JPH0966881A - Braking device of motor assisted bicycle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To transmit the rotation of an electric motor, regardless of pedal operation to perform dynamic braking. SOLUTION: A first pinion 14, a planetary gear 15, a revolved gear frame 17 and fixed first internal teeth 40 form a planetary gear mechanism and form a first speed reducing mechanism. The output of a speed reduced electric motor rotatively drives a second pinion 41. The rotation speed of the second pinion 41 is reduced by second internal teeth 44. The speed reduced rotation drives a hub body 30 rotatively through a one-way clutch 50 to transmit only the power of the electric motor to a front wheel. A clutch mechanism 60 transmits or releases the drive from the hub body 30 to the electric motor, thereby performing and releasing dynamic braking.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a braking device for a powered bicycle. More specifically, the present invention relates to a braking device for a powered bicycle including a clutch mechanism for driving a rotor of an electric motor that drives a rear wheel or a front wheel of the bicycle to perform dynamic braking.

[0002]

2. Description of the Related Art There is known a powered bicycle having a battery loaded with an electric motor. Bicycles are powered by the power of people pedaling.
A powered bicycle is a bicycle equipped with a drive mechanism to assist a person in rowing. Various drive devices for this powered bicycle have been proposed. Among these, a hub in which a DC motor is incorporated is also known (Japanese Patent Laid-Open No. 53-93515).
No. 6-506891).

On the other hand, in the rear hub of a chain-powered bicycle, a free wheel in which the rotational force is transmitted to the drive wheel only in the positive rotation only when it is driven by the pedal and the positive rotation force of the drive wheel is not transmitted to the pedal is used. I have it. The freewheel has a function of transmitting only one direction of rotational force, that is, a one-way clutch mechanism.

Since the front hub normally does not have this freewheel mechanism, when an electric motor is incorporated in the front hub or an electric motor is mounted on a front fork or the like to drive the front wheels, the electric motor is operated when the electric motor is not operating. Even the rotor of the motor is pedal-driven, which causes a problem of heavy pedal operation.

Further, since a powered bicycle is equipped with an electric motor and a battery, its body is heavier than a normal bicycle. Therefore, if a braking device that is normally used in a bicycle is installed, a powered bicycle has a problem that the braking performance does not match. The present invention solves these problems of powered bicycles.

[0006]

The present invention has been made based on the above technical background, and achieves the following objects.

An object of the present invention is to provide a braking device for braking by utilizing a dynamic braking function of an electric motor for driving a bicycle.

Another object of the present invention is to provide a braking device for a powered bicycle equipped with a clutch mechanism so as to turn on / off the dynamic braking of an electric motor.

[0009]

In order to solve the above problems, the present invention adopts the following means.

In the braking device for a power-assisted bicycle of the present invention, the rotation output of the output shaft of the electric motor is transmitted to the hub body of the hub of the rear wheel or the front wheel of the bicycle to drive the rear wheel or the front wheel. Which is interposed between the hub body and the output shaft, and transmits rotation from the rear wheels or the front wheels to rotation of the rear wheels or the front wheels to a rotor of the electric motor. And means for performing dynamic braking.

Also, in the braking device for a power-assisted bicycle of the present invention, the rotational output of the output shaft of the electric motor is transmitted to the hub body of the hub of the rear wheel or the front wheel of the bicycle to drive the rear wheel or the front wheel. A drive device for an attached bicycle, comprising: a clutch that is interposed between the hub body and the output shaft and that transmits a rotation from the rear wheel or the front wheel to a rotor of the electric motor for power braking. It is a thing.

It is preferable that the clutch includes a first one-way clutch for transmitting the rotation output of the electric motor to the hub body to output the rotation. Further, the clutch may include a second one-way clutch for transmitting the rotation from the rear wheel or the front wheel to the rotor of the electric motor.

The second one-way clutch selects either one of two positions: transmission of rotation from the rear wheel or front wheel to the rotor of the electric motor for dynamic braking, or interruption of transmission to neutral. A one-way clutch that can be selected at one time has the effect of enabling finer control.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view of a front hub of a bicycle according to an embodiment of the present invention. The hub shaft 1 is a hollow shaft, and male threads 2 and 3 are formed at both ends thereof.
A nut 7 is screwed into the male screws 2 and 3, and the claw 6 of the front fork 5 is inserted to fix the claw 6 to the hub axle 1.

An electric motor (not shown) is fixed to the front fork 5 outside the hub body 30. The rotation from the output shaft of the electric motor drives the timing pulley 29 via the timing belt 19. Timing pulley 29
Are fixed to the drive disk 23 by serrations 25 and thus cannot rotate relative to each other. A first pinion 14 is integrally formed at the other end of the drive disc 23.

The first pinion 14 meshes with the planet gear 15. The drive disk 23 is made up of steel balls 28 and the hub body 3
It is rotatably supported at 0. Drive disk 23 at the same time
Is rotatably supported by a steel ball 24a that rolls on a ball push 24 that is screwed into and fixed to the hub axle 1.

A planetary gear 15 meshes with the first pinion 14. Three planetary gears 15 are arranged at equal angular positions on the outer circumference of the first pinion 14. The shaft 16 of the planetary gear 15 is supported by the bearing portion 18 of the gear frame 17, and the planetary gear 15 is rotatably supported by the shaft 16.

Therefore, the gear frame 17 has a substantially annular shape, has a space for supporting the three planetary gears 15, and is rotatably arranged around the hub shaft 1. Become. A first ring gear 20 is arranged on the outer periphery of the three planetary gears 15. A spline hole 21 is formed at the center of the first ring gear 20. The spline hole 21 meshes with a spline shaft 22 formed on the hub shaft 1. After all, the first ring gear 20 is fixedly connected to the hub shaft 1 so as not to rotate relative to the hub shaft 1.

A rolling surface 32 is formed on the other end of the hub body 30. A steel ball 33 is rolling on the rolling surface 32.
Since the steel balls 33 are also rolling on the rolling surface 35 of the ball pushing member 34 at the same time, they constitute a bearing.
The hub body 30 is integrally provided with two flanges 37 in parallel. The collar 37 is fixed by hooking one end of a spoke (not shown) in the spoke hole 38.

After all, the steel balls 28, 33 are the ball pushers 25, 3
4 and the hub body 30 are rotatably supported with respect to each other. The planet gears 15 mesh with the first inner peripheral teeth 40, which are annular internal gears formed on the first ring gear 20. The first ring gear 20 includes three second pinions 41.
Is arranged. The shaft 42 of the second pinion 41 has the first
The second pinion 41 is supported on the shaft 42 by being supported by the ring gear 20.
Are rotatably supported.

The second pinion 41 meshes with the outer peripheral teeth 43 provided on the gear frame 17. At the same time, the second pinion 41 meshes with the second inner peripheral teeth 44 of the second ring gear 45. Since the second pinion 41 does not revolve, it is rotated by the outer peripheral teeth 43 due to the revolution of the gear frame 17. Due to the rotation of the second pinion 41, the second ring gear 45 is rotationally driven via the second inner peripheral teeth 44.

As shown in detail in FIG. 2, a one-way clutch 50, that is, a ratchet mechanism is arranged on the outer periphery of the second ring gear 45. FIG. 3 is a detailed sectional view showing the engagement of the one-way clutch. The claws 51 of the one-way clutch 50 mesh with the ratchet teeth 52 formed on the inner peripheral surface of the hub body 30.

The pawl 51 is formed with a spring locking portion 54. A circular spring 53 is engaged with this spring locking portion 54,
It is tightened by spring force toward the center. That is, the ratchet teeth 52 are engaged with each other because they are always urged in the rising direction. Two types of nails 51 are prepared in total. The other type is the one in which the spring locking portion 54 is arranged on the opposite side of the claw 51 (see FIG. 2).

Other types of pawls 51 are arranged at an angle. 180 degrees angle with these two types of nails 51,
Two claws 51 of the same type are arranged in the same direction. After all,
A total of four claws 51 are arranged. This is to prevent the strength from being insufficient even if the transmission torque increases due to the transmission of the power of the electric motor.

Since the one-way clutch 50 has a function of transmitting only a one-way rotational force, that is, a one-way clutch mechanism, only the power of the electric motor can be transmitted to the wheels. The freewheel has a function of transmitting only one direction of rotational force, that is, a one-way clutch mechanism. If the one-way clutch 50 is not provided, when the electric motor is stopped, the rotor of the electric motor is also driven and the pedal becomes heavy. Further, there is an advantage that the moment of inertia of the rotor can be cut off during braking.

The one-way clutch 50 cannot be stopped or released. In the present embodiment, the clutch 60 is further added.
It has. The claw 61 of the clutch 60 has slits 6 arranged at two positions at 180 degrees intervals on the second ring gear 45.
Two are arranged (see FIG. 2). A shaft hole 65 is formed in the claw 61. The claw pin 64 is inserted into the shaft hole 65. The claw pin 64 is inserted into a claw pin hole 65 formed in the second ring gear 45.

The claw bin 64 is fixed by an annular claw pin stop spring 66 so as not to come off from the claw pin hole 65. The claw 61 is biased by a claw spring 67 which is a coil spring,
It always meshes with the ratchet teeth 52. On the other hand, a clutch release cam 70 is provided on the spline shaft 22 of the hub shaft 1 so as to be movable in the axial direction. The clutch release cam 70 is constantly urged by the coil spring 71 in the axial direction of the hub shaft 1.

As shown in FIG. 5, a claw contact surface 72 is formed on the side surface of the clutch releasing cam 70 at an angle θ, which is about 40 ° (contact surface C) in this example. Claw contact surface 7
2, two contact surfaces A, B and C are formed. The angles θ of the contact surfaces A, B, C differ depending on the outer peripheral angular position.
Since the contact surfaces A, B, and C have different inclination angles θ, when the clutch release cam 70 is driven to contact the claw 61, the wedge force varies depending on the contact position.

Therefore, the bell crank mechanism 80 (described later) makes the lever operation smooth when the lever is operated. Further, the pawl 61 has a contact surface 68, and when the clutch release cam 70 comes into contact with the contact surface 68, the pawl 61 is swung about the pawl pin 64, and the pawl 61 and the ratchet teeth 52 mesh with each other. Is released.

The clutch release cam 70 has a semi-circular pin hole 73 formed therein, and the pin 75 is inserted through the hub shaft 1 in the pin hole 73. Therefore, the clutch release cam 70 and the hub shaft 1 are separated from each other. They are connected together. The pin 75 is inserted into a key hole 74 pierced in the hub shaft 1 in the diameter direction, and can move within the key hole 74 by a predetermined distance.
A push rod 76 is provided in the center hole of the hub axle 1 so as to be movable in the axial direction. After all, push rod 76
Is connected to the clutch release cam 70.

The other end of the push rod 76 is connected to the bell crank mechanism 80. Bell crank mechanism 80
The inner crank 82 driven by the clutch control wire 83 drives the bell crank 81 to drive the push rod 76. This bell crank mechanism 8
The structure of 0 is well known and its description is omitted. Eventually, when the push rod 76 is driven by the clutch control wire 83, the push rod 76 is driven in the axial direction to drive the clutch pawl release cam 70, and the pawl contact surface 72 thereof.
Contacts the contact surface 68 of the pawl 61 to release the engagement between the pawl 61 and the ratchet teeth 52.

By releasing this, the electric motor drive system can be disconnected, so that driving like a normal bicycle becomes possible. On the contrary, when the claw 61 and the ratchet tooth 51 are engaged with each other, the drive of the hub body 30 is transmitted from the ratchet tooth 52 to the claw 61 and finally drives the rotor of the electric motor.

As can be understood from the above description, the rotation of the first pinion 14, which is the output of the electric motor, causes the planetary gear 1 to rotate.
5, the revolving gear frame 17, and the first inner peripheral teeth 40, which are fixed ring gears, constitute a planetary gear mechanism and a differential gear mechanism. In other words, the first reduction mechanism that reduces the rotation of the first pinion 14, which is the output rotation of the electric motor, is configured.

The output of the first reduction gear mechanism is output as the rotation of the outer peripheral teeth 43 of the gear frame 17. The output of the decelerated electric motor rotationally drives the second pinion 41. The second pinion 41 rotationally drives the second inner peripheral teeth 44, which is a ring gear. Since the number of teeth of the second pinion 41 is smaller than the number of teeth of the second inner peripheral teeth 44, the speed is further reduced here. This planetary gear mechanism does not constitute a differential gear mechanism but constitutes a second reduction gear mechanism.

The decelerated rotation rotationally drives the hub body 30 via the one-way clutch 50.

(Operation of the Embodiment) Next, the operation of the above embodiment will be described. As can be seen from the above description,
The first pinion 14, the planetary gear 15, the revolving rotary arm 17, and the fixed first inner peripheral teeth 40 of the output shaft 12 of the electric motor constitute a planetary gear mechanism and a differential gear mechanism.
In other words, the first reduction mechanism that reduces the rotation of the first pinion 14, which is the output rotation of the electric motor, is configured.

The output of the first reduction mechanism is output as the rotation of the outer peripheral teeth 43 of the rotary arm 17. The output of the decelerated electric motor rotationally drives the second pinion 41. The second pinion 41 drives the second inner peripheral teeth 44 to rotate. Since the number of teeth of the second pinion 41 is smaller than the number of teeth of the second inner peripheral teeth 44, the speed is further reduced here.

This planetary gear mechanism does not constitute a differential gear mechanism but constitutes a second reduction mechanism. The decelerated rotation rotationally drives the hub body 30 via the one-way clutch 50. The one-way clutch 50 can transmit only the power of the electric motor to the wheels even when the pedal is stopped.

When the push rod 76 is driven by the clutch control wire 83, the push rod 76 is driven in the axial direction to drive the clutch pawl release cam 70,
The claw contact surface 72 comes into contact with the contact surface 68 of the claw 61, and the claw 6
The engagement between 1 and the ratchet teeth 52 is released.

By releasing this, it can be separated from the drive system of the electric motor, so that operation by pedal operation like a normal bicycle becomes possible. On the contrary, when the pawl 61 and the ratchet tooth 51 are engaged with each other, the drive of the hub body 30 is transmitted from the ratchet tooth 51 to the pawl 61, and finally the rotor of the electric motor is driven, so that the dynamic braking is performed. To do. (Other Embodiments) In the above embodiments, the electric motor was mounted on the front fork, but it may be mounted on the hub or mounted on the handle stem, for example. You may arrange | position in another position like this.

[0041]

As described above in detail, the present invention is effective in braking because electric braking is performed by an electric motor. Also,
Since the clutch mechanism is incorporated, the dynamic braking can also be released. Furthermore, the power of the electric motor can be transmitted to the wheels regardless of pedal operation.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a hub showing an embodiment of the present invention.

2A and 2B are cross-sectional views showing details of a second ring gear.

FIG. 3 is a cross-sectional view showing the engagement between a pawl and a ratchet pawl.

FIG. 4 (a), (b), (c) is a diagram showing details of a clutch claw.

5 (a), (b), and (c) are diagrams showing details of a clutch release cam.

[Explanation of symbols]

 1 ... Hub shaft 12 ... Motor output shaft 17 ... Gear frame 20 ... First ring gear 15 ... Planetary gear 30 ... Hub body 41 ... Second pinion 50 ... One-way clutch 51 ... Claw 70 ... Clutch release cam

Claims (5)

[Claims] 1. A drive device for a powered bicycle, wherein a rotational output of an output shaft of an electric motor is transmitted to a hub body of a hub of a rear wheel or a front wheel of a bicycle to drive the rear wheel or the front wheel. A means interposed between the body and the output shaft for transmitting rotation from the rear wheel or the front wheel to rotation from the rear wheel or the front wheel to a rotor of the electric motor for dynamic braking. A braking device for a powered bicycle, which is characterized in that 2. A drive device for a powered bicycle, wherein a rotational output of an output shaft of an electric motor is transmitted to a hub body of a hub of a rear wheel or a front wheel of a bicycle to drive the rear wheel or the front wheel. Braking of a power-assisted bicycle including a clutch interposed between a body and the output shaft, the clutch transmitting the rotation from the rear wheel or the front wheel to the rotor of the electric motor to perform dynamic braking. apparatus. 3. The braking device for a powered bicycle according to claim 2, further comprising a first one-way clutch for transmitting the rotation output of the electric motor to the hub body to output the rotation. 4. The powered clutch according to claim 2 or 3, wherein the clutch is a second one-way clutch for transmitting rotation from the rear wheels or the front wheels to a rotor of the electric motor. Bicycle braking device. 5. The two-position clutch according to claim 4, wherein the second one-way clutch transmits rotation from the rear wheel or the front wheel to a rotor of the electric motor to perform dynamic braking, or cuts off the transmission to be in a neutral position. A braking device for a power-assisted bicycle, which is a one-way clutch capable of selectively selecting any one of the above.