CN204491709U - Loader electronic-hydraulic complex control hydraulic system - Google Patents
Loader electronic-hydraulic complex control hydraulic system Download PDFInfo
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- CN204491709U CN204491709U CN201420807335.XU CN201420807335U CN204491709U CN 204491709 U CN204491709 U CN 204491709U CN 201420807335 U CN201420807335 U CN 201420807335U CN 204491709 U CN204491709 U CN 204491709U
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Abstract
The utility model discloses a kind of loader electronic-hydraulic complex control hydraulic system, comprise hydraulic oil container (1), motor (2), variable pump (3), electric control reversing valve block (4), the 3rd shuttle valve (5), the first shuttle valve (6), the second shuttle valve (7), distributing valve (8), dump ram (9), boom cylinder (10), pilot valve (11), pilot control block (12), electric control handle (26) and controller (27); The utility model carries out complex controll stage by stage according to the actual condition of loader, ensures that loader possesses good fine motion and navigability when action at a slow speed; Energy loss can be reduced further when quick acting, and automatically can adapt to actual loading, reduce load to the impact of pump; Automatically adjust hydraulic system to export when high pressure heavy load, alleviate the impact of load to motor, ensure to start function reliablely and stablely to run.
Description
Technical field
The utility model relates to a kind of loader hydraulic system, specifically loader electronic-hydraulic complex control hydraulic system.
Background technology
Loader is a kind of purposes engineering machinery widely.Different purposes and complicated operating mode determine the complexity of its hydraulic work system.Loader hydraulic system common at present has two quantitative system, constant displacement pump and variable pump combined system, bivariate pumping system etc.Along with society is to the pay attention to day by day of energy-conserving and environment-protective, the variable system with obvious energy-saving effect is widely used in engineering machinery.Wherein, the bivariate pumping system received much concern belongs to the system of comparatively advanced variable, and its typical control methods is hydraulic control load sensing controlled, and because its control mode is simple and reliable, cost is lower, and application widely.Load sensing controlled sets up stable pressure reduction between pumping hole and load, is generally set up by the differential pressure compensator of pump.Operator carrys out control variables pumpage by the throttling size changing main valve valve port, and then the flow of control system.Typical differential pressure compensator pressure setting is 2.5MPa, and the pressure of variable pumping hole is all the time higher than load pressure 2.5MPa thus, causes in variable pump power loss when large discharge exports very large.If turn down compensation pressure, the response speed of system can be slack-off, and flow also can reduce.System pressure generally can improve in main engine plants, and reduce flow system flow and reduce the system power loss compensating pressure and cause, but simple raising system pressure also causes the element cost increase of whole hydraulic system, fault rate raises.
In existing Load sensing system, general arranges pressure shut-off valve at pumping hole, is only after pump intake pressure exceedes cut-out pressure, make the swash plate of pump return row, engine torque and pump shaft moment of torsion is not compared.If motor is in lower-speed state, operator operates machine quick acting, and now pump delivery can reach maximum, if when now load pressure is also high, pump shaft moment of torsion is close to engine torque, then motor is probably suppressed flame-out.If now also have the teamworks such as incision stockpile, then the possibility of engine misses is larger.
Summary of the invention
For above-mentioned prior art Problems existing, the utility model provides loader electronic-hydraulic complex control hydraulic system, and the actual condition according to loader carries out complex controll stage by stage, ensures that loader possesses good fine motion and navigability when action at a slow speed; Energy loss can be reduced further when quick acting, and automatically can adapt to actual loading, reduce load to the impact of pump; Automatically adjust hydraulic system to export when high pressure heavy load, alleviate the impact of load to motor, ensure to start function reliablely and stablely to run.
To achieve these goals, a kind of loader electronic-hydraulic complex control of the utility model hydraulic system, comprises hydraulic oil container, motor, variable pump, electric control reversing valve block, the 3rd shuttle valve, the first shuttle valve, the second shuttle valve, distributing valve, dump ram, boom cylinder, pilot valve, pilot control block, electric control handle and controller; The oil-in of variable pump is connected with hydraulic oil container; The oil-out P of variable pump is connected with the oil inlet P 1 of distributing valve; Distributing valve oil return inlet T 1 is connected with hydraulic oil container; The oil inlet P 2 of pilot control block is connected with the oil-out P of variable pump; The oil-out U of pilot control block is connected with the oil inlet P 3 of pilot valve; Decline hydraulic fluid port ps and the pilot valve of distributing valve decline and join hydraulic fluid port A and be connected; The receipts bucket connection hydraulic fluid port pss of distributing valve and pilot valve are received to struggle against and are joined hydraulic fluid port B and be connected; Lifting hydraulic fluid port pl and the pilot valve of distributing valve promote and join hydraulic fluid port C and be connected; Decline hydraulic fluid port psl and the pilot valve tipping bucket of distributing valve join hydraulic fluid port D and are connected; The tipping bucket cylinder large chamber hydraulic fluid port A7 of distributing valve is connected with the rodless cavity A9 of tipping bucket cylinder; The tipping bucket cylinder loculus hydraulic fluid port B7 of distributing valve is connected with the rod chamber B9 of tipping bucket cylinder; The swing arm cylinder large chamber hydraulic fluid port A8 of distributing valve is connected with the rodless cavity A10 of swing arm cylinder; The swing arm cylinder loculus hydraulic fluid port B8 of distributing valve is connected with the rodless cavity B10 of swing arm cylinder; The load sensing hydraulic fluid port LS1 of distributing valve is connected with the 3rd hydraulic fluid port H3 of electric control reversing valve block; The m3 hydraulic fluid port of the 3rd shuttle valve is connected with electric control reversing valve block H1 hydraulic fluid port; The s3 hydraulic fluid port of the 3rd shuttle valve is connected with the first shuttle valve m1 hydraulic fluid port; The s1 hydraulic fluid port of the first shuttle valve is connected with the decline hydraulic fluid port ps of distributing valve; The n1 hydraulic fluid port of the first shuttle valve joins hydraulic fluid port pss with the receipts bucket of distributing valve and is connected; The s2 hydraulic fluid port of the second shuttle valve is connected with the lifting hydraulic fluid port pl of distributing valve; The n2 hydraulic fluid port of the second shuttle valve is connected with the decline hydraulic fluid port psl of distributing valve; The m2 hydraulic fluid port of the second shuttle valve is connected with the n3 hydraulic fluid port of the 3rd shuttle valve; The H2 hydraulic fluid port of electric control reversing valve block is connected with the K4 hydraulic fluid port of variable pump; The H4 hydraulic fluid port of electric control reversing valve block is connected with hydraulic oil container; The H5 hydraulic fluid port of electric control reversing valve block is connected with the K2 hydraulic fluid port of variable pump; The H6 hydraulic fluid port of electric control reversing valve block is connected with the K3 hydraulic fluid port of variable pump; The H8 hydraulic fluid port of electric control reversing valve block is connected with the LS hydraulic fluid port of variable pump; The delivery outlet X1 of electric control handle is connected with the first input port X2 of controller; Speed probe is connected with motor; Speed probe is connected with the second input port X3 of controller; First delivery outlet X4 of controller is connected with automatically controlled electric control reversing valve block block input port X7; Second delivery outlet X5 of controller is connected with the input port X6 of pilot valve, described dump ram and described boom cylinder respectively with join valve and be connected.
Further, described variable pump comprises pump, overflow valve, flow control valve, pressure shut-off valve and change oil extraction cylinder; The hydraulic fluid port P4 of flow control valve is connected with the oil-out P of pump; Variable pump K1 hydraulic fluid port is connected with the control chamber A1 of flow control valve; Variable pump K2 hydraulic fluid port is connected with the control chamber A2 of flow control valve; Variable pump K3 hydraulic fluid port is connected with the control chamber A3 of flow control valve; Variable pump LS hydraulic fluid port is connected with the spring cavity of flow control valve; The H3 hydraulic fluid port of electric control reversing valve block is connected with the oil suction chamber of overflow valve; The oil return inlet T 8 of overflow valve is connected with the rodless cavity hydraulic fluid port K8 becoming oil extraction cylinder; The pressure spring A6 of overflow valve is connected with the piston rod A5 becoming oil extraction cylinder; The piston rod A5 becoming oil extraction cylinder is connected with the Bian Pai mechanism of pump; The rodless cavity K8 becoming oil extraction cylinder is connected with the K7 hydraulic fluid port of pressure shut-off valve; The A4 hydraulic fluid port of pressure shut-off valve, the P6 hydraulic fluid port of pressure shut-off valve are connected with the oil-out P of pump; The K6 hydraulic fluid port of pressure shut-off valve is connected with the K5 hydraulic fluid port of flow control valve; The leakage hydraulic fluid port T7 of pump, the leakage hydraulic fluid port T6, the leakage hydraulic fluid port T5 of pressure shut-off valve that become oil extraction cylinder, the leakage hydraulic fluid port T4 of flow control valve are connected with the leakage hydraulic fluid port L3 of variable pump.
Further, described flow control valve comprises valve seat, closes mother, the second spool, the first spool, valve body and pressure spring, and the first spool is assembled to valve body by pressure spring, and the second spool is connected with the second spool and is assemblied in valve body; Valve seat is connected with valve body by screw thread; Close mother to be connected with valve seat by screw thread;
Further, be provided with an O type circle between described valve seat and valve body to seal; Be provided with the 2nd O type circle between valve seat and the second spool to seal.
Compared with prior art, the utility model has the advantages that:
(1) have employed Staged composite control, according to the different duty requirements of loader, by the control mode of electric control handle and controller automatic adjustment system, and then meet the control overflow of various operating mode, hydraulic system does not adopt single control mode, and therefore the compliance of system is stronger.
(2) (electric control handle output voltage is lower in slow speed operation region for this system, pilot pressure corresponding is with it also lower), system output stream amount is less, has all advantages of load sensing controlled, has good fretting performance and operability; Fast operating region (electric control handle output voltage is higher, when pilot pressure is higher), system output stream amount rises rapidly, and main valve restriction loss reduces gradually, and in this region, the energy-saving effect of system is obvious.
(3) this system has adapted to the operating mode of loader admirably, and the maneuvering area working time is very short at a slow speed, and flow system flow is less, therefore energy loss is little; The loader major part working time is in fast operating region, and flow system flow is larger, and energy-saving effect is more obvious.
(4) when manipulation electric control handle, make pilot pressure high to certain value time, variable pump switches to Isobarically Control; If pump intake pressure is lower, pump can export by delivery, and when the pressure of pumping hole reaches the controlled pressure of flow control valve setting, pump delivery reduces immediately, and therefore system does not have high pressure kicks to lose.Operator is when sharp work, and pump can adapt to load automatically, and high pressure kicks can be avoided to lose.
(5) variable pump has permanent moment of torsion control control characteristic in high-pressure area, and when guaranteeing that outer load is excessive, pump shaft moment of torsion can not exceed predetermined value, ensures that motor normally runs.
(6) this system integration degree is high, and components and parts are easily processed, and systemic-function is easy to realize.
(7) adopt multi-media Integrate Intelligent Control, eliminate the system energy consumption problems of too that human factor causes, reach energy-conservation object.
Accompanying drawing explanation
Fig. 1 is the utility model electronic-hydraulic complex control hydraulic system principle figure;
Fig. 2 is the structure chart of the utility model variable pump;
Fig. 3 is the structure chart of flow control valve;
Fig. 4 is electric control handle output signal curve figure;
Fig. 5 is pilot valve output pressure change curve in time;
Fig. 6 is that valve core of main valve displacement is with pilot valve output pressure change curve;
Fig. 7 is that valve core of main valve choke area is with pilot pressure change curve;
Fig. 8 is that the control mode of variable pump and discharge capacity are with pilot pressure, pump intake pressure change curve;
Fig. 9 is that the flow of variable pump output is with pilot pressure change curve;
Figure 10 be pump intake pressure lower than 20MPa time, pump delivery is with pilot pressure change curve;
Figure 11 is the variation relation curve map of maximum pump discharge with pump intake pressure of pump;
Figure 12 is the change curve of difference with pilot pressure of pump intake pressure and load pressure;
Figure 13 is the homologous thread figure of the multiplex control system main valve pressure loss and flow system flow;
In figure: 1 hydraulic oil container, 2 motors, 3 variable pumps, 4 electric control reversing valve blocks, 5 the 3rd shuttle valves, 6 first shuttle valves, 7 second shuttle valves, 8 distributing valves, 9 dump rams, 10 boom cylinders, 11 pilot valves, 12 pilot control blocks, 13 pumps, 14 overflow valves, 15 flow control valves, 16 pressure shut-off valves, 17 become oil extraction cylinder, 18 valve seats, and 19 close mother, 20 the one O type circles, 21 the 2nd O type circles, 22 second spools, 23 first spools, 24 valve bodies, 25 pressure springs, 26 electric control handles, 27 controllers.
Detailed description of the invention
In order to make those skilled in the art person understand the utility model scheme better, below in conjunction with the drawings and specific embodiments, the utility model is described in further detail.
As shown in Figure 1, the utility model loader electronic-hydraulic complex control hydraulic system, comprises hydraulic oil container 1, motor 2, variable pump 3, electric control reversing valve block 4, the 3rd shuttle valve 5, first shuttle valve 6, second shuttle valve 7, distributing valve 8, dump ram 9, boom cylinder 10, pilot valve 11, pilot control block 12, electric control handle 26 and controller 27; The oil-in of variable pump 3 is connected with hydraulic oil container 1; The oil-out P of variable pump 3 is connected with the oil inlet P 1 of distributing valve 8; Distributing valve 8 oil return inlet T 1 is connected with hydraulic oil container 1; The oil inlet P 2 of pilot control block 12 is connected with the oil-out P of variable pump 3; The oil-out U of pilot control block 12 is connected with the oil inlet P 3 of pilot valve 11; Decline hydraulic fluid port ps and the pilot valve 11 of distributing valve 8 decline and join hydraulic fluid port A and be connected; The receipts bucket connection hydraulic fluid port pss of distributing valve 8 and pilot valve 11 are received to struggle against and are joined hydraulic fluid port B and be connected; Lifting hydraulic fluid port pl and the pilot valve 11 of distributing valve 8 promote and join hydraulic fluid port C and be connected; The decline hydraulic fluid port psl of distributing valve 8 joins hydraulic fluid port D with pilot valve 11 tipping bucket and is connected; The tipping bucket cylinder large chamber hydraulic fluid port A7 of distributing valve 8 is connected with the rodless cavity A9 of tipping bucket cylinder 9; The tipping bucket cylinder loculus hydraulic fluid port B7 of distributing valve 8 is connected with the rod chamber B9 of tipping bucket cylinder 9; The swing arm cylinder large chamber hydraulic fluid port A8 of distributing valve 8 is connected with the rodless cavity A10 of swing arm cylinder 10; The swing arm cylinder loculus hydraulic fluid port B8 of distributing valve 8 is connected with the rodless cavity B10 of swing arm cylinder 10; The load sensing hydraulic fluid port LS1 of distributing valve 8 is connected with the 3rd hydraulic fluid port H3 of electric control reversing valve block 4; The m3 hydraulic fluid port of the 3rd shuttle valve 5 is connected with electric control reversing valve block 4H1 hydraulic fluid port; The s3 hydraulic fluid port of the 3rd shuttle valve 5 is connected with the first shuttle valve 6m1 hydraulic fluid port; The s1 hydraulic fluid port of the first shuttle valve 6 is connected with the decline hydraulic fluid port ps of distributing valve 8; The n1 hydraulic fluid port of the first shuttle valve 6 joins hydraulic fluid port pss with the receipts bucket of distributing valve 8 and is connected; The s2 hydraulic fluid port of the second shuttle valve 7 is connected with the lifting hydraulic fluid port pl of distributing valve 8; The n2 hydraulic fluid port of the second shuttle valve 7 is connected with the decline hydraulic fluid port psl of distributing valve 8; The m2 hydraulic fluid port of the second shuttle valve 7 is connected with the n3 hydraulic fluid port of the 3rd shuttle valve 5; The H2 hydraulic fluid port of electric control reversing valve block 4 is connected with the K4 hydraulic fluid port of variable pump 3; The H4 hydraulic fluid port of electric control reversing valve block 4 is connected with hydraulic oil container 1; The H5 hydraulic fluid port of electric control reversing valve block 4 is connected with the K2 hydraulic fluid port of variable pump 3; The H6 hydraulic fluid port of electric control reversing valve block 4 is connected with the K3 hydraulic fluid port of variable pump 3; The H8 hydraulic fluid port of electric control reversing valve block 4 is connected with the LS hydraulic fluid port of variable pump 3; The delivery outlet X1 of electric control handle 26 is connected with the first input port X2 of controller 27; Speed probe 28 is connected with motor 2; Speed probe 28 is connected with the second input port X3 of controller 27; First delivery outlet X4 of controller 27 is connected with automatically controlled electric control reversing valve block block 4 input port X7; Second delivery outlet X5 of controller 27 is connected with the input port X6 of pilot valve 11, dump ram 9 and described boom cylinder 10 respectively with join valve 8 and be connected.
As shown in Figure 2, as a kind of scheme of the present utility model, variable pump 3 comprises pump 13, overflow valve 14, flow control valve 15, pressure shut-off valve 16 and becomes oil extraction cylinder 17; The hydraulic fluid port P4 of flow control valve 15 is connected with the oil-out P of pump 13; Variable pump 3K1 hydraulic fluid port is connected with the control chamber A1 of flow control valve 15; Variable pump 3K2 hydraulic fluid port is connected with the control chamber A2 of flow control valve 15; Variable pump 3K3 hydraulic fluid port is connected with the control chamber A3 of flow control valve 15; Variable pump 3LS hydraulic fluid port is connected with the spring cavity of flow control valve 15; The H3 hydraulic fluid port of electric control reversing valve block 4 is connected with the oil suction chamber of overflow valve 14; The oil return inlet T 8 of overflow valve 14 is connected with the rodless cavity hydraulic fluid port K8 becoming oil extraction cylinder 17; The pressure spring A6 of overflow valve 14 is connected with the piston rod A5 becoming oil extraction cylinder 17; The piston rod A5 becoming oil extraction cylinder 17 is connected with the Bian Pai mechanism of pump 13; The rodless cavity K8 becoming oil extraction cylinder 17 is connected with the K7 hydraulic fluid port of pressure shut-off valve 16; The A4 hydraulic fluid port of pressure shut-off valve 16, the P6 hydraulic fluid port of pressure shut-off valve 16 are connected with the oil-out P of pump 13; The K6 hydraulic fluid port of pressure shut-off valve 16 is connected with the K5 hydraulic fluid port of flow control valve 15; The leakage hydraulic fluid port T7 of pump 13, the leakage hydraulic fluid port T6, the leakage hydraulic fluid port T5 of pressure shut-off valve 16 that become oil extraction cylinder 17, the leakage hydraulic fluid port T4 of flow control valve 15 are connected with the leakage hydraulic fluid port L3 of variable pump 3.
As shown in Figure 3, as a kind of scheme of the present utility model, flow control valve 15 comprises valve seat 18, closes female 19, second spool 22, first spool 23, valve body 24 and pressure spring 25, first spool 23 is assembled to valve body 24 by pressure spring 25, and the second spool 22 is connected with the second spool 23 and is assemblied in valve body 24; Valve seat 18 is connected with valve body 24 by screw thread; Close female 19 to be connected with valve seat 18 by screw thread.
On said structure basis, between valve seat 18 and valve body 24, be provided with an O type circle 20; The 2nd O type circle 21 is provided with between valve seat 18 and the second spool 22.Two O type circles, as seal, play sealing function.
Provide the control method utilizing above-mentioned loader electronic-hydraulic complex control hydraulic system below, step is as follows:
A. electric control handle 26 output voltage signal is to controller 27, transformed by controller 27 and output signal to electric-hydraulic proportion pilot valve 11 after amplifying, the pilot pressure that electric-hydraulic proportion pilot valve 11 exports controls distributing valve 8 spool displacement, controls the operating position of electric control reversing valve block 4 simultaneously;
Suppose that operator at the uniform velocity handles electric control handle 26 to maximum opening, then the signal of telecommunication Xa=Cd*t+Ce of electric control handle output; In formula: Cd is the slope of electric control handle 26 curve of output, Ce is constant, the functional value that namely electric control handle 26 curve of output is corresponding with the intersection point of Y-axis.
Output signal Xb=Cf*t+Cg after amplifier 27 processes; In formula: Cf is the slope of amplifier 27 curve of output, Ce is constant, the functional value that namely amplifier 27 curve of output is corresponding with the intersection point of Y-axis; The pilot pressure Px that electric-hydraulic proportion pilot valve 11 exports in time t variation relation is Px=Ka*t+Kb, in formula: Ka is pilot pressure Px slope of a curve, and Kb is constant, the functional value that namely pilot pressure Px curve is corresponding with the intersection point of Y-axis; Then the pass of distributing valve 8 spool displacement Sx and pilot pressure Px is Sx=Kc*Px+Kd, in formula: Kc is distributing valve spool displacement Sx slope of a curve, and Kd is constant, the functional value that namely distributing valve spool displacement Sx curve is corresponding with the intersection point of Y-axis;
After distributing valve 8 spool moves, its valve port choke area Sf changes and the pass of pilot pressure Px is
Ke is first paragraph slope of a curve in choke area Sf curve, and Kf is constant, the functional value that namely in Sf curve, first paragraph curve is corresponding with the intersection point of Y-axis; Ku is second segment slope of a curve in choke area Sf curve, and Kv is constant, the functional value that namely in Sf curve, second segment curve is corresponding with the intersection point of Y-axis; Kw is the 3rd section of slope of a curve in choke area Sf curve, and Kx is constant, i.e. the 3rd section of functional value that curve is corresponding with the intersection point of Y-axis in Sf curve; Ky is constant, i.e. the functional value of the 4th section of curve in Sf curve.
B. along with the change of electric control handle 26 output voltage signal, the functional relation that the control mode of variable pump 3 and discharge capacity Vp change with pilot pressure Px, pump intake pressure Pp is as following table:
Kg is first paragraph slope of a curve in the discharge capacity Vp curve of variable pump 3, and Kh is constant, the functional value that namely in discharge capacity Vp curve, first paragraph curve is corresponding with the intersection point of Y-axis; Ki is second segment slope of a curve in the discharge capacity Vp curve of variable pump 3, and Kj is constant, the functional value that namely in discharge capacity Vp curve, second segment curve is corresponding with the intersection point of Y-axis; Km is the 3rd section of slope of a curve in the discharge capacity Vp curve of variable pump 3, and Kn is constant, i.e. the 3rd section of functional value that curve is corresponding with the intersection point of Y-axis in discharge capacity Vp curve; Ko is constant, i.e. the functional value of the 4th section of curve in discharge capacity Vp curve.
When pilot pressure is lower than F point corresponding pressure, namely during Px≤12, now electric control reversing valve block 4 is failure to actuate, and is in leftmost bit, and variable pump 3 adopts load sensing controlled, now valve port choke area Sf=Ke*Px+Kf, pump delivery Vp=Kg*Px+Kh;
C. when pilot pressure is elevated to the process of G point from F point, namely in 12 < Px≤18, electric control reversing valve block 4 is moved to the left one from leftmost bit, variable pump 3 is still in load sensing controlled region, now along with pump intake pressure raises, the product of pump delivery Vp and pump intake pressure Pp reaches the steady state value Kp of setting, now Vp*Pp=Kp, and variable pump 3 is in load sensing and permanent moment of torsion controls the stage; Kp is for ensureing the constant relevant to maximum engine torque that motor is not flame-out.
D. when pilot pressure Px is elevated to the process of G point from F point, distributing valve choke area Sf=Ku*Px+Kv increases sharply; After electric control reversing valve block 4 is moved to the left one from leftmost bit simultaneously, the pressure oil that pilot valve 11 exports will enter into the A2 control chamber of flow control valve, reduce the compensation pressure of flow control valve 15, the difference △ P of pump intake pressure Pp and load pressure Lp changes with pilot pressure Px, and its variation relation is:
Wherein, Kq is constant, i.e. the functional value of △ P curve during Px≤12; △ P slope of a curve when Kr is 12 < Px≤18, Ks is the functional value of the intersection point of △ P curve second segment curve and Y-axis.Kt is constant, the functional value namely during △ P curve the 3rd section of Px > 18.
The two acting in conjunction, makes pump delivery Vp change according to Vp=Ki*Px+Kj; Assuming that when engine speed Nf is constant, the output flow Qa of system with pilot pressure Px variation relation is: Qa=Nf* (Ki*Px+Kj);
E. along with electric control handle 26 output voltage raises gradually, pilot pressure Px also raises further, distributing valve choke area Sf=Kw*Px+Kx, now electric control reversing valve block 4 moves to rightmost position, flow control valve control chamber A1, A2 communicate with hydraulic oil container, control chamber A3 is connected with shuttle valve m3 hydraulic fluid port, and pump intake pressure oil enters into control chamber A3, and the control mode switching of pump is that constant pressure and constant moment of torsion controls; The pressure of pumping hole lower than setting value Ppmax and Vp*Pp<Kp time, pump exports with maximum pump discharge;
F. when electric control handle 26 output voltage is higher than certain setting value, and the load pressure of pumping hole higher than setting value time, pump delivery Vpmax can decline rapidly, the maximum pump discharge of pump control with the pass of pump intake pressure Pp be:
Wherein, Kp is for ensureing the constant relevant to maximum engine torque that motor is not flame-out.Ca is constant, i.e. the functional value of the first paragraph curve of Vpmax curve; Cc is constant, the absolute value of the 3rd section of slope of a curve of Vpmax curve, and Cb is constant, i.e. the 3rd section of functional value that curve is corresponding with Y-axis intersection point of Vpmax curve.
G. when the rotating speed of motor 2 is input in controller 27 by speed probe 28, when the load of motor 2 is excessive, its rotating speed reduces, when its rotating speed decrease speed exceeds setting value or rotating speed lower than setting value time, controller 27 exports control signal to electric control reversing valve block 4, export control signal to electric-hydraulic proportion pilot valve 11 by its second delivery outlet X4 by its first delivery outlet X3, and the common hydraulic system power that reduces exports.
The utility model control method and operating principle are described below by reference to the accompanying drawings:
When handling electric control handle, handle exports the signal of telecommunication, suppose that operator at the uniform velocity handles electric control handle to maximum opening, and just starting in a period of time, handle angle changes very little, therefore does not have the signal of telecommunication to export, and its curve of output as shown in Figure 4.
After the signal of telecommunication via controller process that electric control handle exports, control pilot valve by the second delivery outlet on the one hand, export pilot pressure oil; Pilot pressure oil enters the control chamber of distributing valve on the one hand, on the other hand by the H2 hydraulic fluid port of the first shuttle valve, the second shuttle valve, the 3rd shuttle valve arrival electric control reversing valve block; The change of the signal of telecommunication exported along with electric control handle, its output pressure change curve presses Fig. 5 change;
The pressure that the spool of distributing valve exports along with pilot valve changes, and spool displacement change is as Fig. 6;
After spool position moves, valve core of main valve choke area with pilot pressure change curve as shown in Figure 7;
Because variable pump adopts complex controll, the increase of the signal of telecommunication exported along with electric control handle, electric control reversing valve block connects by switching oil circuit the control mode changing pump, and the control mode curve of variable pump is as Fig. 8;
If when now engine speed remains unchanged, then the flow of variable pump output with pilot pressure change curve as shown in Figure 9;
As shown in Figure 9, the increase of the signal of telecommunication exported along with electric control handle, the pilot pressure that pilot valve exports raises gradually, and the control mode of variable pump is also gradually changing, and when pump intake pressure is lower than 20MPa, pump delivery is with pilot pressure change curve as shown in Figure 10;
When the pressure of pumping hole rises gradually, and pump delivery is when increasing gradually, the set pressure of overflow valve reduces gradually under the effect becoming oil extraction cylinder piston rod A5, until when the torque value that this product of the product of pump delivery and pump intake pressure is pump shaft reaches setting value, pump delivery can reduce gradually, ensure that the moment of torsion of pump is in setting range, thus ensure engine stabilizer reliably working, unlikely suppress flame-out.When the pressure of pumping hole is higher than constant voltage value 20MPa, pump delivery can reduce rapidly, and pump intake pressure is higher, and pump delivery is less.The maximum pump discharge of pump is shown in Figure 11 with the variation relation curve of pump intake pressure;
By controlling distributing valve and variable pump simultaneously, the difference finally matching pump intake pressure and load pressure is shown in Figure 12 with the change curve of pilot pressure;
Compared with original load sensing controlled system, multiplex control system effectively can reduce the energy loss of system when rapid operation, and the homologous thread of the multiplex control system main valve pressure loss and flow system flow is shown in Figure 10.Namely the trapezoid area area that in Figure 13, XYZV 4 determines is the interval that multiplex control system can be energy-conservation compared with traditional Load sensing system.Flow system flow is larger, and the power that can save is larger, at V point by original power loss 2.5MPa*360L/min/60=15kW, is reduced to 0.9MPa*360L/min/60=5.4kW, saves the power of 9.6kW; At Z point, original power loss 2.5MPa*400L/min/60=16.67kW, is reduced to 0.9MPa*400L/min/60=6.0kW, saves the power of 10.67kW.
Claims (4)
1. a loader electronic-hydraulic complex control hydraulic system, it is characterized in that, comprise hydraulic oil container (1), motor (2), variable pump (3), electric control reversing valve block (4), the 3rd shuttle valve (5), the first shuttle valve (6), the second shuttle valve (7), distributing valve (8), dump ram (9), boom cylinder (10), pilot valve (11), pilot control block (12), electric control handle (26) and controller (27); The oil-in of variable pump (3) is connected with hydraulic oil container (1); The oil-out P of variable pump (3) is connected with the oil inlet P 1 of distributing valve (8); Distributing valve (8) oil return inlet T 1 is connected with hydraulic oil container (1); The oil inlet P 2 of pilot control block (12) is connected with the oil-out P of variable pump (3); The oil-out U of pilot control block (12) is connected with the oil inlet P 3 of pilot valve (11); Decline hydraulic fluid port ps and the pilot valve (11) of distributing valve (8) decline and join hydraulic fluid port A and be connected; The receipts bucket connection hydraulic fluid port pss of distributing valve (8) and pilot valve (11) are received to struggle against and are joined hydraulic fluid port B and be connected; Lifting hydraulic fluid port pl and the pilot valve (11) of distributing valve (8) promote and join hydraulic fluid port C and be connected; The decline hydraulic fluid port psl of distributing valve (8) joins hydraulic fluid port D with pilot valve (11) tipping bucket and is connected; The tipping bucket cylinder large chamber hydraulic fluid port A7 of distributing valve (8) is connected with the rodless cavity A9 of tipping bucket cylinder (9); The tipping bucket cylinder loculus hydraulic fluid port B7 of distributing valve (8) is connected with the rod chamber B9 of tipping bucket cylinder (9); The swing arm cylinder large chamber hydraulic fluid port A8 of distributing valve (8) is connected with the rodless cavity A10 of swing arm cylinder (10); The swing arm cylinder loculus hydraulic fluid port B8 of distributing valve (8) is connected with the rodless cavity B10 of swing arm cylinder (10); The load sensing hydraulic fluid port LS1 of distributing valve (8) is connected with the 3rd hydraulic fluid port H3 of electric control reversing valve block (4); The m3 hydraulic fluid port of the 3rd shuttle valve (5) is connected with electric control reversing valve block (4) H1 hydraulic fluid port; The s3 hydraulic fluid port of the 3rd shuttle valve (5) is connected with the first shuttle valve (6) m1 hydraulic fluid port; The s1 hydraulic fluid port of the first shuttle valve (6) is connected with the decline hydraulic fluid port ps of distributing valve (8); The n1 hydraulic fluid port of the first shuttle valve (6) joins hydraulic fluid port pss with the receipts bucket of distributing valve (8) and is connected; The s2 hydraulic fluid port of the second shuttle valve (7) is connected with the lifting hydraulic fluid port pl of distributing valve (8); The n2 hydraulic fluid port of the second shuttle valve (7) is connected with the decline hydraulic fluid port psl of distributing valve (8); The m2 hydraulic fluid port of the second shuttle valve (7) is connected with the n3 hydraulic fluid port of the 3rd shuttle valve (5); The H2 hydraulic fluid port of electric control reversing valve block (4) is connected with the K4 hydraulic fluid port of variable pump (3); The H4 hydraulic fluid port of electric control reversing valve block (4) is connected with hydraulic oil container (1); The H5 hydraulic fluid port of electric control reversing valve block (4) is connected with the K2 hydraulic fluid port of variable pump (3); The H6 hydraulic fluid port of electric control reversing valve block (4) is connected with the K3 hydraulic fluid port of variable pump (3); The H8 hydraulic fluid port of electric control reversing valve block (4) is connected with the LS hydraulic fluid port of variable pump (3); The delivery outlet X1 of electric control handle (26) is connected with the first input port X2 of controller (27); Speed probe (28) is connected with motor (2); Speed probe (28) is connected with the second input port X3 of controller (27); First delivery outlet X4 of controller (27) is connected with automatically controlled electric control reversing valve block block (4) input port X7; Second delivery outlet X5 of controller (27) is connected with the input port X6 of pilot valve (11), described dump ram (9) and described boom cylinder (10) respectively with join valve (8) and be connected.
2. a kind of loader electronic-hydraulic complex control hydraulic system according to claim 1, it is characterized in that, described variable pump (3) comprises pump (13), overflow valve (14), flow control valve (15), pressure shut-off valve (16) and becomes oil extraction cylinder (17); The hydraulic fluid port P4 of flow control valve (15) is connected with the oil-out P of pump (13); Variable pump (3) K1 hydraulic fluid port is connected with the control chamber A1 of flow control valve (15); Variable pump (3) K2 hydraulic fluid port is connected with the control chamber A2 of flow control valve (15); Variable pump (3) K3 hydraulic fluid port is connected with the control chamber A3 of flow control valve (15); Variable pump (3) LS hydraulic fluid port is connected with the spring cavity of flow control valve (15); The H3 hydraulic fluid port of electric control reversing valve block (4) is connected with the oil suction chamber of overflow valve (14); The oil return inlet T 8 of overflow valve (14) is connected with the rodless cavity hydraulic fluid port K8 becoming oil extraction cylinder (17); The pressure spring A6 of overflow valve (14) is connected with the piston rod A5 becoming oil extraction cylinder (17); The piston rod A5 becoming oil extraction cylinder (17) is connected with the Bian Pai mechanism of pump (13); The rodless cavity K8 becoming oil extraction cylinder (17) is connected with the K7 hydraulic fluid port of pressure shut-off valve (16); The A4 hydraulic fluid port of pressure shut-off valve (16), the P6 hydraulic fluid port of pressure shut-off valve (16) are connected with the oil-out P of pump (13); The K6 hydraulic fluid port of pressure shut-off valve (16) is connected with the K5 hydraulic fluid port of flow control valve (15); The leakage hydraulic fluid port T7 of pump (13), the leakage hydraulic fluid port T6, the leakage hydraulic fluid port T5 of pressure shut-off valve (16) that become oil extraction cylinder (17), the leakage hydraulic fluid port T4 of flow control valve (15) are connected with the leakage hydraulic fluid port L3 of variable pump (3).
3. a kind of loader electronic-hydraulic complex control hydraulic system according to claim 2, it is characterized in that, described flow control valve (15) comprises valve seat (18), closes mother (19), the second spool (22), the first spool (23), valve body (24) and pressure spring (25), first spool (23) is assembled to valve body (24) by pressure spring (25), and the second spool (22) is connected with the second spool (23) and is assemblied in valve body (24); Valve seat (18) is connected with valve body (24) by screw thread; Close mother (19) to be connected with valve seat (18) by screw thread.
4. a kind of loader electronic-hydraulic complex control hydraulic system according to claim 3, is characterized in that, is provided with an O type circle (20) between described valve seat (18) and valve body (24); The 2nd O type circle (21) is provided with between valve seat (18) and the second spool (22).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201420807335.XU CN204491709U (en) | 2014-12-17 | 2014-12-17 | Loader electronic-hydraulic complex control hydraulic system |
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| CN201420807335.XU CN204491709U (en) | 2014-12-17 | 2014-12-17 | Loader electronic-hydraulic complex control hydraulic system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104652523A (en) * | 2014-12-17 | 2015-05-27 | 徐工集团工程机械股份有限公司科技分公司 | Electro-hydraulic compound control hydraulic system of loader and control method thereof |
| CN112805439A (en) * | 2018-10-02 | 2021-05-14 | 克拉克设备公司 | Distributed hydraulic system |
-
2014
- 2014-12-17 CN CN201420807335.XU patent/CN204491709U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104652523A (en) * | 2014-12-17 | 2015-05-27 | 徐工集团工程机械股份有限公司科技分公司 | Electro-hydraulic compound control hydraulic system of loader and control method thereof |
| CN104652523B (en) * | 2014-12-17 | 2018-02-16 | 徐工集团工程机械股份有限公司科技分公司 | A kind of loading machine electronic-hydraulic complex control hydraulic system and its control method |
| CN112805439A (en) * | 2018-10-02 | 2021-05-14 | 克拉克设备公司 | Distributed hydraulic system |
| CN112805439B (en) * | 2018-10-02 | 2023-04-21 | 克拉克设备公司 | Power machine |
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