WO2020006932A1 - Système de mise à niveau de godet pour chariot de travail aérien - Google Patents

Système de mise à niveau de godet pour chariot de travail aérien Download PDF

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Publication number
WO2020006932A1
WO2020006932A1 PCT/CN2018/111594 CN2018111594W WO2020006932A1 WO 2020006932 A1 WO2020006932 A1 WO 2020006932A1 CN 2018111594 W CN2018111594 W CN 2018111594W WO 2020006932 A1 WO2020006932 A1 WO 2020006932A1
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WIPO (PCT)
Prior art keywords
valve
port
oil
proportional
leveling
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2018/111594
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English (en)
Chinese (zh)
Inventor
董洪月
耿艳杰
胡景清
陈时妹
朱赛
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Xuzhou Handler Special Vehicle Co Ltd
Original Assignee
Xuzhou Handler Special Vehicle Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Xuzhou Handler Special Vehicle Co Ltd filed Critical Xuzhou Handler Special Vehicle Co Ltd
Priority to MYPI2020003897A priority Critical patent/MY199697A/en
Priority to GB2011541.6A priority patent/GB2587267B/en
Publication of WO2020006932A1 publication Critical patent/WO2020006932A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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

Definitions

  • the invention relates to an engineering vehicle leveling system, in particular to a working bucket leveling system of an aerial work vehicle, and belongs to the technical field of hydraulic control of engineering machinery.
  • High-altitude operation vehicle is a kind of equipment that transports workers and equipment to a specified height for operation. It belongs to special operation equipment. Its structure is shown in Figure 1. It includes chassis 1, turntable 2, luffing cylinder 3, telescopic cylinder 4, basic The arm 5, the two-joint arm 6, the leveling cylinder 7 and the working bucket 8, the luffing cylinder 3 drives the luffing of the boom, the telescoping cylinder 4 drives the expansion and contraction of the boom, and the leveling cylinder 7 is used to adjust the angle of the working bucket 8.
  • the working bucket 8 When working at height, the working bucket 8 is required to be always parallel to the horizontal plane to ensure the safety and comfort of the operator. Therefore, leveling performance is an important indicator for measuring vehicles.
  • the working principle of the working bucket 8 leveling is shown in FIG. 2.
  • the inclination sensor 9 collects the inclination signal of the working bucket 8 and after the controller 10 processes it, it drives the spool of the electro-hydraulic proportional valve 11 to make corresponding actions.
  • the cylinder rod of the leveling cylinder 7 is extended or retracted, thereby directly driving the work bucket 8 up or down to achieve the level of the work bucket 8.
  • leveling oil supply There are usually two ways of leveling oil supply for the working bucket 8: 1 Gear pump (quantitative pump) supplies oil for leveling separately; 2 The leveling action of the working bucket 8 shares a plunger pump (variable pump) with the boom telescopic and luffing action ).
  • the second leveling oil supply method is widely used because it does not need to be equipped with a gear pump for leveling separate oil supply, and has the advantages of low cost and easy layout.
  • the oil pump In the second method of leveling oil supply, the oil pump is usually located on the lower chassis, and the pipeline between the oil pump and the bucket 8 is relatively long.
  • the working bucket 8 leveling flow is small. If a conventional load-sensitive system is used for the working bucket 8 leveling, the system response is slow and the leveling lag is serious. Therefore, most of the working bucket 8 leveling systems use a constant pressure system, that is, as long as the amplitude is changed.
  • the system is a constant voltage system when in action.
  • the working bucket 8 leveling system in the prior art mainly includes a constant pressure differential variable pump, a main valve, a leveling valve, a telescopic oil cylinder 4, a luffing oil cylinder 3, and a leveling oil cylinder 7.
  • the constant pressure differential variable pump controls the operation of the telescopic cylinder 4 and the luffing cylinder 3 through the main valve, and at the same time, supplies oil to the leveling cylinder 7.
  • the system is a load-sensitive system.
  • the outlet pressure of the constant pressure differential variable pump is higher than the load pressure by a preset fixed value, and the outlet flow rate is the load working flow.
  • the constant pressure differential variable pump is used.
  • the system is a constant pressure system.
  • the leveling flow is changed by changing the opening of the electromagnetic proportional valve in the leveling valve; when the telescopic and variable amplitude are combined, the constant pressure differential variable pump is used as a constant pressure.
  • Variable pump The system is a constant pressure system.
  • the leveling flow is changed by changing the size of the electromagnetic proportional valve opening in the leveling valve.
  • the above-mentioned leveling system has the following technical defects: 1) When the single amplitude-change operation or the telescoping and amplitude-change composite operations are used, the system is a constant pressure system, so the outlet pressure of the constant pressure differential variable pump 13 has been maintained at the maximum value, and Compared with load-sensitive systems, the energy consumption is large; 2) The leveling action of the bucket will cause slow system response and lagging; 3) The pressure difference between the two ends of the electromagnetic proportional valve in the leveling valve changes with the load change. Therefore, the leveling of the bucket 8 is not easy to control.
  • the present invention provides a working bucket leveling system for an aerial work vehicle.
  • the working bucket leveling is easy to control, the lagging action has no lag, the system responds quickly, and at the same time saves energy and reduces consumption.
  • the present invention provides a bucket leveling system for an aerial work vehicle, which includes a constant pressure variable pump, a main valve, a leveling valve, a telescopic oil cylinder, a luffing cylinder, and a leveling oil cylinder; the pressure of the constant pressure variable pump Port P is connected to the main valve pressure port P.
  • the constant pressure differential variable pump load feedback port LS is connected to the main valve load feedback port LS.
  • the hydraulic oil enters the telescopic cylinder and the luffing cylinder through the main valve to control the telescopic movement and variable
  • the pressure port P of the main valve is connected to the pressure port P of the leveling valve.
  • the return port T of the main valve is connected to the return port T of the leveling valve.
  • the hydraulic oil enters the leveling cylinder through the leveling valve.
  • Controls the leveling action of the leveling cylinder it is characterized in that the main valve can be a cartridge valve or a multi-way valve; the maximum load pressure on the telescopic cylinder and the luffing cylinder is fed back to the load-sensitive oil of the constant pressure differential variable pump Port LS; the main valve pressure port P and the leveling valve pressure port P is provided with a directional valve on the oil line, when the directional valve is in the spring position, the pressure of the pressure port P of the leveling valve is zero, When the reversing valve is reversed, the constant pressure differential variable pump pressure port P passes The flow rate adjusting device is in communication with the P port of the leveling valve, and is fed back to the load-sensitive oil port LS of the constant pressure differential variable pump through a check valve connected to the oil outlet of the reversing valve.
  • Sensitive oil port LS so whether it is telescopic action, luffing action, or luffing telescoping action, the system is load-sensitive system, energy saving and environmental protection; when the telescopic action is alone, the directional valve is in the spring position, so there is no pressure oil When entering the leveling valve and the leveling cylinder, the directional valve is in the reversing direction when the luffing action is combined or the telescoping and luffing action is combined. Therefore, the pressure oil enters the leveling cylinder through the flow rate adjustment device and the reversing valve while entering the main valve. , Leveling action quickly without lag.
  • the leveling valve includes a first shuttle valve, a three-position four-way electromagnetic proportional valve and a constant pressure differential valve, a port a, c port of the constant pressure differential valve, and oil inlet of the three-position four-way electromagnetic proportional valve.
  • the port is connected in parallel to the pressure port P of the leveling valve.
  • the first oil outlet of the three-position four-way electromagnetic proportional valve and the first oil inlet of the first shuttle valve are connected in parallel to the rod cavity end of the leveling cylinder.
  • the second oil outlet of the four-way electromagnetic proportional valve and the second oil inlet of the first shuttle valve are connected in parallel to the rodless cavity end of the leveling cylinder.
  • the oil outlet of the first shuttle valve feeds back pressure to the constant pressure differential valve.
  • the d port, the return port of the three-position four-way electromagnetic proportional valve and the b port of the constant pressure differential valve are connected in parallel to the return circuit T of the system.
  • the first shuttle valve feedbacks the larger pressure at both ends of the leveling cylinder as a feedback pressure to the constant pressure differential valve, so that the pressure difference between the oil inlet and the oil return of the three-position four-way electromagnetic proportional valve is always kept constant.
  • the flow rate of the four-way solenoid proportional valve is only related to the opening size of the three-way four-way solenoid proportional valve. Therefore, the leveling flow can be changed by changing the opening size of the first three-way four-way solenoid valve. Actions are more precise and faster.
  • the main valve when it is a cartridge valve, it includes an overflow valve, a proportional flow control valve, a three-position four-way electromagnetic directional valve, a shuttle valve, and a one-way valve.
  • the oil inlet of the flow control valve and the oil inlet of the second proportional flow control valve are connected to the pressure oil port P of the main valve.
  • the oil outlet of the first proportional flow control valve and the first three-position four-way electromagnetic directional valve The oil inlet of the second proportional flow control valve is connected to the oil inlet of the second three-position four-way electromagnetic directional valve, and the first oil outlet of the first three-position four-way electromagnetic directional valve is connected to The first oil inlet of the second shuttle valve is connected in parallel to the rod cavity end of the telescopic oil cylinder, and the second oil outlet of the first three-position four-way electromagnetic directional valve is connected in parallel with the second oil inlet of the second shuttle valve.
  • the rod-less cavity end of the oil cylinder, the first oil outlet of the second three-position four-way electromagnetic directional valve and the first oil inlet of the third shuttle valve are connected in parallel at the rod cavity end of the luffing cylinder, and the second three-position four The second oil outlet of the electromagnetic switching valve and the second oil inlet of the third shuttle valve are connected in parallel at the rodless cavity end of the luffing cylinder.
  • the oil outlet of the second shuttle valve and the second The oil inlet of the check valve is connected, and the oil outlet of the third shuttle valve is connected to the oil inlet of the third check valve.
  • the oil outlets of the first, second and third check valves are all Connected to the load feedback port LS of the main valve, the return port of the first three-position four-way electromagnetic directional valve, the return port of the second three-position four-way electromagnetic directional valve, the return port of the directional valve and the overflow
  • the outlet of the flow valve is connected to the return port T of the main valve.
  • the directional valve is a two-position three-way electromagnetic directional valve, and the flow rate adjusting device is a speed regulating valve.
  • the main valve when it is a multi-way valve, it includes a first coupling, a telescopic coupling, a luffing coupling, a leveling coupling, and a tail coupling, where the telescopic coupling, luffing coupling, and leveling coupling all include a constant pressure differential valve and a hydraulic control ratio.
  • the inlets of the directional valve and check valve, the first hydraulic proportional valve, the second hydraulic proportional valve, and the third hydraulic proportional valve are connected to the pressure port P of the main valve.
  • the oil return ports of one hydraulically controlled proportional directional valve, the second hydraulically controlled proportional directional valve, and the third hydraulically controlled proportional directional valve are connected to the oil return port T of the main valve;
  • the control ports of the differential pressure valve and the third fixed differential pressure valve are connected to the load-sensitive port LS of the main valve;
  • the left control port of the first hydraulic proportional valve is connected to the first electric proportional pressure reducing valve.
  • the right control port of the first hydraulic proportional valve is connected to the second electric proportional pressure reducing valve
  • the left control port of the second hydraulic proportional valve is connected to the third electric proportional pressure reducing valve
  • the second The right control port of the hydraulic proportional valve is connected to the fourth electric proportional pressure reducing valve
  • the left control port of the third hydraulic proportional valve is connected to the fifth electric proportional pressure reducing valve.
  • the right control oil port of the third hydraulic proportional proportional valve is directly connected to the fuel tank.
  • first hydraulically controlled proportional directional valve, the second hydraulically controlled proportional directional valve, and the third hydraulically controlled proportional directional valve are all three-position eight-way directional valves, and the a and c ports of the directional valve Connected and connected in parallel to the oil return port T, the b port is connected to the pressure port T, the d port and the h port of the first hydraulic proportional valve are connected to the rod end and the rodless end of the telescopic oil cylinder, respectively. The cavity ends are connected.
  • the d port and the h port of the second hydraulic proportional proportional valve are respectively connected to the rod cavity end and the rodless cavity end of the luffing cylinder, and the d port and the third hydraulic controlled proportional valve are connected.
  • the h port is connected to the pressure port P and the oil return port T of the main valve respectively.
  • the e port and the g port of the first hydraulic proportional valve are connected in parallel to the oil outlet of the first constant pressure differential valve.
  • the oil outlet of the first certain differential pressure valve is connected to the oil inlet of the fourth check valve, and the e and g ports of the second hydraulic proportional proportional valve are connected in parallel to the oil outlet of the second constant pressure differential valve.
  • the oil outlet of the second constant pressure differential valve is connected to the oil inlet of the fifth check valve, and the e and g ports of the third hydraulic proportional proportional valve are connected in parallel to the third constant pressure valve.
  • the third constant pressure differential valve The oil outlet is connected to the oil inlet of the sixth check valve; the f port of the first hydraulic proportional valve is connected to the oil inlet of the first fixed differential pressure valve, and the f of the second hydraulic proportional valve is The oil port is connected to the oil inlet of the second fixed differential pressure valve, and the f port of the third hydraulic control proportional directional valve is connected to the oil inlet of the third fixed differential pressure valve.
  • the constant pressure differential variable pump in the present invention supplies oil to the bucket leveling operation at a constant flow through the main valve and the leveling valve. Because of the constant pressure differential valve provided at both ends of the three-position four-way electromagnetic proportional valve in the leveling valve, Therefore, it is possible to ensure that the pressure difference between the two ends of the three-position four-way electromagnetic proportional valve is constant. Its passing flow is only related to the opening of the three-position four-way electromagnetic proportional valve. Therefore, the leveling of the working bucket is convenient for control. During operation, no hydraulic oil flows into the leveling valve. When the luffing or telescoping compound action is performed, the hydraulic oil flows into the luffing cylinder and also flows into the leveling valve through the speed regulating valve.
  • the system of the bucket leveling action will not appear in the system.
  • FIG. 1 is a schematic structural diagram of an aerial work vehicle
  • FIG. 2 is a schematic structural diagram of the working principle of the bucket leveling in FIG. 1;
  • FIG. 3 is a schematic structural diagram of a bucket leveling system according to the present invention.
  • FIG. 4 is a schematic structural diagram of another working bucket leveling system according to the present invention.
  • FIG. 5 is an enlarged schematic diagram of the first hydraulically controlled proportional directional valve or the second hydraulically controlled proportional directional valve or the third hydraulically controlled proportional directional valve in FIG. 4;
  • a working bucket leveling system for an aerial work vehicle includes a constant pressure variable pump 23, a main valve 28, a leveling valve 29, a telescopic cylinder 34, a luffing cylinder 33, and a leveling cylinder 37;
  • the differential pressure pump 23 pressure port P is connected to the main valve 28 pressure port P
  • the constant differential pressure pump 23 load feedback port LS is connected to the main valve 28 load feedback port LS
  • the hydraulic oil enters the telescopic cylinder through the main valve 28 34 and luffing cylinder 33 to control telescopic and luffing movements
  • pressure port P1 of main valve 28 is connected to pressure port P of leveling valve 29, and oil return port T1 of main valve 28 and return of leveling valve 29
  • the oil port T is connected, and the hydraulic oil enters the leveling cylinder 37 through the leveling valve 29 to control the leveling action of the leveling cylinder 37.
  • the main valve 28 is a cartridge valve; the maximum load on the telescopic cylinder 34 and the luffing
  • the main valve 28 includes an overflow valve 282, a proportional flow control valve, a three-position four-way electromagnetic directional valve, a shuttle valve, a one-way valve, a two-position three-way electromagnetic directional valve 289, and a speed regulating valve 281.
  • the oil inlet of the relief valve 282, the oil inlet of the first proportional flow control valve 283, and the oil inlet of the second proportional flow control valve 286 are connected to the pressure oil port P of the main valve 28.
  • the oil outlet of the flow control valve 283 is connected to the oil inlet of the first three-position four-way electromagnetic directional valve 284, and the oil outlet of the second proportional flow control valve 286 is connected to the second three-position four-way electromagnetic directional valve 287.
  • the oil inlets are connected.
  • the first oil outlet of the first three-position four-way electromagnetic directional valve 284 and the first oil inlet of the second shuttle valve 285 are connected in parallel at the rod cavity end of the telescopic cylinder 34.
  • the second oil outlet of the electromagnetic switching valve 284 and the second oil inlet of the second shuttle valve 285 are connected in parallel at the rodless cavity end of the telescopic cylinder 34, and the first outlet of the second three-position four-way electromagnetic switching valve 287
  • the oil port is connected in parallel with the first oil inlet of the third shuttle valve 288 at the rod cavity end of the luffing cylinder 33, and the second oil outlet of the second three-position four-way electromagnetic directional valve 287 and the third shuttle valve 288
  • the second oil inlet is connected in parallel to the rodless cavity end of the luffing cylinder 33.
  • the oil outlet of the second shuttle valve 285 is connected to the oil inlet of the second check valve 2810.
  • the oil outlet of the third shuttle valve 288 is connected to the first Three orders
  • the inlet of the check valve 2811 is connected.
  • the outlets of the first check valve 2812, the second check valve 2810 and the third check valve 2811 are connected to the load feedback port LS of the main valve 28.
  • the oil return port of the four-way electromagnetic directional valve 284, the oil return port of the second three-position four-way electromagnetic directional valve 287, the oil return of the directional valve 289, and the oil outlet of the relief valve 282 are all connected to the main valve 28.
  • the oil return port T is connected; the main valve 28 pressure port P and the leveling valve 29 pressure port P are connected on the oil line with a two-position three-way electromagnetic directional valve 289.
  • the pressure port P of the leveling valve 29 is zero.
  • the pressure port P of the constant pressure variable pump 23 passes the speed regulating valve 281 and The P port of the leveling valve 29 is in communication, and is fed back to the load-sensitive oil port LS of the constant pressure differential variable pump 23 through the first check valve 2812 connected to the oil outlet of the two-position three-way electromagnetic directional valve 289;
  • the leveling valve 29 includes a first shuttle valve 292, a three-position four-way electromagnetic proportional valve 291, and a constant pressure differential valve 293.
  • the oil inlet is connected in parallel to the pressure port P of the leveling valve 29.
  • the first oil outlet of the three-position four-way electromagnetic proportional valve 291 and the first oil inlet of the first shuttle valve 292 are connected in parallel to the leveling cylinder 37.
  • the rod outlet end, the second oil outlet of the three-position four-way electromagnetic proportional valve 291 and the second oil inlet of the first shuttle valve are connected in parallel to the rodless cavity end of the leveling cylinder, and the oil output of the first shuttle valve 292 is The port feeds back pressure to the d port of the constant pressure differential valve 293, and the oil return port of the three-position four-way electromagnetic proportional valve 291 and the b port of the constant pressure differential valve 293 are connected in parallel to the oil return path T of the system.
  • the first three-position four-way electromagnetic directional valve 284 is energized, the second three-position four-way electromagnetic directional valve 287 and the two-position three-way electromagnetic directional valve 289 lose power, and the hydraulic oil flows in separately.
  • Telescopic oil cylinder 34 the two-port three-way electromagnetic directional valve 289 is connected to the oil return port, that is, the inlet pressure of the first check valve 2812 is zero, that is, the pressure of the P port of the leveling valve 29 is also zero;
  • the shuttle valve 285 transmits the telescopic action load pressure to the LS port of the constant pressure differential variable pump 23 through the second check valve 2810. At this time, the system is a load-sensitive system.
  • the constant pressure differential valve 293 makes the three-position four-way electromagnetic proportional valve 291 have a constant pressure difference across the two ends.
  • the flow through the three-position four-way electromagnetic proportional valve 291 is only related to the opening of the three-position four-way electromagnetic proportional valve 291. Changing the leveling flow by changing the opening size of the three-position four-way electromagnetic proportional valve 291 is more convenient to control;
  • the three shuttle valve 288 is used to select the load pressure of the luffing action.
  • the third check valve 2811 and the first one-way valve 2812 compare the luffing action load pressure and the leveling action load pressure, and transfer a larger load to the constant load.
  • the LS port of the differential pressure variable pump 23, and the amplitude-changing action system is a load-sensitive system at this time.
  • the first three-position four-way electromagnetic directional valve 284, the second three-position four-way electromagnetic directional valve 287 and the two-position three-way electromagnetic directional valve 289 are energized, and the hydraulic oil is simultaneously It flows into the telescopic oil cylinder 34 and the luffing oil cylinder 33; the two-position three-way electromagnetic directional valve 289 communicates with the oil inlet and the oil outlet, the oil return port is closed, and the hydraulic oil passes through the speed regulating valve 281 to the P of the leveling valve 29 at a constant flow rate.
  • the port is supplied with oil, and the excess flow flows away from the constant pressure differential valve 293.
  • the constant pressure differential valve 293 makes the three-position four-way electromagnetic proportional valve 291 at both ends.
  • the pressure difference is constant.
  • the flow rate through the three-position four-way electromagnetic proportional valve 291 is only related to the opening of the three-position four-way electromagnetic proportional valve 291.
  • the leveling flow is changed by changing the opening size of the three-position four-way electromagnetic proportional valve 291.
  • the second shuttle valve 285 takes the telescopic action load pressure
  • the third shuttle valve 288 takes the luffing action load pressure
  • the first check valve 2812, the second check valve 2810 and the third check valve 2811 will be leveled Compare operating load pressure, telescopic operation load pressure, and luffing operation load pressure The large difference in load transfer to the constant pressure variable pump LS port 23, this time stretching, compound action luffing load sensing system.
  • a bucket leveling system for an aerial work vehicle includes a constant pressure differential variable pump 23, a main valve 28, a leveling valve 29, a telescopic oil cylinder 34, a luffing cylinder 33, and a leveling oil cylinder 37; and the pressure of the constant pressure differential variable pump 23
  • the oil port P is connected to the pressure port P of the main valve 28, and the load feedback port LS of the constant pressure variable pump 23 is connected to the load feedback port LS of the main valve 28.
  • the hydraulic oil enters the telescopic cylinder 34 and the luffing cylinder 33 through the main valve 28.
  • the pressure port P1 of the main valve 28 is connected to the pressure port P of the leveling valve 29, and the return port T1 of the main valve 28 is connected to the return port T of the leveling valve 29.
  • the oil enters the leveling cylinder 37 through the leveling valve 29 to control the leveling action of the leveling cylinder 37.
  • the main valve is a multi-way valve, which includes a first connection 41, a telescopic connection 42, a luffing connection 43, a leveling connection 44 and Tail coupling 45, of which telescopic coupling 42, amplitude-changing coupling 43 and leveling coupling 44 all include constant pressure differential valve, hydraulic proportional proportional valve and check valve, first hydraulic proportional valve, 423 and second hydraulic valve
  • the oil inlets of the proportional directional valve 433 and the third hydraulically controlled proportional directional valve 442 are connected to the pressure port P of the main valve.
  • the first hydraulically controlled proportional directional valve 423 and the second The return ports of the proportional control valve 433 and the third hydraulic proportional valve 442 are connected to the return port T of the main valve; the first constant pressure differential valve 424, the second constant pressure differential valve 434, and the third fixed pressure
  • the control port of the differential pressure valve 443 is connected to the load-sensitive port LS of the main valve; the left control port of the first hydraulic proportional proportional valve 423 is connected to the first electric proportional pressure reducing valve 421, and the first hydraulic control
  • the right control oil port of the proportional valve 423 is connected to the second electric proportional pressure reducing valve 422.
  • the left control oil port of the second hydraulic proportional valve 433 is connected to the third electric proportional pressure reducing valve 431.
  • the right control oil port of the hydraulic proportional valve 433 is connected to the fourth electric proportional pressure reducing valve 432, and the left control oil port of the third hydraulic valve is connected to the fifth electric proportional pressure reducing valve 441.
  • the right control oil port of the third hydraulic proportional proportional valve 442 is directly connected to the fuel tank;
  • the first hydraulically controlled proportional directional valve 423, the second hydraulically controlled proportional directional valve 433, and the third hydraulically controlled proportional directional valve 442 are three-position eight-way directional valves.
  • the a port and the c port of the valve communicate with each other and are connected in parallel to the return port T.
  • the b port is connected to the pressure port T.
  • the d port and the h port of the first hydraulic proportional valve 423 are connected to The rod cavity end and the rod cavity end of the telescopic oil cylinder 34 are connected.
  • the d and h ports of the second hydraulic proportional proportional valve 433 are connected to the rod cavity end and the rodless cavity end of the luffing cylinder 33, respectively.
  • the d and h ports of the third hydraulic proportional valve 442 are connected to the pressure port P1 and the return port T1 of the main valve, respectively.
  • the e and g ports of the first hydraulic proportional valve 423 are connected. Connected in parallel to the oil outlet of the first constant pressure differential valve 424. At the same time, the oil outlet of the first constant pressure differential valve 424 is connected to the oil inlet of the fourth one-way valve 425.
  • the e port and the g port are connected in parallel to the oil outlet of the second constant pressure differential valve 434, while the oil outlet of the second constant pressure differential valve 434 is connected to the oil inlet of the fifth check valve 435, and the third fluid
  • the e port and g port of the proportional control valve 442 are connected in parallel to the At the oil outlet of the constant pressure differential valve 443, at the same time, the oil outlet of the third constant pressure differential valve 443 is connected to the oil inlet of the sixth check valve 444;
  • the f port of the first hydraulic proportional proportional valve 423 is connected to The oil inlet of the first certain differential pressure valve 424 is connected, the f port of the second hydraulic proportional proportional valve 433 is connected to the oil inlet of the second fixed differential pressure valve 434, and the third hydraulic controlled proportional valve 442 is connected.
  • the oil port is connected to the oil inlet of the third fixed differential pressure valve 443;
  • the leveling valve 29 includes a first shuttle valve 292, a three-position four-way electromagnetic proportional valve 291, and a constant pressure differential valve 293.
  • the oil inlet is connected in parallel to the pressure port P of the leveling valve 29.
  • the first oil outlet of the three-position four-way electromagnetic proportional valve 291 and the first oil inlet of the first shuttle valve 292 are connected in parallel to the leveling cylinder 37.
  • the rod outlet end, the second oil outlet of the three-position four-way electromagnetic proportional valve 291 and the second oil inlet of the first shuttle valve are connected in parallel to the rodless cavity end of the leveling cylinder, and the oil output of the first shuttle valve 292 is The port feeds back pressure to the d port of the constant pressure differential valve 293, and the oil return port of the three-position four-way electromagnetic proportional valve 291 and the b port of the constant pressure differential valve 293 are connected in parallel to the oil return path T of the system.
  • the oil inlet of the one-way valve 444 is fed back to the leveling pressure port P1 through the third hydraulic proportional proportional valve 442.
  • the fifth electric proportional pressure reducing valve 441 and the third hydraulic proportional valve The common effect of the directional valve 442 and the third constant pressure differential valve 443 is the same as that of the two-position three-way electromagnetic directional valve and the speed regulating valve in the cartridge valve.
  • the fifth electric proportional pressure reducing valve 441 is energized and the voltage is a constant value.
  • the third hydraulic proportional proportional valve 442 works in the left position, and the P1 port of the leveling union 44 is constant.
  • the flow supplies oil to the leveling valve 29, and the excess flow flows away from the constant pressure differential valve 293.
  • the constant pressure differential valve 293 makes the three-position four-way electromagnetic
  • the pressure difference between the two ends of the proportional valve 291 is constant.
  • the flow rate through the three-position four-way electromagnetic proportional valve 291 is only related to the opening of the three-position four-way electromagnetic proportional valve 291.
  • the leveling flow is changed; the fifth check valve 435 and the sixth check valve 444 compare the luffing action load pressure and the leveling action load pressure, and transmit a larger load to the LS port of the constant pressure differential variable pump 23,
  • the system is a load-sensitive system.
  • the fifth electric proportional pressure reducing valve 441 is energized and the voltage is a constant value.
  • the third hydraulic proportional proportional valve 442 works in the left position, and the P1 port of the leveling union 44 is leveled. Supply oil to the leveling valve 29 at a constant flow rate, and the excess flow will flow off from the constant pressure differential valve 293. At this time, the leveling action of the bucket will not cause slow system response and leveling lag; The pressure difference between the two-way electromagnetic proportional valve 291 is constant. At this time, the flow through the three-position four-way electromagnetic proportional valve 291 is only related to the opening of the three-position four-way electromagnetic proportional valve 291.
  • the fourth check valve 425, the fifth check valve 435, and the sixth check valve 444 compare the telescopic action load pressure, the luffing action load pressure, and the leveling action load pressure, which will be larger
  • the load is transferred to the LS port of the constant pressure differential variable pump 23, and the system is a load-sensitive system at this time.

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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

L'invention concerne un système de mise à niveau de godet pour un chariot de travail aérien, une vanne principale (28) pouvant être une vanne à cartouche ou une vanne à voies multiples ; les pressions de charge maximales sur un cylindre télescopique (34) et un cylindre de relevage (33) sont toutes deux renvoyées à un port de détection de charge LS d'une pompe variable différentielle à pression constante (23) ; une vanne d'inversion est disposée sur un passage de liquide qui relie un port de pression P de la vanne principale (28) et un port de pression P d'une vanne de mise à niveau (29) et, lorsque la vanne d'inversion est dans une position de ressort, la pression du port de pression P de la vanne de mise à niveau (29) est nulle et, lorsque la vanne d'inversion est inversée, le port de pression P de la pompe variable différentielle à pression constante (23) est en communication, au moyen d'une vanne de régulation de vitesse (281), avec le port P de la vanne de mise à niveau (29), et la pression du port P de la vanne de mise à niveau (29) est renvoyée, au moyen d'une vanne unidirectionnelle reliée au niveau du port de la vanne d'inversion, au port de détection de charge LS de la pompe variable différentielle à pression constante (23). Le système de mise à niveau de godet est facile à commander, il n'y a pas de retard d'action de mise à niveau et le système répond rapidement ; l'ensemble du système est un système de détection de charge, économisant sur la consommation d'énergie.
PCT/CN2018/111594 2018-07-03 2018-10-24 Système de mise à niveau de godet pour chariot de travail aérien Ceased WO2020006932A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
MYPI2020003897A MY199697A (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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CN201810715474.2A CN108658019B (zh) 2018-07-03 2018-07-03 一种高空作业车的工作斗调平系统
CN201810715474.2 2018-07-03

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WO2020006932A1 true WO2020006932A1 (fr) 2020-01-09

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CN (1) CN108658019B (fr)
GB (1) GB2587267B (fr)
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CN113683033A (zh) * 2021-09-23 2021-11-23 江苏柳工机械有限公司 臂架式高空作业平台的液压全时浮动控制系统及控制方法
CN113915188A (zh) * 2021-10-18 2022-01-11 山东泰丰智能控制股份有限公司 一种自适应液压控制系统
CN115488891A (zh) * 2022-10-10 2022-12-20 陕煤集团神木柠条塔矿业有限公司 矿用多关节重载液压机械臂的电液控制系统及方法
AU2022478675B2 (en) * 2022-12-19 2025-08-14 Hunan Sinoboom Intelligent Equipment Co., Ltd. Floating control system for fixed displacement pump system

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CN113175460A (zh) * 2021-04-23 2021-07-27 中国人民解放军国防科技大学 一种可变活塞截面大小的液压缸
CN113175460B (zh) * 2021-04-23 2023-09-01 中国人民解放军国防科技大学 一种可变活塞截面大小的液压缸
CN113683033A (zh) * 2021-09-23 2021-11-23 江苏柳工机械有限公司 臂架式高空作业平台的液压全时浮动控制系统及控制方法
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CN115488891A (zh) * 2022-10-10 2022-12-20 陕煤集团神木柠条塔矿业有限公司 矿用多关节重载液压机械臂的电液控制系统及方法
AU2022478675B2 (en) * 2022-12-19 2025-08-14 Hunan Sinoboom Intelligent Equipment Co., Ltd. Floating control system for fixed displacement pump system

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GB202011541D0 (en) 2020-09-09

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