CN201686408U - Mechanically operated three-pump hydraulic system - Google Patents
Mechanically operated three-pump hydraulic system Download PDFInfo
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- CN201686408U CN201686408U CN2010201916205U CN201020191620U CN201686408U CN 201686408 U CN201686408 U CN 201686408U CN 2010201916205 U CN2010201916205 U CN 2010201916205U CN 201020191620 U CN201020191620 U CN 201020191620U CN 201686408 U CN201686408 U CN 201686408U
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Abstract
The utility model relates to a mechanically operated three-pump hydraulic system, which comprises a first oil pump, a second oil pump, a third oil pump, a rotary hydraulic system, a hoisting arm telescopic hydraulic system, a safe load hydraulic system, a lifting hydraulic system, a hoisting arm variable amplitude hydraulic system and a reduced pressure pilot oil source valve group. The opening and closing properties of a rotary brake and main and secondary hoisting brakes adopt constant pressure oil source control modes, and the control of the brakes is intelligently and automatically realized according to the operation of each action without additional external force operation; according to different opening and closing properties of the mechanisms, a quick-opening slow-closing control mode for the rotary mechanism and a slow-opening quick-closing control mode for the main and secondary hoisting mechanisms, the pressure impact of the system is effectively eliminated; an overflow valve at each working oil port of a flow distribution valve and overflow valves at two oil inlet working oil ports are provided with remote control oil ports which are connected with an loading valve group of the system so as to directly solve the safe control problem on a main valve; and elements in the whole vehicle system are high integrated and modularized, pipelines of the whole vehicle system are reduced, and the whole vehicle system is convenient for maintenance.
Description
Technical field
The utility model relates to the technical field of hydraulic efficiency pressure system, and particularly a kind of hydraulic system of mechanically operated triple pump 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 of hoisting crane 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 problem to be solved in the utility model 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 system of mechanically operated triple pump little, applied widely and easy to maintenance.
The utility model solves the problems of the technologies described above the technical scheme that is adopted: hydraulic system of mechanically operated triple pump 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 and decompression guide oil sources valve 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 mechanical control connection, the control of disposing flexible mechanical 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 mechanical control connection and the pair mechanical 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 measure of taking also comprises:
Also dispose the intermediate mechanical control 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 mechanical control connection that hoists, the pair mechanical control connection pressure port that hoists, correspondingly, the oil circuit of the second oil-feed oral-lateral all is connected with flexible mechanical control connection, luffing mechanical 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, be furnished with the first commutation valve rod, second electromagnetic valve, control pressure tap and the first gyroscopic output mouth, the second gyroscopic output mouth in the rotary buffering valve group, the control pressure tap is connected with the 4th oil inlet; Be connected with rotary motor between the first gyroscopic output mouth, the second gyroscopic output mouth, and also be 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 the control pressure tap through second reducing valve.
Be furnished with first electromagnetic valve, first pilot operated directional control valve, second shuttle valve, first one-way throttle valve and second delivery port in the above-mentioned trainstop control cock group, the drive end of first pilot operated directional control valve is connected with the control pressure tap; 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 communicated with second delivery port through first one-way throttle valve, and this second delivery port is connected with trainstop; Also be shaped on the oil return pressure tap on the rotary buffering valve group, and this oil return pressure tap is communicated with the first pilot operated directional control valve spring cavity.
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 mechanical control connection is furnished with the first flexible access port and the second flexible access port respectively, 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 mechanical control connection outlet that hoists is furnished with first pair access port and 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 mechanical control connection outlet that hoists is furnished with the first main access port and the second main access port that hoists of hoisting 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 mechanical control connection is furnished with the first luffing access port and 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 above-mentioned oil pump oil outlet place is fitted with second check valve, and the 3rd above-mentioned oil pump oil outlet place is fitted with the 3rd check valve.
Compared with prior art, the utility model 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 mechanical control connection, the control of disposing flexible mechanical 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 mechanical control connection and the pair mechanical 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.Advantage of the present utility model is: 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 system's hydraulic pressure assembly principle schematic of the utility model embodiment;
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.
The specific embodiment
Embodiment describes in further detail the utility model below in conjunction with accompanying drawing.
To shown in Figure 6, figure grade is described as follows: first oil pump, 11, the second oil pumps 12 as Fig. 1, 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, the first one-way throttle valves 27, trainstop 28, hoisting arm expansion hydraulic efficiency pressure system 3, telescopic oil cylinder transfer valve group 31, the first unidirectional balance cocks 32, first telescopic oil cylinder 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 mechanical control connection 41, the four safety valve 41a, the 5th safety valve 41b, luffing mechanical control connection 42, the six safety valve 42a, the main mechanical control connection 43 that hoists, the tenth safety valve 43a, the 9th safety valve 43b, pair mechanical control connection 44, the eight safety valve 44a that hoist, the 7th safety valve 44b, intermediate mechanical control connection 45, the three safety valves 46, the second safety valves 47, hydraulic efficiency pressure system 5 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 9, the four check valves 91, following vehicle hydraulic system 10, 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, control pressure tap K, oil return pressure tap Pt, 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 utility model embodiment, hydraulic system of mechanically operated triple pump 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 and decompression guide oil sources valve group 7; 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 mechanical control connection 42, the control of disposing flexible mechanical 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 mechanical control connection 43 and the pair mechanical 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.
Fig. 1 and shown in Figure 6 is safety off-load hydraulic efficiency pressure system principle; Also dispose the intermediate mechanical control 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 joins 44 pressure port and is connected with the main mechanical control connection 43 that hoists, the pair mechanical control that hoists, correspondingly, the oil circuit of second oil inlet P, 2 sides all joins 42 pressure port and is connected with flexible mechanical control connection 41, luffing mechanical control; Safe off-load hydraulic efficiency pressure system 8 also includes unloader valve group 9, and this unloader valve group 9 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 91, 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 9 with flow divider valve group 4, unloader valve group 9 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 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, be furnished with the first commutation valve rod 23, the second electromagnetic valve DHF2, control pressure tap K and the first gyroscopic output mouth A11, the second gyroscopic output mouth B11 in the rotary buffering valve group 22, control pressure tap K is connected with the 4th oil inlet P 4; Be connected with rotary motor 24 between the first gyroscopic output mouth A11, the second gyroscopic output mouth B11, and also be 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 control pressure tap K through the second reducing valve 22c.
Be furnished with the first electromagnetic valve DHF1, first pilot operated directional control valve 25, second shuttle valve 26, first one-way throttle valve 27 and the second delivery port Y2 in the trainstop control cock group 21, the drive end 25a of first pilot operated directional control valve 25 is connected with control pressure tap K; The import of the first electromagnetic valve DHF1 and first pilot operated directional control valve 25 all is communicated with 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 communicated with the second delivery port Y2 through first one-way throttle valve 27, and this second delivery port Y2 is connected with trainstop 28; Also be shaped on oil return pressure tap Pt on the rotary buffering valve group 22, and this oil return pressure tap Pt is communicated with first pilot operated directional control valve, 25 spring cavity 25b; The outlet of first reducing valve 71 also is 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 mechanical control first commutation valve rod 23 commutates to the right, work fluid is by the first commutation valve rod 23 and actuator port A11 output, enter rotary motor 24, and build-up pressure driving rotational motor 24, pressure signal is delivered to trainstop control cock group 21 by control pressure tap K simultaneously, open first pilot operated directional control valve 25 of sealing constant voltage fluid, constant voltage fluid select through second shuttle valve 26 and first one-way throttle valve 27 by the second delivery port Y2 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 mechanical control first commutation valve rod 23 commutates left, work fluid is by the first commutation valve rod 23 and actuator port B11 output, enter rotary motor 24, and build-up pressure driving rotational motor 24, pressure signal is delivered to trainstop control cock group 21 by control pressure tap K simultaneously, open first pilot operated directional control valve 25 of sealing constant voltage fluid, constant voltage fluid select through second shuttle valve 26 and first one-way throttle valve 27 by the second delivery port Y2 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 the first commutation valve rod 23 and check valve group, rotary buffering valve group 22 operation pressures 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 second delivery port Y2, 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.Back pressure for anti-rotation stopping mechanism hydraulic circuit generation, the oil return pressure tap Pt mouth of the oil return of the spring cavity of first pilot operated directional control valve 25 and rotary buffering valve group 22 in trainstop control cock group 21 is eliminated swing type mechanism and is caused that by pressure trainstop 28 opens.
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 two actuator ports formation hydraulic circuits that electric low pressure is linked up rotary motor 24 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 second delivery port Y2, 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 control cock group 21, the remaining fluid of trainstop 28 is through the second delivery port Y2, first one-way throttle valve 27, second shuttle valve 26, the first electromagnetic valve DHF1 spool 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, flexible mechanical control connection 41 outlets are furnished with the first flexible access port A7 and the second flexible access port B7 respectively, 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 37 in the telescopic oil cylinder transfer valve group 31, and these damping 37 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 mechanical control of power operation joins 41 valve rods and commutates 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 mechanical 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 through flexible switch spool, flexible oil inlet P 6, the first flexible access port A7 and flexible mechanical control connection 41 to the oil return runners of flow divider valve group 4 to fuel tank, finish 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 flexible switching spool, flexible oil inlet P 6, the first flexible access port A7 and the flexible mechanical 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 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 mechanical control of power operation joins 41 valve rods and commutates left, and the work fluid interflow of first oil pump 11 and second oil pump 12 enters flexible transfer valve group 31 by flexible mechanical 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 mechanical 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 mechanical 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 mechanical control connection 44 outlets that hoist are furnished with first pair access port A9 and 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:
Mechanical control connection 44 commutation to the right that hoists of power operation flow divider valve group 4 pairs, 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 access port A9 and the secondary mechanical control connection 44 that hoists 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:
3, auxiliary hoisting mechanism shut-down operation:
When auxiliary hoisting mechanism 57 quits work, the pair mechanical 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 mechanical control connection 43 outlets that hoist are furnished with the first main access port A10 and the second main access port B10 that hoists of hoisting 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.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 step-down operation of main hoisting mechanism:
Power operation master mechanical control connection 43 commutation to the right that hoists, the work fluid interflow of first oil pump 11 and second oil pump 12 is by main mechanical 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, the first main access port A10 that hoists joins the 43 oil return runners that arrive flow divider valve group 4 to fuel tank with the main mechanical control that hoists, and finishes the main hoisting mechanism down maneuver.
2, a lift operations of main hoisting mechanism:
Power operation master mechanical control connection 43 commutation left that hoists, the work fluid interflow of first oil pump 11 and second oil pump 12 is by main mechanical 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 mechanical 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 mechanical 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 mechanical control connection are furnished with the first luffing access port A8 and 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 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: power operation flow divider valve group 4 luffing mechanical controies connection 42 commutation 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 mechanical 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: power operation luffing mechanical control joins 42 valve rods and commutates 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 mechanical 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.
Advantage of the present utility model is: 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 utility model is illustrated, and various variations or the remodeling made by those of ordinary skills can not break away from scope of the present utility model.
Claims (10)
1. hydraulic system of mechanically operated triple pump 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) and decompression guide's oil sources valve group (7); 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 mechanical control connection (41), the luffing mechanical 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) mechanical control connection (43) and the pair mechanical 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.
2. hydraulic system of mechanically operated triple pump according to claim 1, it is characterized in that: also dispose the intermediate mechanical control 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 mechanical control connection (43) that hoists, pair mechanical control connection (44) pressure port that hoists, correspondingly, the oil circuit of second oil inlet (P2) side all is connected with flexible mechanical control connection (41), luffing mechanical control connection (42) pressure port; The outlet of described first reducing valve (71) also is connected with first safety valve (75).
3. hydraulic system of mechanically operated triple pump 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), be furnished with the first commutation valve rod (23), second electromagnetic valve (DHF2), control pressure tap (K) and the first gyroscopic output mouth (A11), the second gyroscopic output mouth (B11) in the described rotary buffering valve group (22), described control pressure tap (K) is connected with the 4th oil inlet (P4); Be connected with rotary motor (24) between the described first gyroscopic output mouth (A11), the second gyroscopic output mouth (B11), and also be fitted with trainstop (28) on this rotary motor (24); Select to be formed with intermediate loop (22b) through first shuttle valve (22a) between the 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 control pressure tap (K) through second reducing valve (22c).
4. hydraulic system of mechanically operated triple pump 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) and second delivery port (Y2) in the described trainstop control cock group (21), the drive end (25a) of first pilot operated directional control valve (25) is connected with described control pressure tap (K); 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 communicated with described second delivery port (Y2) through first one-way throttle valve (27), and this second delivery port (Y2) is connected with described trainstop (28); Also be shaped on oil return pressure tap (Pt) on the described rotary buffering valve group (22), and this oil return pressure tap (Pt) is communicated with described first pilot operated directional control valve (25) spring cavity (25b).
5. hydraulic system of mechanically operated triple pump according to claim 2 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 mechanical control connection (41) outlet is furnished with the first flexible access port (A7) and the second flexible access port (B7) respectively, 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 system of mechanically operated triple pump 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 (37) in the described telescopic oil cylinder transfer valve group (31), and this damping (37) two ends are communicated with second pilot operated directional control valve (35) return opening, outside return opening (T7) respectively.
7. hydraulic system of mechanically operated triple pump 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); Mechanical control connection (44) outlet that hoists of described pair is furnished with first pair access port (A9) and 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 system of mechanically operated triple pump 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 mechanical control connection (43) outlet that hoists is furnished with the first main access port (A10) and second that hoists respectively and leads the access port (B10) that hoists, 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 system of mechanically operated triple pump 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 mechanical control connection (42) outlet is furnished with the first luffing access port (A8) and the second luffing access port (B8) respectively, 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 system of mechanically operated triple pump 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 (9), and this unloader valve group (9) 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 (91), 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).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201916205U CN201686408U (en) | 2010-05-13 | 2010-05-13 | Mechanically operated three-pump hydraulic system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2010201916205U CN201686408U (en) | 2010-05-13 | 2010-05-13 | Mechanically operated three-pump hydraulic system |
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| CN201686408U true CN201686408U (en) | 2010-12-29 |
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| CN2010201916205U Expired - Lifetime CN201686408U (en) | 2010-05-13 | 2010-05-13 | Mechanically operated three-pump hydraulic system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109185246A (en) * | 2018-11-22 | 2019-01-11 | 徐工消防安全装备有限公司 | Hydraulic control system and aerial working platform vehicle |
| CN110937541A (en) * | 2019-12-27 | 2020-03-31 | 恒天九五重工有限公司 | Winch hydraulic system using O-shaped neutral position function reversing valve |
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2010
- 2010-05-13 CN CN2010201916205U patent/CN201686408U/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109185246A (en) * | 2018-11-22 | 2019-01-11 | 徐工消防安全装备有限公司 | Hydraulic control system and aerial working platform vehicle |
| CN110937541A (en) * | 2019-12-27 | 2020-03-31 | 恒天九五重工有限公司 | Winch hydraulic system using O-shaped neutral position function reversing valve |
| CN110937541B (en) * | 2019-12-27 | 2024-05-03 | 恒天九五重工有限公司 | Winch hydraulic system using O-shaped median function reversing valve |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20101229 Effective date of abandoning: 20120718 |