Drive device

Abstract

To provide a drive device which absorbs an inclination of a planetary carrier and a shaft misalignment with a simple configuration.SOLUTION: A drive device includes: a body 110; a main drive part 120 provided on the body 110; and an auxiliary drive part 130. The main drive part 120 includes a main shaft 121 and a bevel gear 122 that rotates integrally with the main shaft 121 at least in one direction. The auxiliary drive part 130 is connected to a drive source as a speed reduction mechanism of the drive force, and includes: a sun gear 141 in which an auxiliary drive force is input; a planetary gear 142b; an internal gear 144 provided on the body 110; and a planetary carrier 143 rotationally supporting the planetary gear 142b by a pin 146. A bevel pinion boss 151 and a bevel pinion gear 152 connected to the bevel pinion boss 151 are provided as a transmission member of the drive force whose speed has been reduced by the speed reduction mechanism. The bevel gear 122 and the bevel pinion gear 152 are connected, and the planetary gear 142b is configured of a scissors gear.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a drive device having a main body, a drive unit provided in the main body, and a drive auxiliary unit. [Background technology]

[0002] BACKGROUND ART Conventionally, a drive device having a main body, a main drive unit provided in the main body, and an auxiliary drive unit is known, for example, from Patent Document 1 and the like. An electrically assisted vehicle 80 provided with the drive device described in Patent Document 1 has a main body (case main body 93), a main shaft (crankshaft 13) and a rotating member (output gear 98a) that rotates integrally with the main shaft (crankshaft 13) as a main drive unit provided in the main body (case main body 93), an auxiliary drive shaft (rotating shaft 82a) as a drive auxiliary unit, a speed reduction mechanism (planetary roller type speed reduction mechanism 91) connected to the auxiliary drive shaft (rotating shaft 82a), and a transmission member (output gear member 118) that transmits the output of the speed reduction mechanism (planetary roller type speed reduction mechanism 91) to the main shaft (crankshaft 13), and the speed reduction mechanism (planetary roller type speed reduction mechanism 91) is a planetary gear (planetary roller type speed reduction mechanism 91). The planetary gear (planetary roller 111) has a sun gear (rotating shaft 82a) to which a driving assist force is input from a driving source (electric motor 82), a planet carrier (carrier 117) that rotatably supports the planetary gear (planetary roller 111), and an internal gear (outer ring 110) provided on the main body, and the reduction mechanism (planetary roller reduction mechanism 91) and the transmission member (output gear member 118) are connected by a power transmission member (one-way clutch 120), and the transmission member (output gear member 118) is connected to the rotating member (output gear 98a) so that the driving assist force from the driving source (electric motor 82) is transmitted to the main shaft (crankshaft 13). This makes it possible to output a resultant force of the driving force input to the main shaft (crankshaft 13) and the driving assist force from the driving source (electric motor 82). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 10-016874 Summary of the Invention [Problem to be solved by the invention]

[0004] In the known driving device disclosed in Patent Document 1 and the like, the only support member for the carrier 117 connected to the planetary roller type reduction mechanism 91 is the one-way clutch 120. Therefore, for example, when the drive unit is mounted on an electric assisted bicycle 80 and held horizontally, the structure of the one-way clutch 120 creates small gaps between the components of the one-way clutch 120, which could cause the carrier 117 to tilt from its original mounting position or cause the axis of the rotating shaft to become misaligned. Furthermore, if the electric motor 82 rotates with the carrier 117 tilted or with its axis misaligned, the meshing between the rotating shaft 82a, planetary roller 111, and outer ring 110 will become less smooth, which could result in a decrease in the efficiency of power transmission from the electric motor 82, the generation of periodic abnormal noises as the electric motor 82 rotates, and abnormal wear on the tooth surfaces. Furthermore, there is a risk that the one-way clutch 120 may not mesh properly or may wear abnormally due to tilting or misalignment of the carrier 117. The present invention aims to solve these problems and provide a drive unit that has a simple configuration, absorbs tilt and axial misalignment of the planetary carrier, and has excellent quietness and running stability. [Means for solving the problem]

[0005] The drive device of the present invention is a drive device having a main body, a main drive unit provided in the main body, and a drive auxiliary unit that assists in driving the main drive unit, wherein the main drive unit has a main shaft journaled in the main body and a rotating member that rotates integrally with the main shaft in at least one direction, the drive auxiliary unit has an auxiliary drive shaft, a reduction mechanism connected to the auxiliary drive shaft, and a transmission member that transmits the output of the reduction mechanism to the main shaft, the reduction mechanism has a planetary gear, a sun gear to which a drive auxiliary force is input from a drive source, a planet carrier that rotatably supports the planetary gear, and an internal gear provided in the main body, the reduction mechanism and the transmission member are connected by a power transmission member, and the transmission member is connected to the rotating member so that the drive auxiliary force from the drive source is transmitted to the main shaft, and the planetary gear is configured as a scissors gear, thereby solving the above-mentioned problem. [Effects of the Invention]

[0006] According to the inventions of claims 1 and 7, there is provided a drive device having a main body, a main drive unit provided in the main body, and a drive auxiliary unit that assists the drive of the main drive unit, wherein the main drive unit has a main shaft journaled in the main body and a rotating member that rotates integrally with the main shaft in at least one direction, the drive auxiliary unit has an auxiliary drive shaft, a reduction mechanism connected to the auxiliary drive shaft, and a transmission member that transmits the output of the reduction mechanism to the main shaft, and the reduction mechanism includes a planetary gear, a sun gear to which a drive auxiliary force is input from a drive source, a planet carrier that rotatably supports the planetary gear, and an internal gear provided in the main body. The planetary carrier and the transmission member are connected by a power transmission member, and the transmission member is connected to the rotating member so that the auxiliary driving force from the driving source is transmitted to the main shaft. The planetary gear is configured as a scissors gear, so that when the auxiliary driving force is input from the driving source and the planetary carrier and the transmission member rotate together, even if the power transmission member and the planetary carrier are connected at an angle, the scissors gear can absorb tooth gap fluctuations during meshing of the sun gear and internal gear that mesh with the planetary gear, which are caused by the angle of the rotation axis of the planetary carrier relative to the rotation axis of the transmission member. This allows for smoother engagement between the reduction mechanism and each part of the transmission member, suppressing abnormal noise and reducing wear on rotating parts.

[0007] According to the configuration described in claim 2, the rotating member has a bevel gear, the transmission member has a bevel pinion gear, the bevel pinion gear is connected to the bevel gear, the planetary carrier and the transmission member are connected by the power transmission member, the scissors gear has a reference planetary gear, an adjustment planetary gear, and a biasing member, and the reference planetary gear and the adjustment planetary gear are biased in opposite directions to each other in the circumferential direction by the biasing member, thereby eliminating backlash between the reference planetary gear and the adjustment planetary gear, which are respectively connected to the sun gear, and the power input from the drive source can be transmitted to the main shaft reliably and smoothly, and the tilt of the planetary carrier can be more effectively absorbed.

[0008] According to the configuration described in claim 3, the biasing member is configured as a coil spring, so that the reference planetary gear and the adjustment planetary gear can be reliably biased in opposite directions in the circumferential direction with a simple configuration. Furthermore, since the tilt of the planetary carrier can be absorbed without increasing the size of the main body, the weight of the main body can be reduced and the storage space can be reduced.

[0009] According to the configuration described in claim 4, the biasing member is configured as an arc spring, so that the reference planetary gear and the adjustment planetary gear can be reliably biased in opposite directions to each other in the circumferential direction with a simple configuration. Furthermore, since the tilt of the planetary carrier can be absorbed without increasing the size of the main body, the weight of the main body can be reduced and the storage space can be reduced.

[0010] According to the configuration described in claim 5, the planetary carrier has a boss portion formed on its side, and the boss portion functions as a support portion for the power transmission member, so that the transmission member can be provided inside the main body portion, thereby shortening the overall length of the transmission member, and by bringing the outer diameter of the bearing as close as possible to the inner diameter of the drive auxiliary portion side of the main body portion, the transmission member can be securely held, thereby further minimizing axial misalignment of the transmission member.

[0011] According to the configuration of claim 6, the power transmission member is configured as a cam clutch, so that the drag resistance of the electric motor can be suppressed when the electric motor does not input a drive assist force.

[0012] According to the configuration of claim 8, the main shaft is a crankshaft to which a pedal depression force is input, so that the vehicle can be made to assist the pedal depression force of the driver. [Brief explanation of the drawings]

[0013] [Figure 1] 1 is a perspective view of a cross section of a drive unit 100 according to a first embodiment of the present invention, taken along a direction parallel to a main shaft. [Figure 2] 1 is a perspective view of a cross section perpendicular to a main shaft of a drive device 100 according to a first embodiment of the present invention. [Figure 3] 1 is a perspective view of a driving device 100 according to a first embodiment of the present invention, seen from a sprocket side. [Figure 4] 1 is a perspective view of a drive device 100 according to a first embodiment of the present invention, seen from the drive auxiliary unit side. [Figure 5] 3 is a partially enlarged view of a drive auxiliary portion in a cross section parallel to the main shaft of the drive unit 100 according to the first embodiment of the present invention. FIG. [Figure 6] FIG. 2 is a front view of the reduction mechanism 140 of the drive device 100 according to the first embodiment of the present invention. [Figure 7] 1 is a perspective view of a reduction mechanism 140 of a drive device 100 according to a first embodiment of the present invention. [Figure 8]1 is a perspective view of a cross section of a speed reduction mechanism 140 of a drive unit 100 according to a first embodiment of the present invention, taken along a direction parallel to an auxiliary drive shaft. [Figure 9] FIG. 3 is an enlarged view of a coil spring 147 of the reduction mechanism 140 of the drive unit 100 according to the first embodiment of the present invention. [Figure 10] FIG. 2 is a perspective view of a reference planetary gear 145-1 of the reduction mechanism 140 of the drive unit 100 according to the first embodiment of the present invention. [Figure 11] FIG. 2 is a perspective view of an adjustment planetary gear 145-2 of the reduction mechanism 140 of the drive unit 100 according to the first embodiment of the present invention. [Figure 12] FIG. 10 is a front view of a reduction mechanism 140b of a drive device 100b according to a second embodiment of the present invention. [Figure 13] FIG. 10 is a perspective view of a reduction mechanism 140b of a drive device 100b according to a second embodiment of the present invention. [Figure 14] FIG. 10 is a perspective view of a cross section of a speed reduction mechanism 140b of a drive unit 100b according to a second embodiment of the present invention, taken along a direction parallel to an auxiliary drive shaft. [Figure 15] FIG. 10 is an enlarged view of a circular arc spring 148 of a speed reduction mechanism 140b of a drive device 100b according to a second embodiment of the present invention. [Figure 16] FIG. 10 is a perspective view of a cross-sectional view of a reduction mechanism 140b of a drive device 100b according to a second embodiment of the present invention. [Figure 17] FIG. 10 is a perspective view of a reference planetary gear 145-1b of a reduction mechanism 140b of a drive device 100b according to a second embodiment of the present invention. [Figure 18] FIG. 10 is a perspective view of an adjustment planetary gear 145-2b of a reduction mechanism 140b of a drive device 100b according to a second embodiment of the present invention. DETAILED DESCRIPTION OF THE INVENTION

[0014] A driving device 100 according to a first embodiment of the present invention will be described below with reference to the drawings. As shown in FIGS. 1 to 5, the drive device 100 according to the first embodiment of the present invention has a main body 110, a main drive unit 120 provided in the main body 110, and an auxiliary drive unit 130. 1 to 5, the drive source and the gear teeth are not shown, and the speed reduction mechanism 140 in FIGS. 1 to 5 has the configuration shown in FIGS.

[0015] The main drive unit 120 has a main shaft 121 rotatably held by a bearing 126 press-fitted into the main body 110, and a bevel gear 122 which is a rotating member that rotates integrally with the main shaft 121 and is rotatably held by a bearing 125 press-fitted into the main body 110. The main shaft 121 has a through hole in the longitudinal direction, and internal threads are provided on the inner surfaces of both ends of the through hole. Both ends of the main shaft 121 are shaped like square pillars, and cranks can be attached to both ends.

[0016] The bevel gear 122 has a through hole provided in the direction of the central axis of rotation through which the main shaft 121 is inserted, and is connected by a one-way clutch 124 so that the bevel gear 122 can rotate integrally with the main shaft 121 in at least one direction, and when the main shaft 121 rotates in the direction opposite to the drive direction, the bevel gear 122 can rotate freely. A sprocket 123 is attached to one end of the bevel gear 122 so as to be rotatable integrally with the bevel gear 122. When the main shaft 121 rotates, the bevel gear 122 rotates via the one-way clutch 124, and the sprocket 123 also rotates.

[0017] On the other hand, when the main shaft 121 rotates in the direction opposite to the driving direction, the one-way clutch 124 causes the main shaft 121 to spin freely, and the bevel gear 122 does not rotate integrally with the main shaft 121. Therefore, the driving force is not transmitted to the sprocket 123, and the sprocket 123 does not rotate.

[0018] The drive auxiliary unit 130 has an auxiliary drive shaft (not shown) connected to a drive source, a reduction mechanism 140 connected to the auxiliary drive shaft, and a transmission member 150 that transmits the output of the reduction mechanism 140 to the main shaft.

[0019] The reduction mechanism 140 has a sun gear 141 to which the drive auxiliary force of the auxiliary drive shaft is input, a planetary gear 142 to which the drive auxiliary force is transmitted from the sun gear 141, an internal gear 144 provided in the main body 110 and rotatably holding the planetary gear 142, and a planetary carrier 143 that rotatably supports the planetary gear 142 by a pin 146.

[0020] The sun gear 141 has a through hole to which a drive source can be connected, and when the drive source rotates and a drive assist force is input, the sun gear 141 can rotate integrally with the drive source at the same rotation speed.

[0021] The planetary gear 142 is made up of a scissors gear, and in this embodiment, as shown in FIGS. 6 to 11, has a reference planetary gear 145-1, an adjustment planetary gear 145-2, and a coil spring 147 as a biasing member. The reference planetary gear 145-1 and the adjustment planetary gear 145-2 each have a through hole at the center, and a pin 146 is inserted through the through hole, so that the reference planetary gear 145-1 and the adjustment planetary gear 145-2 are held coaxially and rotatably. The reference planetary gear 145-1 also has a boss portion formed on the outer peripheral surface side of the through hole, and the through hole of the adjustment planetary gear 145-2 is inserted into the boss portion, thereby rotatably holding the adjustment planetary gear 145-2.

[0022] The coil spring 147 has a coil spring held portion 147-1 and a coil spring held portion 147-2 at both ends, and in order to hold the coil spring 147, the reference planetary gear 145-1 has a coil spring holding portion 149-1 and the adjustment planetary gear 145-2 has a coil spring holding portion 149-2, with the coil spring held portion 147-1 being held by the coil spring holding portion 149-1 and the coil spring held portion 147-2 being held by the coil spring holding portion 149-2. As a result, when the reference planetary gear 145-1 and the adjustment planetary gear 145-2 are not meshed with any gears, the coil spring 147 assumes its natural length, and the teeth of the reference planetary gear 145-1 and the adjustment planetary gear 145-2 are maintained out of phase with each other.

[0023] On the other hand, when the reference planetary gear 145-1 and the adjustment planetary gear 145-2 are both meshed with gears, the coil spring 147 expands, thereby biasing the reference planetary gear 145-1 and the adjustment planetary gear 145-2 in opposite directions in the circumferential direction. The planetary gear 142 is meshed with the sun gear 141, and when the sun gear 141 rotates, the planetary gear 142 also rotates integrally, making it possible to transmit a driving assist force from the driving source.

[0024] The internal gear 144 is provided inside the main body 110 and is configured to mesh with the planetary gear 142 . Furthermore, since the internal gear 144 is fixed inside the main body 110, it does not rotate by itself, and when the planetary gear 142 rotates, the planetary gear 142 performs planetary motion, rotating around the sun gear 141 while rotating around the pin 146.

[0025] At this time, the reference planetary gear 145-1 and the adjustment planetary gear 145-2 are biased in opposite directions in the circumferential direction by the coil spring 147, so that one of the reference planetary gear 145-1 and the adjustment planetary gear 145-2 is in contact with the sun gear 141 or the internal gear 144. This eliminates backlash in the meshing between the planetary gear 142 and the sun gear 141 and internal gear 144, and smooths the meshing state, thereby suppressing the generation of periodic sounds and abnormal noises associated with the planetary motion of the planetary gear 142 and reducing tooth surface wear.

[0026] A transmission member 150 that transmits the output of the reduction mechanism 140 to the main shaft 121 has a bevel pinion boss 151 and a bevel pinion gear 152 connected to the bevel pinion boss 151 . The planetary carrier 143 of the reduction mechanism 140 and the bevel pinion boss 151 of the transmission member 150 are connected by a cam clutch 153, which is a power transmission member.

[0027] The cam clutch 153 can reduce transmission loss of the drive assist force input from the drive source due to its responsiveness, and can also securely hold the boss portion of the planet carrier 143 with the cam. In this embodiment, the power transmission member is the cam clutch 153, but a one-way clutch of another structure may also be used.

[0028] The planetary carrier 143 is cylindrical with a through hole in the center and has a boss portion formed on the side. A cam clutch 153 is inserted into the outer peripheral surface of the boss portion, so that the planetary carrier 143 is rotatably held inside the main body portion 110. The planetary carrier 143 supports the planetary gear 142 via a pin 146, so that when the planetary gear 142 performs planetary motion, the planetary carrier 143 itself can also perform rotational motion.

[0029] At this time, even if the planetary carrier 143 is held with an inclination or axial misalignment relative to the cam clutch 153, backlash in the meshing between the planetary gear 142 and the sun gear 141 and internal gear 144 is eliminated, and fluctuations in the tooth gaps when the sun gear 141 and internal gear 144 mesh with the planetary gear 142, which are caused by the inclination of the rotation axis of the planetary carrier 143, mesh are also absorbed. This smooths out the uneven meshing state caused by the inclination or axial misalignment of the planetary carrier 143, suppresses the generation of periodic sounds and abnormal noises associated with the planetary motion of the planetary gear 142, reduces tooth surface wear, and also ensures transmission efficiency.

[0030] The drive assisting portion 130 also has a bevel pinion boss 151 and a bevel pinion gear 152 connected to the bevel pinion boss 151 as a transmission member for transmitting the drive force reduced by the reduction mechanism.

[0031] The bevel pinion boss 151 has a through hole and a recess, and the recess holds the cam clutch 153 inserted into the boss portion provided on the planetary carrier 143 from the outer peripheral surface side. In addition, bevel pinion boss 151 is securely held without tilt or misalignment by two bearings 154 and 155 press-fitted inside main body 110, and can rotate coaxially with planet carrier 143 held by bearing 145.

[0032] The bevel pinion gear 152 has a through hole and is connected to the through hole provided in the bevel pinion boss 151, so that the bevel pinion gear 152 is held so as to be rotatable integrally with the bevel pinion boss 151. Furthermore, the bevel pinion gear 152 is connected to the bevel gear 122 so as to be able to transmit power.

[0033] Next, the operation of the driving device 100 according to the first embodiment of the present invention during driving will be described with reference to FIG.

[0034] First, a case will be described in which power is input to the main shaft 121 of the main drive unit 120 in the drive direction, but power is not input to the auxiliary drive unit 130 from the drive source. The main shaft 121 and the bevel gear 122 are connected by the one-way clutch 124 so that they can rotate together in at least one direction. Therefore, when power is input in the drive direction, the bevel gear 122 rotates together with the main shaft 121, and the sprocket 123 connected to the bevel gear 122 also rotates together. Then, power is transmitted from the bevel gear 122 to the bevel pinion gear 152 connected to the bevel gear 122, so that the bevel pinion gear 152 also rotates.

[0035] Here, since the bevel pinion gear 152 and the bevel pinion boss 151 are connected, the bevel pinion boss 151 rotates integrally with the bevel pinion gear 152 as the bevel pinion gear 152 rotates. However, since the bevel pinion boss 151 and the planetary carrier 143 are connected by the cam clutch 153, even if the bevel pinion boss 151 rotates, the cam clutch 153 rotates freely and no power is transmitted to the planetary carrier 143. As a result, when no power is being input from the drive source, the cam clutch 153 rotates freely, and the planetary carrier 143, planetary gear 146, sun gear 141, and drive source do not rotate, so there is no loss of power input to the main shaft 121.

[0036] Next, a case where power is input to the main shaft 121 of the main drive unit 120 in the drive direction and power is input to the auxiliary drive unit 130 from the drive source will be described. When power is input to the main shaft 121 in the drive direction, the power is transmitted in the order of one-way clutch 124, bevel gear 122, and bevel pinion gear 152, and bevel pinion boss 151 connected to bevel pinion gear 152 also rotates integrally. Here, since power is input from the drive source to the sun gear 141, the planet gear 142, which is connected to the sun gear 141 and rotatably held by the internal gear 144, performs planetary motion. Then, the planet carrier 143 connected to the planet gear 142 by the pin 146 also rotates.

[0037] Here, when the rotational speed of the planetary carrier 143 is slower than the rotational speed of the bevel pinion boss 151, the bevel pinion boss 151 and the planetary carrier 143 are connected by the cam clutch 153, so the power transmitted from the drive source to the planetary carrier 143 is not transmitted to the bevel pinion boss 151, and the drive assist force input from the drive source is not transmitted to the main shaft 121. On the other hand, when the rotational speed of the planetary carrier 143 is faster than the rotational speed of the bevel pinion boss 151, the bevel pinion boss 151 and the planetary carrier 143 are connected by the cam clutch 153, so that the planetary carrier 143 increases the rotational speed of the bevel pinion boss 151, and the power transmitted from the drive source is transmitted to the bevel pinion boss 151, assisting the rotational motion of the main shaft 121.

[0038] That is, when the rotational speed of the planetary carrier 143 exceeds the rotational speed of the bevel pinion boss 151, the power input from the drive source is transmitted to the bevel pinion boss 151, thereby assisting the rotational motion of the main shaft 121.

[0039] Next, a driving device 100b according to a second embodiment of the present invention will be described with reference to the drawings. As shown in FIGS. 12 to 14, a driving device 100b according to a second embodiment of the present invention differs from the driving device 100 according to the first embodiment in that the speed reducing mechanism 140 is replaced with a speed reducing mechanism 140b. The speed reduction mechanism 140b differs from the speed reduction mechanism 140 in that only the planetary gear 142 is replaced with a planetary gear 142b.

[0040] As shown in FIGS. 12 to 18, the planetary gear 142b has a reference planetary gear 145-1b, an adjustment planetary gear 145-2b, and an arc spring 148 as a biasing member. The reference planetary gear 145-1b and the adjustment planetary gear 145-2b each have a through hole at the center, and a pin 146 is inserted through the through hole, so that they are held rotatably on the same axis. The reference planetary gear 145-1b also has a boss portion formed on the outer peripheral surface side of the through hole, and the through hole of the adjustment planetary gear 145-2b is inserted into the boss portion, thereby rotatably holding the adjustment planetary gear 145-2b.

[0041] The arc spring 148 has an arc spring held portion 148-1 and an arc spring held portion 148-2 at both ends, and in order to hold the arc spring 148, the reference planetary gear 145-1b has an arc spring holding portion 149-1b and the adjustment planetary gear 145-2b has an arc spring holding portion 149-2b, with the arc spring held portion 148-1 being held by the arc spring holding portion 149-1b and the arc spring held portion 148-2 being held by the arc spring holding portion 149-2b. As a result, when the reference planetary gear 145-1b and the adjustment planetary gear 145-2b are not meshed with any gears, the arc spring 148 assumes its natural length, and the teeth of the reference planetary gear 145-1b and the adjustment planetary gear 145-2b are maintained out of phase with each other.

[0042] On the other hand, when the reference planetary gear 145-1b and the adjustment planetary gear 145-2b are both meshed with gears, the arc spring 148 elastically deforms in the circumferential direction, thereby biasing the reference planetary gear 145-1b and the adjustment planetary gear 145-2b in opposite directions to each other in the circumferential direction.

[0043] Therefore, similar to the planetary gear 142, when the planetary gear 142b performs planetary motion in which it rotates around the sun gear 141, one of the reference planetary gear 145-1b and the adjustment planetary gear 145-2b is in contact with the sun gear 141 or the internal gear 144. This eliminates backlash in the meshing between the planetary gear 142b and the sun gear 141 and internal gear 144, and smooths the meshing state, thereby suppressing the generation of periodic sounds and abnormal noises associated with the planetary motion of the planetary gear 142b and reducing tooth surface wear. Furthermore, even if the planetary carrier 143 is held with an inclination or axial misalignment relative to the cam clutch 153, backlash in the meshing between the planetary gear 142b and the sun gear 141 and the internal gear 144 is eliminated, and fluctuations in the tooth gaps when the sun gear 141 and the internal gear 144 mesh with the planetary gear 142b, which are caused by the inclination of the rotation axis of the planetary carrier 143, mesh are also absorbed. This smooths out the uneven meshing state caused by the inclination or axial misalignment of the planetary carrier 143, suppresses the generation of periodic sounds and abnormal noises associated with the planetary motion of the planetary gear 142, reduces tooth surface wear, and also ensures transmission efficiency.

[0044] Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above embodiments, and various design modifications can be made without departing from the present invention as set forth in the claims.

[0045] In the above-described embodiment, the transmission member consists of a bevel pinion boss and a bevel pinion gear, the bevel pinion boss has a portion that forms the outer ring of the cam clutch, the planetary carrier has a portion that forms the inner ring of the cam clutch, and the outer periphery of the bevel pinion boss is rotatably supported by a bearing, but it may also be configured so that a shaft extending directly from the bevel pinion gear has a portion that forms the inner ring of the cam clutch, the planetary carrier has a portion that forms the outer ring of the cam clutch, and the directly extending shaft is rotatably supported by a bearing. Furthermore, the drive device according to the present invention can be used as a drive device for a variety of purposes, including vehicles using electric motors or the like as a drive source, devices for transporting luggage, and carts.

[0046] In the above-described embodiment, the rotation axis of bevel pinion gear 152 and main shaft 121 are positioned perpendicular to each other, but they may be connected so as to be able to transmit power. For example, the rotation axis direction of bevel pinion gear 152 and the rotation axis direction of main shaft 121 may be arranged parallel to each other, and bevel pinion gear 152 and main shaft 121 may be connected by a chain, a rod, or the like. Also, in Figures 3, 4, 6, 7, 12, 13, and 16, the drive assist unit 130 has three planetary gears 142 or planetary gears 142b, but there is no restriction on the number of planetary gears 142 or planetary gears 142b, and the number may be three or more. In addition, in the above-described embodiment, the main shaft 121 and the bevel gear 122, which is a rotating member, are configured to rotate integrally in at least one direction via the one-way clutch 124, but they may also be configured to rotate integrally in both directions without the one-way clutch 124. The one-way clutch 124 may be of any structure, such as a cam clutch. Furthermore, the coil spring 147 of the planetary gear 142 and the arc spring 148 of the planetary gear 142b are not limited in shape as long as they have the function of biasing the reference planetary gear and the adjustment planetary gear in opposite directions in the circumferential direction. [Explanation of symbols]

[0047] 100 ··· Drive auxiliary device 110 Main body 120 Drive unit 121 ··· Spindle 122 ··· Bevel gear 123 sprocket 124 One-way clutch 125 ··· Bearing 126 Bearing 130 ··· Drive auxiliary unit 140... Reduction mechanism 141 ··· Sun Gear 142 Planetary gear (first embodiment) 142b Planetary gear (second embodiment) 143 Planet carrier 144 Internal gear 145-1 Reference planetary gear (first embodiment) 145-2 Adjusting planetary gear (first embodiment) 145-1b Reference planetary gear (second embodiment) 145-2b Adjusting planetary gear (second embodiment) 146 Pins 147 Coil spring 147-1 Coil spring retained part 147-2 Coil spring retained part 148 Arc spring 148-1 Arc spring retained part 148-2 Arc spring retained part 150 Transmission member 151 Bevel pinion boss 152 Bevel pinion gear 153 Cam clutch 154 Bearing 155 Bearing

Claims

1. A drive device having a main body, a main drive unit provided on the main body, and a drive auxiliary unit that assists the drive of the main drive unit, the main drive unit has a main shaft journaled in the main body unit and a rotating member that rotates integrally with the main shaft in at least one direction, the drive auxiliary unit includes an auxiliary drive shaft, a reduction mechanism connected to the auxiliary drive shaft, and a transmission member that transmits an output of the reduction mechanism to the main shaft, the reduction mechanism includes a planetary gear, a sun gear to which a driving assist force is input from a driving source, a planetary carrier that rotatably supports the planetary gear, and an internal gear provided in the main body portion; the planetary carrier and the transmission member are connected by a power transmission member, the transmission member is connected to the rotating member so that a driving assist force from the driving source is transmitted to the main shaft; A drive device characterized in that the planetary gear is composed of a scissors gear.

2. the rotating member has a bevel gear, the transmission member has a bevel pinion gear, the bevel pinion gear is connected to the bevel gear, the planetary carrier and the transmission member are connected by the power transmission member, 2. The drive device according to claim 1, wherein the scissors gear has a reference planetary gear, an adjustment planetary gear, and a biasing member, and the reference planetary gear and the adjustment planetary gear are biased in opposite directions to each other in the circumferential direction by the biasing member.

3. 2. The drive device according to claim 1, wherein the biasing member is formed of a coil spring.

4. 2. The drive device according to claim 1, wherein the biasing member is formed of an arc spring.

5. The planetary carrier has a boss portion formed on a side surface, 2. The drive device according to claim 1, wherein the boss portion functions as a support portion for the power transmission member.

6. 2. The drive device according to claim 1, wherein the power transmission member is a cam clutch.

7. A vehicle comprising the drive device according to any one of claims 1 to 6.

8. 8. The vehicle according to claim 7, wherein the main shaft is a crankshaft to which a pedal force is input.

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