Power conversion device, and electric power generator provided with the same

Abstract

To provide a technology easily enhancing mountability of a power conversion device on a mounting object.SOLUTION: A linkage mechanism 3 that causes a first planetary gear PG1 and a second planetary gear PG2 to revolve together at the same speed in the same direction includes a carrier coupling member 31 coupling a first carrier CR1 and a second carrier CR2 so as to integrally rotate. In an axial view along an axial direction (L), a first planetary axis X2 as a rotation axis of the first planetary gear PG1 and a second planetary axis X3 as a rotation axis of the second planetary gear PG 2 are disposed on positions opposite one another across a carrier axis X1 as a rotation axis of the first carrier CR1 and the second carrier CR2 and equidistant from the carrier axis X1. A first planetary gear mechanism 21 and a second planetary gear mechanism 22 are dispose apart from each other in the axial direction L. An output member 6 is provided with an intermediate disposition part 60 disposed between the first planetary gear mechanism 21 and the second planetary gear mechanism 22 in the axial direction L.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a power conversion device that converts reciprocating motion into rotational motion, and a power generation device equipped with the same.

Background Art

[0002] Patent Document 1 discloses a power conversion device mounted on a bicycle or the like (see FIGS. 3 and 4 of Patent Document 1). The power conversion device of Patent Document 1 includes a pair of planetary gear mechanisms, a pair of crank members (7), and a pair of input members (8). Note that the reference numerals shown in parentheses in the description of the background art are those of Patent Document 1.

[0003] The pair of planetary gear mechanisms are arranged adjacent to each other in the axial direction (the vertical direction in FIG. 3 of Patent Document 1). Each of the pair of planetary gear mechanisms includes a sun gear (2) supported non-rotatably, an inner planetary gear (3) meshing with the sun gear, an outer planetary gear (4) meshing with the inner planetary gear, and carriers (5, 6) rotatably supporting the inner planetary gear and the outer planetary gear.

[0004] Each of the pair of crank members (7) is formed to extend radially outward from a planetary shaft (11) that rotates integrally with the outer planetary gear (4). Each of the pair of input members (8) is supported by the crank member (7) at a position spaced apart from the planetary shaft (11).

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0006] In the power conversion device of Patent Document 1, one carrier (5) is configured as a pulley around which a belt (19) for transmitting driving force to a wheel is wound. As described above, one carrier (5) rotatably supports an inner planetary gear and an outer planetary gear that mesh with each other. Therefore, the carrier (5) as a pulley is likely to have a large diameter, and the mountability of the power conversion device to a mounting target such as a bicycle is poor.

[0007] Therefore, it is desired to realize a technology that can easily improve the mountability of the power conversion device to the mounting target.

Means for Solving the Problems

[0008] In view of the above, the characteristic configuration of the power conversion device is a support member, a first planetary gear mechanism including a first carrier rotatably supported by the support member and a first planetary gear rotatably supported by the first carrier, a second planetary gear mechanism including a second carrier rotatably supported by the support member and a second planetary gear rotatably supported by the second carrier, a linkage mechanism that interlocks the first planetary gear and the second planetary gear so that they revolve at the same speed and in the same direction, a first crank member that is arranged to extend in a first planetary radial direction, which is a direction orthogonal to a first planetary axis that is the rotation axis of the first planetary gear, and is connected to rotate integrally with the first planetary gear, a first input member that is supported by the first crank member and is arranged on a first input axis that is 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, which is a direction orthogonal to a second planetary axis that is the rotation axis of the second planetary gear, and is connected to rotate integrally with the second planetary gear, a second input member that is supported by the second crank member and is arranged on a second input axis that is spaced apart from the second planetary axis in the second planetary radial direction, An output member connected to an output rotating member that rotates in conjunction with the first carrier and the second carrier, excluding the first planetary gear and the second planetary gear. The interlocking mechanism includes a carrier connecting member that connects the first carrier and the second carrier so that the first carrier and the second carrier rotate integrally. With the direction along the carrier axis, which is the rotation axis of the first carrier and the second carrier, defined as the axial 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 the same distance from the carrier axis. The first planetary gear mechanism and the second planetary gear mechanism are arranged spaced apart from each other in the axial direction. The output member is provided with an intermediate arrangement portion arranged between the first planetary gear mechanism and the second planetary gear mechanism in the axial direction.

[0009] According to this characteristic configuration, an intermediate arrangement portion of the output member is arranged between the first planetary gear mechanism and the second planetary gear mechanism that are arranged spaced apart from each other in the axial direction. Thereby, in a configuration where driving force is transmitted through the intermediate arrangement portion, it is easy to reduce the size of the power conversion device. Therefore, it is easy to improve the mountability of the power conversion device to the mounting target.

Brief Description of the Drawings

[0010]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Figure 13

MODE FOR CARRYING OUT THE INVENTION

[0011] 1. First Embodiment Hereinafter, a power conversion device 10 according to the first embodiment and a power generation device 100 including the same will be described with reference to FIGS. 1 to 7.

[0012] As shown in FIG. 1, the power conversion device 10 includes a support member 1, a first planetary gear mechanism 21, a second planetary gear mechanism 22, an interlocking mechanism 3, a first crank member 41, a second crank member 42, a first input member 51, a second input member 52, and an output member 6.

[0013] The first planetary gear mechanism 21 includes a first carrier CR1 and a first planetary gear PG1. The first carrier CR1 is rotatably supported with respect to the support member 1. The first planetary gear PG1 is rotatably supported with respect to the first carrier CR1.

[0014] The second planetary gear mechanism 22 includes a second carrier CR2 and a second planetary gear PG2. The second carrier CR2 is rotatably supported with respect to the support member 1. The second planetary gear PG2 is rotatably supported with respect to the second carrier CR2.

[0015] In the following description, the direction along the carrier axis X1, which is the rotation axis of the first carrier CR1 and the second carrier CR2, is defined as the "axial direction L". 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".

[0016] The first planetary gear mechanism 21 and the second planetary gear mechanism 22 are arranged coaxially. The first planetary gear mechanism 21 and the second planetary gear mechanism 22 are arranged spaced apart from each other in the axial direction L. In the present embodiment, the first planetary gear mechanism 21 is arranged on the first axial side L1 with respect to the second planetary gear mechanism 22.

[0017] The first planetary gear PG1 is configured to rotate (revolve) around the carrier axis X1 and rotate (rotate on its own axis) around the first planetary axis X2. In the present embodiment, the first planetary gear PG1 rotates once around the first planetary axis X2 while making one revolution around the carrier axis X1. That is, in the present embodiment, the revolution period and the rotation period of the first planetary gear PG1 are equal.

[0018] In the present embodiment, the first planetary gear PG1 is connected so as to rotate integrally with a first planetary shaft PS1, which is a shaft member having a first planetary axis X2 as a 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 first carrier CR1 via a pair of first planetary bearings B1 that are separately disposed on both sides of the first planetary gear PG1 in the axial direction L. Thus, in the present embodiment, the first planetary gear PG1 is supported on both sides in the axial direction L by the first carrier CR1.

[0019] The second planetary gear PG2 is configured to rotate (revolve) around the carrier axis X1 and rotate (rotate on its own axis) around the second planetary axis X3. In the present embodiment, the second planetary gear PG2 rotates once around the second planetary axis X3 while making one revolution around the carrier axis X1. That is, in the present embodiment, the revolution period and the rotation period of the second planetary gear PG2 are equal.

[0020] In the present embodiment, the second planetary gear PG2 is connected so as to rotate integrally with a second planetary shaft PS2, which is a shaft member having a second planetary axis X3 as a 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 second carrier CR2 via a pair of second planetary bearings B2 that are separately disposed on both sides of the second planetary gear PG2 in the axial direction L. Thus, in the present embodiment, the second planetary gear PG2 is supported on both sides in the axial direction L by the second carrier CR2.

[0021] In the present embodiment, the first planetary gear mechanism 21 further includes a first ring gear RG1, a third planetary gear PG3, a fourth planetary gear PG4, and an output sun gear SG.

[0022] The first ring gear RG1 is an internal gear that meshes with the first planetary gear PG1. The first ring gear RG1 is supported so as not to be relatively rotatable with respect to the support member 1.

[0023] 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 to the first planetary shaft PS1. Further, in the present embodiment, the third planetary gear PG3 is formed to have a smaller diameter than the first planetary gear PG1.

[0024] The fourth planetary gear PG4 is rotatably supported with respect to the first carrier CR1. The fourth planetary gear PG4 is configured to rotate (revolve) around the carrier axis X1 and rotate (rotate on its own axis) around an axis different from the first planetary axis X2. The fourth planetary gear PG4 is formed to have the same diameter as the third planetary gear PG3.

[0025] In the present embodiment, the fourth planetary gear PG4 is connected so as to rotate integrally with the third planetary shaft PS3. In the present embodiment, the third planetary shaft PS3 is disposed so as to extend in the first side L1 in the axial direction from the fourth planetary gear PG4. And the third planetary shaft PS3 is rotatably supported with respect to the first carrier CR1 via a pair of third planetary bearings B3 disposed on the first side L1 in the axial direction with respect to the fourth planetary gear PG4.

[0026] The output sun gear SG is disposed on the carrier axis X1. In the present embodiment, the output sun gear SG is connected so as to rotate integrally with the output member 6. Further, in the present embodiment, the output sun gear SG meshes with both the third planetary gear PG3 and the fourth planetary gear PG4. And the output sun gear SG is formed to have a smaller diameter than the third planetary gear PG3 and the fourth planetary gear PG4.

[0027] In the present embodiment, the second planetary gear mechanism 22 further includes a second ring gear RG2. The second ring gear RG2 is an internal gear that meshes with the second planetary gear PG2. The second ring gear RG2 is supported so as not to be relatively rotatable with respect to the support member 1.

[0028] In this 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.

[0029] The linkage mechanism 3 is a mechanism that interlocks the first planetary gear PG1 and the second planetary gear PG2 so that they revolve at the same speed and in the same direction. The linkage mechanism 3 includes a carrier connecting member 31. The carrier connecting member 31 is a member that connects the first carrier CR1 and the second carrier CR2 so that the first carrier CR1 and the second carrier CR2 rotate integrally.

[0030] In this embodiment, the linkage mechanism 3 further includes a ring gear connecting member 32. The ring gear connecting member 32 is a member that connects the first ring gear RG1 and the second ring gear RG2. The ring gear connecting member 32 is fixed to the support member 1. In this embodiment, the ring gear connecting member 32 is formed in a cylindrical shape with the carrier axis X1 as the axis. And the support member 1 is disposed inside the ring gear connecting member 32 in the radial direction R.

[0031] The output member 6 is connected to the output rotating member RM. The output rotating member RM 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 first carrier CR1 and the second carrier CR2. In this embodiment, the output sun gear SG functions as the output rotating member RM. Here, "rotating in conjunction" includes rotating at the same speed and rotating at a predetermined speed ratio, regardless of the rotation direction.

[0032] The output member 6 includes an intermediate arrangement portion 60 disposed between the first planetary gear mechanism 21 and the second planetary gear mechanism 22 in the axial direction L. In the present embodiment, the output member 6 includes a first cylindrical portion 61. The first cylindrical portion 61 is formed in a cylindrical shape. The first cylindrical portion 61 is disposed on the carrier axis X1. That is, the first cylindrical portion 61 is formed in a cylindrical shape with the carrier axis X1 as the axis. In the present embodiment, the first cylindrical portion 61 is disposed so as to extend in the second axial side L2 in the axial direction from the output sun gear SG meshing with the third planetary gear PG3 of the first planetary gear mechanism 21 toward the second planetary gear mechanism 22. Thus, in the present embodiment, the first cylindrical portion 61 functions as the intermediate arrangement portion 60.

[0033] In the present embodiment, the carrier connecting member 31 of the interlocking mechanism 3 is a shaft member extending along the axial direction L. And the carrier connecting member 31 is disposed on the carrier axis X1 so as to penetrate the inside in the radial direction R with respect to the first cylindrical portion 61 in the axial direction L.

[0034] The support member 1 is fixedly non-rotatable. In the present embodiment, the support member 1 includes a pair of first support portions 11 and a pair of second support portions 12.

[0035] The pair of first support portions 11 rotatably support the output member 6. In the present embodiment, the pair of first support portions 11 are formed so as to extend from the ring gear connecting member 32 of the interlocking mechanism 3 toward the inside in the radial direction R. And the pair of first support portions 11 support the first cylindrical portion 61 of the output member 6 from the outside in the radial direction R via a pair of output bearings B4.

[0036] The pair of second support portions 12 rotatably support the first carrier CR1 and the second carrier CR2. In the present embodiment, the pair of second support portions 12 are formed to extend radially inward in the radial direction R from the ring gear connecting member 32 of the interlocking mechanism 3. And the pair of second support portions 12 support the first carrier CR1 and the second carrier CR2 from the outside in the radial direction R via a pair of carrier bearings B5. Also, in the present embodiment, the second support portion 12 on the first axial side L1 is arranged on the first axial side L1 with respect to the first ring gear RG1, and the second support portion 12 on the second axial side L2 is arranged on the second axial side L2 with respect to the second ring gear RG2.

[0037] The first crank member 41 is arranged to extend in the first planetary radial direction Rp1. The first crank member 41 extends across the first planetary axis X2 and the first input axis X4 spaced apart from the first planetary axis X2 in the first planetary radial direction Rp1. The first crank member 41 is connected so as to rotate integrally with the first planetary gear PG1. In the present embodiment, the first crank member 41 is non-rotatably connected to a portion protruding axially on the first side L1 from the first carrier CR1 on the first planetary shaft PS1.

[0038] The first input member 51 is a member to which a predetermined driving force is input from the outside of the power conversion device 10. The first input member 51 is arranged on the first input axis X4. The first input member 51 is supported by the first crank member 41. In the present embodiment, the first input member 51 is a shaft member arranged to protrude axially on the first side L1 from the first crank member 41. And the first input member 51 is non-rotatably connected to the first crank member 41.

[0039] The second crank member 42 is arranged to extend in the second planetary radial direction Rp2. The second crank member 42 extends across the second planetary axis X3 and the second input axis X5 spaced apart from the second planetary axis X3 in the second planetary radial direction Rp2. The second crank member 42 is connected so as to rotate integrally with the second planetary gear PG2. In the present embodiment, the second crank member 42 is connected to a portion protruding axially to the second side L2 from the second carrier CR2 on the second planetary shaft PS2 in a non-rotatable manner relative to the second carrier CR2.

[0040] The second input member 52 is a member to which a predetermined driving force is input from the outside of the power conversion device 10. The second input member 52 is arranged on the second input axis X5. The second input member 52 is supported by the second crank member 42. In the present embodiment, the second input member 52 is a shaft member arranged to protrude axially to the second side L2 from the second crank member 42. And the second input member 52 is connected to the second crank member 42 in a non-rotatable manner relative to the second crank member 42.

[0041] In the present embodiment, a first pedal P1 described later is connected to the first input member 51 so as to be relatively rotatable. And a second pedal P2 described later is connected to the second input member 52 so as to be relatively rotatable.

[0042] In the present embodiment, the distance 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 in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5. Also, the distance in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4 is longer than the distance between the first planetary axis X2 and the carrier axis X1. And the distance in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5 is longer than the distance between the second planetary axis X3 and the carrier axis X1.

[0043] In the present embodiment, the power conversion device 10 further includes a speed increasing mechanism 7. The speed increasing mechanism 7 is arranged in the power transmission path between the first planetary gear PG1 and the output member 6. The speed increasing mechanism 7 increases the rotation speed of the first planetary gear PG1 and transmits it to the output member 6.

[0044] As described above, in the present embodiment, the first planetary gear mechanism 21 includes a fixed first ring gear RG1, a first planetary gear PG1 that meshes with the first ring gear RG1, a third planetary gear PG3 that rotates integrally with the first planetary gear PG1, and an output sun gear SG that meshes with the third planetary gear PG3 and rotates integrally with the output member 6. The third planetary gear PG3 has a smaller diameter than the first planetary gear PG1, and the output sun gear SG has a smaller diameter than the third planetary gear PG3 and the fourth planetary gear PG4. Therefore, in the present embodiment, the first planetary gear mechanism 21 increases the speed of rotation of the first planetary gear PG1 and transmits it to the output member 6. That is, in the present embodiment, the first planetary gear mechanism 21 functions as a speed increasing mechanism 7.

[0045] As shown in FIG. 1, in addition to the above-described power conversion device 10, the power generation device 100 includes a rotating electric machine 9. The rotating electric machine 9 includes a stator 91 and a rotor 92.

[0046] The stator 91 is fixed to a non-rotating member. In the present embodiment, the stator 91 is fixed to the support member 1 as a non-rotating member.

[0047] The rotor 92 is rotatably supported with respect to the stator 91. In the present embodiment, the rotor 92 is disposed between the first planetary gear mechanism 21 and the second planetary gear mechanism 22 in the axial direction L. The rotor 92 is connected to the intermediate arrangement portion 60 so as to rotate integrally with the output member 6. In the illustrated example, the rotor 92 is attached to the outer peripheral surface of the first cylindrical portion 61.

[0048] In the present embodiment, the stator 91 and the rotor 92 are disposed on the carrier axis X1. The rotor 92 is disposed inside the stator 91 in the radial direction R. Further, in the present embodiment, the stator 91 and the rotor 92 are disposed between the pair of first support portions 11 of the support member 1 in the axial direction L.

[0049] In this embodiment, in the power conversion device 10, the reciprocating motions of the first input member 51 and the second input member 52 are converted into the rotational motion of the output member 6. Along with this, the rotor 92 of the rotary electric machine 9 rotates integrally with the output member 6. As a result, the rotary electric machine 9 generates electricity by the driving force transmitted to the rotor 92.

[0050] Here, with reference to FIGS. 2 to 6, the reciprocating motions of the first input member 51 and the second input member 52 according to this embodiment will be described. In FIGS. 2 to 6, the locus T1 indicated by the one-dot chain 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 51 and the second input member 52. Further, 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 51 and the second input member 52.

[0051] As described above, the first planetary gear PG1 and the second planetary gear PG2 revolve around the carrier axis X1. Therefore, the locus T2, which is the moving 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.

[0052] As described above, in this 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 this embodiment, the moving locus of the first planetary axis X2 and the moving locus of the second planetary axis X3 accompanying the reciprocating motions of the first input member 51 and the second input member 52 coincide with each other in the axial direction view along the axial direction L.

[0053] As shown in FIGS. 2 to 6, in the 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, sandwiching the carrier axis X1, and are arranged at positions where the distances from the carrier axis X1 are the same. In the present embodiment, in the axial view along the axial direction L, the first planetary axis X2, the carrier axis X1, and the second planetary axis X3 are arranged so as to be aligned 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°.

[0054] As shown in FIGS. 2 to 6, in the axial view along the axial direction L, the first crank member 41 is connected to the first planetary gear PG1 and the second crank member 42 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, sandwiching the carrier axis X1. 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 41, 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 42, are arranged to be parallel to each other.

[0055] As described above, in the present embodiment, the distance in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4 is longer than the distance between the first planetary axis X2 and the carrier axis X1. And the distance in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5 is longer than the distance between the second planetary axis X3 and the carrier axis X1.

[0056] 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 view along the axial direction L. And the moving directions of the first planetary axis X2 and the second planetary axis X3 (the rotation directions of the first carrier CR1 and the second carrier CR2) along the circular locus T2 are opposite to the moving directions of the first input axis X4 and the second input axis X5 along the elliptical locus T1.

[0057] As described above, in the present embodiment, the distance of the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4 is the same as the distance of 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 to be 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 51 and the second input member 52 coincide with each other in the axial direction view along the axial direction L.

[0058] 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°.

[0059] In the example shown in FIG. 3, 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. 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 rotated counterclockwise about the carrier axis X1 from the state shown in FIG. 2.

[0060] 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, in the axial view along the axial direction L, the first input axis X4 and the second input axis X5 are located on the 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.

[0061] 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 have rotated counterclockwise about the carrier axis X1 from the state shown in FIG. 4.

[0062] 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 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.

[0063] 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 51 and the second input member 52 perform reciprocating motion so that the first input axis X4 and the second input axis X5 draw an elliptical locus T1.

[0064] As shown in FIG. 7, in the present embodiment, the power generation device 100 is mounted on the bicycle B. Therefore, in the present embodiment, the power conversion device 10 of the power generation device 100 converts the reciprocating motion of the first input member 51 and the second input member 52 by the operation of the driver of the bicycle B into a rotational motion of the output member 6 and outputs it.

[0065] 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, and a driven wheel W2. In the present embodiment, the bicycle B further includes a power storage device (not shown) and a motor (not shown).

[0066] 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 hold. 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 10. The support member 1 of the power conversion device 10 is fixed to the frame F via a fixing member FM.

[0067] The drive wheel W1 is a wheel that rotates 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.

[0068] In the present embodiment, the rotary electric machine 9 generates electricity by the driving force transmitted to the output member 6 by the operation of the driver of the bicycle B, and is configured to store the electricity in the above-described power storage device. The above-described motor receives power supply from the above-described power storage device and performs power running to drive the drive wheel W1.

[0069] 2. Second Embodiment Hereinafter, the power transmission device 10 according to the second embodiment and the power generation device 100 including the same will be described with reference to FIG. 8. In the present embodiment, the configurations of the support member 1, the first planetary gear mechanism 21, the second planetary gear mechanism 22, and the interlocking mechanism 3 are different from those 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.

[0070] As shown in FIG. 8, in the present embodiment, the first planetary gear mechanism 21 further includes a fifth planetary gear PG5 and a first sun gear SG1.

[0071] The fifth planetary gear PG5 meshes with the first planetary gear PG1. The fifth planetary gear PG5 is rotatably supported with respect to the first carrier CR1. The fifth planetary gear PG5 is configured to rotate (revolve) around the carrier axis X1 and rotate (rotate on its own axis) around an axis different from the first planetary axis X2.

[0072] The first sun gear SG1 is disposed on the carrier axis X1. The first sun gear SG1 meshes with the first planetary gear PG1 or a gear that rotates in conjunction with the first planetary gear PG1. In the present embodiment, the first sun gear SG1 meshes with the fifth planetary gear PG5. Further, the first sun gear SG1 is disposed on the first side L1 in the axial direction with respect to the output sun gear SG.

[0073] In the present embodiment, the first planetary gear mechanism 21 does not include the first ring gear RG1. Therefore, in the present embodiment, the first planetary gear PG1 does not mesh with the first ring gear RG1. In the present embodiment, the first planetary gear PG1 is formed to have a smaller diameter than the third planetary gear PG3. Further, the output sun gear SG is formed to have a smaller diameter than the third planetary gear PG3.

[0074] Thus, in the present embodiment, the first planetary gear mechanism 21 increases the speed of rotation of the first planetary gear PG1 and transmits it to the output member 6. That is, in the present embodiment, the first planetary gear mechanism 21 functions as a speed increasing mechanism 7.

[0075] In this embodiment, the first carrier CR1 is configured to accommodate the first planetary gear PG1, the third planetary gear PG3, the fourth planetary gear PG4, the fifth planetary gear PG5, the first sun gear SG1, and the output sun gear SG.

[0076] In this embodiment, the first planetary shaft PS1 is arranged to penetrate the first planetary gear PG1 and the third planetary gear PG3 in the axial direction L. The first planetary shaft PS1 is rotatably supported with respect to the first carrier CR1 via a pair of first planetary bearings B1 that are divided and arranged on the first axial side L1 with respect to the first planetary gear PG1 and on the second axial side L2 with respect to the third planetary gear PG3.

[0077] Also, in this embodiment, the third planetary shaft PS3 is arranged to penetrate the fourth planetary gear PG4 in the axial direction L. The third planetary shaft PS3 is rotatably supported with respect to the first carrier CR1 via a pair of third planetary bearings B3 that are divided and arranged on both sides of the fourth planetary gear PG4 in the axial direction L.

[0078] The second planetary gear mechanism 22 further includes a sixth planetary gear PG6 and a second sun gear SG2.

[0079] The sixth planetary gear PG6 meshes with the second planetary gear PG2. The sixth planetary gear PG6 is rotatably supported with respect to the second carrier CR2. The sixth planetary gear PG6 is configured to rotate (revolve) around the carrier axis X1 and rotate (rotate on its own axis) around an axis different from the second planetary axis X3. In this embodiment, the sixth planetary gear PG6 is formed to have the same diameter as the fifth planetary gear PG5.

[0080] The second sun gear SG2 is arranged on the carrier axis X1. The second sun gear SG2 meshes with the second planetary gear PG2 or a gear that rotates in conjunction with the second planetary gear PG2. In this embodiment, the second sun gear SG2 meshes with the sixth planetary gear PG6. Also, the second sun gear SG2 is formed to have the same diameter as the first sun gear SG1.

[0081] In this embodiment, the second planetary gear mechanism 22 does not include a second ring gear RG2. Therefore, in this embodiment, the second planetary gear PG2 does not mesh with the second ring gear RG2.

[0082] In this embodiment, the second carrier CR2 is configured to accommodate the second planetary gear PG2, the sixth planetary gear PG6, and the second sun gear SG2.

[0083] In this embodiment, the interlocking mechanism 3 further includes a sun gear connecting member 33. Note that in this embodiment, the interlocking mechanism 3 does not include a ring gear connecting member 32.

[0084] The sun gear connecting member 33 is a member that connects the first sun gear SG1 and the second sun gear SG2. In this embodiment, the sun gear connecting member 33 is fixed to the support member 1.

[0085] The sun gear connecting member 33 includes a second cylindrical portion 34. The second cylindrical portion 34 is formed in a cylindrical shape. The second cylindrical portion 34 is disposed on the carrier axis X1. That is, the second cylindrical portion 34 is formed in a cylindrical shape with the carrier axis X1 as its axis. The second cylindrical portion 34 is located inside the first cylindrical portion 61 of the output member 6 in the radial direction R and outside the carrier connecting member 31 in the radial direction R.

[0086] In this embodiment, the carrier connecting member 31 is disposed so as to axially penetrate the inside in the radial direction R with respect to the second cylindrical portion 34, the first sun gear SG1, and the second sun gear SG2. The carrier connecting member 31 is rotatably supported with respect to the first sun gear SG1 via the first sun gear bearing B61 and is rotatably supported with respect to the second sun gear SG2 via the second sun gear bearing B62.

[0087] In this embodiment, the support member 1 does not include a pair of second support portions 12. That is, in this embodiment, the support member 1 does not support the first carrier CR1.

[0088] 3. Third Embodiment Hereinafter, the power transmission device 10 according to the third embodiment will be described with reference to FIGS. 9 and 10. In this embodiment, the configurations of the support member 1, the first planetary gear mechanism 21, and the output member 6 are different from those of the second embodiment described above. Hereinafter, the description will focus on the differences from the second embodiment. For points not particularly described, the same applies as in the second embodiment described above.

[0089] As shown in FIG. 9, in this embodiment, the power transmission device 10 is not provided in the power generation device 100. Therefore, in this embodiment, the rotor 92 of the rotating electric machine 9 is not connected to the output member 6. And the stator 91 of the rotating electric machine 9 is not fixed to the support member 1. Accordingly, in this embodiment, the support member 1 does not include a pair of first support portions 11, and is formed in a cylindrical shape that covers the first cylindrical portion 61 of the output member 6 from the outside in the radial direction R. And a pair of output bearings B4 are disposed between the inner peripheral surface of the support member 1 and the outer peripheral surface of the first cylindrical portion 61 in the radial direction R.

[0090] In this embodiment, the first planetary gear mechanism 21 further includes a seventh planetary gear PG7. Note that, in this embodiment, the first planetary gear mechanism 21 does not include the third planetary gear PG3 and the fourth planetary gear PG4.

[0091] In this embodiment, the seventh planetary gear PG7 is connected so as to rotate integrally with the fifth planetary gear PG5. And the seventh planetary gear PG7 meshes with the output sun gear SG. Thus, in this embodiment, the first planetary gear mechanism 21 and the second planetary gear mechanism 22 are configured such that the direction in which the intermediate arrangement portion 60 of the output member 6 rotates is the same as the direction in which the first planetary gear PG1 and the second planetary gear PG2 revolve.

[0092] In this embodiment, the output member 6 further includes a wheel connecting portion 62. The wheel connecting portion 62 is configured to be connected to the drive wheel W1. The wheel connecting portion 62 is connected so as to rotate integrally with the intermediate arrangement portion 60. In this embodiment, the wheel connecting portion 62 rotates in the same direction as the revolution direction of the first planetary gear PG1. Also, in this embodiment, the wheel connecting portion 62 and the intermediate arrangement portion 60 are arranged on the carrier axis X1. In the example shown in FIG. 9, the wheel connecting portion 62 is formed so as to extend outward in the radial direction R from the first cylindrical portion 61 as the intermediate arrangement portion 60.

[0093] As shown in FIG. 10, in this embodiment, the configuration of the bicycle B equipped with the power conversion device 10 is different from that of the first embodiment. Specifically, in this embodiment, the bicycle B further includes a transmission mechanism T.

[0094] The transmission mechanism T is configured to transmit the rotation of the output member 6 of the power conversion device 10 to the drive wheel W1. In this 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.

[0095] The first sprocket SP1 is arranged on the carrier axis X1. In this embodiment, the first sprocket SP1 functions as the wheel connecting portion 62 of the output member 6.

[0096] The first chain CH1 is wound around the first sprocket SP1 and the second sprocket SP2. Therefore, the second sprocket SP2 rotates driven by the first sprocket SP1. In the example shown in FIG. 10, the second sprocket SP2 is formed to have a smaller diameter than the first sprocket SP1.

[0097] The third sprocket SP3 is arranged 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. 10, the third sprocket SP3 is formed to have a larger diameter than the second sprocket SP2.

[0098] The second chain CH2 is wound around the third sprocket SP3 and the fourth sprocket SP4. The fourth sprocket SP4 is arranged coaxially with the drive wheel W1. In the example shown in FIG. 10, the fourth sprocket SP4 is formed to have a smaller diameter than the third sprocket SP3.

[0099] In the present embodiment, the driving force by the operation of the driver of the bicycle B is transmitted from the output member 6 to the drive wheel W1 via the transmission mechanism T.

[0100] 4. Fourth Embodiment Hereinafter, the power conversion device 10 according to the fourth embodiment and the power generation device 100 including the same will be described with reference to FIG. 11. In the present embodiment, the configurations of the first planetary gear mechanism 21 and the output member 6 are different from those of the second embodiment described above. Hereinafter, the description will focus on the differences from the second embodiment described above. For points not particularly described, the same applies as in the second embodiment described above.

[0101] As shown in FIG. 11, in the present embodiment, the third planetary gear PG3 and the output sun gear SG in the first planetary gear mechanism 21 are sprockets connected to each other by the first planetary chain 2a wound around them. The output sun gear SG is formed to have a smaller diameter than the third planetary gear PG3. In the present embodiment, the third planetary gear PG3 and the output sun gear SG are not housed in the first carrier CR1. Further, in the present embodiment, the first planetary gear mechanism 21 does not include the fourth planetary gear PG4.

[0102] In this embodiment, similar to the third embodiment, the output member 6 includes a wheel connection portion 62. Further, the bicycle B equipped with the power conversion device 10 includes a power storage device and a motor, similar to the first embodiment, and includes a transmission mechanism T, similar to the third embodiment. And the first sprocket SP1 of the transmission mechanism T functions as the wheel connection portion 62 of the output member 6.

[0103] In this embodiment, the driving force by the operation of the driver of the bicycle B is transmitted from the output member 6 to the drive wheel W1 via the transmission mechanism T. Also, in this embodiment, the rotary electric machine 9 generates electricity by the driving force by the operation of the driver of the bicycle B and stores the electricity in the above-mentioned power storage device. Then, the above-mentioned motor receives the supply of electric power from the above-mentioned power storage device and performs power running to drive the drive wheel W1.

[0104] 5. Fifth Embodiment Hereinafter, the power conversion device 10 according to the fifth embodiment will be described with reference to FIG. 12. In this embodiment, the configurations of the support member 1, the first planetary gear mechanism 21, the second planetary gear mechanism 22, the first crank member 41, the second crank member 42, and the output member 6 are different from those of the third embodiment. Hereinafter, the description will focus on the differences from the third embodiment. Note that, for points not particularly described, the same applies as in the third embodiment.

[0105] In this embodiment, the first planetary gear mechanism 21 does not include the fifth planetary gear PG5, the seventh planetary gear PG7, and the output sun gear SG.

[0106] As shown in FIG. 12, in the present embodiment, the first planetary gear PG1 and the first sun gear SG1 in the first planetary gear mechanism 21 are sprockets connected to each other by a second planetary chain 2b wound around them. In the present application, when a pair of gears are sprockets connected to each other by a chain wound around them, it is assumed that the pair of gears are meshed with each other. That is, in the present embodiment, the first planetary gear PG1 and the first sun gear SG1, which are sprockets, are meshed with each other. Further, in the present embodiment, the first sun gear SG1 is formed to have a larger diameter than the first planetary gear PG1.

[0107] In the present embodiment, the first planetary gear PG1 and the first sun gear SG1, which are sprockets, are accommodated in the first carrier CR1. In such a configuration, it is preferable that openings for inserting the first planetary gear PG1 and the first sun gear SG1 are respectively formed in the first carrier CR1. Then, after the first planetary gear PG1 and the first sun gear SG1 are accommodated inside the first carrier CR1 through the above openings, it is preferable to insert the first planetary shaft PS1 through the first planetary gear PG1 and insert the second cylindrical portion 34 through the first sun gear SG1.

[0108] In the present embodiment, the output member 6 does not include the first cylindrical portion 61. And the wheel connecting portion 62 of the output member 6 is connected to the first carrier CR1 so as to be positioned between the first planetary gear mechanism 21 and the second planetary gear mechanism 22 in the axial direction L. That is, in the present embodiment, the wheel connecting portion 62 functions as the intermediate arrangement portion 60. And the first carrier CR1 functions as the output rotating member RM.

[0109] In the present embodiment, the support member 1 does not include a pair of first support portions 11. In the present embodiment, the sun gear connecting member 33 is fixed to the support member 1.

[0110] In the present embodiment, the second planetary gear mechanism 22 does not include the sixth planetary gear PG6.

[0111] In this embodiment, the second planetary gear PG2 and the second sun gear SG2 in the second planetary gear mechanism 22 are sprockets connected to each other by a third planetary chain 2c wound around them. Therefore, in this embodiment, the second planetary gear PG2 and the second sun gear SG2, which are sprockets, mesh with each other. Also, in this embodiment, the second sun gear SG2 is formed with a larger diameter than the second planetary gear PG2.

[0112] In this embodiment, the second planetary gear PG2 and the second sun gear SG2, which are sprockets, are housed in the second carrier CR2. In such a configuration, it is preferable that openings for inserting the second planetary gear PG2 and the second sun gear SG2 are respectively formed in the second carrier CR2. Then, after housing the second planetary gear PG2 and the second sun gear SG2 inside the second carrier CR2 through the above openings, it is preferable to insert the second planetary shaft PS2 through the second planetary gear PG2 and insert the second cylindrical portion 34 through the second sun gear SG2.

[0113] In this embodiment, the distance in the first planetary radial direction Rp1 between the first planetary axis X2 and the first input axis X4 is shorter than the distance between the first planetary axis X2 and the carrier axis X1. And the distance in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5 is shorter than the distance between the second planetary axis X3 and the carrier axis X1.

[0114] Therefore, although not shown, in this 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. And the moving directions of the first planetary axis X2 and the second planetary axis X3 (the rotational directions of the first carrier CR1 and the second carrier CR2) along the circular locus T2 are the same as the moving directions of the first input axis X4 and the second input axis X5 along the elliptical locus T1.

[0115] 6. Sixth Embodiment Hereinafter, the power conversion device 10 according to the sixth embodiment and the power generation device 100 including the same will be described with reference to FIG. 13. In the present embodiment, the configurations of the support member 1, the first planetary gear mechanism 21, the output member 6, and the speed increasing mechanism 7 are different from those 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.

[0116] In the present embodiment, the first planetary gear mechanism 21 does not include the third planetary gear PG3, the fourth planetary gear PG4, and the output sun gear SG.

[0117] In the present embodiment, the output member 6 does not include the first cylindrical portion 61 and includes the orthogonal axis portion 63. The orthogonal axis portion 63 is formed in an axial shape along the radial direction R. The orthogonal axis portion 63 is disposed between the axial directions L of the first planetary gear mechanism 21 and the second planetary gear mechanism 22. Therefore, in the present embodiment, the orthogonal axis portion 63 functions as the intermediate disposition portion 60.

[0118] In the present embodiment, the stator 91 and the rotor 92 of the rotating electrical machine 9 are coaxial with the orthogonal axis portion 63 of the output member 6 and are disposed outside the orthogonal axis portion 63 in the radial direction R. The rotor 92 is connected so as to rotate integrally with the orthogonal axis portion 63.

[0119] In the present embodiment, the support member 1 does not include the pair of first support portions 11 that support the first cylindrical portion 61 and includes the third support portion 13 and the fourth support portion 14.

[0120] The third support portion 13 rotatably supports the orthogonal axis portion 63 of the output member 6. In the present embodiment, the third support portion 13 is disposed coaxially with the orthogonal axis portion 63 and is formed in a cylindrical shape that covers the orthogonal axis portion 63. A pair of output bearings B4 are disposed between the inner peripheral surface of the third support portion 13 and the outer peripheral surface of the orthogonal axis portion 63. Further, the third support portion 13 is disposed so as to penetrate the ring gear connecting member 32 in the radial direction R.

[0121] The fourth support portion 14 supports the stator 91 of the rotating electrical machine 9. The fourth support portion 14 is fixed to the third support portion 13.

[0122] In the present embodiment, the speed increasing mechanism 7 includes a first gear 71 and a second gear 72. The first gear 71 is connected so as to rotate integrally with the carrier connecting member 31. The second gear 72 is connected so as to rotate integrally with the orthogonal axis portion 63 of the output member 6. The first gear 71 and the second gear 72 are engaged with each other with their axial centers orthogonal to each other. In the present embodiment, the second gear 72 functions as the output rotating member RM.

[0123] The second gear 72 is formed to have a smaller diameter than the first gear 71. Therefore, the rotation transmitted to the carrier connecting member 31 is speeded up between the first gear 71 and the second gear 72 and transmitted to the output member 6.

[0124] 7. Other Embodiments (1) In the above embodiment, the configuration in which the first input member 51 is a shaft member fixed to the first crank member 41 and the second input member 52 is a shaft member fixed to the second crank member 42 has been described as an example. However, the present invention is not limited to such a configuration. For example, the first input member 51 may be connected to the first crank member 41 so as to be relatively rotatable, and the second input member 52 may be connected to the second crank member 42 so as to be relatively rotatable. Alternatively, a shaft member as the first input member 51 and a shaft member as the second input member 52 may not be provided, and a part of the first crank member 41 may function as the first input member 51 and a part of the second crank member 42 may function as the second input member 52.

[0125] (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°.

[0126] (3) In the above-described embodiment, in the locus T1, as an example, a configuration has been described in which, in an 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, without being limited to such a configuration, in the locus T1, in an axial view along the axial direction L, a configuration may be adopted 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.

[0127] (4) In the above-described embodiment, as an example, a configuration has been 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 41) 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 42) are arranged to be parallel to each other. However, without being limited to such a configuration, the extending direction of the first crank member 41 and the extending direction of the second crank member 42 may be arranged to intersect each other.

[0128] (5) 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 without departing from the spirit of the present disclosure.

[0129] 8. Summary of this embodiment Hereinafter, an overview of the power conversion device (10) and the power generation device (100) described above will be described.

[0130] The power conversion device (10) is a support member (1), a first planetary gear mechanism (21) including a first carrier (CR1) rotatably supported with respect to the support member (1) and a first planetary gear (PG1) rotatably supported with respect to the first carrier (CR1), A second planetary gear mechanism (22) including a second carrier (CR2) rotatably supported with respect to the support member (1), and a second planetary gear (PG2) rotatably supported with respect to the second carrier (CR2). An interlocking mechanism (3) that interlocks the first planetary gear (PG1) and the second planetary gear (PG2) so that they revolve at the same speed and in the same direction with respect to each other. With the direction orthogonal to the first planetary axis (X2) which is the rotation axis of the first planetary gear (PG1) defined as the first planetary radial direction (Rp1), a first crank member (41) is arranged to extend in the first planetary radial direction (Rp1) and is connected so as to rotate integrally with the first planetary gear (PG1). A first input member (51) supported by the first crank member (41) and arranged on a first input axis (X4) spaced apart from the first planetary axis (X2) in the first planetary radial direction (Rp1). With the direction orthogonal to the second planetary axis (X3) which is the rotation axis of the second planetary gear (PG2) defined as the second planetary radial direction (Rp2), a second crank member (42) is arranged to extend in the second planetary radial direction (Rp2) and is connected so as to rotate integrally with the second planetary gear (PG2). A second input member (52) supported by the second crank member (42) and arranged on a second input axis (X5) spaced apart from the second planetary axis (X3) in the second planetary radial direction (Rp2). An output member (6) connected to an output rotating member (RM) that rotates in conjunction with the first carrier (CR1) and the second carrier (CR2), excluding the first planetary gear (PG1) and the second planetary gear (PG2). The interlocking mechanism (3) includes a carrier connecting member (31) that connects the first carrier (CR1) and the second carrier (CR2) so that the first carrier (CR1) and the second carrier (CR2) rotate integrally. With the direction along the carrier axis (X1) which is the rotation axis of the first carrier (CR1) and the second carrier (CR2) defined as the axial direction (L). In an axial view along the axial direction (L), the first planetary axis (X2) and the second planetary axis (X3) are located on opposite sides of the carrier axis (X1) across the carrier axis (X1), and are arranged at positions where the distances from the carrier axis (X1) are the same. The first planetary gear mechanism (21) and the second planetary gear mechanism (22) are arranged spaced apart from each other in the axial direction (L). The output member (6) includes an intermediate arrangement portion (60) arranged between the first planetary gear mechanism (21) and the second planetary gear mechanism (22) in the axial direction (L).

[0131] According to this configuration, the intermediate arrangement portion (60) of the output member (6) is arranged between the first planetary gear mechanism (21) and the second planetary gear mechanism (22) that are arranged spaced apart from each other in the axial direction (L). Thereby, in a configuration in which the driving force is transmitted through the intermediate arrangement portion (60), it is easy to reduce the size of the power conversion device (10). Therefore, it is easy to improve the mountability of the power conversion device (10) to the mounting target.

[0132] Here, the output member (6) includes a first cylindrical portion (61) arranged on the carrier axis (X1). Taking the direction orthogonal to the carrier axis (X1) as the radial direction (R), It is preferable that the carrier connecting member (31) is arranged on the carrier axis (X1) so as to penetrate the inside of the first cylindrical portion (61) in the radial direction (R) in the axial direction (L).

[0133] According to this configuration, while the intermediate arrangement portion (60) is arranged between the first planetary gear mechanism (21) and the second planetary gear mechanism (22) in the axial direction (L), the first carrier (CR1) and the second carrier (CR2) can be appropriately connected by the carrier connecting member (31).

[0134] In the configuration in which the output member (6) includes the first cylindrical portion (61), The first planetary gear mechanism (21) is disposed on the carrier axis (X1), and further includes a first sun gear (SG1) that meshes with the first planetary gear (PG1) or a gear that rotates in conjunction with the first planetary gear (PG1). The second planetary gear mechanism (22) is disposed on the carrier axis (X1), and further includes a second sun gear (SG2) that meshes with the second planetary gear (PG2) or a gear that rotates in conjunction with the second planetary gear (PG2). The interlocking mechanism (3) is fixed to the support member (1), and further includes a sun gear connecting member (33) that connects the first sun gear (SG1) and the second sun gear (SG2). The sun gear connecting member (33) includes a second cylindrical portion (34) disposed on the carrier axis (X1). The second cylindrical portion (34) is preferably disposed inside the first cylindrical portion (61) in the radial direction (R) and outside the carrier connecting member (31) in the radial direction (R).

[0135] According to this configuration, an intermediate arrangement portion (60) is disposed between the first planetary gear mechanism (21) and the second planetary gear mechanism (22) in the axial direction (L), and the first carrier (CR1) and the second carrier (CR2) are connected by the carrier connecting member (31), while the first sun gear (SG1) and the second sun gear (SG2) can be appropriately connected by the sun gear connecting member (33). Therefore, the first planetary gear (PG1) and the second planetary gear (PG2) can be appropriately interlocked.

[0136] The first planetary gear mechanism (21) further includes a first ring gear (RG1) that meshes with the first planetary gear (PG1). The second planetary gear mechanism (22) further includes a second ring gear (RG2) that meshes with the second planetary gear (PG2). The interlocking mechanism (3) further includes a ring gear connecting member (32) that connects the first ring gear (RG1) and the second ring gear (RG2). The ring gear connecting member (32) is preferably fixed to the support member (1).

[0137] According to this configuration, the first planetary gear (PG1) and the second planetary gear (PG2) can be appropriately interlocked with a relatively simple configuration. Further, according to this configuration, when the radius of the first ring gear (RG1) is the same as the radius 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 parts, so it is easy to reduce the number of types of parts.

[0138] Further, the power conversion device (10) is preferably disposed in the power transmission path between the first planetary gear (PG1) and the output member (6), and further includes a speed increasing mechanism (7) that increases the speed of rotation of the first planetary gear (PG1) and transmits it to the output member (6).

[0139] According to this configuration, the rotation of the first crank member (41) can be increased in speed and transmitted to the output member (6). Therefore, for example, when the rotor (92) of the rotary electric machine (9) is connected to the output member (6), it is easy to increase the rotational speed of the rotor (92) of the rotary electric machine (9), and it is easy to reduce the size of the rotary electric machine (9) accordingly. Also, it is advantageous even when the power conversion device (10) is mounted on a vehicle having small-diameter wheels.

[0140] Also, the distance 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 in the second planetary radial direction (Rp2) between the second planetary axis (X3) and the second input axis (X5), it is preferable that the distance in the first planetary radial direction (Rp1) between the first planetary axis (X2) and the first input axis (X4) is longer than the distance between the first planetary axis (X2) and the carrier axis (X1).

[0141] According to this configuration, the movement trajectories (T1) of the first input axis (X4) and the second input axis (X5) accompanying the reciprocating movements of the first input member (51) and the second input member (52) can be made elliptical with reference to the carrier axis (X1). Further, according to this configuration, it becomes easier to secure a large stroke for the reciprocating movements of the first input member (51) and the second input member (52). Therefore, it is easy to reduce the size of the first planetary gear mechanism (21) and the second planetary gear mechanism (22), and by extension, it is easy to reduce the size of the power conversion device (10).

[0142] Also, the output member (6) further includes a wheel connection portion (62) connected to the wheel (W1). The wheel connection portion (62) is connected so as to rotate integrally with the intermediate arrangement portion (60). The wheel connection portion (62) and the intermediate arrangement portion (60) are arranged on the carrier axis (X1). It is preferable that the first planetary gear mechanism (21) and the second planetary gear mechanism (22) are configured such that the direction in which the intermediate arrangement portion (60) rotates is the same as the direction in which the first planetary gear (PG1) and the second planetary gear (PG2) revolve.

[0143] According to this configuration, it is easy to simplify the connection structure between the intermediate arrangement portion (60) and the wheel (W1). Therefore, it is easy to improve the mountability of the power conversion device (10) to the mounting target having the wheel (W1).

[0144] Also, the first planetary gear (PG1) is supported by the first carrier (CR1) on both sides in the axial direction (L). It is preferable that the second planetary gear (PG2) is supported by the second carrier (CR2) on both sides in the axial direction (L).

[0145] According to this configuration, it is easy to increase the support rigidity of the first planetary gear (PG1) and the second planetary gear (PG2). Also, it is easy to hold lubricating oil for lubricating the first planetary gear (PG1) and the second planetary gear (PG2) around those gears.

[0146] The power generation device (100) includes the above-described power conversion device (10), a rotating electrical machine (9) including a stator (91) and a rotor (92), and is a power generation device (100) configured such that the rotor (92) is disposed between the first planetary gear mechanism (21) and the second planetary gear mechanism (22) in the axial direction (L), and is connected to the intermediate arrangement portion (60) so as to rotate integrally with the output member (6).

[0147] According to this configuration, the reciprocating motion of the first input member (51) and the second input member (52) can be converted into the rotational motion of the output member (6), and power generation can be performed by the rotating electrical machine (9). Further, according to this configuration, the rotor (92) of the rotating electrical machine (9) is disposed between the first planetary gear mechanism (21) and the second planetary gear mechanism (22) in the axial direction (L), and is also connected to the intermediate arrangement portion (60) disposed between the first planetary gear mechanism (21) and the second planetary gear mechanism (22) in the axial direction (L). Thereby, the power generation device (100) including the power conversion device (10) and the rotating electrical machine (9) can be downsized.

Industrial Applicability

[0148] The technology according to the present disclosure can be used for a power conversion device that converts reciprocating motion into rotational motion, and a power generation device including the same.

Explanation of Reference Numerals

[0149] 10: Power conversion device, 100: Power generation device, 1: Support member, 21: First planetary gear mechanism, CR1: First carrier, PG1: First planetary gear, RG1: First ring gear, SG1: First sun gear, 22: Second planetary gear mechanism, CR2: Second carrier, PG2: Second planetary gear, RG2: Second ring gear, SG2: Second sun gear, 3: Interlocking mechanism, 31: Carrier connecting member, 32: Ring gear connecting member, 33: Sun gear connecting member, 34: Second cylindrical portion, 41: First crank member, 42: Second crank member, 51: First input member, 52: Second input member, 6: Output member, 60: Intermediate arrangement portion, 61: First cylindrical portion, 62: Wheel connecting portion, 7: Speed increasing mechanism, 9: Rotating electric machine, 91: Stator, 92: Rotor, RM: Output rotating member, X1: Carrier axis, X2: First planetary axis, X3: Second planetary axis, X4: First input axis, X5: Second input axis, L: Axial direction, R: Radial direction, Rp1: First planetary radial direction, Rp2: Second planetary radial direction

Claims

1. A support member, a first planetary gear mechanism including a first carrier rotatably supported with respect to the support member, and a first planetary gear rotatably supported with respect to the first carrier, a second planetary gear mechanism including a second carrier rotatably supported with respect to the support member, and a second planetary gear rotatably supported with respect to the second carrier, an interlocking mechanism that interlocks the first planetary gear and the second planetary gear so as to revolve at the same speed and in the same direction as each other, a first crank member disposed so as to extend in a first planetary radial direction which is a direction orthogonal to a first planetary axis which is a rotation axis of the first planetary gear, and connected so as to rotate integrally with the first planetary gear, a first input member supported by the first crank member and disposed on a first input axis spaced apart from the first planetary axis in the first planetary radial direction, a second crank member disposed so as to extend in a second planetary radial direction which is a direction orthogonal to a second planetary axis which is a rotation axis of the second planetary gear, and connected so as to rotate integrally with the second planetary gear, a second input member supported by the second crank member and disposed on a second input axis spaced apart from the second planetary axis in the second planetary radial direction, an output member connected to an output rotation member that rotates in conjunction with the first carrier and the second carrier, excluding the first planetary gear and the second planetary gear, wherein the interlocking mechanism includes a carrier connecting member that connects the first carrier and the second carrier so that the first carrier and the second carrier rotate integrally, with a direction along a carrier axis which is a rotation axis of the first carrier and the second carrier being defined as an axial direction, in an axial view along the axial direction, the first planetary axis and the second planetary axis are disposed at positions on opposite sides of the carrier axis and at the same distance from the carrier axis, the first planetary gear mechanism and the second planetary gear mechanism are disposed spaced apart from each other in the axial direction, and the output member includes an intermediate disposed portion disposed between the first planetary gear mechanism and the second planetary gear mechanism in the axial direction, a power conversion device.

2. The output member includes a first cylindrical portion disposed on the carrier axis, with a direction orthogonal to the carrier axis being defined as a radial direction, The power conversion device according to claim 1, wherein the carrier connecting member is disposed on the carrier axis so as to penetrate the inside in the radial direction with respect to the first cylindrical portion in the axial direction.

3. The first planetary gear mechanism further includes a first sun gear that is disposed on the carrier axis and meshes with the first planetary gear or a gear that rotates in conjunction with the first planetary gear. The second planetary gear mechanism further includes a second sun gear that is disposed on the carrier axis and meshes with the second planetary gear or a gear that rotates in conjunction with the second planetary gear. The interlocking mechanism further includes a sun gear connecting member that is fixed to the support member and connects the first sun gear and the second sun gear. The sun gear connecting member includes a second cylindrical portion disposed on the carrier axis. The power conversion device according to claim 2, wherein the second cylindrical portion is disposed inside the first cylindrical portion in the radial direction and outside the carrier connecting member in the radial direction.

4. The first planetary gear mechanism further includes a first ring gear that meshes with the first planetary gear. The second planetary gear mechanism further includes a second ring gear that meshes with the second planetary gear. The interlocking mechanism further includes a ring gear connecting member that connects the first ring gear and the second ring gear. The power conversion device according to claim 1, wherein the ring gear connecting member is fixed to the support member.

5. The power conversion device according to claim 1, further comprising a speed increasing mechanism that is disposed in a power transmission path between the first planetary gear and the output member, increases the rotation speed of the first planetary gear, and transmits the increased speed to the output member.

6. 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 5, wherein the distance in the first planetary radial direction between the first planetary axis and the first input axis is longer than the distance between the first planetary axis and the carrier axis.

7. The output member further includes a wheel connecting portion that is connected to a wheel. The wheel connecting portion is connected so as to rotate integrally with the intermediate arrangement portion. The wheel connecting portion and the intermediate arrangement portion are disposed on the carrier axis. The power conversion device according to any one of claims 1 to 5, wherein the first planetary gear mechanism and the second planetary gear mechanism are configured such that the direction in which the intermediate arrangement portion rotates is the same as the direction in which the first planetary gear and the second planetary gear revolve.

8. The first planetary gear is supported on both axial sides by the first carrier, The power conversion device according to any one of claims 1 to 5, wherein the second planetary gear is supported on both axial sides by the second carrier.

9. A power generation device comprising the power conversion device according to any one of claims 1 to 5, and a rotating electric machine including a stator and a rotor, wherein the rotor is disposed between the first planetary gear mechanism and the second planetary gear mechanism in the axial direction and is connected to the intermediate arrangement portion so as to rotate integrally with the output member.

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