Patent Grant
6898993
The present nonprovisional application claims priority under 35 USC 119 to Japanese Patent Application No. 2002-029553 filed on Feb. 6, 2002 the entire contents thereof is hereby incorporated by reference.
1. Field of the Invention
The present invention relates to a transmission for a vehicle, more particularly, to a constant-mesh type transmission for a vehicle in which plural transmission shafts each of which supports plural transmission gears in a row are arranged in parallel so that mutually corresponding transmission gears are engaged.
2. Description of Background Art
For a conventional type transmission for a bicycle, as disclosed in Japanese published unexamined patent application No. Hei9-249183, a planetary gear type transmission is provided with a hub spindle (a sun gear) fastened to a bicycle frame so that the hub spindle is not turned. A hub flange is attached to the periphery of the hub spindle so that the hub flange can be rotated. Plural gears (planetary gears) are provided between the hub spindle and the hub flange wherein pedal effort transmitted to a chain sprocket is varied at multiple stages by the plural planetary gears and each clutch mechanism and is transmitted to the hub flange is known. An actuator for fitting a ratchet one-way mechanism of the clutch mechanism or releasing the fitting is inserted into the hub spindle, and the fitting of the ratchet one-way mechanism and the release of the fitting are executed by revolving the actuator around the hub spindle by a predetermined angle.
The planetary gear type transmission is composed of multiple parts. Thus, the transmission efficiency is low and axial downsizing is particularly difficult because the multiple parts are axially arranged. Therefore, for a transmission for a bicycle the limit of the width is severe. Thus, the conventional type of transmission is not desirable.
In the prior art described above, as the actuator for fitting the ratchet one-way mechanism of the clutch mechanism or releasing the fitting is cylindrical and is required to be turned by a predetermined angle on the periphery of the spindle, it is difficult to apply the prior art to a transmission in which a spindle itself is rotated. Further, in the prior art, the actuator cannot be turned in a state in which torque is applied and the shift is disabled.
It is an object of the present invention to solve the problems of the prior art and to provide a transmission for a bicycle which can be applied to a shift mechanism in which a spindle itself is revolved, has a simple configuration and can be axially miniaturized.
To achieve this object, the present invention includes a transmission for a vehicle in which plural transmission shafts include hollow shafts wherein each hollow shaft supports plural transmission gears in a row that are arranged in parallel so that mutually corresponding transmission gears are engaged and a desired speed reducing ratio is acquired by selectively switching the transmission gear revolving in synchronization with the hollow shaft every transmission shaft.
(1) A clutch mechanism is provided between the hollow shaft and the transmission gear for synchronizing the hollow shaft and each transmission gear or releasing the synchronization. A clutch actuator is housed in the hollow shaft that is provided. The clutch mechanism selectively synchronizes each transmission gear with the hollow shaft or releases the synchronization according to an axial position of the clutch actuator.
(2) The clutch mechanism is provided with a pin member housed in an opening radially piercing the side wall of the hollow shaft so that the pin member can move vertically and a fitting member for fitting each transmission gear to the hollow shaft or releasing the fitting in interlock with the vertical motion of the pin member. The clutch actuator is in the shape of a rod and is provided with an irregular cam part arranged on its outside face according to a predetermined rule. The pin member is selectively made to vertically move by moving the clutch actuator in the hollow shaft and fitting the cam part to the bottom of the pin member.
(3) The cam part is circumferentially provided with an inclined face continuing from a cam groove to a cam crest.
According to the characteristic (1), as the clutch actuator can be housed in the hollow shaft, the constant-mesh type transmission which has a simple configuration and in which axial miniaturization is enabled can also be realized in a drive line in which a shaft itself is revolved.
According to the characteristic (2), the clutch mechanism can be realized by a simple configuration in the constant-mesh type transmission in which the clutch actuator is housed in the shaft.
According to the characteristic (3), as the pin member can be lifted from the cam groove to the cam crest by small force and smoothly, shift is enabled even if pedal effort is applied.
Further scope of applicability of the present invention will become apparent from the detailed description given hereinafter. However, it should be understood that the detailed description and specific examples, while indicating preferred embodiments of the invention, are given by way of illustration only, since various changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art from this detailed description.
The present invention will become more fully understood from the detailed description given hereinbelow and the accompanying drawings which are given by way of illustration only, and thus are not limitative of the present invention, and wherein:
FIGS. 3(a)-3(c) show the configuration of a shift plate 66;
FIGS. 4(a) and 4(b) show the operation of a transmission shaft (1);
FIGS. 5(a) and 5(b) show the operation of the transmission shaft (2);
FIGS. 6(a) and 6(b) show the configuration of a clutch actuator;
FIGS. 8(a) and 8(b) are sectional views showing a roller one-way mechanism;
FIGS. 9(a) and 9(b) are sectional views showing a hollow shaft;
FIGS. 14(a)-14(b) are explanatory drawings for explaining the operation of the third transmission shaft.
Referring to the drawings, preferred embodiments of the invention will be described in detail below.
A body frame 2 of a bicycle 1 is composed of a head pipe 20, a main frame 21 extending diagonally downwardly and rearwardly from the head pipe 20 forkedly right and left and a swing arm 23 supported by a reciprocating shaft 22 provided to the rear of the main frame 21 so that the swing arm can move vertically. A reinforcing pipe 24 is provided under the main frame 21. The reinforcing pipe 24 and the main frame 21 are coupled via a bracket 25 and a reinforcing member 39. The swing arm 23 may be a rear fork.
A rear wheel 3R is supported by the rear end of the swing arm 23. A front fork 4 is supported by the head pipe 20 so that the front fork 4 can steer the bicycle 1. The front fork 4 is an inverted type in which an outer tube and an inner tube are combined and the outer tube is located over the inner tube. A steering handlebar 5 is provided above the front fork 4 and a front wheel 3F is supported by a lower part of the front fork.
The main frame 21 and the reinforcing pipe 24 are coupled in respective lower parts via the coupling member 39. A pedal effort transmission device 6 is supported by the coupling member 39. The pedal effort transmission device 6 includes a transmission that transmits the revolution of a crankshaft 61 to the rear wheel 3R. A pedal 9 is attached to the crankshaft 61 via a crank 8. A pair of right and left cranks 8 and pedals 9 are provided to the crankshaft 61.
A bracket 231 is provided to the swing arm 23, a bracket 211 is provided to the main frame 21 and a cushion member 18 for relieving shock when the swing arm 23 is turned upwardly is provided between the brackets 231 and 211. Working fluid is supplied from a reservoir tank 19 to the cushion member 18.
A rear fender 30 is attached to the main frame 21 and a seat 31 is mounted on the rear fender 30 and the main frame 21. The rear fender 30 can be made of light material such as carbon fibers. Disc brakes 32, 33 are provided to the front wheel 3F and the rear wheel 3R. A transmission operating cable 101 extends from a speed change lever not shown and is mounted on the steering handlebar 5 and extends to the pedal effort transmission device 6 along the reinforcing pipe 24.
Both ends of the crankshaft 61 are supported by ball bearings 681, 691 so that the crankshaft can be turned. The respective outer races of the ball bearings 681, 691 are press-fitted into a right case half 68 and a left case half 69. A pedal sprocket 611 coaxially pierces the substantial center of the crankshaft 61.
In the transmission 60, the first transmission shaft 63 includes a hollow rotation shaft 630 with a rod-shaped clutch actuator 631 which supports the hollow shaft 630 so that the hollow shaft can be turned and which is supported so that the clutch actuator cannot be turned. Transmission gears 632, 633, 634 are supported by the hollow shaft 630 via each clutch mechanism (each ratchet one-way mechanism in this embodiment) 632a, 633a, 634a. A driven sprocket 635 is fixedly inserted into the hollow shaft 630 with pin members 636, 637 which pierce the side wall of the hollow shaft 630 and which are supported so that the pin members can move vertically. A cam guide 638 is provided to one end of the clutch actuator 631.
Both ends of the hollow shaft 630 are supported by ball bearings 682, 692 so that the hollow shaft can be turned. The respective outer races of the ball bearings 682, 692 are press-fitted into the right case half 68 and the left case half 69. The driven sprocket 635 of the first transmission shaft 63 and the pedal sprocket 611 of the crankshaft 61 are coupled via a chain 601 without an end.
Passages 881, 882 are provided to the clutch actuator 631 and a concave portion on the outside face of the clutch actuator 631 communicates with the outside via each passage. As a result, as a problem with the variation of internal pressure is solved, a variation of the volume of the concave portion on the outside face by the vertical motion of the pin members 636, 637, a satisfactory shift field is acquired.
The second transmission shaft 65 of the transmission 60 is mainly composed of a cylindrical hollow shaft 650 and transmission gears 652, 653, 654 fixedly supported by the periphery of the hollow shaft 650. Both ends of the hollow shaft 650 are supported by ball bearings 683, 693 so that the hollow shaft can be turned. The respective outer races of the ball bearings 683, 693 are press-fitted into the right case half 68 and the left case half 69.
The third transmission shaft (the output shaft) 67 of the transmission 60 includes a hollow shaft 670 with a rod-shaped clutch actuator 671 which supports the hollow shaft 670 so that the hollow shaft can be turned and which is supported so that the clutch actuator cannot be turned. Transmission gears 672, 673, 674 are supported by the hollow shaft 670 via each ratchet one-way mechanism 672a, 673a, 674a. Pin members 676, 677 pierce the side wall of the hollow shaft 670 and are supported so that the pin members can move vertically. A cam guide 678 is provided to one end of the clutch actuator 671 and a driving sprocket 679 coupled to the other end of the hollow shaft 670.
Both ends of the hollow shaft 670 are supported by ball bearings 684, 694 so that the hollow shaft can be turned. The respective outer races of the ball bearings 684, 694 are press-fitted into the right case half 68 and the left case half 69. Passages 883, 884 are provided to the clutch actuator 671.
A control face 661 is provided along the outside face of a shift plate 66 and is fitted to each cam guide 638, 678 of the first and third transmission shafts 63, 67. The shift plate 66 is supported by a rotation shaft 662 fixedly arranged on an extended line of the hollow shaft 650 so that the shift plate can be turned. A cable hanger 64 for fitting a nipple of the transmission operating cable 101 is inserted into the end of the shift plate 66. The shift plate 66 is constantly pressed on the side (in a shift up direction) reverse to a direction in which the operating cable is turned (a shift down direction) by a return spring 664 one end of which is fitted to a flange of the rotation shaft 662. The other end of a lost motion spring 663 one end of which is fitted to the shift plate 66 is fitted to the cable hanger 64.
The lost motion spring 663 enables a lost motion of the shift plate 66 when the cable hanger 64 is turned in the shift down direction. The return spring 664 enables a lost motion of the shift plate 66 when the cable hanger 64 is turned in the shift up direction.
FIGS. 3(a)-3(c) show the structure of the shift plate 66. FIG. 3(a) is a front view, FIG. 3(b) is a sectional view viewed along a line B—B in FIG. 3(a) and FIG. 3(c) is an expansion plan showing a control face 661 provided on its outside face in a circumferential direction.
The axial position of the control face 661 is different depending upon positions 1 (M) to 7 (M) and 1 (D) to 7 (D) as shown in FIG. 3C. The positions 1 (M) to 7 (M) are fitted to the cam guide 638 of the first transmission shaft 63 and the positions 1 (D) to 7 (D) are fitted to the cam guide 678 of the third transmission shaft 67. For the number of shifts, if each cam guide 638, 678 is fitted to 1 (M), 1 (D), the number of shifts is one, if each cam guide is fitted to 2 (M), 2 (D), the number is two and if each cam guide is fitted to 7 (M), 7 (D), the number is seven.
FIGS. 4(a)-4(b) and 5(a)-5(b) are side views viewed along the transmission shaft and sectional views viewed along a line I—I for explaining the clutch mechanisms of the first transmission shaft 63 and the third transmission shaft 67. The same reference number denotes the same or the similar part.
The operation in the case of shift down from a fifth stage (the state shown in
As shown in FIGS. 6(a)-6(b) in detail, wherein FIG. 6(b) is a cross-section along the line IV—IV in FIG. 6(a), a cam part in which a cam crest 631a and a cam groove 631c continue is formed on the outside face of the clutch actuator 631. An inclined face 631b connecting the cam crest 631a and the cam groove 631c is formed in a boundary between the cam crest and the cam groove in a circumferential direction.
When the number of shifts is five, the cam guide 638 of the first transmission shaft 63 is fitted to the position 5 (M) shown in
As the pin members 636 and 637 are both located in the cam groove 631c of the clutch actuator 631 in the first transmission shaft 63 as shown in FIG. 4(a) when the number of shifts is five as shown in
However, as the second transmission shaft 65 is turned at the highest speed by a driving force transmitted from the first transmission gear 632 of the first transmission shaft 63 to the first transmission gear 652 of the second transmission shaft, only the driving force transmitted from the first transmission gear 632 of the first transmission shaft 63 acts upon the second transmission shaft 65 as also shown in
At this time, as the pin member 676 is located in the cam groove of the clutch actuator 671 and the pin member 677 is located on the cam crest of the clutch actuator 671 in the third transmission shaft 67 as shown in FIG. 14(a), only the ratchet one-way mechanisms 672a and 673a of the first and second transmission gears 672 and 673 are turned on and are fitted to the hollow shaft 670 in the direction of normal rotation. However, as the second transmission gear 673 has a smaller diameter and the first transmission gear 672 becomes free, pedal effort input to the sprocket 635 is transmitted to the driving sprocket 679 via the first transmission gear 632 of the first transmission shaft 63, the second transmission shaft 65 and the second transmission gear 673 of the third transmission shaft 67.
As a shift operation cable 101 is pulled out when a rider executes shift down operation to the fourth stage, working the pedal, the shift plate 66 is turned against the elastic force of the return spring 664. By the shift operation, the clutch actuator 631 of the first transmission shaft 63 is axially displaced by a cam mechanism composed of the control face 661 and the cam guide 638. When the clutch actuator 631 is displaced by distance ΔL1 as shown in FIG. 4(b), the pin member 636 reaches an entrance of the inclined face 631b of the clutch actuator 631 and further, starts to advance on the inclined face 631b as the hollow shaft 630 is turned.
In case when the rider swiftly makes a shift operation and frequently makes a shift operation or in case when the revolution speed of the crankshaft is small as in a case that the bicycle goes up on a slope and the axial traveling speed of the clutch actuator 631 for the hollow shaft 630 is limited, the revolution speed of the shift plate 66 cannot follow the revolution speed of the cable hanger 64 and elastic force according to phase difference between both is stored in the lost motion spring 663.
Afterward, the pin member 636 starts to go up on the inclined face 631b by interaction between the elastic force stored in the lost motion spring 663 and the inclined face 631b as shown in FIG. 5(a) if pedal effort is input and when the pin member 636 further advances, it climbs on the cam crest 631a of the clutch actuator 631 as shown in FIG. 5(b). As a result, as the free end 632c of the ratchet pawl 632b is radially pushed up by the pin member 636, the fitting between the first transmission gear 632 and the hollow shaft 630 is released and only the transmission gears 633 and 634 can maintain the fitting to the hollow shaft 630.
At this time, the third transmission shaft 67 is also displaced by ΔL1 and the cam guide 678 is fitted to the position 4 (D) of the control face 661. However, as the position 4 (D) is the same as the position 5 (D), the engagement of the third transmission shaft 67 is unchanged. As a result, as the diameter of the second transmission gear 673 is smaller than that of the first transmission gear 672 though the respective clutch mechanisms of the first and second transmission gears 672 and 673 are turned on and the clutch mechanism of the third transmission gear is turned off in the third transmission shaft 67, the first transmission gear 672 becomes free. Therefore, pedal effort input to the sprocket 635 is transmitted to the driving sprocket 679 via the second transmission gear 633 of the first transmission shaft 63, the second transmission shaft 65 and the second transmission gear 673 of the third transmission shaft 67.
In the meantime, as the shift operation cable 101 is pulled in by the elastic force of the return spring 664 when the rider executes a shift up operation to a sixth stage, the shift plate 66 is turned in a direction reverse to the direction in shift down. The clutch actuator 631 of the first transmission shaft 63 is axially displaced by the cam mechanism composed of the control face 661 and the can guide 638 according to the shift operation and the cam guide 638 is fitted to the position 6 (M) of the control face 661.
In this embodiment, as shown in FIG. 3(c), as the position 6 (M) and the position 4 (M) of the control face 661 are the same, the clutch actuator 631 and the pin members 636, 637 are operated as in the shift down to the fourth stage.
As elastic force according to phase difference between both is stored in the return spring 646 in this embodiment when the revolution speed of the shift plate 66 cannot follow the revolution speed of the cable hanger 64 because the operation is swiftly executed in shift up, a lost motion of the shift plate 66 is enabled as described above.
As the pin member 677 also drops in the cam groove of the clutch actuator 671 in the third transmission shaft 67 as shown in FIG. 14(b), the ratchet one-way mechanisms 672a, 673a and 674a of all the transmission gears 672, 673 and 674 are turned on. However, as the diameter of the third transmission gear 674 is the smallest in the third transmission shaft 67, the other transmission gears 672 and 673 become free. Therefore, pedal effort input to the sprocket 635 is transmitted to the driving sprocket 679 via the second transmission gear 633 of the first transmission shaft 63, the second transmission shaft 65 and the third transmission gear 674 of the third transmission shaft 67 as also shown in FIG. 13.
As described above, according to this embodiment, as the clutch actuator 631 can be housed in the hollow shaft 630, the constant-mesh type transmission the axial miniaturization of which is enabled by the simple configuration can be also realized in a drive line in which a shaft itself is revolved.
Also, in this embodiment, as the inclined face 631b connecting the cam groove 631c and the cam crest 631a is circumferentially provided to the irregular cam part formed on the outside face of the clutch actuator 631 and the pin member can be carried from the cam groove 631c to the cam crest 631a by a small force and smoothly, speed can be changed even if pedal effort is applied to the crankshaft.
Further, according to this embodiment, as a shift operation is held in the lost motion spring 663 (in shift down) or the return spring 646 (in shift up) as elastic force in case a shift mechanism cannot follow the shift operation and afterward, the shift mechanism executes shift by the elastic force, secure shift is enabled even if shift operation is swiftly made, shift operation is made a plurality of times or shift operation is made in a low-speed operation. Therefore, a condition related to shift timing is relaxed and a shift degree of freedom is high is enabled.
In the first embodiment, the case in which the ratchet one-way mechanism is adopted for the clutch mechanism for fitting the clutch actuators 631 and 671 of the first and third transmission shafts 63 and 67 and each transmission gear or releasing the fitting is described. However, in this embodiment a roller one-way mechanism is adopted in place of the ratchet one-way mechanism.
In a transmission 70, a first transmission shaft 73 is mainly composed of a cylindrical hollow shaft 730, a rod-shaped clutch actuator 731 inserted into the hollow shaft 730, transmission gears 632, 633, 634 supported by the hollow shaft 730 via a roller one-way mechanism as a clutch mechanism, a sprocket 635 fixedly inserted into the hollow shaft 730, pin members 636, 637 piercing the side wall of the hollow shaft 730 and supported so that the pin member can move vertically and a cam guide 638 provided to one end of the clutch actuator 731.
Both ends of the hollow shaft 730 are supported by ball bearings 682, 692 so that the hollow shaft can be turned. The outer race of each ball bearing 682, 692 is press-fitted into a right case half 68 and a left case half 69. The sprocket 635 of the first transmission shaft 73 and a pedal sprocket 611 of a crankshaft 61 are coupled by a chain 601 without an end. Passages 885, 886 are provided to the clutch actuator 731.
A second transmission shaft 75 of the transmission 70 is provided with a similar configuration to the second transmission shaft 65 in the first embodiment. A third transmission shaft 77 of the transmission 70 is also provided with a similar configuration to the third transmission shaft 67 in the first embodiment except that its clutch mechanism is a roller one-way mechanism and a rod-shaped clutch actuator 771 is inserted into a hollow shaft 770. Passages 886, 887 are provided to the clutch actuator 771.
FIGS. 8(a) and 8(b) are sectional views showing the structure of the roller one-way mechanism, FIG. 9(a) is a sectional view viewed along the axis of the hollow shaft 730, FIG. 9(b) is a sectional view viewed along a line V—V in FIG. 9(a) and the same reference number denotes the same or the similar part.
As shown in FIG. 9(b), the hollow shaft 730 is provided with six slits 730a at an equal interval in an axial direction of the outside face and an opening 730b linked with a central hole is formed on the side of one end of the bottom of each slit 730a. The side of one end on which the opening 730b is formed of the bottom of the slit 730a is shallower than the side of the other end.
As shown in FIGS. 8(a) and 8(b), in each slit 730a of the hollow shaft 730, plural (three in this embodiment) rollers 741 are housed axially in a line and a pin member 676 is housed in each opening 730b so that the pin member can move vertically. As shown in
In such a configuration, the pin member 636 vertically moves according to an axial position of the clutch actuator 731 as described above, in a state in which the pin member 636 is lowered. Each roller 741 is elastically pressed from a deep position to a shallow position in each slit 730a by each rock spring 742 clockwise as shown in FIG. 8(a). Therefore, as the outside face of the hollow shaft 730 and the inside face of the transmission gear 632 are fitted via the roller 741, the transmission gear 632 is also revolved in a direction shown by an arrow B in synchronization when the hollow shaft 730 is revolved in the direction shown by the arrow B according to pedal effort input to the driven sprocket 635.
In the meantime, in a state in which the pin member 636 is lifted, each roller 741 is pushed back counterclockwise against the resilience of each rock spring 742 by the pin member 636 as shown in FIG. 8(b) and is moved from the shallow position to the deep position in each slit of the hollow shaft 730. As a result, as the fitting of the hollow shaft 730 and the transmission gear 632 via the roller 741 is released, the transmission gear 632 is not revolved even if the hollow shaft 730 is revolved in the direction shown by the arrow B according to pedal effort input to the driven sprocket 635.
According to this embodiment, as not only the similar effect to that in the first embodiment is acquired but the lash is smaller in roller on-way structure, compared with that in the ratchet one-way structure, shock and a lash at a pedal when speed is changed, inputting pedal effort can be greatly reduced.
According to the invention, the following effect is acquired.
(1) As the clutch actuator can be housed in the hollow shaft, the constant-mesh type transmission which has a simple configuration and in which axial miniaturization is enabled can also be realized in a drive line in which a shaft itself is revolved.
(2) In the constant-mesh type transmission in which the clutch actuator is housed in the shaft, the clutch mechanism can be realized by a simple configuration. As plural clutch actuators are operated by one cam mechanism, each clutch actuator can be simply and precisely synchronized and as a result, satisfactory shift feeling is acquired.
(3) As the pin member of the clutch mechanism can be lifted from the cam groove to the cam crest respectively formed on the surface of the clutch actuator by a small force and smoothly, shift is also enabled in a state in which pedal effort is applied.
(4) In the case when the shift mechanism cannot follow the shift operation, the shift operation is held in the lost motion spring or the return spring as an elastic force and afterward, as the shift mechanism executes shift by the elastic force, secure shift is enabled even if a shift operation is swiftly made, shift operation is made a plurality of times or shift operation is made in a low-speed operation. Therefore, a condition related to shift timing is relaxed and a degree of freedom of the shift is high is enabled.
(5) In case the roller one-way structure is adopted as the clutch mechanism, shock and a lash at the pedal when speed is changed, inputting pedal effort can be greatly reduced, compared with the case when the ratchet one-way structure is adopted as the clutch mechanism.
The invention being thus described, it will be obvious that the same may be varied in many ways. Such variations are not to be regarded as a departure from the spirit and scope of the invention, and all such modifications as would be obvious to one skilled in the art are intended to be included within the scope of the following claims.
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| 2002-029553 | Feb 2002 | JP | national |
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| Number | Date | Country | |
|---|---|---|---|
| 20030213318 A1 | Nov 2003 | US |
