JP2010154736A - Motor with speed reduction mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a motor with a speed reduction mechanism, capable of sufficiently transmitting rotation force while suppressing an increase in an operating sound of this motor without ensuring molding accuracy of a coupling portion between an armature shaft and a worm shaft so much. <P>SOLUTION: An armature shaft side coupling member 60 is fixed to an armature shaft 24, an uneven hole 71f of a worm shaft side coupling member 70 is press-fitted into a serration portion 43d of the worm shaft 43, and the coupling members 60, 70 are freely fitted. Thus, the coupling members 60, 70 can be each made larger than the diameter of the armature shaft 24 and the molding accuracy of the coupling members 60, 70 is not required so much, so that manufacturing processes can be simplified. The coupling members 60, 70 can be each made larger than the diameter of the armature shaft 24, thereby rotation force can be dispersed to each of the coupling members 60, 70 to suppress tear of each of the coupling members 60, 70 and the rotation force can be sufficiently transmitted while suppressing an increase in the operation sound of the motor with speed reduction mechanism. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a motor with a reduction mechanism provided with a reduction gear that reduces the rotation of a motor unit.

  2. Description of the Related Art Conventionally, as a drive source in a power window device, a sunroof device, or the like mounted on a vehicle such as an automobile, a motor with a speed reduction mechanism that can obtain a large output while being small is used. The motor with a speed reduction mechanism is rotationally driven by an operator operating an operation switch provided in the vehicle interior and the like, and thereby opens and closes an opening / closing body (window glass, sunroof, etc.).

  In-vehicle motors with a reduction mechanism are required to be downsized because they are installed in limited spaces such as the doors and ceilings of vehicles. Regardless, the layout can be improved. Therefore, in order to further reduce the size of the motor with a speed reduction mechanism, the motor unit and the gear unit are separately designed as separate units.

  For example, a small-diameter armature shaft with rigidity that can withstand a predetermined output is used in the motor section, and a worm shaft that has rigidity that can withstand a large reduction ratio in the gear section and has a larger diameter than the amateur shaft. By adopting a design such as adoption, each of the motor unit and the gear unit can be reduced in size, and thus the motor with a speed reduction mechanism can be further reduced in size.

  As a motor with a speed reduction mechanism in which a motor unit and a gear unit are separated, for example, a technique described in Patent Document 1 is known. The motor (motor) with a speed reduction mechanism described in Patent Document 1 has a motor main body (motor part) and a speed reduction part (gear part), and is formed by fixing both with a plurality of screws. . The motor body includes a small-diameter rotating shaft (an amateur shaft), and the speed reduction unit includes a worm shaft having a diameter larger than that of the rotating shaft and a worm wheel rotated by the worm shaft. The rotating shaft and the worm shaft include a clutch. Are connected to each other so as to be able to transmit power to each other.

  The clutch includes a driving-side rotating body (an amateur shaft-side connecting member) provided so as to be integrally rotatable at a connecting portion of the rotating shaft, and a driven-side rotating body (worm shaft) integrally formed with the worm shaft and connected to the driving-side rotating body. Side connecting member). Then, the connecting portion is formed in a two-sided shape having a pair of parallel surfaces, and a drive-side rotator is provided with a connecting hole formed in the same shape as the cross-sectional shape of the connecting portion, and the connecting portion is idled in the connecting hole. By fitting, the shafts of the rotating shaft and the driving side rotating body are allowed to be coupled together so as to be integrally rotatable while allowing the shaft to be displaced.

Japanese Patent No. 3993010 (FIG. 2)

  However, according to the motor with a speed reduction mechanism described in Patent Document 1 described above, the connecting portion of the armature shaft and the connecting hole of the armature shaft side connecting member are loosely fitted in a two-way shape. Since both the connecting portion and the connecting hole are formed on the basis of the diameter of the amateur shaft, the connecting portion and the connecting hole have a small diameter. Therefore, it is difficult to ensure the forming accuracy of the connecting portion and the connecting hole. In addition, since the small-diameter connecting portion is loosely fitted into the small-diameter connecting hole, the connecting portion or the connecting hole is easily worn, and when the wear proceeds, the operating noise of the motor with a speed reduction mechanism is increased and sufficient rotational force is transmitted. Problems such as difficulty may arise.

  An object of the present invention is to provide a speed reduction mechanism capable of transmitting sufficient rotational force while suppressing an increase in operating noise of a motor with a speed reduction mechanism without securing the molding accuracy of a connecting portion between an armature shaft and a worm shaft. It is to provide an attached motor.

  The motor with a speed reduction mechanism of the present invention is a motor with a speed reduction mechanism provided with a speed reduction gear for reducing the rotation of the motor portion, and is fixed to the armature shaft rotatably provided on the motor portion and the end portion of the armature shaft. An armature shaft side connecting member, a worm shaft forming the reduction gear, a serration portion provided at an end portion of the worm shaft and having a plurality of irregularities along a circumferential direction of the worm shaft, and the serration portion A press-fit portion that is press-fitted, rotates integrally with the worm shaft, and includes a worm shaft-side connection member that is connected to the armature shaft-side connection member, the armature shaft-side connection member, and the worm shaft-side connection member; Is loosely fitted.

  The motor with a speed reduction mechanism of the present invention is characterized in that a cushion member is provided between the armature shaft side connecting member and the worm shaft side connecting member.

  The motor with a speed reduction mechanism of the present invention is characterized in that a spherical steel ball is provided between the armature shaft and the worm shaft.

  The motor with a speed reduction mechanism of the present invention is characterized in that a spherical convex portion is formed at an end portion of the armature shaft, a thrust bearing is provided at an end portion of the worm shaft, and the spherical convex portion is brought into contact with the thrust bearing. To do.

  The motor with a speed reduction mechanism of the present invention is characterized in that the worm shaft side connecting member is provided with a sensor magnet for detecting the rotational state of the worm shaft.

  According to the present invention, the armature shaft side connecting member is fixed to the end portion of the armature shaft, the press fit portion of the worm shaft side connecting member is press-fitted into the serration portion provided at the end portion of the worm shaft, and the armature shaft side connecting member and Since the worm shaft side connecting member is loosely fitted, the armature shaft side connecting member and the worm shaft side connecting member connected to each other can be set larger than the diameter dimension of the amateur shaft. Therefore, it is not necessary to ensure the molding accuracy of each connecting member, and the manufacturing process of the motor with a speed reduction mechanism can be simplified. Moreover, since each connecting member can be set larger than the diameter dimension of the armature shaft, it is possible to suppress the wear of each connecting member by distributing the rotational force to each connecting member, thereby suppressing an increase in operating noise of the motor with the speed reduction mechanism. A motor with a speed reduction mechanism capable of transmitting a sufficient rotational force can be provided.

  According to the present invention, since the cushion member is provided between the armature shaft side connecting member and the worm shaft side connecting member, rattling between the armature shaft side connecting member and the worm shaft side connecting member can be suppressed. It becomes possible to further suppress wear of the shaft side connecting member and the worm shaft side connecting member and an increase in operating noise.

  According to the present invention, since the spherical steel ball is provided between the armature shaft and the worm shaft, the rotation of the motor with the speed reduction mechanism can be made smooth when absorbing the misalignment between the armature shaft and the worm shaft. In this case, a spherical convex portion can be formed at the end of the armature shaft, a thrust bearing can be provided at the end of the worm shaft, and the spherical convex portion can be brought into contact with the thrust bearing.

  According to the present invention, the worm shaft side connecting member is provided with the sensor magnet for detecting the rotation state of the worm shaft, so that the sensor magnet can rotate integrally with the worm shaft, and the rotation of the worm shaft. The state can be detected with high accuracy.

It is a fragmentary sectional view of the motor with a speed reduction mechanism concerning a 1st embodiment. It is a perspective view which shows the armature, connecting member, and worm shaft of the motor with a speed reduction mechanism of FIG. It is an expanded sectional view of the broken-line circle A part of FIG. It is a perspective view showing a worm shaft and a pair of bearing members. FIG. 3 is a perspective view of a connecting member viewed from the direction of arrow B in FIG. 2. FIG. 3 is a perspective view of a connecting member viewed from the direction of arrow C in FIG. 2. It is a disassembled perspective view which decomposes | disassembles and shows a connection member. (A), (b) is a perspective view explaining the rigid member which carried out insert molding. (A), (b) is a perspective view explaining the injection-molded cushion member. (A), (b) is explanatory drawing explaining the state of relative rotation with respect to the worm shaft side connection member of an amateur shaft side connection member. (A), (b) is explanatory drawing explaining the state by which the reaction force from a worm wheel was loaded on the worm shaft. It is explanatory drawing explaining the press-fit state of the serration part with respect to a press-fit part. It is an expanded sectional view which expands and shows the connection member concerning a 2nd embodiment.

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

  1 is a partial sectional view of a motor with a speed reduction mechanism according to the first embodiment, FIG. 2 is a perspective view showing an armature, a connecting member, and a worm shaft of the motor with a speed reduction mechanism in FIG. 1, and FIG. FIG. 4 is a perspective view showing the worm shaft and the pair of bearing members, FIG. 5 is a perspective view of the connecting member viewed from the direction of arrow B in FIG. 2, and FIG. 7 is a perspective view of the connecting member as seen from the direction of arrow C, FIG. 7 is an exploded perspective view showing the connecting member in an exploded state, and FIGS. 8A and 8B are perspective views for explaining the insert-molded rigid member. FIGS. 9A and 9B are perspective views for explaining the injection-molded cushion member.

  As shown in FIG. 1, a motor 10 with a speed reduction mechanism is used as a drive source of a power window device (not shown) mounted on a vehicle such as an automobile, and includes a wind regulator (not shown) that raises and lowers the wind glass. To drive. Since the motor 10 with a speed reduction mechanism is installed in a narrow space (not shown) formed in the door of the vehicle, it has a shape in which the thickness dimension along the depth direction in the figure is suppressed from the front side in the figure. Yes. The motor 10 with a speed reduction mechanism includes a motor unit 20 and a gear unit 40, and the motor unit 20 and the gear unit 40 are integrated (unitized) by a plurality of fastening screws 11.

  The motor unit 20 includes a yoke 21 formed into a bottomed cylindrical shape by pressing (deep drawing) a steel plate made of a magnetic material. A pair of magnets 22 is disposed inside the yoke 21 so as to face each other, and an armature 23 around which a coil (not shown) is wound is rotatably provided inside each magnet 22. A brush holder 26 is press-fitted into the opening side (right side in the drawing) of the yoke 21, and the brush holder 26 is disposed so as to close the opening side of the yoke 21.

  An amateur shaft 24 is fixed through the rotation center of the amateur 23, and a commutator 25 is provided at a portion of the amateur shaft 24 adjacent to the amateur 23. The end of the coil wound around the armature 23 is electrically connected to the commutator 25, and a pair of brushes 27 held by the brush holder 26 come into sliding contact with the outer periphery of the commutator 25. ing. Each brush 27 is pressed against the commutator 25 by a spring member 28 at a predetermined pressure. Thereby, a driving current is supplied to each brush 27 from a controller (not shown), thereby rotating the armature 23 (electromagnetic force). The armature shaft 24 rotates at a predetermined rotational speed and rotational torque.

  The bottom side (the left side in the figure) of the yoke 21 is formed in a stepped shape, and the bottomed cylinder portion 21 a having a smaller diameter than the main body portion of the yoke 21 is provided in the portion. A first radial bearing 29 is attached to the bottomed cylindrical portion 21a, and the first radial bearing 29 rotatably supports one axial side (left side in the figure) of the armature shaft 24. A first thrust bearing 30 is disposed on the bottom side of the bottomed cylindrical portion 21a. Between the first thrust bearing 30 and the end portion on one axial side of the armature shaft 24, the first thrust bearing 30 is disposed. A steel ball (steel ball) 31 is provided.

  A second radial bearing 32 is mounted on the brush holder 26, and the second radial bearing 32 rotatably supports the other axial side of the armature shaft 24 (the right side in the figure). As described above, the first radial bearing 29, the first thrust bearing 30 and the first steel ball 31 are provided on the one axial side of the armature shaft 24, and the second radial bearing is disposed on the other axial side of the armature shaft 24. By providing 32, the armature shaft 24, that is, the armature 23 can be smoothly rotated with almost no rotational resistance.

  As shown in FIG. 3, at the end of the amateur shaft 24 on the other side in the axial direction, there is a two-sided portion 24 a having a pair of flat surfaces facing in the radial direction (vertical direction in the figure) of the armature shaft 24. Is provided. An armature shaft side connecting member 60 that forms the connecting member 50 is fixed to the two-way portion 24a.

  As shown in FIG. 1, the gear unit 40 includes a gear case 41 and a connector member 42 attached to the gear case 41. The gear case 41 is formed into a predetermined shape by injection molding a resin material such as plastic, and the gear case 41 is connected to the opening of the yoke 21 via a connector member 42. Inside the gear case 41, a worm shaft 43 having a worm portion 43a (not shown in detail) integrally formed on the outer peripheral portion and a worm wheel 44 having gear teeth (not shown) meshing with the worm portion 43a are rotatable. Contained.

  The worm shaft 43 has a larger diameter than the armature shaft 24 and is provided coaxially with the armature shaft 24 as shown in FIG. One end of the worm shaft 43 in the axial direction is connected to the other end of the armature shaft 24 in the axial direction via a connecting member 50 so as to be integrally rotatable. A second thrust bearing 45 provided in the gear case 41 is disposed on the other side of the worm shaft 43 in the axial direction, and the second thrust bearing 45 and the end of the worm shaft 43 on the other side in the axial direction are arranged. A second steel ball 46 is provided between them. The second thrust bearing 45 and the second steel ball 46 rotate the worm shaft 43 smoothly.

  As shown in FIG. 4, at the both ends in the axial direction of the worm portion 43a provided on the worm shaft 43, a first cover having a diameter smaller than the diameter (9.0 mm to 9.5 mm) of the worm 43a is set. A holding portion 43b and a second held portion 43c are provided. The diameter dimension of the first held portion 43b is set to 5.0 mm to 5.5 mm, the diameter size of the second held portion 43c is set to 7.0 mm to 7.5 mm, and each held portion 43b, 43c The third radial bearing 47 and the fourth radial bearing 48 provided in the gear case 41 are respectively held rotatably.

  The sliding area between the first held portion 43b and the third radial bearing 47 is set by setting the diameter dimensions of the held portions 43b and 43c to substantially the same diameter size (diameter size difference of 2.0 mm or less). The difference in sliding area between the second held portion 43c and the fourth radial bearing 48 is reduced.

  A serration portion 43d is integrally provided at one end of the worm shaft 43 in the axial direction, and the serration portion 43d is an uneven hole 71f (see FIG. 3) of the worm shaft side connecting member 70 forming the connecting member 50. ). The outer peripheral side of the serration portion 43d has a plurality of (9 in the figure) irregularities along the circumferential direction of the worm shaft 43 and is formed in a substantially gear tooth shape. A concave portion 43e having a shape is formed. A spherical third steel ball 80 forming the connecting member 50 enters the recess 43e and comes into line contact therewith.

  As shown in FIG. 1, a pinion 44a as an output shaft is provided at the rotation center of the worm wheel 44 so as to be integrally rotatable, and a gear (not shown) forming a window regulator meshes with the pinion 44a. It is like that. Then, the rotation of the motor unit 20, that is, the rotation of the worm shaft 43 accompanying the rotation of the armature shaft 24 is decelerated by the worm wheel 44 so that the high torque output is transmitted from the pinion 44a to the gear of the window regulator. It has become. Here, the worm shaft 43 and the worm wheel 44 constitute a reduction gear in the present invention.

  A connecting member 50 is provided between the end of the amateur shaft 24 on the other side in the axial direction and the end of the worm shaft 43 on the one side in the axial direction so as to be integrally rotatable. As shown in FIG. 3, the connecting member 50 is set to have a diameter larger than the diameter of the armature shaft 24 and the worm shaft 43, and the armature shaft side connecting member 60, the worm shaft side connecting member 70, and the third steel ball. 80.

  As shown in FIG. 5, the amateur shaft side connecting member 60 is formed into a predetermined shape by pressing (punching) a steel material (made of metal). From the main body portion 61 and the central portion of the main body portion 61, And three projecting portions 62 extending radially. A substantially rectangular fixing hole 63 is provided at the center of the main body 61, and the two-way portion 24 a of the armature shaft 24 is press-fitted into the fixing hole 63 and fixed. Therefore, the armature shaft side connecting member 60 is firmly fixed to the armature shaft 24 without rattling, and rotates integrally with the armature shaft 24. The protrusions 62 are provided at regular intervals (120 ° intervals) along the circumferential direction of the main body 61 and are formed in a substantially fan shape. A side wall surface 64 and another side wall surface 65 are formed on the side portions of each protrusion 62 along the circumferential direction so as to face each other.

  As shown in FIG. 7, the worm shaft side connecting member 70 includes a main body 71, a rigid member 72, and a cushion member 73. The main body 71 is formed in a substantially bottomed shape, and on the bottom side of the main body 71, as shown in FIG. 5, three protrusions 71 a that protrude to one side in the axial direction are provided. The protrusions 71a are provided at regular intervals (120 ° intervals) along the circumferential direction of the main body 71 and are formed in a substantially fan shape. One side wall surface 71b and another side wall surface 71c are formed so as to face each other along the circumferential direction of each protrusion 71a. Between the protrusions 71a along the circumferential direction, each protrusion 62 of the armature shaft side connecting member 60 enters and is connected in a loosely fitted state. The side wall surface 65 is assembled to face the other side wall surface 71c and the one side wall surface 71b of each protrusion 71a. Thereby, when the armature shaft side connecting member 60 rotates, one side wall surface 64b or the other side wall surface 65 of the armature shaft side connecting member 60 is formed on one side wall surface 71b or the other of the protrusion 71a formed on the worm shaft side connecting member 70. Abutting on the side wall surface 71 c, the rotational force of the armature shaft side connecting member 60 is transmitted to the worm shaft side connecting member 70. That is, the worm shaft side connecting member 70 rotates with the rotation of the armature shaft side connecting member 60.

  As shown in FIG. 3, a spherical portion 71d is formed on the bottom of the main body 71. The radius of curvature of the spherical portion 71d is set to be substantially the same value as the radius of curvature of the third steel ball 80, and the third steel ball 80 comes into slidable contact with the spherical portion 71d. Yes. Here, the third steel ball 80 is provided between the armature shaft 24 and the worm shaft 43, and the third steel ball 80 has an end on the other side in the axial direction of the armature shaft 24, the main body portion 71. Each of the spherical surface portion 71d and the concave portion 43e of the worm shaft 43 are in contact with each other.

  As shown in FIG. 6, a plurality of (six in the figure) protrusions 71 e are provided on the opening side of the main body 71, and each protrusion 71 e is arranged around the periphery of the main body 71. It is provided at equal intervals (60 ° intervals) along the direction, and is formed in a substantially cylindrical shape. Each projection 71e is attached with an attachment ring 91 of a sensor magnet 90 provided on the outer periphery of the main body 71, that is, on the outer periphery of the worm shaft side connecting member 70, whereby the sensor magnet 90 is integrated with the worm shaft side connecting member 70. It is provided so as to be rotatable.

  The sensor magnet 90 is formed of a bonded magnet or the like in which magnet powder is bonded with a binder such as resin, and is integrally provided on the outer periphery of a metal mounting ring 91. The sensor magnet 90 is magnetized so that a plurality of magnetic poles (not shown) are alternately arranged at predetermined intervals along the circumferential direction, such as N pole, S pole, N pole, S pole,. ing.

  A concave / convex hole 71f having a plurality of concave / convex portions is formed along the circumferential direction inside the main body 71, and the inner shape of the concave / convex hole 71f is the outer shape of the serration portion 43d provided in the worm shaft 43. Are formed in the same shape. Here, the uneven hole 71f constitutes a press-fit portion in the present invention, and the serration portion 43d is press-fit from the axial direction and fixed to the uneven hole 71f. As a result, the worm shaft side connecting member 70 can rotate integrally with the worm shaft 43 without rattling.

  As shown in the shaded portion in FIG. 8, a rigid member 72 is integrally provided by insert molding inside the main body 71 near the opening. The rigid member 72 is formed in a predetermined shape by pressing a steel plate (made of metal) and plays a role of reinforcing the main body 71. A through hole 72 a into which the serration portion 43 d of the worm shaft 43 can be fitted is formed inside the rigid member 72, and the shape of the through hole 72 a is the same as the uneven hole 71 f of the main body portion 71.

  As shown in the shaded portion in FIG. 9, the main body 71 is provided with a cushion member 73 along the axial direction by injection molding. The cushion member 73 is a molten rubber material (elastomer) between an injection hole (not shown) formed in the main body 71 and a main body 71 and a jig (not shown) covering the main body 71. Is formed in a predetermined shape by injecting at a predetermined pressure and curing.

  On the one side in the axial direction of the cushion member 73, three first cushion portions 73a are provided along the protruding direction of each protruding portion 71a of the main body portion 71. Each of the first cushion portions 73a is formed in a thin shape and is mounted on the radially inner side of each of the protruding portions 71a. The length dimension along the circumferential direction of each 1st cushion part 73a is set to the length dimension longer than the length dimension along the circumferential direction of each protrusion part 71a, The circumference | surroundings of each 1st cushion part 73a A first bulging portion 73b and a second bulging portion 73c that protrude from the protruding portions 71a are provided at both ends along the direction.

  The bulging portions 73b and 73c come into contact with the armature shaft side connecting member 60 in a state where the armature shaft side connecting member 60 is connected to the worm shaft side connecting member 70 (see FIG. 5). ). That is, each bulging part 73b and 73c comprises the cushion member in this invention provided between the armature shaft side connection member 60 and the worm shaft side connection member 70. As shown in FIG. This prevents the armature shaft side connecting member 60 and the worm shaft side connecting member 70 from coming into direct contact with each other in the circumferential direction, and causes wear and noise (operation) of the armature shaft side connecting member 60 and the worm shaft side connecting member 70. Sound) is suppressed.

  Between the circumferential directions of the first cushion portions 73a, there are provided three pressing projections 73d that protrude to one side in the axial direction. The protruding height of each pressing projection 73d is set to a protruding height slightly lower than the protruding height of each first cushion portion 73a toward the one side in the axial direction. The protrusions 62 of the amateur shaft side connecting member 60 come into contact with the inner side in the radial direction (see FIG. 3). This prevents the amateur shaft side connecting member 60 and the worm shaft side connecting member 70 from coming into direct contact with each other in the axial direction, thereby suppressing the generation of noise and the amateur shaft side connecting member 60 and the worm shaft side connecting member. The members 70 are allowed to tilt with respect to each other (see FIG. 11).

  On the other side of the cushion member 73 in the axial direction, the second member is disposed between the worm shaft side connecting member 70 and the worm shaft 43 and close to the rigid member 72, and elastically deforms and bites into the serration portion 43d of the worm shaft 43. A cushion part 73e is provided. The second cushion portion 73e supports the serration portion 43d in the main body portion 71 by elastically deforming and biting into the serration portion 43d.

  As shown in FIG. 3, the connecting member 50 does not directly contact the cushion member 73 and the armature shaft 24 with each other, but the armature shaft 24 is the third steel ball 80 and the cushion member 73 is the armature shaft side connecting member 60. Are in contact with each other. This is to suppress the heat generated in the armature 23 by rotating the motor unit 20 from being transmitted to the cushion member 73 via the armature shaft 24, and thereby the thermal deformation of the cushion member 73. (Deterioration) is suppressed.

  As shown in FIG. 1, the connector member 42 attached to the yoke 21 side of the gear case 41 includes a connector connecting portion 42a to which an external connector (not shown) on the vehicle side is connected, and the inside of the connector connecting portion 42a. A plurality of connection terminals (terminals) (not shown) are provided by insert molding. A part of each connection terminal is electrically connected to each brush 27.

  A sensor board 42b is provided inside the connector member 42, and a part of each connection terminal is electrically connected to the sensor board 42b and a pair of sensor magnets 90 facing the outside in the radial direction. Hall IC 42c (only one is shown in the figure) is mounted.

  Each Hall IC 42c is electrically connected to a controller (not shown), and the controller detects the number of square wave signals from each Hall IC 42c generated according to the rotation of the sensor magnet 90 and the appearance timing thereof, thereby The rotational speed, rotational position, etc. (rotation state) of the shaft 43 are detected. However, in the present embodiment, an MR sensor (magnetoresistive element) can be used instead of the Hall IC 42c.

  Next, the operation of the motor 10 with the speed reduction mechanism according to the first embodiment configured as described above will be described in detail with reference to the drawings.

  10 (a) and 10 (b) are explanatory views for explaining the relative rotation state of the armature shaft side connecting member with respect to the worm shaft side connecting member, and FIGS. 11 (a) and 11 (b) show the reaction force from the worm wheel. FIG. 12 is an explanatory diagram for explaining a state in which the worm shaft is loaded, and FIG. 12 is an explanatory diagram for explaining a press-fitted state of the serration portion with respect to the press-fitting portion.

[CW rotation]
When an operation switch (not shown) is closed to close the window glass, a predetermined drive current is supplied to each brush 27 and the armature shaft 24 rotates clockwise (CW rotation). Then, as shown in FIG. 10A, the armature shaft side connecting member 60 also rotates CW as the armature shaft 24 rotates CW, and the other side wall surface 65 of each protrusion 62 of the armature shaft side connecting member 60 becomes The worm shaft side connecting member 70 is close to the one side wall surface 71b of each protrusion 71a. At this time, since the first bulging portion 73b of the cushion member 73 is disposed between the other side wall surface 65 and the one side wall surface 71b, collision with the one side wall surface 71b of the other side wall surface 65 is avoided ( The occurrence of abnormal noise is suppressed. Thereafter, the rotational force from the armature shaft side connecting member 60 is transmitted to the worm shaft side connecting member 70, and both rotate integrally.

  Here, even if a reaction force is applied to the window glass so that the other side wall surface 65 contacts the one side wall surface 71b, the area of the contact portion between the other side wall surface 65 and the one side wall surface 71b is sufficiently secured. The rotational force can be distributed to the other side wall surface 65 and the one side wall surface 71b. Therefore, wear of the armature shaft side connecting member 60 and the worm shaft side connecting member 70 is suppressed, and efficient transmission of rotational force and suppression of generation of operating noise are achieved.

  Next, with the rotation of the worm shaft side connecting member 70, a rotational force is transmitted to the serration portion 43d, and the worm shaft 43 rotates. Then, with the rotation of the worm shaft 43, the worm wheel 44 having gear teeth that mesh with the worm portion 43a rotates in the direction of the arrow (1) in FIG. Thereby, the pinion 44a of the worm wheel 44 rotates in a predetermined direction, and the window glass is closed via the window regulator. At this time, the driving resistance of the window regulator is transmitted to the worm wheel 44, and a reaction force is applied in the direction (counterclockwise direction) indicated by the broken line arrow in the figure.

  Along with the counterclockwise reaction force applied to the worm wheel 44, a thrust force is applied to the worm shaft 43 in the direction of the arrow (2) in the figure, and the worm portion 43a and the worm wheel 44 are Due to the meshing relationship with the gear teeth, a force is applied in the direction of arrow (3) in the figure, that is, in the direction in which the worm shaft 43 warps upward in the figure. Then, a force F1 indicated by a hollow arrow in the drawing is applied from the second held portion 43c of the worm shaft 43 toward the fourth radial bearing 48, and the second held portion 43c and the fourth radial are loaded. A predetermined frictional force is generated between the bearing 48 and the bearing 48.

  Here, the worm shaft 43 and the worm shaft side connecting member 70 are inclined by a small angle with respect to the amateur shaft side connecting member 60 via the third steel ball 80. At this time, each bulging portion 73b and each pressing protrusion 73d of the cushion member 73 are elastically deformed, and the armature shaft side connecting member 60 and the worm shaft side connecting member 70 rotate together in this state. At this time, due to the flexible elastic deformation of the cushion member 73, the cushion member 73 can rotate together with almost no rotational resistance, and as a result, transmission of the load in the twisting direction from the armature shaft side connecting member 60 to the worm shaft side connecting member 70 is prevented. Thus, the frictional force between the second held portion 43c and the fourth radial bearing 48 is not increased.

[CCW rotation]
When the operation switch is opened to open the window glass, a predetermined drive current is supplied to each brush 27, and the armature shaft 24 rotates counterclockwise (CCW rotation). Then, as shown in FIG. 10B, the armature shaft side connecting member 60 also CCW rotates with the CCW rotation of the armature shaft 24, and the one side wall surface 64 in each protrusion 62 of the armature shaft side connecting member 60 is The worm shaft side connecting member 70 is close to the other side wall surface 71c of each protrusion 71a. At this time, since the second bulging portion 73c of the cushion member 73 is disposed between the one side wall surface 64 and the other side wall surface 71c, collision with the other side wall surface 71c of the one side wall surface 64 is avoided ( The occurrence of abnormal noise is suppressed. Thereafter, the rotational force from the armature shaft side connecting member 60 is transmitted to the worm shaft side connecting member 70, and both rotate integrally.

  Here, even if a reaction force is applied to the window glass so that the one side wall surface 64 contacts the other side wall surface 71c, the area of the contact portion between the one side wall surface 64 and the other side wall surface 71c is sufficiently secured. The rotational force can be distributed to the one side wall surface 64 and the other side wall surface 71c. Therefore, wear of the armature shaft side connecting member 60 and the worm shaft side connecting member 70 is suppressed, and efficient transmission of rotational force and suppression of generation of operating noise are achieved.

  Next, with the rotation of the worm shaft side connecting member 70, a rotational force is transmitted to the serration portion 43d, and the worm shaft 43 rotates. Then, with the rotation of the worm shaft 43, the worm wheel 44 having gear teeth meshing with the worm portion 43a rotates in the direction of the arrow (4) in FIG. Thereby, the pinion 44a of the worm wheel 44 rotates in a predetermined direction, and the window glass is opened via the window regulator. At this time, the driving resistance and the like of the window regulator are transmitted to the worm wheel 44, and a reaction force is applied in the direction (clockwise direction) indicated by the broken line arrow in the figure.

  As the reaction force is applied to the worm wheel 44 in the clockwise direction, a thrust force is applied to the worm shaft 43 in the direction of the arrow (5) in the figure, and the gear between the worm portion 43a and the worm wheel 44 is also applied. Due to the meshing relationship with the teeth, a force is applied in the direction of arrow (6) in the figure, that is, in the direction in which the worm shaft 43 warps upward in the figure. Then, a force F2 indicated by a hollow arrow in the drawing is applied from the first held portion 43b of the worm shaft 43 to the third radial bearing 47, and the first held portion 43b and the third radial portion are loaded. A predetermined frictional force is generated between the bearing 47 and the bearing 47.

  Here, the worm shaft 43 and the worm shaft side connecting member 70 are inclined by a small angle with respect to the amateur shaft side connecting member 60 via the third steel ball 80. At this time, each bulging portion 73c and each pressing projection 73d of the cushion member 73 are elastically deformed, and the armature shaft side connecting member 60 and the worm shaft side connecting member 70 rotate together in this state. At this time, due to the flexible elastic deformation of the cushion member 73, the cushion member 73 can rotate together with almost no rotational resistance, and as a result, transmission of the load in the twisting direction from the armature shaft side connecting member 60 to the worm shaft side connecting member 70 is prevented. Thus, the frictional force between the first held portion 43b and the third radial bearing 47 is not increased.

  Further, since the diameter size of the first held portion 43b and the diameter size of the second held portion 43c are set to substantially the same diameter size, the frictional forces due to the forces F1 and F2 are substantially equal values. It has become. Therefore, the load on the motor unit 20 is substantially equal regardless of the rotation direction of the worm shaft 43 (CW rotation / CCW rotation).

  As described in detail above, according to the motor 10 with the speed reduction mechanism according to the first embodiment, the serration provided on the end portion of the worm shaft 43 with the armature shaft side connecting member 60 fixed to the end portion of the armature shaft 24. The concave and convex holes 71f of the worm shaft side connecting member 70 are press-fitted into the portion 43d, and the armature shaft side connecting member 60 and the worm shaft side connecting member 70 are loosely fitted. Therefore, the armature shaft side connecting member 60 and the worm shaft that are connected to each other The side connecting member 70 can be set larger than the diameter dimension of the armature shaft 24. Therefore, it is not necessary to ensure the molding accuracy of each of the connecting members 60 and 70, and the manufacturing process of the motor 10 with the speed reduction mechanism can be simplified. Further, since each connecting member 60, 70 can be set larger than the diameter dimension of the armature shaft 24, the rotational force can be distributed to each connecting member 60, 70 so that wear of each connecting member 60, 70 can be suppressed. It is possible to provide the motor 10 with a speed reduction mechanism capable of transmitting a sufficient rotational force while suppressing an increase in the operating noise of the attached motor 10.

  Moreover, according to the motor 10 with the speed reduction mechanism according to the first embodiment, since the cushion member 73 is provided between the armature shaft side connecting member 60 and the worm shaft side connecting member 70, the armature shaft side connecting member 60 and Shaking with the worm shaft side connecting member 70 can be suppressed, and wear of the armature shaft side connecting member 60 and the worm shaft side connecting member 70 and an increase in operating noise can be further suppressed.

  Furthermore, according to the motor 10 with the speed reduction mechanism according to the first embodiment, since the third steel ball 80 is provided between the armature shaft 24 and the worm shaft 43, the shaft between the armature shaft 24 and the worm shaft 43 is provided. The rotation of the motor 10 with the speed reduction mechanism when absorbing the deviation can be made smooth.

  Further, since the worm shaft side connecting member 70 is provided with the sensor magnet 90 for detecting the rotation state of the worm shaft 43, the sensor magnet 90 can rotate integrally with the worm shaft 43, and the rotation of the worm shaft 43. The state can be detected with high accuracy.

  Furthermore, the worm shaft side connecting member 70 is provided integrally with the worm shaft side connecting member 70 and has a metal rigid member 72 in which a through hole 72a that can be fitted to the worm shaft 43 is formed. The press-fitting operation of the worm shaft 43 into the concave and convex hole 71f can be facilitated, and the worm shaft side connecting member 70 can be reinforced.

  Next, a second embodiment of the present invention will be described in detail with reference to the drawings. Note that portions having the same functions as those of the first embodiment described above are denoted by the same reference numerals, and detailed description thereof is omitted.

  FIG. 13 is an enlarged cross-sectional view showing the connecting member according to the second embodiment in an enlarged manner.

  As shown in FIG. 13, the connecting member 50 according to the second embodiment is different from the first embodiment in that a worm is replaced with a third steel ball 80 that makes line contact with the recess 43 e of the worm shaft 43. A third thrust bearing 101 is provided in a mounting recess 100 formed at one end of the shaft 43 in the axial direction, and a third thrust bearing is provided at the other axial end of the armature shaft 24. 101, instead of the spherical surface portion 71d of the main body portion 71, the through-hole 103 through which the two-way portion 24a of the armature shaft 24 passes through a predetermined gap is provided. It differs from the provided point.

  Also in the second embodiment configured as described above, the same operational effects as those of the first embodiment described above can be achieved.

  It goes without saying that the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the invention. For example, in each of the above-described embodiments, the motor 10 with the speed reduction mechanism is used as a drive source for a power window device mounted on a vehicle. It can also be used as a drive source.

  Moreover, in each said embodiment, although what employ | adopted the electric motor with a brush as the motor part 20 was shown, this invention is not restricted to this, For example, a brushless electric motor etc. can also be employ | adopted. .

DESCRIPTION OF SYMBOLS 10 Motor with reduction mechanism 11 Fastening screw 20 Motor part 21 Yoke 21a Bottomed cylindrical part 22 Magnet 23 Amateur 24 Amateur shaft 24a Two-way part 25 Commutator 26 Brush holder 27 Brush 28 Spring member 29 1st radial bearing 30 1st Thrust bearing 31 First steel ball 32 Second radial bearing 40 Gear portion 41 Gear case 42 Connector member 42a Connector connection portion 42b Sensor substrate 42c Hall IC
43 Worm shaft (reduction gear)
43a Worm part 43b First held part 43c Second held part 43d Serration part 43e Concave part 44 Worm wheel (reduction gear)
44a pinion 45 second thrust bearing 46 second steel ball 47 third radial bearing 48 fourth radial bearing 50 connecting member 60 amateur shaft side connecting member 61 main body 62 projecting portion 63 fixing hole 64 one side wall surface 65 other Side wall surface 70 Worm shaft side connecting member 71 Main body portion 71a Protruding portion 71b One side wall surface 71c Other side wall surface 71d Spherical surface portion 71e Protrusion 71f Concavity and convexity (press-fit portion)
72 Rigid member 72a Through-hole 73 Cushion member 73a First cushion part 73b First bulge part 73c Second bulge part 73d Holding protrusion 73e Second cushion part 80 Third steel ball (steel ball)
90 sensor magnet 91 mounting ring 100 mounting recess 101 third thrust bearing (thrust bearing)
102 Spherical protrusion 103 Through hole

Claims (5)

A motor with a speed reduction mechanism having a speed reduction gear for reducing the rotation of the motor unit;
An amateur shaft rotatably provided in the motor unit;
An armature shaft side connecting member fixed to an end of the armature shaft;
A worm shaft forming the reduction gear;
A serration portion provided at an end of the worm shaft and having a plurality of irregularities along the circumferential direction of the worm shaft;
A press-fit portion that is press-fitted into the serration portion, rotates integrally with the worm shaft, and includes a worm shaft-side connecting member connected to the amateur shaft-side connecting member;
A motor with a speed reduction mechanism, wherein the armature shaft side connecting member and the worm shaft side connecting member are loosely fitted.   The motor with a speed reduction mechanism according to claim 1, wherein a cushion member is provided between the armature shaft side connecting member and the worm shaft side connecting member.   3. The motor with a speed reduction mechanism according to claim 1, wherein a spherical steel ball is provided between the armature shaft and the worm shaft.   The motor with a speed reduction mechanism according to any one of claims 1 to 3, wherein a spherical convex portion is formed at an end portion of the armature shaft, a thrust bearing is provided at an end portion of the worm shaft, and the spherical convex portion is provided. A motor with a speed reduction mechanism, which is brought into contact with the thrust bearing.   The motor with a speed reduction mechanism according to any one of claims 1 to 4, wherein the worm shaft side coupling member is provided with a sensor magnet for detecting a rotation state of the worm shaft. A motor with a speed reduction mechanism.

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