JP6874983B2 - Decelerator - Google Patents

Description

The present invention relates to a speed reducer.

Conventionally, a speed reducer that is used in a valve timing adjusting device or the like and includes a planetary rotating body, a driving rotating body, and a driven rotating body is known as described in Patent Document 1 or Patent Document 2. This speed reducer changes the relative rotation phase between the driving rotating body and the driven rotating body by causing the planetary rotating body to make a planetary motion with respect to the driving rotating body.

Japanese Unexamined Patent Publication No. 2013-167173

Generally, when two gears rotate and mesh with each other, a force acting in a direction in which the two gears separate in the direction perpendicular to the axis is applied to the two gears.
In the configuration of Patent Document 1, in order to press the outer teeth of the planetary rotating body against the internal teeth of the driving rotating body and the driven rotating body, the urging member that urges the planetary rotating body radially outward of the planetary rotating body rotates the planet. It is provided inside the body. By providing the urging member, the structure of the reduction gear is complicated, the number of parts is increased, and the cost is increased. If there is no urging member, vibration or noise may occur due to the contact between the internal and external teeth.

The present invention has been created in view of these points, and an object of the present invention is to provide a speed reducer that suppresses the generation of vibration and noise with a simple configuration.

The speed reducing device according to the present invention includes a driving rotating body (20), a driven rotating body (30), a planetary rotating body (40), an input rotating body (60) and a pressurized rotating body (80).
The drive rotating body has a drive internal gear portion (21) and a sprocket portion (22) and is rotatable.
The drive internal gear portion includes a first oblique tooth (211) in which the tooth streak is twisted.
The sprocket portion is fitted to the drive internal gear portion.
The driven rotating body is housed in the driving rotating body on the sprocket portion side, has a driven internal gear portion (31), and is rotatable.
The driven internal gear portion includes the second oblique tooth (311) inside.

The planetary rotating body has a driving side planetary external gear portion (41) and a driven side planetary external gear portion (42), and is capable of planetary motion.
The drive-side planetary external gear portion is fitted to the drive internal gear portion and includes a third oblique tooth (411) on the outside.
The driven side planetary external gear portion is fitted to the driven internal gear portion and includes a fourth oblique tooth (421) on the outside.
The input rotating body has an input external gear portion (61), and when the planet rotating body rotates, the planetary rotating body makes a planetary motion to change the relative rotation phase of the driving rotating body or the driven rotating body, and the driving rotating body or the driven rotating body changes the relative rotation phase. Accelerates or decelerates the rotation of.
The input external gear portion is fitted to the drive-side planetary external gear portion and includes a fifth oblique tooth (611) on the outside.

The pressurized rotating body has a pressurized external gear portion (81) and is rotatable.
The pressurized external gear portion is fitted to the driven side planetary external gear portion and includes a sixth oblique tooth (811) on the outside.

Depending on the 3rd and 4th oblique teeth, the force in the direction in which the 5th oblique tooth presses the 3rd oblique tooth in the axial direction or the force in the direction in which the 6th oblique tooth presses the 4th oblique tooth in the axial direction is the drive internal gear. It is converted into a force in the direction in which the planetary rotating body is pressed against the part or the driven internal gear part. Therefore, since the planetary rotating body is directly pressed against the driving rotating body and the driven rotating body in the radial direction, it is not necessary to provide an urging member. Further, the gap between the drive internal gear portion or the driven internal gear portion and the planetary rotating body is reduced, and vibration or noise due to tooth contact between the drive internal gear portion or the driven internal gear portion and the planetary rotating body is suppressed.

The schematic diagram of the valve timing adjustment device in which the reduction gear according to 1st Embodiment is used. FIG. 3 is a cross-sectional view of the reduction gear according to the first embodiment. FIG. 2 is a sectional view taken along line III-III of FIG. FIG. 2 is a sectional view taken along line IV-IV of FIG. The figure for demonstrating the action of the force of the reduction gear according to 1st Embodiment. FIG. 5 is a sectional view taken along line VI-VI of FIG. The figure for demonstrating the twist angle of the 1st oblique tooth and the 2nd oblique tooth of the reduction gear according to 1st Embodiment. The figure for demonstrating the action of the force of the reduction gear according to 1st Embodiment. FIG. 3 is a cross-sectional view of the reduction gear according to the second embodiment. The arrow view seen from X in FIG. FIG. 3 is a cross-sectional view of the reduction gear according to the third embodiment. FIG. 6 is a cross-sectional view of the reduction gear according to the fourth embodiment. FIG. 12 is an enlarged view of part XIII. FIG. 5 is a cross-sectional view of the reduction gear according to the fifth embodiment. FIG. 5 is an external view of a planetary rotating body of a speed reducer according to a fifth embodiment. The figure for demonstrating the pitch circle of the drive internal gear part, the driven internal gear part, the input external gear part and the pressurized external gear part of the reduction gear according to 5th Embodiment. The figure for demonstrating the pitch circle of the drive side planetary external gear part and the driven side planetary external gear part of the reduction gear according to 5th Embodiment. FIG. 5 is a perspective view showing one of the third oblique teeth of the planetary external gear portion on the drive side of the reduction gear according to the fifth embodiment. The figure for demonstrating the time when the planetary rotating body of the speed reduction apparatus by 5th Embodiment is tilted. XX part enlarged view of FIG. The figure for demonstrating the number of the extension part outer teeth number | pressure | pressurization inner tooth number of the reduction device according to 5th Embodiment. The figure for demonstrating the sliding speed of the planetary rotating body of the reduction gear according to 5th Embodiment. FIG. 6 is an external view of a planetary rotating body of a speed reducer according to another embodiment. FIG. 6 is an external view of a planetary rotating body of a speed reducer according to another embodiment. Sectional drawing of the reduction gear according to another embodiment. Sectional drawing of the reduction gear according to another embodiment. Sectional drawing of the reduction gear according to another embodiment. Sectional drawing of the reduction gear according to another embodiment. FIG. 3 is a perspective view showing one of the third oblique teeth of the planetary external gear portion on the drive side of the reduction gear according to another embodiment. FIG. 6 is an external view of a planetary rotating body of a speed reducer according to another embodiment. FIG. 6 is an external view of a planetary rotating body of a speed reducer according to another embodiment. FIG. 6 is an external view of a planetary rotating body of a speed reducer according to another embodiment.

Hereinafter, the speed reducer will be described with reference to the drawings. In the description of the plurality of embodiments, the same reference numerals are given to the configurations substantially the same as those of the first embodiment, and the description thereof will be omitted. Further, the present embodiment includes a plurality of embodiments. The speed reducer of these embodiments is used, for example, in a valve timing adjusting device for an internal combustion engine that adjusts the valve timing of at least one of an intake valve and an exhaust valve.

The valve timing adjusting device 10 used in the speed reducing device 151 of the present embodiment will be described.
As shown in FIG. 1, in the internal combustion engine 1, the chain 7 is wound around the crank gear 3 and the drive rotating body 20 of the speed reducer 151.
The crank gear 3 is fixed to the crankshaft 2 as the drive shaft of the internal combustion engine 1.
The drive rotating body 20 of the speed reducing device 151 is fixed to the cam shafts 4 and 5 as the driven shafts.
Torque Tc is transmitted from the crankshaft 2 to the camshafts 4 and 5 via the chain 7. One camshaft 4 drives the intake valve 8 and the other camshaft 5 drives the exhaust valve 9.

The valve timing adjusting device 10 of the present embodiment adjusts the opening / closing timing of the intake valve 8 or the exhaust valve 9 by changing the relative rotation phases of the crankshaft 2 and the camshafts 4 and 5.
The speed reducer 151 of the present embodiment is used to change the relative rotation phase of the crankshaft 2 and the camshafts 4 and 5.

The valve timing adjusting device 10 causes the intake valve 8 or the exhaust valve 9 to rotate relative to the drive rotating body 20 that rotates integrally with the crankshaft 2 in the same rotation direction as the crankshaft 2. Advance the valve timing. The relative rotation of the camshafts 4 and 5 so that the valve timing of the intake valve 8 or the exhaust valve 9 is earlier is referred to as "advancing".

Further, the valve timing adjusting device 10 delays the valve timing of the intake valve 8 or the exhaust valve 9 by causing the cam shafts 4 and 5 to rotate relative to each other in the direction of rotation opposite to the crankshaft 2. Such relative rotation of the camshafts 4 and 5 so that the valve timing of the intake valve 8 or the exhaust valve 9 is delayed is called "retarding".

(First Embodiment)
As shown in FIG. 2, the speed reducing device 151 includes a driving rotating body 20, a driven rotating body 30, a plurality of planetary rotating bodies 40, an input rotating body 60, a control unit 70, a pressurized rotating body 80, and a "biased portion". The spring 85 is provided.

The drive rotating body 20 has a container shape in which a bottomed cylindrical drive internal gear portion 21 and a bottomed cylindrical sprocket portion 22 are coaxially combined, a space is formed inside, and the drive rotating body 20 can rotate about the rotation axis O. Is formed in.
Further, the drive rotating body 20 is provided coaxially with one cam shaft 4 or the other cam shaft 5.

The drive internal gear portion 21 is formed so that the tooth tip circle is directed in the radial direction of the drive rotating body 20 from the tooth bottom circle, and includes the first oblique tooth 211.
The first oblique tooth 211 is formed on the inner peripheral wall of the drive internal gear portion 21, and the tooth streaks are twisted in one direction.

The sprocket portion 22 is fitted to the drive internal gear portion 21 by a screw 27, and the drive internal gear portion 21 and the sprocket portion 22 are coupled.
The sprocket portion 22 has a receiving portion 23 and a plurality of sprocket teeth 29.

As shown in FIG. 3, the receiving portion 23 extends from the radial outer side of the drive rotating body 20 to the radial inner side, and drives and rotates so as to be able to come into contact with the pawl portion 32 of the driven rotating body 30 in the circumferential direction. It is formed on the inner wall 222 of the body 20.
The plurality of sprocket teeth 29 are provided on the outer peripheral wall of the sprocket portion 22. The chain 7 is wound around the plurality of sprocket teeth 29, and the torque Tc output from the crankshaft 2 is input to the sprocket portion 22 via the chain 7. When the torque Tc is input, the drive rotating body 20 rotates around the rotating shaft O in conjunction with the crankshaft 2. At this time, the rotation direction of the drive rotating body 20 is the clockwise direction of FIG. 1 in the present embodiment.

Returning to FIG. 2, most of the driven rotating body 30 is housed in the driving rotating body 20 on the sprocket portion 22 side coaxially with the driving rotating body 20 and is formed in a bottomed cylindrical shape, and the sleeve bolt 37 is inserted. It has a central hole 38 to be formed in the center.
Further, the driven rotating body 30 is sandwiched between the sleeve bolt 37 and the cam shafts 4 and 5, and is connected and fixed to one cam shaft 4 or the other cam shaft 5, and is interlocked with the cam shafts 4 and 5. It can rotate around the rotation axis O.
Further, the driven rotating body 30 is rotatable relative to the driving rotating body 20 and has a driven internal gear portion 31 and a pawl portion 32.

The driven internal gear portion 31 is formed so that the tooth tip circle is directed in the radial direction of the driven rotating body 30 from the tooth bottom circle, and includes the second oblique tooth 311.
The second oblique tooth 311 is formed on the inner peripheral wall of the driven internal gear portion 31, and the tooth streaks are twisted like the first oblique tooth 211.

Returning to FIG. 3 again, the pawl portion 32 extends from the radial inner side of the driven rotating body 30 to the radial outer side, and is formed on the outer wall 322 of the driven rotating body 30.
When the driving rotating body 20 or the driven rotating body 30 rotates, the pawl portion 32 comes into contact with the receiving portion 23 on the contact surface 321.
The contact surface 321 is inclined with respect to the rotation axis O of the driven rotating body 30, and when it comes into contact with the receiving portion 23, the contact surface 321 is in a direction opposite to the force Fs in the direction in which the drive internal gear portion 21 and the driven internal gear portion 31 are attracted to each other. The force Fo is formed to act on the driving rotating body 20.

Returning to FIG. 2 again, the planetary rotating body 40 is housed in contact with the drive internal gear portion 21 and the driven rotating body 30, and is housed between the drive internal gear portion 21 and the input rotating body 60, and the sprocket portion. Three are provided in the circumferential direction between the 22 and the pressurized rotating body 80.
The planetary rotating body 40 is formed so as to be capable of planetary motion, and when the planetary rotating body moves, the relative rotation phase between the driving rotating body 20 and the driven rotating body 30 is changed to rotate the driving rotating body 20 or the driven rotating body 30. Accelerate or decelerate.
Further, the planetary rotating body 40 has a driving side planetary external gear portion 41 and a driven side planetary external gear portion 42.

The drive-side planetary external gear portion 41 is fitted with the drive internal gear portion 21, and is formed so that the tooth tip circle is directed outward in the radial direction of the planetary rotating body 40 from the tooth bottom circle, and the third oblique tooth. Includes 411.
The third oblique tooth 411 is formed on the outer peripheral wall of the drive-side planetary external gear portion 41, and the tooth streaks are twisted like the first oblique tooth 211 and the second oblique tooth 311.

The driven side planetary external gear portion 42 is fitted with the driven internal gear portion 31, and is formed so that the tooth tip circle is directed outward in the radial direction of the planetary rotating body 40 from the tooth bottom circle, and the fourth oblique tooth 421 is included.
The fourth oblique tooth 421 is formed on the outer peripheral wall of the driven side planetary external gear portion 42, and the tooth streaks are twisted like the third oblique tooth 411.

The input rotating body 60 is formed in a cylindrical shape and is formed so as to be rotatable in contact with the planetary rotating body 40 on the drive internal gear portion 21 side. When the input rotating body 60 rotates, the planetary rotating body 40 becomes a planet. Exercise.
Further, the input rotating body 60 has an input external gear portion 61, an extension portion 62, and a motor connecting portion 63.

As shown in FIG. 4, the input external gear portion 61 is provided on the drive internal gear portion 21 side and is fitted to the drive side planetary external gear portion 41, and the tooth tip circle is from the tooth bottom circle to the input rotating body 60. It is formed so as to be radially outwardly, and includes a fifth oblique tooth 611.
The fifth oblique tooth 611 is formed on the outer peripheral wall of the input external gear portion 61, and is formed so that the tooth streaks are twisted. The fourth oblique tooth 421 is twisted in the direction opposite to the twisting direction.

The extension portion 62 extends from the drive internal gear portion 21 toward the sprocket portion 22, and the outer peripheral wall is fitted with the inner peripheral wall of the pressurized rotating body 80. A large number of grooves are formed on the outer wall of the extension portion 62 so that the input rotating body 60 and the pressurized rotating body 80 are freely displaced in the axial direction and the relative rotation is prevented.
The motor connection portion 63 is a groove to which the motor shaft 74 of the control unit 70 is connected.

Returning to FIG. 2, the control unit 70 is composed of an electric motor 71 and a control circuit 72.
The electric motor 71 is, for example, a permanent magnet type synchronous three-phase AC motor, which is provided on the side opposite to the cam shafts 4 and 5 with the driven rotating body 30 and the input rotating body 60 interposed therebetween. It is housed in 73 and has a motor shaft 74.
The motor shaft 74 is supported by the motor case 73 so as to be rotatable forward and reverse, and is connected to the input rotating body 60 via the motor connecting portion 63.

The control circuit 72 is mainly composed of a microcomputer, and includes a CPU, a readable non-temporary tangible recording medium, a ROM, I / O, a bus line connecting these configurations, and the like. Further, the control circuit 72 is provided outside or inside the motor case 73. The processing in the control circuit 72 may be software processing by executing a program stored in advance in a physical memory device such as ROM by the CPU, or hardware processing by a dedicated electronic circuit. ..

The control circuit 72 is connected to the electric motor 71 and controls the electric motor 71 according to the operating state of the internal combustion engine 1. The controlled electric motor 71 generates a rotating magnetic field around the motor shaft 74, and outputs a rotational torque Tm from the motor shaft 74 in the advance direction X or the retard direction Y according to the direction of the rotating magnetic field. When the rotation torque Tm is output, the input rotating body 60 rotates in the forward and reverse directions.

The pressurized rotating body 80 is formed in a cylindrical shape, accommodates the extension portion 62 inside, is in contact with the planetary rotating body 40 on the sprocket portion 22 side, and is rotatably formed together with the planetary rotating body 40. It has a compression external gear portion 81.
The pressurized external gear portion 81 is provided on the sprocket portion 22 side and is fitted to the driven side planetary external gear portion 42 so that the tooth tip circle is directed outward in the radial direction of the pressurized rotating body 80 from the tooth bottom circle. It is formed in and includes the sixth oblique tooth 811.

The sixth oblique tooth 811 is formed on the outer peripheral wall of the pressurized external gear portion 81, and the tooth streaks are twisted in the same direction as the twisting direction of the fifth oblique tooth 611. The twisting direction is, for example, a right twist if the teeth are upward to the right and a left twist if the teeth are upward to the left when the central axis of the gear is directed to the top and bottom. Here, "same" includes a common sense error range. In the present specification, "identical" shall be broadly interpreted in the same manner.

As shown in FIGS. 5 and 6, the input rotating body 60 acts an axial force Fa1 of the planetary rotating body 40 on the drive-side planetary external gear portion 41.
Further, the pressurized rotating body 80 acts on the driven side planetary external gear portion 42 with a force Fa2 acting in the axial direction of the planetary rotating body 40.

The force Fa1 and the force Fa2 are forces acting in the direction in which the axial distance from the fifth oblique tooth 611 to the sixth oblique tooth 811 changes. Further, the force Fa1 and the force Fa2 are converted into a force Fr in the direction in which the planetary rotating body 40 is pressed against the drive internal gear portion 21 or the driven internal gear portion 31 by the third oblique tooth 411 and the fourth oblique tooth 421. The input rotating body 60 and the pressurized rotating body 80 act on the planetary rotating body 40 with the converted force Fr.
Further, the planetary rotating body 40 acts on the driven rotating body 30 with a force Fs acting in the axial direction of the driven rotating body 30.

The force Fr is a force acting in the direction from the radial inner side to the radial outer side of the planetary rotating body 40.
The force Fs is a force acting in the axial direction of the driven rotating body 30, and the acting direction is reversed depending on the direction of the torque transmitted between the cam shaft 4 and the sprocket portion 22. Further, the force Fs is an axial force that attracts the drive internal gear portion 21 and the driven internal gear portion 31 when the planetary rotating body 40 makes a planetary motion in the direction in which the rotational force of the driven rotating body 30 increases. .. Here, the direction in which the rotational force of the driven rotating body 30 in the speed reducing device 151 increases is the retarding direction Y, which is opposite to the rotational direction of the internal combustion engine 1.
The twisting directions of the oblique teeth 211, 311, 411, 421, 611, and 811 are set so that the force Fr and the force Fs act in such a direction.

The spring 85 is formed of an elastic member such as a spring, and is provided between the input external gear portion 61 and the pressurized external gear portion 81. The axial distance from the input external gear portion 61 to the pressurized external gear portion 81 is defined as the thrust distance L.
The spring 85 urges the input external gear portion 61 and the pressurized external gear portion 81 in the direction in which the thrust distance L changes.

As shown in FIG. 7, in the drive internal gear portion 21 and the driven internal gear portion 31, the twist angle of the first oblique tooth 211 is set to the drive twist angle β1, and the twist angle of the second oblique tooth 311 is set to the drive twist angle β2. ..
The twist angles β1 and β2 are angles at which the first oblique tooth 211 and the second oblique tooth 311 are inclined with respect to the axes of the driving rotating body 20 and the driven rotating body 30.

The drive internal gear portion 21 or the driven internal gear portion 31 is formed so that the drive twist angle β1 is larger than the drive twist angle β2, that is, β1> β2. In FIG. 2, FIG. 5, FIG. 7, FIG. 8, FIG. 9, FIG. 11 and FIG. 12, the twists of the first oblique tooth 211 and the second oblique tooth 311 are exaggeratedly described in order to clarify the twist angle. There is.

The number of teeth of the first oblique tooth 211 is defined as the number of first teeth z1, the number of teeth of the second oblique tooth 311 is defined as the number of second teeth z2, and the number of teeth of the third oblique tooth 411 is defined as the number of third teeth z3. The number of teeth of the fourth oblique tooth 421 is defined as the number of fourth teeth z4, the number of teeth of the fifth oblique tooth 611 is defined as the number of fifth teeth z5, and the number of teeth of the sixth oblique tooth 811 is defined as the number of sixth teeth z6.

The ratio of the fifth tooth number z5 to the third tooth number z3 is the ratio z5 / z3, and the ratio of the sixth tooth number z6 to the fourth tooth number z4 is the ratio z6 / z4.
The planetary rotating body 40, the input rotating body 60, and the pressurized rotating body 80 are formed so that the ratio z5 / z3 becomes equal to the ratio z6 / z4, that is, the following relational expression (1) is obtained. Here, "equally" includes a common-sense error range. In the present specification, "equal" and "equal" are to be broadly interpreted in the same manner.
z5 / z3 = z6 / z4 ... (1)

Further, the ratio of the fifth tooth number z5 to the first tooth number z1 is defined as the ratio z5 / z1, and the ratio of the sixth tooth number z6 to the second tooth number z2 is defined as the ratio z6 / z2.
The drive rotating body 20, the driven rotating body 30, the input rotating body 60, and the pressurized rotating body 80 are formed so that the ratio z5 / z1 is different from the ratio z6 / z2, that is, the following relational expression (2). ing.
z5 / z1 ≠ z6 / z2 ... (2)

(Action)
The operation of the speed reducer 151 of the present embodiment will be described.
When the motor shaft 74 does not rotate relative to the drive rotating body 20, the input rotating body 60 and the pressurized rotating body 80 maintain the meshing position with the planetary rotating body 40, and the planetary rotating body 40 meshes with the driving rotating body 20. While maintaining the position, it rotates together with the driving rotating body 20 and the driven rotating body 30.
At this time, the relative rotation phase between the drive rotating body 20 and the driven rotating body 30 is maintained, so that the valve timing is maintained.

When the motor shaft 74 rotates relative to the drive rotating body 20 in the advance direction X, a rotation torque Tm is generated from the motor shaft 74 in the advance direction X. At this time, the input rotating body 60 rotates relative to the driving rotating body 20 in the advance direction X, and the planetary rotating body 40 makes a planetary motion while changing the meshing position between the driving rotating body 20 and the planetary rotating body 40. .. As the planetary rotating body 40 makes a planetary motion, the driven rotating body 30 rotates relative to the driving rotating body 20 in the advance direction X. The rotation speed of the driven rotating body 30 is accelerated, and the valve timing of the intake valve 8 or the exhaust valve 9 is accelerated.

When the motor shaft 74 rotates relative to the drive rotating body 20 in the retard direction Y, a rotational torque Tm is generated from the motor shaft 74 in the retard direction Y. At this time, the input rotating body 60 rotates relative to the driving rotating body 20 in the retard direction Y, and the planetary rotating body 40 makes a planetary motion while changing the meshing position between the driving rotating body 20 and the planetary rotating body 40. .. As the planetary rotating body 40 makes a planetary motion, the driven rotating body 30 rotates relative to the driving rotating body 20 in the retard direction Y. The rotation speed of the driven rotating body 30 is reduced, and the valve timing of the intake valve 8 or the exhaust valve 9 is delayed.

In this way, when the planetary rotating body 40 and the input rotating body 60 are rotatably connected to each other and the rotation torque Tm is output from the motor shaft 74 and the input rotating body 60 rotates relative to the driving rotating body 20. The planetary rotating body 40 makes a planetary motion. The relative rotation phase of the driving rotating body 20 and the driven rotating body 30 is changed by the planetary motion of the planetary rotating body 40. When the relative rotation phase is changed, the rotation speed of the driven rotating body 30 is accelerated or decelerated, and the valve timing of the intake valve 8 or the exhaust valve 9 is adjusted.

Conventionally, there is known a speed reducer that changes the relative rotation phase between a driving rotating body and a driven rotating body by causing the planetary rotating body to make a planetary motion with respect to the driving rotating body.
Generally, when two gears rotate and mesh with each other, a force acting in a direction in which the two gears separate in the direction perpendicular to the axis is applied to the two gears.

In the configuration of Patent Document 1, in order to press the outer teeth of the planetary rotating body against the internal teeth of the driving rotating body and the driven rotating body, the urging member that urges the planetary rotating body radially outward of the planetary rotating body rotates the planet. It is provided inside the body. The urging member complicates the structure of the speed reducer, increases the number of parts, and increases the cost. If there is no urging member, vibration or noise may occur due to the contact between the internal and external teeth. Further, as described in US Pat. No. 5,680,836, all gears are provided with pressurizing springs, which complicates the structure of the speed reducer. Further, the pressurizing spring increases the frictional force on the sliding surface and lowers the operating efficiency of the reduction gear.
Therefore, in the present embodiment, a speed reducer that suppresses the generation of vibration and noise and improves the operation efficiency with a simple configuration is provided.

(effect)
[1] In the reduction gear 151 of the present embodiment, the fifth oblique tooth 611 and the sixth oblique tooth 811 are provided, and the forces Fa1 and Fa2 are applied to the driven side planetary external gear portion 42 and the driving side planetary external gear portion 41. It works. The forces Fa1 and Fa2 are converted into a force Fr by the third oblique tooth 411 and the fourth oblique tooth 421.

The force Fr can be expressed, for example, by the following relational expression (3). P is the magnitude of the forces Fa1 and Fa2. α3 is the gear pressure angle of the third oblique tooth 411, and extends in the radial direction of the planetary rotating body 40 or the input rotating body 60 with the common tangent of the surface where the third oblique tooth 411 and the fifth oblique tooth 611 come into contact with each other. The angle between the radius line and the radius line. Further, α4 is a gear pressure angle of the fourth oblique tooth 421, and is a common tangent line of the surface where the fourth oblique tooth 421 and the sixth oblique tooth 811 come into contact with each other, and the diameter of the planetary rotating body 40 or the pressurized rotating body 80. It is the angle formed by the radius line extending in the direction. β3 is the twist angle of the third oblique tooth 411, β4 is the twist angle of the fourth oblique tooth 421, and the third oblique tooth 411 and the fourth oblique tooth 421 are inclined with respect to the axis of the planetary rotating body 40. The angle.
Fr = (P × tanβ3) × tanα3 + (P × tanβ4) × tanα4
... (3)

Since the planetary rotating body 40 is directly pressed against the driving rotating body 20 and the driven rotating body 30 by the force Fr in the radial direction, it is not necessary to provide an urging member. It is not necessary to provide a pressurizing spring, the frictional force on the sliding surface is reduced, and the operating efficiency of the speed reducer 151 is improved.
Further, the gap between the drive internal gear portion 21 or the driven internal gear portion 31 and the planetary rotating body 40 becomes small, and vibration or noise due to tooth contact between the drive internal gear portion 21 or the driven internal gear portion 31 and the planetary rotating body 40 is generated. It is suppressed.

[2] The first oblique tooth 211, the second oblique tooth 311 and the third oblique tooth 411 and the fourth oblique tooth 421 are twisted in one direction. Further, the fifth oblique tooth 611 and the sixth oblique tooth 811 are twisted in a direction opposite to the twisting direction of the first oblique tooth 211, the second oblique tooth 311 and the third oblique tooth 411 and the fourth oblique tooth 421.
Further, the driving rotating body 20, the driven rotating body 30, the input rotating body 60 and the pressurized rotating body 80 are formed so that the ratio z5 / z3 and the ratio z6 / z4 are equal to each other.
With this setting, when the input rotating body 60 rotates, the planetary rotating body 40 can rotate without the need for relative rotation between the input rotating body 60 and the pressurized rotating body 80.

[3] The spring 85 urges the input external gear portion 61 and the pressurized external gear portion 81 in the direction in which the thrust distance L changes. The urging force of the spring 85 is decomposed into Fr by the third oblique tooth 411. The planetary rotating body 40 is easily pressed against the drive internal gear portion 21 or the driven internal gear portion 31, and vibration or noise is easily suppressed.

[4] Three planetary rotating bodies 40 are provided in the circumferential direction between the drive internal gear portion 21 and the input rotating body 60 and between the sprocket portion 22 and the pressurized rotating body 80. As a result, the outer center of the triangle formed by connecting the centers of the three planetary rotating bodies 40 is automatically centered so as to be the center of the input rotating body 60 and the pressurized rotating body 80. Therefore, the load applied to the planetary rotating body 40 is easily distributed evenly, and the durability of the planetary rotating body 40 is improved.

[5] Since the drive twist angle β1 is larger than the driven twist angle β2, the force Fr converted by the third oblique tooth 411 is always in the direction in which the input rotating body 60 presses the planetary rotating body 40 against the driving rotating body 20. It works. Therefore, the input rotating body 60, the planet rotating body 40, and the driving rotating body 20 are in constant contact with each other, the operation of the speed reducing device 151 is stable, and the generation of wear or noise due to the rampage can be suppressed.
Further, of both end faces of the input rotating body 60 in the axial direction, the end faces of the input rotating body 60 on the driven rotating body 30 side come into contact with the driven rotating body 30. Therefore, the shape of the end face in the axial direction of the input rotating body 60 on the side opposite to the driven rotating body 30 is not particularly restricted, and the cost can be reduced by reducing the processing cost such as surface roughness.

[6] When the planetary rotating body 40 makes a planetary motion in a direction in which the rotational force of the driven rotating body 30 increases, the planetary rotating body 40 exerts a force Fs on the driven rotating body 30, and the oblique teeth 211, 311 and so on. The twisting directions of 411, 611, and 811 are set. By the force Fs, the force for fitting the drive internal gear portion 21 and the sprocket portion 22 can be reduced. In the present embodiment, the drive internal gear portion 21 and the sprocket portion 22 are fitted by the screw 27, and the fitting force by the screw 27 can be reduced. Therefore, the screw 27 can be reduced, and the speed reducing device 151 can be used. Can be miniaturized.

[7] As shown in FIG. 8, when the pawl portion 32 comes into contact with the receiving portion 23, the contact surface 321 is formed so as to be inclined with respect to the rotation axis O so that a force Fo acting in a direction opposite to the force Fs acts. ing. When the planetary rotating body 40 makes a planetary motion, a force Fs is generated. The force Fs may become excessive due to the rotational force of the planetary rotating body 40, and the drive internal gear portion 21 and the sprocket portion 22 may be damaged. In this case, it is suppressed that the force Fs becomes excessive due to the force Fo, and the damage between the drive internal gear portion 21 and the sprocket portion 22 is prevented.

(Second Embodiment)
The second embodiment is the same as the first embodiment except that a return spring is added.
As shown in FIGS. 9 and 10, the speed reducer 152 of the second embodiment further includes a return spring 86.

The return spring 86 is formed of a leaf spring, is wound around the cam shafts 4 and 5, is provided on the sprocket portion 22 side so as to sandwich the cam shafts 4 and 5. The end surface 123 of the sprocket portion 122 is provided with an insertion hole 88 into which an engaging member 87 that engages with the return spring 86 is inserted.
The return spring 86 engages with the engaging member 87 and urges the drive rotating body 20 in the circumferential direction, and in the speed reducing device 152 of the second embodiment, the return spring 86 is urged in the advance direction X.

In the speed reducing device 152 of the second embodiment, in addition to achieving the same effect as that of the first embodiment, the return spring 86 prevents a sudden load on the driving rotating body 20 and the driven rotating body 30, and the driven rotating body 30 is prevented from being suddenly loaded. It is suppressed that the rotation speed of 30 is excessively accelerated or decelerated. As a result, the drive rotating body 20 and the driven rotating body 30 are less likely to be damaged.

When used in the valve timing adjusting device 10 when the power is off, the speed reducing device 152 is set so that the urging direction by the return spring 86 and the advance angle direction X operate in the same direction. Further, when the valve timing adjusting device 10 advances, the oblique teeth 211, 311, 411, 421, 611 act so that the force Fs acts in the direction in which the drive internal gear portion 21 and the driven internal gear portion 31 are attracted to each other. , 811 twist direction is set. By setting in this way, even when the valve timing adjusting device 10 advances, the excessive load is alleviated inside the speed reducing device 152. As a result, the fitting force of the screw 27 can be reduced, so that the screw 27 can be made smaller and the speed reducer 152 can be made smaller.

(Third Embodiment)
The third embodiment is the same as the first embodiment except that a communication hole is added to the driven rotating body.
As shown in FIG. 11, the driven rotating body 130 of the speed reducing device 153 of the third embodiment further has a communication hole 33.

The communication hole 33 penetrates in the axial direction and is provided so as to be aligned with the input external gear portion 61, the pressurized external gear portion 81, and the spring 85 in the same straight line.
Through the communication hole 33, the pressurized external gear portion 81 is pressurized in the direction of reducing the thrust distance L, and the pressurized portion 34 capable of pressurizing from the outside in the direction of contracting the spring 85 is the end face of the pressurized external gear portion 81. Is formed in.

In the third embodiment, the same effect as that of the first embodiment is obtained. In the third embodiment, since the spring 85 can be further contracted through the communication hole 33, it can be assembled in a state where the fixing between the rotating bodies 20, 40, 60, 80, and 130 is loosened. Therefore, assembly becomes easy. Further, after assembly, the spring 85 is pressurized through the communication hole 33 and the pressurizing portion 34 to enable fine adjustment.

(Fourth Embodiment)
The fourth embodiment is the same as the first embodiment except that the ends of the driving rotating body, the driven rotating body, and the planetary rotating body have a tapered shape.
As shown in FIGS. 12 and 13, the axial cross sections of the drive rotating body 220, the driven rotating body 230, and the planetary rotating body 240 of the speed reducing device 154 of the fourth embodiment are the axes. It is formed so as to incline with respect to the direction.

The end portion 221 of the drive rotating body 220 is a surface that is inside the drive internal gear portion 21 and faces the driven rotating body 230, and is formed in a tapered shape that is inclined in a direction in which the inner diameter is reduced.
The end portion 231 of the driven rotating body 230 is a surface facing the end portion 221 of the driving rotating body 220 on the drive internal gear portion 21 side, and is formed in a tapered shape inclined in a direction in which the inner diameter is reduced.

The end 241 of the planetary rotating body 240 on the driving side planetary external gear 41 side and the end 242 of the planetary rotating body 240 on the driven side planetary external gear 42 side are formed in a tapered shape inclined in the direction of reducing the outer diameter. Has been done.
In FIGS. 12 and 13, the tapered shapes of the ends 221 and 231, 241 and 242 are exaggerated for the sake of clarity. The dimensions, angles or dimensional ratios of the tapered shapes of the ends 221, 231, 241, 242 are not always accurate.

In the fourth embodiment, the same effect as that of the first embodiment is obtained. Further, in the fourth embodiment, since the ends 221, 231 and 241 have a tapered shape, the planetary rotating body 240 can be easily inserted at the time of assembly, which makes it easy to assemble.

(Fifth Embodiment)
The fifth embodiment is the same as the first embodiment except that the forms of the driving rotating body, the driven rotating body, the planetary rotating body, the input rotating body and the pressurized rotating body are different.
As shown in FIG. 14, the drive rotating body 520 of the speed reducer 155 of the fifth embodiment further has a drive recess 521.

The drive recess 521 is formed on the drive facing end surface 522, which is the end surface of the drive rotating body 520 facing the drive side planetary external gear portion 541, and is recessed from the inside in the axial direction to the outside in the axial direction of the drive rotating body 520. There is.
Further, the drive recess 521 is formed in a tapered shape that is inclined in a direction in which the diameter of the drive facing end surface 522 decreases from the inside in the axial direction of the drive rotating body 520 toward the outside in the axial direction.
Further, the drive recess 521 is formed symmetrically with respect to the axis of the drive rotating body 520. The drive recess 521 may be formed asymmetrically with respect to the axis of the drive rotating body 520.

The driven rotating body 530 further has a driven recess 531.
The driven recess 531 is formed on the driven facing end surface 532, which is the end face of the driven rotating body 530 facing the driven side planetary external gear portion 542, and is recessed from the inside in the axial direction to the outside in the axial direction of the driven rotating body 530. It is formed in the same manner as the drive recess 521.
Further, the driven recess 531 is formed in a tapered shape that is inclined in a direction in which the diameter of the driven facing end surface 532 is reduced from the inside in the axial direction to the outside in the axial direction of the driven rotating body 530.
Further, the driven recess 531 is formed symmetrically with respect to the axis of the driven rotating body 530.

As shown in FIG. 15, the planetary rotating body 540 further includes a driving side convex portion 543, a driven side convex portion 544, and a planetary groove portion 547. In FIG. 15, the driving side convex portion 543 and the driven side convex portion 544 are exaggerated so as to clarify the driving side convex portion 543 and the driven side convex portion 544.

The drive-side convex portion 543 is formed on the drive-side planet end surface 545, which is the end surface of the drive-side planetary external gear portion 541 facing the drive-side rotating body 520, and faces from the axially inner side to the axially outer side of the planetary rotating body 540. Is extending.
The drive-side convex portion 543 extends from the drive-side planetary end surface 545 toward the drive-rotating body 520 and comes into contact with the drive-side rotating body 520.

Further, the outer edge of the drive-side convex portion 543 in the radial cross section of the planetary rotating body 540 is curved.
Further, the drive-side convex portion 543 is formed in a spherical shape, and is formed symmetrically with respect to the axis of the planetary rotating body 540.

The driven side convex portion 544 is formed in the same manner as the drive side convex portion 543. The driven-side convex portion 544 is formed on the driven-side planetary end surface 546, which is the end surface of the driven-side planetary external gear portion 542 facing the driven rotating body 530, and faces from the axially inner side to the axially outer side of the planetary rotating body 540. Is extending.
The driven side convex portion 544 extends from the driven side planet end surface 546 toward the driven rotating body 530 and comes into contact with the driven rotating body 530.

Further, the driven side convex portion 544 has a curved outer edge in the radial cross section of the planetary rotating body 540.
Further, the driven side convex portion 544 is formed in a spherical shape, and is formed symmetrically with respect to the axis of the planetary rotating body 540.

The planetary groove portion 547 is formed between the driving side planetary external gear portion 541 and the driven side planetary external gear portion 542, and is recessed from the radial outer side to the radial inner side of the planetary rotating body 540.
Further, the planetary groove portion 547 is formed in an annular shape. The diameter of the planetary groove portion 547 is formed so as to be smaller than the diameter of the driving side planetary external gear portion 541 and the diameter of the driven side planetary external gear portion 542.

The spring 85 acts on the planetary rotating body by the force for urging the pressurized rotating body 80, and the rotational force about the diameter of the planetary rotating body 540 is defined as the urging force moment Ms. The drive internal gear portion 21 or the driven internal gear portion 31 acts on the planetary rotating body 540, and the rotational force about the diameter of the planetary rotating body 540 is defined as the rotational force moment Mr.
The twisting directions of the oblique teeth 211, 311, 411, 421, 611, and 811 are set so that the direction of the urging force moment Ms and the direction of the rotational force moment Mr are the same.

As shown in FIG. 16, the diameter of the pitch circle C1 of the drive internal gear portion 21 when the drive internal gear portion 21 and the drive side planetary external gear portion 541 mesh with each other is defined as the first diameter dw1. Alternatively, the diameter of the pitch circle C1 of the driven internal gear portion 31 when the driven internal gear portion 31 and the driven side planetary external gear portion 542 mesh with each other is set to the first diameter dw1. The diameter of the pitch circle C2 of the input external gear portion 61 when the input external gear portion 561 and the drive-side planetary external gear portion 541 mesh with each other is defined as the second diameter dw2. Alternatively, the diameter of the pitch circle C2 of the pressurized external gear portion 81 when the pressurized external gear portion 81 and the driven side planetary external gear portion 542 mesh with each other is set to the second diameter dw2. The pitch circle is a circle drawn by the contact points of two meshing gears.

As shown in FIG. 17, the diameter of the pitch circle C3 of the drive-side planetary external gear portion 541 on the driven rotating body 530 side when the planetary rotating body 540 rotates is defined as the third diameter dw3. The diameter of the pitch circle C4 of the drive-side planetary external gear portion 541 on the drive-side rotating body 520 side when the planet-rotating body 540 rotates is defined as the fourth diameter dw4. The axial length of the drive-side planetary external gear portion 541 is defined as the drive-side distance Ld. The diameter of the pitch circle C5 of the driven side planetary external gear portion 42 on the drive rotating body 520 side when the planetary rotating body 540 rotates is defined as the fifth diameter dw5. The diameter of the pitch circle C6 of the driven side planetary external gear portion 542 on the driven rotating body 30 side when the planetary rotating body 540 rotates is defined as the sixth diameter dw6. The axial length of the driven side planetary external gear portion 542 is defined as the driven side distance Lf.

The drive-side planetary external gear portion 541 is formed so that the third diameter dw3 is larger than the fourth diameter dw4, that is, dw3> dw4. Further, the drive-side planetary external gear portion 541 is formed with a drive-side slope 551 so that the diameter increases from the drive rotating body 520 toward the driven rotating body 530. The angle at which the drive-side slope 551 is tilted with respect to the axis of the planetary rotating body 540 is defined as the drive-side tilt angle θd.

The driven side planetary external gear portion 542 is formed so that the fifth diameter dw5 is larger than the sixth diameter dw6, that is, dw5> dw6.
Further, the driven side planetary external gear portion 542 is formed with a driven side slope 552 so that the diameter increases from the driven rotating body 530 toward the driving rotating body 520. The angle at which the driven side slope 552 is tilted with respect to the axis of the planetary rotating body 540 is defined as the driven side tilt angle θf.

As shown in FIG. 18, the drive-side planetary external gear portion 541 is formed by crowning the third oblique tooth 411. Crowning is one of tooth profile modification, and is a process of making a bulge in the direction of tooth streaks. Similarly, the driven side planetary external gear portion 542 is formed by crowning the fourth oblique tooth 421.

As shown in FIG. 19, the angle at which the planetary rotating body 540 is tilted with respect to the axis of the driving rotating body 520 or the driven rotating body 530 when the planetary rotating body 540 is tilted is defined as the planetary tilt angle θ. Let x be the amount of movement of the drive-side planetary external gear portion 541 when the planetary rotating body 540 is tilted. The amount of movement x corresponds to the length of an arc having the drive side distance Ld as the radius and the planetary inclination angle θ as the central angle. Let y be the amount of movement of the driven side planetary external gear portion 542 when the planetary rotating body 540 is tilted. The amount of movement y corresponds to the length of an arc having the driven side distance Lf as the radius and the planetary inclination angle θ as the central angle. Since the movement amount x and the movement amount y are minute, they can be linearly approximated. In FIG. 19, the planetary inclination angle θ is exaggerated in order to clarify the planetary inclination angle θ. In reality, as will be described later, the speed reducer 155 is configured so that the planetary rotating body 540 does not tilt.

The drive-side planetary external gear portion 541 is formed so as to satisfy the following relational expressions (4.1)-(4.4).

The driven side planetary external gear portion 542 is formed so as to satisfy the following relational expressions (5.1)-(5.4).

As shown in FIG. 20, the extension portion 562 of the input rotating body 560 includes a plurality of extension portion external teeth 563.
The extension portion 562 is formed in a spiral shape.
The extension outer teeth 563 have twisted tooth streaks and are formed on the outer wall of the extension 562.
The pressurized rotating body 580 includes a pressurized internal tooth 581.
The pressurized internal teeth 581 have twisted tooth streaks and are formed on the inner wall of the pressurized rotating body 580. The extension external tooth 563 and the pressurized internal tooth 581 are fitted.

The number of teeth of the extension external tooth 563 is defined as the number of extension external teeth ze. The number of pressurized internal teeth 581 is defined as the number of pressurized internal teeth zp.
The number of external teeth ze of the extension portion and the number of internal teeth zp under pressure are set so that the value when divided by the prime factor of the fifth tooth number z5 or the prime factor of the sixth tooth number z6 is 2 or more. The prime factor is a prime number that is a divisor of a certain natural number. For example, the prime factors of 60 are 2, 3, and 5.

As shown in FIG. 21, the fifth tooth number z5 is set to 5, and the sixth tooth number z6 is set to 6. Further, the number of external teeth ze of the extension portion and the number of internal teeth of pressurization zp are set to 6, 4, and 60. The prime factor of the fifth tooth number z5 is 5. The prime factors of the sixth tooth number z6 are two or three.
When the number of extension external teeth ze and the number of pressurized internal teeth zp are 6, the number of extension external teeth ze and the number of pressurized internal teeth zp cannot be divided by 5. At this time, the number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization can be divided by 2 and 3, which are prime factors of the 6th number of teeth z6. The value when the number of external teeth ze of the extension portion and the number of internal teeth zp under pressure are divided by 2 and 3 is 1. As described above, the number of external teeth ze of the extension portion and the number of internal teeth of pressurization zp are not set.

When the number of extension external teeth ze and the number of pressurized internal teeth zp are 4, the number of extension external teeth ze and the number of pressurized internal teeth zp cannot be divided by 5 and 3. At this time, the number of external teeth ze of the extension portion and the number of internal teeth of pressurization zp can be divided by two. The value when the number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization are divided by 2 is 2. In this way, the number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization are set.

When the number of extension external teeth ze and the number of pressurized internal teeth zp are 60, the number of extension external teeth ze and the number of pressurized internal teeth zp can be divided by 2, 3 and 5. At this time, the value when the number of external teeth ze of the extension portion and the number of internal teeth zp under pressure are divided by 2, 3 and 5 is 2. In this way, the number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization are set.

Let the fifth tooth number z5 be 5, and the sixth tooth number z6 be 5. Further, the number of external teeth ze of the extension portion and the number of internal teeth of pressurization zp are set to 5, 25, and 6. The prime factor of the fifth tooth number z5 and the prime factor of the sixth tooth number z6 are only 5.
When the number of external teeth of the extension portion and the number of internal teeth of pressurization zp are 5, the number of external teeth of the extension portion and the number of internal teeth of pressurization zp can be divided by 5. The value when the number of external teeth ze of the extension portion and the number of internal teeth zp under pressure are divided by 5 is 1. As described above, the number of external teeth ze of the extension portion and the number of internal teeth of pressurization zp are not set.

When the number of extension external teeth ze and the number of pressurized internal teeth zp are 25, the number of extension external teeth ze and the number of pressurized internal teeth zp can be divided by 5. The value when the number of external teeth ze of the extension portion and the number of internal teeth zp under pressure are divided by 5 is 5. When the prime factors of the fifth tooth number z5 and the sixth tooth number z6 have a common number, the common number shall be divided only once. In this way, the number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization are set.

When the number of extension external teeth ze and the number of pressurized internal teeth zp are 6, the number of extension external teeth ze and the number of pressurized internal teeth zp cannot be divided by 5. At this time, the value obtained by dividing the number of extension outer teeth ze and the number of pressurized internal teeth zp by the prime factor of the fifth number of teeth z5 or the number of sixth teeth z6 is divided by the number of extension outer teeth ze and the number of pressurized internal teeth z6. Let it be the value of zp. That is, it is 6. In this way, the number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization are set.

The fifth tooth number z5 is 42, and the sixth tooth number z6 is 33. Further, the number of external teeth ze of the extension portion and the number of internal teeth of pressurization zp are set to 6, 8 and 56. The prime factors of the fifth tooth number z5 are 2, 3, and 7. The prime factors of the sixth tooth number z6 are 3 and 11. At this time, among the prime factors of the fifth tooth number z5 and the sixth tooth number z6, 3 is a common number.
When the number of extension external teeth ze and the number of pressurized internal teeth zp are 6, the number of extension external teeth ze and the number of pressurized internal teeth zp cannot be divided by 7 and 11. At this time, the number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization can be divided by 2 and 3. The value when the number of external teeth ze of the extension portion and the number of internal teeth zp under pressure are divided by 2 and 3 is 1. As described above, the number of external teeth ze of the extension portion and the number of internal teeth of pressurization zp are not set.

When the number of extension external teeth ze and the number of pressurized internal teeth zp are 8, the number of extension external teeth ze and the number of pressurized internal teeth zp cannot be divided by 3, 7, and 11. The number of external teeth ze and the number of pressurized internal teeth zp of the extension can be divided by two. The value when the number of external teeth ze of the extension portion and the number of internal teeth zp under pressure are divided by 2 is 4. In this way, the number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization are set.

When the number of extension external teeth ze and the number of pressurized internal teeth zp are 56, the number of extension external teeth ze and the number of pressurized internal teeth zp cannot be divided by 3 and 11. The number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization can be divided by 2 and 7. The value when the number of external teeth ze of the extension portion and the number of internal teeth zp under pressure are divided by 2 and 7 is 4. In this way, the number of external teeth ze of the extension portion and the number of internal teeth zp of pressurization are set.
The fifth embodiment also has the same effect as that of the first embodiment.

In the planetary rotating body, a moment about the diameter of the planetary rotating body is likely to work. Therefore, the planetary rotating body tends to tilt with respect to the axis of the driving rotating body or the axis of the driven rotating body. When the planetary rotating body tilts with respect to the axis of the driving rotating body or the driven rotating body, the planetary rotating body hits the driving rotating body or the driven rotating body on one side, the frictional force increases, and the rotation of the planetary rotating body is hindered. Be done. Therefore, the operating efficiency of the speed reducer may decrease.

[8] Therefore, in the speed reducing device 155 of the fifth embodiment, the planetary rotating body 540 has a driving side convex portion 543 or a driven side convex portion 544. As a result, even if the planetary rotating body 540 is tilted, the planetary rotating body 540 does not hit the driving rotating body 520 or the driven rotating body 530. Therefore, the frictional force is not increased, the rotation of the planetary rotating body is not hindered, and the operating efficiency of the speed reducing device 155 is improved.

When the planetary rotating body 540 rotates, the drive facing end surface 522 and the drive side planet end surface 545 slide. Further, when the planetary rotating body 540 rotates, the driven facing end surface 532 and the driven side planet end surface 546 slide. On the sliding surface between the planetary rotating body 540 and the driving rotating body 520 or the driven rotating body 530, the radial inner sliding speed of the driving rotating body 520 or the driven rotating body 530 is defined as the inner sliding speed Vi. On the sliding surface between the planetary rotating body 540 and the driving rotating body 520 or the driven rotating body 530, the radial outer sliding speed of the driving rotating body 520 or the driven rotating body 530 is defined as the outer sliding speed Vo.
As shown in FIG. 22, the inner sliding speed Vi is faster than the outer sliding speed Vo. Therefore, the friction loss of torque tends to increase inside the driving rotating body 520 or the driven rotating body 530 in the radial direction. When the friction loss of torque increases, the operating efficiency of the reduction gear decreases.

[9] Therefore, the drive rotating body 520 has a driving recess 521, and the driven rotating body 530 has a driven recess 531. By bringing the contact point between the planetary rotating body 540 and the driving rotating body 520 or the driven rotating body 530 closer to the meshing point, the planetary rotating body 540 is less likely to come into contact with the driving rotating body 520 or the driven rotating body 530 in the radial direction. Become. Therefore, the friction loss of torque is reduced, and the operating efficiency of the reduction gear is improved.

[10] The direction of the urging force moment Ms and the direction of the rotational force moment Mr are the same direction. When rotating in one direction, the operating efficiency of the speed reducer 155 is improved. It is more preferable that the direction of rotation when the valve timing adjusting device 10 advances is the same as the direction of the urging force moment Ms and the direction of the rotational force moment Mr.

[11] The third diameter dw3 is larger than the fourth diameter dw4. Further, the fifth diameter dw5 is larger than the sixth diameter dw6. As a result, the oblique teeth 211, 311, 411, 421, 611, and 811 are less likely to interfere with each other. Therefore, the friction loss is reduced and the operating efficiency of the speed reducer 155 is improved.

[12] The extension portion 562 has a spiral shape. As a result, the pressurized rotating body 580 can move while rotating in the axial direction. Therefore, the planetary rotating body 540 is pushed by the pressurized rotating body 580, and the planetary rotating body 540 moves radially outward of the planetary rotating body 540. The planetary rotating body 540 is pressed by the driven rotating body 530, and the backlash between the driving rotating body 520 or the driven rotating body 530 and the planetary rotating body 540 becomes zero. This prevents the planetary rotating body 540 from tilting with respect to the axis of the driven rotating body 530.

[13] The space occupied by the spring 85 is increased by the planetary groove portion 547. This increases the degree of freedom in designing the urging section. When the space that the spring 85 can occupy becomes large, the urging portion can be made smaller than the size of the speed reducing device 155, and the speed reducing device 155 can be made smaller.
Further, the driving rotating body 520 or the driven rotating body 530 and the planetary rotating body 540 can be easily assembled.

[14] The number of external teeth ze and the number of pressurized internal teeth zp of the extension portion are set so that the value when divided by the prime factor of the fifth tooth number z5 or the prime factor of the sixth tooth number z6 is 2 or more. There is. As a result, the backlash between the rotating bodies can be offset, and a relatively wide range of backlash can be absorbed.

(Other embodiments)
(I) The urging portion is not limited to the spring, and the input rotating body and the pressurized rotating body may be urged in the direction in which the thrust distance L changes by using an electromagnetic force. Further, the fluid pressure of the oil used for lubricating each rotating body may be used.

(Ii) The planetary rotating body is not limited to the form in which three are provided in the circumferential direction, and at least one may be provided.
(Iii) The communication hole of the third embodiment is provided to form a pressurizing portion 34 that can be pressurized from the outside in the direction in which the spring 85 is contracted, and is a lubricating liquid that lubricates the friction between the rotating bodies. It may also serve as the route of.
(Iv) In the fourth embodiment, any one or more of the end portions of the driving rotating body, the driven rotating body, and the planetary rotating body may have a tapered shape.

Other embodiments that share the idea of the fifth embodiment are shown below.
(V) As shown in FIG. 23, the drive-side convex portion 543 and the driven-side convex portion 544 have a tapered shape that is inclined so that the diameter decreases from the inner side in the axial direction to the outer side in the axial direction of the planetary rotating body 540. It may be. A plurality of drive-side convex portions 543 and driven-side convex portions 544 may be provided and may be protrusions.

As shown in FIG. 24, the driving side convex portion 543 and the driven side convex portion 544 may have a conical shape. Further, the driving side convex portion 543 and the driven side convex portion 544 may have a polygonal prism shape.
As shown in FIG. 25, the driving side convex portion 543 and the driven side convex portion 544 do not have to be located on the axis of the planetary rotating body 540.

(Vi) As shown in FIG. 26, the driving recess 521 and the driven recess 531 may be recessed so that the cross section has a stepped shape.
As shown in FIG. 27, the driving recess 521 and the driven recess 531 may be recessed so that the cross section has a stepped shape and a tapered shape.
As shown in FIG. 28, the driving recess 521 and the driven recess 531 may be formed in an annular shape so as to be provided at positions corresponding to the sliding surfaces. Further, a plurality of driving recesses 521 and driven recesses 531 may be provided.

(Vii) Each oblique tooth may be changed to a flat tooth in order to obtain the effects described in [10] and [12].

(Viii) As shown in FIG. 29, the drive-side planetary external gear portion 541 may be formed by end-relieving the third oblique tooth 411. End relief is one of tooth profile modification and is a method of releasing both ends of the tooth width. Similarly, the driven side planetary external gear portion 542 may be formed by end-relieving the fourth oblique tooth 421.
The driving-side planetary external gear portion 541 and the driven-side planetary external gear portion 542 may be formed so that the dislocation coefficient decreases from the inner side in the axial direction to the outer side in the axial direction of the planetary rotating body 540. The dislocation coefficient is a value obtained by dividing the amount of dislocation, which is the amount of shifting the machining tool, by the module of the gear.

(Ix) As shown in FIG. 30, the planetary groove portion 547 is formed so that the diameter of the planetary rotating body 540 becomes smaller toward the central surface including the center of the axis of the planetary rotating body 540, and has a tapered shape. May be good.
As shown in FIG. 31, the planetary groove portion 547 may have a curved surface and may be formed so that the outer edge in the radial cross section of the planetary rotating body 540 is curved.
As shown in FIG. 32, the planetary groove portion 547 is formed so that the diameter of the planetary rotating body 540 becomes smaller toward the central surface including the center of the planetary rotating body 540, and the diameter of the planetary rotating body 540 is formed near the center. May be formed so that
As described above, the present invention is not limited to such embodiments, and can be implemented in various embodiments without departing from the spirit of the present invention.

20, 520 ・ ・ ・ Drive rotating body, 21 ・ ・ ・ Drive internal gear part,
211 ・ ・ ・ 1st oblique tooth, 22 ・ ・ ・ Sprocket part,
30, 530 ・ ・ ・ Driven rotating body, 31 ・ ・ ・ Driven internal gear part,
311 ・ ・ ・ 2nd oblique tooth, 40,540 ・ ・ ・ Planetary rotating body,
41 ・ ・ ・ Drive side planetary external gear part, 411 ・ ・ ・ Third oblique tooth,
42 ・ ・ ・ Driven side planetary external gear part, 421 ・ ・ ・ 4th oblique tooth,
60, 560 ... Input rotating body,
61 ・ ・ ・ Input external gear, 611 ・ ・ ・ Fifth oblique tooth,
80, 580 ... Pressurized rotating body,
81 ・ ・ ・ Pressurized external gear part, 811 ・ ・ ・ 6th oblique tooth.

Claims (13)

A rotatable drive rotating body having a drive internal gear portion (21) including a first oblique tooth (211) having twisted tooth streaks and a sprocket portion (22) fitted to the drive internal gear portion. (20,520) and
A driven rotating body (30, 530) that is housed in the driving rotating body on the sprocket portion side, has a driven internal gear portion (31) including a second oblique tooth (311) inside, and can rotate.
The drive-side planetary external gear portion (41) fitted to the drive internal gear portion and including the third oblique tooth (411) on the outside, and the fourth oblique tooth (421) fitted to the driven internal gear portion on the outside. A planetary rotating body (40, 540) having a driven side planetary external gear portion (42) and capable of planetary motion, and
It has an input external gear portion (61) that is fitted to the drive-side planetary external gear portion and includes a fifth oblique tooth (611) on the outside. Alternatively, an input rotating body (60, 560) that changes the relative rotation phase of the driven rotating body to accelerate or decelerate the rotation of the driving rotating body or the driven rotating body.
A rotatable pressurized rotating body (80, 580) having a pressurized external gear portion (81) fitted to the driven side planetary external gear portion and including a sixth oblique tooth (811) on the outside.
A speed reducer equipped with. The first aspect of claim 1, wherein the planetary rotating body is provided on an end surface (545) of the driving side planetary external gear portion facing the driving rotating body and has a driving side convex portion (543) in contact with the driving rotating body. Deceleration device. Claim 1 or 2 in which the planetary rotating body is provided on an end surface (546) of the driven side planetary external gear portion facing the driven rotating body and has a driven side convex portion (544) in contact with the driven rotating body. The speed reducer described in. The drive rotating body is formed on an end surface (522) of the driving rotating body facing the drive side planetary external gear portion.
The speed reduction device according to any one of claims 1 to 3, which has a drive recess (521) recessed from the inside in the axial direction to the outside in the axial direction of the drive rotating body. The driven rotating body has a driven recess (531) recessed from the axially inner side to the axially outer side of the driven rotating body on the end surface (532) of the driven rotating body facing the driven side planetary external gear portion. The speed reducer according to any one of claims 1 to 4. Let the thrust distance (L) be the axial distance from the input rotating body to the pressurized rotating body.
Claim 1 further includes an urging portion (85) provided between the input rotating body and the pressurized rotating body to urge the input rotating body and the pressurized rotating body in a direction in which the thrust distance changes. The speed reducer according to any one of 5 to 5. The urging portion acts on the planetary rotating body by the force urging the pressurized rotating body, and the rotational force about the radial direction of the planetary rotating body is defined as the urging force moment (Ms), and the driving internal gear. Assuming that the portion or the driven internal gear portion acts on the planetary rotating body and the rotational force about the radial direction of the planetary rotating body is the rotational force moment (Mr).
The speed reducer according to claim 6, wherein the direction of the urging force moment and the direction of the rotational force moment are the same direction. The deceleration according to any one of claims 1 to 7, wherein the pitch circle drawn by the driven side planetary external gear portion on the drive rotating body side is larger than the pitch circle drawn by the driven side planetary external gear portion on the driven rotating body side. apparatus. The deceleration according to any one of claims 1 to 8, wherein the pitch circle drawn by the driving side planetary external gear portion on the driven rotating body side is larger than the pitch circle drawn by the driving side planetary external gear portion on the driving rotating body side. apparatus. It extends from the input rotating body toward the pressurized rotating body, fits with the pressurized rotating body, and the input rotating body and the pressurized rotating body are freely relatively displaced in the axial direction, and The speed reduction device according to any one of claims 1 to 9, further comprising an extension portion (62, 562) for preventing the input rotating body and the pressurized rotating body from relative rotation. The speed reducer according to claim 10, wherein the extension portion has a spiral shape. If n is a natural number of 2 or more,
The extension has extension outer teeth (563) on the outer wall.
The pressurized rotating body has a pressurized internal tooth (581) fitted to the extension external tooth on the inner wall.
The number of teeth (ze) of the extension external tooth and the number of teeth (zp) of the pressurized internal tooth are predisposing factors for the number of teeth of the fifth oblique tooth (z5) or the number of teeth of the sixth oblique tooth (z6). The speed reducer according to claim 10 or 11, which is set so that the value when divided by a prime factor of is 2 or more. The speed reducing device according to any one of claims 1 to 12, wherein the planetary rotating body has a planetary groove portion (547) between the driving side planetary external gear portion and the driven side planetary external gear portion.

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