WO2011121754A1

WO2011121754A1 - Motor speed reduction mechanism

Info

Publication number: WO2011121754A1
Application number: PCT/JP2010/055840
Authority: WO
Inventors: 山本　健次; 政史三輪
Original assignee: シロキ工業株式会社
Priority date: 2010-03-31
Filing date: 2010-03-31
Publication date: 2011-10-06

Abstract

Provided is a motor speed reduction mechanism for transmitting the rotation driving forces of a plurality of motors (commutator motors) to a helical gear (driven gear) via a warm gear (drive gear), wherein a phenomenon in which the torque is lowered can be prevented. Specifically provided is a motor speed reduction mechanism for transmitting the rotation driving forces of a plurality of motors to a driven gear via a drive gear. Said motor speed reduction mechanism is characterized in that at least one motor among the plurality of motors is disposed such that the switching timing of a commutator with respect to a brush in said one motor is different from the switching timing of a commutator with respect to a brush in another motor.

Description

Motor speed reduction mechanism

The present invention relates to a motor speed reduction mechanism applied to various devices such as a window regulator, a seat slide, and a seat lifter.

The motor speed reduction mechanism transmits the rotational driving force of a plurality of motors (commutator motors) to a helical gear (driven gear) via a worm gear (driving gear), and extracts the reduction power from the helical gear.

For example, Patent Document 1 discloses a technique for engaging two worm gears that are separately motor-driven by one helical gear. It is also possible to mesh three or more worm gears that are separately motor-driven with one helical gear, and it is also possible to rotate one worm gear with a plurality of motors. As described above, if a plurality of motors for driving the worm gear in the forward and reverse directions are provided, there is an advantage that a high torque can be generated using a plurality of relatively inexpensive motors.

JP 2005-186192 A

However, when a plurality of motors that drive the worm gears in the forward and reverse directions are provided, there is a problem that a torque reduction phenomenon occurs at the switching timing when switching of the commutator with respect to the brush occurs simultaneously in the plurality of motors.

Based on the above knowledge, the present invention prevents a torque reduction phenomenon in a motor speed reduction mechanism that transmits the rotational driving force of a plurality of motors (commutator motors) to a helical gear (driven gear) via a worm gear (driving gear). An object of the present invention is to obtain a motor speed reduction mechanism that can be used.

In the present invention, when a plurality of motors of the same specification are driven by the same drive power supply (same phase power supply), at least one motor of the plurality of motors is prevented so that switching of commutators for the brushes of the plurality of motors does not occur simultaneously. Are arranged so that the switching timing of the brush of one motor is different from the switching timing of the commutator for the brush of the other motor (so that the phases of the commutators of the rotors of one motor and the other motor are different). This is based on the viewpoint that the torque reduction phenomenon can be prevented.

That is, the motor speed reduction mechanism of the present invention is a motor speed reduction mechanism that transmits the rotational driving force of a plurality of motors to a driven gear via a drive gear, wherein at least one of the plurality of motors is the one motor. The switching timing of the commutator for the other brush is different from the switching timing of the commutator for the brushes of other motors.

It is preferable that the plurality of motors have a rotor and a plurality of commutators arranged at equal intervals in the circumferential direction, and are arranged so that phases at the time of stopping of the plurality of commutators of the respective rotors are different.

The at least one drive gear can be meshed with the driven gear, and the plurality of motors can be engaged with the at least one drive gear. Further, a plurality of drive gears can be engaged with the driven gear, and at least one of the plurality of motors can be engaged with each of the plurality of drive gears.

It is preferable that the drive gear and the plurality of motors are provided with an index that defines a stop phase with respect to a plurality of commutators of a rotor of the plurality of motors.

In one aspect, the present invention is a regulator driving device having any one of the motor speed reduction mechanisms described above.

In another aspect, the present invention is a motor that engages with at least one drive gear that meshes with a driven gear, and is provided with an index that defines a stop phase for a plurality of commutators of a rotor of the motor. It can be.

According to the present invention, a torque reduction phenomenon can be prevented in a motor speed reduction mechanism that transmits the rotational driving force of a plurality of motors (commutator motors) to a helical gear (driven gear) via a worm gear (driving gear). .

It is a front view which shows one Embodiment which applied the motor deceleration mechanism by this invention to the X arm type | formula window regulator. It is the same exploded perspective view. It is sectional drawing which follows the III-III line of FIG. It is a disassembled perspective view which shows an example of a motor deceleration mechanism. It is a disassembled perspective view which shows the structure of a motor. It is sectional drawing which shows the structure inside a motor. It is a conceptual diagram which shows the mode of switching of the commutator and brush of a motor, and the arrow in a figure has shown the rotation direction of the rotor of a motor. It is a conceptual diagram which shows the mode of switching of the commutator and the brush in the two motors of the present invention, and the arrows in the figure indicate the rotation directions of the rotors of the two motors. It is a timing chart which shows the timing of switching of a commutator and a brush in two motors of the present invention. It is a conceptual diagram which shows the mode of change of a commutator and a brush when two motors make the phase with respect to the commutator of the rotor the same, and the arrow in a figure shows the rotation direction of the rotor of two motors ing. It is a timing chart which shows the switching timing of a commutator and a brush in case two motors make the phase with respect to the commutator of the rotor the same. It is a 1st conceptual diagram which shows another embodiment of the motor deceleration mechanism of this invention. It is a 2nd conceptual diagram which shows another embodiment of the motor deceleration mechanism of this invention. It is a 3rd conceptual diagram which shows another embodiment of the motor deceleration mechanism of this invention. It is a 4th conceptual diagram which shows another embodiment of the motor deceleration mechanism of this invention.

1 to 11, an embodiment in which the motor speed reduction mechanism 30 according to the present invention is applied to an X-arm type window regulator (regulator driving device) will be described. In this embodiment, the motor speed reduction mechanism 30 is a twin in which two motors 100 and 200 (rotor shafts) are engaged (coupled) at both axial ends of a worm gear (drive gear) 39 that meshes with a helical gear (driven gear) 38. A motor speed reduction mechanism will be described as an example. FIG. 1 shows a state in which a motor speed reduction mechanism 30 is mounted on an X-arm type wind regulator. A motor inner device (mounting panel) 10 of a vehicle door is provided with a motor driving device 20 and a horizontal equalizer arm bracket. 11 is fixed. A lift arm bracket 13 in the horizontal direction is fixed to the lower end portion of the elevating window glass 12, and rollers (rolling elements) provided at the upper and lower end portions of the equalizer arm 14 are respectively attached to the lift arm bracket 13 and the equalizer arm bracket 11. , Not shown) is movably fitted. A lift arm 16 is pivotally attached to the equalizer arm 14 by a shaft 15, and a roller (rolling element, not shown) provided at the upper end of the lift arm 16 is similarly movably fitted to the lift arm bracket 13. waiting.

The lift arm 16 is supported so as to be rotatable about a rotation shaft 21 on the motor drive device 20, and a driven gear (rotating member, driven gear) having a sector gear 17 a centering on the rotation shaft 21 at the lower end thereof. Member) 17 is fixed. The sector gear 17a meshes with the pinion 31 (FIGS. 2 to 4) of the motor speed reduction mechanism 30, and when the pinion 31 rotates in the forward and reverse directions, the lift arm 16 (driven gear 17) is moved forward and backward around the rotation shaft 21. It rotates and the raising / lowering glass 12 raises / lowers. The basic structure (operation) of the above X-arm type window regulator is well known.

The motor drive device 20 includes a lift arm 16 fixed to the driven gear 17, a motor speed reduction mechanism 30, a base plate 40, and a mounting leg member 50, and is primarily assembled before being supported on the inner panel 10 (subassembly). ). FIG. 2 shows the motor speed reduction mechanism 30, the lift arm 16 (driven gear 17), the base plate 40, and the mounting leg member 50 in an exploded state, and FIG. 3 shows the state after assembly in cross section.

As shown in FIG. 4, a motor speed reduction mechanism 30 having a pinion 31 has a metal motor holder 36 positioned in a housing 32 (upper housing 32a and lower housing 32b) made of a synthetic resin material. A pair of

motors

100 and 200 are supported on the holder 36. The pair of motors 100 and 200 (rotor shafts) are engaged (coupled) to both ends of the single worm gear (drive gear) 39 in the axial direction so that the worm gear 39 rotates in the same direction. A pair of fixing bolts 33 and a rotation center shaft member 34 are integrally coupled to the motor holder 36. A metal pinion 31 and a synthetic resin helical gear (driven gear) 38 are rotatably supported on the rotation center shaft member 34, and the helical gear 38 is rotationally driven by a pair of

motors

100 and 200. 39 is engaged. That is, the rotational driving force of the pair of

motors

100 and 200 is transmitted to the helical gear 38 via the worm gear 39.

The pinion 31 has a metal gear member 31a at the center and a metal rotation plate 31b that is coaxially coupled to the gear member 31a by serrations 31a 'and 31b'. The helical gear 38 has a plurality of fitting holes 38a formed at intervals in the circumferential direction, and the rotating plate 31b has a plurality of fitting protrusions 31c that fit into the plurality of fitting holes 38a without play. The pinion 31 and the helical gear 38 are coupled so as not to rotate relative to each other.

The base plate 40 made of a pressed product of an elongated metal plate member has a pair of fixing holes 41 for fixing the fixing bolt 33 of the motor speed reduction mechanism 30 at one end, and the circular penetration of the lift arm 16 at the other end. A circular projecting portion 42 projecting from the hole 16a is provided, and a fixing hole 43 corresponding to the rotation center shaft member 34 is provided in an intermediate portion. A fixing nut 44 is screwed to the protruding portion from the base plate 40 to the fixing bolt 33, and a fixing nut 45 is screwed to the fixing screw portion 34a of the protruding portion from the base plate 40 to the rotation center shaft member 34. The base plate 40 and the motor speed reduction mechanism 30 are coupled.

The metal mounting leg member 50, which is a member different from the base plate 40, includes a circular portion 51 that is welded and fixed to the circular protrusion 42 of the base plate 40. That is, the circular protruding portion 42 of the base plate 40 protrudes from the circular through hole 16 a of the lift arm 16, and the circular portion 51 is fixed to the circular protruding portion 42 by welding. The circular projecting portion 42, the circular portion 51, and the circular through hole 16 a constitute the rotating shaft 21 of the lift arm 16. The mounting leg member 50 is provided with a pair of fixed seats 52 located on both sides of the circular portion 51.

A linear gear-opposing contact portion 36a corresponding to the peripheral arc of the helical gear 38 (inner peripheral portion of the tooth portion 38b (meshing portion with the worm gear 39)) protrudes from the helical gear-facing surface (FIG. 3) of the motor holder 36. Is formed. That is, the gear-opposing contact portion 36a has a linear shape that crosses the peripheral arc in the vicinity of the meshing portion of the helical gear 38 with the worm gear 39, and opposes the meshing portion.

On the other hand, on the helical gear facing surface (FIG. 3) of the upper housing 32a, similarly, the arc-shaped gear facing surface corresponding to the peripheral arc of the helical gear 38 (the inner peripheral portion of the tooth portion 38b (meshing portion with the worm gear 39)). A contact portion 32c is formed to project, and a thrust force receiving projection 32d that abuts against the base plate 40 is formed on the surface facing the base plate (upper surface in the figure).

The thrust force receiving protrusion 32d has a columnar shape or a cylindrical shape including at least a part of the meshing portion of the worm gear 39 and the helical gear 38 within a planar profile.

The base plate 40 is formed with an arc-shaped gear abutting convex portion that contacts the peripheral edge of the driven gear 17 (the inner peripheral surface of the gear 17a (the upper surface in the drawing)) in an arc shape. On the other hand, the upper housing 32a is located between the driven gear 17 and the rotating plate 31b that rotate in directions opposite to each other. The upper housing 32a functions to prevent mechanical contact between the two and the driven gear 17 at the same time. That is, the upper housing 32a has an arcuate gear abutment convex portion that contacts the peripheral edge of the driven gear 17 (the back surface on the inner peripheral side of the gear 17a (the lower surface in the drawing)) and the surface of the rotating plate 31b ( Arc-shaped spacer protrusions that are in contact with the upper surface of the figure are formed.

The above motor drive device 20 is fixed on the inner panel 10. That is, the pair of fixing seats 52 of the mounting leg member 50 are fixed to the pair of mounting seats 10a of the inner panel 10 via the fixing bolt nuts 53 and 54 (FIGS. 2 and 3), and the mounting bolt ( The mounting shaft 35 (FIG. 3) is fixed to another mounting seat 10 b of the inner panel 10 by a fixing nut 46. The mounting bolt 35 is the same shaft member as the rotation center shaft member 34 and is implanted (press-fit and fixed) in a metal motor holder 36 (FIGS. 3 and 4) fixed in the housing of the motor speed reduction mechanism 30. And project in opposite directions.

The configuration of the pair of

motors

100 and 200 will be described with reference to FIGS. Since the pair of

motors

100 and 200 have the same specification, only the motor 100 will be described in the present specification (in FIG. 5 to FIG. 7, the reference numeral of the motor 200 is given in parentheses). As shown in FIG. 5, the motor 100 is roughly divided into a housing 110, a rotor (rotor) 120, and a brush unit 130.

The housing 110 is, for example, a steel plate, which is a conductor, drawn by a pressing device, so that the cross section is a quadrangular shape with rounded corners, one end in the axial direction is opened, and the other end is closed by the bottom wall portion 110a. It has a bottomed cylindrical shape. As shown in FIG. 6, four magnets 111 extending in the axial direction are fixed to the four rounded corners of the inner surface of the housing 110 so that the same poles face each other. The housing 110 and the four magnets 111 A magnetic field is formed inside the housing 110.

A rotor 120 is accommodated in the housing 110. The rotor 120 has a shaft 121, and the shaft 121 is pivotally supported at one end thereof by a bearing 112 provided on the bearing support portion 110 b of the bottom wall portion 110 a of the housing 110, so that the shaft 121 is rotatable on the housing 110. It is supported by. An armature 122 is fixed to the shaft 121 so as to be positioned inside a magnetic field formed by the housing 110 and the four magnets 111, and the shaft 121 and the armature 122 rotate integrally. The armature 122 is formed in a substantially cylindrical shape by laminating plate-shaped steel materials (cores) as conductors in the axial direction. As shown in FIG. 6, the armature 122 has a central shaft portion 122a and a peripheral shaft from the central shaft portion 122a. There are six extending portions 122b extending at equal intervals (60 ° intervals) outward in the direction, and six umbrella portions 122c provided at the tips of the respective extending portions 122b. Each of the six extending portions 122b is provided with windings (coils) 123 by lap winding, and these windings 123 rotate together with the armature 122 (shaft 121). Six slits (slots) constituted by the central shaft portion 122a and the adjacent extending portions 122b and umbrella portions 122c serve as paths for the electromagnetic force generated by the current flowing in the winding 123 to flow. In FIG. 6, the winding 123 is not shown.

A commutator 124 is fixed to the shaft 121 adjacent to the armature 122 in the axial direction. The commutator 124 includes six commutator pieces (electrical contacts) 124a arranged at regular intervals (60 ° intervals) in the circumferential direction, and the corresponding windings 123 are electrically connected to the commutator pieces 124a. It is connected. In the present embodiment, as shown in FIG. 7, two opposing sets among the six rectifying pieces 124 a are referred to as 124 a 1, 124 a 2, and 124 a 3.

A brush unit 130 is accommodated in the housing 110. The brush unit 130 has a resin brush holder 131, and two brushes 132 for supplying a drive current to the winding 123 via the commutator 124 (commutator piece 124a) are provided in the radial direction. Is mounted opposite (at intervals of 180 °). The two brushes 132 are held by the brush arm 133, and are elastically slidably contacted with the outer peripheral surface of the commutator 124 (commutator piece 124a). A terminal (not shown) electrically connected to the two brushes 132 extends outside the brush unit 130. The motor 100 also includes a lid member (not shown) that closes the open end of the housing 110 in a state where the rotor 120 and the brush unit 130 are accommodated inside the housing 110. The outside is electrically insulated.

When the motor 100 accommodates the rotor 120 and the brush unit 130 inside the housing 110, one end of the shaft 121 of the rotor 120 is rotatably supported by the bottom wall portion 110 a of the housing 110 and the other end portion of the shaft 121. Is rotatably supported by the brush holder 131 of the brush unit 130. The two brushes 132 of the brush unit 130 are in contact with (electrically connected to) one of the rectifying pieces 124a1, 124a2, and 124a3. When a current is passed through a terminal (not shown) electrically connected to the two brushes 132 in this state, the current is generated from the two brushes 132 in the magnetic field formed inside the housing 110. The two rectifying pieces 124a that are in contact with the two brushes 132 and the corresponding windings 123 flow to the rotor 120, and then the rotor 120 switches between the rectifying pieces 124a that are in contact with the two brushes 132. Continue to rotate while. That is, as shown in FIGS. 7A to 7C, as the rotor 120 rotates, the two brushes 132 switch the rectifying piece 124a in contact with the rectifying piece 124a1, the rectifying piece 124a2, and the rectifying piece 124a3 in this order. To go.

In this embodiment, the shafts of the

rotors

120 and 220 of the two

motors

100 and 200 are generated at different timings (in series) between the

commutators

124 and 224 with respect to the

brushes

132 and 232 in the two

motors

100 and 200. Is engaged (fixed) at both axial ends of the worm gear 39. More specifically, the arrangement of the

housings

110 and 210 and the

brush units

130 and 230 of the

motors

100 and 200 is symmetric, and the

rotors

120 and 220 are arranged in the

motors

100 and 200 as shown in FIG. , 220 with respect to the

commutators

124, 224 are arranged so that the phase at the time of stopping (relative to) is different by 30 ° (the

rotors

120, 220 are arranged by being relatively rotated by 30 °). The stop phase of the

rotors

120 and 220 with respect to the

commutators

124 and 224 is defined by using a cogging torque generated by the attractive force of the

rotors

120 and 220 and the magnets 111 and 211 (the rotation angle of the

rotors

120 and 220 is maintained). ) In addition, the worm gear 39 and the

motors

100 and 200 are provided with an index that defines a stop phase with respect to the plurality of

commutators

124 and 224 of the

rotors

120 and 220 of the

motors

100 and 200. Assembling of the

rotors

120 and 220 is facilitated. For example, the index may be a D-cut provided on the shafts of the worm gear 39 and the

rotors

120 and 220 of the

motors

100 and 200.

According to the motor speed reduction mechanism configured as described above, as shown in the timing chart of FIG. 9, the brush 132 and the commutator 124 (rectifying pieces 124 a 1 to 124 a 3) in the motor 100 are switched (broken lines in FIG. 9), and the motor 200 The switching of the brush 232 and the commutator 224 (the rectifying pieces 224a1 to 224a3) at the same time (the one-dot chain line in FIG. 9) occurs at different timings. Can do.

As shown in FIG. 10, if the phases of the

rotors

120 and 220 of the two

motors

100 and 200 are the same as those of the

commutators

124 and 224, as shown in the timing chart of FIG. Switching of the commutator 124 (rectifying pieces 124a1 to 124a3) and switching of the brush 232 and the commutator 224 (rectifying pieces 224a1 to 224a3) in the motor 200 occur at the same time, and this causes a torque reduction phenomenon. Such a problem does not occur in this form.

In the above embodiment, the case where the number of commutators included in the rotors of the two motors is six is described as an example, but the number of commutators is not limited to this. When the number of commutators is n (the commutator angular interval θ = 360 ° / n), the phase when the two rotors are stopped may be different by θ / 2 (= 180 ° / n).

In the above embodiment, the case where the motor speed reduction mechanism is a twin motor speed reduction mechanism in which the two

motors

100 and 200 are engaged (coupled) at both ends in the axial direction of the worm gear 39 has been described as an example. It is not limited to this. This modification will be described with reference to FIGS.

In FIG. 12A, two motors M1 and M3 are coupled to one end of the worm gear 39 engaged with the helical gear 38 in the axial direction, and one motor M2 is coupled to the other end. In FIG. 12B, two motors M1 and M3 are coupled to one axial end portion of the worm gear meshed with the helical gear 38, and two motors M2 and M4 are coupled to the other end portion.

In FIG. 13A, two

worm gears

39A and 39B are meshed with the helical gear 38, and one motor M1 and M2 are coupled to the two

worm gears

39A and 39B, respectively. In FIG. 13B, three

worm gears

39A, 39B, and 39C are meshed with the helical gear 38, and one motor M1, M2, and M3 is coupled to each of the three

worm gears

39A, 39B, and 39C.

14A, 14B, and 14C, the helical gear 38 is meshed with two worm gears (39A, 39B), three worm gears (39A-39C), and four worm gears (39A-39D), respectively. These worm gears are each coupled with one motor. Each motor is arranged in a windmill shape so that motors coupled to adjacent worm gears do not interfere with each other.

In FIG. 15 (A), two

worm gears

39A and 39B are meshed with a helical gear 38, two motors M1 and M2 are coupled to both axial ends of one worm gear 39A, and two axially opposite ends of the other worm gear 39B. Two motors M3 and M4 are connected. In FIG. 15 (B), two worm gears are meshed with a helical gear, two motors M1 and M2 are coupled to both axial ends of one worm gear 39A, and one motor is coupled to one axial end of the other worm gear 39B. M3 is bound.

12 to 15, at least one of the two motors M1-M2, the three motors M1-M3, or the four motors M1-M4 is connected to the brush of the one motor. The torque switching phenomenon can be prevented by arranging the switching timing of the commutator to be different from the switching timing of the commutator for the brushes of other motors. The same applies when the number of motors is five or more. Further, the engagement of the motor to the worm gear (drive gear) and the engagement of the plurality of motors may be performed by a flexible shaft.

In the above embodiment, the present invention is applied to an arm type window regulator. However, the present invention is a motor speed reduction mechanism that transmits the rotational driving force of a plurality of motors to a driven gear via a driving gear. It can be applied to various devices such as seat slides and seat lifters.

The motor speed reduction mechanism of the present invention is useful as a motor speed reduction mechanism applied to various devices such as a window regulator, a seat slide, and a seat lifter.

10 Inner panel (mounting panel)

10a

10b Mounting seat 11 Equalizer arm bracket 12 Elevating glass 13 Lift arm bracket 14 Equalizer arm 15 Shaft 16 Lift arm 16a Circular through hole 17 Driven gear (rotating member, driven gear member)
17a Sector gear 20 Motor drive device 21 Rotating shaft 30 Motor speed reduction mechanism (twin motor speed reduction mechanism)
31 Pinion

31a Gear member

31b Rotating plate

31c Fitting protrusion 32 Housing 32c Gear facing contact portion 32d Thrust force receiving protrusion 33 Fixing bolt 34 Rotating center shaft member 35 Mounting bolt 36 Motor holder 36a Gear facing contact portion 38 Helical gear (driven gear) )
38a Fitting hole 38b Tooth 39 39A 39B 39C 39D Worm gear (drive gear)
40 Base plate 41 Fixed hole 42 Circular protrusion 43 Fixed hole 50 Mounting leg member 51 Circular portion 52

Fixed seat

100, 200 Pair of

motors

110, 210

Housing

110a, 210a

Bottom wall portion

110b, 210b

Bearing support portion

111, 211

Magnet

112, 212

Bearing

120, 220 Rotor (rotor)
121, 221

Shafts

122, 222

Armatures

122a, 222a

Center shaft portions

122b,

222b Extension portions

122c, 222c

Umbrella portions

123, 223 Windings (coils)
124, 224 Commutator 124a, 124a1, 124a2, 124a3, 224a, 224a1, 224a2, 224a3 Commutator

piece

130, 230

Brush unit

131, 231

Brush holder

132, 232 Brush 133, 233 Brush arm

Claims

In a motor speed reduction mechanism that transmits the rotational driving force of a plurality of motors to a driven gear via a driving gear,
At least one of the plurality of motors is arranged such that the switching timing of the commutator for the brush of the one motor is different from the switching timing of the commutator for the brush of the other motor. Reduction mechanism.
In the motor speed reduction mechanism according to claim 1,
The motor reduction mechanism, wherein the plurality of motors includes a rotor and a plurality of commutators arranged at equal intervals in the circumferential direction, and are arranged such that phases at the time of stopping of the plurality of commutators of the respective rotors are different.
In the motor speed reduction mechanism according to claim 1 or 2,
A motor speed reduction mechanism in which at least one drive gear meshes with the driven gear, and the plurality of motors are engaged with the at least one drive gear.
The motor speed reduction mechanism according to any one of claims 1 to 3,
A motor speed reduction mechanism in which a plurality of drive gears are engaged with the driven gear, and at least one of the plurality of motors is engaged with each of the plurality of drive gears.
The motor speed reduction mechanism according to any one of claims 1 to 4,
A motor speed reduction mechanism in which the driving gear and the plurality of motors are provided with an index for defining a stop phase with respect to a plurality of commutators of a rotor of the plurality of motors.
A motor engaged with at least one drive gear meshing with a driven gear,
The motor provided with the parameter | index which prescribes | regulates the phase at the time of the stop with respect to several commutators of the rotor of the said motor.
A regulator driving device having the motor speed reduction mechanism according to any one of claims 1 to 5.