WO2017070977A1 - 油压式时差煞车装置 - Google Patents

油压式时差煞车装置 Download PDF

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Publication number
WO2017070977A1
WO2017070977A1 PCT/CN2015/093834 CN2015093834W WO2017070977A1 WO 2017070977 A1 WO2017070977 A1 WO 2017070977A1 CN 2015093834 W CN2015093834 W CN 2015093834W WO 2017070977 A1 WO2017070977 A1 WO 2017070977A1
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Prior art keywords
time difference
pump
brake
chamber
pump chamber
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PCT/CN2015/093834
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English (en)
French (fr)
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张瑞龙
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张瑞龙
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Publication of WO2017070977A1 publication Critical patent/WO2017070977A1/zh

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/26—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force characterised by producing differential braking between front and rear wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62L—BRAKES SPECIALLY ADAPTED FOR CYCLES
    • B62L3/00—Brake-actuating mechanisms; Arrangements thereof
    • B62L3/08—Mechanisms specially adapted for braking more than one wheel

Definitions

  • the present invention relates to a brake control device, and more particularly to a hydraulic time difference brake device.
  • the bicycle braking device of the general bicycle presses the brake handle by the rider to drive the brake device to brake the front and rear wheels of the bicycle.
  • one brake handle of the bicycle is correspondingly driven by a brake device
  • the right brake handle is a brake device that controls the rear wheel
  • the left brake handle is linked to the brake device that controls the front wheel.
  • it is usually necessary to drive the brake of the rear wheel first, and then drive the brake of the front wheel.
  • inadvertent manipulation of the brakes of the front and rear wheels is inevitable, resulting in accidents such as bicycle overturning or slipping.
  • a hydraulic type time difference braking device comprising: a master pump mechanism having a master pump chamber, a master pump piston, and a total pump chamber connected thereto a first input pipe and a second input pipe of the chamber, wherein the master pump piston is disposed in the total pump chamber to slip with a pressure change in the total pump chamber, the first input The tube and the second input tube are disposed to be respectively operated by the first brake operating member and the second brake operating member to pressurize the input hydraulic oil into the total pump chamber to cause the total pump piston to be subjected to Pressing to slide along the direction of pressure output;
  • a linked pump mechanism having a linked pump chamber, a linked pump piston, and a first output tube connected to the interlocking pump chamber, wherein the linked pump piston is disposed in the linked pump chamber Indoorly and directly coupled to the master pump piston to pressurize the associated pump chamber with the total pump piston sliding together in the direction of the pressure output to cause the connection
  • the pumping chamber outputs hydraulic oil from the first output pipe to provide direct brake oil pressure to drive the first brake; and a time difference pump mechanism having a time difference pump chamber, a time difference pump piston, and a time difference connected thereto a second output tube of the pump chamber, said time a differential pump piston is disposed in the time difference pump chamber, and the time difference pump piston is spaced apart from the total pump piston in the pressure output direction before the total pump piston is uncompressed a stroke distance such that the master pump piston slides the stroke distance in the pressure output direction to push the time difference pump piston to slip, thereby pressurizing the time difference pump chamber
  • the time difference pump chamber outputs hydraulic oil from the second output pipe, and provides
  • the linked pump chamber and the time difference pump chamber have different chamber radii.
  • the chamber radius of the time difference pump chamber is larger than the chamber radius of the interlocking pump chamber, so that the time difference brake oil pressure is greater than the direct brake oil pressure.
  • the linked pump mechanism further includes a first resetting member coupled to the linked pump piston, and the first resetting member is disposed to be normally opposite to the The direction of the pressure output direction pushes the associated pump piston.
  • the first reset member is a spring
  • the time difference pump mechanism further includes a second reset member coupled to the time difference pump piston, and the second reset member is disposed to be normally opposite to the pressure output The direction of the direction pushes the time difference pump piston.
  • the second reset member is a spring
  • the main pump chamber, the linked pump chamber, and the time difference pump chamber are integrally connected chambers.
  • the first brake device used by the linkage pump mechanism is a rear wheel brake device, and the second brake device used by the time difference pump mechanism is driven.
  • the device is a front wheel brake.
  • the invention can control different tires to perform the braking action with time difference, so that the vehicle has a smoother and stable ideal performance on the brake.
  • the present invention when the present invention is applied to a bicycle, it is possible to effectively avoid the accident that the bicycle is overturned due to premature wheeling of the front wheel or sudden stop of the two wheels, or the rider is moved away from the vehicle body by inertial motion.
  • the present invention when the present invention is applied to an automobile or a locomotive, it is also possible to perform corresponding time difference braking control in accordance with the respective vehicle types to achieve a smooth and stable braking.
  • the ratio of the ratio of the brake oil pressure outputted is adjusted by adjusting the radius ratio between each chamber (the linkage pump chamber and the time difference pump chamber) to realize the application to different tires. The control of the brake force.
  • FIG. 1 is a schematic view showing a hydraulic type time difference braking device according to an embodiment of the present invention
  • Figure 2 is a schematic view showing the continuous operation of the hydraulic type time difference braking device of Figure 1;
  • Fig. 3 is a schematic view showing the continuous operation of the hydraulic type time difference brake device of Fig. 1.
  • a hydraulic type time difference braking device 100 includes: a master pump mechanism 1 having a master pump chamber 10, a master pump piston 11, and a connection thereto. a first input pipe 101 and a second input pipe 102 of the main pump chamber 10, the total pump piston 11 being disposed in the main pump chamber 10 to be in the total pump chamber 10
  • the pressure of the first input pipe 101 and the second input pipe 102 are set to be respectively operated by a first brake operating member L1 and a second brake operating member L2 to The input hydraulic oil H is pressurized in the total pump chamber 10 so that the total pump piston 11 is pressed to slide in a pressure output direction D;
  • a linkage pump mechanism 2 has a linkage pump chamber 20 a pumping piston 21, and a first output pipe 201 connected to the interlocking pump chamber 20, the interlocking pump piston 21 being disposed in the interlocking pump chamber 20 and directly Cooperating with the master pump piston 11 to press the joint motion along the pressure output direction D along with the master pump piston 11 to press
  • time difference pump piston 31 is spaced apart from the total pump piston 11 by a stroke distance D T in the pressure output direction D before the total pump piston 11 is not subjected to the pressure slip. Pressing the total pump piston 11 in the pressure output direction D by sliding the stroke distance D T to push the time difference pump piston 31 to slip, thereby pressurizing the time difference pump chamber 30,
  • the time difference pump chamber 30 is caused to output hydraulic oil from the second output pipe 301, and the time difference brake oil pressure P2 is provided to drive a second brake B2 with a time difference.
  • the hydraulic time difference braking device 100 is applied to a braking system of a bicycle (not shown).
  • the first brake operating member L1 to which the first input pipe 101 is connected is the right brake hydraulic pressure handle of the bicycle, and the second brake operation of the second input pipe 102 is connected.
  • the L2 is the left brake hydraulic handle of the bicycle
  • the first brake B1 to which the first output pipe 201 is connected is the rear rim of the bicycle.
  • the second brake B2 to which the second output pipe 301 is connected is the front wheel brake of the bicycle.
  • the hydraulic time difference braking device 100 may also be connected to the braking operation member and the brake device of the vehicle in other correspondences to be applicable to different vehicles.
  • the total pump chamber 10 of the master pump mechanism 1 is connected to 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 whether the first brake operating member L1 or the second brake operating member L2 is operated (pressing the hydraulic handle), the hydraulic oil H enters the The main pump chamber 10, thereby pushing the master pump piston 11 (Fig. 2).
  • the master pump piston 11 As shown in FIG. 2, after the master pump piston 11 continues to be pushed and the stroke distance D T is slipped, the master pump piston 11 abuts the time difference pump piston 31, so that The time difference pump piston 31 is subsequently pushed by the total pump piston 11 to be slidably moved along the pressure output direction D together with the total pump piston 11. Therefore, the sliding movement of the time difference pump piston 31 in the pressure output direction D causes the volume of the time difference pump chamber 30 to become smaller and the pressure to rise, and the second output pipe 301 is opposed to the second output pipe 301.
  • the second brake device B2 provides a time difference brake hydraulic pressure P2 to drive the second brake device B2. Therefore, it is possible to have a time difference between the output of the time difference brake hydraulic pressure P2 and the output of the direct brake hydraulic pressure P1, so that, for example, the front wheel of the bicycle starts to brake after the bicycle rear wheel starts to brake for a while.
  • the interlocking pump chamber 20 and the time difference pump chamber 30 are disposed such that the chamber radius r2 of the interlocking pump chamber 20 is different from the time difference.
  • the chamber radius r3 of the pump chamber 30 has a predetermined chamber radius ratio such that the time difference brake oil pressure P2 and the direct brake oil pressure P1 correspond to the chamber radius It has a predetermined brake oil pressure ratio, that is, the oil pressure ratio.
  • the linked 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 greater than
  • the chamber radius r2 of the pump chamber 20 is linked such that the time difference brake oil pressure P2 is greater than the direct brake oil pressure P1. Therefore, for example, the front wheel braking speed (motion speed) of the bicycle is made faster than the rear wheel braking speed, so that it is possible to achieve a larger braking force for the front wheel that starts the braking later than the rear wheel that starts the braking earlier.
  • the linked pump mechanism 2 further includes a first resetting member 22 coupled to the linked pump piston 21, and the first resetting 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 linked pump piston 21 is reset to return to the front before slipping when not subjected to other external forces.
  • Position ie, the position shown in Figure 1).
  • the first returning member 22 can be a spring, and the linked pump piston 21 is pushed by the elastic force.
  • 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 be normally opposite to The direction of the pressure output direction D pushes the time difference pump piston 31, so that the time difference pump piston 31 is reset back to the position before the slip when it is not subjected to other external force (ie, the position shown in FIG. 1). ).
  • the second reset member 32 can be a spring, and the time difference pump piston 31 is pushed by the elastic force.
  • the total pump chamber 10, the linked pump chamber 20, and the time difference pump chamber 30 are integrally connected chambers.
  • the main pump chamber 10, the linked pump chamber 20 and the time difference pump chamber 30 are a single space in a single housing 4, and are separated by a piston and a blocking wall.
  • the chamber radius r1 of the total pump chamber 10 is substantially equal to the chamber radius r2 of the linked pump chamber 20 and the chamber of the time difference pump chamber 30.
  • the hydraulic type time difference braking device 100 of the present invention can control different tires to perform a braking operation with a time difference, so that the vehicle has a smoother and stable ideal performance on the brake.
  • the present invention when the present invention is applied to a bicycle, it is possible to effectively avoid the accident that the bicycle is overturned due to premature wheeling of the front wheel or sudden stop of the two wheels, or the rider is moved away from the vehicle body by inertial motion.
  • the present invention is applied to an automobile or a locomotive, it is also possible to perform corresponding time difference braking control in accordance with the respective vehicle types to achieve a smooth and stable braking.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Regulating Braking Force (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

一种油压式时差煞车装置，包括总泵机构（1）、连动泵机构（2）及时差泵机构（3），其中连动泵机构（2）的连动泵活塞（21）直接连动于总泵机构（1）的总泵活塞（11），时差泵机构（3）的时差泵活塞（31）则与总泵活塞（11）相间隔一行程距离，以在总泵机构（1）受到启动煞车操作时，连动泵机构（2）会直接动作，以提供一直接煞车油压驱动第一煞车器，时差泵机构（3）则在经过一预定时间后动作，以提供一时差煞车油压以时差驱动第二煞车器。

Description

油压式时差煞车装置 技术领域
本发明涉及一种煞车控制装置，特别是涉及一种油压式时差煞车装置。
背景技术
在涉及汽车、机车、自行车等各种车辆的煞车控制中，常常会有需要进行具有顺序输出的煞车控制，其用意在于使得不同轮胎的煞车动作之间产生一时间差，令车辆在煞车上具有更平稳、安定的理想表现。
以自行车的煞车控制为例，一般自行车的煞车装置通过骑乘者按压煞车把手以驱使煞车器进行自行车的前后轮的煞车。通常自行车的一个煞车把手为对应驱动一个煞车器，右煞车把手为连动于控制后轮的煞车器，左煞车把手则连动于控制前轮的煞车器。为了在保持平稳、安定的状态下使自行车完成煞车，在煞车时通常必须先驱动后轮的煞车器，后再驱动前轮的煞车器。然而，当遇到危急状况时，难免发生对前后轮的煞车器的误操纵，而造成自行车翻覆或打滑等意外发生。
发明内容
因此，本发明的目的使提供一种油压式时差煞车装置，能够使车辆的不同轮胎进行具有时间差的煞车动作。
本发明为解决现有技术的问题所采用的技术手段是提供一种油压式时差煞车装置，包含：总泵机构，具有总泵腔室、总泵活塞、及连接于所述的总泵腔室的第一输入管及第二输入管，所述的总泵活塞设置于所述的总泵腔室内以随着所述的总泵腔室内的压力变化而滑移，所述的第一输入管与所述的第二输入管经设置而分别受第一煞车操作件与第二煞车操作件操作从而对所述的总泵腔室内输入液压油充压，以使所述的总泵活塞受压从而沿压力输出方向滑移运动；
连动泵机构，具有连动泵腔室、连动泵活塞、及连接于所述的连动泵腔室的第一输出管，所述的连动泵活塞设置于所述的连动泵腔室内并且直接连动于所述的总泵活塞，以随着所述的总泵活塞一起沿所述的压力输出方向滑移运动从而加压所述的连动泵腔室，使所述的连动泵腔室自所述的第一输出管输出液压油，提供直接煞车油压以驱动第一煞车器；以及时差泵机构，具有时差泵腔室、时差泵活塞、及连接于所述的时差泵腔室的第二输出管，所述的时 差泵活塞设置于所述的时差泵腔室内，并且所述的时差泵活塞在所述的总泵活塞未受压滑移前与所述的总泵活塞在所述的压力输出方向上相间隔一行程距离，以使所述的总泵活塞沿所述的压力输出方向经滑移所述的行程距离后推动所述的时差泵活塞滑移，从而加压所述的时差泵腔室，使所述的时差泵腔室自所述的第二输出管输出液压油，提供时差煞车油压以时差驱动第二煞车器，其中所述的连动泵腔室与所述的时差泵腔室经设置而使所述的连动泵腔室的腔室半径与所述的时差泵腔室的腔室半径之间具有一预定的腔室半径比，从而使所述的时差煞车油压与所述的直接煞车油压之间相应于所述的腔室半径比从而具有一预定的煞车油压比。
在本发明的一实施例中，所述的连动泵腔室与所述的时差泵腔室具有不同的腔室半径。
在本发明的一实施例中，所述的时差泵腔室的腔室半径大于所述的连动泵腔室的腔室半径，从而所述的时差煞车油压大于所述的直接煞车油压。
在本发明的一实施例中，所述的连动泵机构还包括第一复位件，连接于所述的连动泵活塞，所述的第一复位件经设置而常态朝一相反于所述的压力输出方向的方向推动所述的连动泵活塞。
在本发明的一实施例中，所述的第一复位件为一弹簧。
在本发明的一实施例中，所述的时差泵机构还包括第二复位件，连接于所述的时差泵活塞，所述的第二复位件经设置而常态朝一相反于所述的压力输出方向的方向推动所述的时差泵活塞。
在本发明的一实施例中，所述的第二复位件为一弹簧。
在本发明的一实施例中，所述的总泵腔室、所述的连动泵腔室及所述的时差泵腔室为一体相连的腔室。
在本发明的一实施例中，所述的连动泵机构所用以驱动的所述的第一煞车器为一后轮煞车器，所述的时差泵机构所用以驱动的所述的第二煞车器为一前轮煞车器。
通过本发明所采用的技术手段，本发明能够控制不同轮胎进行具有时间差的煞车动作，使车辆在煞车上具有更平稳、安定的理想表现。例如，本发明应用于自行车时，能够有效避免自行车因前轮过早煞车或两轮骤然停止而引起的翻覆或骑乘者被惯性运动甩离车体等意外。本发明应用于汽车、机车时，也能够配合各自车辆类型而进行对应的时间差煞车控制，以实现平稳、安定的煞车。此外，在本发明的实施例中，利用调整各腔室(连动泵腔室与时差泵腔室)之间的半径比而改变所输出的煞车油压的比例，以实现对于不同轮胎所施予的煞车力道的控制。
附图说明
图1为显示根据本发明的一实施例的油压式时差煞车装置的示意图；
图2为显示图1的油压式时差煞车装置的连续动作的示意图；
图3为显示图1的油压式时差煞车装置的连续动作的示意图。
【符号说明】
100              油压式时差煞车装置
1                总泵机构
10               总泵腔室
101              第一输入管
102              第二输入管
11               总泵活塞
2                连动泵机构
20               连动泵腔室
201              第一输出管
21               连动泵活塞
22               第一复位件
3                时差泵机构
30               时差泵腔室
301              第二输出管
31               时差泵活塞
32               第二复位件
4                壳体
B1               第一煞车器
B2               第二煞车器
D                压力输出方向
DT               行程距离
H                液压油
L1               第一煞车操作件
L2               第二煞车操作件
P1               直接煞车油压
P2               时差煞车油压
r1               腔室半径
r2               腔室半径
r3               腔室半径
具体实施方式
以下根据图1至图3，说明本发明的实施方式。所述的说明并非为限制本发明的实施方式，而为本发明的实施例的一种。
如图1所示，依据本发明的一实施例的一油压式时差煞车装置100包含：一总泵机构1，具有一总泵腔室10、一总泵活塞11、及连接于所述的总泵腔室10的一第一输入管101及一第二输入管102，所述的总泵活塞11设置于所述的总泵腔室10内以随着所述的总泵腔室10内的压力变化而滑移，所述的第一输入管101与所述的第二输入管102经设置而分别受一第一煞车操作件L1与一第二煞车操作件L2操作从而对所述的总泵腔室10内输入液压油H充压，以使所述的总泵活塞11受压从而沿一压力输出方向D滑移运动；一连动泵机构2，具有一连动泵腔室20、一连动泵活塞21、及一连接于所述的连动泵腔室20的第一输出管201，所述的连动泵活塞21设置于所述的连动泵腔室20内并且直接连动于所述的总泵活塞11，以随着所述的总泵活塞11一起沿所述的压力输出方向D滑移运动从而加压所述的连动泵腔室20，使所述的连动泵腔室20自所述的第一输出管201输出液压油，提供直接煞车油压P1而驱动一第一煞车器B1；以及一时差泵机构3，具有一时差泵腔室30、一时差泵活塞31、及一连接于所述的时差泵腔室30的第二输出管301，所述的时差泵活塞31设置于所述的时差泵腔室30内，并且所述的时差泵活塞31在所述的总泵活塞11未受压滑移前与所述的总泵活塞11在所述的压力输出方向D上相间隔一行程距离DT，以使所述的总泵活塞11沿所述的压力输出方向D经滑移所述的行程距离DT后推动所述的时差泵活塞31滑移，从而加压所述的时差泵腔室30，使所述的时差泵腔室30自所述的第二输出管301输出液压油，提供时差煞车油压P2以时差驱动一第二煞车器B2。
在本实施例中，所述的油压式时差煞车装置100为应用于一自行车(图未示)的煞车系统中。所述的第一输入管101所连接的所述的第一煞车操作件L1为所述的自行车的右煞车油压把手，所述的第二输入管102所连接的所述的第二煞车操作件L2为所述的自行车的左煞车油压把手，所述的第一输出管201所连接的所述的第一煞车器B1为所述的自行车的后轮煞 车器，所述的第二输出管301所连接的所述的第二煞车器B2为所述的自行车的前轮煞车器。当然，本发明并不限于此，所述的油压式时差煞车装置100也可采其它的对应关系与车辆的煞车操作件及煞车器连接，以适用于不同的车辆。
接着，将参照图1至图3说明本发明的油压式时差煞车装置100的细部结构及作动方式。
如图1所示，所述的总泵机构1的总泵腔室10分别通过所述的第一输入管101与所述的第二输入管102连接于所述的第一煞车操作件L1与所述的第二煞车操作件L2，因此无论是所述的第一煞车操作件L1或是所述的第二煞车操作件L2受到操作(按压油压把手)，液压油H皆会进入所述的总泵腔室10，从而推动所述的总泵活塞11(图2)。通过该结构，能够在不改变车辆的原有的煞车系统架构下，彻底解决使用者的误操作问题。
如图2所示，在所述的总泵活塞11受推动而沿所述的压力输出方向D滑移运动时，所述的连动泵活塞21通过与所述的总泵活塞11的直接连动而随着所述的总泵活塞一起沿所述的压力输出方向D滑移运动。从而，所述的连动泵活塞21沿所述的压力输出方向D的滑移运动使所述的连动泵腔室20的体积变小、压力上升，从而透过所述的第一输出管201对所述的第一煞车器B1提供直接煞车油压P1，从而驱动所述的第一煞车器B1。因此，使例如自行车的后轮立即开始煞车。附带一提，达成所述的连动泵活塞21与所述的总泵活塞11的直接连动的方式有许多种，例如，通过将所述的连动泵活塞21与所述的总泵活塞11设置为保持相互抵接，则使得所述的总泵活塞11沿所述的压力输出方向D滑移运动时会推动所述的连动泵活塞21。又例如，通过将所述的连动泵活塞21与所述的总泵活塞11设置为结合成一体，则使得所述的总泵活塞11与所述的连动泵活塞21会一体地运动。
如图2所示，在所述的总泵活塞11继续受推动而经滑移所述的行程距离DT后，所述的总泵活塞11会与所述的时差泵活塞31相抵接，使所述的时差泵活塞31后续会受所述的总泵活塞11的推动，而与所述的总泵活塞11一起沿所述的压力输出方向D滑移运动。从而，所述的时差泵活塞31沿所述的压力输出方向D的滑移运动使所述的时差泵腔室30的体积变小、压力上升，而通过所述的第二输出管301对所述的第二煞车器B2提供时差煞车油压P2，从而驱动所述的第二煞车器B2。因此，能够让时差煞车油压P2的输出与直接煞车油压P1的输出之间具有一时间差，而使例如自行车的前轮在自行车的后轮开始煞车一段时间后才开始煞车。
如图1至图3所示，所述的连动泵腔室20与所述的时差泵腔室30经设置而使所述的连动泵腔室20的腔室半径r2与所述的时差泵腔室30的腔室半径r3之间具有一预定的腔室半径比，从而使所述的时差煞车油压P2与所述的直接煞车油压P1之间相应于所述的腔室半径 比而具有一预定的煞车油压比，即，油压大小比例。在本实施例中，所述的连动泵腔室20与所述的时差泵腔室30具有相异的腔室半径，且所述的时差泵腔室30的腔室半径r3大于所述的连动泵腔室20的腔室半径r2，使所述的时差煞车油压P2大于所述的直接煞车油压P1。因此，使例如自行车的前轮煞车速度(动作速度)比后轮煞车速度快，从而可以达到使较晚开始煞车的前轮比起较早开始煞车的后轮有更大的煞车力道。
如图1至图3所示，在本实施例中，所述的连动泵机构2还包括一第一复位件22，连接于所述的连动泵活塞21，所述的第一复位件22经设置而常态朝一相反于所述的压力输出方向D的方向推动所述的连动泵活塞21，使所述的连动泵活塞21在未受其它外力时会复位回到滑移前的位置(即，图1所示的位置)。所述的第一复位件22可为一弹簧，而通过弹力推动所述的连动泵活塞21。
相似地，在本实施例中，所述的时差泵机构3还包括一第二复位件32，连接于所述的时差泵活塞31，所述的第二复位件32经设置而常态朝一相反于所述的压力输出方向D的方向推动所述的时差泵活塞31，使所述的时差泵活塞31在未受其它外力时会复位回到滑移前的位置(即，图1所示的位置)。所述的第二复位件32可为一弹簧，而通过弹力推动所述的时差泵活塞31。
如图1至图3所示，较佳地，所述的总泵腔室10、所述的连动泵腔室20及所述的时差泵腔室30为一体相连的腔室。详细而言，所述的总泵腔室10、所述的连动泵腔室20及所述的时差泵腔室30为位于单一个壳体4内的单一空间，而由活塞及阻隔壁所相分隔，在本实施例中，所述的总泵腔室10的腔室半径r1实质等于所述的连动泵腔室20的腔室半径r2与所述的时差泵腔室30的腔室半径r3的和。采用此种一体相连的腔室的结构，可以使油压式时差煞车装置100的整体体积更小，并且能通过减少构件之间的连接而提升整体结构可靠度。
通过上述结构，本发明的油压式时差煞车装置100能够控制不同轮胎进行具有时间差的煞车动作，使车辆在煞车上具有更平稳、安定的理想表现。例如，本发明应用于自行车时，能够有效避免自行车因前轮过早煞车或两轮骤然停止而引起的翻覆或骑乘者被惯性运动甩离车体等意外。本发明应用于汽车、机车时，也能够配合各自车辆类型而进行对应的时间差煞车控制，以实现平稳、安定的煞车。
以上的叙述以及说明仅为本发明的较佳实施例的说明，对于本领域技术人员当可依据以下所界定申请专利范围以及上述的说明而作其他的修改，但这些修改仍应是为本发明的发明精神而在本发明的权利范围中。

Claims (9)

  1. 一种油压式时差煞车装置，其特征在于，包含：
    总泵机构，具有总泵腔室、总泵活塞、及连接于所述的总泵腔室的第一输入管及第二输入管，所述的总泵活塞设置于所述的总泵腔室内以随着所述的总泵腔室内的压力变化而滑移，所述的第一输入管与所述的第二输入管经设置而分别受第一煞车操作件与第二煞车操作件操作从而对所述的总泵腔室内输入液压油充压，以使所述的总泵活塞受压从而沿压力输出方向滑移运动；
    连动泵机构，具有连动泵腔室、连动泵活塞、及连接于所述的连动泵腔室的第一输出管，所述的连动泵活塞设置于所述的连动泵腔室内并且直接连动于所述的总泵活塞，以随着所述的总泵活塞一起沿所述的压力输出方向滑移运动从而加压所述的连动泵腔室，使所述的连动泵腔室自所述的第一输出管输出液压油，提供直接煞车油压以驱动第一煞车器；以及
    时差泵机构，具有时差泵腔室、时差泵活塞、及连接于所述的时差泵腔室的第二输出管，所述的时差泵活塞设置于所述的时差泵腔室内，并且所述的时差泵活塞在所述的总泵活塞未受压滑移前与所述的总泵活塞在所述的压力输出方向上相间隔一行程距离，以使所述的总泵活塞沿所述的压力输出方向经滑移所述的行程距离后推动所述的时差泵活塞滑移，从而加压所述的时差泵腔室，使所述的时差泵腔室自所述的第二输出管输出液压油，提供时差煞车油压以时差驱动第二煞车器，
    其中所述的连动泵腔室与所述的时差泵腔室经设置而使所述的连动泵腔室的腔室半径与所述的时差泵腔室的腔室半径之间具有一预定的腔室半径比，从而使所述的时差煞车油压与所述的直接煞车油压之间相应于所述的腔室半径比从而具有一预定的煞车油压比。
  2. 如权利要求1所述的油压式时差煞车装置，其特征在于，所述的连动泵腔室与所述的时差泵腔室具有不同的腔室半径。
  3. 如权利要求1所述的油压式时差煞车装置，其特征在于，所述的时差泵腔室的腔室半径大于所述的连动泵腔室的腔室半径，从而所述的时差煞车油压大于所述的直接煞车油压。
  4. 如权利要求1所述的油压式时差煞车装置，其特征在于，所述的连动泵机构还包括第一复位件，连接于所述的连动泵活塞，所述的第一复位件经设置而常态朝一相反于所述的压力输出方向的方向推动所述的连动泵活塞。
  5. 如权利要求4所述的油压式时差煞车装置，其特征在于，所述的第一复位件为一弹簧。
  6. 如权利要求1所述的油压式时差煞车装置，其特征在于，所述的时差泵机构还包括第 二复位件，连接于所述的时差泵活塞，所述的第二复位件经设置而常态朝一相反于所述的压力输出方向的方向推动所述的时差泵活塞。
  7. 如权利要求6所述的油压式时差煞车装置，其特征在于，所述的第二复位件为一弹簧。
  8. 如权利要求1所述的油压式时差煞车装置，其特征在于，所述的总泵腔室、所述的连动泵腔室及所述的时差泵腔室为一体相连的腔室。
  9. 如权利要求1所述的油压式时差煞车装置，其特征在于，所述的连动泵机构所用以驱动的所述的第一煞车器为一后轮煞车器，所述的时差泵机构所用以驱动的所述的第二煞车器为一前轮煞车器。
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