JP2014217240A - Motor device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To drastically improve the assembly workability while facilitating an alignment work.SOLUTION: A gear case side thrust bearing 52 is rocked around a shaft center C3 of an O-ring 53 via a gear case side radial bearing 51 in a case where axis deviation occurs in an armature shaft 13. A shaft center C4 of the gear case side radial bearing 51 is arranged in the vicinity of the shaft center C3 of the O-ring 53, and axis deviation can be absorbed without increasing a rotation resistance of the armature shaft 13 so much, and alignment can be performed. In addition, because the gear case side radial bearing 51, the gear case side thrust bearing 52, and the O-ring 53 can be attached at the axial direction one side of the armature shaft 13, the gear case side radial bearing 51, the gear case side thrust bearing 52, and the O-ring 53 can be easily assembled to a bearing housing part 34 provided at a deep part of a gear case 31 at once.

Description

  The present invention relates to a motor device including a rotating shaft that is rotatably supported by a bearing provided in a housing.

  2. Description of the Related Art Conventionally, a motor device that is rotationally driven by a drive current from an in-vehicle battery is used as a drive source such as a power window device and a wiper device mounted on a vehicle such as an automobile. The motor device mounted on such a vehicle is provided with a motor unit and a speed reduction unit so that a large output can be obtained while being small. In other words, the speed reduction unit reduces the rotation of the motor unit to a predetermined number of rotations to increase the torque, and outputs the increased torque to an external driving object.

  As the speed reduction mechanism, many worm speed reducers that can obtain a large reduction ratio are employed. In this case, the rotating shaft (armature shaft) fixed to the rotor (armature) also serves as the worm shaft of the worm speed reducer. Structured. In other words, the rotating shaft is arranged so as to straddle both the motor case forming the motor portion and the gear case forming the speed reducing portion, and the worm gear can rotate integrally with the portion protruding into the gear case of the rotating shaft. Is provided. And the said worm gear is meshed | engaged with the tooth | gear part of the worm wheel accommodated rotatably in the gear case.

  As a motor apparatus provided with such a motor part and a reduction part, the technique described in patent document 1 is known, for example. A motor device (motor with a speed reduction mechanism) described in Patent Document 1 includes a rotation shaft (motor shaft) fixed to a rotor (rotor core), and the rotation shaft is provided at the bottom of a motor case (yoke). And a pair of bearings provided in a motor shaft insertion portion of a gear case (deceleration case). That is, the rotating shaft of the motor device described in Patent Document 1 is rotatably supported by the three bearings. Further, an end spacer is disposed at the tip portion of the rotating shaft in order to prevent rattling or the like in the axial direction of the rotating shaft. Thus, the front end side of the rotating shaft is supported by the bearing and the end spacer so as to be rotatable from the radial direction and the axial direction.

JP 09-327153 A (FIGS. 1 and 3)

  However, in the motor device described in Patent Document 1 described above, the rotating shaft is supported by three bearings, and if the shaft centers of the bearings are displaced even a little, the rotational resistance increases or the noise increases. Problems may occur. Therefore, in order to prevent the occurrence of these problems, it is necessary to carefully connect the motor case and the gear case (alignment work) in the assembly process of the motor device. Here, for example, when the alignment work varies and the rotational resistance of the motor device increases, the cases where the shaft centers of the bearings are aligned are once disconnected from each case. And reconnect the cases.

  As described above, in the motor device described in Patent Document 1, it is difficult to perform the alignment work for coaxially arranging the shaft centers of the respective bearings. Further, the end spacers and the bearings are disposed deep in the gear case. There is a problem that the assembly work of the motor device becomes complicated because it is necessary to mount each individually.

  An object of the present invention is to provide a motor device capable of greatly improving assembly workability while facilitating alignment work.

  In one aspect of the present invention, a housing, a rotary shaft that is rotatably provided in the housing, a first bearing that supports the rotary shaft from the radially outer side, and the rotary shaft that is supported from the axially outer side, A bearing housing member provided with the first bearing on the inner side, and an elastic seal provided on the outer side of the bearing housing member so as to overlap the first bearing in the radial direction of the rotating shaft and in contact with the housing. .

  In another aspect of the present invention, the housing is provided with a housing portion that houses the bearing housing member, and the housing portion is filled with a resin that positions the bearing housing member with respect to the rotation shaft.

  In another aspect of the present invention, the housing includes a first case provided with a second bearing and a third bearing that support the rotating shaft from the radially outer side, and a second case provided with the bearing housing member. The second case is made of resin.

  According to the present invention, when a shaft misalignment occurs in the rotation shaft, the bearing housing member is swung around the shaft center of the elastic seal via the first bearing. Since the shaft center of the first bearing is disposed in the vicinity of the shaft center of the elastic seal, the bearing housing member can be easily swung, so that the shaft displacement can be absorbed without increasing the rotational resistance of the rotating shaft so much. Can be aligned. Therefore, the troublesome alignment work such as reassembling the housing as before is unnecessary, and the alignment work of the rotating shaft can be simplified.

  In addition, since the first bearing, the bearing housing member, and the elastic seal can be respectively attached to the rotating shaft when the motor device is assembled, the first bearing, the bearing housing member, and the The elastic seals can be easily assembled at a predetermined location in the housing at a time. Therefore, it is possible to greatly improve the assembly workability of the motor device.

It is sectional drawing of the motor with a speed-reduction mechanism which concerns on one embodiment of this invention. It is a partial expanded sectional view which shows the inside of the broken-line circle | round | yen A part of FIG. It is a partial expanded sectional view which shows the inside of the broken-line circle | round | yen B part of FIG. It is a partial expanded sectional view which shows the inside of the broken-line circle | round | yen C part of FIG. It is a perspective view which shows the detail of a gear case side radial bearing. (A), (b) is a perspective view which shows the detail of a gear case side thrust bearing. It is explanatory drawing explaining the assembly procedure of the motor with a reduction mechanism. (A), (b) is explanatory drawing explaining the axial shift | offset | difference state of an armature shaft.

  Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

  1 is a cross-sectional view of a motor with a speed reduction mechanism according to an embodiment of the present invention, FIG. 2 is a partially enlarged cross-sectional view showing the inside of a broken-line circle A portion of FIG. 1, and FIG. 4 is a partially enlarged sectional view showing the inside of the portion, FIG. 4 is a partially enlarged sectional view showing the inside of the broken-line circle C portion of FIG. 1, FIG. 5 is a perspective view showing details of the gear case side radial bearing, and FIG. ), (B) are perspective views showing the details of the gear case side thrust bearing, FIG. 7 is an explanatory view for explaining the assembly procedure of the motor with a speed reduction mechanism, and FIGS. 8 (a), (b) are shaft misalignments of the armature shaft. The explanatory view explaining a state is shown, respectively.

  A motor (motor device) 10 with a speed reduction mechanism shown in FIG. 1 is used as a drive source of a power window device (not shown) mounted on a vehicle such as an automobile, and a window regulator (not shown) that raises and lowers the wind glass. Is to drive. The motor 10 with a speed reduction mechanism is capable of large output while being small, and is installed in a narrow space (not shown) formed in the door of the vehicle.

  The motor 10 with a speed reduction mechanism includes a motor portion 20 and a speed reduction portion 30, and the motor portion 20 and the speed reduction portion 30 are connected to each other by a pair of fastening screws 11 to be unitized. The motor 10 with a speed reduction mechanism includes a housing 12 that forms an outline thereof. An armature shaft (rotating shaft) 13 is rotatably accommodated in the housing 12. Here, the housing 12 includes a motor case 21 and a brush holder 25 that form the motor unit 20, and a gear case 31 that forms the speed reduction unit 30.

  The motor unit 20 includes a motor case (first case) 21 formed into a bottomed cylindrical shape by pressing (deep drawing) a steel plate made of a magnetic material. A plurality of magnets 22 (two in the drawing) having a substantially arc-shaped cross section are fixed to the inner wall of the motor case 21, and an armature 24 around which a coil 23 is wound is provided inside these magnets 22. , And is rotatably accommodated through a predetermined gap (air gap).

  On the opening side (left side in the figure) of the motor case 21, a brush holder accommodating portion 21a having a larger diameter than the main body portion of the motor case 21 is formed, and the brush holder 25 is accommodated in the brush holder accommodating portion 21a. Has been. The brush holder 25 is attached to the brush holder housing portion 21a so as not to rattle, and closes the opening portion of the motor case 21.

  Here, the armature shaft 13 passes through the inside of the brush holder 25 so as to freely rotate, and the armature shaft 13 is rotatably accommodated inside the brush holder 25 together with the motor case 21. A housing 12 is formed. That is, the brush holder 25 constitutes the first case in the present invention together with the motor case 21.

  The armature shaft 13 penetrates and is fixed to the axial center C1 of the armature 24. The armature shaft 13 is disposed so as to straddle both the motor unit 20 and the speed reduction unit 30, and one side in the axial direction (left side in the figure) of the armature shaft 13 is provided inside the gear case 31, and the axial direction of the armature shaft 13 The other side (the right side in the figure) is provided inside the motor case 21.

  A commutator 26 formed in a substantially cylindrical shape is fixed to a substantially intermediate portion along the axial direction of the armature shaft 13 and a portion close to the armature 24. The end of the coil 23 wound around the armature 24 is electrically connected to the commutator 26.

  A plurality of brushes 27 (two in the figure) slidably held on the holder body 25a of the brush holder 25 are in sliding contact with the outer periphery of the commutator 26. The brushes 27 are elastically contacted with a predetermined pressure toward the commutator 26 by spring members 28, respectively. As a result, by supplying a drive current to each brush 27 from an in-vehicle controller (not shown) or the like, a rotational force (electromagnetic force) is generated in the armature 24, so that the armature shaft 13 rotates at a predetermined rotational speed and rotational torque. It has become.

  A sensor magnet 29 (see FIG. 3) is fixed to a substantially intermediate portion along the axial direction of the armature shaft 13 and on the opposite side of the commutator 26 from the armature 24 side. The sensor magnet 29 is formed in a substantially cylindrical shape by alternately arranging four magnetic poles (not shown) along the rotation direction of the armature shaft 13. The sensor magnet 29 rotates together with the armature shaft 13, thereby passing through a rotation sensor 45 (see FIG. 3) disposed on the radially outer side of the sensor magnet 29 as the armature shaft 13 rotates. The state of the magnetic flux lines to be changed is changed.

  A worm gear 32 is provided on the axial direction side of the armature shaft 13 with respect to the sensor magnet 29. The worm gear 32 is formed in a substantially cylindrical shape and is fixed to the armature shaft 13 by press-fitting. A tooth portion 33a (see FIG. 4) of a worm wheel 33 rotatably provided in the gear case 31 is engaged with the worm gear 32. As a result, the worm gear 32 rotates in the gear case 31 as the armature shaft 13 rotates, and the rotation is transmitted to the worm wheel 33. Here, the speed reduction mechanism SD is formed by the worm gear 32 and the worm wheel 33.

  As shown in FIG. 1, the speed reduction unit 30 includes a gear case (second case) 31 and a connector member 35. The gear case 31 is made of resin and is formed into a predetermined shape by injection molding a resin material such as plastic. The gear case 31 is formed on the opening side of the motor case 21, that is, on the brush holder housing portion 21a side of the motor case 21. These are connected via respective fastening screws 11.

  As shown in FIG. 4, a worm gear housing portion 31 a extending along the axial direction of the armature shaft 13 and a worm wheel housing portion 31 b disposed close to the worm gear housing portion 31 a are formed in the gear case 31. Has been. Inside each of these accommodating portions 31a and 31b, a worm gear 32 and a worm wheel 33 provided with a tooth portion 33a meshing with the worm gear 32 on an outer peripheral portion are accommodated rotatably. Here, the worm gear 32 is formed in a spiral shape, and the tooth portion 33 a is inclined at a gentle inclination angle in the axial direction of the worm wheel 33. Thereby, smooth power transmission from the worm gear 32 to the worm wheel 33 is possible.

  As shown in FIG. 1, an output gear 33b is disposed on an axis C2 of the worm wheel 33 so as to be integrally rotatable. The output gear 33b is connected to a window regulator (not shown) so as to be able to transmit power. It has become so. That is, the rotation of the armature shaft 13 is decelerated by the speed reduction mechanism SD to increase the torque, and the increased rotation is output from the output gear 33b to the window regulator.

  The connector member 35 is formed in a substantially L shape by injection molding a resin material such as plastic, and includes a connector connecting portion 36 and an insertion portion 37. An external connector (not shown) provided on the vehicle side is electrically connected to the connector connecting portion 36, and the insertion portion 37 is inserted into the side surface of the gear case 31 from above in FIG. It is like that. Here, the external connector is electrically connected to an in-vehicle battery, an in-vehicle controller, or the like (both not shown).

  A sensor substrate 44 as shown in FIG. 3 is attached to the insertion portion 37, and a rotation sensor 45 is mounted on the distal end side of the sensor substrate 44. The rotation sensor 45 detects a change in the magnetic flux lines of the sensor magnet 29 and sends the detection signal to an in-vehicle controller or the like. The onboard controller or the like calculates the rotation speed and rotation direction of the armature shaft 13 based on the detection signal from the rotation sensor 45, and controls the rotation of the armature shaft 13 according to the calculation result.

  Here, the rotation sensor 45 is opposed to the sensor magnet 29 via the bearing holding cylinder 25b of the brush holder 25, that is, the bearing holding cylinder 25b functions as a partition wall. Thereby, the abrasion powder of each brush 27 from the sensor magnet 29 side is prevented from reaching the rotation sensor 45, and thus the rotation sensor 45 can be operated normally over a long period of time. The rotation sensor 45 includes a magnetoresistive element (MR element) as a sensor element, and is a GMR sensor to which a giant magnetoresistance effect is applied.

  Next, the bearing structure of the armature shaft 13 will be described in detail with reference to the drawings. Here, the armature shaft 13 is rotatably supported by three radial bearings, and adopts a so-called three-point support bearing structure. Hereinafter, the description will be made in order from the bearing on the motor case 21 side.

  As shown in FIG. 2, the bottom side (right side in the drawing) of the motor case 21 is formed in a stepped shape, and a small diameter portion 21 b having a smaller diameter than the main body portion of the motor case 21 is formed in the stepped shape portion. Is provided. The small diameter portion 21b is formed in a bottomed cylindrical shape, and the motor case side bearing mechanism 40 is accommodated inside the small diameter portion 21b.

  The motor case side bearing mechanism 40 is formed of a motor case side radial bearing 41 and a motor case side thrust bearing 42. The motor case side radial bearing 41 is formed in a substantially cylindrical shape, and supports the other axial side of the armature shaft 13 from the radially outer side. Here, the motor case side radial bearing 41 is formed by impregnating a porous metal body manufactured by powder metallurgy with a lubricating oil, and constitutes the second bearing in the present invention.

  The motor case side thrust bearing 42 includes a plate-like main body portion 42a and a plurality of arm portions 42b, and the plate-like main body portion 42a supports the other axial side of the armature shaft 13 from the outside in the axial direction. Yes. In addition, the motor case side radial bearing 41 is held inside each arm portion 42b. Thus, the motor case side bearing mechanism 40 is configured by integrating the motor case side radial bearing 41 and the motor case side thrust bearing 42, and the other side in the axial direction of the armature shaft 13 is set to the radially outer side and the axially outer side. It is designed to be supported in a freely rotatable manner.

  As shown in FIG. 3, an annular recess 25 c is formed on one side in the axial direction of the bearing holding cylinder 25 b that forms the brush holder 25. A brush holder-side radial bearing 43 that rotatably supports a substantially intermediate portion along the axial direction of the armature shaft 13 from the radially outer side is fitted and fixed to the annular recess 25c. Here, the brush holder side radial bearing 43 is also formed in a substantially cylindrical shape by impregnating a porous metal body manufactured by powder metallurgy with a lubricating oil. In addition, the brush holder side radial bearing 43 comprises the 3rd bearing in this invention.

  As shown in FIG. 4, a bearing housing portion (housing portion) 34 is formed on one side in the axial direction of the worm gear housing portion 31 a in the gear case 31. A gear case side bearing mechanism 50 that rotatably supports one side of the armature shaft 13 in the axial direction is accommodated in the bearing accommodating portion 34.

  The bearing accommodating portion 34 is formed in a stepped shape, and is formed so as to expand the diameter of the small diameter accommodating portion 34a, the large diameter accommodating portion 34b having a larger diameter than the small diameter accommodating portion 34a, and the large diameter accommodating portion 34b. And a tapered surface 34c. And these accommodating parts 34a and 34b and the taper surface 34c are provided in the circumference | surroundings of the resin filling hole 31c formed in the gear case 31, and the said resin filling hole 31c, and it is the some which became smaller diameter than the resin filling hole 31c. It is possible to communicate with the outside of the gear case 31 through an air vent hole 31d (only two are shown in the figure).

  Here, the shaded portion shown in FIG. 4 indicates the resin R filled in the bearing housing portion 34 through the resin filling hole 31c. The resin R changes from a melted state in the bearing housing portion 34 to a hardened state, thereby fixing the gear case side bearing mechanism 50, that is, the gear case side thrust bearing 52, in the bearing housing portion 34, and the armature shaft. 13 with respect to the position.

  When each of the air vent holes 31d is filled with the molten resin R inside the bearing housing portion 34, air (not shown) inside the bearing housing portion 34 passes therethrough. Further, a part of the resin R filled in the bearing accommodating portion 34 enters, so that the resin R cured in each air vent hole 31d functions as a detent, and consequently the bearing accommodating portion. 34, the gear case side bearing mechanism 50 is prevented from rotating or rattling.

  The gear case side bearing mechanism 50 includes a gear case side radial bearing 51 as a first bearing, a gear case side thrust bearing 52 as a bearing housing member, and an O-ring 53 as an elastic seal.

  As shown in FIG. 5, in the gear case side radial bearing 51, as in the case of the other radial bearings 41 and 43 (see FIGS. 2 and 3) described above, a porous metal body manufactured by powder metallurgy is used as a lubricating oil. Is formed into a substantially cylindrical shape. On the radially inner side of the gear case side radial bearing 51, a slidable contact hole 51a with which the armature shaft 13 is slidably contacted is formed. Are formed respectively. As a result, the armature shaft 13 can be easily inserted into the sliding contact hole 51a. Thus, the gear case side radial bearing 51 is configured to rotatably support one axial side of the armature shaft 13 from the radially outer side.

  On the radially outer side of the gear case side radial bearing 51, a concave groove 51c extending in the axial direction of the gear case side radial bearing 51 is provided. A plurality of the recessed grooves 51c are provided side by side at equal intervals in the circumferential direction of the gear case side radial bearing 51. Thereby, the contact area (shaded portion in FIG. 5) of the gear case side radial bearing 51 with the gear case side thrust bearing 52 is reduced, and the gear case side radial bearing 51 can be easily mounted inside the gear case side thrust bearing 52. .

  As shown in FIG. 6, the gear case side thrust bearing 52 is formed in a stepped bottomed cylindrical shape, and includes a bottom portion 52a, a small diameter cylindrical portion 52b, a large diameter cylindrical portion 52c, and a flange portion 52d. As shown in FIG. 4, the bottom portion 52 a supports one side of the armature shaft 13 in the axial direction from the outside in the axial direction.

  The small diameter cylindrical portion 52 b is accommodated inside the small diameter accommodating portion 34 a of the bearing accommodating portion 34. Further, the large diameter cylindrical portion 52 c having a larger diameter than the small diameter cylindrical portion 52 b is accommodated inside the large diameter accommodating portion 34 b of the bearing accommodating portion 34. A clearance CL1 having a predetermined size is formed between the small diameter cylindrical portion 52b and the large diameter cylindrical portion 52c, and the small diameter accommodating portion 34a and the large diameter accommodating portion 34b. It has come in.

  Further, on the radially inner side of the gear case side thrust bearing 52, between the small diameter cylindrical portion 52b and the large diameter cylindrical portion 52c, as shown in FIG. 6B, it extends in the radial direction of the gear case side thrust bearing 52. A support plane part 52e is provided. The support plane portion 52e is in contact with one axial side of the gear case side radial bearing 51 mounted inside the large diameter cylindrical portion 52c, whereby the gear case side thrust of the gear case side radial bearing 51 is contacted. Positioning with respect to the bearing 52 is performed.

  The flange portion 52d is formed in an annular shape, and is integrally provided on the opening side (the right side in FIG. 4) of the large-diameter cylindrical portion 52c. The diameter of the flange portion 52d is set to be slightly larger than the diameter of the large-diameter cylindrical portion 52c, and the flange portion 52d attaches the O-ring 53 attached to the outer periphery of the large-diameter cylindrical portion 52c to the gear case side thrust. The bearing 52 is supported from the axial direction.

  As shown in FIG. 4, a slight clearance CL2 (CL2 <CL1) is formed between the flange portion 52d and the large-diameter accommodating portion 34b, whereby the gear case is formed inside the bearing accommodating portion 34. The side thrust bearing 52 can be tilted (oscillated) with the elastic deformation of the O-ring 53.

  The O-ring 53 is provided outside the gear case-side thrust bearing 52 and is sandwiched between the outer peripheral portion of the large-diameter cylindrical portion 52c and the inner peripheral portion of the large-diameter accommodating portion 34b. That is, the O-ring 53 comes into contact with both the large-diameter cylindrical portion 52c and the large-diameter accommodating portion 34b to seal (seal) the two. Thus, the molten resin R filled in the bearing housing portion 34 is prevented from leaking from the bearing housing portion 34 to the worm gear housing portion 31a side. The O-ring 53 is arranged inside the axial dimension range MA of the gear case side radial bearing 51, that is, arranged so as to overlap the gear case side radial bearing 51 in the radial direction of the armature shaft 13.

  As described above, the clearance CL2 is formed between the flange portion 52d and the large-diameter accommodating portion 34b, and the O-ring 53 is arranged so as to overlap the gear case-side radial bearing 51 in the radial direction of the armature shaft 13. 51 can be swung around the axis C3 of the O-ring 53. That is, when a shaft misalignment or the like occurs in the armature shaft 13, the gear case side radial bearing 51 swings about the axis C <b> 3 of the O-ring 53, thereby the armature shaft 13 is aligned. Yes.

  Next, the assembly procedure of the motor 10 with the speed reduction mechanism formed as described above will be described in detail with reference to the drawings.

  First, as shown in FIG. 7, a gear case 31 in a state where nothing is assembled is prepared. Further, an assembled motor section 20 (see FIG. 1) in which an armature 24 (armature shaft 13) is rotatably provided inside and a brush holder 25 is assembled is prepared. Here, the armature shaft 13 is rotatably supported at two locations of the motor case side radial bearing 41 and the brush holder side radial bearing 43 in a state where the motor unit 20 is assembled (see FIG. 1). .

  Further, a gear case side bearing mechanism 50, that is, a gear case side radial bearing 51, a gear case side thrust bearing 52, and an O-ring 53 are prepared, and these three parts 51, 52, 53 are indicated by an arrow (1) in FIG. The armature shaft 13 protruding from the motor case 21 is sequentially attached to one side in the axial direction. However, the three parts 51, 52, 53 may be assembled in advance to form the gear case side bearing mechanism 50, and the assembled gear case side bearing mechanism 50 may be mounted on one side in the axial direction of the armature shaft 13.

  Thereafter, one side in the axial direction of the armature shaft 13 to which the gear case side bearing mechanism 50 is mounted is inserted into the worm gear accommodating portion 31a of the gear case 31 as indicated by an arrow (2) in the figure. Thereby, as shown in FIG. 4, the gear case side bearing mechanism 50 is accommodated in the bearing accommodating portion 34. At this time, the tapered surface 34 c of the bearing housing portion 34 plays a role of guiding the assembly of the O-ring 53. The gear case side bearing mechanism 50 can be assembled in the bearing housing portion 34 without the O-ring 53 being displaced from the outer peripheral surface of the gear case side thrust bearing 52 by the tapered surface 34c.

  Further, when the gear case side bearing mechanism 50 is assembled in the bearing housing portion 34, a sliding resistance is generated between the large-diameter housing portion 34 b of the bearing housing portion 34 and the O-ring 53. Due to this sliding resistance, when the motor case 21 and the gear case 31 are assembled, the gap between the end face of the armature shaft 13 and the gear case side thrust bearing 52 can be eliminated, and consequently the armature shaft 13 and the gear case side thrust bearing. It is possible to prevent the backlash from occurring with 52.

  Next, as shown in FIG. 1, the gear case 31 and the motor case 21 are connected by screwing the fastening screws 11 together. And after connecting each case 31 and 21, the worm wheel 33 is accommodated in the worm wheel accommodating part 31b of the gear case 31, and the tooth | gear part 33a of the said worm wheel 33 and the worm gear 32 are meshed | engaged.

  Thereafter, as shown in FIG. 8, the resin R melted from a molten resin supply device (not shown) is filled at a predetermined pressure from the resin filling hole 31 c of the gear case 31 into the bearing housing portion 34. Then, the resin R filled in the bearing housing portion 34 reaches the periphery of the gear case side thrust bearing 52 and spreads throughout the bearing housing portion 34. Here, the resin R filled in the bearing housing portion 34 does not leak into the worm gear housing portion 31a beyond the O-ring 53, and as a result, the gear case side thrust bearing 52 is placed at a predetermined position in the bearing housing portion 34. Positioned.

  More specifically, as shown in FIGS. 8A and 8B, for example, when the armature shaft 13 is displaced by ± α °, the gear case side thrust bearing 52 is Along with the inclination of the shaft 13, the shaft 13 is inclined about the axis C <b> 3 of the O-ring 53 via the gear case side radial bearing 51. In this state, the gear case side thrust bearing 52 is positioned by the resin R and fixed at the position.

  Here, the shaft center C3 of the O-ring 53 is disposed very close to the shaft center C4 of the gear case side radial bearing 51, and the shaft center C3 is the center of oscillation of the gear case side radial bearing 51. Therefore, the gear case-side thrust bearing 52 can be easily swung, and as a result, an increase in rotational resistance that occurs when the armature shaft 13 twists the gear case-side radial bearing 51 can be minimized.

  Thus, in the present invention, the gear case side bearing mechanism 50 mounted on one side in the axial direction of the armature shaft 13 is accommodated in the bearing accommodating portion 34, and then the molten resin R is accommodated in the bearing accommodating portion 34. The centering work of the armature shaft 13 is completed by spreading it evenly.

  Here, the gear case side bearing mechanism 50 is accommodated in the bearing accommodating portion 34 in a state where it is preliminarily mounted on one side in the axial direction of the armature shaft 13, and further, on the side where the gear case side thrust bearing 52 is mounted. The tip side is tapered by the small diameter cylindrical portion 52b. Therefore, the gear case-side bearing mechanism 50 including the three parts 51, 52, and 53 can be easily disposed at a time in the bearing housing portion 34 located deep in the gear case 31.

  As described above in detail, according to the motor 10 with the speed reduction mechanism according to the present embodiment, when the armature shaft 13 is displaced, the gear case-side thrust bearing 52 is connected to the O-ring via the gear case-side radial bearing 51. It is swung around the axis C3 of 53. Since the axial center C4 of the gear case side radial bearing 51 is disposed in the vicinity of the axial center C3 of the O-ring 53, the gear case side thrust bearing 52 can easily swing, and thus the rotational resistance of the armature shaft 13 is increased so much. Without misalignment, alignment can be performed by absorbing the shaft misalignment. Therefore, the troublesome alignment work such as reassembling the housing as before is unnecessary, and the alignment work of the armature shaft can be simplified.

  Further, since the gear case side radial bearing 51, the gear case side thrust bearing 52, and the O-ring 53 can be respectively mounted on one side in the axial direction of the armature shaft 13 when the motor 10 with the speed reduction mechanism is assembled, the armature shaft 13 is provided. When assembled to the gear case 31, the gear case side radial bearing 51, the gear case side thrust bearing 52, and the O-ring 53 can be easily assembled to the bearing housing portion 34 of the gear case 31 at a time. Therefore, it is possible to greatly improve the assembly workability of the motor 10 with the speed reduction mechanism.

  Furthermore, since the centering operation can be easily performed by filling the melted resin R in the bearing housing portion 34, the molding accuracy of the gear case 31 can be lowered. That is, even if the gear case 31 is made of resin with low molding accuracy, the gear case-side thrust bearing 52 swings inside the bearing housing portion 34 and the armature shaft 13 is aligned. Therefore, the manufacturing cost and weight of the gear case 31 can be significantly reduced.

  It goes without saying that the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the scope of the invention. For example, in the above embodiment, the motor 10 with the speed reduction mechanism according to the present invention is used as a drive source of the power window device, but the present invention is not limited to this, and the motor 10 with the speed reduction mechanism is It can also be used as a drive source for other purposes such as a wiper device for a vehicle.

  In the above embodiment, the worm gear 32 is separated from the armature shaft 13 and the worm gear 32 is press-fitted to one side of the armature shaft 13 in the axial direction. However, the present invention is not limited to this, and the armature The present invention can also be applied to one in which a worm gear is integrally formed by rolling or the like on the outer peripheral surface on one axial side of the shaft 13.

  Furthermore, in the above embodiment, each of the motor case side radial bearing 41, the brush holder side radial bearing 43, and the gear case side radial bearing 51 is a so-called metal bearing formed in a substantially cylindrical shape by powder metallurgy. Although the present invention is shown, the present invention is not limited to this, and an inner race (inner ring), an outer race (outer ring), a ball bearing including a plurality of balls (steel balls), and the like can also be adopted as a bearing.

10 Motor with reduction mechanism (motor device)
11 Fastening screw 12 Housing 13 Armature shaft (rotating shaft)
20 Motor part 21 Motor case (housing, first case)
21a Brush holder accommodating portion 21b Small diameter portion 22 Magnet 23 Coil 24 Armature 25 Brush holder (housing, first case)
25a Holder body 25b Bearing holding cylinder 25c Annular recess 26 Commutator 27 Brush 28 Spring member 29 Sensor magnet 30 Deceleration part 31 Gear case (housing, second case)
31a Worm gear housing portion 31b Worm wheel housing portion 31c Resin filling hole 31d Air vent hole 32 Worm gear 33 Worm wheel 33a Tooth portion 33b Output gear 34 Bearing housing portion (housing portion)
34a Small diameter accommodation part 34b Large diameter accommodation part 34c Tapered surface 35 Connector member 36 Connector connection part 37 Insertion part 40 Motor case side bearing mechanism 41 Motor case side radial bearing (second bearing)
42 Motor case side thrust bearing 42a Plate-shaped main body 42b Arm 43 Brush holder side radial bearing (third bearing)
44 sensor board 45 rotation sensor 50 gear case side bearing mechanism 51 gear case side radial bearing (first bearing)
51a Sliding contact hole 51b Annular taper 51c Concave groove 52 Gear case side thrust bearing (bearing housing member)
52a bottom part 52b small diameter cylinder part 52c large diameter cylinder part 52d flange part 52e support plane part 53 O-ring (elastic seal)
C1-C4 shaft center CL1, CL2 Clearance MA Axial dimension range R Resin SD Deceleration mechanism

Claims (3)

A housing;
A rotating shaft rotatably provided in the housing;
A first bearing that supports the rotating shaft from a radially outer side;
A bearing housing member that supports the rotating shaft from the outside in the axial direction and is provided with the first bearing on the inside;
An elastic seal provided on the outer side of the bearing housing member so as to overlap the first bearing in the radial direction of the rotating shaft, and being in contact with the housing;
A motor device comprising: The motor device according to claim 1,
The motor device, wherein the housing is provided with a housing portion that houses the bearing housing member, and the housing portion is filled with a resin that positions the bearing housing member with respect to the rotation shaft. The motor apparatus according to claim 1 or 2,
The housing includes a first case provided with a second bearing and a third bearing for supporting the rotating shaft from the radially outer side, and a second case provided with the bearing housing member, and the second case is made of resin. A motor device.

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