CN106608252A - Hydraulic time difference brake device - Google Patents

Abstract

A hydraulic time difference brake device includes: the master cylinder mechanism, the interlock pump mechanism and the time difference pump mechanism, wherein the interlock pump piston of the interlock pump mechanism is directly interlocked with the master cylinder piston of the master cylinder mechanism, the time difference pump piston of the time difference pump mechanism is a stroke distance away from the master cylinder piston, when the master cylinder mechanism is operated by starting brake, the interlock pump mechanism can directly act to provide a direct brake oil pressure to drive the first brake, the time difference pump mechanism acts after a preset time, and the time difference brake oil pressure drives the second brake with the time difference.

Description

Hydraulic time difference braking device

technical field

The invention relates to a braking control device, in particular to an oil pressure time difference braking device.

Background technique

In the braking control of various vehicles involving automobiles, motorcycles, bicycles, etc., it is often necessary to perform braking control with sequential output. Smooth, stable ideal performance.

Taking the brake control of a bicycle as an example, the brake device of a general bicycle drives the brake to brake the front and rear wheels of the bicycle through the rider pressing the brake handle. Usually, a brake handle of a bicycle is used to drive a brake correspondingly, the right brake handle is linked to the brake controlling the rear wheel, and the left brake handle is linked to the brake controlling the front wheel. In order to make the bicycle complete braking in a stable and stable state, the brakes of the rear wheels must be driven first and then the brakes of the front wheels when braking. However, when running into a critical situation, it is unavoidable to misoperate the brakes of the front and rear wheels, causing accidents such as the bicycle to overturn or skid.

Contents of the invention

Therefore, the purpose of the present invention is to provide a hydraulic type time difference braking device, which can make different tires of the vehicle perform braking actions with time difference.

The technical means adopted by the present invention to solve the problems of the prior art is to provide an oil pressure type time difference braking device, comprising: a master pump mechanism with a master pump chamber, a master pump piston, and a master pump chamber connected to the The first input pipe and the second input pipe of the chamber, the master pump piston is set in the master pump chamber to slide with the pressure change in the master pump chamber, the first input The pipe and the second input pipe are arranged to be operated by the first brake operating member and the second brake operating member respectively so as to pressurize the input hydraulic oil in the master pump chamber, so that the master pump piston is subjected to pressure. Press to slide in the direction of pressure output;

The interlocking pump mechanism has an interlocking pump chamber, an interlocking pump piston, and a first output pipe connected to the interlocking pump chamber, and the interlocking pump piston is arranged in the interlocking pump chamber chamber and is directly linked with the master pump piston, so as to slide and move along with the master pump piston along the pressure output direction to pressurize the linked pump chamber, so that the linked pump chamber The dynamic pump chamber outputs hydraulic oil from the first output pipe to provide direct brake oil pressure to drive the first brake; and the time difference pump mechanism has a time difference pump chamber, a time difference pump piston, and is connected to the time difference The second output pipe of the pump chamber, the time difference pump piston is arranged in the time difference pump chamber, and the time difference pump piston is in contact with the master pump before the master pump piston is not pressed and slides The pump pistons are separated by a stroke distance in the pressure output direction, so that the master pump piston slides the stroke distance along the pressure output direction to push the time difference pump piston to slide, Thereby pressurizing the time difference pump chamber so that the time difference pump chamber outputs hydraulic oil from the second output pipe to provide time difference brake oil pressure to drive the second brake with time difference, wherein the linkage The pump chamber and the time difference pump chamber are arranged so that there is a predetermined chamber radius ratio between the chamber radius of the interlocking pump chamber and the chamber radius of the time difference pump chamber, Therefore, there is a predetermined braking oil pressure ratio between the time difference braking oil pressure and the direct braking oil pressure corresponding to the chamber radius ratio.

In an embodiment of the present invention, the interlocking pump chamber and the time difference pump chamber have different chamber radii.

In an embodiment of the present invention, the chamber radius of the time difference pump chamber is greater than the chamber radius of the interlocking pump chamber, so that the time difference braking oil pressure is greater than the direct braking oil pressure .

In an embodiment of the present invention, the interlocking pump mechanism further includes a first reset member connected to the interlock pump piston, and the first reset member is set to normally face a direction opposite to the The direction of the pressure output direction pushes the piston of the linked pump.

In an embodiment of the present invention, the first reset member is a spring.

In an embodiment of the present invention, the time difference pump mechanism further includes a second reset member connected to the time difference pump piston, and the second reset member is set to normally output a pressure opposite to the one described above. The direction of the direction pushes the piston of the time difference pump.

In an embodiment of the present invention, the second reset member is a spring.

In an embodiment of the present invention, the master pump chamber, the interlocking pump chamber and the time difference pump chamber are integrally connected chambers.

In one embodiment of the present invention, the first brake that the linkage pump mechanism drives is a rear wheel brake, and the second brake that the time-difference pump mechanism drives The device is a front wheel brake.

Through the technical means adopted in the present invention, the present invention can control different tires to perform braking actions with a time difference, so that the vehicle has a more stable and stable ideal performance in braking. For example, when the present invention is applied to a bicycle, it can effectively avoid accidents such as the bicycle overturning or the rider being thrown off the vehicle body by inertial motion due to premature braking of the front wheel or sudden stop of the two wheels. When the present invention is applied to automobiles and locomotives, corresponding time-difference braking control can also be carried out in accordance with the respective types of vehicles, so as to realize smooth and stable braking. In addition, in the embodiment of the present invention, the ratio of the output brake oil pressure is changed by adjusting the radius ratio between the chambers (interlocking pump chamber and time difference pump chamber), so as to realize the brake oil pressure applied to different tires. Give the control of the braking force.

Description of drawings

FIG. 1 is a schematic diagram showing a hydraulic differential braking device according to an embodiment of the present invention;

Fig. 2 is a schematic diagram showing the continuous action of the hydraulic time difference braking device of Fig. 1;

FIG. 3 is a schematic diagram showing the continuous operation of the hydraulic differential braking device of FIG. 1 .

【Symbol Description】

100 Hydraulic time difference brake device

1 master pump mechanism

10 Master pump chamber

101 first input pipe

102 Second input tube

11 master cylinder piston

2 linkage pump mechanism

20 interlocking pump chambers

201 First output tube

21 Coupling pump piston

22 First reset

3 Time difference pump mechanism

30 jet lag pump chamber

301 Second output pipe

31 Time difference pump piston

32 Second reset

4 housing

B1 first brake

B2 second brake

D Pressure output direction

_D Ttravel distance

H hydraulic oil

L1 first brake operating part

L2 Second brake operating member

P1 direct brake oil pressure

P2 Time difference brake oil pressure

r1 chamber radius

r2 chamber radius

r3 chamber radius

detailed description

Embodiments of the present invention will be described below with reference to FIGS. 1 to 3 . The description is not intended to limit the implementation of the present invention, but is one of the examples of the present invention.

As shown in FIG. 1 , a hydraulic time difference braking device 100 according to an embodiment of the present invention includes: a master pump mechanism 1 having a master pump chamber 10, a master pump piston 11, and a master pump piston 11 connected to the A first input pipe 101 and a second input pipe 102 of the master pump chamber 10, the master pump piston 11 is set in the master pump chamber 10 to follow the master pump chamber 10 The pressure changes and slides, the first input pipe 101 and the second input pipe 102 are set to be operated by a first brake operating member L1 and a second brake operating member L2 respectively so as to control the The input hydraulic oil H in the master pump chamber 10 is pressurized, so that the master pump piston 11 is pressurized to slide and move along a pressure output direction D; a linked pump mechanism 2 has a linked pump chamber 20 , a linkage pump piston 21, and a first output pipe 201 connected to the linkage pump chamber 20, the linkage pump piston 21 is arranged in the linkage pump chamber 20 and directly Linked with the master pump piston 11, so as to slide and move along with the master pump piston 11 along the pressure output direction D so as to pressurize the linked pump chamber 20, so that the The interlocking pump chamber 20 outputs hydraulic oil from the first output pipe 201 to provide direct brake oil pressure P1 to drive a first brake B1; and a time difference pump mechanism 3, which has a time difference pump chamber 30, a The time difference pump piston 31, and a second output pipe 301 connected to the time difference pump chamber 30, the time difference pump piston 31 is arranged in the time difference pump chamber 30, and the time difference pump piston 31 is separated from the master pump piston 11 by a stroke distance _DT in the pressure output direction D before the master pump piston 11 slides under pressure, so that the master pump piston 11 moves along the The pressure output direction D pushes the time difference pump piston 31 to slide after sliding the stroke distance _DT , thereby pressurizing the time difference pump chamber 30, so that the time difference pump chamber 30 The hydraulic oil is output from the second output pipe 301 to provide the time difference brake oil pressure P2 to drive a second brake B2 with time difference.

In this embodiment, the hydraulic differential braking device 100 is applied to a braking system of a bicycle (not shown). The first brake operating member L1 connected to the first input pipe 101 is the right brake oil pressure handle of the bicycle, and the second brake operating member L1 connected to the second input pipe 102 is Part L2 is the left brake oil pressure handle of the bicycle, the first brake B1 connected to the first output pipe 201 is the rear wheel brake of the bicycle, and the second output The second brake B2 connected to the pipe 301 is the front wheel brake of the bicycle. Certainly, the present invention is not limited thereto, and the hydraulic time difference brake device 100 can also be connected with the brake operating member and the brake of the vehicle in other corresponding relationships, so as to be suitable for different vehicles.

Next, the detailed structure and operation method of the hydraulic differential braking device 100 of the present invention will be described with reference to FIGS. 1 to 3 .

As shown in Figure 1, the master pump chamber 10 of the master pump mechanism 1 is connected to the first brake operating member L1 and the first brake operating member L1 through the first input pipe 101 and the second input pipe 102 respectively. The second brake operating member L2, so no matter whether the first brake operating member L1 or the second brake operating member L2 is operated (press the oil pressure handle), the hydraulic oil H will enter the The master pump chamber 10, thereby pushing the master pump piston 11 (Figure 2). Through this structure, the problem of user's misoperation can be completely solved without changing the original structure of the braking system of the vehicle.

As shown in Figure 2, when the master pump piston 11 is pushed to slide along the pressure output direction D, the linked pump piston 21 is directly connected to the master pump piston 11. Move and slide along the pressure output direction D together with the master pump piston. Therefore, the sliding movement of the interlocking pump piston 21 along the pressure output direction D causes the volume of the interlocking pump chamber 20 to decrease and the pressure to rise, thereby passing through the first output pipe 201 provides direct brake oil pressure P1 to the first brake B1, thereby driving the first brake B1. Thus, for example the rear wheel of a bicycle starts braking immediately. Incidentally, there are many ways to achieve the direct linkage between the linked pump piston 21 and the master pump piston 11, for example, by connecting the linked pump piston 21 with the master pump piston 11 are arranged to keep abutting against each other, so that when the master pump piston 11 slides along the pressure output direction D, it will push the linked pump piston 21 . For another example, by setting the interlocking pump piston 21 and the master pump piston 11 to be integrated, the master pump piston 11 and the interlocking pump piston 21 will move integrally.

As shown in Figure 2, after the master pump piston 11 continues to be pushed and slides the stroke distance _DT , the master pump piston 11 will abut against the time difference pump piston 31, so that The time difference pump piston 31 is subsequently pushed by the master pump piston 11 , and slides along the pressure output direction D together with the master pump piston 11 . Therefore, the sliding movement of the time difference pump piston 31 along the pressure output direction D causes the volume of the time difference pump chamber 30 to decrease and the pressure to rise, and the pressure of the time difference pump chamber 30 to increase through the second output pipe 301 The above-mentioned second brake B2 provides time difference braking oil pressure P2, thereby driving the above-mentioned second brake B2. Therefore, there can be a time difference between the output of the differential braking oil pressure P2 and the output of the direct braking oil pressure P1, so that, for example, the front wheel of the bicycle starts to brake after a certain period of time after the rear wheel of the bicycle starts to brake.

As shown in Figures 1 to 3, the interlocking pump chamber 20 and the time difference pump chamber 30 are set so that the chamber radius r2 of the interlocking pump chamber 20 is equal to the time difference There is a predetermined chamber radius ratio between the chamber radii r3 of the pump chamber 30, so that the time difference braking oil pressure P2 and the direct braking oil pressure P1 correspond to the chamber radius ratio And have a predetermined brake oil pressure ratio, that is, the ratio of oil pressure. In this embodiment, the interlocking pump chamber 20 and the time difference pump chamber 30 have different chamber radii, and the chamber radius r3 of the time difference pump chamber 30 is larger than the The chamber radius r2 of the interlocking pump chamber 20 makes the time difference braking oil pressure P2 greater than the direct braking oil pressure P1. Therefore, for example, the front wheel braking speed (action speed) of a bicycle is faster than the rear wheel braking speed, so that the front wheel that starts braking later has a greater braking force than the rear wheel that starts braking earlier.

As shown in Figures 1 to 3, in this embodiment, the linked pump mechanism 2 further includes a first reset member 22 connected to the linked pump piston 21, and the first reset member 22 is set to normally push the interlocking pump piston 21 in a direction opposite to the pressure output direction D, so that the interlocking pump piston 21 will return to the position before slipping when no other external force is applied. location (ie, the location shown in Figure 1). The first return member 22 can be a spring, and pushes the interlocking pump piston 21 by elastic force.

Similarly, in this embodiment, the time difference pump mechanism 3 further includes a second reset member 32 connected to the time difference pump piston 31, and the second reset member 32 is set to normally face a direction opposite to the The direction of the pressure output direction D pushes the time difference pump piston 31, so that the time difference pump piston 31 will return to the position before slipping (that is, the position shown in FIG. 1 ) when no other external force is applied. ). The second return member 32 can be a spring, and pushes the time difference pump piston 31 by elastic force.

As shown in FIG. 1 to FIG. 3 , preferably, the master pump chamber 10 , the linked pump chamber 20 and the time difference pump chamber 30 are integrally connected chambers. In detail, the master pump chamber 10, the interlocking pump chamber 20 and the time difference pump chamber 30 are a single space located in a single housing 4, and are defined by the piston and the barrier wall. Separated, in this embodiment, the chamber radius r1 of the master pump chamber 10 is substantially equal to the chamber radius r2 of the interlocking pump chamber 20 and the chamber of the time difference pump chamber 30 sum of radii r3. Adopting such a structure of integrally connected chambers can make the overall volume of the hydraulic differential braking device 100 smaller, and can improve the reliability of the overall structure by reducing the connections between components.

Through the above structure, the hydraulic differential braking device 100 of the present invention can control different tires to perform braking actions with a time difference, so that the vehicle has a smoother and more stable ideal performance in braking. For example, when the present invention is applied to a bicycle, it can effectively avoid accidents such as the bicycle overturning or the rider being thrown off the vehicle body by inertial motion due to premature braking of the front wheel or sudden stop of the two wheels. When the present invention is applied to automobiles and locomotives, corresponding time-difference braking control can also be carried out in accordance with the respective types of vehicles, so as to realize smooth and stable braking.

The above descriptions and descriptions are only descriptions of preferred embodiments of the present invention, and those skilled in the art may make other modifications according to the scope of the patent application defined below and the above descriptions, but these modifications should still be part of the present invention. The spirit of the invention is within the scope of rights of the present invention.

Claims (9)

1. a kind of hydraulic type time difference brake device, it is characterised in that include：

Total pump machanism, with total pump chambers, total pump piston and is connected to the first input pipe of described total pump chambers and second defeated Enter pipe, described total pump piston is arranged at described master cylinder within the chamber sliding with the pressure change with described master cylinder within the chamber, The first described input pipe it is configured with the second described input pipe and respectively by first brake operating parts with second brake operating parts grasp Make so as to described master cylinder within the chamber input hydraulic pressure oil pressurising, so that described total pump piston is pressurized so as to along pressure output direction Sliding motion；

Pump machanism is interlocked, with interlocking pump chambers, interlock pump piston and be connected to the first outlet tube of described gearing pump chambers, The described pump piston that interlocks is arranged in described gearing pump chamber room and is directly linked in described total pump piston, with described Total pump piston together along described pressure output direction sliding motion so as to described gearing pump chambers of pressurizeing, make described gearing Pump chambers are from described first outlet tube output hydraulic pressure oil, there is provided directly brake oil pressure is driving the first brake；And

Time difference pump machanism, with time difference pump chambers, time difference pump piston and is connected to the second outlet tube of described time difference pump chambers, Described time difference pump piston is arranged in described time difference pump chamber room, and described time difference pump piston in described total pump piston not Before pressurized sliding with described total pump piston on described pressure output direction separately one stroke distance so that described master cylinder Piston promotes described time difference pump piston sliding Jing after the stroke distances described in sliding along described pressure output direction, so as to pressurize Described time difference pump chambers, make described time difference pump chambers from described the second outlet tube output hydraulic pressure oil, there is provided time difference brake fluid Pressure drives the second brake with the time difference,

Wherein described gearing pump chambers it is configured with described time difference pump chambers and make the chamber radius of described gearings pump chambers and Between the chamber radius of described time difference pump chambers have a predetermined chamber radius ratio so that described time difference brake oil pressure with Described chamber radius ratio is corresponded between described direct brake oil pressure so as to have a predetermined brake oil pressure ratio.

2. hydraulic type time difference brake device as claimed in claim 1, it is characterised in that described gearing pump chambers with it is described Time difference pump chambers have different chamber radius.

3. hydraulic type time difference brake device as claimed in claim 1, it is characterised in that the chamber of described time difference pump chambers half Chamber radius of the footpath more than described gearing pump chambers, so as to described time difference brake oil pressure is more than described direct brake oil pressure.

4. hydraulic type time difference brake device as claimed in claim 1, it is characterised in that described gearing pump machanism also includes the One return unit, is connected to described gearing pump piston, the first described return unit is configured and normality towards one in contrast to described pressure The direction of power outbound course promotes described gearing pump piston.

5. hydraulic type time difference brake device as claimed in claim 4, it is characterised in that the first described return unit is a spring.

6. hydraulic type time difference brake device as claimed in claim 1, it is characterised in that described time difference pump machanism also includes the Two return units, are connected to described time difference pump piston, the second described return unit is configured and normality towards one in contrast to described pressure The direction of power outbound course promotes described time difference pump piston.

7. hydraulic type time difference brake device as claimed in claim 6, it is characterised in that the second described return unit is a spring.

8. hydraulic type time difference brake device as claimed in claim 1, it is characterised in that described total pump chambers, described company Dynamic pump chambers and described time difference pump chambers are integrated connected chamber.

9. hydraulic type time difference brake device as claimed in claim 1, it is characterised in that described gearing pump machanism institute is to drive Dynamic the first described brake is a trailing wheel brake, described time difference pump machanism to the second brake described in driving For a front-wheel brake.