JPH0246342A - Variable speed gear for car - Google Patents

Abstract

PURPOSE: To change a gear ratio steplessly by providing a roller holding member with a plurality of rollers movably in a circumferential direction, fitting the rollers rollably into radial grooves formed at a driving disc, and providing lock mechanism for locking these rollers unmovably to the holding member. CONSTITUTION: A driving disc 1 is fitted to a rear wheel hub or the like of a bicycle, and a roller holding member 2 is fitted to a driving sprocket of the bicycle. When the member 2 is rotatory-driven, a roller assembly held thereto comes into the position of a pressing member 422. Then an elastic part 28 of a spring 27 is deformed abutting the member 422, and an engaging roller 26 moves frontward in a rotating direction to engage the roller assembly unmovably with the member 2. The rotational force of the member 2 is transmitted to the disc 1 through the roller 24 of the roller assembly in the engaged state and a groove 12. When a cable 46 is pulled to decenter the member 2, the abutting position of the roller 24 to the groove 12 of the disc 1 changes, and the distance between this position and the rotational center of the disc 1 changes.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a transmission device for a vehicle such as a bicycle, a two-wheeled vehicle, a three-wheeled vehicle, a four-wheeled vehicle, etc., a vehicle that is driven by human power, or a small motorcycle, and more specifically, The present invention relates to a transmission device that can change the transmission ratio steplessly, has a simple structure, and is lightweight.

[Prior Art] Generally, as a conventional bicycle transmission device, a device in which a plurality of sprockets of different diameters are provided on the rear wheel and the drive chain is selectively engaged with these sprockets to change the speed is widely used. ing. However, with this type of gear, the gear ratio can only be changed in stages, and if you try to increase the range of change in the gear ratio, the number of sprockets increases, making the structure complex and large. There are restrictions on For this reason, the limited power of human power cannot be used effectively, and it is not satisfactory as a bicycle transmission. On the other hand, a device that can change the gear ratio steplessly can effectively utilize human power and is suitable as a transmission device for bicycles or small vehicles.

An example of such a continuously variable transmission is U.S. Patent No. 3,913,945 by C1ark. This thing is
A lever is pivotally mounted to the front of the frame and extends to both sides of the rear. Furthermore, each pedal lever is connected to a chenno by a cable, and this chenno is connected to the rear wheel via a one-way clutch. The connection point between this cable and the lever is configured to be changeable, and the gear ratio can be adjusted by changing the arm length of this lever. However, this device has many parts and has a complicated structure. Also,
Particularly when driving at high speeds, there is a problem that the lever and shaft unit used for shifting gears interfere with the action of the pedals. In general, conventional continuously variable transmission devices for bicycles have complicated structures and have problems with reliable operation.

[Problems to be Solved by the Invention] The present invention has been made in order to solve the problems of conventional continuously variable transmission devices for bicycles.

[Means for Solving the Problems] The device of the present invention includes a drive disk, in which a plurality of grooves are formed substantially along the radial direction.

Further, a roller holding member is provided, and this roller holding member has an annular groove formed therein, and this roller holding member faces the above-mentioned drive disk. A plurality of roller assemblies are slidably held within this annular groove. Each of these roller assemblies is provided with a protruding roller, and these rollers are rotatably fitted into the radial groove of the drive disk. Further, a locking mechanism is provided, and when the roller holding member rotates, the locking mechanism locks the roller assemblies held therein only while the roller assemblies held therein pass through a predetermined circumferential range. is engaged with the roller holding member so as not to move in the circumferential direction. Further, a speed change mechanism is provided, which shifts the roller holding member eccentrically relative to the drive disk, and changes the contact position between the roller of the locked roller assembly and the groove of the drive disk to the drive disk. This changes the distance from the center of rotation to change the gear ratio.

[Operation] In the device of the present invention, the drive disk is attached to the driven side, such as the hub of the rear wheel of a bicycle, and the roller holding member is attached to the drive side, for example, the drive sprocket of the bicycle. When this roller holding member is rotationally driven, the roller assembly held thereon is fixed to the roller holding body by the locking mechanism as it passes through a predetermined circumferential range, and the roller assembly is fixed to the roller holding member in this locked range. The drive disk is rotated via the rollers of the assembly and the grooves of the drive disk. For example, when this roller holding member is eccentrically set by the variable speed mechanism, the position where the roller of the locked roller assembly contacts the groove of the drive disk changes, and this contact position and the rotation center of the drive disk change. The distance between the Therefore, the speed ratio when driving this drive disk changes.

This change in gear ratio is stepless, and the structure of this device is simple.

[Example] Hereinafter, the present invention will be described in detail with reference to the drawings.

1 to 15 show a first embodiment of the present invention. FIG. 1 shows a bicycle equipped with the device of the present invention. In the figure, 5 is a rear wheel, 33 is a driving chino, and 34 is a pedal.

The rear wheel 5 is equipped with a transmission according to the present invention. Reference numeral 1 denotes its drive disk, which is attached to the hub of the rear wheel 5 via a one-way clutch. Also, 2
is a roller holding member, to which a driving sprocket 3 is attached, and when the pedal 34 is depressed, the roller holding member 2 is driven to rotate. Note that 35 is a roller for adjusting the tension of the ceno. Further, a speed change lever 47 is attached to, for example, a handlebar of this bicycle, and this speed change lever is connected to this speed change device via a cable 46.

Next, details of this transmission will be explained. FIG. 2 is a front view of the main parts of this transmission, and FIG. 3 is a side view. This device is equipped with the drive disk 1 described above. As shown in FIG. 4, this drive disk 1 has a substantially disk shape, and has a hole 1 formed in the center for attachment to a rear wheel hub (not shown), and a plurality of holes, for example, six diameter holes. direction groove 1
2 is formed. As shown in FIG. 13, these grooves 12 are formed such that the front edge of the drive disk 1 in the rotational direction runs along the radial direction of the drive disk. The drive disk 1 of this embodiment is formed by press-forming a steel plate to form the grooves 12, as shown in FIG.

Further, a roller holding member 2 faces the side surface of the drive disk 1 with a slight gap therebetween. This roller holding member 2 has an annular shape, and a thread is formed on its outer periphery, and a thread 31 formed on the inner periphery of the drive sprocket 3 described above as shown in FIG. 5 is screwed into this outer periphery. The roller holding member 2 and sprocket 3 are assembled integrally. This drive sprocket 3 is formed with teeth 32 that mesh with a chino 33. And this roller holding member 2
An annular outer groove 22 is formed on the side surface of the roller holding member 2, and an annular inner groove 22a is formed on the inner peripheral surface of the roller holding member 2. Further, a support plate 42 is provided on the side of the roller holding member 2 and faces the roller holding member 2 in close proximity thereto. This support plate 42 has a plurality of support rollers 421, for example, three support rollers.
These support rollers 421 are rotatably fitted into the inner groove 22a on the inner peripheral surface of the roller holding member 2, and the roller holding member 2 is fitted into the support plate 42. It is rotatably supported. This support plate 42 is attached to and supported by the shaft 51 of the rear wheel via the plate 41.

A plurality of roller assemblies as shown in FIGS. 6 to 8 are arranged in the outer groove 22 on the side surface of the roller holding member 2. As shown in FIGS. The number of these roller assemblies is the same as the number of grooves 12 in the drive disk 1. Each of the roller assemblies has a sliding block 23 that is slidably fitted within the outer groove 22. Each of these sliding blocks 23 is provided with a roller 24, and these rollers 24 protrude from the side surface of this roller holding member 2, and these rollers 24 fit into the groove 12 of the corresponding drive disk 1.
It is fitted so that it can roll freely.

Further, a locking mechanism is provided for immovably locking these roller assemblies within the outer groove 22 of the roller holding member 2. That is, each of the above sliding blocks 23 is formed with a wedge portion 25, and this wedge portion 25 is formed in a shape such that the width of the wedge portion 25 gradually decreases toward the rear side in the rotational direction of the roller holding member 2. There is. Stopper wall portions 251 and 252 are formed at both front and rear ends of the wedge portion 25, respectively. Two locking rollers 2 are provided on each side of these wedge portions 25.
6 is placed. These locking rollers 26 are configured to fit between the slope of the wedge portion 25 and the circumferential surface of the outer groove 22, and this roller assembly moves relative to this roller holding member 2 in the rotation direction thereof. However, it is configured to prevent movement in the opposite direction to the rotational direction. Each of these roller assemblies is provided with a spring 27. This spring 27 is a leaf spring, and one end thereof holds the above-mentioned locking roller 26, and the other end is attached to this sliding block 23. A dogleg-shaped elastic portion 28 is formed on the spring 27, and the elastic force of the elastic portion 28 urges the locking roller 26 toward the rear in the rotational direction of the roller holding member 2. Therefore, in a normal state, these locking rollers 26 and the wedge portion 25 of the sliding block 23 are disengaged, and these roller assemblies freely move within the outer groove 22 of the roller holding member 2. It is constructed so that it can be slid. Further, the elastic portion 28 of the spring 27 protrudes inward from the inner circumferential surface of the roller holding member 2. When the elastic portions 28 are pressed outward, the elastic portions 28 are deformed and the locking rollers 26 move forward in the rotation direction, and these locking rollers 26 engage the wedge portions 25 of the sliding block 23. It is engaged between the slope portion and the circumferential surface of the outer groove 22, so that the roller assembly is engaged with the roller holding member 2 so that it cannot move rearward in the direction of rotation thereof.

Further, a pressing member 422 is provided to protrude from the support plate 42 . This pressing member 422 has an arc shape and is arranged along the inner circumferential surface of the roller holding member 2.

When the roller holding member 2 rotates and the roller assembly reaches the position of the suppressing member 422, the elastic portion 28 of the spring 27 comes into contact with the pressing member 422 and is deformed, causing the roller assembly to engage. The stop roller 26 is moved forward in the rotational direction, and the roller assembly is immovably engaged with the roller holding member 2.

Therefore, the rotational force of this roller holding member 2 is transmitted to this drive disk 1 via the roller 24 of the roller assembly in the engaged state of: and the groove 12 of the drive disk 1.

The length of the pressing member 422 is set to approximately correspond to the arrangement pitch of these roller assemblies, and one roller assembly is configured to correspond to this pressing member 422 at all times. Therefore, the rotational force of the roller holding member 2 is transmitted to the drive disk 1 via one roller assembly corresponding to this suppression member 422, and the other roller assemblies are transmitted to this roller holding member 2. It is in a freely sliding state and does not contribute to the transmission of rotational force. Further, the rollers 24 of these roller assemblies are each connected to the groove 1 of the drive disk 1.
2 so that the other roller assembly in this slidable condition rotates with this drive disk 1;
A predetermined pitch interval is maintained.

The speed change ratio of this transmission device is changed by making the roller holding member 2 and the support plate 42 eccentric with respect to the drive disk 1. That is, when these are made eccentric, the distance between the position where the roller 24 of the roller assembly in the engaged state contacts the groove 12 of the drive disk 1 and the center of rotation of the drive disk 1 changes. In contrast, roller 2 of the roller assembly in this engaged state
4 is always at a constant distance from the rotation center of this roller holding member 2. Therefore, the speed is changed based on the difference in these circumferential velocities. Such eccentricity of the roller holding member 2 is achieved by a speed change mechanism described below.

That is, as described above, this roller holding member 2 is rotatably supported by the support plate 42.

Further, in the above-mentioned mounting, the plate 41 is attached to the shaft 51 of the rear wheel. The rear end of the roller holding member 42 is rotatably supported by a pivot shaft 412 on the rear end of the plate 41 .

Therefore, this roller holding member 2 is attached to this pivot shaft 412.
It is configured to rotate in the vertical direction, that is, in the direction in which the above-mentioned suppressing member 422 is arranged.

Note that an arcuate guide groove 42 is provided in the center of the support plate 42.
3 is formed, and a rear wheel shaft 51 is slidably inserted into this guide groove. Further, in the above-mentioned installation, a bracket portion 411 is formed at the front end of the plate 41, and a guide rod 44 is inserted through this bracket portion 411. This guide rod 44 is prevented from being removed by a pin 411. This guide rod 44 extends rearward and is connected to the lower part of the rear end of the support plate 42 via a stopper mechanism.

This stopper mechanism is constructed as follows.

That is, a pin 4 is provided at the lower part of the rear end of the support plate 42.
25 is provided in a protruding manner, and a pair of stopper claws 431 are pivotally attached to this pin 425. Holes are formed at the tips of these stopper claws 431, and the guide rod 44 passes through these holes. A coil spring 433 is interposed between these stopper claws 431, and urges these stopper claws 431 in a direction away from each other. These stopper claws 431 have holes in their tips engaged with the guide rod 422 in a state where their tips are inclined so as to separate from each other. Therefore, in this state, the stopper claw 431 and the bottle 425 are immovable with respect to the guide rod 44.

Further, 45 is a moving member, and this moving member 45 is approximately U
It has a letter-like shape, and holes are formed in each of its legs, and the guide rod 44 is slidably passed through these holes.

The stopper claw 431 described above is housed between these legs. Therefore, when this moving member 45 moves, the leg portion of this moving member moves to one stopper claw 431.
Since the stopper claw 431 and the guide rod 44 are disengaged from each other, the stopper claw 431 and the bottle 425 move together with the moving member 45 along the guide rod 44 . Therefore, the support plate 42 and the roller holding member 2 are connected to the pivot shaft 412.
It rotates around , and is eccentric in the vertical direction with respect to the drive disk 1. In addition, the above-mentioned moving member 45 and the mounting plate 41
A compression coil spring 442 is interposed between the moving member 45 and the bracket portion 411, and this spring urges the moving member 45 to move rearward. A cable 46 is connected to the above-mentioned moving member 45, and this cable 46 is connected to the above-mentioned speed change lever 47. Therefore, when the speed change lever 47 is operated and the cable 46 is pulled, the support plate 42 and the roller holding member 2 are eccentrically moved upwardly, and when the cable is loosened, they are eccentrically downwardly moved. Further, when the speed change lever 47 is not operated, the pair of stopper claws 431 engage in both the front and rear directions, and the roller holding member 2 and the support plate 42 are held in that position.

Further, the above drive disk l is shown in FIGS. 13 and 14.
It is attached to the rear wheel 5 via a one-way clutch mechanism as shown in the figure. That is, a large number of holes 483 are formed in the hub 481 of the rear wheel 5 along the circumferential direction. One or more clutch keys 482 are provided in the driving member 1 so as to be freely protrusive and retractable in correspondence with these holes 483, and these clutch keys 282 are supported by springs 48.
4 in the protruding direction. The tip of the clutch key 482 is formed into an inclined surface, and when the drive disk 1 rotates the rear wheel 5 in the forward direction, the clutch key 482 engages with the hole 483 of the hub 481 and rotates. In the case of rotation in the opposite direction, the clutch keys 482 are disengaged and the rear wheel 5 is configured to rotate freely.

Next, the operation of this transmission will be explained. First, when the rider steps on the pedal 34 of this bicycle, the roller holding member 2 is rotated via the chain pedal 33 and the drive sprocket 3.

When the roller assembly held by the roller holding member 2 reaches the position of the pressing member 422, the elastic portion 28 of the spring 27 comes into contact with the pressing member 422 and is deformed, causing the engagement roller 26 to deform. moves forward in the rotational direction, and the roller assembly is immovably engaged with the roller holding member 2. Therefore, the rotational force of the roller holding member 2 is transmitted to the drive disc 1 through the roller 24 of the roller assembly in this engaged state and the groove 12 of the drive disc 1, and the rear wheel 5 is rotated to rotate the bicycle. runs.

When the rotation center of the roller holding member 2 is coincident with the rotation center of the drive disk 1, that is, when the roller holding member 2 is not eccentric as shown in FIGS. 2 and 9, The distance between the roller 24 of this roller assembly and the center of rotation of this roller holding member 2 is equal to the distance between the abutment position of this roller 24 and groove 12 and the center of rotation of drive disk 1. . Therefore, the gear ratio in this case is 1. In addition, the above-mentioned gear shift lever 47
When the cable 46 is pulled by operating the roller holding member 2, the roller holding member 2 is eccentrically moved upward, that is, in the direction in which the pressing member 422 is arranged, as shown in FIG.

In this case, the distance from the roller 24 to the rotation center of the roller holding member 2 does not change, but the distance between the roller 24 and the groove 1
The distance from the abutting position with drive disk 2 to the center of rotation of drive disk 1 increases. Since the circumferential speed of the roller 24 does not change, in this case, the speed is changed in accordance with the ratio of the distances to the rotation centers. Note that the gear ratio in this case is 1 or less, that is, deceleration, and the driving torque of the rear wheels 5 becomes large. On the other hand, if you loosen the cable 46,
As shown in FIG. 12, this roller holding member 2 is eccentrically downward. Therefore, the distance between the abutment position of the roller 24 and the groove 12 and the rotation center of the drive disk 1 becomes smaller.
In this case, the gear ratio is 1 or more, that is, the speed is increased. In this way, by operating the speed change lever 47, an arbitrary speed change ratio can be selected, and this speed change can be performed steplessly.

Note that this transmission transmits rotational force only by the roller assembly that corresponds to the pressing member 422, so the roller assembly that corresponds to this pressing member 422 separates from this pressing member and transfers to the next roller assembly. When the solid body corresponds to this pressing member, some impact occurs. However, this transmission is intended for transmission of relatively small amounts of power, and the various parts are not damaged by this impact. In order to reduce such impact, the number of roller assemblies may be increased. For example, in the case of a bicycle, if the number of roller assemblies is four, the rider will feel a slight shock when stepping on the pedals, but if the number of roller assemblies is six, You will hardly feel the shock. Therefore, when this transmission is applied to a bicycle, the number of roller assemblies should be four or more, preferably six or more. Incidentally, FIG. 15 schematically shows the relationship between the roller 24 and the groove 12.

In addition, in the case of this embodiment, as shown in FIG.
The front edge of the groove 12 in the drive disk 1 in the rotational direction is slightly inclined and arranged exactly along the radial direction of the drive disk 1. With this arrangement, when the drive disk 1 is rotationally driven via the roller 24,
Generation of radial component force on these rollers 24 is prevented.

In addition, since the drive disc 1 is attached to the hub of the rear wheel 5 via a one-way clutch mechanism, there is no need to rotate the pedals when coasting or when applying sudden braking, which is more convenient than before. It is as easy to drive as a bicycle.

Note that the present invention is not limited to the above embodiments.

For example, FIGS. 16-18 show a second embodiment of the present invention. This second embodiment differs from the first embodiment in the engagement mechanism of the roller assembly. That is, in this embodiment, a large number of sawtooth locking teeth 221a are provided on the outer peripheral surface of the outer groove 22 of the roller holding member 2.
is formed. Each roller assembly is provided with a locking pawl 26a, and these locking pawls 26a are urged by a spring 280 so as to disengage from the locking teeth 221a. Also, this spring 2
A contact portion 29 is formed at 90, and this contact portion protrudes from the inner circumferential surface of the roller holding member 2. When the contact portion 29 contacts the contact member 422, the locking pawl 26a engages with the locking tooth 221a, and the roller assembly cannot move relative to the roller holding member 2. It is configured to be locked to. It should be noted that this second embodiment has the same structure as the first embodiment except for the above-mentioned unintended structure, and also has the same operation.

Further, FIGS. 19 and 20 show a third embodiment of the present invention. In this embodiment, the roller holding member 2 is eccentric with respect to the drive disk 1 from the beginning. A pressing member 47 is rotatably provided at the center of the support plate 42a of the roller holding member 2. An arcuate surface 471 is formed at the tip of the suppressing member 47. This pressing member 47 is a spring 47
4 to rotate counterclockwise. Further, a pulley 473 is attached to the shaft 472 of this pressing member 47.
A cable 46 is installed in the groove 46 of the boot.
is wound. When the cable 46 is pulled by operating the speed change lever 47, the pressing member 47 is rotated from the position indicated by the broken line in FIG. 19 to the position indicated by the two-dot chain line. In this case, the roller assembly corresponding to the arcuate surface 471 of the suppressing member 47 is immovably locked to the roller holding member 2.

The roller holding member 2 is eccentric with respect to the drive disk 1 from the beginning, and by rotating the pressing member 47, the position at which the roller assembly is locked changes, and the position at which the roller assembly is locked changes. The distance between the contact position between the roller 24 of the roller assembly and the groove of the drive disk 1 and the center of rotation of the drive disk 1 is continuously changed. therefore,
Rotating this pressing member 47 is the same as making this roller holding member 2 eccentric as described above, and the speed ratio can be changed steplessly as in the above embodiment.

Further, FIG. 21 shows a fourth embodiment of the present invention. In this device, instead of forming a groove in the drive disk 1, a groove hole 12a is formed in the drive disk 1, and a roller 24 is fitted into the groove hole 12a so as to be able to freely roll. In this case, the drive disk 1 is easy to manufacture. Note that the configuration other than this is the same as that of the previous embodiment.

Furthermore, FIG. 22 shows a locking mechanism according to a fifth embodiment of the present invention. This is the sliding block 23 of the roller assembly.
A pair of wedge portions 25a are formed on the outside of the wedge portions 25a, and locking rollers 26a are provided on the outside and inside of these wedge portions 25a, respectively.
These locking rollers 26a are urged forward in the rotational direction of the roller holding member 2 by a spring 27a. Therefore, this roller assembly freely moves in the forward direction of the rotational direction relative to the roller holding member 2, but does not move in the rearward direction of the rotational direction. In this embodiment, the suppressing member 422
is not provided. In this embodiment, when the roller holding member 2 is eccentric with respect to the driving disk 1, the circumferential speed of the driving disk 1 is the slowest relative to the circumferential speed of the outer groove 22 of the roller holding member 20, for example, as shown in FIG. The roller assembly is engaged with the roller holding member 2 only in the upper portion, and rotational force is transmitted to the drive disk 1 via the roller assembly only in this portion.

In other parts, the circumferential speed of the drive disk 1 is relatively faster than the circumferential speed of the outer groove 22 of the roller holding member 2, so the roller assembly at these positions is Move the inner part forward in the direction of rotation,
No rotational force is transmitted. In this embodiment, since there is no need to provide the suppressing member 422 as described above, the structure is simple. Furthermore, the outer locking roller 26a and the inner locking roller 2
6a are aligned in the radial direction R of the circular outer groove 22, and the roller assembly is configured to slide and lock smoothly and reliably.

Further, FIG. 23 shows a sixth embodiment of the present invention. In this case, the front edge of the groove 12b of the drive disk 1 is inclined by an angle θ with respect to the radial direction 1a of the drive disk 1. In this embodiment, the roller holding member 2 is urged by a spring (not shown) or the like so as to move downward in FIG. 23. This produces a radially outward, ie upward component force on the roller 24 when the drive disk 1 is driven by the roller 24. When the torque of the rear wheel 5 increases, for example when the bicycle climbs a slope, this component force increases,
As a result, the roller holding member 2 is eccentrically upward until this component force and the urging force of the spring urging the roller holding member 2 downward are balanced. Therefore, when the torque applied to the rear wheels 5 increases, the reduction ratio automatically increases.
Furthermore, when the rear wheel torque decreases, the reduction ratio automatically decreases. Therefore, this device can automatically change gears without operating the gear shift lever. The characteristics of this automatic speed change depend on the slope θ of the groove 12a and the roller holding member 2.
Any desired characteristics can be obtained by setting the relationship between the spring characteristics and the spring characteristics that apply the force. Also,
By making the groove 12a curved, the component force generated on the roller 24 changes in accordance with the amount of eccentricity of the roller holding member 2, so that the characteristics of this automatic speed change can be set over a wider range.

Further, FIG. 24 shows another example of the one-way clutch mechanism as shown in FIGS. 13 and 14. In this vehicle, a disk-shaped intermediate drive member 485 is interposed between the drive disk 1 and the hub 481 of the rear wheel 5. and,
The hub 481 is provided with a plurality of buffer members 486. These buffer members 486 are made of an elastic material such as synthetic rubber, have a substantially disk shape, and are integrally embedded in the knob 481. In addition, the above intermediate drive member 4
A plurality of pins 4851 are provided protruding from the buffer member 85, and these pins are integrally embedded in the center of the buffer member 486. The intermediate drive member 485 also has the thirteenth
Similar to the one-way clutch mechanism in the figure, a large number of holes 483 are formed along the circumferential direction. A clutch key 482 provided on the drive disk 1 is engaged with these holes 483 by the biasing force of a spring 484, and is configured to function as a one-way clutch.

Such a one-way clutch mechanism includes the above-mentioned buffer member 48.
Since the torque is transmitted through the transmission gear 6, torque fluctuations and other vibrations are absorbed, the load applied to the transmission of the present invention is reduced, and smoother running characteristics can be obtained.

Furthermore, FIG. 25 shows another example of the transmission mechanism.

That is, 42' in the figure is a support plate, and the roller holding member is rotatably held on this support plate via a support roller 421'', and the pressing member 42 is similarly held as before.
2- is provided protrudingly. This support plate 42' is rotatably supported on the plate 41' by a pivot shaft 412', and the plate 41' is attached to the shaft of the rear wheel 5, etc. in the same manner as described above. . In addition, for this installation, a speed change cam body 43- is rotatably attached to the plate 41''. This speed change cam body 43' is formed by stamping a plate material, and a cam groove 431- of a predetermined shape is formed. has been done.

A slider 426' is attached to the support plate 42'' via a pin 425'', and the slider 426'' is slidably fitted into the cam groove 431'. Also,
A pulley 45- is attached to the above-mentioned speed change cam body 43', and a cable 46' is wound around this pulley.This cable is connected to the above-mentioned speed change lever 47, etc. When the cable 46' is pulled, the speed change cam body 43' is configured to rotate counterclockwise in the figure. Also, this speed change cam body 43' is biased to rotate clockwise by a spring 44', and when the cable 46' is loosened, this speed change cam body 43' is rotated clockwise by the biasing force of this spring. It is configured to rotate.

In this case, as the speed change cam body 43' rotates, the slider 426' slides in the cam groove 431', the support plate 42' rotates, and the slider 426' is biased against the drive disk. The gear ratio changes with care.

Also, this thing is connected to the support plate 42' through the cam groove 431''.
is moved, so if the shape of this cam groove is set appropriately, this support plate 42-
The relationship between the amount of eccentricity can be set arbitrarily, and the speed change characteristics can be set to various types. Moreover, if the slope of this cam groove is made gentle, this eccentric cam body will not rotate due to the load from the support plate 42-. Therefore, there is no need to provide a special stopper mechanism as in the embodiments described above.

Furthermore, it is clear that the present invention is not limited to the above-described embodiments, and that various modifications can be made.

[Effects of the Invention] As described above, the present invention provides a roller holding member with a plurality of rollers movable in the circumferential direction, and the rollers are fitted in the radial groove formed by the drive disk so as to be freely rolling. , a locking mechanism is provided that locks these gorges immovably to the roller holding member only at a portion in the circumferential direction of the roller holding member, and the driving disk is removed from the roller holding member via the locked roller. The drive disk is configured to transmit rotational force to the drive disk, and is provided with a speed change mechanism that changes the distance between the contact position of the locked roller and the groove and the center of rotation of the drive disk. Therefore, the gear ratio can be adjusted steplessly, the structure is simple, and the effects are great.

[Brief explanation of the drawing]

1 to 14 show a first embodiment of the present invention,
Fig. 1 is a diagram schematically showing the entire bicycle equipped with the transmission of the present invention, Fig. 2 is a front view of the transmission of the invention, and Fig. 3 is a rear view of the transmission of Fig. 2. 4 is a perspective view of the drive disk, FIG. 5 is a perspective view of the drive sprocket, FIG. 6 is a front view showing the relationship between the roller holding member and the roller assembly, and FIG. 7 is a side view thereof. Figure 8 is a detailed view of the roller assembly, Figure 9 is a front view of the transmission mechanism,
Fig. 10 is a top view thereof, Figs. 11 and 12 are front views showing the eccentric state of the support plate, Fig. 13 is a side view of the one-way clutch mechanism, and Fig. 14 is a line 14-14 in Fig. 13. FIG. Moreover, FIG. 15 is a schematic diagram explaining the operation. 16 to 18 are views showing a second embodiment of the present invention, in which FIG. 16 is a front view of the roller holding member and roller assembly, FIG. 17 is a side view, and FIG. 18 is a view of the roller assembly. FIG. 3 shows a detailed view of the assembly. Figure 19 and 2
FIG. 0 shows a third embodiment of the present invention, FIG. 19 is a front view of the main part, and FIG. 20 is a side view thereof. Figure 21 is the fourth
FIG. 3 is a front view of the drive disk of the embodiment. FIG. 22 is a front view showing details of the roller assembly of the fifth embodiment. FIG. 23 is a front view of the drive disk of the sixth embodiment. FIG. 24 is a partially sectional side view showing another example of the one-way clutch mechanism. FIG. 25 is a side view showing another example of the transmission mechanism. 1... Drive disk, 2... Roller holding member, 12
...Groove, 22...Outside groove, 24...Roller, 23
...Sliding block, 25...Wedge part, 26...
Locking roller, 27... Spring, 42... Support plate, 422... Spring

Claims (10)

[Claims] (1) A drive disk connected to the driven side is provided, and this drive disk has a plurality of grooves formed along the approximate radial direction, and a roller retainer facing the drive disk and connected to the drive side The roller holding member has an annular groove formed therein, and a plurality of roller assemblies are slidably fitted into the grooves of the roller holding member, and these roller assemblies is provided with rollers, these rollers are rotatably fitted in the radial groove of the drive disk, and the roller assembly is moved to a predetermined portion of the circumferential direction of the roller holding member. It is equipped with a locking mechanism that locks the roller holding member immovably only within the range, and from the position where the roller of the roller assembly in this locked state contacts the groove of the drive disk, the drive disk is A transmission device for a vehicle, comprising a transmission mechanism that changes a distance to a center of rotation. (2) The locking mechanism includes: a wedge portion formed on the roller assembly; a locking roller disposed between the wedge portion and a wall of the groove of the roller holding member; A pressing member disposed close to the roller holding member over a predetermined circumferential range, and a spring biasing the locking roller to move rearward in the rotational direction of the roller holding member, the spring When a part of the locking roller comes into contact with the pressing member, the locking roller is moved forward in the rotation direction, and the roller is pressed between the wedge portion and the wall of the groove to close the roller assembly. 2. The vehicle transmission device according to claim 1, wherein the transmission device is immovably locked to the roller holding member. (3) The locking mechanism includes a large number of locking teeth formed on the wall of the groove of the roller holder, and locking teeth that are respectively provided on the roller assembly and removably engage with the locking teeth. A retaining pawl, a pressing member disposed close to the roller holding member over a predetermined range in the circumferential direction of the roller holding member, and a spring biasing the retaining pawl to a disengaged state, the spring When a portion of the roller assembly comes into contact with the pressing member, the locking pawl engages with the locking tooth, and the roller assembly is immovably locked with respect to the roller holding member. A transmission device for a vehicle according to claim 1 of the preceding patent. (4) The locking mechanism includes: a wedge portion formed on the roller assembly; a locking roller disposed between the wedge portion and the wall of the groove of the roller holding member; a spring that biases the roller toward the front side in the rotational direction of the roller holding member, which allows the roller assembly to move forward in the rotational direction relative to the roller holding member; Claim 1 is characterized in that it prevents movement of
Transmission device for the vehicle described in Section 1. (5) The locking mechanism includes outer and inner locking rollers provided between the outer and inner surfaces of the wedge portion and the groove wall of the roller holding member, and the locking rollers include outer and inner locking rollers. 5. The vehicle transmission device according to claim 4, wherein the locking rollers are aligned in the radial direction of the groove. (6) The speed change mechanism makes the roller holding member eccentric with respect to the drive disk, thereby shifting the drive disk from the abutment position of the roller of the roller assembly in the locked state and the groove of the drive disk. The vehicle transmission device according to claim 1, characterized in that the transmission device changes the distance to the center of rotation. (7) The sixth aspect of the present invention is characterized in that the roller holding member is moved via a cam body.
Transmission device for the vehicle described in Section 1. (8) The roller holding member is arranged eccentrically by a certain amount with respect to the drive disk, and the speed change mechanism moves the pressing member in the circumferential direction of the roller holding member, thereby causing the locking. Claims 1 to 10 are characterized in that the distance from the contact position of the roller of the roller assembly in the state of contact with the groove of the drive disk to the center of rotation of the drive disk is changed. The vehicle transmission device according to any one of Item 3. (9) The groove of the drive disk is arranged obliquely with respect to the radial direction of the drive disk, and is configured to apply a radial component force to the roller of the roller assembly that fits into the groove. The first aspect of the present invention is characterized in that the transmission mechanism includes a spring that biases the roller holding member eccentrically, and balances the biasing force of the spring with the component force described above. The vehicle transmission device according to any one of items 1 to 4. (10) The above-mentioned claim characterized in that the drive disk is connected to the wheels of the vehicle via a one-way clutch mechanism that transmits only forward torque and a buffer member that absorbs fluctuations in torque. The vehicle transmission device according to item 1.