JP3439888B2 - Powered bicycle braking device - Google Patents

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 freewheel in which the rotational force is transmitted to the drive wheels only in the positive rotation only when it is driven by the pedal and the positive rotation force of the drive wheels 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.

[0010] The braking device for a power with a bicycle of the present invention, self
The hub body of the rear wheel or front wheel of the rolling car is rotatably supported.
On the same axis as the hub axle fixed to the bicycle and inside
The hub shaft is arranged so as to penetrate therethrough, and
And an output member driven by
Provided adjacent to the hub axle in the axial direction and coaxial with the hub axle
And so that the hub axle penetrates inside
And a deceleration output member that decelerates the rotation of the output member.
A first reduction mechanism that transmits to a deceleration output member, and the hub body
Drive member for rotationally driving a vehicle, and the first reduction mechanism
Is provided adjacent to the hub shaft in the axial direction,
Deceleration The rotation of the output member is decelerated and transmitted to the drive member.
Between the second reduction mechanism and the drive member and the hub body
The hub is interposed so that the drive member rotates only in one direction.
A first one-way clutch for transmission to the body, and the drive member
It is interposed between the hub body and the hub body to rotate the hub body.
And a clutch for transmitting to the drive member .

In addition, in the braking device for the above-mentioned powered bicycle,
The first one-way clutch is transmitted to the clutch.
Rotation of the hub body in the same direction as the rotation direction of the drive member
Second one-way clutch that transmits only rolling to the drive member
Is preferred.

In addition, in the braking device for the above-mentioned powered bicycle,
The forced transmission of rotation of the second one-way clutch
It is preferable to have a clutch releasing means for disconnecting.

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. The outer periphery of the three planetary formic Ya 15, first ring gear 20 is disposed. 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 the hub shaft 1
It will be connected and fixed so that it cannot rotate relative to.

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 24 , 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.
Are 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.
Is 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. 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.
Is equipped with. The claw 61 of the clutch 60 has slits 6 arranged at two positions at 180 degrees intervals on the second ring gear 45.
Are arranged in two (see Fig. 2). The claw 61 has a shaft hole 6
3 is formed. A claw pin 64 is inserted in the shaft hole 63 . The claw pin 64 is inserted into a claw pin hole 65 formed in the second ring gear 45.

The pawl pin 64 is stopped by the annular pawl pinning spring 66 so as not to escape from the pawl 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 around 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. Conversely, when the pawl 61 and the ratchet teeth 5 2 are engaged drive hub body 30 is transmitted from the ratchet teeth 52 on the pawl 61, eventually to drive 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 Embodiment) Next, the operation of the above embodiment will be described. As can be understood from the above description, the first pinion 14, which outputs the rotation of the electric motor, the planetary gear 15, the revolving rotary arm 17, and the fixed first inner peripheral teeth 40 constitute a planetary gear mechanism,
It forms 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. Conversely, when the pawl 61 and the ratchet teeth 5 2 are engaged drive hub body 30 is transmitted from the ratchet teeth 5 2 the pawl 61, eventually to drive the rotor of the electric motor Dynamic braking. Other Embodiments In the above embodiment, 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 axle 12 ... Motor output shaft 17 ... Gear frame 20 ... 1st ring gear 15 ... Planetary gear 30 ... Hub body 41 ... Second pinion 50 ... One-way clutch 51 ... nails 70 ... Clutch release cam

─────────────────────────────────────────────────── ─── Continuation of front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) B62M 23/02

Claims (3)

(57) [Claims] 1. Hub body (30) for a rear wheel or a front wheel of a bicycle
Hub axle fixed to the bicycle to rotatably support
The hub axle (1) penetrates inside and coaxially with (1).
Output, driven by an electric motor.
A force member (23) and an axial direction of the hub axle (1) with respect to the output member (23)
Direction adjacent to each other, coaxial with the hub axle (1),
One is arranged so that the hub axle (1) penetrates inside
And a deceleration output member (17) for decelerating the rotation of the output member (23).
A first reduction mechanism that transmits to the material (17) and a driving member (4) for rotationally driving the hub body (30).
5) and the axial direction of the hub axle (1) with respect to the first reduction mechanism
Rotation of the deceleration output member (17) provided adjacent to the
Second deceleration for decelerating and transmitting to the drive member (45)
A mechanism between the drive member (45) and the hub body (30).
And the drive member (45) is rotated only in one direction.
The first one-way clutch (5) transmitted to the hub body (30).
0) and between the drive member (45) and the hub body (30).
And rotating the hub body (30) to rotate the drive member (4).
5) A braking device for a motorized bicycle having a clutch (60) for transmission to . 2. The braking of the powered bicycle according to claim 1.
The device comprises a first one-way clutch (50) for transmitting the clutch.
Of the drive member (45) in the same direction as the rotation direction of the drive member (45).
Only the rotation of the body (30) is transmitted to the drive member (45).
A second one-way clutch (60) for braking a powered bicycle. 3. The braking of the powered bicycle according to claim 2.
A device for forcing rotation transmission of the second one-way clutch (60)
A braking device for a power-operated bicycle, which has a clutch releasing means (70) for disconnecting it .