JP2003049876A - Braking device for simplified vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a braking device for a simplified vehicle automatically decelerating in a downhill slope, preventing backing of the simplified vehicle in an uphill slope, and capable of easily carrying out a change-over. SOLUTION: The braking device for the simplified vehicle has a fixed shaft 12 provided on a simplified vehicle body and rotatably supporting a hub 13, a gear mechanism 16 provided in an inner side of the hub 13, a turntable 17 connected with the gear mechanism 16 and having a rotational frequency different from the hub 13, a decelerating means 19 swingably provided on the turntable 17 and decelerating a wheel 58 by centrifugal force, a clutch mechanism 41 swingably provided on the fixed shaft 12 and provided with a change-over gear 56 capable of meshing or releasing meshing with one of an internal gear 29 or an external gear 16, and a change-over ring 47. The clutch mechanism 41 is provided with synchronizing members 74 and 75 energizing the change-over gear 56 toward the internal gear 29 or the gear mechanism 16 between the change-over ring 47 and the change-over gear 56, and it smoothly changes over a power transmitting state.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a wheelchair,
The present invention relates to a braking device for a simple vehicle attached to a hub of a light vehicle such as a walker or a luggage cart.

[0002]

2. Description of the Related Art Conventionally, a simple vehicle other than a wheelchair, for example, a simple vehicle such as a walker, a luggage trolley, a rear car, or the like has a light object to be conveyed and has a low conveyance speed, and therefore has no hand brake or parking brake. There were many. on the other hand,
Wheelchairs are self-propelled, where the passengers themselves operate the wheelchair,
There were assisting types in which an assistant pushed from the rear of the wheelchair, and compound types that were both self-propelled and assisted. The self-propelled type and the composite type are provided with a hand rim on the outside of the wheel, and a passenger can run and stop by operating the hand rim. In the assisted and compound types, a handle is provided at the rear of the wheelchair, and an assistant can drive the wheelchair by pushing the handle, and the handbrake provided in the handle controls the speed of the wheelchair. We were able to. In addition, each wheelchair is provided with a parking brake that comes into direct contact with the wheels to prevent the wheels from rotating, and the passenger can operate the parking brake to fix the wheels of the wheelchair so that they cannot rotate.

[0003]

However, the conventional simple vehicle having no handbrake or parking brake has a greater burden on the operator when moving on a slope or the like than when moving on a level ground. Further, since the hand brake of the wheelchair cannot be operated by the passenger, when the passenger alone travels on a steep downhill using a self-propelled or compound wheelchair, the hand rim is There was no choice but to slow down with, and the operation was difficult. When using an assisted wheelchair, an assistant can operate the handbrake to decelerate, but using the brake continuously for a long time puts a strain on the hand. In addition, when traveling uphill using a self-propelled wheelchair, in order to prevent the wheelchair from descending backwards, the passenger releases the hand rim and applies the parking brake, and then the parking brake again. Fatigue was great because the operation of releasing and turning the hand rim was repeated. In addition, many other braking devices directly wear the tire, which often shortens the durability time of the tire or the braking force is not stable. In addition, since the parking brake needs to engage or disengage the engaging member on the wheel when torque is applied to the wheel, it is difficult to operate, and there are many cases where switching of the engaging state is not successful. . The present invention has been made in view of such circumstances, and a braking device for a simple vehicle that automatically performs deceleration on a downhill, prevents a simple vehicle from moving backward on an uphill, and can easily perform switching. The purpose is to provide.

[0004]

A braking device for a simple vehicle according to the present invention which meets the above object is a braking device for a simple vehicle, which is provided inside a hub of a wheel of a simple vehicle and controls the rotation of the wheel. A fixed shaft provided on the simple vehicle body for rotatably supporting the hub, a gear mechanism provided inside the hub for inputting rotation of the wheels, and rotatably provided on the fixed shaft. A rotary plate that is connected to the gear mechanism and has a different rotational speed from the hub, and is swingably provided on the rotary plate, and is moved radially outward by the centrifugal force generated by the rotation of the wheels. A deceleration unit that contacts the peripheral surface to decelerate the wheel, and an internal gear formed on the fixed shaft so as to be swingable and one of the internal gear formed on the inner periphery of the hub and the gear mechanism are meshed or released from meshing. Clutch with possible switching gears And a switching ring that is provided on one side in the axial direction of the hub and that can operate the radial position of the switching gear, and the clutch mechanism is provided between the switching ring and the switching gear. A tuning member that biases the switching gear toward the internal gear or the gear mechanism is provided to smoothly switch the power transmission state.

Here, the simple vehicle is, for example, a wheelchair,
It refers to a walker, a luggage cart, a rear car, and the like, and the braking device is provided on at least one of the plurality of wheels, but is preferably provided on all the wheels. The different rotation speeds mean that the relative speed of the hub and the rotary plate is not substantially 0, and the rotation speeds are always different when the rotation directions are opposite. It is preferable that the hub and the rotary plate rotate in opposite directions. This is because even if the speed of the rotating plate is slow, the relative speed with the hub becomes large and the speed can be efficiently reduced. For the deceleration means, for example, a brake shoe having a large frictional force can be used, and the brake shoe can be provided with a heavy object such as a metal weight for increasing centrifugal force. Further, the deceleration means may be provided with a biasing means such as a spring to bias the brake shoe toward the axial center of the fixed shaft. The wheel includes, for example, a tire on the outer peripheral portion and a hub on the axial center portion. The hub and the wheels are integrally provided, and when traveling the simple vehicle, they rotate in the same direction at the same rotation speed.

When the hub is rotated after the switching gear is engaged with the gear mechanism by the clutch mechanism, the rotary plate connected to the gear mechanism also rotates. When the rotational speed exceeds a certain value, the speed reducing means provided on the rotary plate moves radially outward due to the centrifugal force and comes into contact with the inner peripheral surface of the hub. Since the rotation speed of the rotary plate is different from the rotation speed of the hub, the rotation speed of the simple vehicle can be reduced by sliding on the inner peripheral surface of the hub and the sliding resistance at this time. For example, when the switching gear is meshed with the internal gear, the wheel is slowly rotated while pressing the switching gear radially outward, and the internal gear is slowly rotated together with the hub. Then, the switching gears and the internal gears are rotated while slipping from the contacting tooth tips, and the tooth tips are fitted into and mesh with the corresponding tooth groove portions. At this time, if the pressure of the switching gear is too strong, the rotation of the wheels is hindered, and if it is too weak, the timing of meshing is missed. It is difficult for the operator to slowly rotate the wheel while adjusting the pressing force, but since the tuning member is provided, the wheel is rotated while applying a certain amount of pressing force to the switching gear. be able to. Further, when the switching gear is meshed with the external gear, the pressing force can be applied to the switching gear via the tuning member in the same manner.

Here, it is also possible to attach the front side of the fixed shaft integrally and relatively rotatably to the hub and attach the base side of the fixed shaft to the simple vehicle body in a detachable manner. Is. With this configuration, for example, at the time of maintenance or failure of the braking device, the braking device together with the hub can be easily removed from the simple vehicle for repair, and repair work can be easily performed. In the case of a wheelchair, it can be easily installed in a car.

Further, the gear mechanism rotates the first and second planetary gears that mesh with the internal gear and can revolve around the fixed shaft, and the first and second planetary gears, respectively. The first and second planetary frames that are rotatably mounted and rotatable about the fixed shaft, and the rotary plate that rotates in a direction opposite to the rotation direction of the hub, and mesh with the first planetary gears. A first sun gear, a second sun gear provided on the first planetary frame and meshing with the second planetary gear, and an external gear provided on the second planetary frame. It is also possible to restrict rotation of the hub or operate the deceleration means by providing a one-way clutch on the switching gear of the clutch mechanism and switching the position of the switching gear.

The one-way clutch is free to rotate in one direction and locks when trying to rotate in the other direction. When the switching gear is moved to the axial center side of the fixed shaft and meshed with the external gear of the second planetary frame, the hub can freely rotate in one direction. When the hub is rotated in the other direction, the first and second planetary gears that mesh with the internal gear of the hub each try to rotate in the other direction. At this time, in the second planetary frame to which the second planetary gear is attached, the external gear meshes with the switching gear, so the external gear locks together with the switching gear and cannot rotate in the other direction. ing. Therefore, the second
The planetary gears of 1) rotate in the other direction without revolving and without changing their center positions, and rotate the 2nd sun gear of the meshing first planetary frame in one direction. Since the first planetary frame integrally provided with the second sun gear rotates in one direction, the first planetary gear attached to the first planetary frame revolves in one direction,
Further, the internal gear of the meshing hub rotates in the other direction, so that it rotates in the other direction. When the first planetary gear rotates in the other direction, the meshing first sun gear rotates in one direction, and the rotating plate integrally provided with the first sun gear rotates in one direction.

On the other hand, when the switching gear is moved outward in the radial direction and meshed with the internal gear on the inner periphery of the hub to rotate the hub in the other direction, the switching gear locks,
The hub cannot rotate freely. When the hub is rotated in one direction, the first and second planetary gears that mesh with the internal gear of the hub tend to rotate in one direction. At this time, since the switching gear is not meshed with the external gear of the second planetary frame, the second planetary frame is in a state in which it can rotate without load (hereinafter, referred to as idle state). . The gear mechanism tries to maintain a state in which the load is minimized when there is a free gear train. When the first and second planetary frames and the rotating plate rotate at the same speed as the hub, torque is not transmitted between the gears, and the load is in a minimum state. Rotate integrally at the same speed as. Therefore, since the rotation speed of the rotating plate is not increased and the rotation speed is low, the speed reducing means provided on the rotating plate does not operate, and even if it operates, the speed reducing means contacts the hub at the same speed as the hub. The hub does not decelerate as it touches. With this configuration, the deceleration operation and the rotation restriction operation can be reliably performed.

[0011]

BEST MODE FOR CARRYING OUT THE INVENTION Next, referring to the attached drawings, an embodiment in which the present invention is embodied will be described to provide an understanding of the present invention. As shown in FIG. 1, a braking device 10 for a simplified vehicle according to an embodiment of the present invention is mounted substantially horizontally on a left side support 11 of a wheelchair body, which is an example of a simplified vehicle body, and has a hub 13 attached thereto. It has a fixed shaft 12 that rotatably supports it. Braking device 1 including fixed shaft 12
Reference numeral 0 is a device that is provided inside the hub 13 and that controls the rotation of the wheels. The details will be described below. The braking device is provided symmetrically with respect to the wheelchair body,
Hereinafter, only the braking device 10 provided on the left side will be described, and description of the braking device provided on the right side will be omitted. Further, the rotation direction of the wheels in the present embodiment is
The forward direction is the direction in which the wheelchair body is moved forward, and the backward direction is the opposite direction.

The braking device 10 is provided inside the cylindrical hub 13 and is rotatable by the rotation of the hub 13, that is, the gear mechanism 16 which receives the rotation of the wheel 58 (see FIG. 13) and the fixed shaft 12. It is rotatably provided on the axially front side, is connected to the gear mechanism 16, and is fixed to two positions that face each other with the rotating plate 17 having a different rotation speed from the hub 13 and the fixed shaft 12 on the front side of the rotating plate 17 sandwiched therebetween. A clutch mechanism including a brake shoe 19 that is an example of a reduction gear that is swingably provided via a pin 18, and a switching gear 56 that is swingably provided on a fixed shaft 12 that is closer to the base side of the gear mechanism 16. 41
And a switching ring 47 provided on the base side (one side) in the axial direction of the hub 13. First, the fixed state of the hub 13 will be described. As shown in FIGS. 1 and 2, the hub 13 has a cylindrical shape, and spoke attachment flanges 13a are provided on both sides of the outer circumference in the axial direction. Further, the axially front end portion and the base end portion of the hub 13 are fixed to the outer circumferences of ring-shaped cover members 14 and 15 which are substantially annular. Further, an internal gear 29 is formed over the entire circumference at an axially intermediate position on the inner circumference of the hub 13. The ring-shaped cover member 14 on the front side has an annular flange portion protruding toward the base side on the outer peripheral edge and the inner peripheral edge,
A flange portion on the inner peripheral edge side is attached to the fixed shaft 12 via a bearing 60. The inner diameter of the ring-shaped cover member 15 on the base side is larger than the inner diameter of the ring-shaped cover member 14 on the front side. Ring-shaped cover member 15
The inner peripheral edge of is attached to a squared portion 24 formed at an intermediate portion of the fixed shaft 12 via a bearing 61 and a clutch support member 20 having a circular attachment plate 23. With such a configuration, the ring-shaped cover members 14 and 15 and the hub 1
The unit 3 can rotate integrally with the fixed shaft 12.

Next, with reference to FIGS. 3A and 3B, the clutch support member 20 integrally fixed to the fixed shaft 12 will be described. The clutch support member 20 has a circular flat plate-shaped mounting plate 23 and a cylindrical portion 23a having a base end attached to the outer circumference of the mounting plate 23. Partial flanges are provided at the upper and lower ends of the front end of the cylindrical portion 23a. The portion 22 is provided, and a female screw to which the stepped pin 52 (see FIG. 1 and FIG. 11) is screwed and attached is formed inside the partial flange portion 22, and a mounting hole that penetrates in the axial direction of the fixed shaft 12 is formed. 21 is formed. At the center of the mounting plate 23, a square hole 25 that matches the square-shaped portion 24 of the fixed shaft 12 is formed. At the positions above and below the square hole 25 of the mounting plate 23, their centers are aligned with the axis of the fixed shaft 12, and the central angle θ2 is 10 to 1.
The arcuate holes 26 having a predetermined width set to 80 degrees, for example, 20 to 40 degrees are formed facing each other. On both sides of the cylindrical portion 23a of the clutch support member 20, a plurality of positioning holes 20a penetrating in the radial direction are formed at seven positions every θ3 = 15 degrees.

Referring to FIGS. 1 and 4 to 8, the fixed shaft 12 is swingably provided on the front side of the clutch support member 20 via the clutch support member 20, and the inner circumference of the hub 13 is provided. The clutch mechanism 41 provided with the switching gear 56 capable of meshing with or disengaging one of the internal gear 29 and the gear mechanism 16 formed in, and provided on the base side of the clutch support member 20 in the radial direction of the switching gear 56. The switching ring 47 whose position can be operated will be described. The clutch mechanism 41 includes a first clutch member 42, which is externally rotatably inserted from the base side to the fixed shaft 12 ahead of the clutch support member 20, and two tuning members having the same shape and axially opposed to each other. 74, 7
5 and the second clutch member 42a. Further, a switching gear 56 is provided on the front side of the second clutch member 42a via two link arms 51 swingably supported by the clutch support member 20. As shown in FIGS. 1, 4A, and 4B, the first clutch member 42 is a disk-shaped member, and the insertion hole 43 is formed in the center thereof.
And is disposed inside the cylindrical portion 23a of the clutch support member 20. On the base side of the first clutch member 42,
A ring-shaped recess 43a that is concentric with the insertion hole 43 is formed, and rotation pins 44 that can be fitted into the arc-shaped holes 26 of the clutch support member 20 are provided above and below the recess 43a so as to project in the axial direction. There is. Female screws 46 are formed on the upper and lower pivot pins 44 and open to the base side of the fixed shaft 12.

On both sides of the outer periphery of the first clutch member 42, mounting holes 44a, 4a for positioning balls 46a each having a circular bottom shape are provided toward the axis of the first clutch member 42.
5, 45a are formed respectively. Mounting hole 44a
Is on both sides in the horizontal direction, the mounting hole 45 is 30 degrees above the mounting hole 44a, and the mounting hole 45a is 30 on the mounting hole 44a.
The openings are formed on the lower side. A biasing member such as a spring (not shown) and a positioning ball 46a are inserted into the respective mounting holes 44a, 45, 45a in this order.
The positioning balls 46a are each biased outward in the radial direction. Then, a part of each is inserted into the positioning holes 20a having a diameter smaller than that of the positioning spheres 46a formed at seven positions on both sides of the cylindrical portion 23a of the clutch support member 20, and the first clutch member 42 is circumferentially arranged. Position. The positioning hole 20a of the clutch support member 20 is
It is formed in seven places at intervals of 15 degrees (θ3 = θ2 / 2). The first clutch member 42 has an angle θ of the arcuate hole 26.
Since it can move within the range of 2, that is, 30 degrees at intervals of 15 degrees, the first clutch member 42 can switch the rotation position to three positions and stop.

Here, referring to FIG. 1, the switching ring 4
7 will be described. The switching ring 47 is an annular member having an insertion hole 48 formed in the center, and is a clutch support member 2
It is rotatably attached to the enlarged diameter portion 12a of the fixed shaft 12 on the base side of 0. Above and below the insertion hole 48, the female screw portion 46 is provided at a position corresponding to the female screw portion 46 of the first clutch member 42.
A mounting hole 49 through which the male screw member 50 that is screwed into is inserted is formed. For the male screw member 50, for example, a hexagon bolt, a pan screw, a countersunk screw, a screw with a hexagonal hole, or the like can be used according to the structure of the simple vehicle to be used, and the shape of the mounting hole of the switching ring 47 is also the same as that of the male screw member. It can be changed according to the shape. Since the switching ring 47 is fixed to the first clutch member 42 by sandwiching the mounting plate 23 of the clutch support member 20 fixed to the fixed shaft 12, the switching ring 47 and the first clutch member 42 are fixed.
It can be smoothly rotated around. Stoppers 65 are provided above and below the front side of the first clutch member 42. The stopper portion 65 is formed to have the same radius and center position as the first clutch member 42, for example, a fan-shaped inner corner portion with a central angle of about 21 degrees is rounded.

As shown in FIG. 5, the first clutch member 42
The second clutch member 42a arranged on the front side of the
Is a disk-shaped member having a diameter slightly larger than that of the clutch member 42, and has an insertion hole 72 formed in the center through which the fixed shaft 12 can be inserted. On the base side of the second clutch member 42a,
A stopper portion 66 that is arranged to face the stopper portion 65 of the first clutch member 42 is provided, and at the outer peripheral end of the second clutch member 42a, the same height as the stopper portion 66 is provided on the base side in the axial direction. A protruding cylindrical outer peripheral edge portion 67 is formed. Further, the fixing portion 7 in which the female screw portion 68 for attaching the guide pin 83 is formed on the outer side in the radial direction from the center of the second clutch member 42a by 45 degrees from the horizontal direction.
0 is provided respectively, and a fixing portion 71 having an internal thread portion 69 is provided at a position facing the internal thread portion 68 with respect to the center of the second clutch member 42a. As shown in FIG. 1, a sleeve portion 73 that surrounds the periphery of the insertion hole 72 is formed on the front side of the second clutch member 42a.

As shown in FIGS. 1 and 8, the link arm 5
1 is a stepped pin 5 provided on the clutch support member 20.
2 is swingably supported via a mounting hole 86.
The stepped pin 52 is formed by forming a male screw at the base end portion and reducing the diameter of the tip end portion, and the link arm 51 is externally inserted in the middle portion thereof. The link arm 51 is a substantially flat plate member whose center is bent at an obtuse angle, and a mounting hole 86 corresponding to the stepped pin 52 is formed in the center bent portion. A fixed shaft 87 is provided at one end of the link arm 51 so as to project axially forward, and the deformed hole 8 is provided at the other end.
8 is formed. In addition, around the mounting hole 86,
A sleeve portion 86a is formed so as to project to the front side in the axial direction. In the fixed shaft 87 provided on the link arm 51,
The switching gear 56 having the one-way clutch 55 is attached to the inside thereof, and the deformed hole 88 has the second clutch member 42a.
The guide pin 83 fixed to is inserted. 1 and 11
As shown in (A), a reinforcing ring 52a is attached to the tip of the stepped pin 52. The reinforcing ring 52a is a ring-shaped plate-shaped member, is concentrically arranged outside the fixed shaft 12, and has fixing holes at two upper and lower positions for attaching the reduced diameter tip ends of the stepped pins 52. By providing the reinforcing ring 52a, the tip ends of the two guide pins 83 can be connected to each other to prevent the guide gear 83 from falling, and the switching gear 56 can be prevented from slipping out to the front side. The internal gear 29 of the hub 13 is arranged on the radially outer side of the switching gear 56, and the fixed shaft 1 is provided on the radially inner side of the switching gear 56.
External gear 40 which is a part of the gear mechanism 16 extrapolated to 2
Are arranged.

As shown in FIGS. 6 and 7, the two tuning members 74 and 75 arranged between the first and second clutch members 42 and 42a have the same shape, so here, the first tuning member 74 and 75. Only the tuning member 74 provided on the clutch member 42 side will be described. The tuning member 74 is provided in a thin ring-shaped support portion 76 having an insertion hole 76a formed at the center thereof through which the fixed shaft 12 can be inserted, and two opposing outer sides of the ring-shaped support portion 76. It is surrounded by two straight lines passing through the center of 76 at an angle of about 71 degrees, a circle slightly larger than the outer shape of the ring-shaped support portion 76, and a circle having a diameter about twice that of the ring-shaped support portion 76. Adjusting unit 77, 7
8 and. The adjusting portions 77 and 78 project to one side in the axial direction of the ring-shaped support portion 76 (leftward in FIG. 6B) and have a thickness about twice that of the ring-shaped support portion 76. The adjusting portion 77 has a U-shaped notch groove 79 that is open in the forward direction (counterclockwise direction in FIG. 6A) and in the axial base side and is U-shaped in a side view. Further, although the notch groove 80 having the same shape is formed in the adjusting portion 78, the notch groove 8 is formed.
Reference numeral 0 indicates the forward direction in the circumferential direction, which is open to the front side in the axial direction.

As shown in FIGS. 1 and 7, the tuning member 74,
Reference numeral 75 denotes a base side between the first and second clutch members 42 and 42a so that one side in the axial direction of each ring-shaped support portion 76 faces each other so that the adjusting portions 77 and 78 do not overlap in the axial direction. It is arranged in order from. Further, the coil springs 84 and 85 are respectively provided in the cutout grooves 79 and 80 of the adjusting portions 77 and 78.
Are mounted with their both ends in contact with the circumferential ends of the cutout grooves 79, 80, respectively. Adjacent tuning member 7
The opening angle θ1 of the portion where the coil springs 84 and 85 of 4 and 75 are arranged is set to, for example, about 16 degrees. The switching ring 47 can be rotated in the forward direction and the backward direction within a range smaller than the angle θ1. The angle θ1 is set to be larger than the angle θ3.

The operation of the clutch mechanism 41 including the tuning members 74 and 75 will be described in more detail with reference to FIGS. 1 and 7. A lever arm (not shown) for operation can be attached to the switching ring 47. When the lever arm is rotated in the forward direction, the switching ring 47
The first clutch member 42 rotates in the forward direction via. The first clutch member 42 can be rotated up to 16 degrees (angle θ1) together with the switching ring 47, but the first clutch member 42 can be positioned when rotated by 15 degrees (angle θ3) by the positioning ball 46a and the biasing member that presses the ball 46a. Even if the lever arm is released in this state, it does not return to the original position. on the other hand,
Two stopper portions 65 of the first clutch member 42
Is rotated in the forward direction, and the tuning member 7 arranged on the front side.
The adjusting members 77 and 78 of No. 4 are pressed to adjust the tuning member 74.
Rotate in the forward direction. At this time, the turning angle of the lever arm, the switching ring 47, the first clutch member 42, and the tuning member 74 is 15 degrees (angle θ3).

When the tuning member 74 rotates in the forward direction, the coil springs 84 and 85 are compressed, and the stopper portion 66 of the second clutch member 42a is pressed in the forward direction via the front tuning member 75. At this time, the second clutch member 4
If the force for holding 2a is small, the second clutch member 42a rotates in the forward direction, and if the holding force is large, the second clutch member 42a receives the biasing force from the coil springs 84, 85 in the forward direction, It is waiting on the spot until the holding power becomes low. When the second clutch member 42a rotates in the forward direction, the biasing forces of the coil springs 84 and 85 disappear, and the lever arm, the switching ring 47, and the first clutch member 42 move in the forward direction from the initial position by 15 degrees. Degree (angle θ3)
It is stably supported in the rotated state.

From this state, when the lever arm is rotated in the backward direction and returned to the initial position, the switching ring 4
The first clutch member 42 is rotated by 15 degrees (angle θ3) in the backward direction via 7 to be positioned and stopped. Then, the tuning member 74 on the base side is pressed by the first clutch member 42 to rotate in the backward direction, and the second clutch member 42 is rotated.
The a receives the biasing force from the tuning member 75 on the front side in the backward direction. If the holding force is not applied to the second clutch member 42a, the second clutch member 42a pivots in the backward direction and returns to the initial position, and if the holding force is applied, the coil springs 84, 85. While receiving the biasing force from the backward direction, it waits on the spot until the holding force becomes small.

Next, the shape of the deformed hole 88 of the link arm 51 and the operations of the second clutch member 42 and the switching gear 56 will be described in detail. As shown in FIGS. 11A to 11C, the link arm 51 is supported by the stepped pin 52 of the clutch support member 20 that does not rotate with respect to the fixed shaft 12. On the other hand, the guide pin 83 that moves in the deformed hole 88
Is attached to the rotatable second clutch support member 42a, and the center position of the guide pin 83 is maintained at a constant distance from the center of the fixed shaft 12 to rotate the positions of P1 to P7. You can move. The angle between the adjacent positions of P1 to P7 with respect to the axis of the fixed shaft 12 is the angle θ3 between the adjacent positioning holes 20a of the clutch support member 20 = 3.
It is set to about 1/3 of 15 degrees, that is, about 5 degrees.

As shown in FIG. 11A, the guide pin 83
When the center of the switching gear 56 is at the position P4, the switching gear 56 is at a position separated from the internal gear 29 and the external gear 40 of the hub 13, and at this time, the first and second clutch members 42, 4
2a is arranged at the initial position (position shown in FIG. 9). When the guide pin 83 rotates within the range of P3 to P5, the deformed hole 88 is formed so that the distance from the axis of the fixed shaft 12 of P3 to P5 does not change, so that the position of the switching gear 56 is changed. Does not move. As shown in FIG. 11B, when the guide pin 83 rotates in the forward direction and moves in the range of P1 to P2, the switching gear 56 moves inside the hub 13 in the radial direction to the outside, and It is meshed with the internal gear 29. The deformed holes 88 are formed so that the distances P1 to P2 from the axis of the fixed shaft 12 do not change, so that the inter-axial distance between the switching gear 56 and the internal gear 29 can be kept constant and meshed. it can. When the guide pin 83 is at the position P1, the first and second clutch members 42 and 42a are in a state of being rotated by 15 degrees in the forward direction.

As shown in FIG. 11C, the guide pin 83
Is rotated in the range of P6 to P7, the switching gear 56
Is in a position meshing with the external gear 40. Deformed hole 88
Is formed so that the distance from the axis of the fixed shaft 12 of P6 to P7 does not change, so that the switching gear 56 can mesh with the external gear 40 with a constant axial distance. When the guide pin 83 is at the position P7, the first and second clutch members 42, 42a move in the backward direction by 1
It has been rotated 5 degrees. 11 (B), (C)
As shown in FIG. 7, the guide pins 83 are linearly connected between P5 to P6 and P2 to P3 with a movable width.
When 3 moves between P5 to P6 and P2 to P3, the link arm 51 rotates to switch the position of the switching gear 56.

When the guide pin 83 moves from P4 to P1, when the teeth of the switching gear 56 and the teeth of the internal gear 29 come into contact with each other, the guide pin 83 has a second position at an intermediate position between P3 and P2. The clutch member 42a stands by while receiving an urging force in the forward direction. When the guide pin 83 moves from P4 to P7 and the teeth of the switching gear 56 and the external gear 40 come into contact with each other, the guide pin 83 moves to P
The second clutch member 42a is provided at an intermediate position between 5 and P6.
It stands by while receiving a biasing force from the backward direction. With such a configuration, the switching gear 56 can be made to stand by in a state where a constant pressure is applied to the internal gear 29 or the external gear 40, and the meshing state switching operation can be smoothly performed. That is, the clutch mechanism 41 includes the switching ring 47.
Since the tuning members 74 and 75 are provided between the switching gear 56 and the switching gear 56, the switching gear 56 can be urged toward the internal gear 29 or the external gear 40 of the gear mechanism 16, and the hands can be released. Since it is possible to maintain a state in which a predetermined torque is applied and biased, it is possible to smoothly switch the power transmission state.

Next, the gear mechanism 16 arranged on the front side of the clutch mechanism 41 will be described. On the base side of the rotating plate 17, in order from the front side, the bearing portions 36 of the first and second planetary frames 32 and 33 of substantially the same shape shown in FIGS. 1, 9A and 9B, 37 is provided rotatably with respect to the fixed shaft 12. Bearing portion 3 of first and second planetary frames 32 and 33
Arms 38 and 39 are integrally provided at three positions every 120 degrees on the outer sides in the radial direction of 6 and 37, and support shaft portions projecting to the front side are formed at the front ends of the arms 38 and 39. First and second planetary gears 30, which mesh with the internal gear 29 and can revolve around the fixed shaft 12, are provided at the respective support shaft portions.
Each of the three 31 is rotatably attached.

A first sun gear 34 having the same axis as that of the rotary plate 17 is integrally provided on the rotary plate 17 on the base side of the rotary plate 17, and meshes with the first planetary gear 30. . Further, on the base side of the first planetary frame 32, a second sun gear 35 having the same shaft center as the bearing portion 36 of the first planetary frame 32 is integrally provided, and the second planetary gear 31 Meshes with.
Further, the second planetary frame 3 is provided on the base side of the second planetary frame 33.
The third planetary frame 33 is integrally provided with a connecting gear 40a having the same shaft center as that of the third bearing 37 and the same shape as the first and second sun gears 34 and 35. Connection gear 40
An external gear 40 is provided on the base side of a. The external gear 40 has a connecting tooth portion 41a which covers the connecting gear 40a from the base side and meshes in a non-rotatable state inside, and is integrated with the second planetary frame 33 at the time of use. Used in the state. Since the external gear 40 is manufactured in a state where it is separated from the second planetary frame 33, the first and second sun gears 3
4, 35 and the connecting gear 40a can be formed in substantially the same shape, and can be manufactured quickly. In addition, the first planetary frame 32, the second sun gear 35, and the second
Since the members in which the planetary frame 33 and the connection gear 40a are integrally provided have the same shape, the number of parts can be reduced and manufacturing control can be easily performed.

Next, referring to FIGS. 1 and 10, the rotary plate 17 and the front side of the rotary plate 17 are moved radially outward by the centrifugal force generated by the rotation of the wheels 58, and the hub 1
The brake shoe 19 that contacts the inner peripheral surface of the wheel 3 to reduce the rotational speed of the wheel 58 will be described. The rotary plate 17 provided on the front side of the fixed shaft 12 has a through hole 17a formed at the center thereof through which the fixed shaft 12 can be inserted, and a cylindrical bearing fitting portion 27 is provided around the front end of the through hole 17a. Bearing fitting portion 27
It is rotatably attached to the fixed shaft 12 via a bearing 59 fixed therein. As the material of the brake shoe body 53, for example, MC nylon, urethane rubber, natural rubber or the like having a large sliding resistance is used. Brake shoe 1
Reference numeral 9 denotes a semi-circular member, the end of which in the advancing direction in the circumferential direction is rotatably attached to the fixed pin 18 of the rotary plate 17. In addition, two fixed pins 18 provided on the rotary plate 17
At the positions respectively moved by 90 degrees around the fixed shaft 12, the fitting pins 18a having substantially the same shape as the fixing pins 18 are provided, and the center of the brake shoe 19 at the position where the fitting pins 18a overlap with the fitting pins 18a. An arcuate hole 19a centering on the fixing pin 18 is formed in the vicinity. The center angle of the arcuate hole 19a is, for example, about 5 degrees, and is configured so as not to contact the fixed shaft 12 even if the brake shoe 19 moves to the fixed shaft 12 side.

The outer peripheral surface of the brake shoe 19 in the radial direction in the backward direction is formed so as to have a small gap with the inner peripheral surface 16a of the hub 13. When the rotary plate 17 rotates at a different rotational speed from the hub 13 and a centrifugal force is applied to the brake shoe 19, the outer peripheral surface of the brake shoe 19 on the side closer to the fixed pin 18 (forward direction) is driven by the principle of leverage. A large force can be applied to the inner peripheral surface 16a of the hub 13 that abuts. When the rotating plate 17 rotates with the rotation of the wheels 58 and a centrifugal force is applied to the brake shoe 19, the brake shoe 19 rotates around the fixing pin 18 and moves to the outside in the radial direction of the rotating plate 17. , Inner surface 1 of hub 13
6a is contacted and pressed. With this configuration, the wheels 58 can be decelerated.

Although the brake shoe 19 is constructed so as to directly contact the inner peripheral surface 16a of the hub 13, a brake ring (not shown) is attached to the inner peripheral surface 16a of the hub 13 to attach the brake shoe 19 to the brake ring. It is also possible to make it contact with. With this configuration, the worn brake shoes 19 and the brake rings can be replaced, and the life of the device can be extended. It is also possible to attach a biasing means such as a spring to the end of the brake shoe 19 in the backward direction so that the brake shoe 19 is biased toward the axial center of the fixed shaft 12. With this configuration, the brake shoe 19 can be prevented from coming into contact with the hub 13 during normal operation. In order to prevent the radially inner peripheral surface of the brake shoe 19 from coming into contact with the ring-shaped cover member 14, the separation pin that comes into contact with the inner peripheral surface of the brake shoe 19 at the front side of the rotating plate 17 is provided. It is also possible to provide a separating flange.

Next, the power transmission state of the gear train of the gear mechanism 16 and the state of the brake shoe 19 will be described with reference to FIGS. 1 and 11A to 11C. Switching ring 47
11 to operate the switching gear 5 as shown in FIG. 11 (C).
When 6 is meshed with the internal gear 29 of the hub 13, the hub 1
No. 3 can rotate freely in the forward direction and locks when trying to rotate it in the backward direction. At this time, since the external gear 40 does not mesh with the switching gear 56, the second planetary frame 33
Can be idle. In this state, when the hub 13 is rotated in the forward direction, the first gear that meshes with the internal gear 29 of the hub 13 via the first and second planetary gears 30 and 31,
Since the second planetary frames 32 and 33 and the rotary plate 17 rotate at the same angular velocity as the hub 13, and the first and second planetary gears 30 and 31 revolve at the same angular velocity as the hub 13, the gear trains meshing with each other are , The state where the meshing position is not changed. Therefore, the brake shoe 19 provided on the rotary plate 17 rotates at the same speed as the hub 13 and does not receive a large centrifugal force, and therefore does not move in the radial direction.
Even if is moved outward in the radial direction and comes into contact with the inner circumference of the hub 13, the brake shoe 19 and the hub 13 are rotating at the same speed, so that the hub 13 is not decelerated.

In the present embodiment, the planetary gear mechanism is configured in two stages, and the speed ratio of the external gear 40 to the internal gear 29 is 10 to 5 when the second planetary frame 33 is locked.
Since it is set to 0 times (preferably 20 to 30 times),
The rotating plate 17 can be rotated at a high speed in a direction opposite to the rotating direction of the hub 13. Next, as shown in FIG. 11B, when the switching gear 56 is meshed with the external gear 40 that is integrally connected to the second planetary frame 33, the second planetary frame 3
3 can rotate freely in the backward direction and locks when it is rotated in the forward direction. In this state, when the hub 13 is rotated in the forward direction, the second planetary gear 31 and the second planetary frame 33 that mesh with the internal gear 29 of the hub 13 try to rotate in the forward direction. Since the planetary frame 33 is locked, only the second planetary gear 31 rotates in the forward direction without being able to revolve. Since the second planetary gear 31 meshes with the second sun gear 35, the second sun gear 35 and the first planetary frame 32 integrated with the second sun gear 35 rotate in the backward direction. The first planetary gear 30, which is attached to the first planetary frame 32 and revolves in the backward direction, includes the hub 1 that meshes with the first planetary gear 30.
Since the third internal gear 29 rotates in the forward direction, it rotates in the forward direction, and the first sun gear 34 that meshes with the first planetary gear 30 rotates in the backward direction.

Next, the switching gear 56 is moved to the second planetary frame 33.
When it is attempted to rotate the hub 13 in the backward direction while meshing with the external gear 40, the second planetary gear 31 meshing with the internal gear 29 of the hub 13 and the second planetary frame supporting the second planetary gear 31. 33 tries to rotate in the backward direction. Switching gear 56 meshing with external gear 40 and one-way clutch 55
Can freely rotate in the forward direction, so that the second planetary frame 33 provided with the external gear 40 can freely rotate in the backward direction. At this time, since the second planetary frame 33 is in the idling state, the gear train rotates at substantially the same speed as the hub 13, and the hub 13 is not decelerated. And
When the switching gear 56 is set so as not to mesh with either the internal gear 29 of the hub 13 or the external gear 40 of the second planetary frame 33, the hub 13 is free to move in either the forward or backward direction. Since the second planetary frame 33 can rotate, and the second planetary frame 33 rotates in either direction, the hub 13 is not decelerated. In this way, by switching the position of the switching gear 56, the rotation of the hub 13 can be restricted or the brake shoe 19 can be operated.

Next, referring to FIGS. 12A and 12B,
The connection state between the support 11 and the fixed shaft 12 will be described. The support 11 has a round hole 89 formed on the base side and a square hole 90 formed on the front side in a communicating state.
The fixed shaft 12 includes a square processing portion 24 on the front side of the expanded diameter portion 12a provided in the middle, and further includes a square processed portion 24a on the base side of the expanded diameter portion 12a, and supports the square processed portion 24a.
One square hole 90 can be fitted and fixed. Also,
On the front side and the base side of each of the squared portions 24, 24a,
Round tube portions 91 and 92 are provided, respectively. At the tip of the round tubular portion 91 on the front side, a nut-shaped retaining portion 93 that is arranged further on the front side of the ring-shaped cover member 14 and has an expanded loosening stopper that prevents the ring-shaped cover member 14 from falling off is provided. Are formed. Inside the fixed shaft 12, mounting holes 94 to 96 are formed so as to communicate with each other in the axial direction. The mounting hole 94 formed on the front side has a large diameter, and the coil spring 97 can be arranged inside. Further, the mounting hole 96 formed on the base side has a diameter slightly larger than that of the mounting hole 95 at the intermediate position. As shown in Figure 1,
The round cylinder portion 91 on the front side has a ring-shaped cover member 1 attached to the hub 13.
4, 15, bearings 60, 61, and clutch support member 20.
Is attached integrally and relatively rotatably via
The base side of the fixed shaft 12 is detachably attached to the simple vehicle body.

An advancing / retreating shaft 98 for mounting and demounting the fixed shaft 12 is disposed in the mounting holes 94 to 96. Advance axis 9
The reference numeral 8 includes a diameter-expanding shaft portion 99 which is expanded in diameter toward the base side and can be fitted into the mounting hole 96, and a diameter-increasing pressing portion 100 which can be fitted into the mounting hole 94 is provided at the front side. The coil spring 97 arranged inside the mounting hole 94 is arranged with the pressing portion 100 biased toward the front side. At the base end of the round tubular portion 92,
A plurality of, for example, two fixing holes 101, which penetrate the radial direction and communicate with the mounting hole 96, are formed. The fixing holes 101 are respectively provided with hooking balls 102 that can partially project outward in the radial direction from the outer peripheral surface of the round tubular portion 92. The outer ends of the fixing holes 101 in the radial direction are formed with a slightly reduced diameter so that the locking balls 102 do not fall. In a normal state, the retaining balls 102 are arranged in such a state that they are brought into contact with the outer periphery of the diameter-expanding shaft portion 99, respectively, and a part of the retaining balls 102 is projected outward from the fixing hole 101. Therefore, as shown in FIG. 1, the locking ball 102 can prevent the fixed shaft 12 from falling off while being locked to the base end of the support 11.

As shown in FIG. 12B, the pressing portion 100
When is pushed toward the base side against the coil spring 97, the diameter expansion shaft portion 99 of the advancing / retreating shaft 98 slightly moves to the base side. Then, since the diameter-enlarged shaft portion 99 separates from the locking ball 102, the locking ball 102 moves inward in the radial direction, and the outer end thereof is arranged radially inward from the outer peripheral surface of the round tubular portion 92. To be done. The fixed shaft 12 can be pulled out to the front side from the round hole 89 of the support 11 in a state where the advancing / retreating shaft 98 is moved to the base side with respect to the fixed shaft 12. With this configuration, the braking device 10
Since the maintenance can be performed with the wheelchair removed from the main body, the work can be easily performed.
Further, it can be easily mounted on a vehicle.

Next, referring to FIGS. 13A to 13C,
A method of using the braking device 10 when it is applied to a wheelchair 57 which is an example of a simple vehicle will be described. In addition, the white arrow in the figure represents the direction in which the mobile body can freely move, and the arrow with diagonal lines represents the direction in which the vehicle decelerates while moving. As shown in FIG. 13A, the wheels 58 of the wheelchair 57 are configured to rotate in the same direction as the hub 13 via spokes (not shown) around the hub 13. When traveling on level ground,
The switching ring 47 is fixed in the center so that the switching gear 56 is not meshed. In this state, the wheelchair 57 can travel freely forward and backward.

As shown in FIG. 13B, when traveling uphill, the switching ring 47 is rotated in the forward direction so that the switching gear 56 meshes with the internal gear 29 of the hub 13. In this state, the wheelchair 57 can only move forward,
You cannot move backwards. With this configuration, the slope can be efficiently climbed without using the hand brake. As shown in FIG. 13C, when traveling downhill, the switching ring 47 is rotated in the backward direction so that the switching gear 56 moves the external gear 4 of the second planetary frame 33.
Mesh with 0. In this state, move the wheelchair 57 forward,
The brakes are automatically applied when the speed exceeds a certain level. In addition, you can move back freely. that's all,
Although the embodiment according to the present invention has been described, the present invention is not limited to the above-mentioned embodiment, and for example, the coil springs 84, 8 for biasing the tuning members 74, 75 are provided.
5 can be changed according to the resistance when the link arm 51 and the switching gear 56 move.

[0041]

In the braking device for a simple vehicle according to the present invention, since the tuning member is provided, the switching gear is switched to the internal gear or the external gear while applying a certain amount of pressing force. The gears can be meshed with each other, and the meshing state can be switched easily and reliably. Further, since the gear mechanism is provided inside the hub, it is possible to reliably transmit power and perform an accurate operation, and it is possible to reduce the size. Further, since it has a speed reducing means that moves outward in the radial direction by centrifugal force, it is possible to automatically reduce the speed according to the speed of the wheel. Particularly, in the braking device for a simple vehicle according to claim 2, since the base side of the fixed shaft is detachably attached to the main body of the simple vehicle, for example, at the time of maintenance or failure of the braking device, the braking device together with the hub can be used as the simple vehicle. Can be easily removed and repaired, and repair work can be performed easily. Further, in the braking device for a simple vehicle according to the third aspect, since the first and second planetary gears are provided, the speed ratio of the gear mechanism can be increased and the size can be reduced. . Furthermore, since the switching gear with a one-way clutch is provided, when the switching gear is moved to the outside, the rotation direction of the hub can be restricted only to the forward direction, preventing the wheelchair from retreating uphill. can do. Further, when the switching gear is moved inward, the rotation of the hub can be transmitted to the speed reducing means, and when it is positioned in the middle, the hub can be freely rotated in both directions.

[Brief description of drawings]

FIG. 1 is a front sectional view of a braking device for a simplified vehicle according to an embodiment of the present invention.

FIG. 2 is a side view of a hub of the braking device for the simple vehicle.

3A and 3B are a left side view and a front sectional view, respectively, of a clutch support member of the braking device for the simplified vehicle.

4A and 4B are a left side view and a front sectional view, respectively, of a first clutch member of the braking device for the simple vehicle.

FIG. 5 is a right side view of a second clutch member of the braking device for the simple vehicle.

6 (A) and 6 (B) are a left side view and a front view of a tuning member of the braking device of the same vehicle, respectively.

FIG. 7 is an explanatory diagram of a clutch mechanism of the braking device of the same vehicle.

FIG. 8 is a left side view of a link arm of the braking device of the same vehicle.

9 (A) and 9 (B) are front cross-sectional views of a first planetary frame of the braking system of the same vehicle, and a first planetary gear on the first planetary frame of the braking system of the same vehicle. It is explanatory drawing of the state which attached.

FIG. 10 is a left side cross-sectional view showing a mounted state of a speed reducer of the braking device of the simple vehicle.

11 (A) to (C) are explanatory views showing the operation of the switching gear and the link arm of the braking device of the same simple vehicle during free rotation, during one-way rotation restriction, and during operation of the speed reduction means, respectively.

12 (A) and 12 (B) are an explanatory view showing a fixed shaft and a support attached / detached state of the braking device of the same vehicle, and a partially enlarged front sectional view showing a base end portion of the fixed shaft, respectively.

13A to 13C are explanatory views showing states of flat traveling, uphill traveling, and downhill traveling when the braking device of the same simple vehicle is applied to a wheelchair.

[Explanation of symbols]

10: Braking device, 11: Support, 12: Fixed shaft, 12
a: expanded diameter part, 13: hub, 13a: spoke attachment flange, 14, 15: ring-shaped cover member, 16: gear mechanism, 16a: inner peripheral surface of hub, 17: rotating plate, 17a: through hole, 18: Fixed pin, 18a: Fitting pin, 19: Brake shoe (decelerator), 19a: Arc hole, 20: Clutch support member, 20a: Positioning hole, 21: Mounting hole, 22: Partial flange portion, 23: Mounting plate , 23a:
Cylindrical part, 24, 24a: Square processing part, 25: Square hole, 2
6: Arc-shaped hole, 27: Bearing fitting portion, 29: Internal gear, 3
0: first planetary gear, 31: second planetary gear, 32: first planetary frame, 33: second planetary frame, 34: first sun gear, 35: second sun gear, 36, 37: Bearing part, 3
8, 39: Arms, 40: External gears, 40a: Connection gears, 41: Clutch mechanism, 41a: Connection teeth, 42:
1st clutch member, 42a: 2nd clutch member, 4
3: insertion hole, 43a: dent, 44: turning pin, 44
a, 45, 45a: mounting hole, 46: female screw portion, 46
a: positioning ball, 47: switching ring, 48: insertion hole, 49: mounting hole, 50: male screw member, 51: link arm, 52: stepped pin, 52a: reinforcing ring, 5
3: Brake shoe body, 55: One-way clutch, 5
6: switching gear, 57: wheelchair (simple vehicle), 58: wheels, 59: bearing, 60: bearing, 61: bearing, 65, 6
6: stopper part, 67: outer peripheral edge part, 68, 69: female screw part, 70, 71: fixed part, 72: insertion hole, 73: sleeve part, 74, 75: tuning member, 76: ring-shaped support part, 76a : Insertion hole, 77, 78: adjustment part, 79, 8
0: Notch groove, 83: Guide pin, 84, 85: Coil spring, 86: Mounting hole, 86a: Sleeve part, 87: Fixed shaft, 88: Deformed hole, 89: Round hole, 90: Square hole, 91, 9
2: round cylinder portion, 93: retaining portion, 94 to 96: mounting holes,
97: coil spring, 98: advancing / retreating shaft, 99: expanded diameter shaft portion, 1
00: pressing part, 101: fixing hole, 102: hook ball

Continued front page    F-term (reference) 3D046 AA00 BB17 BB26 LL14                 3D050 AA01 DD01 JJ01                 3J058 AA03 AA07 AA13 AA17 AA24                       AA30 CA01 CC06 CC66 CC76                       FA09                 3J062 AA01 AA18 AB06 AC02 BA12                       BA14 BA22 CG03 CG14 CG62                       CG84

Claims (3)

[Claims] 1. A braking device for a simple vehicle, which is provided inside a hub of a wheel of a simple vehicle and controls the rotation of the wheel, the fixed shaft being provided in a body of the simple vehicle and rotatably supporting the hub. A gear mechanism that is provided inside the hub and that receives rotation of the wheel as an input; and a rotation plate that is rotatably provided on the fixed shaft and is connected to the gear mechanism and that has a rotational speed different from that of the hub. A decelerating unit that is swingably provided on the rotating plate, moves radially outward by a centrifugal force generated by the rotation of the wheels, contacts the inner peripheral surface of the hub to decelerate the wheels, and the fixed shaft. It is swingable,
A clutch mechanism provided with an internal gear formed on the inner circumference of the hub and one of the gear mechanisms, or provided with a switching gear that can be disengaged, and provided on one side in the axial direction of the hub,
A switching ring capable of operating the radial position of the switching gear, and wherein the clutch mechanism directs the switching gear between the switching ring and the switching gear toward the internal gear or the gear mechanism. A braking device for a simple vehicle, comprising a tuning member for urging, and smoothly switching between power transmission states. 2. The braking device for a simple vehicle according to claim 1, wherein a front side of the fixed shaft is integrally and relatively rotatably attached to the hub, and a base side of the fixed shaft is: A braking device for a simple vehicle, which is detachably attached to the simple vehicle body. 3. The braking device for a simplified vehicle according to claim 1 or 2, wherein the gear mechanism meshes with the internal gear and is capable of revolving around the fixed shaft. The first and second planetary gears are rotatably attached to each other, and the first and second planetary frames rotatable about the fixed shaft, and the hub rotating in a direction opposite to the rotation direction of the hub. A first sun gear that is provided on a rotating plate and that meshes with the first planetary gear; a second sun gear that is provided on the first planetary frame and that meshes with the second planetary gear; 2 has an external gear provided on the planetary frame, the switching gear of the clutch mechanism includes a one-way clutch, and the rotation of the hub is restricted by switching the position of the switching gear, or A braking device for a simple vehicle, characterized in that it operates deceleration means.