JP7337586B2 - Transmission for human-powered vehicle and assist system for human-powered vehicle equipped with this transmission - Google Patents

Description

TECHNICAL FIELD The present invention relates to a transmission for a human-powered vehicle and an assist system for a human-powered vehicle provided with this transmission.

A transmission for a manpowered vehicle disclosed in Patent Document 1 includes an internal transmission that changes the gear ratio of the manpowered vehicle stepwise. The internal transmission includes a first transmission unit and a second transmission unit. In the transmission of Patent Document 1, the rotation is changed by the first transmission unit in the second and third shift stages, and the rotation is output to the output body without being changed by the second transmission unit. In the transmission of Patent Document 1, the rotation is changed by both the first transmission unit and the second transmission unit in the fourth transmission stage and the fifth transmission stage having the maximum transmission gear ratio, and output to the output body.

Japanese Patent No. 4564978

In the above transmission, since the transmission unit once used for shifting to increase the transmission ratio is always used for transmission when the transmission ratio is further increased, the degree of freedom in the configuration of the transmission stages is low.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a transmission for a man-powered vehicle and an assist system for a man-powered vehicle with which the gear stages can be configured in a favorable manner.

A transmission according to a first aspect of the present invention is a transmission for a manpowered vehicle, and includes a first transmission unit having a first transmission path for shifting input rotation and a second transmission unit for shifting input rotation. a second transmission unit having a transmission path and configured to transmit rotation to the first transmission unit; The transmission unit has a first planetary gear unit, and the switching unit changes the rotational state of at least one of the first transmission unit and the second transmission unit to change the rotation state of the first transmission unit and the second transmission. The transmission path of the rotation input to the unit is switched, and the transmission path includes at least a first transmission path that passes through the first shift path and a second transmission path that passes through the second shift path and does not pass through the first shift path. 2 transmission path, and a third transmission path that passes through both the first transmission path and the second transmission path, and the switching unit is configured to increase the transmission gear ratio stepwise. The paths are switched in order of the first transmission path, the second transmission path, and the third transmission path.
According to the transmission of the first aspect, when the switching unit increases the gear ratio in stages, between the first transmission path and the third transmission path via the first transmission path of the first transmission unit Since there is a second transmission path that does not pass through the first transmission path of the first transmission unit, it is possible to form a suitable gear shift stage. According to the transmission of the first side, when switching from the first transmission path to the second transmission path, it is suppressed that the transmission path becomes difficult to switch due to the torque input to the first planetary gear unit.

In the transmission according to the second side according to the first side, the first speed change path has a first path and a second path, and the switching section includes at least one of the first transmission path and the third transmission path. In one, it is configured to switch from one of the first shift path including the first path and the first shift path including the second path to the other, and the first transmission path and the third transmission path In each case, the gear ratio when the first gear path includes the second path is greater than the gear ratio when the first gear path includes the first path.
According to the transmission of the second side, at least one of the first transmission path and the third transmission path can form two speed stages.

A transmission of a third aspect according to said second aspect, wherein said first planetary gear unit engages respectively with at least two first sun gears, at least one first ring gear, said at least two first sun gears At least two first planetary gears, and a first carrier supporting the at least two first planetary gears movably around the corresponding first sun gears, the switching unit configured to 1, the transmission path is configured to pass through one of the at least two first sun gears by changing the rotational state of one sun gear, the first path being configured to pass through one of the at least two first sun gears; and said second path is via a different one of said at least two first sun gears than said first sun gear via said first path.
According to the transmission of the third aspect, by making the first sun gear through which the first path and the second path respectively pass different, two gear shift stages can be preferably formed.

In the transmission according to the fourth aspect according to the second aspect, the first transmission path further has a third path, and the switching unit includes, in at least one of the first transmission path and the third transmission path, The first transmission path including the second path and the first transmission path including the third path are configured to be switched from one to the other, and in each of the first transmission path and the third transmission path, The gear ratio when the first gear path includes the third path is greater than the gear ratio when the first gear path includes the second path.
According to the transmission of the fourth aspect, three speed stages can be formed in at least one of the first transmission path and the third transmission path.

In the transmission according to the fifth aspect according to the third aspect, the first transmission path further has a third path, and the switching unit includes, in at least one of the first transmission path and the third transmission path, The first transmission path including the second path and the first transmission path including the third path are configured to be switched from one to the other, and in each of the first transmission path and the third transmission path, The gear ratio when the first gear path includes the third path is greater than the gear ratio when the first gear path includes the second path, and the first planetary gear unit includes: having at least three first sun gears, wherein the third path is different from the first sun gears through which the first and second paths of the at least three first sun gears are routed; Via Sun Gear.
According to the speed change device of the fifth aspect, by making the first sun gear through which the first route and the second route are different, three shift stages can be preferably formed.

In the transmission of the sixth aspect according to any one of the first to fifth aspects, the transmission path further includes a fourth transmission path that transmits the input rotation without speed change, and the switching unit comprises , when increasing the gear ratio stepwise, the transmission path is switched in the order of the fourth transmission path, the first transmission path, the second transmission path, and the third transmission path.
According to the transmission of the sixth aspect, the number of gear shift steps can be increased by the fourth transmission path that transmits the input rotation without speed change.

The transmission of the seventh aspect according to the third or fifth aspect, wherein said second transmission unit comprises a second planetary gear unit, said second planetary gear unit comprising at least one second sun gear, at least one a second ring gear, at least one second planetary gear engaging said at least one second sun gear, and a second supporting said second planetary gear for movement about said at least one second sun gear. 2 carriers, wherein the switching unit is configured to change the rotational state of the at least one second sun gear so that the transmission path passes through one of the at least one second sun gear; The first carrier and the second ring gear are connected by a transmission portion, the first carrier and the second carrier are connected by a first one-way clutch, and the second carrier is connected in the first transmission path. rotates the first carrier through the first one-way clutch, and in the third transmission path, rotation of the second ring gear rotates the first carrier through the transmission portion.
According to the transmission of the seventh aspect, in the first transmission path, the rotation of the second carrier can be suitably transmitted to the first carrier via the first one-way clutch, and in the third transmission path, via the transmission section. can suitably transmit the rotation of the second ring gear to the first carrier.

In the transmission according to the eighth aspect according to the seventh aspect, the transmission path further includes a fourth transmission path that transmits the input rotation without speed change, and the fourth transmission path includes the second carrier. Rotation rotates the first carrier through the first one-way clutch, and rotation of the first carrier rotates the second ring gear through the transmission.
According to the transmission of the eighth aspect, the rotation of the first carrier can be suitably transmitted to the second ring gear via the first one-way clutch in the fourth transmission path.

In the transmission according to the ninth aspect according to the seventh aspect, the switching unit increases the gear ratio stepwise and switches the transmission path from the first transmission path to the second transmission path. , changing the rotational state of the at least two first sun gears after changing the rotational state of the at least one second sun gear.
According to the transmission of the ninth aspect, it is possible to prevent the rotation state of the first sun gear from being changed before changing the rotation state of the second sun gear.

In the transmission according to the tenth aspect according to the ninth aspect, the transmission portion includes one of a concave portion and a convex portion provided on one of the outer peripheral portion of the first carrier and the inner peripheral portion of the second ring gear, and the 1 carrier and the other of a concave portion and a convex portion provided on the other of the inner peripheral portion of the second ring gear, and the circumferential length of the concave portion is longer than the circumferential length of the convex portion. big.
According to the transmission of the tenth aspect, both when the rotation is transmitted from the first carrier to the second ring gear and when the rotation is transmitted from the second ring gear to the first carrier, the Rotation can be transmitted.

The transmission of the eleventh aspect according to any one of the seventh to tenth aspects, further comprising an output body, a second one-way clutch, and a third one-way clutch, wherein the first ring gear comprises the second one-way It is connected to the output body via a clutch, and the second ring gear is connected to the output body via the third one-way clutch.
According to the transmission of the eleventh aspect, the second one-way clutch suppresses transmission of the rotation of the output body to the first ring gear, and the third one-way clutch transmits the rotation of the output body to the second ring gear. transmission is suppressed.

A transmission according to a twelfth aspect of the present invention is a transmission for a manpowered vehicle, and includes a first transmission unit having a first transmission path for shifting input rotation and a second transmission unit for shifting input rotation. a second transmission unit having a transmission path and configured to transmit rotation to the first transmission unit; The transmission unit has a first planetary gear unit, the first transmission path has a plurality of paths each having a different gear ratio, and the switching section is configured to switch between at least the first transmission unit and the second transmission unit. When one of the rotation states is changed to switch the transmission path of the rotation input to the first transmission unit and the second transmission unit, and the transmission path passes through the first transmission path, one of the plurality of transmission paths and the transmission path is configured to switch from one to the other of the first shift path including one of the plurality of paths and the other one of the plurality of paths, and the transmission gear ratio is changed to In the case of stepwise increase, a gear shift stage formed by a transmission path passing through a first gear shift path including a path forming a first gear ratio among the plurality of paths, and the first gear ratio among the plurality of paths It includes a shift stage formed by a transmission path that does not pass through the first shift path between a shift stage formed by a transmission path that passes through the first shift path that forms a gear ratio that is less than one gear ratio.
According to the transmission of the twelfth aspect, when increasing the gear ratio in stages including a path forming a gear ratio smaller than the first gear ratio among the plurality of paths in stages, a plurality of can be greater than the gear ratio of the gear shift stage including the path forming the first gear ratio of the paths of . For this reason, it is possible to configure the speed change stage in a suitable manner.

The transmission of the thirteenth aspect according to any one of the first to twelfth aspects further includes a hub accommodating the first transmission unit, the second transmission unit, and the switching section.
According to the transmission of the thirteenth aspect, it is possible to suitably configure gear shift stages in a transmission provided with a hub.

An assist system according to a fourteenth aspect of the present invention is an assist system for a human-powered vehicle, comprising a transmission according to any one of the first to thirteenth aspects, and a motor that assists the human-powered driving force.
According to the assist system of the fourteenth aspect, it is possible to suitably configure the shift stage in the assist system provided with the motor. According to the transmission of the fourteenth aspect, it is possible to suitably configure the speed change stages in the transmission in which the rotational torque input by the motor is large.

The assist system according to the fifteenth aspect according to the fourteenth aspect, further comprising an operation unit that is manually operated to operate the transmission, wherein the transmission operates the human-powered vehicle according to the operation of the operation unit. change the gear ratio of the
According to the transmission device of the fourteenth aspect, it is possible to suitably configure the gear shift stage in an assist system having an operation unit that is manually operated.

The transmission for a man-powered vehicle of the present disclosure and the assist system for a man-powered vehicle equipped with this transmission can preferably configure a gear shift stage.

1 is a side view of a manpowered vehicle including a transmission for a manpowered vehicle according to a first embodiment and an assist system for a manpowered vehicle provided with this transmission; FIG. FIG. 2 is a front view of the transmission for the manpowered vehicle of FIG. 1; FIG. 3 is a cross-sectional view taken along line D3-D3 in FIG. 2; FIG. 4 is a cross-sectional view taken along line D4-D4 in FIG. 3; The front view of the switching part of FIG. FIG. 4 is a cross-sectional view taken along line D6-D6 in FIG. 3; FIG. 4 is a cross-sectional view taken along line D7-D7 in FIG. 3; 4 is a perspective view of the arm member of FIG. 3; FIG. FIG. 4 is a side view of the arm member of FIG. 3; 5 is a partial cross-sectional view showing a state in which driving force is transmitted from the first carrier to the second ring gear in the switching portion of FIG. 4; FIG. 5 is a partial cross-sectional view showing a state in which driving force is transmitted from the second ring gear to the first carrier in the switching portion of FIG. 4; FIG. FIG. 4 is a schematic diagram showing the transmission path in the first gear stage of the transmission for the manpowered vehicle of FIG. 3 ; FIG. 4 is a schematic diagram showing the transmission path in the second gear stage of the transmission for the man-powered vehicle of FIG. 3 ; FIG. 4 is a schematic diagram showing the transmission path in the third shift stage of the transmission for the man-powered vehicle of FIG. 3 ; FIG. 4 is a schematic diagram showing a transmission path in a fourth shift stage of the transmission for the manpowered vehicle of FIG. 3; FIG. 4 is a schematic diagram showing the transmission path in the fifth gear stage of the transmission for the manpowered vehicle of FIG. 3 ; The side view of the arm member of 2nd Embodiment. The schematic diagram which shows the transmission path in the 1st gear shift stage of the transmission for manpower-driven vehicles of 2nd Embodiment. The schematic diagram which shows the transmission path in the 2nd gear shift stage of the transmission for manpower-driven vehicles of 2nd Embodiment. The schematic diagram which shows the transmission path in the 3rd gear shift stage of the transmission for manpower-driven vehicles of 2nd Embodiment. The schematic diagram which shows the transmission path in the 4th gear shift stage of the transmission for manpower-driven vehicles of 2nd Embodiment. The schematic diagram which shows the transmission path in the 5th gear shift stage of the transmission for manpower-driven vehicles of 2nd Embodiment. The schematic diagram which shows the transmission path in the 6th gear shift stage of the transmission for manpower-driven vehicles of 2nd Embodiment. The schematic diagram which shows the transmission path in the 7th gear shift stage of the transmission for manpower-driven vehicles of 2nd Embodiment. The schematic diagram which shows the transmission path in the 8th gear shift stage of the transmission for manpower-driven vehicles of 2nd Embodiment.

<First Embodiment>
An assist system 40 for a human-powered vehicle and a transmission 50 for a human-powered vehicle according to the first embodiment will be described with reference to FIGS. 1 to 16 . The human-powered vehicle 10 is a vehicle that can be driven at least by human-powered driving force. The manpowered vehicle 10 is not limited in the number of wheels, and includes, for example, unicycles and vehicles with three or more wheels. Human powered vehicles 10 include various types of bicycles, such as mountain bikes, road bikes, city bikes, cargo bikes, and recumbents, as well as electric bicycles (E-bikes). Electric bicycles include power-assisted bicycles that assist the propulsion of the vehicle with an electric motor. Hereinafter, in the embodiments, the manpowered vehicle 10 will be described as a bicycle.

A human-powered vehicle 10 includes a crank 12 to which a human-powered driving force is input, wheels 14, and a vehicle body 16. - 特許庁The wheels 14 include rear wheels 14A and front wheels 14B. Body 16 includes a frame 18 . The crank 12 includes a crankshaft 12A rotatable with respect to the frame 18, and crank arms 12B provided at axial ends of the crankshaft 12A. A pedal 20 is connected to each crank arm 12B. The rear wheel 14A is driven by the crank 12 rotating. Rear wheel 14A is supported by frame 18 . A drive mechanism 22 connects the crank 12 and the rear wheel 14A. The drive mechanism 22 includes a first rotating body 24 connected to the crankshaft 12A. The crankshaft 12A and the first rotor 24 may be connected via a one-way clutch. The one-way clutch rotates the first rotating body 24 forward when the crank 12 rotates forward, and prevents the first rotating body 24 from rotating backward when the crank 12 rotates backward. The first rotating body 24 includes a sprocket, pulley, or bevel gear. Drive mechanism 22 further includes a second rotating body 26 and a connecting member 28 . The connecting member 28 transmits the rotational force of the first rotating body 24 to the second rotating body 26 . Coupling member 28 includes, for example, a chain, belt, or shaft.

The second rotating body 26 is connected to the rear wheel 14A. The second rotating body 26 includes a sprocket, pulley, or bevel gear. A one-way clutch is preferably provided between the second rotor 26 and the rear wheel 14A. The one-way clutch rotates the rear wheel 14A forward when the second rotating body 26 rotates forward, and prevents the rear wheel 14A from rotating backward when the second rotating body 26 rotates backward.

A front wheel 14</b>B is attached to the frame 18 via a front fork 30 . A handlebar 34 is connected to the front fork 30 via a stem 32 . In this embodiment, the rear wheels 14A are connected to the cranks 12 by the drive mechanism 22, but at least one of the rear wheels 14A and the front wheels 14B may be connected to the cranks 12 by the drive mechanism 22.

The manpowered vehicle 10 includes a battery 36 for the manpowered vehicle. Battery 36 includes one or more battery elements. The battery element includes a rechargeable battery (secondary battery). Battery 36 powers motor 42 of assist system 40 . Battery 36 is preferably communicatively connected to the controller of motor 42 by wire or wirelessly. The battery 36 can communicate with the controller of the motor 42 by, for example, power line communication (PLC).

The assist system 40 includes a transmission 50 and a motor 42 that assists the human driving force. The motor 42 provides propulsion to the manpowered vehicle 10 . Motor 42 includes one or more electric motors. The motor 42 is configured to transmit rotation to at least one of the power transmission path of the manpower driving force from the pedals 20 to the rear wheels 14A and the front wheels 14B. A power transmission path for manpower driving force from the pedals 20 to the rear wheels 14A includes the rear wheels 14A. In this embodiment, the motor 42 is provided on the frame 18 of the manpowered vehicle 10 and is configured to transmit rotation to the first rotor 24 . A drive unit is configured including a motor 42 and a housing in which the motor 42 is provided. The power transmission path between the motor 42 and the crankshaft 12A preferably has a shaft so that the torque of the crank 12 does not cause the motor 42 to rotate when the crankshaft 12A is rotated in the direction in which the manpowered vehicle 10 moves forward. A one-way clutch is provided. If at least one of the rear wheels 14A and front wheels 14B is provided with a motor 42, the motor 42 may include a hub motor.

Preferably, the assist system 40 further includes an operating section 44 that is manually operated to operate the transmission 50 . The transmission 50 changes the gear ratio of the manpowered vehicle 10 according to the operation of the operation unit 44 . The gear ratio is the ratio of the rotational speed of the rear wheel 14A to the rotational speed of the crank 12 (first rotating body 24). The operating portion 44 is provided on the handlebar 34, for example. Preferably, the operating portion 44 is connected to the transmission 50 by a Bowden cable. When the inner cable of the Bowden cable is moved by operating the operating portion 44, the transmission 50 is operated and the gear ratio is changed. Transmission 50 may include a motor for changing the transmission ratio. In this case, the operation unit 44 and the motor of the transmission 50 are configured to be able to communicate with each other through wired communication or wireless communication.

As shown in FIG. 3, the transmission 50 includes a first transmission unit 52, a second transmission unit 54, and a switching section 56 that changes the gear ratio of the manpowered vehicle 10 stepwise. The first shift unit 52 has a first shift path L1 for shifting the input rotation. The second transmission unit 54 has a second transmission path L<b>2 for shifting the input rotation, and is configured to transmit the rotation to the first transmission unit 52 . Transmission 50 further includes a shaft member 58 . The shaft member 58 is a hub shaft supported by the frame 18 . The first transmission unit 52 and the second transmission unit 54 are provided on the shaft member 58 so as to be adjacent to each other in the axial direction of the shaft member 58 .

The first transmission unit 52 has a first planetary gear unit 60 . Preferably, the first planetary gear unit 60 has at least two first sun gears 62 , at least one first ring gear 64 , at least two first planetary gears 66 and a first carrier 68 . At least two first planetary gears 66 engage with at least two first sun gears 62 respectively. A first carrier 68 supports at least two first planetary gears 66 for movement about corresponding first sun gears 62 . In this embodiment, the first planetary gear unit 60 has two first sun gears 62 , one first ring gear 64 and two first planetary gears 66 . The first sun gear 62 has a first sun gear 62A and a first sun gear 62B. The two first planetary gears 66 have a first planetary gear 66A engaging the first sun gear 62A and a first planetary gear 66B engaging the first sun gear 62B.

The first planetary gear 66A and the first planetary gear 66B are integrally formed to form a stepped first planetary gear body 66C. Preferably, the first planetary gear unit 60 has a plurality of first planetary gear bodies 66C. For example, the first planetary gear unit 60 has four first planetary gear bodies 66C. The first carrier 68 includes a first portion 68A passing through each of the plurality of first planetary gear bodies 66C, and a second portion integrally supporting the first portion 68A on one side of the first planetary gear body 66C in the axial direction. 68B and a third portion 68C integrally supporting the first portion 68A on the other axial side of the first planetary gear body 66C. The first portion 68A supports the first planetary gear body 66C rotatably with respect to the first planetary gear body 66C. The first portion 68A may be configured to rotate relative to the second portion 68B and the third portion 68C.

The number of teeth of the first sun gear 62A is less than the number of teeth of the first sun gear 62B. The number of teeth of the first planetary gear 66A is greater than the number of teeth of the first planetary gear 66B. The gear ratio when the rotation input to the first planetary gear unit 60 is output via the first sun gear 62A is as follows: Smaller than the gear ratio for output. Preferably, the at least two first sun gears 62 have a larger number of teeth in the axial direction of the shaft member 58 from the side closer to the second transmission unit 54 toward the side farther from the second transmission unit 54. 62 are placed. In this embodiment, the first sun gear 62A is arranged at a position farther from the second transmission unit 54 than the first sun gear 62B in the axial direction of the shaft member 58 .

Preferably, the second transmission unit 54 has a second planetary gear unit 70 . The second planetary gear unit 70 has at least one second sun gear 72 , at least one second ring gear 74 , at least one second planetary gear 76 and a second carrier 78 . At least one second planetary gear 76 engages at least one second sun gear 72 . A second carrier 78 supports second planetary gears 76 for movement about at least one second sun gear 72 . In this embodiment, the second planetary gear unit 70 has one second sun gear 72 , one second ring gear 74 and one second planetary gear 76 .

The second planetary gear 76 is provided in a second planetary gear body 76A. Preferably, the second planetary gear unit 70 has a plurality of second planetary gear bodies 76A. For example, the second planetary gear unit 70 has four second planetary gear bodies 76A. The second carrier 78 has a first portion 78A passing through the plurality of second planetary gear bodies 76A, and a second portion 68B integrally supporting the first portion 68A on one side of the second planetary gear bodies 76A in the axial direction. , and a third portion 78C integrally supporting the first portion 78A on the other axial side of the second planetary gear body 76A. The first portion 78A supports the second planetary gear body 76A rotatably with respect to the second planetary gear body 76A. The first portion 78A may be configured to be rotatable with respect to the second portion 78B and the third portion 78C.

The number of teeth of the second sun gear 72 is equal to the number of teeth of the first sun gear 62B. The number of teeth of the second ring gear 74 is equal to the number of teeth of the first ring gear 64 . The number of teeth of the second sun gear 72 may be greater than the number of teeth of the first sun gear 62B or may be less than the number of teeth of the first sun gear 62B. The number of teeth of the second sun gear 72 may be equal to the number of teeth of the first sun gear 62A, may be greater than the number of teeth of the first sun gear 62A, or may be less than the number of teeth of the first sun gear 62A. may The number of teeth of at least two first sun gears 62 and the number of teeth of at least one second sun gear 72 are determined according to the gear ratio required for transmission 50 .

Preferably, transmission 50 further includes a transmission portion 80 . A transmission portion 80 connects the first carrier 68 and the second ring gear 74 . As shown in FIG. 3, the transmission portion 80 includes one of a concave portion 80A and a convex portion 80B provided on one of the outer peripheral portion of the first carrier 68 and the inner peripheral portion of the second ring gear 74, and the outer peripheral portion of the first carrier 68. and the other of the concave portion 80A and the convex portion 80B provided on the other of the inner peripheral portion of the second ring gear 74 . The circumferential length of the concave portion 80A is greater than the circumferential length of the convex portion 80B. The transmission portion 80 is provided on the outer peripheral portion of the second portion 68</b>B of the first carrier 68 and the inner peripheral portion of the second ring gear 74 .

Preferably, transmission 50 further includes a first one-way clutch 82 (see FIG. 2). The first carrier 68 and the second carrier 78 are connected by a first one-way clutch 82 . The first one-way clutch 82 is provided between the inner peripheral portion of the second portion 68B of the first carrier 68 and the outer peripheral portion of the third portion 78C of the second carrier 78 . The first one-way clutch 82 transmits rotation of the second carrier 78 to the first carrier 68 and does not transmit rotation of the first carrier 68 to the second carrier 78 .

Preferably, transmission 50 further comprises output 84 , second one-way clutch 86 and third one-way clutch 88 . The first ring gear 64 is connected to the output body 84 via a second one-way clutch 86 . The second ring gear 74 is connected to the output body 84 via a third one-way clutch 88 .

Transmission 50 further includes a hub 90 that accommodates first transmission unit 52 , second transmission unit 54 , and switching section 56 . Hub 90 rotates together with output body 84 . The output member 84 is provided on the inner peripheral portion of the hub 90 . The output body 84 rotates integrally with the hub 90 by, for example, a spline fit or a serration fit. Output body 84 and hub 90 may be integrally formed. Flanges 92 are provided at both ends of the hub 90 in the axial direction on the outer periphery of the hub 90 . The flange 92 is formed with holes 92A that engage spokes of the rear wheel 14A.

The second one-way clutch 86 is provided between the outer peripheral portion of the first ring gear 64 and the inner peripheral portion of the output body 84 . The second one-way clutch 86 transmits rotation of the first ring gear 64 to the output body 84 and does not transmit rotation of the output body 84 to the first ring gear 64 .

The third one-way clutch 88 is provided between the outer peripheral portion of the second ring gear 74 and the inner peripheral portion of the output body 84 . The third one-way clutch 88 transmits rotation of the second ring gear 74 to the output body 84 and does not transmit rotation of the output body 84 to the second ring gear 74 .

Transmission 50 further includes an input 94 . The input body 94 is provided on the shaft member 58 so as to be rotatable with respect to the shaft member 58 . The input body 94 transmits the rotation of the second rotating body 26 to the second transmission unit 54 . One axial end of the shaft member 58 of the input body 94 is connected to the second rotating body 26 . The other axial end of the shaft member 58 of the input body 94 is connected to the outer peripheral portion of the second portion 78B of the second carrier 78 . Rotation of input 94 is output from second transmission unit 54 to output 84 or from second transmission unit 54 and first transmission unit 52 to output 84 .

The switching unit 56 switches the transmission path S of the rotation input to the first transmission unit 52 and the second transmission unit 54 by changing the rotation state of at least one of the first transmission unit 52 and the second transmission unit 54 .

The transmission path S includes at least a first transmission path S1 that passes through the first shift path L1, a second transmission path S2 that passes through the second shift path L2 but does not pass through the first shift path L1, and the first transmission path L1. and a third transmission path S3 that passes through both of the transmission path L2 and the second transmission path L2. The switching unit 56 switches the transmission path S in order of the first transmission path S1, the second transmission path S2, and the third transmission path S3 when increasing the gear ratio in stages.

The first shift path L1 has a first path L11 and a second path L12. When the transmission path S passes through the first gear path L1, the switching unit 56 switches from one of the first gear path L1 including the first path L11 and the first gear path L1 including the second path L12 to the other. It is configured to switch S. In at least one of the first transmission path S1 and the third transmission path S3, the switching unit 56 switches from one of the first transmission path L1 including the first path L11 and the first transmission path L1 including the second path L12 to the other. configured to switch to In each of the first transmission path S1 and the third transmission path S3, the gear ratio when the first gear path L1 includes the second path L12 is the gear ratio when the first gear path L1 includes the first path L11. Greater than ratio.

The transmission path S further has a fourth transmission path S4 that transmits the input rotation without speed change. The switching unit 56 switches the transmission path S in order of the fourth transmission path S4, the first transmission path S1, the second transmission path S2, and the third transmission path S3 when increasing the gear ratio in stages. In the fourth transmission path S4, neither the first gear path L1 nor the second gear path L2 is passed.

Table 1 shows the transmission path S at each shift stage formed by the transmission 50 of this embodiment. The gear ratio in each gear shift stage increases in order of the first gear stage, the second gear stage, the third gear stage, the fourth gear stage, and the fifth gear stage. In the present embodiment, the switching unit 56 is configured to switch from one of the first shift path L1 including the first path L11 and the first shift path L1 including the second path L12 to the other in the third transmission path S3. be done. In the present embodiment, when switching from one of the fourth gear stage and the fifth gear stage to the other of the fourth gear stage and the fifth gear stage, the switching unit 56 switches to the first gear shift path including the first path L11. It is configured to switch the transmission path S from one side to the other side of the first shift path L1 including L1 and the second path L12.

Preferably, the gear ratio of the first transmission unit 52 in the first transmission path S1 corresponding to the gear ratio that is one step smaller than the gear ratio of the second transmission path S2 is smaller than the gear ratio of the second transmission path S2. In this embodiment, the gear ratio of the first planetary gear unit 60 via the first sun gear 62A is smaller than the gear ratio of the second planetary gear unit 70 via the second sun gear 72 .

The switching portion 56 has a claw member 96 , an arm member 98 and a biasing member 100 . A pawl member 96 is provided corresponding to each of the at least two first sun gears 62 and the at least one second sun gear 72 .

The pawl member 96 is provided on the outer peripheral portion of the shaft member 58 so as to be movable with respect to the shaft member 58 . The pawl member 96 has a first pawl member 96A, a second pawl member 96B, and a third pawl member 96C. The first pawl member 96A is arranged between the outer peripheral portion of the shaft member 58 and the inner peripheral portion of the first sun gear 62A. The second pawl member 96B is arranged between the outer peripheral portion of the shaft member 58 and the inner peripheral portion of the first sun gear 62B. The third pawl member 96</b>C is arranged between the outer peripheral portion of the shaft member 58 and the inner peripheral portion of the second sun gear 72 .

The arm member 98 is provided on the outer peripheral portion of the shaft member 58 so as to be rotatable with respect to the shaft member 58 . The arm member 98 has a base portion 98A, a first arm 98B, a second arm 98C and a third arm 98D. The base portion 98A extends in the axial direction of the shaft member 58 .

The switching section 56 has a first switching section 56A, a second switching section 56B, and a third switching section 56C. The first switching portion 56A includes a first claw member 96A and a first arm 98B. The second switching portion 56B includes a second claw member 96B and a second arm 98C. The third switching portion 56C includes a third claw member 96C and a third arm 98D.

A biasing member 100 is provided corresponding to each claw member 96 . The biasing member 100 biases each claw member 96 in a direction in which the projection amount of each claw member 96 from the shaft member 58 increases. Each pawl member 96 includes a first state in which each pawl member 96 protrudes from the shaft member 58 by a small amount, and a second state in which each pawl member 96 protrudes from the shaft member 58 by a large amount. The arm member 98 is configured to rotate around the shaft member 58 according to the operation of the operating portion 44 . By rotating the arm member 98 around the shaft member 58, the claw member 96 is changed from one of the first state and the second state to the other of the first state and the second state.

The first arm 98B presses the first pawl member 96A against the shaft member 58 to form the second state. In the first state, the first pawl member 96A does not engage with the recess 102 provided in the inner peripheral portion of the first sun gear 62A and allows the rotation of the first sun gear 62A with respect to the shaft member 58 . In the second state, the first pawl member 96A engages with a concave portion 102 provided in the inner peripheral portion of the first sun gear 62A to restrict rotation of the first sun gear 62A with respect to the shaft member 58 .

The second arm 98C presses the second pawl member 96B against the shaft member 58 to form the second state. In the first state, the second pawl member 96B does not engage with the recess 102 provided in the inner peripheral portion of the first sun gear 62B and allows the rotation of the first sun gear 62B with respect to the shaft member 58 . In the second state, the second pawl member 96B engages with a recess 102 provided in the inner peripheral portion of the first sun gear 62B to restrict rotation of the first sun gear 62B with respect to the shaft member 58 .

The third arm 98D presses the third claw member 96C against the shaft member 58 to form the second state. In the first state, the third pawl member 96</b>C does not engage with the recessed portion 102 provided in the inner peripheral portion of the second sun gear 72 and allows the rotation of the second sun gear 72 with respect to the shaft member 58 . In the second state, the third pawl member 96</b>C engages with a recessed portion 102 provided in the inner peripheral portion of the second sun gear 72 to restrict rotation of the second sun gear 72 with respect to the shaft member 58 .

The first arm 98B, the second arm 98C, and the third arm 98D are configured such that the corresponding pawl member 96 is in the first state or the second state at the rotational phase R with respect to the shaft member 58. In this embodiment, the rotation phases R of the arm member 98 with respect to the shaft member 58 are a first rotation phase R1, a second rotation phase R2, a third rotation phase R3, a fourth rotation phase R4, and a fifth rotation phase R5. have When the rotational phase R is the first rotational phase R1, the transmission 50 forms a first gear stage. When the rotational phase R is the second rotational phase R2, the transmission 50 forms a second gear stage. When the rotational phase R is the third rotational phase R3, the transmission 50 forms a third gear stage. When the rotational phase R is the fourth rotational phase R4, the transmission 50 forms a fourth gear stage. If the rotational phase R is a fifth rotational phase R5, the transmission 50 forms a fifth gear stage.

The switching unit 56 is configured such that the transmission path S passes through one of the at least two first sun gears 62 by changing the rotation state of the at least two first sun gears 62 . A first path L11 passes through one of the at least two first sun gears 62, and a second path L12 passes through the first sun gears 62 in the first path L11 of the at least two first sun gears 62. via a different one. For example, the first path L11 goes through the first sun gear 62A and the second path L12 goes through the first sun gear 62B. The switching unit 56 sets the first claw member 96A to the second state and the second claw member 96B to the first state so that the transmission path S passes through the first sun gear 62A. The switching unit 56 sets the first claw member 96A to the first state and the second claw member 96B to the second state so that the transmission path S passes through the first sun gear 62B.

The switching unit 56 is configured such that the transmission path S passes through one of the at least one second sun gears 72 by changing the rotational state of the at least one second sun gear 72 . The switching unit 56 causes the transmission path S to pass through the second sun gear 72 by setting the third claw member 96C to the second state.

The switching unit 56 changes the rotational state of at least one second sun gear 72 when increasing the gear ratio in stages and when switching the transmission path S from the first transmission path S1 to the second transmission path S2. After that, the rotation state of the at least two first sun gears 62 is changed. The second arm 98C is configured such that the state of the third pawl member 96C is in the second state between the second rotation phase R2 and the third rotation phase R3, and the first arm 98B is configured to be in the third rotation phase R3. In the rotation phase R3, the state of the first claw member 96A is configured to be the first state. Since the rotation of the first sun gear 62 with respect to the shaft member 58 is permitted after the rotation of the second sun gear 72 with respect to the shaft member 58 is restricted, both the shaft members 58 of the second sun gear 72 and the first sun gear 62 are allowed to rotate with respect to the shaft member 58 . It is difficult to form a state in which rotation with respect to is permitted. Therefore, it is possible to suitably change the shift stage.

Table 2 shows the rotational states of the first sun gear 62A, the first sun gear 62B, and the second sun gear 72 in each shift stage formed by the arm member 98 of this embodiment.

In the fourth transmission path S4 shown in FIG. 12, the rotation of the second carrier 78 rotates the first carrier 68 via the first one-way clutch 82, and the rotation of the first carrier 68 rotates the second ring via the transmission portion 80. Gear 74 is rotated. Both the first sun gear 62 and the second sun gear 72 are allowed to rotate relative to the shaft member 58 in the fourth transmission path S4. Therefore, the rotation input from the input member 94 to the first transmission unit 52 is output to the output member 84 via the third one-way clutch 88 without being changed.

In the first transmission path S1 shown in FIG. 13, the rotation of the second carrier 78 rotates the first carrier 68 via the first one-way clutch 82, and in the third transmission path S3, the rotation of the second ring gear 74 is transmitted. Rotate first carrier 68 via portion 80 .

In the first transmission path S1, the second sun gear 72 is allowed to rotate with respect to the shaft member 58. Therefore, the rotation input from the input body 94 to the first transmission unit 52 is not changed, and the first one-way clutch 82 is rotated. input to the second transmission unit 54 via the The rotation input to the second transmission unit 54 is accelerated by a transmission ratio corresponding to the number of teeth of the first sun gear 62A whose rotation is restricted, and is output to the output body 84 via the second one-way clutch 86. . In the first transmission path S<b>1 , the second ring gear 74 rotates the first carrier 68 via the transmission portion 80 .

In the second transmission path S2 shown in FIG. 14, the rotation of the second sun gear 72 with respect to the shaft member 58 is restricted, so that the rotation input from the input member 94 to the first transmission unit 52 is accelerated to the third transmission path S2. It is output to the output member 84 via the one-way clutch 88 . Since all the first sun gears 62 are allowed to rotate with respect to the shaft member 58 on the second transmission path S2, the rotation of the output member 84 is not transmitted to the first transmission unit 52 by the second one-way clutch 86.

As shown in FIG. 10, in the first transmission path S1 shown in FIG. 13, the rotation of the second sun gear 72 relative to the shaft member 58 is allowed, so that the rotation of the first carrier 68 rotates the second ring gear 74. Let Since the rotational speeds of the first carrier 68 and the second ring gear 74 are lower than the rotational speeds of the first ring gear 64 and the output body 84 , the relative rotation between the second ring gear 74 and the output body 84 is controlled by the third one-way clutch 88 . is allowed.

In the state of FIG. 10, the switching unit 56 changes the state in which the rotation of the second sun gear 72 with respect to the shaft member 58 is permitted to the state in which the rotation with respect to the shaft member 58 is restricted. The rotation speed becomes higher than the rotation speed of the first carrier 68 . Therefore, the convex portion 80B moves relative to the concave portion 80A, and the second ring gear 74 and the first carrier 68 start to rotate relative to each other. In this state, the gear ratio of the first transmission unit 52 when passing through the first sun gear 62A is smaller than the gear ratio of the second transmission unit 54 when passing through the second sun gear 72, the second ring gear. The rotation speed of 74 is faster than the rotation speed of the first ring gear 64 . Therefore, the rotation of the second ring gear 74 rotates the output member 84 by the third one-way clutch 88 , and the relative rotation between the first ring gear 64 and the output member 84 is permitted by the second one-way clutch 86 . In this state, the switching unit 56 changes the state in which rotation of the first sun gear 62A with respect to the shaft member 58 is restricted to a state in which the rotation is permitted. Since the relative rotation between the first ring gear 64 and the output member 84 is permitted, the rotational state of the first sun gear 62A can be suitably changed when the load on the first sun gear 62A is small.

As shown in FIG. 11, when the convex portion 80B reaches the opposite end in the rotational direction within the concave portion 80A, the rotation of the second ring gear 74 causes the first carrier 68 to rotate. Therefore, the rotation of the second carrier 78 is not transmitted to the first carrier 68 by the first one-way clutch 82 in the second transmission path S2 shown in FIG.

In the third transmission path S3 shown in FIG. 15, the rotation of the second sun gear 72 with respect to the shaft member 58 is restricted, so that the rotation input from the input member 94 to the first transmission unit 52 is accelerated and It is input to the second transmission unit 54 via 80 . The rotation input to the second transmission unit 54 is accelerated by a transmission ratio corresponding to the number of teeth of the first sun gear 62A whose rotation is restricted, and is output to the output body 84 via the second one-way clutch 86. .

In the third transmission path S3 shown in FIG. 16, the rotation of the second sun gear 72 with respect to the shaft member 58 is restricted, so that the rotation input from the input body 94 to the first transmission unit 52 is accelerated and It is input to the second transmission unit 54 via 80 . The rotation input to the second transmission unit 54 is accelerated by a transmission ratio corresponding to the number of teeth of the first sun gear 62B whose rotation is restricted, and is output to the output body 84 via the second one-way clutch 86. .

<Second embodiment>
A transmission 50A of the second embodiment will be described with reference to FIGS. 17 to 25. FIG. The transmission 50A of the second embodiment is the same as the transmission 50 of the first embodiment except that it is configured to have eight shift stages. , are denoted by the same reference numerals as in the first embodiment, and overlapping descriptions are omitted.

As shown in FIG. 18, the transmission 50A includes a first transmission unit 52A, a second transmission unit 54, and a switching section 56 that changes the transmission ratio of the manpowered vehicle 10 stepwise. The first transmission unit 52A has a first transmission path L1 for shifting the input rotation. The second transmission unit 54 has a second transmission path L2 for shifting the input rotation, and can transmit the rotation to the first transmission unit 52A.

The first transmission unit 52A has a first planetary gear unit 60A. Preferably, the first planetary gear unit 60A has at least two first sun gears 62 , at least one first ring gear 64 , at least two first planetary gears 66 and a first carrier 68 . At least two first planetary gears 66 engage with at least two first sun gears 62 respectively. A first carrier 68 supports at least two first planetary gears 66 for movement about corresponding first sun gears 62 . In this embodiment, the first planetary gear unit 60A has at least three first sun gears 62 . In this embodiment, the first planetary gear unit 60A has three first sun gears 62, one first ring gear 64, and three first planetary gears 66. The first sun gear 62 has a first sun gear 62A, a first sun gear 62B and a first sun gear 62C. The three first planetary gears 66 are the first planetary gear 66A engaging the first sun gear 62A, the first planetary gear 66B engaging the first sun gear 62B, and the first sun gear 62C. It has a first planetary gear 66D.

The first planetary gear 66A, the first planetary gear 66B, and the first planetary gear 66D are integrally formed to form a stepped first planetary gear body 66E. Preferably, the first planetary gear unit 60A has a plurality of first planetary gear bodies 66E. For example, the first planetary gear unit 60A has four first planetary gear bodies 66E. The first carrier 68 includes a first portion 68A passing through each of the plurality of first planetary gear bodies 66E, and a second portion integrally supporting the first portion 68A on one side of the first planetary gear body 66E in the axial direction. 68B and a second portion 68B integrally supporting the first portion 68A on the other axial side of the first planetary gear body 66E. The first portion 78A supports the first planetary gear body 66E rotatably with respect to the first planetary gear body 66E. The first portion 68A may be configured to rotate relative to the second portion 68B and the third portion 68C.

The number of teeth of the first sun gear 62B is less than the number of teeth of the first sun gear 62C. The number of teeth of the first planetary gear 66B is greater than the number of teeth of the first planetary gear 66D. The gear ratio when the rotation input to the first planetary gear unit 60A is output via the first sun gear 62B is Smaller than the gear ratio for output. Preferably, the at least three first sun gears 62 have a larger number of teeth in the axial direction of the shaft member 58 from the side closer to the second transmission unit 54 toward the side farther from the second transmission unit 54. 62 are placed. In this embodiment, the first sun gear 62B is arranged at a position farther from the second transmission unit 54 than the first sun gear 62C in the axial direction of the shaft member 58 .

In this embodiment, preferably the number of teeth of the second sun gear 72 is greater than the number of teeth of the first sun gear 62C, and the number of teeth of the second ring gear 74 is equal to the number of teeth of the first ring gear 64. . The number of teeth of the second sun gear 72 may be less than the number of teeth of the first sun gear 62C and may be equal to the number of teeth of the first sun gear 62C. The number of teeth of the second sun gear 72 may be equal to the number of teeth of the first sun gear 62A, may be greater than the number of teeth of the first sun gear 62A, or may be less than the number of teeth of the first sun gear 62A. may The number of teeth of the second sun gear 72 may be equal to the number of teeth of the first sun gear 62B, may be greater than the number of teeth of the first sun gear 62B, or may be less than the number of teeth of the first sun gear 62B. may The number of teeth of at least three first sun gears 62 and the number of teeth of at least one second sun gear 72 are determined according to the gear ratio required for transmission 50A.

Preferably, the transmission 50A further includes a transmission section 80, a first one-way clutch 82, an output body 84, a second one-way clutch 86, and a third one-way clutch 88. Preferably, the transmission 50A further includes a hub 90 that accommodates the first transmission unit 52A, the second transmission unit 54, and the switching section 56. As shown in FIG. Preferably, transmission 50A further includes input body 94 . The rotation of the input member 94 is output from the second transmission unit 54 to the output member 84 or from the second transmission unit 54 and the first transmission unit 52A to the output member 84 .

The switching unit 56 changes the rotational state of at least one of the first transmission unit 52A and the second transmission unit 54 to switch the transmission path S of the rotation input to the first transmission unit 52A and the second transmission unit 54 into one. The transmission path S is switched to another transmission path S.

In this embodiment, the first shift path L1 further has a third path L13. In at least one of the first transmission path S1 and the third transmission path S3, the switching unit 56 switches from one of the first transmission path L1 including the second path L12 and the first transmission path L1 including the third path L13 to the other. configured to switch to In each of the first transmission path S1 and the third transmission path S3, the gear ratio when the first gear path L1 includes the third path L13 is the gear ratio when the first gear path L1 includes the second path L12. Greater than ratio. The third path L13 passes through a first sun gear 62 of the at least three first sun gears 62 that is different from the first sun gears 62 that pass through in the first path L11 and the second path L12. In this embodiment, the third path L13 passes through the first sun gear 62C.

Table 3 shows the transmission path S at each shift stage formed by the transmission 50 of this embodiment. The gear ratio in each gear stage is the first gear stage, the second gear stage, the third gear stage, the fourth gear stage, the fifth gear stage, the sixth gear stage, the seventh gear stage, and the eighth gear stage. increase in order.

In the present embodiment, the switching unit 56 switches from one of the first transmission path L1 including the first path L11 and the first transmission path L1 including the second path L12 in the first transmission path S1 and the third transmission path S3. configured to switch to the other. In the present embodiment, when switching from one of the second gear stage and the third gear stage to the other of the second gear stage and the third gear stage, the switching unit 56 switches to the first gear shift path including the first path L11. It is configured to switch the transmission path S from one side to the other side of the first shift path L1 including L1 and the second path L12. In the present embodiment, when switching from one of the sixth shift stage and the seventh shift stage to the other of the sixth shift stage and the seventh shift stage, the switching unit 56 switches the first shift path including the first path L11. It is configured to switch the transmission path S from one side to the other side of the first shift path L1 including L1 and the second path L12.

In the present embodiment, the switching unit 56 switches from one of the first transmission path L1 including the second path L12 and the first transmission path L1 including the third path L13 in the first transmission path S1 and the third transmission path S3. configured to switch to the other. In the present embodiment, when switching from one of the third gear stage and the fourth gear stage to the other of the third gear stage and the fourth gear stage, the switching unit 56 switches to the first gear shift path including the second path L12. It is configured to switch the transmission path S from one side to the other side of the first shift path L1 including L1 and the third path L13. In the present embodiment, when switching from one of the seventh gear stage and the eighth gear stage to the other of the seventh gear stage and the eighth gear stage, the switching unit 56 switches to the first gear shift path including the second path L12. It is configured to switch the transmission path S from one side to the other side of the first shift path L1 including L1 and the third path L13.

Preferably, the gear ratio of the first transmission unit 52 in the first transmission path S1 corresponding to the gear ratio that is one step smaller than the gear ratio of the second transmission path S2 is smaller than the gear ratio of the second transmission path S2. In this embodiment, the gear ratio of the first planetary gear unit 60 via the first sun gear 62C is smaller than the gear ratio of the second planetary gear unit 70 via the second sun gear 72 .

The first gear path L1 has a plurality of paths with different gear ratios. When the transmission path S passes through the first shift path L1, the switching unit 56 switches between the first shift path L1 including one of the plurality of paths and the first shift path L1 including the other one of the plurality of paths. It is configured to switch the transmission path from one of the transmission paths L1 to the other. When the switching unit 56 increases the gear ratio in stages, the gear shift step formed by the transmission path S passing through the first gear path L1 including the path forming the first gear ratio among the plurality of paths, A transmission path that does not pass through the first shift path L1 between the shift stages formed by the transmission path S that passes through the first shift path L1 that forms a gear ratio that is smaller than the first gear ratio of the plurality of paths. , including the gearshift stage formed by S. Preferably, the path forming the first gear ratio among the plurality of paths corresponds to the path capable of forming the largest gear ratio among the plurality of paths. Preferably, the path forming a gear ratio smaller than the first gear ratio among the plurality of paths corresponds to the path capable of forming the smallest gear ratio among the plurality of paths. In this embodiment, the route forming the first speed ratio among the plurality of routes corresponds to the third route L13, and the route forming the speed ratio smaller than the first speed ratio among the plurality of routes corresponds to the third route L13. It corresponds to 1 route L11. In this embodiment, the shift stage formed by the transmission path S via the first shift path L1 including the path forming the first gear ratio among the plurality of paths corresponds to the fourth shift stage. The gear stage formed by the transmission path S via the first gear path L1 forming a gear ratio smaller than the first gear ratio of the plurality of paths corresponds to the sixth gear gear stage. The shift stage formed by the transmission path S not via the first shift path L1 corresponds to the sixth shift stage.

The switching portion 56 has a claw member 96 , an arm member 104 and a biasing member 100 . The pawl member 96 further has a fourth pawl member arranged between the outer peripheral portion of the shaft member 58 and the inner peripheral portion of the first sun gear 62C.

Arm member 104 shown in FIG. 17 is provided on the outer peripheral portion of shaft member 58 so as to be rotatable with respect to shaft member 58 . The arm member 104 has a base portion 104A, a first arm 104B, a second arm 104C, a third arm 104D and a fourth arm 104E. The base portion 104A extends in the axial direction of the shaft member 58 .

The switching section 56 has a first switching section 56A, a second switching section 56B, and a third switching section 56C. The first switching portion 56A includes a first claw member 96A and a first arm 104B. The second switching portion 56B includes a second claw member 96B and a second arm 104C. The third switching portion 56C includes a third claw member 96C and a third arm 104D. The fourth switching portion 56D includes a fourth claw member and a fourth arm 104E.

The first arm 104B presses the first pawl member 96A against the shaft member 58 to form the second state. In the first state, the first pawl member 96A does not engage with the recess 102 provided in the inner peripheral portion of the first sun gear 62A and allows the rotation of the first sun gear 62A with respect to the shaft member 58 . In the second state, the first pawl member 96A engages with a concave portion 102 provided in the inner peripheral portion of the first sun gear 62A to restrict rotation of the first sun gear 62A with respect to the shaft member 58 .

The second arm 104C presses the second pawl member 96B against the shaft member 58 to form the second state. In the first state, the second pawl member 96B does not engage with the recess 102 provided in the inner peripheral portion of the first sun gear 62B and allows the rotation of the first sun gear 62B with respect to the shaft member 58 . In the second state, the second pawl member 96B engages with a recess 102 provided in the inner peripheral portion of the first sun gear 62B to restrict rotation of the first sun gear 62B with respect to the shaft member 58 .

The third arm 104D presses the third pawl member 96C against the shaft member 58 to form the second state. In the first state, the third pawl member 96</b>C does not engage with the recessed portion 102 provided in the inner peripheral portion of the second sun gear 72 and allows the rotation of the second sun gear 72 with respect to the shaft member 58 . In the second state, the second pawl member 96B engages with a concave portion 102 provided in the inner peripheral portion of the second sun gear 72 to restrict rotation of the second sun gear 72 with respect to the shaft member 58 .

The fourth arm 104E presses the fourth pawl member against the shaft member 58 to form the second state. In the first state, the fourth pawl member does not engage with the concave portion 102 provided in the inner peripheral portion of the first sun gear 62C and allows rotation of the first sun gear 62C with respect to the shaft member 58 . In the second state, the fourth pawl member engages with the concave portion 102 provided in the inner peripheral portion of the first sun gear 62C to restrict rotation of the first sun gear 62C with respect to the shaft member 58 .

The first arm 104B, the second arm 104C, the third arm 104D, and the fourth arm 104E are configured such that the corresponding pawl member 96 is in the first state or the second state at the rotational phase Q with respect to the shaft member 58. be done. In this embodiment, the rotation phase Q of the arm member 104 with respect to the shaft member 58 includes a first rotation phase Q1, a second rotation phase Q2, a third rotation phase Q3, a fourth rotation phase Q4, a fifth rotation phase Q5, a It has 6 rotation phases Q6, 7th rotation phase Q7, and 8th rotation phase Q8. When the rotational phase Q is the first rotational phase Q1, the transmission 50A forms the first gear stage. When the rotational phase Q is the second rotational phase Q2, the transmission 50A forms the second gear stage. When the rotational phase Q is the third rotational phase Q3, the transmission 50A forms the third gear stage. When the rotational phase Q is the fourth rotational phase Q4, the transmission 50A forms the fourth gear stage. When the rotational phase Q is the fifth rotational phase Q5, the transmission 50A forms the fifth gear stage. When the rotational phase Q is the sixth rotational phase Q6, the transmission 50A forms the sixth gear stage. When the rotational phase Q is the seventh rotational phase Q7, the transmission 50A forms the seventh gear stage. When the rotational phase Q is the eighth rotational phase Q8, the transmission 50A forms the eighth gear stage.

The switching unit 56 is configured such that the transmission path S passes through one of the at least two first sun gears 62 by changing the rotational state of the first sun gears 62 . A first path L11 passes through one of the at least two first sun gears 62, and a second path L12 passes through the first sun gears 62 in the first path L11 of the at least two first sun gears 62. via a different one. For example, the first path L11 goes through the first sun gear 62A, the second path L12 goes through the first sun gear 62B, and the third path L13 goes through the first sun gear 62C. The switching unit 56 sets the first claw member 96A to the second state, the second claw member 96B to the first state, and the fourth claw member to the first state, whereby the transmission path S is changed to the first sun gear 62A. make it go through The switching unit 56 sets the first claw member 96A to the first state, the second claw member 96B to the second state, and the fourth claw member to the first state, whereby the transmission path S is changed to the first sun gear 62B. make it go through The switching unit 56 sets the first claw member 96A to the first state, the second claw member 96B to the first state, and the fourth claw member to the second state, whereby the transmission path S is changed to the first sun gear 62C. make it go through

The switching unit 56 changes the rotational state of at least one second sun gear 72 when increasing the gear ratio in stages and when switching the transmission path S from the first transmission path S1 to the second transmission path S2. After that, the rotation state of the at least two first sun gears 62 is changed. The second arm 104C is configured such that the state of the fourth pawl member is in the second state between the fourth rotation phase Q4 and the fifth rotation phase Q5, and the first arm 104B is configured to be in the fifth rotation phase Q5. In phase R5, the state of the first claw member 96A is configured to be the first state.

Table 4 shows the rotational states of the first sun gear 62A, the first sun gear 62B, the first sun gear 62C, and the second sun gear 72 in each transmission stage formed by the arm member 104 of this embodiment. .

In the fourth transmission path S4 shown in FIG. 18, the rotation of the second carrier 78 rotates the first carrier 68 via the first one-way clutch 82, and the rotation of the first carrier 68 rotates the second ring via the transmission portion 80. Gear 74 is rotated. Both the first sun gear 62 and the second sun gear 72 are allowed to rotate relative to the shaft member 58 in the fourth transmission path S4. Therefore, the rotation input from the input member 94 to the first transmission unit 52 is output to the output member 84 via the third one-way clutch 88 without being changed.

In the first transmission path S1 shown in FIGS. 19, 20 and 21, the rotation of the second carrier 78 rotates the first carrier 68 via the first one-way clutch 82, and in the third transmission path S3, the Rotation of the second ring gear 74 rotates the first carrier 68 via the transmission section 80 .

In the first transmission path S1, the second sun gear 72 is allowed to rotate with respect to the shaft member 58. Therefore, the rotation input from the input body 94 to the first transmission unit 52 is not changed, and the first one-way clutch 82 is rotated. input to the second transmission unit 54 via the

In the first transmission path S1 shown in FIG. 19, the rotation input to the second transmission unit 54 is accelerated by a gear ratio corresponding to the number of teeth of the first sun gear 62A whose rotation is restricted, and the second one-way clutch 86 to output 84 . In the first transmission path S<b>1 , the second ring gear 74 rotates the first carrier 68 via the transmission portion 80 .

In the first transmission path S1 shown in FIG. 20, the rotation input to the second transmission unit 54 is accelerated by a gear ratio corresponding to the number of teeth of the first sun gear 62B whose rotation is restricted, and the second one-way clutch 86 to output 84 . In the first transmission path S<b>1 , the second ring gear 74 rotates the first carrier 68 via the transmission portion 80 .

In the first transmission path S1 shown in FIG. 21, the rotation input to the second transmission unit 54 is accelerated by a gear ratio corresponding to the number of teeth of the first sun gear 62C whose rotation is restricted, and the second one-way clutch 86 to output 84 . In the first transmission path S<b>1 , the second ring gear 74 rotates the first carrier 68 via the transmission portion 80 .

In the second transmission path S2 shown in FIG. 22, the rotation of the second sun gear 72 with respect to the shaft member 58 is restricted, so that the rotation input from the input body 94 to the first transmission unit 52 is accelerated to the third transmission path S2. It is output to the output member 84 via the one-way clutch 88 . Since all the first sun gears 62 are allowed to rotate with respect to the shaft member 58 on the second transmission path S2, the rotation of the output member 84 is not transmitted to the first transmission unit 52 by the second one-way clutch 86.

As shown in FIG. 10, in the first transmission path S1 shown in FIG. 21, the rotation of the second sun gear 72 with respect to the shaft member 58 is allowed, so that the rotation of the first carrier 68 rotates the second ring gear 74. Let Since the rotational speeds of the first carrier 68 and the second ring gear 74 are lower than the rotational speeds of the first ring gear 64 and the output body 84 , the relative rotation between the second ring gear 74 and the output body 84 is controlled by the third one-way clutch 88 . is allowed.

In the state of FIG. 10, the switching unit 56 changes the state in which the rotation of the second sun gear 72 with respect to the shaft member 58 is permitted to the state in which the rotation with respect to the shaft member 58 is restricted. The rotation speed becomes higher than the rotation speed of the first carrier 68 . Therefore, the convex portion 80B moves relative to the concave portion 80A, and the second ring gear 74 and the first carrier 68 start to rotate relative to each other. In this state, since the gear ratio of the first transmission unit 52 when passing through the first sun gear 62C is smaller than the gear ratio of the second transmission unit 54 when passing through the second sun gear 72, the second ring The rotation speed of gear 74 is faster than the rotation speed of first ring gear 64 . Therefore, the rotation of the second ring gear 74 rotates the output member 84 by the third one-way clutch 88 , and the relative rotation between the first ring gear 64 and the output member 84 is permitted by the second one-way clutch 86 . In this state, the switching unit 56 changes the state in which rotation of the first sun gear 62C with respect to the shaft member 58 is restricted to a state in which the rotation is permitted. Since the relative rotation between the first ring gear 64 and the output body 84 is permitted, the rotational state of the first sun gear 62C can be changed favorably when the load on the first sun gear 62A is small.

As shown in FIG. 11, when the convex portion 80B reaches the opposite end in the rotational direction within the concave portion 80A, the rotation of the second ring gear 74 causes the first carrier 68 to rotate. Therefore, the rotation of the second carrier 78 is not transmitted to the first carrier 68 by the first one-way clutch 82 in the second transmission path S2 shown in FIG.

In the third transmission path S3 shown in FIG. 23, the rotation of the second sun gear 72 with respect to the shaft member 58 is restricted, so that the rotation input from the input member 94 to the first transmission unit 52 is accelerated and It is input to the second transmission unit 54 via 80 . The rotation input to the second transmission unit 54 is accelerated by a transmission ratio corresponding to the number of teeth of the first sun gear 62A whose rotation is restricted, and is output to the output body 84 via the second one-way clutch 86. .

In the third transmission path S3 shown in FIG. 24, the rotation of the second sun gear 72 with respect to the shaft member 58 is restricted, so that the rotation input from the input body 94 to the first transmission unit 52 is accelerated and It is input to the second transmission unit 54 via 80 . The rotation input to the second transmission unit 54 is accelerated by a transmission ratio corresponding to the number of teeth of the first sun gear 62B whose rotation is restricted, and is output to the output body 84 via the second one-way clutch 86. .

In the third transmission path S3 shown in FIG. 25, the rotation of the second sun gear 72 with respect to the shaft member 58 is restricted, so that the rotation input from the input member 94 to the first transmission unit 52 is accelerated and It is input to the second transmission unit 54 via 80 . The rotation input to the second transmission unit 54 is accelerated by a transmission ratio corresponding to the number of teeth of the first sun gear 62C whose rotation is restricted, and is output to the output body 84 via the second one-way clutch 86. .

<Modification>
The description of the embodiment is an example of the form that the transmission for a manpowered vehicle and the assist system for a manpowered vehicle provided with this transmission according to the present invention can take, and is not intended to limit the form. A transmission for a manpowered vehicle according to the present invention and an assist system for a manpowered vehicle provided with this transmission can be combined, for example, with the variants of the embodiments shown below and at least two variants not contradicting each other. can take the form of In the following modified examples, the same reference numerals as in the embodiment are given to the parts that are common to the embodiment, and the description thereof is omitted.

- The first sun gears 62 may include four or more first sun gears 62 . In this case, the switching section 56 is provided for all first sun gears 62 .

- The second transmission unit 54 may be provided with a transmission other than a planetary gear mechanism instead of or in addition to the second planetary gear unit 70 . The transmission, for example, the second transmission unit 54 includes a manual transmission and a continuously variable transmission.

- The second planetary gear unit 70 may include two or more second sun gears 72 . In this case, preferably, the switching unit 56 is configured to restrict rotation of the second sun gear 72 included in the second planetary gear unit 70 with respect to zero or one shaft member 58 in each speed change step. .

- The transmission 50 may be configured to change the speed of the rotation input to the crankshaft 12A and transmit the rotation to the first rotating body 24 . In this case, the transmission 50 may be provided on the crankshaft 12A.

- The transmissions 50 and 50A may be used in the manpowered vehicle 10 that does not include the motor 42 .

As used herein, the phrase "at least one" means "one or more" of the desired option. As an example, the phrase "at least one" as used herein means "only one option" or "both of the two options" if the number of options is two. As another example, the expression "at least one" used herein means "only one option" or "any combination of two or more options" if the number of options is three or more. means.

DESCRIPTION OF SYMBOLS 10... Human-powered vehicle, 40... Assist system, 42... Motor, 44... Operation part, 50, 50A... Transmission, 52, 52A... First transmission unit, 60, 60A... First planetary gear unit, 62, 62A, 62B, 62C... first sun gear, 64... first ring gear, 66, 66A, 66B, 66D... first planetary gear, 68... first carrier, 54... second transmission unit, 70... second planetary gear unit, 72... Second sun gear 74... Second ring gear 76... Second planetary gear 78... Second carrier 56... Switching part 80... Transmission part 80A... Concave part 80B... Convex part 82... First One-way clutch 84 Output member 86 Second one-way clutch 88 Third one-way clutch 90 Hub.

Claims (15)

A transmission for a human powered vehicle, comprising:
a first transmission unit having a first transmission path for shifting input rotation;
a second transmission unit having a second transmission path for shifting input rotation and configured to transmit rotation to the first transmission unit;
a switching unit that changes the gear ratio of the manpowered vehicle step by step,
The first transmission unit has a first planetary gear unit,
The switching unit switches a transmission path of rotation input to the first transmission unit and the second transmission unit by changing a rotational state of at least one of the first transmission unit and the second transmission unit,
The transmission path includes at least a first transmission path that passes through the first shift path, a second transmission path that passes through the second shift path and does not pass through the first shift path, the first shift path and the a third transmission path that passes through both of the second transmission paths;
The switching unit switches the transmission path in order of the first transmission path, the second transmission path, and the third transmission path when increasing the gear ratio in stages. The first shift path has a first path and a second path,
In at least one of the first transmission path and the third transmission path, the switching portion switches from one of the first transmission path including the first path and the first transmission path including the second path to the other. configured to switch to
In each of the first transmission path and the third transmission path, the transmission gear ratio when the second transmission path is included in the first transmission path is the same as that when the first transmission path is included in the first transmission path. 2. Transmission according to claim 1, greater than said transmission ratio. Said first planetary gear unit comprises at least two first sun gears, at least one first ring gear, at least two first planetary gears respectively engaging said at least two first sun gears, and corresponding said a first carrier supporting the at least two first planetary gears for movement about a first sun gear;
The switching unit is configured to change the rotation state of the at least two first sun gears so that the transmission path passes through one of the at least two first sun gears,
the first path is via one of the at least two first sun gears;
3. The transmission of claim 2, wherein said second path traverses a different one of said at least two first sun gears than said first sun gear traversed in said first path. The first shift path further has a third path,
In at least one of the first transmission path and the third transmission path, the switching portion switches from one of the first transmission path including the second path and the first transmission path including the third path to the other. configured to switch to
In each of the first transmission path and the third transmission path, the transmission gear ratio when the third transmission path is included in the first transmission path is the same as that when the second transmission path is included in the first transmission path. 3. Transmission according to claim 2, greater than said transmission ratio. The first shift path further has a third path,
In at least one of the first transmission path and the third transmission path, the switching portion switches from one of the first transmission path including the second path and the first transmission path including the third path to the other. configured to switch to
In each of the first transmission path and the third transmission path, the transmission gear ratio when the third transmission path is included in the first transmission path is the same as that when the second transmission path is included in the first transmission path. larger than the gear ratio,
said first planetary gear unit having at least three said first sun gears;
4. The method of claim 3, wherein the third path traverses a first sun gear of at least three first sun gears that is different from the first sun gears traversed in the first path and the second path. gearbox. The transmission path further has a fourth transmission path that transmits the input rotation without speed change,
The switching unit switches the transmission path in order of the fourth transmission path, the first transmission path, the second transmission path, and the third transmission path when increasing the gear ratio in stages. A transmission according to any one of claims 1 to 5. The second transmission unit has a second planetary gear unit,
Said second planetary gear unit comprises at least one second sun gear, at least one second ring gear, at least one second planetary gear engaging said at least one second sun gear, and said at least one a second carrier supporting the second planetary gear for movement around a second sun gear;
the switching unit is configured to change the rotational state of the at least one second sun gear so that the transmission path passes through one of the at least one second sun gears;
The first carrier and the second ring gear are connected by a transmission section,
the first carrier and the second carrier are connected by a first one-way clutch;
In the first transmission path, rotation of the second carrier rotates the first carrier via the first one-way clutch,
The transmission according to claim 3 or 5, wherein in said third transmission path, rotation of said second ring gear rotates said first carrier via said transmission portion. The transmission path further has a fourth transmission path that transmits the input rotation without speed change,
In the fourth transmission path, rotation of the second carrier rotates the first carrier via the first one-way clutch, and rotation of the first carrier rotates the second ring gear via the transmission section. 8. The transmission according to claim 7, allowing The switching unit changes the rotation state of the at least one second sun gear when increasing the gear ratio stepwise and when switching the transmission path from the first transmission path to the second transmission path. 8. Transmission according to claim 7, configured to change the rotational state of the at least two first sun gears after changing. The transmitting portion includes one of a concave portion and a convex portion provided on one of the outer peripheral portion of the first carrier and the inner peripheral portion of the second ring gear, and the inner peripheral portion of the first carrier and the second ring gear. Including the other of the concave portion and the convex portion provided on the other of the peripheral portions,
The transmission according to claim 9, wherein the circumferential length of the recess is greater than the circumferential length of the projection. further comprising an output body, a second one-way clutch, and a third one-way clutch;
The first ring gear is connected to the output body via the second one-way clutch,
The transmission according to any one of claims 7 to 10, wherein said second ring gear is connected to said output body via said third one-way clutch. A transmission for a human powered vehicle, comprising:
a first transmission unit having a first transmission path for shifting input rotation;
a second transmission unit having a second transmission path for shifting input rotation and configured to transmit rotation to the first transmission unit;
a switching unit that changes the gear ratio of the manpowered vehicle step by step,
The first transmission unit has a first planetary gear unit,
the first gear shift path has a plurality of paths with different gear ratios,
The switching unit is
changing a rotational state of at least one of the first transmission unit and the second transmission unit to switch a transmission path of the rotation input to the first transmission unit and the second transmission unit;
When the transmission path passes through the first shift path, the first shift path including one of the plurality of paths and the first shift path including the other one of the plurality of paths configured to switch the transmission path from one to the other of
When increasing the gear ratio stepwise, a gear shift step formed by a transmission path passing through a first gear shift path including a path forming the first gear ratio among the plurality of paths, and Between the shift stage formed by the transmission path passing through the first shift path including the path forming the gear ratio smaller than the first gear ratio, the transmission path formed by the transmission path not passing through the first gear shift path gearbox, including gearshift stages that The transmission according to any one of claims 1 to 12, further comprising a hub that accommodates the first transmission unit, the second transmission unit, and the switching section. An assist system for a human-powered vehicle, comprising:
A transmission according to any one of claims 1 to 13;
An assist system comprising: a motor for assisting human driving force. further comprising an operation unit that is manually operated to operate the transmission;
15. The assist system according to claim 14, wherein the transmission changes the transmission gear ratio of the manpowered vehicle according to the operation of the operation unit.