Two-way clutch

Abstract

To provide a two-way clutch which is suppressed in a torque loss.SOLUTION: A planetary gear mechanism 1 is composed of an inner gear 11, planetary gears 12, 13 which rotate and revolve on the inner gear 11, a rotating shaft 14 existing in a center in the inner gear 11, and planetary gear carriers 15, 16 for connecting shafts 12a, 13a of the planetary gears 12, 13 and the rotating shaft 14 to each other. An input shaft 2 is connected to a front part of the rotating shaft 14 of the planetary gear mechanism 1 so as to be coaxially rotatable, and an output shaft 3 is contacted to a rear part of the rotating shaft 14 of the planetary gear mechanism 1 so as to be coaxially rotatable. The input shaft 2 has a rotating body, for example, a circular plate 21 in which holes 22, 23 for inserting the shafts 12a, 13a of the planetary gears 12, 13 therein are formed. The output shaft 3 has a rotating body, for example, a circular plate 31 in which holes 32, 33 for inserting the shafts 12a, 13a of the planetary gears 12, 13 are formed.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present invention relates to a two-way clutch. [Background technology]

[0002] In a two-way clutch, which is one type of backdrive prevention mechanism, when the input shaft is rotated, the output shaft also rotates, but even if the output shaft is rotated, the output shaft itself is locked, so power is not transmitted to the input shaft and the input shaft does not rotate.

[0003] FIG. 11 is a cross-sectional view showing a conventional two-way clutch (see: NTN Corporation Lock Type Torque Diode TDL (registered trademark)).

[0004] In the initial state of Fig. 11(A), an input shaft 102 and an output shaft 104 fitted between a cage 103 and an input shaft 102 are provided in a fixed cylindrical housing 101. Two rollers 106-1 and 106-2 pressed by a spring 105 are provided in a space S surrounded by the housing 101, the ends 103a and 103b of the cage 103, and the flat portion 104a of the output shaft 104. In this case, the height of the space S is greater at the center and smaller at the ends. Therefore, Retainer 103 End of 103a, 103b, The curved portion of the housing 101 and the flat portion 104a of the output shaft 104 form cam surfaces for the rollers 106-1 and 106-2. In this initial state, the rollers 106-1 and 106-2 are engaged with the cam surfaces in the space S, so that the output shaft 104 is locked in both directions by contact forces F1 and F2 generated at the contact points of the rollers 106-1 and 106-2 with the housing 101 and the output shaft 104.

[0005] Next, the operation of the two-way clutch of FIG. 11(A) will be described with reference to FIGS. 11(B) and 11(C).

[0006] As shown in FIG. 11B, when the input shaft 102 is rotated counterclockwise, the cage 103 also rotates counterclockwise. As a result, the roller 106-2 is pushed leftward from the cam surface by the cage 103 and unlocked, and the roller 106-1 also disengages from the cage 103 and moves to the left while rotating clockwise and rolling. As a result, as the input shaft 102 and the cage 103 further rotate counterclockwise, the output shaft 104 also rotates counterclockwise. Similarly, as the input shaft 102 rotates clockwise, the output shaft 104 also rotates clockwise. In other words, the rotation of the input shaft 102 causes the output shaft 104 to rotate.

[0007] 11(C), when the output shaft 104 is rotated counterclockwise, the roller 106-2 is sandwiched between the cam surfaces of the housing 101 and the flat portion 104a of the output shaft 104, resulting in a tightly locked state. Similarly, when the output shaft 104 is rotated clockwise, the roller 106-1 is tightly locked, and the output shaft 104 is also locked. In other words, even when the output shaft 104 rotates, the input shaft 102 does not rotate. Summary of the Invention [Problem to be solved by the invention]

[0008] However, in the conventional two-way clutch shown in FIG. 11, when the input shaft 102 rotates, the rollers, for example, 106-1, roll after being unlocked and move, which poses a problem of torque loss and wear due to friction force F3 between the rollers and the flat portion 104a of the output shaft 104 shown in FIG. 11(B).

[0009] Another problem is that unlocking the rollers 106-1 and 106-2 when the input shaft 102 rotates requires energy greater than the load in the initial state. [Means for solving the problem]

[0010] In order to solve the above-mentioned problems, a two-way clutch according to the present invention comprises a planetary gear mechanism having an internal gear, first and second planetary gears that rotate and revolve on the internal gear, a rotation shaft at the center of the internal gear, and first and second planetary gear carriers that connect the shafts of the first and second planetary gears to the rotation shaft, an input shaft that is rotatably connected coaxially to one side of the rotation shaft of the planetary gear mechanism, and an output shaft that is rotatably connected coaxially to the other side of the rotation shaft of the planetary gear mechanism, wherein the input shaft is equipped with planetary gear separating means for separating the first and second planetary gears to bring them into a disengaged state when the input shaft rotates, and the output shaft is equipped with planetary gear approaching means for bringing the first and second planetary gears closer to each other to bring them into mesh when the output shaft rotates. [Effects of the Invention]

[0011] According to the present invention, when the input shaft rotates, the planetary gears can freely revolve while meshing with the internal gear, so there is no torque loss due to friction. In addition, unlocking is performed by separating the planetary gears from each other, so it can be released with a force equivalent to the load. [Brief explanation of the drawings]

[0012] [Figure 1] 1A and 1B are cross-sectional views showing a planetary gear mechanism applied to the present invention, in which FIG. 1A shows an unlocked state and FIG. 1B shows a locked state. [Figure 2] 1 is an exploded perspective view showing a first embodiment of a two-way clutch according to the present invention. [Figure 3] 3 is a diagram for explaining the input shaft rotation operation of the two-way clutch of FIG. 2. FIG. [Figure 4] 3 is a diagram for explaining the rotational operation of the output shaft of the two-way clutch of FIG. 2. FIG. [Figure 5] FIG. 4 is an exploded perspective view showing a second embodiment of a two-way clutch according to the present invention. [Figure 6] 6 is a diagram for explaining the input shaft rotation operation of the two-way clutch of FIG. 5. [Figure 7]6 is a diagram for explaining the rotational operation of the output shaft of the two-way clutch of FIG. 5. FIG. [Figure 8] FIG. 6 is an exploded perspective view showing a first modified example of the two-way clutch of FIGS. 2 and 5. [Figure 9] 2 and 5, in which (A) is a top view, (B) is a perspective view seen from the input shaft, and (C) is a perspective view seen from the output shaft. [Figure 10] This shows details of (A) in Figure 9, where (A)-1 is a front view seen from the input shaft, (A)-2 is a cross-sectional view taken along line AA, (B) is a cross-sectional view taken along line BB, (C)-1 is a back view seen from the output shaft side, and (C)-2 is a cross-sectional view taken along line CC. [Figure 11] 1A and 1B are cross-sectional views showing a conventional two-way clutch, in which (A) shows the initial state, (B) shows the state when the input shaft is rotated, and (C) shows the state when the output shaft is rotated. DETAILED DESCRIPTION OF THE INVENTION

[0013] FIG. 1 is a cross-sectional view showing a planetary gear mechanism applied to the present invention, where (A) shows the unlocked state (non-engaged state) and (B) shows the locked state (engaged state).

[0014] The planetary gear mechanism 1 comprises an internal gear 11 fixed to a base or the like (not shown), planetary gears 12 and 13 that rotate and revolve on the internal gear 11, a rotation shaft 14 located at the center of the internal gear 11, and planetary gear carriers 15 and 16 that connect shafts 12a and 13a of the planetary gears 12 and 13 to the rotation shaft 14.

[0015] In the unlocked state shown in Figure 1(A), the planetary gears 12 and 13 are not meshed, and the meshing between the planetary gear 12 and the internal gear 11 and the meshing between the planetary gear 13 and the internal gear 11 are independent. In this case, the planetary gears 12 and 13 rotate in the same direction and can rotate and revolve on the internal gear 11. Therefore, the planetary gears 12 and 13 can rotate around the rotation shaft 14 via the planetary gear carriers 15 and 16. The operation of the input shaft 2, which will be described later, utilizes this unlocked state. Note that the unlocked state is achieved by the meshing between the internal gear 11 and the planetary gears 12 and 13, so there is no loss due to slippage.

[0016] In the locked state shown in Figure 1(B), the planetary gears 12 and 13 are meshed, and the planetary gear 12, the internal gear 11, and the planetary gear 13 are meshed in an annular fashion. In this case, the planetary gears 12 and 13 cannot rotate in the same direction, so the rotation and revolution of the internal gear 11 are restricted. Therefore, the planetary gears 12 and 13 cannot rotate around the rotation axis 14 by the planetary gear carriers 15 and 16. The operation of the output shaft 3, which will be described later, utilizes this locked state.

[0017] FIG. 2 is an exploded perspective view showing a first embodiment of a two-way clutch according to the present invention.

[0018] In FIG. 2, a planetary gear mechanism 1 is connected between an input shaft 2 and an output shaft 3 .

[0019] The input shaft 2 is rotatably connected to the front of the rotating shaft 14 of the planetary gear mechanism 1 coaxially by a bearing (not shown), while the output shaft 3 is rotatably connected to the rear of the rotating shaft 14 of the planetary gear mechanism 1 coaxially by a bearing (not shown).

[0020] The input shaft 2 has a rotating body, such as a disk 21, with holes 22 and 23 formed therein for inserting the shafts 12a and 13a of the planetary gears 12 and 13. In this case, the distance between the centers of the holes 22 and 23 is larger by a predetermined value than the distance between the shafts 12a and 13a of the planetary gears 12 and 13 in the locked state. The holes 22 and 23 also have larger cross-sectional areas than the shafts 12a and 13a. As a result, the distance between the shafts 12a and 13a of the planetary gears 12 and 13 is variable within the range of the holes 22 and 23. The holes 22 and 23 can have various shapes, such as circular or oval.

[0021] The output shaft 3 has a rotating body, such as a disk 31, with holes 32 and 33 formed therein for inserting the shafts 12a and 13a of the planetary gears 12 and 13. In this case, the distance between the centers of the holes 32 and 33 is the same as the distance between the shafts 12a and 13a of the planetary gears 12 and 13 in the locked state. The cross-sectional areas of the holes 32 and 33 are larger than the cross-sectional areas of the shafts 12a and 13a. As a result, the distance between the shafts 12a and 13a of the planetary gears 12 and 13 is variable within the range of the holes 32 and 33. The holes 32 and 33 can have various shapes, such as circular or oval.

[0022] FIG. 3 is a diagram for explaining the input shaft rotation operation of the two-way clutch of FIG.

[0023] 3A, the planetary gears 12 and 13 are in mesh. In this state, the distance between the holes 22 and 23 of the input shaft 2 is slightly larger than the center distance between the shafts 12a and 13a of the planetary gears 12 and 13 in the locked state, while the center distance between the holes 32 and 33 of the output shaft 3 is the same as the center distance between the shafts 12a and 13a of the planetary gears 12 and 13 in the locked state.

[0024] Next, as shown in FIG. 3B (the unlocked transition state), when the input shaft 2 rotates clockwise as indicated by the arrow, the distance between the centers of the holes 22 and 23 is greater than the distance between the axes 12a and 13a of the planetary gears 12 and 13. This causes the hole 23 of the input shaft 2 to come into contact with the axis 13a of the planetary gear 13. As a result, the planetary gear 13 revolves clockwise, i.e., moves outward, and rotates counterclockwise. Meanwhile, although the hole 22 of the input shaft 2 does not come into contact with the axis 12a of the planetary gear 12, the counterclockwise rotation of the engaged planetary gear 13 causes the planetary gear 12 to rotate clockwise. As a result, the planetary gears 12 and 13 rotate in opposite directions, separating them, and the system transitions to the unlocked state, where they are not engaged. In this unlocked transition state, the output shaft 3 barely moves. This unlocking transition can be achieved by applying a force to the input shaft 2 sufficient to disengage the planetary gears 12 and 13 from meshing.

[0025] Furthermore, when the input shaft 2 is rotated clockwise in the unlocked state, the hole 22 of the input shaft 2 also comes into contact with the shaft 12a of the planetary gear 12, as shown in Figure 3(C). As a result, the planetary gear 12 also revolves clockwise and rotates counterclockwise. Therefore, the two planetary gears 12 and 13 revolve clockwise while maintaining a constant distance between them, and the shaft 13a of the planetary gear 13 rotates the output shaft 3 clockwise via the hole 33.

[0026] In this way, when the input shaft 2 rotates clockwise, the output shaft 3 also rotates clockwise by the planetary gear mechanism 1. Similarly, when the input shaft 2 rotates counterclockwise, the output shaft 3 also rotates counterclockwise by the planetary gear mechanism 1.

[0027] FIG. 4 is a diagram for explaining the rotational operation of the output shaft of the two-way clutch of FIG.

[0028] 4A, the planetary gears 12 and 13 are not meshed. In this state, the distance between the centers of the holes 22 and 23 of the input shaft 2 is approximately the same as the distance between the shafts 12a and 13a of the planetary gears 12 and 13 in the unlocked state, while the distance between the centers of the holes 32 and 33 of the output shaft 3 is slightly smaller than the distance between the shafts 12a and 13a of the planetary gears 12 and 13 in the unlocked state.

[0029] Next, as shown in the locked state in Fig. 4(B), when the output shaft 3 rotates clockwise, the shaft 12a of the planetary gear 12 moves toward the planetary gear 13 through the hole 32 of the output shaft 3. In other words, the planetary gear 12 moves inward. As a result, the planetary gear 12 rotates counterclockwise and revolves clockwise, and the planetary gears 12 and 13 transition to a locked state in which they are engaged with each other.

[0030] Furthermore, in the locked state, when the planetary gears 12 and 13 mesh with each other at the standard pitch circle, as shown in Figure 4(C), the shaft 13a of the planetary gear 13 comes into contact with the hole 33 of the output shaft 3. In this locked state, the planetary gears 12 and 13 cannot revolve, and therefore the input shaft 2 cannot rotate.

[0031] In the initial locked state where the planetary gears 12 and 13 are meshed, when the planetary gears 12 and 13 mesh with each other at the standard pitch circle, the shaft 13a of the planetary gear 13 also comes into contact with the hole 33 of the output shaft 3. In this locked state, the planetary gears 12 and 13 cannot revolve, and therefore the input shaft 2 cannot rotate.

[0032] On the other hand, when the output shaft 3 rotates counterclockwise, the shaft 13a of the planetary gear 13 moves toward the planetary gear 12 due to the hole 33 of the output shaft 3. In other words, the planetary gear 13 moves inward. As a result, the planetary gear 13 rotates clockwise and revolves counterclockwise, and the planetary gears 12, 13 enter a locked state in which they mesh. At this time, when the planetary gears 12, 13 mesh with each other at the standard pitch circle, the shaft 12a of the planetary gear 12 comes into contact with the hole 32 of the output shaft 3. Even in this locked state, the planetary gears 12, 13 cannot revolve, and therefore the input shaft 2 cannot rotate.

[0033] The same applies to the case where the planetary gears 12 and 13 are initially in a locked state where they are engaged with each other.

[0034] FIG. 5 is an exploded perspective view showing a second embodiment of a two-way clutch according to the present invention.

[0035] In FIG. 5, an input shaft 4 is provided in place of the input shaft 2 in FIG. 2, while an output shaft 5 is provided in place of the output shaft 3 in FIG.

[0036] The input shaft 4 has a planet gear carrier spacing pin 41 inserted between the planet gear carriers 15, 16. When the input shaft 4 rotates counterclockwise, the planet gear carrier spacing pin 41 acts to move the planet gear carrier 15, i.e., the planet gears 12, away from the planet gear carrier 16, i.e., the planet gears 13, and on the other hand, when the input shaft 4 rotates clockwise, the planet gear carrier spacing pin 41 acts to move the planet gear carrier 16, i.e., the planet gears 13, away from the planet gear carrier 15, i.e., the planet gears 12. In this way, the planet gear carrier spacing pin 41 acts to increase the distance between the axes 12a, 13a of the planet gears 12, 13.

[0037] The output shaft 5 has planet gear carrier proximity pins 51, 52 inserted on the non-opposing sides, i.e., the outsides, of the planet gear carriers 15, 16. When the output shaft 5 rotates counterclockwise, the planet gear carrier proximity pin 52 acts to move the planet gear carrier 16, i.e., the planet gear 13, closer to the planet gear carrier 15, i.e., the planet gear 12, and on the other hand, when the output shaft 5 rotates clockwise, the planet gear carrier proximity pin 51 acts to move the planet gear carrier 15, i.e., the planet gear 12, closer to the planet gear carrier 16, i.e., the planet gear 13. In this way, the planet gear carrier proximity pins 51, 52 act to reduce the axial distance between the axes 12a, 13a of the planet gears 12, 13.

[0038] FIG. 6 is a diagram for explaining the input shaft rotation operation of the two-way clutch of FIG.

[0039] 6(A) (initial state), the planetary gears 12 and 13 are in mesh. In this case, the planetary gear carrier separating pin 41 of the input shaft 4 is located in the middle of the planetary gear carriers 15 and 16 in the locked state, while the planetary gear carrier proximity pins 51 and 52 of the output shaft 5 are located outside the planetary gear carriers 15 and 16 in the locked state.

[0040] Next, as shown in the unlocked transition state in FIG. 6B, when the input shaft 4 rotates clockwise as indicated by the arrow, the planetary gear carrier separation pin 41 of the input shaft 4 comes into contact with the planetary gear carrier 16. As a result, the planetary gear 13 revolves clockwise, i.e., moves outward and rotates counterclockwise. Meanwhile, the counterclockwise rotation of the meshed planetary gear 13 causes the planetary gear 12 to rotate clockwise. As a result, the planetary gears 12 and 13 rotate in opposite directions, separating them, and the system transitions to a non-meshed unlocked state. In this unlocked transition state, the output shaft 5 hardly moves. Note that this unlocked transition can be achieved by applying a force to the input shaft 4 sufficient to disengage the planetary gears 12 and 13.

[0041] Furthermore, when the input shaft 4 is rotated clockwise in the unlocked state, as shown in Figure 6(C), the planetary gear carrier 16, pressed by the planetary gear carrier separating pin 41 of the input shaft 4, presses the planetary gear carrier proximity pin 52 of the output shaft 5. As a result, the planetary gear carrier proximity pin 51 also revolves clockwise, and the planetary gear carrier proximity pin 51 presses the planet gear carrier 15. This causes the planetary gear 12 to also revolve clockwise and rotate counterclockwise. Therefore, the two planetary gears 12, 13 revolve clockwise while maintaining a constant distance between them, causing the output shaft 5 to rotate clockwise.

[0042] In this way, when the input shaft 4 rotates clockwise, the output shaft 5 also rotates clockwise by the planetary gear mechanism 1. Similarly, when the input shaft 4 rotates counterclockwise, the output shaft 5 also rotates counterclockwise by the planetary gear mechanism 1.

[0043] FIG. 7 is a diagram for explaining the rotational operation of the output shaft of the two-way clutch of FIG.

[0044] In the unlocked state (initial state) of FIG. 7(A), the planetary gears 12 and 13 are in a non-meshing state, similar to the unlocked state (initial state) of FIG. 4(A).

[0045] Next, as shown in the locked state in Figure 7(B), when the output shaft 5 rotates clockwise, the planetary gear carrier proximity pins 51, 52 also rotate clockwise due to the output shaft 5. Therefore, the planetary gear carrier proximity pin 51 comes into contact with the planetary gear carrier 15. In other words, the planetary gear 12 moves inward. As a result, the planetary gear 12 rotates counterclockwise and revolves clockwise, and the planetary gears 12, 13 transition to a locked state in which they are engaged.

[0046] Furthermore, in the locked state, when the planetary gears 12 and 13 mesh with each other at the standard pitch circle, a completely locked state is reached, as shown in FIG. 7(C). In this completely locked state, the planetary gears 12 and 13 cannot revolve, and therefore the input shaft 4 cannot rotate.

[0047] In addition, in the initial state where the planetary gears 12 and 13 are meshed and in a locked state, when the planetary gears 12 and 13 mesh with each other at the standard pitch circle, the state becomes completely locked. In this completely locked state, the planetary gears 12 and 13 cannot revolve, and therefore the input shaft 4 cannot rotate.

[0048] On the other hand, when the output shaft 5 rotates counterclockwise, the planetary gear carrier proximity pins 51 and 52 also rotate counterclockwise due to the output shaft 5. Therefore, the planetary gear carrier proximity pin 52 comes into contact with the planetary gear carrier 16. In other words, the planetary gear 13 moves inward. As a result, the planetary gear 13 rotates clockwise and revolves counterclockwise, and the planetary gears 12 and 13 enter a locked state in which they are meshed.

[0049] Furthermore, when the planetary gears 12 and 13 mesh with each other at the standard pitch circle, they are in a completely locked state. In this completely locked state, the planetary gears 12 and 13 cannot revolve, and therefore the input shaft 4 cannot rotate.

[0050] In addition, in the initial state where the planetary gears 12 and 13 are meshed and in a locked state, when the planetary gears 12 and 13 mesh with each other at the standard pitch circle, the state becomes completely locked. In this completely locked state, the planetary gears 12 and 13 cannot revolve, and therefore the input shaft 4 cannot rotate.

[0051] Figure 8 is an exploded perspective view showing a first modified example of the two-way clutch of Figures 2 and 5. That is, in Figure 2, as shown in Figure 8(A), the input shaft 4 of Figure 5 can be used instead of the input shaft 2, and as shown in Figure 8(B), the output shaft 5 of Figure 5 can be used instead of the output shaft 3.

[0052] Figure 9 shows a second modified example of the two-way clutch of Figures 2 and 5, where (A) is a top view, (B) is a perspective view seen from the input shaft, and (C) is a perspective view seen from the output shaft. That is, in (A) of Figure 8, instead of the planetary gear mechanism 1 having two planetary gears 12, 13, two planetary gear carriers 15, 16, and one rotating shaft 14, a planetary gear mechanism 1' having four planetary gears 12, 13, 12', 13' and four planetary gear carriers 15, 16, 15', 16' symmetrically arranged about the rotating shaft 14 may be provided, instead of the input shaft 4 having one planetary gear carrier spacing pin 41, an input shaft 4' having two planetary gear carrier spacing pins 41, 41' axially symmetrically arranged, and instead of the output shaft 3 having two holes 31, 32, 31', 32' axially symmetrically arranged, may be provided. The planetary gear mechanism 1', input shaft 4', and output shaft 3' are fixed to a base 6. This allows the gravity of the vertical two-way clutch to be balanced.

[0053] A front view of FIG. 9A as seen from the input shaft side is shown in FIG. 10A-1, a cross-sectional view taken along line AA in FIG. 9 is shown in FIG. 10A-2, a cross-sectional view taken along line BB in FIG. 9A is shown in FIG. 10B, a back view of FIG. 9A as seen from the output shaft side is shown in FIG. 10C-1, and a cross-sectional view taken along line CC in FIG. 9A is shown in FIG. 10C-2. That is, the axisymmetric planetary gear carriers 15, 15' and planetary gear carriers 16, 16' are integrated on the rotating shaft 14. In this case, the planetary gears 12, 12' rotate coaxially on the internal gear 11, and the planetary gears 13, 13' rotate coaxially on the internal gear 11. Also, the planetary gear carrier spacing pins 41, 41' may be one, and the holes 31, 32; 31', 32' may be paired.

[0054] Furthermore, it may be configured with an input shaft having four holes, a planetary gear mechanism 1', and an output shaft having two pairs of planetary gear proximity pins, or it may be configured with an input shaft having four holes, a planetary gear mechanism 1', and an output shaft having four holes, or it may be configured with an input shaft having two planetary gear spacing pins, a planetary gear mechanism 1', and an output shaft having two pairs of planetary gear proximity pins.

[0055] 9, the planetary gear mechanism 1' has two pairs of planet gears and two pairs of planet gear carriers arranged symmetrically about the axis, the input shaft 4' has two pairs of holes or two pairs of planet gear carrier spacing pins arranged symmetrically about the axis, and the output shaft 3' has two pairs of holes or two pairs of planet gear carrier proximity pins. However, the planetary gear mechanism 1' may have three or more pairs of planet gears and three or more pairs of planet gear carriers arranged symmetrically about the axis, the input shaft has three or more pairs of holes or three or more pairs of planet gear carrier spacing pins arranged symmetrically about the axis, and the output shaft has three or more pairs of holes or three or more pairs of planet gear carrier proximity pins arranged symmetrically about the axis. In this case, multiple planet gear carriers may be integrated on the rotating shaft 14 so that the planet gears connected to these multiple planet gear carriers rotate coaxially on the internal gear 11. In this case, the number of pairs of holes or multiple planet gear carrier spacing pins on the input shaft may be reduced, and the number of pairs of holes or multiple pairs of planet gear carrier proximity pins on the output shaft may be reduced.

[0056] The present invention can be applied to any modifications within the scope of the above-described embodiment. [Industrial Applicability]

[0057] The two-way clutch according to the present invention can be used as a seat angle adjuster for a vehicle. [Explanation of symbols]

[0058] 1, 1': Planetary gear mechanism 11: Internal gear 12, 13, 12', 13': Planetary gear 12a, 13a: Axis 14: Rotation axis 15, 16: Planetary gear carrier 2, 2': Input shaft 21:Disc (rotating body) 22, 23, 22', 23': hole 3, 3': Output shaft 31:Disc (rotating body) 32, 33, 32', 33': hole 4, 4': Input shaft 41, 41': Planetary gear carrier spacing pin 5, 5': Output shaft 51, 52, 51', 52': Planet gear carrier proximity pins 6: Base 101: Housing 102: Input shaft 103:Retainer 103a, 103b: End 104: Output shaft 104a: Flat part 105: Spring 106-1, 106-2: Laura S: Space

Claims

1. a planetary gear mechanism including an internal gear, first and second planetary gears that rotate and revolve on the internal gear, a rotation shaft that is at the center of the internal gear, and first and second planetary gear carriers that connect the shafts of the first and second planetary gears to the rotation shaft; an input shaft rotatably connected to one side of the rotation shaft of the planetary gear mechanism; an output shaft rotatably connected coaxially to the other side of the rotation shaft of the planetary gear mechanism; Equipped with the input shaft is provided with planetary gear spacing means for spacing the first and second planetary gears apart to put the first and second planetary gears into a disengaged state when the input shaft rotates; a two-way clutch including a planetary gear approaching means for bringing the first and second planetary gears closer together and bringing the first and second planetary gears into mesh with each other when the output shaft rotates;

2. 2. The two-way clutch according to claim 1, wherein the planetary gear spacing means comprises a first rotor fixed to the input shaft and provided with first and second holes into which the shafts of the first and second planetary gears are inserted, and the distance between the centers of the first and second holes is greater than the distance between the centers of the first and second planetary gears in the meshed state.

3. 2. A two-way clutch according to claim 1, wherein said planet gear spacing means comprises a first planet gear carrier spacing pin fixed to said input shaft and inserted between said first and second planet gear carriers.

4. 4. A two-way clutch according to claim 2 or 3, wherein the planetary gear approaching means comprises a second rotor fixed to the output shaft and provided with third and fourth holes into which the shafts of the first and second planetary gears are inserted, and the distance between the centers of the third and fourth holes is the same as the center-to-center distance between the first and second planetary gears in the meshed state.

5. 4. A two-way clutch according to claim 2 or 3, wherein the planetary gear approach means comprises second and third planetary gear carrier approach pins fixed to the output shaft and inserted into non-opposing sides of each of the first and second planetary gear carriers.

6. 3. A two-way clutch according to claim 2, wherein the first and second holes have cross-sectional areas larger than the shafts of the first and second planetary gears.

7. 5. A two-way clutch according to claim 4, wherein the third and fourth holes have cross-sectional areas larger than the shafts of the first and second planetary gears.

8. a planetary gear mechanism including an internal gear, a plurality of pairs of planetary gears that rotate and revolve on the internal gear, a rotation shaft at the center of the internal gear, and a plurality of planetary gear carriers that connect the shafts of the planetary gears to the rotation shaft; an input shaft rotatably connected to one side of the rotation shaft of the planetary gear mechanism; an output shaft rotatably connected coaxially to the other side of the rotation shaft of the planetary gear mechanism; Equipped with the input shaft is provided with planetary gear spacing means for spacing the pairs of planetary gears apart to put the pairs of planetary gears into a disengaged state when the input shaft rotates; a two-way clutch, the output shaft including planetary gear approaching means for bringing the pairs of planetary gears closer together to bring the pairs of planetary gears into mesh with each other when the output shaft rotates;

9. 9. The two-way clutch according to claim 8, wherein the planetary gear spacing means includes a first rotor fixed to the input shaft and provided with a plurality of pairs of first holes into which the shafts of each of the pairs of planetary gears are inserted, and the distance between the centers of each of the pairs of first holes is greater than the center-to-center distance of each of the pairs of planetary gears in the meshed state.

10. 9. The two-way clutch according to claim 8, wherein said planet gear spacing means comprises a plurality of planet gear carrier spacing pins fixed to said input shaft and inserted between said plurality of planet gear carriers.

11. 11. A two-way clutch according to claim 9 or 10, wherein the planetary gear approaching means comprises a second rotor fixed to the output shaft and provided with a plurality of pairs of second holes into which the shafts of each of the pairs of planetary gears are inserted, and the distance between the centers of each of the pairs of second holes is the same as the center-to-center distance of each of the pairs of planetary gears in the meshed state.

12. 11. A two-way clutch according to claim 9 or 10, wherein the planetary gear approaching means comprises a plurality of pairs of planetary gear carrier approach pins fixed to the output shaft and inserted into non-opposing sides of each pair of planetary gear carriers.

13. a planetary gear mechanism including an internal gear, a plurality of pairs of planetary gears that rotate and revolve on the internal gear, a rotation shaft at the center of the internal gear, and a plurality of planetary gear carriers that connect the shafts of the planetary gears to the rotation shaft; an input shaft rotatably connected to one side of the rotation shaft of the planetary gear mechanism; an output shaft rotatably connected coaxially to the other side of the rotation shaft of the planetary gear mechanism; Equipped with the input shaft has a first rotor provided with a plurality of pairs of holes into which the shafts of the planetary gears of each pair are inserted, or a plurality of planetary gear carrier spacing pins inserted between the planetary gear carriers of each pair; The output shaft is a two-way clutch having a second rotor having multiple pairs of holes inserted onto the shafts of each of the pairs of planetary gears, or multiple pairs of planetary gear carrier proximity pins inserted onto non-opposing sides of each of the pairs of planetary gear carriers.

14. 14. A two-way clutch according to claim 8 or 13, wherein two of the plurality of planetary gear carriers that are symmetrical with respect to the rotational shaft are integrated on the rotational shaft.

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