JP4802494B2 - Window regulator - Google Patents

Description

  The present invention relates to a window regulator.

As a mechanism for raising and lowering the window glass to open and close the vehicle window, for example, there is an X-arm type window regulator disclosed in Patent Document 1.
This window regulator supports a window glass by a lift arm that is rotatably supported by a base plate, and an equalizer arm that is pivotally supported at a substantially central portion in the longitudinal direction of the lift arm. A driven gear is fixed to the lift arm, and the driven gear meshes with a pinion gear that is rotationally driven by an actuator fixed to the base plate. The actuator includes, for example, an electric motor and a speed reduction mechanism that reduces the rotational speed of the electric motor, and the pinion gear is attached to the output shaft of the speed reduction mechanism so as to be integrally rotatable.

The window regulator drives the lift arm by reducing the rotational speed of the driven gear relative to the rotational speed of the pinion according to the radius of the pinion and the radius of the driven gear. Accordingly, the window regulator can obtain a sufficient torque for moving the drive arm up and down by a small electric motor to raise and lower the window glass.
JP 2001-55865 A

  However, the reduction ratio obtained by the above-described reduction mechanism is determined by the radius of the worm and the worm wheel. Therefore, there is a limit to the torque that can be obtained by the lift arm of the window regulator disposed in a limited space by reducing the rotational speed of the motor. In addition, it is difficult to reduce the size of the entire window regulator.

  This invention is made | formed in view of such a situation, The objective is to provide the window regulator which can achieve size reduction.

In order to solve the above-mentioned problem, the invention according to claim 1 is a window regulator that moves up and down the window glass by being attached to a vehicle door and rotating a rotating arm by a motor, and is rotated by the motor. And a cam having a slope inclined with respect to the rotation shaft, and formed into a disk shape, and formed with a first annular tooth portion and a second tooth portion on a flat surface, and is rocked in contact with the slope of the cam. Meshing with the first tooth portion of the rocking gear, the fixed gear having the same number of teeth as the first tooth portion, and the second tooth portion of the rocking gear; The second tooth portion includes a reduction gear mechanism that includes a number of teeth having a different number of teeth and is configured to include an output gear that is coupled to the rotation arm so as not to be relatively rotatable.

The invention according to claim 2 is the window regulator according to claim 1, further comprising a first reduction mechanism comprising a worm and a worm wheel, wherein the worm wheel abuts on the rocking gear at an end surface thereof, The cam is formed integrally with the end surface.

According to the first aspect of the present invention, the oscillating gear, which is oscillated by the inclined surface of the cam by the forward and reverse rotation of the cam, the fixed gear and the output gear are fitted, and the output gear rotates relative to the fixed gear. As a result, the rotating arm rotates. Therefore, since the rotating shaft of the cam and the rotating shaft of the rotating arm are coaxial, that is, the input shaft and the output shaft of the speed reduction mechanism are coaxial, the motor approaches the rotating shaft of the rotating arm and is small. It becomes. Further, since the conventional base plate is unnecessary, the number of parts is reduced. Further, in such a reduction mechanism, the reduction ratio is determined by the difference in the number of teeth provided in the fixed gear and the teeth provided in the output gear. Therefore, since the reduction ratio is high, a large torque can be generated or the motor can be downsized.

According to the second aspect of the present invention, the rotation of the motor can be further decelerated by the worm gear, so that a larger torque can be generated or the motor can be downsized. Further, since the cam and the worm wheel are integrated, the size can be reduced as compared with the speed reduction mechanism that can obtain the same speed reduction ratio.

DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment of the invention will be described with reference to the drawings.
(First embodiment)
FIG. 1 is a schematic configuration diagram of a window regulator according to a first embodiment of the present invention.

The window regulator 1 is accommodated in a space surrounded by an inner wall 2a and an outer wall (not shown) of the door 2, and moves the window glass 3 in the vertical direction in the state shown in FIG.
As shown in FIG. 1, the window regulator 1 according to the present invention includes a lift arm 4a as a pivot arm, and an equalizer arm 4b supported so as to be pivotable at a substantially longitudinal center of the lift arm 4a. X-arm type. The lift arm 4a is rotated by a drive unit 5 as a drive source. By rotating the lift arm 4a by the driving unit 5, the window glass 3 is moved up and down in the state shown in FIG.

  One end of the lift arm 4a is slidably supported by a lift arm bracket 4c arranged in a manner extending in the longitudinal direction on the base end side of the window glass 3. The other end is fixed to the drive unit 5.

  As with the lift arm 4a, one end of the equalizer arm 4b is slidably supported by a lift arm bracket 4c disposed on the base end side of the window glass 3 so as to extend in the longitudinal direction. The other end is slidably supported on the inner wall 2a of the door 2 by an equalizer arm bracket 4d disposed in parallel with the lift arm bracket 4c.

  The drive unit 5 includes a motor 6 as a drive source controlled by a control device (not shown), and a speed reduction mechanism 7 for decelerating the rotation of the motor 6 and transmitting it to the lift arm 4a. It has. The control device determines the driving mode of the window regulator 1 according to a signal from a master switch or door switch (not shown).

  FIG. 2 is a schematic front view showing a driving mode of the window regulator 1. The solid line is the stop position of the window regulator 1 when the front end of the window glass 3 is in contact with the frame 2b of the door 2, that is, the vehicle window is closed, and the two-dot broken line is the state where the vehicle window is fully open. Is the stop position of the window regulator 1 (see FIG. 1).

  By driving the motor 6, the lift arm 4 a at the position indicated by the solid line in FIG. 2 rotates clockwise around the drive unit 5. As the lift arm 4a rotates, the lift arm 4a and the equalizer arm 4b change the relative angle around the rotation axis while being guided by the lift arm bracket 4c and the equalizer arm bracket 4d.

  At this time, the torque corresponding to the torque acting according to the weight of the window glass 3 and the sliding resistance due to the sliding of the lift arm bracket 4c and the equalizer arm bracket 4d is transmitted from the speed reduction mechanism 7 to the lift arm 4a. Yes.

  Here, one end side of the lift arm 4a is allowed to rotate only, and one end side of the equalizer arm 4b is allowed to move only in the left-right direction as shown in FIG. 2 by the equalizer arm bracket 4d. Therefore, the distance from the vehicle fixing position of each arm 4a, 4b to the tip of each arm 4a, 4b is equal in the vertical direction in the state shown in FIG. 2, and the lift arm bracket 4c is parallel to the equalizer arm bracket 4d. That is, it moves along the inner wall 2a and moves to a state indicated by a two-dot broken line in FIG.

  Although only the solid line and the two-dot broken line are shown in FIG. 2 as the stop state of the window regulator 1, the open / close state of the vehicle window can be adjusted by appropriately changing the rotation of the lift arm 4a.

  Next, the drive unit 5 will be described with reference to FIGS. As described above, the lift arm 4a of the X-arm type window regulator 1 requires not only the weight of the window glass 3 but also a torque that can overcome the sliding resistance (see FIG. 1 or 2). Therefore, the drive part 5 is comprised from the motor 6 and the speed reduction mechanism 7 as a motive power source. The speed reduction mechanism 7 is a mechanism for obtaining a torque large enough to rotate the lift arm 4 a from the small motor 6.

  3 is a front view of the drive unit 5, and FIG. 4 is a cross-sectional view taken along line AA in FIG. FIG. 5 is a partially enlarged view of the lift arm 4a. In addition, in the front view shown in FIG. 3, the lift arm 4a and the cover 12 mentioned later are abbreviate | omitted.

  As shown in FIGS. 3 and 4, the drive unit 5 includes a motor 6, a first speed reduction mechanism 8, and a second speed reduction mechanism 9, and the motor 6 input to the first speed reduction mechanism 8. The rotation is input to the second reduction mechanism 9 via the shaft 10 and transmitted to the lift arm 4a.

The first speed reduction mechanism 8 and the second speed reduction mechanism 9 are included in a case 13 having a recess 11 that is recessed in a substantially cylindrical shape and a cover 12 that closes the opening.
Further, the shaft 10 is rotatably supported by a shaft hole 12 a formed at the approximate center of the cover 12 and a bearing 11 b disposed at the approximate center of the bottom surface 11 a of the recess 11.

  The first speed reduction mechanism 8 is a worm gear composed of a worm 14 fixed to an output shaft 6 a of the motor 6 so as to be integrally rotatable and a worm wheel 15. The driving force input to the drive unit 5 from the output shaft 6a of the motor 6 is decelerated by the worm gear (worm 14 and worm wheel 15), and the second reduction mechanism via the shaft 10 attached to the approximate center of the worm wheel 15. 9 is input.

  The second speed reduction mechanism 9 is formed in a substantially low-cylindrical shape, a cam 16 that rotates integrally with the shaft 10, an annular member 17 that is formed in a circular tube shape and abuts against the base end of the lift arm 4a at its end. And a gear 18.

  The cam 16 is formed in a plate shape having an elliptical end surface, and is in contact with the inner periphery of the annular member 17 on the outer periphery thereof. The cam 16 includes a through-hole 16a formed in a manner that penetrates substantially the center of the end surface. A shaft 10 that penetrates the rotation center of the worm wheel 15 substantially vertically is fixed to the through hole 16a so as to be integrally rotatable.

  The annular member 17 includes a plurality of rollers 17a serving as cylindrical members, pins 17b penetrating the end surfaces of the rollers 17a, and plates 17c serving as plate-like connecting members that are disposed on both ends of the roller 17a and connect adjacent pins 17b. And an endless chain. The roller 17 a is rotatably supported by a pin 17 b and is disposed in parallel to the shaft 10 that passes through the approximate center of the cam 16. The annular member 17 is in contact with the lift arm 4a in such a manner that one end face side is closed by the lift arm 4a. In the present embodiment, the roller 17a corresponds to a fitting member.

  One end side of the lift arm 4a is penetrated substantially perpendicularly to the shaft 10, and a plurality of slits 19 extending radially about the shaft 10 are formed. When the pin 17b of the annular member 17 passes through the slit 19, the annular member 17 is attached to the proximal end side of the lift arm 4a (see FIG. 5).

  In the present embodiment, n slits 19 and 17 pins 17b (n = 30 in this embodiment) are formed, and one slit 19 is penetrated by one pin 17b.

  The gear 18 accommodates the cam 16 and the annular member 17 on the inner peripheral side thereof, and is fixed to the concave portion 11 on the outer peripheral side thereof. The gear 18 is formed in a substantially bottomed cylindrical shape having an opening end 18a on the cover 12 side. The inner peripheral surface 18b of the gear 18 extends parallel to the shaft 10 and has an outer peripheral shape of the roller 17a. Correspondingly, grooves 18c are formed as a plurality of recessed portions. That is, the groove 18c is a tooth disposed on the inner peripheral side of the gear. Further, the substantially center of the bottom surface 11 a is penetrated by the shaft 10. In this embodiment, n + 2 (n + 2 = 32 in this embodiment) grooves 18c are formed.

  Here, the annular member 17, the gear 18, and the cam 16 are in contact with the groove 18 c of the gear 18 on the long axis side end surface 16 b of the cam 16 in such a manner that the roller 17 a of the annular member 17 is fitted. That is, the position where the annular member 17 and the gear 18 abut is on the extended line of the long axis of the ellipse forming the cam 16, and the roller 17a and the groove 18c in the other portions are completely separated.

  Next, the drive mode of the drive unit 5 of the window regulator 1 according to the present embodiment will be described focusing on the second reduction mechanism 9. As an example, it is assumed that the lift arm 4a is rotated clockwise in order to bring the window glass 3 in the state shown by the solid line in FIG. 2 into the state shown by the two-dot broken line.

The control device (not shown) drives the motor 6 by detecting the operation of the master switch or the door switch by the occupant.
The rotation of the motor 6 is decelerated by the first reduction mechanism 8, rotates the shaft 10, and is input to the second reduction mechanism 9.

  As the shaft 10 rotates, the cam 16 changes the position of the end face 16b on the long axis side with respect to the gear 18, so that the position where the roller 17a of the annular member 17 and the groove 18c of the gear 18 mesh with each other sequentially moves.

  At this time, since the groove 18c is formed two more than the roller 17a, when the cam 16 makes one rotation counterclockwise, the annular member 17 rotates relative to the gear 18 or the case 13 by the difference between the groove 18c and the roller 17a. Relative rotation around.

  The annular member 17 and the lift arm 4 a are connected by a pin 17 b and a slit 19. Since the pin 17 b is guided by the slit 19, the relative displacement of the annular member 17 with respect to the lift arm 4 a is allowed only in the radial direction around the shaft 10, and with the rotation of the annular member 17 around the shaft 10. The lift arm 4a also rotates clockwise about the shaft 10.

According to the first embodiment described above, the following effects are obtained.
(1) Input from the first reduction mechanism 8 to the second reduction mechanism 9 via the shaft 10. Further, the lift arm 4a rotates around the axis 10. Therefore, since the input from the first reduction mechanism 8 to the second reduction mechanism 9 and the output from the second reduction mechanism 9 to the lift arm 4a are made coaxially, the reduction mechanism 7 is reduced in size along the inner wall and the outer wall. Thus, a small window regulator 1 can be obtained.

  Further, since the second reduction mechanism 9 can obtain a reduction ratio corresponding to the difference in the number of the groove 18c of the gear 18 and the roller 17a of the annular member 17, the rotation of the motor 6 is converted into a large torque and the lift arm 4a can be transmitted. Therefore, compared with a conventional window regulator using a driven gear and a base plate as the second speed reduction mechanism 9, although the equivalent torque is transmitted from the motor 6 to the lift arm 4a, in the direction along the inner wall and the outer wall. A downsized window regulator can be obtained.

  In addition, since the reduction ratio obtained by the second reduction mechanism 9 is determined by the difference in the number of rollers 17a and grooves 18c, the reduction ratio is determined by the radius of the driven gear and the base plate. And a large reduction ratio can be obtained.

  (2) The side surface of the annular member 17 is formed of an endless chain. Since the pin 17b is guided by the slit 19, movement in the circumferential direction is restricted, and the cam 16 that contacts the inner periphery of the annular member 17 is provided. The outer peripheral surface is relatively moved only in the radial direction with respect to the rotation axis of the lift arm 4a by rotation. The annular member 17 formed in this way can change the shape of the side surface in the radial direction by the rotation of the plate 17c with the pin 17b as the rotation axis at the relative position of the rollers 17a adjacent to each other.

  Further, since the roller 17a and the groove 18c can be reliably fitted, slipping between the roller 17a and the groove 18c is suppressed. Accordingly, since the force acting in the circumferential direction of the shaft 10 at the fitting position between the roller 17a and the groove 18c is reliably transmitted from the roller 17a to the groove 18c, a large torque can be transmitted.

  (3) Since the speed reduction mechanism 7 is composed of the first speed reduction mechanism 8 and the second speed reduction mechanism 9, the rotational speed input to the speed reduction mechanism 7 can be sufficiently reduced and output, and a small motor Even so, the torque required to rotate the lift arm 4a can be obtained.

In addition, you may change embodiment of this invention as follows.
In the above embodiment, n = 30 rollers 17a and n + 2 = 32 grooves 18c are formed. However, the number of rollers 17a and grooves 18c and the number of the rollers 17a and grooves 18c are not necessarily limited thereto. The difference (2 in this embodiment) can be changed as appropriate without departing from the essence of the present invention. In other words, the difference occurs without the number of rollers 17a and the grooves 18c being in agreement, and the change is made as long as the fitting position of the rollers 17a and the grooves 18c is sequentially fed by the rotation of the cam 16. May be.

(Second Embodiment)
A second embodiment of the present invention will be described below with reference to FIGS. In addition, 2nd Embodiment mainly changes the drive part 5 of 1st Embodiment, and the structure of the lift arm 4a or the equalizer arm 4b, those drive aspects, etc. are the same as 1st Embodiment. The description of the constituent parts is omitted.

  6 is a front view of the drive unit 5a, and FIG. 7 is a cross-sectional view taken along the line BB in FIG. In FIG. 6, a lift arm 20, an output gear 32, and a cover 25 (see FIG. 7) described later are omitted.

  As shown in FIGS. 6 and 7, the speed reduction mechanism 21 according to the present embodiment includes a first speed reduction mechanism 22 and a second speed reduction mechanism 23, and the rotation of the motor 6 is the first speed reduction mechanism 22 and After being decelerated by the second reduction mechanism 23, it is transmitted to the lift arm 20.

The first reduction mechanism 22 and the second reduction mechanism 23 are included in a case 26 that includes a recess 24 that is recessed in a substantially cylindrical shape and a cover 25 that closes the opening.
As in the first embodiment, the first reduction mechanism 22 is a worm gear that includes a worm 27 fixed to the output shaft 6 a of the motor 6 so as to be integrally rotatable, and a worm wheel 28. The driving force input from the output shaft 6 a of the motor 6 to the speed reduction mechanism 21 is decelerated by the disk-shaped worm wheel 28.

  Unlike the first embodiment, one end surface of the worm wheel 28 is formed with a holding portion 29 that is recessed in a cylindrical shape so that the bottom surface thereof is slightly inclined with respect to the end surface of the worm wheel 28. . Further, the worm wheel 28 is rotatably supported by a bearing 24b fixed to the approximate center of the bottom surface 24a of the recess 24 of the case 26.

  The second reduction mechanism 23 is fixed to the rocking gear 30 housed in the holding portion 29 of the worm wheel 28, the gear portion 31 as a fixed gear formed integrally with the cover 25, and the base end side of the lift arm 20. Output gear 32.

  The oscillating gear 30 is formed in a disk shape, and is formed with a first tooth portion 30b and a second tooth portion 30c each having n teeth annularly along the outer periphery of one plane 30a. The flat surface 30d is rotatably accommodated so as to abut on the inclined surface 29a of the holding portion 29 of the worm wheel 28. In addition, the 1st tooth | gear part 30b is arrange | positioned at the outer peripheral side of the 2nd tooth | gear part 30c. Further, the swing gear 30 and the worm wheel 28 are slidable and can be rotated relative to each other.

  The gear portion 31 is formed in such a manner that n teeth 31 a that mesh with the first tooth portion 30 b of the swing gear 30 protrude from the cover 25 toward the worm wheel 28 in an annular shape. A bearing hole 25 a is formed in the cover 25 so as to penetrate a position corresponding to the approximate center of the gear portion 31.

  The output gear 32 is a bevel gear having a substantially disc shape and provided with (n−1) teeth 32a meshing with the second tooth portion 30c of the swing gear 30 on the end surface on the worm wheel 28 side. A fixed shaft 32b is formed on the end surface facing the case 26 so as to protrude substantially vertically. The output gear 32 is disposed on the inner peripheral side of the gear portion 31, and the fixed shaft 32 b protrudes from the case 26 and is fixed to the lift arm 20 so as to penetrate a bearing hole 25 a formed at the center of the gear portion 31. ing. The fixed shaft 32b is not prevented from rotating by the bearing hole 25a.

  The first tooth portion 30b and the second tooth portion 30c of the swinging gear 30 are located only at a position closest to the cover 25 (the output gear 32 or the gear portion 31) by the inclined surface 29a of the holding portion 29. And mesh.

Next, the drive mode of the drive unit 5a of the window regulator according to the second embodiment will be described focusing on the second reduction mechanism 23.
The rotation of the motor 6 is transmitted to the worm wheel 28 via the worm 27 attached to the output shaft 6a.

  As the worm wheel 28 rotates, the rotational surface of the oscillating gear 30 accommodated in the holding portion 29 changes the position of the oscillating gear 30, the output gear 32, and the gear portion 31. The adjacent positions change sequentially. That is, the holding portion 29 of the worm wheel 28 functions as a cam, and the swing gear 30 accommodated in the holding portion 29 behaves as a follower.

At this time, since the number of teeth of the first tooth portion 30b of the swing gear 30 and the number of teeth of the gear portion 31 are 1: 1, the swing gear 30 swings without rotating with respect to the gear portion 31. Only.
On the other hand, since the number of teeth of the output gear 32 is smaller than the number of teeth of the second tooth portion 30 c of the swing gear 30, the output gear 32 rotates relative to the gear portion 31 by the difference (1 in the present embodiment). The lift arm 20 fixed to the fixed shaft 32 b of the output gear 32 rotates as the output gear 32 rotates.

The second embodiment described above has the following effects.
(4) The second speed reduction mechanism 23 includes a swing gear 30 disposed on the end surface of the worm wheel 28 of the first speed reduction mechanism 22 and an output gear 32 disposed opposite to the swing gear 30. The lift arm 20 is driven. Therefore, the input from the first reduction mechanism 22 to the second reduction mechanism 23 and the output from the second reduction mechanism 23 to the lift arm 20 are made coaxially. Therefore, the speed reduction mechanism 21 can be downsized in the direction along the inner wall and the outer wall, and a small window regulator can be obtained as a whole.

  Further, since the second reduction mechanism 23 can obtain a reduction ratio corresponding to the difference between the number of teeth of the gear portion 31 and the number of teeth of the output gear 32, the rotation of the motor 6 is converted into a large torque and the lift arm 20 is converted. Can be communicated to. Therefore, as compared with a conventional window regulator using a driven gear and a base plate as the second reduction mechanism 23, the equivalent torque is transmitted from the motor 6 to the lift arm 20, but in the direction along the inner wall and the outer wall. A downsized window regulator can be obtained.

  Further, since the reduction ratio obtained by the second reduction mechanism 23 is determined by the difference between the number of teeth of the gear portion 31 and the number of teeth of the output gear 32, the reduction ratio is configured by a driven gear and a base plate whose reduction ratio is determined by the radius. It is possible to obtain a large reduction ratio as compared with the reduction mechanism.

  (5) Since the speed reduction mechanism 21 is composed of the first speed reduction mechanism 22 and the second speed reduction mechanism 23, the rotational speed input to the speed reduction mechanism 7 can be sufficiently reduced and output, and a small motor Even so, the torque required to rotate the lift arm 20 can be obtained.

In addition, you may change embodiment of this invention as follows.
In the above embodiment, the difference in the number of teeth between the gear unit 31 and the output gear 32 is 1, but the difference in the number of teeth may be 2. That is, the meshing position of the oscillating gear 30, the gear portion 31, and the output gear 32 can be changed as appropriate within a range in which the oscillating gear 30 can be moved sequentially by the oscillation of the oscillating gear 30.

  -In the said embodiment, the fitting in a fitting part is fitting with the gear part 31, the output gear 32, and the teeth 31a and 32a formed in the rocking gear 30, and the 1st tooth part 30b and the 2nd tooth part 30c. However, the present invention is not limited to such a configuration. For example, a configuration in which one of the fitting portions has a groove and the other side has a convex portion that fits into the groove is also conceivable.

  In the above embodiment, the output gear 32 fixed to the lift arm 20 is disposed on the inner peripheral side of the gear portion 31, but is not limited to such a mode. For example, as shown in FIG. 8 which is a cross-sectional view of a position corresponding to FIG. 7, the gear portion 36 is fixed to the distal end side of the support shaft 35 formed in a mode of protruding from the approximate center of the bottom surface 33 toward the cover 34. The output gear 37 can be disposed on the outer peripheral side.

The front view which shows schematic structure of the window regulator which concerns on this Embodiment. The front view which shows schematic structure of 1st Embodiment which concerns on this Embodiment. The front view which shows schematic structure of 1st Embodiment which concerns on this Embodiment. AA sectional drawing of FIG. The front view which shows a part of 1st Embodiment which concerns on this Embodiment. The front view which shows schematic structure of 2nd Embodiment which concerns on this Embodiment. BB sectional drawing of FIG. Sectional drawing which shows another example of 2nd Embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Window regulator, 2 ... Door, 2a ... Inner wall, 3 ... Window glass, 6 ... Motor, 7, 21 ... Reduction mechanism, 8, 22 ... First reduction mechanism, 9, 23 ... Second reduction mechanism, 10 ... Shaft , 11, 24 ... recess, 13, 26 ... case, 14, 27 ... worm, 15 ... worm wheel, 16 ... cam, 16b ... long axis side end surface, 17 ... annular member, 17a ... roller (fitting member), 17b ... Pin, 17c ... Plate (connection member), 18 ... Gear, 18b ... Inner peripheral surface, 18c ... Groove, 19 ... Slit, 28 ... Worm wheel (cam with inclined slope), 29a ... Slope, 30 ... Oscillation Gear, 30a, 30d ... plane, 30b ... first tooth, 30c ... second tooth, 31, 36 ... gear (fixed gear), 31a ... gear teeth, 32, 37 ... output gear, 32a ... output Gear teeth.

Claims (2)

A window regulator that moves up and down a window glass by rotating a rotating arm by a motor attached to a vehicle door,
A cam that is rotationally driven by the motor and has a slope inclined with respect to the rotation axis;
An oscillating gear that is formed in a disc shape, has annular first teeth and second teeth formed on a plane, and is oscillated in contact with the inclined surface of the cam;
A fixed gear meshing with the first tooth portion of the swing gear and having the same number of teeth as the first tooth portion;
An output gear that meshes with the second tooth portion of the rocking gear and has a number of teeth having a different number of teeth from the second tooth portion, and is connected to the rotating arm so as not to be relatively rotatable. A window regulator comprising a reduced speed reduction mechanism . The window regulator according to claim 1,
A first reduction mechanism comprising a worm and a worm wheel;
The worm wheel is in contact with the rocking gear at its end face,
The cam is formed integrally with the end surface.
A window regulator characterized by that.

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