JPH11105770A - Brake device for bar handle vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide preferable braking force for the body condition, performance, and intended purpose of a bar handle vehicle in each of both brakes by increasing or decreasing a total of output load much more than the input load of a brake operating element while distributing the input load of the brake operating element as the output load to the respective brakes at the time of interlocking the hydraulic pressure type brake with a mechanical brake. SOLUTION: This device is provided with a master cylinder unit 7 constituted of a hydraulic pressure master cylinder 40, an operating force conversion means 60, and an output distribution means 70. The first rotating lever 62 and a knocker 63 are formed at the operating force conversion means 60. The piston pressing part 63a of the knocker 63 is brought into contact with the outer end of a piston. The second rotating lever 71 and an equalizer lever 72 are formed at the output distribution means 70. The intermediate part of the second rotating lever 71 is pivoted by a fixed support 73, and one end of the equalizer lever 72 is pivoted on its one end with a floating support point 74, and the other end 71b is brought into contact with the piston pressing part 63a.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a brake device applicable to various kinds of bar handle vehicles such as motorcycles, three-wheeled vehicles, and three- and four-wheeled buggy vehicles. In the operation of one brake operator, either one of the front wheel brake and the rear wheel brake operates independently, and in the operation of the other brake operator, both the front wheel brake and the rear wheel brake operate in conjunction. The present invention relates to a bar handle vehicle brake device having an operating structure.

[0002]

2. Description of the Related Art A brake device that operates in conjunction with a front wheel brake and a rear wheel brake of a bar handle vehicle is disclosed in, for example, Japanese Patent Application Laid-Open No. 5-16862. This technology adopts a mechanical brake that is activated by the pulling of the driven side linking means for each of the front wheel brake and the rear wheel brake, and a pair of brake levers are pivotally supported on both ends of the handlebar with support shafts. An output distributing means is disposed near a support shaft of one of the brake operating elements, and the output distributing means is connected to the pair of driven-side linking means, and an output across the support axis of the one brake operating element is provided. On the side opposite to the distributing means, the traction side linking means connected to the other brake operator is connected, and both the front wheel brake and the rear wheel brake operate in conjunction with either one or the other brake operator. I can do it.

The above-mentioned output distribution means is a plate-shaped equalizer lever rotatably supported at a floating fulcrum near a support shaft of one of the brake operating members, and is provided on both sides of the output distribution means with the floating fulcrum interposed therebetween. The connecting means for the front wheel brake and the connecting means for the rear wheel brake are connected to each other, and the front wheel brake and the rear wheel brake are connected by changing the length from the floating fulcrum to the connecting point of both brake connecting means. So that the output load can be varied.

[0004]

However, in the above-mentioned interlocking type brake device, the input load from the brake operator is simply distributed as output load to the front wheel brake and the rear wheel brake by the output distribution means. Since the output load to both brakes cannot be increased or decreased more than the input load, it was not possible to set the braking force for the front wheel brakes and the rear wheel brakes according to the vehicle conditions, performance and intended use .

Therefore, the present invention can increase or decrease the output load to the front wheel brake and the rear wheel brake when interlocking the front wheel brake and the rear wheel brake with respect to the input load of the brake operator. As a result, it is an object of the present invention to provide a brake device for a bar handle vehicle that can set a suitable braking force for each of a front wheel brake and a rear wheel brake in accordance with vehicle conditions, performance, and intended use.

[0006]

According to the above object, according to the first aspect of the present invention, one of the front wheel brake and the rear wheel brake of a bar handle vehicle is connected to a single system brake by operating a first brake operating member. A hydraulic brake which is operated by hydraulic pressure generated in the hydraulic master cylinder by pulling the means, and a mechanical brake which is operated by pulling the linkage means for the interlocking brake by operating the second brake operating element. In addition, an operating force converting means for converting the input load of the first brake operator into a hydraulic pressure of the hydraulic master cylinder, and an input load of the second brake operator are applied to the hydraulic master cylinder. By combining output distribution means for distributing the hydraulic pressure of the master cylinder and the operating force of the mechanical brake, these hydraulic master cylinders, operating force conversion means and output distribution means are used. The first brake operating member is connected to the operating force converting means by a linking means for a single system brake, and the operating force converting means is rotated about a support shaft by operating the first brake operating element. A first rotating lever;
By the pushing of the first rotating lever, the hydraulic master cylinder is rotated in the direction of the cylinder hole opening with the support shaft as a fulcrum, and the piston of the hydraulic master cylinder is moved into the cylinder hole by the piston pushing portion. Is provided, and the interlocking brake linking means is divided into a traction side linking means connected to the second brake operator and a driven side linking means linked to the mechanical brake, The output distributing means is interposed between the traction side connecting means and the driven side connecting means, and the intermediate part is pivotally supported at a fixed fulcrum by the output distributing means, and the piston of the hydraulic master cylinder is connected to the knocker. A second pivoting lever that is pushed through the second pivoting lever, and one end of the second pivoting lever,
One of the middle part and one end is pivoted at the floating fulcrum,
An equalizer lever supported so as to be swingable, connecting the traction-side linking means and the driven-side linking means of the interlocking brake linking means to the equalizer lever, and connecting the other end of the second pivot lever , Disposed on the non-operating side of the knocker.

According to the second aspect of the present invention, one of the front wheel brake and the rear wheel brake of the bar handle vehicle is pulled by the independent brake connecting means by the operation of the first brake operating member, and is moved to the hydraulic master cylinder. A hydraulic brake that operates with the generated hydraulic pressure, and a mechanical brake that operates by pulling the interlocking means for the interlocking brake by operating the second brake operator, and the hydraulic master cylinder includes: Operating force converting means for converting the input load of the first brake operator to the hydraulic pressure of the hydraulic master cylinder; and the input load of the second brake operator for converting the input load of the hydraulic master cylinder to the hydraulic pressure of the hydraulic master cylinder. Combining the output distribution means for distributing to the operating force and the hydraulic pressure master cylinder, the operating force conversion means and the output distribution means to constitute a master cylinder unit, Power conversion means, first rotates the first connected by the brake operation element and sole system brake cooperative means, fulcrum shaft by the operation of the first brake operation element 1
A pivoting lever, a piston pushing portion for pushing the piston of the hydraulic master cylinder into the cylinder bore is provided on the first pivoting lever, and the interlocking brake linking means is connected to the second brake operation. A traction-side connecting means connected to the child,
Divided into driven-side connecting means connected to the mechanical brake, the output distribution means is interposed between the traction-side connecting means and the driven-side connecting means, and an intermediate portion is fixed to the output distributing means. A second pivoting lever pivotally supported at a fulcrum and pushing the piston of the hydraulic master cylinder; and one end of the second pivoting lever pivotally supported at one of an intermediate portion and one end at a floating fulcrum. And an equalizer lever that is swingably supported. The equalizer lever is connected to the traction-side linking means and the driven-side linking means of the interlocking brake linking means, and the second rotating lever is The other end, together with the piston pushing portion of the first rotary lever, is disposed so as to face the piston of the hydraulic master cylinder in parallel.

According to a third aspect of the present invention, when the second rotary lever of the first or second aspect of the present invention rotates in the direction of pushing the piston, a stopper for restricting the rotation of the second rotary lever is provided. Provide.

According to a fourth aspect of the present invention, one of the front wheel brake and the rear wheel brake of the bar handle vehicle is pulled by the independent brake connecting means by the operation of the first brake operating member, and is moved to the hydraulic master cylinder. A hydraulic brake that operates with the generated hydraulic pressure, and a mechanical brake that operates by pulling the interlocking means for the interlocking brake by operating the second brake operator, and the hydraulic master cylinder includes: Operating force converting means for converting the input load of the first brake operator to the hydraulic pressure of the hydraulic master cylinder; and the input load of the second brake operator for converting the input load of the hydraulic master cylinder to the hydraulic pressure of the hydraulic master cylinder. Combining the output distribution means for distributing to the operating force and the hydraulic pressure master cylinder, the operating force conversion means and the output distribution means to constitute a master cylinder unit, The power conversion means, first rotates the first connected by the brake operation element and sole system brake cooperative means, fulcrum shaft by the operation of the first brake operation element 1
When the pivoting lever and the first pivoting lever are pushed, the pivoting lever pivots toward the cylinder hole opening of the hydraulic master cylinder about a fulcrum, and the piston of the hydraulic master cylinder is pushed by a piston pushing portion. A knocker that pushes into the cylinder hole at the same time, the linking means for the interlocking brake is connected to a traction-side linking means connected to the second brake operator, and a driven-side linking means connected to the mechanical brake. And the output distributing means is interposed between the traction-side connecting means and the driven-side connecting means, and the output distributing means is provided with a second rotating lever pivotally supported at an intermediate portion at a fixed fulcrum. One end of the second rotary lever is pivotally supported at one of the intermediate portion and one end at a floating fulcrum, and pushes the piston of the hydraulic master cylinder through the knocker. And a moving equalizer lever. The lever is connected to the traction side connecting means of the interlocking brake connecting means, and the other end of the equalizer lever is disposed on the non-operating side surface of the knocker. The driven side connecting means of the interlocking brake connecting means is connected.

According to the fifth aspect of the present invention, one of the front wheel brake and the rear wheel brake of the bar handle vehicle is pulled by the independent brake connecting means by the operation of the first brake operating member, and is moved to the hydraulic master cylinder. A hydraulic brake that operates with the generated hydraulic pressure, and a mechanical brake that operates by pulling the interlocking means for the interlocking brake by operating the second brake operator, and the hydraulic master cylinder includes: Operating force converting means for converting the input load of the first brake operator to the hydraulic pressure of the hydraulic master cylinder; and the input load of the second brake operator for converting the input load of the hydraulic master cylinder to the hydraulic pressure of the hydraulic master cylinder. Combining the output distribution means for distributing to the operating force and the hydraulic pressure master cylinder, the operating force conversion means and the output distribution means to constitute a master cylinder unit, Power conversion means, first rotates the first connected by the brake operation element and sole system brake cooperative means, fulcrum shaft by the operation of the first brake operation element 1
A pivoting lever, a piston pushing portion for pushing the piston of the hydraulic master cylinder into the cylinder bore is provided on the first pivoting lever, and the interlocking brake linking means is connected to the second brake operation. A traction-side connecting means connected to the child,
Divided into driven-side connecting means connected to the mechanical brake, the output distribution means is interposed between the traction-side connecting means and the driven-side connecting means, and an intermediate portion is fixed to the output distributing means. A second pivot lever pivotally supported at a fulcrum;
An equalizer lever is provided at one end of the rotating lever, which is pivotally supported at one of the intermediate portion and one end at a floating fulcrum and is swingably supported, and pushes a piston of the hydraulic master cylinder. A lever connected to a traction side connecting means of the interlocking brake linking means, and the other end of the second rotary lever connected to a driven side linking means of the interlocking brake linking means; Of the hydraulic master cylinder together with the piston pushing portion of the first rotary lever are arranged in parallel with the piston of the hydraulic master cylinder.

According to a sixth aspect of the present invention, a stopper is provided for regulating the rotation of the equalizer lever when the equalizer lever of the fourth or fifth aspect of the invention rotates in the piston pushing direction.

According to the invention of claim 7, in claim 1 to claim 6,
The first brake operator and the second brake operator according to any one of the inventions are brake levers attached to a handlebar, and the master cylinder unit is disposed between the handlebar and the front wheels.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to a scooter type motorcycle will be described below with reference to the drawings. 1 to 8 show a first embodiment of the present invention, FIG. 1 is a schematic diagram of a brake device in a non-operating state, and FIG. 2 is a front view of a scooter type motorcycle equipped with the brake device of FIG. FIG. 3 is a partially sectional front view showing a non-operating state of the master cylinder unit used in the brake device, FIG. 4 is a sectional view taken along line IV-IV of FIG. 3, and FIG. 5 is a sectional view taken along line VV of FIG. 6 is a partial sectional front view of the master cylinder unit when only the independent brake system is operated, FIG. 7 is a partial sectional front view of the master cylinder unit when only the interlocked brake system is operated,
FIG. 8 is a partial sectional front view of the master cylinder unit when both the independent brake system and the interlocking brake system are operated.

FIGS. 9 to 24 show the second to fourth embodiments of the present invention.
Embodiments are shown. In these second to fourth embodiments, FIGS. 1 and 2 of the first embodiment are appropriately referred to for the description of the overall structure, and the same reference numerals are used for the structures common to each embodiment. The detailed description is omitted.

A brake device 2 for a motorcycle 1 shown in a first embodiment shown in FIGS. 1 to 8 includes a first brake operator 4 and a second brake operator 5 attached to a handlebar 3, a front part of a vehicle body. And a master cylinder unit 7 disposed in a leg shield 6 that covers the front wheel. The front wheel brake disposed on one side of the front wheel 9 at the lower end of the front fork 8 steered by the handlebar 3 is hydraulically operated. A mechanical brake 12 is provided at the rear end of the swing arm 11 in a rear wheel (not shown) or at one side of the rear wheel.

The first brake operator 4 is a handlebar 3
The right brake lever and the second brake operator 5 disposed in front of the accelerator grip 13 attached to the right end of the
Fixed grip 14 attached to the left end of handlebar 3
The brake device 2 is a single brake system 15 that operates the hydraulic brake 10 independently by the gripping operation of the first brake operator 4.
And an interlocking brake system 16 that operates by interlocking the hydraulic brake 10 and the mechanical brake 12 by the gripping operation of the second brake operator 5.

The independent brake system 15 includes a first brake operator 4, a hydraulic brake 10, a master cylinder unit 7, an independent brake linking means 17, and a hydraulic pipe 18.
The interlocking brake system 16 includes a second brake operator 5, a hydraulic brake 10, a mechanical brake 12, a linking means 19 for an interlocking brake, and a master cylinder unit also serving as the independent brake system 15. 7 and a hydraulic line 18.

The hydraulic brake 10 includes a hydraulic disc brake in which a disc rotor 30 and a caliper body 31 are combined, and the mechanical brake 12 includes a pair of brake shoes 33,
Leading & trailing type mechanical drum brakes for expanding the opening 33 with the anchor pin 34 as a fulcrum are applied, and the connecting means 17 for the independent brake and the connecting means 19 for the interlocking brake are respectively provided with wires. Cables are used.

The master cylinder unit 7 includes a hydraulic master cylinder 40 for supplying hydraulic pressure to the hydraulic brake 10,
An operating force converting means 60 for converting an input load of the first brake operator 4 into a hydraulic pressure of the hydraulic master cylinder 40, and an input force of the second brake operator 5 for converting the input load of the hydraulic master cylinder 40
And an output distributing means 70 for distributing the hydraulic pressure and the operating force of the mechanical brake 12.

The first brake operator 4 is connected to the operating force converting means 60 by the independent brake connecting means 17, and the hydraulic brake 10 and the hydraulic master cylinder 40 are connected by the hydraulic piping 18. I have. The interlocking brake linking means 19 is divided into a traction-side linking means 20 connected to the second brake operator 5 and a driven-side linking means 21 connected to the mechanical brake 12. An output distribution unit 70 is interposed between the power supply unit and the driven side connection unit 21.

In the hydraulic master cylinder 40, an output port 42 and a cylinder hole 43 are connected to a vertical cylindrical cylinder body 41. The hydraulic port 18 is connected to the lower output port 42. The liquid communication pipe 4 connected to a separate reservoir 44 is connected to the boss 41a communicating with the cylinder hole 43 of
5 is connected.

A piston 46 is liquid-tightly and movably inserted into the cylinder hole 43, and the piston 46 and the output port 42
A hydraulic chamber 47 is defined between the hydraulic chamber 47 and the bottom. Hydraulic chamber 4
7, a first return spring 48 is contracted, and the piston 4
6, the cylinder hole 43 is urged toward the upper opening by the resilience of the first return spring 48, and the retraction is limited to the contact with the retaining ring 49 engaged with the opening of the cylinder hole 43. It is regulated by.

A pair of lever holders 41b, 41b is provided on one side of the cylinder body 41, and a mounting bracket 41c is provided on the other side of the body 41, respectively.
The above-mentioned operating force conversion means 60 is attached to the lever holders 41b, 41b, and the guide bracket 50 which extends so as to integrally cover the opening of the cylinder hole 43 and the upper part of the operating force conversion means 60 is fixed to the mounting bracket 41c. ing. The guide bracket 50 has three vehicle mounting holes 5
0a, a bifurcated first stopper 50b protruding toward the opening end of the cylinder hole 43, and a protruding second stopper 50c located on the same plane as the first stopper 50b near the mounting portion of the guide bracket 50. The master cylinder unit 7 is fixed in the leg shield 6 using the vehicle body mounting hole 50a, and the above-described output distribution means 70 is mounted at a position above the second stopper 50c.

The operating force converting means 60 includes a lever holder 41
The first turning lever 62 has a first end 17a connected to the first brake operating member 4 and a knocker 63. The other end 17b of the independent brake linking means 17 is connected, and the vicinity of the other end 17b is supported by a wire guide 50d at the tip of the guide bracket 50, and between the first rotating lever 62 and the knocker 63. The second return spring 64 is contracted.

The second return spring 64 has the first
A set load weaker than the return spring 48 is set,
The first pivoting lever 62 and the knocker 63 are repelled in directions away from each other, and the first pivoting lever 62 and the knocker 63 are urged to the inoperative position where the stoppers 62a and 63b abut on the cylinder body 41, and at the same time, The independent brake connecting means 17 is stretched without loosening, and the piston pushing portion 63a of the knocker 63 is brought into contact with the outer end of the piston 46 between the forked first stoppers 50b.

The output distributing means 70 pulls the traction side connecting means 20 of the interlocking brake connecting means 19 by the gripping operation of the second brake operating element 5, and reduces the traction force of the traction side connecting means 20 by a hydraulic pressure. The load is branched into a hydraulic pressure pipe 18 for the brake and a driven side connecting means 21 for the mechanical brake, and the input load from the second brake operator 5 is applied to the hydraulic pressure for the hydraulic brake and the traction force for the mechanical brake. The output distribution means 70 of this embodiment is a combination of a second rotary lever 71 for a hydraulic brake and an equalizer lever 72 for a mechanical brake.

Second rotating lever 71 and equalizer lever 7
2 are each formed in a strip shape, and the second rotating lever 71 is pivotally supported at an intermediate portion to a lever holder 50e of the guide bracket 50 by using a fixed fulcrum 73. One end 71a, 72 of the equalizer lever 72
a is pivotally supported at the floating fulcrum 74, and the equalizer lever 72 is swingably supported by the second rotating lever 71. At the middle portion 72c of the equalizer lever 72, the other end 20b of the traction side connecting means 20 having one end 20a connected to the second brake operator 5 is connected to the wire guide 5 of the guide bracket 50.
0f, and the other end 21b of the driven-side linking means 21 having one end 21a connected to the operating lever 35 of the mechanical brake 12 at the other end 72b of the equalizer lever 72.
b is connected through the guide bracket 50.

A third return spring 75 is stretched between the floating fulcrum 74 and the locking piece 50g of the guide bracket 50, and the second rotating lever 71 and one ends 71a, 72a of the equalizer lever 72 are moved downward from the vehicle body. And is brought into contact with the second stopper 50c. The retraction limit of the second pivoting lever 71 during non-operation is restricted by the contact between the one end 71a and the second stopper 50c, and the other end 71b is brought into contact with the non-operating side surface of the piston pushing portion 63a of the knocker 63. (Figure 1
3), a gap C is set between the other end 71b and the first stopper 50b of the guide bracket 50.

The equalizer lever 72 has one end 72a abutting on the second stopper 50c and the other end 72b abuts on the guide bracket 50 as described above, and is urged to a non-operating state (FIGS. 1 to 10). 3) The traction-side linking means 20 and the driven-side linking means 21 connected to the equalizer lever 72 are:
When the equalizer lever 72 is not operated, the first brake operating member 4 or the operating lever 3 of the mechanical brake 12 is operated.
5 are stretched without looseness.

An intermediate portion 72c of the equalizer lever 72 to which the other end 20b of the traction side linking means 20 is connected is located closer to the other end 72b than the middle point of the equalizer lever 72, and is intermediate with the other end 72b of the equalizer lever 72. Part 72c
Are located on both left and right sides of the fixed fulcrum 73. The floating fulcrum 74, which is the connection point between the second rotation lever 71 and the equalizer lever 72, rotates about the fixed fulcrum 73 when an operating force is applied to one of the levers 71, 72. Is transmitted to the other.

When the second rotating lever 71 is not operated, the other end 7
C set between the first stopper 50b and the first stopper 50b
When the interlocking brake system 16 is operated, even if the second rotating lever 71 pushes the knocker 63 in the direction of the hydraulic master cylinder 40, the reaction force from the knocker 63 acts on the second rotating lever 71. If it does not act, the first stopper 50b
Supports the other end 71b of the second rotating lever 71 and regulates the rotation of the second rotating lever 71, thereby applying a reaction force to the second rotating lever 71, and This is for operating the levers 71 and 72. When the second rotation lever 71 fills the gap C and comes into contact with the first stopper 50b, the rotation amount of the knocker 63 that pushes the piston 46 is regulated. For this reason, the gap C is set to have a length capable of supplying sufficient hydraulic fluid to the hydraulic brake 10 to normally brake the front wheel 9 by the rotation of the second rotation lever 71.

The present embodiment is configured as described above, and each component of the brake device 2 is not operated when the first and second brake operators 4 and 5 are gripped and not operated. Is located in the state shown in FIG.

First, the operation of the independent brake system 15 using the first brake operator 4 will be described with reference to FIG. 6. When the first brake operator 4 is gripped, the independent brake linking means 17 is pulled. Operating force conversion means 60
The first turning lever 62 turns in the operating direction (clockwise direction in FIG. 6) about the support shaft 61, and the first turning lever 62 comes into contact with the knocker 63.
With the second rotation lever 71 left in the non-operation position (the position shown in FIGS. 1 to 5), the first rotation lever 62 is integrally formed in the operation direction (clockwise direction in FIG. 6) with the support shaft 61 as a fulcrum. Go around
The piston pushing portion 63 a pushes the piston 46 of the hydraulic master cylinder 40 toward the bottom of the cylinder hole 43 to increase the pressure of the hydraulic fluid in the hydraulic chamber 47. The hydraulic fluid pressurized in the hydraulic chamber 47 is sent from the output port 42 on the bottom wall of the cylinder hole to the caliper body 31 of the hydraulic brake 10 through the hydraulic pipe 18 and hydraulically operates the caliper body 31.
The braking of the front wheel 9 is performed.

Next, the operation of the interlocking brake system 16 using the second brake operator 5 will be described with reference to FIG. 7. The gripping operation of the second brake operator 5 causes the interlocking brake connecting means 19 to operate. Is pulled, the equalizer lever 72 of the output distribution means 70 rotates in the operating direction (clockwise in FIG. 7) about the floating fulcrum 74 at one end 72a, and is connected to the other end 72b. The driven side linking means 21 is pulled.

At this time, a traction force is also generated in the direction in which the floating fulcrum 74 moves upward in FIG. 7 on the one end 72a side, but the floating fulcrum 74 is connected to the second rotating lever 71 by a third return spring 75. One ends 71a, 72a of the equalizer lever 72
7 is generated in the downward direction in FIG. 7, so that the second rotation lever 71 is in the non-operation position unless the traction force generated at one end 72 a of the equalizer lever 72 exceeds the tension of the third return spring 75. Does not rotate from

Then, one end 72 of the equalizer lever 72
When the traction force generated at the position (a) exceeds the tension of the third return spring 75, the one end 72 a of the equalizer lever 72 moves to the fixed fulcrum 7.
7, the second rotary lever 71 is rotated in the operating direction (counterclockwise direction in FIG. 7) to generate hydraulic pressure in the hydraulic master cylinder 40 via the knocker 63, and the equalizer lever 72 itself is The second pivot lever 71 pivots in the operating direction (clockwise in FIG. 7) around the floating fulcrum 74 at one end 72a that moves upward in FIG. 7 by the rotation of the second pivot lever 71, and is driven by the other end 72b. The side linking means 21 is further pulled.

The driven linking means 21 pulled by the equalizer lever 72 is connected to the operating lever 35 of the mechanical brake 12.
And the camshaft 36 integrated with the operating lever 35 expands the brake shoes 33, 33 to brake the rear wheels. On the other hand, the second rotating lever 71 is rotated in the operating direction (counterclockwise in FIG. 7) about the fixed fulcrum 73 as described above, and the other end 71b is moved to the piston pushing portion 63a of the knocker 63.
And the piston pushing portion 63a pushes the piston 46 of the hydraulic master cylinder 40, and the hydraulic fluid in the hydraulic chamber 47 is hydraulically operated in the same manner as the operation of the independent brake system 15 described above. The brake is supplied to the caliper body 31 of the brake 10 to brake the front wheel 9.

The distance C between the other end 71b of the second pivoting lever 71 and the first stopper 50b of the guide bracket 50 is determined by the second pivoting lever 71 being the piston pushing portion 63 of the knocker 63.
As you push a, it is gradually buried and the second
When the other end 71b of the rotating lever 71 contacts the first stopper 50b, the rotation of the knocker 63 is restricted (FIG. 7).

In the operation of the interlocking brake system 16 described above, the input load from the second brake operator 5 is distributed by the output distribution means 70 as the output load to the hydraulic brake 10 and the mechanical brake 12, and Brake 10
And the mechanical brake 12 operate in conjunction.

When both the independent brake system 15 and the interlocking brake system 16 are operated, the hydraulic brake 10 that is operated by either of the brake systems 15, 16 is connected to the second brake lever 71. End 71b is first
Until the stopper 50b comes into contact with the stopper 50b, the operation is performed by the sum of the gripping operation forces of the first brake operator 4 and the second brake operator 5.

FIG. 8 shows a case in which the gripping operation force of the first brake operator 4 is large.
Then, the other end 7 of the second rotating lever 71 of the output distribution means 70
1b is in contact with the first stopper 50b and the knocker 6
In contrast, in the single brake system 15, the first brake operating member 4 is strongly gripped and operated, so that the first rotating lever 6 of the operating force converting means 60 is moved.
2 and the knocker 63 are largely rotated, and the piston pushing portion 63a pushes the piston 46, and at the same time, is separated from the other end 71b of the second rotating lever 71.

Next, the operation of the interlocking brake system 16 after the operation of the independent brake system 15 will be described with reference to FIGS.
This will be described with reference to FIG. In the first operation of the independent brake system 15, the front wheel 9 is braked by the hydraulic brake 10 as described above, and the first rotating lever 62 of the operating force conversion means 60 rotates the knocker 63 around the support shaft 61. As a result, the piston pressing portion 63a of the knocker 63 is already separated from the other end 72b of the equalizer lever 72 (FIG. 6). In the post-operation of the interlocking brake system 16 following the independent brake system 15, the gripping operation of the second brake operator 5 causes the equalizer lever 72 of the output distribution means 70 to operate.
However, the rear wheel is braked by the mechanical brake 12 by pulling the driven-side linking means 21 at the other end 72b.

When the piston pushing portion 63a of the knocker 63 is located above the first stopper 50b and the input load from the second brake operator 5 is larger than the input load from the first brake operator 4, Is the second rotating lever 7
The other end 71b of the first 1 pushes the piston pushing portion 63a until it contacts the first stopper 50b, and the hydraulic brake 10 is operated by the interlocking brake system 16.

In the first operation of the interlocking brake system 16, braking of the front wheels 9 by the hydraulic brake 10 and braking of the rear wheels by the mechanical brake 12 are performed as described above. In operation, when the input load from the first brake operator 4 is larger than the input load from the second brake operator 5, the piston pushing portion 63 a of the knocker 63 is moved to the other end 72 b of the equalizer lever 72.
, The piston 46 of the hydraulic master cylinder 40 is pushed alone, and the hydraulic brake 10 is operated by the independent brake system 15.

In the output distributing means 70 of this embodiment using the lever mechanism, when the interlocking brake system 15 operates, the second
The input load from the brake operator 5 is applied to the hydraulic brake 1
The total output load to the hydraulic brake 10 and the mechanical brake 12 may be increased or decreased from the input load from the second brake operator 5 while distributing the output load to the mechanical brake 12 as 0. Wi = input load from second brake operator 5 Wf = output load to hydraulic brake 10 Wr = output load to mechanical brake 12 Ws = load applied to floating fulcrum 74 P = second pivot lever The other end 71b of 71 and knocker 63
Wp = Tension of the third return spring 75 L1 = Floating fulcrum 74 and the other end 20b of the traction side connecting means 20
L2 = Length of the other end 20b of the traction side connecting means 20 and the other end 21b of the driven side connecting means 21 L3 = Length of the fixed fulcrum 73 and the floating fulcrum 74 L4 = The fixed fulcrum 73 and the contact point When the length is set to P, the relational expression of Wi = Wr + Ws (1) Ws × L1 = Wr × L2 (2) Ws × L3 = Wf × L4 (3) holds .

However, as condition 1, the second rotating lever 71
From the above-described equations (1) and (2), the input load W is maintained until the other end 71b of the first member abuts on the first stopper 50b from the inoperative position.
i is distributed in a ratio of Wr: Ws = L1: L2.

However, since the tension Wp of the third return spring 75 acts on the floating fulcrum 74 in the direction in which the floating fulcrum 74 is brought into contact with the non-operating position, when Ws ≦ Wp, the second rotating lever 71 is not actuated. The output load Wf is not distributed to the hydraulic brake 10 without rotating.

On the other hand, the output load W to the mechanical brake 12
For r, the input load Wi is distributed at a ratio of Wi: Wr = (L1 + L2): L1 according to the relationship of Wi × L1 = Wr × (L1 + L2) (4).

The load Ws applied to the floating fulcrum 74
Overcomes the tension Wp of the third return spring 75 (Ws>
Wp), the output load Wr to the mechanical brake 12 is distributed at a ratio of Wr: Ws = L1: L2 from the above equations (1) and (2), and the output load Wf to the hydraulic brake 10 is obtained.
Is determined from the load of Ws and the ratio of L3: L4 according to the above equation (3).

As condition 2, the second rotating lever 71
After the other end 71b of the contact member comes into contact with the first stopper 50b,
Since the rotation of the second rotation lever 71 is restricted, the output load Wf is no longer distributed to the hydraulic brake 10 again,
The output load Wr to the mechanical brake 12 includes the input load W
i is given by Wi: Wr = (L1 +
L2): Distributed at a ratio of L1.

The above equation (4) can be easily derived from the above equations (1) and (2). The output load Wr to the mechanical brake 12 is determined by the other end 71b of the second rotating lever 71. Regardless of whether or not the first stopper 50b contacts the first stopper 50b, the first stopper 50b always has a relationship proportional to the input load Wi.

For example, the input load Wi of the second brake operator 5 is set to 1, the length L1 = L2 = L4 = 1, and the length L
When 3 = 2, the output load Wf on the hydraulic brake 10 is 1.0, the output load Wr on the mechanical brake 12 is 0.5, and the total output load Wf + Wr is 1.5 times the input load Wi. To increase.

As described above, in this embodiment, when the interlocking brake system 16 is operated, the input load of the second brake operator 5 is output to the hydraulic brake 10 and the mechanical brake 12 by the output distribution means 70. In addition to distributing as a load,
The total output load to the hydraulic brake 10 and the mechanical brake 12 is applied to the second by the output distribution means 70 of the lever mechanism.
The hydraulic brake 10 and the mechanical brake 1 can increase or decrease the input load of the brake operator 5.
It is possible to set a more preferable braking force in accordance with the vehicle body condition and performance set for the motorcycle and the purpose of use for each of the two.

Further, by changing the lever ratio between the second rotating lever 71 and the equalizer lever 72 of the output distribution means 70, the present invention can be applied to other bar-handled vehicles, and the front and rear brakes have different performances. It is not necessary to change the braking force, so that a more suitable braking force can be set at low cost, and the versatility in practical use is extremely high.

Further, in this embodiment, the hydraulic master cylinder 40
The master cylinder unit 7 in which the first and second brake operating members 4 and 5 are attached and the leg shield between the front wheel 9 and the master cylinder unit 7 in which the 6, the connecting means 17 for the independent brake, the wiring of the traction-side connecting means 20 and the driven-side connecting means 21 of the connecting means 19 for the interlocking brake, and the piping of the hydraulic piping 18 are the shortest. In addition to being excellent in assembling workability, maintainability and economical efficiency,
Since the master cylinder unit 7 is not exposed to the outside of the vehicle body, the appearance can be beautifully treated, and the master cylinder unit 7 can be protected from external force, weather and dust, and the durability can be kept good.

Next, a second embodiment of the present invention will be described with reference to FIGS.
4 will be described. 9 is a partially sectional front view of the master cylinder unit in a non-operating state, FIG. 10 is a sectional view taken along line XX of FIG. 9, FIG. 11 is a sectional view taken along line XI-XI of FIG. 9, and FIG. 13 is a partial sectional front view of the master cylinder unit when only the brake system is operated, FIG. 13 is a partial sectional front view of the master cylinder unit when only the interlocking brake system is operated, and FIG. FIG. 4 is a partial cross-sectional front view of the master cylinder unit when both system brake systems are operated.

In this embodiment, the master cylinder unit 80
Of the first embodiment, the first turning lever 81 of the first embodiment, in which the first turning lever and the knocker are integrated, is provided on the piston 46 of the hydraulic master cylinder 40. And a stopper 81b for regulating the retreat limit.
The other end 71b of the second rotary lever 71 is provided with a plate-shaped and elliptical piston pressing portion 71c protruding toward the hydraulic master cylinder 40, and the pistons of the first and second rotary levers 81 and 71 are provided. The pushing portions 81a and 71c are moved from the bifurcated first stopper 50b to the piston 46 of the hydraulic master cylinder 40.
Is different from the first embodiment in that the piston 46 can be directly pushed by one or both of the first and second pivot levers 81 and 71 by contacting the outer end of the piston in parallel. I have.

The other end 71 of the second rotating lever 71 when not operating
A gap C similar to that of the first embodiment is set between the first stopper 50b and the first stopper 50b, and the other end 71b of the second pivot lever 71 pushes the piston of the first pivot lever 81. Part 8
A slit 82 for accommodating 1a is provided so that the first and second rotating levers 81 and 71 can rotate without interfering with each other.

The present embodiment is configured as described above, and each component of the master cylinder unit 80 is configured so that the first and second brake operators 4 and 5 shown in FIGS. In operation, it is in the state shown in FIGS.

When only the independent brake system 15 is operated from the above-mentioned non-operating state (FIG. 12), the gripping operation of the first brake operator 4 causes the independent brake connecting means 17 to operate.
Is pulled, and a first rotating lever 8 as an operating force converting means is provided.
1 rotates in the operation direction (clockwise direction in FIG. 12) around the support shaft 61 while the second rotation lever 71 of the output distribution unit 70 remains in the non-operation position (the position in FIGS. 9 to 11). Then, the piston pushing portion 81a is connected to the piston 4 of the hydraulic master cylinder 40.
6 is pushed toward the bottom of the cylinder hole 43, and the hydraulic fluid pressurized in the hydraulic chamber 47 is supplied to the caliper body 31 of the hydraulic brake 10, and the front wheel 9 is braked.

When only the interlocking brake system 16 is operated (FIG. 13), the traction side connecting means 20 of the interlocking brake connecting means 19 is towed by the gripping operation of the second brake operator 5, and the output distribution means is operated. 70 second rotating lever 7
1 and the equalizer lever 72 operate in the same manner as in the first embodiment, the equalizer lever 72 operates the mechanical brake 12 to brake the rear wheels, and the second rotary lever 71 While the one-rotation lever 81 remains at the non-operation position (the position shown in FIGS. 9 to 11), the piston pressing portion 71
c directly pushes the piston 46 of the hydraulic master cylinder 40 to operate the hydraulic brake 10 and brake the front wheel 9.

The amount of rotation of the second pivoting lever 71 is at most a distance until the second pivoting lever 71 is brought into contact with the first stopper 50b by filling the gap C between the second pivoting lever 71 and the first stopper 50b. Is set to a length that allows hydraulic fluid 10 to supply hydraulic fluid sufficient for normal front wheel 9 braking.

When both the independent brake system 15 and the interlock brake system 16 are operated (FIG. 14),
The hydraulic brake 10 that is operated by any of these brake systems 15 and 16 includes a first and second pivot levers 8.
The piston pushing portions 81a and 71c of the first and 71 push the piston 46 of the hydraulic master cylinder 40 and are actuated by the gripping force of the first brake operator 4 and the second brake operator 5 whichever is greater. I do. In FIG. 14, even after the other end 71b of the second rotating lever 71 comes into contact with the first stopper 50b, the piston pushing portion 81a of the first rotating lever 81 can use the piston 46 of the hydraulic master cylinder 40 alone. 2 shows a state in which the brake is pushed to increase the braking force of the hydraulic brake 10.

Next, a third embodiment of the present invention will be described with reference to FIGS. 15 is a partially sectional front view of the master cylinder unit in a non-operating state, FIG. 16 is a sectional view taken along the line XVI-XVI of FIG. 15, and FIG.
-XVII sectional view, FIG. 18 is a partial sectional front view of the master cylinder unit when only the independent brake system is operated,
FIG. 19 is a partial cross-sectional front view of the master cylinder unit when only the interlocking brake system is operated, and FIG. 20 is a partial cross-sectional front view of the master cylinder unit when both the independent brake system and the interlocking brake system are operated. FIG.

In this embodiment, the master cylinder unit 90
Is constituted by a first turning lever 62 and a knocker 63 as in the first embodiment, whereas the second turning lever 71 and the equalizer lever 72 of the output distribution means 70 are The relationship is set opposite to that of the first and second embodiments.

That is, in this embodiment, the second rotating lever 71 used for the hydraulic brake 10 in the first and second embodiments is applied to the mechanical brake 12, and the mechanical The equalizer lever 72 used for the type brake 12 is applied to the hydraulic brake 10, and the second rotating lever 71 is
One end of the intermediate portion is pivotally supported at a fixed fulcrum 73 by a lever holder 50e of the guide bracket 50, and at the other end 71b,
The other end 21b of the driven side linking means 21 into which the wire guide 50h of the guide bracket 50 is inserted is connected.

The equalizer lever 72 is pivotally supported at one end 71a of the second rotating lever 71 and a floating fulcrum 74 at an intermediate portion 72c near the other end so as to be swingably supported by the one end 72a of the equalizer lever 72. Is connected to the other end 20b of the traction side linking means 20 through which the wire guide 50f of the guide bracket 50 is inserted, and the other end 72b of the equalizer lever 72 is brought into contact with the non-operating side surface of the piston pushing portion 63a of the knocker 63. By doing so (FIG. 15), a gap C is set between the other end 72b and the first stopper 50b of the guide bracket 50.

The guide bracket 50 is provided with a second stopper 50c at a position above the second rotation lever 71, and the second rotation lever 71 is moved in the non-operation direction by the pulling force of the mechanical brake 12. 15, 18 to 20 (upward direction)
And the retreat limit is restricted by contact with the second stopper 50c (FIGS. 15, 17 to 20).

A third stopper 71d is provided at a lower portion on one end side of the second rotating lever 71 so as to face the second stopper 50c. The third stopper 71d is provided between the one end 72a of the equalizer lever 72 and the locking piece 50f of the guide bracket 50. A third return spring 75 is stretched between them, and the equalizer lever 72
Non-operating direction due to the tensile force of the return spring 75 (FIGS. 15 and 18)
20 (downward in FIG. 20), and the retreat limit is restricted by contact with the third stopper 71d.
b, the piston pushing portion 63a of the knocker 63 as described above.
(FIGS. 15 and 17).

The master cylinder unit 90 according to the present embodiment having the above-described configuration includes the first and second brake operators 4 and 4.
5 is in the state shown in FIG. 15 to FIG.

In the operation of the independent brake system 15 using the first brake operating element 4 (FIG. 18), the piston pushing portion 63a of the knocker 63 of the operating force converting means 60
With the equalizer lever 72 of the power distribution means 70 in the inactive position, the piston 46 of the hydraulic master cylinder 40
To supply the hydraulic fluid pressurized in the hydraulic chamber 47 to the caliper body 31 of the hydraulic brake 10, whereby the front wheels 9 are braked.

In the operation of the interlocking brake system 16 using the second brake operating element 5 (FIG. 19), the gripping operation of the second brake operating element 5 causes the linking means 19 for the interlocking brake to be connected to the traction side. When the tow 20 is towed, the other end 20b of the tow-side connecting means 20 is connected to the output distribution means 7
While the equalizer lever 72 of 0 rotates the second rotation lever 71 in the operating direction (clockwise direction in FIG. 18) about the fixed fulcrum 73, the equalizer lever 72 itself rotates by the rotation of the second rotation lever 71 in FIG. 18 around the floating fulcrum 74 moving upward in the operating direction (counterclockwise in FIG. 18).

The other end 72 b of the equalizer lever 72 pushes the piston pushing portion 63 a of the knocker 63, and the hydraulic fluid pressurized in the hydraulic chamber 47 of the hydraulic master cylinder 40 is supplied to the caliper body 31 of the hydraulic brake 10. To brake the front wheels 9. On the other hand, the second rotating lever 71
By the above-mentioned rotation, the driven side linking means 21 is pulled, and the mechanical brake 12 is operated to perform braking of the rear wheels.

In the operation of both the independent brake system 15 and the interlocking brake system 16 (FIG. 20), the hydraulic brake 10 operated by either of the brake systems 15 and 16 is connected to the piston 46 of the hydraulic master cylinder 40.
Until the knocker 63 of the operating force conversion means 60 and the equalizer lever 72 of the output distribution means 70 are pushed, and the other end 72b of the equalizer lever 72 contacts the first stopper 50b, the first brake operator 4 Second brake operator 5
Operates by the sum of the gripping operation force with.

In FIG. 20, after the other end 72b of the equalizer lever 72 comes into contact with the first stopper 50b, the piston pushing portion 63a of the knocker 63 is
0 by pushing the piston 46 of the hydraulic brake 1 alone.
0 shows that the braking force of 0 is being increased.

Further, the output distribution means 70 of this embodiment is provided when the interlocking brake system 16 shown in FIGS.
The other end 72b of the equalizer lever 72 is
b, the towing side linking means 20 can be further towed by the gripping operation of the second brake operator 5, and the second
Towing side connecting means 2 by increasing the grip of brake operator 5
When the zero is greatly towed, the other end 72b of the equalizer lever 72 slides on the first stopper 50b toward the fixed fulcrum 73, and moves the floating fulcrum 74 upward in FIGS. 19 and 20, and the second rotating lever 71 is moved upward by the floating fulcrum 74 to move around the fixed fulcrum 73 (clockwise in FIGS. 19 and 20). ), The driven side linking means 21 is pulled, and a large braking force is applied by the mechanical brake 12 to brake the rear wheels.

Next, a fourth embodiment of the present invention will be described with reference to FIGS. 21 is a partially sectional front view of the master cylinder unit in a non-operating state, FIG. 22 is a partially sectional front view of the master cylinder unit when only the independent brake system is operated, and FIG. 23 is an interlocking brake system. FIG. 24 is a partial sectional front view of the master cylinder unit when both the independent brake system and the interlocking brake system are activated.

[0078] Master cylinder unit 100 of the present embodiment
Is a hydraulic master cylinder 40 common to the first to third embodiments.
The first rotating lever 81 of the second embodiment in which the first rotating lever and the knocker are integrated is applied as the operating force converting means, the equalizer lever 72 is used for the hydraulic brake 10, and the mechanical brake 12 is used. And the other end 72b of the equalizer lever 72, and the same piston pressing as the second rotating lever 71 of the second embodiment. A moving portion 72d is provided, and the first rotating lever 81 and the piston pressing portions 81a and 72d of the equalizer lever 72 are connected to the first stopper 50b.
, The piston 46 of the hydraulic master cylinder 40 is brought into parallel contact with the outer end of the piston 46 of the hydraulic master cylinder 40 so that the first rotating lever 81 and the equalizer lever 72
It is characterized in that one or both of them can be directly pushed.

The master cylinder unit 100 of the present embodiment configured as described above operates only the independent brake system 15 from the non-operation state shown in FIG. 21 (FIG. 2).
2), the first rotating lever 81 as the operating force converting means is
While the equalizer lever 72 of the output distribution means 70 is left at the non-operation position (the position shown in FIGS. 21 and 22), it is rotated in the operation direction (clockwise direction in FIG. 12) about the support shaft 61 as a fulcrum, and the piston pushing part 81a is rotated. Pushes the piston 46 of the hydraulic master cylinder 40 toward the bottom of the cylinder hole 43, and pressurizes the hydraulic fluid in the hydraulic chamber 47 to the caliper body 3 of the hydraulic brake 10.
1 to brake the front wheel 9.

When only the interlocking brake system 16 is operated (FIG. 23), the second rotation lever 7 of the output distribution means 70 is operated.
1 and the equalizer lever 72 operate in the same manner as in the third embodiment, the second turning lever 71 operates the mechanical brake 12 to perform braking on the rear wheels, and the equalizer lever 72 operates While the one-rotation lever 81 remains at the non-operation position (the position shown in FIGS. 21 and 23), the piston pressing portion 72
d directly pushes the piston 46 of the hydraulic master cylinder 40 to operate the hydraulic brake 10 and brake the front wheel 9.

In the operation of both the independent brake system 15 and the interlocking brake system 16 (FIG. 24), the piston 46 of the hydraulic master cylinder 40 is
Until both the rotating lever 81 and the equalizer lever 72 of the output distribution means 70 are pushed and the piston pushing part 72d of the equalizer lever 72 comes into contact with the first stopper 50b, the first brake operator 4 and the second brake The hydraulic brake 10 is actuated by a greater gripping force with the brake operator 5.

In FIG. 24, after the other end 72b of the equalizer lever 72 abuts on the first stopper 50b, the piston pushing portion 81a of the first rotary lever 81 can use the piston 46 of the hydraulic master cylinder 40 alone. 2 shows a state in which the brake is pushed to increase the braking force of the hydraulic brake 10.

The output distributing means 70 of this embodiment operates when the interlocking brake system 16 shown in FIGS.
The other end 72b of the equalizer lever 72 is
After the contact with the second brake operating member b, the second brake operator 5 can be further gripped to apply a larger braking force to the mechanical brake 12 to brake the rear wheels as in the case of the third embodiment. Come.

The same effects as in the first embodiment can be obtained in the above-described second to fourth embodiments illustrated in FIGS. 9 to 24. In the second and fourth embodiments in which the first pivot lever integrated with the knocker is used as the output distribution means, the number of components is reduced, resulting in excellent assemblability and economy.

In each of the above embodiments, the other end of the second rotating lever or the equalizer lever of the output distribution means is brought into contact with the stopper. However, the present invention can omit this stopper. . In this case, the second rotation lever or the equalizer lever can be rotated following the piston of the hydraulic master cylinder so that the second rotation lever or the equalizer lever is directly moved from the piston at the movement limit. Alternatively, the reaction force can be received through the knocker at the rotation limit.

In the first and third embodiments in which the second pivoting lever pushes the piston of the hydraulic master cylinder via the knocker, the other end of the second pivoting lever is connected to the non-movement of the piston pushing portion of the knocker. Although it was in contact with the side of the piston, which is the working side,
The second pivoting lever only has to push the knocker in the operating direction (piston pushing direction). For example, the other end of the second pivoting lever is provided so as to abut or separate from the non-operating side surface of the stopper of the knocker. You may.

Further, the hydraulic brake and the mechanical brake may be used for the front wheel brake and the rear wheel brake of a bar handle vehicle in a manner opposite to the above embodiment. The first and second brake operating members may be brake pedals, and a plurality of rods may be connected or a combination of a wire cable and a rod may be used as the traction-side connecting means and the driven-side connecting means.

The knocker and the piston pressing portion of the first rotating lever may be separated from the piston of the hydraulic master cylinder. Also, the piston pressing portion of the second rotary lever or the equalizer lever may be separated from the knocker, the piston pressing portion of the first rotary lever, or the piston of the hydraulic master cylinder.

Further, when the master cylinder unit is disposed between the handlebar and the front wheel, there is an effect that piping and wiring can be routed with the shortest length, etc. Further, in a scooter type vehicle as in the embodiment, By being housed in a body cover such as a leg shield or the like, it is more preferable to be able to protect from external force, weather and dust, but the present invention does not hinder the arrangement of the master cylinder unit other than between the handlebar and the front wheel.

[0090]

As described above, claims 1, 2, and 3
According to the inventions described in the fourth and fifth aspects, when the hydraulic brake and the mechanical brake are operated in conjunction with each other, the input load of the interlocking brake operator is applied to the hydraulic brake and the mechanical brake by the output distribution means. By adjusting the lever ratio of the lever mechanism used in the output distribution means while distributing the output load to the hydraulic brake and the mechanical brake, the total output load to the hydraulic brake and the mechanical brake can be reduced from the input load of the interlocking brake operator. Can be increased or decreased, so that a more preferable braking force can be set for each of the hydraulic brake and the mechanical brake in accordance with the vehicle body conditions and performance of the bar handle vehicle and the intended use. Further, even in an existing bar handle vehicle, by simply changing the lever ratio of the lever mechanism used for the output distribution means, a suitable braking force can be obtained at low cost by the hydraulic brake and the mechanical brake of the target bar handle vehicle. Therefore, practical versatility is extremely high.

According to the third and sixth aspects of the present invention, the second rotary lever or the equalizer lever of the output distribution means for pushing the piston of the hydraulic master cylinder directly or via the knocker of the operating force conversion means. By restricting the rotation by the stopper, a reaction force is applied to the second rotation lever or the equalizer lever that abuts on the stopper, so that the other second rotation lever or the equalizer lever used for the mechanical brake can be reliably used. Can be activated.

Furthermore, according to the invention of claim 7, wiring of the independent brake connecting means, the traction side connecting means and the driven side connecting means of the interlocking brake connecting means, and the hydraulic pressure used for the hydraulic brake Since the piping can be routed with the shortest length, it is excellent in assembling workability, maintainability, and economy.

[Brief description of the drawings]

FIG. 1 is a schematic view showing a non-operating state of a brake device for a bar handle vehicle according to a first embodiment of the present invention.

FIG. 2 is a front view of a scooter type bar handle vehicle equipped with the brake device of FIG. 1 showing a first embodiment of the present invention;

FIG. 3 is a partial cross-sectional front view showing a first embodiment of the present invention in a non-operating state of a master cylinder unit used in the brake device of FIGS. 1 and 2;

FIG. 4 is a sectional view taken along line IV-IV of FIG.

FIG. 5 is a sectional view taken along line VV of FIG. 3;

FIG. 6 is a partial cross-sectional front view of the master cylinder unit when only the independent brake system according to the first embodiment of the present invention is operated.

FIG. 7 is a partial sectional front view of the master cylinder unit when only the interlocking brake system according to the first embodiment of the present invention is operated.

FIG. 8 is a partial cross-sectional front view of the master cylinder unit when both the independent brake system and the interlocking brake system according to the first embodiment of the present invention are operated.

FIG. 9 is a partially sectional front view of a master cylinder unit showing a second embodiment of the present invention in a non-operating state.

FIG. 10 is a sectional view taken along line XX of FIG. 9 showing a second embodiment of the present invention.

FIG. 11 shows a second embodiment of the present invention.
I cross section

FIG. 12 is a partial cross-sectional front view of the master cylinder unit when only the independent brake system according to the second embodiment of the present invention is operated.

FIG. 13 is a partial cross-sectional front view of a master cylinder unit when only an interlocking brake system according to a second embodiment of the present invention is operated.

FIG. 14 is a partial cross-sectional front view of the master cylinder unit when both the independent brake system and the interlocking brake system are operated, showing the second embodiment of the present invention.

FIG. 15 is a partially sectional front view of a non-operating state of a master cylinder unit according to a third embodiment of the present invention.

16 shows a third embodiment of the present invention.
XVI cross section

17 shows a third embodiment of the present invention.
XVII cross section

FIG. 18 is a partial sectional front view of the master cylinder unit when only the independent brake system according to the third embodiment of the present invention is operated.

FIG. 19 is a partial cross-sectional front view of a master cylinder unit when only an interlocking brake system according to a third embodiment of the present invention is operated.

FIG. 20 is a partial cross-sectional front view of the master cylinder unit when both the independent brake system and the interlocking brake system according to the third embodiment of the present invention are operated.

FIG. 21 is a partial sectional front view of a non-operating state of a master cylinder unit according to a fourth embodiment of the present invention.

FIG. 22 is a partial sectional front view of the master cylinder unit when only the independent brake system according to the fourth embodiment of the present invention is operated.

FIG. 23 is a partial cross-sectional front view of a master cylinder unit when only an interlocking brake system according to a fourth embodiment of the present invention is operated.

FIG. 24 is a partial cross-sectional front view of the master cylinder unit when both the independent brake system and the interlocking brake system according to the fourth embodiment of the present invention are operated.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Scooter type motorcycle 2 ... Brake device 3 ... Handlebar 4 ... First brake operator using brake lever 5 ... Second brake operator using brake lever 7 ... Hydraulic master cylinder 40 and operating force conversion Master cylinder unit comprising means 60 and output distribution means 70 9 Front wheel 10 Hydraulic brake (front wheel brake) 12 Mechanical brake (rear wheel brake) 15 Single brake operated by first brake operator 4 System 16: Interlocking brake system operated by the second brake operator 5 17: Linking means for independent system brakes 17a, 20a, 21a: One end 17b, 20b, 21b: Other end 18: Hydraulic pipe 19: Interlocking brake Connecting means 20 for traction side connecting means 21 for follower side connecting means 40 hydraulic master cylinder 41 cylinder body 42 Output port 43 ... Cylinder hole 46 ... Piston 47 ... Hydraulic chamber 48 ... First return spring 50 ... Guide bracket 50b ... First stopper (stopper of the present invention) 50c ... Second stopper 60 ... Operating force conversion means 61 ... Support shaft 62: first rotating lever 63: knocker 63a: piston pressing portion 64: second return spring 70: output distribution means 71: second rotating lever 72: equalizer levers 71a, 72a: one end 71b, 72b: other end 71c , 72d: piston pressing portion 71d: third stopper 72c: intermediate portion 73: fixed fulcrum 74: floating fulcrum 75: third return spring C: gap Wi: input load from the second brake operator 5 Wf: hydraulic brake Output load to 10 Wr: Output load to mechanical brake 12 Ws: Load applied to floating fulcrum 74 P: Other end of second rotating lever 71 1b and the knocker 63
Wp: tension of third return spring 75 L1: floating fulcrum 74 and the other end 20b of traction side linking means 20
L2: the length of the other end 20b of the traction-side connecting means 20 and the other end 21b of the driven-side connecting means 21 L3: the length of the fixed fulcrum 73 and the floating fulcrum 74 L4: the fixed fulcrum 73 and the contact point Length with P

Claims (7)

[Claims] 1. A hydraulic pressure generated in a hydraulic master cylinder by pulling one of a front wheel brake and a rear wheel brake of a bar handle vehicle by an independent brake connecting means by operating a first brake operating member. A hydraulic brake to be actuated, the other being a mechanical brake which is operated by pulling a linking means for an interlocking brake by operating a second brake manipulator, and wherein the hydraulic master cylinder is provided with the first brake manipulator; Operating force converting means for converting the input load of the second cylinder into the hydraulic pressure of the hydraulic master cylinder, and distributing the input load of the second brake operator to the hydraulic pressure of the hydraulic master cylinder and the operating force of the mechanical brake. The hydraulic cylinder, the operating force converting means, and the output distributing means constitute a master cylinder unit. A first rotating lever connected to the first brake operating member by a linking means for an independent brake, the first rotating lever rotating about a support shaft by operating the first brake operating member, With the pusher, a knocker that rotates in the direction of the cylinder hole opening of the hydraulic master cylinder with the support shaft as a fulcrum, and pushes the piston of the hydraulic master cylinder into the cylinder hole with the piston pushing portion. And the linking means for the interlocking brake is divided into a traction-side linking means connected to the second brake operator and a driven-side linking means connected to the mechanical brake, and the traction-side linking means and the driven The output distributing means is interposed between the side distributing means and the output distributing means, the intermediate portion is pivotally supported at a fixed fulcrum, and pushes the piston of the hydraulic master cylinder via the knocker. A two-rotation lever and the second rotation lever And an equalizer lever pivotally supported at one of the intermediate portion and the one end at a floating fulcrum and swingably supported, and the equalizer lever is provided on the traction side of the interlocking system linking means. A brake device for a bar handle vehicle, wherein a connecting means and a driven side connecting means are connected, and the other end of the second pivot lever is disposed on a non-operating side surface of the knocker. 2. A hydraulic pressure generated in a hydraulic master cylinder by pulling one of a front wheel brake and a rear wheel brake of a bar handle vehicle by an independent brake connecting means by operating a first brake operator. A hydraulic brake to be actuated, the other being a mechanical brake which is operated by pulling a linking means for an interlocking brake by operating a second brake manipulator, and wherein the hydraulic master cylinder is provided with the first brake manipulator; Operating force converting means for converting the input load of the second cylinder into the hydraulic pressure of the hydraulic master cylinder, and distributing the input load of the second brake operator to the hydraulic pressure of the hydraulic master cylinder and the operating force of the mechanical brake. The hydraulic pressure master cylinder, the working force converting means, and the output distributing means constitute a master cylinder unit. A first rotating lever connected to the first brake operating member by a linking means for an independent brake, the first rotating lever not rotating about a support shaft by operation of the first brake operating member; A piston pushing portion for pushing a piston of the hydraulic master cylinder into a cylinder bore, wherein the linking means for interlocking brake is connected to a traction side linking means connected to the second brake operator, and the machine It is divided into the driven side connecting means connected to the type brake, and the output distribution means is interposed between the traction side connecting means and the driven side connecting means, and the intermediate part is fixed to the output supporting means. A second pivoting lever pivotally supported and pushing a piston of the hydraulic master cylinder; and one end of the second pivoting lever,
One of the middle part and one end is pivoted at the floating fulcrum,
An equalizer lever supported so as to be swingable, connecting the traction-side linking means and the driven-side linking means of the interlocking brake linking means to the equalizer lever, and connecting the other end of the second pivot lever A brake device for a bar handle vehicle, wherein the brake device is disposed so as to face the piston of the hydraulic master cylinder in parallel with the piston pressing portion of the first rotary lever. 3. A stopper according to claim 1, further comprising a stopper for restricting the rotation of the second rotating lever when the second rotating lever is rotated in the direction of pushing the piston. Brake equipment for bar handle vehicles. 4. A hydraulic pressure generated in a hydraulic master cylinder by pulling one of a front wheel brake and a rear wheel brake of a bar handle vehicle by operating an independent brake connecting means by operating a first brake operating member. A hydraulic brake to be actuated, the other being a mechanical brake which is operated by pulling a linking means for an interlocking brake by operating a second brake manipulator, and wherein the hydraulic master cylinder is provided with the first brake manipulator; Operating force converting means for converting the input load of the second cylinder into the hydraulic pressure of the hydraulic master cylinder, and distributing the input load of the second brake operator to the hydraulic pressure of the hydraulic master cylinder and the operating force of the mechanical brake. The hydraulic cylinder, the operating force converting means, and the output distributing means constitute a master cylinder unit. A first rotating lever connected to the first brake operating member by a linking means for an independent brake, the first rotating lever rotating about a support shaft by operating the first brake operating member, With the pusher, a knocker that rotates in the direction of the cylinder hole opening of the hydraulic master cylinder with the support shaft as a fulcrum, and pushes the piston of the hydraulic master cylinder into the cylinder hole with the piston pushing portion. And the linking means for the interlocking brake is divided into a traction-side linking means connected to the second brake operator and a driven-side linking means connected to the mechanical brake, and the traction-side linking means and the driven The output distributing means is interposed between the side distributing means and the output distributing means. The output distributing means has a second pivot lever pivotally supported at an intermediate portion at a fixed fulcrum, and one end of the second pivot lever. Either the middle part or one end is pivoted at the floating fulcrum An equalizer lever that is supported so as to push the piston of the hydraulic pressure master cylinder through the knocker, and connects the traction-side linking means of the linking means for the interlocking brake to the equalizer lever, and A bar handle, characterized in that the other end of the lever is disposed on the non-operating side surface of the knocker, and the other end of the second pivot lever is connected to the driven side connecting means of the interlocking brake connecting means. Vehicle brake system. 5. A hydraulic pressure generated in a hydraulic master cylinder by pulling one of a front wheel brake and a rear wheel brake of a bar handle vehicle by an independent brake connecting means by operating a first brake operator. A hydraulic brake to be actuated, the other being a mechanical brake which is operated by pulling a linking means for an interlocking brake by operating a second brake manipulator, and wherein the hydraulic master cylinder is provided with the first brake manipulator; Operating force converting means for converting the input load of the second cylinder into the hydraulic pressure of the hydraulic master cylinder, and distributing the input load of the second brake operator to the hydraulic pressure of the hydraulic master cylinder and the operating force of the mechanical brake. The hydraulic pressure master cylinder, the working force converting means, and the output distributing means constitute a master cylinder unit. A first rotating lever connected to the first brake operating member by a linking means for an independent brake, the first rotating lever not rotating about a support shaft by operation of the first brake operating member; A piston pushing portion for pushing a piston of the hydraulic master cylinder into a cylinder bore, wherein the linking means for interlocking brake is connected to a traction side linking means connected to the second brake operator, and the machine It is divided into the driven side connecting means connected to the type brake, and the output distribution means is interposed between the traction side connecting means and the driven side connecting means, and the intermediate part is fixed to the output supporting means. A second pivot lever pivotally supported at one end, and one end of the second pivot lever is pivotally supported at one of an intermediate portion and one end at a floating fulcrum, and is pivotably supported. Set up an equalizer lever that pushes the cylinder piston. Connecting the traction side connecting means of the interlocking brake linking means to the equalizer lever, and connecting the driven side linking means of the interlocking brake linking means to the other end of the second rotating lever, A brake device for a bar handle vehicle, wherein the other end of the equalizer lever is disposed so as to face a piston of the hydraulic master cylinder in parallel with a piston pressing portion of the first rotary lever. 6. The bar handle vehicle brake according to claim 4, wherein a stopper is provided for restricting the rotation of the equalizer lever when the equalizer lever rotates in the piston pushing direction. apparatus. 7. The system according to claim 1, wherein the first brake operator and the second brake operator are brake levers attached to a handlebar, and the master cylinder unit is disposed between the handlebar and the front wheels. The brake device for a bar handle vehicle according to any one of claims 1 to 6.