Power conversion device and electric power generation device provided with same

Abstract

According to the present invention, a linkage mechanism (3) that causes a first planetary gear (PG1) and a second planetary gear (PG2) to revolve together in the same direction and at the same speed comprises a carrier coupling member (31) that couples a first carrier (CR1) and a second carrier (CR2) so as to rotate in a unitary manner. In an axial view along an axial direction (L), a first planetary axis (X2), which is the axis of rotation of the first planetary gear (PG1), and a second planetary axis (X3), which is the axis of rotation of the second planetary gear (PG2), are disposed at positions opposite one another across a carrier axis (X1), which is the axis of rotation of the first carrier (CR1) and the second carrier (CR2), and equidistant from the carrier axis center (X1). A first planetary gear mechanism (21) and a second planetary gear mechanism (22) are disposed apart from each other in the axial direction (L). An output member (6) comprises an intermediate arrangement part (60) disposed between the first planetary gear mechanism (21) and the second planetary gear mechanism (22) in the axial direction (L).

Description

Power conversion device and power generation device equipped with the same

[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.

[0002] Patent Document 1 discloses a power conversion device mounted on a bicycle or the like (see Figures 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 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 Figure 3 of Patent Document 1). Each of the pair of planetary gear mechanisms includes a sun gear (2) supported so as not to rotate, 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) that rotatably support 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).

[0005] Japanese Patent Application Laid-Open No. 2008-201397

[0006] In the power conversion device of Patent Document 1, one of the carriers (5) is configured as a pulley around which a belt (19) that transmits driving force to a wheel is wound. As described above, the one of the carriers (5) rotatably supports the meshing inner and outer planetary gears. Therefore, the diameter of the carrier (5) as a pulley tends to be large, which makes it difficult to mount the power conversion device on an object such as a bicycle.

[0007] Therefore, it is desirable to realize a technology that makes it easier to install a power conversion device on an object.

[0008] In view of the above, the characteristic configuration of the power conversion device includes: a support member; a first planetary gear mechanism including a first carrier rotatably supported on the support member and a first planetary gear rotatably supported on the first carrier; a second planetary gear mechanism including a second carrier rotatably supported on the support member and a second planetary gear rotatably supported on the second carrier; an interlocking 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 planetary radial direction is a direction perpendicular to a first planetary axis that is the rotational axis of the first planetary gear, the first crank member being arranged to extend in the first planetary radial direction and connected to the first planetary gear so as to rotate integrally with the first planetary gear; and a first input member supported by the first crank member and arranged on a first input axis spaced apart from the first planetary axis in the first planetary radial direction. a second crank member disposed to extend in the second planetary radial direction, with a direction perpendicular to a second planetary axis that is the rotational axis of the second planetary gear defined as a second planetary radial direction, and connected 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 that is spaced apart from the second planetary axis in the second planetary radial direction; and 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; wherein the interlocking mechanism comprises a carrier connecting member that connects the first carrier and the second carrier so that the first carrier and the second carrier rotate integrally; and an axial direction is a direction along a carrier axis that is the rotational axis of the first carrier and the second carrier; When viewed in the axial direction 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; and the output member has an intermediate portion arranged axially between the first planetary gear mechanism and the second planetary gear mechanism.

[0009] According to this characteristic configuration, the intermediate portion of the output member is disposed axially between the first planetary gear mechanism and the second planetary gear mechanism, which are disposed axially spaced apart from each other. This facilitates miniaturization of the power conversion device in a configuration in which driving force is transmitted via the intermediate portion. This also facilitates the ease of mounting the power conversion device on an object.

[0010] FIG. 1 is a cross-sectional view of a power conversion device according to a first embodiment and a power generation device including the same; FIG. 2 is a cross-sectional view of a power conversion device according to a first embodiment, and a power generation device including the same; FIG. 3 is a cross-sectional view of a power conversion device according to a sixth embodiment, and a power generation device including the same;

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

[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 by the support member 1. The first planetary gear PG1 is rotatably supported by 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 by the support member 1. The second planetary gear PG2 is rotatably supported by 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 referred to as the "axial direction L." One side of the axial direction L is referred to as the "first axial side L1," and the other side of the axial direction L is referred to as the "second axial side L2." Furthermore, the direction perpendicular to the carrier axis X1 is referred to as the "radial direction R." Furthermore, the direction perpendicular to the first planetary axis X2, which is the rotation axis of the first planetary gear PG1, is referred to as the "first planetary radial direction Rp1." Furthermore, the direction perpendicular to the second planetary axis X3, which is the rotation axis of the second planetary gear PG2, is referred to 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 this embodiment, the first planetary gear mechanism 21 is arranged on a first axial side L1 with respect to the second planetary gear mechanism 22.

[0017] The first planetary gear PG1 is configured to rotate (revolve) about the carrier axis X1 and also rotate (spin) about the first planetary axis X2. In this embodiment, the first planetary gear PG1 rotates once about the first planetary axis X2 while making one revolution about the carrier axis X1. In other words, in this embodiment, the orbital period and rotation period of the first planetary gear PG1 are equal.

[0018] In this embodiment, the first planetary gear PG1 is coupled to and rotates integrally with the first planetary shaft PS1, which is a shaft member whose rotation axis is the first planetary axis X2. In this 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 by the first carrier CR1 via a pair of first planetary bearings B1 disposed separately on both sides of the first planetary gear PG1 in the axial direction L. In this way, in this 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) about the carrier axis X1 and also rotate (spin) about the second planetary axis X3. In this embodiment, the second planetary gear PG2 rotates once about the second planetary axis X3 while making one revolution about the carrier axis X1. In other words, in this embodiment, the orbital period and rotation period of the second planetary gear PG2 are equal.

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

[0021] In this 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 internally toothed gear that meshes with the first planetary gear PG1. The first ring gear RG1 is supported by the support member 1 so as to be non-rotatable relative to the support member 1.

[0023] The third planetary gear PG3 is connected to the first planetary gear PG1 so as to rotate integrally with the first planetary gear PG1. In this embodiment, the third planetary gear PG3 is disposed on the second axial side L2 relative to the first planetary gear PG1. The third planetary gear PG3 is connected to the first planetary shaft PS1. In this embodiment, the third planetary gear PG3 has a smaller diameter than the first planetary gear PG1.

[0024] The fourth planetary gear PG4 is rotatably supported by the first carrier CR1. The fourth planetary gear PG4 rotates (revolves) around the carrier axis X1 and also rotates (spins) around an axis different from the first planetary axis X2. The fourth planetary gear PG4 has the same diameter as the third planetary gear PG3.

[0025] In this embodiment, the fourth planetary gear PG4 is coupled to the third planetary shaft PS3 so as to rotate integrally with the fourth planetary gear PG4. In this embodiment, the third planetary shaft PS3 is disposed to extend from the fourth planetary gear PG4 toward the first axial side L1. The third planetary shaft PS3 is rotatably supported relative to the first carrier CR1 via a pair of third planetary bearings B3 that are disposed on the first axial side L1 relative to the fourth planetary gear PG4.

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

[0027] In this embodiment, the second planetary gear mechanism 22 further includes a second ring gear RG2. The second ring gear RG2 is an internally toothed gear that meshes with the second planetary gear PG2. The second ring gear RG2 is supported by the support member 1 so as to be non-rotatable relative 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 interlocking mechanism 3 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 interlocking mechanism 3 includes a carrier coupling member 31. The carrier coupling member 31 couples the first carrier CR1 and the second carrier CR2 so that they rotate integrally.

[0030] In this embodiment, the interlocking mechanism 3 further includes a ring gear connecting member 32. The ring gear connecting member 32 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 its axis coincident with the carrier axis X1. The support member 1 is disposed radially inward of the ring gear connecting member 32 in the R direction.

[0031] The output member 6 is connected to an 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 with" includes rotating at the same speed and rotating at a predetermined gear ratio, regardless of the rotation direction.

[0032] The output member 6 includes an intermediate portion 60 that is 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 its axis center coincident with the carrier axis X1. In the present embodiment, the first cylindrical portion 61 is disposed so as to extend from the output sun gear SG that meshes with the third planetary gear PG3 of the first planetary gear mechanism 21 to the second axial side L2 toward the second planetary gear mechanism 22. In this manner, in the present embodiment, the first cylindrical portion 61 functions as the intermediate 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. The carrier connecting member 31 is disposed on the carrier axis X1 so as to penetrate in the axial direction L inside the first cylindrical portion 61 in the radial direction R.

[0034] The support member 1 is fixed so as not to be rotatable. In this 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 this embodiment, the pair of first support portions 11 are formed to extend inward in the radial direction R from the ring gear connecting member 32 of the interlocking mechanism 3. 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 inward in the radial direction R from the ring gear connecting member 32 of the interlocking mechanism 3. 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. In the present embodiment, the second support portion 12 on the first axial side L1 is disposed 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 disposed on the second axial side L2 with respect to the second ring gear RG2.

[0037] The first crank member 41 is disposed to extend in the first planetary radial direction Rp1. The first crank member 41 extends between the first planetary axis X2 and a first input axis X4 spaced from the first planetary axis X2 in the first planetary radial direction Rp1. The first crank member 41 is connected to the first planetary gear PG1 so as to rotate integrally with the first planetary gear PG1. In this embodiment, the first crank member 41 is connected to a portion of the first planetary shaft PS1 that protrudes from the first carrier CR1 toward the first axial side L1 so as to be non-rotatable relative to the first planetary shaft PS1.

[0038] The first input member 51 is a member to which a predetermined driving force is input from outside the power conversion device 10. The first input member 51 is disposed on the first input axis X4. The first input member 51 is supported by the first crank member 41. In this embodiment, the first input member 51 is a shaft member disposed so as to protrude from the first crank member 41 toward the first axial side L1. The first input member 51 is coupled to the first crank member 41 so as not to be rotatable relative to the first crank member 41.

[0039] The second crank member 42 is disposed to extend in the second planetary radial direction Rp2. The second crank member 42 extends between the second planetary axis X3 and a second input axis X5 spaced from the second planetary axis X3 in the second planetary radial direction Rp2. The second crank member 42 is connected to the second planetary gear PG2 so as to rotate integrally with the second planetary gear PG2. In this embodiment, the second crank member 42 is connected to a portion of the second planetary shaft PS2 that protrudes from the second carrier CR2 toward the second axial side L2 so as not to rotate relative to the second planetary shaft PS2.

[0040] The second input member 52 is a member to which a predetermined driving force is input from outside the power conversion device 10. The second input member 52 is disposed on the second input axis X5. The second input member 52 is supported by the second crank member 42. In this embodiment, the second input member 52 is a shaft member disposed so as to protrude from the second crank member 42 toward the second axial side L2. The second input member 52 is coupled to the second crank member 42 so as not to be rotatable relative to the second crank member 42.

[0041] In this 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 this 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. Furthermore, 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. Furthermore, 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 this embodiment, the power conversion device 10 further includes a speed increasing mechanism 7. The speed increasing mechanism 7 is disposed in a power transmission path between the first planetary gear PG1 and the output member 6. The speed increasing mechanism 7 increases the rotation of the first planetary gear PG1 and transmits the rotation to the output member 6.

[0044] As described above, in this embodiment, the first planetary gear mechanism 21 includes the fixed first ring gear RG1, the first planetary gear PG1 meshing with the first ring gear RG1, the third planetary gear PG3 rotating integrally with the first planetary gear PG1, and the output sun gear SG meshing with the third planetary gear PG3 and rotating 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 this embodiment, the first planetary gear mechanism 21 accelerates the rotation of the first planetary gear PG1 and transmits it to the output member 6. That is, in this embodiment, the first planetary gear mechanism 21 functions as the speed-increasing mechanism 7.

[0045] 1 , the power generating device 100 includes a rotating electric machine 9 in addition to the power conversion device 10 described above. 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 this embodiment, the stator 91 is fixed to a support member 1 serving as a non-rotating member.

[0047] The rotor 92 is rotatably supported relative to the stator 91. In this 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 portion 60 so as to rotate integrally with the output member 6. In the illustrated example, the rotor 92 is attached to the outer circumferential surface of the first cylindrical portion 61.

[0048] In this embodiment, the stator 91 and the rotor 92 are disposed on the carrier axis X1. The rotor 92 is disposed radially inward of the stator 91 in the radial direction R. In this 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 motion of the first input member 51 and the second input member 52 is converted into the rotational motion of the output member 6. Accordingly, the rotor 92 of the rotating electric machine 9 rotates integrally with the output member 6. As a result, the rotating electric machine 9 generates electricity using the driving force transmitted to the rotor 92.

[0050] 2 to 6, the reciprocating motion of the first input member 51 and the second input member 52 according to this embodiment will be described. Note that in Figures 2 to 6, a locus T1 indicated by a dashed line is the movement locus of the first input shaft center X4 and the second input shaft center X5 associated with the reciprocating motion of the first input member 51 and the second input member 52. Furthermore, a locus T2 indicated by a dashed line is the movement locus of the first planetary shaft center X2 and the second planetary shaft center X3 associated with the reciprocating motion 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 movement locus of the first planetary axis X2, which is the rotational axis of the first planetary gear PG1, and the second planetary axis X3, which is the rotational axis of the second planetary gear PG2, is circular with the carrier axis X1 as the center when viewed in 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 movement locus of the first planetary axis X2 and the movement locus of the second planetary axis X3 caused by the reciprocating motion of the first input member 51 and the second input member 52 coincide with each other when viewed in the axial direction L.

[0053] 2 to 6 , in an axial view along the axial direction L, the first planetary axis X2 and the second planetary axis X3 are disposed on opposite sides of the carrier axis X1 and at positions that are the same distance from the carrier axis X1. In this embodiment, in an axial view along the axial direction L, the first planetary axis X2, the carrier axis X1, and the second planetary axis X3 are disposed so as to be aligned on a straight line. That is, in this embodiment, the first planetary axis X2 and the second planetary axis X3 are disposed with a phase difference of 180°.

[0054] 2 to 6 , 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, so that the first input shaft center X4 and the second input shaft center X5 are located on opposite sides of the carrier shaft center X1 when viewed in the axial direction L. In this embodiment, the direction along a straight line passing through the first planetary shaft center X2 and the first input shaft center X4, i.e., the extension direction of the first crank member 41, and the direction along a straight line passing through the second planetary shaft center X3 and the second input shaft center X5, i.e., the extension direction of the second crank member 42, are arranged to be parallel to each other.

[0055] As described above, 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 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 this embodiment, a locus T1, which is a movement locus of the first input shaft center X4 and the second input shaft center X5, is elliptical with the carrier shaft center X1 as the center when viewed in the axial direction L. The movement direction of the first input shaft center X4 and the second input shaft center X5 along the elliptical locus T1 is opposite to the movement direction of the first planetary shaft center X2 and the second planetary shaft center X3 along the circular locus T2 (the rotation direction of the first carrier CR1 and the second carrier CR2).

[0057] As described above, 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 the same as the distance in the second planetary radial direction Rp2 between the second planetary axis X3 and the second input axis X5. The first input axis X4, the carrier axis X1, and the second input axis X5 are arranged to be aligned on a straight line when viewed in the axial direction L. Therefore, in this embodiment, the movement locus of the first input axis X4 and the movement locus of the second input axis X5, which are caused by the reciprocating motion of the first input member 51 and the second input member 52, coincide with each other when viewed in the axial direction L.

[0058] 2, in an axial view along the axial direction L, the first input shaft center X4 is located on the opposite side of the carrier shaft center X1 with respect to the first planetary shaft center X2, and the second input shaft center X5 is located on the opposite side of the carrier shaft center X1 with respect to the second planetary shaft center X3. In addition, in an axial view along the axial direction L, the first input shaft center X4, the first planetary shaft center X2, the carrier shaft center X1, the second planetary shaft center X3, and the second input shaft center X5 are aligned on a straight line. In this case, based on the circular locus T2, the phase of the first planetary shaft center X2 is set to 0°, and the phase of the second planetary shaft center X3 is set to 180°.

[0059] In the example shown in Fig. 3, the first planetary shaft center X2 and the second planetary shaft center X3 have rotated 45° clockwise around the carrier shaft center X1 from the state shown in Fig. 2. In other words, the phase of the first planetary shaft center X2 is 45°, and the phase of the second planetary shaft center X3 is 225°. At this time, the first input shaft center X4 and the second input shaft center X5 have rotated counterclockwise around the carrier shaft center X1 from the state shown in Fig. 2.

[0060] In the example shown in Fig. 4, the first planetary shaft center X2 and the second planetary shaft center X3 are rotated 45° clockwise around the carrier shaft center X1 from the state shown in Fig. 3. In other words, the phase of the first planetary shaft center X2 is 90°, and the phase of the second planetary shaft center X3 is 270°. At this time, when viewed in the axial direction L, the first input shaft center X4 and the second input shaft center X5 are located on a straight line passing through the first planetary shaft center X2, the carrier shaft center X1, and the second planetary shaft center X3. In other words, when viewed in the axial direction along the axial direction L, the first input 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 so that 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.

[0061] In the example shown in Fig. 5, the first planetary shaft center X2 and the second planetary shaft center X3 have rotated 45° clockwise around the carrier shaft center X1 from the state shown in Fig. 4. In other words, the phase of the first planetary shaft center X2 is 135°, and the phase of the second planetary shaft center X3 is 315°. At this time, the first input shaft center X4 and the second input shaft center X5 have rotated counterclockwise around the carrier shaft center X1 from the state shown in Fig. 4.

[0062] In the example shown in Fig. 6, the first planetary shaft center X2 and the second planetary shaft center X3 are rotated 45° clockwise around the carrier shaft center X1 from the state shown in Fig. 5. In other words, the phase of the first planetary shaft center X2 is 180°, and the phase of the second planetary shaft center X3 is 0°. At this time, as viewed in the axial direction L, the first input shaft center X4 is located on the opposite side of the carrier shaft center X1 with respect to the first planetary shaft center X2, and the second input shaft center X5 is located on the opposite side of the carrier shaft center X1 with respect to the second planetary shaft center X3. As viewed in the axial direction L, the first input shaft center X4, the first planetary shaft center X2, the carrier shaft center X1, the second planetary shaft center X3, and the second input shaft center X5 are aligned on a straight line.

[0063] Note that, although a description of the process until the phase of the first planetary axis X2 becomes 0° will be 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 describe an elliptical locus T1.

[0064] 7, in this embodiment, the power generation device 100 is mounted on a bicycle B. Therefore, in this 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, which is caused by operation by the rider of the bicycle B, into rotational motion of the output member 6 and outputs the rotational motion.

[0065] In addition to the first pedal P1 and the second pedal P2, the bicycle B includes a seat S, a handlebar H, a frame F, a driving wheel W1, and a driven wheel W2. In this embodiment, the bicycle B further includes an electricity storage device (not shown) and a motor (not shown).

[0066] The first pedal P1 and the second pedal P2 are members that the driver steps on with his / her feet. The seat S is a member on which the driver sits. The handlebars H are a member that the driver grips. The frame F is a member that supports the seat S, the handlebars H, the driving wheels W1, the driven wheels W2, and the power conversion device 10. A 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 driver's operation. The driven wheel W2 is rotatably supported on the frame F. In this embodiment, the drive wheel W1 is a rear wheel, and the driven wheel W2 is a front wheel.

[0068] In this embodiment, the rotating electric machine 9 generates electricity using the driving force transmitted to the output member 6 by the rider of the bicycle B, and stores the electricity in the power storage device. The motor receives power from the power storage device to drive the drive wheel W1.

[0069] 2. Second Embodiment A power conversion device 10 according to a second embodiment and a power generation device 100 including the same will be described below with reference to FIG. 8. In this 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. The following description will focus on the differences from the first embodiment. Note that points that are not specifically described are the same as those in the first embodiment.

[0070] As shown in FIG. 8, in this 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 by the first carrier CR1. The fifth planetary gear PG5 rotates (revolves) around the carrier axis X1 and also rotates (spins) 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 this embodiment, the first sun gear SG1 meshes with the fifth planetary gear PG5. The first sun gear SG1 is disposed on the first axial side L1 relative to the output sun gear SG.

[0073] In this embodiment, the first planetary gear mechanism 21 does not include a first ring gear RG1. Therefore, in this embodiment, the first planetary gear PG1 does not mesh with the first ring gear RG1. In this embodiment, the first planetary gear PG1 has a smaller diameter than the third planetary gear PG3. In addition, the output sun gear SG has a smaller diameter than the third planetary gear PG3.

[0074] Thus, in this embodiment, the first planetary gear mechanism 21 increases the rotation speed of the first planetary gear PG1 and transmits the rotation to the output member 6. That is, in this 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 disposed so as 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 by the first carrier CR1 via a pair of first planetary bearings B1 that are disposed separately on a first axial side L1 relative to the first planetary gear PG1 and a second axial side L2 relative to the third planetary gear PG3.

[0077] In this embodiment, the third planetary shaft PS3 is disposed so as 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 disposed separately 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 by the second carrier CR2. The sixth planetary gear PG6 rotates (revolves) around the carrier axis X1 and also rotates (spins) around an axis different from the second planetary axis X3. In this embodiment, the sixth planetary gear PG6 has the same diameter as the fifth planetary gear PG5.

[0080] The second sun gear SG2 is disposed 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. The second sun gear SG2 has 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, so 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 its axis center coincident with the carrier axis X1. The second cylindrical portion 34 is disposed 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 the present embodiment, the carrier connecting member 31 is disposed so as to penetrate inward in the radial direction R relative to the second cylindrical portion 34, the first sun gear SG1, and the second sun gear SG2 in the axial direction L. The carrier connecting member 31 is rotatably supported relative to the first sun gear SG1 via a first sun gear bearing B61, and is rotatably supported relative to the second sun gear SG2 via a 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 A power conversion device 10 according to a third embodiment will be described below 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. The following description will focus on the differences from the second embodiment. Note that points that are not specifically described are the same as those in the second embodiment.

[0089] As shown in Fig. 9, in this embodiment, the power conversion device 10 is not included 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. Furthermore, 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. Furthermore, a pair of output bearings B4 are arranged between the inner circumferential surface of the support member 1 and the outer circumferential 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 to the fifth planetary gear PG5 so as to rotate integrally with the fifth planetary gear PG5. The seventh planetary gear PG7 is meshed with the output sun gear SG. In this manner, in this embodiment, the first planetary gear mechanism 21 and the second planetary gear mechanism 22 are configured so that the direction in which the intermediate 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 the present embodiment, the output member 6 further includes a wheel coupling portion 62. The wheel coupling portion 62 is configured to be coupled to the drive wheel W1. The wheel coupling portion 62 is coupled to the intermediate portion 60 so as to rotate integrally therewith. In the present embodiment, the wheel coupling portion 62 rotates in the same direction as the revolution direction of the first planetary gear PG1. In addition, in the present embodiment, the wheel coupling portion 62 and the intermediate portion 60 are disposed on the carrier axis X1. In the example shown in FIG. 9 , the wheel coupling portion 62 is formed so as to extend outward in the radial direction R from the first cylindrical portion 61 serving as the intermediate portion 60.

[0093] 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 disposed on the carrier axis X1. In this embodiment, the first sprocket SP1 functions as a wheel coupling 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 in accordance with the rotation of the first sprocket SP1. In the example shown in Figure 10, the second sprocket SP2 has a smaller diameter than the first sprocket SP1.

[0097] The third sprocket SP3 is arranged coaxially with the second sprocket SP2 and is connected to the second sprocket SP2 so as to rotate integrally with the second sprocket SP2. In the example shown in Figure 10, the third sprocket SP3 has a larger diameter than the second sprocket SP2.

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

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

[0100] 4. Fourth Embodiment A power conversion device 10 according to a fourth embodiment and a power generation device 100 including the same will be described below with reference to FIG. 11 . In this embodiment, the configurations of the first planetary gear mechanism 21 and the output member 6 are different from those of the second embodiment. The following description will focus on the differences from the second embodiment. Note that points that are not specifically described are the same as those of the second embodiment.

[0101] As shown in FIG. 11 , in this 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 a first planetary chain 2a wound around them. The output sun gear SG has a smaller diameter than the third planetary gear PG3. In this embodiment, the third planetary gear PG3 and the output sun gear SG are not housed in the first carrier CR1. In addition, in this embodiment, the first planetary gear mechanism 21 does not include a fourth planetary gear PG4.

[0102] In this embodiment, as in the third embodiment, the output member 6 includes a wheel coupling portion 62. Furthermore, the bicycle B on which the power conversion device 10 is mounted includes an electric storage device and a motor, as in the first embodiment, and also includes a transmission mechanism T, as in the third embodiment. The first sprocket SP1 of the transmission mechanism T functions as the wheel coupling portion 62 of the output member 6.

[0103] In this embodiment, the driving force generated by the operation of the rider of bicycle B is transmitted from the output member 6 to the drive wheel W1 via the transmission mechanism T. Also, in this embodiment, the rotating electric machine 9 generates electricity using the driving force generated by the operation of the rider of bicycle B, and stores the electricity in the power storage device. The motor then receives power from the power storage device and runs, driving the drive wheel W1.

[0104] 5. Fifth Embodiment A power conversion device 10 according to a fifth embodiment will be described below 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. The following description will focus on the differences from the third embodiment. Note that aspects that are not specifically described are the same as those of 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 this 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 this application, when a pair of gears are sprockets connected to each other by a chain wound around them, the pair of gears is considered to be meshed with each other. In other words, in this embodiment, the first planetary gear PG1 and the first sun gear SG1, which are sprockets, are meshed with each other. In this embodiment, the first sun gear SG1 has a larger diameter than the first planetary gear PG1.

[0107] In this embodiment, the first planetary gear PG1 and the first sun gear SG1, which are sprockets, are housed in the first carrier CR1. In this configuration, it is preferable that the first carrier CR1 has openings for inserting the first planetary gear PG1 and the first sun gear SG1. Then, it is preferable that the first planetary gear PG1 and the first sun gear SG1 are housed inside the first carrier CR1 through the openings, and then the first planetary shaft PS1 is inserted through the first planetary gear PG1 and the second cylindrical portion 34 is inserted through the first sun gear SG1.

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

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

[0110] In this embodiment, the second planetary gear mechanism 22 does not include a 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. In addition, in this embodiment, the second sun gear SG2 has a larger diameter than the second planetary gear PG2.

[0112] In this embodiment, the second planetary gears PG2 and the second sun gear SG2, which are sprockets, are housed in the second carrier CR2. In this configuration, it is preferable that the second carrier CR2 has openings for inserting the second planetary gears PG2 and the second sun gears SG2. Then, it is preferable that the second planetary gears PG2 and the second sun gears SG2 are housed inside the second carrier CR2 through the openings, and then the second planetary shaft PS2 is inserted through the second planetary gears PG2 and the second cylindrical portion 34 is inserted 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] For this reason, although not shown in the drawings, in this embodiment, a locus T1, which is a movement locus of the first input shaft center X4 and the second input shaft center X5, is elliptical with the carrier shaft center X1 as the center when viewed in the axial direction L. The movement direction of the first input shaft center X4 and the second input shaft center X5 along the elliptical locus T1 is the same as the movement direction of the first planetary shaft center X2 and the second planetary shaft center X3 along the circular locus T2 (the rotation direction of the first carrier CR1 and the second carrier CR2).

[0115] 6. Sixth Embodiment A power conversion device 10 according to a sixth embodiment and a power generation device 100 including the same will be described below with reference to FIG. 13 . In this 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. The following description will focus on the differences from the first embodiment. Note that points that are not specifically described are the same as those of the first embodiment.

[0116] In this 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 a first cylindrical portion 61, but includes an orthogonal shaft portion 63. The orthogonal shaft portion 63 is formed in an axial shape along the radial direction R. The orthogonal shaft portion 63 is disposed between the first planetary gear mechanism 21 and the second planetary gear mechanism 22 in the axial direction L. Therefore, in the present embodiment, the orthogonal shaft portion 63 functions as the intermediate portion 60.

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

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

[0120] The third support portion 13 rotatably supports the orthogonal shaft portion 63 of the output member 6. In this embodiment, the third support portion 13 is disposed coaxially with the orthogonal shaft portion 63 and is formed in a cylindrical shape that covers the orthogonal shaft portion 63. A pair of output bearings B4 are disposed between the inner circumferential surface of the third support portion 13 and the outer circumferential surface of the orthogonal shaft portion 63. 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 this embodiment, the speed-increasing mechanism 7 includes a first gear 71 and a second gear 72. The first gear 71 is connected to the carrier connecting member 31 so as to rotate integrally therewith. The second gear 72 is connected to the orthogonal shaft portion 63 of the output member 6 so as to rotate integrally therewith. The first gear 71 and the second gear 72 mesh with each other with their axes perpendicular to each other. In this 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 accelerated between the first gear 71 and the second gear 72 and then transmitted to the output member 6.

[0124] 7. Other Embodiments (1) In the above embodiment, an example has been described 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. However, without being 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 rotatable relative to the first crank member 41, and the second input member 52 may be connected to the second crank member 42 so as to be rotatable relative to the second crank member 42. Alternatively, a configuration may be adopted in which a shaft member as the first input member 51 and a shaft member as the second input member 52 are not provided, and a part of the first crank member 41 functions as the first input member 51, and a part of the second crank member 42 functions as the second input member 52.

[0125] (2) In the above embodiment, the first planetary shaft center X2 and the second planetary shaft center X3 are arranged with a phase difference of 180°. However, the present invention is not limited to such a configuration, and the first planetary shaft center X2 and the second planetary shaft center X3 may be arranged with a phase difference other than 180°.

[0126] (3) In the above embodiment, an example has been described in which there is a phase in which the first input shaft center X4, the first planetary shaft center X2, the carrier shaft center X1, the second planetary shaft center X3, and the second input shaft center X5 are aligned on a straight line on the locus T1 when viewed in the axial direction along the axial direction L. However, the present invention is not limited to such a configuration, and there may be a configuration in which there is no phase in which the first input shaft center X4, the first planetary shaft center X2, the carrier shaft center X1, the second planetary shaft center X3, and the second input shaft center X5 are aligned on a straight line on the locus T1 when viewed in the axial direction along the axial direction L.

[0127] (4) In the above embodiment, the first crank member 41 extends parallel to the line passing through the first planetary axis X2 and the first input axis X4 (the direction in which the first crank member 41 extends) and the second crank member 42 extends parallel to the line passing through the second planetary axis X3 and the second input axis X5 (the direction in which the second crank member 42 extends). However, the present invention is not limited to this configuration, and the first crank member 41 and the second crank member 42 may extend in a direction that intersects with each other.

[0128] (5) The configurations disclosed in the above-described embodiments can be applied in combination with configurations disclosed in other embodiments, as long as no contradictions arise. Regarding other configurations, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications can be made as appropriate within the scope of the present disclosure.

[0129] 8. Summary of the Present Embodiment The power conversion device (10) and the power generation device (100) described above will be outlined below.

[0130] The power conversion device (10) includes: a support member (1); a first planetary gear mechanism (21) including a first carrier (CR1) rotatably supported on the support member (1) and a first planetary gear (PG1) rotatably supported on the first carrier (CR1); a second planetary gear mechanism (22) including a second carrier (CR2) rotatably supported on the support member (1) and a second planetary gear (PG2) rotatably supported on the second carrier (CR2); and 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. a first crank member (41) disposed to extend in a first planetary radial direction (Rp1), with a direction orthogonal to a first planetary axis (X2) that is the rotation axis of the first planetary gear (PG1) being defined as a first planetary radial direction (Rp1), and connected to rotate integrally with the first planetary gear (PG1); a first input member (51) supported by the first crank member (41) and disposed on a first input axis (X4) spaced apart from the first planetary axis (X2) in the first planetary radial direction (Rp1); a second crank member (42) disposed to extend in a second planetary radial direction (Rp2), with a direction orthogonal to a second planetary axis (X3) that is the rotation axis of the second planetary gear (PG2), being defined as a second planetary radial direction (Rp2), and connected to rotate integrally with the second planetary gear (PG2); the interlocking mechanism (3) comprises: a second input member (52) supported by the second crank member (42) and disposed on a second input axis (X5) spaced apart from the second planetary axis (X3) in the second planetary radial direction (Rp2); and 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) comprising: 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; and a direction along a carrier axis (X1), which is the rotation axis of the first carrier (CR1) and the second carrier (CR2), is defined as an axial direction (L),When viewed in the axial direction along the axial direction (L), the first planetary axis (X2) and the second planetary axis (X3) are arranged on opposite sides of the carrier axis (X1) and at the same distance from the carrier axis (X1), 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), and the output member (6) has 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 portion (60) of the output member (6) is disposed between the first planetary gear mechanism (21) and the second planetary gear mechanism (22), which are disposed apart from each other in the axial direction (L). This facilitates downsizing of the power conversion device (10) in a configuration in which driving force is transmitted via the intermediate portion (60). This facilitates improving the mountability of the power conversion device (10) on an object to be mounted.

[0132] Here, it is preferable that the output member (6) has a first cylindrical portion (61) arranged on the carrier axis (X1), a direction perpendicular to the carrier axis (X1) is defined as a radial direction (R), and the carrier connecting member (31) is arranged on the carrier axis (X1) so as to penetrate the inside of the radial direction (R) relative to the first cylindrical portion (61) in the axial direction (L).

[0133] According to this configuration, the intermediate portion (60) is arranged 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) can be appropriately connected by the carrier connecting member (31).

[0134] In a configuration in which the output member (6) includes the first cylindrical portion (61), the first planetary gear mechanism (21) is arranged 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 arranged 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), and the interlocking mechanism (3) further includes a sun gear connecting member (33) that is fixed to the support member (1) and connects the first sun gear (SG1) and the second sun gear (SG2), The sun gear connecting member (33) has a second cylindrical portion (34) arranged on the carrier axis (X1), and it is preferable that the second cylindrical portion (34) is arranged 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, the intermediate 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] It is also preferable that the first planetary gear mechanism (21) further comprises a first ring gear (RG1) meshing with the first planetary gear (PG1), the second planetary gear mechanism (22) further comprises a second ring gear (RG2) meshing with the second planetary gear (PG2), the interlocking mechanism (3) further comprises a ring gear connecting member (32) connecting the first ring gear (RG1) and the second ring gear (RG2), and the ring gear connecting member (32) is 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 each other using a relatively simple configuration. Furthermore, according to this configuration, if the radius of the first ring gear (RG1) and the radius of the second ring gear (RG2) are the same, 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, which makes it easy to reduce the number of types of parts.

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

[0139] This configuration allows the rotation of the first crank member 41 to be accelerated and transmitted to the output member 6. Therefore, for example, when the rotor 92 of the rotating electric machine 9 is connected to the output member 6, it is easy to achieve high rotation speed of the rotor 92 of the rotating electric machine 9, which in turn makes it easy to reduce the size of the rotating electric machine 9. This is also advantageous when the power conversion device 10 is installed on a vehicle with small-diameter wheels.

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

[0141] According to this configuration, the movement loci (T1) of the first input shaft center (X4) and the second input shaft center (X5) accompanying the reciprocating motion of the first input member (51) and the second input member (52) can be made elliptical with respect to the carrier shaft center (X1). Furthermore, according to this configuration, it is easy to ensure a large stroke of the reciprocating motion 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 therefore the size of the power conversion device (10).

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

[0143] This configuration makes it easy to simplify the connection structure between the intermediate portion (60) and the wheel (W1), thereby making it easy to improve the mountability of the power conversion device (10) on an object having a wheel (W1).

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

[0145] This configuration makes it easy to increase the support rigidity of the first planetary gear (PG1) and the second planetary gear (PG2), and also makes it easy to retain lubricating oil for lubricating the first planetary gear (PG1) and the second planetary gear (PG2) around these gears.

[0146] The power generating device (100) comprises the above-mentioned power conversion device (10) and a rotating electric machine (9) having a stator (91) and a rotor (92), wherein 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 positioning 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 electricity can be generated by the rotating electric machine (9). Furthermore, according to this configuration, the rotor (92) of the rotating electric 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 connected to an intermediate portion (60) also disposed between the first planetary gear mechanism (21) and the second planetary gear mechanism (22) in the axial direction (L). This allows the power conversion device (10) and the power generation device (100) including the rotating electric machine (9) to be miniaturized.

[0148] The technology disclosed herein can be used in a power conversion device that converts reciprocating motion into rotational motion, and in a power generation device equipped with the same.

[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: Second 1 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 coupling portion, 7: speed increasing mechanism, 9: rotating electric machine, 91: stator, 92: rotor, RM: output rotating member, X1: carrier axis, X2: first planet axis, X3: second planet axis, X4: first input axis, X5: second input axis, L: axial direction, R: radial direction, Rp1: first planet radial direction, Rp2: second planet radial direction

Claims

1. A power conversion device comprising: 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; an interlocking mechanism for interlocking 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 arranged 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 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 which is a 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 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. In a direction along a carrier axis which is a rotation axis of the first carrier and the second carrier as an 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 positions where the distances from the carrier axis are the same. 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 includes an intermediate arrangement portion arranged between the first planetary gear mechanism and the second planetary gear mechanism in the axial direction.

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

3. The first planetary gear mechanism further includes a first sun gear disposed on the carrier axis and meshing 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 disposed on the carrier axis and meshing 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 fixed to the support member and connecting 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 second cylindrical portion is disposed inside the first cylindrical portion in the radial direction and outside the carrier connecting member in the radial direction. The power conversion device according to claim 2.

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

5. The power conversion device according to claim 1 further includes a speed increasing mechanism disposed in the power transmission path between the first planetary gear and the output member, for increasing the speed of rotation of the first planetary gear and transmitting it 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, and 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. The power conversion device according to any one of claims 1 to 5.

7. The output member further includes a wheel connection portion connected to the wheel, the wheel connection portion is connected so as to rotate integrally with the intermediate arrangement portion, the wheel connection portion and the intermediate arrangement portion are arranged on the carrier axis, and 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. The power conversion device according to any one of claims 1 to 5.

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

9. A power generation device comprising the power conversion device according to any one of claims 1 to 5 and a rotating electrical machine including a stator and a rotor, wherein the rotor is arranged 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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