WO2019128013A1 - Soupape de commande de frein inverse pour système hydraulique de marche - Google Patents

Soupape de commande de frein inverse pour système hydraulique de marche 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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WO
WIPO (PCT)
Prior art keywords
valve
pressure
hydraulic
oil
way solenoid
Prior art date
Application number
PCT/CN2018/084988
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English (en)
Chinese (zh)
Inventor
熊文辉
张峥明
任剡
汪宏
Original Assignee
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/fr

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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

L'invention concerne une soupape de commande de frein inverse pour un système hydraulique de marche, comprenant un corps de soupape (15), une électrovanne à trois voies et à deux positions A (1) et une électrovanne à trois voies et à deux positions B (3) étant disposées dans le corps de soupape (15), et l'électrovanne à trois voies et à deux positions A (1) et l'électrovanne à trois voies et à deux positions B (3) comprenant toutes deux des orifices, un côté amont de l'électrovanne à trois voies et à deux positions A (1) étant relié à un orifice d'entrée d'huile MB (20), et un côté amont de l'électrovanne à trois voies et à deux positions B (3) étant relié à un orifice d'entrée d'huile MA (23) ; un côté aval de l'électrovanne à trois voies et à deux positions A (1) est relié à une soupape de séquence A (14), et un côté aval de la soupape de séquence A (14) est relié à des orifices de sortie d'huile XIV au moyen d'un clapet de non-retour C (11) et d'un clapet de non-retour D (12), respectivement. Une électrovanne directionnelle, une soupape de trop-plein et des éléments similaires montés dans le corps de soupape fourni par la soupape de commande de frein inverse adoptent des pièces d'insertion filetées, la structure est compacte, et le processus de commande de la pression de freinage inverse est une commande automatique hydraulique, la réaction est rapide, sensible et précise, et peut limiter efficacement la force de freinage hydraulique inverse maximale du système de marche, ce qui permet de commander l'amplitude de la force anti-traction du système de marche sur le moteur, de manière à assurer le fonctionnement normal du moteur et des éléments du circuit d'entraînement hydraulique, ainsi que la sécurité de fonctionnement de l'ensemble du véhicule.
PCT/CN2018/084988 2017-12-28 2018-04-28 Soupape de commande de frein inverse pour système hydraulique de marche WO2019128013A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201711461624.3A CN109973452B (zh) 2017-12-28 2017-12-28 一种液压走行系统用反向制动控制阀
CN201711461624.3 2017-12-28

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WO2019128013A1 true WO2019128013A1 (fr) 2019-07-04

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WO (1) WO2019128013A1 (fr)

Cited By (6)

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CN110778551A (zh) * 2019-11-30 2020-02-11 安徽柳工起重机有限公司 起重机的全闭式液压系统
CN110843904A (zh) * 2019-11-14 2020-02-28 湘电重型装备有限公司 一种大型电动轮自卸车集成转向及制动控制系统
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CN111631021A (zh) * 2020-05-11 2020-09-08 宁夏农林科学院枸杞工程技术研究所 枸杞采摘用液电控制系统
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