CN106759621A - Load-sensitive formula loading machine determines variable delivery hydraulic system - Google Patents
Load-sensitive formula loading machine determines variable delivery hydraulic system Download PDFInfo
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- CN106759621A CN106759621A CN201710005638.8A CN201710005638A CN106759621A CN 106759621 A CN106759621 A CN 106759621A CN 201710005638 A CN201710005638 A CN 201710005638A CN 106759621 A CN106759621 A CN 106759621A
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
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Abstract
Determine variable delivery hydraulic system the present invention relates to loader hydraulic system, more particularly to a kind of load-sensitive formula loading machine, include logic control valve and flow control valve；The EF hydraulic fluid ports of the logic control valve connect banked direction control valves by the hydraulic-control throttling valve of flow control valve, and pilot valve connects the pilot operated directional control valve KL hydraulic fluid ports of logic control valve and the hydraulic-control throttling valve LS8 hydraulic fluid ports of flow control valve respectively.The present invention sets up three-way pressure compensating device in current quantitative work system and hydraulic-control throttling valve group is closed, work system is realized by by-pass tee pressure compensator Low-pressure load discharge and constant displacement pump load pressure self adaptation, and then realizes that the flow unrelated with load change is precisely exported；And variable pump full working scope change discharge capacity is realized, at utmost play variable pump advantage.
Description
Technical field
Determine variable delivery hydraulic system the present invention relates to engineering machinery, more particularly to a kind of loading machine.
Background technology
Loading machine is a kind of operating efficiency engineering machinery high, widely used, and its hydraulic system is main by working hydraulic pressure system
System and steering hydraulic system composition.Domestic existing loader hydraulic system has full fixed dilivery hydraulic system, entire variable hydraulic system, determines
Variable delivery hydraulic system etc..Wherein full fixed dilivery hydraulic system, i.e. steering and work system using the system of constant displacement pump, its into
This is relatively low, but belongs to out middle position overflowing and speed system, there is spill losses, restriction loss, middle bit-loss, therefore the hydraulic system
High energy consumption, the big, efficiency comparison that generates heat are low；Entire variable hydraulic system, i.e., closed using double load-reacting plunger displacement pumps, load-sensitive
The Hydraulic Elements such as middle level control valve, relative quantification hydraulic system operation comfortableness will get well, and can realize Power Control and energy-conservation, but main
Want problem be it is relatively costly, it is very sensitive to system clean degree, small pollution will to the performance of product, quality, use the longevity
Life and reliability are that time between failures generation has a strong impact on；Determine variable delivery hydraulic system, i.e. steering and use load-sensitive
Variable plunger pump, work system uses constant displacement pump, with regard to its cost and energy-saving effect comprehensive assessment, determine variable delivery hydraulic system have compared with
Cost performance high, principle is simply easily achieved, but present determines variable delivery hydraulic system and there is problems with use：
（1）When whole machine equipment is acted, the existing Variable plunger pump for determining variable system is changed into constant pressure variable displacement pump to collaborate to work
Make hydraulic system, i.e., before pressure regulator valve setting pressure on not up to variable pump, variable pump swash plate is in sail angle, pumpage
Maximum and displacement constant, actually this suitable constant displacement pump of stage constant pressure variable displacement pump.And then interflow when equipment micro-control and
There is high pressure restriction loss during in maximum pressure and spill losses variable pump advantage is not played to greatest extent.Such as Fig. 5 and Fig. 6
It is shown, the load-sensitive signal of variable pump in Parker and CN104405006A and CN104929183A technical schemes disclosed in Xu works
LS/X takes from the oil inlet P/A of banked direction control valves, and when work system works, the load-sensitive valve two ends pressure difference of variable pump is less than setting
Value, variable pump swash plate is in sail angle, is exported with maximum pump discharge, interflow to work system, now loses and becomes displacement function.
（2）Existing to determine variable system, the widely used center six of opening of paced work system leads to banked direction control valves, speed governing is using side
The combination that road throttles with meter in, its speed governing effect is throttled by valve rod, and control goes the amount of opening of oil cylinder and oil return box
Realize.Overcome load pressure due to being the pressure set up by meter out, therefore governor control characteristics receives load pressure and oil pump
The influence of flow.When spool stroke is certain, load pressure increase goes the flow of oil cylinder to be reduced by.Whole working load pressure
Power be it is unstable vary, the flow of hydraulic pump makes its speed governing maneuvering performance very unstable also being continually changing, and manipulation is tired
It is difficult；And valve rod steering force is big, because load pressure change causes valve port △ P to change, hydraulic power change causes valve rod steering force
Change, the scrambling of steering force makes vernier control more difficult.In a word, the oil circuit poor controllability, operator wants precise control
Equipment is highly difficult, entirely by operator's sensation, experience and performance.
（3）, when work system does not work, its flow can be by holding middle position banked direction control valves for the existing constant displacement pump for determining variable system
Fuel tank is flowed back to, larger middle position linear loss is produced, so causing hydraulic system to produce very big heat, energy consumption is big.
The content of the invention
Regarding to the issue above, it is an object of the invention to propose a kind of more energy-conservation, handling it is good, compared with high performance-price ratio
Load-sensitive formula loading machine determine variable delivery hydraulic system.
The present invention is realized using following technical scheme：A kind of load-sensitive formula loading machine determines variable delivery hydraulic system, including
There are variable pump, constant displacement pump, fuel tank, flow control valve, pilot valve, boom cylinder and rotary ink tank, banked direction control valves, shuttle valve block, flow
Amplifying valve block, steering gear, logic control valve；The CF hydraulic fluid port connection traffic amplifying valve blocks that variable pump passes through logic control valve, logic
Control valve T1 oil return openings connection fuel tank, constant displacement pump by flow control valve connect banked direction control valves, banked direction control valves connect rotary ink tank with
Boom cylinder, the EF hydraulic fluid ports of the logic control valve connect banked direction control valves by the hydraulic-control throttling valve of flow control valve, and pilot valve leads to
Cross shuttle valve block and connect the pilot operated directional control valve KL hydraulic fluid ports of logic control valve and the hydraulic-control throttling valve LS8 hydraulic fluid ports of flow control valve respectively；
When the signal pressure that shuttle valve block LS6 passes to the hydraulic-control throttling valve LS8 hydraulic fluid ports of flow control valve is low, pressure difference before and after hydraulic-control throttling valve
When closing setting pressure higher than the pressure-compensated valve of logic control valve, variable pump fluid is not to flow control valve interflow only for turning to
System, constant displacement pump flow according to needed for the hydraulic-control throttling valve opening of flow control valve exports rotary ink tank and boom cylinder is unnecessary
Flow oil return box；When the signal pressure that shuttle valve block LS6 hydraulic fluid ports pass to hydraulic-control throttling valve LS8 hydraulic fluid ports is high, and rotary ink tank and dynamic
Flow needed for arm oil cylinder is more than flow needed for constant displacement pump, pressure-compensated valve of the pressure difference less than logic control valve before and after hydraulic-control throttling valve
When closing setting pressure, variable pump collaborates to banked direction control valves to flow control valve, there is provided shortcoming flow.
Described flow control valve includes three-way pressure compensating device, damping hole, check valve, hydraulic-control throttling valve, Stress control
Valve, unloading valve and P6 hydraulic fluid ports, P7 hydraulic fluid ports, P8 hydraulic fluid ports, LS7 hydraulic fluid ports, LS8 hydraulic fluid ports, T4 hydraulic fluid ports；Three-way pressure compensating device enters
Mouthful with P6 mouthfuls, unloading valve, check valve import be connected, the outlet of three-way pressure compensating device and off-load valve outlet, pressure-control valve
Outlet is connected after connecting with T4 mouthfuls；One-way valved outlet is connected in the import of P8 hydraulic fluid ports, hydraulic-control throttling valve, and pressure-control valve
Stress control mouthful；The spring cavity of unloading valve connects the import in pressure-control valve；P6 hydraulic fluid ports connect constant displacement pump, and the connection of P7 hydraulic fluid ports is more
Road valve, P8 hydraulic fluid ports are connected with the EF hydraulic fluid ports of logic control valve, and LS7 hydraulic fluid ports connect logic control valve LS3 hydraulic fluid ports and transmit work and bear
Information carrying number, LS8 hydraulic fluid ports are connected with shuttle valve block LS6 hydraulic fluid ports；Pressure difference between P7 hydraulic fluid ports, the P8 hydraulic fluid ports of hydraulic-control throttling valve is by threeway pressure
Force compensating device sets, the pilot signal regulation that the hydraulic-control throttling valve opening is transmitted according to shuttle valve block, needed for output services system
Flow.
Described logic control valve includes fixed pressure reducing valve, pilot operated directional control valve, flow compensation valve, pressure-compensated valve, shuttle
Valve, check valve and P1 hydraulic fluid ports, PX hydraulic fluid ports, PSt hydraulic fluid ports, LS1 hydraulic fluid ports, LS2 hydraulic fluid ports, LS3 hydraulic fluid ports, KL hydraulic fluid ports, CF hydraulic fluid ports, EF
Hydraulic fluid port, T1 hydraulic fluid ports；The P1 hydraulic fluid ports connect CF hydraulic fluid ports, and P1 hydraulic fluid ports are connected PX hydraulic fluid ports, another road and passed through all the way by fixed pressure reducing valve
Check valve connects PSt hydraulic fluid ports, flow compensation valve spring cavity is connected by pilot operated directional control valve, by flow compensation valve, pressure compensation
Valve connects EF hydraulic fluid ports；The LS2 hydraulic fluid ports and the LS3 hydraulic fluid ports are connected through shuttle valve selection with the LS1 hydraulic fluid ports；The KL hydraulic fluid ports
Connection pilot operated directional control valve control end；The spring cavity of the fixed pressure reducing valve and pilot operated directional control valve is connected with T1 hydraulic fluid ports；The LS3 oil
Mouth is connected with pressure-compensated valve spring cavity；CF hydraulic fluid port preferential attachment flux amplification valve blocks, P1 hydraulic fluid port link variable pumps, T1 hydraulic fluid ports connect
Connected tank, KL hydraulic fluid ports take from the signal of shuttle valve block, and EF hydraulic fluid port connection flow control valves, LS3 takes from flow control valve load feedback
Mouthful, the connection steering gear of PX hydraulic fluid ports, PSt hydraulic fluid ports connection pilot valve；Pressure difference between EF hydraulic fluid ports and LS3 hydraulic fluid ports determines pressure-compensated valve
Aperture, control steering whether to work system collaborate and interflow flow.
The shuttle valve block include the first shuttle valve, the second shuttle valve, the 3rd shuttle valve, two-way pilot operated valve device and D1 hydraulic fluid ports, D2 hydraulic fluid ports,
C1 hydraulic fluid ports, C2 hydraulic fluid ports, LS5 hydraulic fluid ports, LS6 hydraulic fluid ports, D1 hydraulic fluid ports, D2 hydraulic fluid ports are connected after being gated through the first shuttle valve by two-way pilot operated valve device
3rd shuttle valve left end, C1 hydraulic fluid ports, C2 hydraulic fluid ports connect the 3rd shuttle valve right-hand member, the 3rd shuttle valve outlet after being gated through the second shuttle valve
LS5 hydraulic fluid ports, LS6 hydraulic fluid ports；Two-way pilot operated valve device control end and the second shuttle valve outlet；LS5 hydraulic fluid ports connect the KL of logic control valve
Hydraulic fluid port, the LS8 hydraulic fluid ports of LS6 hydraulic fluid port connection flow control valves；D1 hydraulic fluid ports, D2 hydraulic fluid ports, C1 hydraulic fluid ports, the connection pilot valve control of C2 hydraulic fluid ports
Mouthful.
The C1 hydraulic fluid ports of the shuttle valve block, C2 hydraulic fluid ports connect pilot valve rotating bucket control mouth A, rotating bucket control mouth C, D1 oil respectively
Mouth, D2 hydraulic fluid ports connect pilot valve swing arm control mouth B, swing arm control mouth D, C1 hydraulic fluid port/C2 hydraulic fluid ports fuel injection pressure signal and promote two-way respectively
Pilot operated valve device is in bottom, makes D1 hydraulic fluid ports/D2 hydraulic fluid port signal-off.
The logic control valve also includes safety valve, and safety valve connects P1 hydraulic fluid ports and T1 hydraulic fluid ports.
The steering includes flux amplification valve block.
Three-way pressure compensating device of the invention can be applied in constant displacement pump pressure compensating system.The pressure compensator is applied
In hydraulic system with constant displacement pump, and coordinate with choke valve, not only solve automatic pressure compensation, it is ensured that by throttling during load change
The flow of valve is basicly stable, and the outlet pressure of pump can be made to match with load all the time, realizes energy-conservation, causes successively whole
The power drop of hydraulic system.The present invention determines variable delivery hydraulic system using load-sensitive formula loading machine, in current quantitative job family
Three-way pressure compensating device and hydraulic-control throttling valve group is set up in system to close so that current quantitative pump open middle position overflowing and speed system upgrade into
Constant displacement pump load sensitive system, realizes work system by by-pass tee pressure compensator Low-pressure load discharge and quantitative pump load pressure
Force adaptive, and then realize that the flow unrelated with load change is precisely exported；Another technical scheme is also closed in variable pump
Set up pressure-compensated valve in diverter module logic control valve, and the pressure-compensated valve and variable pump load-sensitive valve keying and liquid
Pressure difference association before and after control choke valve, realizes variable pump full working scope and becomes discharge capacity, at utmost plays variable pump advantage.With existing skill
Art is compared and had the advantage that：
（1）In constant displacement pump pressure compensating system, when banked direction control valves does not work in middle position, pump is realized by three-way pressure compensating device
Off-load, to pumping up step-down and protective effect.Three-way pressure compensating device pressure unloading is small simultaneously, section when realizing that system does not work
Energy.
（2）When the system is operating, banked direction control valves import is poor with outlet pressure when three-way pressure compensating device ensure that load change
It is constant, system is realized and precisely exported with the load unrelated flow of change, that is, flow through the size and valve element of banked direction control valves flow
Displacement is relevant, unrelated with load variations；Can not only very well realize that the load of the constant i.e. pressure compensator of pressure difference before and after flow controller is mended
The effect of repaying, and it is poor that the outlet of pump can be made only to be higher by a level pressure than load pressure in real time, so as to realize that load pressure is adaptive
Should.
（3）Pressure-compensated valve, and the pressure-compensated valve and variable are set up in variable pump closes diverter module logic control valve
The keying of pump load sensitive valve is associated with pressure difference before and after hydraulic-control throttling valve, is realized variable pump full working scope and is become discharge capacity, at utmost
Play variable pump advantage.
Brief description of the drawings
Fig. 1 is embodiment of the present invention systematic schematic diagram；
Fig. 2 is the schematic diagram of logic control valve in the embodiment of the present invention；
Fig. 3 is the schematic diagram of shuttle valve block in the embodiment of the present invention；
Fig. 4 is the schematic diagram of flow control valve in the embodiment of the present invention；
Fig. 5 is system diagram disclosed in CN104405006A；
Fig. 6 is system diagram disclosed in CN104929183A；
Description of symbols in figure：
1- variable pumps, 2- constant displacement pumps, 3- filters, 4- fuel tanks, 5- flow control valves, 6- accumulators, 7- pilot valves, 8- swing arms oil
Cylinder, 9- rotary ink tanks, 10- banked direction control valves, 11- shuttle valve blocks, 12- steering cylinders, 13- flux amplification valve blocks, 14- steering gears, 15- is patrolled
Collect control valve, 16- fixed pressure reducing valves, 17- pilot operated directional control valves, 18- flow compensation valves, 19- safety valves, 20- damping holes, 21- pressures
Force compensating valve, 22- damping holes, 23- shuttle valves, 24- damping holes, 25- check valves, 26- three-way pressure compensating devices, 27- damping holes,
28- check valves, 29- hydraulic-control throttling valves, 30- pressure-control valves, 31- unloading valves, the shuttle valves of 32- first, 33- two-way pilot operated valve devices, 34-
Second shuttle valve, the shuttle valves of 35- the 3rd.
Specific embodiment
To further understand the present invention, technical scheme is done into one with reference to the accompanying drawings and detailed description
Step explanation, referring to Fig. 1 to Fig. 4：
As shown in figure 1, hydraulic system in the present embodiment, including variable pump 1, constant displacement pump 2, filter 3, fuel tank 4, flow control valve
5th, accumulator 6, pilot valve 7, boom cylinder 8, rotary ink tank 9, banked direction control valves 10, shuttle valve block 11, steering cylinder 12, flux amplification valve
Block 13, steering gear 14, logic control valve 15 etc. are constituted.The inlet port of variable pump 1 is connected with hydraulic oil container 4；Variable pump 1 it is fuel-displaced
Mouth is connected with P1 mouthfuls of logic control valve 15；LS2 mouthfuls of logic control valve 15 is connected with LS4 mouthfuls of flux amplification valve block 13；Patrol
Collect control valve 15 CF mouthfuls is connected with P2 mouthfuls of flux amplification valve block 13；KL mouthfuls of logic control valve 15 with the LS5 of shuttle valve block 11
Mouth is connected；LS3 mouthfuls of logic control valve 15 is connected with LS7 mouthfuls of flow control valve 5；EF mouthfuls of logic control valve 15 and flow control
The P8 of valve processed 5 is connected；T1 mouthfuls of logic control valve 15 with T2 mouthfuls of steering gear 14, T3 mouthfuls of flux amplification valve block 13, flow
Control T4 mouthful of valve 5, T5 mouthfuls of banked direction control valves 10 it is connected after be connected with filter 3 again, be finally connected with fuel tank 4；Logic control valve
Px mouthfuls of 15 is connected with P4 mouthfuls of steering gear 14；Pst mouthfuls of logic control valve 15 and accumulator 6, P5 mouthfuls of pilot valve 7 be connected；
LS1 mouthfuls of logic control valve 15 is connected with LS mouthfuls of variable pump 1；A/B mouthfuls of flux amplification valve block 13 with the phase of steering cylinder 12
Chamber is answered to be connected.The L mouthfuls of a of flux amplification valve block 13 of steering gear 14 is connected；R mouthfuls of steering gear 10 and flux amplification valve block 13
B is connected；C mouthfuls of pilot valve 7 is connected with b1 mouthfuls of banked direction control valves 10, C2 mouthfuls of shuttle valve block 11；A mouthfuls of pilot valve 7 and banked direction control valves 10
A1 mouthfuls, C1 mouthfuls of shuttle valve block 11 be connected；B mouthfuls of pilot valve 7 is connected with a2 mouthfuls of banked direction control valves 10, D1 mouthfuls of shuttle valve block 11；First
D mouthfuls of pilot valve 7 is connected with b2 mouthfuls of banked direction control valves 10, D2 mouthfuls of shuttle valve block 11；A1 mouthfuls of banked direction control valves 10 with the rodless cavity of rotating bucket cylinder 9
It is connected；B1 mouthfuls of banked direction control valves 10 is connected with the rod chamber of rotating bucket cylinder 9；A2 mouthfuls of banked direction control valves 10 is connected with the rodless cavity of swing arm cylinder 8；
B2 mouthfuls of banked direction control valves 10 is connected with the rod chamber of swing arm cylinder 8；The LS8 hydraulic fluid port phases of LS6 mouthfuls of shuttle valve block 11 and flow control valve 5
Even；The inlet port of constant displacement pump 2 is connected with fuel tank 4；The oil-out of constant displacement pump 2 is connected with P6 mouthfuls of flow control valve 5；Flow is controlled
P7 mouthfuls of valve 5 is connected with P3 mouthfuls of banked direction control valves 10.
In the present embodiment, as shown in Fig. 2 logic control valve includes that fixed pressure reducing valve 16, pilot operated directional control valve 17, flow are mended
Repay valve 18, safety valve 19, damping hole 20, pressure-compensated valve 21, damping hole 22, shuttle valve 23, damping hole 24, check valve 25 and P1
The groups such as hydraulic fluid port, LS2 hydraulic fluid ports, CF hydraulic fluid ports, KL hydraulic fluid ports, LS3 hydraulic fluid ports, EF hydraulic fluid ports, T1 hydraulic fluid ports, PX hydraulic fluid ports, PSt hydraulic fluid ports, LS1 hydraulic fluid ports
Into.The P1 hydraulic fluid ports are connected in the oil inlet of fixed pressure reducing valve 16, flow compensation valve 18, and are connected at pilot operated directional control valve 17
Oil inlet at bottom；The LS2 hydraulic fluid ports are connected in the left end of shuttle valve 23, and oil-feed of the pilot operated directional control valve 17 when being in upper
Mouthful；The LS3 hydraulic fluid ports are connected in the spring cavity of pressure-compensated valve 21 through damping hole 20, and are connected with the right-hand member of shuttle valve 23；Shuttle valve 23 goes out
Hydraulic fluid port is connected in LS1 hydraulic fluid ports through damping hole 24；Fixed pressure reducing valve 16 is connected in the oil inlet of check valve 25 and PX hydraulic fluid ports, check valve 25
Oil-out and PSt hydraulic fluid ports connect；The liquid controling cavity of pilot operated directional control valve 17 is connected with KL hydraulic fluid ports, and oil-out is through damping hole 22 and flow
The spring cavity of recuperation valve 18 is connected；The oil-out of flow compensation valve 18 is connected in the oil inlet of pressure-compensated valve 21, pressure compensation
The oil-out of valve 21 is connected with EF hydraulic fluid ports；The oil inlet of safety valve 19 is connected with P1 hydraulic fluid ports and CF hydraulic fluid ports, and oil-out connects through T1 hydraulic fluid ports
Oil return box 4.
In the present embodiment, as shown in figure 4, flow control valve includes three-way pressure compensating device 26, damping hole 27, check valve
28th, hydraulic-control throttling valve 29, pressure-control valve 30, unloading valve 31 and P6 hydraulic fluid ports, LS7 hydraulic fluid ports, LS8 hydraulic fluid ports, P7 hydraulic fluid ports, T4 oil
The composition such as mouth.The oil inlet of three-way pressure compensating device 26 with P6 mouthfuls, unloading valve 31, check valve 28 oil inlet be connected, threeway pressure
The oil-out of force compensating device 26 is connected after being connected with the oil-out of unloading valve 31, the oil-out of pressure-control valve 30 with T4 mouthfuls；Check valve
28 oil-outs are connected in the oil inlet of P8 hydraulic fluid ports, three-way pressure compensating device 26, and pressure-control valve 30 Stress control hydraulic fluid port；
The spring cavity of unloading valve 31 is connected in the oil inlet of pressure-control valve 306.The oil-out P7 and multichannel of three-way pressure compensating device 26
The import P3 connections of valve 10.
Operation principle of the invention is：
When the 1st, without steering, without work.Steering gear 14 is not worked, then the LS4 oil ducts of flux amplification valve block 13 are communicated with oil return T3, instead
The LS pressure for being fed to variable pump 1 is 0.Pilot valve 7 does not work, and pilot valve output pressure is 0, during each valve element of banked direction control valves 10 is in
Position, valve port is closed, the 2/2-way valve 33 in shuttle valve block 11 be in it is upper in figure, because oil-collecting hole C1, C2, D1, D2 are without elder generation
Pilot power is input into, so load signal LS5, LS6 output pressure of shuttle valve block 11 is zero, so the hydraulic control in flow control valve 5
Choke valve 29 is in right position in figure, and valve port is closed, and the pilot operated directional control valve 17 in logic control valve 15 is in initial bit
Bottom in figure is put, the spring cavity of flow compensation valve 18 and ante-chamber are all communicated with the hydraulic fluid port that pumps out of load-reacting pump, and the valve element will
Closed state is constantly in, is collaborated obstructed to the oil circuit of work system.The outlet pressure of the hydraulic-control throttling valve 29 in flow control valve 5
Power is 0, and the three-way pressure compensating device 26 in flow control valve 5 is in open state, and the oil of constant displacement pump 2 is through three-way pressure compensating
The off-load oil return box of device 26；Load-sensitive valve spring cavity pressure in variable pump 1 is 0, and Ioad-sensing control valve is in left position in figure,
Variable pump swash plate angle is minimum swash angle, and output flow is 0, and the output pressure of variable pump 1 is the pressure difference of its Ioad-sensing control valve
Setting value, variable pump 1 is in stand-by operation state.
Work system does not work, when steering works.
Pilot valve 7 is not worked, and pilot valve output pressure is 0, and each valve element of banked direction control valves 10 is in middle position, and valve port is closed, shuttle valve
2/2-way valve 33 in block 11 be in it is upper in figure, because oil-collecting hole C1, C2, D1, D2 are input into without pilot pressure, so shuttle
Load signal LS5, LS6 output pressure of valve block 11 are 0, so the hydraulic-control throttling valve 29 in flow control valve 5 is in the right side in figure
Position, valve port is closed, and the pilot operated directional control valve 17 in logic control valve 15 is in bottom in initial position figure, flow-compensated
The spring cavity of valve 18 and ante-chamber are all communicated with P1 hydraulic fluid ports, and the valve element will always be in closed state, the oil circuit at interflow to work system
It is obstructed.When steering gear 14 is rotated, the fluid of variable pump 1 enters steering gear afterwards by the fixed pressure reducing valve 16 of logic control valve 15
14, the pressure output control of steering gear 14 promotes the valve core movement of flux amplification valve block 13, and the output flow of variable pump 1 is through Flow amplification
Valve block 13 enters steering cylinder 12, turns to work.The load pressure of steering cylinder 12 feeds back to flux amplification valve by LS4 oil circuits
The fixed poor flow valve spring cavity of block 13 and LS mouthfuls of variable pump 1, make the output pressure of variable pump 1 only higher than steering load pressure one
Pressure set points, variable pump 1 automatically adjusts swash plate angle, flow needed for only output is corresponding with steering gear rotating speed.Due to flow control
The outlet pressure of the hydraulic-control throttling valve 29 in valve processed 5 is 0, and the three-way pressure compensating device 26 in flow control valve 5 is in open
State, therefore the oil of constant displacement pump 2 is through the off-load oil return box 4 of three-way pressure compensating device 26.
Steering does not work, when work system works
（1）Boom arm lift is acted.When pilot valve 7 is manipulated to boom arm lift position, the 2/2-way valve 33 in shuttle valve block 11 works
Upper in figure, the boom arm lift pilot pressure of pilot valve 7 is through the shuttle valve 32 in shuttle valve block 11,2/2-way valve 33, shuttle valve 35
The liquid controling cavity of pilot operated directional control valve 17 in the hydraulic-control throttling valve 29 and logic control valve 15 that pass to respectively in flow control valve 5, in the ban
When pilot power reaches a certain setting value, promote the valve element of pilot operated directional control valve 17 to commutate into figure upper, arrive steering LS2 pressure feedbacks
The spring cavity of flow compensation valve 18, the oil liquid pressure of variable pump 1 acts on the valve element epicoele of flow compensation valve 18, flow compensation valve 18 dozens
Open.
When the output pressure of pilot valve 7 is relatively low, the hydraulic-control throttling valve 29 in flow control valve 5 is in small open-work, when
When pressure difference is more than a certain setting value before and after the valve of hydraulic-control throttling valve 29, the valve port of pressure-compensated valve 21 in logic control valve 15 subtracts
Small, until close, the not output flow of variable pump 1, now variable pump 1 does not conform to and flow to work system.Simultaneously in flow control valve 5
The two ends pressure difference of three-way pressure compensating device 26 exceedes spring setting value, and valve element is moved downward, and makes three-way pressure compensating device 23 and oil return
The aperture increase in road, the flow needed for the output services device of constant displacement pump 2 enters raise-position on the swing arm of banked direction control valves 10, and excess traffic is through three
Lead to the direct off-load of pressure compensator 23 to fuel tank 4.
When the output pressure of pilot valve 7 increases, the valve port increase of the hydraulic-control throttling valve 29 in flow control valve 5, hydraulic control section
Pressure difference reduces before and after flowing the valve of valve 29, and the three-way pressure compensating device 26 in flow control valve 5 is turned down with drainback passage, when pressure difference is small
In after spring setting value, three-way pressure compensating device 26 is closed with drainback passage, and the flow of constant displacement pump 2 all flow to work system.Together
When reduce with the pressure difference of banked direction control valves inlet pressure and load pressure, the valve port of pressure-compensated valve 21 in logic control valve 15 is slow
Increase, while load pressure reaches LS mouthfuls in variable pump 1 through shuttle valve 23, the output fluid of variable pump 1 enters hydraulic system of working,
Flow needed for supplement work system, realizes Dual-pump flow-converging, and now the output flow size of variable pump 1 is depending in logic control valve 15
The valve port opening of pressure-compensated valve 21.
（2）Swing arm down maneuver.Circuit theory is no longer described with " boom arm lift action ".
（3）Swing arm floating is acted.Circuit theory is no longer described with " boom arm lift action ".
（4）When steering and work system work simultaneously by taking boom arm lift action as an example.When steering hydraulic system works,
During hydraulic system of working boom arm lift, LS4 mouthfuls of flux amplification valve block 13 has load pressure signal, and pilot valve 7 also has pressure to believe
Number, the left end interface of the LS4 signal transmissions of flux amplification valve block 13 to the shuttle valve 23 in logic control valve 15.Pilot valve 7 it is dynamic
Arm lifting pilot pressure is passed in flow control valve 5 respectively through the shuttle valve 32 in shuttle valve block 11,2/2-way valve 33, shuttle valve 35
The liquid controling cavity of pilot operated directional control valve 17 in hydraulic-control throttling valve 29 and logic control valve 15, when pilot pressure reaches a certain setting value,
Promote the valve element of pilot operated directional control valve 17 to commutate into figure upper, make steering LS2 pressure feedbacks to the spring cavity of flow compensation valve 18, variable
The oil liquid pressure of pump 1 acts on the valve element epicoele of flow compensation valve 18.The outlet pressure of the hydraulic-control throttling valve 29 in flow control valve 5
The bullet of pressure-compensated valve 21 in the spring cavity of three-way pressure compensating device 26, the logic control valve 15 that pass to respectively in flow control valve 5
Spring chamber and the right-hand member interface of shuttle valve 23.The fluid of constant displacement pump 2 gives the upper raise-position fuel feeding of the swing arm of banked direction control valves 10 through flow control valve 5, many
Residual current amount is through the off-load oil return box of three-way pressure compensating device 26.
When steering pressure ratio work system is high, the LS4 signals of flux amplification valve block 13 are through in logic control valve 15
Shuttle valve 23 gate and be delivered to LS hydraulic fluid ports in variable pump 1.When pilot pressure reaches a certain setting value, logic control valve is promoted
The valve element of pilot operated directional control valve 17 in 15 commutates into figure upper, makes steering LS2 pressure feedbacks to the spring cavity of flow compensation valve 18, becomes
The oil liquid pressure for measuring pump 1 acts on the epicoele of flow compensation valve 18.When the engine is idling, the output flow of variable pump 1 is less, if
Now fast steering, then the output flow of variable pump 1 be not enough to push logic open by the pressure difference that the valve element of flux amplification valve block 13 is formed
The flow compensation valve 18 of valve 15 is controlled, so the flow of variable pump 1 all supplies steering, is not collaborated to work system.Variable
The output pressure of pump 1 is the pressure value for turning to operating pressure plus fixed poor flow valve setting on flux amplification valve block 13, variable pump 1
Output flow depends on the aperture of the valve element of flux amplification valve block 13 of steering.When the slow-speed of steering gear 14 or engine speed
During rising, the flow of variable pump 1 meets flow needed for steering gear rotating speed correspondence, and excess traffic is formed by flux amplification valve block 13
Pressure difference will be above the pressure differential resetting value of flow compensation valve 18 on logic control valve 15, so as to push the valve element of flow compensation valve 18, flow open
Recuperation valve 18 is opened.Pressure of the pressure difference more than logic control valve 15 before and after the valve of the hydraulic-control throttling valve 29 in flow control valve 5
During 21 pressure differential resetting value of recuperation valve, the pressure-compensated valve 21 in logic control valve 15 is closed, and now variable pump 1 is still only to steering system
System fuel feeding, not to work system fuel feeding.Pressure difference is less than setting value before and after the valve of the hydraulic-control throttling valve 29 in flow control valve 5
When, the pressure-compensated valve 21 in logic control valve 15 is slowly opened, and unnecessary fluid is flowed to work system, realizes interflow, now
The output pressure of variable pump 1 is steering maximum pressure.
When work system is higher than steering pressure, work system load pressure signal LS3 is through in logic control valve 15
Shuttle valve 23 gate and be delivered to LS hydraulic fluid ports in variable pump 1.When the engine is idling, the output flow of variable pump 1 is small, if steering gear
14 quick rotations, the output flow of variable pump 1 is not enough to push logic control valve 15 open by the pressure difference that flux amplification valve block 13 is formed
Upper flow compensation valve 18, so the flow of variable pump 1 all supplies steering, does not collaborate to work system.When steering gear 14 is slow
Turn or engine speed is raised, the flow of variable pump 1 meets flow needed for steering gear rotating speed correspondence, excess traffic is put by flow
The pressure difference that big valve block 13 is formed will be above the pressure differential resetting value of flow compensation valve 18 on logic control valve 15, flow-compensated so as to push open
The valve element of valve 18, flow compensation valve 18 is opened.Pressure difference is more than logic control before and after the valve of the hydraulic-control throttling valve 29 in flow control valve 5
During 21 pressure differential resetting value of pressure-compensated valve in valve processed 15, the pressure-compensated valve 21 in logic control valve 15 is closed, this variations per hour
Pump 1 still only to steering fuel feeding, not to work system fuel feeding.Before and after the valve of the hydraulic-control throttling valve 29 in flow control valve 5
When pressure difference is less than setting value, the pressure-compensated valve 21 in logic control valve 15 is slowly opened, and unnecessary fluid is flowed to work system,
Interflow is realized, now the output pressure of variable pump 1 is work system maximum pressure.
（5）Work system pressure exceedes unloading valve pressure unloading.When work system pressure rise is to more than flow control valve 5
During the setting pressure of upper pressure-control valve 30, pressure-control valve 30 is opened, and the fluid of constant displacement pump 2 is returned by the Low-pressure load discharge of unloading valve 31
Fuel tank, only variable pump 1 are work system and steering fuel feeding.
The constant pressure stop valve of variable pump 1 sets 25MPa pressure, when work system pressure is more than 25MPa, the pump of variable pump 1
Mouth pressure makes constant pressure stop valve commutate to the left position of diagram, reduces the swash plate angle of variable pump 1, interflow is subtracted to work system flow
It is few, it is 0 L/min towards work system flow when work system pressure is more than 25MPa, if the not work of now steering gear 14
Make, then now variable pump 1 is in 25MPa high pressures, 0 L/min flow packing states.If steering gear 14 works, variable pump 1
Flow needed for output steering.
Claims (7)
1. a kind of load-sensitive formula loading machine determines variable delivery hydraulic system, includes variable pump（1）, constant displacement pump（2）, fuel tank（4）, stream
Control valve（5）, pilot valve（7）, boom cylinder（8）, rotary ink tank（9）, banked direction control valves（10）, shuttle valve block（11）, Flow amplification
Valve block（13）, small displacement steering gear (14), logic control valve（15）；Variable pump（1）By logic control valve（15）CF hydraulic fluid ports
Connection traffic amplifying valve block（13）, logic control valve（15）T1 oil return openings connection fuel tank（4）, constant displacement pump（2）By flow control
Valve processed（5）Connection banked direction control valves（10）, banked direction control valves（10）Connection rotary ink tank（9）And boom cylinder（8）, it is characterised in that：It is described
Logic control valve（15）EF hydraulic fluid ports pass through flow control valve（5）Hydraulic-control throttling valve（29）Connection banked direction control valves（10）, pilot valve
（7）By shuttle valve block（11）Logic control valve is connected respectively（15）Pilot operated directional control valve（17）KL hydraulic fluid ports and flow control valve（5）
Hydraulic-control throttling valve（29）LS8 hydraulic fluid ports；
When shuttle valve block（11）LS6 passes to flow control valve（5）Hydraulic-control throttling valve（29）The signal pressure of LS8 hydraulic fluid ports is low, liquid
Control choke valve（29）Front and rear pressure difference is higher than logic control valve（15）Pressure-compensated valve（21）When closing setting pressure, variable pump
（1）Fluid is not to flow control valve（5）Interflow only supplies steering, constant displacement pump（2）According to flow control valve（5）Hydraulic-control throttling
Valve（29）Aperture exports rotary ink tank（9）And boom cylinder（8）Required flow, excess traffic oil return box（4）；
When shuttle valve block（11）LS6 hydraulic fluid ports pass to hydraulic-control throttling valve（29）The signal pressure of LS8 hydraulic fluid ports is high, and rotary ink tank（9）
And boom cylinder（8）Required flow is more than constant displacement pump（2）Required flow, hydraulic-control throttling valve（29）Front and rear pressure difference is less than logic control
Valve（15）Pressure-compensated valve（21）When closing setting pressure, variable pump（1）To flow control valve（4）Collaborate to banked direction control valves
（10）, there is provided shortcoming flow.
2. load-sensitive formula loading machine according to claim 1 determines variable delivery hydraulic system, it is characterised in that：Described flow
Control valve（5）Including three-way pressure compensating device（26）, damping hole（27）, check valve（28）, hydraulic-control throttling valve（29）, Stress control
Valve（30）, unloading valve（31）And P6 hydraulic fluid ports, P7 hydraulic fluid ports, P8 hydraulic fluid ports, LS7 hydraulic fluid ports, LS8 hydraulic fluid ports, T4 hydraulic fluid ports；Three-way pressure is mended
Repay device（26）Import and P6 mouthfuls, unloading valve（31）, check valve（28）Import be connected, three-way pressure compensating device（26）Outlet
With unloading valve（31）Outlet, pressure-control valve（30）Outlet is connected after connecting with T4 mouthfuls；Check valve（28）Outlet is connected in P8 oil
Mouth, hydraulic-control throttling valve（29）Import, and pressure-control valve（30）Stress control mouthful；Unloading valve（31）Spring cavity connect
In pressure-control valve（30）Import；P6 hydraulic fluid ports connect constant displacement pump（2）, P7 hydraulic fluid ports connection banked direction control valves（10）, P8 hydraulic fluid ports and logic
Control valve（15）EF hydraulic fluid ports connection, LS7 hydraulic fluid ports connection logic control valve（15）LS3 hydraulic fluid ports simultaneously transmit workload signal, LS8
Hydraulic fluid port and shuttle valve block（11）LS6 hydraulic fluid ports are connected；Hydraulic-control throttling valve（29）P7 hydraulic fluid ports, P8 hydraulic fluid ports between pressure difference by three-way pressure
Compensator（26）Setting, the hydraulic-control throttling valve（29）Aperture is according to shuttle valve block（11）The pilot signal regulation of transmission, exports work
Make flow needed for system.
3. load-sensitive formula loading machine according to claim 1 determines variable delivery hydraulic system, it is characterised in that：Described logic
Control valve（15）Include fixed pressure reducing valve（16）, pilot operated directional control valve（17）, flow compensation valve（18）, pressure-compensated valve（21）、
Shuttle valve（23）, check valve（25）And P1 hydraulic fluid ports, PX hydraulic fluid ports, PSt hydraulic fluid ports, LS1 hydraulic fluid ports, LS2 hydraulic fluid ports, LS3 hydraulic fluid ports, KL hydraulic fluid ports,
CF hydraulic fluid ports, EF hydraulic fluid ports, T1 hydraulic fluid ports；The P1 hydraulic fluid ports connect CF hydraulic fluid ports, and P1 hydraulic fluid ports pass through fixed pressure reducing valve（16）PX is connected all the way
Hydraulic fluid port, another road are through check valve（25）PSt hydraulic fluid ports are connected, by pilot operated directional control valve（17）Connect flow compensation valve（18）Spring
Chamber, by flow compensation valve（18）, pressure-compensated valve（21）Connect EF hydraulic fluid ports；The LS2 hydraulic fluid ports and the LS3 hydraulic fluid ports are through shuttle
Valve（23）Selection is connected with the LS1 hydraulic fluid ports；The KL hydraulic fluid ports connect pilot operated directional control valve（17）Control end；The fixed pressure reducing valve
（16）And pilot operated directional control valve（17）Spring cavity connected with T1 hydraulic fluid ports；The LS3 hydraulic fluid ports and pressure-compensated valve（21）Spring cavity connects
It is logical；CF hydraulic fluid port preferential attachment flux amplification valve blocks（13）, P1 hydraulic fluid port link variable pumps（1）, T1 hydraulic fluid ports connection fuel tank（4）, KL oil
Mouth takes from shuttle valve block（11）Signal, EF hydraulic fluid port connection flow control valves（5）, LS3 takes from flow control valve（5）Load feedback
Mouthful, the connection steering gear of PX hydraulic fluid ports（14）, PSt hydraulic fluid ports connection pilot valve（7）；Pressure difference between EF hydraulic fluid ports and LS3 hydraulic fluid ports determines pressure
Force compensating valve（21）Aperture, control steering whether to work system collaborate and interflow flow.
4. load-sensitive formula loading machine according to claim 1 determines variable delivery hydraulic system, it is characterised in that：The shuttle valve block
（11）Including the first shuttle valve（32）, the second shuttle valve（34）, the 3rd shuttle valve（35）, two-way pilot operated valve device（33）And D1 hydraulic fluid ports, D2 oil
Mouth, C1 hydraulic fluid ports, C2 hydraulic fluid ports, LS5 hydraulic fluid ports, LS6 hydraulic fluid ports, D1 hydraulic fluid ports, D2 hydraulic fluid ports are through the first shuttle valve（32）Pass through two-way liquid after gating
Control valve（33）Connect the 3rd shuttle valve（35）Left end, C1 hydraulic fluid ports, C2 hydraulic fluid ports are through the second shuttle valve（34）The 3rd shuttle valve is connected after gating
（35）Right-hand member, the 3rd shuttle valve（35）Outlet LS5 hydraulic fluid ports, LS6 hydraulic fluid ports；Two-way pilot operated valve device（33）Control end and the second shuttle valve
（34）Outlet；LS5 hydraulic fluid ports connect logic control valve（15）KL hydraulic fluid ports, LS6 hydraulic fluid port connection flow control valves（5）LS8
Hydraulic fluid port；D1 hydraulic fluid ports, D2 hydraulic fluid ports, C1 hydraulic fluid ports, C2 hydraulic fluid ports connection pilot valve（7）Control mouth.
5. load-sensitive formula loading machine according to claim 4 determines variable delivery hydraulic system, it is characterised in that：The shuttle valve block
（11）C1 hydraulic fluid ports, C2 hydraulic fluid ports connect pilot valve respectively（7）Rotating bucket control mouth A, rotating bucket control mouth C, D1 hydraulic fluid port, D2 hydraulic fluid ports difference
Connection pilot valve（7）Swing arm control mouth B, swing arm control mouth D, C1 hydraulic fluid port/C2 hydraulic fluid ports fuel injection pressure signal promote two-way pilot operated valve device（33）
In bottom, make D1 hydraulic fluid ports/D2 hydraulic fluid port signal-off.
6. load-sensitive formula loading machine according to claim 3 determines variable delivery hydraulic system, it is characterised in that：The logic control
Valve processed（15）Also include safety valve（19）, safety valve（19）Connect P1 hydraulic fluid ports and T1 hydraulic fluid ports.
7. load-sensitive formula loading machine according to claim 1 determines variable delivery hydraulic system, it is characterised in that：The steering system
System includes flux amplification valve block（13）.
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| CN201710005638.8A CN106759621B (en) | 2017-01-04 | 2017-01-04 | Load-sensitive formula loading machine determines variable delivery hydraulic system |
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| CN201710005638.8A CN106759621B (en) | 2017-01-04 | 2017-01-04 | Load-sensitive formula loading machine determines variable delivery hydraulic system |
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| CN107269609A (en) * | 2017-07-26 | 2017-10-20 | 无锡市钻通工程机械有限公司 | Combining hydraulic system in load-sensitive valve |
| CN107339277A (en) * | 2017-08-31 | 2017-11-10 | 雷沃重工股份有限公司 | A kind of tractor load-sensitive formula banked direction control valves |
| CN107724454A (en) * | 2017-11-10 | 2018-02-23 | 广西柳工机械股份有限公司 | Loading machine determines variable delivery hydraulic system |
| CN107762995A (en) * | 2017-09-13 | 2018-03-06 | 江苏恒立液压科技有限公司 | Novel electric proportional overflow device |
| CN110259741A (en) * | 2019-06-21 | 2019-09-20 | 徐工集团工程机械股份有限公司科技分公司 | A kind of quantitatively composite control hydraulic system and engineering machinery |
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| CN110905875A (en) * | 2019-12-14 | 2020-03-24 | 洛阳智能农业装备研究院有限公司 | Double-pump combined-split load sensing hydraulic system of tractor |
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| CN111677717A (en) * | 2020-05-19 | 2020-09-18 | 江苏理工学院 | Hydraulic system of hydraulic valve test bench |
| CN113494111A (en) * | 2021-07-27 | 2021-10-12 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
| CN113669314A (en) * | 2021-08-05 | 2021-11-19 | 天津工程机械研究院有限公司 | Hydraulic system of pure electric engineering vehicle |
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| CN114215797A (en) * | 2021-11-15 | 2022-03-22 | 中船华南船舶机械有限公司 | Method for controlling flow of variable pump by hydraulic system |
| CN114658708A (en) * | 2022-04-11 | 2022-06-24 | 华侨大学 | Load rotating speed double-sensitive anti-flow saturation system and engineering mechanical device thereof |
| CN117432673A (en) * | 2023-12-13 | 2024-01-23 | 张家口宣化英诺威克凿岩机械有限公司 | Hydraulic station, action control system and method of new energy furnace disassembly machine and electronic equipment |
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| CN107269609A (en) * | 2017-07-26 | 2017-10-20 | 无锡市钻通工程机械有限公司 | Combining hydraulic system in load-sensitive valve |
| CN107269609B (en) * | 2017-07-26 | 2018-10-26 | 无锡市钻通工程机械有限公司 | Combining hydraulic system in load-sensitive valve |
| CN107339277A (en) * | 2017-08-31 | 2017-11-10 | 雷沃重工股份有限公司 | A kind of tractor load-sensitive formula banked direction control valves |
| CN107339277B (en) * | 2017-08-31 | 2024-05-14 | 潍柴雷沃智慧农业科技股份有限公司 | Tractor load sensitive type multi-way valve |
| CN107762995A (en) * | 2017-09-13 | 2018-03-06 | 江苏恒立液压科技有限公司 | Novel electric proportional overflow device |
| CN107762995B (en) * | 2017-09-13 | 2023-12-22 | 江苏恒立液压科技有限公司 | Novel electric proportion overflow device |
| CN107724454A (en) * | 2017-11-10 | 2018-02-23 | 广西柳工机械股份有限公司 | Loading machine determines variable delivery hydraulic system |
| CN110259741A (en) * | 2019-06-21 | 2019-09-20 | 徐工集团工程机械股份有限公司科技分公司 | A kind of quantitatively composite control hydraulic system and engineering machinery |
| CN110578726A (en) * | 2019-09-29 | 2019-12-17 | 徐工集团工程机械股份有限公司科技分公司 | hydraulic system with quantitative system variable |
| CN110578726B (en) * | 2019-09-29 | 2024-04-30 | 徐工集团工程机械股份有限公司科技分公司 | Quantitative system variable hydraulic system |
| CN110745182A (en) * | 2019-10-21 | 2020-02-04 | 三一汽车起重机械有限公司 | Auxiliary steering control system and crane |
| CN110953198A (en) * | 2019-11-01 | 2020-04-03 | 徽瑞智能装备（黄山）有限责任公司 | Load transfer hydraulic system and device for improving driving state of engineering machinery |
| CN110872857A (en) * | 2019-11-29 | 2020-03-10 | 徐州徐工液压件有限公司 | Multifunctional energy recovery device and hydraulic excavator system carrying same |
| CN110905875A (en) * | 2019-12-14 | 2020-03-24 | 洛阳智能农业装备研究院有限公司 | Double-pump combined-split load sensing hydraulic system of tractor |
| CN111086558A (en) * | 2019-12-26 | 2020-05-01 | 北汽福田汽车股份有限公司 | Hydraulic power-assisted steering system, control method and engineering vehicle |
| CN111255007A (en) * | 2020-03-02 | 2020-06-09 | 浙江高宇液压机电有限公司 | Loader constant-variable hydraulic system based on load signal direct control |
| CN111677717A (en) * | 2020-05-19 | 2020-09-18 | 江苏理工学院 | Hydraulic system of hydraulic valve test bench |
| CN113494111B (en) * | 2021-07-27 | 2022-08-05 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
| CN113494111A (en) * | 2021-07-27 | 2021-10-12 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
| CN113669314A (en) * | 2021-08-05 | 2021-11-19 | 天津工程机械研究院有限公司 | Hydraulic system of pure electric engineering vehicle |
| US12077225B2 (en) | 2021-10-29 | 2024-09-03 | Shanghai Sany Heavy Machinery Co., Ltd. | Hydraulic system switchable between fixed- displacement and fixed/variable-displacement, control method thereof and working machine |
| CN114215797A (en) * | 2021-11-15 | 2022-03-22 | 中船华南船舶机械有限公司 | Method for controlling flow of variable pump by hydraulic system |
| CN114215797B (en) * | 2021-11-15 | 2024-04-19 | 中船华南船舶机械有限公司 | Method for controlling flow of variable pump by hydraulic system |
| CN114109936A (en) * | 2021-11-29 | 2022-03-01 | 浙江大学 | Boom hydraulic transmission system and control method thereof |
| CN114658708A (en) * | 2022-04-11 | 2022-06-24 | 华侨大学 | Load rotating speed double-sensitive anti-flow saturation system and engineering mechanical device thereof |
| CN117432673A (en) * | 2023-12-13 | 2024-01-23 | 张家口宣化英诺威克凿岩机械有限公司 | Hydraulic station, action control system and method of new energy furnace disassembly machine and electronic equipment |
| CN117432673B (en) * | 2023-12-13 | 2024-02-23 | 张家口宣化英诺威克凿岩机械有限公司 | Hydraulic station, action control system and method of new energy furnace disassembly machine and electronic equipment |
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