Power conversion device

Abstract

To provide a power conversion device which can easily transmit a drive force to an input member.SOLUTION: A radius r1 of a ring gear RG is twice of a radius r2 of a first planetary gear PG1. The first planetary gear PG1 and a second planetary gear PG2 are configured to revolute about a carrier axial core X1 which is a rotation axial core of a carrier CR at the same speed in the same direction. In an axial view, a first planetary axial core X2 which is a rotational axis of the first planetary gear PG1 and a second planetary axial core X3 which is a rotational axis of the second planetary gear PG2 are arranged at positions opposite to each other across the carrier axial core X1 and at the same distance from the carrier axial core X1. In an axial view, a first crank member 2 is connected to the first planetary gear PG1 and a second crank member 4 is connected to the second planetary gear PG2 such that a first input axial core X4 which is away from the first planetary axial core X2 in a first planetary radial direction Rp1 and a second input axial core X5 which is away from the second planetary axial core X3 in a second planetary radial direction Rp2 are positioned opposite to each other across the carrier axial core X1.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a power conversion device that converts reciprocating motion into rotational motion.

Background Art

[0002] Patent Document 1 discloses a power conversion device mounted on a bicycle or the like. In the power conversion device of Patent Document 1, the reciprocating motion of an input member (85) by human power is converted into the rotational motion of an output member (1) via a planetary gear mechanism or the like. Note that the reference numerals shown in parentheses in the description of the background art are those of Patent Document 1.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In the power conversion device of Patent Document 1, the input member (85) moves so as to draw a curved locus at a position displaced from the rotational axis center of the output member (1) (see FIG. 3 of Patent Document 1). Therefore, the above power conversion device has a configuration in which it is difficult to transmit a driving force to the input member (85).

[0005] Therefore, it is desired to realize a power conversion device in which a driving force can be easily transmitted to the input member.

Means for Solving the Problems

[0006] In view of the above, the characteristic configuration of the power conversion device is a planetary gear mechanism including a ring gear which is a fixed internal gear, a first planetary gear meshing with the ring gear, a second planetary gear disposed on a different axis from the first planetary gear, and a carrier rotatably supporting the first planetary gear and the second planetary gear, and A first crank member that is arranged to extend in a first planetary radial direction orthogonal to a first planetary axis that is the rotation axis of the first planetary gear, and that is connected so as to rotate integrally with the first planetary gear; A first input member that is supported by the first crank member and that is arranged on a first input axis spaced apart from the first planetary axis in the first planetary radial direction; A second crank member that is arranged to extend in a second planetary radial direction orthogonal to a second planetary axis that is the rotation axis of the second planetary gear, and that is connected so as to rotate integrally with the second planetary gear; A second input member that is supported by the second crank member and that is arranged on a second input axis spaced apart from the second planetary axis in the second planetary radial direction; An output member that is connected to a specific rotating member that rotates in conjunction with the carrier, excluding the first planetary gear and the second planetary gear; The radius of the ring gear is twice the radius of the first planetary gear; Taking the direction along the carrier axis that is the rotation axis of the carrier as the axial direction; The first planetary gear and the second planetary gear are configured to revolve around the carrier axis at the same speed and in the same direction; In an axial view along the axial direction, the first planetary axis and the second planetary axis are arranged on opposite sides of the carrier axis and at positions where the distances from the carrier axis are the same; In the axial view, the first crank member is connected to the first planetary gear and the second crank member is connected to the second planetary gear such that the first input axis and the second input axis are located on opposite sides of the carrier axis.

[0007] According to this characteristic configuration, the respective movement trajectories of the first input axis and the second input axis accompanying the reciprocating movements of the first input member and the second input member can be linear or elliptical with respect to the carrier axis. Also, the phase difference between the first input axis and the second input axis can be set to 180° or a value close thereto. Therefore, it is possible to realize a power conversion device that easily transmits a driving force to each of the first input member disposed on the first input axis and the second input member disposed on the second input axis.

Brief Description of the Drawings

[0008]

Figure 1

Figure 2

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Figure 8

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Modes for Carrying Out the Invention

[0009] 1. First Embodiment Hereinafter, the power conversion device 100 according to the first embodiment will be described with reference to FIGS. 1 to 7.

[0010] As shown in FIG. 1, the power conversion device 100 includes a planetary gear mechanism 1, a first crank member 2, a first input member 3, a second crank member 4, a second input member 5, and an output member 6. The power conversion device 100 is a device that converts the reciprocating motions of the first input member 3 and the second input member 5 into the rotational motion of the output member 6 by the planetary gear mechanism 1.

[0011] The planetary gear mechanism 1 includes a ring gear RG, a first planetary gear PG1, a second planetary gear PG2, and a carrier CR. The ring gear RG is an internal gear fixed non-rotatably. The first planetary gear PG1 meshes with the ring gear RG. The second planetary gear PG2 is disposed on a different axis from the first planetary gear PG1. The carrier CR rotatably supports the first planetary gear PG1 and the second planetary gear PG2.

[0012] In the following description, the direction along the carrier axis X1, which is the rotation axis of the carrier CR, is defined as the "axial direction L". And one side of the axial direction L is defined as the "first axial side L1", and the other side of the axial direction L is defined as the "second axial side L2". Further, the direction orthogonal to the carrier axis X1 is defined as the "radial direction R". Also, the direction orthogonal to the first planetary axis X2, which is the rotation axis of the first planetary gear PG1, is defined as the "first planetary radial direction Rp1". And the direction orthogonal to the second planetary axis X3, which is the rotation axis of the second planetary gear PG2, is defined as the "second planetary radial direction Rp2".

[0013] The first planetary gear PG1 and the second planetary gear PG2 are configured to rotate (revolve) around the carrier axis X1 at the same speed and in the same direction as each other.

[0014] The first planetary gear PG1 is configured to rotate (rotate on its own axis) around the first planetary axis X2. In the present embodiment, the first planetary gear PG1 is connected so as to rotate integrally with the first planetary shaft PS1, which is a shaft member having the first planetary axis X2 as its rotation axis. In the present embodiment, the first planetary shaft PS1 is disposed so as to penetrate the first planetary gear PG1 in the axial direction L. The first planetary shaft PS1 is rotatably supported with respect to the carrier CR via a pair of first planetary bearings B1 that are disposed on both sides of the first planetary gear PG1 in the axial direction L.

[0015] The second planetary gear PG2 is configured to rotate (rotate on its own axis) around the second planetary axis X3. In the present embodiment, the second planetary gear PG2 is connected so as to rotate integrally with the second planetary shaft PS2, which is a shaft member having the second planetary axis X3 as its rotation axis. In the present embodiment, the second planetary shaft PS2 is disposed so as to penetrate the second planetary gear PG2 in the axial direction L. The second planetary shaft PS2 is rotatably supported with respect to the carrier CR via a pair of second planetary bearings B2 that are disposed on both sides of the second planetary gear PG2 in the axial direction L.

[0016] In the present embodiment, the planetary gear mechanism 1 further includes a second ring gear RG2 in addition to the first ring gear RG1 as the ring gear RG.

[0017] The second ring gear RG2 is an internal gear that is fixed non-rotatably. The second ring gear RG2 meshes with the second planetary gear PG2. In the present embodiment, the second ring gear RG2 is disposed on the second side L2 in the axial direction with respect to the first ring gear RG1.

[0018] In this embodiment, the first ring gear RG1 and the second ring gear RG2 are fixed to a ring gear support portion RS disposed between their axial directions L. The ring gear support portion RS rotatably supports the carrier CR from the outside in the radial direction R via a ring gear bearing B3. In this embodiment, the ring gear support portion RS is formed to extend inward in the radial direction R from the first ring gear RG1 and the second ring gear RG2. Then, the first planetary gear PG1 and the first planetary shaft PS1 are disposed on the first axial side L1 with respect to the ring gear support portion RS, and the second planetary gear PG2 and the second planetary shaft PS2 are disposed on the second axial side L2 with respect to the ring gear support portion RS.

[0019] The radius r1 of the ring gear RG (the first ring gear RG1) is twice the radius r2 of the first planetary gear PG1 (r1 = r2 × 2). Therefore, while the first planetary gear PG1 makes one revolution around the carrier axis X1, it makes one rotation around the first planetary axis X2. That is, the revolution period and the rotation period of the first planetary gear PG1 are equal. In the present application, the "radius of the gear" means the radius of the pitch circle of the gear.

[0020] In this embodiment, the radius r3 of the second ring gear RG2 is twice the radius r4 of the second planetary gear PG2 (r3 = r4 × 2). Therefore, in this embodiment, while the second planetary gear PG2 makes one revolution around the carrier axis X1, it makes one rotation around the second planetary axis X3. That is, in this embodiment, the revolution period and the rotation period of the second planetary gear PG2 are equal.

[0021] Also, in this embodiment, the first ring gear RG1 and the second ring gear RG2 have the same diameter (r1 = r3). And the first planetary gear PG1 and the second planetary gear PG2 have the same diameter (r2 = r4).

[0022] As shown in FIG. 1, the first crank member 2 is arranged to extend in the first planetary radial direction Rp1. The first crank member 2 extends across the first planetary axis X2 and a first input axis X4 spaced apart from the first planetary axis X2 in the first planetary radial direction Rp1. The first crank member 2 is connected so as to rotate integrally with the first planetary gear PG1. In the present embodiment, the first crank member 2 is connected to be non-rotatable relative to a portion on the first axial side L1 of the first planetary gear PG1 on the first planetary shaft PS1.

[0023] The first input member 3 is a member to which a predetermined driving force is input from the outside of the power conversion device 100. The first input member 3 is arranged on the first input axis X4. The first input member 3 is supported by the first crank member 2. In the present embodiment, the first input member 3 is a shaft member arranged to protrude from the first crank member 2 in the first axial direction L1. And the first input member 3 is connected so as to rotate integrally with the first crank member 2.

[0024] The second crank member 4 is arranged to extend in the second planetary radial direction Rp2. The second crank member 4 extends across the second planetary axis X3 and a second input axis X5 spaced apart from the second planetary axis X3 in the second planetary radial direction Rp2. The second crank member 4 is connected so as to rotate integrally with the second planetary gear PG2. In the present embodiment, the second crank member 4 is connected to be non-rotatable relative to a portion on the second axial side L2 of the second planetary gear PG2 on the second planetary shaft PS2.

[0025] The second input member 5 is a member to which a predetermined driving force is input from the outside of the power conversion device 100. The second input member 5 is arranged on the second input axis X5. The second input member 5 is supported by the second crank member 4. In the present embodiment, the second input member 5 is a shaft member arranged to protrude from the second crank member 4 in the second axial direction L2. And the second input member 5 is connected so as to rotate integrally with the second crank member 4.

[0026] In this embodiment, the distance d1 between the first planetary axis X2 and the first input axis X4 in the first planetary radial direction Rp1 is the same as the distance d2 between the second planetary axis X3 and the second input axis X5 in the second planetary radial direction Rp2 (d1 = d2). Also, the radius r2 of the first planetary gear PG1 is the same as the distance d1 between the first planetary axis X2 and the first input axis X4 in the first planetary radial direction Rp1 (r2 = d1). And the radius r4 of the second planetary gear PG2 is the same as the distance d2 between the second planetary axis X3 and the second input axis X5 in the second planetary radial direction Rp2 (r4 = d2).

[0027] Also, in this embodiment, a first pedal P1, which will be described later, is connected to the first input member 3 so as to be relatively rotatable. And a second pedal P2, which will be described later, is connected to the second input member 5 so as to be relatively rotatable.

[0028] The output member 6 is connected to a specific rotating member RT. The specific rotating member RT is a rotating member excluding the first planetary gear PG1 and the second planetary gear PG2, and is a rotating member that rotates in conjunction with the carrier CR. In this embodiment, the specific rotating member RT is the carrier CR. Here, "rotating in conjunction" includes rotating at the same speed and rotating at a predetermined speed ratio, and the direction of rotation is not limited.

[0029] Here, referring to FIGS. 2 to 6, the reciprocating motions of the first input member 3 and the second input member 5 according to this embodiment will be described. In FIGS. 2 to 6, the locus T1 indicated by the dashed-dotted line is the moving locus of each of the first input axis X4 and the second input axis X5 accompanying the reciprocating motions of the first input member 3 and the second input member 5. Also, the locus T2 indicated by the two-dot chain line is the moving locus of each of the first planetary axis X2 and the second planetary axis X3 accompanying the reciprocating motions of the first input member 3 and the second input member 5.

[0030] As described above, the first planetary gear PG1 and the second planetary gear PG2 revolve around the carrier axis X1. Therefore, a locus T2, which is the movement locus of the first planetary axis X2, which is the rotation axis of the first planetary gear PG1, and the second planetary axis X3, which is the rotation axis of the second planetary gear PG2, is circular with the carrier axis X1 as the center in the axial direction view along the axial direction L.

[0031] As described above, in the present embodiment, the first ring gear RG1 and the second ring gear RG2 have the same diameter, and the first planetary gear PG1 and the second planetary gear PG2 have the same diameter. Therefore, in the present embodiment, the movement locus of the first planetary axis X2 and the movement locus of the second planetary axis X3 accompanying the reciprocating movement of the first input member 3 and the second input member 5 coincide with each other in the axial direction view along the axial direction L.

[0032] As shown in FIGS. 2 to 6, in the axial direction view along the axial direction L, the first planetary axis X2 and the second planetary axis X3 are on opposite sides of each other with the carrier axis X1 interposed therebetween, and are arranged at positions where the distances from the carrier axis X1 are the same. In the present embodiment, in the axial direction view along the axial direction L, the first planetary axis X2, the carrier axis X1, and the second planetary axis X3 are arranged in a straight line. That is, in the present embodiment, the first planetary axis X2 and the second planetary axis X3 are arranged with a phase difference of 180°.

[0033] As shown in FIGS. 2 to 6, in the axial direction view along the axial direction L, the first crank member 2 is connected to the first planetary gear PG1 and the second crank member 4 is connected to the second planetary gear PG2 such that the first input axis X4 and the second input axis X5 are located on opposite sides of each other with the carrier axis X1 interposed therebetween. In the present embodiment, the direction along the straight line passing through the first planetary axis X2 and the first input axis X4, that is, the extending direction of the first crank member 2, and the direction along the straight line passing through the second planetary axis X3 and the second input axis X5, that is, the extending direction of the second crank member 4, are arranged to be parallel to each other.

[0034] As described above, in the present embodiment, the radius r2 of the first planetary gear PG1 is the same as the distance d1 in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4, and the radius r4 of the second planetary gear PG2 is the same as the distance d2 in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5. Therefore, in the present embodiment, the locus T1, which is the movement locus of the first input axis X4 and the second input axis X5, is linear and passes through the carrier axis X1 in the axial direction view along the axial direction L.

[0035] As described above, in the present embodiment, the distance d1 in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4 is the same as the distance d2 in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5. And, in the axial direction view along the axial direction L, the first input axis X4, the carrier axis X1, and the second input axis X5 are arranged in a straight line. Therefore, in the present embodiment, the movement locus of the first input axis X4 and the movement locus of the second input axis X5 accompanying the reciprocating movement of the first input member 3 and the second input member 5 coincide with each other in the axial direction view along the axial direction L.

[0036] In the example shown in FIG. 2, in the axial direction view along the axial direction L, the first input axis X4 is located on the opposite side of the carrier axis X1 with respect to the first planetary axis X2, and the second input axis X5 is located on the opposite side of the carrier axis X1 with respect to the second planetary axis X3. And, in the axial direction view along the axial direction L, the first input axis X4, the first planetary axis X2, the carrier axis X1, the second planetary axis X3, and the second input axis X5 are arranged in a straight line. At this time, based on the circular locus T2, the phase of the first planetary axis X2 is set to 0°, and the phase of the second planetary axis X3 is set to 180°.

[0037] In the example shown in FIG. 3, the first planetary axis X2 and the second planetary axis X3 are rotated clockwise by 45° about the carrier axis X1 from the state shown in FIG. 2. That is, the phase of the first planetary axis X2 is 45°, and the phase of the second planetary axis X3 is 225°. At this time, the first input axis X4 and the second input axis X5 are closer to the carrier axis X1 than in the state shown in FIG. 2.

[0038] In the example shown in FIG. 4, the first planetary axis X2 and the second planetary axis X3 have rotated 45° clockwise about the carrier axis X1 from the state shown in FIG. 3. That is, the phase of the first planetary axis X2 is 90°, and the phase of the second planetary axis X3 is 270°. At this time, the first input axis X4 and the second input axis X5 are located on the carrier axis X1.

[0039] In the example shown in FIG. 5, the first planetary axis X2 and the second planetary axis X3 have rotated 45° clockwise about the carrier axis X1 from the state shown in FIG. 4. That is, the phase of the first planetary axis X2 is 135°, and the phase of the second planetary axis X3 is 315°. At this time, the first input axis X4 and the second input axis X5 are separated from the carrier axis X1 more than in the state shown in FIG. 4.

[0040] In the example shown in FIG. 6, the first planetary axis X2 and the second planetary axis X3 have rotated 45° clockwise about the carrier axis X1 from the state shown in FIG. 5. That is, the phase of the first planetary axis X2 is 180°, and the phase of the second planetary axis X3 is 0°. At this time, in the axial direction view along the axial direction L, the first input axis X4 is located on the side opposite to the carrier axis X1 with respect to the first planetary axis X2, and the second input axis X5 is located on the side opposite to the carrier axis X1 with respect to the second planetary axis X3. And, in the axial direction view along the axial direction L, the first input axis X4, the first planetary axis X2, the carrier axis X1, the second planetary axis X3, and the second input axis X5 are aligned in a straight line.

[0041] Note that the description of the process until the phase of the first planetary axis X2 becomes 0° hereafter is omitted, but as described above, the first input member 3 and the second input member 5 perform a reciprocating motion so that the first input axis X4 and the second input axis X5 draw a linear locus T1.

[0042] As described above, in the axial view along the axial direction L, the first input axis center X4 and the second input axis center X5 are located on opposite sides of the carrier axis center X1 with the carrier axis center X1 interposed therebetween. The first crank member 2 is connected to the first planetary gear PG1, and the second crank member 4 is connected to the second planetary gear PG2. Here, in the present embodiment, a locus T1 is drawn such that the first input axis center X4 and the second input axis center X5 pass above the carrier axis center X1. Therefore, in the present application, "in the axial view along the axial direction L, the first input axis center X4 and the second input axis center X5 are located on opposite sides of the carrier axis center X1 with the carrier axis center X1 interposed therebetween" includes that at least one of the first input axis center X4 and the second input axis center X5 is arranged so as to draw a locus T1 passing above the carrier axis center X1.

[0043] As shown in FIG. 7, in the present embodiment, the power conversion device 100 is mounted on the bicycle B. Therefore, in the present embodiment, the power conversion device 100 converts the reciprocating motion of the first input member 3 and the second input member 5 by the operation of the driver of the bicycle B into a rotational motion of the output member 6 and outputs the rotational motion. In the example shown in FIG. 7, the power conversion device 100 is arranged such that the locus T1 is inclined with respect to the horizontal direction and goes upward as it goes toward the rear of the bicycle B (the right side in FIG. 7).

[0044] In addition to the first pedal P1 and the second pedal P2 described above, the bicycle B includes a seat S, a handle H, a frame F, a drive wheel W1, a driven wheel W2, and a transmission mechanism T.

[0045] The first pedal P1 and the second pedal P2 are members for the driver to step on with their feet. The seat S is a member for the driver to sit on. The handle H is a member for the driver to grip. The frame F is a member that supports the seat S, the handle H, the drive wheel W1, the driven wheel W2, and the power conversion device 100. The ring gear RG of the planetary gear mechanism 1 in the power conversion device 100 is fixed to the frame F via a ring gear fixing member RF.

[0046] The drive wheel W1 is configured to rotate in conjunction with the operation of the driver. The driven wheel W2 is rotatably supported with respect to the frame F. In the present embodiment, the drive wheel W1 is the rear wheel and the driven wheel W2 is the front wheel.

[0047] The transmission mechanism T is configured to transmit the rotation of the output member 6 of the power conversion device 100 to the drive wheel W1. In the present embodiment, the transmission mechanism T includes a first sprocket SP1, a second sprocket SP2, a third sprocket SP3, a fourth sprocket SP4, a first chain CH1, and a second chain CH2.

[0048] The first sprocket SP1 is disposed on the carrier axis X1. In the present embodiment, the first sprocket SP1 is connected so as to rotate integrally with the carrier CR as the specific rotating member RT (see FIG. 1). That is, in the present embodiment, the first sprocket SP1 functions as the output member 6.

[0049] The first chain CH1 is wound around the first sprocket SP1 and the second sprocket SP2. Therefore, the second sprocket SP2 rotates following the first sprocket SP1. In the example shown in FIG. 7, the second sprocket SP2 is formed to have a smaller diameter than the first sprocket SP1.

[0050] The third sprocket SP3 is disposed coaxially with the second sprocket SP2. The third sprocket SP3 is connected so as to rotate integrally with the second sprocket SP2. In the example shown in FIG. 7, the third sprocket SP3 is formed to have a larger diameter than the second sprocket SP2.

[0051] The second chain CH2 is wound around the third sprocket SP3 and the fourth sprocket SP4. The fourth sprocket SP4 is disposed coaxially with the drive wheel W1. In the example shown in FIG. 7, the fourth sprocket SP4 is formed to have a smaller diameter than the third sprocket SP3.

[0052] 2. Second Embodiment Hereinafter, the power transmission device 100 according to the second embodiment will be described with reference to FIGS. 8 to 14. In this embodiment, the configurations of the first crank member 2 and the second crank member 4 are different from those of the first embodiment described above. Hereinafter, the description will focus on the differences from the first embodiment. Note that, for points not particularly described, the same applies as in the first embodiment.

[0053] As shown in FIG. 8, in this embodiment, the radius r2 of the first planetary gear PG1 is different from the distance d1 in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4 (r2 ≠ d1). And the radius r4 of the second planetary gear PG2 is different from the distance d2 in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5 (r4 ≠ d2). In the example shown in FIG. 8, the distance d1 in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4 is larger than the radius r2 of the first planetary gear PG1 (r2 < d1). And the distance d2 in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5 is larger than the radius r4 of the second planetary gear PG2 (r4 < d2). Note that also in this embodiment, similar to the first embodiment, the distance d1 in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4 and the distance d2 in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5 are the same (d1 = d2).

[0054] Here, with reference to FIGS. 9 to 13, the reciprocating motions of the first input member 3 and the second input member 5 according to this embodiment will be described. In FIGS. 9 to 13, the locus T1 indicated by the dashed-dotted line is the moving locus of each of the first input axis X4 and the second input axis X5 accompanying the reciprocating motions of the first input member 3 and the second input member 5. Also, the locus T2 indicated by the two-dot chain line is the moving locus of each of the first planetary axis X2 and the second planetary axis X3 accompanying the reciprocating motions of the first input member 3 and the second input member 5.

[0055] As described above, in the present embodiment, the radius r2 of the first planetary gear PG1 is different from the distance d1 in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4, and the radius r4 of the second planetary gear PG2 is different from the distance d2 in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5. Therefore, in the present embodiment, the locus T1, which is the movement locus of the first input axis X4 and the second input axis X5, is elliptical with the carrier axis X1 as the center in the axial direction view along the axial direction L.

[0056] As described above, in the present embodiment, the distance d1 in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4 is the same as the distance d2 in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5. And, in the axial direction view along the axial direction L, the first input axis X4, the carrier axis X1, and the second input axis X5 are arranged in a straight line. Therefore, in the present embodiment, the movement locus of the first input axis X4 and the movement locus of the second input axis X5 accompanying the reciprocating movement of the first input member 3 and the second input member 5 coincide with each other in the axial direction view along the axial direction L.

[0057] In the example shown in FIG. 9, in the axial direction view along the axial direction L, the first input axis X4 is located on the side opposite to the carrier axis X1 with respect to the first planetary axis X2, and the second input axis X5 is located on the side opposite to the carrier axis X1 with respect to the second planetary axis X3. And, in the axial direction view along the axial direction L, the first input axis X4, the first planetary axis X2, the carrier axis X1, the second planetary axis X3, and the second input axis X5 are arranged in a straight line. At this time, based on the circular locus T2, the phase of the first planetary axis X2 is set to 0°, and the phase of the second planetary axis X3 is set to 180°.

[0058] In the example shown in FIG. 10, the first planetary axis X2 and the second planetary axis X3 are rotated 45° clockwise about the carrier axis X1 from the state shown in FIG. 9. That is, the phase of the first planetary axis X2 is 45°, and the phase of the second planetary axis X3 is 225°. At this time, the first input axis X4 and the second input axis X5 are rotated counterclockwise about the carrier axis X1 from the state shown in FIG. 9.

[0059] In the example shown in FIG. 11, the first planetary axis X2 and the second planetary axis X3 have rotated 45° clockwise about the carrier axis X1 from the state shown in FIG. 10. That is, the phase of the first planetary axis X2 is 90°, and the phase of the second planetary axis X3 is 270°. At this time, in the axial view along the axial direction L, the first input axis X4 and the second input axis X5 are located on a straight line passing through the first planetary axis X2, the carrier axis X1, and the second planetary axis X3. That is, in the axial view along the axial direction L, the first input axis X4 is located between the carrier axis X1 and the second planetary axis X3, and the second input axis X5 is located between the carrier axis X1 and the first planetary axis X2, so that the first planetary axis X2, the second input axis X5, the carrier axis X1, the first input axis X4, and the second planetary axis X3 are aligned in a straight line.

[0060] In the example shown in FIG. 12, the first planetary axis X2 and the second planetary axis X3 have rotated 45° clockwise about the carrier axis X1 from the state shown in FIG. 11. That is, the phase of the first planetary axis X2 is 135°, and the phase of the second planetary axis X3 is 315°. At this time, the first input axis X4 and the second input axis X5 have rotated counterclockwise about the carrier axis X1 from the state shown in FIG. 11.

[0061] In the example shown in FIG. 13, the first planetary axis X2 and the second planetary axis X3 have rotated 45° clockwise about the carrier axis X1 from the state shown in FIG. 12. That is, the phase of the first planetary axis X2 is 180°, and the phase of the second planetary axis X3 is 0°. At this time, in the axial view along the axial direction L, the first input axis X4 is located on the side opposite to the carrier axis X1 with respect to the first planetary axis X2, and the second input axis X5 is located on the side opposite to the carrier axis X1 with respect to the second planetary axis X3. And, in the axial view along the axial direction L, the first input axis X4, the first planetary axis X2, the carrier axis X1, the second planetary axis X3, and the second input axis X5 are aligned in a straight line.

[0062] Note that the description of the process until the phase of the first planetary axis X2 becomes 0° hereinafter is omitted. As described above, the first input member 3 and the second input member 5 perform reciprocating motions such that the first input axis X4 and the second input axis X5 draw an elliptical locus T1.

[0063] As shown in FIG. 14, in the present embodiment, the configuration of the bicycle B equipped with the power conversion device 100 is different from that of the first embodiment. Specifically, in the present embodiment, the bicycle B further includes a generator G and a motor (not shown). And the transmission mechanism T is configured to transmit the rotation of the output member 6 of the power conversion device 100 to the generator G.

[0064] In the present embodiment, instead of the second sprocket SP2, the third sprocket SP3, the fourth sprocket SP4, the first chain CH1, and the second chain CH2, the transmission mechanism T includes a fifth sprocket SP5 and a third chain CH3.

[0065] The fifth sprocket SP5 is connected so as to rotate integrally with the rotor of the generator G. The third chain CH3 is wound around the first sprocket SP1 and the fifth sprocket SP5. In the example shown in FIG. 14, the fifth sprocket SP5 is formed to have a smaller diameter than the first sprocket SP1.

[0066] The generator G is configured to generate electricity by the driving force transmitted through the transmission mechanism T and store the electricity in a power storage device (not shown). The motor receives power supply from the power storage device and performs power running to drive the drive wheel W1.

[0067] 3. Third Embodiment Hereinafter, the power conversion device 100 according to the third embodiment will be described with reference to FIG. 15. In the present embodiment, the configuration of the planetary gear mechanism 1 is different from that of the first embodiment. Hereinafter, the description will focus on the differences from the first embodiment. Note that points not particularly described are the same as those in the first embodiment.

[0068] As shown in FIG. 15, in the present embodiment, the planetary gear mechanism 1 further includes a third planetary gear PG3 and a sun gear SG. In the present embodiment, the planetary gear mechanism 1 does not include a second ring gear RG2.

[0069] The third planetary gear PG3 is disposed on the first planetary axis X2 at a position different from that of the first planetary gear PG1 in the axial direction L. The third planetary gear PG3 is connected so as to rotate integrally with the first planetary gear PG1. In the present embodiment, the third planetary gear PG3 is disposed on the second side L2 in the axial direction with respect to the first planetary gear PG1. And the third planetary gear PG3 is connected so as to rotate integrally with the first planetary shaft PS1.

[0070] In the present embodiment, the first planetary shaft PS1 is disposed so as to penetrate the first planetary gear PG1 and the third planetary gear PG3 in the axial direction L. And the first planetary shaft PS1 is rotatably supported with respect to the carrier CR via a pair of first planetary bearings B1 that are separated and disposed on the first side L1 in the axial direction with respect to the first planetary gear PG1 and on the second side L2 in the axial direction with respect to the third planetary gear PG3.

[0071] The sun gear SG is disposed on the carrier axis X1. The sun gear SG meshes with the second planetary gear PG2 and the third planetary gear PG3. In the present embodiment, the sun gear SG is rotatably supported with respect to the carrier CR via a sun gear bearing B6 disposed inside the sun gear SG in the radial direction R.

[0072] In the present embodiment, the radius r4 of the second planetary gear PG2 is the same as the radius r5 of the third planetary gear PG3. That is, the second planetary gear PG2 and the third planetary gear PG3 have the same diameter. Also, each of the radius r4 of the second planetary gear PG2 and the radius r5 of the third planetary gear PG3 is smaller than the radius r2 of the first planetary gear PG1. That is, each of the second planetary gear PG2 and the third planetary gear PG3 has a smaller diameter than the first planetary gear PG1.

[0073] In this embodiment, the ring gear RG is fixed to the first ring gear support portion RS1 and the second ring gear support portion RS2. The first ring gear support portion RS1 is disposed on the first axial side L1 with respect to the ring gear RG. The first ring gear support portion RS1 rotatably supports the carrier CR from the outside in the radial direction R via the first ring gear bearing B4. The second ring gear support portion RS2 is disposed on the second axial side L2 with respect to the ring gear RG. The second ring gear support portion RS2 rotatably supports the carrier CR from the outside in the radial direction R via the second ring gear bearing B5.

[0074] In this embodiment, the first planetary bearing B1 on the first axial side L1, the second planetary bearing B2 on the first axial side L1, and the first ring gear bearing B4 are arranged such that their arrangement regions in the axial direction L overlap each other. Further, the first planetary bearing B1 on the second axial side L2, the second planetary bearing B2 on the second axial side L2, and the second ring gear bearing B5 are arranged such that their arrangement regions in the axial direction L overlap each other. Thereby, the dimension of the planetary gear mechanism 1 in the axial direction L can be suppressed to be small, and by extension, the axial dimension of the power conversion device 100 can be reduced.

[0075] 4. Other Embodiments (1) In the above embodiment, the configuration in which the first input member 3 is a shaft member fixed to the first crank member 2 and the second input member 5 is a shaft member fixed to the second crank member 4 has been described as an example. However, the present invention is not limited to such a configuration. For example, a shaft member as the first input member 3 and a shaft member as the second input member 5 may not be provided, and a part of the first crank member 2 may function as the first input member 3, and a part of the second crank member 4 may function as the second input member 5.

[0076] (2) In the above embodiment, the configuration in which the first planetary axis X2 and the second planetary axis X3 are arranged with a phase difference of 180° has been described as an example. However, the present invention is not limited to such a configuration, and the first planetary axis X2 and the second planetary axis X3 may be arranged with a phase difference different from 180°.

[0077] (3) In the above-described embodiment, in the locus T1, as an example, a configuration is described in which, in the axial view along the axial direction L, the first input axis center X4, the first planetary axis center X2, the carrier axis center X1, the second planetary axis center X3, and the second input axis center X5 are aligned in a straight line. However, the present invention is not limited to such a configuration, and in the locus T1, in the axial view along the axial direction L, a configuration in which the first input axis center X4, the first planetary axis center X2, the carrier axis center X1, the second planetary axis center X3, and the second input axis center X5 are not aligned in a straight line may also be used.

[0078] (4) In the above-described embodiment, as an example, a configuration is described in which the direction along the straight line passing through the first planetary axis center X2 and the first input axis center X4 (the extending direction of the first crank member 2) and the direction along the straight line passing through the second planetary axis center X3 and the second input axis center X5 (the extending direction of the second crank member 4) are arranged to be parallel to each other. However, the present invention is not limited to such a configuration, and the extending direction of the first crank member 2 and the extending direction of the second crank member 4 may be arranged to intersect each other.

[0079] (5) In the above-described embodiment, as an example, a configuration is described in which the first ring gear RG1 and the second ring gear RG2 have the same diameter. However, the present invention is not limited to such a configuration, and the first ring gear RG1 and the second ring gear RG2 may have different diameters.

[0080] (6) In addition, the configurations disclosed in the above-described embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction occurs. Regarding other configurations as well, all the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications can be made as appropriate within the scope not departing from the gist of the present disclosure.

[0081] 5. Summary of this embodiment Hereinafter, an overview of the power transmission device (100) described above will be described.

[0082] The power transmission device (100) is A planetary gear mechanism (1) comprising a ring gear (RG) which is a fixed internal gear, a first planetary gear (PG1) meshing with the ring gear (RG), a second planetary gear (PG2) disposed on a different axis from the first planetary gear (PG1), and a carrier (CR) rotatably supporting the first planetary gear (PG1) and the second planetary gear (PG2). A first crank member (2) which is arranged to extend in a first planetary radial direction (Rp1) orthogonal to a first planetary axis (X2) which is the rotation axis of the first planetary gear (PG1), and is connected so as to rotate integrally with the first planetary gear (PG1). A first input member (3) supported by the first crank member (2) and disposed on a first input axis (X4) spaced from the first planetary axis (X2) in the first planetary radial direction (Rp1). A second crank member (4) which is arranged to extend in a second planetary radial direction (Rp2) orthogonal to a second planetary axis (X3) which is the rotation axis of the second planetary gear (PG2), and is connected so as to rotate integrally with the second planetary gear (PG2). A second input member (5) supported by the second crank member (4) and disposed on a second input axis (X5) spaced from the second planetary axis (X3) in the second planetary radial direction (Rp2). An output member (6) connected to a specific rotating member (RT) that rotates in conjunction with the carrier (CR) excluding the first planetary gear (PG1) and the second planetary gear (PG2). The radius (r1) of the ring gear (RG) is twice the radius (r2) of the first planetary gear (PG1). Taking the direction along the carrier axis (X1) which is the rotation axis of the carrier (CR) as the axial direction (L). The first planetary gear (PG1) and the second planetary gear (PG2) are configured to revolve around the carrier axis (X1) at the same speed and in the same direction. In an axial view along the axial direction (L), the first planetary axis (X2) and the second planetary axis (X3) are on opposite sides of the carrier axis (X1) with the carrier axis (X1) in between, and are arranged at positions where the distances from the carrier axis (X1) are the same. In the axial direction view, the first crank member (2) is connected to the first planetary gear (PG1), and the second crank member (4) is connected to the second planetary gear (PG2) such that the first input axis (X4) and the second input axis (X5) are located on opposite sides of the carrier axis (X1).

[0083] According to this configuration, the movement trajectories (T1) of the first input axis (X4) and the second input axis (X5) accompanying the reciprocating motions of the first input member (3) and the second input member (5) can be made linear or elliptical with respect to the carrier axis (X1). Also, the phase difference between the first input axis (X4) and the second input axis (X5) can be made 180° or a value close thereto. Therefore, a power conversion device (100) that can easily transmit the driving force to each of the first input member (3) disposed on the first input axis (X4) and the second input member (5) disposed on the second input axis (X5) can be realized.

[0084] Here, the planetary gear mechanism (1) further includes a second ring gear (RG2) which is a fixed internal gear in addition to the first ring gear (RG1) as the ring gear (RG). The second planetary gear (PG2) meshes with the second ring gear (RG2). Preferably, the radius (r3) of the second ring gear (RG2) is twice the radius (r4) of the second planetary gear (PG2).

[0085] According to this configuration, the driving force transmission structure from the first crank member (2) to the carrier (CR) and the driving force transmission structure from the second crank member (4) to the carrier (CR) can be made similar. Therefore, the power conversion device (100) can be easily configured simply. Further, according to this configuration, when the radius (r1) of the first ring gear (RG1) is made the same as the radius (r3) of the second ring gear (RG2), the first ring gear (RG1) and the first planetary gear (PG1), and the second ring gear (RG2) and the second planetary gear (PG2) can share components, making it easy to reduce the number of types of components.

[0086] Further, the planetary gear mechanism (1) includes a third planetary gear (PG3) that is disposed on the first planetary axis (X2) at a position different from the first planetary gear (PG1) in the axial direction (L) and is connected to rotate integrally with the first planetary gear (PG1), and a sun gear (SG) disposed on the carrier axis (X1). The radius (r4) of the second planetary gear (PG2) is the same as the radius (r5) of the third planetary gear (PG3). It is preferable that the second planetary gear (PG2) and the third planetary gear (PG3) mesh with the sun gear (SG).

[0087] According to this configuration, a configuration in which the first planetary gear (PG1) and the second planetary gear (PG2) rotate at the same speed and in the same direction can be appropriately realized.

[0088] Further, the distance (d1) in the first planetary radial direction (Rp1) between the first planetary axis (X2) and the first input axis (X4) is the same as the distance (d2) in the second planetary radial direction (Rp2) between the second planetary axis (X3) and the second input axis (X5). It is preferable that the radius (r2) of the first planetary gear (PG1) is different from the distance (d1) in the first planetary radial direction (Rp1) between the first planetary axis (X2) and the first input axis (X4).

[0089] According to this configuration, the respective movement trajectories (T1) of the first input axis (X4) and the second input axis (X5) accompanying the reciprocating movements of the first input member (3) and the second input member (5) can be made elliptical with the carrier axis (X1) as the center. Also, according to this configuration, when the distance (d1) in the first planetary radial direction (Rp1) between the first planetary axis (X2) and the first input axis (X4) is made larger than the radius (r2) of the first planetary gear (PG1), it becomes easier to ensure a larger stroke of the reciprocating motion of the first input member (3) and the second input member (5). Therefore, it is easy to reduce the size of the planetary gear mechanism (1). Also, according to this configuration, when the distance (d1) in the first planetary radial direction (Rp1) between the first planetary axis (X2) and the first input axis (X4) is made smaller than the radius (r2) of the first planetary gear (PG1), the rotational directions (directions of elliptical movement) of the first input axis (X4) and the second input axis (X5) accompanying the reciprocating motion of the first input member (3) and the second input member (5) can be made the same as the rotational direction of the carrier (CR).

Industrial Applicability

[0090] The technology according to the present disclosure can be used in a power conversion device that converts reciprocating motion into rotational motion.

Explanation of Reference Numerals

[0091] 100: Power conversion device, 1: Planetary gear mechanism, RG: Ring gear, RG1: First ring gear, RG2: Second ring gear, PG1: First planetary gear, PG2: Second planetary gear, PG3: Third planetary gear, CR: Carrier, SG: Sun gear, 2: First crank member, 3: First input member, 4: Second crank member, 5: Second input member, 6: Output member, RT: Specific rotating member, X1: Carrier axis, X2: First planetary axis, X3: Second planetary axis, X4: First input axis, X5: Second input axis, L: Axial direction, Rp1: First planetary radial direction, Rp2: Second planetary radial direction

Claims

1. A planetary gear mechanism comprising a ring gear which is a fixed internal gear, a first planetary gear meshing with the ring gear, a second planetary gear arranged on a different axis from the first planetary gear, and a carrier rotatably supporting the first planetary gear and the second planetary gear, a first crank member arranged to extend in a first planetary radial direction orthogonal to a first planetary axis which is a rotation axis of the first planetary gear, and connected to rotate integrally with the first planetary gear, a first input member supported by the first crank member and arranged on a first input axis spaced from the first planetary axis in the first planetary radial direction, a second crank member arranged to extend in a second planetary radial direction orthogonal to a second planetary axis which is a rotation axis of the second planetary gear, and connected to rotate integrally with the second planetary gear, a second input member supported by the second crank member and arranged on a second input axis spaced from the second planetary axis in the second planetary radial direction, and an output member connected to a specific rotating member that rotates in conjunction with the carrier, excluding the first planetary gear and the second planetary gear, wherein a radius of the ring gear is twice a radius of the first planetary gear, with a direction along a carrier axis which is a rotation axis of the carrier as an axial direction, wherein the first planetary gear and the second planetary gear are configured to revolve around the carrier axis at the same speed and in the same direction, in an axial view along the axial direction, the first planetary axis and the second planetary axis are located on opposite sides of the carrier axis and at positions where distances from the carrier axis are the same, in the axial view, the first crank member is connected to the first planetary gear and the second crank member is connected to the second planetary gear such that the first input axis and the second input axis are located on opposite sides of the carrier axis. A power conversion device.

2. The planetary gear mechanism further comprises a second ring gear which is a fixed internal gear in addition to the first ring gear as the ring gear, the second planetary gear meshes with the second ring gear, wherein a radius of the second ring gear is twice a radius of the second planetary gear. The power conversion device according to Claim 1.

3. The planetary gear mechanism further includes a third planetary gear that is disposed on the first planetary axis and at a position different from the first planetary gear in the axial direction and is connected so as to rotate integrally with the first planetary gear, and a sun gear disposed on the carrier axis. The radius of the second planetary gear is the same as the radius of the third planetary gear. The power conversion device according to claim 1, wherein the second planetary gear and the third planetary gear are engaged with the sun gear.

4. The distance in the first planetary radial direction between the first planetary axis and the first input axis is the same as the distance in the second planetary radial direction between the second planetary axis and the second input axis. The power conversion device according to any one of claims 1 to 3, wherein the radius of the first planetary gear is different from the distance in the first planetary radial direction between the first planetary axis and the first input axis.

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