WO2019128013A1 - 一种液压走行***用反向制动控制阀 - Google Patents

一种液压走行***用反向制动控制阀 Download PDF

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Publication number
WO2019128013A1
WO2019128013A1 PCT/CN2018/084988 CN2018084988W WO2019128013A1 WO 2019128013 A1 WO2019128013 A1 WO 2019128013A1 CN 2018084988 W CN2018084988 W CN 2018084988W WO 2019128013 A1 WO2019128013 A1 WO 2019128013A1
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WIPO (PCT)
Prior art keywords
valve
pressure
hydraulic
oil
way solenoid
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PCT/CN2018/084988
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English (en)
French (fr)
Inventor
熊文辉
张峥明
任剡
汪宏
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中国铁建高新装备股份有限公司
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Publication of WO2019128013A1 publication Critical patent/WO2019128013A1/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
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • 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
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/28—Valves specially adapted therefor
    • 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
    • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
    • B60T15/02—Application and release valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components

Definitions

  • the invention relates to a hydraulic control valve, in particular to a reverse brake control valve for a hydraulic running system, belonging to the technical field of hydraulic control.
  • the maximum running speed is usually 80-100km/h
  • its running drive has three common transmission modes: hydraulic mechanical transmission, hydraulic transmission and electric transmission.
  • the hydraulic transmission travel system also known as the hydraulic travel system, is usually driven by a closed hydraulic circuit consisting of a hydraulic variable pump and a variable motor.
  • the output flow of the pump is controlled by an electronically controlled or hydraulically controlled travel handle to drive the hydraulic motor mounted on the axle.
  • the hydraulic motor then drives the wheels to rotate to achieve the vehicle.
  • the vehicle speed is adjusted by controlling the displacement of the variable pump, and the system working pressure varies with the operating conditions to meet the driving force requirements.
  • the hydraulically-traveled vehicle will be turned into a pump working condition when the running handle is quickly pulled back for deceleration or running on a long ramp.
  • the driving circuit With the motor working condition, the driving circuit generates the reverse hydraulic braking force through the hydraulic motor, and the hydraulic pump will reverse the engine. If no measures are taken, when the reverse drag pressure is too high, that is, the reverse hydraulic braking force is too large, It may cause the engine to fly, or damage the hydraulic components of the running drive circuit, affecting the normal running function of the whole vehicle, and even threatening the operation safety of the railway line.
  • the Chinese invention patent application with the application number 201510364468.3 relates to a control device for an actuator with a brake valve, comprising an oil inlet passage, an oil return passage, a three-position four-way reversing valve, and the three-position four-way reversing valve
  • the valve is provided with a first port connected to the oil inlet passage, a second port connected to the oil return passage, and a third port and a fourth port connected to the actuator, and the oil inlet passage and the oil return passage are further provided.
  • the control device can be used for emergency braking in the operating state of the actuator without impact. However, it still cannot solve the braking problem of large road maintenance machinery.
  • the invention provides a reverse brake control valve for a hydraulic running system, and is particularly suitable for reverse braking control of a hydraulic running system of a large road maintenance machine.
  • the reverse brake control valve for the hydraulic running system of the present invention comprises a valve body, wherein the valve body is provided with a two-position three-way solenoid valve A and a two-position three-way solenoid valve B, the two-position three-way solenoid valve A and two positions
  • the three-way solenoid valve B includes an orifice, the two-position three-way solenoid valve A is connected upstream of the oil inlet port MB, and the two-position three-way solenoid valve B is connected upstream to the oil inlet port MA; the two-position three-way electromagnetic
  • the valve A is connected downstream of the sequence valve A, and the downstream of the sequence valve A is connected to an output port XIV through a check valve C and a check valve D.
  • the two-position three-way solenoid valve B is connected downstream with a sequence valve B, and the sequence valve B Downstream, one output port XIII is connected to each of the check valve A and the check valve B, and an output port XIII downstream of the check valve A and an output port XIV downstream of the check valve C are further equipped with two
  • the two-way solenoid valve B is further provided with a two-position two-way solenoid valve A between the output port XIII downstream of the check valve B and the output port XIV downstream of the check valve D, the sequence valve A A shuttle valve is also connected between the downstream and the downstream of the sequence valve B, and the shuttle valve is connected to the relief valve.
  • the pressure of the relief valve ranges from 40 to 50 bar
  • the outlet of the shuttle valve installed between the sequence valve A and the oil passage after the sequence valve B in the two branches is connected to the relief valve.
  • the pressurized oil reaches the inlet of the overflow valve through the shuttle valve, and begins to overflow when the pressure of the pressure oil reaches the set pressure of the relief valve, thereby
  • the maximum pressure of the pressurized oil after the sequence valve A and the sequence valve B are limited does not exceed the set pressure range of the relief valve by 40-50 bar.
  • oil inlets MA and MB are connected to the main ports A and B of the hydraulic traveling system drive circuit, respectively.
  • the relief valve is also connected to the K pressure tap to detect its working pressure.
  • sequence valve A is connected to the K1 pressure tap to detect its working pressure.
  • sequence valve B is connected to the K2 pressure tap to detect its working pressure.
  • the orifice of the two-position three-way solenoid valve A is a fixed orifice A.
  • the orifice of the two-position three-way solenoid valve B is a fixed orifice B.
  • the fixed orifice A has a diameter of 2-3 mm.
  • the fixed orifice B has a diameter of 2-3 mm.
  • valve body includes a eye nut for transportation.
  • the set pressure of the sequence valve is the maximum pressure of the hydraulic reverse brake, which can be adjusted according to the requirements of the entire vehicle.
  • the set pressure of the sequence valve ranges from 90 to 120 bar.
  • the relief valve employs a threaded insert.
  • each hydraulic component and the oil passage in the valve body form a parallel branch, the composition of each branch is basically the same, starting from the inlet port MA or MB, through the two-position three-way solenoid valve, fixed orifice, sequence valve , check valve to output port XIII or XIV.
  • the two-position three-way solenoid valve A or the two-position three-way solenoid valve B passes the power loss or the power logic to control whether the input port and the sequence valve are connected or disconnected, when the two-position three-way solenoid valve A or two After the three-way solenoid valve B is de-energized, when the pressure of the inlet of the sequence valve A or the sequence valve B reaches its set opening pressure, the sequence valve A or the sequence valve B will be turned on, and the pressure oil passes through the sequence valve A or B and The latter check valve A or check valve B or check valve C or check valve D reaches the output port XIII or XIV, so that the variable mechanism of the hydraulic pump automatically adjusts the hydraulic pump, and the fixed orifice in the path A or fixed orifice B limits the flow through the sequence valve.
  • the check valve ensures that the pressure oil can only flow out of the output port XIII or XIV, while ensuring that the two sets of output ports XIII or XIV are independent and do not affect each other, thereby enabling control of one pump or simultaneous control of both pumps.
  • the closed hydraulic drive circuit realizes the required rotational speed and working pressure through the flow matching of the variable pump and the variable motor. Under normal circumstances, the hydraulic pump output flow drives the motor to rotate, and establishes a certain pressure between the hydraulic pump outlet and the motor inlet. The output flow of the hydraulic pump determines the speed of the motor.
  • the flow rate of the hydraulic pump output will be less than the flow required by the hydraulic motor to maintain the rotational speed, and the flow output of the hydraulic motor is greater than the flow drawn by the hydraulic pump.
  • the hydraulic motor will become the pump working condition
  • the hydraulic pump will become the motor working condition
  • the hydraulic motor will drive the hydraulic pump to rotate; or when the displacement of the hydraulic pump is constant and the speed of the hydraulic motor is rapidly increased, the output of the hydraulic pump
  • the flow rate is also less than the flow drawn by the hydraulic motor.
  • the flow output from the hydraulic motor is greater than the flow drawn by the hydraulic pump.
  • the hydraulic pump will become the motor operating condition and the hydraulic motor will become the pump operating condition.
  • the above technical solution can be connected to the high-voltage side and the low-pressure side of the main circuit of the traveling system through the oil inlets MA and MB, and then the oil on the low-pressure side can be controlled by controlling the power loss of the two-position three-way electromagnetic reversing valve.
  • the liquid reaches the sequence valve through the two-position three-way solenoid valve and the fixed orifice, and the oil on the high pressure side and the sequence valve are not connected.
  • the pump and motor of the running circuit The working conditions change, the pressure on the high pressure side and the low pressure side of the system also changes.
  • the pressure on the original low pressure side rises, and the running drive circuit generates reverse hydraulic braking force.
  • the speed of the whole vehicle will gradually decrease or the speed will no longer increase.
  • the sequence valve is turned on, and the displacement of the pressure oil into the variable control cylinder of the hydraulic pump automatically increases the displacement of the pump, thereby absorbing the output flow of the hydraulic motor and making the original low pressure.
  • the pressure on the side is no longer raised.
  • the above solution includes two sets of output port XIII and two sets of output port XIV, which can control two parallel running pumps at the same time, or only use one set of output ports XIII or XIV to control a running pump, specifically Choose according to the number of running pumps.
  • the reverse running brake control valve of the hydraulic running system of the invention can detect the change of the pressure in the driving circuit of the running system, automatically control the displacement of the running pump, and limit the maximum reverse hydraulic braking force of the driving system, thereby effectively controlling the running system pair.
  • the reverse thrust of the engine ensures the normal function of the engine and hydraulic drive circuit components and the operational safety of the vehicle.
  • the electromagnetic reversing valve and the relief valve installed in the valve body of the invention adopt the threaded inserting parts, and the structure is compact, and the reverse brake pressure control process is hydraulic automatic control, and the reaction is quick, sensitive and accurate, and can effectively limit the maximum reverse of the running system.
  • the hydraulic braking force is used to control the magnitude of the anti-pull force of the running system to ensure the normal function of the engine and the hydraulic drive circuit components and the operational safety of the vehicle.
  • Sequence valve A and sequence valve B set a pressure of 100 bar and a relief valve set pressure of 40 bar.
  • the two-position two-way solenoid valve When the walking handle is moved forward, the two-position two-way solenoid valve is energized, and the two sets of X and X are disconnected. It is assumed that the high-pressure side is connected to the port MA at this time, and the low-pressure side is connected to the port MB. At this time, the two-position three-way solenoid valve is de-energized, MB is connected to the sequence valve A, the two-position three-way solenoid valve is energized, and the MA is disconnected from the sequence valve B.
  • the pressure on the low pressure side of the running circuit is about 28 bar, the sequence valve A is in the closed state, and the hydraulic pump operates under the control of the running handle.
  • the sequence valve A When the pressure of the port MB reaches 100 bar, the sequence valve A is opened, the pressure oil passes through the sequence valve A and the check valve C and the check valve D, and then enters the variable control mechanism of the hydraulic pump through the X port, in the shuttle valve and Under the action of the relief valve, the oil pressure of the port X is limited to 40 bar, and the displacement of the hydraulic pump is increased under the action of the pressure oil, thereby absorbing the oil output from the motor, so that the oil pressure of the port MB is not maintained.
  • the reverse hydraulic braking force reaches a limited maximum value, and the whole vehicle is decelerated by the action of the hydraulic brake.
  • the two-position two-way solenoid valves (9) and (10) are energized, and the two sets of XIII and XIV ports are disconnected, assuming that the port connected to the port MA is the low pressure side, and the oil The port MB is connected to the high pressure side.
  • the two-position three-way solenoid valve (1) is energized, MB is disconnected from the sequence valve A (14), the two-position three-way solenoid valve (3) is de-energized, MA and the sequence valve B (5) is turned on.
  • the pressure on the low pressure side of the running circuit is about 28 bar
  • the sequence valve B (5) is in the closed state, and the hydraulic pump operates under the control of the running handle.
  • the oil pressure of the port XIII is limited to 40 bar, and the displacement of the hydraulic pump is increased under the action of the pressure oil. Therefore, the oil outputted by the motor is absorbed, so that the oil pressure of the oil port MA is kept rising, and the reverse hydraulic braking force reaches a limited maximum value, and the whole vehicle is decelerated by the action of the hydraulic brake.
  • the original low pressure side pressure of the running circuit that is, the oil pressure of the MA port will drop below 100 bar, the sequence valve B (5) is closed, and the displacement of the pump is restored to the running handle control state.
  • FIG. 1 is a hydraulic schematic diagram of a preferred embodiment of a reverse brake control valve for a hydraulic running system according to the present invention
  • Figure 2 is a front elevational view showing the structure of the embodiment shown in Figure 1;
  • Figure 3 is a left side view of the embodiment of Figure 2;
  • Figure 4 is a bottom plan view of the embodiment of Figure 2;
  • a reverse brake control valve for a hydraulic running system includes a valve body 15 in which a two-position three-way solenoid valve A 1 and a two-position three-way solenoid valve B 3 are disposed, and two-position three-way electromagnetic
  • the valve A 1 is connected upstream of the oil inlet port MB 20
  • the two-position three-way solenoid valve B3 is connected upstream of the oil inlet port MA 23
  • the two-position three-way solenoid valve A 1 includes a fixed orifice A 2
  • the fixed orifice A 2 has a diameter of 2mm
  • the two-position three-way solenoid valve B 3 includes a fixed orifice B 4
  • the fixed orifice B 4 has a diameter of 2 mm
  • the two-position three-way solenoid valve A 1 is connected downstream with a sequence valve A 14
  • the sequence valve A 14 passes downstream
  • the check valve C 11 is connected to the output port XIVA 22, and the downstream of the sequence valve A 14 is also connected to
  • the pressure of the relief valve 13 ranges from 40 to 50 bar, and the outlet of the shuttle valve 6 installed between the oil passages of the sequence valve A14 and the sequence valve B5 in the two branches is connected to the relief valve 13, no matter which one In the branch, it is pressure oil, and the pressure oil reaches the inlet of the relief valve 13 through the shuttle valve 6.
  • the overflow begins, thereby limiting the sequence valve A14 and the sequence valve B5.
  • the maximum pressure of the pressurized oil does not exceed the set pressure range of the relief valve 13 by 40-50 bar; the relief valve 13 is also connected to the K3 pressure measuring port 18 to detect its working pressure; the sequence valve A14 is connected to the K1 pressure measuring port 16 so that The working pressure is detected; the sequence valve B5 is connected to the K2 pressure measuring port 17 to detect its working pressure.
  • the inlet port MA 23 and the inlet port MB 20 are connected to the main ports A and B of the hydraulic traveling system drive circuit, respectively.
  • the set pressure of the sequence valve A14 and the sequence valve B5 is the maximum pressure of the hydraulic reverse brake, which can be adjusted according to the requirements of the whole vehicle.
  • the set pressure of the sequence valve A14 and the sequence valve B5 ranges from 90 to 120 bar.
  • Each hydraulic component and the oil passage in the valve body form two parallel branches, and the composition of each branch is basically the same, starting from the oil inlet port MA 23 or the oil inlet port MB 20, and being fixed by a two-position three-way solenoid valve. Throttle, sequence valve, check valve to output port XIII or XIV.
  • the two-position three-way solenoid valve A 1 or the two-position three-way solenoid valve B3 passes the power failure or the power logic to control whether the input port and the sequence valve are connected or disconnected, when the two-position three-way solenoid valve A 1 or After the two-position three-way solenoid valve B3 is de-energized, when the pressure of the inlet of the sequence valve A 14 or the sequence valve B 5 reaches its set opening pressure, the sequence valve A 14 or the sequence valve B 5 will be turned on, and the pressure oil passes through the sequence.
  • Valve A 14 or sequence valve B5 and its check valve A or check valve B or check valve C or check valve D reach the output port XIIIA 21 or the output port XIIIB 25 or the output port XIVA 22 or the output The port XIVB 24, whereby the variable mechanism entering the hydraulic pump automatically adjusts the hydraulic pump, and the fixed orifice A or fixed orifice B in the path limits the flow through the sequence valve A14 and the sequence valve B5.
  • the check valve ensures that the pressure oil can only flow out from the output port XIIIA21 or the output port XIIIB 25 or the output port XIVA 22 or the output port XIVB 24, while ensuring two sets of output port XIIIA 21, output port XIIIB 25 or output
  • the oil port XIVA 22 and the output port XIVB 24 are independent and do not affect each other, so that one pump can be controlled or two pumps can be controlled at the same time.
  • the closed hydraulic drive circuit realizes the required rotational speed and working pressure through the flow matching of the variable pump and the variable motor.
  • the hydraulic pump output flow drives the motor to rotate, and establishes a certain pressure between the hydraulic pump outlet and the motor inlet.
  • the output flow of the hydraulic pump determines the speed of the motor.
  • the hydraulic pump When the hydraulic motor will become the pump working condition, the hydraulic pump will become the motor working condition, the hydraulic motor will drive the hydraulic pump to rotate; or when the displacement of the hydraulic pump is constant and the speed of the hydraulic motor is rapidly increased, the output of the hydraulic pump
  • the flow rate is also less than the flow drawn by the hydraulic motor.
  • the flow output from the hydraulic motor is greater than the flow drawn by the hydraulic pump.
  • the hydraulic pump will become the motor operating condition and the hydraulic motor will become the pump operating condition.
  • the above embodiment includes two sets of output port XIII and two sets of output port XIV, that is, the output port XIIIA 21 and the output port XIIIB 25, the output port XIVA 22 and the output port XIVB 24, through the output port XIIIA 21 and output port XIIIB 25, output port XIVA 22 and output port XIVB 24 can simultaneously control two parallel running pumps.
  • Embodiment 1.2 A reverse brake control valve for a hydraulic running system is the same as Embodiment 1.1 except that only one set of output port XIIIA 21 and output port XIIIB 25 are used to control a running pump.
  • Embodiment 1.3 A reverse travel brake control valve for a hydraulic running system is the same as Embodiment 1.1 except that only one set of output port XIVA 22 and output port XIVB 24 are used to control a running pump.
  • Embodiment 1.4 A reverse brake control valve for a hydraulic running system is the same as Embodiment 1.1 except that the fixed orifice A 2 has a diameter of 2.5 mm.
  • Embodiment 1.5 A reverse brake control valve for a hydraulic running system, which is the same as Embodiment 1.1 or 1.4, except that the fixed orifice B 4 has a diameter of 2.5 mm.
  • Embodiment 1.6 A reverse brake control valve for a hydraulic running system is the same as Embodiment 1.1 except that the fixed orifice A 2 has a diameter of 3 mm.
  • Embodiment 1.7 A reverse brake control valve for a hydraulic running system is the same as Embodiment 1.1 or 1.6 except that the fixed orifice B 4 has a diameter of 3 mm.
  • the reverse running brake control valve of the hydraulic running system of the above embodiment can detect the change of the pressure in the driving circuit of the running system, automatically control the displacement of the running pump, and limit the maximum reverse hydraulic braking force of the driving system, thereby effectively controlling the running system.
  • the reverse drag of the engine ensures the normal function of the engine and hydraulic drive circuit components and the operational safety of the vehicle.
  • Embodiment 2.1 A reverse braking control method for a hydraulic running system, comprising:
  • the inlet port MA23 and the inlet port MB20 are connected to the high-pressure side and the low-pressure side of the main circuit of the running system, and then the low-voltage condition of the two-position three-way electromagnetic reversing valve is controlled to make the low voltage
  • the oil on the side reaches the sequence valve through the two-position three-way solenoid valve and the fixed orifice;
  • the oil on the high pressure side is not connected to the sequence valve.
  • the pump and motor operating conditions of the running circuit change, and the pressure on the high pressure side and the low pressure side of the system also changes.
  • the pressure on the original low pressure side rises, and the running drive circuit generates the reverse hydraulic braking force.
  • the speed of the whole vehicle will gradually decrease or the speed will not increase any more.
  • the sequence When the pressure on the original low pressure side rises to the set pressure of the sequence valve, the sequence When the valve is turned on, the pressure oil enters the variable pressure cylinder of the hydraulic pump, and the displacement of the automatic control pump is rapidly increased, thereby absorbing the output flow of the hydraulic motor, so that the pressure on the original low pressure side is no longer raised;
  • Steps a1, b1, and c1 are sequentially executed to reach the reverse braking control of the hydraulic running system.
  • Embodiment 2.2 A reverse braking control method for a hydraulic running system, comprising:
  • Sequence valve A14 and sequence valve B5 set pressure is 100bar, relief valve 13 set pressure is 40bar; forward self-propelled, reverse brake pressure does not exceed 100bar;
  • the two-position two-way solenoid valve A9 and the two-position two-way solenoid valve B10 are de-energized, and the two output ports XIII and XIV are connected, that is, the output port XIIIA 21 and the output port are connected.
  • the XIVA22 is connected, the output port XIIIB 25 is in communication with the output port XIVB 24; the hydraulic pump is in the bypass state, and the variable control cannot be performed, thereby effectively avoiding the malfunction of the hydraulic pump control and improving the parking safety.
  • Steps a2, b2, c2, d2, e2, and f2 are sequentially performed.
  • Embodiment 2.3 A reverse braking control method for a hydraulic running system, comprising:
  • Sequence valve A14 and sequence valve B5 set pressure is 100bar, relief valve 13 set pressure is 40bar; backward self-propelled, reverse brake pressure does not exceed 100bar;
  • Steps a3, b3, c3, d3, e3, and f3 are sequentially performed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

一种液压走行***用反向制动控制阀，其包括阀体(15)，该阀体(15)内设置二位三通电磁阀A(1)和二位三通电磁阀B(3)，该二位三通电磁阀A(1)和二位三通电磁阀B(3)均包括节流孔，所述二位三通电磁阀A(1)上游连接进油口MB(20)，所述二位三通电磁阀B(3)上游连接进油口MA(23)；所述二位三通电磁阀A(1)下游连接顺序阀A(14)，该顺序阀A(14)下游通过单向阀C(11)和单向阀D(12)各连接一个输出油口XIV。本反向制动控制阀所提供的阀体内安装的电磁换向阀、溢流阀等采用螺纹插装件，结构紧凑，反向制动压力控制过程为液压自动控制，反应迅速、灵敏、准确，可有效限制走行***最大反向液压制动力，从而控制走行***对发动机反拖力的大小，保证发动机及液压驱动回路元件的正常功能和整车的运行安全性。

Description

一种液压走行***用反向制动控制阀 技术领域
本发明涉及一种液压控制阀，尤其是一种液压走行***用反向制动控制阀，属于液压控制技术领域。
背景技术
大型养路机械在轨道线路进行区间自走行时，最高运行速度通常为80-100km/h，其走行驱动有液力机械传动、液压传动和电传动三种常用传动方式。
采用液压传动的走行***又称液压走行***，通常由液压变量泵和变量马达组成的闭式液压回路驱动，通过电控或液控走行手柄控制泵的输出流量，驱动安装于车轴上的液压马达，液压马达再驱动车轮转动从而实现整车走行。整车速度通过控制变量泵的排量进行调节，***工作压力随运行情况变化从而满足驱动力的要求。
由于大型养路机械整车自重大，惯性也大，采用液压走行的车辆在走行手柄迅速回拉进行减速或在长大坡道上运行时，由于整车惯性液压马达将变成泵工况，液压泵变成马达工况，驱动回路通过液压马达产生反向液压制动力的同时，液压泵将对发动机造成反拖，如不采取措施，当反拖压力过高即反向液压制动力过大时，可能会造成发动机飞车，或损坏走行驱动回路液压元件，影响整车的正常走行功能，甚至威胁铁道线路的运行安全。
申请号为201510364468.3的中国发明专利申请涉及一种带制动阀的执行机构的控制装置，包括有进油通道、回油通道、三位四通换向阀，所述的三位四通换向阀上设有与进油通道连接的第一端口、与回油通道连接的第二端口以及与执行机构连接的第三端口、第四端口，所述进油通道与回油通道之间还设有用于控制进油通道与回油通道通、断的制动阀，制动阀与进油通道的连接位置位于进油通道的进油端与第一端口之间，制动阀与回油通道的连接位置位于回油通道的回油端与第二端口之间。采用上述技术方案的控制装置，能在执行机构运转状态下紧急制动，无冲击。但是其仍然不能解决大型养路机械的制动问题。
发明内容
本发明提供一种液压走行***用反向制动控制阀,尤其适用于大型养路机械液压走行***的反向制动控制。
本发明所述的液压走行***用反向制动控制阀包括阀体，该阀体内设置二位三通电磁阀A和二位三通电磁阀B，该二位三通电磁阀A和二位三通电磁阀B均 包括节流孔，所述二位三通电磁阀A上游连接进油口MB，所述二位三通电磁阀B上游连接进油口MA；所述二位三通电磁阀A下游连接顺序阀A，该顺序阀A下游通过单向阀C和单向阀D各连接一个输出油口XIV，所述二位三通电磁阀B下游连接顺序阀B，该顺序阀B下游通过单向阀A和单向阀B各连接一个输出油口XIII，所述单向阀A下游的输出油口XIII与所述单向阀C下游的输出油口XIV之间还装有二位二通电磁阀B，所述单向阀B下游的输出油口XIII与所述单向阀D下游的输出油口XIV之间还装有二位二通电磁阀A，所述顺序阀A下游和顺序阀B下游之间还连接梭阀，该梭阀连接溢流阀。
优选的是，所述溢流阀的压力范围为40-50bar，两条支路中顺序阀A和顺序阀B后的油路之间安装的所述梭阀的出油口与溢流阀相连，无论是哪条支路中为压力油，压力油都会通过所述梭阀到达所述溢流阀的入口，当压力油的压力达到所述溢流阀的设定压力时开始溢流，从而限制所述顺序阀A和顺序阀B后的压力油最高压力不超过所述溢流阀的设定压力范围40-50bar。
在上述任一方案中优选的是，当所述二位二通电磁阀B和二位二通电磁阀A失电时，输出油口XIII和输出油口XIV相通，液压泵的变量缸两端压力相同，因此无法进行变量控制，液压泵无流量输出，当整车停车时，可防止由于泵误动作造成整车移动。
在上述任一方案中优选的是，进油口MA和MB，分别和液压走行***驱动回路的主油口A和B相连。
在上述任一方案中优选的是，所述溢流阀还连接K测压口，以便检测其工作压力。
在上述任一方案中优选的是，所述顺序阀A连接K1测压口，以便检测其工作压力。
在上述任一方案中优选的是，所述顺序阀B连接K2测压口，以便检测其工作压力。
在上述任一方案中优选的是，所述二位三通电磁阀A包含的节流孔为固定节流孔A。
在上述任一方案中优选的是，所述二位三通电磁阀B包含的节流孔为固定节流孔B。
在上述任一方案中优选的是，所述固定节流孔A直径为2－3mm。
在上述任一方案中优选的是，所述固定节流孔B直径为2－3mm。
在上述任一方案中优选的是，所述阀体外包括吊环螺母，便于运输。
在上述任一方案中优选的是，所述顺序阀的设定压力即为液压反向制动的最 大压力，可根据整车的要求进行调节。
在上述任一方案中优选的是，所述顺序阀的设定压力的范围为90-120bar。
在上述任一方案中优选的是，所述溢流阀采用螺纹插装件。
各液压元件和阀体内的油道形成了条并行的支路，每条支路的组成基本相同，从进油口MA或MB开始，经二位三通电磁阀、固定节流孔、顺序阀、单向阀再到输出油口XIII或XIV。
所述二位三通电磁阀A或二位三通电磁阀B通过失电或得电逻辑，控制输入油口与顺序阀是接通还是断开，当二位三通电磁阀A或二位三通电磁阀B失电后，当顺序阀A或顺序阀B入口的压力达到其设定的开启压力时，顺序阀A或顺序阀B将接通，压力油通过顺序阀A或B及其后面的单向阀A或单向阀B或单向阀C或单向阀D到达输出油口XIII或XIV，从而进入液压泵的变量机构对液压泵进行自动调节，路径中的固定节流孔A或固定节流孔B可限制经过顺序阀的流量。单向阀确保压力油只能从输出油口XIII或XIV流出，同时保证两组输出油口XIII或XIV独立，相互不影响，从而实现控制一个泵或同时控制两个泵。闭式液压驱动回路是通过变量泵和变量马达的流量匹配实现所需的转速和工作压力，正常情况下，液压泵输出流量驱动马达转动，并在液压泵出口和马达入口间建立一定的压力，液压泵的输出流量决定了马达的转速。当液压泵的排量迅速减小，而液压马达仍保持原来的转速，则液压泵输出的流量将小于液压马达维持转速所需的流量，而液压马达输出的流量大于液压泵吸入的流量，此时，液压马达将变成泵工况，而液压泵将变成马达工况，液压马达驱动液压泵转动；或者当液压泵的排量不变，液压马达的转速迅速提高时，液压泵的输出流量同样也会小于液压马达吸入的流量，液压马达输出的流量大于液压泵吸入的流量，液压泵将变成马达工况，液压马达变成泵工况。
上述技术方案在自走行过程中，可通过进油口MA和MB与走行***主回路高压侧和低压侧相连，再通过控制二位三通电磁换向阀的得失电情况，使低压侧的油液通过二位三通电磁阀和固定节流孔到达顺序阀，而高压侧的油液与顺序阀不通，当通过走行手柄回拉减速或在长大坡道上运行时，走行回路的泵和马达工况发生变化，***的高压侧和低压侧压力也发生变化，原低压侧的压力升高，走行驱动回路产生反向液压制动力，整车的速度将逐渐降低或速度不再增加，当原低压侧的压力升高达到顺序阀的设定压力时，顺序阀接通，压力油进入液压泵的变量控制缸自动控制泵的排量迅速增大，从而吸收液压马达的输出流量，使原低压侧的压力保持不再升高，当车速降到一定值后，低压侧压力将降低到顺序阀的开启压力以下时，顺序阀关闭，液压泵的排量恢复到原走行手柄控制的状态。
上述方案中包括两组输出油口XIII和两组输出油口XIV，可对两个并联的走行泵同时进行控制，也可只采用一组输出油口XIII或XIV，控制一个走行泵，具体可根据走行泵的数量选择。
本发明所述液压走行***用反向制动控制阀能够检测走行***驱动回路中压力的变化，自动控制走行泵的排量，限制驱动***的最大反向液压制动力，从而有效控制走行***对发动机反拖力的大小，保证发动机及液压驱动回路元件的正常功能和整车的运行安全性。
本发明阀体内安装的电磁换向阀、溢流阀等采用螺纹插装件，结构紧凑，反向制动压力控制过程为液压自动控制，反应迅速、灵敏、准确，可有效限制走行***最大反向液压制动力，从而控制走行***对发动机反拖力的大小，保证发动机及液压驱动回路元件的正常功能和整车的运行安全性。
顺序阀A和顺序阀B设定压力为100bar，溢流阀设定压力为40bar。
当整车处于静止状态时，二位二通电磁阀和失电，两组X和X相通，液压泵处于旁通状态，无法进行变量控制，从而有效避免液压泵控制的误动作，提高停车安全性。
工况1：向前自走行，反向制动压力不超过100bar。
当推走行手柄向前走行时，二位二通电磁阀和得电，两组X和X断开，假设此时与油口MA相连的为高压侧，与油口MB相连的为低压侧，此时，二位三通电磁阀失电，MB与顺序阀A接通，二位三通电磁阀得电，MA与顺序阀B断开。向前正常走行时，走行回路低压侧压力约为28bar，顺序阀A处于关闭状态，液压泵在走行手柄控制下工作。当在下坡路段整车由于惯性加速或正常走行过程中回拉走行手柄减速时，马达将变成泵工况，油口MB的压力将升高，车加速越快或手柄回拉越快，油口MB的压力升得越快，由于马达变成泵工况，则走行***会产生反向液压制动力。当油口MB的压力达到100bar时，顺序阀A开启，压力油经过顺序阀A以及单向阀C和单向阀D，再经个X油口进入液压泵的变量控制机构，在梭阀和溢流阀的作用下，油口X的油液压力被限定到40bar，液压泵在压力油的作用下排量变大，从而吸收马达输出的油液，使油口MB的油液压力保持不再上升，此时反向液压制动力达到限定的最大值，整车在液压制动的作用下减速。当车速降低到一定值时，走行回路原低压侧即MB口的油液压力将降到100bar以下，顺序阀A(14)关闭，泵的排量恢复到走行手柄控制状态。
工况2：向后自走行，反向制动压力不超过100bar。
当推走行手柄向前走行时，二位二通电磁阀(9)和(10)得电，两组XIII和XIV油口断开，假设此时与油口MA相连的为低压侧，与油口MB相连的为高 压侧，此时，二位三通电磁阀(1)得电，MB与顺序阀A(14)断开，二位三通电磁阀(3)失电，MA与顺序阀B(5)接通。向后正常走行时，走行回路低压侧压力约为28bar，顺序阀B(5)处于关闭状态，液压泵在走行手柄控制下工作。当在下坡路段整车由于惯性加速或正常走行过程中回拉走行手柄减速时，马达将变成泵工况，油口MA的压力将升高，车加速越快或手柄回拉越快，油口MA的压力升得越快，由于马达变成泵工况，则走行***会产生反向液压制动力。当油口MA的压力达到100bar时，顺序阀B(5)开启，压力油经过顺序阀B(5)以及单向阀A(7)和单向阀B(8)，再经2个XIII油口进入液压泵的变量控制机构，在梭阀(6)和溢流阀(13)的作用下，油口XIII的油液压力被限定到40bar，液压泵在压力油的作用下排量变大，从而吸收马达输出的油液，使油口MA的油液压力保持不再上升，此时反向液压制动力达到限定的最大值，整车在液压制动的作用下减速。当车速降低到一定值激发，走行回路原低压侧压力即MA口的油液压力将降到100bar以下，顺序阀B(5)关闭，泵的排量恢复到走行手柄控制状态。
附图说明
图1为本发明所述液压走行***用反向制动控制阀的一优选实施例的液压原理图；
图2为图1所示实施例的结构主视图；
图3为图2所示实施例的左视图；
图4为图2的实施例的仰视图；
图1-图4中数字标号的含义为：
1二位三通电磁阀A 2固定节流孔A 3二位三通电磁阀B
4固定节流孔B 5顺序阀B 6梭阀 7单向阀A 8单向阀B
9二位二通电磁换向阀B 10二位二通电磁换向阀A 11单向阀C
12单向阀D 13溢流阀 14顺序阀A 15阀体 17K2测压口
18K3测压口 19吊环螺母 16K1测压口 20MB油口
21输出油口XIIIA 22输出油口 XIVA23进油口MA 24输出油口XIVB
25输出油口XIIIB。
具体实施方式
实施例1.1:一种液压走行***用反向制动控制阀包括阀体15，该阀体15内设置二位三通电磁阀A 1和二位三通电磁阀B 3，二位三通电磁阀A 1上游连接进油口MB 20，二位三通电磁阀B3上游连接进油口MA 23，二位三通电磁阀A 1包括固定节流孔A 2，固定节流孔A 2直径为2mm；二位三通电磁阀B 3包 括固定节流孔B 4，固定节流孔B 4直径为2mm；二位三通电磁阀A 1下游连接顺序阀A 14，该顺序阀A 14下游通过单向阀C 11连接至输出油口XIVA 22，顺序阀A 14下游还通过单向阀D 12连接至输出油口XIVB 24，所述二位三通电磁阀B 3下游连接顺序阀B 5，该顺序阀B5下游通过单向阀A 7连接至输出油口XIIIA 21，顺序阀B 5还通过单向阀B 8连接至输出油口XIV A 22，所述单向阀A 7下游的输出油口XIIIA21与单向阀C 11下游的输出油口X IV A 22之间还装有二位二通电磁阀B 9，单向阀B 8下游的输出油口XIV A 22与单向阀D 12下游的输出油口XIV B 24之间还装有二位二通电磁阀A 10，顺序阀A 14下游和顺序阀B 5下游之间还连接梭阀6，该梭阀6连接溢流阀13，溢流阀采用螺纹插装件，阀体15外包括吊环螺母19，便于运输。
溢流阀13的压力范围为40-50bar，两条支路中顺序阀A14和顺序阀B5后的油路之间安装的梭阀6的出油口与溢流阀13相连，无论是哪条支路中为压力油，压力油都会通过梭阀6到达溢流阀13的入口，当压力油的压力达到溢流阀13的设定压力时开始溢流，从而限制顺序阀A14和顺序阀B5后的压力油最高压力不超过溢流阀13的设定压力范围40-50bar；溢流阀13还连接K3测压口18，以便检测其工作压力；顺序阀A14连接K1测压口16，以便检测其工作压力；顺序阀B5连接K2测压口17，以便检测其工作压力。
二位二通电磁阀B 9和二位二通电磁阀A 10失电时，输出油口XIII和输出油口XIV相通，液压泵的变量缸两端压力相同，因此无法进行变量控制，液压泵无流量输出，当整车停车时，可防止由于泵误动作造成整车移动。
进油口MA 23和进油口MB 20分别与液压走行***驱动回路的主油口A和B相连。
顺序阀A14和顺序阀B5的设定压力即为液压反向制动的最大压力，可根据整车的要求进行调节，顺序阀A14和顺序阀B5的设定压力的范围为90-120bar。各液压元件和阀体内的油道形成了两条并行的支路，每条支路的组成基本相同，从进油口MA 23或进油口MB 20开始，经二位三通电磁阀、固定节流孔、顺序阀、单向阀再到输出油口XIII或XIV。
所述二位三通电磁阀A 1或二位三通电磁阀B3通过失电或得电逻辑，控制输入油口与顺序阀是接通还是断开，当二位三通电磁阀A 1或二位三通电磁阀B3失电后，当顺序阀A 14或顺序阀B 5入口的压力达到其设定的开启压力时，顺序阀A 14或顺序阀B 5将接通，压力油通过顺序阀A 14或顺序阀B5及其后面的单向阀A或单向阀B或单向阀C或单向阀D到达输出油口XIIIA 21或输出油口XIIIB 25或输出油口XIVA 22或输出油口XIVB 24，从而进入液压泵的变 量机构对液压泵进行自动调节，路径中的固定节流孔A或固定节流孔B可限制经过顺序阀A14和顺序阀B5的流量。单向阀确保压力油只能从输出油口XIIIA21或输出油口XIIIB 25或输出油口XIVA 22或输出油口XIVB 24流出，同时保证两组输出油口XIIIA 21、输出油口XIIIB 25或输出油口XIVA 22、输出油口XIVB 24独立，相互不影响，从而实现控制一个泵或同时控制两个泵。
闭式液压驱动回路是通过变量泵和变量马达的流量匹配实现所需的转速和工作压力，正常情况下，液压泵输出流量驱动马达转动，并在液压泵出口和马达入口间建立一定的压力，液压泵的输出流量决定了马达的转速。当液压泵的排量迅速减小，而液压马达仍保持原来的转速，则液压泵输出的流量将小于液压马达维持转速所需的流量，而液压马达输出的流量大于液压泵吸入的流量，此时，液压马达将变成泵工况，而液压泵将变成马达工况，液压马达驱动液压泵转动；或者当液压泵的排量不变，液压马达的转速迅速提高时，液压泵的输出流量同样也会小于液压马达吸入的流量，液压马达输出的流量大于液压泵吸入的流量，液压泵将变成马达工况，液压马达变成泵工况。
上述实施例中包括两组输出油口XIII和两组输出油口XIV，即，输出油口XIIIA 21与输出油口XIIIB 25、输出油口XIVA 22与输出油口XIVB 24，通过输出油口XIIIA 21与输出油口XIIIB 25、输出油口XIVA 22与输出油口XIVB 24可对两个并联的走行泵同时进行控制。
实施例1.2:一种液压走行***用反向制动控制阀，同实施例1.1，不同之处在于：只采用一组输出油口XIIIA 21与输出油口XIIIB 25控制一个走行泵。
实施例1.3:一种液压走行***用反向制动控制阀，同实施例1.1，不同之处在于：只采用一组输出油口XIVA 22与输出油口XIVB 24控制一个走行泵。
实施例1.4:一种液压走行***用反向制动控制阀，同实施例1.1，不同之处在于：固定节流孔A 2直径为2.5mm。
实施例1.5:一种液压走行***用反向制动控制阀，同实施例1.1或1.4，不同之处在于：固定节流孔B 4直径为2.5mm。
实施例1.6:一种液压走行***用反向制动控制阀，同实施例1.1，不同之处在于：固定节流孔A 2直径为3mm。
实施例1.7:一种液压走行***用反向制动控制阀，同实施例1.1或1.6，不同之处在于：固定节流孔B 4直径为3mm。
上述实施例所述液压走行***用反向制动控制阀能够检测走行***驱动回路中压力的变化，自动控制走行泵的排量，限制驱动***的最大反向液压制动力，从而有效控制走行***对发动机反拖力的大小，保证发动机及液压驱动回路元件 的正常功能和整车的运行安全性。
实施例2.1:一种液压走行***用反向制动控制方法，其包括：
a1.在作业车自走行过程中，通过进油口MA23和进油口MB20与走行***主回路高压侧和低压侧相连，再通过控制二位三通电磁换向阀的得失电情况，使低压侧的油液通过二位三通电磁阀和固定节流孔到达顺序阀；
b1.高压侧的油液与顺序阀不通，当通过走行手柄回拉减速或在长大坡道上运行时，走行回路的泵和马达工况发生变化，***的高压侧和低压侧压力也发生变化，原低压侧的压力升高，走行驱动回路产生反向液压制动力，整车的速度将逐渐降低或速度不再增加，将原低压侧的压力升高达到顺序阀的设定压力时，顺序阀接通，压力油进入液压泵的变量控制缸自动控制泵的排量迅速增大，从而吸收液压马达的输出流量，使原低压侧的压力保持不再升高；
c1.当车速降到一定值后，低压侧压力将降低到顺序阀的开启压力以下时，顺序阀关闭，液压泵的排量恢复到原走行手柄控制的状态。
依次执行步骤a1、b1、c1达到液压走行***的反向制动控制。
实施例2.2:一种液压走行***用反向制动控制方法，其包括：
a2.顺序阀A14和顺序阀B5设定压力为100bar，溢流阀13设定压力为40bar；向前自走行，反向制动压力不超过100bar；
b2.当推走行手柄向前走行时，使二位二通电磁阀9和10得电，输出油口XIIIA 21与输出油口XIVA 22断开，输出油口XIIIB 25与输出油口XIVB 24断开；假设此时与进油口MA 23相连的为高压侧，与进油口MB 20相连的为低压侧，此时，二位三通电磁阀1失电，进油口MB 20与顺序阀A14接通，二位三通电磁阀3得电，进油口MA23与顺序阀B5断开；向前正常走行时，走行回路低压侧压力约为28bar，顺序阀A14处于关闭状态，液压泵在走行手柄控制下工作；
c2.当在下坡路段整车由于惯性加速或正常走行过程中回拉走行手柄减速时，马达将变成泵工况，进油口MB 20的压力将升高，车加速越快或手柄回拉越快，进油口MB 20的压力升得越快，由于马达变成泵工况，则走行***会产生反向液压制动力；
d2.当进油口MB 20的压力达到100bar时，顺序阀A14开启，压力油经过顺序阀A14以及单向阀C11和单向阀D12，再经输出油口XIVA 22和输出油口XIVB 24进入液压泵的变量控制机构，在梭阀6和溢流阀13的作用下，油口XIV 的油液压力被限定到40bar，液压泵在压力油的作用下排量变大，从而吸收马达输出的油液，使进油口MB 20的油液压力保持不再上升，此时反向液压制动力达到限定的最大值，整车在液压制动的作用下减速；
e2.当车速降低到一定值时，走行回路原低压侧即进油口MB 20的油液压力将降到100bar以下，顺序阀A14关闭，泵的排量恢复到走行手柄控制状态；
f2.当整车处于静止状态时，使二位二通电磁阀A9和二位二通电磁阀B10失电，两组输出油口XIII和XIV相通，即，输出油口XIIIA 21与输出油口XIVA22相通，输出油口XIIIB 25与输出油口XIVB 24相通；液压泵处于旁通状态，无法进行变量控制，从而有效避免液压泵控制的误动作，提高停车安全性。
依次执行步骤a2、b2、c2、d2、e2、f2。
实施例2.3:一种液压走行***用反向制动控制方法，其包括：
a3.顺序阀A14和顺序阀B5设定压力为100bar，溢流阀13设定压力为40bar；向后自走行，反向制动压力不超过100bar；
b3.当推走行手柄向前走行时，二位二通电磁阀9和10得电，输出油口XIIIA21与输出油口XIVA 22断开，输出油口XIIIB 25与输出油口XIVB 24断开；假设此时与进油口MA 23相连的为低压侧，与进油口MB 20相连的为高压侧，此时，二位三通电磁阀1得电，进油口MB 20与顺序阀A14断开，二位三通电磁阀3失电，进油口MA 23与顺序阀B5接通；
c3.向后正常走行时，走行回路低压侧压力约为28bar，顺序阀B5处于关闭状态，液压泵在走行手柄控制下工作；当在下坡路段整车由于惯性加速或正常走行过程中回拉走行手柄减速时，马达将变成泵工况，进油口MA 23的压力将升高，车加速越快或手柄回拉越快，进油口MA 23的压力升得越快，由于马达变成泵工况，则走行***会产生反向液压制动力；
d3.当进油口MA 23的压力达到100bar时，顺序阀B5开启，压力油经过顺序阀B5以及单向阀A7和单向阀B8，再经输出油口XIIIA 21和输出油口XIIIB 25进入液压泵的变量控制机构；
e3.在梭阀6和溢流阀13的作用下，输出油口XIIIA 21和输出油口XIIIB 25的油液压力被限定到40bar，液压泵在压力油的作用下排量变大，从而吸收马达输出的油液，使进油口MA 23的油液压力保持不再上升，此时反向液压制动力达到限定的最大值，整车在液压制动的作用下减速；
f3.当车速降低到一定值激发，走行回路原低压侧压力即进油口MA 23的油液压力将降到100bar以下，顺序阀B5关闭，泵的排量恢复到走行手柄控制状态。 依次执行步骤a3、b3、c3、d3、e3、f3。

Claims (10)

  1. 一种液压走行***用反向制动控制阀，其包括阀体15，该阀体15内设置二位三通电磁阀A(1)和二位三通电磁阀B(3)，该二位三通电磁阀A(1)和二位三通电磁阀B(3)均包括节流孔，所述二位三通电磁阀A(1)上游连接进油口MB(20)，所述二位三通电磁阀B(3)上游连接进油口MA(23)；其特征在于：所述二位三通电磁阀A(1)下游连接顺序阀A(14)，该顺序阀A(14)下游通过单向阀C(11)和单向阀D(12)各连接一个输出油口XIV，二位三通电磁阀B(3)下游连接顺序阀B(5)，该顺序阀B(5)下游通过单向阀A(7)和单向阀B(8)各连接一个输出油口XIII，单向阀A(7)下游的输出油口XIII与单向阀C(11)下游的输出油口XIV之间还装有二位二通电磁阀B(9)，单向阀B(8)下游的输出油口XIII与单向阀D(12)下游的输出油口XIV之间还装有二位二通电磁阀A(10)，顺序阀A(14)下游和顺序阀B(5)下游之间还连接梭阀(6)，该梭阀(6)连接溢流阀(13)。
  2. 如权利要求1所述的液压走行***用反向制动控制阀，其特征在于：所述溢流阀的压力范围为40-50bar，两条支路中顺序阀A(14)和顺序阀B(5)后的油路之间安装的梭阀(6)的出油口与溢流阀相连，无论是哪条支路中为压力油，压力油都会通过所述梭阀到达所述溢流阀的入口，当压力油的压力达到所述溢流阀的设定压力时开始溢流，从而限制顺序阀A(14)和顺序阀B(5)后的压力油最高压力不超过所述溢流阀的设定压力范围40-50bar。
  3. 如权利要求1所述的液压走行***用反向制动控制阀，其特征在于：进油口MA(23)和进油口MB(20)，分别和液压走行***驱动回路的主油口A和B相连。
  4. 如权利要求1所述的液压走行***用反向制动控制阀，其特征在于：溢流阀(13)还连接K3测压口(18)，顺序阀A(14)连接K1测压口(16)，顺序阀B(5)连接K2测压口(17)。
  5. 如权利要求1所述的液压走行***用反向制动控制阀，其特征在于：二位三通电磁阀A(1)包含的节流孔为固定节流孔A(2)，固定节流孔A(2)直径为2－3mm。
  6. 如权利要求1所述的液压走行***用反向制动控制阀，其特征在于：二位三通电磁阀B(3)包含的节流孔为固定节流孔B(4)，固定节流孔B(4)直径为2－3mm。
  7. 如权利要求1所述的液压走行***用反向制动控制阀，其特征在于：顺序阀A(14)和顺序阀B(5)的设定压力即为液压反向制动的最大压力，顺序阀A(14)和顺序阀B(5)的设定压力的范围为90-120bar。
  8. 一种液压走行***用反向制动控制方法，其其特征在于包括：
    a1.在作业车自走行过程中，通过进油口MA 23和进油口MB 20与走行***主回路高压侧和低压侧相连，再通过控制二位三通电磁换向阀的得失电情况，使低压侧的油液通过二位三通电磁阀和固定节流孔到达顺序阀；
    b1.高压侧的油液与顺序阀不通，当通过走行手柄回拉减速或在长大坡道上运行时，走行回路的泵和马达工况发生变化，***的高压侧和低压侧压力也发生变化，原低压侧的压力升高，走行驱动回路产生反向液压制动力，整车的速度将逐渐降低或速度不再增加，将原低压侧的压力升高达到顺序阀的设定压力时，顺序阀接通，压力油进入液压泵的变量控制缸自动控制泵的排量迅速增大，从而吸收液压马达的输出流量，使原低压侧的压力保持不再升高；
    c1.当车速降到一定值后，低压侧压力将降低到顺序阀的开启压力以下时，顺序阀关闭，液压泵的排量恢复到原走行手柄控制的状态；
    依次执行步骤a1、b1、c1达到液压走行***的反向制动控制。
  9. 一种液压走行***用反向制动控制方法，其特征在于包括以下步骤：
    a2.顺序阀A14和顺序阀B5设定压力为100bar，溢流阀13设定压力为40bar；向前自走行，反向制动压力不超过100bar；
    b2.当推走行手柄向前走行时，使二位二通电磁阀9和10得电，输出油口XIIIA 21与输出油口XIVA 22断开，输出油口XIIIB 25与输出油口XIVB 24断开；假设此时与进油口MA 23相连的为高压侧，与进油口MB 20相连的为低压侧，此时，二位三通电磁阀1失电，进油口MB 20与顺序阀A14接通，二位三通电磁阀3得电，进油口MA23与顺序阀B5断开；向前正常走行时，走行回路低压侧压力约为28bar，顺序阀A14处于关闭状态，液压泵在走行手柄控制下工作；
    c2.当在下坡路段整车由于惯性加速或正常走行过程中回拉走行手柄减速时，马达将变成泵工况，进油口MB 20的压力将升高，车加速越快或手柄回拉越快，进油口MB 20的压力升得越快，由于马达变成泵工况，则走行***会产生反向液压制动力；
    d2.当进油口MB 20的压力达到100bar时，顺序阀A14开启，压力油经过顺序阀A14以及单向阀C11和单向阀D12，再经输出油口XIVA 22和输出油口XIVB 24进入液压泵的变量控制机构，在梭阀6和溢流阀13的作用下，油口XIV的油液压力被限定到40bar，液压泵在压力油的作用下排量变大，从而吸收马达输出的油液，使进油口MB 20的油液压力保持不再上升，此时反向液压制动力达到限定的最大值，整车在液压制动的作用下减速；
    e2.当车速降低到一定值时，走行回路原低压侧即进油口MB 20的油液压力 将降到100bar以下，顺序阀A14关闭，泵的排量恢复到走行手柄控制状态；
    f2.当整车处于静止状态时，使二位二通电磁阀A9和二位二通电磁阀B10失电，两组输出油口XIII和XIV相通，即，输出油口XIIIA 21与输出油口XIVA 22相通，输出油口XIIIB 25与输出油口XIVB 24相通；液压泵处于旁通状态，无法进行变量控制，从而有效避免液压泵控制的误动作，提高停车安全性；
    其特征在于：依次执行步骤a2、b2、c2、d2、e2、f2。
  10. 一种液压走行***用反向制动控制方法，其其特征在于包括：
    a3.顺序阀A14和顺序阀B5设定压力为100bar，溢流阀13设定压力为40bar；向后自走行，反向制动压力不超过100bar；
    b3.当推走行手柄向前走行时，二位二通电磁阀9和10得电，输出油口XIIIA 21与输出油口XIVA 22断开，输出油口XIIIB 25与输出油口XIVB 24断开；假设此时与进油口MA 23相连的为低压侧，与进油口MB 20相连的为高压侧，此时，二位三通电磁阀1得电，进油口MB 20与顺序阀A14断开，二位三通电磁阀3失电，进油口MA 23与顺序阀B5接通；
    c3.向后正常走行时，走行回路低压侧压力约为28bar，顺序阀B5处于关闭状态，液压泵在走行手柄控制下工作；当在下坡路段整车由于惯性加速或正常走行过程中回拉走行手柄减速时，马达将变成泵工况，进油口MA 23的压力将升高，车加速越快或手柄回拉越快，进油口MA 23的压力升得越快，由于马达变成泵工况，则走行***会产生反向液压制动力；
    d3.当进油口MA 23的压力达到100bar时，顺序阀B5开启，压力油经过顺序阀B5以及单向阀A7和单向阀B8，再经输出油口XIIIA 21和输出油口XIIIB 25进入液压泵的变量控制机构；
    e3.在梭阀6和溢流阀13的作用下，输出油口XIIIA 21和输出油口XIIIB 25的油液压力被限定到40bar，液压泵在压力油的作用下排量变大，从而吸收马达输出的油液，使进油口MA 23的油液压力保持不再上升，此时反向液压制动力达到限定的最大值，整车在液压制动的作用下减速；
    f3.当车速降低到一定值激发，走行回路原低压侧压力即进油口MA 23的油液压力将降到100bar以下，顺序阀B5关闭，泵的排量恢复到走行手柄控制状态；
    依次执行步骤a3、b3、c3、d3、e3、f3。
PCT/CN2018/084988 2017-12-28 2018-04-28 一种液压走行***用反向制动控制阀 WO2019128013A1 (zh)

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