JP2015132289A - Planetary gear device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a planetary gear device capable of suppressing noise and abrasion of gears with a simple constitution.SOLUTION: A planetary gear device 10 includes a sun gear 11, a planetary gear 14 engaged with the sun gear 11, and a first ring gear 17 and a second ring gear 26 engaged with the planetary gear 14. Each of the gears is a conical gear having tapered teeth. The planetary gear 14 is disposed in a state of being axially held by the first ring gear 17 and the second ring gear 26. An axial distance of the first ring gear 17 and the second ring gear 26 is adjusted by adjusting means. According to this constitution, backlash of the ring gears 17, 26 and the planetary gear 14 can be eliminated by adjusting only the axial distance between the first ring gear 17 and the second ring gear 26.

Description

  The present invention relates to a planetary gear device.

  The planetary gear device is widely used because a large reduction ratio can be obtained with a small number of stages, a large torque can be transmitted, and an input shaft and an output shaft can be arranged coaxially. For example, the planetary gear device is provided in a rotation transmission path from the crankshaft of the internal combustion engine to the camshaft, and changes the rotation phase between the crankshaft and the camshaft by reducing the rotation of the actuator and transmitting it to the camshaft. Used as a valve timing adjustment device. In Patent Document 1, a planetary gear device is connected to a sun gear connected to an actuator, a carrier having a sprocket that can rotate integrally with a crankshaft, a planetary gear that is rotatably supported by the carrier, and a camshaft. Ring gear.

US Pat. No. 5,680,836

  By the way, the backlash between the gears of the planetary gear device causes abnormal noise and gear wear. For example, in the case of the valve timing adjusting device, the torque fluctuation of the cam shaft is transmitted to the ring gear, so that a collision occurs between the ring gear and the planetary gear, and the above-described noise and gear wear occur. Therefore, in order to suppress abnormal noise and gear wear, it is important to reduce backlash.

  On the other hand, the planetary gear of the planetary gear device of Patent Document 1 is a taper gear, and is biased in the axial direction by a coil spring against a ring gear that is also a taper gear. Thereby, the backlash between the ring gear and the planetary gear is reduced.

However, the planetary gear device of Patent Document 1 has a drawback that a coil spring is required for each planetary gear, and the structure becomes complicated.
The present invention has been made in view of the above points, and an object of the present invention is to provide a planetary gear device that can suppress abnormal noise and gear wear with a simple configuration.

  A planetary gear device according to the present invention includes a sun gear, a planetary gear, a first ring gear, a second ring gear, and adjusting means. The sun gear has first tapered outer teeth that are tapered outer teeth. The planetary gear is located on the side opposite to the small diameter end with respect to the second taper external teeth, which are tapered external teeth meshing with the first taper external teeth, and the large diameter end of the second taper external teeth, And it has the 3rd taper external tooth which is a taper-shaped external tooth where an outer diameter becomes small as it spaces apart from a 2nd taper external tooth to an axial direction.

  The 1st ring gear has the 1st taper internal tooth which is located on the same axis as the sun gear, and is a taper-like internal tooth which meshes with the 2nd taper external tooth. The second ring gear is positioned coaxially with the sun gear, has second tapered inner teeth that are tapered inner teeth meshing with the third tapered outer teeth, and is rotatable relative to the first ring gear. The adjusting means adjusts the axial distance between the first ring gear and the second ring gear.

  With this configuration, if only the axial distance between the first ring gear and the second ring gear is adjusted, the backlash between each ring gear and the planetary gear can be reduced. Therefore, abnormal noise and gear wear can be suppressed with a simple configuration.

It is sectional drawing which shows the valve timing adjustment apparatus with which the planetary gear apparatus by 1st Embodiment of this invention was applied. It is a figure explaining the schematic structure of the internal combustion engine provided with the valve timing adjustment apparatus of FIG. It is the figure which looked at the planetary gear apparatus of FIG. 1 from the arrow III direction. It is the IV-IV sectional view taken on the line of FIG. It is an enlarged view of the V part of FIG. It is sectional drawing which shows the valve timing adjustment apparatus with which the planetary gear apparatus by 2nd Embodiment of this invention was applied. It is sectional drawing which shows the valve timing adjustment apparatus with which the planetary gear apparatus by 3rd Embodiment of this invention was applied. It is sectional drawing which shows the valve timing adjustment apparatus with which the planetary gear apparatus by 4th Embodiment of this invention was applied. It is sectional drawing which shows the valve timing adjustment apparatus with which the planetary gear apparatus by 5th Embodiment of this invention was applied. FIG. 10 is an enlarged view of a portion X in FIG. 9. It is sectional drawing which shows the valve timing adjustment apparatus with which the planetary gear apparatus by 6th Embodiment of this invention was applied.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In the embodiments, substantially the same components are denoted by the same reference numerals and description thereof is omitted.
<First Embodiment>
FIG. 1 shows a valve timing adjusting device to which the planetary gear device according to the first embodiment of the present invention is applied. The valve timing adjusting device 5 is for adjusting the opening / closing timing of the intake valve 91 of the internal combustion engine 90 shown in FIG. As shown in FIG. 2, the rotation of the crankshaft 92 of the internal combustion engine 90 is transmitted to the camshafts 97 and 98 via a chain 96 wound around the sprockets 93, 94 and 95. The intake valve 91 is driven to open and close by a cam shaft 97, and the exhaust valve 99 is driven to open and close by a cam shaft 98.

The valve timing adjusting device 5 advances the opening / closing timing of the intake valve 91 by rotating the cam shaft 97 relative to the sprocket 93 that rotates in conjunction with the crankshaft 92 in the rotational direction. The relative rotation of the cam shaft 97 so that the opening / closing timing of the intake valve 91 is advanced in this way is referred to as “advance”.
Further, the valve timing adjusting device 5 delays the opening / closing timing of the intake valve 91 by rotating the cam shaft 97 relative to the sprocket 93 in the direction opposite to the rotation direction. The relative rotation of the cam shaft 97 so that the opening / closing timing of the intake valve 91 is delayed in this way is referred to as “retarding”.

(overall structure)
First, the overall configuration of the valve timing adjusting device 5 will be described with reference to FIGS.
The valve timing adjusting device 5 includes a motor 6 and a planetary gear device 10.
The motor 6 is composed of, for example, a brushless motor, and is fixed to the chain cover 9 of the internal combustion engine 90. The rotation state of the motor shaft 7 is controlled by an electronic control device (not shown).

The planetary gear device 10 includes a sun gear 11, a planetary gear 14, a first ring gear 17, a sprocket shaft 21, a second ring gear 26, and the like.
The sun gear 11 is located coaxially with the cam shaft 97 and has a cylindrical shaft 12 and external teeth 13. The cylindrical shaft 12 is connected to the motor shaft 7 of the motor 6 through the connecting member 8 so as to be able to transmit rotation. The external teeth 13 are formed on the end of the cylindrical shaft 12 opposite to the motor 6.

The planetary gear 14 has external teeth 15 that mesh with the external teeth 13 of the sun gear 11 and external teeth 16 that are located on the opposite side of the motor 6 from the external teeth 15, and can revolve around the sun gear 11. In the present embodiment, three planetary gears 14 are provided.
The first ring gear 17 is positioned coaxially with the cam shaft 97 and has internal teeth 18 that mesh with the external teeth 15 of the planetary gear 14.

  The sprocket shaft 21 is a bottomed cylindrical member having a cylindrical portion 22 positioned coaxially with the cam shaft 97 and a bottom portion 23 positioned at one end of the cylindrical portion 22. The bottom 23 of the sprocket shaft 21 has a through hole 24 through which the end of the cam shaft 97 is inserted. The first ring gear 17 is fixed to the open end of the cylindrical portion 22 of the sprocket shaft 21. In the present embodiment, the first ring gear 17 is fixed to the sprocket shaft 21 with a screw 25, for example. The sprocket 93 is formed integrally with the cylindrical portion 22 of the sprocket shaft 21. The first ring gear 17, the sprocket shaft 21 and the sprocket 93 can be rotated relative to the cam shaft 97.

  The second ring gear 26 is provided inside the cylindrical portion 22 of the sprocket shaft 21, is positioned coaxially with the cam shaft 97, and has inner teeth 27 that mesh with the outer teeth 16 of the planetary gear 14. The second ring gear 26 has a fitting hole 28 into which an end of the cam shaft 97 is fitted, and is fixed to the cam shaft 97 by a bolt 29.

  A value obtained by dividing the number of teeth of the external teeth 15 of the planetary gear 14 by the number of teeth of the internal teeth 18 of the first ring gear 17 is a first gear ratio, and the number of teeth of the external teeth 16 of the planetary gear 14 is the internal teeth of the second ring gear 26. If the value divided by the number of 27 teeth is the second tooth number ratio, the second tooth number ratio is set to be different from the first tooth number ratio. In the present embodiment, for example, the second tooth number ratio is set to be smaller than the first tooth number ratio.

  In the valve timing adjusting device 5 configured as described above, when the rotational phase of the cam shaft 97 with respect to the crank shaft 92 coincides with the target value, the motor shaft 7 of the motor 6 is rotated at the same speed as the sprocket 93. Thereby, the rotation phase of the cam shaft 97 with respect to the crankshaft 92 does not change, and the opening / closing timing of the intake valve is not changed.

  When the rotational phase of the cam shaft 97 with respect to the crank shaft 92 is on the retard side with respect to the target value, the motor shaft 7 of the motor 6 is rotated at a high speed with respect to the sprocket 93. At this time, the rotation of the motor shaft 7 is decelerated by the planetary gear device 10 and transmitted to the cam shaft 97. Thereby, the rotational phase of the cam shaft 97 with respect to the crankshaft 92 changes to the advance side, and the opening / closing timing of the intake valve is advanced.

  Further, when the rotational phase of the cam shaft 97 with respect to the crankshaft 92 is on the more advanced side than the target value, the motor shaft 7 of the motor 6 is rotated at a low speed or reversely with respect to the sprocket 93. At this time, the rotation of the motor shaft 7 is decelerated by the planetary gear device 10 and transmitted to the cam shaft 97. As a result, the rotational phase of the camshaft 97 relative to the crankshaft 92 changes to the retard side, and the intake valve opening / closing timing is delayed.

(Feature configuration)
Next, the characteristic configuration of the planetary gear device 10 will be described with reference to FIGS.
The sun gear 11, the planetary gear 14, the first ring gear 17 and the second ring gear 26 are conical gears. The conical gear is also called a taper gear, and is a gear having a conical shape by continuously shifting teeth in the axial direction.
The outer teeth 13 of the sun gear 11 are formed in a tapered shape so that the outer diameter decreases as the distance from the motor 6 in the axial direction decreases. Hereinafter, the external teeth 13 are referred to as first tapered external teeth 13.

The external teeth 15 of the planetary gear 14 mesh with the first tapered external teeth 13 and are tapered so that the outer diameter increases as the distance from the motor 6 in the axial direction increases. Hereinafter, the external teeth 15 are referred to as second tapered external teeth 15.
The external teeth 16 of the planetary gear 14 are positioned on the opposite side of the large-diameter end of the second tapered external tooth 15 from the small-diameter end, and the external diameter decreases with increasing distance from the second tapered external tooth 15 in the axial direction. It is formed in a tapered shape. Hereinafter, the external teeth 16 are referred to as third tapered external teeth 16.

The inner teeth 18 of the first ring gear 17 mesh with the second tapered outer teeth 15 and are tapered so that the inner diameter increases as the distance from the motor 6 increases in the axial direction. Hereinafter, the internal teeth 18 are referred to as first tapered internal teeth 18.
The inner teeth 27 of the second ring gear 26 mesh with the third tapered outer teeth 16 and are tapered so that the inner diameter decreases as the distance from the motor 6 increases in the axial direction. Hereinafter, the inner teeth 27 are referred to as second tapered inner teeth 27.

The planetary gear device 10 further includes a disc spring 31 and a support ring 32 as adjusting means for adjusting the axial distance between the first ring gear 17 and the second ring gear 26.
The disc spring 31 is provided between the bottom 23 of the sprocket shaft 21 and the second ring gear 26, and generates a pressing force that presses the second ring gear 26 toward the first ring gear 17 in the axial direction. The sprocket shaft 21 corresponds to a “rotary body” described in the claims. The bottom portion 23 of the sprocket shaft 21 is located on the opposite side of the second ring gear 26 from the first ring gear 17 and corresponds to a “support portion” recited in the claims. The cylindrical portion 22 of the sprocket shaft 21 connects the bottom portion 23 and the first ring gear 17 and corresponds to a “connecting portion” described in the claims.

  The support ring 32 is an annular member positioned coaxially with the cam shaft 97, is rotatable relative to the sun gear 11, and supports the planetary gear 14 radially inward of the planetary gear 14. In the present embodiment, the planetary gear 14 has an annular protrusion 33 that is in contact with the support ring 32 between the second tapered outer teeth 15 and the third tapered outer teeth 16. The support ring 32 is formed to have a relatively small radial thickness so that it can be elastically deformed in the radial direction, and generates a reaction force that pushes the planetary gear 14 radially outward by an elastic force.

  In the planetary gear device 10 configured as described above, the first taper inner teeth 18 are pressed against the second taper outer teeth 15 in the axial direction by the pressing force of the disc spring 31, and the second taper inner teeth 27 are third. The taper outer teeth 16 are pressed in the axial direction. Further, due to the reaction force of the support ring 32, the third tapered outer teeth 16 are pressed against the second tapered inner teeth 27 in the radial direction while the second tapered outer teeth 15 are pressed against the first tapered inner teeth 18 in the radial direction. Yes. Thus, the axial distance between the first ring gear 17 and the second ring gear 26 is adjusted, and the backlash between the planetary gear 14 and the first ring gear 17 and the backlash between the planetary gear 14 and the second ring gear 26 are reduced. Has been removed.

(effect)
As described above, the planetary gear device 10 according to the first embodiment includes the sun gear 11, the planetary gear 14 that meshes with the sun gear 11, and the first ring gear 17 and the second ring gear 26 that mesh with the planetary gear 14. Each gear is a conical gear having tapered teeth. The planetary gear 14 is provided so as to be sandwiched between the first ring gear 17 and the second ring gear 26 in the axial direction. The axial distance between the first ring gear 17 and the second ring gear 26 is adjusted by adjusting means.

  With this configuration, only the axial distance between the first ring gear 17 and the second ring gear 26 can be adjusted, and the backlash between the ring gears 17 and 26 and the planetary gear 14 can be eliminated. Therefore, abnormal noise and gear wear can be suppressed with a simple configuration.

  In the first embodiment, the adjusting means includes a disc spring 31 and a sprocket shaft 21 and generates a pressing force that presses the second ring gear 26 toward the first ring gear 17 in the axial direction. The sprocket shaft 21 integrally forms a cylindrical portion 22 fixed to the first ring gear 17 and a bottom portion 23 located on the opposite side of the second ring gear 26 from the first ring gear 17. The disc spring 31 is provided between the bottom 23 of the sprocket shaft 21 and the second ring gear 26.

As a result, the first tapered inner teeth 18 are pressed against the second tapered outer teeth 15 in the axial direction, while the second tapered inner teeth 27 are pressed against the third tapered outer teeth 16 in the axial direction, so that the ring gears 17 and 26 and the planetary gear 14 are pressed. And backlash can be eliminated.
Further, the pressing force by the disc spring 31 follows the progress of the wear of the teeth of each gear to narrow the axial distance between the first ring gear 17 and the second ring gear 26, and the first taper inner teeth 18 are outside the second taper. The pressing state to the teeth 15 and the pressing state of the second tapered inner teeth 27 to the third tapered outer teeth 16 can be maintained.

In the first embodiment, a support ring 32 is provided on the inner side in the radial direction of the planetary gear 14. The support ring 32 is an annular member positioned coaxially with the sun gear 11, is rotatable relative to the sun gear 11, and supports the planetary gear 14. The support ring 32 does not restrain the planetary gears 14 in the circumferential direction.
Thereby, the radial load generated in the planetary gear 14 according to the adjustment of the axial distance between the first ring gear 17 and the second ring gear 26 and the torque transmitted from the cam shaft is received by the support ring 32, and the first taper of the sun gear 11 is received. The surface pressure acting on the external teeth 13 can be reduced. Therefore, the sun gear 11 can be reduced in size.

  Further, it is possible to make backlash between the sun gear 11 and the planetary gear 14 while eliminating backlash between the ring gears 17 and 26 and the planetary gear 14. Therefore, it is possible to allow a positional shift between the second tapered outer teeth 15 and the third tapered outer teeth 16 of the planetary gear 14 that occurs in manufacturing. Therefore, the manufacturing cost can be reduced.

  Further, in the first embodiment, each gear is constituted by a conical gear, and each planetary gear 14 is pressed against the support ring 32 by being pressed in the axial direction so that the first ring gear 81 and the second ring gear 83 approach each other. ing. Thereby, each planetary gear 14 and the support ring 32 can always be contacted. Therefore, the rotational force of the planetary gear 14 meshed with the sun gear 11 at a certain point is transmitted to the support ring 32 by friction and then transmitted to the planetary gear 14 not meshed with the sun gear 11.

In the first embodiment, three planetary gears 14 are provided around the support ring 32.
Therefore, all the planetary gears 14 can be reliably supported by the support ring 32.

Further, in the first embodiment, the support ring 32 can be elastically deformed in the radial direction, and generates a reaction force that pushes the planetary gear 14 radially outward by the elastic force, so that the second taper outer teeth 15 have the first taper inside. The axial distance between the first ring gear 17 and the second ring gear 26 is adjusted by pressing the teeth 18 and pressing the third tapered outer teeth 16 against the second tapered inner teeth 27.
Thereby, the backlash between the ring gears 17 and 26 and the planetary gear 14 can be eliminated with a simple configuration.
In addition, all the planetary gears 14 can be more reliably supported by the support ring 32.

Second Embodiment
A planetary gear device 40 according to a second embodiment of the present invention will be described with reference to FIG.
The second ring gear 41 of the planetary gear device 40 is slidably provided on the inner wall surface of the cylindrical portion 43 of the sprocket shaft 42. The sprocket shaft 42 forms a hydraulic pressure chamber 44 on the side opposite to the first ring gear 17 with respect to the second ring gear 41, and hydraulic fluid that presses the second ring gear 41 toward the first ring gear 17 in the axial direction. 44 can be accommodated. The hydraulic fluid is pumped from the pump 45 to the hydraulic pressure chamber 44 via the direction switching valve 46 and the passage 47 of the cam shaft 97. In this embodiment, the pump 45 is a mechanical oil pump that rotates in conjunction with the crankshaft of the internal combustion engine, and pumps engine oil as hydraulic fluid. The sprocket shaft 42 corresponds to a “hydraulic chamber forming member” recited in the claims.

In the second embodiment, the sprocket shaft 42 adjusts the axial distance between the first ring gear 17 and the second ring gear 41 by generating a pressing force that presses the second ring gear 41 toward the first ring gear 17 in the axial direction. Functions as a means.
With this configuration, only the axial distance between the first ring gear 17 and the second ring gear 41 can be adjusted, and the backlash between the ring gears 17 and 41 and the planetary gear 14 can be eliminated. Therefore, abnormal noise and gear wear can be suppressed with a simple configuration.
Further, since the above-mentioned pressing force increases following the cam torque that increases as the engine speed increases, the pressing force can be adjusted efficiently.

<Third Embodiment>
A planetary gear device 50 according to a third embodiment of the present invention will be described with reference to FIG.
In the planetary gear device 50, the adjusting means for adjusting the axial distance between the first ring gear 17 and the second ring gear 26 includes the sprocket shaft 21 and the shim plate 51. The shim plate 51 is provided between the bottom 23 of the sprocket shaft 21 and the second ring gear 26. The thickness of the shim plate 51 is set so that the backlash between the planetary gear 14 and the first ring gear 17 and the backlash between the planetary gear 14 and the second ring gear 26 are eliminated as much as possible.

  With this configuration, only the axial distance between the first ring gear 17 and the second ring gear 26 can be adjusted, and the backlash between the ring gears 17 and 26 and the planetary gear 14 can be eliminated as much as possible. Therefore, abnormal noise and gear wear can be suppressed with a simple configuration.

<Fourth embodiment>
A planetary gear device 60 according to a fourth embodiment of the present invention will be described with reference to FIG.
In the planetary gear device 60, the bottom portion 23 of the sprocket shaft 21 restricts the second ring gear 26 from moving in the axial direction so as to be separated from the first ring gear 17 by the reaction force of the support ring 32. In the fourth embodiment, only the support ring 32 is the adjusting means for adjusting the axial distance between the first ring gear 17 and the second ring gear 26.
With this configuration, the backlash between the ring gears 17 and 26 and the planetary gear 14 can be eliminated by using only the support ring 32.

<Fifth Embodiment>
A planetary gear device 70 according to a fifth embodiment of the present invention will be described with reference to FIGS.
In the planetary gear device 70, an elastic member 71 is provided between the support ring 32 and the annular protrusion 33 of the planetary gear 14. The elastic member 71 is made of rubber, for example, and can be elastically deformed in the radial direction. The elastic member 71 generates a reaction force that pushes the planetary gear 14 radially outward by elastic force, and presses the second taper outer teeth 15 against the first taper inner teeth 18 and the third taper outer teeth 16 within the second taper. It functions as an adjusting means for adjusting the axial distance between the first ring gear 17 and the second ring gear 26 by being pressed against the teeth 27.
With this configuration, the backlash between the ring gears 17 and 26 and the planetary gear 14 can be eliminated by using only the support ring 32 and the elastic member 71.

<Sixth Embodiment>
A planetary gear device 80 according to a sixth embodiment of the present invention will be described with reference to FIG.
In the planetary gear device 80, the number of teeth of the first tapered inner teeth 82 of the first ring gear 81 and the number of teeth of the second tapered inner teeth 84 of the second ring gear 83 are an integral multiple of the number (three) of the planetary gears 14. Different. Accordingly, the planetary gears 14 are arranged at unequal pitches around the sun gear 11.

  Here, when a plurality of planetary gears having the same shape are arranged at unequal pitches around the sun gear, the planetary gears and the ring gears are not meshed at the same time. Such a meshing state causes abnormal noise and gear wear. Therefore, in the conventional form in which each planetary gear is rotatably supported by the planetary carrier, the planetary carrier bearings are manufactured at unequal pitches, and a part of torque transmission is imposed on the planetary carrier, or a plurality of types having different shapes are used. It was necessary to make a planetary gear.

  On the other hand, in the sixth embodiment, the planetary gear 14 is supported by the support ring 32 without the planetary carrier. This eliminates the need for a planetary carrier and allows each planetary gear 14 to have the same shape, thereby reducing manufacturing costs. In addition, since there is no particular problem in arranging the plurality of planetary gears 14 at unequal pitches around the sun gear 11, the range of selection of the number of teeth of each gear is widened, and the degree of freedom in design is increased.

<Other embodiments>
In another embodiment of the present invention, four or more planetary gears may be provided. In this case, the support ring can be elastically deformed in the radial direction, or by providing an elastic member between the support ring and the planetary gear, all the planetary gears can be reliably supported by the support ring. As the number of planetary gears increases, the load applied to one planetary gear is reduced, and the planetary gear device can be made smaller.

In another embodiment of the present invention, the urging member constituting the adjusting means is not limited to a disc spring, and may be another spring such as a wave washer or a coil spring.
In another embodiment of the present invention, an adjusting screw may be provided as the adjusting means instead of the shim plate.
In another embodiment of the present invention, the elastic member provided between the planetary gear and the support ring as the adjusting means is not limited to rubber, and may be made of, for example, an elastic resin or a spring. .
In another embodiment of the present invention, the support ring may be formed with relatively high rigidity and inelastically deformable in the radial direction.

In another embodiment of the present invention, the valve timing adjusting device may adjust the valve timing of the exhaust valve of the internal combustion engine.
In another embodiment of the present invention, the planetary gear device may be applied not only to the valve timing adjusting device but also to other devices as a speed reducer.
The present invention is not limited to the embodiments described above, and can be implemented in various forms without departing from the spirit of the invention.

10, 40, 50, 60, 70, 80 ... planetary gear unit 11 ... sun gear 13 ... first taper external tooth 14 ... planetary gear 15 ... second taper external tooth 16 ... first 3 taper outer teeth 17, 81 ... first ring gear 18, 82 ... first taper inner teeth 26, 83 ... second ring gears 27, 84 ... second taper inner teeth 31 ... disc spring (Adjustment means)
32 ... Support ring (adjustment means)
42... Sprocket shaft (hydraulic chamber forming member, adjusting means)
51 .. shim plate (adjustment means)
71 ... elastic member (adjusting means)

Claims (12)

A sun gear (11) having first tapered external teeth (13) which are tapered external teeth;
A second tapered outer tooth (15) which is a tapered outer tooth meshing with the first tapered outer tooth, and a position opposite to the small diameter end with respect to the large diameter end of the second tapered outer tooth And one or more planetary gears (14) having third tapered outer teeth (16), which are tapered outer teeth whose outer diameter decreases as they are spaced apart from the second tapered outer teeth in the axial direction. When,
A first ring gear (17, 81) having first tapered inner teeth (18, 82) which are coaxially located with the sun gear and are tapered inner teeth meshing with the second tapered outer teeth; ,
It has 2nd taper internal teeth (27, 84) which are located on the same axis as the sun gear, and are meshing with the 3rd taper external teeth, and can rotate relatively to the 1st ring gear. A second ring gear (26, 83);
Adjusting means (31, 32, 42, 51, 71) for adjusting the axial distance between the first ring gear and the second ring gear;
A planetary gear device (10, 40, 50, 60, 70, 80) comprising:   The planetary gear device (1) according to claim 1, wherein the adjusting means (31, 42) generates a pressing force that presses one of the first ring gear and the second ring gear in the axial direction to the other side. 10, 40, 70). The adjusting means includes
A rotating body having a support portion (23) positioned on the opposite side of the second ring gear from the first ring gear, and a connection portion (22) connecting the support portion and the first ring gear. (21) and
A biasing member (31) provided between the support portion of the rotating body and the second ring gear;
The planetary gear set (10, 70) according to claim 2, characterized by comprising:   The adjusting means forms a hydraulic pressure chamber (44) on the side opposite to the first ring gear with respect to the second ring gear, and a hydraulic pressure capable of accommodating the hydraulic fluid that presses the second ring gear in the hydraulic pressure chamber. The planetary gear set (40) according to claim 2 or 3, characterized in that it includes a chamber forming member (42). The adjusting means includes
A rotating part having a support part located on the opposite side to the first ring gear with respect to the second ring gear, and a connection part connecting the support part and the first ring gear;
A shim plate (51) provided between the support portion of the rotating body and the second ring gear;
The planetary gear set (50) according to claim 1, characterized by comprising:   The annular member located coaxially with the sun gear, further comprising a support ring (32) supporting the planetary gear radially inward of the planetary gear. A planetary gear device according to claim 1.   The support ring is elastically deformable in a radial direction, generates a reaction force that pushes the planetary gear outward in the radial direction by an elastic force, and presses the second tapered outer teeth against the first tapered inner teeth and the first 7. The planetary gear according to claim 6, wherein the planetary gear is an adjusting means for adjusting an axial distance between the first ring gear and the second ring gear by pressing three taper outer teeth against the second taper inner teeth. apparatus.   The first taper of the second taper external teeth is provided between the support ring and the planetary gear, is elastically deformable in a radial direction, and generates a reaction force that pushes the planetary gear radially outward by an elastic force. An elastic member (71) as the adjusting means for adjusting the axial distance between the first ring gear and the second ring gear by pressing against the inner teeth and pressing the third tapered outer teeth against the second tapered inner teeth The planetary gear device (70) according to claim 6, further comprising:   An annular member positioned coaxially with the sun gear, supports the planetary gear radially inward of the planetary gear, is elastically deformable in the radial direction, and pushes the planetary gear radially outward by an elastic force. Force is generated, and the first taper gear and the second ring gear are pressed by pressing the second tapered outer teeth against the first tapered inner teeth and pressing the third tapered outer teeth against the second tapered inner teeth. The planetary gear device according to claim 1, further comprising a support ring as the adjusting means for adjusting an axial distance. An annular member located coaxially with the sun gear, and a support ring supporting the planetary gear radially inward of the planetary gear;
The first taper of the second taper external teeth is provided between the support ring and the planetary gear, is elastically deformable in a radial direction, and generates a reaction force that pushes the planetary gear radially outward by an elastic force. An elastic member as the adjusting means for adjusting an axial distance between the first ring gear and the second ring gear by pressing against an inner tooth and pressing the third tapered outer tooth against the second tapered inner tooth;
The planetary gear device according to claim 1, further comprising:   11. At least one of the number of teeth of the first tapered inner teeth and the number of teeth of the second tapered inner teeth is different from an integer multiple of the number of planetary gears. A planetary gear device (80) according to claim 1. The first ring gear is rotatable integrally with a crankshaft (92) of the internal combustion engine (90),
The second ring gear is rotatable integrally with a camshaft (97) of the internal combustion engine;
The sun gear is connectable to an actuator (6),
It is possible to adjust the valve timing of the valve that the camshaft is driven to open and close by decelerating the rotation output from the actuator and transmitting it to the camshaft and changing the rotational phase of the crankshaft and the camshaft. The planetary gear device according to any one of claims 1 to 11, wherein

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