Power conversion device

Abstract

This invention relates to a power conversion device. The radius (r1) of the ring gear (RG) is twice the radius (r2) of the first planetary gear (PG1). The first planetary gear (PG1) and the second planetary gear (PG2) are configured to revolve around the axis of rotation of the planet carrier (CR), i.e., the axis of rotation of the planet carrier (X1), at the same speed and in the same direction. When viewed axially, the axis of rotation of the first planetary gear (PG1), i.e., the first planetary axis (X2), and the axis of rotation of the second planetary gear (PG2), i.e., the second planetary axis (X3), are positioned across the axis of rotation of the planet carrier (X1). On the opposite side and at the same distance from the planetary carrier axis (X1), when viewed axially, the first crank assembly (2) is connected to the first planetary gear (PG1), and the second crank assembly (4) is connected to the second planetary gear (PG2), so that the first input shaft (X4), which is separated from the first planetary axis (X2) along the first planetary radial direction (Rp1), and the second input shaft (X5), which is separated from the second planetary axis (X3) along the second planetary radial direction (Rp2), are located on opposite sides across the planetary carrier axis (X1).

Description

Technical Field

[0001] This invention relates to a power conversion device that converts reciprocating motion into rotational motion. Background Technology

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

[0003] Patent Document 1: Japanese Patent Application Publication No. 9-323691

[0004] In the power conversion device of Patent Document 1, the input component (85) moves in a manner that traces a curved trajectory at a position offset from the rotation axis of the output component (1) (see Patent Document 1). Figure 3 Therefore, the aforementioned power conversion device becomes a structure that makes it difficult to transmit driving force to the input component (85). Summary of the Invention

[0005] Therefore, it is desirable to realize a power conversion device that can easily transmit driving force to the input component.

[0006] In view of the above, the power conversion device is characterized by the following features: it comprises: a planetary gear mechanism, which includes a fixed internal gear, i.e., a gear ring, a first planetary gear meshing with the gear ring, a second planetary gear disposed on a shaft different from the first planetary gear, and a planet carrier supporting the first planetary gear and the second planetary gear for rotation; a first crank member, which is disposed extending along a first planetary radial direction orthogonal to the rotation axis of the first planetary gear, i.e., the first planetary axis, and is integrally rotatably connected to the first planetary gear; a first input member, which is supported by the first crank member and disposed on a first input shaft that is separate from the first planetary axis along the first planetary radial direction; a second crank member, which is disposed extending along a second planetary radial direction orthogonal to the rotation axis of the second planetary gear, i.e., the second planetary axis, and is integrally rotatably connected to the second planetary gear; and a second input member, which is supported by the second crank member and disposed on a first input shaft that is separate from the first planetary axis along the first planetary radial direction; a second crank member, which is disposed extending along a second planetary radial direction orthogonal to the rotation axis of the second planetary gear, i.e., the second planetary axis, and is integrally rotatably connected to the second planetary gear; and a second input member, which is supported by the second crank member and disposed on a first input shaft that is integrally rotatably connected to the second planetary gear. The planetary axis is located on a second input axis that is radially separated from the second planetary axis; and an output component connected to a specific rotating component that, in addition to the first planetary gear and the second planetary gear, rotates in conjunction with the planetary carrier. The radius of the gear ring is twice the radius of the first planetary gear. The axis is defined as the direction along the rotation axis of the planetary carrier, i.e., the planetary carrier axis. The first planetary gear and the second planetary gear are configured to revolve around the planetary carrier axis at the same speed in the same direction. When viewed along the axial direction, the first planetary axis and the second planetary axis are arranged on opposite sides of each other across the planetary carrier axis and are arranged at the same distance from the planetary carrier axis. When viewed along the axial direction, the first crank component is connected to the first planetary gear and the second crank component is connected to the second planetary gear in such a way that the first input axis and the second input axis are located on opposite sides of each other across the planetary carrier axis.

[0007] Based on this feature structure, the respective movement trajectories of the first and second input shafts, which accompany the reciprocating motion of the first and second input components, can be set as a straight line or an ellipse with reference to the planetary carrier axis. Furthermore, the phase difference between the first and second input shafts can be set to 180° or a value close to that. Therefore, a power conversion device can be realized that easily transmits driving force to the first input component mounted on the first input shaft and the second input component mounted on the second input shaft. Attached Figure Description

[0008] Figure 1 This is a cross-sectional view of the power conversion device according to the first embodiment.

[0009] Figure 2This diagram illustrates the reciprocating motion of the first input component and the second input component in the first embodiment.

[0010] Figure 3 This diagram illustrates the reciprocating motion of the first input component and the second input component in the first embodiment.

[0011] Figure 4 This diagram illustrates the reciprocating motion of the first input component and the second input component in the first embodiment.

[0012] Figure 5 This diagram illustrates the reciprocating motion of the first input component and the second input component in the first embodiment.

[0013] Figure 6 This diagram illustrates the reciprocating motion of the first input component and the second input component in the first embodiment.

[0014] Figure 7 This is a diagram of a bicycle equipped with the power conversion device of the first embodiment.

[0015] Figure 8 This is a cross-sectional view showing the power conversion device of the second embodiment.

[0016] Figure 9 This diagram illustrates the reciprocating motion of the first input component and the second input component in the second embodiment.

[0017] Figure 10 This diagram illustrates the reciprocating motion of the first input component and the second input component in the second embodiment.

[0018] Figure 11 This diagram illustrates the reciprocating motion of the first input component and the second input component in the second embodiment.

[0019] Figure 12 This diagram illustrates the reciprocating motion of the first input component and the second input component in the second embodiment.

[0020] Figure 13 This diagram illustrates the reciprocating motion of the first input component and the second input component in the second embodiment.

[0021] Figure 14 This is a diagram of a bicycle equipped with the power conversion device according to the second embodiment.

[0022] Figure 15 This is a cross-sectional view of the power conversion device according to the third embodiment. Detailed Implementation

[0023] 1. First Implementation Method

[0024] The following is for reference Figures 1-7 The power conversion device 100 of the first embodiment will be described.

[0025] like Figure 1 As shown, the power conversion device 100 includes: a planetary gear mechanism 1, a first crank assembly 2, a first input assembly 3, a second crank assembly 4, a second input assembly 5, and an output assembly 6. The power conversion device 100 is a device that converts the reciprocating motion of the first input assembly 3 and the second input assembly 5 into the rotational motion of the output assembly 6 via the planetary gear mechanism 1.

[0026] The planetary gear mechanism 1 includes a ring gear RG, a first planetary gear PG1, a second planetary gear PG2, and a planet carrier CR. The ring gear RG is an internal gear that is fixed in place without rotation. The first planetary gear PG1 meshes with the ring gear RG. The second planetary gear PG2 is mounted on a different shaft than the first planetary gear PG1. The planet carrier CR supports the first planetary gear PG1 and the second planetary gear PG2 so that they can rotate.

[0027] In the following description, the direction along the rotation axis of the planet carrier CR, i.e., the planet carrier axis X1, is designated as "axial direction L". Furthermore, one side of axial direction L is designated as "first axial side L1", and the other side of axial direction L is designated as "second axial side L2". The direction orthogonal to the planet carrier axis X1 is designated as "radial direction R". Additionally, the direction orthogonal to the rotation axis of the first planetary gear PG1, i.e., the first planetary axis X2, is designated as "first planetary radial direction Rp1". Furthermore, the direction orthogonal to the rotation axis of the second planetary gear PG2, i.e., the second planetary axis X3, is designated as "second planetary radial direction Rp2".

[0028] The first planetary gear PG1 and the second planetary gear PG2 are configured to rotate (revolve) about the planet carrier axis X1 at the same speed and in the same direction.

[0029] The first planetary gear PG1 is configured to rotate (spin) about the first planetary axis X2. In this embodiment, the first planetary gear PG1 is integrally connected to the shaft component, namely the first planetary shaft PS1, which has the first planetary axis X2 as its axis of rotation. In this embodiment, the first planetary shaft PS1 is configured to pass through the first planetary gear PG1 along the axial direction L. Moreover, the first planetary shaft PS1 is supported by the planet carrier CR and is rotatable via a pair of first planetary bearings B1 that are separately disposed on both sides of the first planetary gear PG1 along the axial direction L.

[0030] The second planetary gear PG2 is configured to rotate (spin) about the second planetary axis X3. In this embodiment, the second planetary gear PG2 is integrally connected to the shaft component, namely the second planetary shaft PS2, which has the second planetary axis X3 as its axis of rotation. In this embodiment, the second planetary shaft PS2 is configured to pass through the second planetary gear PG2 along the axial direction L. Furthermore, the second planetary shaft PS2 is supported by the planet carrier CR and is rotatable via a pair of second planetary bearings B2 that are separately disposed on both sides of the second planetary gear PG2 along the axial direction L.

[0031] In this embodiment, the planetary gear mechanism 1 has a first gear ring RG1 as a gear ring RG, and also has a second gear ring RG2.

[0032] The second gear ring RG2 is an internal gear that is fixed in a non-rotatable manner. The second gear ring RG2 meshes with the second planetary gear PG2. In this embodiment, the second gear ring RG2 is disposed on the second axial side L2 relative to the first gear ring RG1.

[0033] In this embodiment, the first ring gear RG1 and the second ring gear RG2 are fixed to a ring gear support RS disposed between them in the axial direction L. The ring gear support RS supports the planet carrier CR from the outer side in the radial direction R via a ring gear bearing B3, enabling it to rotate. In this embodiment, the ring gear support RS is formed to extend from the first ring gear RG1 and the second ring gear RG2 toward the inner side in the radial direction R. Furthermore, a first planetary gear PG1 and a first planetary shaft PS1 are disposed on the first axial side L1 relative to the ring gear support RS, and a second planetary gear PG2 and a second planetary shaft PS2 are disposed on the second axial side L2 relative to the ring gear support RS.

[0034] The radius r1 of the ring gear RG (first ring gear RG1) is twice the radius r2 of the first planetary gear PG1 (r1 = r2 × 2). Therefore, the first planetary gear PG1 rotates once around the first planetary axis X2 during the period it takes to rotate once around the planet carrier axis X1. That is, the revolution period and rotation period of the first planetary gear PG1 are equal. Furthermore, in this application, "radius of a gear" refers to the radius of its pitch circle.

[0035] In this embodiment, the radius r3 of the second ring gear RG2 is twice the radius r4 of the second planetary gear PG2 (r3 = r4 × 2). Therefore, in this embodiment, the second planetary gear PG2 rotates once around the second planetary axis X3 during the period when it rotates once around the planet carrier axis X1. That is, in this embodiment, the revolution period and the rotation period of the second planetary gear PG2 are equal.

[0036] Furthermore, in this embodiment, the first gear ring RG1 and the second gear ring RG2 have the same diameter (r1=r3). Moreover, the first planetary gear PG1 and the second planetary gear PG2 have the same diameter (r2=r4).

[0037] like Figure 1 As shown, the first crank component 2 is configured to extend along the first planetary radial direction Rp1. The first crank component 2 extends over the first planetary axis X2 and the first input axis X4 extending from the first planetary axis X2 toward the first planetary radial direction Rp1. The first crank component 2 is integrally rotatably connected to the first planetary gear PG1. In this embodiment, the first crank component 2 is connected to the portion of the first planetary shaft PS1 that is axially closer to the first side L1 than the first planetary gear PG1 in a non-rotatable manner.

[0038] The first input component 3 is a component that inputs a predetermined driving force from the outside of the power conversion device 100. The first input component 3 is disposed on the first input shaft X4. The first input component 3 is supported by the first crank component 2. In this embodiment, the first input component 3 is a shaft component disposed in a manner that protrudes from the first crank component 2 toward a first axial side L1. Moreover, the first input component 3 is integrally rotatably connected to the first crank component 2.

[0039] The second crank assembly 4 is configured to extend along the radial direction Rp2 of the second planetary gear. The second crank assembly 4 extends over the second planetary shaft X3 and a second input shaft X5, which is separated from the second planetary shaft X3 in the radial direction Rp2. The second crank assembly 4 is integrally rotatably connected to the second planetary gear PG2. In this embodiment, the second crank assembly 4 is connected to the portion of the second planetary shaft PS2 that is axially positioned on the second side L2 of the second planetary gear PG2, in a manner that prevents relative rotation.

[0040] The second input component 5 is a component that inputs a predetermined driving force from the outside of the power conversion device 100. The second input component 5 is disposed on the second input shaft X5. The second input component 5 is supported by the second crank component 4. In this embodiment, the second input component 5 is a shaft component disposed in a manner that protrudes from the second crank component 4 toward the axial second side L2. Moreover, the second input component 5 is integrally rotatably connected to the second crank component 4.

[0041] In this embodiment, the distance d1 between the first planetary axis X2 and the first input axis X4 (first planetary radial distance Rp1) and the distance d2 between the second planetary axis X3 and the second input axis X5 (second planetary radial distance Rp2) are the same (d1=d2). Furthermore, the radius r2 of the first planetary gear PG1 and the distance d1 between the first planetary axis X2 and the first input axis X4 (first planetary radial distance Rp1) are the same (r2=d1). Moreover, the radius r4 of the second planetary gear PG2 and the distance d2 between the second planetary axis X3 and the second input axis X5 (second planetary radial distance Rp2) are the same (r4=d2).

[0042] Furthermore, in this embodiment, the first pedal P1, described later, is connected to the first input component 3 in a rotatable manner. Also, the second pedal P2, described later, is connected to the second input component 5 in a rotatable manner.

[0043] Output component 6 is connected to a specific rotating component RT. The specific rotating component RT is a rotating component other than the first planetary gear PG1 and the second planetary gear PG2, and it is a rotating component that rotates in conjunction with the planet carrier CR. In this embodiment, the specific rotating component RT is the planet carrier CR. Here, "rotating in conjunction" includes rotating at the same speed and rotating at a predetermined gear ratio, and the direction of rotation is not limited.

[0044] Here, refer to Figures 2-6 The reciprocating motion of the first input component 3 and the second input component 5 in this embodiment will be described. Furthermore, in Figures 2-6 In the diagram, trajectory T1, represented by a single-dotted line, is the movement trajectory of the first input axis X4 and the second input axis X5, respectively, accompanying the reciprocating motion of the first input component 3 and the second input component 5. Similarly, trajectory T2, represented by a double-dotted line, is the movement trajectory of the first planetary axis X2 and the second planetary axis X3, respectively, accompanying the reciprocating motion of the first input component 3 and the second input component 5.

[0045] As described above, the first planetary gear PG1 and the second planetary gear PG2 revolve around the planet carrier axis X1. Therefore, the trajectory T2 of the first planetary axis X2, which is the axis of rotation of the first planetary gear PG1, and the second planetary axis X3, which is the axis of rotation of the second planetary gear PG2, is a circle centered on the planet carrier axis X1 when viewed along the axis L.

[0046] Furthermore, as described above, in this embodiment, the first gear ring RG1 and the second gear ring 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 trajectories of the first planetary axis X2 and the second planetary axis X3, which accompany the reciprocating motion of the first input component 3 and the second input component 5, are consistent when viewed along the axial direction L.

[0047] like Figures 2-6 As shown, when viewed along the axis L, the first planetary axis X2 and the second planetary axis X3 are arranged on opposite sides of the planet carrier axis X1, separated by the planet carrier axis X1, and are positioned at the same distance from the planet carrier axis X1. In this embodiment, when viewed along the axis L, the first planetary axis X2, the planet carrier axis X1, and the second planetary axis X3 are arranged in a straight line. That is, in this embodiment, the first planetary axis X2 and the second planetary axis X3 are arranged with a 180° phase difference.

[0048] like Figures 2-6 As shown, viewed axially along axis L, the first crank assembly 2 is connected to the first planetary gear PG1 with the first input shaft X4 and the second input shaft X5 located on opposite sides of each other across the planetary carrier shaft X1, and the second crank assembly 4 is connected to the second planetary gear PG2. In this embodiment, the crank assembly 2 is arranged parallel to each other along the direction of the straight line passing through the first planetary shaft X2 and the first input shaft X4, i.e., the extension direction of the first crank assembly 2, and along the direction of the straight line passing through the second planetary shaft X3 and the second input shaft X5, i.e., the extension direction of the second crank assembly 4.

[0049] As described above, in this embodiment, the radius r2 of the first planetary gear PG1 and the distance d1 between the first planetary axis X2 and the first planetary radial distance Rp1 of the first input axis X4 are the same. Similarly, the radius r4 of the second planetary gear PG2 and the distance d2 between the second planetary axis X3 and the second planetary radial distance Rp2 of the second input axis X5 are the same. Therefore, in this embodiment, the movement trajectory T1 of the first input axis X4 and the second input axis X5, when viewed along the axial direction L, is a straight line passing through the planetary carrier axis X1.

[0050] Furthermore, as described above, in this embodiment, the distance d1 between the first planetary axis X2 and the first input axis X4 (first planetary radial distance Rp1) and the distance d2 between the second planetary axis X3 and the second input axis X5 (second planetary radial distance Rp2) are the same. Moreover, when viewed axially along axis L, the first input axis X4, the planetary carrier axis X1, and the second input axis X5 are arranged in a straight line. Therefore, in this embodiment, the movement trajectories of the first input axis X4 and the second input axis X5, accompanying the reciprocating motion of the first input component 3 and the second input component 5, are consistent when viewed axially along axis L.

[0051] exist Figure 2 In the example shown, when viewed along the axis L, the first input axis X4 is located on the opposite side of the planetary carrier axis X1 relative to the first planetary axis X2, and the second input axis X5 is located on the opposite side of the planetary carrier axis X1 relative to the second planetary axis X3. Furthermore, when viewed along the axis L, the first input axis X4, the first planetary axis X2, the planetary carrier axis X1, the second planetary axis X3, and the second input axis X5 are aligned in a straight line. At this point, based on the circular trajectory 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°.

[0052] exist Figure 3 In the example shown, the first planetary axis X2 and the second planetary axis X3 are from Figure 2 The state shown is rotated 45° clockwise around the planetary carrier axis X1. 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... Figure 2 The state shown is closer to the planetary carrier axis X1.

[0053] exist Figure 4 In the example shown, the first planetary axis X2 and the second planetary axis X3 are from Figure 3 The state shown is rotated 45° clockwise around the planetary carrier axis X1. That is, the phase of the first planetary axis X2 is 90°, and the phase of the second planetary axis X3 is 270°. At this time, the first input axis X4 and the second input axis X5 are located on the planetary carrier axis X1.

[0054] exist Figure 5 In the example shown, the first planetary axis X2 and the second planetary axis X3 are from Figure 4 The state shown is rotated 45° clockwise around the planetary carrier axis X1. That is, the phase of the first planetary axis X2 is 135°, and the phase of the second planetary axis X3 is 315°. At this time, the first input axis X4 and the second input axis X5 are...Figure 4 The state shown is further away from the planetary carrier axis X1.

[0055] exist Figure 6 In the example shown, the first planetary axis X2 and the second planetary axis X3 are from Figure 5 The shown configuration is rotated 45° clockwise around the planetary carrier axis X1. 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 point, viewed along axis L, the first input axis X4 is located on the opposite side of the planetary carrier axis X1 relative to the first planetary axis X2, and the second input axis X5 is located on the opposite side of the planetary carrier axis X1 relative to the second planetary axis X3. Furthermore, viewed along axis L, the first input axis X4, the first planetary axis X2, the planetary carrier axis X1, the second planetary axis X3, and the second input axis X5 are aligned in a straight line.

[0056] Furthermore, omitting the explanation of the process before the phase of the first planetary axis X2 becomes 0°, as described above, the first input component 3 and the second input component 5 reciprocate in such a way that the first input axis X4 and the second input axis X5 trace a straight trajectory T1.

[0057] Furthermore, as described above, when viewed axially along the axis L, the first crank assembly 2 is connected to the first planetary gear PG1, and the second crank assembly 4 is connected to the second planetary gear PG2, with the first input shaft X4 and the second input shaft X5 located on opposite sides of each other across the planetary carrier shaft X1. Here, in this embodiment, the trajectory T1 is drawn such that the first input shaft X4 and the second input shaft X5 pass through the planetary carrier shaft X1. Therefore, the phrase "when viewed axially along the axis L, the first input shaft X4 and the second input shaft X5 are located on opposite sides of each other across the planetary carrier shaft X1" in this application includes a configuration to draw the trajectory T1 in which at least one of the first input shaft X4 and the second input shaft X5 passes through the planetary carrier shaft X1.

[0058] like Figure 7 As shown, in this embodiment, the power conversion device 100 is mounted on the bicycle B. Therefore, in this embodiment, the power conversion device 100 converts the reciprocating motion of the first input component 3 and the second input component 5 caused by the operation of the bicycle B's rider into the rotational motion of the output component 6 and outputs it. Figure 7 In the example shown, the power conversion device 100 is configured such that trajectory T1 is tilted relative to the horizontal direction, and moves towards the rear of bicycle B ( Figure 7 (on the right side) and facing upwards.

[0059] In addition to the first pedal P1 and the second pedal P2 mentioned above, bicycle B also has a seat S, handlebars H, frame F, drive wheel W1, driven wheel W2, and transmission mechanism T.

[0060] The first pedal P1 and the second pedal P2 are components for the driver to step on. The seat S is a component for the driver to sit on. The handlebars H are a component for the driver to hold. The frame F is a component that supports the seat S, handlebars H, drive wheel W1, driven wheel W2, and power conversion device 100. The ring gear of the planetary gear mechanism 1 in the power conversion device 100 is fixed to the frame F via the ring gear fixing component RF.

[0061] The drive wheel W1 is configured to rotate in conjunction with the driver's operation. The driven wheel W2 is supported by the frame F and is capable of rotation. In this embodiment, the drive wheel W1 is the rear wheel, and the driven wheel W2 is the front wheel.

[0062] The transmission mechanism T is configured to transmit the rotation of the output component 6 of the power conversion device 100 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.

[0063] The first sprocket SP1 is mounted on the planetary carrier shaft X1. In this embodiment, the first sprocket SP1 is connected to the planetary carrier CR, which is a specific rotating component RT, in a manner that allows the first sprocket SP1 to rotate integrally (see reference). Figure 1 In this embodiment, the first sprocket SP1 functions as the output component 6.

[0064] 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. Figure 7 In the example shown, the second sprocket SP2 is formed with a smaller diameter than the first sprocket SP1.

[0065] The third sprocket SP3 and the second sprocket SP2 are mounted on the same shaft. The third sprocket SP3 is connected to the second sprocket SP2 in a manner that allows it to rotate as a single unit. Figure 7 In the example shown, the third sprocket SP3 is formed with a diameter larger than that of the second sprocket SP2.

[0066] The second chain CH2 is wound around the third sprocket SP3 and the fourth sprocket SP4. The fourth sprocket SP4 is mounted coaxially with the drive wheel W1. Figure 7 In the example shown, the fourth sprocket SP4 is formed with a smaller diameter than the third sprocket SP3.

[0067] 2. Second Implementation Method

[0068] The following is for referenceFigures 8-14 The power conversion device 100 of the second embodiment will be described. In this embodiment, the structures of the first crank component 2 and the second crank component 4 differ from those of the first embodiment described above. Hereinafter, the description will focus on the differences from the first embodiment. Furthermore, aspects not specifically described are the same as those in the first embodiment described above.

[0069] like Figure 8 As shown, in this embodiment, the radius r2 of the first planetary gear PG1 and the distance d1 between the first planetary axis X2 and the first planetary radial distance Rp1 between the first input axis X4 are different (r2 ≠ d1). Furthermore, the radius r4 of the second planetary gear PG2 and the distance d2 between the second planetary axis X3 and the second input axis X5 are different (r4 ≠ d2). Figure 8 In the example shown, the distance d1 between the first planetary axis X2 and the first input axis X4 is greater than the radius r2 of the first planetary gear PG1 (r2 < d1). Furthermore, the distance d2 between the second planetary axis X3 and the second input axis X5 is greater than the radius r4 of the second planetary gear PG2 (r4 < d2). In this embodiment, similar to the first embodiment described above, the distance d1 between the first planetary axis X2 and the first input axis X4, and the distance d2 between the second planetary axis X3 and the second input axis X5 are the same (d1 = d2).

[0070] Here, refer to Figures 9-13 The reciprocating motion of the first input component 3 and the second input component 5 in this embodiment will be described. Furthermore, in Figures 9-13 In the diagram, trajectory T1, represented by a single-dotted line, is the movement trajectory of the first input axis X4 and the second input axis X5, respectively, accompanying the reciprocating motion of the first input component 3 and the second input component 5. Similarly, trajectory T2, represented by a double-dotted line, is the movement trajectory of the first planetary axis X2 and the second planetary axis X3, respectively, accompanying the reciprocating motion of the first input component 3 and the second input component 5.

[0071] As described above, in this embodiment, the radius r2 of the first planetary gear PG1 and the distance d1 between the first planetary axis X2 and the first planetary radial distance Rp1 of the first input axis X4 are different. Similarly, the radius r4 of the second planetary gear PG2 and the distance d2 between the second planetary axis X3 and the second planetary radial distance Rp2 of the second input axis X5 are different. Therefore, in this embodiment, the movement trajectory T1 of the first input axis X4 and the second input axis X5, when viewed along the axial direction L, is an ellipse centered on the planetary carrier axis X1.

[0072] Furthermore, as described above, in this embodiment, the distance d1 between the first planetary axis X2 and the first input axis X4 (first planetary radial distance Rp1) and the distance d2 between the second planetary axis X3 and the second input axis X5 (second planetary radial distance Rp2) are the same. Moreover, when viewed axially along axis L, the first input axis X4, the planetary carrier axis X1, and the second input axis X5 are aligned in a straight line. Therefore, in this embodiment, the movement trajectories of the first input axis X4 and the second input axis X5, accompanying the reciprocating motion of the first input component 3 and the second input component 5, are consistent when viewed axially along axis L.

[0073] exist Figure 9 In the example shown, when viewed along the axis L, the first input axis X4 is located on the opposite side of the planetary carrier axis X1 relative to the first planetary axis X2, and the second input axis X5 is located on the opposite side of the planetary carrier axis X1 relative to the second planetary axis X3. Furthermore, when viewed along the axis L, the first input axis X4, the first planetary axis X2, the planetary carrier axis X1, the second planetary axis X3, and the second input axis X5 are aligned in a straight line. At this point, based on the circular trajectory 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°.

[0074] exist Figure 10 In the example shown, the first planetary axis X2 and the second planetary axis X3 are from Figure 9 The state shown is rotated 45° clockwise around the planetary carrier axis X1. 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 from... Figure 9 The state shown is rotated counterclockwise around the planetary carrier axis X1.

[0075] exist Figure 11 In the example shown, the first planetary axis X2 and the second planetary axis X3 are from Figure 10The shown configuration is rotated 45° clockwise around the planetary carrier axis X1. 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 point, viewed along axis L, the first input axis X4 and the second input axis X5 lie on a straight line passing through the first planetary axis X2, the planetary carrier axis X1, and the second planetary axis X3. In other words, viewed along axis L, with the first input axis X4 located between the planetary carrier axis X1 and the second planetary axis X3, and the second input axis X5 located between the planetary carrier axis X1 and the first planetary axis X2, the first planetary axis X2, the second input axis X5, the planetary carrier axis X1, the first input axis X4, and the second planetary axis X3 are aligned in a straight line.

[0076] exist Figure 12 In the example shown, the first planetary axis X2 and the second planetary axis X3 are from Figure 11 The state shown is rotated 45° clockwise around the planetary carrier axis X1. That is, the phase of the first planetary axis X2 is 135°, and the phase of the second planetary axis X3 is 315°. At this time, the first input axis X4 and the second input axis X5 are rotated from... Figure 11 The state shown is rotated counterclockwise around the planetary carrier axis X1.

[0077] exist Figure 13 In the example shown, the first planetary axis X2 and the second planetary axis X3 are from Figure 12 The shown configuration is rotated 45° clockwise around the planetary carrier axis X1. 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 point, viewed along axis L, the first input axis X4 is located on the opposite side of the planetary carrier axis X1 relative to the first planetary axis X2, and the second input axis X5 is located on the opposite side of the planetary carrier axis X1 relative to the second planetary axis X3. Furthermore, viewed along axis L, the first input axis X4, the first planetary axis X2, the planetary carrier axis X1, the second planetary axis X3, and the second input axis X5 are aligned in a straight line.

[0078] Furthermore, although the process before the phase of the first planetary axis X2 becomes 0° is omitted, as described above, the first input component 3 and the second input component 5 reciprocate in a manner that traces an elliptical trajectory T1 with the first input axis X4 and the second input axis X5.

[0079] like Figure 14As shown, in this embodiment, the structure of the bicycle B equipped with the power conversion device 100 differs from that of the first embodiment described above. Specifically, in this embodiment, the bicycle B also includes a generator G and a motor (not shown). Furthermore, the transmission mechanism T is configured to transmit the rotation of the output component 6 of the power conversion device 100 to the generator G.

[0080] In this embodiment, the transmission mechanism T replaces the second sprocket SP2, the third sprocket SP3, the fourth sprocket SP4, the first chain CH1, and the second chain CH2, and includes a fifth sprocket SP5 and a third chain CH3.

[0081] The fifth sprocket SP5 is connected to the rotor of the generator G in a rotating manner. The third chain CH3 is wound around the first sprocket SP1 and the fifth sprocket SP5. Figure 14 In the example shown, the fifth sprocket SP5 is formed with a smaller diameter than the first sprocket SP1.

[0082] The generator G generates electricity through driving force transmitted via the transmission mechanism T and stores it in an energy storage device (not shown). The motor receives power from the energy storage device to operate and drives the drive wheel W1.

[0083] 3. Third Implementation Method

[0084] The following is for reference Figure 15 The power conversion device 100 of the third embodiment will be described. In this embodiment, the structure of the planetary gear mechanism 1 differs from that of the first embodiment described above. Hereinafter, the description will focus on the differences from the first embodiment. Furthermore, aspects not specifically described are the same as those in the first embodiment described above.

[0085] like Figure 15 As shown, in this embodiment, the planetary gear mechanism 1 further includes a third planetary gear PG3 and a sun gear SG. Furthermore, in this embodiment, the planetary gear mechanism 1 does not include a second ring gear RG2.

[0086] The third planetary gear PG3 is disposed on the first planetary shaft X2 and at a different position from the first planetary gear PG1 in the axial direction L. The third planetary gear PG3 is integrally rotatably connected to 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. Moreover, the third planetary gear PG3 is integrally rotatably connected to the first planetary shaft PS1.

[0087] In this embodiment, the first planetary shaft PS1 is configured to pass through the first planetary gear PG1 and the third planetary gear PG3 along the axial direction L. Moreover, the first planetary shaft PS1 is supported by the planet carrier CR via a pair of first planetary bearings B1 respectively disposed on the first axial side L1 relative to the first planetary gear PG1 and on the second axial side L2 relative to the third planetary gear PG3, so that it can rotate.

[0088] The sun gear SG is mounted on the planet carrier shaft X1. The sun gear SG meshes with the second planetary gear PG2 and the third planetary gear PG3. In this embodiment, the sun gear SG is supported by the planet carrier CR and is rotatable via a sun gear bearing B6 located radially inside the sun gear SG.

[0089] In this embodiment, the radius r4 of the second planetary gear PG2 and the radius r5 of the third planetary gear PG3 are the same. That is, the diameters of the second planetary gear PG2 and the third planetary gear PG3 are the same. Furthermore, the radius r4 of the second planetary gear PG2 and the radius r5 of the third planetary gear PG3 are each smaller than the radius r2 of the first planetary gear PG1. That is, the diameters of the second planetary gear PG2 and the third planetary gear PG3 are each smaller than the diameter of the first planetary gear PG1.

[0090] In this embodiment, the ring gear RG is fixed to a first ring gear support RS1 and a second ring gear support RS2. The first ring gear support RS1 is disposed on a first axial side L1 relative to the ring gear RG. The first ring gear support RS1 supports the planet carrier CR from the outer side of the radial direction R via a first ring gear bearing B4, enabling it to rotate. The second ring gear support RS2 is disposed on a second axial side L2 relative to the ring gear RG. The second ring gear support RS2 supports the planet carrier CR from the outer side of the radial direction R via a second ring gear bearing B5, enabling it to rotate.

[0091] In this embodiment, the first planetary bearing B1, the second planetary bearing B2, and the first ring gear bearing B4 on the first axial side L1 are configured such that their axial L configuration areas overlap. Furthermore, the first planetary bearing B1, the second planetary bearing B2, and the second ring gear bearing B5 on the second axial side L2 are configured such that their axial L configuration areas overlap. Therefore, the axial L dimension of the planetary gear mechanism 1 can be minimized, and the axial L dimension of the power conversion device 100 can be miniaturized.

[0092] 4. Other implementation methods

[0093] (1) In the above embodiment, the structure in which the first input component 3 is fixed to the shaft component of the first crank component 2 and the second input component 5 is fixed to the shaft component of the second crank component 4 is described as an example. However, it is not limited to such a structure. For example, it is also possible to omit the shaft component as the first input component 3 and the shaft component as the second input component 5, and instead set a structure in which a part of the first crank component 2 functions as the first input component 3 and a part of the second crank component 4 functions as the second input component 5.

[0094] (2) In the above embodiment, the structure in which the first planetary axis X2 and the second planetary axis X3 are configured with a phase difference of 180° is described as an example. However, it is not limited to such a structure, and the first planetary axis X2 and the second planetary axis X3 may also be configured with a phase difference different from 180°.

[0095] (3) In the above embodiment, the structure of the trajectory T1 is described as follows: when viewed along the axis L, there exists a phase in which the first input axis X4, the first planetary axis X2, the planet carrier axis X1, the second planetary axis X3, and the second input axis X5 are arranged in a straight line. However, it is not limited to this structure. It is also possible to set the structure in the trajectory T1 such that when viewed along the axis L, there is no phase in which the first input axis X4, the first planetary axis X2, the planet carrier axis X1, the second planetary axis X3, and the second input axis X5 are arranged in a straight line.

[0096] (4) In the above embodiment, as an example, a structure was described in which the directions along the straight line passing through the first planetary axis X2 and the first input axis X4 (the extension direction of the first crank component 2) and the direction along the straight line passing through the second planetary axis X3 and the second input axis X5 (the extension direction of the second crank component 4) are arranged to be parallel to each other. However, the structure is not limited to this, and the extension directions of the first crank component 2 and the second crank component 4 may also be arranged to intersect each other.

[0097] (5) In the above embodiment, the structure in which the first gear ring RG1 and the second gear ring RG2 have the same diameter was described as an example. However, it is not limited to such a structure, and the first gear ring RG1 and the second gear ring RG2 may also have different diameters.

[0098] (6) Furthermore, the structures disclosed in the above embodiments can be combined with structures disclosed in other embodiments, provided that they do not create contradictions. Regarding other structures, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications can be appropriately made without departing from the spirit of the invention.

[0099] 5. Summary of this implementation method

[0100] The following is a summary description of the power conversion device 100 described above.

[0101] The power conversion device 100 includes:

[0102] The planetary gear mechanism 1 includes a fixed internal gear, i.e., a gear ring RG, a first planetary gear PG1 that meshes with the gear ring RG, a second planetary gear PG2 disposed on a different shaft from the first planetary gear PG1, and a planet carrier CR that supports the first planetary gear PG1 and the second planetary gear PG2 so that they can rotate.

[0103] The first crank component 2 is configured to extend along the first planetary radial direction Rp1, which is orthogonal to the rotation axis of the first planetary gear PG1, i.e., the first planetary axis X2, and is connected to the first planetary gear PG1 in an integral rotational manner.

[0104] The first input component 3 is supported by the first crank component 2 and is disposed on the first input shaft X4 which is separated from the first planetary axis X2 along the first planetary radial direction Rp1.

[0105] The second crank component 4 is configured to extend along the second planetary radial direction Rp2, which is orthogonal to the rotation axis of the second planetary gear PG2, i.e., the second planetary axis X3, and is connected to the second planetary gear PG2 in an integral rotational manner.

[0106] The second input component 5, supported by the second crank component 4, is disposed on a second input shaft X5 that is separated from the second planetary axis X3 along the second planetary radial direction Rp2; and

[0107] Output component 6 is connected to a specific rotating component RT, which, in addition to the aforementioned first planetary gear PG1 and second planetary gear PG2, rotates in conjunction with the aforementioned planetary carrier CR.

[0108] The radius r1 of the aforementioned gear ring RG is twice the radius r2 of the aforementioned first planetary gear PG1.

[0109] Let the axis L be the direction along the rotation axis of the planet carrier CR, that is, the axis X1 of the planet carrier.

[0110] The first planetary gear PG1 and the second planetary gear PG2 are configured to revolve around the planet carrier axis X1 at the same speed and in the same direction.

[0111] Viewed along the aforementioned axis L, the first planetary axis X2 and the second planetary axis X3 are positioned opposite each other, separated by the planet carrier axis X1, and are located at the same distance from the planet carrier axis X1.

[0112] Viewed along the aforementioned axial direction, with the first input shaft X4 and the second input shaft X5 located on opposite sides of each other across the planetary carrier shaft X1, the first crank assembly 2 is connected to the first planetary gear PG1, and the second crank assembly 4 is connected to the second planetary gear PG2.

[0113] According to this structure, the respective movement trajectories T1 of the first input shaft X4 and the second input shaft X5, which accompany the reciprocating motion of the first input component 3 and the second input component 5, can be set as a straight line or an ellipse with reference to the planetary carrier axis X1. Furthermore, the phase difference between the first input shaft X4 and the second input shaft X5 can be set to 180° or a value close to that. Therefore, a power conversion device 100 can be realized that easily transmits driving force to the first input component 3 disposed on the first input shaft X4 and the second input component 5 disposed on the second input shaft X5.

[0114] Here, preferably, the planetary gear mechanism 1, in addition to serving as the first gear ring RG1 of the aforementioned gear ring RG, also includes a fixed internal gear, namely the second gear ring RG2.

[0115] The aforementioned second planetary gear PG2 meshes with the aforementioned second ring gear RG2.

[0116] The radius r3 of the second gear ring RG2 is twice the radius r4 of the second planetary gear PG2.

[0117] Based on this structure, it is easy to make the transmission mechanism for the driving force from the first crank component 2 to the planetary carrier CR and the transmission mechanism for the driving force from the second crank component 4 to the planetary carrier CR similar. Therefore, the power conversion device 100 can be made into a simple structure.

[0118] Furthermore, according to this structure, when the radius r1 of the first gear ring RG1 is the same as the radius r3 of the second gear ring RG2, the components can be shared in the first gear ring RG1 and the first planetary gear PG1, as well as the second gear ring RG2 and the second planetary gear PG2, thus easily reducing the number of different types of components.

[0119] Furthermore, the planetary gear mechanism 1 preferably includes: a third planetary gear PG3 disposed on the first planetary axis X2 and at a different position from the first planetary gear PG1 in the axial direction L, and connected to the first planetary gear PG1 in a manner that allows it to rotate integrally; and a sun gear SG disposed on the planetary carrier axis X1.

[0120] The radius r4 of the second planetary gear PG2 and the radius r5 of the third planetary gear PG3 are the same.

[0121] The aforementioned second planetary gear PG2 and the aforementioned third planetary gear PG3 mesh with the aforementioned sun gear SG.

[0122] According to this structure, it is possible to properly realize a structure in which the first planetary gear PG1 and the second planetary gear PG2 rotate at the same speed in the same direction.

[0123] Furthermore, it is preferable that the distance d1 between the first planetary axis X2 and the first input axis X4, and the distance d2 between the second planetary axis X3 and the second input axis X5, are the same.

[0124] The radius r2 of the first planetary gear PG1 and the distance d1 between the first planetary axis X2 and the first input axis X4 of the first planetary radial direction Rp1 are different.

[0125] According to this structure, the respective movement trajectories T1 of the first input axis X4 and the second input axis X5, which accompany the reciprocating motion of the first input component 3 and the second input component 5, can be set as an ellipse centered on the planetary carrier axis X1.

[0126] Furthermore, according to this structure, when the distance d1 between the first planetary axis X2 and the first input axis X4 is larger than the radius r2 of the first planetary gear PG1, it is easier to ensure a larger stroke for the reciprocating motion of the first input component 3 and the second input component 5. Therefore, it is easy to miniaturize the planetary gear mechanism 1.

[0127] Furthermore, according to this structure, when the distance d1 between the first planetary axis X2 and the first input axis X4 is less than the radius r2 of the first planetary gear PG1, the rotation direction of the first input axis X4 and the second input axis X5, which are accompanied by the reciprocating motion of the first input component 3 and the second input component 5, can be such that the direction of their respective rotation is elliptical and the direction of rotation of the planet carrier CR is the same.

[0128] Industrial applications

[0129] The technology of this invention can be applied to a power conversion device that converts reciprocating motion into rotational motion.

[0130] Explanation of reference numerals in the attached figures

[0131] 100: Power conversion device; 1: Planetary gear mechanism; RG: Ring gear; RG1: First ring gear; RG2: Second ring gear; PG1: First planetary gear; PG2: Second planetary gear; PG3: Third planetary gear; CR: Planetary carrier; SG: Sun gear; 2: First crank assembly; 3: First input assembly; 4: Second crank assembly; 5: Second input assembly; 6: Output assembly; RT: Specific rotating assembly; X1: Planetary carrier shaft; X2: First planetary shaft; X3: Second planetary shaft; X4: First input shaft; X5: Second input shaft; L: Axial direction; Rp1: First planetary radial direction; Rp2: Second planetary radial direction.

Claims

1. A power conversion device, comprising: A planetary gear mechanism comprising a fixed internal gear, i.e., a gear ring, a first planetary gear meshing with the gear ring, a second planetary gear disposed on a shaft different from the first planetary gear, and a planet carrier supporting the first planetary gear and the second planetary gear so as to be rotatable. The first crank component is configured to extend radially along the first planetary gear, which is orthogonal to the rotation axis of the first planetary gear, i.e., the axis of the first planet, and is connected to the first planetary gear in an integral rotatable manner. The first input component is supported by the first crank component and is disposed on a first input shaft that is separated from the first planetary axis along the radial direction of the first planet. The second crank assembly is configured to extend radially along the second planetary gear, which is orthogonal to the rotation axis of the second planetary gear, i.e., the axis of the second planetary gear, and is connected to the second planetary gear in a manner that allows it to rotate integrally. The second input component, supported by the second crank component, is disposed on a second input shaft that is radially separated from the second planetary axis; and The output component is connected to a specific rotating component, which, in addition to the aforementioned first and second planetary gears, rotates in conjunction with the planet carrier. The radius of the aforementioned gear ring is twice the radius of the aforementioned first planetary gear. Let the direction along the rotation axis of the planet carrier, that is, the axis of the planet carrier, be defined as the axial direction. The first planetary gear and the second planetary gear are configured to revolve around the planet carrier axis at the same speed and in the same direction. Viewed along the aforementioned axis, the first planetary axis and the second planetary axis are positioned opposite each other, separated by the planet carrier axis, and are located at the same distance from the planet carrier axis. Viewed along the aforementioned axial direction, the first crank assembly is connected to the first planetary gear and the second crank assembly is connected to the second planetary gear in such a manner that the first input shaft and the second input shaft are located on opposite sides of each other across the planetary carrier shaft.

2. The power conversion device according to claim 1, wherein, In addition to serving as the first gear ring, the aforementioned planetary gear mechanism also includes a fixed internal gear, namely the second gear ring. The aforementioned second planetary gear meshes with the aforementioned second ring gear. The radius of the second gear ring is twice the radius of the second planetary gear.

3. The power conversion device according to claim 1, wherein, The aforementioned planetary gear mechanism further comprises: a third planetary gear disposed on the first planetary axis and at a different position from the first planetary gear in the axial direction, and connected to the first planetary gear in a manner that allows it to rotate integrally; and a sun gear disposed on the planet carrier axis. The radius of the second planetary gear is the same as the radius of the third planetary gear. The aforementioned second planetary gear and the aforementioned third planetary gear mesh with the aforementioned sun gear.

4. The power conversion device according to any one of claims 1 to 3, wherein, The radial distance between the first planet's axis and the first input axis, and the radial distance between the second planet's axis and the second input axis, are the same. The radius of the first planetary gear and the radial distance between the first planetary axis and the first input axis are different.

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