JP2013046522A - Motor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a motor which reliably and easily inhibits shaft misalignment between a rotation shaft and a warm shaft.SOLUTION: A taper recessed part 61a, arranged coaxially with a warm shaft 33 (a warm shaft part 38) and forming a recessed shape in the axial direction, is included at one end side of a driven side rotor 39 (a body part 39c), and a part of a ball 46 is housed in the taper recessed part 61a.

Description

  The present invention relates to a motor.

  2. Description of the Related Art Conventionally, a motor used in a power window device or the like is composed of a motor body and a speed reduction unit. The motor main body includes a yoke, a rotor including a rotating shaft that is driven to rotate by a supply current, and a brush holder fitted to the yoke. The speed reduction unit includes a gear housing fixed to the yoke and a speed reduction mechanism accommodated in the gear housing. The speed reduction mechanism of the speed reduction unit includes a worm shaft that is coaxially connected to the rotation shaft of the rotor, and a wheel gear that meshes with the worm shaft and integrally includes an output shaft.

  By the way, in the motor shown in Patent Document 1, a pair of positioning holes are formed in the brush holder in order to align the axial center of the rotor (rotating shaft) and the worm shaft of the speed reduction mechanism, and the positioning is performed in the opening of the housing. A configuration is disclosed in which positioning protrusions are formed at positions corresponding to the holes and the positioning protrusions are fitted into the positioning holes so that the shaft centers are aligned.

JP 2003-143804 A

However, depending on the dimensional accuracy of the positioning hole and the positioning protrusion, the shaft center may be shifted and noise may be generated, and there is a risk of increasing the cost in order to increase the dimensional accuracy.
The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a motor that can more reliably and easily suppress the axial deviation between the rotating shaft and the worm shaft.

  In order to solve the above-mentioned problem, the invention according to claim 1 includes a motor main body that rotationally drives a rotary shaft, and a deceleration that includes a worm shaft that is assembled to the motor main body and provided substantially coaxially with the rotary shaft. A motor comprising: a speed reducing portion having a mechanism; and a connecting means for connecting the worm shaft of the speed reducing portion and the rotating shaft of the motor body so as to be integrally rotatable, the connecting means being connected to the rotating shaft A drive-side rotator that is integrally rotatable; a driven-side rotator that is engaged with the drive-side rotator in the rotational direction and is provided at one end of the worm shaft and is capable of rotating integrally with the worm shaft; A ball member that is coaxially and rotatably provided at one axial end of the rotating shaft, and a concave portion that is coaxial with the worm shaft and that is concave in the axial direction is provided at one end of the driven rotating body. The ball member And also as its gist that a part is accommodated in the recess.

  In the present invention, a concave portion that is coaxial with the worm shaft and has a concave shape in the axial direction is provided on one end side of the driven side rotating body, and at least a part of the ball member is accommodated in the concave portion. In this way, the ball member disposed coaxially with the drive-side rotating body rotated integrally with the rotating shaft is accommodated in the concave portion coaxial with the worm shaft, and the ball member is positioned. As a result, the ball member and the coaxial rotation shaft (drive-side rotator) are coaxial with the worm shaft, so that the rotation shaft can be arranged coaxially with the worm shaft more securely and with less axial deviation. be able to.

The invention according to claim 2 is the motor according to claim 1, wherein the concave portion is formed such that a contact surface with the ball member is formed in a tapered shape.
In this invention, since the contact surface with the ball member is formed in a taper shape in this invention, when the motor body and the speed reduction portion are assembled, the taper contact of the recess in which the ball member forms a concave shape in the axial direction. The contact with the surface suppresses the movement of the ball member in the direction perpendicular to the axis. In addition, since the contact surface of the recess is tapered, the ball member can be naturally disposed on the axis of the worm shaft.

  According to a third aspect of the present invention, in the motor according to the first or second aspect, at least the contact surface with the ball member is configured to have higher hardness than other portions of the driven-side rotating body. This is the gist.

  In the present invention, since the concave portion has at least a contact surface with the ball member having higher hardness than other portions of the driven-side rotator, the concave portion is caused by the frictional force in the axial direction of the ball member accompanying the rotation of the rotation shaft. Deformation of the recess can be suppressed, and axial misalignment between the worm shaft and the rotation shaft can be suppressed.

  Therefore, according to the above described invention, it is possible to provide a motor that can more reliably and easily suppress the axial deviation between the rotating shaft and the worm shaft.

It is sectional drawing of the motor of this embodiment. It is a partial expanded sectional view of a motor. It is a disassembled perspective view of a clutch part. It is a top view of a gear housing. (A) is sectional drawing of a brush holder, (b) is a bottom view of a brush holder. It is a disassembled sectional view for demonstrating the assembly of a clutch part. It is AA sectional drawing of FIG. It is sectional drawing for demonstrating operation | movement of a clutch. It is sectional drawing for demonstrating operation | movement of a clutch. It is a principal part expanded sectional view of the motor of another example.

DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment of the invention will be described with reference to the drawings.
As shown in FIG. 1, the motor 11 includes a flat motor body 12, a speed reduction unit 13, and a clutch 30.

  As shown in FIG. 1, the motor body 12 includes a yoke housing (hereinafter simply referred to as a yoke) 14, a pair of magnets 15, a rotating shaft 16, an armature (armature) 17, a commutator 18, a brush holder 19, and a brush 20. It has.

  The yoke 14 is formed in a substantially bottomed flat cylindrical shape, and a pair of magnets 15 are fixed to the inner peripheral surface of the yoke 14 so as to face each other. An armature 17 is accommodated inside the magnet 15. The armature 17 has a rotating shaft 16, and the base end portion of the rotating shaft 16 is rotatably supported by a bearing 21 provided at the center of the bottom of the yoke 14. On the other hand, a commutator 18 is fixed to a predetermined portion on the distal end side of the rotating shaft 16. Further, as shown in FIGS. 2 and 3, a connecting portion 16 a having a cross-sectional two-surface width shape that is chamfered in parallel from a cylindrical shape is formed at the distal end portion of the rotating shaft 16.

  A brush holder 19 as shown in FIGS. 5A and 5B is fitted into the opening of the yoke 14. The brush holder 19 includes a holder main body 19 a that substantially covers the opening of the yoke 14, and a connector portion 19 b that is integrally provided from the holder main body 19 a and protrudes radially outward of the yoke 14.

  A bearing 22 is provided at the center of the holder main body 19a, and a portion of the rotating shaft 16 between the commutator 18 and the connecting portion 16a is rotatably supported by the bearing 22. Further, on the yoke 14 side of the holder main body 19a, a pair of brushes 20 that are connected to the connector portion 19b by wires (not shown) and are in sliding contact with the commutator 18 are held by the brush holding portions 19d. The brush 20 supplies external power supplied via the connector portion 19b to the coil winding wound around the armature 17 via the commutator 18, and rotates the armature 17 (rotating shaft 16), that is, the motor main body 12 is rotated. Drive to rotate.

  Further, as shown in FIG. 5 (a), a holding portion 19c that is held between the yoke 14 and an opening of a gear housing 31 described later is provided on the outer periphery of the holder main body 19a over the entire periphery. ing. The holding portion 19c is covered with a seal member 23 made of an elastic member. The seal member 23 extends to the connector portion 19b side. The opening portions of the yoke 14 and the gear housing 31 are sealed by the seal member 23 to form a waterproof structure.

  As shown in FIG. 1, a flange portion 14 a that extends outward in the longitudinal direction of the cross section in the direction perpendicular to the axis of the yoke 14 is formed in the opening of the yoke 14. Each flange portion 14a is provided with a screw insertion hole (not shown) for inserting a screw 24 into a predetermined portion.

The speed reduction unit 13 includes a gear housing 31, bearings 32 a and 32 b, a worm shaft 33, a worm wheel 34, and an output shaft 35.
The gear housing 31 is made of resin, and a side (upper side in FIG. 1) end portion (hereinafter referred to as an upper end portion) fixed to the motor main body 12 has a flat shape (hereinafter referred to as an opening portion of the yoke 14). (Substantially rectangular). As shown in FIGS. 3 and 4, a fitting recess 31 a into which the holding portion 19 c of the holder main body 19 a of the brush holder 19 is fitted is formed at the upper end portion of the gear housing 31. Further, screw holes 31b and 31c into which the screws 24 are screwed are formed at positions corresponding to the screw insertion holes of the yoke 14 at the upper end portion of the gear housing 31, respectively. Then, with the brush holder 19 attached to the opening of the yoke 14, the holding portion 19 c of the holder body 19 a is fitted into the fitting recess 31 a of the gear housing 31, and the screw holes 31 b and 31 c of the gear housing 31 are screwed. By screwing 24, the yoke 14 and the gear housing 31 are connected to each other.

  The gear housing 31 is formed with a recess 31d that is recessed from the center of the bottom of the fitting recess 31a and opens long in the longitudinal direction of the fitting recess 31a. The gear housing 31 has a circular clutch housing recess 31e that is recessed from the center of the bottom of the recess 31d, and a worm that is recessed from the center of the bottom of the clutch housing recess 31e so as to extend along the axial direction of the rotary shaft 16. A shaft accommodating portion 31f (see FIG. 2) is formed. The gear housing 31 is formed with a wheel housing portion 31g that communicates with the worm shaft housing portion 31f in the direction perpendicular to the axis of the intermediate portion of the worm shaft housing portion 31f (right direction in FIG. 1).

  As shown in FIG. 3, an annular flange fitting recess 31h is formed in the opening of the clutch housing recess 31e. Engagement recesses 31i extending in the longitudinal direction are continuously formed at both longitudinal ends of the recess 31d in the flange fitting recess 31h.

  Further, as shown in FIG. 3, two pedestals 31j are formed at the bottom of the recess 31d. Each pedestal 31j is formed around the engaging recess 31i. That is, the base 31j is formed in a substantially U shape so as to have a wall surface continuous with the wall surface of the engaging recess 31i. Cylindrical engagement protrusions 31k are formed at both ends in the short direction of the recess 31d on the upper surface of each pedestal 31j.

  Further, as shown in FIG. 2, a bearing holding portion 31l is formed at the bottom of the clutch housing recess 31e so as to be able to bend in the direction perpendicular to the axis. The bearing holding portion 31l is formed in a substantially cylindrical shape having an inner diameter larger than that of the worm shaft housing portion 31f and an outer diameter smaller than the inner diameter of the clutch housing recess 31e. Further, the bearing holding portion 31l is formed so as to extend in the axial direction to the vicinity of the approximate center of the clutch housing recess 31e. Further, as shown in FIGS. 2 and 4, eight ribs 31m connected to the inner peripheral surface of the clutch housing recess 31e are provided at eight equiangular (45 °) intervals on the proximal end side of the outer peripheral surface of the bearing holding portion 31l. Is formed.

  The bearings 32a and 32b are metal and substantially cylindrical slide bearings (metal bearings), and the bearing 32a is fitted in the bearing holding portion 31l. The inner diameter of the bearing 32a is set smaller than the inner diameter of the worm shaft accommodating portion 31f. Further, the bearing 32b is fitted into the bottom side (lower side in FIG. 1) of the worm shaft housing portion 31f.

  The worm shaft 33 is made of a metal material, and includes a worm shaft portion 38 and a driven-side rotator 39 integrally formed at the end of the worm shaft portion 38 on the motor body 12 side (see FIG. 3). The worm shaft portion 38 is formed with a worm 38a at an intermediate portion thereof, and is rotatably supported by the bearings 32a and 32b at both ends thereof and is housed in the worm shaft housing portion 31f.

  The worm wheel 34 meshes with the worm 38a and is accommodated in the wheel accommodating portion 31g so as to be rotatable about the axis in the direction orthogonal to the worm shaft 33 (the direction orthogonal to the plane of FIG. 1). The output shaft 35 is coupled to the worm wheel 34 so as to rotate coaxially with the rotation of the worm wheel 34. The output shaft 35 is drivingly connected to a known window regulator (not shown) for raising and lowering the window glass.

  The rotating shaft 16 is connected to a worm shaft portion 38 via a clutch 30. As shown in FIGS. 2 and 3, the clutch 30 includes the driven side rotating body 39, the collar 41, a plurality of (three) rolling elements 42, a support member 43, a stopper 44, a driving side rotating body 45, and a ball member. The ball 46 is provided.

  The collar 41 has a cylindrical outer ring 41a, an annular flange portion 41b extending radially outward from one end of the outer ring 41a (the upper end in FIGS. 2 and 3), and a 180-degree interval from the flange portion 41b. It consists of a pair of engaging part 41c extended in the direction outer side. As for the collar 41, the outer ring | wheel 41a is internally fitted by the clutch accommodation recessed part 31e, and the flange part 41b is fitted by the flange fitting recessed part 31h. The collar 41 is prevented from rotating by engaging the engaging portion 41c with the engaging recess 31i. The outer ring 41a of the collar 41 is fitted in the other end (lower end in FIG. 2) to the vicinity of the tip (upper end in FIG. 2) position of the bearing holding portion 31l and does not hinder the bending of the bearing holding portion 31l. . The driven rotary body 39 is disposed inside the outer ring 41a.

  As shown in FIG. 3, the driven side rotating body 39 includes a shaft portion 39a extending coaxially from the base end portion of the worm shaft portion 38 to the motor body 12 side (rotating shaft 16 side), and the shaft portion 39a. A main body portion 39c having three engaging convex portions 39b extending radially outward at an angle (120 °) interval is provided. The engaging convex part 39b is formed so that the width in the circumferential direction increases toward the outer side in the radial direction. Moreover, as shown in FIG. 7 which is AA sectional drawing of FIG. 2, as for the radial direction outer side surface of the engagement convex part 39b, the distance with the inner peripheral surface 41d of the outer ring | wheel 41a of the collar 41 changes to a rotation direction. A control surface 51 is formed. The control surface 51 of the present embodiment is formed in a planar shape in which the distance from the inner peripheral surface 41 d of the collar 41 becomes shorter toward the end in the rotational direction of the driven-side rotator 39. As shown in FIG. 3, the driven-side rotator 39 is provided with a reinforcing rib 39 d of the engaging convex portion 39 b. The reinforcing rib 39d is formed so as to connect the circumferential end surfaces of the engaging convex portions 39b adjacent in the circumferential direction at the end portion of the engaging convex portion 39b on the worm shaft portion 38 side. Further, as shown in FIGS. 2 and 3, on the upper surface 39 i of the main body 39 c constituting the driven-side rotator 39, there is a plate housing recess 39 j for housing the hard plate 60 constituting the driven-side rotator 39. It is recessed in the direction.

  Each rolling element 42 is formed of a resin material in a substantially cylindrical shape, and is disposed between the control surface 51 of the engaging convex portion 39b and the inner peripheral surface 41d of the collar 41 as shown in FIG. The diameter of the rolling element 42 is smaller than the distance between the central portion (rotational direction central portion) 51a of the control surface 51 and the inner peripheral surface 41d of the collar 41, and the side portions (rotational direction end portions) 51b, 51c of the control surface 51. And the length of the interval between the inner peripheral surface 41d of the collar 41 is set to be larger. That is, the diameter of the rolling element 42 is set to be equal to the length of the interval between the intermediate portion 51 d between the central portion 51 a and the side portions 51 b and 51 c and the inner peripheral surface 41 d of the collar 41.

  The support member 43 holds the rolling elements 42 so as to be rotatable and substantially parallel at equal angular intervals. More specifically, the support member 43 is made of a resin material, and as shown in FIGS. 2 and 3, the ring portion 43a, three inwardly extending portions 43b, three pairs of roller supports 43c, and three connecting portions 43d. It consists of. The ring portion 43a is formed in an annular shape having a larger diameter than the outer ring 41a. The three inward extending portions 43b are extended from the inner periphery of the ring portion 43a radially inward at equal angular intervals. Each roller support 43c extends in the axial direction from both circumferential ends on the radially inner side of the inwardly extending portion 43b. Each connecting portion 43d is formed in an arc shape so as to connect adjacent roller supports 43c. In addition, a pair of locking projections 43e facing in the circumferential direction are formed at the tip of each roller support 43c. And each rolling element 42 is hold | maintained between each pair of roller support 43c and between the inward extension part 43b and the latching convex part 43e, and it cannot move to the circumferential direction and an axial direction with respect to the ring part 43a. Retained. As described above, the support member 43 holding the rolling elements 42 has the roller supports 43c arranged on the outer ring 41a so that the rolling elements 42 are disposed between the control surface 51 and the inner peripheral surface 41d of the collar 41 as described above. The ring portion 43 a is disposed in contact with the flange portion 41 b on the outer side in the axial direction of the collar 41.

  The stopper 44 is formed of a metal plate having a uniform thickness. The stopper 44 includes an abutting portion 44a formed in an annular shape having substantially the same diameter as the ring portion 43a of the support member 43, and an abutment thereof. And an extended portion 44b extending radially outward from the portion 44a at intervals of 180 °. As shown in FIG. 2, the inner and outer diameters of the contact portion 44 a are set to be approximately the same as the inner and outer diameters of the outer ring 41 a of the collar 41. A fixed portion 44c is formed in the extended portion 44b. The fixing portions 44 c are formed at the four corners of the stopper 44 so as to correspond to the engaging protrusions 31 k of the gear housing 31. The stopper 44 is fixed to the gear housing 31 by inserting the engaging protrusion 31k into the fixing portion 44c. The contact portion 44 a of the stopper 44 is disposed on the upper portion (the upper portion in FIG. 1) of the ring portion 43 a of the support member 43. The stopper 44 regulates the movement of the rolling element 42 in the axial direction together with the support member 43 when the ring portion 43a of the support member 43 contacts the contact portion 44a. Further, as shown in FIGS. 2 and 3, a restricting portion 44d is formed in the approximate center of each extending portion 44b. The restricting part 44d is formed by cutting and raising a part of the extended part 44b. The restricting portion 44d is in contact with the engaging portion 41c of the collar 41 at its tip, and restricts the movement of the collar 41 in the axial direction.

  The drive-side rotator 45 includes a shaft portion 45a, a disk portion 45b having a diameter larger than that of the shaft portion 45a, and a ball holding portion 45c provided at the center of the disk portion 45b. The ball holding portion 45 c is formed with a ball housing recess 45 d for holding the ball 46. The ball 46 held in the ball housing recess 45d is preliminarily heat-treated and hard-processed, and is held in a state where a part of the ball 46 protrudes in both axial directions. As shown in FIGS. 2 and 3, the balls 46 abut against the end surface 16 b of the rotating shaft 16 and the end surface of the hard plate 60 disposed on the upper surface 39 i of the main body 39 c constituting the driven-side rotating body 39. ing.

  The hard plate 60 is obtained by heat-treating (quenching) a metal in advance, is harder than the main body 39c of the driven-side rotating body 39, and has the same hardness as the rotary shaft 16 and the ball 46 that are also heat-treated. Have A concave tapered portion 61a is formed on the upper surface 61 of the hard plate 60 below. The hard plate 60 is housed in a plate housing recess 39j that is recessed in the upper surface 39i of the main body 39c of the driven-side rotator 39. More specifically, after injecting grease into the plate housing recess 39j, the hard plate 60 is press-fitted into the plate housing recess 39j and is disposed so as not to rotate with respect to the main body 39c of the driven side rotating body 39. In the axial direction, the end surface 16b of the rotating shaft 16, the ball 46, and the upper surface 61 of the hard plate 60 are always in contact with each other. That is, the rotating shaft 16 is in contact with the driven side rotating body 39 through the ball 46 and the hard plate 60 without a gap.

  The drive-side rotating body 45 has an axial center extending from a base end (upper end in FIG. 2) of the shaft portion 45a toward the lower ball holding portion 45c and having a pair of parallel surfaces and a cross-sectional two-surface width shape. A hole 45e is formed to communicate with the ball housing recess 45d. The connecting portion 45a of the rotating shaft 16 is loosely fitted in the connecting hole 45e. That is, the connecting hole 45e is set so that the dimension thereof is relatively larger than the connecting portion 16a of the rotating shaft 16 by a predetermined value, and a gap S is generated between them. Then, the connecting portion 16a of the rotating shaft 16 is loosely fitted in the connecting hole 45e, so that the driving side rotating body 45 and the rotating shaft 16 are drivingly connected so as to be integrally rotatable. In this case, since the coupling portion 16a of the rotating shaft 16 is loosely fitted in the coupling hole 45e, even if an axial deviation occurs with the rotating shaft 16, the axial deviation is allowed.

  Here, the drive-side rotating body 45 of the present embodiment has an elastomer resin that has a metal plate 47 inserted in a resin that forms a substantially outer shape and has an elastic force to form an elastic holding portion 48 and a buffer portion 53 to be described later. Are integrally formed.

  The metal plate 47 has a connection hole 47a having the same cross-sectional shape as the connection hole 45e exposed in the connection hole 45e, and extends to each protruding portion 52 described later. The inner peripheral surface of the connecting hole 47a is flush with the inner peripheral surface of the connecting hole 45e. The metal plate 47 engages with the driving side rotating body 45, in particular the driven side rotating body 39, and engages with the rigidity of each projecting portion 52 that transmits the driving force and with the connecting portion 16a of the rotating shaft 16, thereby supplying the driving force. It is inserted to improve the rigidity of the connecting hole 45e portion for transmission.

  And in the connection hole 45e which the connection hole 47a of this metal plate 47 exposes, it engages with the connection part 16a of the said rotating shaft 16 in a rotation direction. In this case, the connecting hole 45e is short in the axial direction, but the rigidity is improved by the metal plate 47, so that the rotational driving force from the rotary shaft 16 is reliably received while suppressing the enlargement in the axial direction. Yes. In addition, since the connecting hole 45e is shortened in the axial direction, the inclination angle of the rotating shaft 16 with respect to the driving side rotating body 45 can be widened. Therefore, even when the inclination of the rotating shaft 16 is large, it can be easily handled.

  In addition, an elastic holding portion 48 made of an elastomer resin having an elastic force is integrally formed on the driving side rotating body 45 so as to be continuous from the opening portion of the connecting hole 45e. Note that the inner diameter of the shaft portion 45a formed integrally with the elastic holding portion 48 is set larger than the inner diameter of the connecting hole 45e. Although not shown, the elastic holding portion 48 has a slightly smaller inner diameter at each plane portion of the connecting hole 45e. Therefore, the elastic holding portion 48 is in pressure contact with each flat portion of the connecting portion 16a of the rotating shaft 16. Therefore, when the driving side rotating body 45 is mounted on the rotating shaft 16 when the motor 11 is assembled, the driving side rotating body 45 is elastically held by the elastic holding portion 48 so as not to fall off the rotating shaft 16, and the assembly workability of the motor 11 is improved. Has improved. As described above, even if an axial deviation occurs between the drive-side rotator 45 and the rotary shaft 16, the elastic holding portion 48 is only elastically deformed and does not adversely affect it.

  As shown in FIG. 3, a substantially fan-shaped protrusion is provided on the distal end side (lower side in FIG. 2) of the drive-side rotating body 45 so as to extend radially outward and project in the axial direction from the distal end. A plurality (three) of the parts 52 are formed at equiangular intervals. As shown in FIG. 7, each protruding portion 52 is formed along the inner peripheral surface 41 d with a large arc surface having a slightly smaller diameter than the inner peripheral surface 41 d of the collar 41. In other words, the drive-side rotator 45 is formed such that the protruding portion 52 can be inserted in the axial direction from the center hole of the contact portion 44 a of the stopper 44. The protruding portion 52 is formed with a fitting groove 52a (see FIG. 7) extending in the radial direction from the radially inner side to the middle of the protruding portion 52. In the outer ring 41a, the projecting portions 52 are disposed between the respective engaging convex portions 39b of the driven side rotating body 39 and between the respective rolling elements 42 (each roller support 43c).

  A buffer portion 53 made of an elastomer resin having an elastic force is integrally formed in the fitting groove 52a. The buffer portion 53 is provided continuously with the elastic holding portion 48 through a through hole 45f (see FIG. 2) provided at a predetermined position of the resin portion of the drive side rotating body 45. The buffer portion 53 is formed with a buffer portion 53a that protrudes inward in the radial direction of the projecting portion 52 from the fitting groove 52a and extends in the circumferential direction. As shown in FIG. 7, the circumferential width of the buffer portion 53 a is set to be slightly larger than the circumferential width of the inner circumferential surface of the projecting portion 52.

  One side surface (counterclockwise surface) 53b of the buffer portion 53a is engaged when the drive side rotating body 45 rotates counterclockwise (arrow X direction) with respect to the driven side rotating body 39 to a predetermined position. The first abutment surface 39e formed on the radially inner side of the clockwise side surface of the portion 39b comes into contact. Further, one side surface (counterclockwise surface) 52b formed on the radially inner side of the projecting portion 52 is when the driving side rotating body 45 rotates further counterclockwise (arrow X direction) than the predetermined position. Then, it comes into contact with the first contact surface 39f formed on the radially outer side of the surface on the clockwise side of the engagement convex portion 39b. The drive-side rotator 45 further rotates counterclockwise (arrow X direction) from the predetermined position when the buffer portion 53a is bent (collapsed) in the circumferential direction (see FIG. 8).

  Further, the other side surface (counterclockwise surface) 53c of the buffer portion 53a is engaged when the driving side rotating body 45 rotates to the predetermined position in the clockwise direction (arrow Y direction) with respect to the driven side rotating body 39. It abuts against a second buffer surface 39g formed radially inside the counterclockwise surface of the convex portion 39b. Further, the other side surface (clockwise side surface) 52c formed on the radially inner side of the projecting portion 52 is engaged when the driving side rotating body 45 further rotates in the clockwise direction (arrow Y direction) from the predetermined position. It abuts on the second abutment surface 39h formed on the radially outer side of the counterclockwise surface of the mating convex portion 39b. In addition, the drive side rotating body 45 rotates further in the clockwise direction (arrow Y direction) from the predetermined position when the buffer portion 53a is bent (collapsed) in the circumferential direction.

  As shown in FIG. 8, each member 42, 52, 39b, 43c has one side surface 52b of the projecting portion 52 in contact with the first contact surface 39f of the engaging convex portion 39b. A state in which the first pressing surface 52d formed on the radially outer side of the counterclockwise surface is in contact with the roller support 43c (see FIG. 8), and the other side surface 52c of the projecting portion 52 is the engaging convex portion 39b. In each of the states in which the second pressing surface 52e that is in contact with the second contact surface 39h and is formed on the radially outer side of the surface on the clockwise side of the protruding portion 52 is in contact with the roller support 43c, the rolling element 42 Are arranged at positions corresponding to the central portion 51a of the control surface 51, and the shapes and dimensions of the members 42, 52, 39b, and 43c are set.

  In addition, a sensor magnet 55 having a ring shape and being multipolarly magnetized in the rotation direction is attached to the shaft portion 45a of the drive side rotating body 45 so as to rotate integrally. On the other hand, the brush holder 19 is provided with a magnetic detection element (not shown) such as a Hall element or a magnetoresistive element at a position located in the vicinity of the sensor magnet 55. The magnetic detection element is provided to detect a change in the magnetic field accompanying the rotation of the sensor magnet 55 and to detect the number of rotations of the rotary shaft 16 that rotates integrally with the drive side rotating body 45.

Next, the operation of this embodiment will be described.
When the motor main body 12 is driven and the rotating shaft 16 rotates in the counterclockwise direction (arrow X direction) of FIG. The part 52) rotates integrally in the same direction (arrow X direction). As shown in FIG. 8, when the one side surface 52b of the projecting portion 52 comes into contact with the first contact surface 39f of the engagement convex portion 39b and the first pressing surface 52d comes into contact with the roller support 43c, the rolling element 42 is disposed at a position corresponding to the central portion 51a of the control surface 51 (hereinafter referred to as a neutral position). In this case, before the one side surface 52b of the projecting portion 52 contacts the first contact surface 39f, the one side surface 53b of the buffer portion 53a contacts the first buffer surface 39e of the engagement convex portion 39b first. Therefore, the impact at the time of contact is reduced.

  In this neutral state, the rolling element 42 is not sandwiched between the control surface 51 of the engaging convex portion 39 b and the inner peripheral surface 41 d of the collar 41, so that the driven side rotating body 39 can rotate with respect to the collar 41. Therefore, when the driving side rotating body 45 further rotates counterclockwise, the rotational force is transmitted from the projecting portion 52 to the driven side rotating body 39, and the driven side rotating body 39 is rotated. At this time, the rotational force in the same direction (arrow X direction) is transmitted from the first pressing surface 52d to the roller support 43c (support member 43), and the roller support 43c (support member 43) moves in the same direction together with the rolling elements 42. Moving.

  On the contrary, when the rotating shaft 16 rotates in the clockwise direction (arrow Y direction) in FIG. 7, the rolling element 42 is disposed at the neutral position by the projecting portion 52 as described above. In this state, the rolling element 42 is not sandwiched between the control surface 51 of the engaging convex portion 39 b and the inner peripheral surface 41 d of the collar 41, so that the driven side rotating body 39 can rotate with respect to the collar 41. Accordingly, the rotational force of the driving side rotating body 45 is transmitted from the projecting portion 52 to the driven side rotating body 39, and the driven side rotating body 39 is rotated.

  Then, the worm shaft 33 rotates together with the driven-side rotator 39, and the worm wheel 34 and the output shaft 35 rotate according to the rotation. Accordingly, the window regulator that is drivingly connected to the output shaft 35 is operated, and the window glass is opened and closed (raised and lowered).

  On the other hand, when a load is applied to the output shaft 35 from the load side (window glass side) while the motor 11 is stopped, the driven side rotating body 39 tends to rotate due to the load. When the driven-side rotator 39 is rotated in the clockwise direction (arrow Y direction) in FIG. 7, the rolling element 42 is relatively moved toward the side 51b of the control surface 51 of the engaging convex portion 39b. Eventually, as shown in FIG. 9, when the driven-side rotating body 39 rotates in the same direction until the rolling element 42 reaches the intermediate portion 51 d on the side portion 51 b side, the rolling element 42 moves to the inner periphery of the control surface 51 and the collar 41. It is clamped by the surface 41d (becomes locked). And since the outer ring | wheel 41a is being fixed, the further rotation of the driven side rotary body 39 in the same direction is prevented, and the drive side rotary body 45 is not rotated.

  On the contrary, when the driven-side rotator 39 is rotated in the counterclockwise direction (arrow X direction) in FIG. 7 by the load, the rolling element 42 is relatively opposed to the side 51c side of the control surface 51 of the engaging convex portion 39b. Moving. Eventually, when the driven rotating body 39 rotates in the same direction until the rolling element 42 reaches the intermediate portion 51d on the side 51c side, the rolling element 42 is sandwiched between the control surface 51 and the inner peripheral surface 41d of the collar 41 ( Locked). And since the outer ring | wheel 41a is being fixed, the further rotation of the driven side rotary body 39 in the same direction is prevented, and the drive side rotary body 45 is not rotated.

  Thus, even if a large load is applied from the load side (window glass side) to the output shaft 35 side, the rotation of the driven side rotating body 39 is prevented. Therefore, the window glass connected to the output shaft 35 is prevented from moving unexpectedly due to its own weight, vibration, external force or the like.

  In the motor 11 of such a power window device, the clutch 30 is assembled at the same time that the yoke 14 assembled with the armature 17 and the brush holder 19 and the gear housing 31 assembled with the worm shaft 33 and the like are assembled. Specifically, as shown in FIG. 6, the drive-side rotator 45 is mounted in advance on the rotary shaft 16, and the components of the clutch 30 other than the drive-side rotator 45 are assembled in advance in the gear housing 31. Then, at the same time as the yoke 14 and the gear housing 31 are assembled, the driving side rotating body 45 is disposed at a predetermined position with respect to the driven side rotating body 39, the support member 43, etc., and the clutch 30 is completed.

  Further, when the speed reduction unit 13 and the motor body 12 are assembled, a part of the ball 46 is accommodated in the tapered recess 61 a of the hard plate 60 and the ball 46 is positioned. That is, the ball 46 coaxial with the rotating shaft 16 is positioned by the tapered recess 61a coaxial with the worm shaft 33, and the worm shaft 33 and the rotating shaft 16 are arranged coaxially.

As described above, the present embodiment has the following effects.
(1) A tapered recess 61a that is coaxial with the worm shaft 33 (worm shaft portion 38) and has a concave shape in the axial direction is provided on one end side of the driven side rotating body 39 (main body portion 39c). , A part of which is accommodated in the tapered recess 61a. In this way, the ball 46 disposed coaxially with the drive side rotating body 45 rotated integrally with the rotating shaft 16 is accommodated in the tapered recess 61a coaxial with the worm shaft 33, and the ball 46 is positioned. Thereby, since the rotation axis 16 (drive-side rotator 45) coaxial with the ball 46 is coaxial with the worm shaft 33, the rotation axis 16 can be arranged coaxially with the worm shaft 33 more reliably and easily. The axial deviation can be suppressed.

  (2) Since the taper recess 61a has a tapered contact surface with the ball 46, when the motor main body 12 and the speed reduction portion 13 are assembled, the taper recess 61a has a taper recess 61a that is concave in the axial direction. Abutting on the tapered abutting surface, the movement of the ball 46 in the direction perpendicular to the axis is suppressed. Further, since the contact surface of the tapered recess 61a is tapered, the ball 46 can be naturally disposed on the axis of the worm shaft 33.

  (3) Since the taper recess 61a has a higher contact surface with the ball 46 than the other portion (main body portion 39c) of the driven-side rotator 39, the taper recess 61a It is possible to suppress the taper recess 61a from being deformed by the frictional force in the axial direction, and it is possible to suppress the axial displacement between the worm shaft 33 and the rotary shaft 16.

In addition, you may change embodiment of this invention as follows.
In the above embodiment, a part of the ball 46 as a ball member is accommodated in the tapered recess 61a of the hard plate 60 that constitutes the driven side rotating body 39. However, the present invention is not limited to this. For example, as shown in FIG. 10, a concave portion 70 is formed on one end side in the axial direction of the main body portion 39c constituting the driven side rotating body 39, and the ball 46 is accommodated in the concave portion 70 (all in the drawing). You may employ | adopt the structure arrange | positioned coaxially with the worm shaft 33. FIG.

In the above embodiment, the contact surface of the tapered recess 61a with the ball 46 is formed in a tapered shape, but the present invention is not limited to this.
In the above embodiment, the hard plate 60 is configured with higher hardness than the other part (main body part 39c) of the driven-side rotator 39, but is not limited thereto.

  In the above embodiment, the connecting portion 16a of the rotating shaft 16 and the connecting hole 45e of the driving side rotating body 45 have a two-sided cross-sectional shape, but may have other shapes that engage with each other in the rotation direction. For example, it may be a polygonal shape such as a square or a hexagon.

  -The shape and material of the elastic holding | maintenance part 48 of the said embodiment are not limited to this, You may change suitably. Further, although the elastic holding portion 48 is integrally formed with the driving side rotating body 45, the elastic holding portion 48 may be assembled to the driving side rotating body 45. Further, the elastic holding portion 48 may be omitted if there is no concern that the drive side rotating body 45 may fall off the rotating shaft 16 during the assembly, for example, the assembly is performed with the connecting portion 16a facing upward.

  In the above embodiment, the configurations of the motor main body 12 and the speed reduction unit 13 may be changed as appropriate. For example, a motor having a configuration in which a circuit board on which a control circuit for controlling the rotation of the motor 11 and a rotation detecting element for detecting the rotation of the motor 11 are mounted in the speed reduction unit 13 (gear housing 31) is integrally accommodated. Good.

  In the above embodiment, the motor 11 is used as a drive source for the power window device, but may be used as a drive source for other devices.

  DESCRIPTION OF SYMBOLS 11 ... Motor, 12 ... Motor main body, 13 ... Deceleration part, 16 ... Rotary shaft, 30 ... Clutch (connection means), 33 ... Worm shaft, 39 ... Driven side rotary body, 45 ... Drive side rotary body, 61a ... Tapered recessed part (Recessed part), 70... Recessed part.

Claims (3)

A motor body that rotationally drives the rotating shaft;
A speed reduction portion having a speed reduction mechanism including a worm shaft assembled to the motor body and provided substantially coaxially with the rotation shaft;
A motor provided with a connecting means for connecting the worm shaft of the speed reduction unit and the rotating shaft of the motor body so as to be integrally rotatable;
The connecting means is a drive-side rotator that can rotate integrally with the rotation shaft, and is engaged with the drive-side rotator in the rotational direction and is provided at one end of the worm shaft so as to rotate integrally with the worm shaft. A driven member that can be driven, and a ball member that is coaxially and rotatably provided at one axial end of the rotating shaft,
On one end side of the driven-side rotating body, a concave portion that is coaxial with the worm shaft and has a concave shape in the axial direction is provided,
At least a part of the ball member is accommodated in the recess. The motor according to claim 1,
The concave portion has a contact surface with the ball member formed in a tapered shape. The motor according to claim 1 or 2,
The motor according to claim 1, wherein at least a contact surface with the ball member has a higher hardness than other portions of the driven-side rotating body.