JP3177887B2 - Speed change bicycle - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a speed change bicycle.

[0002]

2. Description of the Related Art There are many types of bicycles driven and driven by human power, depending on various shapes, dimensional finishes and the like. Basically, a frame, front and rear wheels pivotally supported by the frame, a crankshaft that rotates with the pressing force applied to the pedal,
And an endless chain for transmitting the torque of the crankshaft to the hub of the rear wheel. Also, a plurality of rear chain gears having about 3 to 5 different diameters are provided on the end side of the hub body of the rear wheel. The chain is hung,
A speed change mechanism that switches the endless chain to a rear chain gear of an arbitrary diameter on the hub body side in a laterally moving manner and adjusts the speed by shifting the band is generally used. In this transmission mechanism, the endless chain is moved to an arbitrary rear chain gear by operating a gear shift lever provided on the frame during traveling, and while changing the gear ratio of the front and rear chain gears, various factors such as ups and downs of a road, wind direction, leg force, etc. are changed. The gear shifting operation is being performed according to the conditions.

[0003]

However, in the above-mentioned transmission mechanism, a mechanism for laterally moving a plurality of rear chain gears or endless chains provided on a hub body of a rear wheel to an arbitrary rear chain gear has a bulky shape. However, there is a drawback that these components become excessive loads and require a large driving rotational force. In addition, when the endless chain is decelerated and switched to any rear chain gear having a different diameter in a lateral movement, the end chain is detached from the rear chain gear, and it is easy to cause a failure. There is a disadvantage that requires. Further, there is a problem that the work of attaching to the hub body is troublesome because the transmission mechanism is large and heavy.

The present invention has been made in view of the above-mentioned conventional problems, and one object of the present invention is to provide a deceleration mechanism in which a mechanism for deceleration is structurally simple and the entire mechanism is reduced in size. It is an object of the present invention to provide a speed change switching bicycle capable of reducing the weight of a portion and reducing a load. Further, another object of the present invention is to be able to drive and rotate with a small force without applying an extra load to the drive rotation of the crankshaft,
It is an object of the present invention to provide a speed change bicycle that can easily run for a long time. Another object of the present invention is to provide a speed changeover bicycle that hardly causes a failure or the like during deceleration switching operation and requires no cost or time for maintenance. Still another object of the present invention is to provide a speed change-over bicycle in which the mechanism for deceleration is reduced in size and the work of mounting on a crankshaft can be easily performed.

[0005]

SUMMARY OF THE INVENTION The present invention is directed to a crankshaft 14 rotatably supported by a hanger portion 12 of a bicycle and being inputted and rotating, a speed reducing means 16 interlocked with the crankshaft 14, a decelerating state. Switching means 18 and this deceleration means 1
And a transmission mechanism 22 for transmitting the rotational force to the wheel hub body 20.
4, comprising a differential gear mechanism 44 including at least one or a plurality of planetary gears 40 rotating by receiving the driving force of 4, and at least one driven gear 42 rotating while meshing with the planetary gears 40, The speed changeover bicycle 10 is characterized in that deceleration / non-deceleration operation is performed while switching the planetary motion of the planetary gear 40 of the differential gear mechanism 44 by the switching means 18.

The differential gear mechanism 44 includes the driven gear 42 and one or a plurality of planetary gears 4 that engage with the driven gear 42 on both sides of the driven gear 42.
0, of which the planetary gear 40 on one side is provided so as to be interlocked with the crankshaft 14.

The driven gear 4 of the differential gear mechanism 44
2 may be formed in a substantially Z-shaped cross section.

Further, the switching means 18 includes a clutch portion 82 for connecting or disconnecting the driven gear 42 and the crankshaft 14 and a pivot shaft 72 of the planetary gear 40 in a non-planetary state or a planetary state. And a planetary gear switching mechanism 84 for switching to

When the planetary gear 40 is in the planetary state, the driven gear 42 and the transmission mechanism 22 are connected to each other, and when the planetary gear 40 is not in the planetary state, the transmission mechanism connection / interruption device is released. 62 may be provided.

[0010]

BRIEF DESCRIPTION OF THE DRAWINGS FIG.
A crankshaft rotatably supported by a hanger portion of the bicycle, and being inputted and rotating; a deceleration means interlocked with the crankshaft; a deceleration state switching means; and engaged with the deceleration means,
A transmission mechanism for transmitting a rotational force to the wheel hub body, wherein the speed reducing means rotates at least one or a plurality of planetary gears receiving the driving force of the crankshaft, and rotates while engaging with the planetary gears. And a differential gear mechanism including at least one driven gear. The switching means switches between the planetary motions of the planetary gears of the differential gear mechanism to perform deceleration / non-reduction operation.

The differential gear mechanism includes at least one or more planetary gears that rotate by receiving a driving force of a crankshaft;
At least one driven gear that rotates while meshing with these planetary gears may be provided. However, at the time of deceleration rotation, the planetary gear rotates in the direction opposite to the input rotation direction of the crankshaft, and the reversely rotating output is taken out by the driven gear rotating in the same direction as the planetary gear. Therefore, it is necessary to extract an output that rotates in the same direction as the input rotation of the crankshaft. For this purpose, one or a plurality of planetary gears meshing with the driven gear are arranged on both sides of the driven gear with the driven gear as a center, and the planetary gear on one side is interlocked with the crankshaft, and the driven An output that rotates in the same direction as the input rotation of the crankshaft is output by a planetary gear on the other side that is interlocked with the gear. Further, by forming the driven gear to have a substantially Z-shaped cross section, assembly of the planetary gears on both side surfaces of the driven gear can be simplified and made compact.

In the differential gear mechanism, the planetary gear is rotated by the driving force of the crankshaft in a non-planetary state in which the planetary gear is held at a fixed position by the switching means, and the driven gear engaged with the planetary gear is rotated with respect to the rotation of the crankshaft. Rotate at reduced speed. Further, the planetary gear is held in the idle state in which the planetary gear idles around the crankshaft by the switching means, and in this state, the driven gear engaged with the planetary gear is driven at substantially the same speed as the crankshaft (the gear ratio is about 1: 1). For non-deceleration rotation. Further, the mechanism for deceleration is provided on the crankshaft, but is not limited to this, and may be provided on the hub body side of the rear wheel so as to interlock with the crankshaft.

Further, the differential gear mechanism comprises the driven gear, and one or more planetary gears meshing with the driven gear on both sides with the driven gear as a center. The side planetary gear may be provided so as to be interlocked with the crankshaft. With the planetary gears arranged on the other side, a deceleration output that rotates in the same direction as the crankshaft is obtained.

Preferably, the driven gear of the differential gear mechanism has a substantially Z-shaped cross section .

Further, the switching means includes a clutch unit for connecting or disconnecting the driven gear and the crankshaft;
A planetary gear switching mechanism may be provided for stopping the pivot shaft of the planetary gear in the non-planetary state or switching the planetary gear to the planetary state. The clutch portion may be provided with a concave / convex portion that is engaged with the driven gear and the driving gear, and may be engaged or disengaged by causing the driven gear or the driving gear to move forward and backward along the crankshaft. In addition, the planetary gear switching mechanism arranges an annular plate on which the pivot shaft of the planetary gear is fixed in a circumferential groove provided on the inner wall of the cover body, and presses the braking piece or the braking band against the outer peripheral surface of the annular plate. , May be provided with a mechanism for stopping or releasing the annular plate by separating. When the crankshaft and the driven gear are connected by the clutch portion, the stop of the annular plate by the planetary gear switching mechanism is released, the planetary gear is held in the planetary state, and the driven gear rotates at a reduced speed. In the state where the connection between the crankshaft and the driven gear is cut off by the clutch,
The annular plate is stopped by the planetary gear switching mechanism, the planetary gear is kept in a non-planetary state and rotates, and the driven gear rotates at a reduced speed.

In addition, a transmission mechanism connection / interruption device is provided for bringing the driven gear and the transmission mechanism into a connected state when the planetary gear is in the planetary state, and releasing the connection when the planetary gear is in the non-planetary state. It may be that. The transmission mechanism connection / interruption device may be configured to engage an urging claw provided on the outer surface of the driven gear with an inner rack tooth provided on the transmission mechanism side.

[0017]

Preferred embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is an enlarged side explanatory view of a main part of a deceleration mechanism attached to a crankshaft of a speed change bicycle according to an embodiment of the present invention. FIG. 2 is a partially sectional explanatory view taken along line AA of FIG. FIG. 3 is an exploded perspective view of a main part of the mechanism for deceleration. A shift-switching bicycle 10 according to the present invention is rotatably supported by a hanger portion 12 of the bicycle, and is provided with a crankshaft 14 that is inputted and rotates, a deceleration unit 16 that is interlocked with the crankshaft 14, and a deceleration state switching unit. 18 and a transmission mechanism 22 that is engaged with the speed reduction means 16 and transmits a rotational force to the wheel hub body 20.

As shown in FIGS. 6 and 7, the speed change switching bicycle 10 has a frame 2 made of a metal pipe.
4 and a saddle 26 provided at a central upper position of the frame 24 so as to be adjustable in height. A handle 28 is connected to a front fork 27 provided at a front position of the frame 24, and a front wheel 30 is assembled. The wheel hub body 20 of the rear wheel 32 is attached to the rear end position of the frame 24, and the crankshaft 14 is supported by the hanger 12 at the lower center of the frame 24.

As shown in FIGS. 1 and 2, the crankshaft 14
Are bearings 34 fixed to the hanger portion 12 in both directions.
At both ends of the crankshaft 14, crank arms 38, 38 having a pedal 36 at the tip thereof are horizontally supported at both ends thereof, as shown in FIGS. 6 and 7. It is connected in the direction. The transmission mechanism 22 is adjusted from the speed reduction means 16 provided on the crankshaft 14 to the wheel hub body 20 of the rear wheel 32.

The speed reducing means 16 includes at least two planetary gears 40 which rotate by receiving the driving force of the crankshaft 14.
And a differential gear mechanism 44 including at least one driven gear 42 that rotates while meshing with the planetary gears 40. The differential gear mechanism 44 by the switching means 18
The planetary gear 40 is switched in the planetary motion to perform deceleration / non-deceleration operation of bicycle running. Thus, by using the differential gear mechanism 44 as a mechanism for speed reduction, the mechanism is simple, the size of the entire mechanism is reduced, and
The load of the reduction mechanism can be reduced by reducing the weight. Also,
An extra load is not applied to the driving rotation of the crankshaft, and the driving rotation can be performed with a small force.

As shown in FIG. 1 and FIG.
Are provided so that the diameter of the crankshaft 14 is increased in the circumferential direction of the crankshaft 14 . That is, the drive gear 46 is fixed to the crankshaft 14 on the side of the bearing 34 installed on the hanger portion 12 of the bicycle frame. This drive gear 4
At least two planetary gears 40 are arranged on the outer periphery of the gear 6 and mesh with the drive gear 46. As shown in FIG. 2, the driven gear 42 is rotatably supported at an outer peripheral position near the end of the bearing 34 on the drive gear 46 side.

The crankshaft 14 and the bearing 3
4, drive gear 46, plural planetary gears 40, driven gear 42
And the like, as shown in the enlarged side view of FIG.
Are arranged concentrically around the center. In the embodiment, the differential gear mechanism 44 is disposed on both sides of the driven gear 42 with the driven gear 42 as a center.
2 and one or a plurality of planetary gears 40 that mesh with each other.

That is, as shown in the sectional view of FIG. 2, the driven gear 42 is supported by the bearing 34 and has one of a circular body 48 having a larger diameter than the drive gear 46 and one of the circular bodies 48 adjacent to the drive gear 46. An internal tooth 50 is formed on the peripheral edge of the side surface so as to protrude upward from the driving gear 46, and an external tooth 52 is formed at the center of the other side surface of the circular body 48 so as to protrude around the bearing 34. Have. The cross section from these internal teeth 50 to the external teeth 52 via the circular main body 48 is formed in a substantially Z-shape. A planetary gear 40a arranged on one side of the circular body 48 meshes with the internal teeth 50 and the drive gear 46, and a planetary gear 40b arranged on the other side engages with the external teeth 52 while meshing. As a result, it is possible to ensure the effectiveness of a compact structure for deceleration. Also,
Since the planetary gears 40a and 40b are arranged on both sides of the driven gear 42, the balance is good, and thus the gear operates smoothly.
Accuracy and reliability of the deceleration operation are increased. In addition, the differential gear mechanism 44 operates smoothly, so that no trouble or the like occurs.

As shown in FIGS. 1 and 2, a transmission mechanism 22 for transmitting the rotational force of the crankshaft 14 to the wheel hub 20 of the rear wheel 32 is provided on the outer peripheral surface of the driven gear 42. The transmission mechanism 22 includes a transmission gear 54 engaged so as to cover the outer peripheral surface of the driven gear 42 and a transmission gear 5
4 and an endless chain 60 wrapped around the outer peripheral surface. The transmission gear 54 is formed in a hollow cylindrical shape, and a chain tooth 56 is implanted around the outer peripheral surface thereof. An endless chain 60 is looped around the chain teeth 56 and a chain gear 58 provided at a position near the end of the wheel hub body 20. As the transmission mechanism 22, a timing belt, other transmission ropes, or the like may be used. In this case, the transmission gear 54 and the wheel hub body 20 are provided with groove teeth that engage with these belts and ropes.

In order to rotate the driven gear 42 and the transmission gear 54 in conjunction with each other, a transmission mechanism connection / interruption device 62 is provided on the outer peripheral surface of the driven gear 42 and the inner peripheral surface of the transmission gear 54. The transmission mechanism connection / interruption device 62 is
When the driven gear 42 rotates in the same direction as the following (hereinafter referred to as forward rotation), the driven gear 42 and the transmission gear 54 are engaged with each other. When the driven gear 42 rotates in the reverse direction, the driven gear 42 It slips against the transmission gear 54 to release the engagement.

That is, as shown in FIGS. 1 and 2, the transmission mechanism connection / interruption device 62 includes one or a plurality of biasing members disposed on the outer peripheral surface side of the driven gear 42 for rotating the transmission gear 54 forward. A feed pawl 64, and first internal teeth 66 that are engraved around the substantially central position of the inner peripheral surface of the transmission gear 54 and engage with the urging feed pawl 64 to rotate the transmission gear 54 in conjunction therewith. ing. Further, second internal teeth 68 are provided on the side end side of the inner peripheral surface of the transmission gear 54 corresponding to the external teeth 52 of the driven gear 42.

The drive gear 46 of the crankshaft 14 and the driven gear 42 are directly connected by the switching means 18 described later, and the driven gear 42 rotates forward in the same direction as the crankshaft 14 when the planetary gears 40a and 40b are in the planetary state. During the deceleration operation, the urging feed pawl 64 of the driven gear 42 engages with the first internal teeth 66 on the inner surface of the transmission gear 52, and the transmission gear 52 rotates forward in the same direction as the crankshaft 14. In the running state of the non-deceleration operation, even if the rotation of the crankshaft 14 is stopped to stop the rotation of the driven gear 42, the urging feed pawl 64 on the driven gear 42 side
On the other hand, the first internal teeth 66 slip, and the transmission gear 42 idles by inertia in conjunction with the rear wheel 32.

Further, the connection between the driving gear 46 and the driven gear 42 is released by the switching means 18, and the planetary gears 40a, 40b
Is in a non-planetary state, and the driving gear 46 meshes with the planetary gear 40a, and further, the driven gear 42 rotates in reverse to the rotation of the crankshaft 14 due to the meshing of the planetary gear 40a and the internal teeth 50 of the driven gear 42. Then, the urging feed pawl 64 of the driven gear 42 slips against the first internal teeth 66 on the inner surface of the transmission gear 54. At this time, the driven gear 4 rotating in the reverse direction to the crankshaft 14
The idler gear 40b on the other side meshes with the second external teeth 52, and the idler gear 40b meshes with the second internal teeth 68 of the transmission gear 54, so that the transmission gear 54 rotates at a reduced speed in the same direction as the crankshaft 14. I do.

As described above, the driven gear 42 and the transmission gear 54
The transmission mechanism connection / interruption device 62 is provided mutually, and the speed change is reliably switched between the non-deceleration operation in the planetary state of the planetary gears 40a and 40b and the deceleration operation in the non-planetary state of the planetary gears 40a and 40b. be able to. Further, switching between the connected state and the unconnected state of the driven gear 42 and the transmission mechanism 22 can be reliably performed with a simple structure.

As shown in FIGS. 2 and 3, one or a plurality of planetary gears 40a,
Reference numeral 0b denotes pivot shafts 72a, 72 on opposed inner surfaces of donut-shaped annular plates 70a, 70b which are vertically arranged to face each other.
b is fixed vertically, and the planetary gears 40a, 40b are rotatably mounted on the pivot shafts 72a, 72b.

As shown in FIGS. 2 and 3, the hanger portion 12 of the frame 24 is rotatably supported on the bearing 34 of the reduction means 14, the drive gear 46 fixed to the crankshaft 14, and the outer periphery of the bearing 34. A two-stage cylindrical cover body 74 that shields the driven gear 42, the transmission gear 54 engaged with and connected to the driven gear 42, and the like is provided. The inner surfaces of both side walls 76a and 76b of the cover body 74 that protrude in the circumferential direction include:
Circumferential grooves 78a, 78b for rotatably engaging donut-shaped annular plates 70a, 70b so as to rotate around the crankshaft 14 are opened. The annular plates 70a, 70b are engaged in the circumferential grooves 78a, 78b, and the planetary gear 40 pivotally supported by one of the annular plates 70a.
a is meshed with the driving gear 46 and the internal teeth 50 of the driven gear 42, and the planetary gear 40b pivotally supported by the other annular plate 70b is connected to the external teeth 52 of the driven gear 42 and the second internal teeth 68 of the transmission gear 54. Are engaged. In the drawing, reference numerals 80, 80 denote chain access holes opened in the cover body 74.

In the traveling operation of the gearshift bicycle 10, the deceleration means 16 is switched to, for example, one of a non-deceleration operation for traveling on a flat portion and a deceleration rotation for traveling on an uphill portion. . Switching means 1 for this switching
Reference numeral 8 denotes a clutch unit 82 for connecting or disconnecting the driven gear 42 and the crankshaft 14, and a planetary gear switch for controlling the pivot shafts 70a, 70b of the planetary gears 40a, 40b to be in the non-planetary state or for switching the planetary state to the planetary state. And a mechanism 84.

As shown in FIGS. 2 and 3, the clutch 82
The operating cylinder 86 slidably and rotatably fitted in the axial direction on the outer peripheral surface of the bearing 34 in the cover 74, and protrudes toward the driven gear 42 at one end of the operating cylinder 86. A plurality of claws 88, and claw holes 90a and 90b are provided on the body side of the driving gear 46 and the driven gear 42, and are formed with communication holes so that the plurality of claws 88 can be moved forward and backward to engage and disengage.

When the operating cylinder 86 is advanced toward the driving gear 46, the plurality of claws 88 are engaged with the claw holes 90b of the driven gear 42 and the claw holes 90a of the driving gear 46, so that the driven gear 42 and the driving gear 46 are integrated. Are linked together. As a result, the driven gear 4
2 is connected to the crankshaft 14 via a drive gear 46. When the operating cylinder 86 is retracted, the tips of the plurality of claws 88 are disengaged from the claw holes 90a of the drive gear 46 and are engaged and held in the claw holes 90b of the driven gear 42, and the driven gear 42 Is disconnected, and the operating cylinder 86 is held by the bearing 34 in a freely rotating state together with the driven gear 42. The plurality of claws 88 may be retracted from the claw holes 90b of the driven gear 42, but the forward engagement of the driven gear 42 and the driving gear 46 into the claw holes becomes complicated, so that the claw holes 90b of the driven gear 42 become complicated.
It is preferable to wait in the inside, and the operation of connection and release by the pawl 88 is simplified.

As shown in FIGS. 2 and 7, a circumferential groove 92 is formed on the outer peripheral surface near the end of the operating cylinder 86 to move the operating cylinder 86 forward and backward. Opposite to the circumferential groove 92, long holes 94, 94 are opened in both body side portions of the cover body 74 in the advancing and retreating direction of the operation cylinder 86. This long hole 9
A substantially elliptical operation lever 96 is arranged on the outer periphery of the cover body 74 so as to go around the outer periphery of the fourth and fourth members 94. The operation lever 96 is pivotally mounted on a hinge 97 provided on the lower surface side of the cover body 74 so as to swing in the direction of the long hole 94. The operating lever 96 has guide pins 98, 9 that pass through the elongated holes 94, 94 and engage with the circumferential groove 92 of the operating cylinder 86.
8 is fixed.

An operation wire 102 extending from a hand lever 100 attached to the frame 24 near the saddle 26 of the bicycle is connected to an operation lever 96. By pulling the operation lever 96 with the hand lever 100,
The working cylinder 86 advances, and the tip of the claw 88 engages with the claw hole 90a of the drive gear 46, so that the driven gear 42 and the drive gear 46 are integrally connected. When the traction of the operation lever 96 is released, the operation lever 96 is retracted together with the operating cylinder 86 by an urging spring provided on the operation wire 102, and the tip of the claw 88 is moved to the drive gear 46.
Of the driven gear 42 and the driving gear 46
Is disconnected.

As shown in FIGS. 2 and 7, the planetary gear switching mechanism 84 includes two side walls 76a, 76
The brake screws 104, 104, which are screwed from the outer surface side of the outer ring 6 a to the annular bodies 70 a, 70 b of the planetary gears arranged on the inner surface side, and are composed of left and right screws,
Tightening arm 1 projecting obliquely upward from the head of 4, 104
06 and 106. This fastening arm 106, 1
An operation wire 112 extending from a hand lever 110 attached to the frame 24 at a position near the saddle 26 is connected to an operation lever 108 connected to 06. When the operation wire 112 is pulled by the hand lever 110 and the tightening arms 106, 106 are pulled upward, the braking screw 104,
104 is screwed into the wall, and the annular plates 70a, 70b are stopped by the braking screws 104, 104. Hand lever 11
When the operation wire 112 is released from being pulled, the urging springs provided on the operation wire 112 cause the tightening arms 106, 106 to be released.
Is lowered, and the annular plate 70 is
The stop of the a and 70b is released, and the annular plates 70a and 70b float.

Thus, during non-deceleration operation, the driven gear 42 and the driving gear 46 are connected by the forward operation of the operating cylinder 86 of the clutch portion 82, and the torque of the crankshaft 14 is transmitted to the driven gear 42 without being reduced. Is done. Further, the urging feed pawl 64 on the driven gear 42 side of the transmission mechanism connection / interruption device 62
Engages with the first internal teeth 66 of the transmission gear 54 so that the transmission gear 54
Rotates in the same direction as the drive gear 46 at the same speed, and the endless chain 60 transmits the rotational force to the hub body of the rear wheel 32, so that the bicycle operates without deceleration. At this time, without pulling the operation wire 112 by the hand lever 110 of the planetary gear switching mechanism 84, the annular bodies 70a, 70b are held in a free state, and the planetary gear 40a locked by the drive gear 46 and the driven gear 42 , 40b planetary with the toroids 70a, 70b.

During deceleration operation, the clutch unit 8
The second operating cylinder 86 is moved backward to release the connection between the driven gear 42 and the driving gear 46. At the same time, by operating the planetary gear switching mechanism 84, the annular bodies 70a and 70b are
The planetary gears 40a, 40b are pivotally held in a non-planetary state by stopping at 4, 104. As a result, the rotational force of the crankshaft 14 is reduced by the drive gear 46, the planetary gears 40a and the planetary gears 4a.
0a and the internal teeth 50 of the driven gear 42
Rotates at a reduced speed in a direction opposite to that of the crankshaft 14. At this time,
The urging feed pawl 64 on the driven gear 42 side of the transmission mechanism connection / interruption device 62 reversely rotates in an idling manner with respect to the first internal teeth 66 of the transmission gear 54. Further, the external teeth 5 on the other side of the driven gear 42
2, the planetary gear 40b and the planetary gear 40b and the transmission gear 54
The transmission gear 54 is meshed with the second internal teeth 68 of the
6 is rotated at a low speed in the same direction as
Due to 0, the decelerated rotational force is transmitted to the wheel hub body 20 of the rear wheel 32, and the bicycle decelerates.

Therefore, the clutch lever 82 and the planetary gear switching mechanism 84 are selectively operated by alternately operating the hand levers 100 and 110 provided near the saddle 26 of the bicycle, and the flat portion is not operated by the deceleration operation. This makes it possible to ensure the traveling of the uphill portion by traveling and decelerating operation.

Next, the operation of the speed change bicycle according to the embodiment of the present invention will be described. As shown in FIGS. 6 and 7, when the shift-switching bicycle 10 starts traveling or when traveling on an uphill, a large torque is applied to the rear wheel 32, so that the deceleration means 16 switches to deceleration operation and travels. However, after the speed is increased in the flat portion, the vehicle can travel with a small torque, so that the speed reduction means 16 switches to non-deceleration operation and travels. Accordingly, the driver riding on the saddle 26 retracts the operating cylinder 86 of the clutch unit 82 to the end side of the bearing 34 while the one hand lever 100 is tilted forward during the deceleration operation at the start of traveling. The drive gear 46 and the driven gear 42 are kept disconnected.

Then, the other hand lever 110 on the planetary gear switching mechanism 84 side is tilted forward, the operation wire 112 is pulled, and the fastening arm 10 is connected with the operation lever 108 connected thereto.
6 and 106 are pulled up and the braking screws 104 and 104
Is screwed into the annular plates 70a, 70b and locked, and the planetary gears 40a, 40b are pivotally held in a non-planetary state. As a result, the rotational force of the crankshaft 14 is reduced by the driving gear 46 and the planetary gear 40a, and the planetary gear 40a and the internal gear 50 of the driven gear 42.
, The driven gear 42 is decelerated and rotated in the direction opposite to the crankshaft 14, and the driven gear 42
The biasing feed pawl 64 on the side rotates in an idling manner with respect to the first internal teeth 66 of the transmission gear 54. Further, the transmission gear 54 is meshed with the external teeth 52 on the other side of the driven gear 42 and the planetary gear 40b, and the planetary gear 40b and the second internal teeth 68 of the transmission gear 54.
The bicycle is decelerated and rotated at a low speed in the same direction as the drive gear 46, and the endless chain 60 transmits the reduced rotational force to the hub body of the rear wheel, whereby the bicycle is decelerated.

When the speed of the bicycle increases, the deceleration means 16
Is switched to non-deceleration operation. At this time, the hand lever 110 of the planetary gear switching mechanism 84 is tilted forward to
06, 106 is lowered to release the locking of the annular plates 70a, 70b by the braking screws 104, 104 and the planetary gear 40
a and 40b are kept in a planetary state. Furthermore, hand lever 1
00, the operation wire 112 is pulled to pull forward the operating cylinder 86 of the clutch portion 82, and the plurality of claws 88 engaged with the claw holes 90b of the driven gear 42 are moved to the driving gear 46.
The driven gear 42 and the driving gear 46
And are directly connected. Thus, the rotational force of the crankshaft 14 is transmitted from the reduced drive gear 46 to the driven gear 42.

Further, the urging feed pawl 64 on the driven gear 42 side of the transmission mechanism connection / interruption device 62 is connected to the first internal teeth 6 of the transmission gear 54.
6, the transmission gear 54 rotates in the same direction as the drive gear 46 at the same speed, and the endless chain 60 transmits the rotational force to the hub body of the rear wheel, so that the bicycle operates without deceleration. At this time, the annular bodies 70a, 70b of the planetary gear switching mechanism 84
Are held in a free state without being locked, so that the planetary gears 40a and 40b on both sides of the driven gear 42 perform planetary motion without rotating while being locked by the driving gear 46 and the driven gear 42. .

As described above, by using the differential gear mechanism 44 as a mechanism for speed reduction, the mechanism is simple, the size of the entire mechanism is reduced, the speed reduction mechanism portion is lightened, and the load can be reduced. . Further, no extra load is applied to the driving rotation of the crankshaft 14, and the driving rotation can be performed with a small force. Therefore, long-time running becomes easy. Further, a failure or the like hardly occurs during the operation of the deceleration switching, and the cost and time for maintenance are unnecessary. Further, since the structure of the speed reduction means is reduced in size, the work of mounting on the crankshaft can be easily performed.

[0046]

As described above, according to the speed change switching bicycle of the present invention, a crankshaft rotatably supported by a hanger portion of the bicycle and inputted and rotated, and a deceleration interlocked with the crankshaft. Means, a decelerating state switching means, and a transmission mechanism engaged with the deceleration means and transmitting a rotational force to the wheel hub body, wherein the deceleration means rotates by receiving a driving force of the crankshaft. A differential gear mechanism including one or more planetary gears and at least one driven gear that rotates while meshing with the planetary gears, wherein the switching means causes planetary motion of the planetary gears of the differential gear mechanism; The deceleration / non-deceleration operation is performed while switching the speed, so that the mechanism for deceleration is structurally simple, the size of the entire mechanism is reduced, and There is weight of the same reduction mechanism portion with to hold the design sense of the cleanest, it is possible to reduce the load. Further, the drive rotation of the crankshaft can be performed with a light force without applying an extra load. Therefore, long-time running becomes easy. Further, a failure or the like hardly occurs during the operation of the deceleration switching, and the cost and time for maintenance are unnecessary. Further, since the structure of the speed reduction means is reduced in size, the work of mounting on the crankshaft can be easily performed.

Further, the differential gear mechanism comprises the driven gear, and one or more planetary gears meshing with the driven gear on both sides with the driven gear at the center. Since the side planetary gear is provided so as to be interlocked with the crankshaft, it is possible to ensure the effectiveness of the reduction in the structure of the reduction means. In addition, since the planetary gears are arranged on both sides of the driven gear, the gears are well-balanced, so that they operate smoothly, and the accuracy and reliability of the deceleration operation increase.

Further, since the driven gear of the differential gear mechanism is formed in a substantially Z-shaped cross section, the compact gear of the differential gear mechanism can be effectively maintained. In addition, the planetary gears can be arranged on both sides of the driven gear in a well-balanced manner, and the differential gear mechanism operates smoothly, so that no trouble or the like occurs.

The switching means includes a clutch unit for connecting or disconnecting the driven gear and the crankshaft;
A planetary gear switching mechanism that stops the planetary gear's pivot shaft in a non-planetary state or switches the planetary state to a planetary state is provided, so that the clutch unit and the planetary gear switching mechanism are selectively operated, and non-reduction is performed. Effectiveness of traveling on a flat portion by driving and traveling on an uphill portion by deceleration can be ensured.

Further, a transmission mechanism connection / interruption device is provided for bringing the driven gear and the transmission mechanism into a connected state when the planetary gear is in the planetary state, and releasing the connection when the planetary gear is in the non-planetary state. Accordingly, the transmission mechanism connection / interruption device can reliably switch the speed between the non-deceleration operation in the planetary gear in the planetary state and the deceleration operation in the non-planetary state in the planetary gear. Further, switching between the connected state and the non-connected state of the driven gear and the transmission mechanism can be reliably performed with a simple structure.

[Brief description of the drawings]

FIG. 1 is an enlarged side elevational view of a main part of a speed reduction mechanism mounted on a crankshaft of a speed changeover vehicle according to an embodiment of the present invention.

FIG. 2 is a partial cross-sectional explanatory view taken along the line AA of FIG. 1;

FIG. 3 is an exploded perspective view of an essential part of the speed reduction mechanism.

FIG. 4 is an explanatory diagram of a rotation direction of a main part of a speed reduction mechanism in a non-deceleration operation state.

FIG. 5 is an explanatory diagram of a rotation direction of a main part of the speed reduction mechanism in a deceleration operation state.

FIG. 6 is a side view of the speed change bicycle according to the embodiment of the present invention.

FIG. 7 is an explanatory perspective view of a hanger unit to which a mechanism for deceleration is attached.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Speed change bicycle 12 Hanger part 14 Crankshaft 16 Deceleration means 18 Switching means 20 Wheel hub body 22 Transmission mechanism 40 Planetary gear 42 Follower gear 44 Differential mechanism 62 Transmission mechanism connection / interruption device 72 Pivot shaft 82 Clutch portion 84 Planetary gear switching mechanism

Claims (3)

(57) [Claims] 1. A rotatably supported pivot on a hanger portion of a bicycle.
A crankshaft that is rotated by being input,Switch between deceleration and non-deceleration of bicycle The switching means is engaged with the speed reduction means to transmit a rotational force to the wheel hub body.
A transmission mechanism, wherein the deceleration means rotates by receiving a driving force of the crankshaft.
At least one or more planetary gears,
At least one driven tooth that rotates while meshing with the planetary gear
And a differential gear mechanism including a car,The differential gear mechanism includes the driven gear and the driven gear.
One or both of which are engaged with the driven gear on both sides
And a plurality of planetary gears, The driven gear is located on the circumference of one side of the circular body.
Internal teeth that protrude and engage one or more planetary gears
And a projection formed at the center of the other side surface of the same circular main body.
External teeth that mesh with one or more planetary gears.
Formed in a substantially Z-shaped cross section, Internal gear side of planetary gears arranged on both sides of driven gear
Planetary gear is interlocked with the crankshaft,  The planetary gear of the planetary gear of the differential gear mechanism by the switching means
Perform deceleration / non-deceleration operation while switching motions
A speed changeover bicycle characterized by the following. 2. The switching means according to claim 1 , wherein said driven gear is connected to said clutch.
A clutch portion for connecting or disconnecting the rank shaft, and a pivot shaft of the planetary gear being stopped in a non-planetary state, or
The speed change switching bicycle according to claim 1 , further comprising: a planetary gear switching mechanism that performs idle switching between states . 3. When the planetary gear is in the planetary state,
With the driven gear and the transmission mechanism being connected,
When the planetary gear is in the non-planetary state, this connection is released.
And a transmission mechanism connection / interruption device.
The shift change bicycle according to the description .