JP2009133398A - Non-stage transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a low cost non-stage transmission which is mounted on all-purpose bicycles, while sufficiently securing a variation width of a change gear ratio. <P>SOLUTION: The non-stage transmission A has: an input gear 12 and a large circular plate 13 to mutually rotate and engage around an axle 11; a pair of small circular plates 21 contacting with the large circular plate 13 while engaging and rotating with a square shank 27 substantially orthogonal to the axle 11; a first and a second bevel gear 15, 17; an output side bush 19; and a first and second connecting member 45, 47 which can rotate, interlocking with the output side bush 19. The non-stage transmission A further has inner side and outer side magnetic bodies 30, 31 with N and S poles divided into four, a position control plate 35 which varies the position by a reciprocating plate 39, and controls a slide position on the square shank 27 of the small circular plate 21 and controls the change gear ratio according to the torque. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a continuously variable transmission mounted on a vehicle such as a bicycle.

Conventionally, various proposals have been made for continuously variable transmissions that do not require manual switching as mechanisms for changing the transmission ratio of a bicycle.
For example, in the technique disclosed in Patent Document 1, when the pedal force of the crank pedal becomes strong, for example, when climbing, when the torque transmitted from the crank pedal shaft exceeds the set torque, the deceleration position is automatically set. In order to change, the width of the pulley having the V-groove is made variable so that the gear ratio is continuously changed according to the position of the belt having a predetermined width.
Patent Document 2 discloses a structure provided with a plurality of link units that convert the rotational motion of the input shaft into a swinging motion and a one-way clutch that converts the swinging motion into a rotational motion of the output shaft. ing.
Further, Patent Document 3 includes a pair of large and small discs that come into contact with each other as a continuously variable transmission for a three-wheeled vehicle or a four-wheeled vehicle such as a disabled person or an elderly person, both of which are continuously variable transmissions. A structure that also functions as a differential transmission is disclosed.

JP-A-9-144824 JP 2004-1650 A JP 10-89432 A

  However, the structure of the continuously variable transmission of Patent Documents 1 and 2 is complicated, and it is difficult to reduce the cost to the extent that it can be put into practical use as a component of a general-purpose bicycle. On the other hand, the structure of the continuously variable transmission of Patent Document 3 is a simple structure capable of relatively reducing costs, but from the viewpoint of the function as a continuously variable transmission, it is difficult to secure a large change ratio of the gear ratio. There is.

  An object of the present invention is to provide a low-cost continuously variable transmission that can be mounted on a general-purpose bicycle or the like while ensuring a sufficient range of change in gear ratio.

  A continuously variable transmission according to the present invention is provided with a large disk that can rotate around a first axis, a second disk that can rotate around a second axis that intersects the first axis, and that can slide along the second axis. A small disk on the second shaft according to the load applied to the output side rotating body by transmitting the rotation of the large disk from the small disk to the output side rotating body by friction force. Is provided with a sliding position control mechanism for controlling the speed ratio.

  As a result, the gear ratio can be continuously controlled according to the load with a simple configuration. And if the sliding range of a small disc is lengthened, the change range of a gear ratio can be ensured easily easily. Therefore, a low-cost continuously variable transmission that can be mounted on a general-purpose bicycle or the like is obtained.

  Since the inner circumference of the small disk has a taper, the small disk can slide smoothly, and the speed ratio can be quickly switched. In particular, it is more preferable to provide a taper that expands on both sides, with the inner circumference of the small disk having a minimum diameter at an intermediate position.

  The sliding position control mechanism has a plurality of N poles and S poles, an inner magnet body that rotates in conjunction with the output side rotating body, a plurality of N poles and S poles, and an inner magnet An outer magnet body rotatably provided around the body, a reciprocating body provided to be interlocked with the outer magnet body, a limiting mechanism for limiting a rotation range of the reciprocating body, and a rotation of the reciprocating body. By having an interlocking mechanism that interlocks the moving width and the sliding position on the second axis of the small disk, the sliding position of the small rotating plate through the interlocking mechanism according to the rotational speed of the output side rotating body, That is, the gear ratio can be controlled reliably.

  The sliding position control mechanism has a mechanism that releases the connection state between the outer magnet body and the reciprocating body, thereby eliminating unnecessary movement of the reciprocating body in some situations such as when the load is stable. Therefore, it is possible to reduce the energy consumed for traveling a bicycle or the like.

  According to the continuously variable transmission of the present invention, it is possible to obtain a low-cost continuously variable transmission that can be mounted on a general-purpose bicycle or the like while ensuring a sufficient range of change in the gear ratio.

-Outline structure of continuously variable transmission-
FIG. 1 is a longitudinal sectional view showing a structure of a continuously variable transmission for a bicycle according to an embodiment of the present invention. 2 is a cross-sectional view of the continuously variable transmission according to the embodiment taken along line II-II shown in FIG.
As shown in FIGS. 1 and 2, the continuously variable transmission A according to this embodiment includes an axle 11 (first shaft) that serves as a rotating shaft of a rear wheel of a bicycle and a rotational force of a pedal via a chain. In response, the input gear 12 and the large disk 13 that rotate in conjunction with each other around the axle 11, the angular shaft 27 (second axis) that is substantially orthogonal to the axle 11, and the angular gear 27 rotate in conjunction with each other, And a pair of small disks 21 in contact with the large disk 13. The inner peripheral portion of the small disc 21 is a square hole 21a so that it can rotate in conjunction with the angular shaft 27, and the small disc 21 can easily slide along the angular axis 27 as will be described later. As can be seen, the square hole 21 a is provided in a tapered shape that loosely fits the square shaft 27.

  The input gear 12 and the large disc 13 have a wedge-shaped connecting portion, and when the input gear 12 starts to rotate by stepping on the pedal, the large disc 13 is moved slightly to the left in the figure. . As a result, the large disk 13 is strongly pressed against the small disk 21, and the two are interlocked by the frictional force. The outer peripheral portion of the small disk 21 that contacts the large disk 13 is formed of rubber so as to ensure a large frictional force. On the other hand, when the pedal is released, the pressing force between the large disk 13 and the small disk 21 becomes weak, and as a result, the small disk 21 can slide along the angular axis 27.

  The continuously variable transmission A is provided between the first bevel gear 15 fixed to the tip of the angular shaft 27 and the fixing member FL1 so as to be rotatable around the axle 11 via a radial bearing RB. A second bevel gear 17 that meshes with the first bevel gear 15, an output-side bush 19 connected to the second bevel gear 17, a first connection member 45 that can rotate in conjunction with the output-side bush 19, and an output gear 50. And a second connecting member 47 that is attached to the output gear 50 and engages with the first connecting member 45.

  That is, when the small disk 21 rotates at a speed ratio determined according to the position of the small disk 21 on the square shaft 27, the output-side bush 19 rotates via the first and second bevel gears 15 and 17. The rotation is transmitted to the output gear 50 via the first and second connecting members 45 and 47. As a result, the stepping on the pedal causes rotation of the rear wheel of the bicycle. The output-side bush 19, the first and second connecting members 45 and 47, and the output gear 50 function as an output-side rotating body that rotates at a predetermined speed ratio with respect to the rotation of the input gear 12 and the large disc 13. .

-Configuration of sliding position control mechanism-
Next, position control (gear ratio control) on the small shaft 21 on the angular axis 27 will be described.
As shown in FIGS. 1 and 2, as a member connected to each small disk 21, a deformed plate 23 (see FIG. 5) rotatably attached via a radial bearing RB around the outer periphery of the protruding portion 21 b of the small disk 21. 3), an arm member 25 rotatably attached to the edge of the deformed plate 23 by a screw 24, and a position control plate 35 connected to the tip of the arm member 25 by a screw 36.

  In addition, an outer side of the output side bush 19 is arranged with an inner magnet body 30 having four divided N poles and S poles, and an outer side of the inner magnet body 30, and the inner magnet body 30 is arranged with a certain gap. An outer magnet body 31 having four divided N poles and S poles, and a magnet cover 33 that tightly covers the outer magnet body 31 are provided. The position control plate 35 and the magnet cover 33 are provided so as to be relatively rotatable via a radial bearing RB. When the position control plate 35 is at the solid line position shown in FIG. 2, the small disc 21 connected to the arm member 25 is positioned on the inner side of the square shaft 27 and the output gear 50 rotates at a relatively low speed. When the position control plate 35 is located at the two-dot chain line position shown in FIG. 2, the small disk 21 is positioned on the outer side of the square shaft 27 and the output gear 50 rotates at a relatively high speed (shown in FIG. 1). position).

  In the present embodiment, two pairs of small disks 21, a square shaft 27, a deformed plate 23, an arm member 25, and the like are attached to the position control plate 35, so that the sliding position control mechanism serves as a differential gear. However, it is not always necessary to provide two sets of these members. Even if only one set of small disk 21, square shaft 27, deformed plate 23, arm member 25, etc. is provided, the sliding position control function is provided. It can be demonstrated.

  Further, between the magnet cover 33 and the output gear 50, the first and second connecting members 45 and 47 described above and the outer periphery of the magnet cover 33 are rotatable relative to the magnet cover 33 via a radial bearing RB. A reciprocating plate 39 attached to the clutch, a clutch member 40 engaged with the inner periphery of the reciprocating plate 39, a thrust bearing TB interposed between the clutch member 40 and the first connecting member, and the tip of the magnet cover 33 A compression spring 41 is disposed between the first member and the clutch member 40.

  A stopper pin 42 and a position control pin 44 are attached to two opposing positions on the outer peripheral portion of the reciprocating plate 39. The position control pin 44 is engaged with a position control cam 38 attached to the position control plate 35. On the other hand, the stopper pin 42 is configured to be engageable with two stopper cams 37a and 37b attached to the fixing member FL2.

-Operation of sliding position control mechanism-
FIG. 4 is a plan view showing the basic principle of sliding position control in the present embodiment. In FIG. 4, the shape of each member is shown modified from the shape of the present embodiment. When the distal end cylindrical portion 17a of the second bevel gear 17 rotates (counterclockwise in FIG. 4) and the inner magnet body 32 rotates in cooperation therewith, the action of the repulsive force between the same poles and the attractive force between the different poles. Thus, the outer magnet body 33 and the magnet cover 33 are rotated in the same direction. At this time, since the clutch member 40 is fitted to the inner peripheral portion of the reciprocating plate 39, the reciprocating plate 39 rotates in the same direction, but when the stopper pin 42 hits one stopper cam 37b, the outer magnet The body 31, the magnet cover 33, and the reciprocating plate 39 rotate in opposite directions (clockwise in FIG. 4). When the inner magnet body 30 rotates at a low speed, the outer magnet body 31, the magnet cover 33, and the reciprocating plate 39 rotate clockwise until the stopper pin 42 hits the stopper cam 37a, and counterclockwise when it hits the stopper. Repeat the motion of rotating.

  On the other hand, when the rotation speed of the inner magnet body 30 exceeds a certain rotation speed (about 80 rpm in the present embodiment), the outer magnet body 31, the magnet cover 33, and the reciprocating motion plate 39 are moved before the stopper pin 42 hits the stopper cam 37a. From the clockwise rotation to the counterclockwise rotation. That is, the angle α between the position where the rotation is reversed and the stopper cam 37b is determined according to the rotation speed.

  Therefore, by holding the position of the position control cam 38 of the position control plate 35 at a position where the position control pin 44 attached to the reciprocating plate 39 is reversed, as shown in FIG. The angular position of is determined. Then, the sliding position of the small circular plate 21 on the angular axis 27 can be controlled via the arm member 25 in accordance with the angular position of the position control plate 35. At this time, as shown in the lower left diagram of FIG. 2, if the inner periphery of the small disk 21 is provided in a tapered shape, the small disk 21 is swung when the small disk 21 slides on the square shaft 27. Since this causes an axial vector component, sliding is facilitated.

  FIG. 5 is a view for explaining the engagement between the stopper pin 42 of the reciprocating plate 39 and the stopper cams 37a and 37b. The stopper cams 37a and 37b are provided so as to be rotatable around a rotation shaft (not shown in FIG. 1) in FIG. 5 and are pulled to one side by a tension spring. It is in the position shown in the stopper cam 37b. On the other hand, when the stopper pin 42 hits the stopper cam 37a due to the rotation of the reciprocating plate 39 interlocked with the outer magnet body 31, the stopper cam 37a rotates to stop the stopper pin 42. However, when the outer magnet body 31 (reciprocating plate 39) rotates at a high speed, the reciprocating plate 39 reverses before the stopper pin 42 hits the stopper cam 37a.

  On the other hand, the position control cam 38 is pulled in the direction shown in FIG. 5, and when the position control pin 44 rotates clockwise and abuts against the position control cam 44, the position control pin 44 and the position control cam 38 is engaged, and the position control plate 35 is rotated clockwise. On the other hand, when the position control pin 44 is reversed (counterclockwise), the engagement between the two is released and the position of the position control pin 44 is maintained. However, if the state where the rotational force of the pedal is not applied is continued, the contact state between the large disk 13 and the small disk 21 is loosened, so that the small disk 21 can move along the angular axis 27. Accordingly, the position control plate 35 is rotatable, that is, the position control cam 38 is movable. Then, the engagement position of the position control pin 44 and the position control cam 38 is controlled according to the new pedal torque (torque), and the small circle is determined from the rotational speed of the input gear 12 (large disk 13). The gear ratio to the rotation speed of the plate 21 (output gear 50) is controlled to be constant.

  That is, the stopper pin 42 and the stopper cams 37a and 37b function as a limiting mechanism that limits the rotation range of the reciprocating body (reciprocating plate 39). Further, the position control plate 35, the position control pin 44, and the arm member 25 are configured such that the rotational width of the reciprocating body (reciprocating motion plate 39) and the sliding position on the second axis (angular axis 27) of the small circular plate 21. It functions as an interlocking mechanism that interlocks with.

On the other hand, once the transmission ratio is determined, the position of the position control cam 38 is not changed, but the reciprocating plate 39 is reciprocated according to the rotation of the inner magnet body 30 regardless of this. As a result, extra energy is consumed. Therefore, a clutch member 40 and first and second connecting members 45 and 47 for releasing the cooperative movement (connected state) between the magnet cover 33 and the reciprocating plate 39 are provided.

FIGS. 6A and 6B are a side view and a cross-sectional view of the first connection member 45 and the second connection member 47 in order to explain the operation of the connection release mechanism.
As shown in FIG. 6 (a), the outer periphery of the magnet cover 33 (tip portion) and the inner periphery of the clutch member 40 are both loosely fitted with an octagonal cross section, and the two cooperate with each other. However, relative movement is possible in the axial direction. Similarly, the outer periphery of the clutch member 40 and the inner periphery of the reciprocating motion plate 39 also have an octagonal cross section and are loosely fitted to each other and rotate together, but move relative to each other in the axial direction. Is possible. Further, although not shown in FIG. 5, the inner periphery (not shown in FIG. 5) of the first connecting member 45 also has an octagonal cross section, and the outer periphery of the octagonal output side bush 19 Since they are loosely fitted, they rotate in unison with each other, but relative movement in the axial direction is possible.

  With the above structure, when the first connecting member 45 rotates in the direction of the arrow in the cross section shown in FIG. 6B, the torque does not reach the frictional force between the first connecting member 45 and the second connecting member 47. On the other hand, the 1st connection member 45 and the 2nd connection member 47 rotate integrally. On the other hand, when the torque exceeds a predetermined value (in this embodiment, the limit torque between the inner magnet body 30 and the outer magnet body 31-for example, 0.6 kg weight (about 5.9 N)), the compression spring 41 resists the compressive force. Then, the first connecting member 45 is moved to the right. As a result, the clutch member 40 and the reciprocating plate 39 are disengaged. Thereby, the useless torque by reciprocating the reciprocating motion plate 35 can be reduced, and the bicycle travel can be lightened.

-Effect of the present invention-
According to the continuously variable transmission of this embodiment, it is possible to continuously change the gear ratio according to the load (torque) applied to the pedal when the bicycle is running.
For example, when the load applied to the pedal is small on a flat road or downhill, the rotational speed of the small disk 21 increases via the input gear 12 and the large disk 13. On the other hand, the force that presses the large disk 13 to the left in the figure from the input gear 12 shown in FIG. 1 is weakened, so that the frictional force between the large disk 13 and the small disk 21 is weakened. 21 becomes slidable along the angular axis 27. Further, since the pressing force between the first connecting member 45 and the second connecting member 47 is also weakened, the clutch member 40 is connected to the state shown in FIG. In this state, the rotational speed of the output side bush 19, the first and second connecting members 45, 47, and the output gear 50 increases, and the position control pin 44 of the reciprocating plate 39 shown in FIG. Move to the right. That is, when the load is small, the small disk 21 moves outward on the square shaft 27 and changes in a direction in which the load increases, that is, in a direction in which the gear ratio increases.

  On the other hand, if you want to reduce the gear ratio on an uphill, stop pedaling. Then, the force for pressing the large disk 13 to the left in the figure from the input gear 12 shown in FIG. 1 is almost eliminated, and the frictional force between the large disk 13 and the small disk 21 becomes weak, and the small disk 21 becomes slidable along the angular axis 27. Further, since the pressing force between the first connecting member 45 and the second connecting member 47 is also weakened, the clutch member 40 is connected to the state shown in FIG. By not stepping on the pedal, the rotational speed of the small disk 21 decreases, so that the rotational speeds of the output side bush 19, the first and second connecting members 45, 47, and the output gear 50 decrease. Accordingly, the position control pin 44 of the reciprocating plate 39 shown in FIG. 2 moves to the left in the drawing. That is, the small disc 21 moves outward on the angular axis 27 and changes in a direction in which the load is reduced, that is, in a direction in which the gear ratio is reduced.

  As described above, the gear ratio can be determined so that the torque applied to the pedal is substantially constant. That is, the gear ratio is easily adjusted according to the state of the road on which the bicycle runs and the leg strength of the user.

  Moreover, the continuously variable transmission A according to the present embodiment does not use a complicated belt mechanism or multi-stage gear, so that the manufacturing cost can be reduced. In addition, by sliding the small disk 21 along the angular axis 27, a sufficient range of change in the gear ratio can be ensured. Therefore, it is possible to provide a low-cost continuously variable transmission that can be mounted on a general-purpose bicycle while ensuring the change width of the gear ratio.

  In particular, by providing the inner periphery of the small disc 21 (in this embodiment, the square hole 21a) in a tapered shape, the small disc 21 can smoothly slide along the angular axis 27, and the gear ratio can be quickly switched. Is possible. In particular, as shown in FIG. 2, it is more preferable that the inner circumference of the small circular plate 21 has a minimum diameter at a midway portion and is provided with a taper that expands on both sides, so that sliding can be smoother.

  Furthermore, by providing a connection release mechanism comprising the clutch member 40, the compression spring 41, and the first and second connection members 45 and 47, unnecessary reciprocation of the reciprocation plate 39 is eliminated, and a load during traveling of the bicycle is eliminated. Can be reduced.

  In the above embodiment, an example in which the continuously variable transmission of the present invention is used in a bicycle has been described. However, the continuously variable transmission of the present invention is not limited to a bicycle (two-wheeled vehicle), but is a tricycle for persons with physical disabilities and children. It can also be used for four-wheeled vehicles and unicycles. Moreover, it can be used not only for two-wheeled vehicles, three-wheeled vehicles, four-wheeled vehicles, etc., but also for two-wheeled vehicles, three-wheeled vehicles, four-wheeled vehicles, etc. that use electricity as a power source. In that case, an effect of reducing power consumption can be exhibited by reducing useless loads.

  The structure of the embodiment of the present invention disclosed above is merely an example, and the scope of the present invention is not limited to the scope of these descriptions. The scope of the present invention is indicated by the description of the scope of claims, and further includes meanings equivalent to the description of the scope of claims and all modifications within the scope.

  The continuously variable transmission of the present invention can be used as a transmission mechanism for a unicycle, a two-wheeled vehicle, a three-wheeled vehicle, a four-wheeled vehicle or the like.

1 is a longitudinal sectional view showing the structure of a continuously variable transmission for a bicycle according to an embodiment of the present invention. It is sectional drawing in the II-II line | wire shown in FIG. 1 of the continuously variable transmission which concerns on embodiment. It is a top view of a small disk and a variant board concerning an embodiment. It is a top view which shows the basic principle of sliding position control in embodiment. It is a figure for demonstrating engagement with the stopper pin and stopper cam of a reciprocating plate. (A), (b) is a side view for demonstrating operation | movement of a connection cancellation | release mechanism in order, and sectional drawing of an engaging member and a to-be-engaged member.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Axle 12 Input gear 13 Large disk 15 1st bevel gear 17 2nd bevel gear 17a Tip cylinder part 19 Output side bush
21 Small disk 21a Square hole 21b Protruding part 23 Profile plate 24 Screw 25 Arm member 27 Square shaft 30 Inner magnet body 31 Outer magnet body 33 Magnet cover 35 Position control plate 36 Screw 37a, 37b Stopper cam 38 Position control cam 39 Reciprocating motion Plate 40 Clutch member 41 Compression spring 42 Stopper pin 44 Position control pin 45 First connecting member 47 Second connecting member 50 Output gear RB Radial bearing TB Thrust bearing FL1, FL2 Fixing member

Claims (4)

A large disk that can rotate about the first axis under rotational force;
A small disk that is rotatable about a second axis that intersects the first axis and is slidable along the second axis, and transmits the rotation of the large disk by a frictional force;
An output-side rotating body that transmits the rotation of the small disk to the wheel side;
A sliding position control mechanism for controlling a gear ratio by controlling a position of the small disk on the second shaft according to a load applied to the output-side rotating body;
A continuously variable transmission. The continuously variable transmission according to claim 1, wherein
A continuously variable transmission in which the inner circumference of the small disk has a taper. The continuously variable transmission according to claim 1 or 2,
The sliding position control mechanism is
An inner magnet body having a plurality of N poles and S poles alternately arranged in the circumferential direction and rotating in conjunction with the output side rotating body;
An outer magnet body having a plurality of N poles and S poles alternately arranged in the circumferential direction, and rotatably provided around the inner magnet body;
A reciprocating body provided to be interlocked with the outer magnet body;
A limiting mechanism for limiting the rotation range of the reciprocating body;
An interlocking mechanism that interlocks the rotational width of the reciprocating body with the sliding position of the small disk on the second axis;
A continuously variable transmission. The continuously variable transmission according to claim 3,
The said sliding position control mechanism is a continuously variable transmission which has a mechanism which cancels | releases the connection state of the said outer magnet body and the said reciprocating body when the load more than a setting value acts.

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