CN108658019B - A kind of working bucket leveling system of high-altitude operation vehicle - Google Patents
A kind of working bucket leveling system of high-altitude operation vehicle Download PDFInfo
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- CN108658019B CN108658019B CN201810715474.2A CN201810715474A CN108658019B CN 108658019 B CN108658019 B CN 108658019B CN 201810715474 A CN201810715474 A CN 201810715474A CN 108658019 B CN108658019 B CN 108658019B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F11/00—Lifting devices specially adapted for particular uses not otherwise provided for
- B66F11/04—Lifting devices specially adapted for particular uses not otherwise provided for for movable platforms or cabins, e.g. on vehicles, permitting workmen to place themselves in any desired position for carrying out required operations
- B66F11/044—Working platforms suspended from booms
- B66F11/046—Working platforms suspended from booms of the telescoping type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
- B66C23/64—Jibs
- B66C23/70—Jibs constructed of sections adapted to be assembled to form jibs or various lengths
- B66C23/701—Jibs constructed of sections adapted to be assembled to form jibs or various lengths telescopic
- B66C23/705—Jibs constructed of sections adapted to be assembled to form jibs or various lengths telescopic telescoped by hydraulic jacks
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
- B66C23/82—Luffing gear
- B66C23/821—Bracing equipment for booms
- B66C23/826—Bracing equipment acting at an inclined angle to vertical and horizontal directions
- B66C23/828—Bracing equipment acting at an inclined angle to vertical and horizontal directions where the angle is adjustable
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- 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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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- 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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- 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
- F15B2013/004—Cartridge valves
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
- F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
- F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7053—Double-acting output members
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7057—Linear output members being of the telescopic type
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
- F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Fluid-Pressure Circuits (AREA)
- Forklifts And Lifting Vehicles (AREA)
- Operation Control Of Excavators (AREA)
Abstract
The invention discloses a kind of working bucket leveling systems of high-altitude operation vehicle, and wherein main valve can be inserted valve or multi-way valve；Maximum load pressure on telescopic oil cylinder and amplitude oil cylinder feeds back to the load-sensitive hydraulic fluid port LS of constant-pressure drop variable pump；The main valve pressure oil port P is equipped with reversal valve with the leveling valve pressure oil port P oil circuit connecting, when reversal valve is in spring position, the pressure oil port P pressure for leveling valve is zero, when reversal valve commutation, constant-pressure drop variable pump pressure oil port P is connected to by speed governing valve with the P mouth for leveling valve, and levels the load-sensitive hydraulic fluid port LS that valve P mouthfuls of pressure feeds back to constant-pressure drop variable pump by being connected to the check valve of reversal valve oil outlet.Working bucket leveling of the present invention is convenient for control, and leveling movement is without lag, and system response is fast, and simultaneity factor is always load sensitive system, energy-saving.
Description
Technical field
The present invention relates to a kind of engineering truck leveling systems, and in particular to a kind of working bucket leveling system of high-altitude operation vehicle,
Belong to engineering machinery hydraulic control technology field.
Background technique
High-altitude operation vehicle is that staff and equipment are transported to a kind of equipment that specified altitude assignment carries out operation, belongs to special type
Operating equipment, structure as shown in Figure 1, include chassis 1, turntable 2, amplitude oil cylinder 3, telescopic oil cylinder 4, basic arm 5, two joint arms 6,
Leveling cyclinder 7 and working bucket 8, amplitude oil cylinder 3 drive luffing range of cantilever support, and telescopic oil cylinder 4 drives the flexible of cantilever crane, and leveling cyclinder 7 is used
In the angle for adjusting working bucket 8.
When high-lift operation car require working bucket 8 always with horizontal plane keeping parallelism, to guarantee the peace of operator
It is complete and comfortable.Therefore leveling performance is to measure an important indicator of vehicle.Working bucket 8 levels working principle, as shown in Figure 2.
When luffing range of cantilever support, 8 bottom surface of working bucket will no longer keep horizontal, at this time 9 collecting work bucket of obliquity sensor, 8 dip angle signal, warp
After crossing the processing of controller 10, driving 11 spool of electro-hydraulic proportional valve makes corresponding actions, and 7 cylinder rod of leveling cyclinder is made to stretch out or retract,
To directly drive rotation or backspin in working bucket 8, realize that working bucket 8 is horizontal.
There are two types of the leveling of working bucket 8 fuel system is usual: 1. gear pump (constant displacement pump) individually gives leveling fuel feeding；2. working bucket
8 leveling movement acts with boom frame telescopic, luffing and shares a plunger pump (variable pump).Wherein, the 2. kind leveling fuel system due to
It does not need to be allocated to the gear pump for leveling independent fuel feeding and have the advantages that at low cost, easy arrangement and be widely used.
In the 2. kind leveling fuel system, usual oil pump is located at lower chassis, between oil pump and working bucket 8 compared with pipeline
It is long.It is smaller that working bucket 8 levels flow, if working bucket 8 levels conventional load sensory system, system responds slow, leveling
Lag is than more serious, so 8 leveling system of working bucket mostly uses greatly constant-voltage system, as long as system is constant pressure system when that is, luffing acts
System.
8 leveling system of working bucket in the prior art mainly includes constant-pressure drop variable pump, main valve, leveling valve, telescopic oil cylinder
4, amplitude oil cylinder 3 and leveling cyclinder 7.Constant-pressure drop variable pump controls telescopic oil cylinder 4 by main valve and amplitude oil cylinder 3 acts, simultaneously
Oil liquid is provided to leveling cyclinder 7.When independent expanding-contracting action, system is load sensitive system, constant-pressure drop variable pump discharge pressure
A preset fixed value higher than load pressure, rate of discharge are load working flow；When the movement of independent luffing, constant-pressure drop becomes
Amount pump is used as constant pressure variable displacement pump, and system is constant-voltage system, is changed by changing the openings of sizes of electromagnetic proportional valve in leveling valve
Level flow；When flexible, luffing composite move, constant-pressure drop variable pump is used as constant pressure variable displacement pump at this time, and system is constant-voltage system,
Change leveling flow by changing the openings of sizes of electromagnetic proportional valve in leveling valve.
There are following technological deficiencies for above-mentioned leveling system: 1), when independent luffing acts or flexible, luffing composite move
When, system is constant-voltage system, therefore 13 outlet pressure of constant-pressure drop variable pump is always held at maximum value, with load sensitive system phase
Than energy consumption is big；2), working bucket leveling movement will appear the phenomenon that system low-response, leveling lag；3) electromagnetism ratio in valve, is leveled
Example valve both ends pressure difference changes with load and is changed, therefore the leveling of working bucket 8 is not easy to control.
Summary of the invention
In order to overcome deficiencies of the prior art, the present invention provides a kind of working bucket leveling system of high-altitude operation vehicle
System, working bucket leveling is convenient for control, and without lag, system response is fast while energy-saving for leveling movement.
To solve the above-mentioned problems, a kind of working bucket leveling system of high-altitude operation vehicle of the present invention, including constant-pressure drop variable
Pump, main valve, leveling valve, telescopic oil cylinder, amplitude oil cylinder and leveling cyclinder；Constant-pressure drop variable pump pressure oil port P and main valve pressure oil
Mouth P is connected, and constant-pressure drop variable pump load feedback hydraulic fluid port LS is connected with main valve load feedback hydraulic fluid port LS, and hydraulic oil passes through main valve and enters
Telescopic oil cylinder and amplitude oil cylinder are to control expanding-contracting action and luffing movement；The pressure oil port P of main valve and the pressure oil of leveling valve
Mouth P is connected, and the oil return inlet T of main valve is connected with the oil return inlet T of leveling valve, and hydraulic oil enters leveling cyclinder by leveling valve to control
The leveling of leveling cyclinder processed acts；It is characterized in that, the main valve can be inserted valve or multi-way valve；Telescopic oil cylinder and luffing
Maximum load pressure on oil cylinder feeds back to the load-sensitive hydraulic fluid port LS of constant-pressure drop variable pump；The main valve pressure oil port P with
The oil circuit of leveling valve pressure oil port P connection is equipped with reversal valve and levels the pressure oil port P of valve when reversal valve is in spring position
Pressure is zero, and when reversal valve commutation, constant-pressure drop variable pump pressure oil port P is by flow rate adjustment device and the P mouth company for leveling valve
It is logical, and the check valve by being connected to reversal valve oil outlet feeds back to the load-sensitive hydraulic fluid port LS of constant-pressure drop variable pump.
Since the maximum load pressure on telescopic oil cylinder and amplitude oil cylinder feeds back to the load-sensitive of constant-pressure drop variable pump
Hydraulic fluid port LS, and the pressure oil port P for leveling valve feeds back to the load-sensitive hydraulic fluid port LS of constant-pressure drop variable pump also by check valve, therefore
Either expanding-contracting action, luffing movement, or luffing stretch composite move when, system is load sensitive system, energy conservation and environmental protection；
When independent expanding-contracting action, reversal valve is in spring position, therefore no pressure oil enters leveling valve and leveling cyclinder, becomes when independent
When width movement or flexible luffing composite move, reversal valve is in commutation, therefore pressure oil passes through stream while entering main valve
Velocity modulation regulating device and reversal valve enter leveling cyclinder, level no lag that is swift in motion.
Further, the leveling valve includes the first shuttle valve, 3-position 4-way electromagnetic proportional valve and pressure-differentially-set valve, pressure-differentially-set valve
A hydraulic fluid port, c hydraulic fluid port and 3-position 4-way electromagnetic proportional valve oil inlet be connected in parallel at the pressure oil port P of leveling valve simultaneously, three
First oil outlet of four-way electromagnetic proportioning valve and the first oil inlet of the first shuttle valve are connected in parallel on the rod chamber end of leveling cyclinder, and three
Second oil outlet of position four-way electromagnetic proportioning valve and the second oil inlet of the first shuttle valve are connected in parallel on the rodless cavity end of leveling cyclinder,
The oil outlet of first shuttle valve is by the d hydraulic fluid port of pressure feedback to pressure-differentially-set valve, the oil return opening and level pressure of 3-position 4-way electromagnetic proportional valve
The b hydraulic fluid port of difference limen is connected in parallel to the oil return line T of system.
First shuttle valve feeds back to pressure-differentially-set valve using the larger pressure in leveling cyclinder both ends as feedback pressure, therefore makes three four
The pressure difference of logical electromagnetic proportional valve oil inlet and oil return opening remains constant always, passes through the flow of 3-position 4-way electromagnetic proportional valve at this time
It is only related with the openings of sizes of 3-position 4-way electromagnetic proportional valve, therefore the opening of the first three position four-way electromagnetic valve of change can be passed through
Size changes leveling flow, control it is more simple, leveling movement more it is accurate fast.
Specifically, when main valve be inserted valve when, including overflow valve, operated proportional flow control valve, three-position four-way electromagnetic directional valve,
Shuttle valve and check valve, the oil inlet of the overflow valve, the oil inlet of the first operated proportional flow control valve and the control of the second proportional flow
The oil inlet of valve is connected with the pressure oil port P of main valve, the oil outlet of the first operated proportional flow control valve and the first 3-position 4-way electricity
The oil inlet of magnetic reversal valve is connected, the oil inlet of the oil outlet of the second operated proportional flow control valve and the second three-position four-way electromagnetic directional valve
Mouth is connected, and the first oil outlet of the first three-position four-way electromagnetic directional valve and the first oil inlet of the second shuttle valve are connected in parallel on telescopic oil cylinder
Rod chamber end, the second oil outlet of the first three-position four-way electromagnetic directional valve is connected in parallel on flexible with the second oil inlet of the second shuttle valve
The rodless cavity end of oil cylinder, the first oil outlet of the second three-position four-way electromagnetic directional valve are connected in parallel on the first oil inlet of third shuttle valve
Second oil inlet of the rod chamber end of amplitude oil cylinder, the second oil outlet of the second three-position four-way electromagnetic directional valve and third shuttle valve is simultaneously
It is associated in the rodless cavity end of amplitude oil cylinder, the oil outlet of the second shuttle valve is connected with the oil inlet of second one-way valve, and third shuttle valve goes out
Hydraulic fluid port is connected with the oil inlet of third check valve, the oil outlet of the first check valve, second one-way valve and third check valve with master
The load feedback hydraulic fluid port LS of valve is connected, the oil return opening of the first three-position four-way electromagnetic directional valve, the second three-position four-way electromagnetic directional valve
Oil return opening, the oil return opening of reversal valve and the oil outlet of overflow valve be connected with the oil return inlet T of main valve.
The reversal valve is two-bit triplet solenoid directional control valve, and the flow rate adjustment device is speed governing valve.
Specifically, when main valve is multi-way valve, including first, flexible connection, luffing connection, leveling connection and tail connection, wherein stretching
Connection, luffing connection and leveling connection include pressure-differentially-set valve, hydraulic control proportional reversing valve and check valve, the first hydraulic control proportional reversing valve, the
Two hydraulic control proportional reversing valves, third hydraulic control proportional reversing valve oil inlet be connected with the pressure oil port P of main valve, the first hydraulic control ratio
Example reversal valve, the second hydraulic control proportional reversing valve, third hydraulic control proportional reversing valve oil return opening be connected with the oil return inlet T of main valve；
The control port of first pressure-differentially-set valve, the second pressure-differentially-set valve and third pressure-differentially-set valve with the load-sensitive hydraulic fluid port LS phase of main valve
Even；The left side control port of first hydraulic control proportional reversing valve is connected with the first electric proportional pressure-reducing valve, the first hydraulic control proportional reversing valve
Right side control port be connected with the second electric proportional pressure-reducing valve, the left side control port of the second hydraulic control proportional reversing valve and third are electric
Proportional pressure-reducing valve is connected, and the right side control port of the second hydraulic control proportional reversing valve is connected with the 4th electric proportional pressure-reducing valve, third liquid
The left side control port for controlling proportional reversing valve is connected with the 5th electric proportional pressure-reducing valve, the right side control of third hydraulic control proportional reversing valve
Hydraulic fluid port is directly connected with fuel tank.
Further, the first hydraulic control proportional reversing valve, the second hydraulic control proportional reversing valve, third hydraulic control proportional reversing valve are
Three eight logical reversal valves, a hydraulic fluid port of reversal valve is connected to c hydraulic fluid port, and is connected in parallel to oil return inlet T, b hydraulic fluid port with pressure oil port T
It is connected, the d hydraulic fluid port and h hydraulic fluid port of the first hydraulic control proportional reversing valve are connected with the rod chamber end of telescopic oil cylinder and rodless cavity end respectively,
The d hydraulic fluid port and h hydraulic fluid port of second hydraulic control proportional reversing valve are connected with the rod chamber end of amplitude oil cylinder and rodless cavity end respectively, third liquid
The d hydraulic fluid port and h hydraulic fluid port for controlling proportional reversing valve are connected with the pressure oil port P and oil return inlet T of main valve respectively, the commutation of the first hydraulic control ratio
The e hydraulic fluid port and g hydraulic fluid port of valve are connected in parallel to the oil outlet of the first pressure-differentially-set valve, while the oil outlet of the first pressure-differentially-set valve and the 4th list
It is connected to the oil inlet of valve, the e hydraulic fluid port and g hydraulic fluid port of the second hydraulic control proportional reversing valve are connected in parallel to the oil outlet of the second pressure-differentially-set valve
Place, while the oil outlet of the second pressure-differentially-set valve is connected with the oil inlet of the 5th check valve, the e hydraulic fluid port of third hydraulic control proportional reversing valve
Be connected in parallel to the oil outlet of third pressure-differentially-set valve with g hydraulic fluid port, at the same the oil outlet of third pressure-differentially-set valve and the 6th check valve into
Hydraulic fluid port is connected；The oil inlet that the f hydraulic fluid port of first hydraulic control proportional reversing valve determines differential valve with first is connected, the commutation of the second hydraulic control ratio
The oil inlet that the f hydraulic fluid port of valve determines differential valve with second is connected, and the f hydraulic fluid port and third of third hydraulic control proportional reversing valve determine differential valve
Oil inlet is connected.
Constant-pressure drop variable pump in the present invention acts fuel feeding to working bucket leveling with constant flow rate by main valve and leveling valve,
Due to the pressure-differentially-set valve of the 3-position 4-way electromagnetic proportional valve both ends setting in leveling valve, it can guarantee 3-position 4-way electromagnetism ratio
Example valve both ends pressure difference is constant, only related with 3-position 4-way electromagnetic proportional valve opening by flow, therefore working bucket leveling is convenient for control
System；It is controlled and is commutated by reversal valve, leveling valve is flowed into without hydraulic oil when only expanding-contracting action, when luffing or flexible luffing are compound
When movement, hydraulic oil will also pass through speed governing valve and flow into leveling valve while flowing into amplitude oil cylinder, so working bucket leveling movement is not
It will appear system low-response, leveling hysteresis；Cantilever crane is multiple in independent expanding-contracting action, the movement of independent luffing and flexible luffing simultaneously
Conjunction is load sensitive system when acting, energy-saving；The main valve in this system is not limited only to inserted valve simultaneously, can also be applicable in
In multi-way valve, therefore it can be used for various working, the scope of application is wider.
Detailed description of the invention
Fig. 1 is high-altitude operation vehicle structural schematic diagram；
Fig. 2 is the working bucket leveling working principle structural schematic diagram in Fig. 1；
Fig. 3 is a kind of working bucket leveling system structure diagram of the invention；
Fig. 4 is another working bucket leveling system structure diagram of the invention；
Fig. 5 is the first hydraulic control proportional reversing valve or the second hydraulic control proportional reversing valve or third hydraulic control proportional reversing valve in Fig. 4
Enlarged diagram；
In figure: 1, chassis, 2, turntable, 3, amplitude oil cylinder, 4, telescopic oil cylinder, 5, basic arm, 6, two joint arms, 7, leveling oil
Cylinder, 8, working bucket, 9, obliquity sensor, 10, controller, 11, electro-hydraulic proportional valve, 12, leveling cyclinder balanced valve；
23, constant-pressure drop variable pump, 28, main valve, 281, speed governing valve, 282, overflow valve, the 283, first operated proportional flow control valve,
284, the first three-position four-way electromagnetic directional valve, the 285, second shuttle valve, the 286, second operated proportional flow control valve, 287, the 2nd 3 four
Electric change valve, 288, third shuttle valve, 289, two-bit triplet solenoid directional control valve, 2810, second one-way valve, 2811, third list
To valve, the 2812, first check valve, 29, leveling valve, the 291, first three-position four-way electromagnetic directional valve, the 292, first shuttle valve, 293, fixed
Valve for pressure difference, 33, amplitude oil cylinder, 34, telescopic oil cylinder, 37, leveling cyclinder, 41, first, 42, flexible connection, the 421, first electric ratio subtract
Pressure valve, the 422, second electric proportional pressure-reducing valve, the 423, first hydraulic control proportional reversing valve, the 424, first pressure-differentially-set valve, the 425, the 4th is single
To valve, 43, luffing connection, 431, third electricity proportional pressure-reducing valve, the 432, the 4th electric proportional pressure-reducing valve, the commutation of the 433, second hydraulic control ratio
Valve, the 434, second pressure-differentially-set valve, the 435, the 5th check valve, 44, leveling connection, the 441, the 5th electric proportional pressure-reducing valve, 442, third liquid
Control proportional reversing valve, 443, third pressure-differentially-set valve, the 444, the 6th check valve, 45, tail connection
Specific embodiment
The present invention is described in detail in the following with reference to the drawings and specific embodiments.
Embodiment one
As shown in figure 3, a kind of working bucket leveling system of high-altitude operation vehicle, including constant-pressure drop variable pump 23, main valve 28, tune
Flat valve 29, telescopic oil cylinder 34, amplitude oil cylinder 33 and leveling cyclinder 37；23 pressure oil port P of constant-pressure drop variable pump and 28 pressure of main valve
Hydraulic fluid port P is connected, and 23 load feedback hydraulic fluid port LS of constant-pressure drop variable pump is connected with 28 load feedback hydraulic fluid port LS of main valve, and hydraulic oil passes through master
Valve 28 enters telescopic oil cylinder 34 and amplitude oil cylinder 33 to control expanding-contracting action and luffing movement；The pressure oil port P1 of main valve 28 with
The pressure oil port P for leveling valve 29 is connected, and the oil return inlet T 1 of main valve 28 is connected with the oil return inlet T of leveling valve 29, and hydraulic oil passes through tune
Flat valve 29 enters leveling cyclinder 37 to control the leveling movement of leveling cyclinder 37；The main valve 28 is inserted valve；Telescopic oil cylinder
34 and amplitude oil cylinder 33 on maximum load pressure feed back to the load-sensitive hydraulic fluid port LS of constant-pressure drop variable pump 23；
The main valve 28 includes overflow valve 282, operated proportional flow control valve, three-position four-way electromagnetic directional valve, shuttle valve, unidirectional
Valve, two-bit triplet solenoid directional control valve 289 and speed governing valve 281., oil inlet, the first operated proportional flow control valve of the overflow valve 282
The oil inlet of 283 oil inlet and the second operated proportional flow control valve 286 is connected with the pressure oil port P of main valve 28, the first ratio
The oil outlet of flow control valve 283 is connected with the oil inlet of the first three-position four-way electromagnetic directional valve 284, the control of the second proportional flow
The oil outlet of valve 286 is connected with the oil inlet of the second three-position four-way electromagnetic directional valve 287, the first three-position four-way electromagnetic directional valve
First oil inlet of 284 the first oil outlet and the second shuttle valve 285 is connected in parallel on the rod chamber end of telescopic oil cylinder 34, and the one or three four
Second oil inlet of the second oil outlet of electric change valve 284 and the second shuttle valve 285 is connected in parallel on the rodless cavity of telescopic oil cylinder 34
End, the first oil outlet of the second three-position four-way electromagnetic directional valve 287 and the first oil inlet of third shuttle valve 288 are connected in parallel on luffing oil
The rod chamber end of cylinder 33, the second oil outlet of the second three-position four-way electromagnetic directional valve 287 and the second oil inlet of third shuttle valve 288
It is connected in parallel on the rodless cavity end of amplitude oil cylinder 33, the oil outlet of the second shuttle valve 285 is connected with the oil inlet of second one-way valve 2810, the
The oil outlet of three shuttle valves 288 is connected with the oil inlet of third check valve 2811, the first check valve 2812,2810 and of second one-way valve
The oil outlet of third check valve 2811 is connected with the load feedback hydraulic fluid port LS of main valve 28, the first three-position four-way electromagnetic directional valve
284 oil return opening, the oil return opening of the second three-position four-way electromagnetic directional valve 287, the oil return opening of reversal valve 289 and overflow valve 282
Oil outlet is connected with the oil return inlet T of main valve 28；The oil that the 28 pressure oil port P of main valve is connect with leveling 29 pressure oil port P of valve
Road is equipped with two-bit triplet solenoid directional control valve 289, when two-bit triplet 289 power loss of solenoid directional control valve, levels the pressure oil of valve 29
Mouth P pressure is zero, and when two-bit triplet solenoid directional control valve 289 obtains electric commutation, 23 pressure oil port P of constant-pressure drop variable pump is by speed regulation
Valve 281 is connected to the P mouth of leveling valve 29, and first by being connected to 289 oil outlet of two-bit triplet solenoid directional control valve is unidirectional
Valve 2812 feeds back to the load-sensitive hydraulic fluid port LS of constant-pressure drop variable pump 23；
The leveling valve 29 includes the first shuttle valve 292,3-position 4-way electromagnetic proportional valve 291 and pressure-differentially-set valve 293, and level pressure is poor
The a hydraulic fluid port of valve 293, the oil inlet of c hydraulic fluid port and 3-position 4-way electromagnetic proportional valve 291 while the pressure oil for being connected in parallel on leveling valve 29
At mouth P, the first oil inlet of the first oil outlet of 3-position 4-way electromagnetic proportional valve 291 and the first shuttle valve 292 is connected in parallel on leveling
Second oil inlet of the rod chamber end of oil cylinder 37, the second oil outlet of 3-position 4-way electromagnetic proportional valve 291 and the first shuttle valve is simultaneously
It is associated in the rodless cavity end of leveling cyclinder, the oil outlet of the first shuttle valve 292 is by the d hydraulic fluid port of pressure feedback to pressure-differentially-set valve 293, and three
The oil return opening of four-way electromagnetic proportioning valve 291 and the b hydraulic fluid port of pressure-differentially-set valve 293 are connected in parallel to the oil return line T of system.
The specific working principle is as follows:
A) when independent expanding-contracting action, the first three-position four-way electromagnetic directional valve 284 obtains electric, the second 3-position 4-way electromagnetic switch
289 power loss of valve 287 and two-bit triplet solenoid directional control valve, hydraulic oil individually flow into telescopic oil cylinder 34, two-bit triplet solenoid directional control valve
289 oil outlet mouths are connected with oil return opening, i.e. 2812 inlet pressure of the first check valve is zero, i.e. the P mouth pressure of leveling valve 29 is also
Zero；Expanding-contracting action load pressure is passed to the LS mouth of constant-pressure drop variable pump 23 by the second shuttle valve 285 by second one-way valve 2810,
System is load sensitive system at this time.
B) when independent luffing acts, 284 power loss of the first three-position four-way electromagnetic directional valve, the second 3-position 4-way electromagnetic switch
Valve 287 and two-bit triplet solenoid directional control valve 289 obtain electric, hydraulic oil inflow amplitude oil cylinder 33；Two-bit triplet solenoid directional control valve 289 into
Hydraulic fluid port is connected to oil outlet, and oil return opening is closed, and hydraulic oil is oily with the P confession of constant flow rate to leveling valve 29 by speed governing valve 281,
Excess traffic pours off from pressure-differentially-set valve 293, and working bucket leveling movement at this time is not in system low-response, leveling hysteresis；
Pressure-differentially-set valve 293 keeps 291 both ends pressure difference of 3-position 4-way electromagnetic proportional valve constant, passes through 3-position 4-way electromagnetic proportional valve 291 at this time
Flow only it is related with the opening of 3-position 4-way electromagnetic proportional valve 291, pass through change 3-position 4-way electromagnetic proportional valve 291 opening
Size changes leveling flow, easily facilitates control；The load pressure that third shuttle valve 288 is used to that luffing to be selected to act, third list
Luffing operating duty pressure and leveling operating duty pressure are compared to valve 2811 and the first check valve 2812, it will be biggish
Load passes to the LS mouth of constant-pressure drop variable pump 23, and luffing moving system is load sensitive system at this time.
C) when flexible, luffing composite move, the first three-position four-way electromagnetic directional valve 284, the second 3-position 4-way electromagnetism are changed
Must be electric to valve 287 and two-bit triplet solenoid directional control valve 289, hydraulic oil flows into telescopic oil cylinder 34 and amplitude oil cylinder 33 simultaneously；Two
289 oil inlet of three-way solenoid valve is connected to oil outlet, and oil return opening is closed, and hydraulic oil is by speed governing valve 281 with constant flow rate
To the P confession oil of leveling valve 29, excess traffic pours off from pressure-differentially-set valve 293, and working bucket leveling movement at this time is not in system
Low-response, leveling hysteresis；Pressure-differentially-set valve 293 keeps 291 both ends pressure difference of 3-position 4-way electromagnetic proportional valve constant, passes through three at this time
The flow of position four-way electromagnetic proportioning valve 291 is only related with the opening of 3-position 4-way electromagnetic proportional valve 291, by changing 3-position 4-way
The openings of sizes of electromagnetic proportional valve 291 changes leveling flow, easily facilitates control；Second shuttle valve 285 takes expanding-contracting action to load
Pressure, third shuttle valve 288 take luffing operating duty pressure, the first check valve 2812, second one-way valve 2810 and third check valve
2811 are compared leveling operating duty pressure, expanding-contracting action load pressure, luffing operating duty pressure, by biggish load
The LS mouth of constant-pressure drop variable pump 23 is passed to, is stretched at this time, luffing composite move system is load sensitive system.
Embodiment two
A kind of working bucket leveling system of high-altitude operation vehicle, including constant-pressure drop variable pump 23, main valve 28, leveling valve 29, stretch
Contracting oil cylinder 34, amplitude oil cylinder 33 and leveling cyclinder 37；23 pressure oil port P of constant-pressure drop variable pump is connected with 28 pressure oil port P of main valve,
23 load feedback hydraulic fluid port LS of constant-pressure drop variable pump is connected with 28 load feedback hydraulic fluid port LS of main valve, and hydraulic oil is entered by main valve 28 to be stretched
Contracting oil cylinder 34 and amplitude oil cylinder 33 are to control expanding-contracting action and luffing movement；The pressure oil port P1 of main valve 28 and leveling valve 29
Pressure oil port P is connected, and the oil return inlet T 1 of main valve 28 is connected with the oil return inlet T of leveling valve 29, and hydraulic oil is entered by leveling valve 29
Leveling cyclinder 37 acts to control the leveling of leveling cyclinder 37；The main valve is multi-way valve, including first 41, flexible connection 42,
Luffing connection 43, leveling connection 44 and tail connection 45, wherein flexible connection 42, luffing connection 43 and leveling connection 44 include pressure-differentially-set valve, hydraulic control
Proportional reversing valve and check valve, the first hydraulic control proportional reversing valve 423, the second hydraulic control proportional reversing valve 433, third hydraulic control ratio are changed
It is connected to the oil inlet of valve 442 with the pressure oil port P of main valve, the first hydraulic control proportional reversing valve 423, the commutation of the second hydraulic control ratio
Valve 433, third hydraulic control proportional reversing valve 442 oil return opening be connected with the oil return inlet T of main valve；First pressure-differentially-set valve 424, second
The control port of pressure-differentially-set valve 434 and third pressure-differentially-set valve 443 is connected with the load-sensitive hydraulic fluid port LS of main valve；First hydraulic control ratio
The left side control port of example reversal valve 423 is connected with the first electric proportional pressure-reducing valve 421, the right side of the first hydraulic control proportional reversing valve 423
Side control port is connected with the second electric proportional pressure-reducing valve 422, the left side control port and third of the second hydraulic control proportional reversing valve 433
Electric proportional pressure-reducing valve 431 is connected, the right side control port of the second hydraulic control proportional reversing valve 433 and the 4th electric proportional pressure-reducing valve 432
It is connected, the left side control port of third hydraulic control proportional reversing valve 442 is connected with the 5th electric proportional pressure-reducing valve 441, third hydraulic control ratio
The right side control port of example reversal valve 442 is directly connected with fuel tank；
As shown in Figure 4 and Figure 5, the first hydraulic control proportional reversing valve 423, the second hydraulic control proportional reversing valve 433, third hydraulic control ratio
Example reversal valve 442 is three eight logical reversal valves, and a hydraulic fluid port of reversal valve is connected to c hydraulic fluid port, and is connected in parallel to oil return inlet T, b oil
Mouth connects with pressure oil port T-phase, and the d hydraulic fluid port and h hydraulic fluid port of the first hydraulic control proportional reversing valve 423 has bar with telescopic oil cylinder 34 respectively
Chamber end is connected with rodless cavity end, and the d hydraulic fluid port and h hydraulic fluid port of the second hydraulic control proportional reversing valve 433 has bar with amplitude oil cylinder 33 respectively
Chamber end is connected with rodless cavity end, the d hydraulic fluid port and h hydraulic fluid port of third hydraulic control proportional reversing valve 442 respectively with the pressure oil port P1 of main valve
It is connected with oil return inlet T 1, the e hydraulic fluid port and g hydraulic fluid port of the first hydraulic control proportional reversing valve 423 are connected in parallel to the fuel-displaced of the first pressure-differentially-set valve 424
At mouthful, while the oil outlet of the first pressure-differentially-set valve 424 is connected with the oil inlet of the 4th check valve 425, the commutation of the second hydraulic control ratio
The e hydraulic fluid port and g hydraulic fluid port of valve 433 are connected in parallel to the oil outlet of the second pressure-differentially-set valve 434, while the second pressure-differentially-set valve 434 is fuel-displaced
Mouth is connected with the oil inlet of the 5th check valve 435, and it is fixed that the e hydraulic fluid port and g hydraulic fluid port of third hydraulic control proportional reversing valve 442 are connected in parallel to third
The oil outlet of valve for pressure difference 443, while the oil outlet of third pressure-differentially-set valve 443 is connected with the oil inlet of the 6th check valve 444；The
The oil inlet that the f hydraulic fluid port of one hydraulic control proportional reversing valve 423 determines differential valve 424 with first is connected, the second hydraulic control proportional reversing valve 433
The f hydraulic fluid port oil inlet of determining differential valve 434 with second be connected, the f hydraulic fluid port and third of third hydraulic control proportional reversing valve 442 determine differential pressure
The oil inlet of valve 443 is connected；
The leveling valve 29 includes the first shuttle valve 292,3-position 4-way electromagnetic proportional valve 291 and pressure-differentially-set valve 293, and level pressure is poor
The a hydraulic fluid port of valve 293, the oil inlet of c hydraulic fluid port and 3-position 4-way electromagnetic proportional valve 291 while the pressure oil for being connected in parallel on leveling valve 29
At mouth P, the first oil inlet of the first oil outlet of 3-position 4-way electromagnetic proportional valve 291 and the first shuttle valve 292 is connected in parallel on leveling
Second oil inlet of the rod chamber end of oil cylinder 37, the second oil outlet of 3-position 4-way electromagnetic proportional valve 291 and the first shuttle valve is simultaneously
It is associated in the rodless cavity end of leveling cyclinder, the oil outlet of the first shuttle valve 292 is by the d hydraulic fluid port of pressure feedback to pressure-differentially-set valve 293, and three
The oil return opening of four-way electromagnetic proportioning valve 291 and the b hydraulic fluid port of pressure-differentially-set valve 293 are connected in parallel to the oil return line T of system.
When leveling the 5th electric 441 power loss of proportional pressure-reducing valve in connection, 442 control terminal no pressure of third hydraulic control proportional reversing valve
Input, thus act on middle position, at this time without hydraulic oil by third hydraulic control proportional reversing valve 442, thus level connection 44 P1 mouth,
T1 mouthfuls of pressure are zero, and 444 inlet pressure of the 6th check valve is zero；When 5th electric proportional pressure-reducing valve 441 obtains electric, hydraulic control ratio is changed
To the work of valve 442 in left position, there is 442 control terminal of third hydraulic control proportional reversing valve a constant pressure to control its commutation, hydraulic
Oil is transferred at the oil inlet of the 6th check valve 444 by third hydraulic control proportional reversing valve 442, third pressure-differentially-set valve 443, with this
It is fed back at leveling connection pressure oil port P1 by third hydraulic control proportional reversing valve 442 again, due to third hydraulic control proportional reversing valve 442
Both ends connection third pressure-differentially-set valve 443, thus keep the pressure at its both ends constant, so the P1 mouth of leveling connection 44 is with steady flow
It measures to 29 fuel feeding of valve is leveled, at this time the 5th electric proportional pressure-reducing valve 441, third hydraulic control proportional reversing valve 442 and third pressure-differentially-set valve
443 collective effect is identical as the effect of two-bit triplet solenoid directional control valve and speed governing valve in inserted valve.
The specific working principle is as follows:
A) when independent expanding-contracting action, the 5th 441 power loss of electric proportional pressure-reducing valve, third hydraulic control proportional reversing valve 442 works
In middle position, the P1 mouth of leveling connection 44, T1 mouthfuls of pressure are zero, and 444 inlet pressure of the 6th check valve is zero；Flexible 42 load pressure of connection
Power passes to the LS mouth of constant-pressure drop variable pump 23 by the 4th check valve 425, and system is load sensitive system at this time.
B) when independent luffing acts, the 5th electric proportional pressure-reducing valve 441 must be electric, and voltage is a steady state value, third hydraulic control
The work of proportional reversing valve 442 is in left position, and P1 mouth of leveling connection 44 is with constant flow rate to leveling 29 fuel feeding of valve, and excess traffic is from level pressure
Difference limen 293 pours off, and working bucket leveling movement at this time is not in system low-response, leveling hysteresis；Pressure-differentially-set valve 293 makes three
Position four-way electromagnetic 291 both ends pressure differences of proportioning valve are constant, pass through the flow of 3-position 4-way electromagnetic proportional valve 291 and three four at this time
The opening of logical electromagnetic proportional valve 291 is related, changes leveling stream by changing the openings of sizes of 3-position 4-way electromagnetic proportional valve 291
Amount；Luffing operating duty pressure and leveling operating duty pressure are compared by the 5th check valve 435 and the 6th check valve 444,
Biggish load is passed to the LS mouth of constant-pressure drop variable pump 23, system is load sensitive system at this time.
C) when flexible, luffing composite move, the 5th electric proportional pressure-reducing valve 441 it is electric, and voltage is a steady state value, third
The work of hydraulic control proportional reversing valve 442 in left position, P1 mouth of leveling connection 44 with constant flow rate to leveling 29 fuel feeding of valve, excess traffic from
Pressure-differentially-set valve 293 pours off, and working bucket leveling movement at this time is not in system low-response, leveling hysteresis；Pressure-differentially-set valve 293
Keep 291 both ends pressure difference of 3-position 4-way electromagnetic proportional valve constant, passes through the flow of 3-position 4-way electromagnetic proportional valve 291 and three at this time
The opening of position four-way electromagnetic proportioning valve 291 is related, is adjusted by changing the openings of sizes of 3-position 4-way electromagnetic proportional valve 291 to change
Advection amount；4th check valve 425, the 5th check valve 435 and the 6th check valve 444 act expanding-contracting action load pressure, luffing
Load pressure and leveling operating duty pressure are compared, and biggish load is passed to the LS mouth of constant-pressure drop variable pump 23, this
When system be load sensitive system.
Claims (6)
1. a kind of working bucket leveling system of high-altitude operation vehicle, including constant-pressure drop variable pump (23), main valve (28), leveling valve
(29), telescopic oil cylinder (34), amplitude oil cylinder (33) and leveling cyclinder (37)；Constant-pressure drop variable pump (23) pressure oil port P and main valve
(28) pressure oil port P is connected, and constant-pressure drop variable pump (23) load feedback hydraulic fluid port LS is connected with main valve (28) load feedback hydraulic fluid port LS,
Hydraulic oil enters telescopic oil cylinder (34) and amplitude oil cylinder (33) by main valve (28) to control expanding-contracting action and luffing movement；It is main
The pressure oil port P1 of valve (28) is connected with the pressure oil port P of leveling valve (29), the oil return inlet T 1 and leveling valve (29) of main valve (28)
Oil return inlet T be connected, hydraulic oil enters leveling cyclinder (37) by leveling valve (29) to control the leveling of leveling cyclinder (37)
Movement；It is characterized in that, the main valve (28) can be inserted valve or multi-way valve；Telescopic oil cylinder (34) and amplitude oil cylinder (33)
On maximum load pressure feed back to the load-sensitive hydraulic fluid port LS of constant-pressure drop variable pump (23)；Main valve (28) pressure oil port
P is equipped with reversal valve with leveling valve (29) pressure oil port P oil circuit connecting, and when reversal valve is in spring position, levels valve (29)
Pressure oil port P pressure be zero, when reversal valve commutation when, constant-pressure drop variable pump (23) pressure oil port P pass through flow rate adjustment device
It is connected to the P mouth of leveling valve (29), and the check valve by being connected to reversal valve oil outlet feeds back to constant-pressure drop variable pump
(23) load-sensitive hydraulic fluid port LS.
2. the working bucket leveling system of high-altitude operation vehicle according to claim 1, which is characterized in that the leveling valve (29)
Including the first shuttle valve (292), 3-position 4-way electromagnetic proportional valve (291) and pressure-differentially-set valve (293), a oil of pressure-differentially-set valve (293)
The oil inlet of mouth, c hydraulic fluid port and 3-position 4-way electromagnetic proportional valve (291) is connected in parallel on simultaneously at the pressure oil port P of leveling valve (29),
First oil outlet of 3-position 4-way electromagnetic proportional valve (291) and the first oil inlet of the first shuttle valve (292) are connected in parallel on leveling oil
The rod chamber end of cylinder (37), the second oil outlet of 3-position 4-way electromagnetic proportional valve (291) and the second oil inlet of the first shuttle valve
It is connected in parallel on the rodless cavity end of leveling cyclinder, the oil outlet of the first shuttle valve (292) is oily by the d of pressure feedback to pressure-differentially-set valve (293)
Mouthful, the oil return opening of 3-position 4-way electromagnetic proportional valve (291) is connected in parallel to the oil return line T of system with the b hydraulic fluid port of pressure-differentially-set valve (293).
3. the working bucket leveling system of high-altitude operation vehicle according to claim 2, which is characterized in that when main valve (28) is slotting
When filling valve, including overflow valve (282), operated proportional flow control valve, three-position four-way electromagnetic directional valve, shuttle valve and check valve, it is described to overflow
Flow the oil inlet of valve (282), the oil inlet of the first operated proportional flow control valve (283) and the second operated proportional flow control valve (286)
Oil inlet is connected with the pressure oil port P of main valve (28), the oil outlet of the first operated proportional flow control valve (283) and the one or three four
The oil inlet of electric change valve (284) is connected, the oil outlet of the second operated proportional flow control valve (286) and the second 3-position 4-way electricity
The oil inlet of magnetic reversal valve (287) is connected, the first oil outlet and the second shuttle valve of the first three-position four-way electromagnetic directional valve (284)
(285) the first oil inlet is connected in parallel on the rod chamber end of telescopic oil cylinder (34), and the of the first three-position four-way electromagnetic directional valve (284)
Second oil inlet of two oil outlets and the second shuttle valve (285) is connected in parallel on the rodless cavity end of telescopic oil cylinder (34), the second 3-position 4-way
First oil outlet of solenoid directional control valve (287) and the first oil inlet of third shuttle valve (288) are connected in parallel on having for amplitude oil cylinder (33)
Second oil outlet at rod cavity end, the second three-position four-way electromagnetic directional valve (287) is in parallel with the second oil inlet of third shuttle valve (288)
At the rodless cavity end of amplitude oil cylinder (33), the oil outlet of the second shuttle valve (285) is connected with the oil inlet of second one-way valve (2810),
The oil outlet of third shuttle valve (288) is connected with the oil inlet of third check valve (2811), and the first check valve (2812), second are unidirectionally
The oil outlet of valve (2810) and third check valve (2811) is connected with the load feedback hydraulic fluid port LS of main valve (28), and the one or three four
Time of the oil return opening of electric change valve (284), the oil return opening of the second three-position four-way electromagnetic directional valve (287), reversal valve (289)
The oil outlet of hydraulic fluid port and overflow valve (282) is connected with the oil return inlet T of main valve 28.
4. the working bucket leveling system of high-altitude operation vehicle according to claim 3, which is characterized in that the reversal valve is two
Position three-way solenoid valve (289), the flow rate adjustment device are speed governing valve (281).
5. the working bucket leveling system of high-altitude operation vehicle according to claim 2, which is characterized in that when main valve is multi-way valve
When, including first (41), the connection (42) that stretches, luffing join (43), leveling joins (44) and tail joins (45), wherein flexible join (42), become
Width joins (43) and leveling connection (44) includes pressure-differentially-set valve, hydraulic control proportional reversing valve and check valve, the first hydraulic control proportional reversing valve
(423), the second hydraulic control proportional reversing valve (433), third hydraulic control proportional reversing valve (442) oil inlet with the pressure oil of main valve
Mouth P is connected, the first hydraulic control proportional reversing valve (423), the second hydraulic control proportional reversing valve (433), third hydraulic control proportional reversing valve
(442) oil return opening is connected with the oil return inlet T of main valve；First pressure-differentially-set valve (424), the second pressure-differentially-set valve (434) and third
The control port of pressure-differentially-set valve (443) is connected with the load-sensitive hydraulic fluid port LS of main valve；First hydraulic control proportional reversing valve (423)
Left side control port is connected with the first electric proportional pressure-reducing valve (421), the right side control port of the first hydraulic control proportional reversing valve (423)
It is connected with the second electric proportional pressure-reducing valve (422), the left side control port and third electricity ratio of the second hydraulic control proportional reversing valve (433)
Pressure reducing valve (431) is connected, the right side control port of the second hydraulic control proportional reversing valve (433) and the 4th electric proportional pressure-reducing valve (432)
It is connected, the left side control port of third hydraulic control proportional reversing valve (442) is connected with the 5th electric proportional pressure-reducing valve (441), third liquid
The right side control port of control proportional reversing valve (442) is directly connected with fuel tank.
6. the working bucket leveling system of high-altitude operation vehicle according to claim 5, which is characterized in that the first hydraulic control ratio is changed
It is three eight logical reversal valves to valve (423), the second hydraulic control proportional reversing valve (433), third hydraulic control proportional reversing valve (442),
The a hydraulic fluid port of reversal valve is connected to c hydraulic fluid port, and is connected in parallel to oil return inlet T, and b hydraulic fluid port connects with pressure oil port T-phase, the first hydraulic control ratio
The d hydraulic fluid port and h hydraulic fluid port of example reversal valve (423) are connected with the rod chamber end of telescopic oil cylinder (34) and rodless cavity end respectively, the second liquid
The d hydraulic fluid port and h hydraulic fluid port for controlling proportional reversing valve (433) are connected with the rod chamber end of amplitude oil cylinder (33) and rodless cavity end respectively, the
The d hydraulic fluid port and h hydraulic fluid port of three hydraulic control proportional reversing valves (442) are connected with the pressure oil port P1 of main valve and oil return inlet T 1 respectively, and first
The e hydraulic fluid port and g hydraulic fluid port of hydraulic control proportional reversing valve (423) are connected in parallel to the oil outlet of the first pressure-differentially-set valve (424), while first is fixed
The oil outlet of valve for pressure difference (424) is connected with the oil inlet of the 4th check valve (425), the e oil of the second hydraulic control proportional reversing valve (433)
Mouthful and g hydraulic fluid port be connected in parallel to the oil outlets of the second pressure-differentially-set valve (434), while the oil outlet of the second pressure-differentially-set valve (434) and the
The oil inlet of five check valves (435) is connected, and the e hydraulic fluid port and g hydraulic fluid port of third hydraulic control proportional reversing valve (442) are connected in parallel to third level pressure
The oil outlet of difference limen (443), while the oil inlet phase of the oil outlet of third pressure-differentially-set valve (443) and the 6th check valve (444)
Even；The oil inlet that the f hydraulic fluid port of first hydraulic control proportional reversing valve (423) determines differential valve (424) with first is connected, the second hydraulic control ratio
The oil inlet that the f hydraulic fluid port of reversal valve (433) determines differential valve (434) with second is connected, the f of third hydraulic control proportional reversing valve (442)
Hydraulic fluid port is connected with the oil inlet that third determines differential valve (443).
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810715474.2A CN108658019B (en) | 2018-07-03 | 2018-07-03 | A kind of working bucket leveling system of high-altitude operation vehicle |
| PCT/CN2018/111594 WO2020006932A1 (en) | 2018-07-03 | 2018-10-24 | Bucket leveling system for aerial work truck |
| GB2011541.6A GB2587267B (en) | 2018-07-03 | 2018-10-24 | Bucket leveling system for aerial work truck |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810715474.2A CN108658019B (en) | 2018-07-03 | 2018-07-03 | A kind of working bucket leveling system of high-altitude operation vehicle |
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| CN108658019A CN108658019A (en) | 2018-10-16 |
| CN108658019B true CN108658019B (en) | 2019-07-30 |
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| CN201810715474.2A Active CN108658019B (en) | 2018-07-03 | 2018-07-03 | A kind of working bucket leveling system of high-altitude operation vehicle |
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| CN (1) | CN108658019B (en) |
| GB (1) | GB2587267B (en) |
| WO (1) | WO2020006932A1 (en) |
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| CN108658019B (en) * | 2018-07-03 | 2019-07-30 | 徐州海伦哲专用车辆股份有限公司 | A kind of working bucket leveling system of high-altitude operation vehicle |
| CN109058195B (en) * | 2018-10-30 | 2024-04-30 | 江苏徐工工程机械研究院有限公司 | Hydraulic control system of rescue equipment and rescue equipment |
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| CN108658019B (en) * | 2018-07-03 | 2019-07-30 | 徐州海伦哲专用车辆股份有限公司 | A kind of working bucket leveling system of high-altitude operation vehicle |
| CN208532159U (en) * | 2018-07-03 | 2019-02-22 | 徐州海伦哲专用车辆股份有限公司 | A kind of working bucket leveling system of high-altitude operation vehicle |
-
2018
- 2018-07-03 CN CN201810715474.2A patent/CN108658019B/en active Active
- 2018-10-24 WO PCT/CN2018/111594 patent/WO2020006932A1/en active Application Filing
- 2018-10-24 GB GB2011541.6A patent/GB2587267B/en active Active
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| GB202011541D0 (en) | 2020-09-09 |
| GB2587267A (en) | 2021-03-24 |
| GB2587267B (en) | 2021-08-18 |
| CN108658019A (en) | 2018-10-16 |
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