CN104153419B - Power control valve and loading machine are determined variable delivery hydraulic system - Google Patents
Power control valve and loading machine are determined variable delivery hydraulic system Download PDFInfo
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- CN104153419B CN104153419B CN201410349567.XA CN201410349567A CN104153419B CN 104153419 B CN104153419 B CN 104153419B CN 201410349567 A CN201410349567 A CN 201410349567A CN 104153419 B CN104153419 B CN 104153419B
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Abstract
The present invention relates to loading machine and determine variable delivery hydraulic system, determine the large shortcoming of variable pump input power accounting in variable delivery hydraulic system for solving existing loading machine, the open power control valve of the present invention, in valve body, the first chamber and PLS mouth are communicated with and act on the right-hand member of main valve plug, the left end of main valve plug is established valve core spring, valve pocket is set on main valve plug, the second chamber is communicated with P1 mouth and acts on valve pocket right-hand member, the 3rd chamber and P mouth are communicated with and act on the left end of valve pocket, valve pocket spring provides elastic force left to valve pocket, main valve plug and valve pocket are provided with the draining passage that is communicated with the 3rd chamber and T mouth, draining passage conducting in the time that the relative valve pocket of main valve plug is moved to the left, in the time that the relative main valve plug of valve pocket is moved to the left, draining passage reduces or closes. valve pocket and main valve plug composition follower in the present invention, realizes this power control valve and determine variable delivery hydraulic system at loading machine the input power of variable pump is controlled, and avoids power to input accounting excessive.
Description
Technical field
The present invention relates to a kind of loader hydraulic system, relate in particular to the power control valve that a kind of loading machine determines to use in variable delivery hydraulic system and the loading machine with this power control valve and determine variable delivery hydraulic system.
Background technology
At present, conventional loader hydraulic system comprises fixed dilivery hydraulic system, determines variable delivery hydraulic system and entire variable hydraulic system. Each hydraulic system technical characterstic is as follows:
The restriction loss of fixed dilivery hydraulic system, spill losses, linear loss constant power lose greatly, energy conversion efficiency is lower, but system forms simply, cost is lower;
Entire variable hydraulic system is without spill losses, and restriction loss and linear loss minimum, energy conversion efficiency is high, energy-saving effect is better, but Hydraulic Elements are expensive, dependence on import, maintenance maintenance cost are high;
Determine variable delivery hydraulic system and have the features such as cost is moderate, energy-saving effect is better, energy conversion efficiency is between fixed dilivery hydraulic system and entire variable hydraulic system;
The energy-saving and cost-reducing development trend that has become loader hydraulic system, the various hydraulic systems that possess power-saving technology are arisen at the historic moment. conventional energy-saving hydraulic system has the variable delivery hydraulic system of determining and entire variable hydraulic system at present. in sum, determine variable delivery hydraulic system cost performance higher, but still there are some shortcomings in it, as: when the operation of operated pilot handle, the load control port meeting of load-reacting pump is connected with its main hydraulic fluid port, cause load-reacting pump cannot realize load-sensitive control function, now pump is with rated discharge fuel feeding, if pressure raises, can cause the required power input of pump sharply to raise, under severe duty, pump is with rated discharge fuel feeding, can cause the power accounting in complete machine of hydraulic system too high, thereby the power of reduced walk mechanism input, cause complete machine to occur that walking is unable, in the time that complete machine bearing power exceedes engine power rating, can cause the phenomenons such as engine misses. when complete machine is during in fine motion operating mode, the required flow of the executive component of hydraulic system is less, and the unnecessary flow that pump is discharged is by the oil return of distributing valve meta, and system produces restriction loss, causes energy loss.
Summary of the invention
The object of the invention is to determine variable pump in variable delivery hydraulic system for existing loading machine is that while causing heavy load because of rated discharge output, the input power accounting of pump causes running gear power to input not enough shortcoming greatly, and provides the power control valve that a kind of loading machine determines to use in variable delivery hydraulic system and the loading machine with this power control valve to determine variable delivery hydraulic system.
The present invention is that to realize the technical scheme of its object be such: construct a kind of power control valve, it comprises valve body, on valve body, be provided with P mouth, T mouth, P1 mouth, PLS mouth, in valve body, be provided with main valve plug, valve pocket, the first chamber, the second chamber, the 3rd chamber, valve core spring, valve pocket spring, the first chamber be communicated with PLS mouth and the first chamber in hydraulic oil act on the right-hand member of main valve plug, valve core spring is arranged on the left end of main valve plug, valve pocket is set on described main valve plug, the second chamber is communicated with P1 mouth and the second intraluminal fluid force feed acts on valve pocket right-hand member, the 3rd chamber is communicated with P mouth and the 3rd intraluminal fluid force feed acts on the left end of valve pocket, valve pocket spring provides elastic force left to valve pocket, on main valve plug and valve pocket, be provided with the draining passage that is communicated with the 3rd chamber and T mouth, draining passage conducting in the time that the relative valve pocket of main valve plug is moved to the left, in the time that the relative main valve plug of valve pocket is moved to the left, draining passage reduces or closes.
In power control valve of the present invention, draining passage comprises the oil groove being arranged on main valve plug and is arranged on the radial direction oil hole on valve pocket, in valve body, be provided with the oil duct that radial direction oil hole is communicated with T mouth, draining passage conducting when oil groove left end exposes valve pocket left side, draining passage cut-off when oil groove left end is positioned at valve pocket endoporus.
In power control valve of the present invention, valve body is provided with spring cavity, valve core spring establish with spring cavity in, the left end of main valve plug is positioned at spring cavity. In main valve plug, be provided with the oil duct of spring cavity and draining channel connection.
In power control valve of the present invention, valve pocket is stepped, and its left section of radial dimension is greater than right section of radial dimension, and it is right section of valve pocket that valve pocket spring housing is located at valve pocket reduced diameter section.
The present invention for another technical scheme that realizes its object and provide be such: construct a kind of loading machine and determine variable delivery hydraulic system, comprise load-reacting pump, constant displacement pump, distributing valve, pilot valve, operating cylinder, fuel tank, the operating cylinder that pilot valve is connected with distributing valve and is connected with distributing valve through distributing valve control, also comprise in addition above-mentioned power control valve, the T mouth of power control valve is communicated with fuel tank, the PLS mouth of power control valve is communicated with the main hydraulic fluid port of load-reacting pump, and the P mouth of power control valve is communicated with the LS mouth of load-reacting pump, and the P1 mouth of power control valve is communicated with the P mouth of distributing valve. in the present invention, the elastic force of main valve plug spring is adjustable, by the pretightning force of regulating spool spring, and the pressure regulation power that opens of capable of regulating power control valve. in the time that complete machine does not start, main valve plug under main valve plug spring action in least significant, valve pocket under spring action in leftmost position, draining pathway closure. when operation element device action, when the main hydraulic fluid port pressure of load-reacting pump be less than power control valve open pressure regulation power time, as shown in Figure 1, power control valve P mouth and T mouth disconnect the state of power control valve, power control valve is inoperative, and pump is with rated discharge fuel feeding. when the main hydraulic fluid port pressure of load-reacting pump be greater than power control valve open pressure regulation power time, the active force that the main valve plug of power control valve can overcome valve core spring moves to left, main valve plug finishing bathtray exposes from the left end of valve pocket, the conducting of draining passage, the P mouth of power control valve is through the 3rd chamber, draining passage and T mouth are connected, now the load controlled pressure oil of load-reacting pump is also that the LS mouth of load-reacting pump is by the T mouth draining of power control valve, thereby the load controlled pressure of load-reacting pump is declined, the main valve plug of the LS valve in load-reacting pump moves to right, the oil-feed of servo-cylinder rodless cavity, servo-cylinder promotes swash plate angle and reduces, cause pumpage to reduce. due to reducing of pumpage, cause the pressure differential Δ P at the valve pocket two ends of power control valve to reduce, valve pocket disequilibrium, valve pocket moves to left under the effect of valve pocket spring, design by coupling, the displacement that keeps each valve pocket to move to left is less than the displacement of main valve plug, when main valve plug and valve pocket are during all in balance, long-pending certain definite value that keeps of opening section of draining passage, pumpage keeps certain definite value. if load pressure continues to raise, main valve plug continues to move to left, and valve pocket is servo-actuated to move to left, because the displacement of each valve pocket is all less than main valve plug, therefore the sectional area of draining passage constantly increases, the decline of the load controlled pressure of load-reacting pump is more, thereby pumpage is further reduced. if when load pressure reduces, main valve plug moves to right under main valve plug spring action, reduce the sectional area of draining passage, the load controlled pressure of pump raises, pumpage is increased, due to the increase of pumpage, cause the pressure differential Δ P at the valve pocket two ends of power control valve to increase, move right thereby promote valve pocket, until reach a new equalization point. in the time that load pressure opens pressure regulation power lower than power control valve, power control valve recovers state shown in accompanying drawing 1.
In sum, power control valve can be realized and determine variable delivery hydraulic system and be inversely prroportional relationship at the responsive variable pump delivery of certain section of pressure range internal burden with load pressure and change, maintenance hydraulic system at certain section of pressure range in permanent power rating.
Determine in variable delivery hydraulic system at loading machine of the present invention, also comprise that hydraulic steering system, hydraulic steering system comprise load-sensitive steering gear, load-sensitive flux amplification valve, steering cylinder; The steering cylinder that load-sensitive steering gear is connected with load-sensitive flux amplification valve and is connected with load-sensitive flux amplification valve through the control of load-sensitive flux amplification valve, the main hydraulic fluid port of load-reacting pump is connected with load-sensitive flux amplification valve, and the interflow hydraulic fluid port of load-sensitive flux amplification valve is communicated with the P mouth of distributing valve.
Determine in variable delivery hydraulic system at loading machine of the present invention, also comprise two position four-way valves, the P1 mouth of the hydraulic control end of two position four-way valves is communicated with the shuttle valve C mouth in first rodding, the pressure signal of shuttle valve is taken from pilot valve, the feedback LS mouth of load-sensitive flux amplification valve and load-reacting pump is communicated with P5 mouth and the P4 mouth of two position four-way valves respectively, and the P2 mouth of two position four-way valves and P3 mouth are communicated with the LS mouth of load-sensitive steering gear and the main hydraulic fluid port of load-reacting pump respectively; When the pressure signal of two position four-way valve hydraulic control ends is greater than spring force, valve is in right function position, now its P2 mouth and the conducting of P5 mouth, P3 mouth and the conducting of P4 mouth, when the pressure signal of two position four-way valve hydraulic control ends is less than spring force, valve is in left function position, and now its P2 mouth and the conducting of P4 mouth, P2 mouth and P5 mouth disconnect.
Determine in variable delivery hydraulic system at loading machine of the present invention, between the LS mouth of load-reacting pump and the P4 mouth of two position four-way valves, be provided with adjustable throttling.
The present invention compared with prior art, advantage of the present invention:
1, the peak power of restriction hydraulic system, reduce the power accounting of hydraulic system in complete machine, ensure that complete machine running gear has enough power inputs, improve loading machine tractive force and associating operating mode work capacity, improve complete machine power division, while avoiding transshipping operating mode, occur the phenomenons such as engine misses.
2, under permanent power rating, hydraulic system can reduce pumpage, improve system pressure, make working device of loader obtain larger digging force and lifting force, more meet loading machine demand to hydraulic system " high pressure low discharge " in the time of spading and heavy duty lifting operating mode.
3, improve and determine the restriction loss that variable delivery hydraulic system causes when unnecessary flow draining under fine motion operating mode, reduce energy loss, raising energy-saving effect.
4, reduce hydraulic oil temperature, can improve the volumetric efficiency of component life, system reliability and the pump of hydraulic system.
5, the present invention for the hydraulic system with control function of power, has the advantages such as cost is lower, power regulating range is wider, dismounting is more flexible with respect to other. This loading machine with control function of power is determined variable delivery hydraulic system and can not changed under the prerequisite of former Hydraulic Elements, increases control function of power by be connected in parallel power control valve and choke valve, makes hydraulic system can match flexibly control function of power.
Brief description of the drawings
Fig. 1 is the structural representation of power control valve of the present invention;
Fig. 2 is the hydraulic principle schematic diagram that loading machine of the present invention is determined variable delivery hydraulic system.
Parts title and sequence number in figure:
Load-reacting pump 1, power control valve 2, oil filter 3, fuel tank 4, constant displacement pump 5, adjustable throttling 6, guide's delivery valve 7, unloader 8, two position four-way valves 9, shuttle valve 10, pilot valve 11, load-sensitive steering gear 12, load-sensitive flux amplification valve 13, distributing valve 14, steering cylinder 15, rotary ink tank 16, boom cylinder 17, valve body 21, main valve plug 22, valve pocket 23, the first chamber 24, the second chamber 25, the 3rd chamber 26, valve pocket spring 27, valve core spring 28, oil groove 221, oil duct 222, radial hole 231, the 4th chamber 29, spring cavity 30.
Detailed description of the invention
Below in conjunction with brief description of the drawings specific embodiments.
In the present embodiment, loading machine is determined variable delivery hydraulic system and is comprised load-reacting pump 1, constant displacement pump 5, distributing valve 14, pilot valve 11, shuttle valve 10, operating cylinder, fuel tank 4, hydraulic steering system, two position four-way valves 9, power control valve 2, operating cylinder comprises rotary ink tank 16, boom cylinder 17, and hydraulic steering system comprises load-sensitive steering gear 12, load-sensitive flux amplification valve 13, steering cylinder 15; Load-sensitive steering gear 13 is connected with load-sensitive flux amplification valve 13 and controls through load-sensitive flux amplification valve 13 steering cylinder 15 being connected with load-sensitive flux amplification valve 13, the main hydraulic fluid port of load-reacting pump 1 is connected with load-sensitive flux amplification valve 13, and the interflow hydraulic fluid port of load-sensitive flux amplification valve 13 is communicated with the P mouth of distributing valve 14. The P1 mouth of the hydraulic control end of two position four-way valves 9 is communicated with the outlet of shuttle valve 10, the oil-in of shuttle valve group 10 is communicated with guide's oil circuit of pilot valve 11, the guide that shuttle valve 10 forms pilot valve feeds back LS mouth, the feedback LS mouth of load-sensitive flux amplification valve 13 and load-reacting pump 1 is communicated with P5 mouth and the P4 mouth of two position four-way valves 9 respectively, and the P2 mouth of two position four-way valves 9 and P3 mouth are communicated with the LS mouth of load-sensitive steering gear 12 and the main hydraulic fluid port of load-reacting pump 1 respectively; When pilot valve has action, in pilot valve 11, the pressure of guide oil acts on the hydraulic control end P1 mouth of two position four-way valves through shuttle valve 10. In the time that the hydraulic control end pressure of two position four-way valves 9 is greater than spring force, two position four-way valve places 9 are in right function position, now its P3 mouth and the conducting of P4 mouth, P2 and the conducting of P5 mouth; In the time that the hydraulic control end pressure of two position four-way valves 9 is less than spring force, two position four-way valves 9 are in left function position, and now its P2 mouth and the conducting of P4 mouth, P3 mouth and P5 mouth disconnect. Between the P4 mouth of the LS mouth of load-reacting pump 1 and two position four-way valves 9, be provided with adjustable throttling 6. Pilot valve 11 is connected with distributing valve 14 and controls through distributing valve 14 rotary ink tank 16 and the boom cylinder 17 that are connected with distributing valve 14. The main hydraulic fluid port of constant displacement pump 5 is communicated with to distributing valve 14 fuel feeding with the P mouth of distributing valve 14 through unloader 8; The main hydraulic fluid port of load-reacting pump 1 is also communicated with pilot valve 11 by oil filter 3, guide's delivery valve 7, and pilot control is provided.
Power control valve 2 comprises valve body 21, on valve body, be provided with P mouth, T mouth, P1 mouth, PLS mouth, in valve body, be provided with main valve plug 22, valve pocket 23, the first chamber 24, the second chamber 25, the 3rd chamber 26, valve pocket spring 27, valve core spring 28, the first chamber 24 be communicated with PLS mouth and the first chamber 24 in hydraulic oil act on the right-hand member of main valve plug 22, be provided with valve core spring 28 at the left end of main valve plug 22, valve pocket 23 is set on main valve plug 22, the second chamber 25 is communicated with P1 mouth and the second interior hydraulic oil in chamber 25 acts on valve pocket 23 right-hand members, the 3rd chamber 26 is communicated with P mouth and the 3rd interior hydraulic oil in chamber 26 acts on the left end of valve pocket 23, valve pocket spring 27 provides elastic force left to valve pocket 23, on main valve plug 22 and valve pocket 23, be provided with the draining passage that is communicated with the 3rd chamber 26 and T mouth, draining passage comprises the oil groove 221 being arranged on main valve plug 22 and is arranged on the radial direction oil hole 231 on valve pocket 23, in valve body, be provided with the 4th chamber 29, the 4th chamber 29 is communicated with the oil duct that forms connection radial hole 231 and T mouth simultaneously with T mouth with radial direction oil hole 231. in the time that the relative valve pocket 23 of main valve plug 22 is moved to the left, oil groove 221 left ends expose valve pocket 23 left sides, the conducting of draining passage, and in the time that the relative main valve plug 22 of valve pocket 23 is moved to the left, the sectional area of draining passage reduces or closes. valve body is provided with spring cavity 30, valve core spring 28 establish with spring cavity 30 in, the left end of main valve plug 22 is positioned at spring cavity 30. in main valve plug 22, be provided with the oil duct 222 with draining channel connection by spring cavity 30, oil duct 222 is by being arranged on oil duct axial in main valve plug and oil duct radially forms. valve pocket 23 is stepped, and its left section of radial dimension is greater than right section of radial dimension, and it is right section of valve pocket that valve pocket spring 27 is set in valve pocket 23 reduced diameter sections.
The T mouth of power control valve 2 is communicated with fuel tank 4, and the PLS mouth of power control valve 2 is communicated with the main hydraulic fluid port of load-reacting pump 1, and the P mouth of power control valve is communicated with the LS mouth of load-reacting pump 1, and the P1 mouth of power control valve 2 is communicated with the P mouth of distributing valve 14. in the present invention, the elastic force of valve core spring 28 is adjustable, by the pretightning force of regulating spool spring 28, the pressure regulation power that opens of capable of regulating power control valve, when the main hydraulic fluid port pressure of load-reacting pump be less than power control valve open pressure regulation power time, as shown in Figure 1, power control valve P mouth and T mouth disconnect the state of power control valve, power control valve is inoperative, and pump is with rated discharge fuel feeding. when the main hydraulic fluid port pressure of load-reacting pump be greater than power control valve open pressure regulation power time, the active force that the main valve plug of power control valve can overcome valve core spring moves to left, main valve plug finishing bathtray exposes from the left end of valve pocket, the conducting of draining passage, the P mouth of power control valve is through the 3rd chamber, draining passage and T mouth are connected, now the load controlled pressure oil of load-reacting pump is also that the LS mouth of load-reacting pump is by the T mouth draining of power control valve, thereby the load controlled pressure of load-reacting pump is declined, the main valve plug of the LS valve in load-reacting pump moves to right, the oil-feed of servo-cylinder rodless cavity, servo-cylinder promotes swash plate angle and reduces, cause pumpage to reduce. due to reducing of pumpage, cause the pressure differential Δ P at the valve pocket two ends of power control valve to reduce, valve pocket disequilibrium, valve pocket moves to left under the effect of valve pocket spring, design by coupling, the displacement that keeps each valve pocket to move to left is less than the displacement of main valve plug, when main valve plug and valve pocket are during all in balance, the sectional area of drain tap keeps certain definite value, and pumpage keeps certain definite value. if load pressure continues to raise, main valve plug continues to move to left, and valve pocket is servo-actuated to move to left, because the displacement of each valve pocket is all less than main valve plug, therefore drain tap sectional area constantly increases, the decline of the load controlled pressure of load-reacting pump is more, thereby pumpage is further reduced. if when load pressure reduces, main valve plug moves to right under main valve plug spring action, reduce the sectional area of draining passage, the load controlled pressure that carries responsive variable pump raises, pumpage is increased, due to the increase of pumpage, cause the pressure differential Δ P at the valve pocket two ends of power control valve to increase, move right thereby promote valve pocket, until reach a new equalization point. in the time that load pressure opens pressure regulation power lower than power control valve, power control valve recovers state shown in accompanying drawing 1. the operation principle that above-mentioned loading machine is determined variable delivery hydraulic system is as follows:
Complete machine standby operating mode:
At engine idle, when complete machine does not carry out any operational motion, load-sensitive flux amplification valve 13 is in closing Median Function, and distributing valve 14 is in leaving Median Function. Two position four-way valves work in left position, load-reacting pump 1 is non-loaded, and controlled pressure oil enters its LS mouth, the LS valve of load-reacting pump 1 moves to left function position under main hydraulic fluid port pressure-acting, pressure oil is by the servo variable displacement oil cylinder rodless cavity of LS valve, stop valve inflow pump inside simultaneously, in servo variable displacement oil cylinder pushing pump, swash plate makes its angle convergence zero degree, load-reacting pump 1 is in closed condition, and only output supplements and leaks and maintain the required tiny flow quantity of armed state pressure initiation continuous-flow. Load-reacting pump 1 does not cause any energy loss under this operating mode.
Constant displacement pump 5 keeps rated discharge output flow, and flow through unloader 8, distributing valve 14 Median Functions of hydraulic oil got back to hydraulic oil container 1. Because distributing valve 14 Median Functions exist back pressure, therefore constant displacement pump 5 causes local losses, and running of hydraulic power oil generation linear loss, cause energy loss.
Steering situation separately:
In the time that independent operation turns to, the LS mouth of load-sensitive steering gear 12 communicates with load-sensitive flux amplification valve 13 oil-outs, it is steering load pressure from the load controlled pressure oil of load-sensitive steering gear 12 that the LS mouth of load-reacting pump 1 receives, because the load controlled pressure oil load-sensitive flux amplification valve 13, load-sensitive steering gear 12 of flowing through can produce pressure loss Δ P, if Δ P value is greater than the spring force of load-reacting pump LS valve, LS valve is still in left function position, and load-reacting pump 1 is in closed condition; When Δ P is less than after LS valve spring power, under spring action, LS valve moves to right function position, and servo variable displacement oil cylinder rodless cavity hydraulic oil flows out, and in servo variable displacement oil cylinder pushing pump, swash plate increases its angle, and load-reacting pump 1 starts outside output flow.
Rotating of steering wheel speed speed determines the main valve plug aperture of load-sensitive flux amplification valve 13, in the time that rotating of steering wheel speed is fast, the main valve plug aperture of load-sensitive flux amplification valve 13 increases, Δ P value reduces, LS valve moves to left gradually, servo-cylinder rodless cavity draining, servo-cylinder promotes swash plate angle and increases, and load-reacting pumpage increases; Otherwise in the time that rotating of steering wheel speed is slow, the main valve plug aperture of load-sensitive flux amplification valve 13 reduces, Δ P value increases, and LS valve moves to right gradually, the oil-feed of servo-cylinder rodless cavity, and servo-cylinder promotes swash plate angle and reduces, and pumpage reduces; So load-reacting pump 1 can carry out fuel feeding according to the required oil mass of steering, the energy consumption of avoiding unnecessary flow overflow to cause. The flow that load-reacting pump 1 is exported can produce local losses and linear loss.
In the time that steering cylinder moves to extreme position, the stop valve of load-reacting pump 1 cuts off pumpage, and now load-reacting pump 1 is only exported tiny flow quantity, avoids hydraulic system to produce spill losses.
Constant displacement pump 5 keeps rated discharge output flow, and flow through unloader 8, distributing valve 14 Median Functions of hydraulic oil got back to hydraulic oil container. Because distributing valve 14 Median Functions exist back pressure, therefore constant displacement pump 5 causes local losses, and running of hydraulic power oil generation linear loss, cause energy loss.
Operating mode works independently:
In the time that pilot valve 11 moves, pilot pressure oil enters the P1 mouth of two position four-way valves 9 through pilot valve 11, shuttle valve 10, under the effect of pilot pressure oil, the spool of two position four-way valves 9 moves to left, two position four-way valves 9 work in right position, and the main hydraulic fluid port of load-reacting pump 1 is connected with its load control port LS mouth after P4 mouth, adjustable throttling 6 through the P3 mouth of two position four-way valves 9. Power control valve 2 is being connected in parallel at the LS of load-reacting pump 1 mouth place. When the main hydraulic fluid port pressure of load-reacting pump 1 lower than power control valve 2 open pressure regulation power time, power control valve 2 is in off position, because LS valve spring power is greater than the pressure loss that load pressure control oil produces through adjustable throttling 6, therefore under the effect of LS valve spring power, LS spool moves to right function position, servo-cylinder rodless cavity draining, servo-cylinder promotes swash plate angle and increases to maximum, load-reacting pump 1 is with rated discharge fuel feeding, and load-reacting pump 1 has now become a constant flow pump. Because steering cylinder is not worked, therefore steering does not need flow, the pressure-gradient control valve in load-sensitive flux amplification valve 13 is moved to left function position by the pressure oil that load-reacting pump 1 is exported, the hydraulic oil that load-reacting pump 1 is exported collaborates mouthful (an EF mouth) by flux amplification valve and collaborates to distributing valve 14, jointly to boom cylinder or rotary ink tank fuel feeding, improve the operating efficiency of equipment through the P of distributing valve 14 mouth and constant displacement pump 5.
Constant displacement pump 5 keeps rated discharge output flow, and hydraulic oil is flowed through unloader 7, distributing valve 14 afterwards to boom cylinder 17 or rotary ink tank 16 fuel feeding. When the main hydraulic fluid port pressure of constant displacement pump 5 is during higher than the pressure unloading of unloader, hydraulic oil is directly let out back hydraulic oil container 4 by unloader 8, hydraulic system now only has the independent oil cylinder fuel feeding to equipment of load-reacting pump 1, thereby reduces the power accounting of hydraulic system in complete machine.
When the main hydraulic fluid port pressure of load-reacting pump be greater than power control valve open pressure regulation power time, the active force that the main valve plug of power control valve can overcome valve core spring moves to left, main valve plug finishing bathtray exposes from the left end of valve pocket, the conducting of draining passage, the P mouth of power control valve is through the 3rd chamber, draining passage and T mouth are connected, now the load controlled pressure oil of load-reacting pump is also that the LS mouth of load-reacting pump is by the T mouth draining of power control valve, thereby the load controlled pressure of load-reacting pump is declined, the main valve plug of the LS valve in load-reacting pump moves to right, the oil-feed of servo-cylinder rodless cavity, servo-cylinder promotes swash plate angle and reduces, cause pumpage to reduce. due to reducing of pumpage, cause the pressure differential Δ P at the valve pocket two ends of power control valve to reduce, valve pocket disequilibrium, valve pocket moves to left under the effect of valve pocket spring, design by coupling, the displacement that keeps each valve pocket to move to left is less than the displacement of main valve plug, when main valve plug and valve pocket are during all in balance, the sectional area of draining passage keeps certain definite value, and load-reacting pumpage keeps certain definite value. if load pressure continues to raise, main valve plug continues to move to left, and valve pocket is servo-actuated to move to left, because the displacement of each valve pocket is all less than main valve plug, therefore drain tap sectional area constantly increases, the decline of the load controlled pressure of load-reacting pump is more, thereby pumpage is further reduced. if when load pressure reduces, main valve plug moves to right under main valve plug spring action, reduces the sectional area of draining passage, the increased pressure in the 3rd chamber, also the load controlled pressure that is load-reacting pump raises, and pumpage is increased, thereby realizes the permanent power rating of hydraulic system. under the severe duties such as spading, loading machine is generally high pressure low discharge to the requirement of hydraulic system, therefore power control valve 2 can obtain high pressure output by reducing the discharge capacity of load-reacting pump 1, and the power accounting of the responsive variable pump 1 of proof load can be not too high and cause running gear unable, the even phenomenon such as engine misses.
Because hydraulic system is to control by the spool aperture of control distributing valve 14 flow that enters oil cylinder, if two pumps have unnecessary flow to produce as large throttle, little aperture, unnecessary flow can be from distributing valve 14 meta oil returns to hydraulic oil container 4, if the main valve plug of distributing valve 14 is little aperture, the meta of its main valve plug can not closed completely, now can produce restriction loss in distributing valve 14 meta oil returns place, if load pressure is now high pressure, the ability loss that restriction loss causes is larger. Load-reacting pump 1 reduces discharge capacity under severe duty also can reduce restriction loss amount, reaches and reduces the effect that hydraulic system energy consumes.
4, work and turn to composite move operating mode:
In the time that pilot valve 11 and load-sensitive steering gear 12 are moved simultaneously, pilot pressure oil enters the P1 mouth of two position four-way valves 9 after pilot valve 11, shuttle valve group 10, under the effect of pilot pressure oil, the spool of two position four-way valves 9 moves to left, and the main hydraulic fluid port of load-reacting pump 1 is connected with its load control port (LS mouth) after the P3 mouth of two position four-way valves 9, P4 mouth, adjustable throttling 6. Because LS valve spring power is greater than the pressure loss that load pressure control oil produces through adjustable throttling 6, therefore under the effect of LS valve spring power, LS spool moves to right function position, servo-cylinder rodless cavity draining, servo-cylinder promotes swash plate angle and increases to maximum, and load-reacting pump 1 is with rated discharge fuel feeding. Under this operating mode, load-reacting pump 1 cannot provide corresponding discharge according to loading demand. Because load-sensitive flux amplification valve 13 inside are provided with pressure-gradient control valve, therefore the flow that load-reacting pump 1 is exported is meeting after the required flow of steering, unnecessary flow is collaborated to the oil cylinder fuel feeding of distributing valve to equipment. The power control operation principle of load-reacting pump 1 is consistent with the operating mode that works independently.
The operation principle of constant displacement pump 5 is consistent with the operating mode that works independently.
Claims (9)
1. a power control valve, comprise valve body, it is characterized in that being provided with P mouth on valve body, T mouth, P1 mouth, PLS mouth, in valve body, be provided with main valve plug, valve pocket, the first chamber, the second chamber, the 3rd chamber, valve core spring, valve pocket spring, described the first chamber be communicated with PLS mouth and the first chamber in hydraulic oil act on the right-hand member of main valve plug, valve core spring is arranged on the left end of main valve plug, described valve pocket is set on described main valve plug, the second chamber is communicated with P1 mouth and the second intraluminal fluid force feed acts on valve pocket right-hand member, described the 3rd chamber is communicated with P mouth and the 3rd intraluminal fluid force feed acts on the left end of described valve pocket, described valve pocket spring provides elastic force left to valve pocket, on main valve plug and valve pocket, be provided with the draining passage for being communicated with the 3rd chamber and T mouth, draining passage conducting described in the time that the relative valve pocket of main valve plug is moved to the left, described in the time that the relative main valve plug of valve pocket is moved to the left, draining passage reduces or closes.
2. power control valve according to claim 1, it is characterized in that described draining passage comprises the oil groove that is arranged on main valve plug, is arranged on the radial direction oil hole on valve pocket, in valve body, be provided with the oil duct that radial direction oil hole is communicated with T mouth, described oil groove right-hand member is communicated with described radial direction oil hole, draining passage conducting described in when described oil groove left end exposes described valve pocket left side, when described oil groove left end is positioned at described valve pocket endoporus described in draining passage cut-off.
3. power control valve according to claim 1 and 2, is characterized in that described valve body is provided with spring cavity, and described main valve plug spring is located in described spring cavity, and the left end of described main valve plug is positioned at described spring cavity.
4. power control valve according to claim 3, is characterized in that being provided with the oil duct of spring cavity and draining channel connection in described main valve plug.
5. power control valve according to claim 1, is characterized in that described valve pocket is stepped, and its left section of radial dimension is greater than right section of radial dimension, and described valve pocket spring housing is located at described valve pocket reduced diameter section.
6. loading machine is determined a variable delivery hydraulic system, comprises load-reacting pump, constant displacement pump, distributing valve, pilot valve, operating cylinder, fuel tank; The operating cylinder that described pilot valve is connected with distributing valve and is connected with distributing valve through distributing valve control; Characterized by further comprising the power control valve described in any one in claim 1 to 5, the T mouth of described power control valve is communicated with fuel tank, the PLS mouth of power control valve is communicated with load-reacting delivery side of pump, the P mouth of power control valve is communicated with the LS mouth of load-reacting pump, and the P1 mouth of power control valve is communicated with the P mouth of distributing valve.
7. loading machine according to claim 6 is determined variable delivery hydraulic system, characterized by further comprising hydraulic steering system, and described hydraulic steering system comprises load-sensitive steering gear, load-sensitive flux amplification valve, steering cylinder; The steering cylinder that described load-sensitive steering gear is connected with load-sensitive flux amplification valve and is connected with load-sensitive flux amplification valve through the control of load-sensitive flux amplification valve, described load-reacting delivery side of pump is connected with load-sensitive flux amplification valve, and the interflow hydraulic fluid port of described load-sensitive flux amplification valve is communicated with the P mouth of distributing valve.
8. loading machine according to claim 7 is determined variable delivery hydraulic system, characterized by further comprising two position four-way valves, the P1 mouth of described two position four-way valve hydraulic control ends is communicated with the shuttle valve C mouth in first rodding, the pressure signal of shuttle valve is taken from pilot valve, the LS mouth of described load-sensitive flux amplification valve and load-reacting pump is communicated with P5 mouth and the P4 mouth of two position four-way valves respectively, and the P2 mouth of two position four-way valves and P3 mouth are communicated with the LS mouth of load-sensitive steering gear and the main hydraulic fluid port of load-reacting pump respectively; When the P1 mouth pressure of the hydraulic control end of two position four-way valves is greater than spring force, valve is in right function position, the P2 mouth of two position four-way valves and the conducting of P5 mouth, P3 mouth and the conducting of P4 mouth, when the P1 mouth pressure of the hydraulic control end of two position four-way valves is less than spring force, valve is in left function position, and the P2 mouth of two position four-way valves and the conducting of P4 mouth, P2 mouth and P5 mouth disconnect.
9. loading machine according to claim 8 is determined variable delivery hydraulic system, it is characterized in that being provided with adjustable throttling between the LS mouth of described load-reacting pump and the P4 mouth of two position four-way valves.
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| CN201410349567.XA CN104153419B (en) | 2014-07-22 | 2014-07-22 | Power control valve and loading machine are determined variable delivery hydraulic system |
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| CN201410349567.XA CN104153419B (en) | 2014-07-22 | 2014-07-22 | Power control valve and loading machine are determined variable delivery hydraulic system |
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| CN104153419B true CN104153419B (en) | 2016-05-25 |
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| CN104929183B (en) * | 2015-05-21 | 2017-03-15 | 徐工集团工程机械股份有限公司科技分公司 | A kind of loader turned to based on Flow amplification determines variable delivery hydraulic system |
| CN106321537B (en) * | 2015-06-19 | 2020-11-13 | 博世力士乐（北京）液压有限公司 | Hydraulic control system and corresponding mobile working device |
| JP7002251B2 (en) * | 2017-08-31 | 2022-01-20 | 川崎重工業株式会社 | Removal judgment device and control unit |
| CN107882798B (en) * | 2017-11-10 | 2019-08-20 | 广西柳工机械股份有限公司 | Load simulation valve and loading machine variable system |
| CN107781126B (en) * | 2017-11-22 | 2023-12-05 | 江苏恒立液压科技有限公司 | Hydraulic pump control valve |
| CN111980977B (en) * | 2020-07-24 | 2022-09-20 | 中国航空工业集团公司西安飞行自动控制研究所 | Cross power control valve for duplex hydraulic pump and duplex hydraulic pump |
| CN116044732B (en) * | 2022-12-26 | 2024-06-11 | 厦门大学 | Three-stage pressure control system and method |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US4201116A (en) * | 1977-07-11 | 1980-05-06 | The Cessna Aircraft Company | Electro-hydraulic proportional control servo valve |
| KR940009219B1 (en) * | 1989-03-30 | 1994-10-01 | 히다찌 겐끼 가부시기가이샤 | Hydraulic driving apparatus of caterpillar vehicle |
| CN201027637Y (en) * | 2007-04-10 | 2008-02-27 | 仙居永灵液压机械有限公司 | Flux-sensitive control valve system used for load-sensitive hydraulic pump |
| CN101922445B (en) * | 2010-07-29 | 2013-08-21 | 杭州力龙液压有限公司 | Constant power control valve |
| CN103791129B (en) * | 2014-02-28 | 2016-05-11 | 昆明中铁大型养路机械集团有限公司 | The traveling control load valve that a kind of closed type hydraulic system drives |
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