JP2004156661A - Planetary gear type clutch mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a planetary gear type clutch mechanism with a wide range of design discretion, in which more than two of tooth edges of a planetary gear and a standby gear are not simultaneously brought into contact with each other, when the planetary gear and the standby gear start to engage with each other. <P>SOLUTION: When a sun gear 1 is rotated to a counterclockwise direction, a phase limit member 70 is also rotated to a counterclockwise direction such that tooth edges 22 of the planetary gear 2 are interfered with a phase limit portion 71 of the phase limit member 70. The planetary gear 2 rotates on a central axis to a counterclockwise direction while it is rotated on its own axis to a clockwise direction until a rotation phase of the planetary gear 2 being dependent on a position of the phase limit portion 71 of the phase limit member 70 stopped under contact with a control member 65, and breaks away from an interference position with the phase limit member 70. The planetary gear 2 is positioned in a rotation phase in which tooth edges 23 of the planetary gear is located on a straight line combined with an axis 21 of the planetary gear and an axis 63 of the standby gear, and therefore, a pair of adjacent teeth of the planetary gear 2 and the standby gear 9 are not simultaneously brought into contact with each other in spite of any rotation phase of the standby gear 9. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a clutch mechanism for switching a power transmission direction.
[0002]
[Prior art]
BACKGROUND ART A planetary gear clutch mechanism including a sun gear, a planetary gear that can revolve around the sun gear, and a standby gear that can mesh with the planetary gear by the revolving motion of the planetary gear is known (Patent Document 1). Further, in such a planetary gear type clutch mechanism, when the planetary gear starts to mesh with the standby gear, two or more tooth tips of the planetary gear and the standby gear do not simultaneously come into contact with each other so that rotation lock or the like does not occur. There is a known configuration in which a member that regulates the rotational phase of a planetary gear when the planetary gear starts to mesh with a standby gear is provided (Patent Document 2).
[0003]
[Patent Document 1]
JP-A-8-160511 [Patent Document 2]
JP-A-6-159448
[Problems to be solved by the invention]
In such a planetary gear type clutch mechanism, a member that regulates the rotation phase of the planetary gear when the planetary gear starts to mesh with the standby gear is provided. However, in a state where the planetary gear and the standby gear are engaged with each other and the standby gear is driven, the planetary gear and the phase limiter of the member that regulates the rotational phase must not interfere with each other. Therefore, there is a limit in reducing the distance between the two standby gears, which is a design constraint.
[0005]
SUMMARY OF THE INVENTION An object of the present invention is to provide a planetary gear type clutch mechanism in which two or more tooth tips of a planetary gear and a standby gear do not abut at the same time when the planetary gear starts to mesh with a standby gear, so that the degree of design freedom is high. It is in.
[0006]
[Means for Solving the Problems]
(1) The invention according to claim 1 includes a sun gear, a planetary gear that meshes with the sun gear and can revolve around the sun gear, at least one standby gear that can mesh with the planetary gear depending on the revolving position of the planetary gear, When the planetary gear begins to mesh with the standby gear due to the revolving motion of the planetary gear, the rotation phase of the planetary gear is adjusted so that the tip of the planetary gear is located on a straight line connecting the rotation axis of the planetary gear and the rotation axis of the standby gear. In a planetary gear type clutch mechanism having a deciding member for deciding, the deciding member is movable with the revolving motion of the planetary gear.
(2) The invention according to claim 2 is the planetary gear type clutch mechanism according to claim 1, wherein the determining member restricts a movable range by a restricting member that restricts a range of the revolving motion of the planetary gear. Features.
[0007]
BEST MODE FOR CARRYING OUT THE INVENTION
――― Planetary gear type clutch mechanism ―――
An embodiment of the planetary gear type clutch mechanism according to the present invention will be described with reference to FIGS. FIG. 1 is a diagram showing a meshing state of gears when the planetary gear type clutch mechanism is viewed from the front. The planetary gear type clutch mechanism includes a sun gear 1, a planetary gear 2, and standby gears 8 and 9. FIG. 2 is a cross-sectional view of the planetary gear type clutch mechanism according to the embodiment when viewed from the side. A center shaft 61 is formed on the gear base 6. The sun shaft 11 is rotatably fitted to the center shaft 61. The connecting member 3 is fixed to the upper surface of the sun shaft 11. The sun gear 1 is rotatably fitted on the outer periphery of the sun shaft 11. The sun shaft 11 and the sun gear 1 are prevented from falling off from the center shaft 61 by the holding plate 10. A connecting member protrusion 31 is formed at the tip of the connecting member 3. When the connecting member projection 31 of the connecting member 3 that rotates about the central axis 61 abuts on the regulating members 64 and 65 formed on the gear base 6, the rotation of the connecting member 3 about the central axis 61 is achieved. Limited to a certain angle.
[0008]
A planet shaft 21 is attached to the distal end side of the connecting member 3, and the planet gear 2 is rotatably fitted to the outer periphery of the planet shaft 21. The coil spring 7 is interposed between the planet shaft 21 and the planet gear 2. When the planet shaft 21 is attached to the connecting member 3, the coil spring 7 is slightly compressed, and the restoring force causes the connecting member 3 and the planet gear 2 to be frictionally coupled to each other.
[0009]
Standby gears 8 and 9 having the same number of teeth as the planetary gear 2 are rotatably fitted to standby shafts 62 and 63 formed on the gear base 6, respectively. These standby gears 8 and 9 mesh with the planetary gear 2 revolving around the center shaft 61, whereby the driving force of the sun gear 1 is transmitted to the standby gears 8 and 9 via the planetary gear 2. As shown in FIG. 1, the teeth of the planetary gear 2 and the standby gears 8 and 9 have a pointed tip.
[0010]
A phase limiting member 70 is rotatably fitted to a center shaft 61 formed on the gear base 6. When the tip portions 72 and 73 of the phase limiting member 70 that rotates about the central axis 61 abut against the regulating members 64 and 65 formed on the gear base 6, the phase limiting member 70 is centered on the central axis 61 of the phase limiting member 70. Rotation is restricted within a certain angle. The phase limiting section 71 of the phase limiting member 70 is a determining member that determines the rotational phase of the planetary gear 2 when the revolving planetary gear 2 starts meshing with the standby gears 8 and 9 as described later. The rotation angle of the phase limiting member 70 about the central axis 61 can be arbitrarily set depending on the shapes of the distal ends 72 and 73.
[0011]
――― Operation of planetary gear type clutch mechanism ―――
The operation of the planetary gear type clutch mechanism according to one embodiment will be described with reference to FIGS. As shown in FIG. 1, when the sun gear 1 rotates clockwise, since the planetary gear 2 is in frictional contact with the connecting member 3 by the coil spring 7, resistance occurs in the rotation of the planetary gear 2 and thereby the planetary gear 2 2 revolves clockwise. The revolving motion of the planetary gear 2 is regulated by the contact of the connecting member projection 31 with the regulating member 64. The planetary gear 2 meshes with the standby gear 8 in the restricted position. At this time, the leading end 72 of the phase limiting member 70 is in contact with the regulating member 64.
[0012]
When the clockwise rotation of the sun gear 1 stops and starts to rotate counterclockwise, the planetary gear 2 releases the engagement with the standby gear 2 and revolves counterclockwise due to the rotation resistance of the planetary gear 2 described above. Start. At this time, as shown in FIG. 3, the tip 22 of the planetary gear 2 which is located on the standby gear 8 side and is closest to the phase limiting portion 71 of the phase limiting member 70 interferes with the phase limiting portion 71, so that the phase The member 70 rotates counterclockwise. Thereafter, as shown in FIG. 4, the distal end 73 of the phase regulating member 70 comes into contact with the regulating member 65, and the rotation of the phase limiting member 70 in the counterclockwise direction stops. When the planetary gear 2 further revolves due to the further rotation of the sun gear 1 in the counterclockwise direction, as shown in FIG. 4, since the tooth tip 22 interferes with the phase limiting portion 71 of the phase limiting member 70, the planetary gear 2 Revolves counterclockwise while rotating clockwise. Then, the planetary gear 2 revolves in the counterclockwise direction while rotating in the clockwise direction up to the rotation phase of the planetary gear 2 depending on the position of the phase limiting portion 71, and separates from the interference position with the phase limiting member 70. At this time, the planetary gear 2 has a rotational phase in which the tooth tip 23 is located on a straight line connecting the planetary shaft 21 and the standby shaft 63. When the rotation of the planetary gear 2 stops and the revolution further proceeds, the planetary gear 2 and the standby gear 9 start to mesh with each other. Thereafter, as shown in FIG. 5, the connecting member protrusion 31 comes into contact with the regulating member 65, and the switching of the standby gear to which the power is transmitted is completed.
[0013]
Similarly, when the sun gear 1 stops rotating in the counterclockwise direction and rotates in the clockwise direction, two adjacent teeth of the planetary gear 2 and the standby gear 8 similarly do not abut simultaneously.
[0014]
The above-described planetary gear type clutch mechanism according to the embodiment has the following operational effects.
(1) When the planetary gear 2 and the standby gear 9 start to mesh with each other, the planetary gear 2 is positioned on a straight line connecting the planetary shaft 21 and the standby shaft 63 due to the interference with the phase limiting portion 71. The rotation phase. As a result, regardless of the rotational phase of the standby gear 9, two adjacent teeth of the planetary gear 2 and the standby gear 9 do not abut simultaneously. As a result, it is possible to avoid a lock caused by two adjacent teeth of the planetary gear 2 and the standby gear 9 simultaneously abutting at the beginning of meshing. Therefore, wear and dents on the tooth surface can be reduced, and durability can be improved.
(2) The phase limiting member 70 can rotate with the revolution of the planetary gear 2 with respect to the center shaft 61. In a state where the planetary gear 2 and the standby gear 8 or the standby gear 9 are engaged with each other and the standby gear 8 or the standby gear 9 is driven, the revolution range of the phase limiting member 70 is regulated by the regulating members 64 and 65. The planetary gear 2 and the phase limiter 71 do not interfere. Accordingly, it is possible to cope with a compact design in which the positions of the position standby gears 8 and 9 are brought close to each other, so that the degree of freedom in design is high and the size of the entire device can be reduced.
(3) The phase limiting member 70 is rotatable with the revolution of the planetary gear 2 with respect to the center shaft 61 within a range regulated by the regulating members 64 and 65. The rotation angle of the phase limiting member 70 about the central axis 61 can be arbitrarily set by the shapes of the tip portions 72 and 73. Thus, the design of the phase limiting member 70 can be easily changed according to the positions of the standby gears 8 and 9, and the degree of freedom in designing is high.
[0015]
――― Modifications ―――
In the planetary gear type clutch mechanism of the above-described embodiment, the planetary gear 2 and the standby gears 8 and 9 have the same number of teeth, but are not limited thereto. In the planetary gear type clutch mechanism according to the above-described embodiment, the phase limiter 71 is provided on the phase limiter 70 and is rotatable with respect to the center shaft 61 together with the phase limiter 70. Absent. The phase limiting section 71 may be fixed to the gear base 6. Further, one standby gear may be provided. The above-described embodiments and modified examples may be combined. Furthermore, the present invention is not limited to the above-described embodiment and its modifications as long as the characteristic functions of the present invention are not impaired.
[0016]
【The invention's effect】
According to the present invention, when the planetary gear starts to mesh with the standby gear, the determining member that determines the rotational phase of the planetary gear so that two or more tooth tips of the planetary gear and the standby gear do not simultaneously contact each other is provided. It is possible to move with the orbital movement. This prevents locking of the rotation, reduces wear and dents on the tooth surface, and increases the degree of freedom in designing a planetary gear clutch mechanism with improved durability. Becomes easier.
[Brief description of the drawings]
FIG. 1 is a diagram showing a meshing state of gears when a planetary gear type clutch mechanism according to the present invention is viewed from the front.
FIG. 2 is a cross-sectional view of the planetary gear type clutch mechanism of FIG. 1 when viewed from a side.
FIG. 3 is a view for explaining the operation of the planetary gear type clutch mechanism of FIG. 1;
FIG. 4 is a view for explaining the operation of the planetary gear type clutch mechanism of FIG. 1;
FIG. 5 is a diagram for explaining the operation of the planetary gear type clutch mechanism of FIG. 1;
[Explanation of symbols]
REFERENCE SIGNS LIST 1 sun gear 2 planetary gear 3 connecting member 6 gearhead 8, 9 standby gear 10 holding plate 11 sun shaft 21 planet shaft 31 connecting member protrusion 61 central shaft 62, 63 standby shaft 64, 65 regulating member 70 phase limiting member 71 phase limiting Parts 72, 73 Tip

Claims (2)

Sun gear,
A planetary gear that can revolve around the sun gear meshing with the sun gear,
At least one standby gear capable of meshing with the planetary gear by the revolving position of the planetary gear;
When the planetary gear begins to mesh with the standby gear due to the revolving motion of the planetary gear, the tip of the planetary gear is located on a straight line connecting the rotation axis of the planetary gear and the rotation axis of the standby gear, A planetary gear type clutch mechanism having a determining member for determining a rotational phase of the planetary gear,
The planetary gear type clutch mechanism, wherein the determining member is movable with the revolving motion of the planetary gear. The planetary gear type clutch mechanism according to claim 1,
The planetary gear type clutch mechanism, wherein a movable range of the determining member is restricted by a restricting member that restricts a revolving range of the planetary gear.

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