JPS63154488A - Non-stage transmission for bicycle - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention (Industrial Field of Application) The present invention is an automatic transmission device mainly suitable for bicycle transmissions, which can perform stepless speed transmission by double feed meshing with internal ratchets. This invention relates to a gear transmission.

(Prior Art) The present applicant previously filed Japanese Patent Application No. 77557.77558.77559 for a continuously variable bicycle transmission.

(Problems to be Solved by the Invention) However, in the device of the prior application mentioned above, the contact between the internal ratchet provided on the inner periphery of the drive rotating member and several pawls is
Since this occurs also outside the transmission area, there is a problem in that noise is generated due to the sliding contact between the ratchet and the pawl.

In addition, the above device has a problem in that when a reverse input is applied, pulsation occurs in the output of the reverse input because the engagement between the pawl and the internal tooth ratchet occurs even outside the transmission range under normal human power. There was a point.

(Means for Solving the Problems) In order to solve the above-mentioned problems, in the present invention, an internal ratchet is provided on the inner periphery of the driving rotating member, and the base of the pawl that meshes with the internal ratchet is connected to the driven rotating member. In a device in which the eccentricity of the driven rotary member can be freely adjusted with respect to the driving rotary member, and the rear wheel is driven by the driven rotary member, a protrusion branched from the tip of the pawl is provided. and after the pawl and the internal ratchet are engaged in a transmission range, the protrusion comes into sliding contact with the driving rotation member to release the engaged state, thereby configuring the continuously variable transmission for a bicycle. .

(Function) Since the device of the present invention is configured as described above, after the pawl and the internal tooth ratchet are engaged in the transmission range, the protrusion provided on the pawl comes into sliding contact with the drive rotating member, so that the pawl and the internal tooth ratchet are engaged. It is possible to release the meshing state with the ratchet.

Therefore, it is possible to eliminate noise caused by sliding contact between the pawl and the internal tooth ratchet, and to reduce output pulsation of reverse input at the time of reverse input.

(Example) Hereinafter, an example of the continuously variable transmission device for a bicycle according to the present invention will be described with reference to the drawings.

In the figure, 1 is a bicycle frame chain stay, 2 (see Figure 2) is a back fork, 3 is a rear claw, 4 is a rear wheel hub shaft fixed to the rear claw 3 with a lock nut 5, and 6 is rotatable via a bearing 7. The rear wheel hub is fitted into the rear wheel hub, and 8 is the spoke.

In this embodiment, a substantially hollow cylindrical driven rotating body 9 is fitted to the lower rear wheel hub shaft 4 in FIG. It is designed to rotate as one. Reference numeral 11 denotes a ring member which is integrally screwed together with the driven rotating body 9, and has a groove for supporting a ball bearing 12 formed therein.

13 is a ring plate fitted to the rear wheel hub shaft 4 on the lower side of the driven rotor 9 in FIG. 1, 14 is a ball bearing interposed between the ring plate 13 and the driven rotor 9, and 15 is a This is a disc-shaped cover inserted between the ring plate 13 and the lock nut 5.

Further, 16 is a shaft cylinder rotatably provided via the ball bearing 12 and a ball bearing 17 provided on the outer periphery of the driven rotor 9, and 18 is a hollow disc-shaped eccentric cam integrally connected to this shaft cylinder. 18a is an eccentric cam disk 1
As shown in FIG. 2 vs. 1 like D2. Only eccentric.

Reference numeral 19 denotes a ring-shaped eccentric cam ring that is partially fitted into the inner periphery of the outer peripheral edge taa of the eccentric cam disc 18 and is rotatably provided, and a bearing ring member fitted on the inner periphery of the eccentric cam ring 19. As shown in FIG. 5, the center of the circle formed by the inner circumferential surface 1911 of the cam disk 19a is 0.0. It is eccentric by β2 as shown in FIG. Note that in the case of this embodiment, 1 = L. Further, 19C is an annular groove provided on the outer peripheral surface of the eccentric cam ring 19;
Eccentric cam ring 1 20 is engaged with this annular groove 19c.
This is an engagement pin 9 which has a locking function and is screwed in from the outside of the outer peripheral edge 18a. Further, 19d (see Fig. 1.4.5) is an arc-shaped groove carved on the side surface of the eccentric cam ring 19 (this is an arc-shaped groove extending over an area of about 120°), and 21 is an arc-shaped groove carved in the side surface of the eccentric cam ring 19 (see Fig. 1.4.5).
This is a stopper pin that protrudes from the eccentric cam disc 18 so as to fit into the stopper pin 9d.

Reference numeral 22 denotes a hollow cylindrical driving rotation member, which is rotatably provided within the eccentric cam ring 19 via a ball bearing 23. Reference numeral 22a denotes a holding ring for the ball bearing 23, which is screwed onto the eccentric cam ring 19. A sprocket 24 is integrally fitted to the outer periphery of the portion protruding from the eccentric cam ring 19. 25 is the sprocket 24 and the sprocket (
This is a cheno played 7 times over (not shown).

Two rows of internal tooth ratchets (IJ songs 7) are fitted into the inner peripheral portion of the drive rotating member 22 via a one-way clutch 26. 26a (see FIG. 4) is a ball of the one-way clutch 26, and 26b is a spring. This one-way clutch 26 may be of other types.

27a is an internal ratchet of the internal ratchet ring 27, and 27b is an annular groove provided in the middle of the internal ratchet 27a. The bases of a plurality of pawls 28 (in this embodiment, three pawls in each row) that mesh with the internal ratchets 27a are pivoted to the driven rotary body 9 by pins 29 at positions equally divided on the left and right alternate circumferences. The spring 30 (
(see Figure 3), the winter melon 28 always has internal tooth ratchet)
It is urged to rotate in the direction of meshing with 27a. Further, as shown in Fig. 3.4.5, a protrusion 28a branched from the tip of the claw 28 is provided, and a roller 32 is rotatably provided at the tip of the protrusion 28a via a pin 31. The transmission range between the pawl 28 and the internal tooth ratchet 27a (in this embodiment, there are a total of six pawls 28, so the transmission range of the winter melon 28 is 360 ÷6=60°, so the range is approximately 60°.
By making contact with the pawl 28 and the internal tooth ratchet) 27
It is configured to release the meshing state with a. That is, the pawl 28 meshes with the internal ratchet 27a within the transmission area, but after that, the roller 32 engages with the annular groove 27b.
By contacting the pawl 28 with the internal tooth ratchet 27a
Let it rise from the top.

Note that FIG. 7 shows another embodiment, in which a plurality of ratchet rings (in this embodiment, six
The ring plate 34 is rotatably provided with respect to the drive rotating member 22 via the rollers 33 of the ring plate 34, so that the tip of the protrusion 28a where the roller 32 is not provided is in direct contact with the inner circumferential surface 34a of the ring plate 34. It is something.

Also, as shown in Figure 1.3.6, the left and right internal teeth ratchet)
A pair of advance rings 36 are rotatably provided between the IJ songs 7 via a plurality of (five in this embodiment) rollers 35 that roll into contact with the inner periphery of the drive rotation member 22. 3
7 is a shaft that pivots the roller 35 to the advance ring 36.

The advance rings 36 are then frictionally joined to the internally toothed ratchet rings 27, respectively. To explain an example of the friction joining means, annular step portions 27c are formed on the opposing sides of the left and right internal toothed ratchet rings 270, and these step portions 2
A ring spring 38 is fitted into each of the rollers 7c, and the shaft 37 of one roller 35 is extended and engaged with the ring spring 38.

In addition, there are two advance rings 36 on the left and right that sandwich the roller 35.
One end of the two-piece connecting link 39 is connected between them by a pin 40, and the base is inserted into an annular slit provided in the driven rotating body 9, and connected to the driven rotating body 9 by the pin 29. An intermediate connecting fitting 42 is fixed to the protruding portion 41a of the connecting fitting 41 with two screws 43, and the protruding portion 42a of the intermediate connecting fitting 42 is inserted between the other ends of the two connecting links 39. A forwarding mechanism is constructed by connecting the two with a pin 44.

FIG. 8 shows another embodiment of the advance mechanism, which has a plurality of (
In this embodiment, they are connected by six coil springs 45. In the figure, 46 is a pin for connecting the inner end of the coil spring 45 to the driven rotating body 9, and 47 is a pin for connecting the coil spring 4 to the driven rotating body 9.
This is a connecting rod for connecting the outer end of 5 to the advance ring 36.

Further, in FIGS. 1 and 2, 48 is an annular cover fitted to the outer end of the drive rotating member 22, and 49 is an annular cover provided to seal the gap between the disc-shaped cover 15 and the annular cover 48. This is a seal ring made of elastic material.

Next, the speed change operation mechanism of the device configured as described above will be explained. As shown in FIGS. 1 and 2, 50 is the rear claw 3
A reel support arm is fastened to the rear wheel hub shaft 4 between the reel support arm 50 and the lock nut 5, and 51 is a reel rotatably supported by a shaft 53 on a bracket 52 protruding from the middle of the reel support arm 50. An annular groove 51a is formed in the reel 51.

Further, 18b is an annular groove carved on the outer peripheral surface of the outer peripheral edge 18a of the eccentric cam disk 18, and 19e is an annular groove carved on the outer peripheral surface of the eccentric cam ring 19. The distal end of the reel support arm 50 is fixed to a bracket 54 protruding from the chainstay 1 via a bolt 55 and a nut 56, and the distal end is bent to form a bracket for attaching an operating wire.
50a, and the ends of two outer wires 57 are fixed to this bracket 50a with screws 57a and nuts 57b. 58 is an operating wire that slides inside the outer wire 57, and 59 is a wire guide that projects inside the reel support arm 50. As shown in FIG. 9, the operating wire 58 on the right side is first wound around the groove 19e of the eccentric cam ring 19 from bottom to top via the wire guide 59, and then wrapped around the groove 51a of the reel 51. The wire is wound from top to bottom, reversed, and then wound from top to bottom around the groove 18b of the eccentric cam disc 18, and then passed through the wire guide 59 to another araku wire 57 (see FIG. 1). guided by.

Note that 60 is a set screw for fixing the operating wire 58 wound around the groove 19e, and 61 is a holding piece for fixing the operating wire 58 wound around the groove 18b. The pin 20 is fastened to the eccentric cam disk 18 by a threaded portion.

Next, the operation of the apparatus of the present invention constructed as described above will be explained. First, to explain the transmission order, the crank gear rotates via a crank pedal (not shown), and the rotation is transmitted to the sprocket 24 by the chino 25. Since the sprocket 24 is integrally connected to the drive rotating member 22, the rotation of the sprocket 24 is controlled by the one-way clutch 26.
1 to the internally toothed ratchet ring 27 via the internally toothed ratchet 27a, and then to the driven rotating body 9 through the pawl 28 and pin 29 from the internally toothed ratchet 27a. When the driven rotary body 9 rotates, the rear wheel hub 6 integrally connected to the driven rotary body 9 rotates.
rotates and the bicycle travels.

In Figures 1.2 and 3.4, the drive rotating member 22 is the rear wheel hub shaft 4.
However, when the drive rotation member 22 becomes concentric with the rear wheel hub axle 4, the internal ratchet ring 27 also becomes concentric with the rear wheel hub axle 4, so the drive in this state is not eccentric. When the sprocket 24 integrated with the rotating member 22 rotates in the direction of the arrow in FIG.
Since each internal toothed ratchet ring 27, pawl 28, and driven rotary body 9 all rotate integrally via the gear mechanism 6, the gear ratio in this case is 1:1.

In addition, from the above-mentioned concentric state, the gear shift operation lever (not shown)
When the operating wire 58 is moved in the directions of arrows B and C as shown in FIG. As a result of rotating in the direction of
1 moves from the position shown in FIG. 4 to the position shown in FIG. Maximum eccentricity is reached. In this case, the locus of the center 03 (see FIG. 5) of the driving rotation member 22 becomes a straight line along the vertical direction of the bicycle, as shown by arrow F in FIG. 6. For this reason, the distance between the front crank gear and the rear wheel sprocket 24 hardly changes, so there is no risk of the chenno 25 becoming slack or becoming excessively tense.

In the maximum eccentric state shown in Fig. 5.6.7.8,
When the sprocket 24 rotates in the direction of arrow A in FIG.
One rotation can be transmitted to the driven rotary body 9 via.

If the drive rotating member 22 is eccentric, the claw 28 in which the pin 29 is located within the transmission 1tEG (in this case, there are 6 molds, so the angle is approximately 60° divided into 6 equal parts of 360°) as shown in FIG. Since the speed increase rate is the maximum, the driven rotating body 9 is rotated at an increased speed by this pawl 28, and this transmission type 28
When the pin 29 moves out of the transmission range G, the roller 35 or the protrusion 28a comes into contact with the annular groove 27b to release the engagement between the pawl 28 and the internally toothed ratchet 27a.

Then, as the pin 29 of the pawl 28 comes out of the transmission range G,
When the pin 29 of the next pawl 28 enters the transmission range G, it is then driven at an increased speed via that pawl 28, and the transmission type is sequentially changed to the succeeding pawl.

The gear ratio (speed increase ratio) in this case is the center 0 of the rear wheel hub shaft 4.
．． The angle θ1, which is the transmission range based on , and the driven rotating body 9
It is the ratio of the angle θ2 which is the transmission range with the center 03 as the base point.

Next, the operation of the advance ring 36 shown in FIG. 1.3.6.8 will be explained.

In the embodiment shown in Fig. 1.3.6, the driven rotor 9 and the advance ring 36 are connected by a link type connecting member (41°42, 3
9), and in the embodiment shown in FIG. 8, the driven rotary member 9 and the advance ring 36 are connected by six coil springs 45 arranged radially, so that the driving rotary member 22 and the driven rotary When the body 9 is concentric, the driven rotating body 9 rotates at the same speed as the driving rotating member 22 as described above, so the advance ring 36 also rotates at the same speed as the driving rotating member 22 and the internally toothed ratchet ring 27. do. That is, in this case, the advance ring 36 is not advanced with respect to the internal ratchet 27a, but when the amount of eccentricity is zero, all the pawls 28 remain engaged with the internal ratchet 27a, so there is no need to advance the advance.

When the driven rotary body 9 is eccentrically shifted relative to the driving rotary member 22 (speed increase), the driven rotary body 9 is driven to increase its speed as described above, so that the advance ring 36 connected thereto also has a higher speed than the internal toothed ratchet 27a. Rotates at increased speed. Since the advance ring 36 is frictionally connected to each internally toothed ratchet ring 27 via the roller 35 and the ring spring 38, the internally toothed ratchet ring 27 meshes with either one of the left and right pawls 28 and transmits power. (either one of the ratchets) is in a differential state with the IJ song advance ring 36, but the idle internal toothed ratchet ring 27 is advanced at an increased speed due to the frictional engagement of the advance ring 36.

Therefore, if the pawl 28 is a transmission relay, the ratchet 2
Even if there is a gap between the teeth of the pawl 7a and the tooth tip of the pawl 28, the internal tooth ratchet ring 27 is rotated at an increased speed of the advance ring 36.
As the ratchet 27a immediately catches up with the pawl 28, the gap between the tooth tips disappears.

Note that while the ratchet 27a and the pawl 28 are fully engaged and driven, the ring spring 38 appropriately slips on each member and absorbs the speed difference between each member.

Furthermore, although the above explanation has been made for the case of zero eccentricity and the case of maximum eccentricity, this eccentricity can be freely set between zero and maximum, so this device can be continuously variable. Needless to say.

(Effects of the Invention) Since the device of the present invention is configured as described above, after the pawl 28 and the internal tooth ratchet 27a are engaged within the transmission range, the protrusion 28a provided on the pawl 28 passes through the roller 32. Alternatively, by slidingly contacting the annular groove 27b of the internally toothed ratchet ring 27 that rotates integrally with the direct drive rotating member 22, the engagement state between the pawl 28 and the internally toothed ratchet 27a can be released. That is, the engagement between the pawl 28 and the internally toothed ratchet 27a can be made within a more limited range than in the prior art.

Therefore, according to the present invention, the pawl 28 and the internal tooth ratchet 27
The excellent effects of eliminating noise caused by sliding contact with a and reducing output pulsation of reverse input at the time of reverse input are obtained.

[Brief explanation of the drawing]

Figure 1 is a (yellow sectional plan view) of the device of the present invention, Figure 2 is a side view of Figure 1, Figure 3 is a side view showing a part of Figure 2 in section, and Figure 4 is the arrangement of the claws. 5 is a partial sectional view showing the maximum eccentricity state, FIG. 6 is a partial sectional view showing the advance mechanism in the maximum eccentricity state, and FIGS. 7 and 8 are examples of the pond. FIG. 9 is a perspective view showing how the operating wire is hooked up. 4. Rear wheel hub axle 6. Rear wheel hub 9.
Driven rotating body 18... Eccentric cam disc 18a...
・Outer peripheral edge 19... Eccentric cam ring 22...
・Drive rotation member 24... Sprocket 25...
・Cheno 26...One-way clutch 27・
...Internal tooth ratchet ring 27a...Internal tooth ratchet 28...Claw 28&...
・Protrusion 32...Roller 36...Advance ring 50...Reel support arm 51...Reel 57...Araku wire 58...Operation wire Patent applicant Brideston Cycle Co., Ltd.
Continued Amendment Written by the Commissioner of the Japan Patent Office on February 2, 1988, Black 1) Akio Yu, Indication of the incident, Patent Application No. 301796, filed in 1988, 2, Name of the invention, Continuously Variable Transmission Device for Bicycles 3, Person making the amendment Relationship to the case Patent applicant Brideston Cycle Co., Ltd. 4, agent address ``Detailed description of the invention'' column of the same specification, drawing 6, content of amendment (as attached) 1. Specification No. 6 "Eccentric cam ring 19" in the fifth and sixth lines of the page is corrected to "drive rotating member 22." 2. Change "roller 35" in the second line of page 14 to "roller 3".
Corrected to 2. 3. Figures 1 and 7 in the attached drawings are corrected as shown in the attached corrected drawings.

Claims (1)

[Claims] 1. An internal toothed ratchet is provided on the inner periphery of the drive rotating member, and the base of the pawl that engages with this internal toothed ratchet is pivoted to a driven rotating body, so that the amount of eccentricity of this driven rotating body relative to the driving rotating member can be adjusted freely. At the same time, in the device in which the rear wheel is driven by this driven rotary body, a protrusion branched from the tip of the pawl is provided, and after the pawl and the internal tooth ratchet are engaged within the transmission range, the A continuously variable transmission device for a bicycle, characterized in that the meshing state is released by a projection slidingly contacting the drive rotation member.