CN101863421A - Hydraulic operation triple pump hydraulic system - Google Patents

Hydraulic operation triple pump hydraulic system Download PDF

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CN101863421A
CN101863421A CN201010173075A CN201010173075A CN101863421A CN 101863421 A CN101863421 A CN 101863421A CN 201010173075 A CN201010173075 A CN 201010173075A CN 201010173075 A CN201010173075 A CN 201010173075A CN 101863421 A CN101863421 A CN 101863421A
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control
valve
hydraulic
hoists
oil
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CN101863421B (en
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卢宇
李新
邹泉敏
刘峰
刘富良
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Abstract

The invention relates to a hydraulic operation triple pump hydraulic system, which comprises a first oil pump, a second oil pump, a third oil pump, a rotary hydraulic system, a hoisting arm extension and retraction system, a safety unload hydraulic system, a lifting hydraulic system, a hoisting arm amplitude variation hydraulic system, a pressure reduction pilot oil source valve group and a control valve group, wherein the starting and closing characteristics of a rotary braking device, a main hoisting braking device and a sub hoisting braking device adopt the constant-pressure oil source control mode without additional external force operation, and the control on the braking devices can be intelligently and automatically realized according to the operation of each action. The invention realizes the fast-opening slow-closing control mode on a rotary structure and the slow-opening fast-closing control mode on main and sub hosting mechanisms according to different starting and closing characteristics of each mechanism, and effectively eliminates the pressure impact on the system. A flow distribution valve adopts the flow distribution mode irrelevant with a load, so slow action or no action of executing mechanisms with high load pressure caused by pressure interference among all executing mechanisms can be effectively prevented. Each element in the whole vehicle system has high integration and modularization, and the maintenance is convenient.

Description

Hydraulic operation triple pump hydraulic system
Technical field
The present invention relates to the technical field of hydraulic efficiency pressure system, particularly a kind of hydraulic operation triple pump hydraulic system is 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 finish frequently that thing carries that lifting, band carry that revolution, weight are transferred, 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 requirement that the open and shut characteristic of the safety control of each actuating unit, each actuating unit and car load hydraulic efficiency pressure system element heights are integrated.
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 between a plurality of actuating units in parallel and interfere, the actuating unit that resistance is bigger then 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 investigation fault and maintenance.
The keying control of swing type mechanism, master winch mechanism and secondary hoisting mechanism drg, at present working oil path high-voltage oil liquid direct controls that adopt more, 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 reduce the service life of system works efficient and element like this, control is complicated, increases operation fatigue.
Summary of the invention
Technical matters to be solved by this invention is the present situation at prior art, provide a kind of and have Based Intelligent Control, have open and close fast slow characteristic, hydraulic efficiency impact is little, structure is integrated, modularization, system pipeline structure hydraulic operation triple 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 is adopted: hydraulic control operation triple pump hydraulic system includes first oil pump, second oil pump, the 3rd oil pump, Hydraulic slewing system, hoisting arm expansion hydraulic efficiency pressure system, safe off-load hydraulic efficiency pressure system, the hydraulic efficiency pressure system that hoists, arm luffing hydraulic efficiency pressure system, decompression guide's oil sources valve group and control cock group; Safe off-load hydraulic efficiency pressure system includes the flow divider valve group, and flow divider valve group two ends are equipped with the 3rd oil inlet that is communicated with the outlet of first oil pump, second oil inlet that is communicated with the outlet of second oil pump respectively; Luffing hydraulic control control connection, the control of disposing flexible hydraulic control control connection, the control arm luffing hydraulic efficiency pressure system of control hoisting arm expansion hydraulic efficiency pressure system on the flow divider valve group master of hydraulic efficiency pressure system hydraulic control control connection and the pair hydraulic control control connection that hoists that hoists that hoists; Dispose first oil inlet that is communicated with the outlet of the 3rd oil pump on the decompression guide oil sources valve group, the first oil inlet exit end is connected with the check valve and first reducing valve respectively, energy storage and constant pressure oil source delivery port are disposed in the outlet of first reducing valve respectively, and first outlet of check valve 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 control cooperates mutually; The control cock group includes the 3rd drive block of the main hydraulic control control connection spool commutation that hoists of second drive block, control of first drive block, the commutation of control luffing hydraulic control control connection spool of the flexible hydraulic control control of control connection spool commutation and the 4 wheel driven motion block of the secondary hydraulic control control connection spool commutation that hoists of control, and the control port on the control cock group all is communicated with constant pressure oil source delivery port oil circuit.
The measure of taking also comprises:
Also dispose the intermediate controlled connection that control second oil inlet, the 3rd oil inlet liquid flow point close on the above-mentioned flow divider valve group, the oil circuit of the 3rd oil-feed oral-lateral all is connected with the main hydraulic control control connection that hoists, the pair hydraulic control control connection pressure port that hoists, correspondingly, the oil circuit of the second oil-feed oral-lateral all is connected with flexible hydraulic control control connection, luffing hydraulic control control connection pressure port; The outlet of first reducing valve also is connected with first safety valve.
Above-mentioned Hydraulic slewing system also includes and the 4th oil inlet bonded assembly rotary buffering valve group, is furnished with the first commutation valve rod, second electromagnetic valve and the first gyroscopic output mouth, the second gyroscopic output mouth in the rotary buffering valve group; Connecting between the first gyroscopic output mouth, the second gyroscopic output mouth and driving has rotary motor, and is fitted with trainstop on this rotary motor; Select to be formed with intermediate loop through 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 second electromagnetic valve outlet is connected with above-mentioned the 4th oil inlet through second reducing valve.
Be furnished with first electromagnetic valve, first pilot operated directional control valve, second shuttle valve, first one-way throttle valve, second delivery port and the first control shuttle valve in the above-mentioned trainstop control cock group, the drive end of first pilot operated directional control valve is connected with the first control shuttle valve intermediate ends; The control cock group also includes the 5th drive block, the 5th drive block output has the first revolution control mouthful, the second revolution control mouthful of the control first commutation valve rod commutation, and the first revolution control mouthful, the second revolution control mouth are connected with the two side ends of the first control shuttle valve respectively; The import of first electromagnetic valve and 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 second shuttle valve respectively, and the intermediate ends of this second shuttle valve is connected with above-mentioned trainstop through first one-way throttle valve, second delivery port.
Above-mentioned hoisting arm expansion hydraulic efficiency pressure system also includes first telescopic oil cylinder, second telescopic oil cylinder; Is furnished with the first flexible delivery port on the telescopic oil cylinder transfer valve group, second flexible delivery port and the flexible oil inlet, the outlet of flexible hydraulic control control connection is furnished with the first flexible access port respectively, the second flexible access port, the first flexible access port is connected with flexible oil inlet, the first flexible delivery port is connected with the rodless cavity oil inlet end of first telescopic oil cylinder through the first unidirectional balance cock, the second flexible delivery port is through the second unidirectional balance cock, the first telescopic oil cylinder middle transitional sleeve pipe is connected with the rodless cavity oil inlet end of second telescopic oil cylinder, and first telescopic oil cylinder, the rod chamber oil inlet end of second telescopic oil cylinder is connected with the second flexible access port simultaneously.
The first extension and contraction control mouth of the first above-mentioned unidirectional balance cock, the second extension and contraction control mouth of the second unidirectional balance cock all are communicated with the second flexible access port; Telescopic oil cylinder transfer valve group also is furnished with the 3rd electromagnetic valve and 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 second pilot operated directional control valve; Also be equipped with damping in the telescopic oil cylinder transfer valve group, and these 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 the secondary lifting motor; The pair hydraulic control control connection outlet that hoists is furnished with first pair access port, second pair access port that hoists that hoists respectively, and first pair access port that hoists is connected with secondary lifting motor one end through the pair balance cock group that hoists, and 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 first control end on the balance cock, the 3rd shuttle valve one side of pair all is connected with second pair access port that hoists, another side of the 3rd shuttle valve and first pair access port that hoists is connected, and the drive end of the 3rd pilot operated directional control valve in first intermediate ends of the 3rd shuttle valve and the 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 the main lifting motor; The main hydraulic control control connection outlet that hoists is furnished with the first main access port that hoists, the second main access port that hoists respectively, 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, 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 second intermediate ends of the 4th shuttle valve and the 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 arm luffing hydraulic efficiency pressure system includes amplitude oil cylinder balance cock group and amplitude oil cylinder, the outlet of luffing hydraulic control control connection is furnished with the first luffing access port, the second luffing access port respectively, the first luffing access port is connected with the 3rd control mouth of amplitude oil cylinder rod chamber, amplitude oil cylinder balance cock group, and the second luffing access port is connected with the amplitude oil cylinder rodless cavity through amplitude oil cylinder balance cock group.
On the above-mentioned flow divider valve group also configuration limit the 3rd oil inlet pressure second safety valve, limit the 3rd safety valve of the second oil inlet pressure, the first flexible access port disposes the 4th safety valve, the second flexible access port and disposes the 5th safety valve, the first luffing access port and dispose the 6th safety valve, first pair access port that hoists and dispose the 7th safety valve, 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 on the flow divider valve group.
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 second safety valve, the 3rd safety valve respectively, and control mutually; The 5th electromagnetic valve is connected with the pilot control opening of the tenth safety valve, and control mutually; 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 control mutually.
The first above-mentioned oil pump oil outlet place is fitted with first check valve, and the second oil pump oil outlet place is fitted with second check valve, and the 3rd oil pump oil outlet place is fitted with the 3rd check valve.
Compared with prior art, the present invention is equipped with the 3rd oil inlet that is communicated with the outlet of first oil pump, second oil inlet that is communicated with the outlet of second oil pump respectively at flow divider valve group two ends; Luffing hydraulic control control connection, the control of disposing flexible hydraulic control control connection, the control arm luffing hydraulic efficiency pressure system of control hoisting arm expansion hydraulic efficiency pressure system on the flow divider valve group master of hydraulic efficiency pressure system hydraulic control control connection and the pair hydraulic control control connection that hoists that hoists that hoists; Dispose first oil inlet that is communicated with the outlet of the 3rd oil pump on the decompression guide oil sources valve group, the first oil inlet exit end is connected with the check valve and first reducing valve respectively, energy storage and constant pressure oil source delivery port are disposed in the outlet of first reducing valve respectively, and first outlet of check valve 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 control cooperates mutually; The control cock group includes the 3rd drive block of the main hydraulic control control connection spool commutation that hoists of second drive block, control of first drive block, the commutation of control luffing hydraulic control control connection spool of the flexible hydraulic control control of control connection spool commutation and the 4 wheel driven motion block of the secondary hydraulic control control connection spool commutation that hoists of control, and the control port on the control cock group all is communicated with 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 the mode of pass soon, 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 and the irrelevant assignment of traffic pattern of 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; Integrated and the modularization of each element heights has reduced the Full Vehicle System pipeline in the Full Vehicle System, maintains easily; Full Vehicle System is applicable to variable pump systems and Constant Pump System simultaneously; The car load hydraulic efficiency pressure system adopts pressure-reduction module valve group, reduces by a control oil pump.
Description of drawings
Fig. 1 is the system synthesis hydraulic principle scheme drawing of the embodiment of the invention;
Fig. 2 is a Hydraulic slewing system principle schematic among Fig. 1;
Fig. 3 is a hoisting arm expansion hydraulic efficiency pressure system principle schematic among Fig. 1;
Fig. 4 is the hydraulic efficiency pressure system principle schematic that hoists among Fig. 1;
Fig. 5 is an arm luffing hydraulic efficiency pressure system principle schematic among Fig. 1;
Fig. 6 is a safe off-load hydraulic efficiency pressure system principle schematic among Fig. 1;
Fig. 7 is the hydraulic efficiency pressure system principle schematic of control cock group among Fig. 1.
The specific embodiment
Embodiment describes in further detail the present invention below in conjunction with accompanying drawing.
Extremely shown in Figure 7 as Fig. 1, figure grade is described as follows: first oil pump 11, 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, first pilot operated directional control valve 25, drive end 25a, spring cavity 25b, second shuttle valve 26, first one-way throttle valve 27, trainstop 28, the first control shuttle valves 29, hoisting arm expansion hydraulic efficiency pressure system 3, telescopic oil cylinder transfer valve group 31, first unidirectional balance cock 32, the first telescopic oil cylinders 33, transition spool piece 33a, second telescopic oil cylinder 34, second pilot operated directional control valve 35, drive end 35a, the second unidirectional balance cock 36, damping 37, flexible with check valve 38, flow divider valve group 4, flexible hydraulic control control connection 41, the 4th safety valve 41a, the 5th safety valve 41b, luffing hydraulic control control connection 42, the six safety valve 42a, the main hydraulic control control connection 43 that hoists, the tenth safety valve 43a, the 9th safety valve 43b, the pair hydraulic control control connection 44 that hoists, the 8th safety valve 44a, the 7th safety valve 44b, intermediate controlled connection 45, the three safety valves 46, second safety valve 47, the hydraulic efficiency pressure system 5 that hoists, duplex hoist brake control cock group 51, the three 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, arm luffing hydraulic efficiency pressure system 6, amplitude oil cylinder balance cock group 61, amplitude oil cylinder 62, decompression guide oil sources valve group 7, first reducing valve 71, check valve 72, energy storage 73, air-conditioning 74, first safety valve 75, safe off-load hydraulic efficiency pressure system 8, unloader valve group 81, the 4th check valve 82, control cock group 9, the first drive blocks 91, the second drive blocks 92, the 3rd drive block 93,4 wheel driven motion block 94, the five drive blocks 95, operation control valve 96, following vehicle hydraulic system 10, the first revolution control mouthful a0, the second revolution control mouthful b0, the first extension and contraction control mouth a1, the second extension and contraction control mouth b1, first luffing control mouthful a2, second luffing control mouthful b2, first pair hoists and controls a mouthful a3, second pair hoists and controls a mouthful b3, the first main control mouthful a4 that hoists, the second main control mouthful b4 that hoists, the first flexible access port A7, the second flexible access port B7, the first luffing access port A8, the second luffing access port B8, first pair access port A9 that hoists, 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, 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 control 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 first outlet Y1, the second delivery port Y2.
The embodiment of the invention, hydraulic control operation triple pump hydraulic system includes first oil pump 11, second oil pump 12, the 3rd oil pump 13, Hydraulic slewing system 2, hoisting arm expansion hydraulic efficiency pressure system 3, safe off-load hydraulic efficiency pressure system 8, the hydraulic efficiency pressure system that hoists 5, arm luffing hydraulic efficiency pressure system 6, decompression guide's oil sources valve group 7 and control cock group 9; Safe off-load hydraulic efficiency pressure system 8 includes flow divider valve group 4, and flow divider valve group 4 two ends are equipped with the 3rd oil inlet P 3 that is communicated with 11 outlets of first oil pump, second oil inlet P 2 that is communicated with 12 outlets of second oil pump respectively; Luffing hydraulic control control connection 42, the control of disposing flexible hydraulic control control connection 41, the control arm luffing hydraulic efficiency pressure system 6 of control hoisting arm expansion hydraulic efficiency pressure system 3 on the flow divider valve group 4 master of hydraulic efficiency pressure system 5 hydraulic control control connection 43 and the pair hydraulic control control connection 44 that hoists that hoists that hoists; Dispose first oil inlet P 1 that is communicated with 13 outlets of the 3rd oil pump on the decompression guide oil sources valve group 7, first oil inlet P, 1 exit end is connected with the check valve 72 and first reducing valve 71 respectively, energy storage 73 and constant pressure oil source delivery port Y are disposed in the outlet of first reducing valve 71 respectively, and the first outlet Y1 of check valve 72 is 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 control cooperates mutually; Control cock group 9 includes the 3rd drive block 93 of the main hydraulic control control connection 43 spools commutation that hoists of second drive block 92, control of first drive block 91, the commutation of control luffing hydraulic control control connection 42 spools of the flexible hydraulic control control of control connection 41 spools commutation and the 4 wheel driven motion block 94 of the secondary hydraulic control control connection 44 spools commutation that hoists of control, and the control port P on the 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 safety off-load hydraulic efficiency pressure system principle; Also dispose the intermediate controlled connection 45 that control second oil inlet P 2, the 3rd oil inlet P 3 liquid flow points close on the flow divider valve group 4, the oil circuit of the 3rd oil inlet P 3 sides all is connected with the main hydraulic control control connection 43 that hoists, pair hydraulic control control connection 44 pressure port that hoist, correspondingly, the oil circuit of second oil inlet P, 2 sides all is connected with flexible hydraulic control control connection 41, luffing hydraulic control control connection 42 pressure port; 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 second safety valve 47, the 3rd safety valve 46 respectively, and control mutually; The 5th electromagnetic valve DHF5 is connected with the pilot control opening of the tenth safety valve 43a, and control mutually; 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 control mutually; First oil pump, 11 oil outlet places are fitted with the first check valve DF1, and 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.
Also dispose second safety valve 47 that limits the 3rd oil inlet P 3 pressure on the flow divider valve group 4, limit the 3rd safety valve 46 of second oil inlet P, 2 pressure, the first flexible access port A7 disposes the 4th safety valve 41a on the flow divider valve group 4, the second flexible access port B7 disposes the 5th safety valve 41b, the first luffing access port A8 disposes the 6th safety valve 42a, first pair access port A9 that hoists disposes the 7th safety valve 44b, 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 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, and 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 47 off-loads of second safety valve, the flow divider valve group can't build-up pressure, hoisting arm expansion hydraulic efficiency pressure system 3, arm luffing 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 main hoisting mechanism can't be finished down maneuver in the hydraulic efficiency pressure system that hoists 5.
When the 6th electromagnetic valve DHF6 gets; flow divider valve group 4 actuator port VA10, VB9, VA8, VA7 can't build-up pressures; main hoisting mechanism can't finish in the action that hoists, the hydraulic efficiency pressure system that hoists 5 that auxiliary hoisting mechanism can't be finished down maneuver, arm changing-breadth system 6 can't finish width of cloth action and hoisting arm expansion hydraulic efficiency pressure system 3 can't be finished stretch, forms the protection to whole hydraulic efficiency pressure system safe action in the hydraulic efficiency pressure system that hoists 5.
As Fig. 1 and shown in Figure 7, be the hydraulic efficiency pressure system principle of control cock group, concentrating in the control cock group 9 has first drive block 91, 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 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 control connection 41 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 connection 41 two ends by the first extension and contraction control mouth a1, the second extension and contraction control mouth b1, promptly realized the operation of flexible hydraulic control control connection 41 valve rods.
Dispose two operation control valves 96 in second drive block 92, each operation control valve 96 is all exported first luffing control mouthful a2 and second luffing control mouthful b2, correspondingly, luffing hydraulic control control connection 42 is furnished with first a luffing control mouthful a2 and second a luffing control mouthful b2 being positioned on flow divider valve group 4 sides, the operation that is operation control valve 96 produces hydraulic power, input to luffing hydraulic control control connection 42 two ends by first a luffing control mouthful a2 and second a luffing control mouthful b2, promptly realized the operation of luffing hydraulic control control connection 42 valve rods.
Dispose two operation control valves 96 in the 4 wheel driven motion block 94, each operation control valve 96 is all exported first pair control mouthful a3 and the second pair control mouthful b3 that hoists that hoists, correspondingly, the pair hydraulic control control connection 44 that hoists is furnished with first pair control mouthful a3 and the second pair control mouthful b3 that hoists that hoists being positioned on flow divider valve group 4 sides, the operation that is operation control valve 96 produces hydraulic power, input to pair hydraulic control control connection 44 two ends that hoist by first pair control mouthful a3 and the second pair control mouthful b3 that hoists that hoists, promptly realized the operation of secondary hydraulic control control connection 44 valve rods that hoist.
Dispose two operation control valves 96 in the 3rd drive block 93, each operation control valve 96 is all exported the first main control mouthful a4 and the second main control mouthful b4 that hoists of hoisting, correspondingly, the main hydraulic control control connection 43 that hoists is furnished with first a main control mouthful a4 and the second main control mouthful b4 that hoists of hoisting being positioned on flow divider valve group 4 sides, the operation that is operation control valve 96 produces hydraulic power, input to main hydraulic control control connection 43 two ends that hoist by first main control mouthful a4 and the second main control mouthful b4 that hoists of hoisting, promptly 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 the first revolution control mouthful a0 and the second revolution control mouthful b0, correspondingly, the first commutation valve rod, 23 two ends are furnished with the first revolution control mouthful a0 and the second revolution control mouthful b0, the operation that is operation control valve 96 produces hydraulic power, input to the first commutation valve rod, 23 two ends by the first revolution control mouthful a0 and second a revolution control mouthful b0, promptly 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 and the 4th oil inlet P 4 bonded assembly rotary buffering valve groups 22, is furnished with first commutation valve rod 23, the second electromagnetic valve DHF2 and the first gyroscopic output mouth A11, the second gyroscopic output mouth B11 in the rotary buffering valve group 22; Connecting between the first gyroscopic output mouth A11, the second gyroscopic output mouth B11 and driving has 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 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 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 that is furnished with the first electromagnetic valve DHF1, first pilot operated directional control valve 25, second shuttle valve 26, first one-way throttle valve 27, the second delivery port Y2 and the first control shuttle valve, 29, the first pilot operated directional control valves 25 in the trainstop control cock group 21 is connected with the first control shuttle valve, 29 intermediate ends; Control cock group 9 also includes the 5th drive block 95,95 outputs of the 5th drive block have the first revolution control mouthful a0, the second revolution control mouthful b0 of the control first commutation valve rod 23 commutations, and the described first revolution control mouthful a0, the second revolution control mouthful b0 are connected with the two side ends of the first control shuttle valve 29 respectively; The import of the first electromagnetic valve DHF1 and 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 second shuttle valve 26 respectively, and the intermediate ends of this second shuttle valve 2 is connected with trainstop 28 through first one-way throttle valve 27, the second delivery port Y2.71 outlets of first reducing valve also are connected with first safety valve 75.
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 3rd oil pump 3 by the 3rd check valve DF3, down vehicle hydraulic system 10, in return, pressure-reduction module valve group 7 and air-conditioning 74, enter rotary buffering valve group 22 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, promptly control the first revolution control mouthful a0 end build-up pressure, work fluid is by the first commutation valve rod 23, first gyroscopic output mouth A11 output, enter rotary motor 24 by actuator port A24, and build-up pressure driving rotational motor 24, the transmission of pressure of the first revolution control mouthful a0 end is to trainstop control cock group 21 simultaneously, select to open first pilot operated directional control valve 25 of sealing constant voltage fluid through the first control shuttle valve 29, constant voltage fluid select through second shuttle valve 26 and first one-way throttle valve 27 by the first delivery port Y1 to trainstop 28, open trainstop 28 fast, swing type mechanism steadily enters right-hand rotation work operating mode;
2, the left side of Hydraulic slewing system revolution operation:
The valve rod that the first commutation valve rod 23 is handled in hydraulic control commutates left, the i.e. second revolution control mouthful b0 end build-up pressure, work fluid is by the first commutation valve rod 23, second gyroscopic output mouth B11 output, enter rotary motor 24 by actuator port B24, and build-up pressure driving rotational motor 24, the transmission of pressure of the second revolution control mouthful b0 is to trainstop control cock group 21 simultaneously, select to open first pilot operated directional control valve 25 of sealing constant voltage fluid through the first control shuttle valve 29, constant voltage fluid select through second shuttle valve 26 and first one-way throttle valve 27 by the first delivery port Y1 to trainstop 28, open trainstop 28 fast, swing type mechanism steadily enters left revolution work operating mode;
3, the free centering operation of Hydraulic slewing system:
When swing type mechanism quits work, the first commutation valve rod 23 is replied meta under the spring force effect, work fluid returns system's fuel tank through first commutation valve rod 23 valve rods and check valve group, rotary buffering valve group 22 control end cap pressure disappear, first pilot operated directional control valve 25 resets under the spring force effect in the trainstop control cock group 21, cut off constant voltage fluid, the remaining fluid of trainstop 28 is through the first delivery port Y1, first one-way throttle valve 27, second shuttle valve 26, first pilot operated directional control valve 25 and oil return inlet T 6 slow off-load to systems do not have back pressure runner oil sump tank, trainstop 28 is slowly closed, and swing type mechanism quits work.
When swing type mechanism need carry out free centering operating mode, the first electromagnetic valve DHF1 is simultaneously in the second electromagnetic valve DHF2 and the trainstop control cock group 21 in the 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 the rotary buffering valve group 22, the first electromagnetic valve DHF1 gets in the trainstop control cock group 21, open the electromagnetic valve core of sealing constant pressure oil source, constant pressure oil source enters trainstop 28 through second shuttle valve 26 and first one-way throttle valve 27 by the first delivery port Y1, open trainstop 28 rapidly, realize that swing type mechanism freely turns round operation.
When swing type mechanism need finish free centering operating mode, cut off in the rotary buffering valve group 22 electric signal of the first electromagnetic valve DHF1 among the second electromagnetic valve DHF2 and trainstop control cock group 21 simultaneously, second electromagnetic valve DHF2 outage cut off low is linked up the hydraulic circuit of two actuator ports formation of rotary motor 24 in the rotary buffering valve group 22, constant pressure oil source is cut off in first electromagnetic valve DHF1 outage in the trainstop 28 control cock groups, the remaining fluid of trainstop 28 is through the first delivery port Y1, first one-way throttle valve 27, second shuttle valve 26, electromagnetic valve core and oil return inlet T 6 slow off-load to systems do not have back pressure runner oil sump tank, trainstop 28 is slowly closed, and swing type mechanism stops free centering operation.
As shown in figures 1 and 3, be hoisting arm expansion hydraulic efficiency pressure system principle; Hoisting arm expansion hydraulic efficiency pressure system 3 also includes first telescopic oil cylinder 33, second telescopic oil cylinder 34; Is furnished with the first flexible delivery port A12 on the telescopic oil cylinder transfer valve group 31, second flexible delivery port B12 and the flexible oil inlet P 6,41 outlets of flexible hydraulic control control connection are furnished with the first flexible access port A7 respectively, the second flexible access port B7, the first flexible access port A7 is connected with flexible oil inlet P 6, the first flexible delivery port A12 is connected with the rodless cavity oil inlet end of first telescopic oil cylinder 33 through the first unidirectional balance cock 32, the second flexible delivery port B12 is through the second unidirectional balance cock 36, first telescopic oil cylinder, 33 middle transitional sleeve pipe 33a are connected with the rodless cavity oil inlet end of second telescopic oil cylinder 34, and first telescopic oil cylinder 33, the rod chamber oil inlet end of second telescopic oil cylinder 34 is connected with the second flexible access port B7 simultaneously.
The first extension and contraction control mouth P7 of the first unidirectional balance cock 32, the second extension and contraction control mouth P8 of the second unidirectional balance cock 36 all are communicated with the second flexible access port B7; Telescopic oil cylinder transfer valve group 31 also is furnished with the 3rd electromagnetic valve DHF3 and 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 second pilot operated directional control valve 35; Also be equipped with damping 38 in the telescopic oil cylinder transfer valve group 31, and these damping 38 two ends are communicated with 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 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 first oil inlet P 2.
1, the arm operation of contracting of this hoisting arm expansion hydraulic efficiency pressure system:
The flexible hydraulic control control of hydraulic operation connection 41 valve rods commutate to the right, the work fluid interflow of first oil pump 11 and second oil pump 12 enters the rod chamber of first telescopic oil cylinder 33 and second telescopic oil cylinder 34 respectively by flexible hydraulic control control the connection 41 and second flexible access port B7 output, build-up pressure promotes two telescopic oil cylinders, pressure signal is delivered to two telescopic oil cylinders, the first unidirectional balance cock 32 respectively simultaneously, the first extension and contraction control mouth P7 of the second unidirectional balance cock 36, the second extension and contraction control mouth P8, and steadily open two telescopic oil cylinders, the first unidirectional balance cock 32, the second unidirectional balance cock 36, two telescopic oil cylinders 33, the fluid of 34 rodless cavities is under the effect of rod chamber pressure, the work fluid of first telescopic oil cylinder, 33 rodless cavities is by actuator port B13, balance valve core, actuator port A13 and actuator port A12 enter the work fluid of flexible transfer valve group 31, the second telescopic oil cylinders 34 rodless cavities by actuator port B14, balance valve core, actuator port A14 and actuator port B12 enter flexible transfer valve group 31.Under the 3rd electromagnetic valve DHF3 in the flexible transfer valve group 31 must not electric situation, the work fluid that enters flexible transfer valve group 31 actuator port A12 joins the 41 oil return runners that arrive flow divider valve group 4 to fuel tank through the switching spool that stretches, flexible oil inlet P 6, the first flexible access port A7 and flexible hydraulic control control, finishes the arm action of contracting of first telescopic oil cylinder 33.
When flexible transfer valve group 31 the 3rd electromagnetic valve DHF3 gets under the electric situation, open second pilot operated directional control valve, 35 spools of sealing constant pressure oil source, constant voltage fluid promotes the flexible spool that switches and commutates, the work fluid that enters actuator port B12 through the flexible switching spool of commutation, flexible oil inlet P 6, the first flexible access port A7 and flexible hydraulic control control connection 41 to the oil return runners of flow divider valve group 4 to fuel tank, the arm that contracts of finishing 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 remaining fluid of second pilot operated directional control valve, 35 spool control ends by off-load mouth L2 to no back pressure off-load runner to fuel tank, the switching spool resets under the spring force effect.Simultaneously at first telescopic oil cylinder 33 and second telescopic oil cylinder 34 under full semi-girder state, operate first telescopic oil cylinder 33 separately, because transition spool piece 33a volume diminishes, cause voltage rise height in the transition spool piece 33a, transition spool piece 33a pressure oil liquid effectively discharges by the damping 37 in the flexible transfer valve group 31 at this moment; Also can prevent simultaneously interlock, promptly second telescopic oil cylinder 34, first telescopic oil cylinder 33 that contracts when not stretching out state entirely causes second telescopic oil cylinder, 34 overhanging phenomenons; At first telescopic oil cylinder 33 and second telescopic oil cylinder 34 under full reduced arm state, operate first telescopic oil cylinder 33 separately, because it is big that transition spool piece 33a volume becomes, cause forming in the transition spool piece 33a vacuum, transition spool piece 33a does not have back pressure off-load runner oil suction with check valve 38 from system through flexible.Also can prevent simultaneously interlock, i.e. second telescopic oil cylinder 34, first telescopic oil cylinder 33 that when not full reduced time state, contracts, cause second telescopic oil cylinder, 34 rebound phenomenons, the fluid that flexible transfer valve group 31 is switched core retracing spring chambeies by return opening L1 to no 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 control of hydraulic operation connection 41 valve rods commutate left, and the work fluid interflow of first oil pump 11 and second oil pump 12 enters flexible transfer valve group 31 by flexible hydraulic control control the connection 41 and first flexible access port A7 output by flexible oil inlet P 6.Flexible transfer valve group 31 the 3rd electromagnetic valve DHF3 is under must not electric situation, the work fluid that is entered by flexible oil inlet P 6 is through switching the rodless cavity that spool, actuator port A12, actuator port A13, the first unidirectional balance cock 32 and actuator port B13 enter first telescopic oil cylinder 33, build-up pressure promotes first telescopic oil cylinder 33, the work fluid of first telescopic oil cylinder, 33 rod chambers under pressure promotes by the second flexible access port B7, flexible hydraulic control control connection 41 to flow divider valve group 4 oil return runners to fuel tank, finish the semi-girder operation of first telescopic oil cylinder 33.
Flexible transfer valve group 31 the 3rd electromagnetic valve DHF3 is getting under the electric situation, open the 3rd electromagnetic valve DHF3 of sealing constant pressure oil source, constant voltage fluid promotes 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 unidirectional balance cock 36 and actuator port B14 enter the rodless cavity of second telescopic oil cylinder 34, build-up pressure promotes second telescopic oil cylinder 34, the work fluid of second telescopic oil cylinder, 34 rod chambers under pressure promotes by the second flexible access port B7, flexible hydraulic control control connection 41 to fuel tank, is finished the semi-girder operation of second telescopic oil cylinder 34 to flow divider valve group 4 oil return runners.
As shown in Figure 1 and Figure 4, be the hydraulic efficiency pressure 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 the secondary lifting motor 52; Pair hydraulic control control connection 44 outlets that hoist are furnished with first pair access port A9, second pair access port B9 that hoists that hoists respectively, 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 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 the balance cock 55a, the 3rd shuttle valve 55b one side of pair all is connected with second pair access port B9 that hoists, another side of the 3rd shuttle valve 55b and 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 the 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 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 second oil pump 12, the second check valve DF2 and in return and enter flow divider valve group 4 for 2 mouthfuls by second oil inlet P.
1, auxiliary hoisting mechanism step-down operation:
Hydraulic control control connection 44 commutation to the right that hoists of fluid control pair, the work fluid of first oil pump 11 and second oil pump 12 interflow is by the access port B9 output that hoists of second pair, enter secondary lifting motor 52 by actuator port B17, build-up pressure also drives secondary lifting motor 52, the pressure signal transmission pair 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, export by the first intermediate ends C1, 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 secondary lifting motor 52 postrotational work fluid by actuator port A17, actuator port B16, balance valve core, actuator port A16, first pair hoist the secondary hydraulic control control connection 44 that hoists of access port A9 and control to the oil return runners of flow divider valve group 4 to fuel tank, finish the auxiliary hoisting mechanism down maneuver.
2, auxiliary hoisting mechanism plays lift operations:
Hydraulic control control connection 44 commutation left that hoists of hydraulic operation pair, the work fluid of first oil pump 11 and second oil pump 12 interflow is by the access port A9 output that hoists of 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 the balance cock group 55, by hoist balance cock group 55 first intermediate ends C1 output of pair, 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 secondary lifting motor 52 postrotational work fluid by actuator port B17, second pair hoist the secondary hydraulic control control connection 44 that hoists of access port B9 and control to the oil return runners of flow divider valve group 4 to fuel tank, finish 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 control connection 44 that hoists is replied meta under the spring force effect, 52 liang of actuator port A17 of secondary lifting motor, B17 pressure disappear, the 3rd pilot operated directional control valve 51a in the duplex hoist brake control cock group 51 resets under the spring force effect, cut off constant voltage fluid, the remaining fluid of secondary lifting motor drg 58 does not have back pressure runner oil sump tank through output oil port b5 and the steady off-load of damping through oil return inlet T 8 to system, 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 the main lifting motor 53; Main hydraulic control control connection 43 outlets that hoist are furnished with the first main access port A10 that hoists, the second main access port B10 that hoists respectively, 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 the 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:
Main hydraulic control control connection 43 commutations to the right that hoist of hydraulic operation, the work fluid interflow of first oil pump 11 and second oil pump 12 is by main hydraulic control control the connection 43 and second main access port B10 output that hoists that hoists, enter main lifting motor 53 by actuator port B19 again, build-up pressure also drives main lifting motor 53, the pressure signal transmission master 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, export by the second intermediate ends C2, 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 main lifting motor 53 postrotational work fluid by actuator port A19, actuator port B18, balance valve core, the main balance cock group actuator port A18 that hoists, first main hoist access port A10 and the main hydraulic control control connection 43 that hoists to fuel tank, finished the main hoisting mechanism down maneuver to the oil return runners of flow divider valve group 4.
2, a lift operations of main hoisting mechanism:
Main hydraulic control control connection 43 commutations left that hoist of hydraulic operation, the work fluid interflow of first oil pump 11 and second oil pump 12 is by main hydraulic control control the connection 43 and first main access port A10 output that hoists 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, export by the second intermediate ends C2, 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 main lifting motor 53 postrotational work fluid by actuator port B19, second main hoist access port B10 and the main hydraulic control control connection 43 that hoists to fuel tank, finished the main hoisting mechanism action that hoists to the oil return runners of flow divider valve group 4.
3, the shut-down operation of main hoisting mechanism:
When main hoisting mechanism quits work, the main hydraulic control control connection 43 that hoists is replied meta under the spring force effect, 53 liang of actuator port A19 of main lifting motor, B19 pressure disappear, pilot operated directional control valve in the duplex hoist brake control cock group 51 resets under the spring force effect, cut off constant voltage fluid, the remaining fluid of main lifting motor drg 59 does not have back pressure runner oil sump tank through output oil port b6 and the steady off-load of damping through oil return inlet T 8 to system, main lifting motor drg 59 is steadily closed, and main hoisting mechanism quits work.
As Fig. 1 and shown in Figure 5, be arm luffing hydraulic efficiency pressure system principle; Arm luffing hydraulic efficiency pressure system 6 includes amplitude oil cylinder balance cock group 61 and amplitude oil cylinder 62,42 outlets of luffing hydraulic control control connection are furnished with the first luffing access port A8, the second luffing access port B8 respectively, the first luffing access port A8 is connected with the 3rd a control mouthful P9 of amplitude oil cylinder 62 rod chambers, amplitude oil cylinder balance cock group 61, 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 arm luffing hydraulic efficiency pressure system is as described below:
The work fluid of 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 for 2 mouthfuls by second oil inlet P.
1, the width of cloth operation that falls of amplitude oil cylinder: hydraulic operation flow divider valve group 4 luffing hydraulic controls control connection 42 commutations to the right, the work fluid interflow of first oil pump 11 and second oil pump 12 enters the rod chamber of amplitude oil cylinder 62 by 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 effect of rod chamber pressure, 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 control connection 42 to fuel tank, is finished amplitude oil cylinder 62 width of cloth action that falls to the oil return runners of flow divider valve group 4.
2, the width of cloth that rises of amplitude oil cylinder is operated: hydraulic operation luffing hydraulic control control connection 42 valve rods commutate left, the work fluid interflow of first oil pump 1 and second oil pump 2 is by 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, luffing hydraulic control control connection 42 to fuel tank, is finished a width of cloth operation of amplitude oil cylinder 62 to flow divider valve group 4 oil return runners.
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 the mode of pass soon, 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 and the irrelevant assignment of traffic pattern of 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; Integrated and the modularization of each element heights has reduced the Full Vehicle System pipeline in the Full Vehicle System, maintains easily; Full Vehicle System is applicable to variable pump systems and Constant Pump System simultaneously; The car load hydraulic efficiency pressure system adopts pressure-reduction module valve group, reduces by a control oil pump.
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 control operation triple pump hydraulic system includes first oil pump (11), second oil pump (12), the 3rd oil pump (13), Hydraulic slewing system (2), hoisting arm expansion hydraulic efficiency pressure system (3), safe off-load hydraulic efficiency pressure system (8), the hydraulic efficiency pressure system that hoists (5), arm luffing hydraulic efficiency pressure system (6), decompression guide's oil sources valve group (7) and control cock group (9); It is characterized in that: described safe off-load hydraulic efficiency pressure system (8) includes flow divider valve group (4), and described flow divider valve group (4) two ends are equipped with the 3rd oil inlet (P3) that is communicated with first oil pump (11) outlet, second oil inlet (P2) that is communicated with second oil pump (12) outlet respectively; Flexible hydraulic control control connection (41), the luffing hydraulic control control connection (42) of control arm luffing hydraulic efficiency pressure system (6), the control of disposing control hoisting arm expansion hydraulic efficiency pressure system (3) on the described flow divider valve group (4) master of hydraulic efficiency pressure system (5) hydraulic control control connection (43) and the pair hydraulic control control that hoists that hoists that hoists joins (44);
Dispose first oil inlet (P1) that is communicated with the 3rd oil pump (13) outlet on described decompression guide's oil sources valve group (7), described first oil inlet (P1) exit end is connected with check valve (72) and first reducing valve (71) respectively, energy storage (73) and constant pressure oil source delivery port (Y) are disposed in the outlet of first reducing valve (71) respectively, and first outlet (Y1) of described check valve (72) 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 control cooperates mutually;
Described control cock group (9) includes the 3rd drive block (93) of main hydraulic control control connection (43) spool commutation that hoists of second drive block (92), control of first drive block (91), the commutation of control luffing hydraulic control control connection (42) spool of the flexible hydraulic control control of control connection (41) spool commutation and the control pair 4 wheel driven motion block (94) that hydraulic control control connection (44) spool commutates that hoists, and the control port (P) on the control cock group (9) all is communicated with described constant pressure oil source delivery port (Y) oil circuit.
2. hydraulic control operation triple pump hydraulic system according to claim 1, it is characterized in that: also dispose the intermediate controlled connection (45) that control second oil inlet (P2), the 3rd oil inlet (P3) liquid flow point close on the described flow divider valve group (4), the oil circuit of the 3rd oil inlet (P3) side all is connected with the main hydraulic control control connection (43) that hoists, pair hydraulic control control connection (44) pressure port that hoists, correspondingly, the oil circuit of second oil inlet (P2) side all is connected with flexible hydraulic control control connection (41), luffing hydraulic control control connection (42) pressure port; The outlet of described first reducing valve (71) also is connected with first safety valve (75).
3. hydraulic control operation triple pump hydraulic system according to claim 2, it is characterized in that: described Hydraulic slewing system (2) also includes and the 4th oil inlet (P4) bonded assembly rotary buffering valve group (22), is furnished with the first commutation valve rod (23), second electromagnetic valve (DHF2) and the first gyroscopic output mouth (A11), the second gyroscopic output mouth (B11) in the described rotary buffering valve group (22); Connecting between the described first gyroscopic output mouth (A11), the second gyroscopic output mouth (B11) and driving has rotary motor (24), and is fitted with trainstop (28) on this rotary motor (24); Select to be formed with intermediate loop (22b) through first shuttle valve (22a) between the described first gyroscopic output mouth (A11), the second gyroscopic output mouth (B11), this intermediate loop (22b) is connected with second electromagnetic valve (DHF2) import, and second electromagnetic valve (DHF2) outlet is connected with described the 4th oil inlet (P4) through second reducing valve (22c).
4. hydraulic control operation triple pump hydraulic system according to claim 3, it is characterized in that: be furnished with first electromagnetic valve (DHF1), first pilot operated directional control valve (25), second shuttle valve (26), first one-way throttle valve (27), second delivery port (Y2) and the first control shuttle valve (29) in the described trainstop control cock group (21), the drive end (25a) of first pilot operated directional control valve (25) is connected with described first control shuttle valve (29) intermediate ends; Described control cock group (9) also includes the 5th drive block (95), the 5th drive block (95) output has the first revolution control mouth (a0), the second revolution control mouthful (b0) of controlling first commutation valve rod (23) commutation, and mouthful (a0) controlled in described first revolution, the second revolution control mouthful (b0) is connected with first two side ends of controlling shuttle valve (29) respectively; The import of first electromagnetic valve (DHF1) and 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 second shuttle valve (26) respectively, and the intermediate ends of this second shuttle valve (2) is connected with described trainstop (28) through first one-way throttle valve (27), second delivery port (Y2).
5. hydraulic control operation triple pump hydraulic system according to claim 2, it is characterized in that: described hoisting arm expansion hydraulic efficiency pressure system (3) also includes first telescopic oil cylinder (33), second telescopic oil cylinder (34); Is furnished with the first flexible delivery port (A12) on the described telescopic oil cylinder transfer valve group (31), second flexible delivery port (B12) and the flexible oil inlet (P6), described flexible hydraulic control control connection (41) outlet is furnished with the first flexible access port (A7) respectively, the second flexible access port (B7), the first flexible access port (A7) is connected with flexible oil inlet (P6), the first flexible delivery port (A12) is connected with the rodless cavity oil inlet end of first telescopic oil cylinder (33) through the first unidirectional balance cock (32), the second flexible delivery port (B12) is through the second unidirectional balance cock (36), first telescopic oil cylinder (33) middle transitional sleeve pipe (33a) is connected with the rodless cavity oil inlet end of second telescopic oil cylinder (34), and first telescopic oil cylinder (33), the rod chamber oil inlet end of second telescopic oil cylinder (34) is connected with the second flexible access port (B7) simultaneously.
6. hydraulic control operation triple pump hydraulic system according to claim 5 is characterized in that: the first extension and contraction control mouth (P7) of the described first unidirectional balance cock (32), the second extension and contraction control mouth (P8) of the second unidirectional balance cock (36) all are communicated with the described second flexible access port (B7); Described telescopic oil cylinder transfer valve group (31) also is furnished with the 3rd electromagnetic valve (DHF3) and 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 second pilot operated directional control valve (35); Also be equipped with damping (38) in the described telescopic oil cylinder transfer valve group (31), and this damping (38) two ends are communicated with second pilot operated directional control valve (35) return opening, outside return opening (T7) respectively.
7. hydraulic control operation triple 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 the described secondary lifting motor (52); Hydraulic control control connection (44) outlet that hoists of described pair is furnished with first pair access port (A9), second pair access port (B9) that hoists that hoists respectively, 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 (B9) is connected with secondary lifting motor (52) other end and 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), hoist first control end (X1) on the balance cock (55a), the 3rd shuttle valve (55b) side of pair all is connected with second pair access port (B9) that hoists, another side of the 3rd shuttle valve (55b) and first pair access port (A9) that hoists is connected, and the drive end of the 3rd pilot operated directional control valve (51a) in first intermediate ends (C1) of the 3rd shuttle valve (55b) and the 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 control operation triple 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 the described main lifting motor (53); Described master hydraulic control control connection (43) outlet that hoists is furnished with the first main access port (A10) that hoists, the second main access port (B10) that hoists respectively, 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, second control end (X2) on the main balance cock (54a) that hoists, the 4th shuttle valve (54b) 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 second intermediate ends (C2) of the 4th shuttle valve (54b) and the 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 control operation triple pump hydraulic system according to claim 2, it is characterized in that: described arm luffing hydraulic efficiency pressure system (6) includes amplitude oil cylinder balance cock group (61) and amplitude oil cylinder (62), described luffing hydraulic control control connection (42) outlet is furnished with the first luffing access port (A8) respectively, the second luffing access port (B8), described first luffing access port (A8) and amplitude oil cylinder (62) rod chamber, the 3rd control mouthful (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 control operation triple pump hydraulic system according to claim 2, it is characterized in that: also dispose second safety valve (47) that limits the 3rd oil inlet (P3) pressure on the described flow divider valve group (4), limit the 3rd safety valve (46) of second oil inlet (P2) pressure, described flow divider valve group (4) the last first flexible access port (A7) disposes the 4th safety valve (41a), the second flexible access port (B7) disposes the 5th safety valve (41b), the first luffing access port (A8) disposes the 6th safety valve (42a), first pair access port (A9) that hoists disposes the 7th safety valve (44b), 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);
Described 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); Described the 4th electromagnetic valve (DHF4) is connected with the pilot control opening of second safety valve (47), the 3rd safety valve (46) respectively, and control mutually; Described the 5th electromagnetic valve (DHF5) is connected with the pilot control opening of the tenth safety valve (43a), and control mutually; 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 (82), and control mutually;
Described first oil pump (11) oil outlet place is fitted with first check valve (DF1), and described second oil pump (12) oil outlet place is fitted with second check valve (DF2), and described the 3rd oil pump (13) oil outlet place is fitted with the 3rd check valve (DF3).
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CN102425579A (en) * 2011-10-28 2012-04-25 中联重科股份有限公司 Hydraulic rotary system, hydraulic air-conditioning system arrangement structure and engineering mechanical equipment thereof
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CN106744329B (en) * 2016-12-22 2018-08-07 北汽福田汽车股份有限公司 A kind of crane and its telescoping mechanism and secondary hoisting mechanism coordinated control system

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