-side cam surface 34e extends along the axial direction from one end to the other end of the intermediate transmission section. 34b The locking element 34, that the drive-side cam surfaces 34e exhibits, and the drive-side rotating body 32 (Drive transmission section) 32c ) form the drive-side cam mechanism.

[0043] Each contact section 34c , which runs in a straight line along the axial direction from one end to the other end of the intermediate transmission section 34b extends, forming a projection that extends radially outwards. Each intermediate transmission section 34b It has a semicircular cross-sectional shape in a direction orthogonal to the axial direction.

[0044] As in the Fig. 2 and Fig. 6(b) shows the pair of locking elements 34 in the clutch housing 31 between the pair of drive transmission sections 32c of the drive-side rotating body 32 arranged. More precisely, the pair of locking elements is 34into the support element 33 from a pair of respective openings of the support element 33 here in such a way that the driven-side curve surfaces 34d point to each other. The supporting element 33 , in which the pair of locking elements 34 is used, is between the drive transmission sections 32c arranged in the radial direction inside the clutch housing 31 opposite each other. The contact section 34c and the intermediate transmission section 34b , which emerges from the opening of the support element 33 protrudes outwards in the radial direction, between the transmission part 32e of a drive transmission section 32c and the transmission part 32e of the other drive transmission section 32c , which are adjacent in the circumferential direction, are arranged. Furthermore, the pair of drive-side cam surfaces is 34ein each locking element 34 arranged so that it is in the direction of rotation of the drive-side rotating body 32 on the pair of transmission parts 32e is attached. The locking element 34 is along the radial direction of the rotating shaft 7 (same as the radial direction of the clutch housing) 31 ) movable and simultaneously from the supporting element 33 guided. If the locking element 34 When the outer end in the radial direction is reached, the contact section occurs. 34c on the inner circumferential surface of the support element 33 in the appendix.

[0045] If the locking element 34 is arranged on the outermost side in the radial direction, i.e. in a state where the contact section 34c on the inner circumferential surface of the clutch housing 31 The distance between the opposing output-side curve surfaces is [value missing]. 34dso that its value is less than the length in the principal axis direction of the cross-sectional shape, i.e., the length relative to the axial direction of the driven-side rotating body. 24b orthogonal elliptical shape.

[0046] The output-side rotating body 24b extends through the pair of through holes 33a of the support element 33 and is between the two output-side curve surfaces 34d , which are opposite each other in the radial direction, thus inside the clutch housing 31 arranged so that it was between the pair of locking elements 34 is recorded lying down. In the output-side rotating body 24b The two side surfaces lie 24e the output-side curve surface 34d in the diameter direction of the clutch housing 31 opposite (pointing in the radial direction of the rotating shaft) 7 towards each other). The driven-side rotating body 24band the pair of locking elements 34 , each of which forms the driven-side curve surface 34d They form the output-side cam mechanism. The rotating shaft 7 , the clutch housing 31 , the drive-side rotating body 32 and the snail shaft 24 with the output-side rotating body 24b are positioned coaxially, i.e., their center axes lie along the same straight line when the coupling 3 in the clutch mounting recess 21c has been recorded.

[0047] The operation of the engine will now be described, with a focus on the operation of the clutch. 3 described.

[0048] With reference to the Fig. 6(a) and Fig. 6(b) if the load or the disk is in the stopped state of the motor unit 1 , i.e., in the non-rotating driven state of the rotating shaft 7and in the non-rotating state of the drive-side rotating body 32 the output shaft 27 When subjected to a load, this load acts in the sense of a rotation of the driven-side rotating body. 24b (snail shaft) 24 ). If the driven-side rotating body 24b in the direction of arrow X between the pair of locking elements 34 When rotating, the output-side cam mechanism acts in the sense of a movement of the pair of locking elements. 34 in opposite directions, radially outwards. More precisely, because the cross-section of the driven-side rotating body 24b Being elliptical, it pushes when the driven-side rotating body rotates. 24b the pair of circular arc-shaped side surfaces that intersects the main axis of the elliptical shape, the downstream curved surface 34d of the pair of locking elements 34 in the radial direction outwards (see arrow Y in Fig. 6(b)). The pair of locking elements 34 , that of the driven-side rotating body 24b When pushed outwards in the radial direction, it moves in the radial direction of the clutch housing. 31 outwards, while it is supported by the pair of supporting elements 33 is led, and the contact section 34c of the locking element 34 occurs on the inner circumferential surface of the clutch housing 31 in the attachment. If the contact section 34c on the inner circumferential surface of the clutch housing 31 If this is the case, a further movement of the locking element is required. 34 in the radial direction towards the outside, the locking element is thus prevented. 34 between the clutch housing 31 and the output-side rotating body 24b The image was taken in a horizontal position. Consequently, a further rotation of the output-side rotating body is required. 24b through the space between the clutch housing 31and the output-side rotating body 24b horizontally recorded locking element 34 prevented. That is, between the contact section 34c of the locking element 34 and the inner circumferential surface of the clutch housing 31 A frictional force is generated, which causes a rotation of the driven-side rotating body. 24b This prevents the worm shaft from rotating. 24 prevented, and the transmission of a drive torque from the worm shaft 24 on the rotating shaft 7 is prevented.

[0049] In a state where the contact section 34c of the pair of locking elements 34 on the inner circumferential surface of the clutch housing 31 applies and thereby causes a rotation of the output-side rotating body. 24b To prevent this, two locking elements are used. 34moved radially outwards and away from each other, so that two drive-side cam surfaces 34e , which the two transmission parts 32e each drive transmission section 32c opposite each other, in the direction of the diameter of the clutch housing 31 are spaced apart from each other. The two drive transmission sections 32c of the drive-side rotating body 32 are each arranged in a neutral position, which is relative to the movement of the drive-side cam surface 34e on the middle section in the circumferential direction between the two locking elements 34 lies. As a result, the transmission part shifts 32e of the drive-side rotating body 32 the drive-side curve surface 34e immediately in the direction of rotation, even if the motor unit 1 is in a stopped state, and the rotating shaft 7It is rotated either in the forward or backward direction.

[0050] A rotation of the output-side rotating body 24b is prevented in the same way even if the output shaft 27 applied load on the output-side rotating body 24b in the direction of arrow X (see Fig. 6(b)) opposite direction between the pair of locking elements 34 rotates while the motor unit 1 is in a stopped state.

[0051] As in the Fig. 7(a) and Fig. As shown in 7(b), the drive-side rotating body rotates 32 (see arrow α) with the rotating shaft 7 , which are in the driven state of the motor unit 1 , i.e., during the rotating drive of the rotating shaft 7 , is rotated in the forward direction. The transmission part 32e , which is present in every drive transmission section 32con the forward side in the direction of rotation of the drive-side rotating body 32 is located by the rotation of the drive-side rotating body 32 against the drive-side curve surface in the opposite circumferential direction 34e pushed. Since the drive-side curve surface 34e The contact section moves when inclined to the radial direction. 34c of the locking element 34 consequently in the radial direction from the inner circumferential surface of the clutch housing 31 inwards due to a force component F1 in the radial direction of a shear force F, with which the transmission part 32e of the drive-side rotating body 32 the drive-side curve surface 34e shifts (see arrow β). In this case, the pair of locking elements moves. 34 in the radial direction of the clutch housing 31 towards the inside, while it is supported by the pair of support elements 33is guided. The output-side curve surface 34d of the pair of locking elements 34 emerges from the outside in the radial direction of the clutch housing. 31 on the pair of arcuate side surfaces 24e of the output-side rotating body 24b in the appendix. Furthermore, the pair of locking elements 34 from the force component F1 onto the output-side rotating body 24b pushed towards and holds the output-side rotating body 24b between themselves. Furthermore, the pair of locking elements 34 , which the output-side rotating body 24b holds, from a circumferential force component F2 of the thrust force F together with the output-side rotating body 24b (cf. arrow γ) as a unit with the drive-side rotating body 32 around the central axis L1 of the rotating shaft 7 Rotated. In other words, the drive-side rotating body is rotated. 32and the output-side rotating body 24b from the rotating body on the drive side 32 and the output-side rotating body 24b horizontally arranged locking element 34 coupled and rotated as a unit. In this process, the support element 33 by means of the locking element 34 as a unit with the drive-side rotating body 32 and the output-side rotating body 24b turned.

[0052] In this way, the drive torque of the rotary shaft is 7 through the drive-side rotating body 32 and the locking element 34 on the output-side rotating body 24b transmitted. This rotates the worm shaft. 24 , and the worm gear 26 and the output shaft 27 rotate accordingly. This will connect it to the output shaft. 27The coupled window regulator drive is activated, and the window pane is opened and closed (raised and lowered). The drive torque is transmitted to the worm shaft in the same way. 24 transmitted when the rotating shaft 7 in the direction that leads to the Fig. 7(a) and Fig. 7(b) shown in the example is in the opposite direction (i.e. in the reverse direction) and is driven by rotation.

[0053] The present embodiment has the advantages described below. (1) The clutch 3 It has six components, namely the clutch housing 31 , the drive-side rotating body 32 , the supporting element 33 , the pair of locking elements 34 , and the output-side rotating body 24b This reduces the number of components compared to the state of the art. This simplifies the coupling's operating mechanism. 3Furthermore, the pair of locking elements 34 from the output-side rotating body 24b pushed, upon which a rotational force is applied, and in the non-rotating state of the drive-side rotating body 32 moved radially outwards. During a rotation of the drive-side rotating body. 32 The pair of locking elements will 34 also from the drive-side rotating body 32 pushed from the direction of rotation and onto the driven-side rotating body 24b towards and against the output-side rotating body 24b moves. In other words, the clutch transmits 3 the drive torque of the rotating shaft 7 onto the snail shaft 24 and prevents the transmission of rotation from the worm shaft 24 on the rotating shaft 7 by means of a simple design using the cam mechanism. Thus, the coupling requires 3which has fewer components and a simplified operating mechanism, requires fewer production facilities and shortens assembly time. This reduces manufacturing costs. Furthermore, the manufacturing costs of a motor that uses the clutch are also reduced. 3 has been reduced. (2) The locking element 34 , which is the drive torque of the drive-side rotating body 32 (Transmission part) 32e ) is recorded, can be determined from the drive-side curve surface 34e , which has a simple shape and is shaped in such a way that it is in relation to the radial direction of the rotating shaft 7 It is inclined, moving slightly in the radial direction. Thus, the drive-side rotating body 32 and the output-side rotating body 24b during a rotation of the rotating shaft 7 in a simple way through the pair of locking elements 34 coupled together. (3) In the locking element 34is the drive-side curve surface 34e , which are attached to the transmission part from the direction of rotation 32e of the drive-side rotating body 32 occurs on both sides of the contact section. 34c arranged. Therefore, the transmission part occurs. 32e of the drive-side rotating body 32 to the drive-side cam surface 34e in the system, so that it is present both during a forward rotation and a reverse rotation of the drive-side rotating body. 32 , which are caused by the forward rotation and the reverse rotation of the rotating shaft 7 each locking element is caused 34 moved inwards in the radial direction. The pair of drive-side cam surfaces 34e in each locking element 34 is symmetrical on both circumferential sides of the contact section 34c arranged. Thus, the radial movement of the locking element occurs. 34both during a forward rotation and a reverse rotation of the drive-side rotating body 32 in the same way. (4) The pair of locking elements 34 is arranged in such a way that it forms the output-side rotating body 24b between them, and the locking elements 34 are along the radial direction of the rotating shaft 7 moved. In the non-rotating state of the drive-side rotating body. 32 The contact sections will be 34c of the pair of locking elements 34 , which are moved outwards in the radial direction, by the rotation of the output-side rotating body 24b moved away from each other and impact the inner circumferential surface of the clutch housing. 31 in the attachment. A further rotation of the output-side rotating body. 24b is prevented in a more reliable way because the pair of locking elements 34 between the output-side rotating body24b and the clutch housing 31 is arranged. During a rotation of the drive-side rotating body. 32 The drive torque of the drive-side rotating body is 32 in a more reliable way onto the output-side rotating body 24b transferred because the pair of locking elements 34 , which is moved inwards in the radial direction, towards each other and the side surface 24e of the output-side rotating body 24b pushes. (5) The pair of locking elements 34 is on the support element 33 attached. The support element 33 stabilizes during rotation of the drive-side rotating body 32 and the output-side rotating body 24b the movement of the locking element 34 in the radial direction. This stabilizes the transmission of the drive torque to the driven rotating body. 24b through the locking element 34during a rotation of the drive-side rotating body 32 and when rotation of the output-side rotating body is prevented 24b in the non-rotating state of the drive-side rotating body 32 Furthermore, the supporting element bears 33 constantly the locking element 34 , because the drive-side rotating body 32 and the output-side rotating body 24b as a unit of the locking element 34 to be rotated. (6) The output-side rotating body 24b is rod-shaped, and each of the pair of locking elements 34 The outgoing side curve surface 34d on, which the output-side rotating body 24b on the side surface on the opposite side of the contact section 34c radially opposite. In the non-rotating state of the drive-side rotating body. 32 The output-side curve surface 34d from the output-side rotating body 24bpushed outwards in the radial direction when the driven-side rotating body 24b is rotated so that the locking element 34 moved radially outwards. Thus, the rod-shaped, output-side rotating body acts 24b and the output-side curve surface 34d in the non-rotating state of the drive-side rotating body 32 so that the locking element 34 is moved outwards in a simple radial direction. (7) The clutch 3 The pair of locking elements 34 on, which is arranged in such a way that it forms the rod-shaped output-side rotating body 24b between itself. During a rotation of the drive-side rotating body. 32 holds the pair of locking elements 34 the rod-shaped output-side rotating body 24b on the output side of the curve surface 34dbetween themselves, when it is the driving torque of the drive-side rotating body 32 absorbs. This prevents the transmission of the drive torque through the locking element. 34 carried out in an even more stable manner. (8) The output-side rotating body 24b It has a simple, elliptical cross-section and is therefore easy to manufacture. In particular, the metal worm shaft... 24 arranged output-side rotating bodies 24b easily formed by machining. The rotation of the output-side rotating body. 24b , which has an elliptical cross-section, pushes the locking element 34 in a simple way in the radial direction outwards. (9) The shape of each output-side curve surface 34d When viewed from the axial direction, it is arc-shaped, so that it forms the side surface 24e of the output-side rotating body 24bcan be held between themselves. Thus, the pair of locking elements holds 34 during a rotation of the drive-side rotating body 32 the output-side rotating body 24b in a more reliable way. Furthermore, the locking element 34 in the non-driving state of the drive-side rotating body 32s moved outwards in the radial direction without any problems, while the output-side rotating body 24b turns. (10) The output-side rotating body 24b It is rod-shaped and has an elliptical cross-section, and can therefore be smaller in the radial direction than the conventional output-side rotating body. Furthermore, the output-side rotating body has 24b A simple design. This reduces the costs for tooling, material, and machining to form the output-side rotary body. 24b . (11) The conventional coupling is designed to prevent rotation of the output-side rotating body by applying the wedge effect, which occurs when the rolling element is positioned between the output-side rotating body and the collar in the driven state of the rotating shaft. This requires high component accuracy for the coupling components. The coupling 3 In contrast, the present embodiment is designed in such a way that it prevents a rotation of the output-side rotating body. 24b applying the frictional force between the locking element 34 and the clutch housing 31 prevents this. Therefore, the components of the clutch need 3 It does not offer the same high precision as a conventional coupling. This increases the manufacturing costs for the coupling. 3 reduced.

[0054] A second embodiment of the present invention will now be described with reference to the Fig. 8 to Fig. 11. In the second embodiment, the same components as in the first embodiment are provided with the same reference numerals and are not described.

[0055] One in Fig. 8 clutches shown 51 is instead of the clutch 3 of the first embodiment, arranged in the engine. The clutch 51 In the present embodiment, the clutch housing has 31 , a drive-side rotating body 52 , a support element 53 , the pair of locking elements 34 , a driven-side rotating body 54 , and a steel ball 55 on.

[0056] As in Fig. Figure 9 shows the drive-side rotating body. 52 , which is inside the clutch housing 31is arranged, made of resin and integral with the drive coupling section 32a , the carrier section 32b , and the pair of drive transmission sections 32c trained. As in Fig. Figure 10(a) shows a pair of transfer leads. 52a on the inner circumferential surface of the coupling hole 32d formed, which forms the central part of the drive coupling section 32a and the carrier section 32b in the direction of the central axis 14 permeated. The pair of transfer advantages 52a is one-piece on a pair of flat sections 32f arranged parallel to each other on the inner circumferential surface of the coupling hole 32d delimiting support section 32b extend. The pair of transfer leads 52a extends to the center of the coupling hole 32d there. The support section 32bevery transmission advantage 52a possesses when viewed from the direction of the central axis 14 a trapezoidal shape in which the circumferential width increases from the basal end (section closer to the flat section). 32f ) to the distal end (section closer to the central axis) 14 ) becomes narrower. Both circumferential end surfaces of each transfer projection 52a are drive-side transmission surfaces 52b , 52c , which run parallel to the central axis 14 extend. The pair of transfer leads 52a The present embodiment, when considering the drive coupling section, shows 32a her (i.e. in the in Fig. 10(a) shown condition) the drive-side transmission surface 52b in the clockwise direction and the drive-side transmission surface 52c in the counter-clockwise direction.

[0057] According to the representation in Fig. 8 and Fig. 9 is a pair of access hooks 56 , which run along the central axis 14 of the support section 32b extend, at the middle part in the circumferential direction, at the distal end in the axial direction of the pair of drive transmission sections 32c trained. The intervention hooks 56 of the pair are in the drive-side rotating body 52 spaced 180° apart in the circumferential direction. Each engagement hook 56 features a square prism-shaped engagement wave section 56a on, which extends from the distal end face of the drive-side rotating body 52 along the axial direction of the rotating shaft 7 extends, as well as providing an intervention advantage 56b , which originates from the distal end of the intervention wave section 56a protrudes inwards in the radial direction. The radially outer side surface of the engagement shaft section. 56a each engagement hook56 is flush with the radially outer side surface of the drive transmission section 32c , and the radially inner side surface of the engagement shaft section 56a lies on the radially inner side surface of the drive transmission section 32c radially outwards. Each engagement hook 56 can be caused by elastic deformation in the radial direction of the rotating shaft 7 be tipped over.

[0058] As in Fig. As shown in 9, this is the connection between the pair of drive transmission sections. 32c arranged support element made of resin material and, like the support element, possesses 33 The first embodiment has a hollow box shape. A main support body section 53a , which is the supporting element 53 represents, has a similar shape to the supporting element 33 of the first embodiment. In other words, the support element 53a pair of end walls that are aligned with each other in the axial direction of the rotating shaft 7 opposite each other, and a circular through-hole 33a is formed in the end wall.

[0059] A substantially ring-shaped base section 53b , which extends outwards in the radial direction, is a unit with the lower end of the main support body section 53a trained. The basic section 53b , which is perpendicular to the axial direction of the rotating shaft 7 The extension is designed such that the outer diameter is slightly larger than the outer diameter of the entire pair of drive transmission sections. 32c in the drive-side rotating body 52 and slightly smaller than the inner diameter of the clutch housing 31 is. Furthermore, according to the presentation in Fig. 8 the thickness of the base section 53b essentially equal to the length of the section of the engagement hook 56with the exception of the intervention advantage 56b , i.e., the axial length of the engagement shaft section 56a .

[0060] As in Fig. Figure 9 shows two pairs of obstacle sections. 53c as a unit with the outer circumferential edge of the base section 53b trained. Each pair of obstacle sections 53c Each corresponds to one drive transmission section. 32c of the drive-side rotating body 52 A pair of obstacle sections 53c is trained in a position separated from the other pair of obstacle sections 53c is spaced 180° apart in the circumferential direction. Each obstacle section 53c extends along the axial direction of the rotating shaft 7 , so that the distal end points upwards (towards the drive-side rotating body) 52 (points out). The distance T between the pair of obstacle sections 53cis such that it is larger than the circumferential width t of the engagement hook. 56 is. The curvature of the obstacle surface 53d or the inner circumferential area of ​​each obstacle section 53c is such that it is equal to the curvature (cf. Fig. 10(b)) of the outer circumferential surface of the section between the transmission parts 32e of the drive transmission section 32c is. Furthermore, the obstacle areas are 53d all obstacle sections 53c arranged on the same circle (not shown), the center of which is the center of the base section 53b represents the diameter of the circle defined by the obstacle areas. 53d all obstacle sections 53c The extension is equal to the outer diameter of the entire pair of drive transmission sections. 32c in the drive-side rotating body 52 The outer diameter of the base section 53bincluding the obstacle section 53c is slightly smaller than the inner diameter of the clutch housing 31 .

[0061] An intervention recess 53e is between the pair of obstacle sections 53c in the basic section 53b trained. The two access recesses 53e are engaged with the two engagement hooks 56 of the drive-side rotating body 52 , to the drive-side rotating body 52 and the support element 53 to unite. Every intervention recess 53e is from the outer circumferential edge of the base section 53b here recessed inwards in the radial direction. As in Fig. Figure 8 shows the radial length at the section of the two engagement recesses. 53e equal to the space between the intervention wave sections 56a of the pair of intervention hooks 56 in the basic section 53bThe circumferential width of each access recess 53e is such that it is equal to the distance T between the pair of obstacle sections 53c is.

[0062] The support element 53 is relative to the drive-side rotating body 52 arranged so that the main body section of the carrier 53a , which is the pair of locking elements 34 records, between the pair of drive transmission sections 32c and with the drive-side rotating body 52 is integrated when the engagement hook 56 at the distal end of each drive transmission section 32c into the corresponding intervention recess 53e intervenes. In this case, which is in Fig. 8 and Fig. As shown in 9, the support element is 53 relative to the drive-side rotating body 52 arranged so that the main body section of the carrier 53afrom the distal end of the pair of drive transmission sections 32c between the pair of drive transmission sections 32c is inserted, and the pair of engagement hooks 56 into the pair of access openings 53e is used. The basic section 53b (Incision recess) 53e ) and the engagement hook 56 are interlocked by the engagement lead 56b of the intervention hook 56 from the side of the main body section 53a over the base section 53b is moved outwards, so that the support element 53 and the drive-side rotating body 52 are united with each other.

[0063] In the support element 53 and the drive-side rotating body 52 , which are connected by the pair of engagement hooks 56 when they are joined together, it is a pair of obstacle sections. 53cfrom the outer circumferential surface of each drive transmission section 32c arranged radially outwards, and the obstacle surface 53d of the pair of obstacle sections 53c occurs in the attachment on the outer circumferential surface at the distal end of each drive transmission section. 32c Thus, every drive transmission section 32c through the obstacle section 53c prevented from moving radially outwards. The distance T between the pair of obstruction sections. 53c is larger than the circumferential width t of the engagement hook 56 Thus, the drive-side rotating body can 52 in the circumferential direction relative to the support element 53 in the area of ​​the distance T between the obstacle sections 53c turn.

[0064] In the same way as the driven-side rotating body 24bIn the first embodiment, the output-side rotating body extends 54 from the basal end face of the worm shaft main body 24a It runs along the axial direction and is rod-shaped, so that the cross-section has an elliptical shape orthogonal to the axial direction. The central axis 17 of the output-side rotating body 54 corresponds to the center axis 12 of the worm shaft main body 24a The output-side rotating body 54 is between two output-side curve surfaces 34d arranged in the radial direction inside the clutch housing 31 opposite each other, so that it is separated from the pair of locking elements 34 about the pair of through holes 33a of the support element 53 is absorbed between itself. The distal end of the output-side rotating body. 54 is in the coupling hole 32d of the support section 32bused, and the steel ball 55 , which the thrust load of the rotating shaft 7 and the snail shaft 24 The shaft is located between the distal end face of the rotating shaft. 7 and the distal end face of the output-side rotating body 54 arranged.

[0065] As in the Fig. 9 and Fig. As shown in Figure 10(a), the pair of transmission recesses is 54a at the distal end of the output-side rotating body 54 formed, and the distal ends of a rotating body attached to the drive-side 52 arranged pair of transmission projections 52a are each in the pair of transmission recesses 54a inserted. Each recess of the pair of transmission recesses 54a opens radially outwards in the direction of the short side in the cross-section of the drive-side rotating body 52 Each recess of the pair of transmission recesses54a opens to the side of the distal end (top in) Fig. 9) of the drive-side rotating body 52 to. Each transmission recess 54a possesses when viewed from the direction of the central axis 17 of the output-side rotating body 54 Essentially a trapezoidal shape, where the circumferential width narrows from the radially outer opening to the radially inner base surface. The inner side surfaces at both ends in the circumferential direction of each transmission recess. 54a form the output-side transmission surfaces 54b , 54c , which has a planar shape parallel to the central axis 17 of the output-side rotating body 54 possess. Each transmission recess 54a The present embodiment, when viewed from the side of the distal end of the output-side rotating body, exhibits 54 her, i.e. in which in Fig. 10(a) the state shown, the output-side transmission surface 54b in the clockwise direction and the output-side transmission surface 54c in the counter-clockwise direction.

[0066] A detailed description of the drive-side transmission surfaces will now follow. 52b , 52c and the output-side transmission surfaces 54b , 54c As in Fig. Figure 10(a) shows that in each transmission recess 54a arranged transfer advantage 52a when viewed from the side of the distal end of the output-side rotating body 54 here the output-side transmission surface 54b in the clockwise direction, which is the output-side transmission surface 54b in the direction clockwise of the transmission recess 54a opposite in the circumferential direction, as well as the drive-side transmission surface 52cin the counterclockwise direction, which is the output-side transmission surface 54c in the direction counterclockwise of the transmission recess 54a opposite in the circumferential direction. The drive-side transmission surface 52b and the output-side transmission surface 54b , which are opposite each other, and the drive-side transmission surface 52c and the output-side transmission surface 54c , which are opposite each other, have an angle of inclination or the like which is set so that the opposing surfaces come into contact with each other when the rotational force is applied by the drive-side rotating body 52 here acts, and the opposing surfaces do not come into contact with each other when the rotational force is applied by the driven-side rotating body. 54 acting from this direction. When the rotational force originates from the drive-side rotating body. 52where it acts, the drive-side transmission surface therefore comes into play. 52b and the output-side transmission surface 54b , which are opposite each other, as well as the drive-side transmission surface 52c and the output-side transmission surface 54c , which are opposite each other, each in a position adjacent to the other, and the drive torque is transmitted via the output-side transmission surfaces 54b , 54c from the drive-side transmission surfaces 52b , 52c on the output-side rotating bodies 54 transmitted.

[0067] The operation of the engine will now be explained, with a focus on the operation of the clutch. 51 described.

[0068] If according to the presentation in the Fig. 10(a) and Fig. 10(b) the load, i.e. the window pane, the output shaft 27 in the non-driving state of the rotating shaft 7and the non-rotating state of the drive-side rotating body 52 When subjected to a load, this load acts in the sense of a rotation of the driven-side rotating body. 54 (snail shaft) 24 ). If the driven-side rotating body 54 in the direction of arrow X2 between the pair of locking elements 34 When rotating, the output-side cam mechanism acts in the sense of a movement of the pair of locking elements. 34 in opposite directions in the radial direction outwards (see arrow Y2 in Fig. 10(b)). More precisely, since the cross-section of the driven-side rotating body 24b elliptical in shape, pushes when the driven-side rotating body rotates 54 Both ends in the main axis direction of the elliptical shape, the driven-side curved surfaces 34d of the pair of locking elements 34 in the radial direction outwards. The pair of locking elements 34, that of the driven-side rotating bodies 54 When pushed outwards in the radial direction, it moves in the radial direction of the clutch housing. 31 towards the outside, while it is separated from the pair of main body sections. 53a is guided so that the contact section 34c of the locking element 34 on the inner circumferential surface of the clutch housing 31 in the system. If the contact section 34c on the inner circumferential surface of the clutch housing 31 In the system, a further movement of the locking element occurs. 34 The outward movement is prevented in the radial direction. Thus, the locking element is 34 between the clutch housing 31 and the output-side rotating body 54 The image was taken in a horizontal position. Consequently, further rotation of the output-side rotating body is not possible. 54 through the space between the clutch housing 31 and the output-side rotating body 54horizontally recorded locking element 34 prevented. That is, between the contact section 34c of the locking element 34 and the inner circumferential surface of the clutch housing 31 A frictional force is generated, which causes a rotation of the driven-side rotating body. 54 This prevents the worm shaft from rotating. 24 prevented, and transmission of the drive torque from the worm shaft 24 on the rotating shaft 7 is prevented. The frictional force in this case is expressed as μ·T1, where T1 is the radial force component of the rotating body on the driven side. 54 on the locking element 34 applied thrust force T (force component of the thrust force T in the direction along the direction of movement of the locking element) 34 ), and μ is the coefficient of friction. In this case, the rotational force is not directly transferred from the driven-side rotating body. 54on the drive-side rotating body 52 acted upon, since the drive-side transmission surface 52b and the output-side transmission surface 54b as well as the drive-side transmission surface 52c and the output-side transmission surface 54c , which each align with each other in the direction of rotation of the output-side rotating body 54 are opposite each other, held in a non-touching state.

[0069] If the driven-side rotating body 54 in the non-driving state of the rotating shaft 7 from the output shaft 27 (cf.) Fig. 1) in the opposite direction to that in the Fig. 10(a) and Fig. In the example shown in 10(b), rotation is prevented in the same way.

[0070] As in the Fig. 11(a) and Fig. As shown in 11(b), the drive-side rotating body rotates 52in the rotating driving state of the rotating shaft 7 (cf. arrow α 2) with the forward-rotating rotating shaft 7 The transmission part 32e on the front side in the direction of rotation in each drive transmission section 32c is then caused by the rotation of the drive-side rotating body 52 against the drive-side curve surface opposite in the circumferential direction 34e pushed. When the rotating shaft 7 from the into the Fig. 10(a) and Fig. In the state shown in 10(b) where the locking element is driven in a rotating manner, the locking element is locked (prevents rotation). 34 canceled when the circumferential force component P1 of the thrust force P is used to push the drive-side cam surface 34e greater than or equal to the frictional force μ·T1 (see below). Fig. 10(b)), which between the contact section 34c of the locking element 34 and the inner circumferential surface of the clutch housing 31is generated.

[0071] If each drive transmission section 32c by the rotation of the drive-side rotating body 52 against the drive-side curve surface 34e When pushed at the front in the direction of rotation, the contact section 34c of the locking element 34 through the radial force component P2 of the thrust force P of the transmission part 32e from the inner circumferential surface of the clutch housing 31 moved away (see arrow β 2) because the drive-side curve surface 34e is inclined relative to the radial direction. In this case, the pair of locking elements moves 34 in the radial direction of the clutch housing 31 towards the inside, while they are separated from the pair of support elements 53 is guided. The output-side curve surfaces 34d of the pair of locking elements 34emerge from the outside in the radial direction of the clutch housing. 31 on the pair of arcuate side surfaces 24e of the output-side rotating body 54 in the attachment. The pair of output-side curved surfaces 34d refers to the output-side rotating body 54 along the secondary axis direction of the elliptical shape in the output-side rotating body 54 brought into the facility. Furthermore, the pair of locking elements is 34 through the force component P2 on the output-side rotating body 54 pushed towards it, so that it forms the driven-side rotating body 54 Keep between them.

[0072] If the drive-side rotating body 52 is rotated and each drive transmission section 32c against the drive-side curve surface 348 is pushed at the front in the direction of rotation, so that the pair of locking elements 34moving inwards in the radial direction, any drive-side transmission surface can 52b at the direction of rotation of the drive-side rotating body 52 opposite output-side transmission surface 54b enter into operation. The drive torque of the rotary shaft 7 is then applied to the output-side rotating body 54 transferred. In this case, the pair of locking elements is transferred. 34 , which the output-side rotating body 54 between itself, from the circumferential force component P1 of the thrust force P, which is from the transmission part 32e together with the output-side rotating body 54 is generated as a unit with the drive-side rotating body 52 around the central axis L1 of the rotating shaft 7 rotated (cf.

[0073] Arrow γ 2). In other words, the drive-side rotating body 52 and the output-side rotating body 54coupled together and are connected by the locking element 34 , which is located between the drive-side rotating body 52 and the output-side rotating body 54 is recorded lying down, and furthermore through the drive-side transmission surface 52b and the output-side transmission surface 54b Rotated as a unit. By means of the locking element. 34 rotates the support element 53 as a unit with the drive-side rotating body 52 and the output-side rotating body 54 .

[0074] Thus, the drive torque of the rotary shaft 7 through the drive-side rotating body 52 and the locking element 34 on the output-side rotating body 54 transferred. When the worm shaft 24 turns, the worm gear turns 26 and the output shaft 27 corresponding to this rotation. Thus, the one connected to the output shaft 27The coupled window regulators are activated, and the window pane is opened and closed (raised and lowered). The drive torque is transmitted to the worm shaft in the same way. 24 transmitted when the rotating shaft 7 in the opposite direction to that in Fig. 11(a) and Fig. 11(b) shown in the example (i.e., in the reverse direction).

[0075] In addition to the advantages (1) to (11) of the first embodiment, the present embodiment has the advantages described below. (12) The pair of drive transmission sections 32c is through the in the support element 53 arranged obstacle section 53c prevented from moving radially outwards. Thus, the drive transmission section pushes 32c efficiently the drive-side curve surface 34e in the direction of rotation of the drive-side rotating body52 with the rotation of the drive-side rotating body 52 during a rotation of the drive-side rotating body 52 . (13) The drive-side rotating body 52 and the support element 53 are joined by inserting the engagement hooks 56 into the intervention recess 53e and their locking onto the base section 53b Thus, the drive-side rotating body can 52 and the support element 53 They are treated as a single unit. As a result, component management is simplified, and the work involved in assembling the coupling is reduced. 51 are easy to execute. (14) The drive-side transmission surfaces 52b , 52c , which are located in the drive-side rotating body 52 are arranged, and the output-side transmission surfaces 54b , 54c , which are located in the output-side rotating body 54are arranged, occur during a rotation of the drive-side rotating body. 52 in the direction of rotation of the drive-side rotating body 52 in a system adjacent to one another, so that the drive torque of the drive-side rotating body 52 efficiently on the output-side rotating body 54 is transmitted. Furthermore, the rotational transmission can be carried out from the drive-side rotating body. 52 on the output-side rotating body 54 using the drive-side transmission surfaces 52b , 52c and the output-side transmission surfaces 54b , 54c This can be achieved. Therefore, the dimensional accuracy of each element can be reduced, and noise and vibration are reduced compared to the case where the rotational transmission is from the drive-side rotating body. 32 on the output-side rotating body 24b like with the clutch 3the first embodiment with the pair of locking elements 34 and the output-side rotating body 24b is accomplished.

[0076] The embodiments of the present invention can be modified as described below.

[0077] In the first and second embodiments, the present invention was described using the example of a motor used as a drive source for the window regulator device; however, the present invention can be applied to a motor that powers the motor unit. 1 with the rotating shaft 7 and the delay unit 2 with the snail shaft 24 It has no motor for use as a drive source for a window regulator. Apart from the motor, the clutch 3 , 51in a device with a drive shaft for rotary driving and a driven shaft to which the drive torque of the drive shaft is transferred.

[0078] At the clutch 3 In the first embodiment, the pair of locking elements 34 in the non-rotating state of the drive-side rotating body 32 between the output-side rotating body 24b and the inner circumferential surface of the clutch housing 31 It is recorded lying down and is designed so that it is in a state in which the desired frictional force is achieved between the contact section. 34c each locking element 34 and the inner circumferential surface of the clutch housing 31 A rotation of the output-side rotating body is generated. 24b related to the pair of locking elements 34 allows. In other words, if the driven-side rotating body 24bin the non-rotating state of the drive-side rotating body 32 As it is rotated, the connection between the contact section becomes more difficult. 34c and the inner circumferential surface of the clutch housing 31 The generated frictional force causes a rotation of the driven-side rotating body. 24b , and a rotation of the pair of locking elements 34 referring to the clutch housing 31 is prevented. Accordingly, the clutch can be easily attached. 3 be designed, since the pair of locking elements 34 and the output-side rotating body 24b They only need to be manufactured with a mold suitable for generating the desired frictional force. As a result, the manufacturing costs for the clutch can be reduced. 3 further reduced. Regarding the clutch 51 The situation is similar to the second embodiment.

[0079] In the motor of the first embodiment, the pair of locking elements 34in the non-rotating state of the rotating shaft 7 between the output-side rotating body 24b and the inner circumferential surface of the clutch housing 31 Recorded lying down, a rotation of the output-side rotating body 24b related to the pair of locking elements 34 is permitted in a state in which the desired frictional force between the contact section 34c of the locking element 34 and the inner circumferential surface of the clutch housing 31 is generated, and a transmission of the torque from the drive to the worm gear 26 coupled output shaft 27 on the rotating shaft 7 can at least be prevented by the engagement load of the worm gear 26 and the screw tooth section 24c of the worm shaft main body 24a , the frictional load of the worm shaft main body 24a and the camp 25a , 25b, which the worm shaft main body 24a axially supportive, and the rotational load of the coupling 3 The rotational load of the coupling 3 is the one inside the clutch 3 generated frictional force (friction load). Thus, the drive torque of the rotating shaft 7 through the clutch 3 , the worm shaft main body 24a with the screw tooth section 24c and the worm gear 26 on the output shaft 27 transferred, whereas a transmission of the rotational force from the output shaft 27 on the rotating shaft 7 at least through the engagement load of the worm gear 26 and the screw tooth section 24c , the frictional load of the worm shaft main body 24a and the camp 25a , 25b as well as the rotational load of the coupling 3 is prevented. That is, instead of a transmission of the torque from the output shaft. 27on the rotating shaft 7 only with the clutch 3 To prevent this, the transmission of torque from the output shaft is blocked. 27 on the rotating shaft 7 with the engine as a whole, including the clutch 3 prevented, which is why high dimensional accuracy is not possible on every component of the coupling. 3 This is necessary. This allows the manufacturing costs of the motor to be further reduced. The load to prevent the transmission of rotational force from the output shaft. 27 on the rotating shaft 7 is not related to the engagement load of the worm gear 26 and the screw tooth section 24c , the frictional load of the worm shaft main body 24a and the camp 25a , 25b as well as the frictional load of the clutch 3 not limited, but can also include the frictional load or similar of other sliding parts within the engine. In the case of the clutch51 The situation is similar for the motor equipped with the second embodiment.

[0080] In each embodiment of the foregoing description, the cross-section is orthogonal to the axial direction in the output-side rotating bodies. 24b , 54 elliptical, and the output-side rotating bodies 24b , 54 They are generally rod-shaped. The cross-sectional shape is orthogonal to the axial direction in the driven-side bodies of revolution. 24b , 54 However, it can be flat as long as a shape is formed that allows the locking element to 34 during its rotation, it is pushed outwards in the radial direction. The cross-section in the output-side rotating bodies 24b , 54 For example, a shape orthogonal to the axial direction can be rectangular, and the output-side bodies of revolution 24b , 54 They can all have a columnar shape.

[0081] In each embodiment of the foregoing description, the output-side cam surface 34d It is formed in a circular arc shape, but can also have a flat shape parallel to the axial direction.

[0082] In the first embodiment of the foregoing description, the coupling has 3 a pair of locking elements 34 open, but can also only be a locking element 34 exhibit. In this case, during a rotation of the drive-side rotating body, 32 the drive torque of the drive-side rotating body 32 through the locking element 34 on the output-side rotating body 24b transmitted when a rotating body is driven from the drive side 32 pushed locking element 34 against the output-side rotating body 24b is being pushed. The clutch 3 can be designed in such a way that it has three locking elements 34exhibits. In this case, according to the number of locking elements. 34 three drive transmission sections 32c on the drive-side rotating body 32 arranged. This is similar to the clutch. 51 the second embodiment.

[0083] In the second embodiment of the foregoing description, the pair of engagement hooks 56 for the axial engagement between the drive-side rotating body 52 and the support element 53 and their union on the drive-side rotating body 52 arranged. The pair of engagement hooks 56 However, it can also be attached to the support element 53 be arranged in relation to the drive-side rotating body 52 can be brought into axial engagement. The pair of engagement hooks 56 and the pair of surgical incisions 53e It only needs to be attached to at least one of either the drive-side rotating body52 or the support element 53 to be designed, while their shape is not limited to the design of the second embodiment. The pair of engagement hooks 56 and the pair of surgical incisions 53e are for axial engagement with the drive-side rotating body 52 and the support element 53 designed while undergoing a relative rotation in the circumferential direction of the support element 53 and the drive-side rotating body 52 allow.

[0084] In the second embodiment of the foregoing description, the support element has 53 two obstacle sections 53c corresponding to each drive transmission section 32c on. However, there can also be only one obstacle section. 53c corresponding to each drive transmission section 32c or three or more of them corresponding to each drive transmission section 32cbe arranged.

[0085] In the first embodiment of the foregoing description, the locking element 34 from the support element 33 worn, however, the carrier element can be affected 33 can be dispensed with as long as the locking element 34 with the rotation of the drive-side rotating body 32 and the output-side rotating body 24b can move along the radial direction. Furthermore, during coupling, 51 of the second embodiment on the support element 53 can be dispensed with as long as the locking element 34 with the rotation of the drive-side rotating body 52 and the output-side rotating body 54 can move along the radial direction.

[0086] In each embodiment of the foregoing description, each locking element has 34 a pair of drive-side cam surfaces 34e each locking element 34However, it can be designed in such a way that it has a drive-side cam surface. 34e exhibits. In this case, the motor unit 1 designed so that it rotates the shaft 7 rotates only in one direction, and the drive-side cam surface 34e is designed in such a way that, with regard to the drive transmission section 32c on the front side in the direction of rotation of the rotating shaft 7 is arranged.

[0087] In each embodiment of the foregoing description, the output-side rotating body can 24b , 54 as one of the worm shaft main body 24a a separate body. In this case, the output-side rotating body 24b , 54 and the worm shaft main body 24a They are designed so that they can rotate as a unit (engage in the direction of rotation). The drive-side rotating body 32 , 52can be used as a unit with the rotating shaft 7 be trained. Reference symbol list 1 motor unit 2 Delay unit 3.51 Clutch 7 Rotating shaft with drive shaft function 24a Worm shaft main body with function of a driven shaft 24b, 54 output-side rotating body with function of a cam shaft 24c screw tooth section 25a, 25b storage 26 worm gear 27 Output shaft 31 Clutch housing 32, 52 drive-side rotary body 33, 53 Support element 34 Locking element 34c Contact section 34d output side curve surface 34e drive-side cam surface 52b, 52c drive-side transmission surface with transmission surface function 53c Obstacle section 54b, 54c output-side transmission surface with transmission surface function 56 engagement hooks with engagement section function QUOTES INCLUDED IN THE DESCRIPTION

[0088] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0089] JP 2003-278784

[0006]

Claims

[1] Coupling which has: a drive shaft; a drive-side rotating body that can be rotated as a unit with the drive shaft; a driven shaft that is arranged coaxially with the drive shaft; a rotating body on the output side, which can be rotated as a unit with the driven shaft; a coupling housing suitable for arranging the drive-side rotating body and the driven-side rotating body; and a locking element arranged between the drive-side rotating body and the driven-side rotating body inside the coupling housing, wherein the locking element has a contact section that comes into contact with and moves away from the inner circumferential surface of the coupling housing, and a drive-side cam surface against which the drive-side rotating body comes into contact from one direction of rotation, where When the output-side rotating body is rotated while the input-side rotating body is in a non-rotating state, the locking element is pushed by the output-side rotating body and moved radially outwards, thereby bringing the contact section into contact with the inner circumferential surface of the coupling housing, so that the locking element is positioned between the coupling housing and the output-side rotating body and prevents further rotation of the output-side rotating body; and In the rotating state of the drive-side rotating body, the drive-side rotating body pushes the drive-side cam surface in the direction of rotation, and the drive-side cam surface causes the locking element to move inwards in the radial direction and the locking element to be pushed against the driven-side rotating body, so that the locking element is located between the drive-side rotating body and the driven-side rotating body, thereby coupling the drive-side rotating body and the driven-side rotating body to the locking element, so that they can be rotated as a unit. [2] Coupling according to claim 1, wherein the drive-side cam surface is inclined relative to the radial direction of the drive shaft, so that the locking element is moved in the radial direction of the drive shaft when the drive-side cam surface is pushed by the drive-side rotating body in the direction of rotation. [3] Coupling according to claim 2, wherein the locking element has a pair of drive-side cam surfaces, and the pair of drive-side cam surfaces is arranged symmetrically on two circumferential sides of the contact section. [4] Coupling according to one of claims 1 to 3, wherein the locking element is arranged as a pair to accommodate the output-side rotating body in the radial direction between them, and the pair of locking elements is movable in opposite directions along the radial direction of the drive shaft. [5] Coupling according to one of claims 1 to 4, which further comprises a support element which carries the locking element in such a way that it is movable in the radial direction of the drive shaft and rotates by means of the locking element as a unit with the drive-side rotating body and the driven-side rotating body. [6] Coupling according to claim 5, wherein the drive-side rotating body has a pair of drive transmission sections extending in an axial direction of the drive shaft and opposite each other in the radial direction of the drive shaft, and the pair of drive transmission sections is designed such that, when the drive-side rotating body rotates, it shifts the drive-side cam surface in the direction of rotation of the drive-side rotating body; and the support element is arranged between the pair of drive transmission sections and has a hindrance section that prevents the drive transmission sections from spreading outwards in the radial direction. [7] Coupling according to claim 5 or 6, wherein at least one of the drive-side rotating body and the support element has an engagement section which brings the drive-side rotating body and the support element into integral engagement with each other in the axial direction. [8] Coupling according to any one of claims 9 to 7, wherein the output-side rotating body has a cam shaft; the locking element has a cam surface on the output side, which is opposite the cam shaft in the radial direction on a side surface set away from the contact section; and when the output-side rotating body rotates in the non-rotating state of the input-side rotating body, the cam shaft pushes the output-side cam surface and moves the locking element outwards in the radial direction. [9] Coupling according to claim 8, wherein the locking element is arranged as a pair such that it accommodates the cam shaft lying between it, and the pair of locking elements is movable in opposite directions along the radial direction of the drive shaft; and During a rotation of the drive-side rotating body, the pair of locking elements, which is moved radially inwards, holds the cam shaft with the output-side cam surfaces of the pair of locking elements and transmits a drive torque from the drive-side rotating body to the output-side rotating body through the locking elements. [10] Coupling according to claim 8 or 9, wherein the cam shaft is rod-shaped and has an elliptical cross-section. [11] Coupling according to claim 10, wherein the output-side cam surface has a circular arc shape when viewed from an axial direction, so that the cam shaft can be held in a secondary axis direction of the cam shaft from both side surfaces. [12] Coupling according to one of claims 1 to 11, wherein the drive-side rotating body and the driven-side rotating body have transmission surfaces which come into contact with each other during a rotation of the drive-side rotating body in the direction of rotation of the drive-side rotating body. [13] Coupling according to one of claims 1 to 12, wherein the locking element is held in the non-rotating state of the drive-side rotating body by the output-side rotating body and the inner circumferential surface of the coupling housing, and in a state in which a desired frictional force is generated between the contact section and the inner circumferential surface of the coupling housing, rotation of the output-side rotating body relative to the locking element is permitted. [14] Engine which features: a motor unit with a drive shaft; a delay unit with a driven shaft arranged coaxially with the drive shaft and onto which a drive torque of the drive shaft is transmitted, wherein the delay unit delays and releases the drive torque transmitted to the driven shaft; and the coupling according to one of claims 1 to 13, which is arranged between the drive shaft and the driven shaft. [15] Motor according to claim 14, wherein The delay unit comprises a driven shaft, a worm gear, and an output shaft, wherein the driven shaft is arranged so that it is rotatable as a unit with the output-side rotating body, is rotatably mounted by a bearing, and has a helical tooth section, the worm gear is in mesh with the helical tooth section, and the output shaft is drivenly coupled to the worm gear; and The locking element is held in the non-rotating state of the drive shaft by the output-side rotating body and the inner circumferential surface of the clutch housing, in a state in which a desired frictional force is generated between the contact section and the inner circumferential surface of the clutch housing, rotation of the output-side rotating body is permitted, and transmission of the rotational force from the output shaft to the drive shaft is prevented by at least one engagement load of the worm gear and the helical tooth section, a frictional load of the driven shaft and the bearing, and a rotational load of the clutch.