CN109695601B - Energy-saving proportional reversing valve based on four-way hydraulic transformer valve post compensation - Google Patents
Energy-saving proportional reversing valve based on four-way hydraulic transformer valve post compensation Download PDFInfo
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- CN109695601B CN109695601B CN201910154629.4A CN201910154629A CN109695601B CN 109695601 B CN109695601 B CN 109695601B CN 201910154629 A CN201910154629 A CN 201910154629A CN 109695601 B CN109695601 B CN 109695601B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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Abstract
The invention discloses an energy-saving proportional reversing valve based on four-way hydraulic transformer valve post compensation, which comprises a four-way hydraulic transformer and an operation part which is connected into a hydraulic system and corresponds to an execution elementA valve having a working oil port; the four-way hydraulic transformer is provided with a high-pressure oil inlet, a low-pressure oil outlet, a recovery oil outlet and a low-pressure oil suction port, when the load pressure of an execution element controlled by a loop where the operating valve is located is not the maximum load pressure of the hydraulic system, the four-way hydraulic transformer and the operating valve are connected in series and connected into the hydraulic system, the transformation ratio of the four-way hydraulic transformer is adjusted until the pressure of the high-pressure oil inlet reaches the maximum load pressure of the hydraulic system, and the hydraulic energy recovered by the four-way hydraulic transformer can be recovered fromOThe port is used together with a pressure oil port for supplying oil to a hydraulic system; when the load pressure of an actuating element controlled by a circuit where the operating valve is located is the maximum load pressure of the hydraulic system, the four-way hydraulic transformer is not connected into the hydraulic system.
Description
Technical Field
The invention relates to a pressure compensation device in a hydraulic transmission and control system, in particular to an energy-saving proportional reversing valve based on four-way hydraulic transformer valve post compensation.
Background
At present, most engineering machinery adopts a few-pump multi-load loop hydraulic system, for example, when a hydraulic excavator works, the independent actions of a movable arm, a bucket rod and a bucket of the hydraulic excavator need to be ensured, and the movable arm, the bucket rod and the bucket of the hydraulic excavator need to be matched with each other to realize a composite action; similarly, the work device action and the rotary table rotation can be carried out independently, and the composite action can be realized, so that the work efficiency of the excavator is improved. Most hydraulic excavators employ a load-sensitive pump and a common load-sensitive system, but when they drive a plurality of actuators at the same time, the output pressure of the pump can only be adapted to the highest load pressure, i.e. the load-sensitive system can only act on the highest-pressure load circuit. Since the hydraulic excavator has complex actions and the operation and working conditions thereof vary widely, the working pressure and flow rate required by each working device are different. When the sum of the flow required by each load is larger than the flow limit output by the main pump, most hydraulic oil flows to the oil circuit where the small load is located, so that the phenomenon that a working device with a light load occupies the hydraulic oil of a working device with a heavy load often occurs, and the composite action is difficult to realize.
In order to solve the above problems, most of the conventional methods mainly adopt a load independent flow distribution system (LUDV) for pressure compensation after a valve to perform pressure compensation on each loop, so that the valve port pressure difference is kept constant, and thus independent adjustment of a plurality of execution elements is realized.
In order to improve the operability of the engineering machinery and reduce the labor intensity of a driver, a valve control system is mainly adopted in the existing engineering machinery, a load independent flow distribution system (LUDV) is mainly adopted at present, so that the differential pressure of valve ports of all the operating valves is the same fixed value (the difference between the system oil supply pressure and the maximum load pressure), the motion speed of all executing elements can be reduced in proportion when the oil supply capacity of a pump is insufficient, and the speed of each executing element is only related to the size of the opening of the operating valve and is unrelated to the load pressure. Although the load independent flow distribution system has the advantages, the working pressure required by each working device is different due to the fact that engineering machinery works and working conditions are changeable. Except the maximum load loop, the oil of other load loops passes through the pressure compensation valve and all can generate pressure drop (the difference between the maximum load pressure and the load pressure of an execution element of the loop), and particularly, a large throttle is generated at the pressure compensation valve of a low-pressure load, so that hydraulic energy is converted into heat energy to be wasted, the efficiency of a hydraulic system is reduced, the temperature of hydraulic oil is increased, in order to prevent the oil from being aged due to overheating, cooling equipment is required to be additionally arranged, and the energy waste is further increased.
Therefore, it is desired to solve the above problems.
Disclosure of Invention
The purpose of the invention is as follows: the invention aims to provide an energy-saving proportional reversing valve based on four-way hydraulic transformer valve post-compensation, which avoids throttling loss caused by using a pressure compensation valve while ensuring the stability of control load and the maneuverability of equipment, improves the efficiency of a hydraulic system, avoids the phenomenon of system heating caused by the rise of oil temperature to a great extent, reduces the specification of radiator equipment equipped in the system and has obvious energy-saving effect.
The technical scheme is as follows: in order to achieve the above purpose, the energy-saving proportional reversing valve based on the four-way hydraulic transformer valve post compensation comprises a four-way hydraulic transformer and an operating valve which is connected into a hydraulic system and corresponds to an execution element, wherein the operating valve is provided with working oil ports A, B, C, D, E and F, and the four-way hydraulic transformer is provided with a high-pressure oil inlet PALow pressure oil outlet PBAnd a recovery oil outlet POAnd a low pressure suction port PTWhen the load pressure of an executing element controlled by a loop where the operating valve is located is not the maximum load pressure LS of the hydraulic system, the four-way hydraulic transformer is connected with the operating valve in series and connected into the hydraulic system, and the transformation ratio of the four-way hydraulic transformer is automatically adjusted until the high-pressure oil inlet PAThe pressure of the four-way hydraulic transformer reaches the maximum load pressure LS of the hydraulic system, and the hydraulic energy recovered by the four-way hydraulic transformer is recovered from the pressure POThe port is converged with a pressure oil port P for supplying oil to a hydraulic system for use; when the load pressure of an actuating element controlled by a circuit where the operating valve is located is the maximum load pressure LS of the hydraulic system, the four-way hydraulic transformer is not connected into the hydraulic system.
The hydraulic control system further comprises a hydraulic reversing valve, the hydraulic reversing valve is a two-position three-way reversing valve with three working oil ports R, S and a U, the position of a valve core of the hydraulic reversing valve is controlled by the pressure difference of two control oil ports of the hydraulic reversing valve, the two control oil ports are respectively connected with the maximum load pressure LS of a hydraulic system and the F port of an operating valve, the U port of the hydraulic reversing valve is connected with the maximum load pressure LS of the hydraulic system, the R port of the hydraulic reversing valve is connected with the F port of the operating valve, and the operating valve and a four-way hydraulic transformer are connected in series by switching the working position of the hydraulic reversing valve.
Preferably, the hydraulic control system further comprises a valve plate corner oil cylinder and a corner control valve, wherein the corner control valve is a three-position four-way proportional valve with four working oil ports G, H, J and K, the position of a valve core of the corner control valve is controlled by the pressure difference of two control oil ports of the corner control valve, the two control oil ports are respectively connected with the maximum load pressure LS of a hydraulic system and the F port of an operating valve, the G port of the corner control valve is connected with an oil return port T of the hydraulic system, the H port of the corner control valve is connected with a pressure oil port P, and the J port and the K port of the corner control valve 6 are respectively connected with a left piston rod cavity and a right piston rod cavity of the valve; after the four-way hydraulic transformer is connected with the operating valve in series and is connected into a hydraulic system, the four-way hydraulic transformer is controlled by the corner oil cylinder of the valve plate to change the transformation ratio.
And moreover, the four-way hydraulic transformer is a plunger type oil inlet and outlet flow four-way hydraulic transformer, a left piston and a right piston of a valve plate corner oil cylinder move to drive a valve plate to rotate, a control angle of the valve plate is changed, and the ratio of the differential pressure of a recovery oil outlet and a low-pressure oil suction port to the differential pressure of a high-pressure oil inlet and a low-pressure oil outlet is changed, so that the transformation is realized.
The hydraulic control valve further comprises a first overload valve, a second overload valve, a first check valve, a second check valve and a load oil cylinder, wherein the first overload valve is provided with two working oil ports M1 and N1, an M1 port is connected with a D port of the operating valve, an N1 port is connected with an oil return port T, the second overload valve is provided with two working oil ports M2 and N2, an M2 port is connected with an E port of the operating valve, and an N2 port is connected with the oil return port T; p for recovering hydraulic energy of four-way hydraulic transformerOThe pressure oil port P is connected with the pressure oil port P through a second one-way valveBThe port is connected with a port C of the operating valve through a first one-way valve; the piston rod cavity of the load oil cylinder is connected with the port E of the operating valve, and the piston cavity is connected with the port D of the operating valve.
Has the advantages that: compared with the prior art, the invention has the following remarkable advantages: the four-way hydraulic transformer is used, the oil way is switched through the hydraulic reversing valve, when the load of the loop is not the maximum load, the four-way hydraulic transformer is connected into the hydraulic loop in series, through transformation, the pressure drop originally generated on the pressure compensation valve is converted into pressure difference energy through the hydraulic transformer to be recycled while the pressure difference between the front and the rear of the throttling port of the control valve is ensured to be the difference between the oil supply pressure of the system and the maximum load pressure, and the pressure difference energy is converged into the oil supply loop of the hydraulic pump through the recycled oil port of the hydraulic transformer to be directly utilized, so that the energy is saved; the energy-saving proportional reversing valve based on the four-way hydraulic transformer valve post compensation is used, the throttling loss generated by using the pressure compensation valve is avoided while the stability of control load and the maneuverability of equipment are ensured, the efficiency of a hydraulic system is improved, the phenomenon of system heating caused by the rise of the temperature of oil is avoided to a great extent, the specification of radiator equipment equipped in the system is reduced, and the energy-saving proportional reversing valve has an obvious energy-saving effect.
Drawings
FIG. 1 is a schematic diagram of the system of the present invention;
the figure includes: the hydraulic control system comprises an operating valve 1, overload valves 2 a-2 b, a hydraulic reversing valve 3, a four-way hydraulic transformer 4, a valve plate corner oil cylinder 5, a corner control valve 6, check valves 7 a-7 b and a load oil cylinder 8.
Detailed Description
The technical scheme of the invention is further explained by combining the attached drawings.
As shown in figure 1, the energy-saving proportional reversing valve based on the four-way hydraulic transformer valve post compensation comprises a control valve 1, a first overload valve 2a, a second overload valve 2b, a hydraulic reversing valve 3, a four-way hydraulic transformer 4, a valve plate corner oil cylinder 5, a corner control valve 6, a first one-way valve 7a, a second one-way valve 7b and a load oil cylinder 8.
The operating valve 1 is a three-position six-way proportional valve which not only has a reversing function, but also has a throttling function, the position of a valve core of the operating valve 1 is controlled by an external pilot control valve and springs at two ends of the operating valve, the valve core of the operating valve 1 is centered by the springs at two ends of the operating valve, namely when the external pilot control valve has no output signal, the valve core works in a middle position. The operating valve 1 is provided with six working oil ports which are respectively marked as an A port, a B port, a C port, a D port, an E port and an F port; the port A is an inlet of a throttle opening of the operating valve 1, the port F is an outlet of the throttle opening of the operating valve 1, the port A is connected with a pressure oil port P, the port B is connected with an oil return port T, and the port C is connected with the P of the four-way hydraulic transformer 4BThe port and the S port and the D port of the hydraulic reversing valve 3 are connected with a piston cavity of a load oil cylinder 8 and a second portThe M1 port of an overload valve 2a, the E port are connected with the piston rod cavity of the load oil cylinder 8 and the M2 port of a second overload valve 2b, and the F port is connected with the P port of a four-way hydraulic transformer 4AA port and an R port of the hydraulic change valve 3. When the valve core works at the left position, oil flows from the port A to the port F, flows from the port E to the port B and flows from the port C to the port D; when the valve core works in the middle position, the port A, the port B, the port C, the port D, the port E and the port F are not communicated with each other; when the valve core works at the right position, oil flows from the port A to the port F, and the port C flows to the port E and from the port D to the port B.
The hydraulic reversing valve 3 is a two-position three-way reversing valve, the position of a valve core of the hydraulic reversing valve 3 is controlled by the pressure difference of two control oil ports of the hydraulic reversing valve 3, the two control oil ports of the hydraulic reversing valve 3 are respectively connected with the maximum load pressure LS and the F port of the operating valve 1, and the maximum load pressure LS is the maximum load pressure obtained by connecting a whole hydraulic system loop through a plurality of shuttle valves. The hydraulic reversing valve 3 is provided with three oil ports which are respectively marked as an R port, an S port and a U port, the U port is connected with the maximum load pressure LS, the R port is connected with the F port of the operating valve 1, and the S port is connected with the C port of the operating valve 1; when the valve core works on the upper position, the R port, the S port and the U port are not communicated with each other; when the lower position of the valve core works, the oil flows from the port R to the port S and from the port R to the port U.
The four-way hydraulic transformer 4 of the invention is a plunger type oil inlet and outlet flow four-way hydraulic transformer, which is provided with four working oil ports respectively marked as PAMouth, PBMouth, POMouth, PTMouth, PTThe port is connected with the oil return port T, POThe port is connected with pressure oil ports P and P of a system oil supply way through a second one-way valve 7bBThe port is connected to port C of the pilot valve via a first check valve 7 a. The valve plate corner of the four-way hydraulic transformer 4 is controlled by the oil inlet pressure difference of two control oil ports of the valve plate corner oil cylinder 5; the transformation ratio lambda of the four-way hydraulic transformer 4 is defined as POMouth and PTPressure difference between ports and PAMouth and PBThe ratio of the pressure difference between the ports, i.e.: λ ═ tan θ ═ PPO-PPT)/(PPA-PPB) Theta is a control angle of a valve plate of the four-way hydraulic transformer 4; p of four-way hydraulic transformer 4APressure ratio PBWhen the outlet is higher than a certain pressure, the four-way hydraulic transformerThe pressure device will operate and the higher pressure will be used to overcome the frictional resistance of the four-way hydraulic transformer 4 during operation.
The control valve 1 of the invention is connected into a hydraulic system and corresponds to an execution element, when the load pressure of the execution element controlled by a loop where the control valve 1 is positioned is not the maximum load pressure LS of the hydraulic system, the valve core of the hydraulic reversing valve 3 works in an upper position, oil flows to a load loop after passing through the control valve and the four-way hydraulic transformer 4, the four-way hydraulic transformer 4 is connected with the control valve 1 in series and connected into the hydraulic system, and the transformation ratio of the four-way hydraulic transformer 4 is adjusted until a high-pressure oil inlet PAThe pressure of the four-way hydraulic transformer 4 reaches the maximum load pressure LS of the hydraulic system, and the hydraulic energy recovered by the four-way hydraulic transformer 4 is recovered from the pressure POThe port is used together with a pressure oil port P for supplying oil to the system; when the load pressure of an executing element controlled by a loop where the operating valve 1 is located is the maximum load pressure LS of a hydraulic system, the valve core of the hydraulic reversing valve 3 works at the lower position, oil flows to the load loop after passing through the operating valve and the hydraulic reversing valve, and the four-way hydraulic transformer 4 is not connected into the hydraulic system.
The corner control valve 6 is a three-position four-way proportional valve, the position of a valve core of the corner control valve 6 is controlled by pressure difference of two control oil ports of the corner control valve 6 and centering springs at two ends of the corner control valve, the two control oil ports of the corner control valve 6 are respectively connected with the maximum load pressure LS and an F port of the control valve 1, when the two control oil ports of the corner control valve 6 are not input, the valve core of the corner control valve 6 is centered under the action of the spring forces at the two ends, and the middle position of the valve core works; when the oil inlet pressures of the two control oil ports of the corner control valve 6 are equal, namely the corner control valve 6 is in a stable state, and the valve core works in a middle position; the corner control valve 6 has four working oil ports, which are respectively marked as a G port, an H port, a J port and a K port, the J port and the K port are respectively connected with a left piston rod cavity and a right piston rod cavity of the valve plate corner oil cylinder 5, the G port is connected with an oil return port T, and the H port is connected with a pressure oil port P of a system oil supply way: when the valve core works at the left position, oil flows from the port H to the port J and from the port K to the port G; when the valve core works in the middle position, the port G, the port H, the port J and the port K are not communicated with each other; when the valve core works at the right position, oil flows from the port H to the port K and from the port J to the port G.
According to the invention, after the four-way hydraulic transformer 4 and the operating valve 1 are connected in series and connected into a hydraulic system, the corner control valve 6 controls the movement of a piston in the corner oil cylinder 5 of the valve plate, the left piston and the right piston of the corner oil cylinder 5 of the valve plate move to drive the valve plate to rotate, the control angle of the valve plate is changed, the ratio of the differential pressure of a recovery oil outlet and a low-pressure oil suction port to the differential pressure of a high-pressure oil inlet and a low-pressure oil outlet is changed, and the transformation is.
The first overload valve 2a is provided with two working oil ports which are respectively marked as an M1 port and an N1 port, an M1 port is connected with a D port of the operating valve, an N1 port is connected with an oil return port T, the second overload valve 2b is provided with two working oil ports which are respectively marked as an M2 port and an N2 port, an M2 port is connected with an E port of the operating valve, and an N2 port is connected with the oil return port T.
The invention relates to an energy-saving proportional reversing valve based on four-way hydraulic transformer valve post compensation, which is used for controlling the oil flow direction when the valve is in different load loops and different working conditions of a hydraulic system, and is described as follows.
Working condition (one): when the load of the executing element controlled by the loop where the control valve 1 is located is not the maximum load in the whole hydraulic system, the oil inlet pressure of the upper control oil port of the hydraulic reversing valve 3, namely the maximum load pressure LS, is greater than the oil inlet pressure of the lower control oil port of the hydraulic reversing valve 3, the valve core moves downwards, and the valve core works upwards.
1) Working condition 1: the piston rod of the load oil cylinder 8 extends out, namely, the valve core of the control valve 1 is moved to the right under the control of an external pilot control valve, and the valve core works at the left position.
An oil inlet path: system pressure port P → port a of the pilot valve 1 → port F of the pilot valve 1 → P of the four-way hydraulic transformer 4APort → P of four-way hydraulic transformer 4BPort → the first check valve 7a → port C of the pilot valve 1 → port D of the pilot valve 1 → the piston chamber of the load cylinder 8/port M1 of the first overload valve 2a → port N1 of the first overload valve 2a → the oil return port T;
an oil return path: the piston rod chamber of the load cylinder 8 → the port E of the pilot valve 1 → the port B of the pilot valve 1 → the oil return port T;
oil way compensation: oil return port T → P of four-way hydraulic transformer 4TA mouth;
and (3) oil way recovery: p of four-way hydraulic transformer 4OPort → second check valve 7b → system pressure port P;
2) working condition 2: the piston rod of the load oil cylinder 8 retracts, namely, the valve core of the operating valve 1 moves leftwards under the control of the external pilot control valve, and the valve core works rightwards.
An oil inlet path: system pressure port P → port a of the pilot valve 1 → port F of the pilot valve 1 → P of the four-way hydraulic transformer 4APort → P of four-way hydraulic transformer 4BPort → the first check valve 7a → port C of the pilot valve → port E of the pilot valve 1 → the rod chamber of the load cylinder 8/port M2 of the second overload valve 2b → port N2 of the second overload valve 2b → the oil return port T;
an oil return port: the piston chamber of the load cylinder 8 → the D port of the pilot valve 1 → the B port of the pilot valve 1 → the oil return port T;
oil way compensation: oil return port T → P of four-way hydraulic transformer 4TA mouth;
and (3) oil way recovery: p of four-way hydraulic transformer 4OPort → second check valve 7b → system pressure port P;
working conditions (II): when the load of the executing element controlled by the loop where the operating valve is located is the maximum load in the whole hydraulic system, the oil inlet pressure of the upper control oil port of the hydraulic reversing valve 3 is smaller than that of the lower control oil port of the hydraulic reversing valve 3, the valve core moves upwards, and the valve core works at the lower position.
1) Working condition 1: the piston rod of the load oil cylinder 8 extends out, namely, the valve core of the control valve 1 is moved to the right under the control of an external pilot control valve, and the valve core works at the left position.
An oil inlet path: a system pressure port P → the port a of the pilot valve 1 → the port F of the pilot valve 1 → the port R of the hydraulically operated directional control valve 3 → the port S of the hydraulically operated directional control valve 3 → the first check valve 7a → the port C of the pilot valve 1 → the port D of the pilot valve 1 → the piston chamber of the load cylinder 8/the port M1 of the first overload valve 2a → the port N1 of the first overload valve 2a → the oil return port T;
an oil return path: the rod chamber of the load cylinder 8 → the E port of the pilot valve 1 → the B port of the pilot valve 1 → the oil return port T.
2) Working condition 2: the piston rod of the load oil cylinder 8 retracts, namely, the valve core of the operating valve 1 moves leftwards under the control of the external pilot control valve, and the valve core works rightwards.
An oil inlet path: a system pressure port P → the port a of the pilot valve 1 → the port F of the pilot valve 1 → the port R of the hydraulically operated directional control valve 3 → the port S of the hydraulically operated directional control valve 3 → the first check valve 7a → the port C of the pilot valve 1 → the port E of the pilot valve 1 → the rod chamber of the load cylinder 8/the port M2 of the second overload valve 2b → the port N2 of the second overload valve 2b → the oil return port T;
an oil return path: the load cylinder 8 piston chamber → the D port of the pilot valve 1 → the B port of the pilot valve 1 → the oil return port T.
When pressure signals are sent to two control oil ports a or b of the operating valve 1, the operating valve 1 is reversed, and the port A is communicated with the port F through a throttling port in the valve. If the load of an execution element controlled by a loop where the control valve 1 is located is not the maximum load in the whole hydraulic system, the oil inlet pressure of a control oil port at the upper end of a valve core of the hydraulic reversing valve 3 is greater than the oil inlet pressure of a control oil port at the lower end of the valve core of the hydraulic reversing valve 3, the valve core moves downwards, and the valve core works upwards; at the moment, after the four-way hydraulic transformer 4 is connected in series with the operating valve 1, the valve plate of the four-way hydraulic transformer 4 is driven to rotate by the valve plate corner oil cylinder 5, the valve plate corner is changed, the transformation ratio of the four-way hydraulic transformer 4 is changed, and therefore the P of the four-way hydraulic transformer 4 is changedAThe pressure of the port is up to the maximum load pressure LS, so that the pressure difference value between the port A and the port F of the operating valve 1 is the difference between the oil supply pressure of the system and the maximum load pressure, the pressure compensation of the operating valve 1 is realized, the movement speed of an actuating element controlled by an oil circuit where the proportional directional valve is located is only related to the opening size of the operating valve 1 and is unrelated to the load pressure, the stability of the movement speed of the actuating element controlled by the operating valve 1 is ensured, and the operability of the equipment is greatly improved; the pressure drop generated on the pressure compensating valve in the traditional hydraulic system is converted into pressure difference energy through the four-way hydraulic transformer 4, and the oil port P is recovered through the pressure difference energyOThe pressure oil port P of the recovery and collection system is directly utilized, so that the throttling loss caused by the use of a pressure compensation valve in the traditional hydraulic system is avoided, and the efficiency of the hydraulic system is improved.
If the load controlled by the circuit in which the proportional reversing valve is positioned is the maximum load in the whole hydraulic system, when the pressure at the F port of the operating valve 1 is not more than the maximum load pressure LS, namely the P of the four-way hydraulic transformer 4AThe pressure of the port is less than or equal toPBWhen the pressure of the port is high, the hydraulic transformer does not work, and when the pressure of the port F of the control valve 1 just exceeds the maximum load pressure LS, the four-way hydraulic transformer 4 still does not work because the high pressure is insufficient to overcome the friction resistance of the four-way hydraulic transformer during operation. At the moment, because the pressure of the control oil port at the upper end of the valve core of the hydraulic reversing valve 3 is smaller than the pressure of the control oil port at the lower end of the valve core of the hydraulic reversing valve 3, the valve core moves upwards, and the valve core works at the lower position; at this time, the port R and the port U of the hydraulic directional valve 3 are communicated, so that the pressure at the port R is the maximum load pressure LS, that is, the pressure at the port F of the pilot valve 1 is the maximum load pressure LS. Under the working condition, after the four-way hydraulic transformer 4 is not connected in series with the operating valve 1, the pressure difference between the port A and the port F of the operating valve 1 is the difference between the oil supply pressure of the system and the maximum load pressure, so that the movement speed of an executing element controlled by an oil circuit where the operating valve 1 is located is only related to the opening size of the operating valve 1 and is unrelated to the load pressure, and the stability of the movement speed of the executing element controlled by the operating valve 1 is ensured; and because the pressure compensation is not needed after the operation valve 1 under the working condition, no throttling loss exists, the oil at the F port of the operation valve 1 crosses the four-way hydraulic transformer 4 and directly controls the speed of the execution element through a passage from the R port to the S port of the hydraulic reversing valve 3, and the pressure loss and the influence on the speed control stability of the execution element caused by the fact that the four-way hydraulic transformer 4 is not needed to recover pressure difference energy under the working condition and the pressure loss is caused by the fact that the four-way hydraulic transformer 4 is connected into a loop in series are avoided.
The invention takes the load of the executive component controlled by the loop where the operating valve 1 is positioned not the maximum load in the whole hydraulic system, the pressure control signal of the port a to make the valve core of the operating valve 1 move to the right and the valve core work to the left as an example to explain the working process of the invention:
the pressure control signal of the pilot valve 1 is constant, the spool displacement and the valve opening amount thereof are constant, and the maximum load pressure LS is constant. The system starts to supply oil, because the valve core of the operating valve 1 works at the left position at the moment, the oil flows to the port F through the port A of the operating valve 1 and then flows to the port P of the four-way hydraulic transformer 4AThe port, the R port of the hydraulic reversing valve 3, the right control oil port of the corner control valve 6, the F port of the operating valve 1 and the P port of the four-way hydraulic transformer 4ARight control of R port and corner control valve 6 of port and hydraulic reversing valve 3The port pressures remain equal. Then the oil supply liquid of the system is filled in the oil passage, and as the system continues to supply oil, the F port of the valve 1 (P of the four-way hydraulic transformer 4) is operatedAThe port, the R port of the hydraulic reversing valve 3 and the right control oil port of the corner control valve 6) gradually rise, when the P of the four-way hydraulic transformer 4AThe port pressure is higher than the load pressure of the actuator, i.e. P of the four-way hydraulic transformer 4BThe pressure of the port (the higher pressure is enough to overcome the frictional resistance when the four-way hydraulic transformer 4 is operated, and PAThe pressure of the port is less than the maximum load pressure LS), the four-way hydraulic transformer operates, and the pressure of the port is less than the maximum load pressure LS), and the four-way hydraulic transformer 4 is operated at this timeAThe port pressure is less than the maximum load pressure LS, similarly, the valve core of the hydraulic reversing valve 3 moves down when the oil inlet pressure of the lower control port of the hydraulic reversing valve 3 is less than the oil inlet pressure (maximum load pressure LS) of the upper control port of the hydraulic reversing valve 3, and the valve core of the hydraulic reversing valve 3 works upwards, namely, the ports R, S and U of the hydraulic reversing valve 3 are not communicated with each other. Meanwhile, the oil inlet pressure of a right control oil port of the corner oil cylinder control valve 6 is smaller than the oil inlet pressure (maximum load pressure LS) of a left control oil port of the corner oil cylinder control valve 6, at the moment, a valve core of the corner oil cylinder control valve 6 moves rightwards, the valve core works leftwards, system oil is supplied to enter a left cavity of the valve plate corner oil cylinder 5, a piston of the valve plate corner oil cylinder 5 moves rightwards, a valve plate of the four-way hydraulic transformer 4 is driven to rotate, the valve plate control angle of the four-way hydraulic transformer 4 is reduced, and therefore the transformation ratio of the four-way hydraulic transformer 4 is reducedBMouth, POMouth, PTThe port pressure is constant, and the P of the four-way hydraulic transformer 4 is defined according to the transformation ratio of the four-way hydraulic transformer 4AThe port pressure rises until the P of the four-way hydraulic transformer 4AThe port pressure is equal to the maximum load pressure LS, the oil inlet pressure of the left control oil port and the oil inlet pressure of the right control oil port of the corner control valve 6 are equal at the moment, under the action of centering springs at two ends of the corner control valve 6, the middle position of the valve core of the corner control valve 6 works, the control angle of the valve plate of the four-way hydraulic transformer 4 is not changed, namely the P of the four-way hydraulic transformer 4AThe port pressure remains constant, equal to the maximum load pressure LS.
Thereafter, case 1: if the execution element is loadedPressure increase, i.e. P of the four-way hydraulic transformer 4BThe pressure of the port rises, and at the moment, the transformation ratio of the four-way hydraulic transformer 4 is unchanged, so that the P of the four-way hydraulic transformer 4 is constantAThe port pressure rises along with the rising of the port pressure to be larger than the maximum load pressure LS, namely the oil inlet pressure of the right end control oil port of the corner control valve 6 is larger than the oil inlet pressure of the left end control oil port of the corner control valve 6, the valve core of the corner control valve 6 moves leftwards, the valve core works at the right position, the system supplies oil to enter the right cavity of the valve plate corner oil cylinder 5, the piston of the valve plate corner oil cylinder 5 moves leftwards to drive the valve plate of the four-way hydraulic transformer 4, the valve plate control angle of the four-way hydraulic transformer 4 is increased, and therefore the transformation ratio of the four-way hydraulic transformer 4 is increasedBMouth, POMouth, PTThe port pressure is constant, and the P of the four-way hydraulic transformer 4 can be known according to the transformation ratio formula of the four-way hydraulic transformer 4AThe port pressure is reduced until the P of the four-way hydraulic transformer 4AThe port pressure is equal to the maximum load pressure LS, the oil inlet pressure of the left control oil port and the oil inlet pressure of the right control oil port of the corner control valve 6 are equal at the moment, under the action of centering springs at two ends of the corner control valve 6, the middle position of the valve core of the corner control valve 6 works, the control angle of the valve plate of the four-way hydraulic transformer 4 is not changed, namely the P of the four-way hydraulic transformer 4AThe port pressure is kept constant and equal to the maximum load pressure LS, and the differential pressure between the ports a and F of the pilot valve 1 is the difference between the system supply pressure and the maximum load pressure LS.
Thereafter, case 2: if the load pressure of the actuator is reduced, P of the four-way hydraulic transformer 4BThe port pressure is reduced, and at the moment, the transformation ratio of the four-way hydraulic transformer 4 is unchanged, so that the P of the four-way hydraulic transformer 4 is reducedAThe port pressure is reduced to be smaller than the maximum load pressure LS, namely the oil inlet pressure of the left end control oil port of the corner control valve 6 is larger than the oil inlet pressure of the right end control oil port of the corner control valve 6, the valve core of the corner control valve 6 moves to the right, the valve core works to the left, the system supplies oil to enter the left cavity of the valve plate corner oil cylinder 5, the piston of the valve plate corner oil cylinder 5 moves to the right, the valve plate is driven to rotate, the valve plate control angle of the four-way hydraulic transformer 4 is reduced, and therefore the four-way hydraulic transformer is reduced4 transformation ratio, four-way hydraulic transformer 4P due to this momentBMouth, POMouth, PTThe port pressure is not changed, and the four-way hydraulic transformer 4P can be known according to the transformation ratio formula of the four-way hydraulic transformer 4AThe port pressure rises until the P of the four-way hydraulic transformer 4AThe port pressure is equal to the maximum load pressure LS, the oil inlet pressure of the left control oil port and the oil inlet pressure of the right control oil port of the corner control valve 6 are equal at the moment, under the action of centering springs at two ends of the corner control valve 6, the middle position of the valve core of the corner control valve 6 works, the control angle of the valve plate of the four-way hydraulic transformer 4 is not changed, namely the four-way hydraulic transformer 4PAThe port pressure is kept constant and equal to the maximum load pressure LS, and the differential pressure between the ports a and F of the pilot valve 1 is the difference between the system supply pressure and the maximum load pressure LS.
According to the analysis, no matter the load pressure of the execution element connected with the loop where the operating valve is located is increased or reduced, the valve plate is driven to rotate by the valve plate corner oil cylinder 5, the size of the control angle of the valve plate is rapidly adjusted, and therefore the transformation ratio of the four-way hydraulic transformer 4 is changed, and the P of the four-way hydraulic transformer 4 is enabled to be higher than the P of the four-way hydraulic transformer 4AThe pressure of the port is equal to the maximum load pressure LS, so that the pressure difference between the port A and the port F of the operating valve 1 is kept to be the difference between the oil supply pressure of the system and the maximum load pressure LS, and the pressure compensation of the operating valve 1 is realized. Thereby ensuring that the movement speed of the actuator is only related to the opening of the operating valve and is not influenced by the load change of the actuator; and the four-way hydraulic transformer 4 will transform PAMouth and PBThe pressure difference (difference between the maximum load pressure and the load of the actuator) is converted into pressure difference energy, and the pressure difference energy is recovered through the recovery oil port POThe oil supply path of the afflux system is directly utilized, and energy conservation is realized.
The working principle analysis of the circuit connecting execution element where other operating valves are located is similar, and the working principle is not described in detail.
Claims (4)
1. The utility model provides an energy-conserving proportional reversing valve based on compensation behind four-way hydraulic transformer valve which characterized in that: comprises a four-way hydraulic transformer (4) and an operating valve (1) which is connected into a hydraulic system and corresponds to an actuating element, wherein the operating valve (1) is provided with a working oil port A, B, C, D,E and F; the four-way hydraulic transformer (4) is provided with a high-pressure oil inlet PALow pressure oil outlet PBAnd a recovery oil outlet POAnd a low pressure suction port PTWhen the load pressure of an executing element controlled by a loop where the operating valve (1) is located is not the maximum load pressure LS of the hydraulic system, the four-way hydraulic transformer (4) is connected in series with the operating valve (1) and connected into the hydraulic system, and the transformation ratio of the four-way hydraulic transformer (4) is adjusted until the high-pressure oil inlet P is connected to the high-pressure oil inletAThe pressure of the four-way hydraulic transformer (4) reaches the maximum load pressure LS of the hydraulic system, and the recovered hydraulic energy of the four-way hydraulic transformer (4) is POThe port is converged with a pressure oil port P for supplying oil to a hydraulic system for use; when the load pressure of an executive component controlled by a loop where the operating valve (1) is located is the maximum load pressure LS of the hydraulic system, the four-way hydraulic transformer (4) is not connected into the hydraulic system; the hydraulic control valve is characterized by further comprising a hydraulic reversing valve (3), the hydraulic reversing valve (3) is a two-position three-way reversing valve with three working oil ports R, S and U, the position of a valve core of the hydraulic reversing valve (3) is controlled through pressure difference of two control oil ports of the hydraulic reversing valve (3), the two control oil ports are respectively connected with the maximum load pressure LS of a hydraulic system and the F port of an operating valve, the U port of the hydraulic reversing valve (3) is connected with the maximum load pressure LS of the hydraulic system, the R port of the hydraulic reversing valve (3) is connected with the F port of the operating valve (1), and series connection of the operating valve (1) and a four-way hydraulic transformer (4) is achieved by switching the working position of the hydraulic reversing valve (3).
2. The energy-saving proportional reversing valve based on four-way hydraulic transformer valve post-compensation of claim 1, characterized in that: the hydraulic control system is characterized by further comprising a valve plate corner oil cylinder (5) and a corner control valve (6), wherein the corner control valve (6) is a three-position four-way proportional valve with four working oil ports G, H, J and K, the position of a valve core of the corner control valve (6) is controlled through pressure difference of two control oil ports of the corner control valve (6), the two control oil ports are respectively connected with the maximum load pressure LS of a hydraulic system and the F port of an operating valve (1), the G port of the corner control valve (6) is connected with an oil return port T of the hydraulic system, the H port of the corner control valve (6) is connected with a pressure oil port P, and the J port and the K port of the corner control valve (6) are respectively connected with left and right piston rod cavities of the valve plate corner oil cylinder (5; after the four-way hydraulic transformer (4) is connected with the operating valve (1) in series and connected into a hydraulic system, the four-way hydraulic transformer (4) is controlled by the valve plate corner oil cylinder (5) to change the transformation ratio.
3. The energy-saving proportional reversing valve based on four-way hydraulic transformer valve post-compensation of claim 2, wherein: the four-way hydraulic transformer (4) is a plunger type oil inlet and outlet flow four-way hydraulic transformer, a left piston and a right piston of a valve plate corner oil cylinder (5) move to drive a valve plate to rotate, the control angle of the valve plate is changed, and a recovery oil outlet P is changedOAnd a low pressure suction port PTDifferential pressure and high pressure oil inlet PAAnd a low pressure oil outlet PBThe pressure difference ratio realizes the pressure change.
4. The energy-saving proportional reversing valve based on four-way hydraulic transformer valve post-compensation of claim 1, characterized in that: the overload protection valve further comprises a first overload valve (2a), a second overload valve (2b), a first check valve (7a) and a second check valve (7b), wherein the first overload valve (2a) is provided with two working oil ports M1 and N1, an M1 port is connected with a D port of the operating valve, an N1 port is connected with an oil return port T, the second overload valve (2b) is provided with two working oil ports M2 and N2, an M2 port is connected with an E port of the operating valve, and an N2 port is connected with the oil return port T; p for recovering hydraulic energy of four-way hydraulic transformerOThe pressure oil ports P and P are connected with a second one-way valve (7b) throughBThe port is connected with a port C of the operating valve through a first one-way valve (7 a); and a piston rod cavity of the load oil cylinder (8) is connected with an E port of the operating valve, and a piston cavity is connected with a D port of the operating valve.
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| CN201910154629.4A CN109695601B (en) | 2019-03-01 | 2019-03-01 | Energy-saving proportional reversing valve based on four-way hydraulic transformer valve post compensation |
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| CN201910154629.4A CN109695601B (en) | 2019-03-01 | 2019-03-01 | Energy-saving proportional reversing valve based on four-way hydraulic transformer valve post compensation |
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106884824A (en) * | 2017-04-07 | 2017-06-23 | 江苏师范大学 | A kind of pressure-transforming energy-saving threeway proportional flow commutator |
| CN106949104A (en) * | 2017-04-07 | 2017-07-14 | 江苏师范大学 | A kind of plunger type enters fuel-displaced flow four-way hydraulic transformer of Denging |
| CN108278232A (en) * | 2018-02-05 | 2018-07-13 | 浙江大学 | A kind of passive heave compensation system of hydraulic cylinder type based on hydraulic transformer |
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2019
- 2019-03-01 CN CN201910154629.4A patent/CN109695601B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106884824A (en) * | 2017-04-07 | 2017-06-23 | 江苏师范大学 | A kind of pressure-transforming energy-saving threeway proportional flow commutator |
| CN106949104A (en) * | 2017-04-07 | 2017-07-14 | 江苏师范大学 | A kind of plunger type enters fuel-displaced flow four-way hydraulic transformer of Denging |
| CN108278232A (en) * | 2018-02-05 | 2018-07-13 | 浙江大学 | A kind of passive heave compensation system of hydraulic cylinder type based on hydraulic transformer |
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Address after: 221011 No. 2 Yucai Road, Jiawang District, Jiangsu, Xuzhou Patentee after: Jiangsu Normal University Address before: 221116 No. 101, Shanghai Road, Copper Mt. New District, Jiangsu, Xuzhou Patentee before: Jiangsu Normal University |
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Granted publication date: 20200529 |