JP3218877B2 - Bicycle brake operating device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bicycle brake operating device.

[0002]

2. Description of the Related Art Generally, a brake operating device has a lever 1 and a bracket 2 rotatably mounted on a lever rotation shaft as shown in FIG. 18, and an inner wire end (hereinafter abbreviated as a wire end) 4 is also a lever of the lever 1. It is fitted at a position a dimension away from the rotating shaft 3. b is an initial width between the handlebar (hereinafter abbreviated as a bar) 5 and the lever 1. If this width is too large, the lever 1 becomes difficult to grip, and the brake operability deteriorates.

[0003] When the lever 1 is operated and rotated, the wire end 4 rotates about the lever rotation shaft 3, whereby the inner wire 6 is pulled. At this time, the ratio of the distance from the lever rotation shaft 3 to the wire end 4 and the distance from the lever rotation shaft 3 to the power point of the lever 1 (hereinafter referred to as lever ratio) is constant. For this reason, in the case of a caliper brake, for example, the pulling direction changes at the same lever ratio after the shoe starts braking until the shoe contacts the rim, so that the following inconvenience has occurred.

The angle formed by the inner wire 6 and the straight line connecting the lever rotation shaft 3 and the wire end 4 is initially approximately a right angle α1, but changes to an acute angle α2 when the lever 1 comes into contact with the bar 5. However, the arm length of the moment becomes shorter. As a result, the wire feed amount (hereinafter referred to as wire feed ratio) with respect to the unit change angle of the lever 1 becomes smaller,
Ratio of wire tension P to input F (hereinafter referred to as force ratio)
Increases (see g1 in FIGS. 6 and 7).

As described above, the wire feed ratio is large in the early stage of the operation of the lever 1, slightly reduced near the start of braking, and greatly reduced as the lever 1 approaches the bar 5, so that the lever 1 can easily contact the bar 5. (See g1 in FIG. 7).

Further, the braking force of the brake with respect to the amount of operation of the lever 1 does not change linearly, that is, the power ratio becomes a curve that rises to the right.
Despite the necessity of delicate braking operation for braking, braking controllability was poor (see g1 in FIG. 6).

[0007] In order to solve these disadvantages of the general brake operation device, there is known an example in which a lever ratio and a wire feed ratio are variable. For example, Japanese Utility Model Laid-Open No. 53-6675
Japanese Patent Application Publication No. 6-No.

The prior art will be described below with reference to FIG. In FIG. 19, the pivot pin 7 slides in the guide path 8, which is a groove parallel to the direction of the inner wire, in response to the movement of the lever 9. In the example of FIG.
The length c obtained by dividing the length c before and after the straight line X is C1,
Assuming that C2, C1> C2, so that the lever rotation shaft 10
And the distance to the shaft support pin 7, that is, the dimension related to the wire tension P changes from d2 to d1, and the lever rotation shaft 1
0, perpendicular to the wire tension line (wire feed direction)
The arm length of the so-called moment is constant at d2, but the lever ratio and the wire feed ratio change. That is, the guide path 8 and the pivot pin 7 function as a mechanism for changing the force ratio. The straight line X is a perpendicular line to the guideway 8 passing through the lever rotation shaft 10.

In the case of this conventional example, the change in the force ratio is greatest when the pivot pin 7 comes on a straight line X located closer to the end of movement than the start end of movement of the pivot pin 7 in the middle of the stroke. Before and after that, since the wire feed direction and the major axis direction of the guide path 8 are parallel, the arm length of the moment is constant,
The force ratio gradually decreases and the wire feed ratio increases (see g2 in FIGS. 6 and 7). Looking at the change of the force ratio in this example, if the stroke of the lever rotation operation range is divided into three equal parts, the first half, the middle part, and the second half, the force ratio of the middle part is larger than that of the processes on both sides. Further, the peak of the force ratio is located on the moving end side. The peak of the force ratio is set after the middle point of the lever rotation operation range, that is, during the braking stroke.

However, in the case of this example, in actual use, there is a drawback that the wire tension is not proportional to the input, and the braking force is reduced as the force is applied to the lever, due to the mechanical frictional resistance and the like. This tendency was remarkable especially when the wire adjustment was insufficient.

[0011]

As described above, when braking, the power ratio is almost constant, and if the output is directly proportional to the input, the braking control is good and the handling is easy. It is desirable that the feed amount is large. Further, it is desirable that a sufficient braking force can be secured by a small lever rotation operation input.

However, these are mutually contradictory characteristics, and it has been difficult to satisfy all of them. In the general brake operating device shown in FIG. 18, when the wire pulling amount required by the brake body is secured, the initial width b is too large, and the initial width b is limited in terms of ease of gripping. The ratio could not be too large. Further, in the last stage of the lever operation, the force ratio becomes unnecessarily large, so that not only the stability at the time of braking is lacking, but also there are various problems such as the lever 1 easily coming into contact with the bar 5.

In the case of the prior art shown in FIG. 19, in the latter half of the operation of the lever 9, the force ratio is not linear, but decreases in an acceleration manner. There was a problem that P did not increase so much, braking was difficult to operate, and braking controllability was poor.

SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned conventional drawbacks and to realize a bicycle brake operating device which can be operated effectively with a small lever rotation operation input and has good operability while securing a sufficient wire pulling amount. Is to do.

[0015]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a bracket mounted on a handlebar,
A lever pivotally supported by the bracket, an inner wire for transmitting a braking force for braking the wheel, and a connection fitting for connecting one end of the inner wire and one end of the lever, are provided at one end of the lever. It was the connecting fitting causes rotatably supported in elongated holes, the connecting fitting
Move the shaft support by guiding it to the guide edge provided on the bracket.
So that the lever operating range is
During the period, a straight guide edge parallel to the inner wire direction is set.
In the latter period, the power ratio is almost constant independently of the lever operation angle range.
This is a configuration in which

[0016]

By taking the above measures, in relation to the lever operation angle of a constant stroke required as a brake,
The lever ratio is small in the first half, especially near the start of movement, the wire is pulled greatly at a small lever movement angle, braking starts faster than before, and a nearly constant force ratio and constant wire feed from the middle to the second half As a result, the output with respect to the input becomes almost linear, and a high braking controllability according to the will is obtained for the bicycle operator. Furthermore, when the grip width between the lever and the handle is the same as before, the braking force can be increased because the force ratio at the time of braking can be increased, while the grip width can be reduced if the same braking performance is used, making it easier to grip. Usability can be improved, and brakes having various characteristics can be provided.

[0017]

【Example】

(Embodiment 1) An embodiment of the present invention will be described below with reference to the drawings.

In FIG. 1, a bracket 11 has a bar 12
Are fixed with mounting brackets 13 and screws 14. The lever 15 is rotatably supported on the bracket 11 by a lever rotation shaft 16. The lever 15 and the inner wire 17 for transmitting the braking force for braking the wheel are connected via a connecting member 18, and the inner wire 17 and the connecting member 18 are connected.
Are rotatably connected by a cylindrical inner wire end 19. Reference numerals 20 and 21 denote pulleys and metal shafts that constitute the shaft support portions of the connecting metal member 18 and the lever 15. Two pulleys 20 are arranged so as to sandwich the lever 15 from the left and right, and the two pulleys 20 are always in contact with the guide edge 22 of the bracket 11. The wire feed amount c until the lever 15 comes into contact with the bar 12 is substantially equally divided as C1 ≒ C2 with respect to a perpendicular X passing through the lever rotation shaft 16 and perpendicular to the wire feed direction. The guide edge 22 is formed by a straight line portion 22a perpendicular to the perpendicular X and parallel to the inner wire direction, and a curved portion 22b to be described later. P indicates the wire tension.

FIGS. 2 and 3 are perspective views of main parts.
15a is a fitting hole of the lever rotating shaft 16, and 15b is a fitting shaft 2.
1 and a slot for guiding the rotatable ring 23.
b is provided such that the major axis is straight and parallel to the perpendicular X. The wall portion 15 having the elongated hole 15b formed therein
c is stored in the space 18a of the connection fitting 18, and the ring 23 is stored in the elongated hole 15b between the left and right walls 18b. The two pulleys 20 on the outer side of the ring 23 are rotatably connected to each other by a metal fitting shaft 21. 18c is a fitting hole of the metal shaft 21; 18d is an inner wire end 19;
Are the fitting holes. 20 'indicates the position of the pulley when the lever 15 contacts the bar 12.

The operation of the above configuration will be described.
With the operation of the lever 15, the pulley 20 is guided on the guide edge 22 and rotates around the fitting shaft 21 as a rotation center. Therefore, on the straight part 22a, the distance C3 moves linearly, and on the curved part 22b, the distance C4 moves to the position of the pulley 20 '. Here, a point (inflection point) at which the tendency of the power ratio is positively changed is defined as a first half and a second half of the lever rotation operation range. In this embodiment, C3 corresponds to the first half and C4 corresponds to the second half. The connection fitting 18 and the inner wire end 19 move in conjunction with this movement. The linear locus of the center of the pulley on the straight portion 22a is n, and the locus on the curved portion 22b is m
And The straight line n coincides with the wire feed direction, and the curve m has a curvature larger than the circumference of the radius d2.

FIG. 5 shows a distance comparison of the moving amount. Lever 1
The movement amount of the pulley 20 corresponding to the δγ angle change of 5 is represented by a straight line n.
In the above, it is δc5 in the perpendicular X portion, but becomes δc7 when the distance C2 is large, and the length relationship is δc5 <δc7. Conversely, on the curve having the radius d2, at the distance C2, similarly, the wire direction component of the movement amount of the pulley 20 corresponding to the change in the angle of the lever 15 with the small angle δγ, that is, the wire feed amount is δc
6, and δc5> δc6.

Now, the curve m is such that the distance d4 from the lever rotation shaft 16 is smaller than d2 and the radius d2 is smaller than the distance d2 so that the movement amount δc5 is the same as that of the perpendicular X portion even if the distance C2 is changed. Is designed to have a curvature greater than the distance d5 of
In the latter stage C4, the wire feed amount and the force ratio are almost constant. In general, since the wire feed amount c and the wire tension P are inversely proportional, in the first half C3 in which the pulley 20 moves linearly, the initial force ratio is minimum and sequentially increases substantially in a sinusoidal curve (the first half of the curve g3 in FIG. 6). Conversely, the wire feed ratio decreases sequentially at the maximum (FIG. 7, the first half of the curve g3).

In this embodiment, as shown in FIG. 6, the differential coefficient of the power ratio as a function of the lever operation angle is expressed by
3 and the second half C4, the first straight line portion 22a and the second half curved portion 2 of the leading edge so as to smoothly change so as to be continuous.
2b are formed smoothly and continuously.

Next, the points of design will be described. Near the start of the movement of the operating lever, the distance (referred to as distance d) from the lever rotation axis to the bracket axis connecting the connecting bracket and the lever is larger than the vicinity of the perpendicular X, thereby increasing the wire feed ratio. From the part to the latter half, the distance d is adjusted by varying the lever angle so that the wire feed ratio at the end of movement is almost the same as that of the middle part.

That is, the lever is attached to the bracket via the lever rotating shaft, the wire end is fitted to the connecting fitting, and the distance d of the fitting shaft connecting the connecting fitting and the lever from the lever rotating shaft is made variable, At the start of the operation lever movement, the bracket shaft is brought into linear contact with the bracket shaft in the wire direction to secure a large d. In addition, the angle γ between the wire and the distance d is set to be larger than 90 °, and when d becomes smaller after the middle of the operation range, γ is set to be around 90 °. The shape of the contact curve between the bracket and the bracket shaft after the middle portion is designed so that the value of the force ratio between the general brake device and the conventional device (Japanese Utility Model Application Laid-Open No. 53-66756) is kept almost constant ( (See FIG. 6, g3). Further, the force ratio changing portion C3 is set to 40% for the wire movement amount c.

In the present embodiment, the shaft of the connecting member is formed separately from the bracket shaft 21, the pulley 20, and the ring 23. However, the effect is not changed even if the connecting member is formed as an integral connecting member shaft supporting portion and slid. . Further, the guiding edge is not limited to the side shape but may be a groove shape.

The first half C3 and the second half C4 are represented by C1, C2
May be the same as In this case, the moment length is constant in the first half and decreases in the second half. In this case, it is necessary to separately design the ratio between C1 and C2 according to the brake characteristics.

In the vicinity of the perpendicular X, the force ratio is substantially constant with respect to the rotation of the lever 15, and even if the pulley 20 does not contact the guide edge 22, the pulley 20 rotates while contacting the slot 15b first. Is also good.

Further, even if the shape of the guide edge is designed so that the force ratio is theoretically substantially constant as in the present embodiment, the shape may not be constant due to the influence of friction or the like. It is also included in the present invention to design. Of course, it goes without saying that the design includes a shape in which the force ratio is almost constant in theory.

(Embodiment 2) A second embodiment of the present invention will be described with reference to FIGS.

In this embodiment, a part of the brake operating device of the first embodiment is improved. Therefore, only the differences between the first embodiment and the first embodiment will be described.

In FIG. 8, the inner wire 17 is
Cylindrical inner wire end 19 and wire end holder 2
It is linearly connected to lever 15 via 4.

In FIG. 9, the inner wire end 19 is fitted into the wire end holder 24 and the wire end holder 2
4 to be rotatable. The wire end holder 24 is housed in the long hole 15b of the lever 15, and can slide freely in the long hole 15b. As described above, in this embodiment, the inner wire end 19 and the lever 15 are directly supported via the elongated hole 15b instead of the connection fitting. The long hole 15b is provided in parallel to the perpendicular X as in the first embodiment.

The guide edge 22 provided on the bracket 11
Are parallel to the direction of the inner wire 17 from the lever movement start position to the perpendicular X, and are not provided thereafter.

The operation of the above configuration will be described. With the operation of the lever 15, the wire end 19 moves inward in the elongated hole 15b up to the perpendicular X while being guided by the guiding edge 22. This process corresponds to the first half of the lever operation range. At this time, since the inner wire end 19 moves in the direction of the inner wire 17, the amount of wire pulling is large as in the first embodiment, so that the braking can be started with a slight lever operation.

When the inner wire end 19 passes through the perpendicular X, it is released from the guide of the guiding edge 22. At this time, the wire end 19 is located inside the long hole 15b, that is, on the side of the lever rotation shaft 16, and the wire end 19 rotates and moves with the radius d2 with the subsequent lever operation. This process corresponds to the latter period. At this time, the force ratio increases in a substantially cosine curve shape, but since the inflection point of the force ratio is at the position of the perpendicular X,
As shown by the curve g4 in FIG. 10, the increase is gradual at the beginning from the inflection point, and the force ratio is almost constant particularly in the vicinity of the perpendicular X.

That is, as described above, when the lever rotation operation range is divided into three equal parts of the first half, the middle and the second half, the curve g4 in FIG.
As described above, since the substantially sine curve and the substantially cosine curve are smoothly continuous at the inflection point, the force ratio is substantially constant.

As described above, according to the second embodiment, no connecting fitting is required, and the guide edge may be provided only with a straight portion.
It also has the advantages of simple structure and inexpensive manufacturing.

(Embodiment 3) A third embodiment of the present invention will be described with reference to the drawings.

In FIG. 11, the bracket 31 is fixed to the handlebar 32 with a fixing bracket 33, a mounting bracket housed inside the bracket 31, and screws (not shown). The lever 34 is rotatably supported on the bracket 31 by a lever rotation shaft 35. An inner wire 36 for transmitting a braking force for braking the wheel is connected to the lever 34 via a connection fitting 37. Inner wire 3
6 and the connecting fitting 37 are rotatably connected by a cylindrical inner wire end 38 provided at one end of the inner wire 36, and the lever 34 and the connecting fitting 37 are rotatably connected by a fitting shaft 39. An outer wire 40 covers and protects the inner wire.
The end of the “0” is accommodated in the metal fitting 41, and the end of the metal fitting 41 is fitted in the locking hole 31 a provided in the bracket 31.

In FIG. 11, reference numeral 39 denotes a bracket shaft, and reference numeral 42 denotes a pulley. The bracket shaft 39 and the pulley 42 constitute a shaft supporting portion of the connecting bracket. Two pulleys 42 are arranged so as to sandwich the lever 34 from the left and right, and are in contact with the guide edge 43 of the bracket 31. In the present embodiment, the guide edge 43 is provided on the opposite side of the handlebar 32, that is, on the outside, in contrast to the case of the first embodiment. The wire feed amount C until the lever 34 comes into contact with the handle bar 32 is approximately 2 for C1 and C2 with respect to a perpendicular X passing through the lever rotation axis 35 and perpendicular to the wire feed direction.
It is divided into 1. The leading edge 43 is the inner wire 3
It is parallel to the six directions and extends to near the perpendicular X. In the initial state where no force is applied to the lever 34, the distance d3 between the lever rotation shaft 35 and the bracket shaft 39 is shorter than d1, and the distance between the straight line in the direction of the inner wire 36 and the lever rotation shaft 35 is determined by the long hole 34b and the lever rotation. The distance d2 is set equal to the short distance between the shafts 35. Reference numeral 42 'indicates the position of the pulley when the lever 34 contacts the handlebar 32.

FIG. 12 is an exploded perspective view of the lever 34.
34a is a fitting hole of the lever rotating shaft 35, and 34b is a fitting shaft 3.
9 and a slot for guiding the rotatable ring 44.
“b” is provided such that the long diameter portion comes on a line connecting the lever rotation shaft 35 and the bracket shaft 39. The wall portion 34c in which the elongated hole 34b is formed is housed in the internal space of the connecting member 37, and the ring 44 is housed in the internal space of the connecting member 37 and the elongated hole 34b. The two pulleys 42 on the outer side of the wheel 44 are rotatably connected to each other by a fitting shaft 39 together with the two pulleys 42. The center distance between the fitting hole 34a and the long hole 34b is d2 at the short part and d at the long part.
It is one.

The operation of the above construction will now be described. With the operation of the lever 34, the pulley 4
2 is rotated and guided by the guiding edge 43. At this time, the distance between the bracket shaft 39 and the lever rotation shaft 35 is perpendicular X
Until the time point, it gradually decreases from d3 to d2. This process corresponds to the first half.

After the perpendicular X, the radius d2 is the same, that is, the bracket shaft 39 is rotated by contacting the long hole 34b near the lever rotation shaft 35. This corresponds to the latter period.

In the stroke corresponding to the wire feed ratio C1, that is, in the first half, the pulley 42 moves while abutting on the guide edge 43. In short, the metal shaft 39 is the inner wire 3
During the movement in parallel with the six directions, the curve g5 in FIG.
The force ratio rises substantially sinusoidally, as in the 2/3 part before. The moment length is constant during that time.

Next, in the stroke corresponding to C2, that is, in the latter period, the pulley 42 separates from the guiding edge 43, the fitting shaft 39 is rotated about the lever rotation shaft 35, and the power ratio is 1 after the curve g5 in FIG. Although it rises in a substantially cosine function like the portion of / 3, since the rotation starts from a position perpendicular to the direction of the inner wire 36, the length of the moment with the lever rotation shaft 35 at the end of the stroke is smaller than d2 in FIG.
Since only e shown in FIG. 1 decreases, the force ratio is almost constant.

Similarly, the change in the power ratio is very small near the inflection point as shown by the curve g5 in FIG. 10, and the power ratio is almost constant in the intermediate portion and the rear half portion corresponding to the actual braking portion. Become.

In the present embodiment, the guide edge 43 extends up to the perpendicular X. However, similar to the first embodiment, the same effect can be obtained by expanding the perpendicular edge X and thereafter with a curvature.

Further, as shown in FIG. 13, the guiding edge 43 may be provided by using the mating surface 31c formed when the bracket is formed by press-molding a sheet metal. By doing so, the appearance is further refined, and the strength of the bracket 31 itself is also improved. In this case, the guide edge 43 and the pulley 42 are provided only on one side, but the operation and effect are the same as those of the above-described embodiment.

In this embodiment, the wire feed amount C is set to C
1: C2 = 2: 1, but this division ratio can be changed appropriately according to the purpose of the brake operating device.

(Embodiment 4) A fourth embodiment of the present invention will be described with reference to the drawings.

In this embodiment, instead of the combination of the guiding edge and the pulley, both sides of the bracket 51 sandwiching the groove 51c are pressed as shown in FIG. 15, and the inner surface of the pressed portion is guided to the connecting metal 37. Used as 52. Other configurations such as the shape of the long hole are the same as those of the third embodiment.

The operation of this embodiment with the above configuration will be described. In FIG. 14, when the lever 34 is operated and rotated, the upper surface of the connecting member 37 is initially restricted by the guide surface 52, so that the connecting member 37 moves parallel to the direction of the inner wire 36, and at the same time, the inside of the elongated hole 34b. The metal shaft 39 gradually moves to the lever rotation shaft 35 side. At this time, the length of the moment is constant. Then, as the operation rotation of the lever 34 advances, the contact surface between the guide surface 52 and the upper surface of the connection fitting 37 decreases,
When the fitting shaft 39 is on the perpendicular X, the connecting fitting 37 is released from the regulation of the guide surface 52. And at this time, the bracket shaft 3
Reference numeral 9 denotes a position near the lever rotation shaft 35 in the elongated hole 34b. The steps so far correspond to the previous term.

Further, when the lever 34 is rotated, the metal shaft 39 rotates around the lever rotation shaft 35 while maintaining the radius d2. At this time, the moment length continues to decrease. This process corresponds to the latter period. The force ratio at this time is exactly the same as that of the third embodiment, and changes as shown by a curve g5 in FIG. 10, and the operation and effect are almost the same.

Also in the present embodiment, no special parts such as pulleys and guide edges are required, and the guide surfaces need only be formed by press working. It has the advantage that it can respond.

(Embodiment 5) A fifth embodiment of the present invention will be described with reference to the drawings.

FIG. 16 is a side view of the brake operating device in a state where a resin cover covering a main part is removed. Note that the same components as those in the above-described embodiment are given the same reference numerals, and description thereof will be omitted.

The lever 61 is rotatably supported on a bracket 62 by a lever rotation shaft 35. The inner wire 36 that transmits the braking force for braking the lever 61 and the wheel
Is rotatably connected via a connection fitting 37. Reference numerals 42 and 39 denote a wheel and a metal shaft, respectively, which form a shaft supporting portion for rotatably supporting the connecting metal member 37 and the lever 61. The wheel 42 rotates in the long hole 61b of the lever. Slot 6
1b has a shape in which the major diameter portion draws a curve. Long hole 61
The detailed shape of b will be described later. The wire feed amount C until the lever 61 comes into contact with the bar 32 is divided at a ratio of C1 ≒ 2C2 with respect to a perpendicular X passing through the shaft 35 and perpendicular to the tension direction of the inner wire 36 as in the third embodiment. F
Indicates lever input, and P indicates inner wire tension. d1
Is the initial axial distance between the lever rotation shaft 35 and the bracket shaft 42,
d2 indicates the length of the moment of the inner wire tension P with respect to the axis 35.

FIG. 17 shows a long hole 61b, a ring 42, and a bracket shaft 39.
It is a conceptual diagram which shows the relationship of. 61a is a lever rotation shaft 35
And the axis Y is a line connecting the fitting hole 61a and the center of the long hole 61b on the fitting hole 61a side, and forms an angle between the perpendicular X and α when the lever is not operated. Z is a tangent line of the long hole 61b extending from the contact point of the ring 42. The long hole 61b has a curvature of a long diameter portion such that the inner wire tension line W and the tangent line Z are always vertical until the metal shaft 39 reaches the perpendicular X regardless of the lever operation angle. Length is d
The shape is set to be constant at 2.

The operation of the above configuration will be described. When the lever is not operated, the angle between the perpendicular X and the axis Y is α, but gradually decreases with the operation of the lever 61. At this time, the angle β between the tangent line Z and the axis line Y also gradually decreases.
Rotates toward the lever rotation shaft 35 and is always positioned on the inner wire tension line W. When the ring 42 comes on the perpendicular line X, the ring 42 is located on the side of the lever rotation shaft 35 of the long hole 61b. The steps so far correspond to the previous term. The distance between the bracket shaft 39 and the lever rotation shaft 35 is:
It decreases from the initial d1 to d2. Therefore, in the first half, the wire feed amount rapidly decreases, and the power ratio increases (the first half of the curve g5 in FIG. 10). In the vicinity of the vertical line X, a power curve is drawn with a substantially sinusoidal curve that hardly changes.

After the perpendicular X, the ring 42 rotates while drawing an arc having a radius d2 in a state where the ring 42 is in contact with the long hole 61b on the lever rotating shaft 35 side. This process corresponds to the latter period. Therefore, in the latter period, the power ratio rises in a substantially cosine curve (the latter half of the curve g5 in FIG. 10), but the latter half is 1/3 of the entire stroke, and the perpendicular X is the power ratio. Since it is an inflection point, there is almost no change in the force ratio, and the change is small even at the end of the stroke. Therefore, at the time of actual braking, the operability is good because the output is substantially proportional to the input F.

In the present embodiment, the first half and the middle part where the bracket shaft slides toward the lever rotation shaft 35 while the ring 42 rotates in the long hole 61b, and the second half that rotates. The inflection points of the force ratios are made to coincide with each other, and the derivative is continuous (see curve g5 in FIG. 10).

In the present embodiment, the long hole 61b is formed by a curved line protruding toward the inner wire 36, so that the movement of the ring 42 is smooth. In the initial stage, the distance d between the shafts is initially set due to the vector component relationship between the inner wire tension P of the ring 42 and the axis Y.
At 1, there is no change in the movement to become d2 after the perpendicular X. However, the change in the power ratio does not become a sinusoidal curve due to the rotational resistance of the wheels and the vector component action in the first half and the middle part, and the power ratio rapidly increases near the vertical line X. Different from the embodiment.

In each of the embodiments, the substantially sine curve and the substantially cosine curve do not mean that an accurate sine curve and a cosine curve are drawn, but that the change tendency is a sine curve and a cosine curve.

Further, as another embodiment, it is also possible to adopt a configuration in which the wheel slides in the elongated hole even after the perpendicular X to change the force ratio.

[0066]

In general, in the case of operating the brake lever, the first half, which corresponds to the first half of the total operating angle, is the idle movement distance until the brake starts to work and the initial contact.
An intermediate portion corresponding to / 3 is a contact and braking effect exerting portion. The latter half, which is one third of the latter half, is not normally used, but is a full braking or an emergency response part close thereto.

According to the present invention, in the first half which does not contribute to braking, the lever operation angle is small but the wire pulling amount is large, and the force ratio from the middle to the second half is constant or increases substantially in a cosine function. Since the increase is gradual and the output is almost proportional to the input, the braking control faithfully responds to the operator's will and the controllability is good. Further, since the distribution of the wire feed amount can be arranged more in the first half, the force ratio of the middle portion can be set higher than that of a general lever, so that the effect is improved and a highly usable bicycle brake operating device can be provided.

Further, since the power ratio change curve has a shape in which the first half and the second half are smoothly continuous, the change in the power ratio during braking is also smooth, and the braking controllability is higher and the safety is higher.

[Brief description of the drawings]

FIG. 1 is a side view showing a bicycle brake operating device according to a first embodiment of the present invention.

FIG. 2 is an exploded perspective view of main parts of the brake operating device.

FIG. 3 is a perspective view of a connecting bracket of the brake operating device.

FIG. 4 is a side view of a main part of the brake operating device.

FIG. 5 is a conceptual diagram comparing a moving amount with respect to a change in lever angle in the conventional example and the structure of the present invention.

FIG. 6 is a comparative diagram showing a relationship between a lever operation angle and a force ratio in a conventional example and the present invention.

FIG. 7 is a comparative diagram showing a relationship between a lever operation angle and a wire feed ratio in a conventional example and the present invention.

FIG. 8 is a side view showing a bicycle brake operating device according to a second embodiment of the present invention.

FIG. 9 is a perspective view of a main part of the brake operating device.

FIG. 10 is a comparative diagram showing a relationship between a lever operation angle and a force ratio in the present invention.

FIG. 11 is a side view showing a bicycle brake operating device according to a third embodiment of the present invention.

FIG. 12 is an exploded perspective view of main parts of the brake operating device.

FIG. 13 is a perspective view showing another embodiment of the brake operating device.

FIG. 14 is a side view showing a bicycle brake operating device according to a fourth embodiment of the present invention.

FIG. 15 is a perspective view of the brake operating device.

FIG. 16 is a side view showing a bicycle brake operating device according to a fifth embodiment of the present invention.

FIG. 17 is an exploded perspective view of main parts of the brake operating device.

FIG. 18 is a side view showing a conventional brake operation device.

FIG. 19 is a side view showing another example of the conventional brake operating device.

[Explanation of symbols]

 11, 31, 51 Bracket 12, 32 Handlebar 15, 34, 61 Lever 16, 35 Lever rotation shaft 17, 36 Inner wire 18, 37 Connection fitting 20, 42 Pulley 21, 39 Fitting shaft 22, 43 Guide edge 15b, 34b , 61b slot 52 guide surface

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-3-14782 (JP, A) JP-A-3-292280 (JP, A) JP-A-6-127454 (JP, A) 9693 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) B62L 3/02

Claims (7)

(57) [Claims] 1. A bracket mounted on a handlebar, a lever pivotally supported by the bracket, an inner wire for transmitting a braking force for braking a wheel, and one end of the inner wire and one end of the lever. A guide rim provided with a connection fitting for coupling , wherein the connection fitting is rotatably supported in an elongated hole provided at one end of the lever, and a shaft support portion of the connection fitting is provided on the bracket.
To be guided and moved, and
In the previous period, the rotation operation range was flat with the inner wire direction.
Linear guide edge, and in the latter stage, the lever operation angle range
That the power ratio is almost constant independently of the enclosure.
Characteristic bicycle brake operating device. 2. A bracket mounted on a handlebar, a lever pivotally supported by the bracket, an inner wire for transmitting a braking force for braking a wheel, and one end of the inner wire and one end of the lever. A connecting metal fitting for connecting, the connecting metal fitting is rotatably supported in an elongated hole provided at one end of the lever, and a shaft supporting part of the connecting metal fitting is formed on a guide edge provided on a bracket.
And the rotation of the lever
For the operating range, the first half was parallel to the inner wire direction.
A straight guide edge is provided, and the power ratio increases in a substantially cosine curve in the latter period.
Bicycle brake characterized by being configured to increase
Key operation device. Wherein the bracket is induced edge curved shape corresponding to the later stage of the rotational operation range of the lever, the Le <br/> independently of the bar operation angular displacement, substantially constant or substantially cosine curve force ratio Claim 1 or Claim 2 having a gradually increasing curvature.
Is a bicycle brake operating device according to 2. Wherein said inductive edge, said formed only year of the rotational operation range of the lever, Late to rotate about the lever rotation shaft fitted to a bracket shaft support of the connecting bracket away from the induction end 3. The bicycle brake operating device according to claim 2, wherein: 5. A bracket mounted on a handlebar.
And the lever and the wheel supported by this bracket
An inner wire that transmits the braking force for braking and this inner wire
Connect one end of the inner wire to one end of the lever
A connecting metal fitting, and a length provided at one end of the lever.
The connecting fitting together is rotatably supported in the hole, year of the rotational operation range of the lever is configured to move while being guided by guide surface provided with the connecting fitting to the inner surface of the <br/> bracket and the guide surface is formed in a plane parallel to the said inner wire direction to the rotational operation range of the lever, late of the rotational operation range of the lever is the connecting fitting leaves the guide surface, the shaft support of the connecting fitting There axis self <br/> rolling wheel brake operating device that is configured to rotate about the said lever being fitted to the bracket. 6. A bracket attached to a handlebar, a lever pivotally supported by the bracket, an inner wire for transmitting a braking force for braking a wheel, and one end of the inner wire and one end of the lever. becomes more and connecting fitting for connecting the coupling fitting to the long hole provided at one end with is rotatably supported in the lever, the shape of the long hole, the rotating operation of the lever shaft support of the connecting fitting range to, previous period parallel to the inner wire direction, late shape as the bicycles <br/> wheel brake operating device such as the traction for rotation about a lever shaft fitted to the bracket. And 7. One end and the lever of the inner wire in place of the connecting fitting, serial claim 1 which has been directly axially supported through a long hole provided at one end of the lever to either the 4 or 6 <br / > Brake operation device for bicycle.