CN101863420B - Hydraulically operated four-pump hydraulic system - Google Patents

Hydraulically operated four-pump hydraulic system Download PDF

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CN101863420B
CN101863420B CN 201010173062 CN201010173062A CN101863420B CN 101863420 B CN101863420 B CN 101863420B CN 201010173062 CN201010173062 CN 201010173062 CN 201010173062 A CN201010173062 A CN 201010173062A CN 101863420 B CN101863420 B CN 101863420B
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valve
control
hydraulic
oil
hoists
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CN101863420A (en
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卢宇
李新
邹泉敏
刘峰
刘富良
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卢宇
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Abstract

The invention discloses a hydraulically operated four-pump hydraulic system. The hydraulic system comprises a first oil pump, a second oil pump, a third oil pump, a fourth oil pump, a rotary hydraulic system, a boom telescopic hydraulic system, a control hydraulic system, a lifting hydraulic system, a boom luffing hydraulic system, a piloted oil-source valve block and a control valve block. The opening and closing of a rotary brake, a main hoisting brake and a subsidiary hoisting brake adopt a constant pressure oil source control way and does not need additional external operation to intellectually and automatically realize the control of the brakes according to the operation of each action; according to the different opening-closing characteristics of each mechanism, the rotary structure adopts a control way of fast-opening and slow-closing and the main and subsidiary hoisting mechanisms adopt the control way of fast-closing and slow-opening to effectively eliminate the pressure impact of the system; a flow distribution valve adopts a flow distribution mode irrespective of a load to effectively prevent the pressure interference generated among each actuator from causing the slow action or no action of the actuators having a high load pressure; and each component of the whole system has high integration and modularization and convenient maintenance.

Description

Hydraulically operated four-pump hydraulic system
Technical field
The present invention relates to the technical field of hydraulic efficiency pressure system, particularly a kind of hydraulically operated four-pump hydraulic system, be suitable for the use of getting on the bus of car hosit, crawler crane and lorry-mounted crane.
Background technology
Hoisting crane in the course of the work, need to complete frequently that thing carries that lifting, band carry that revolution, weight are transferred, the actions such as luffing and unloaded backhaul, in order to realize efficient operation, need the hoisting crane can composite move, be that above-mentioned two or more move simultaneously, along with making constant progress of hoisting crane technology, also more and more higher to the open and shut characteristic of the safety control of each actuating unit, each actuating unit and the integrated requirement of car load hydraulic efficiency pressure system element heights.
At present, the hydraulic efficiency pressure system that hoisting crane is many adopts many actuating units parallel system, be that the hydraulic oil source parallel connection is to a plurality of hydraulic actuator fuel feeding, this hydraulic efficiency pressure system is when carrying out above-mentioned composite move, it is required during with oil that the hydraulic oil that provides when pump can not satisfy composite move simultaneously, i.e. during the flow oversaturation of valve, produce Pressure interference between a plurality of actuating units in parallel, the actuating unit that resistance is larger can not obtain required fluid flow and cause slow in one's movementsly, even can't move.The secure side of the car hosit of hydraulic pilot manipulation at present adopts combined control valve substantially to mode, and this mode causes the system pipeline bulky complex, is difficult for the investigation trouble shooting.
The keying of swing type mechanism, master winch mechanism and secondary hoisting mechanism drg is controlled, the working oil path high-voltage oil liquids that adopt are directly controlled more at present, in Japan many fields system, its drg is the manual draw bar mechanical operation, the moving device of work schedule is for often opening, can cause like this reduce the service life of system works efficient and element, control complexity, increase operation fatigue.
Summary of the invention
Technical matters to be solved by this invention is the present situation for prior art, provide a kind of and have Based Intelligent Control, have open and close that fast slow characteristic, hydraulic efficiency impact are little, structure assembly, modularization, system pipeline structure hydraulically operated four-pump hydraulic system little, applied widely and easy to maintenance.
The present invention solves the problems of the technologies described above the technical scheme that adopts: hydraulic controlled operation quadruple pump hydraulic system includes the first oil pump, the second oil pump, the 3rd oil pump, the 4th oil pump, Hydraulic slewing system, hoisting arm expansion hydraulic efficiency pressure system, controls hydraulic efficiency pressure system, the hydraulic efficiency pressure system that hoists, suspension arm variable-amplitude hydraulic efficiency pressure system, guide oil source valve group and control cock group; Control hydraulic efficiency pressure system and include the flow divider valve group, flow divider valve group two ends are equipped with respectively the 3rd oil inlet that is communicated with the first oil pump outlet, export with the second oil pump the second oil inlet that is communicated with; The master who dispose on the flow divider valve group that connection is controlled in the flexible hydraulic control of controlling the hoisting arm expansion hydraulic efficiency pressure system, connection is controlled in the luffing hydraulic control of controlling the suspension arm variable-amplitude hydraulic efficiency pressure system, controls the hydraulic efficiency pressure system that the hoists hydraulic control that hoists is controlled the hydraulic control that hoists of connection and pair and is controlled connection; Dispose the first oil inlet that is communicated with the 3rd oil pump outlet on the guide oil source valve group, the first oil inlet exit end is connected with respectively constant voltage controlling water kick valve, energy storage and constant pressure oil source delivery port; The 4th oil pump oil outlet is connected with the 4th oil inlet of Hydraulic slewing system through air-conditioning; The constant pressure oil source delivery port is connected with the duplex hoist brake control cock group of the trainstop control cock group of Hydraulic slewing system, the telescopic oil cylinder transfer valve group of hoisting arm expansion hydraulic efficiency pressure system, the hydraulic efficiency pressure system that hoists respectively, and phase control coordinates; The control cock group includes to be controlled flexible hydraulic control and controls the first drive block of connection spool commutation, controls the luffing hydraulic control and control the second drive block of connection spool commutation, control the main hydraulic control that hoists and control the 3rd drive block of connection spool commutation and control the 4 wheel driven motion block that the commutation of connection spool is controlled in the secondary hydraulic control that hoists, and the control port on the control cock group all is communicated with described constant pressure oil source delivery port oil circuit.
Adopts measure also comprises:
Also dispose on above-mentioned flow divider valve group control that the second oil inlet, the 3rd oil-feed oral fluid flow point close in the middle of control connection, the oil circuit of the 3rd oil inlet side is all controlled the hydraulic control that hoists of connection, pair with the main hydraulic control that hoists and is controlled the connection pressure port and be connected, correspondingly, the oil circuit of the second oil inlet side is all controlled connection with flexible hydraulic control, the luffing hydraulic control is controlled the connection pressure port and is connected.
Above-mentioned Hydraulic slewing system also includes the rotary buffering valve group that is connected with the 4th oil inlet, is furnished with the first commutation valve rod, the second electromagnetic valve and the first gyroscopic output mouth, the second gyroscopic output mouth in the rotary buffering valve group; Connect between the first gyroscopic output mouth, the second gyroscopic output mouth and driven rotary motor, and being fitted with trainstop on this rotary motor; Select to be formed with intermediate loop through the first shuttle valve between the first gyroscopic output mouth, the second gyroscopic output mouth, this intermediate loop is connected with the second electromagnetic valve import, and the second electromagnetic valve outlet is connected with above-mentioned the 4th oil inlet through the second reducing valve.
Be furnished with the first electromagnetic valve, the first pilot operated directional control valve, the second shuttle valve, the first one-way throttle valve, the second delivery port and the first control shuttle valve in above-mentioned trainstop control cock group, the drive end of the first pilot operated directional control valve and first is controlled the shuttle valve intermediate ends and is connected; The control cock group also includes the 5th drive block, the 5th drive block output has that the first revolution of controlling the first commutation valve rod commutation is controlled mouthful, the second revolution is controlled mouthful, and the first revolution is controlled mouthful, the second revolution is controlled mouth and is connected with the first two side ends of controlling shuttle valve respectively; The import of the first electromagnetic valve and the first pilot operated directional control valve all is communicated with constant pressure oil source delivery port oil circuit, and outlet is connected with the two side ends of the second shuttle valve respectively, and the intermediate ends of this second shuttle valve is connected with above-mentioned trainstop through the first one-way throttle valve, the first delivery port.
above-mentioned hoisting arm expansion hydraulic efficiency pressure system also includes the first telescopic oil cylinder, the second telescopic oil cylinder, is furnished with the first flexible delivery port on telescopic oil cylinder transfer valve group, the second flexible delivery port and flexible oil inlet, flexible hydraulic control is controlled the connection outlet and is furnished with respectively the first telescoping connection entrance, the second telescoping connection entrance, the first telescoping connection entrance is connected with flexible oil inlet, the first flexible delivery port is connected with the rodless cavity oil inlet end of the first telescopic oil cylinder through the first one-way balance valve, the second flexible delivery port is through the second one-way balance valve, transition spool piece in the middle of the first telescopic oil cylinder is connected with the rodless cavity oil inlet end of the second telescopic oil cylinder, and the first telescopic oil cylinder, the rod chamber oil inlet end of the second telescopic oil cylinder is connected with the second telescoping connection entrance simultaneously.
The first extension and contraction control mouth of the first above-mentioned one-way balance valve, the second extension and contraction control mouth of the second one-way balance valve all are communicated with the second telescoping connection entrance; Telescopic oil cylinder transfer valve group also is furnished with the 3rd electromagnetic valve and the second pilot operated directional control valve, and the import of the 3rd electromagnetic valve is communicated with constant pressure oil source delivery port oil circuit, and the outlet of the 3rd electromagnetic valve is communicated with the drive end of the second pilot operated directional control valve; Also be equipped with damping in telescopic oil cylinder transfer valve group, and this damping two ends are communicated with the second pilot operated directional control valve return opening, outside return opening respectively.
The above-mentioned hydraulic efficiency pressure system that hoists includes main hoisting mechanism and auxiliary hoisting mechanism, and auxiliary hoisting mechanism includes pair hoist balance cock group, secondary lifting motor, disposes secondary lifting motor drg on secondary lifting motor; The pair hydraulic control that hoists is controlled the connection outlet and is furnished with respectively the first pair access port, the second pair access port that hoists that hoists, and the first pair access port that hoists is connected with secondary lifting motor one end through the pair balance cock group that hoists, and the second pair access port that hoists is connected with the secondary lifting motor other end; The pair balance cock assembly that hoists has pair hoist balance cock and the 3rd shuttle valve, hoist the first control end on balance cock, the 3rd shuttle valve one side of pair all is connected with the second pair access port that hoists, another side of the 3rd shuttle valve and the first pair access port that hoists is connected, and the drive end of the 3rd pilot operated directional control valve in the first intermediate ends of the 3rd shuttle valve and duplex hoist brake control cock group is connected; The 3rd pilot operated directional control valve oil inlet is communicated with constant pressure oil source delivery port oil circuit, and the oil outlet of the 3rd pilot operated directional control valve is connected with secondary lifting motor drg.
Above-mentioned main hoisting mechanism includes main hoist balance cock group, main lifting motor, disposes main lifting motor drg on main lifting motor; The main hydraulic control that hoists is controlled the connection outlet and is furnished with respectively the first main access port that hoists, the second main access port that hoists, and the first main access port that hoists is connected with main lifting motor one end through the main balance cock group that hoists, and the second main access port that hoists is connected with the main lifting motor other end; The main balance cock assembly that hoists has main hoist balance cock and the 4th shuttle valve, the second control end on the main balance cock that hoists, the 4th shuttle valve one side all are connected with the second main access port that hoists, another side of the 4th shuttle valve and the first main access port that hoists are connected, and the drive end of the 4th pilot operated directional control valve in the second intermediate ends of the 4th shuttle valve and duplex hoist brake control cock group is connected; The oil inlet of the 4th pilot operated directional control valve is communicated with constant pressure oil source delivery port oil circuit, and the oil outlet of the 4th pilot operated directional control valve is connected with main lifting motor drg.
Above-mentioned suspension arm variable-amplitude hydraulic efficiency pressure system includes amplitude oil cylinder balance cock group and amplitude oil cylinder, the luffing hydraulic control is controlled the connection outlet and is furnished with respectively the first luffing access port, the second luffing access port, the first luffing access port is controlled mouth with the 3rd of amplitude oil cylinder rod chamber, amplitude oil cylinder balance cock group and is connected, and the second luffing access port is connected with the amplitude oil cylinder rodless cavity through amplitude oil cylinder balance cock group.
On above-mentioned flow divider valve group also configuration limit the 3rd inlet pressure the second safety valve, limit the 3rd safety valve of the second inlet pressure, on the flow divider valve group, the first telescoping connection entrance disposes the 4th safety valve, the second telescoping connection entrance and disposes the 5th safety valve, the first luffing access port and dispose the 6th safety valve, the first pair access port that hoists and dispose the 7th safety valve, the second pair access port that hoists and dispose that the 8th safety valve, the first main access port that hoists dispose the 9th safety valve, the second main access port that hoists disposes the tenth safety valve.
Above-mentioned safe off-load hydraulic efficiency pressure system also includes the unloader valve group, and this unloader valve assembly has the 4th electromagnetic valve, the 5th electromagnetic valve, the 6th electromagnetic valve; The 4th electromagnetic valve is connected with the pilot control opening of the second safety valve, the 3rd safety valve respectively, and phase control; The 5th electromagnetic valve is connected with the pilot control opening of the tenth safety valve, and phase control; The 6th electromagnetic valve is connected with the pilot control opening of the 4th safety valve, the 6th safety valve, the 9th safety valve, the 8th safety valve respectively through the 4th check valve, and phase control.
Above-mentioned the first oil pump oil outlet place is fitted with the first check valve, and the second oil pump oil outlet place is fitted with the second check valve, and the 3rd oil pump oil outlet place is fitted with the 3rd check valve, and the 4th oil pump oil outlet place is fitted with the 4th check valve.
Compared with prior art, the present invention is equipped with respectively the 3rd oil inlet that is communicated with the first oil pump outlet, exports with the second oil pump the second oil inlet that is communicated with at flow divider valve group two ends; The master who dispose on the flow divider valve group that connection is controlled in the flexible hydraulic control of controlling the hoisting arm expansion hydraulic efficiency pressure system, connection is controlled in the luffing hydraulic control of controlling the suspension arm variable-amplitude hydraulic efficiency pressure system, controls the hydraulic efficiency pressure system that the hoists hydraulic control that hoists is controlled the hydraulic control that hoists of connection and pair and is controlled connection; Dispose the first oil inlet that is communicated with the 3rd oil pump outlet on the guide oil source valve group, the first oil inlet exit end is connected with respectively constant voltage controlling water kick valve, energy storage and constant pressure oil source delivery port; The 4th oil pump oil outlet is connected with the 4th oil inlet of Hydraulic slewing system through air-conditioning; The constant pressure oil source delivery port is connected with the duplex hoist brake control cock group of the trainstop control cock group of Hydraulic slewing system, the telescopic oil cylinder transfer valve group of hoisting arm expansion hydraulic efficiency pressure system, the hydraulic efficiency pressure system that hoists respectively, and phase control coordinates; The control cock group includes to be controlled flexible hydraulic control and controls the first drive block of connection spool commutation, controls the luffing hydraulic control and control the second drive block of connection spool commutation, control the main hydraulic control that hoists and control the 3rd drive block of connection spool commutation and control the 4 wheel driven motion block that the commutation of connection spool is controlled in the secondary hydraulic control that hoists, and the control port on the control cock group all is communicated with described constant pressure oil source delivery port oil circuit.The invention has the advantages that: the open and shut characteristic of trainstop, major and minor hoist brake all adopts the constant pressure oil source mode, all need not the additional external force operation, and intelligence realizes the control of drg automatically according to the operation of each action; According to the different open and shut characteristics of each mechanism, revolving structure is changed down soon the mode of pass, to the mode of major and minor hoisting mechanism slow opening fast shutting, actv. is eliminated the compression shock of system; Flow divider valve adopts the assignment of traffic pattern irrelevant with load, and actv. prevents that the Pressure interference that produces between each actuating unit from causing the slow in one's movements or attonity of the high actuating unit of load pressure; The by pass valve of the by pass valve of each actuator port of flow divider valve and two oil-feed actuator ports all is provided with the remote control hydraulic fluid port, and connected system unloader valve group directly solves Security Control Problem on main valve; In Full Vehicle System, the integrated and modularization of each element heights, reduced the Full Vehicle System pipeline, maintains easily; Full Vehicle System is applicable to variable pump systems and Constant Pump System simultaneously.
Description of drawings
Fig. 1 is the system synthesis hydraulic principle schematic diagram of the embodiment of the present invention;
Fig. 2 is Hydraulic slewing system principle schematic in Fig. 1;
Fig. 3 is hoisting arm expansion Hydraulic System Principle schematic diagram in Fig. 1;
Fig. 4 is the Hydraulic System Principle schematic diagram that hoists in Fig. 1;
Fig. 5 is suspension arm variable-amplitude Hydraulic System Principle schematic diagram in Fig. 1;
Fig. 6 is safe off-load Hydraulic System Principle schematic diagram in Fig. 1;
Fig. 7 is the Hydraulic System Principle schematic diagram of control cock group in Fig. 1.
The specific embodiment
Embodiment is described in further detail the present invention below in conjunction with accompanying drawing.
as extremely shown in Figure 7 in Fig. 1, figure grade is described as follows: the first oil pump 11, the second oil pump 12, the 3rd oil pump 13, Hydraulic slewing system 2, trainstop control cock group 21, rotary buffering valve group 22, the first shuttle valve 22a, intermediate loop 22b, the second reducing valve 22c, the first commutation valve rod 23, rotary motor 24, the first pilot operated directional control valve 25, drive end 25a, spring cavity 25b, the second shuttle valve 26, the first one-way throttle valve 27, trainstop 28, first controls shuttle valve 29, hoisting arm expansion hydraulic efficiency pressure system 3, telescopic oil cylinder transfer valve group 31, the first one-way balance valve 32, the first telescopic oil cylinder 33, transition spool piece 33a, the second telescopic oil cylinder 34, the second pilot operated directional control valve 35, drive end 35a, the second one-way balance valve 36, damping 37, flexible with check valve 38, flow divider valve group 4, connection 41 is controlled in flexible hydraulic control, the 4th safety valve 41a, the 5th safety valve 41b, connection 42 is controlled in the luffing hydraulic control, the 6th safety valve 42a, connection 43 is controlled in the main hydraulic control that hoists, the tenth safety valve 43a, the 9th safety valve 43b, connection 44 is controlled in the pair hydraulic control that hoists, the 8th safety valve 44a, the 7th safety valve 44b, the middle connection 45 of controlling, the 3rd safety valve 46, the second safety valve 47, hydraulic efficiency pressure system 5 hoists, duplex hoist brake control cock group 51, the 3rd pilot operated directional control valve 51a, the 4th pilot operated directional control valve 51b, secondary lifting motor 52, main lifting motor 53, the main balance cock group 54 that hoists, the main balance cock 54a that hoists, the 4th shuttle valve 54b, the pair balance cock group 55 that hoists, the pair balance cock 55a that hoists, the 3rd shuttle valve 55b, main hoisting mechanism 56, auxiliary hoisting mechanism 57, secondary lifting motor drg 58, main lifting motor drg 59, suspension arm variable-amplitude hydraulic efficiency pressure system 6, amplitude oil cylinder balance cock group 61, amplitude oil cylinder 62, guide oil source valve group 7, constant voltage controlling water kick valve 71, energy storage 72, air-conditioning 74, safe off-load hydraulic efficiency pressure system 8, unloader valve group 81, the 4th check valve 82, control cock group 9, the first drive block 91, the second drive block 92, the 3rd drive block 93, 4 wheel driven motion block 94, the 5th drive block 95, operation control valve 96, lower vehicle hydraulic system 10, a mouthful a0 is controlled in the first revolution, a mouthful b0 is controlled in the second revolution, the first extension and contraction control mouth a1, the second extension and contraction control mouth b1, the first luffing is controlled a mouthful a2, the second luffing is controlled a mouthful b2, the first secondary lift control mouth a3, the second secondary lift control mouth b3, the first main lift control mouth a4, the second main lift control mouth b4, the first telescoping connection entrance A7, the second telescoping connection entrance B7, the first luffing access port A8, the second luffing access port B8, the first pair access port A9 that hoists, the second pair access port B9 that hoists, the first main access port A10 that hoists, the second main access port B10 that hoists, the first gyroscopic output mouth A11, the second gyroscopic output mouth B11, the first flexible delivery port A12, the second flexible delivery port B12, the first intermediate ends C1, the second intermediate ends C2, the first electromagnetic valve DHF1, the second electromagnetic valve DHF2, the 3rd electromagnetic valve DHF3, the 4th electromagnetic valve DHF4, the 5th electromagnetic valve DHF5, the 6th electromagnetic valve DHF6, the first check valve DF1, the second check valve DF2, the 3rd check valve DF3, the 4th check valve DF4, the first oil inlet P 1, the second oil inlet P 2, the 3rd oil inlet P 3, the 4th oil inlet P 4, flexible oil inlet P 6, the first extension and contraction control mouth P7, the second extension and contraction control mouth P8, the 3rd controls a mouthful P9, outside oil return inlet T 7, the first control end X1, the second control end X2, constant pressure oil source delivery port Y, the second delivery port Y1.
The embodiment of the present invention, hydraulic controlled operation quadruple pump hydraulic system includes the first oil pump 11, the second oil pump 12, the 3rd oil pump 13, the 4th oil pump 14, Hydraulic slewing system 2, hoisting arm expansion hydraulic efficiency pressure system 3, controls hydraulic efficiency pressure system 8, the hydraulic efficiency pressure system that hoists 5, suspension arm variable-amplitude hydraulic efficiency pressure system 6, guide oil source valve group 7 and control cock group 9; Control hydraulic efficiency pressure system 8 and include flow divider valve group 4, flow divider valve group 4 two ends are equipped with respectively the 3rd oil inlet P 3 that is communicated with the first oil pump 11 outlets, export with the second oil pump 12 the second oil inlet P 2 that is communicated with; The master who dispose on flow divider valve group 4 that connection 41 is controlled in the flexible hydraulic control of controlling hoisting arm expansion hydraulic efficiency pressure system 3, connection 42 is controlled in the luffing hydraulic control of controlling suspension arm variable-amplitude hydraulic efficiency pressure system 6, controls the hydraulic efficiency pressure system 5 that the hoists hydraulic control that hoists is controlled the hydraulic control that hoists of connection 43 and pair and is controlled connection 44.
Dispose the first oil inlet P 1, the first oil inlet P 1 exit end that is communicated with the 3rd oil pump 13 outlets on guide oil source valve group 7 and be connected with respectively constant voltage controlling water kick valve 71, energy storage 72 and constant pressure oil source delivery port Y; The 4th oil pump 14 oil outlets are connected with the 4th oil inlet P 4 of Hydraulic slewing system 2 through air-conditioning 74; Constant pressure oil source delivery port Y is connected with the trainstop control cock group 21 of Hydraulic slewing system 2, the telescopic oil cylinder transfer valve group 31 of hoisting arm expansion hydraulic efficiency pressure system 3, the duplex hoist brake control cock group 51 of the hydraulic efficiency pressure system that hoists 5 respectively, and phase control coordinates.
Control cock group 9 includes to be controlled flexible hydraulic control and controls the first drive block 91 of connection 41 spools commutations, controls the luffing hydraulic control and control the second drive block 92 of connection 42 spools commutations, control the main hydraulic control that hoists and control the 3rd drive block 93 of connection 43 spools commutations and control the 4 wheel driven motion block 94 that connection 44 spools commutations are controlled in the secondary hydraulic control that hoists, and the control port P on control cock group 9 all is communicated with constant pressure oil source delivery port Y oil circuit.
Fig. 1 and shown in Figure 6 is safe off-load Hydraulic System Principle; Also dispose on flow divider valve group 4 control that the second oil inlet P 2, the 3rd oil inlet P 3 liquid flow points close in the middle of control connection 45, the oil circuit of the 3rd oil inlet P 3 sides is all controlled the hydraulic control that hoists of connection 43, pair with the main hydraulic control that hoists and is controlled connection 44 pressure port and be connected, correspondingly, the oil circuit of the second oil inlet P 2 sides is all controlled connection 41 with flexible hydraulic control, the luffing hydraulic control is controlled connection 42 pressure port and is connected; Safe off-load hydraulic efficiency pressure system 8 also includes unloader valve group 81, and this unloader valve group 81 is furnished with the 4th electromagnetic valve DHF4, the 5th electromagnetic valve DHF5, the 6th electromagnetic valve DHF6; The 4th electromagnetic valve DHF4 is connected with the pilot control opening of the second safety valve 47, the 3rd safety valve 46 respectively, and phase control; The 5th electromagnetic valve DHF5 is connected with the pilot control opening of the tenth safety valve 43a, and phase control; The 6th electromagnetic valve DHF6 is connected with the pilot control opening of the 4th safety valve 41a, the 6th safety valve 42a, the 9th safety valve 43b, the 8th safety valve 44a respectively through the 4th check valve 82, and phase control; The first oil pump 11 oil outlet places are fitted with the first check valve DF1, and the second oil pump 12 oil outlet places are fitted with the second check valve DF2, and the 3rd oil pump 13 oil outlet places are fitted with the 3rd check valve DF3, and the 4th oil pump 14 oil outlet places are fitted with the 4th check valve DF4.
also configure the second safety valve 47 that limits the 3rd oil inlet P 3 pressure on flow divider valve group 4, limit the 3rd safety valve 46 of the second oil inlet P 2 pressure, on flow divider valve group 4, the first telescoping connection entrance A7 disposes the 4th safety valve 41a, the second telescoping connection entrance B7 disposes the 5th safety valve 41b, the first luffing access port A8 disposes the 6th safety valve 42a, the first pair access port A9 that hoists disposes the 7th safety valve 44b, the second pair access port B9 that hoists disposes the 8th safety valve 44a, the first main access port A10 that hoists disposes the 9th safety valve 43b, the second main access port B10 that hoists disposes the tenth safety valve 43a.
The workflow of this safe off-load hydraulic pressure is as described below:
by the combination of unloader valve group 81 with flow divider valve group 4, unloader valve group 81 is provided with eight actuator ports, be respectively A20, B20, B21, A22, B22, A23, B23, wherein actuator port A20 connects the remote control mouth V3 of the second safety valve 47, actuator port B20 connects the remote control mouth V2 of the 3rd safety valve 46, actuator port B21 connects the remote control mouth VB10 of the tenth safety valve 43a, actuator port A22 connects the remote control mouth VA10 of the 9th safety valve 43b, actuator port B22 connects the remote control mouth VB9 of the 8th safety valve 44a, actuator port A23 connects the remote control mouth VA8 of the 6th safety valve 42a, actuator port B23 connects the remote control mouth VA7 of the 4th safety valve 41a.
When the 4th electromagnetic valve DHF4 get electric, the 3rd safety valve 46 and the second safety valve 47 off-loads, the flow divider valve group can't build-up pressure, hoisting arm expansion hydraulic efficiency pressure system 3, suspension arm variable-amplitude hydraulic efficiency pressure system 6 and the hydraulic efficiency pressure system 2 that hoists can't be moved; When the 5th electromagnetic valve DHF5 gets electricly, the second main access port B10 that hoists can't build-up pressure, and in the hydraulic efficiency pressure system that hoists 5, main hoisting mechanism can't be completed down maneuver.
When the 6th electromagnetic valve DHF6 gets electric; flow divider valve group 4 actuator port VA10, VB9, VA8, VA7 can't build-up pressures; in the hydraulic efficiency pressure system that hoists 5, main hoisting mechanism can't be completed in the action that hoists, the hydraulic efficiency pressure system that hoists 5 auxiliary hoisting mechanism and can't complete that down maneuver, suspension arm variable-amplitude system 6 can't complete the width action and hoisting arm expansion hydraulic efficiency pressure system 3 can't be completed stretch, forms the protection to whole hydraulic efficiency pressure system safe action.
As Fig. 1 and shown in Figure 7, be the Hydraulic System Principle of control cock group, interior the concentrating of control cock group 9 has the first drive block 91, the second drive block 92, the 3rd drive block 93,4 wheel driven motion block 94 and the 5th drive block 95 and operation control valve 96.
Dispose two operation control valves 96 in the first drive block 91, each operation control valve 96 is all exported the first extension and contraction control mouth a1 and the second extension and contraction control mouth b1, correspondingly, flexible hydraulic control is controlled connection 41 and is furnished with the first extension and contraction control mouth a1 and the second extension and contraction control mouth b1 being positioned on flow divider valve group 4 sides, the operation that is operation control valve 96 produces hydraulic power, input to flexible hydraulic control control by the first extension and contraction control mouth a1, the second extension and contraction control mouth b1 and join 41 two ends, namely realized the operation of flexible hydraulic control control connection 41 valve rods.
Dispose two operation control valves 96 in the second drive block 92, each operation control valve 96 is all exported has the first luffing to control mouthful a2 and the second luffing control mouthful b2, correspondingly, the luffing hydraulic control is controlled connection 42 and is furnished with on flow divider valve group 4 sides that the first luffing is controlled mouthful a2 and the second luffing is controlled a mouthful b2 being positioned at, the operation that is operation control valve 96 produces hydraulic power, input to luffing hydraulic control control by the first luffing control mouth a2 and the second luffing control mouthful b2 and join 42 two ends, realized that namely luffing hydraulic control control joins the operation of 42 valve rods.
Dispose two operation control valves 96 in 4 wheel driven motion block 94, each operation control valve 96 is all exported the first secondary lift control mouth a3 and the second secondary lift control mouth b3, correspondingly, the pair hydraulic control that hoists is controlled connection 44 and is furnished with the first secondary lift control mouth a3 and the second secondary lift control mouth b3 being positioned on flow divider valve group 4 sides, the operation that is operation control valve 96 produces hydraulic power, input to the pair hydraulic control that hoists by the first secondary lift control mouth a3 and the second secondary lift control mouth b3 and control connection 44 two ends, realized that namely the secondary hydraulic control that hoists controls the operation of connection 44 valve rods.
Dispose two operation control valves 96 in the 3rd drive block 93, each operation control valve 96 is all exported the first main lift control mouth a4 and the second main lift control mouth b4, correspondingly, the main hydraulic control that hoists is controlled connection 43 and is furnished with the first main lift control mouth a4 and the second main lift control mouth b4 being positioned on flow divider valve group 4 sides, the operation that is operation control valve 96 produces hydraulic power, input to the main hydraulic control control that hoists by the first main lift control mouth a4 and the second main lift control mouth b4 and join 43 two ends, namely realized the operation of main hydraulic control control connection 43 valve rods that hoist.
Dispose two operation control valves 96 in the 5th drive block 95, each operation control valve 96 is all exported has the first revolution to control mouthful a0 and second a revolution control mouthful b0, correspondingly, the first commutation valve rod 23 two ends are furnished with that mouthful a0 is controlled in the first revolution and a mouthful b0 is controlled in the second revolution, the operation that is operation control valve 96 produces hydraulic power, control mouthful a0 and the second revolution by the first revolution and control a mouthful b0 and input to the first commutation valve rod 23 two ends, namely realized the operation of the first commutation valve rod 23 valve rods.
As depicted in figs. 1 and 2, Hydraulic slewing system principle; Hydraulic slewing system 2 also includes the rotary buffering valve group 22 that is connected with the 4th oil inlet P 4, is furnished with the first commutation valve rod 23, the second electromagnetic valve DHF2 and the first gyroscopic output mouth A11, the second gyroscopic output mouth B11 in rotary buffering valve group 22; Connect between the first gyroscopic output mouth A11, the second gyroscopic output mouth B11 and driven rotary motor 24, and being fitted with trainstop 28 on this rotary motor 24; Select to be formed with intermediate loop 22b through the first shuttle valve 22a between the first gyroscopic output mouth A11, the second gyroscopic output mouth B11, this intermediate loop 22b is connected with the second electromagnetic valve DHF2 import, and the second electromagnetic valve DHF2 outlet is connected with described the 4th oil inlet P 4 through the second reducing valve 22c.
The drive end 25a and first that is furnished with the first electromagnetic valve DHF1, the first pilot operated directional control valve 25, the second shuttle valve 26, the first one-way throttle valve 27, the second delivery port Y1 and the first control shuttle valve 29, the first pilot operated directional control valves 25 in trainstop control cock group 21 controls shuttle valve 29 intermediate ends and is connected; Control cock group 9 also includes the 5th drive block 95, the 5th drive block 95 output has that a mouthful a0 is controlled in the first revolution of controlling the first commutation valve rod 23 commutations, a mouthful b0 is controlled in the second revolution, and a mouthful a0 is controlled in described the first revolution, the second revolution is controlled mouthful b0 and is connected with the first two side ends of controlling shuttle valve 29 respectively; The import of the first electromagnetic valve DHF1 and the first pilot operated directional control valve 25 all is communicated with described constant pressure oil source delivery port Y oil circuit, and outlet is connected with the two side ends of the second shuttle valve 26 respectively, and the intermediate ends of this second shuttle valve 2 is connected with trainstop 28 through the first one-way throttle valve 27, the second delivery port Y1.
The workflow of this rotary system hydraulic pressure is as described below:
1, the right-hand rotation of Hydraulic slewing system operation:
The work fluid of the 4th oil pump 4 enters rotary buffering valve group 22 by the 4th check valve DF4, lower vehicle hydraulic system 10 and air-conditioning 74 by the 4th oil inlet P 4.the valve rod that the first commutation valve rod 23 is handled in hydraulic control commutates to the right, namely control the first revolution and control a mouthful a0 end build-up pressure, work fluid is by the first commutation valve rod 23, the first gyroscopic output mouth A11 output, enter rotary motor 24 by actuator port A24, and build-up pressure drives rotary motor 24, the first revolution is simultaneously controlled mouthful pressure of a0 end and is delivered to trainstop control cock group 21, control through first the first pilot operated directional control valve 25 that shuttle valve 29 selects to open sealing constant voltage fluid, constant voltage fluid select through the second shuttle valve 26 and the first one-way throttle valve 27 by the second delivery port Y1 to trainstop 28, open fast trainstop 28, swing type mechanism steadily enters the right-hand rotation working,
2, the left revolution operation of Hydraulic slewing system:
the valve rod that the first commutation valve rod 23 is handled in hydraulic control commutates left, a mouthful b0 end build-up pressure is controlled in i.e. the second revolution, work fluid is by the first commutation valve rod 23, the second gyroscopic output mouth B11 output, enter rotary motor 24 by actuator port B24, and build-up pressure drives rotary motor 24, the pressure that mouthful b0 is controlled in the second revolution simultaneously is delivered to trainstop control cock group 21, control through first the first pilot operated directional control valve 25 that shuttle valve 29 selects to open sealing constant voltage fluid, constant voltage fluid select through the second shuttle valve 26 and the first one-way throttle valve 27 by the second delivery port Y1 to trainstop 28, open fast trainstop 28, swing type mechanism steadily enters left revolution working,
3, the freedom centering of Hydraulic slewing system operation:
when swing type mechanism quits work, the first commutation valve rod 23 is replied meta under spring-force driven dual, work fluid returns system's fuel tank through the first commutation valve rod 23 valve rods and check valve group, rotary buffering valve group 22 is controlled end cap pressure and is disappeared, in trainstop control cock group 21, the first pilot operated directional control valve 25 resets under spring-force driven dual, cut off constant voltage fluid, the remaining fluid of trainstop 28 is through the second delivery port Y1, the first one-way throttle valve 27, the second shuttle valve 26, the first pilot operated directional control valve 25 and the slow off-load of oil return inlet T 6 to system without back pressure runner oil sump tank, trainstop 28 slowly closings, swing type mechanism quits work.
when swing type mechanism need to carry out the freedom centering operating mode, in rotary buffering valve group 22 in the second electromagnetic valve DHF2 and trainstop control cock group 21 the first electromagnetic valve DHF1 simultaneously electric, in rotary buffering valve group 22, the second electromagnetic valve DHF2 gets electric low pressure and links up the first gyroscopic output mouth A11 and two actuator ports of the second gyroscopic output mouth B11 of rotary motor 24 and select to form hydraulic circuit by the first shuttle valve 22a, in trainstop control cock group 21, the first electromagnetic valve DHF1 gets electric, the electromagnetic valve core of opening enclosed constant pressure oil source, constant pressure oil source enters trainstop 28 through the second shuttle valve 26 and the first one-way throttle valve 27 by the second delivery port Y1, open rapidly trainstop 28, realize that swing type mechanism freely turns round operation.
when swing type mechanism need to finish the freedom centering operating mode, cut off simultaneously in rotary buffering valve group 22 electric signal of the first electromagnetic valve DHF1 in the second electromagnetic valve DHF2 and trainstop control cock group 21, in rotary buffering valve group 22, the second electromagnetic valve DHF2 outage cut off low is linked up the hydraulic circuit of two actuator ports formation of rotary motor 24, in trainstop 28 control cock groups, constant pressure oil source is cut off in the first electromagnetic valve DHF1 outage, the remaining fluid of trainstop 28 is through the second delivery port Y1, the first one-way throttle valve 27, the second shuttle valve 26, electromagnetic valve core and the slow off-load of oil return inlet T 6 to system without back pressure runner oil sump tank, trainstop 28 slowly closings, swing type mechanism stops the freedom centering operation.
as shown in figures 1 and 3, be the hoisting arm expansion Hydraulic System Principle, hoisting arm expansion hydraulic efficiency pressure system 3 also includes the first telescopic oil cylinder 33, the second telescopic oil cylinder 34, is furnished with the first flexible delivery port A12 on telescopic oil cylinder transfer valve group 31, the second flexible delivery port B12 and flexible oil inlet P 6, flexible hydraulic control is controlled connection 41 outlets and is furnished with respectively the first telescoping connection entrance A7, the second telescoping connection entrance B7, the first telescoping connection entrance A7 is connected with flexible oil inlet P 6, the first flexible delivery port A12 is connected through the rodless cavity oil inlet end of the first one-way balance valve 32 with the first telescopic oil cylinder 33, the second flexible delivery port B12 is through the second one-way balance valve 36, transition spool piece 33a in the middle of the first telescopic oil cylinder 33 is connected with the rodless cavity oil inlet end of the second telescopic oil cylinder 34, and the first telescopic oil cylinder 33, the rod chamber oil inlet end of the second telescopic oil cylinder 34 is connected with the second telescoping connection entrance B7 simultaneously.
The first extension and contraction control mouth P7 of the first one-way balance valve 32, the second extension and contraction control mouth P8 of the second one-way balance valve 36 all are communicated with the second telescoping connection entrance B7; Telescopic oil cylinder transfer valve group 31 also is furnished with the 3rd electromagnetic valve DHF3 and the second pilot operated directional control valve 35, the import of the 3rd electromagnetic valve DHF3 is communicated with constant pressure oil source delivery port Y oil circuit, and the outlet of the 3rd electromagnetic valve DHF3 is communicated with the drive end 35a of the second pilot operated directional control valve 35; Also be equipped with damping 38 in telescopic oil cylinder transfer valve group 31, and this damping 38 two ends are communicated with the second pilot operated directional control valve 35 return openings, outside oil return inlet T 7 respectively.
The workflow of this hoisting arm expansion hydraulic efficiency pressure system is as described below:
The work fluid of the first oil pump 11 by the first check valve DF1 and in return the work fluid that enters flow divider valve group 4, the second oil pumps 12 by the 3rd oil inlet P 3 by the second check valve DF2 and in return and enter flow divider valve group 4 by the first oil inlet P 2.
1, the contracting arm of this hoisting arm expansion hydraulic efficiency pressure system operation:
the flexible hydraulic control of hydraulic operation is controlled connection 41 valve rods and is commutated to the right, the work fluid of the first oil pump 11 and the second oil pump 12 collaborates to control by flexible hydraulic control the rod chamber that connection the 41 and second telescoping connection entrance B7 output enters respectively the first telescopic oil cylinder 33 and the second telescopic oil cylinder 34, build-up pressure promotes two telescopic oil cylinders, pressure signal is delivered to respectively two telescopic oil cylinders the first one-way balance valve 32 simultaneously, the first extension and contraction control mouth P7 of the second one-way balance valve 36, the second extension and contraction control mouth P8, and steadily open two telescopic oil cylinders the first one-way balance valve 32, the second one-way balance valve 36, two telescopic oil cylinders 33, the fluid of 34 rodless cavities is under the rod chamber pressure-acting, the work fluid of the first telescopic oil cylinder 33 rodless cavities is by actuator port B13, balance valve core, actuator port A13 and actuator port A12 enter flexible transfer valve group 31, the work fluid of the second telescopic oil cylinder 34 rodless cavities is by actuator port B14, balance valve core, actuator port A14 and actuator port B12 enter flexible transfer valve group 31.In the 3rd electromagnetic valve DHF3 in flexible transfer valve group 31 must not electric situation, the work fluid that enters flexible transfer valve group 31 actuator port A12 switches spool, flexible oil inlet P 6, the first telescoping connection entrance A7 and flexible hydraulic control and controls connection 41 to the oil return runners of flow divider valve group 4 to fuel tank through flexible, completes the contracting arm action of the first telescopic oil cylinder 33.
When flexible transfer valve group 31 the 3rd electromagnetic valve DHF3 gets in electric situation, the second pilot operated directional control valve 35 spools of opening enclosed constant pressure oil source, constant voltage fluid promotes the flexible spool that switches and commutates, the flexible switching spool, flexible oil inlet P 6, the first telescoping connection entrance A7 and the flexible hydraulic control control that enter the work fluid process commutation of actuator port B12 join the 41 oil return runners that arrive flow divider valve group 4 to fuel tank, and the contracting arm of completing the second telescopic oil cylinder 34 is moving.
When flexible transfer valve group 31 the 3rd electromagnetic valve DHF3 outage, the 3rd electromagnetic valve DHF3 spool resets under acting force of the spring, cut off constant pressure oil source, and link up to switch the second remaining fluid of pilot operated directional control valve 35 spool control ends by unloading port L2 to without back pressure off-load runner to fuel tank, the switching spool resets under spring-force driven dual.Simultaneously at the first telescopic oil cylinder 33 and the second telescopic oil cylinder 34 under full semi-girder state, operate separately the first telescopic oil cylinder 33, because transition spool piece 33a volume diminishes, cause the interior voltage rise of transition spool piece 33a high, transition spool piece 33a pressure oil liquid effectively discharges by the damping 37 in flexible transfer valve group 31 at this moment; Also can prevent simultaneously interlock, namely the second telescopic oil cylinder 34 first telescopic oil cylinder 33 that contracts when entirely not stretching out state, cause the second overhanging phenomenon of telescopic oil cylinder 34; At the first telescopic oil cylinder 33 and the second telescopic oil cylinder 34 under full reduced arm state, operate separately the first telescopic oil cylinder 33, because transition spool piece 33a volume becomes large, cause forming in transition spool piece 33a vacuum, transition spool piece 33a through flexible with check valve 38 from system without the oil suction of back pressure off-load runner.Also can prevent simultaneously interlock, i.e. the second telescopic oil cylinder 34 first telescopic oil cylinder 33 that contracts when not full reduced time state, cause the second telescopic oil cylinder 34 rebound phenomenons, the fluid that flexible transfer valve group 31 is switched core retracing spring chamber by return opening L1 to without back pressure off-load runner to fuel tank.
2, the semi-girder of this hoisting arm expansion hydraulic efficiency pressure system operation:
The flexible hydraulic control of hydraulic operation is controlled connection 41 valve rods and is commutated left, and the work fluid of the first oil pump 11 and the second oil pump 12 collaborates to control connection the 41 and first telescoping connection entrance A7 by flexible hydraulic control to be exported, and enters flexible transfer valve group 31 by flexible oil inlet P 6.Flexible transfer valve group 31 the 3rd electromagnetic valve DHF3 is in must not electric situation, the work fluid that is entered by flexible oil inlet P 6 enters the rodless cavity of the first telescopic oil cylinder 33 through switching spool, actuator port A12, actuator port A13, the first one-way balance valve 32 and actuator port B13, build-up pressure promotes the first telescopic oil cylinder 33, the work fluid of the first telescopic oil cylinder 33 rod chambers is controlled connection 41 to flow divider valve group 4 oil return runners to fuel tank by the second telescoping connection entrance B7, flexible hydraulic control under pressure promotes, complete the semi-girder operation of the first telescopic oil cylinder 33.
flexible transfer valve group 31 the 3rd electromagnetic valve DHF3 is getting in electric situation, the 3rd electromagnetic valve DHF3 of opening enclosed constant pressure oil source, constant voltage fluid promotes the second pilot operated directional control valve 35 spools and commutates, the work fluid that is entered by flexible oil inlet P 6 is through the switching spool of commutation, actuator port B12, actuator port A14, the second one-way balance valve 36 and actuator port B14 enter the rodless cavity of the second telescopic oil cylinder 34, build-up pressure promotes the second telescopic oil cylinder 34, the work fluid of the second telescopic oil cylinder 34 rod chambers under pressure promotes by the second telescoping connection entrance B7, flexible hydraulic control is controlled connection 41 to flow divider valve group 4 oil return runners to fuel tank, complete the semi-girder operation of the second telescopic oil cylinder 34.
As shown in Figure 1 and Figure 4, be the Hydraulic System Principle that hoists; The hydraulic efficiency pressure system that hoists 5 includes main hoisting mechanism 56 and auxiliary hoisting mechanism 57, and auxiliary hoisting mechanism 57 includes pair hoist balance cock group 55, secondary lifting motor 52, disposes secondary lifting motor drg 58 on secondary lifting motor 52; The pair hydraulic control that hoists is controlled connection 44 outlets and is furnished with respectively the first pair access port A9, the second pair access port B9 that hoists that hoists, the first pair access port A9 that hoists is connected with secondary lifting motor 52 1 ends through the pair balance cock group 55 that hoists, and access port B9 is connected with secondary lifting motor 52 other ends and the second pair hoists; The pair balance cock group 55 that hoists is furnished with pair hoist balance cock 55a and the 3rd shuttle valve 55b, hoist the first control end X1 on balance cock 55a, the 3rd shuttle valve 55b one side of pair all is connected with the second pair access port B9 that hoists, another side of the 3rd shuttle valve 55b and the first pair access port A9 that hoists is connected, and the drive end of the 3rd pilot operated directional control valve 51a in the first intermediate ends C1 of the 3rd shuttle valve 55b and duplex hoist brake control cock group 51 is connected; The 3rd pilot operated directional control valve 51a oil inlet is communicated with constant pressure oil source delivery port Y oil circuit, and the oil outlet of the 3rd pilot operated directional control valve 51a is connected with secondary lifting motor drg 58.
One, the workflow of this auxiliary hoisting mechanism is as described below:
The work fluid of the first oil pump 1 by the first check valve DF1 and in return the work fluid that enters flow divider valve group 4, the second oil pumps 12 by 3 mouthfuls of the 3rd oil inlet P by the second oil pump 12, the second check valve DF2 and in return and enter flow divider valve group 4 by 2 mouthfuls of the second oil inlet P.
1, auxiliary hoisting mechanism step-down operation:
connection 44 commutation is to the right controlled in the hydraulic control that hoists of fluid control pair, the work fluid of the first oil pump 11 and the second oil pump 12 interflow is by the access port B9 output that hoists of the second pair, enter secondary lifting motor 52 by actuator port B17, build-up pressure also drives secondary lifting motor 52, pressure signal transmission pair the first control end X1 of balance cock group 55 that hoists simultaneously, a pressure signal fluid part is steadily opened the pair balance cock 55a core that hoists, another part is selected through hoist the 3rd shuttle valve 55b of balance cock group 55 of pair, by the first intermediate ends C1 output, be delivered to duplex hoist brake control cock group 51 control port a5, the pressure signal fluid of duplex hoist brake control cock group 51 control port a5 is opened the pilot operated directional control valve 51a of sealing constant voltage fluid, constant pressure oil source delivery port Y steadily opens secondary lifting motor drg 58 through damping by delivery port b5 output, secondary lifting motor 52 steadily enters the decline operating mode, drive the postrotational work fluid of secondary lifting motor 52 by actuator port A17, actuator port B16, balance valve core, actuator port A16, hoist access port A9 and control the secondary hydraulic control that hoists and control connection 44 to the oil return runner of flow divider valve group 4 to fuel tank of the first pair, complete the auxiliary hoisting mechanism down maneuver.
2, auxiliary hoisting mechanism plays lift operations:
connection 44 commutation is left controlled in the hydraulic control that hoists of hydraulic operation pair, the work fluid of the first oil pump 11 and the second oil pump 12 interflow is by the access port A9 output that hoists of the first pair, by actuator port A16, the pair balance cock group 55 that hoists, actuator port B16 and actuator port A17 enter secondary lifting motor 52, and build-up pressure drives secondary lifting motor 52, simultaneously pressure signal is selected by the 3rd shuttle valve 55b that pair hoists in balance cock group 55, by the pair balance cock group 55 first intermediate ends C1 outputs that hoist, be delivered to duplex hoist brake control cock group 51 control port a5, the pressure signal fluid of duplex hoist brake control cock group 51 control port a5 is opened the 3rd pilot operated directional control valve 51a of sealing constant voltage fluid, constant voltage fluid is steadily opened secondary lifting motor drg 58 through damping by delivery port b5 output, secondary lifting motor 52 steadily enters the operating mode that hoists, drive the postrotational work fluid of secondary lifting motor 52 by actuator port B17, hoist access port B9 and control the secondary hydraulic control that hoists and control connection 44 to the oil return runner of flow divider valve group 4 to fuel tank of the second pair, complete the auxiliary hoisting mechanism action that hoists.
3, auxiliary hoisting mechanism shut-down operation:
When auxiliary hoisting mechanism 57 quits work, the pair hydraulic control that hoists is controlled connection 44 reply meta under spring-force driven dual, 52 liang of actuator port A17 of secondary lifting motor, B17 pressure disappear, the 3rd pilot operated directional control valve 51a in duplex hoist brake control cock group 51 resets under spring-force driven dual, cut off constant voltage fluid, the remaining fluid of secondary lifting motor drg 58 through output oil port b5 and the steady off-load of damping through oil return inlet T 8 to system without back pressure runner oil sump tank, secondary lifting motor drg 58 is steadily closed, and auxiliary hoisting mechanism quits work.
Two, the workflow of main hoisting mechanism is as described below:
Main hoisting mechanism 56 includes main hoist balance cock group 54, main lifting motor 53, disposes main lifting motor drg 59 on main lifting motor 53; The main hydraulic control that hoists is controlled connection 43 outlets and is furnished with respectively the first main access port A10 that hoists, the second main access port B10 that hoists, the first main access port A10 that hoists is connected with main lifting motor 53 1 ends through the main balance cock group 54 that hoists, and the second main access port B10 that hoists is connected with main lifting motor 53 other ends; The main balance cock group 54 that hoists is furnished with main hoist balance cock 54a and the 4th shuttle valve 54b, the second control end X2 on the main balance cock 54a that hoists, the 4th shuttle valve 54b one side all are connected with the second main access port B10 that hoists, another side of the 4th shuttle valve 54b and the first main access port A10 that hoists are connected, and the drive end of the 4th pilot operated directional control valve 51b in the second intermediate ends C2 of the 4th shuttle valve 54b and duplex hoist brake control cock group 51 is connected; The oil inlet of the 4th pilot operated directional control valve 51b is communicated with constant pressure oil source delivery port Y oil circuit, and the oil outlet of the 4th pilot operated directional control valve 51b is connected with main lifting motor drg 59.
1, the step-down operation of main hoisting mechanism:
connection 43 commutation is to the right controlled in the main hydraulic control that hoists of hydraulic operation, the work fluid of the first oil pump 11 and the second oil pump 12 interflow is controlled the main access port B10 that hoists of connection 43 and second and is exported by the master hydraulic control that hoists, enter main lifting motor 53 by actuator port B19 again, build-up pressure also drives main lifting motor 53, pressure signal transmission master the second control end X2 of balance cock group 54 that hoists simultaneously, a pressure signal fluid part is steadily opened the main balance valve core 54a that hoists, another part is selected through the 4th shuttle valve 54b of the main balance cock group 54 that hoists, by the second intermediate ends C2 output, be delivered to duplex hoist brake control cock group 51 control port a6, the pressure signal fluid of duplex hoist brake control cock group 51 control port a6 is opened the 4th pilot operated directional control valve 51b of sealing constant voltage fluid, constant voltage fluid is steadily opened main lifting motor drg 59 through damping by delivery port b6 output, main lifting motor 53 steadily enters the decline operating mode, drive the postrotational work fluid of main lifting motor 53 by actuator port A19, actuator port B18, balance valve core, the main balance cock group actuator port A18 that hoists, the first main hoist access port A10 and main hydraulic control that hoists controlled connection 43 to the oil return runner of flow divider valve group 4 to fuel tank, complete the main hoisting mechanism down maneuver.
2, a lift operations of main hoisting mechanism:
connection 43 commutation is left controlled in the main hydraulic control that hoists of hydraulic operation, the work fluid of the first oil pump 11 and the second oil pump 12 interflow is controlled the main access port A10 that hoists of connection 43 and first and is exported by the master hydraulic control that hoists, by actuator port A18, the main balance cock group check valve 54a that hoists, actuator port B18 and actuator port A19 enter main lifting motor 53, and build-up pressure drives main lifting motor 53, pressure signal is selected by the 4th shuttle valve 54b in the main balance cock group 54 that hoists simultaneously, by the second intermediate ends C2 output, be delivered to duplex hoist brake control cock group 51 control port a6, the pressure signal fluid of duplex hoist brake control cock group 51 control port a6 is opened the 4th pilot operated directional control valve 51a of sealing constant voltage fluid, constant voltage fluid is steadily opened main lifting motor drg 59 through damping by delivery port b6 output, main lifting motor 53 steadily enters the operating mode that hoists, drive the postrotational work fluid of main lifting motor 53 by actuator port B19, the second main hoist access port B10 and main hydraulic control that hoists controlled connection 43 to the oil return runner of flow divider valve group 4 to fuel tank, complete the main hoisting mechanism action that hoists.
3, the shut-down operation of main hoisting mechanism:
When main hoisting mechanism quits work, the main hydraulic control that hoists is controlled connection 43 and reply meta under spring-force driven dual, 53 liang of actuator port A19 of main lifting motor, B19 pressure disappear, pilot operated directional control valve in duplex hoist brake control cock group 51 resets under spring-force driven dual, cut off constant voltage fluid, the remaining fluid of main lifting motor drg 59 through output oil port b6 and the steady off-load of damping through oil return inlet T 8 to system without back pressure runner oil sump tank, main lifting motor drg 59 is steadily closed, and main hoisting mechanism quits work.
As Fig. 1 and shown in Figure 5, be the suspension arm variable-amplitude Hydraulic System Principle; Suspension arm variable-amplitude hydraulic efficiency pressure system 6 includes amplitude oil cylinder balance cock group 61 and amplitude oil cylinder 62, the luffing hydraulic control is controlled connection 42 outlets and is furnished with respectively the first luffing access port A8, the second luffing access port B8, the first luffing access port A8 controls a mouthful P9 with the 3rd of amplitude oil cylinder 62 rod chambers, amplitude oil cylinder balance cock group 61 and is connected, and the second luffing access port B8 is connected with described amplitude oil cylinder 62 rodless cavities through amplitude oil cylinder balance cock group 61.
The workflow of this suspension arm variable-amplitude hydraulic efficiency pressure system is as described below:
The work fluid of the first oil pump 11 by the first check valve DF1 and in return the work fluid that enters flow divider valve group 4, the second oil pumps 12 by 3 mouthfuls of the 3rd oil inlet P by the second check valve DF2 and in return and enter flow divider valve group 4 by 2 mouthfuls of the second oil inlet P.
1, the width operation that falls of amplitude oil cylinder: connection 42 commutation is to the right controlled in the 4 luffing hydraulic controls of hydraulic operation flow divider valve group, the work fluid of the first oil pump 11 and the second oil pump 12 collaborates to enter the rod chamber of amplitude oil cylinder 62 by the first luffing access port A8 output, build-up pressure promotes amplitude oil cylinder 62, the control port P9 of while pressure signal transmission amplitude oil cylinder balance cock 61, and steadily open amplitude oil cylinder balance cock 61 cores, the fluid of amplitude oil cylinder 62 rodless cavities is under the rod chamber pressure-acting, the work fluid of amplitude oil cylinder 62 rodless cavities is by amplitude oil cylinder balance cock group 61 actuator port B15, balance valve core, amplitude oil cylinder balance cock group 61 actuator port A15, the second luffing access port B8 and luffing hydraulic control are controlled connection 42 and are arrived the oil return runner of flow divider valve group 4 to fuel tank, complete fall width action of amplitude oil cylinder 62.
2, the width that rises of amplitude oil cylinder operates: the hydraulic control of hydraulic operation luffing is controlled connection 42 valve rods and is commutated left, the work fluid of the first oil pump 1 and the second oil pump 2 collaborates by the second luffing access port B8 output, by actuator port A15, amplitude oil cylinder balance cock 61 nonreturn valve cores and actuator port B15 enter the rodless cavity of amplitude oil cylinder 62, build-up pressure promotes amplitude oil cylinder 62, the work fluid of amplitude oil cylinder 62 rod chambers under pressure promotes by flow divider valve group 4 first luffing access port A8, the luffing hydraulic control is controlled connection 42 to flow divider valve group 4 oil return runners to fuel tank, complete a width operation of amplitude oil cylinder 62.
The invention has the advantages that: the open and shut characteristic of trainstop, major and minor hoist brake all adopts the constant pressure oil source mode, all need not the additional external force operation, and intelligence realizes the control of drg automatically according to the operation of each action; According to the different open and shut characteristics of each mechanism, revolving structure is changed down soon the mode of pass, to the mode of major and minor hoisting mechanism slow opening fast shutting, actv. is eliminated the compression shock of system; Flow divider valve adopts the assignment of traffic pattern irrelevant with load, and actv. prevents that the Pressure interference that produces between each actuating unit from causing the slow in one's movements or attonity of the high actuating unit of load pressure; The by pass valve of the by pass valve of each actuator port of flow divider valve and two oil-feed actuator ports all is provided with the remote control hydraulic fluid port, and connected system unloader valve group directly solves Security Control Problem on main valve; In Full Vehicle System, the integrated and modularization of each element heights, reduced the Full Vehicle System pipeline, maintains easily; Full Vehicle System is applicable to variable pump systems and Constant Pump System simultaneously.
Most preferred embodiment of the present invention is illustrated, and various variations or the remodeling made by those of ordinary skills can not depart from the scope of the present invention.

Claims (10)

1. hydraulic controlled operation quadruple pump hydraulic system, include the first oil pump (11), the second oil pump (12), the 3rd oil pump (13), the 4th oil pump (14), Hydraulic slewing system (2), hoisting arm expansion hydraulic efficiency pressure system (3), control hydraulic efficiency pressure system (8), the hydraulic efficiency pressure system that hoists (5), suspension arm variable-amplitude hydraulic efficiency pressure system (6), guide oil source valve group (7) and control cock group (9); It is characterized in that: described control hydraulic efficiency pressure system (8) includes flow divider valve group (4), and described flow divider valve group (4) two ends are equipped with respectively the 3rd oil inlet (P3) that is communicated with the first oil pump (11) outlet, export with the second oil pump (12) the second oil inlet (P2) that is communicated with; The master who dispose on described flow divider valve group (4) that connection (41) is controlled in the flexible hydraulic control of controlling hoisting arm expansion hydraulic efficiency pressure system (3), connection (42) is controlled in the luffing hydraulic control of controlling suspension arm variable-amplitude hydraulic efficiency pressure system (6), controls the hydraulic efficiency pressure system (5) that the hoists hydraulic control that hoists is controlled the hydraulic control that hoists of connection (43) and pair and is controlled and join (44);
Dispose the first oil inlet (P1) that is communicated with the 3rd oil pump (13) outlet on described guide oil source valve group (7), described the first oil inlet (P1) exit end is connected with respectively constant voltage controlling water kick valve (71), energy storage (72) and constant pressure oil source delivery port (Y); Described the 4th oil pump (14) oil outlet is connected with the 4th oil inlet (P4) of Hydraulic slewing system (2) through air-conditioning (74); Described constant pressure oil source delivery port (Y) is connected with the duplex hoist brake control cock group (51) of the trainstop control cock group (21) of Hydraulic slewing system (2), the telescopic oil cylinder transfer valve group (31) of hoisting arm expansion hydraulic efficiency pressure system (3), the hydraulic efficiency pressure system that hoists (5) respectively, and this constant pressure oil source delivery port (Y) is implemented to control;
Described control cock group (9) includes to be controlled flexible hydraulic control and controls first drive block (91) of connection (41) spool commutation, controls the luffing hydraulic control and control second drive block (92) of connection (42) spool commutation, control the main hydraulic control that hoists and control the 3rd drive block (93) of connection (43) spool commutation and control the pair hydraulic control that hoists and control the 4 wheel driven motion block (94) that connection (44) spool commutates, and the control port (P) on control cock group (9) all is communicated with described constant pressure oil source delivery port (Y) oil circuit.
2. hydraulic controlled operation quadruple pump hydraulic system according to claim 1, it is characterized in that: also dispose on described flow divider valve group (4) and control the second oil inlet (P2), connection (45) is controlled in the middle hydraulic control that the 3rd oil inlet (P3) liquid flow point closes, the oil circuit of the 3rd oil inlet (P3) side is all controlled connection (43) with the main hydraulic control that hoists, the pair hydraulic control that hoists is controlled connection (44) pressure port and is connected, correspondingly, the oil circuit of the second oil inlet (P2) side is all controlled connection (41) with flexible hydraulic control, the luffing hydraulic control is controlled connection (42) pressure port and is connected.
3. hydraulic controlled operation quadruple pump hydraulic system according to claim 2, it is characterized in that: described Hydraulic slewing system (2) also includes the rotary buffering valve group (22) that is connected with the 4th oil inlet (P4), is furnished with the first commutation valve rod (23), the second electromagnetic valve (DHF2) and the first delivery port (A11, B11) in described rotary buffering valve group (22); Described the first delivery port (A11, B11) termination connects and has driven rotary motor (24), and is fitted with trainstop (28) on this rotary motor (24); Select to be formed with intermediate loop (22b) through the first shuttle valve (22a) between described the first delivery port (A11, B11), this intermediate loop (22b) is connected with the second electromagnetic valve (DHF2) import, and the second electromagnetic valve (DHF2) outlet is connected with described the 4th oil inlet (P4) through the second reducing valve (22c).
4. hydraulic controlled operation quadruple pump hydraulic system according to claim 3, it is characterized in that: be furnished with the first electromagnetic valve (DHF1), the first pilot operated directional control valve (25), the second shuttle valve (26), the first one-way throttle valve (27), the second delivery port (Y1) and the first control shuttle valve (28) in described trainstop control cock group (21), the drive end (25a) of the first pilot operated directional control valve (25) and described first is controlled shuttle valve (28) intermediate ends and is connected; Described control cock group (9) also includes the 5th drive block (95), the 5th drive block (95) output has the control mouth (a0, b0) of controlling the first commutation valve rod (23) commutation, and described control mouthful (a0, b0) is connected with the first two side ends of controlling shuttle valve (28) respectively; The import of the first electromagnetic valve (DHF1) and the first pilot operated directional control valve (25) all is communicated with described constant pressure oil source delivery port (Y) oil circuit, and outlet is connected with the two side ends of the second shuttle valve (26) respectively, and the intermediate ends of this second shuttle valve (26) is connected with described trainstop (28) through the first one-way throttle valve (27), the second delivery port (Y1).
5. hydraulic controlled operation quadruple pump hydraulic system according to claim 2, it is characterized in that: described hoisting arm expansion hydraulic efficiency pressure system (3) also includes the first telescopic oil cylinder (33), the second telescopic oil cylinder (34), be furnished with first group of port on described telescopic oil cylinder transfer valve group (31), described flexible hydraulic control is controlled connection (41) outlet and is furnished with respectively second group of port, the first telescoping connection entrance (A7) is connected with the second telescoping connection entrance (P6), the first flexible delivery port (A12) is connected through the rodless cavity oil inlet end of the first one-way balance valve (32) with the first telescopic oil cylinder (33), the second flexible delivery port (B12) is through the second one-way balance valve (36), transition spool piece (33a) in the middle of the first telescopic oil cylinder (33) is connected with the rodless cavity oil inlet end of the second telescopic oil cylinder (34), and the first telescopic oil cylinder (33), the rod chamber oil inlet end of the second telescopic oil cylinder (34) is connected with the second telescoping connection entrance (B7) simultaneously.
6. hydraulic controlled operation quadruple pump hydraulic system according to claim 5, it is characterized in that: the control mouth (P7) of described the first one-way balance valve (32), the control mouth (P8) of the second one-way balance valve (36) all are communicated with described the second telescoping connection entrance (B7); Described telescopic oil cylinder transfer valve group (31) also is furnished with the 3rd electromagnetic valve (DHF3) and the second pilot operated directional control valve (35), the import of the 3rd electromagnetic valve (DHF3) is communicated with constant pressure oil source delivery port (Y) oil circuit, and the outlet of the 3rd electromagnetic valve (DHF3) is communicated with the drive end (35a) of the second pilot operated directional control valve (35); Also be equipped with damping (38) in described telescopic oil cylinder transfer valve group (31), and this damping (38) two ends are communicated with the second pilot operated directional control valve (35) return opening, outside return opening (T7) respectively.
7. hydraulic controlled operation quadruple pump hydraulic system according to claim 2, it is characterized in that: the described hydraulic efficiency pressure system that hoists (5) includes main hoisting mechanism (56) and auxiliary hoisting mechanism (57), described auxiliary hoisting mechanism (57) includes pair hoist balance cock group (55), secondary lifting motor (52), disposes secondary lifting motor drg (58) on described secondary lifting motor (52); The hydraulic control that hoists of described pair is controlled connection (44) outlet and is furnished with respectively the 3rd group of port, the first pair access port (A9) that hoists is connected with secondary lifting motor (52) one ends through the pair balance cock group (55) that hoists, and access port (A9) is connected with secondary lifting motor (52) other end and the second pair hoists; the described pair balance cock group (55) that hoists is furnished with pair hoist balance cock (55a) and the 3rd shuttle valve (55b), pair the first control end (X1) on balance cock (55a) that hoists, the 3rd shuttle valve (55b) side all is connected with the second pair access port (A9) that hoists, another side of the 3rd shuttle valve (55b) and the first pair access port (A9) that hoists is connected, and the drive end of the 3rd pilot operated directional control valve (51a) in the intermediate ends (C1) of the 3rd shuttle valve (55b) and duplex hoist brake control cock group (51) is connected, described the 3rd pilot operated directional control valve (51a) oil inlet is communicated with constant pressure oil source delivery port (Y) oil circuit, and the oil outlet of the 3rd pilot operated directional control valve (51a) is connected with described secondary lifting motor drg (58).
8. hydraulic controlled operation quadruple pump hydraulic system according to claim 7, it is characterized in that: described main hoisting mechanism (56) includes main hoist balance cock group (54), main lifting motor (53), disposes main lifting motor drg (59) on described main lifting motor (53); The described master hydraulic control that hoists is controlled connection (43) outlet and is furnished with respectively the 4th group of port, the first main access port (A10) that hoists is connected with main lifting motor (53) one ends through the main balance cock group (54) that hoists, and the second main access port (B10) that hoists is connected with main lifting motor (53) other end; the described master balance cock group (54) that hoists is furnished with main balance cock (54a) and the 4th shuttle valve (54b) of hoisting, the second control end (X2) on the main balance cock (54a) that hoists, the 4th shuttle valve (54b) side all is connected with the second main access port (B10) that hoists, another side of the 4th shuttle valve (54b) is connected with the first main access port (A10) that hoists, and the drive end of the 4th pilot operated directional control valve (51b) in the intermediate ends (C2) of the 4th shuttle valve (54b) and duplex hoist brake control cock group (51) is connected, the oil inlet of described the 4th pilot operated directional control valve (51b) is communicated with constant pressure oil source delivery port (Y) oil circuit, and the oil outlet of the 4th pilot operated directional control valve (51b) is connected with described main lifting motor drg (59).
9. hydraulic controlled operation quadruple pump hydraulic system according to claim 2, it is characterized in that: described suspension arm variable-amplitude hydraulic efficiency pressure system (6) includes amplitude oil cylinder balance cock group (61) and amplitude oil cylinder (62), described luffing hydraulic control is controlled connection (42) outlet and is furnished with respectively the 5th group of port, the first luffing access port (A8) and amplitude oil cylinder (62) rod chamber, the control mouth (P9) of amplitude oil cylinder balance cock group (61) connects, and the second luffing access port (B8) is connected with described amplitude oil cylinder (62) rodless cavity through amplitude oil cylinder balance cock group (61).
10. hydraulic controlled operation quadruple pump hydraulic system according to claim 2, it is characterized in that: also configure the second safety valve (47) that limits the 3rd oil inlet (P3) pressure on described flow divider valve group (4), limit the 3rd safety valve (46) of the second oil inlet (P2) pressure, upper the first telescoping connection entrance (A7) of described flow divider valve group (4) disposes the 4th safety valve (41a), the second telescoping connection entrance (B7) disposes the 5th safety valve (41b), the first luffing access port (A8) disposes the 6th safety valve (42a), the first pair access port (A9) that hoists disposes the 7th safety valve (44b), the second pair access port (A9) that hoists disposes the 8th safety valve (44a), the first main access port (A10) that hoists disposes the 9th safety valve (43b), the second main access port (B10) that hoists disposes the tenth safety valve (43a), described control hydraulic efficiency pressure system (8) also includes unloader valve group (81), and this unloader valve group (81) is furnished with the 4th electromagnetic valve (DHF4), the 5th electromagnetic valve (DHF5), the 6th electromagnetic valve (DHF6), described the 4th electromagnetic valve (DHF4) is connected with the pilot control opening of the second safety valve (47), the 3rd safety valve (46) respectively, and phase control, described the 5th electromagnetic valve (DHF5) is connected with the pilot control opening of the tenth safety valve (43a), and phase control, described the 6th electromagnetic valve (DHF6) is connected with the pilot control opening of the 4th safety valve (41a), the 6th safety valve (42a), the 9th safety valve (43b), the 8th safety valve (44a) respectively through the 4th check valve (91), and the 6th electromagnetic valve (DHF6) is implemented to control, described the first oil pump (11) oil outlet place is fitted with the first check valve (DF1), described the second oil pump (12) oil outlet place is fitted with the second check valve (DF2), described the 3rd oil pump (13) oil outlet place is fitted with the 3rd check valve (DF3), and described the 4th oil pump (14) oil outlet place is fitted with the 4th check valve (DF4).
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CN103420272B (en) * 2012-05-24 2015-11-11 合肥神马科技集团有限公司 The hydraulic efficiency pressure system of a kind of hoisting crane and control composite move thereof
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