JPH0565094A - Gear shifting device for bicycle - Google Patents

Abstract

PURPOSE:To make gear shifting easily with a bicycle transmission, which makes gear shift with the rise/fall changing-over of a transmission pawl, so that shift shocks are not likely to occur even though shift operation takes place under running with the drive. CONSTITUTION:Even though a shift operating tool 60 is turned, a spring S1 or S2 only reserves the operating force and operational piece 8 or 40 remains out of execution of work if a large drive torque acts on a driving body 2 and the degree of engagement of shift pawls 21, 22a, 23a or a one 19a with a stationary shaft 1 or gear frame 5a is large, and the pawls 21a, 22a, 23a or the one 19a does not fallen to execute no shift operation. The spring S1 or S2 actuates the operational piece 8 or 40 in association with drop of the degree of engagement of the pawls 21a, 22a, 23a or the one 19a caused by drop of the drive torque acting on the driving body 2, and the shift pawls 21a, 22a, 23a or the one 19a falls to execute the shift operation.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is provided with a plurality of speed change pawls in an upright state in which a plurality of speed change pawls are engaged with a member to be engaged and disengaged and a fall state in which the plurality of speed change claws are disengaged from the member to be engaged and disengaged. The present invention relates to a bicycle speed change device that is operated to change gears by raising and lowering a speed change claw.

[0002]

2. Description of the Related Art In the above-mentioned bicycle transmission,
For example, as shown in Japanese Utility Model Laid-Open No. 2-26996,
By transmitting the speed change operation force applied by the artificial speed change operation tool to the speed change claw via the rigid transmission member,
He was supposed to operate the shifting pawl.

[0003]

Conventionally, when the vehicle is driven to run, the engagement between the speed change claw and the engagement / disengagement target member becomes strong due to the transmission load, and the speed change claw disengages from the engaged member. Due to this difficulty, when the speed is changed, the crank pedal should be sewn so that the transmission load does not act on the speed change pawl and the disengagement of the speed change pawl from the engagement / disengagement target member is facilitated. It was necessary to shift gears while stopping the operation. An object of the present invention is to provide a speed change device that can easily perform a speed change while driving a vehicle while preventing a speed change impact.

[0004]

In the bicycle transmission according to the present invention, in order to achieve the object, in the one described at the beginning, an operating force for operating the shifting pawl is applied to the operating body for the shifting pawl. When the resistance to disengage the shift claw from the engagement / disengagement target member is greater than the set resistance value, the applied spring causes the operation body to operate in preference to the operation of the artificial speed change operation tool. In a state in which the speed change pawl is stopped and allowed to stand upright, and when the disengagement resistance of the speed change pawl from the engagement / disengagement target member is equal to or less than the set resistance value, the operating body is operated to operate the The speed change pawl is operated to act on the operating body in a state in which the speed change claw is changed to fall, and further in a state in which the speed change claw is operated to fall while the traveling drive torque is being applied, and the spring operates the speed change claw to move downward. Made when Maximum torque of the traveling drive torque you are, characterized in that one of the transmission pawl are provided with means for revealing the state in which the same or substantially the same even when the laid-down operation target nail. Its action and effect are as follows. As the speed change claw, any shape of claw may be adopted, but it is advantageous to adopt a shape in which the claw body and the fall operation portion are displaced in the direction of the undulating axis. .. Further, the spring may have any shape or arrangement such as a tension spring interposed between the operating body and the manual operation tool, but it may be formed as a torsion coil spring and formed into a tubular shape. It is advantageous that the external fitting is arranged on the operating body as described below.

[0005]

[Operation] Even if the shift operation tool is operated to apply the shift operation force, the travel drive operation is performed and the travel drive torque acts,
If the disengagement resistance of the speed change pawl from the engagement / disengagement target member is greater than the set resistance value due to the transmission load acting on the speed change pawl, the shift operation is executed due to the magnitude of the disengagement resistance. In spite of this, in reality, the spring does not operate the operation body in a predetermined manner, the shift claw does not fall down and the transmission itself does not perform the shift operation, and the shift is not executed. The crank is positioned at or near top dead center or bottom dead center for driving operation, the traveling drive torque decreases and the transmission load acting on the speed change claw decreases, and the disengagement target engaged by the speed change claw. As the detachment resistance from the member decreases to the set resistance value, the detachment resistance decreases, and the spring operates the operating body in a predetermined manner so that the speed change pawl changes to fall and the transmission itself performs the speed change operation. To actually execute the shift. But it becomes possible by setting appropriately based on the acting force of the spring in the set resistance value. In addition, since the speed change claws exhibit different transmission ratios, the set resistance value may differ depending on the speed change claws. Even when the speed of the gear is in the speed state, when the crank being operated reaches the top dead center, the bottom dead center, or the vicinity thereof, and the traveling drive torque decreases and the transmission load of the speed change claw decreases, the speed change claw moves to the spring. You will be able to change the lodge by operating force. As a result, even if the gear shift operation is performed while the traveling drive operation is performed, and the target speed to be newly expressed by the gear shift operation is set to any stage speed, the crank to be driven and operated does not reach the top dead center or the top dead center. A large transmission load is applied to the speed change pawl at a position other than or near bottom dead center, and if the speed change pawl changes its fall position, the other transmission or speed change pawls in the upright state are subject to engagement / disengagement. In the case of the gear shift operation timing under the traveling drive condition in which the gear suddenly engages and the gear shift shock is largely generated, the spring suspends the gear shift operation and the transmission does not actually perform the gear shift operation.
When the crank reaches the top dead center, the bottom dead center, or the vicinity thereof, the transmission load acting on the speed change pawl is reduced from that during the gear change operation, and the speed change claw that should stand up and down for gear change operation of the transmission itself is subject to engagement and disengagement. At the timing of running drive condition where the member relatively quietly engages and the gear shift shock is less likely to occur, the spring executes the gear shift operation to shift the gear shift target to a new speed stage. Will be completed. If a pawl with a shape in which the pawl main body and the fall operation portion are displaced in the direction of the undulation axis is used as the speed change pawl, the arm length from the undulation axis of the pawl body to the engagement point with the engagement / disengagement target member and the fall It is relatively easy to design the arm length from the undulating axis of the operating portion to the contact point with the operating body, and the ratio of the both arms can be made equal for the torque while enabling the operation of the shifting pawl by the operating body. It becomes easy to set the ratio. When the spring is formed as a torsion coil spring and is externally fitted to the operating body, it becomes relatively easy to incorporate the spring while making the entire transmission compact.

[0006]

By the action of the spring and the torque equalizing means, it is possible to drive the vehicle even if the gear shift target speed is changed such that the vehicle can be shifted while driving so as not to stop traveling even when starting or climbing a hill. It has become possible to shift gears while operating so that traveling is not stopped and the shift shock is light and agile. Moreover, it is not necessary to pay attention to the timing of the gear shifting operation, such as determining the timing when the transmission load acting on the gear shifting claw is reduced, and the gear shifting operation can be easily performed from this aspect. If the shift claw is of a position shift type between the claw body and the fall operation portion, it is easy to obtain a means for equalizing the torque, and the accuracy of the torque equalization is further improved. When the spring is formed into a torsion coil shape and is fitted onto the operating body, it is advantageous in terms of handling and accuracy due to the compactness and internalization.

[0007]

The first embodiment of the present invention will now be described with reference to the drawings.
An example will be described. As shown in FIG. 1, the internal transmission of the present invention generally has a fixed shaft 1 fixed to a bicycle frame, a driving body 2 having a chain wheel 2a, and hubs 3a, 3a supporting spokes. The hub barrel 3 is pivotally supported, and a power transmission system from the driving body 2 to the hub barrel 3 is provided with a first planetary gear train 4 for speed-up and a second planetary gear train 5 for speed reduction,
A coaster brake 6 is provided on the side opposite to the driving body 2. Further, as will be described later, a tubular operation body 8 for operating the clutch on / off mechanism 7 for switching the power transmission system and operating the control unit for selecting whether to rotate the sun gear,
The fixed shaft 1 is rotatably fitted onto the fixed shaft 1. It should be noted that in the present embodiment, it is possible to perform a 7-speed shift as will be described later.

The planetary gear trains 4 and 5 are respectively provided with first and second gear frames 4a and 5a which are engaged with each other so that they cannot rotate relative to each other. The first gear frame 4a is relayed from the coaster brake 6 side. The body 9 is fitted so as not to rotate relative to it. The first and second sun gears 11a and 12a of the first planetary gear train 4 and the third and fourth sun gears 13a and 14a of the second planetary gear train 5 are independently rotatable with respect to the fixed shaft 1 and The first and second sun gears 11 are supported so as to be immovable in the axial direction.
First and second planetary gears 11b, which mesh with a and 12a,
12b is integrally formed, and the third and fourth sun gears 13a, 1
3rd and 4th planetary gears 13b and 14b respectively meshing with 4a
Is also integrally formed. In addition, the second planetary gear 12
A first ring gear 15 is meshed with b, and a second ring gear 16 is meshed with the fourth planetary gear 14b. Incidentally, each sun gear 11a, 12a, 13a, 14 with respect to the fixed shaft 1
Whether or not a can be rotated can be selected by the operation body 8 described later.

The first ring gear 15 is used as an output for the hub barrel 3 selectively with the relay body 9, and the second ring gear 16 is used as an input for the drive body 2 selectively with the second gear frame 5a. Used. A one-way clutch is used to transmit power between these members. Such a one-way clutch includes the relay 9 or the first
Output transmission first and second transmission clutches 17 and 18 provided between the ring gear 15 and the hub barrel 3, and a second gear frame 5a.
Alternatively, it is composed of third and fourth transmission clutches 19 and 20 provided between the second ring gear 16 and the driving body 2. Each of these clutches includes a ratchet pawl, first to fourth transmission pawls 17a,
18a, 19a, 20a and a plurality of ratchet teeth 1st
~ 4th transmission tooth 17b, 18b, 19b, 20b, each transmission claw 17a, 18a, 19a, 20a is constantly biased by a spring to each transmission tooth 17b, 18b, 19b, 20b side. First to fourth transmission pawls 17a, 18a, 19
a and 20a are attached to the relay body 9, the first ring gear 15, and the drive body 2, respectively, and the transmission claws 17a, 18a and 19a are provided.
The pawls are oriented in the direction in which the hub barrel 3, the second gear frame 5a, or the second ring gear 16 corresponding to the respective pawls are driven only when the members to which a and 20a are attached rotate in the driving direction K. The third transmission pawl 19a meshes over the front width of the third transmission tooth 19b, and the third transmission clutch 1
9 can be turned on and off by a clutch on / off mechanism 7 described later.

As shown in FIGS. 1 and 10 to 17, the first to fourth sun gears 11a, 12a, 13a, 14a are provided.
The first to fourth sun clutches 21, 22, 23, 24 as one-way clutches are provided between the fixed shaft 1 and the fixed shaft 1. These first to fourth sun clutches 21, 22, 2
3 and 24 are first to fourth sun gears 11a, 12a, 13
1st-4th sun nail 21 attached to the inner circumference of a, 14a
a, 22a, 23a, and 24a are provided in a state in which they are always biased toward the fixed shaft 1, and these first to third sun claws 21a,
The fixed shaft 1 is integrally formed with first and second restricting protrusions 21b and 22b that are engaged with the fixed shaft 1 and are restricted from rotating with respect to the fixed shaft 1 in only one direction. Of these, the second restricting protrusion 22b is commonly used for the second and third sun claws 22a and 23a. Here, the first and second sun clutches 21,
22 is configured to allow rotation about the fixed shaft 1 in the opposite direction to the driving direction F, and the third sun clutch 23 is configured to allow rotation about the fixed shaft 1 about the driving direction K (FIGS. 10 to 16). You can easily understand the reason by comparing and referring to. Since the first sun gear 11a has a small diameter, a part of the first sun gear 11a extends leftward to provide the first sun clutch 21. In the figure, 24b is a claw mounting member as shown in FIG. 24, which is attached to the fixed shaft 1 so as not to rotate,
A claw mounting portion is formed on the fixed shaft 1.

As shown in FIGS. 1 and 4, the operating body 8 has first and second sleeves 25, 26 fitted to the fixed shaft 1 so as to be sequentially rotatable from the coaster brake 6 side.
And a wire hook 27 for locking the nipple of the operation wire C. The first sleeve 25 includes a first fork portion 25a extending rightward, and the second sleeve 2
The reference numeral 6 includes second and third fork portions 26a and 26b which respectively extend to the left and right. Both sleeves 25, 26
Is relatively rotated only at the set angle D due to the difference between the sleeve circumferential clearance between the second fork portions 26a and 26a as shown in FIG. 8 and the sleeve circumferential thickness of the first fork portion 25a, The first fork portion 25a and the second fork portion 26a are configured to be assembled in a state of being concentrically engaged so as to rotate integrally with the first fork portion 25a and the second fork portion 26a. First fork part 2
The cam body 41 configured to rotate integrally with the first sleeve 25 for engaging with the spring 5a has a spring mounting hole 41.
One end side of the first spring S1 is locked using b, and the other end side of the first spring S1 is locked in the second sleeve 26 using the spring mounting hole 26c, and the second sleeve 26 is driven. When rotating in the direction opposite to the direction K, the first
When the sleeve 25 rotates following the second sleeve 26 and when the rotation resistance more than the set value acts on the first sleeve 25, the second sleeve 26 sets the set angle D with respect to the first sleeve 25. The first spring S1 is configured to interlock the sleeve 25 with the sleeve 26 in a state where the first spring S1 is allowed to rotate forward. Further, since the third fork tip end portion 26b is fitted into the groove 27b provided in the protruding portion 27a protruding toward the central portion of the wire hook 27, the operating body 8 as a whole is fixed to the fixed shaft 1. It is possible to rotate integrally. A second spring S in which one end side is locked by using the spring mounting hole 53 in the pawl mounting member 24b.
The other end side of 2 is attached to the spring receiving plate 54 by a spring mounting notch 54
The spring receiving plate 54 is locked by utilizing the a, and the first spring S1 is locked in the spring mounting hole 54b of the spring receiving plate 54 via the first spring S1 and the cam body 41. Since the second spring S2 is locked to the sleeve 25, the second spring S2 is rolled up by the sleeve 25 as the operating body 8 rotates in the direction opposite to the driving direction K, and the sleeve 25 is in the same driving direction K. It is configured so as to urge the return in the rotation direction. Spring S1
And S2 are formed on a torsion coil spring so as to exert an elastic restoring force due to torsion as an urging force, and the fixed shaft 1 is positioned inside the transmission.
It is placed on the outside.

Each of the sun clutches 21, 22, 23 can be turned on and off by rotating the first sleeve 25. That is, the first sleeve 25 shown in FIG.
As shown in FIGS. 10 to 16, the third to third control parts 31, 32 and 33 are matched with the first and second regulating protrusions 21b and 22b, so that the first to third sun claws 21a and 22b.
a, 23a to the first to third sun gears 11a, 12a, 13
The control projections 21b and 22b and the first to the third sun claws 21 are operated by operating in a state of falling down to the side a and separating from the fixed shaft 1.
The engagement with the a, 22a and 23a is prevented, and the free rotation of the first to third sun gears 11a, 12a and 13a is allowed. And the 1st-3rd control part 31, 32, 33 removes the code | symbol with the 1st, 2nd control protrusion 21b, 22b, and attaches the 1st-3rd sun nail 21a, 22a, 23a. It is operated so as to stand up by the force and engage with the fixed shaft 1, and the respective regulation projections 21b, 22b, 23b are engaged with the first to third sun claws 21a, 22a, 23a to make the first
~ Lock the third sun gears 11a, 12a, 13a so that they cannot rotate. The control of the fourth sun clutch 24 is unnecessary.

As shown in FIG. 1, the ball pusher 34 as shown in FIG. 5 is brought into contact with the protrusion 27a on the right and left sides of the wire hook 27, and the rotation angle thereof is regulated within a predetermined range as shown in FIG. Such a rotation restricting body 35 is non-rotatably fitted onto the fixed shaft 1 via a fixing groove 1a formed therein. Reference numeral 36 in the drawing denotes a retaining nut for each member. Further, between the ball pusher 34 and the driving body 2, and between the driving body 2 and the hub barrel 3
Balls for allowing rotation are respectively interposed between and.

As shown in FIG. 1, the clutch engagement / disengagement mechanism 7 operates the third transmission clutch 19 by placing the third transmission pawl 19a in a state of standing up by a biasing force and engaging with the gear frame 5a. A clutch on / off body 40 for disengaging the third transmission clutch 19 by turning on and off the third transmission pawl 19a toward the drive body 2 side to disengage from the gear frame 5a. And a cam body 41 that is fitted to the first fork portion 25a in a non-rotatable manner and that is rotatably fitted in the fixed plate 42. The fixing plate 42 is the fixing groove 1
It is non-rotatably supported on the fixed shaft 1 via a, and the inner peripheral portion of the clutch on / off member 40 is fitted to the clutch on / off member 40.
Is prevented from rotating with respect to the fixed shaft 1. Cam body 41
4 is a cam as shown in FIG. 4, and the fork portion 41a is used to scissor a pin 43 projecting inward from the fixing plate 42 of the clutch engagement / disengagement body 40 to transmit the rotational force of the operating body 8 to this pin 43, thereby engaging the clutch engagement. The cut body 40 is configured to be rotated. The cam body 41 is prevented from moving to the right by contacting the ball pusher 34 via the fixing plate 42, and the head of the pin 43 press-fitted into the clutch on / off body 40 is pressed as a cam follower. The clutch on / off body 41 is moved to the left by. As shown in FIGS. 21 to 22, the clutch on / off body 40 is provided with an operation portion 40K for the third transmission pawl 19a. The operating portion 40K is brought into contact with the third transmission pawl 19a to lift the pawl 19a to the outer peripheral portion of the clutch engaging / disengaging body 40 so as to switch the pawl 19a to the lying state, and a third transmission portion 40a. Nail 19
A second contact portion 40b for contacting a and maintaining the claw 19a in the laid state is formed. Clutch insert 40
Is biased to the right by a compression spring 44.

In the coaster brake 6, when the drive body 2 is rotated in the reverse direction, the gear frames 4a and 5a are rotated in the reverse direction via a brake clutch 47 as a one-way clutch provided between the drive body 2 and the second gear frame 5a. It works by
The coaster brake 6 is provided on the inner surface of the hub barrel 3 as the braking surface 3
The brake shoe 48 is annularly arranged to face b, and a plurality of rollers 49 are arranged on the inner surface of the brake shoe, and
Cam surface 50 that pushes out the roller 49 in the radial direction at the time of reverse rotation
Is formed on the first gear frame 4a.

The brake clutch 47 is shown in FIGS.
And, as shown in FIG. 3, the ratchet brake claw 47.
a and the third transmission tooth 19b, the brake pawl 47
A is always urged by a spring toward the third transmission tooth 19b side, and the brake claw 47a is oriented on the side opposite to the third transmission clutch 19. The fourth transmission pawl 20a includes the notch portion 51a formed in the annular pawl cage 51 to the fourth transmission tooth 20.
It is projected to the b side, and a part of the claw cage 51 is extended to the base side of the brake claw 47a. The base of the brake pawl 47a is movably supported with respect to the driving body 2 when the brake pawl 47a is engaged with the third transmission tooth 19b, and the notch 51a of the pawl cage 51 is moved to the driving body 2 by the movement of the base. The fourth transmission claw 20a is laid down relative to the first transmission claw 20a to disengage the fourth transmission clutch 20. Therefore, when the drive body 2 rotates in the reverse direction, the coaster brake 6 is operated via the brake clutch 47 and the gear frames 4a and 5a, and the interference between the fourth transmission clutch 20 and the brake clutch 47 is prevented. In the figure, 52 is the fourth
The claw cage 5 is provided on the side where the transmission clutch 20 becomes operable.
It is a torsion spring for urging 1 to return.

Next, referring to Table 1 and the drawings, the switching of the power transmission system and the sun gears 11a, 12a, 13a, 14 are performed.
Regarding the control of a, the basic operation will be described separately for the first planetary gear train 4 and the second planetary gear train 5, and then the switching of the first to seventh stages will be described. In Table 1, "-" indicates a state in which the one-way clutches 17 to 20 and 21 to 24 are not activated and the relative rotation thereof is allowed, and will be referred to as "inoperative state" hereinafter. "O" indicates a state in which the one-way clutch is activated and its relative rotation is blocked, and is hereinafter referred to as "engaged state". “X” indicates a state in which the one-way clutch is forcibly blocked from engaging and the relative rotation thereof is allowed, and is hereinafter referred to as a “disengaged state”. Clutch without "x" is
It means no control is required. Further, for ease of understanding, FIG. 17 shows a simplified diagram of the above configuration.

[0018]

[Table 1]

In the first planetary gear train 4 for speed-up, when one of the first and second sun clutches 21 and 22 is engaged, the angular velocity of the first ring gear 15 is the angular velocity of the relay body 9. Therefore, the second transmission clutch 18 is in the engaged state, while the first transmission clutch 17 is in the inoperative state, and the power transmission system is from the first ring gear 15 via the second transmission clutch 18 to the hub cylinder. The speed-up system reaches 3. On the other hand, the first and second sun clutches 21, 2
When both of the two are in the disengaged state, the second transmission clutch 18 is in the inoperative state, and the power transmission system is a constant velocity system from the relay body 9 to the hub barrel 3 via the first transmission clutch 17. Therefore, in the first planetary gear train 4, the first,
The power transmission system can be switched only by controlling the second sun clutches 21 and 22, and as can be seen from the absence of “x” in the first and second transmission clutches 17 and 18 columns of Table 1, these first and It is not necessary to control the second transmission clutches 17 and 18.

In the second planetary gear train 5 for reduction,
When the transmission clutch 19 is in the engaged state, the power transmission system is a constant velocity system that reaches the gear frame 5a via the driving body 2 and the third transmission clutch 19. On the other hand, when the third transmission clutch 19 is in the disengaged state via the clutch on / off mechanism 7, the power transmission system includes the drive body 2, the fourth transmission clutch 20, and the second ring gear 16 to form a gear. Frame 5
The speed reduction system reaches a. Therefore, the second planetary gear train 5
In the above, the power transmission system can be switched by operating the clutch on / off mechanism 7.

When the operating wire C is pulled to perform the gear shifting operation and the operating body 8 is rotated stepwise by a predetermined angle in the direction opposite to the driving direction K, the first to third control sections 31 to 33 are provided. , And the respective sun clutches 21, 22, 23 and the third transmission pawl 19a can be controlled by the operation of the clutch on / off mechanism 7. Then, based on the above rule, the speed increasing operation can be performed in seven steps in sequence from the lowest 3rd speed L3 to the highest 3rd speed H3. On the other hand, by loosening the operation wire C, the operation body 8 is returned in the same direction as the driving direction K by the restoring force of the second spring S2, and the highest speed high speed three-stage H3.
It is possible to perform the deceleration-side gear shifting operation from to the lowest three speeds L3. The states of the first to third sun clutches 21, 22, and 23 corresponding to the respective states from the highest speed high speed 3rd stage H3 to the lowest speed low speed 3rd stage L3,
Shown in FIGS.

That is, the swing lever type artificial speed change operation tool 6
By the turning operation of the operating body 8 via the operation wire C by 0 and the sliding operation of the clutch on / off body 40 by this turning operation, the third transmission clutch 19 and the second sun clutch 22 are turned on, First and third sun clutches 21,23
Is operated to deactivate the fourth sun clutch 24, the first and fourth transmission clutches 17 and 20, the second transmission clutch 18 is turned on, and the high-speed three-stage H3 is established. The rotational power of is transmitted to the hub barrel 3 via the third transmission clutch 19, the gear frame 5a, the gear frame 4a, the first ring gear 15, and the second transmission clutch 18. With the third transmission clutch 19 and the first sun clutch 21 engaged,
The second sun clutch 22 is disengaged, and the third sun clutch 23
Is operated to the inoperative state, the fourth sun clutch 24, the first and fourth transmission clutches 17 and 20 are inoperative, the second transmission clutch 18 is engaged, and the high speed two-stage H2 is established. The rotational power of is transmitted to the hub barrel 3 via the third transmission clutch 19, the gear frame 5a, the gear frame 4a, the first ring gear 15, and the second transmission clutch 18. With the third transmission clutch 19 disengaged, the second and third sun clutches 2
When the first and second sun clutches 21 and 2 are operated to be in the non-operated state by turning on the second and third clutches 23 and 24, the fourth sun clutch 24 and the first transmission clutch 17 are in the non-operative state, and the second and fourth transmission clutches 1
When 8 and 20 are turned on, the high speed first stage H1 is achieved, and the rotational force of the driving body 2 is the fourth transmission clutch 20 and the second ring gear 1.
It is transmitted to the hub barrel 3 via 6, the gear frame 5a, the gear frame 4a, the first ring gear 15, and the second transmission clutch 18. Third transmission clutch 19 and third sun clutch 23
Turn off the first sun clutch 21 in the inoperative state,
When the sun clutch 22 is turned on and off, the fourth sun clutch 24, the second and fourth transmission clutches 18 and 20 are turned on, the first transmission clutch 17 is deactivated, and the medium speed stage M is set. The turning power of 2 is the 4th transmission clutch 2
0, the gear frame 5a, the gear frame 4a, and the second transmission clutch 18 are transmitted to the hub barrel 3. Disengage the third transmission clutch 19, the second and third sun clutches 22, 23,
When the first sun clutch 21 is turned on and off, the fourth sun clutch 24, the second and fourth transmission clutches 18 and 20 are turned on, the first transmission clutch 17 is deactivated, and the low speed first stage L1 is established. The rotational force of the driving body 2 is the fourth transmission clutch 20, the second ring gear 16, the gear frame 5a, the gear frame 4
It is transmitted to the hub barrel 3 via a, the first ring gear 15, and the second transmission clutch 18. Third transmission clutch 1
9, when the first and second sun clutches 21 and 22 are disengaged and the third sun clutch 23 is turned on and off, the fourth sun clutch 24 and the second transmission clutch 18 are in the inoperative state,
And the 4th transmission clutches 17 and 20 are engaged, and the low speed second stage L2 is established, and the rotational force of the driving body 2 is the 4th transmission clutch 20, the second ring gear 16, the gear frame 5a, the gear frame 4a,
It is transmitted to the hub barrel 3 via the relay body 9 and the first transmission clutch 17. When the third transmission clutch 19, the first, second and third sun clutches 21, 22, 23 are turned off, the fourth sun clutch 24, the first and fourth transmission clutches 17, 20 are engaged, and the second transmission clutch 18 is turned on. In the non-operating state, the low-speed three-stage L3 is established, and the rotational force of the driving body 2 causes the fourth transmission clutch 20, the second ring gear 16, and the gear frame 5 to rotate.
It is transmitted to the hub barrel 3 via a, the gear frame 4a, the relay body 9, and the first transmission clutch 17.

As shown in Table 1 and FIGS. 10 to 16, the third transmission pawl 19a and the sun pawl 2 are used for speed-up and speed-down shifts.
This is accompanied by a switching operation of the 1a, 22a, and 23a from the standing state to the lying state, and when the traveling driving torque is applied to the driving body 2 by the traveling driving operation, the transmission in the standing state is performed. Due to the transmission load acting on the claws 19a and the sun claws 21a, 22a, 23a, the transmission claw 19a and the sun claws 21a, 22a, 23a are engaged or disengaged from the gear frame 5a or the fixed shaft 1. Withdrawal resistance increases,
In addition, the detachment resistance varies depending on the difference in the operation target claws to be fallen down. However, since the springs S1 and S2 are configured to apply the operating force to the operating body 8 and the clutch on / off body 40, any one of the transmission pawl 19a and the sun pawls 21a, 22a, and 23a can be operated to fall. Even in such a case, even if the shift operation is performed while the traveling drive operation is performed, the torque equalizing means is provided so that the maximum torques of the traveling drive torques acting during the fall operation are the same or almost the same. Regardless of whether the gear shift target speed that should be generated by the gear shifting operation is from the high speed third gear H3 to the low speed third gear L3, the gear shifting can be performed in a state in which the maximum travel drive torque that can be applied is substantially the same. Is considered. That is, at the time of gear shifting on the speed increasing side, the first spring S1 is moved by the first spring S1 when the second sleeve 26 is rotated by the gear shift operation device 60.
The sleeve 25 and the clutch insertion / disconnection body 40 are interlocked. Then, the transmission claw 19a and the sun claws 21a, 22a,
When the detachment resistance of the gear 23a from the gear frame 5a or the fixed shaft 1 is less than or equal to the set resistance value, the first spring S1
The release resistance is overcome, and the first sleeve 25 and the clutch on / off member 40 are rotated or slidably operated immediately in association with the rotation of the second sleeve 26, and the sun claw 2 by the first sleeve 25 is operated.
1a, 22a, and 23a are operated to lay down, and the clutch pawl 40 is operated to lay down the transmission pawl 19a. Then, the transmission claw 19a and the sun claws 21a, 22
When the disengagement resistance of the a and 23a from the gear frame 5a or the fixed shaft 1 is larger than the set resistance value, the disengagement resistance and the turning force of the second sleeve 26 due to the manual shift operation,
Due to the interlocking accommodation of the set angle D between the sleeves 25 and 26, the gear shift operating device R is further connected to the gear shift operating tool 60.
The first spring S1 is elastically deformed and the operating force is applied to the first sleeve 25 and the clutch on / off body 40 in order to hold the first sleeve 25 and the clutch on / off state. The body 40 is a gear shift operation tool 60.
Even though the operation of the gear shift operation tool 60 has already been performed, the operation is stopped prior to the operation of the gear shift operation tool 60, and the transmission claw 19a is stopped.
The sun claws 21a, 22a, 23a are maintained in the upright state. Then, the operated crank reaches the top dead center, the bottom dead center, or the vicinity thereof, and the drive torque acting on the driving body 2 is reduced, so that the transmission claw 19a and the sun claws 21a, 22a.
As the detachment resistance of the a and 23a from the gear frame 5a or the fixed shaft 1 decreases to the set resistance value, the first spring S1
Rotates or slides the first sleeve 25 or the clutch engagement / disengagement body 40 by the operating force charged until then, and the sun claws 21a, 22a, 2 by the first sleeve 25 are moved.
3a and the switching of the transmission pawl 19a by the clutch insertion / disconnection body 40 are performed. At the time of gear shifting on the deceleration side, the second spring S2 is wound up at the time of gear shifting to increase speed, and the elastic restoring force charged causes the first sleeve 2 to move.
5 or the clutch on / off body 40 is rotated or slid. Then, the transmission claw 19a and the sun claws 21a, 22
When the separation resistance of the a and 23a from the gear frame 5a or the fixed shaft 1 is less than or equal to the set resistance value, the second spring S2
However, when the first sleeve 25 and the clutch on / off member 40 are rotated or slidably operated in synchronism with the rotation of the second sleeve 26, the sun claws 21a, 22a, 23a is operated to lay down, and the clutch pawl 40 is used to lay down the transmission pawl 19a. Then, the transmission claw 19a and the sun claw 21a,
When the disengagement resistance of the gears 22a and 23a from the gear frame 5a or the fixed shaft 1 is larger than the set resistance value, the disengagement resistance and the slack of the operation wire C further cause the speed change operation device R to change the speed. In order to hold the operating tool 60 at the operated new operating position, the second spring S2 does not elastically restore the predetermined trooke, and only the operating force for the first sleeve 25 and the clutch on / off body 40 is charged. , The first sleeve 25 and the clutch on / off body 40 stop operating by prioritizing the operation of the speed change operation tool 60 even though the operation of the speed change operation tool 60 has already been performed. The claws 21a, 22a and 23a are maintained in the standing state. Then, the operated crank reaches the top dead center, the bottom dead center, or the vicinity thereof, and the driving torque acting on the driving body 2 is reduced, so that the transmission pawl 19a and the sun pawl 21a,
As the disengagement resistance of the gears 22a and 23a from the gear frame 5a or the fixed shaft 1 decreases to the set resistance value, the second spring S2 sufficiently elastically restores the predetermined stroke so that the first sleeve 25 and the clutch engagement / disengagement body 40 are removed. The sun claws 21a, 22a, 2 by the first sleeve 25 are rotated or slid.
3a and the switching of the transmission pawl 19a by the clutch insertion / disconnection body 40 are performed. The torque equalizing means includes a first arm length L1, a second arm length L2, a claw inclination angle X, an overlapping angle Y, a cam angle Z, a first inclination angle A, and a second inclination shown in FIGS. It is at corner B. That is, the cam angle Z is for the transmission pawl 19a,
The disengagement resistance force W due to the gear frame 5a and the clutch on / off body 40
Is a relative angle with respect to the lodging operation force F. The fall operation force F is determined by the setting of the first inclination angle A and the second inclination angle B of the operation cam surface portion 40a acting on the transmission pawl 19a of the clutch on / off body 40 as shown in FIGS. The cam angle Z is changed by changing the angle A and the second tilt angle B. The first inclination angle A is determined by the clutch insertion / disconnection body 40.
Is an angle for camming the transmission pawl 19a by sliding in the axial direction of the fixed shaft 1. The second inclination angle B is an angle for camming the transmission pawl 19a for rotating the transmission pawl 19a with respect to the clutch on / off body 40.
The first arm length L1, the second arm length L2, the claw inclination angle X, and the overlapping angle Y are for the sun claws 21a, 22a, 23a. The first arm length L1 is the undulating axis P
And the position where the operating body 8 acts on the fall operation force F. The second arm length L2 is defined by the undulating axis P and the fixed axis 1.
This is the distance from the location where the lodging resistance force W is applied. Even if the falling resistance of the sun nail is constant, the operating force required for falling operation of the nail is changed by changing the ratio between the first arm length L1 and the second arm length L2. Claw tilt angle X
Indicates the degree of inclination of the sun nail relative to the fixed axis 1,
Even if the transmission load is constant, the larger the claw inclination angle X, the greater the claw disengagement resistance. The overlapping angle Y indicates the degree of overlap between the rotation locus of the tip of the claw and the ratchet portion of the fixed shaft 1. Even if the transmission load is constant, the larger the overlapping angle Y, the greater the resistance of the claw to separate. is there. That is,
By changing the nail inclination angle X and the overlapping angle Y, the operating force required for the fall operation of the nail changes. In other words, even if the traveling drive torque is constant, the resistance to disengagement of the transmission pawl 19a and the sun pawls 21a, 22a, and 23a from the gear frame 5a or the fixed shaft 1 differs depending on the pawl, and the springs S1 and S2 are The yielding operation force to be exerted differs depending on the difference in the gear shift target speed that should be produced. The cam angle Z of the transmission pawl 19a and the sun pawls 21a, 22a, 23a, the first arm length L1 and the second arm length. Depending on the setting of the ratio of L2, the overlapping angle Y, and the claw inclination angle X, the maximum torque of the traveling drive torque that allows the fall operation even while the traveling drive torque is being applied is the transmission claw 19a, the sun claws 21a, 22a, It becomes the same or almost the same regardless of which of the 23a is the fall operation target nail. In constructing the sun claws 21a, 22a, 23a, as shown in FIGS. 9 (a) to 9 (c), the claw body T is attached to the mounting portion T1 on one end side by the sun gear 11a, 12a or 13a so as to provide the axis P. It is supported so as to oscillate and oscillate around, and the regulating projection 21b of the fixed shaft 1 is supported by the toe portion T2 on the free end side.
And 22b, and the control portion 31, 32 or 3 of the first sleeve 25 is provided on the lateral side of the free end side of the pawl body T.
3 is provided with a laying operation portion G that abuts, so that the laying operation portion G and the claw main body T are provided with an undulating axis so that the ratio between the first arm L1 and the second arm L2 can be easily set to a desired ratio. The position is displaced in the P direction.

[Second Embodiment] Next, a second embodiment of the present invention will be described. As shown in FIG. 24, a cylindrical axle 6 configured to be non-rotatably fastened and fixed to a vehicle body frame (not shown).
1, the driving body 2 through the ball retainer 62 and the ball 63.
While the hub barrel 3 is rotatably attached, a driving force is introduced into the driving body 2 by the chain wheel 2a, and the turning force of the driving body 2 is changed by the first to fourth transmission pawls 66 to 69 and the planetary gear 7.
The transmission main body including 0 and the like is configured to change the speed in three stages of high / medium / low speed and transmit the speed to the hub barrel 3, thereby forming an internal transmission for a bicycle capable of three-speed shifting. The speed change device is configured to perform a speed change operation by a switching operation of a speed change device main body by a speed change operation mechanism E including a first operation cam 71, a second operation cam 72, an operation rod 73, and the like. Configured.

The transmission main body includes a first transmission rotating body 74 and a carrier 75 which are rotatably fitted on the cylinder wheel shaft 61 and the driving body 2.
And a second transmission rotary body 76, the first transmission pawl 66 located between the drive body 2 and the first transmission rotary body 74, the second transmission located between the drive body 2 and the second transmission rotary body 76. Nail 6
7, the third transmission pawl 68 located between the first transmission rotor 74 and the hub barrel 3, and the planetary gear 7 attached to the carrier 75.
0, the fourth transmission pawl 69 located between the carrier 75 and the hub barrel 3, and the like. The first transmission pawl 66 is
As shown in FIG. 27, it is attached to the outer peripheral side of the drive body 2 so as to rotate integrally with the drive body 2 and to oscillate and swing, and the toe portion is for passive use of the first transmission rotary body 74. The ratchet pawl is urged upright by a pawl spring 66a so as to engage with the ratchet tooth 74a. That is, the first transmission pawl 66 engages with the ratchet teeth 74a for standing up bias due to the difference in rotational speed between the drive body 2 and the first transmission rotary body 74, and the rotational force of the drive body 2 is transmitted by the first transmission. The standing transmission state transmitted to the rotating body 74 and the ratchet tooth portion 74
It is configured to be automatically retracted from the first transmission rotator 74 for the pressure swing operation by a and to be switched to a non-transmission state in which the first transmission rotator 74 is allowed to rotate ahead of the drive body 2. I am doing it. The second transmission pawl 67 rotates integrally with the driving body 2 on the inner peripheral side of the driving body 2 as shown in FIG.
It is attached so as to oscillate and oscillate, and by undulating, the toe portion engages with the passive tooth portion 76a of the second transmission rotary body 76 to transmit the rotational power of the drive body 2 to the second transmission rotary body 76. It is configured to switch between a standing power transmission state and a fall non-transmission state in which the toe portion is disengaged from the second transmission rotary body 76 and the transmission from the drive body 2 to the second transmission rotary body 76 is cut off. Claw spring 67a so that it can automatically return to the state
Is standing up by. The second transmission rotator 76 is rotatably fitted onto the cylinder wheel shaft 61, and is attached to the carrier 75 by a transmission tooth portion 76b provided at an end portion opposite to a side where the passive tooth portion 76a is located. It is engaged so that it can rotate integrally. The planetary gear 70 rotates around the axis of the mounting shaft 77 as the carrier 75 rotates, and rotates around the carrier 7.
The carrier 75 is rotated so as to revolve around the rotation axis of the carrier 5.
It is pivotally attached to and is engaged with the sun gear portion 61a of the cylinder wheel shaft 61. The first transmission rotor 74 is engaged with the planetary gear 70 by an internal gear 74b provided at the end opposite to the side where the ratchet teeth 74a are located. That is, when the second transmission pawl 67 is in the standing transmission state, the rotational force of the driving body 2 is transmitted to the carrier 75 by the second transmission rotary body 76, and the rotational force of the carrier 75 is increased by the planetary gear 70 to make the first transmission. It is configured to be transmitted to the rotating body 74. At this time, the first transmission rotator 74 is configured to rotate ahead of the drive body 2 due to the speed-up action of the planetary gear 70 and the advance rotation permission of the first transmission pawl 66. .. When the second transmission pawl 67 is in the laid-down non-transmission state, the rotational force of the driving body 2 is set to the first transmission pawl 66 by the first transmission pawl 66.
The transmission power is transmitted to the transmission rotary body 74, and the rotational force of the first transmission rotary body 74 is reduced by the planetary gear 70 and transmitted to the carrier 75. As clearly shown in FIG. 28, the third transmission pawl 68 is mounted so that the first transmission rotary body 74 is integrally rotated by a pivot shaft 78 and oscillates and oscillates. The standing transmission state in which the rotary power of the first transmission rotor 74 is transmitted to the hub barrel 3 by engaging the passive tooth portion 3a of the hub barrel 3 and the toe portion is disengaged from the hub barrel 3 The transmission to the hub barrel 3 is switched to a fallen non-transmission state in which the transmission to the hub barrel 3 is cut off, and a standing spring is urged by a pawl spring 68a so as to automatically return to the standing transmission state. The third transmission pawl 69 is attached to the carrier 75 so as to rotate integrally with the carrier 75 so as to oscillate and oscillate, and the tip of the pawl is a passive ratchet tooth 3 b of the hub barrel 3.
The ratchet pawl is urged upright by a pawl spring 69a so as to engage with. That is, due to the difference in rotational speed between the carrier 75 and the hub barrel 3, the fourth transmission pawl 69 is engaged with the ratchet teeth 3b for urging the standing force and the motive power of the carrier 75 is transmitted to the hub barrel 3. And the hub barrel 3 for the state and the pressing and swinging operation by the ratchet teeth 3b.
It is configured to be automatically retracted from the retracted state to the non-transmission state in which the hub barrel 3 is allowed to rotate forward with respect to the carrier 75. That is, the second transmission claw 67 and the third transmission claw 6
8 by switching the undulations, the action that enables the first and fourth transmission claws 66 and 69 to be transmitted and the preceding rotation, and the speed change action of the planetary gear 70 cause the drive unit 2 to the hub barrel 3 to move.
As shown in Table 2 below, the power transmission state is switched between high, medium and low speed. That is, when both the second transmission claw 67 and the third transmission claw 68 are in the upright transmission state, the turning force of the drive body 2 causes the second transmission claw 67 and the second transmission rotary body 7 to rotate.
6, carrier 75, planetary gear 70, first transmission rotor 74
And, it is transmitted to the hub barrel 3 via the first transmission pawl 68, and the high speed state is achieved. When the second transmission pawl 67 is in the resting non-transmission state and the third transmission pawl 68 is in the standing transmission state, the rotational force of the driving body 2 is transmitted through the first transmission pawl 66, the first transmission rotor 74 and the third transmission pawl 68. Is transmitted to the hub barrel 3 and becomes a medium speed state. When both the second transmission pawl 67 and the third transmission pawl 68 are in the non-laid-down state, the rotational force of the driving body 2 causes the first transmission pawl 66, the first transmission rotor 74, the planet gear 70, the carrier 75, and the 4 is transmitted to the hub barrel 3 via the transmission claw 69,
It becomes a low speed state.

The speed change operation mechanism E includes a first operation cam 71 for operating the second transmission pawl 67, a second operation cam 72 for operating the third transmission pawl 68, a first operation cam 71 and a ball. A coil type feed spring 79 located between the presser foot 62, a coil type return spring 80 located between the second operation cam 72 and the sun gear portion 61a, a cylinder axle 61.
The operating rod 73 positioned inside the operating rod 73, and the operating rod 73 that is interlocked with the operating rod 73 via the interlocking mechanism 81 and the speed change wire 82. By sliding operation of 73, a speed state at a predetermined stage is revealed. That is, the first operation cam 71 is provided on the cylindrical axle 6
It is externally fitted to the cylinder axle 61 so as to slide in the axle axis direction while being rotated by the rotation stopper 85 with respect to 1, and this sliding causes the stopper portion 2b of the driving body 2 as shown in FIG. The cam surface 86 as shown in FIG.
A standing operation position for operating the second transmission pawl 67 in the standing transmission state by allowing the second transmission pawl 67 to stand up by the pawl spring 67a away from the transmission pawl 67, and the standing operation position as shown in FIGS. 25 and 26. It is configured to move from the position to the second transmission pawl 67, and to switch to the laying operation position where the cam surface 86 is pressed to push the second transmission pawl 67 to the laid-up non-transmission state. The rotation stopper 85 is configured to slide the first operation cam 71 by sliding with respect to the cylinder wheel shaft 61 by the action of the elongated hole shape of the rotation stopper insertion hole 61b of the cylinder wheel shaft 61. There is. The second operation cam 72 is formed by the large-diameter portion of the second transmission rotary body 76.
While being engaged with the carrier 75 of the transmission rotor 76, it is configured to slide in the axial direction with respect to the cylinder axle 61 for sliding with respect to the cylinder axle 61, and by this sliding,
As shown in FIGS. 24 and 25, the cam surface 87 as shown in FIG. 33 comes into contact with the stopper ring 88 of the cylinder wheel shaft 61, and is separated from the third transmission pawl 68 to permit the standing movement of the third transmission pawl 68 by the pawl spring 68a. By doing so, the third transmission pawl 68 is moved to the upright transmission position, and from the upright operation position to the third transmission pawl 68 as shown in FIG. The claw 68 is configured to be switched to a fall operation position where the claw 68 is pressed in a fall non-transmission state. The return spring 80 switches the second operation cam 72 to the upright operation position to bias the second operation cam 72.
3 is configured so as to automatically return to the upright operation position, and the urging force P ₁ of the return spring 80 with respect to the second operation cam 72 is caused by sliding of the second operation cam 72.
It is configured to change as shown in FIG. The feed spring 79 urges the first operation cam 71 to be urged by the urging force P _{2 as} shown in FIG. 34 to the fall operation position until the transmission main body is switched from the high speed state to the medium speed state. After switching to the high speed state, the second operation cam 72
The second operation cam 72 via the first operation cam 71 that contacts the
And the urging force P ₁ of the return spring 79 acts to urge the second operation cam 72 from the upright operation position to the fall operation position by the urging force P ₃ shown in FIG. It is configured as follows. As shown in FIGS. 24 to 26, as the shift lever 84 is rocked, the lever operating force is changed to the shift wire 82 and the interlocking mechanism 81.
Is transmitted to the operation rod 73 through the operation rod 73, and the operation rod 73 slides on the entry side with respect to the cylinder axle 61 to push and slide the detent 85 against the feed spring 79.
The first operation cam 71 is switched and the second operation cam 7 is operated.
2 is operated by the biasing force of the return spring 80, or the operation rod 73 is slid toward the protruding side with respect to the cylinder axle 61 to allow the switching operation by the feed spring 79. The second operation cam 72 is configured to be switched. The operation rod 73 is held at a predetermined sliding position due to the operation of holding the speed change lever of the speed change operation section 83, and the first operation cam 71 is moved to the fall operation position or the standing operation position and the spring 7 is moved.
It is constructed so as to be received and held against 9. That is, as shown in FIGS. 24 to 26, when the speed change lever 84 is operated to the high speed position H, the operation rod 73 becomes the operation position shown in FIG. 24, and the first operation cam 71 is erected by the operation force of the operation rod 73. When the second transmission pawl 67 is in the position, the second transmission pawl 67 is operated in the standing transmission state, and the second operation cam 72 is in the standing operation position by the operation force of the return spring 80.
By operating 8 to the upright transmission state, the high speed state is revealed. When the speed change lever 84 is operated to the medium speed position M, the operation rod 73 becomes the operation position shown in FIG.
The first operation cam 71 is in the fall position due to the sliding operation by the elastic restoring force of the feed spring 79 and the stopper action of the operation rod 73, and the second transmission pawl 67 is operated in the fall non-transmission state to perform the second operation. The cam 72 is moved to the upright operation position by the operation force of the return spring 80, and the third transmission pawl 68 is operated to the upright transmission state, whereby the medium speed state is revealed. When the speed change lever 84 is operated to the low speed position L, the operation rod 73 becomes the operation position shown in FIG. 26, and the first operation cam 71 slides by the elastic restoring force of the feed spring 79 and the stopper action of the second operation cam 72. And the second transmission pawl 67 is operated in the laid-down non-transmission state to move the second operation cam 72 to the laid-down operation position by the sliding operation force due to the elastic restoring force of the feed spring 79. By operating the transmission pawl 68 to the non-transmission state of the lodging,
The low speed state is revealed.

[0027]

[Table 2]

The cam surface 86 of the first operation cam 71,
Also, the cam surface 87 of the second operation cam 72 switches the transmission pawl 67 or 68 from the falling position and the operation cam 7
A plurality of first cam surfaces 86a arranged in the circumferential direction of 1 or 72
Or 87a and the second position that keeps the transmission pawl 67 or 68 in the fall position and continues in the circumferential direction of the operation cam 71 or 72.
It is constituted by the cam surface 86b or 87b. The first cam surface 87a has a first inclination angle A as shown in FIG. 31 or 33 and a second inclination angle B as shown in FIG. 30 or 33 with respect to the sliding axis H of the operation cam 71 or 72. Due to this, the transmission claw 67 or 68 falls down due to relative sliding between the operation cam 71 or 72 and the transmission claw 67 or 68 in either the rotational axis direction or the rotation direction of the drive body 2 or the first transmission rotary body 74. It is formed by a flat inclined surface. That is, as the first operation cam 71 and the second operation cam 72 slide from the upright operation position and come into contact with the transmission pawl 67 or 68, the lodging action by the cam action by the first inclination angle A, the transmission pawl 67.
Or 68 is rotated together with the drive body 2 or the first transmission rotary body 74 to rotate with respect to the operation cam 71 or 72, and both the fall action due to the cam action due to the second inclination angle B. The falling action causes the transmission pawl 67 or 68 to fall, and the transmission pawl 67 or 68 is promptly switched to the non-transmission state for the sliding stroke and sliding operation force of the operation cam 71 or 72. There is.

The spring 79 operates the operation cams 71 and 72.
By applying a nail operating force to the
No matter which of claws 87 and 87 is the fall operation target nail, the travel drive operation can be performed by providing a torque equalizing means for making the maximum torque of the travel drive torque acting during the fall operation the same or substantially the same. However, even if a gear shift operation is performed, the gear shift is executed only when the crank (not shown) is located at a low drive load point at or near top dead center or bottom dead center. There is. That is, the torque equalizing means is the first inclination angle A and the second inclination angle B shown in FIGS. 29 to 33, and the second transmission pawl 67 shown in FIG.
The cam angle Z as shown in FIG. 8 and the first arm length L1 and the second arm length L2 of the third transmission pawl 68 as shown in FIG. The cam angle Z is determined by the disengagement resistance force W due to the engagement of the transmission claw 67 with the transmission rotating body 76, and the first operation cam 71.
Is a relative angle with respect to the lodging operation force F. The cam angle Z changes depending on the setting of the first tilt angle A and the second tilt angle B of the operation cam 72. The first arm length L1 is the distance between the undulating axis P and the location where the fall operation force F is applied by the second operating cam 72, and the second arm length L2 is the undulating axis P and the hub barrel 3 This is the distance from the location where the lodging resistance force W is exerted by the engagement with. By changing the ratio between the first arm length L1 and the second arm length L2, the operating force required for the fall operation of the pawl 68 is changed. The first inclination angle A and the second inclination angle B of the first cam surface 86a of the first operation cam 71 and the first cam surface 87a of the second operation cam 72 are formed as shown in Table 3 below. As a result, the sliding force of the first operation cam 71 acts on the second transmission pawl 67 as a fall operation force, and the sliding force of the second operation cam 72 acts on the third transmission pawl 68 as a fall operation force. The shapes of the first cam surfaces 86a and 87a are made different so that the efficiency of doing so is different.

[0030]

[Table 3]

That is, the first operation cam 71 is operated by shifting operation.
Even if the sliding operation force by the feed spring 79 acts on the second operation cam 72 or the second operation cam 72, the crank is located at a position other than the low drive load portion, and a driving torque larger than the set torque acts on the driving body 2, When the transmission load acting on the second transmission claw 67 and the third transmission claw 68 is larger than the set load, the second operation cam 7 of the second transmission claw 67 and the third transmission claw 68 due to this transmission load.
The feed spring 79 does not elastically return to a predetermined position because of resistance to detachment from the hub barrel 3 or the first operation cam 71.
Therefore, the second operation cam 72 does not switch to the fallen operation position. Then, the crank is located at the low drive load portion, the traveling drive torque acting on the driving body 2 is reduced to the set torque, and the transmission load acting on the second transmission pawl 67 and the third transmission pawl 68 is set to the set load. As the resistance of the second transmission pawl 67 and the third transmission pawl 68 from the second operation cam 72 or the hub barrel 3 decreases, the feed spring 79 elastically restores as predetermined and the first operation cam 71 decreases. Further, the second operation cam 72 is switched to the fallen operation position. And the second
Although the maximum disengagement resistance where the transmission pawl 67 can be disengaged from the second operation cam 72 and the maximum disengagement resistance where the third transmission pawl 68 can be disengaged from the hub barrel 3 are different. Regardless of the fact that the same spring 79 applies an operating force to both operation cams 71 and 72, the cam angle Z of the second transmission pawl 67 and the third transmission pawl 68 and the arm length L1, In order to set L2 and to set the first tilt angle A and the second tilt angle B of the operation cams 71 and 72, the fall operation target claw is set to the second transmission claw 67 and the third transmission claw 68. In either case, the maximum torque of the traveling drive torque becomes the same or almost the same when the falling operation of the transmission pawls 67 and 68 becomes possible.

It should be noted that reference numerals are given in the claims for convenience of comparison with the drawings, but the present invention is not limited to the configurations of the accompanying drawings by the entry.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a 7-speed internal transmission.

FIG. 2 is a sectional view in a direction orthogonal to a fixed axis, showing a relationship between a brake clutch and a fourth transmission pawl.

FIG. 3 is a sectional view in a direction orthogonal to a fixed axis showing a relationship between a fourth transmission pawl and a pawl cage.

FIG. 4 is a perspective view of an operating body and a spring.

FIG. 5 is a perspective view of a ball pushing device.

FIG. 6 is a perspective view of a wire hook.

FIG. 7 is a perspective view of a rotation restricting body.

FIG. 8 is a sectional view of the operating body.

FIG. 9 is an explanatory diagram of a sun nail.

FIG. 10 is a sectional view in the direction orthogonal to the fixed axis showing the high speed three-stage state of each sun clutch.

FIG. 11 is a sectional view in the direction orthogonal to the fixed axis showing the high speed two-stage state of each sun clutch.

FIG. 12 is a sectional view in the direction orthogonal to the fixed axis showing the high speed one-stage state of each sun clutch.

FIG. 13 is a cross-sectional view in the direction orthogonal to the fixed axis showing the medium speed stage state of each sun clutch.

FIG. 14 is a cross-sectional view in the direction orthogonal to the fixed axis showing the low speed one-stage state of each sun clutch.

FIG. 15 is a cross-sectional view orthogonal to the fixed axis showing the low speed two-stage state of each sun clutch.

FIG. 16 is a sectional view in the direction orthogonal to the fixed axis showing the low speed three-stage state of each sun clutch.

FIG. 17: Diagram of 7-speed internal transmission

FIG. 18 is a side view of the transmission pawl.

FIG. 19 is a side view of the sun nail.

FIG. 20 is a side view of the sun nail.

FIG. 21 is a front view of the clutch insert / cut body.

FIG. 22 is a side view of the clutch insert / cut body.

FIG. 23 is a cross-sectional view of the clutch insert / cut body.

FIG. 24 is a sectional view of the three-speed transmission in a high speed state.

FIG. 25 is a cross-sectional view of the 3-speed transmission in a medium speed state.

FIG. 26 is a sectional view of the three-speed transmission in a low speed state.

FIG. 27 is a sectional view of a second transmission pawl disposition portion.

FIG. 28 is a cross-sectional view of a third transmission pawl disposition portion.

FIG. 29 is a front view of the first operation cam.

FIG. 30 is a plan view of the first operation cam.

FIG. 31 is a sectional view of a first operation cam.

FIG. 32 is a front view of a second operation cam.

FIG. 33 is a partially cutaway plan view of the second operation cam.

FIG. 34 is an explanatory diagram of spring biasing force.

FIG. 35 is a front view of a transmission pawl.

[Explanation of symbols]

1,3,5a, 76 Engagement target member 8,40,71,72 Operation body S1, S2,79 Spring 19a, 21a, 22a, 23a, 67,68 Speed change claw 60,84 Manual speed change operation tool A, B, L1, L2, X, Y, Z Means T Claw body G Falling operation part P Lifting shaft core

Claims (3)

[Claims] 1. A plurality of speed change pawls (19a), (21a), (2)
2a), (23a), (67), and (68) are engaged / disengaged members (5
a), (1), (76), standing state in which it engages with (3), and a fallen state in which it disengages from the members (5a), (1), (76), (3) to be engaged and disengaged. Each of the gear shift claws (19a), (21a), (22a), (23a),
A bicycle transmission which is operated to shift gears by undulating operations of (67) and (68), the shift gears (19a), (21a), (22a), (23a),
Operation bodies (8), (40), (7) for (67), (68)
The springs (S1), (S2), (79) for applying an operating force for operating the speed change pawls to (1), (72) are provided with the speed change pawls (1).
9a), (21a), (22a), (23a), (67), (6
8) The members to be engaged / disengaged (5a), (1), (76), (3)
When the disengagement resistance from is larger than the set resistance value, due to the disengagement resistance, the operation bodies (8), (40), (are given priority over the operation of the artificial speed change operation tools (60), (84). 71), (7
2) stops operating and the speed change pawls (19a), (21a),
(22a), (23a), (67), and (68) are allowed to stand upright, and the speed change pawls (19a),
The detachment resistance of (21a), (22a), (23a), (67), (68) from the engagement / disengagement target members (5a), (1), (76), (3) is less than or equal to the preset resistance value. , The operating bodies (8), (40), (71), (72) are actuated to operate the speed change pawls (19a), (21a), (22a), (23a), (67),
In the state in which (68) is changed to fall, and further in the state where the traveling drive torque is applied, the speed change pawls (19a), (2
1a), (22a), (23a), (67), (68) in a state of performing a fall operation, the operating bodies (8), (40), (71),
(72), the springs (S1), (S2), (79) cause the speed change pawls (19a), (21a), (22a), (23a), (67),
The maximum torque of the traveling drive torque acting when the (68) is tilted is determined by which of the speed change pawls (19a),
Even when (21a), (22a), (23a), (67), and (68) are used as fallen operation target nails, means (L1), (L2), () that show the same or almost the same state X), (Y),
A bicycle transmission including (Z), (A), and (B). 2. The speed change pawls (21a), (22a), (23)
In the configuration of a), the claw body (T) that is engaged and disengaged with the engagement and disengagement target member (1) and the fall operation section (G) on which the operating body (8) acts are provided with the speed change claw (21a), (22a), (23
The bicycle transmission according to claim 1, wherein the transmission is provided so as to be displaced in the direction of the undulating axis (P) of (a). 3. The engagement / disengagement target member (1) is a fixed shaft, and the operation body (8) is a cylindrical operation body rotatably fitted on the engagement / disengagement target member (1). Spring (S
The bicycle transmission according to claim 1 or 2, wherein (1) and (S2) are formed in a torsion coil spring and are externally fitted to the operating body (8).