CN109973452B - Reverse braking control valve for hydraulic traveling system - Google Patents

Reverse braking control valve for hydraulic traveling system Download PDF

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Publication number
CN109973452B
CN109973452B CN201711461624.3A CN201711461624A CN109973452B CN 109973452 B CN109973452 B CN 109973452B CN 201711461624 A CN201711461624 A CN 201711461624A CN 109973452 B CN109973452 B CN 109973452B
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China
Prior art keywords
valve
pressure
oil
hydraulic
way electromagnetic
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CN201711461624.3A
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CN109973452A (en
Inventor
熊文辉
张峥明
任剡
汪宏
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CRCC High Tech Equipment Corp Ltd
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CRCC High Tech Equipment Corp Ltd
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Priority to CN201711461624.3A priority Critical patent/CN109973452B/en
Priority to PCT/CN2018/084988 priority patent/WO2019128013A1/en
Publication of CN109973452A publication Critical patent/CN109973452A/en
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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

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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

The reverse braking control valve for the hydraulic traveling system comprises a valve body 15, wherein a two-position three-way electromagnetic valve A (1) and a two-position three-way electromagnetic valve B (3) are arranged in the valve body 15, the two-position three-way electromagnetic valve A (1) and the two-position three-way electromagnetic valve B (3) both comprise orifices, the upstream of the two-position three-way electromagnetic valve A (1) is connected with an oil inlet MB (20), and the upstream of the two-position three-way electromagnetic valve B (3) is connected with an oil inlet MA (23); the downstream of the two-position three-way electromagnetic valve A (1) is connected with a sequence valve A (14), and the downstream of the sequence valve A (14) is respectively connected with an output oil port XIV through a one-way valve C (11) and a one-way valve D (12). The electromagnetic reversing valve, the overflow valve and the like arranged in the valve body are threaded plug-in components, the structure is compact, the reverse braking pressure control process is hydraulic automatic control, the response is rapid, sensitive and accurate, and the maximum reverse hydraulic braking force of the running system can be effectively limited, so that the magnitude of the reverse dragging force of the running system to the engine is controlled, and the normal functions of the engine and the hydraulic driving loop element and the running safety of the whole vehicle are ensured.

Description

Reverse braking control valve for hydraulic traveling system
Technical Field
The invention relates to a hydraulic control valve, in particular to a reverse braking control valve for a hydraulic traveling system, and belongs to the technical field of hydraulic control.
Background
When the large road maintenance machine is in interval self-walking on the track line, the highest running speed is usually 80-100km/h, and the running drive of the large road maintenance machine is provided with three common transmission modes of hydraulic mechanical transmission, hydraulic transmission and electric transmission.
The hydraulic transmission running system is also called a hydraulic running system, is usually driven by a closed hydraulic circuit consisting of a hydraulic variable pump and a variable motor, controls the output flow of the pump through an electric control or hydraulic control running handle, drives a hydraulic motor arranged on an axle, and drives wheels to rotate so as to realize running of the whole vehicle. The speed of the whole vehicle is regulated by controlling the displacement of the variable pump, and the working pressure of the system changes along with the running condition so as to meet the requirement of driving force.
Because the large road maintenance machinery whole vehicle has large self weight and large inertia, when a vehicle adopting hydraulic running is quickly pulled back to slow down or runs on a long ramp by a running handle, the whole vehicle inertial hydraulic motor is changed into a pump working condition, a hydraulic pump is changed into a motor working condition, a driving loop generates reverse hydraulic braking force through the hydraulic motor, and meanwhile, the hydraulic pump can cause reverse dragging on an engine, if no measures are taken, when the reverse dragging pressure is too high, namely the reverse hydraulic braking force is too large, the engine galloping can be caused, or a hydraulic element of a running driving loop is damaged, the normal running function of the whole vehicle is influenced, and even the running safety of a railway line is threatened.
The Chinese patent application with the application number 201510364468.3 relates to a control device of an actuating mechanism with a brake valve, which comprises an oil inlet channel, an oil return channel and a three-position four-way reversing valve, wherein a first port connected with the oil inlet channel, a second port connected with the oil return channel, a third port connected with the actuating mechanism and a fourth port connected with the actuating mechanism are arranged on the three-position four-way reversing valve, a brake valve for controlling the on and off of the oil inlet channel and the oil return channel is further arranged between the oil inlet channel and the oil return channel, the connection position of the brake valve and the oil inlet channel is positioned between the oil inlet end and the first port of the oil inlet channel, and the connection position of the brake valve and the oil return channel is positioned between the oil return end and the second port of the oil return channel. The control device adopting the technical scheme can realize emergency braking in the running state of the actuating mechanism without impact. But it still does not solve the braking problem of large road maintenance machines.
Disclosure of Invention
The invention provides a reverse braking control valve for a hydraulic traveling system, which is particularly suitable for reverse braking control of the hydraulic traveling system of a large-scale road maintenance machine.
The reverse braking control valve for the hydraulic traveling system comprises a valve body, wherein a two-position three-way electromagnetic valve A and a two-position three-way electromagnetic valve B are arranged in the valve body, the two-position three-way electromagnetic valve A and the two-position three-way electromagnetic valve B both comprise orifices, the upstream of the two-position three-way electromagnetic valve A is connected with an oil inlet MB, and the upstream of the two-position three-way electromagnetic valve B is connected with an oil inlet MA; the downstream of the two-position three-way electromagnetic valve A is connected with a sequence valve A, the downstream of the sequence valve A is connected with an output oil port XIV through a check valve C and a check valve D respectively, the downstream of the two-position three-way electromagnetic valve B is connected with a sequence valve B, the downstream of the sequence valve B is connected with an output oil port XIII through the check valve A and the check valve B respectively, a two-position two-way electromagnetic valve B is further arranged between the output oil port XIII of the downstream of the check valve A and the output oil port XIV of the downstream of the check valve C, a two-position two-way electromagnetic valve A is further arranged between the output oil port XIII of the downstream of the check valve B and the output oil port XIV of the downstream of the check valve D, and a shuttle valve is further connected between the downstream of the sequence valve A and the downstream of the sequence valve B and is connected with an overflow valve.
Preferably, the pressure range of the overflow valve is 40-50bar, the oil outlet of the shuttle valve installed between the oil paths behind the sequence valve A and the sequence valve B in the two branches is connected with the overflow valve, no matter which branch is the pressure oil, the pressure oil can reach the inlet of the overflow valve through the shuttle valve, and when the pressure of the pressure oil reaches the set pressure of the overflow valve, the overflow is started, so that the highest pressure of the pressure oil behind the sequence valve A and the sequence valve B is limited to be not more than 40-50bar of the set pressure range of the overflow valve.
In any of the above schemes, preferably, when the two-position two-way electromagnetic valve B and the two-position two-way electromagnetic valve a are powered off, the output oil port XIII is communicated with the output oil port XIV, and the pressures at the two ends of the variable cylinder of the hydraulic pump are the same, so that variable control cannot be performed, the hydraulic pump has no flow output, and when the whole vehicle is parked, the movement of the whole vehicle caused by misoperation of the pump can be prevented.
In any of the above solutions, the oil inlets MA and MB are preferably connected to the main oil ports a and B of the hydraulic travel system drive circuit, respectively.
In any of the above embodiments, it is preferable that the relief valve is further connected to a K pressure tap for detecting the operating pressure thereof.
In any of the above embodiments, it is preferable that the sequence valve a is connected to the K1 pressure measuring port so as to detect the operating pressure thereof.
In any of the above embodiments, it is preferable that the sequence valve B is connected to the K2 pressure measuring port so as to detect the operating pressure thereof.
In any of the above embodiments, it is preferable that the orifice included in the two-position three-way electromagnetic valve a is a fixed orifice a.
In any of the above aspects, preferably, the orifice included in the two-position three-way electromagnetic valve B is a fixed orifice B.
In any of the above embodiments, preferably, the fixed orifice a has a diameter of 2 to 3mm.
In any of the above embodiments, preferably, the fixed orifice B has a diameter of 2 to 3mm.
In any of the above solutions, preferably, the valve body includes an eye nut outside, so as to facilitate transportation.
In any of the above schemes, preferably, the set pressure of the sequence valve is the maximum pressure of the hydraulic reverse braking, and can be adjusted according to the requirement of the whole vehicle.
In any of the above schemes, it is preferable that the set pressure of the sequence valve is in the range of 90-120bar.
In any of the above aspects, preferably, the relief valve is a threaded insert.
The hydraulic components and the oil ducts in the valve body form parallel branches, the components of each branch are basically the same, and the branches start from the oil inlet MA or MB and go through a two-position three-way electromagnetic valve, a fixed orifice, a sequence valve and a one-way valve to the output oil port XIII or XIV.
The two-position three-way electromagnetic valve A or the two-position three-way electromagnetic valve B is connected or disconnected with the sequence valve through a power-losing or power-obtaining logic, when the pressure of the inlet of the sequence valve A or the sequence valve B reaches the set opening pressure after the two-position three-way electromagnetic valve A or the two-position three-way electromagnetic valve B is powered down, the sequence valve A or the sequence valve B is connected, and pressure oil reaches the output oil port XIII or XIV through the sequence valve A or the sequence valve B and the check valve A or the check valve B or the check valve C or the check valve D behind the sequence valve A or the sequence valve B, so that a variable mechanism entering the hydraulic pump automatically adjusts the hydraulic pump, and a fixed orifice A or the fixed orifice B in a path can limit the flow passing through the sequence valve. The check valve ensures that the pressure oil can only flow out from the output oil ports XIII or XIV, and simultaneously ensures that two groups of output oil ports XIII or XIV are independent and do not affect each other, thereby realizing control of one pump or control of two pumps simultaneously. The closed hydraulic driving loop realizes the required rotating speed and working pressure through the flow matching of the variable pump and the variable motor, and under normal conditions, the output flow of the hydraulic pump drives the motor to rotate, and establishes a certain pressure between the outlet of the hydraulic pump and the inlet of the motor, and the output flow of the hydraulic pump determines the rotating speed of the motor. When the displacement of the hydraulic pump is rapidly reduced and the hydraulic motor still maintains the original rotating speed, the output flow of the hydraulic pump is smaller than the flow required by the hydraulic motor to maintain the rotating speed, and the output flow of the hydraulic motor is larger than the suction flow of the hydraulic pump, at the moment, the hydraulic motor becomes a pump working condition, the hydraulic pump becomes a motor working condition, and the hydraulic motor drives the hydraulic pump to rotate; or when the displacement of the hydraulic pump is unchanged and the rotating speed of the hydraulic motor is rapidly increased, the output flow of the hydraulic pump is also smaller than the flow inhaled by the hydraulic motor, the output flow of the hydraulic motor is larger than the flow inhaled by the hydraulic pump, the hydraulic pump becomes a motor working condition, and the hydraulic motor becomes a pump working condition.
According to the technical scheme, in the self-walking process, the oil inlet MA and MB can be connected with the high-pressure side and the low-pressure side of a main loop of a walking system, the power-off condition of the two-position three-way electromagnetic reversing valve is controlled, so that oil liquid at the low-pressure side reaches the sequence valve through the two-position three-way electromagnetic valve and the fixed orifice, the oil liquid at the high-pressure side is not communicated with the sequence valve, when the traveling handle is pulled back to slow down or runs on a long ramp, the working conditions of a pump and a motor of the walking loop change, the high-pressure side pressure and the low-pressure side pressure of the system also change, the pressure at the original low-pressure side rises, the traveling driving loop generates reverse hydraulic braking force, the speed of the whole vehicle gradually decreases or the speed is not increased any more, when the pressure at the original low-pressure side rises to reach the set pressure of the sequence valve, the sequence valve is switched on, the variable control cylinder of the pressure oil entering the hydraulic pump is automatically controlled to be increased, so that the output flow of the hydraulic motor is absorbed, the pressure at the original low-pressure side is kept not rising any more, the pressure is reduced below the opening pressure of the sequence valve, the hydraulic pump is switched off, and the traveling handle returns to the original displacement state.
The scheme comprises two groups of output oil ports XIII and two groups of output oil ports XIV, two parallel running pumps can be controlled simultaneously, one running pump can be controlled by only adopting one group of output oil ports XIII or XIV, and the running pump can be specifically selected according to the number of the running pumps.
The reverse braking control valve for the hydraulic traveling system can detect the pressure change in the driving loop of the traveling system, automatically control the displacement of the traveling pump and limit the maximum reverse hydraulic braking force of the driving system, thereby effectively controlling the reverse dragging force of the traveling system to the engine and ensuring the normal functions of the engine and the hydraulic driving loop elements and the running safety of the whole vehicle.
The electromagnetic reversing valve, the overflow valve and the like arranged in the valve body are threaded plug-in components, the structure is compact, the reverse braking pressure control process is hydraulic automatic control, the reaction is rapid, sensitive and accurate, and the maximum reverse hydraulic braking force of the running system can be effectively limited, so that the magnitude of the reverse dragging force of the running system to the engine is controlled, and the normal functions of the engine and the hydraulic driving loop element and the running safety of the whole vehicle are ensured.
The sequence valve A and the sequence valve B set a pressure of 100bar and the relief valve set a pressure of 40bar.
When the whole vehicle is in a static state, the two-position two-way electromagnetic valve is powered off, the two groups of X and X are communicated, the hydraulic pump is in a bypass state, and variable control cannot be performed, so that misoperation of hydraulic pump control is effectively avoided, and parking safety is improved.
Working condition 1: the vehicle is propelled forward, and the reverse braking pressure is not more than 100bar.
When the pushing handle moves forward, the two-position two-way electromagnetic valve is powered on, the two groups X and X are disconnected, the high-pressure side connected with the oil port MA is assumed, the low-pressure side connected with the oil port MB is assumed, at the moment, the two-position three-way electromagnetic valve is powered off, the MB is connected with the sequence valve A, the two-position three-way electromagnetic valve is powered on, and the MA is disconnected with the sequence valve B. When the hydraulic pump runs forward normally, the low-pressure side pressure of the running loop is about 28bar, the sequence valve A is in a closed state, and the hydraulic pump works under the control of the running handle. When the whole vehicle on the downhill road section is decelerated due to inertial acceleration or during normal running, the motor becomes a pump working condition, the pressure of the oil port MB rises, the faster the vehicle accelerates or the handle is pulled back, the faster the pressure of the oil port MB rises, and the running system can generate reverse hydraulic braking force due to the fact that the motor becomes the pump working condition. When the pressure of the oil port MB reaches 100bar, the sequence valve A is opened, pressure oil passes through the sequence valve A, the one-way valve C and the one-way valve D, and then enters a variable control mechanism of the hydraulic pump through the X oil ports, the oil pressure of the oil port X is limited to 40bar under the action of the shuttle valve and the overflow valve, the displacement of the hydraulic pump is increased under the action of the pressure oil, so that the oil output by the motor is absorbed, the oil pressure of the oil port MB is kept not to rise, the reverse hydraulic braking force reaches the limited maximum value at the moment, and the whole vehicle is decelerated under the action of hydraulic braking. When the speed of the vehicle is reduced to a certain value, the oil pressure of the MB port at the original low-pressure side of the running loop is reduced to be lower than 100bar, the sequence valve A (14) is closed, and the displacement of the pump is restored to the running handle control state.
Working condition 2: and the vehicle is propelled backwards, and the reverse braking pressure is not more than 100bar.
When the pushing handle moves forwards, the two-position two-way electromagnetic valves (9) and (10) are powered on, the two groups of XIII and XIV oil ports are disconnected, the low-pressure side connected with the oil port MA is assumed, the high-pressure side connected with the oil port MB is assumed, the two-position three-way electromagnetic valve (1) is powered on, the MB is disconnected from the sequence valve A (14), the two-position three-way electromagnetic valve (3) is powered off, and the MA is connected with the sequence valve B (5). When the hydraulic pump runs backwards normally, the low-pressure side pressure of the running loop is about 28bar, the sequence valve B (5) is in a closed state, and the hydraulic pump works under the control of the running handle. When the whole vehicle on the downhill road section is decelerated due to inertial acceleration or during normal running, the motor becomes a pump working condition, the pressure of the oil port MA rises, the faster the vehicle is accelerated or the handle is pulled back, the faster the pressure of the oil port MA rises, and the running system can generate reverse hydraulic braking force due to the fact that the motor becomes the pump working condition. When the pressure of the oil port MA reaches 100bar, the sequence valve B (5) is opened, pressure oil passes through the sequence valve B (5), the one-way valve A (7) and the one-way valve B (8), and then enters a variable control mechanism of the hydraulic pump through 2 XIII oil ports, under the action of the shuttle valve (6) and the overflow valve (13), the oil pressure of the oil port XIII is limited to 40bar, the displacement of the hydraulic pump is increased under the action of the pressure oil, so that the oil output by a motor is absorbed, the oil pressure of the oil port MA is kept not rising, the reverse hydraulic braking force reaches the limited maximum value at the moment, and the whole vehicle is decelerated under the action of hydraulic braking. When the vehicle speed is reduced to a certain value to excite, the original low-pressure side pressure of the running loop, namely the oil pressure of an MA port, is reduced to be lower than 100bar, the sequence valve B (5) is closed, and the discharge capacity of the pump is restored to the running handle control state.
Drawings
FIG. 1 is a hydraulic schematic diagram of a preferred embodiment of a reverse brake control valve for a hydraulic travel system according to the present invention;
FIG. 2 is a front elevational view of the embodiment of FIG. 1;
FIG. 3 is a left side view of the embodiment shown in FIG. 2;
FIG. 4 is a bottom view of the embodiment of FIG. 2;
the meaning of the numerical designations in fig. 1-4 is:
1 two-position three-way electromagnetic valve A2 fixed orifice A3 two-position three-way electromagnetic valve B
4 fixed orifice B5 sequence valve B6 shuttle valve 7 check valve A8 check valve B
9 two-position two-way electromagnetic directional valve B10 two-position two-way electromagnetic directional valve A11 one-way valve C
12 one-way valve D13 overflow valve 14 sequence valve A15 valve body 17 K2 pressure measuring port
18 K3 pressure measuring port 19 flying ring nut 16 K1 pressure measuring port 20 MB oil port
21 output oil port XIIIA 22 output oil port XIVA 23 oil inlet MA 24 output oil port XIVB
25 outlet port XIIIB.
Detailed Description
The reverse braking control valve for the hydraulic traveling system comprises a valve body 15, wherein a two-position three-way electromagnetic valve A1 and a two-position three-way electromagnetic valve B3 are arranged in the valve body 15, the upstream of the two-position three-way electromagnetic valve A1 is connected with an oil inlet MB20, the upstream of the two-position three-way electromagnetic valve B3 is connected with an oil inlet MA23, the two-position three-way electromagnetic valve A1 comprises a fixed orifice A2, and the diameter of the fixed orifice A2 is 2mm; the two-position three-way electromagnetic valve B3 comprises a fixed throttle hole B4, and the diameter of the fixed throttle hole B4 is 2mm; the downstream of the two-position three-way electromagnetic valve A1 is connected with the sequence valve A14, the downstream of the sequence valve A14 is connected with the output oil port XIVA22 through a one-way valve C11, the downstream of the sequence valve A14 is also connected with the output oil port XIVB 24 through a one-way valve D12, the downstream of the two-position three-way electromagnetic valve B3 is connected with the sequence valve B5, the downstream of the sequence valve B5 is connected with the output oil port XIIIA21 through a one-way valve A7, the sequence valve B5 is also connected with the output oil port XIV A22 through a one-way valve B8, a two-position two-way electromagnetic valve B9 is further arranged between the output oil port XIIA 21 downstream of the one-way valve A7 and the output oil port XIV A22 downstream of the one-way valve C11, a two-position two-way electromagnetic valve A10 is further arranged between the output oil port XIV 22 downstream of the one-way valve B8 and the output oil port XIV B24 downstream of the one-way valve D12, a shuttle valve 6 is further connected between the downstream of the sequence valve A14 and the downstream of the sequence valve B5, the shuttle valve 6 is connected with the overflow valve 13, the overflow valve adopts a threaded plug-in assembly, and the valve body 15 comprises a lifting ring nut 19 for transportation.
The pressure range of the overflow valve 13 is 40-50bar, the oil outlet of the shuttle valve 6 arranged between the oil paths behind the sequence valve A14 and the sequence valve B5 in the two branches is connected with the overflow valve 13, no matter which branch is the pressure oil, the pressure oil can reach the inlet of the overflow valve 13 through the shuttle valve 6, and when the pressure of the pressure oil reaches the set pressure of the overflow valve 13, the overflow is started, so that the highest pressure of the pressure oil behind the sequence valve A14 and the sequence valve B5 is limited to be not more than 40-50bar of the set pressure range of the overflow valve 13; the overflow valve 13 is also connected with a K3 pressure measuring port 18 so as to detect the working pressure thereof; sequence valve A14 is connected to K1 pressure tap 16 to sense its operating pressure; sequence valve B5 is connected to K2 pressure tap 17 to detect its operating pressure.
When the two-position two-way electromagnetic valve B9 and the two-position two-way electromagnetic valve A10 lose electricity, the output oil port XIII is communicated with the output oil port XIV, and the pressures at the two ends of the variable cylinder of the hydraulic pump are the same, so that variable control cannot be performed, the hydraulic pump has no flow output, and when the whole vehicle is parked, the movement of the whole vehicle caused by misoperation of the pump can be prevented.
The oil inlet MA23 and the oil inlet MB20 are respectively connected with main oil ports A and B of a hydraulic traveling system driving circuit.
The set pressure of the sequence valve A14 and the sequence valve B5 is the maximum pressure of the hydraulic reverse braking, and can be adjusted according to the requirement of the whole vehicle, and the range of the set pressure of the sequence valve A14 and the sequence valve B5 is 90-120bar. The hydraulic components and the oil ducts in the valve body form two parallel branches, the components of each branch are basically the same, and the branches start from the oil inlet MA23 or the oil inlet MB20 and then go to the output oil ports XIII or XIV through a two-position three-way electromagnetic valve, a fixed orifice, a sequence valve and a one-way valve.
The two-position three-way electromagnetic valve A1 or the two-position three-way electromagnetic valve B3 controls whether the input oil port and the sequence valve are connected or disconnected through a power-losing or power-obtaining logic, when the pressure of the inlet of the sequence valve A14 or the sequence valve B5 reaches the set opening pressure after the two-position three-way electromagnetic valve A1 or the two-position three-way electromagnetic valve B3 is powered off, the sequence valve A14 or the sequence valve B5 is connected, and pressure oil reaches the output oil port XIIIA21 or the output oil port XIIB 25 or the output oil port XIVA22 or the output oil port XIVB 24 through the sequence valve A14 or the sequence valve B5 and the one-way valve A or the one-way valve B or the one-way valve C or the one-way valve D behind the sequence valve A14 or the sequence valve B5, so that a variable mechanism entering the hydraulic pump can automatically regulate the hydraulic pump, and a fixed orifice A or the fixed orifice B in a path can limit the flow passing through the sequence valve A14 and the sequence valve B5. The check valve ensures that pressure oil can only flow out from the output oil port XIIIA21 or the output oil port XIIB 25 or the output oil port XIVA22 or the output oil port XIVB 24, and simultaneously ensures that two groups of output oil ports XIIIA21, XIIB 25 or the output oil port XIVA22 and the output oil port XIVB 24 are independent and are not influenced by each other, thereby realizing control of one pump or control of two pumps simultaneously.
The closed hydraulic driving loop realizes the required rotating speed and working pressure through the flow matching of the variable pump and the variable motor, and under normal conditions, the output flow of the hydraulic pump drives the motor to rotate, and establishes a certain pressure between the outlet of the hydraulic pump and the inlet of the motor, and the output flow of the hydraulic pump determines the rotating speed of the motor. When the displacement of the hydraulic pump is rapidly reduced and the hydraulic motor still maintains the original rotating speed, the output flow of the hydraulic pump is smaller than the flow required by the hydraulic motor to maintain the rotating speed, and the output flow of the hydraulic motor is larger than the suction flow of the hydraulic pump, at the moment, the hydraulic motor becomes a pump working condition, the hydraulic pump becomes a motor working condition, and the hydraulic motor drives the hydraulic pump to rotate; or when the displacement of the hydraulic pump is unchanged and the rotating speed of the hydraulic motor is rapidly increased, the output flow of the hydraulic pump is also smaller than the flow inhaled by the hydraulic motor, the output flow of the hydraulic motor is larger than the flow inhaled by the hydraulic pump, the hydraulic pump becomes a motor working condition, and the hydraulic motor becomes a pump working condition.
In the above embodiment, the two parallel running pumps can be controlled simultaneously by the output port XIIIA21 and the output port XIIIB 25, the output port XIVA22 and the output port XIVB 24, and the output port XIIIA21 and the output port XIIIB 25, and the output port XIVA22 and the output port XIVB 24.
Embodiment 1.2 a reverse brake control valve for a hydraulic travel system is different from embodiment 1.1 in that: only one set of outlet port XIIIA21 and outlet port XIIIB 25 is used to control one travelling pump.
Embodiment 1.3 a reverse brake control valve for a hydraulic travel system is different from embodiment 1.1 in that: only one set of output oil ports XIVA22 and XIVB 24 is used to control one traveling pump.
Embodiment 1.4 a reverse brake control valve for a hydraulic travel system is different from embodiment 1.1 in that: the fixed orifice A2 has a diameter of 2.5mm.
Example 1.5 a reverse brake control valve for a hydraulic travel system, which is different from example 1.1 or 1.4 in that: the fixed orifice B4 has a diameter of 2.5mm.
Embodiment 1.6 a reverse brake control valve for a hydraulic travel system is different from embodiment 1.1 in that: the fixed orifice A2 has a diameter of 3mm.
Example 1.7 a reverse brake control valve for a hydraulic travel system, which is different from example 1.1 or 1.6 in that: the fixed orifice B4 has a diameter of 3mm.
According to the reverse braking control valve for the hydraulic traveling system, disclosed by the embodiment, the change of pressure in a driving loop of the traveling system can be detected, the displacement of the traveling pump is automatically controlled, and the maximum reverse hydraulic braking force of the driving system is limited, so that the magnitude of reverse dragging force of the traveling system to an engine is effectively controlled, and the normal functions of the engine and the hydraulic driving loop element and the running safety of the whole vehicle are ensured.
Embodiment 2.1 a reverse brake control method for a hydraulic travel system includes:
a1. in the self-running process of the working vehicle, the working vehicle is connected with the high-pressure side and the low-pressure side of a main loop of a running system through an oil inlet MA23 and an oil inlet MB20, and oil liquid at the low-pressure side reaches a sequence valve through a two-position three-way electromagnetic valve and a fixed orifice by controlling the power-on and power-off condition of the two-position three-way electromagnetic reversing valve;
b1. the oil liquid at the high pressure side is not communicated with the sequence valve, when the oil liquid is pulled back to slow down through a traveling handle or runs on a long and large ramp, the working conditions of a pump and a motor of a traveling loop are changed, the pressure at the high pressure side and the pressure at the low pressure side of the system are also changed, the pressure at the original low pressure side is increased, a traveling driving loop generates reverse hydraulic braking force, the speed of the whole vehicle is gradually reduced or the speed is not increased any more, when the pressure at the original low pressure side is increased to reach the set pressure of the sequence valve, the sequence valve is communicated, and the displacement of the pump is automatically controlled by a variable control cylinder of the pressure oil entering the hydraulic pump to be rapidly increased, so that the output flow of the hydraulic motor is absorbed, and the pressure at the original low pressure side is kept not increased any more;
c1. when the vehicle speed is reduced to a certain value, the low-pressure side pressure is reduced below the opening pressure of the sequence valve, the sequence valve is closed, and the displacement of the hydraulic pump is restored to the original running handle control state.
Steps a1, b1 and c1 are sequentially executed to achieve the reverse braking control of the hydraulic traveling system.
Embodiment 2.2 a reverse brake control method for a hydraulic travel system, comprising:
a2. sequence valve A14 and sequence valve B5 set 100bar and relief valve 13 set 40bar; forward self-walking, and the reverse braking pressure is not more than 100bar;
b2. when the pushing handle moves forwards, the two-position two-way electromagnetic valves 9 and 10 are powered, the output oil port XIIIA21 is disconnected from the output oil port XIVA22, and the output oil port XIIIB 25 is disconnected from the output oil port XIVB 24; assuming that the connection with the oil inlet MA23 is a high-pressure side and the connection with the oil inlet MB20 is a low-pressure side, at the moment, the two-position three-way electromagnetic valve 1 is powered off, the oil inlet MB20 is connected with the sequence valve A14, the two-position three-way electromagnetic valve 3 is powered on, and the oil inlet MA23 is disconnected with the sequence valve B5; when the hydraulic pump runs forward normally, the low-pressure side pressure of the running loop is about 28bar, the sequence valve A14 is in a closed state, and the hydraulic pump works under the control of the running handle;
c2. when the whole vehicle on the downhill road section is pulled back to the running handle to be decelerated due to inertial acceleration or normal running, the motor becomes a pump working condition, the pressure of the oil inlet MB20 rises, the faster the vehicle is accelerated or the handle is pulled back, the faster the pressure of the oil inlet MB20 rises, and the running system can generate reverse hydraulic braking force due to the fact that the motor becomes the pump working condition;
d2. when the pressure of the oil inlet MB20 reaches 100bar, the sequence valve A14 is opened, pressure oil passes through the sequence valve A14, the one-way valve C11 and the one-way valve D12, and then enters a variable control mechanism of the hydraulic pump through the output oil port XIVA22 and the output oil port XIVB 24, under the action of the shuttle valve 6 and the overflow valve 13, the oil pressure of the oil port XIV is limited to 40bar, the displacement of the hydraulic pump is increased under the action of the pressure oil, so that the oil output by the motor is absorbed, the oil pressure of the oil inlet MB20 is kept not to rise, the reverse hydraulic braking force reaches the limited maximum value at the moment, and the whole vehicle is decelerated under the action of hydraulic braking;
e2. when the speed of the vehicle is reduced to a certain value, the original low-pressure side of the running loop, namely the oil pressure of the oil inlet MB20, is reduced to be lower than 100bar, the sequence valve A14 is closed, and the displacement of the pump is restored to the running handle control state;
f2. when the whole vehicle is in a static state, the two-position two-way electromagnetic valve A9 and the two-position two-way electromagnetic valve B10 are powered off, and two groups of output oil ports XIII and XIV are communicated, namely an output oil port XIIIA21 is communicated with an output oil port XIVA22, and an output oil port XIIIB 25 is communicated with an output oil port XIVB 24; the hydraulic pump is in a bypass state and variable control cannot be performed, so that misoperation of hydraulic pump control is effectively avoided, and parking safety is improved.
Steps a2, b2, c2, d2, e2, f2 are performed sequentially.
Embodiment 2.3 a reverse brake control method for a hydraulic travel system, comprising:
a3. sequence valve A14 and sequence valve B5 set 100bar and relief valve 13 set 40bar; the vehicle is self-propelled backwards, and the reverse braking pressure is not more than 100bar;
b3. when the pushing handle moves forwards, the two-position two-way electromagnetic valves 9 and 10 are powered, the output oil port XIIIA21 is disconnected from the output oil port XIVA22, and the output oil port XIIIB 25 is disconnected from the output oil port XIVB 24; assuming that the connection with the oil inlet MA23 is a low-pressure side and the connection with the oil inlet MB20 is a high-pressure side, at the moment, the two-position three-way electromagnetic valve 1 is powered on, the oil inlet MB20 is disconnected from the sequence valve A14, the two-position three-way electromagnetic valve 3 is powered off, and the oil inlet MA23 is connected with the sequence valve B5;
c3. when the hydraulic pump runs backwards normally, the low-pressure side pressure of the running loop is about 28bar, the sequence valve B5 is in a closed state, and the hydraulic pump works under the control of the running handle; when the whole vehicle on the downhill road section is pulled back to the running handle to be decelerated due to inertial acceleration or normal running, the motor becomes a pump working condition, the pressure of the oil inlet MA23 rises, the faster the vehicle is accelerated or the handle is pulled back, the faster the pressure of the oil inlet MA23 rises, and the running system can generate reverse hydraulic braking force due to the fact that the motor becomes the pump working condition;
d3. when the pressure of the oil inlet MA23 reaches 100bar, the sequence valve B5 is opened, and the pressure oil passes through the sequence valve B5, the one-way valve A7 and the one-way valve B8 and then enters a variable control mechanism of the hydraulic pump through the output oil port XIIIA21 and the output oil port XIIIB 25;
e3. under the action of the shuttle valve 6 and the overflow valve 13, the oil pressure of the output oil port XIIIA21 and the output oil port XIIIB 25 is limited to 40bar, the displacement of the hydraulic pump is increased under the action of pressure oil, so that the oil output by the motor is absorbed, the oil pressure of the oil inlet MA23 is kept not to rise any more, the reverse hydraulic braking force reaches the limited maximum value at the moment, and the whole vehicle is decelerated under the action of hydraulic braking;
f3. when the vehicle speed is reduced to a certain value to excite, the original low-pressure side pressure of the running loop, namely the oil pressure of the oil inlet MA23, is reduced to be lower than 100bar, the sequence valve B5 is closed, and the displacement of the pump is restored to the running handle control state. Steps a3, b3, c3, d3, e3, f3 are sequentially performed.

Claims (10)

1. The reverse braking control valve for the hydraulic traveling system comprises a valve body 15, wherein a two-position three-way electromagnetic valve A (1) and a two-position three-way electromagnetic valve B (3) are arranged in the valve body 15, the two-position three-way electromagnetic valve A (1) and the two-position three-way electromagnetic valve B (3) both comprise orifices, the upstream of the two-position three-way electromagnetic valve A (1) is connected with an oil inlet MB (20), and the upstream of the two-position three-way electromagnetic valve B (3) is connected with an oil inlet MA (23); the method is characterized in that: the downstream of the two-position three-way electromagnetic valve A (1) is connected with the sequence valve A (14), the downstream of the sequence valve A (14) is respectively connected with an output oil port XIV through a one-way valve C (11) and a one-way valve D (12), the downstream of the two-position three-way electromagnetic valve B (3) is connected with the sequence valve B (5), the downstream of the sequence valve B (5) is respectively connected with an output oil port XIII through a one-way valve A (7) and a one-way valve B (8), a two-position two-way electromagnetic valve B (9) is further arranged between the output oil port XIII of the downstream of the one-way valve A (7) and the output oil port XIV of the downstream of the one-way valve C (11), a two-position two-way electromagnetic valve A (10) is further arranged between the output oil port XIII of the downstream of the one-way valve B (8) and the output oil port XIV of the downstream of the one-way valve D (12), a shuttle valve (6) is further connected between the downstream of the sequence valve A (14) and the downstream of the sequence valve B (5), and the shuttle valve (6) is connected with the overflow valve (13).
2. The reverse brake control valve for a hydraulic travel system according to claim 1, wherein: the pressure range of the overflow valve is 40-50bar, the oil outlet of a shuttle valve (6) arranged between the oil paths behind a sequence valve A (14) and a sequence valve B (5) in two branches is connected with the overflow valve, no matter which branch is pressure oil, the pressure oil can reach the inlet of the overflow valve through the shuttle valve, and when the pressure of the pressure oil reaches the set pressure of the overflow valve, the overflow is started, so that the highest pressure of the pressure oil behind the sequence valve A (14) and the sequence valve B (5) is limited to be not more than 40-50bar.
3. The reverse brake control valve for a hydraulic travel system according to claim 1, wherein: and the oil inlet MA (23) and the oil inlet MB (20) are respectively connected with the main oil ports A and B of the hydraulic traveling system driving circuit.
4. The reverse brake control valve for a hydraulic travel system according to claim 1, wherein: the overflow valve (13) is also connected with a K3 pressure measuring port (18), the sequence valve A (14) is connected with a K1 pressure measuring port (16), and the sequence valve B (5) is connected with a K2 pressure measuring port (17).
5. The reverse brake control valve for a hydraulic travel system according to claim 1, wherein: the two-position three-way electromagnetic valve A (1) comprises a fixed orifice A (2), and the diameter of the fixed orifice A (2) is 2-3mm.
6. The reverse brake control valve for a hydraulic travel system according to claim 1, wherein: the two-position three-way electromagnetic valve B (3) comprises a fixed orifice B (4), and the diameter of the fixed orifice B (4) is 2-3mm.
7. The reverse brake control valve for a hydraulic travel system according to claim 1, wherein: the set pressures of the sequence valve A (14) and the sequence valve B (5) are the maximum pressures of the hydraulic reverse braking, and the range of the set pressures of the sequence valve A (14) and the sequence valve B (5) is 90-120bar.
8. A control method of a reverse brake control valve for a hydraulic travel system according to claim 1, characterized by comprising:
a1. in the self-running process of the working vehicle, the working vehicle is connected with the high-pressure side and the low-pressure side of a main loop of a running system through an oil inlet MA23 and an oil inlet MB20, and oil liquid at the low-pressure side reaches a sequence valve through a two-position three-way electromagnetic valve and a fixed orifice by controlling the power-on and power-off condition of the two-position three-way electromagnetic reversing valve;
b1. the oil liquid at the high pressure side is not communicated with the sequence valve, when the oil liquid is pulled back to slow down through a traveling handle or runs on a long and large ramp, the working conditions of a pump and a motor of a traveling loop are changed, the pressure at the high pressure side and the pressure at the low pressure side of the system are also changed, the pressure at the original low pressure side is increased, a traveling driving loop generates reverse hydraulic braking force, the speed of the whole vehicle is gradually reduced or the speed is not increased any more, when the pressure at the original low pressure side is increased to reach the set pressure of the sequence valve, the sequence valve is communicated, and the displacement of the pump is automatically controlled by a variable control cylinder of the pressure oil entering the hydraulic pump to be rapidly increased, so that the output flow of the hydraulic motor is absorbed, and the pressure at the original low pressure side is kept not increased any more;
c1. when the vehicle speed is reduced to a certain value, the low-pressure side pressure is reduced to be lower than the opening pressure of the sequence valve, the sequence valve is closed, and the displacement of the hydraulic pump is restored to the state of original running handle control;
steps a1, b1 and c1 are sequentially executed to achieve the reverse braking control of the hydraulic traveling system.
9. A control method of a reverse brake control valve for a hydraulic travel system according to claim 1, characterized by comprising the steps of:
a2. sequence valve A14 and sequence valve B5 set 100bar and relief valve 13 set 40bar; forward self-walking, and the reverse braking pressure is not more than 100bar;
b2. when the pushing handle moves forwards, the two-position two-way electromagnetic valves 9 and 10 are powered, the output oil port XIIIA21 is disconnected from the output oil port XIVA22, and the output oil port XIIIB 25 is disconnected from the output oil port XIVB 24; assuming that the connection with the oil inlet MA23 is a high-pressure side and the connection with the oil inlet MB20 is a low-pressure side, at the moment, the two-position three-way electromagnetic valve 1 is powered off, the oil inlet MB20 is connected with the sequence valve A14, the two-position three-way electromagnetic valve 3 is powered on, and the oil inlet MA23 is disconnected with the sequence valve B5; when the hydraulic pump runs forward normally, the low-pressure side pressure of the running loop is about 28bar, the sequence valve A14 is in a closed state, and the hydraulic pump works under the control of the running handle;
c2. when the whole vehicle on the downhill road section is pulled back to the running handle to be decelerated due to inertial acceleration or normal running, the motor becomes a pump working condition, the pressure of the oil inlet MB20 rises, the faster the vehicle is accelerated or the handle is pulled back, the faster the pressure of the oil inlet MB20 rises, and the running system can generate reverse hydraulic braking force due to the fact that the motor becomes the pump working condition;
d2. when the pressure of the oil inlet MB20 reaches 100bar, the sequence valve A14 is opened, pressure oil passes through the sequence valve A14, the one-way valve C11 and the one-way valve D12, and then enters a variable control mechanism of the hydraulic pump through the output oil port XIVA22 and the output oil port XIVB 24, under the action of the shuttle valve 6 and the overflow valve 13, the oil pressure of the oil port XIV is limited to 40bar, the displacement of the hydraulic pump is increased under the action of the pressure oil, so that the oil output by the motor is absorbed, the oil pressure of the oil inlet MB20 is kept not to rise, the reverse hydraulic braking force reaches the limited maximum value at the moment, and the whole vehicle is decelerated under the action of hydraulic braking;
e2. when the speed of the vehicle is reduced to a certain value, the original low-pressure side of the running loop, namely the oil pressure of the oil inlet MB20, is reduced to be lower than 100bar, the sequence valve A14 is closed, and the displacement of the pump is restored to the running handle control state;
f2. when the whole vehicle is in a static state, the two-position two-way electromagnetic valve A9 and the two-position two-way electromagnetic valve B10 are powered off, and two groups of output oil ports XIII and XIV are communicated, namely an output oil port XIIIA21 is communicated with an output oil port XIVA22, and an output oil port XIIIB 25 is communicated with an output oil port XIVB 24; the hydraulic pump is in a bypass state and variable control cannot be performed, so that misoperation of hydraulic pump control is effectively avoided, and parking safety is improved;
the method is characterized in that: steps a2, b2, c2, d2, e2, f2 are performed sequentially.
10. A control method of a reverse brake control valve for a hydraulic travel system according to claim 1, characterized by comprising:
a3. sequence valve A14 and sequence valve B5 set 100bar and relief valve 13 set 40bar; the vehicle is self-propelled backwards, and the reverse braking pressure is not more than 100bar;
b3. when the pushing handle moves forwards, the two-position two-way electromagnetic valves 9 and 10 are powered, the output oil port XIIIA21 is disconnected from the output oil port XIVA22, and the output oil port XIIIB 25 is disconnected from the output oil port XIVB 24; assuming that the connection with the oil inlet MA23 is a low-pressure side and the connection with the oil inlet MB20 is a high-pressure side, at the moment, the two-position three-way electromagnetic valve 1 is powered on, the oil inlet MB20 is disconnected from the sequence valve A14, the two-position three-way electromagnetic valve 3 is powered off, and the oil inlet MA23 is connected with the sequence valve B5;
c3. when the hydraulic pump runs backwards normally, the low-pressure side pressure of the running loop is about 28bar, the sequence valve B5 is in a closed state, and the hydraulic pump works under the control of the running handle; when the whole vehicle on the downhill road section is pulled back to the running handle to be decelerated due to inertial acceleration or normal running, the motor becomes a pump working condition, the pressure of the oil inlet MA23 rises, the faster the vehicle is accelerated or the handle is pulled back, the faster the pressure of the oil inlet MA23 rises, and the running system can generate reverse hydraulic braking force due to the fact that the motor becomes the pump working condition;
d3. when the pressure of the oil inlet MA23 reaches 100bar, the sequence valve B5 is opened, and the pressure oil passes through the sequence valve B5, the one-way valve A7 and the one-way valve B8 and then enters a variable control mechanism of the hydraulic pump through the output oil port XIIIA21 and the output oil port XIIIB 25;
e3. under the action of the shuttle valve 6 and the overflow valve 13, the oil pressure of the output oil port XIIIA21 and the output oil port XIIIB 25 is limited to 40bar, the displacement of the hydraulic pump is increased under the action of pressure oil, so that the oil output by the motor is absorbed, the oil pressure of the oil inlet MA23 is kept not to rise any more, the reverse hydraulic braking force reaches the limited maximum value at the moment, and the whole vehicle is decelerated under the action of hydraulic braking;
f3. when the vehicle speed is reduced to a certain value to excite, the original low-pressure side pressure of the running loop, namely the oil pressure of the oil inlet MA23, is reduced to be lower than 100bar, the sequence valve B5 is closed, and the discharge capacity of the pump is restored to the running handle control state;
steps a3, b3, c3, d3, e3, f3 are sequentially performed.
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Publication number Priority date Publication date Assignee Title
CN110843904A (en) * 2019-11-14 2020-02-28 湘电重型装备有限公司 Integrated steering and braking control system of large electric wheel dumper
CN110778551B (en) * 2019-11-30 2024-04-30 安徽柳工起重机有限公司 Full-closed hydraulic system of crane
CN114352597B (en) * 2022-01-25 2024-04-23 佳木斯大学 Overload reverse impact valve and overload prevention method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06345387A (en) * 1993-06-07 1994-12-20 Tadano Ltd Control pressure oil supplier for hydraulically-driven winch
CN104564885A (en) * 2015-01-08 2015-04-29 宁波宇洲液压科技有限公司 High-integration bidirectional rotary valve for pilot control mode
WO2015165344A1 (en) * 2014-04-29 2015-11-05 三一汽车制造有限公司 Rotary hydraulic system and concrete conveying pump apparatus
CN106088208A (en) * 2016-06-21 2016-11-09 柳州柳工挖掘机有限公司 Excavator revolution hydraulic control system
CN205876871U (en) * 2016-05-25 2017-01-11 华侨大学 Automatic actuating system of retrieving and recycling of engineering machine tool revolving stage energy
CN207989417U (en) * 2017-12-28 2018-10-19 中国铁建高新装备股份有限公司 A kind of hydraulic pressure walking system plugging control valve

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2267328B (en) * 1992-05-22 1995-06-14 Linde Ag Hydrostatic drive system
CN101649849B (en) * 2008-08-14 2012-05-23 陈庆桐 Brake circuit of hydraulic motor
DE102011101921A1 (en) * 2011-05-18 2012-11-22 Linde Material Handling Gmbh Hydraulic brake valve device for use in wheel or chain excavators for controlling discharge side of internal combustion engine, has pre-opening connecting side of load with container and switchable between locking and flow positions
CN102897159A (en) * 2012-09-07 2013-01-30 徐州万邦道路工程装备服务股份公司 Hydraulic brake system of spreading machine
CN202945535U (en) * 2012-11-16 2013-05-22 陕西中大机械集团有限责任公司 Hydraulic control system for vibration and travel braking of small double-steel-wheel road roller
CN203805886U (en) * 2014-05-16 2014-09-03 山推工程机械股份有限公司 Brake control device for hydraulic drive engineering vehicles
CN205478612U (en) * 2016-04-05 2016-08-17 山推工程机械股份有限公司 Engineering machine tool hydraulic braking system
CN106348167A (en) * 2016-11-07 2017-01-25 安徽理工大学 Spring single-braking manual control mine monorail crane walking mechanism hydraulic system

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06345387A (en) * 1993-06-07 1994-12-20 Tadano Ltd Control pressure oil supplier for hydraulically-driven winch
WO2015165344A1 (en) * 2014-04-29 2015-11-05 三一汽车制造有限公司 Rotary hydraulic system and concrete conveying pump apparatus
CN104564885A (en) * 2015-01-08 2015-04-29 宁波宇洲液压科技有限公司 High-integration bidirectional rotary valve for pilot control mode
CN205876871U (en) * 2016-05-25 2017-01-11 华侨大学 Automatic actuating system of retrieving and recycling of engineering machine tool revolving stage energy
CN106088208A (en) * 2016-06-21 2016-11-09 柳州柳工挖掘机有限公司 Excavator revolution hydraulic control system
CN207989417U (en) * 2017-12-28 2018-10-19 中国铁建高新装备股份有限公司 A kind of hydraulic pressure walking system plugging control valve

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