JPH08244673A - Auxiliary power assisted bicycle - Google Patents

Abstract

(57) [Abstract] [Purpose] To simplify the flow of parts involved in manufacturing and assembling an electric motor and a planetary roller reduction mechanism, and to reduce the cost and manufacturing time of the auxiliary power assist device. Further, the auxiliary power assist device is reduced in size and weight, and at the same time, the reverse rotation preventing capacity of the reverse rotation preventing means for preventing reverse rotation of the electric motor is sufficiently secured. According to the auxiliary power assisted bicycle of the present invention, a main shaft 66 of an electric motor 61 and a sun roller 71 of a planetary roller reduction mechanism 70 are axially supported on the same axis line so that both members 66, 71 are integrally rotated and separated. The bearing 73 is connected to the connecting portion 71a at the same position in the vehicle width direction with respect to the connecting portion 71a. On the other hand, a one-way clutch 84, which is a reverse rotation preventing means, is arranged between the electric motor 61 and the reduction gear train G in the vehicle width direction.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention mounts an auxiliary power assist device having an electric motor built into a bicycle body, and assists human power with the auxiliary power of the electric motor to travel uphill or while receiving a headwind. A power assisted bicycle that facilitates

[0002]

2. Description of the Related Art FIG. 7 is a cross-sectional view showing one structural example of such an auxiliary power assist device. The auxiliary power assist device 200 includes a crankshaft 201 that extends in the vehicle width direction and is rotationally driven in the rotational direction indicated by arrow A by the pedal effort.
Is supported, and a differential device 202 is provided coaxially with the crankshaft 201.

The differential device 202 includes, for example, a bevel gear-shaped human power input gear 203 and an auxiliary power input gear 204, and one to two pairs of planetary gears 205, which mesh with these both input gears 203, 204.
206 and a differential carrier 207 that rotatably holds the planetary gears 205 and 206.
A drive sprocket 208 is integrally provided on the 7 for rotation.

The human power input gear 203 is integrally rotated with the crankshaft 201, and the auxiliary power input gear 204 is the clutch sleeve 2.
It can rotate around the crankshaft 201 together with 09. In addition, the differential carrier 207 has an auxiliary power input gear on one side.
It is rotatably supported around 204 and the other side is crankshaft 20
Since it is rotatably supported by 1, the crankshaft 201 can freely rotate around it.

An electric motor 211 is installed in the vicinity of the differential device 202 thus constructed.
The auxiliary power generated by 211 is reduced by the planetary roller reduction mechanism 212 and reduction gear train 213 and transmitted to the differential device 202.

The planetary roller speed reduction mechanism 212 includes an electric motor 21.
1, a ring roller 214 fixed to one side, and a few planetary rollers 215 contacting the inner peripheral surface of the ring roller 214,
The planetary roller 215 is supported by the deceleration carrier 216 that rotates while being supported by the electric motor 211.
A main shaft 217 of the is squeezed between the planet rollers 215 as a sun roller. The end of the deceleration carrier 216 on the side opposite to the electric motor 211 is supported by the bearing 218.

When the electric motor 211 operates, the main shaft 217 rotating in the direction indicated by the arrow B and the fixed ring roller
Each planetary roller 215 rotates between itself and the main shaft 217.
The rotation of the decelerating carrier 216 is revolved, and the deceleration carrier 216 is decelerated and driven in the B direction.

On the other hand, the reduction gear train 213 includes the reduction carrier 21.
6 Primary drive gear 219 that is integrally provided on one side of 6
A large diameter driven gear 220 that meshes with the primary drive gear 219, a small diameter secondary drive gear 221 rotatably integrated with the primary driven gear 220, and a secondary shaft that is rotatably supported by the crankshaft 201. Drive gear 221
And a secondary driven gear 222 that meshes with. The secondary driven gear 222 is connected to the clutch sleeve 209 and the differential device 202 by coupling the dog clutch 223.
It becomes integral with the auxiliary power input gear 204.

Primary driven gear 220 and secondary drive gear
221 is pivotally supported by a one-way clutch 225 on an intermediate shaft 224 that is installed in the vehicle width direction. This one-way clutch 225 is a reverse rotation preventing means for preventing the reverse rotation of the electric motor 211 by allowing only the primary driven gear 220 and the secondary drive gear 221 to rotate in the rotational direction indicated by the arrow C.

When the crankshaft 201 is rotated in the direction A by human power, the human power input gear 203 of the differential unit 202 moves to the crankshaft.
Rotate in the same direction as 201. When the electric motor 211 operates, its auxiliary power is reduced to the planetary roller reduction mechanism 212 and the reduction gear train 213 and transmitted to the clutch sleeve 209 and the auxiliary power input gear 204, and the auxiliary power input gear 204 also rotates in the A direction. To do.

Thus, both input gears 20 of the differential 202 are
Since 3,204 rotates in the A direction at the same time, planet gears 205,20
6 revolves around the crankshaft 201 in the A direction, whereby the differential carrier 207 rotates together with the drive sprocket 208 in the A direction around the crankshaft 201. Then, the drive sprocket 208 drives the drive wheel (rear wheel of the bicycle) via a chain (not shown). By using such a differential device 202, human power and auxiliary power can be smoothly combined,
The resultant force can be output to the drive wheel side.

According to this auxiliary power assist device 200,
It is also possible to drive the auxiliary power assisted bicycle by human power alone without operating the electric motor 211. In this case, when the crankshaft 201 is rotationally driven in the A direction by the pedal effort, the human power input gear 203 of the differential device 202 also rotates in the A direction, but the differential carrier 207 receives a load from the driving wheels. Therefore, the auxiliary power input gear 204 rotates in the direction opposite to the A direction to try to reverse the electric motor 211.

However, since the one-way clutch 225 prevents the electric motor 211 from rotating in the reverse direction, the reaction thereof drives the differential carrier 207 to rotate in the direction A at a speed half that of the manual input gear 203. Therefore, the rotation of the crankshaft 201 is reduced by half and transmitted to the drive sprocket 208. At this time, the pedaling force becomes very light, and therefore it becomes easy to drive only by human power.

[0014]

The deceleration carrier 216 of the planetary roller deceleration mechanism 212 is the anti-electric motor of the deceleration carrier 216.
The end on the 211 side is pivotally supported by the bearing 218, and the end on the electric motor 211 side is connected to the main shaft 2 of the electric motor 211 via the planetary roller 215.
It is supported coaxially with 17. Therefore, it is not necessary to support the end of the deceleration carrier 216 on the electric motor 211 side with a dedicated bearing, and by omitting the bearing in this way, the size of the auxiliary power assist device 200 in the vehicle width direction is made compact. .

However, this planetary roller reduction mechanism 21
In the assembly procedure of 2, first, the planetary roller 215 is decelerated and the deceleration carrier 21
This is complicated because it is assembled into the ring roller 214 together with the 6 and then the main shaft 217 of the electric motor 211 is press-fitted between the planetary rollers 215. The work must be done independently by the manufacturer of the planetary roller speed reducer 212.

In addition, in terms of press-fitting accuracy, the spindle 217 also has to be processed by the manufacturer of the planetary roller reduction mechanism 212. For this reason, the spindle 217 manufactured by the manufacturer of the planetary roller reduction mechanism 212 is once delivered to the manufacturer of the electric motor 211, and the assembled electric motor 211 is returned to the manufacturer of the planetary roller reduction mechanism 212 and the spindle 217 is replaced. Planetary roller
It becomes a procedure of press-fitting between 215, and the flow of parts becomes very complicated, resulting in a great increase in cost and loss of manufacturing time.

On the other hand, in the case of such an auxiliary power assisted bicycle, since the capacity of the battery as the power source of the electric motor 211 cannot be increased, it is difficult to increase the output of the electric motor 211. Therefore, it is necessary to increase the reduction ratio of the reduction gear train 213 as much as possible to obtain driving torque and compensate for the low output of the electric motor 211.

As described above, in order to increase the reduction ratio of the reduction gear train 213, it is desirable to increase the outer diameter of the primary driven gear 220 to increase the difference in the number of teeth from the secondary drive gear 221. In relation to primary driven gear 22
The outer diameter of 0 cannot be too large. Therefore, the outer diameter of the secondary drive gear 221 must be made as small as possible to widen the difference in the number of teeth between the two gears 220 and 221 and increase the reduction ratio.

However, since the one-way clutch 225 is provided between the secondary drive gear 221 and the intermediate shaft 224, there is a limit to the reduction of the diameter of the secondary drive gear 221, and as a compromise, the outside of the primary driven gear 220 is compromised. This was dealt with by increasing the diameter slightly, but if the outer diameter of the primary driven gear 220 is increased, the axial distance between the main shaft 217 of the electric motor 211 and the crankshaft 201 (intermediate shaft 224) will increase, and the auxiliary The power assist device 200 is inevitably increased in size and weight.

It is conceivable to reduce the outer diameter of the one-way clutch 225 to reduce the diameter of the secondary drive gear 221. However, if this is done, the reverse rotation prevention capacity of the one-way clutch 225 will decrease, and for example, the crankshaft 201 will have a strong force when traveling manually. There is a concern that the one-way clutch 225 will slip and reverse the electric motor 211 when a large pedaling force is applied.

The present invention has been made to solve the above-mentioned problems, and simplifies the flow of parts involved in the manufacture and assembly of the electric motor and the planetary roller speed reduction mechanism, thus reducing the cost of the auxiliary power assist device. It is an object of the present invention to provide an auxiliary power assist type bicycle that can reduce the manufacturing time.

Another object of the present invention is to reduce the size and weight of the auxiliary power assist device, and at the same time, to secure a sufficient reverse rotation preventing capacity of the reverse rotation preventing means for preventing reverse rotation of the electric motor.

A further object of the present invention is to detect the rotational speed and phase angle of the electric motor with high accuracy.

[0024]

In order to achieve the above object, an auxiliary power assist type bicycle according to the present invention has an auxiliary power assist device mounted on a vehicle body frame and a vehicle width as described in claim 1. A crankshaft that extends in the same direction and is driven to rotate by the pedal depression force is axially supported, and an electric motor that outputs auxiliary power to the crankshaft side and a planetary roller reduction mechanism that reduces the rotation of the electric motor are built-in. In an auxiliary power assist type bicycle in which the main shaft of the electric motor is axially supported in parallel with the crank shaft, the main shaft of the electric motor and the sun roller of the planetary roller speed reduction mechanism are axially supported on the same axis line to rotate both members integrally. In addition, the bearings are provided at the same position in the vehicle width direction with respect to the connecting portion.

Further, as described in claim 2, the auxiliary power assist device mounted on the vehicle body frame has the crankshaft rotatably driven by the pedaling force in the vehicle width direction, and the crankshaft side. It has a built-in electric motor that outputs auxiliary power, a reduction gear train that reduces the rotation of the electric motor, and reverse rotation prevention means that prevents reverse rotation of the electric motor.The main shaft of the electric motor is supported in parallel with the crankshaft. In the auxiliary power assisted bicycle, the reverse rotation preventing means is arranged between the electric motor and the reduction gear train in the vehicle width direction.

Further, as described in claim 3, the outer peripheral portion of the deceleration carrier of the planetary roller deceleration mechanism is provided with concavo-convex shapes at equal intervals, and the movement of the concavo-convex shape during rotation of the deceleration carrier is read by the sensor means. By doing so, the rotation speed and the phase angle of the electric motor are detected.

As described in claim 4, the concavo-convex shape is formed on the outer peripheral surface of the deceleration carrier, and the long axis direction of the sensor means is orthogonal to the outer peripheral surface of the deceleration carrier.

[0028]

According to the present invention, since the main shaft of the electric motor and the sun roller of the planetary roller reduction mechanism can be separated from each other, the main shaft of the electric motor can be used as the sun roller of the planetary roller reduction mechanism as in the prior art. There is no need to directly press fit between the planet rollers, and the electric motor and the planet roller reduction mechanism can be manufactured consistently by their respective manufacturers. It should be noted that no specialized technique is required when combining the electric motor and the planetary roller reduction mechanism.

According to the second aspect of the invention, the diameter of the gears can be reduced and the reverse rotation can be prevented as compared with the conventional case where the reverse rotation preventing means is provided at the central portion of the gears constituting the reduction gear train. It is possible to increase the diameter of the means.

On the other hand, in the case of the third aspect, the uneven shape provided on the outer peripheral portion of the decelerating carrier moves in the circumferential direction along with the rotation of the decelerating carrier, that is, the rotation of the electric motor. Is read by the sensor means to detect the rotation speed and the phase angle of the electric motor. In this case, the rotation speed and the phase angle of the electric motor can be accurately detected without expanding the size of the auxiliary power assist device in the vehicle width direction.

Further, in the case of the construction as claimed in claim 4,
Since the sensor means does not project in the vehicle width direction with respect to the deceleration carrier, the sensor means can be provided without expanding the dimension of the auxiliary power assist device in the vehicle width direction.

[0032]

An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a left side view of an auxiliary power assisted bicycle according to the present invention.

This auxiliary power assisted bicycle 1 is equipped with a parallel tube type vehicle body frame 2, and an auxiliary power assisting device 3 is mounted in the lower center part of the vehicle body frame 2.

A head pipe 4 is located at the front of the body frame 2, and an upper tube 5 and a lower tube 6 extend from the head pipe 4 in a diagonally rearward and downward direction. The middle portion of the upper tube 5 and the vicinity of the rear end portion of the lower tube 6 are connected by a bridge member 7, and the rear end portion of the upper tube 5 is joined to the lower end portion of a seat tube 8 provided at a steep angle via a seat lug 9. To be done.

A pair of left and right joint tubes 11 extend downward from the seat lug 9, the lower end of the joint tube 11 is opened left and right, and a pipe-shaped chain lug 12 extending in the vehicle width direction is fixed. There is. Then, from the chain lug 12, a pair of left and right chain stays 13
Extends rearward.

On the other hand, a pair of left and right seat stays 14 extends obliquely rearward and downward from the vicinity of the upper end of the seat tube 8, and the lower ends of these seat stays 14 are rear ends 15.
It is joined to the rear end of the chain stay 13 via.

Mounting brackets 16, 17, 18 are fixed to the rear end portion of the lower tube 6, the intermediate portion of the joint tube 11 and the lower portion of the chain lug 12, respectively. The auxiliary power assist device 3 is fixed by bolts. Therefore, the rear end portion of the lower tube 6 is connected to the chain lug 12 via the auxiliary power assist device 3, and the auxiliary power assist device 3 also serves as a structural member of the vehicle body frame 2.

A front fork 19 is pivotally supported on the head pipe 4 of the vehicle body frame 2 so as to be rotatable left and right, and a front wheel 20 is supported on a lower end portion of the front fork 19. A handlebar 22 is fixed to the upper part of the front fork 19 via a handle post 21, and further, a front fender 23 for covering the front wheels 20, a front brake 24 for braking the front wheels 24, and a basket 25 for loading luggage on the front forks 19. Etc. are integrally provided for rotation.

A rear wheel 26 is pivotally supported by the rear end 15 located at the rear end of the vehicle body frame 2, and a rear fender 27 covering the rear wheel 26 is provided with a chain stay 13 and a seat stay.
A rear brake 28 for braking the rear wheels is provided on the seat stay 14 and is fixed to the rear end 15 and the rear end 15. The rear end 15 has a stand device 29 for erecting the vehicle body when parking the bicycle.
Is provided.

A seat post 31 is inserted into and fixed to the seat tube 8 from above.
A saddle 32 is attached to the upper end of the. On the other hand, a crank shaft 33 extending in the vehicle width direction is rotatably supported by the auxiliary power assist device 3, and the crank 34 is provided at both ends of the crank shaft 33.
L and crank 34R are fixed, both cranks 34L, 34
A pedal 35 is rotatably provided at the tip of each R.

A drive sprocket 36 located on the right side of the auxiliary power assist device 3 is axially mounted on the crankshaft 33, and between the drive sprocket 36 and the driven sprocket 37 provided on the rear wheel 26. Chain 38
Is wrapped around.

The crankshaft 33 is driven in the rotational direction indicated by the arrow A when an occupant seated on the saddle 32 depresses the pedal 35 with his / her foot. At that time, the drive sprocket 36 rotates in the same direction as the crankshaft 33. This rotation is transmitted to the driven sprocket 37 by the chain 38 to drive the rear wheel 26.

A battery package 40 for operating an electric motor incorporated in the auxiliary power assist device 3 is fixed between the upper tube 5 and the lower tube 6 of the vehicle body frame 2. This battery package 40
Has a structure in which, for example, fifteen batteries 41 and a charger (not shown) are sealed in a battery case 42 made of synthetic resin. A control device 43 for controlling the output of the electric motor is attached to the lower portion of the lower tube 6.

FIG. 2 is a cross-sectional view of an auxiliary power assist device 3 showing an embodiment of the present invention, and FIG. 3 is a III-II line of FIG.
I is a left side view of the auxiliary power assist device 3 as viewed from the arrow.
Further, FIG. 4 is a conceptual diagram of the mechanism of the auxiliary power assist device 3.

The casing 45 forming the outer shell of the auxiliary power assist device 3 is made of, for example, an aluminum alloy, and as shown in FIG. 2, the left case half body 46 and the right case half body 47 have several bolts 48. The outer cover 49 is joined to the left side of the case half body 46 and fixed by several bolts 50. Note that FIG. 3 shows a state in which the outer cover 49 is removed.

The space between the left and right case halves 46, 47 is a partition wall.
A front side is an electric motor chamber 52, a rear side is a differential device chamber 53, and a space between the case half body 46 and the outer cover 49 is a reduction gear train chamber 54.

The crankshaft 33 is rotatably supported at the center of the differential gear chamber 53 by using bearings 56, 57 and 58, and the crank 34L is provided at both ends of the crankshaft 33 protruding left and right from the casing 45. And 34R are fixed with bolts 59. Also,
A sprocket boss 60 is rotatably mounted on the right side of the crankshaft 33, and the drive sprocket 36 is fixed to the sprocket boss 60 so as to rotate integrally therewith.

In the electric motor chamber 52, the above-mentioned electric motor 61 is provided.
Is installed. This electric motor 61 has its outer case
62 is fixed to the case half 46 side with bolts 63, and a main shaft 66 is rotatably supported by two bearings 64, 65 provided on the outer case 62. The main shaft 66 is parallel to the crankshaft 33, and the coil 67 is provided integrally with the crankshaft so as to rotate together. Also,
A magnet 68 surrounding the outer circumference of the coil 67 is fixed to the inner circumference of the outer case 62.

A planetary roller speed reduction mechanism 70 is provided on the left side of the electric motor 61. This planetary roller reduction mechanism 70
The sun roller 71 of the electric motor 61 has a shaft shape.
Is supported on the same axis as the main shaft 66 of. And the spindle
66 and the sun roller 71 are rotatably integrated and separably connected by a connecting portion 71a.

As shown in the enlarged view of FIG. 5, the structure of the connecting portion 71a is such that, for example, the right end portion of the sun roller 71 is expanded in a bowl shape to form an expanding portion 71b. While the spline 71c is engraved on the inner peripheral surface, a spline 66a is engraved on the left end outer periphery of the main shaft 66, and the spline 66a is configured to engage with the spline 71c of the expanded portion 71b.

The left end of the sun roller 71 is pivotally supported by a bearing 72 provided on the outer cover 49 side, and the right end is pivotally supported by a bearing 73 provided on the case half body 46 side. Here, the bearing 73 is located at the same position in the vehicle width direction with respect to the connecting portion 71a, that is, the sun roller 71.
It is provided so as to hold the outer circumference of the expanded portion 71b.
The bearing 64 on the electric motor 61 side is also arranged near the connecting portion 71a.

Ring roller 74 of planetary roller reduction mechanism 70
Is fixed to the case half body 46 side with bolts 75, and a reduction carrier 76 is rotatably supported around the sun roller 71 via a bearing 77 on the left side of the ring roller 74. The deceleration carrier 76 is provided with four roller shafts 78 parallel to the sun roller 71, and planet rollers 79 are rotatably supported on the roller shafts 78, respectively.

At the time of assembling the planetary roller reduction mechanism 70, the sun roller 71 is press-fitted between the four planetary rollers 79.
The outer peripheral surface of each planetary roller 79 is pressed against the inner peripheral surface of the ring roller 74 and the outer peripheral surface of the sun roller 71. A primary drive gear 81 is rotatably provided on the left side surface of the reduction carrier 76.

When the main shaft 66 of the electric motor 61 rotates, the sun roller 71 also rotates integrally, and each planet roller 79 rotates while rotating between the fixed ring roller 74 and the rotating sun roller 71. Revolving around, the deceleration carrier 76 is driven to decelerate and rotate. Sun roller 71 is the main shaft
Together with 66, it rotates in the direction indicated by arrow B, and the primary drive gear 81 also rotates in the same direction.

Incidentally, FIG. 6 shows a second embodiment in the connecting portion between the main shaft of the electric motor 61 and the sun roller of the planetary roller reduction mechanism 70. In the structure of the connecting portion 71B, for example, the spline 71C is engraved on the outer periphery of the right end of the sun roller 71A, while the left end portion of the main shaft 66A is formed in a bowl shape so that the bowl portion 66B is formed.
Is formed, and the spline 71C of the sun roller 71A is engaged with the spline 66C engraved on the inner peripheral surface of the main shaft 66A.
The sun roller 71A and the sun roller 71A are connected so as to rotate together.

The left end of the main shaft 66A is supported by a bearing 64A, and the bearing 64A is provided at the same position in the vehicle width direction with respect to the connecting portion 71B, that is, here, to hold the outer periphery of the bowl portion 66B. There is. Since the bearing 64A also serves as the right end bearing of the sun roller 71A, the number of bearings is reduced and the size in the vehicle width direction is reduced.

An intermediate shaft 82 is installed between the planetary roller speed reduction mechanism 70 and the crankshaft 33. The intermediate shaft 82 is rotatably supported by a bearing 83 provided on the outer cover 49 side and a one-way clutch 84 provided on the case half body 46 side, and has a large diameter driven gear 85 that meshes with the primary drive gear 81. A small-diameter secondary drive gear 86 located inside the primary driven gear 85 is integrally provided for rotation.

The crankshaft 33 has a secondary driven gear.
87 is rotatably supported by the crankshaft 33 so as to mesh with the secondary drive gear 86. The secondary driven gear 87 constitutes a reduction gear train G together with the primary drive gear 81, the primary driven gear 85, and the secondary drive gear 86.

In the one-way clutch 84, the intermediate shaft 82 together with the primary driven gear 85 and the secondary drive gear 86 is indicated by an arrow C.
This allows the electric motor 61 to rotate only in the direction indicated by, and thereby serves as a reverse rotation preventing means for preventing reverse rotation of the electric motor 61. The one-way clutch 84 is arranged between the electric motor 61 and the reduction gear train G in the vehicle width direction.

A differential device is installed in the differential device chamber 53.
88 will be installed. The differential device 88 is a device that combines the rotational force (pedal pedal force) of the crankshaft 33 and the auxiliary power of the electric motor 61 and outputs the resultant force to the rear wheel 26 side that is the drive wheel. As shown in FIGS. 2 to 4, the differential device 88 is arranged coaxially with the crankshaft 33, and is configured as follows.

First, a human power input gear 89 is axially mounted on the crankshaft 33 via a one-way clutch 90. The one-way clutch 90 causes the human power input gear 89 to rotate integrally with the crank shaft 33 when the crank shaft 33 is rotating in the A direction, and cuts off the rotational input to the human power input gear 89 when the crank shaft 33 reverses. This is a clutch mechanism that prevents reverse rotation of the gear 89.

An auxiliary power input gear 91 is rotatably supported by the crankshaft 33 on the left side of the human power input gear 89. The number of teeth of the auxiliary power input gear 91 is set to be the same as the number of teeth of the human power input gear 89.

A differential carrier 92 is rotatably provided around the crankshaft 33. It should be noted that in FIG. 4, in order to make the structure of the differential device 88 as a whole easy to understand,
92 is written in a simplified bar shape.

In this differential carrier 92, a left carrier half body 92L and a right carrier half body 92R are assembled with bolts 93. The carrier half body 92L is an auxiliary power input gear.
The boss 91a of 91 is rotatably supported on the outer periphery of the boss 91a, and the carrier half body 92R is integrally connected to the sprocket boss 60.

On the differential carrier 92, a pair of first planetary gears 95 meshing with the human power input gear 89 and a pair of second planetary gears 96 meshing with the auxiliary power input gear 91 are rotatably held by a shaft 97. The first planetary gear 95 and the second planetary gear 96 mesh with each other. Both planetary gears 95, 96
The number of teeth is set to the same.

In this embodiment, the first planetary gear 95 and the second planetary gear 96 are supported by the differential carrier 92 in pairs.
For example, two or more pairs may be provided. Since the gears 89, 91, 95, 96 incorporated in the differential device 88 are all spur gears, the differential device 88 is very easy to manufacture.

The boss 91a of the auxiliary power input gear 91 extends toward the secondary driven gear 87, and the boss of the secondary driven gear 87 is
87a extends to the auxiliary power input gear 91 side. Splines 99 and 100 are engraved on the outer circumferences of both of these bosses 87a and 91a, and a sleeve member 101 that engages with the splines 99 and 100 by splines connects the secondary driven gear 87 and the auxiliary power input gear 91 in a rotationally integrated manner. As a result, the rotation of the reduction gear train G is transmitted to the differential device 88.

The sleeve member 101 can be moved in the axial direction of the crankshaft 33 by the moving mechanism 102 shown in FIGS. 2 and 3, and when the sleeve member 100 moves to the differential device 88 side, the reduction gear train 99 is formed. Is disconnected from the differential device 88.

When the auxiliary power assisted bicycle 1 is running, the pedaling force applied to the crankshaft 33 causes a differential device.
Since the human power input gear 89 of 88 is rotationally driven in the A direction, the auxiliary power input gear 91 of the differential device 88 is also rotationally driven in the A direction by the auxiliary power of the electric motor 61. Therefore, both gears 89, 91 are simultaneously driven. The rotation causes the first and second planetary gears 95 and 96 to revolve around the crankshaft 33 in the A direction. Therefore, the differential carrier 92 is rotationally driven in the direction A together with the drive sprocket 36, and the rear wheel 26 is driven via the chain 38.

The difference in rotational speed between the human power input gear 89 and the auxiliary power input gear 91 is absorbed by the rotation of the first and second planetary gears 95 and 96 (differential of the differential device 88). Therefore, the human power and the auxiliary power are always smoothly combined. Then, the combined force of human power and auxiliary power is efficiently output to the rear wheel 26 side,
The pedal effort of the 35 is greatly reduced, making it extremely easy to run uphill and while receiving head wind. When the crankshaft 33 is rotated in the reverse direction, the one-way clutch 90 acts to prevent the manual input gear 89 from rotating in the reverse direction.

By the way, on the outer peripheral portion (outer peripheral surface) of the decelerating carrier 76 of the planetary roller decelerating mechanism 70, the uneven shapes 103 are provided at equal intervals, and the sensor means 104 makes the major axis direction the outer periphery of the decelerating carrier 76. The casing 45 is provided so as to be orthogonal to the plane. The sensor means 104 is fixed to the case half body 46 with, for example, two bolts 105.

Along with the operation of the electric motor 61, the deceleration carrier
When the 76 rotates, the movement of the uneven shape 103 formed on the outer peripheral surface of the deceleration carrier 76 is read by the sensor means 104, and the rotation speed and the phase angle of the electric motor 61 are detected and input to the control device 43.

On the other hand, a ring-shaped sensor plate 107 is rotatably provided on the inner surface of the drive sprocket 36, and the sensor plate 107 is provided with projections 108 standing on the casing 45 side at equal intervals over the entire circumference. It is projected in. The casing 45 is provided with the sensor means 109. The sensor means 109 is fixed to the case half body 47 side with a bolt 110 so that the long axis direction thereof is orthogonal to the portion of the protrusion 108 of the sensor plate 107.

When the sensor plate 107 rotates together with the drive sprocket 36, the movement of the protrusion 108 formed on the sensor plate 107 is read by the sensor means 108, and the rotation speed and the phase angle of the drive sprocket 36 are detected and the control device 43 is operated. Entered in.

The control device 43 detects the rotation speed and the phase angle of the electric motor 61 and the drive sprocket 36 based on the inputs from the sensor means 104 and the sensor means 109. For example, the auxiliary power of the electric motor 61 is always equal to the pedal effort. In other words, the output of the electric motor 61 is controlled so that there is no difference in rotational speed between the human power input gear 89 and the auxiliary power input gear 91 of the differential device 88.

When the auxiliary power assist type bicycle 1 is run only by human power without operating the electric motor 61, when the crankshaft 33 is rotationally driven in the direction A by the pedal effort,
The human power input gear 89 of the differential device 88 also rotates in the A direction, but since the load from the rear wheel 26 is applied to the differential carrier 92, the auxiliary power input gear 91 rotates in the anti-A direction and the electric motor 61.
Try to reverse. However, the one-way clutch 84
Since the reverse rotation of the electric motor 61 is prevented by the reaction, the differential carrier 92 is rotationally driven in the A direction at the speed of half the speed of the human power input gear 89 by the reaction, and the rotation of the crankshaft 33 is reduced to half. It is decelerated and transmitted to the drive sprocket 36.

In the present invention, the main shaft 66 of the electric motor 61 and the sun roller 71 of the planetary roller speed reduction mechanism 70 are axially supported on the same axis line so that the two members 66, 71 are rotatably integrated and separably connected.
Since the bearing 73 is provided at the same position in the vehicle width direction with respect to the connecting portion 71a, there is no need to directly press-fit the main shaft of the electric motor between the planet rollers of the planet roller reduction mechanism as in the conventional case.

Therefore, the electric motor 61 and the planetary roller reduction mechanism 70 can be manufactured consistently by their respective manufacturers, and the flow of parts involved in the manufacture and assembly of the electric motor 61 and the planetary roller reduction mechanism 70 can be reduced. Since it is extremely simplified, the cost and manufacturing time of the auxiliary power assist device 3 can be reduced.

The electric motor 61 and the planetary roller reduction mechanism
No special technique is required for combining the electric motor 61 and the planetary roller speed reduction mechanism 70 in the assembled state in the case half body 46.

Further, in the present invention, the one-way clutch 84, which is a reverse rotation preventing means of the electric motor 61, is arranged between the electric motor 61 and the reduction gear train G in the vehicle width direction, so that the reduction gear train is constructed as in the conventional case. It is possible to reduce the diameter of the gears (85, 86) and simultaneously increase the diameter of the one-way clutch 84, as compared with the case where a reverse rotation prevention device is provided at the center of the gears such as the primary driven gear 85 and the secondary drive gear 86. .

For this reason, the distance between the main shaft 66 of the electric motor 61 and the crankshaft 33 is shortened to reduce the size and weight of the auxiliary power assist device 3, and the reverse rotation preventing capacity of the one-way clutch 84, which is the reverse rotation preventing means. Can be sufficiently secured.

Further, according to the present invention, the planetary roller speed reduction mechanism is used.
The deceleration carrier 76 of 70 is provided with irregularities 103 at equal intervals on the outer periphery thereof, and the movement of the irregularity 103 during rotation of the deceleration carrier 76 is read by the sensor means 104 so that the electric motor
Since the rotation speed and phase angle of 61 are detected,
The rotation speed and the phase angle of the electric motor 61 can be accurately detected without expanding the dimension of the auxiliary power assist device 3 in the vehicle width direction.

That is, for example, as compared with the case where a disc-shaped sensor plate is separately provided on the main shaft 66 of the electric motor 61 and the irregular movements formed at equal intervals on the outer peripheral portion of the sensor plate are read by the sensor means. Since the sensor plate itself is unnecessary, the total length of the main shaft 66 can be shortened, and the dimension of the auxiliary power assist device 3 in the vehicle width direction can be kept compact.

Further, for example, when the sensor means is provided on the outer peripheral portion of the gears constituting the reduction gear train G and the sensor means is made to read the movement of the unevenness of the tooth portion of the gears, the gears are The sensor means is apt to cause misreading because the tooth depth of the tooth is shallow.
If the uneven shape 103 is formed on the outer peripheral portion of the 76, the uneven shape 103
Since a large depth can be taken, the reading accuracy of the sensor means 104 can be improved (misreading can be avoided).

Further, in the present invention, since the concave-convex shape 103 is formed on the outer peripheral surface of the deceleration carrier 76 and the major axis direction of the sensor means 104 is made orthogonal to the outer peripheral surface of the deceleration carrier 76, the sensor means 104 is decelerated. In contrast, the sensor means 104 can be provided without projecting in the vehicle width direction without expanding the dimension of the auxiliary power assist device 3 in the vehicle width direction. Therefore, it is possible to further contribute to downsizing of the auxiliary power assist device 3.

[0086]

As described above, in the auxiliary power assisted bicycle according to the present invention, the main shaft of the electric motor and the sun roller of the planetary roller reduction mechanism are pivotally supported on the same axis and both members are integrally rotated. Since they are separably connected and the bearings are provided at the same position in the vehicle width direction with respect to the connecting portions, the electric motor and the planetary roller reduction mechanism can be manufactured consistently by their respective manufacturers. Therefore, the flow of parts involved in manufacturing and assembling the electric motor and the planetary roller reduction mechanism can be simplified, and the cost and manufacturing time of the auxiliary power assist device can be reduced.

Further, in the auxiliary power assisted bicycle according to the present invention, since the reverse rotation preventing means is arranged between the electric motor and the reduction gear train in the vehicle width direction, the gears constituting the reduction gear train are made smaller in diameter and assisted. The size and weight of the power assist device can be reduced, and at the same time, the reverse rotation preventing means can be increased in diameter to sufficiently secure the reverse rotation prevention capacity.

Furthermore, in the auxiliary power assisted bicycle according to the present invention, the outer peripheral portion of the deceleration carrier of the planetary roller deceleration mechanism is provided with irregular shapes at equal intervals, and the movement of the irregular shape during rotation of the deceleration carrier is detected by the sensor means. Since the rotation speed and the phase angle of the electric motor are detected by reading, the rotation speed and the phase angle of the electric motor can be accurately detected without expanding the dimension of the auxiliary power assist device in the vehicle width direction.

Further, in the auxiliary power assisted bicycle according to the present invention, since the uneven shape is formed on the outer peripheral surface of the deceleration carrier and the major axis direction of the sensor means is orthogonal to the outer peripheral surface of the deceleration carrier, the auxiliary Sensor means can be provided without expanding the dimension of the power assist device in the vehicle width direction,
This can further contribute to downsizing of the auxiliary power assist device.

[Brief description of drawings]

FIG. 1 is a left side view of an auxiliary power assist type bicycle according to the present invention.

FIG. 2 is a cross-sectional view of an auxiliary power assist device showing an embodiment of the present invention.

3 is a left side view of the auxiliary power assist device taken along the line III-III of FIG.

FIG. 4 is a conceptual diagram of a mechanism of an auxiliary power assist device.

FIG. 5 is an enlarged view showing a first embodiment of a connecting portion between a main shaft of an electric motor and a sun roller of a planetary roller reduction mechanism.

FIG. 6 is an enlarged view showing a second embodiment in a connecting portion between a main shaft of an electric motor and a sun roller of a planetary roller reduction mechanism.

FIG. 7 is a cross-sectional view of an auxiliary power assist device showing a conventional technique.

[Explanation of symbols]

 1 Auxiliary power assist type bicycle 2 Body frame 3 Auxiliary power assist device 33 Crankshaft 61 Electric motor 66 Main shaft of electric motor 70 Planetary roller speed reduction mechanism 71 Sun roller 73 Bearing 76 Speed reduction carrier 84 One-way clutch 103 as reverse rotation prevention means 103 Uneven shape 104 Sensor means G Reduction gear train

Front page continuation (72) Inventor Tadashi Matsuura 300, Takatsuka-cho, Hamamatsu-shi, Shizuoka Suzuki Stock Company

Claims (4)

[Claims] 1. A power-assisting device mounted on a vehicle body frame supports a crankshaft extending in the vehicle width direction and rotationally driven by pedaling force, and an electric motor that outputs auxiliary power to the crankshaft side. In an auxiliary power assisted bicycle in which a motor and a planetary roller speed reduction mechanism that reduces the rotation of the electric motor are built-in, and the main shaft of the electric motor is supported in parallel with the crankshaft, the main shaft of the electric motor and the planetary roller speed reduction Auxiliary power, characterized in that the sun roller of the mechanism is pivotally supported on the same axis and both members are connected so as to be rotatable integrally and separably, and a bearing is provided at the same position in the vehicle width direction with respect to the connecting portion Assisted bicycle. 2. An auxiliary power assist device mounted on a vehicle body frame, wherein a crankshaft rotatably driven by pedaling force is axially supported in the vehicle width direction, and an electric motor for outputting auxiliary power to the crankshaft side. In the auxiliary power assist type bicycle in which a reduction gear train for reducing the rotation of the electric motor and a reverse rotation preventing means for preventing the reverse rotation of the electric motor are built in, and the main shaft of the electric motor is axially supported in parallel with the crankshaft. An auxiliary power assisted bicycle characterized in that reverse rotation preventing means is arranged between the electric motor and the reduction gear train in the vehicle width direction. 3. The rotation speed and phase of the electric motor are provided by equipping the outer peripheral portion of the deceleration carrier of the planetary roller deceleration mechanism with irregularities at equal intervals, and reading the movement of the irregularities when the deceleration carrier is rotated by a sensor means. The auxiliary power assisted bicycle according to claim 1, wherein a corner is detected. 4. The auxiliary power assisted bicycle according to claim 3, wherein the concavo-convex shape is formed on the outer peripheral surface of the speed reducing carrier, and the long axis direction of the sensor means is orthogonal to the outer peripheral surface of the speed reducing carrier.