CN115059606A - Load-sensitive pump control loop simulation test system - Google Patents
Load-sensitive pump control loop simulation test system Download PDFInfo
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- CN115059606A CN115059606A CN202210705882.6A CN202210705882A CN115059606A CN 115059606 A CN115059606 A CN 115059606A CN 202210705882 A CN202210705882 A CN 202210705882A CN 115059606 A CN115059606 A CN 115059606A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B51/00—Testing machines, pumps, or pumping installations
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
- F15B19/007—Simulation or modelling
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E30/00—Energy generation of nuclear origin
- Y02E30/30—Nuclear fission reactors
Abstract
The invention discloses a load-sensitive pump control loop simulation test system, wherein the oil outlet of a tested load-sensitive pump in the system is connected with the inlet of a proportional throttle valve, the outlet of the proportional throttle valve is connected with an independent actuator, and is connected with the LS oil port of the tested load-sensitive pump through an independent stop reversing valve and a pressure feedback hose in sequence, the cascade actuator comprises a plurality of shuttle valves, for the first-stage shuttle valve, two comparison ends of the two shuttle valves are respectively connected with the sub-actuator, an output end of the two shuttle valves is connected with one comparison end of the shuttle valve of the previous stage, for other shuttle valves of higher stage, the two comparison ends are respectively connected with the output ends of two shuttle valves in the next stage, and for the highest stage shuttle valve, one comparison end of the pressure feedback hose is connected with the output end of the secondary high-grade shuttle valve, the other comparison end of the pressure feedback hose is connected with the outlet of the proportional throttle valve, and the output end of the pressure feedback hose is connected with the LS oil port of the tested load sensitive pump. The invention can simulate the LS responsiveness test of the load sensitive pump under the multi-load working condition.
Description
Technical Field
The invention belongs to the field of hydraulic tests, and particularly relates to a load-sensitive pump control loop simulation test system.
Background
The load-sensitive pump is widely applied to construction machinery such as an excavator, a crane and the like with a plurality of actuators. The core of the working principle of the load-sensitive pump is constant-current variable-pressure, as shown in figure 1, the pump outlet pressure is P, and the load pressure P of an actuating element is P LS The pump output fluid is directed to the actuator (motor or cylinder) through a main valve orifice across which a pressure differential Δ P-P is provided LS P is acted on the left end of the valve core of the load sensitive valve, and the load pressure P LS And spring preset pressure P K The two components act together on the right end of the valve core of the load sensitive valve, when the load sensitive valve is stressed in balance, namely P K ＝P-P LS At this point the pump is maintained at a steady displacement. When the external load changes, the dynamic delta P is larger or smaller than the preset spring pressure P K At the moment, the stress of the load sensitive valve is in an unbalanced state, and in order to recover to the stress balance state, the valve core of the load sensitive valve moves leftwards or rightwards, so that the inclination angle of the swash plate of the pump is changed, the displacement of the pump is changed, the output flow is increased or decreased, and the delta P is changed into P again K The adjusting process is a Load Sensing (LS) response process. In the system, the load-sensitive pump realizes LS response with a certain time lag, so the research on the LS response performance of the load-sensitive pump needs to be carried outA simulation test system for a load sensitive pump was investigated.
An external pilot pump is introduced into an existing first load sensitive pump test system shown in fig. 2, and the pressure of an LS oil port of a tested load sensitive pump is controlled through a proportional overflow valve, so that the purpose of variably controlling the pressure of the LS oil port of the tested load sensitive pump is achieved. According to the scheme, due to the introduction of the oil of the pilot pump, the oil drainage quantity tested by the oil drainage port of the load sensitive pump contains partial oil drainage of the external pilot pump, and the calculated pump efficiency is inaccurate.
The second load-sensitive pump test system in the prior art is shown in fig. 3, and directly introduces hydraulic oil at an outlet of a tested load-sensitive pump into an LS oil port of the tested load-sensitive pump, so that the problem of inaccurate oil discharge measurement is avoided, but the test system has the defect of nonadjustable pressure of the LS oil port.
In the existing third load-sensitive pump test system, as shown in fig. 4, a variable frequency motor drives a tested load-sensitive pump, a first flow meter detects the output flow of the tested load-sensitive pump, a proportional overflow valve loads the pump, and the pump is loaded by an instruction signal in a proportional control manner. When the first cut-off reversing valve of the bypass is opened, high-pressure oil output by the tested load sensitive pump can enter the LS oil port of the load sensitive pump, and the LS oil port can control oil to be introduced by the tested load sensitive pump. And opening the second stop reversing valve, and adjusting the opening of the proportional flow control valve to realize the purpose of variably controlling the pressure of the LS oil port of the tested load sensitive pump. The limitation of the existing solution is that the influence of the response delay of the multi-actuator shuttle valve network on the response of the load sensitive pump LS is not considered.
Disclosure of Invention
The invention mainly solves the technical problem of providing a load-sensitive pump control loop simulation test system to solve the problem that when a multi-actuator is connected into a load-sensitive pump control system and is provided with a shuttle valve, the influence of response delay of the shuttle valve and pipelines with different lengths on the LS response performance of a load-sensitive pump cannot be tested.
In order to solve the technical problems, the invention adopts the technical scheme that a load-sensitive pump control loop simulation test system is provided, which comprises a tested load-sensitive pump, a proportional throttle valve, an independent stop reversing valve, a pressure feedback hose, an independent actuator and a cascade actuator, wherein an oil outlet of the tested load-sensitive pump is connected with an inlet of the proportional throttle valve, an outlet of the proportional throttle valve is connected with the independent actuator and is connected with a pressure feedback LS oil port of the tested load-sensitive pump sequentially through the independent stop reversing valve and the pressure feedback hose, the cascade actuator comprises a plurality of shuttle valves, for a first-stage shuttle valve, two comparison ends of the first-stage shuttle valve are respectively connected with corresponding sub-actuators, an output end of the first-stage shuttle valve is connected with a comparison end of a previous-stage shuttle valve, for other higher-stage shuttle valves, two comparison ends of the first-stage shuttle valve are respectively connected with output ends of corresponding two shuttle valves in a next-stage shuttle valve, for the highest-level shuttle valve, one comparison end of the highest-level shuttle valve is connected with the output end of the second-level shuttle valve, the other comparison end of the highest-level shuttle valve is connected with the outlet of the proportional throttle valve, and the output end of the highest-level shuttle valve is connected with the LS oil port of the tested load sensitive pump through the pressure feedback hose; each sub actuator comprises a stop reversing valve, a proportional overflow valve and a hydraulic pump; the independent actuator comprises a proportional overflow valve; the proportional overflow valve is used for adjusting the overflow pressure output by the corresponding actuator; the shuttle valve compares the overflow pressure input by the comparison end of the shuttle valve, and selects oil with higher overflow pressure to output;
controlling the independent stop reversing valves and the stop reversing valves in the sub-actuators to enable the actuators of different numbers in any combination to be connected into the LS oil ports of the tested load sensitive pump through pressure feedback hoses; and a sensor is arranged at a corresponding position, and the influence of response delay of a shuttle valve and a pressure feedback hose on LS response performance in a tested load sensitive pump control loop is simulated and tested according to data detected by the sensor.
In an optional implementation manner, when the independent cut-off and reversing valve is switched on, the tested load-sensitive pump, the proportional throttle valve, the independent cut-off and reversing valve and the pressure feedback hose form a tested load-sensitive pump control loop, and a test load-sensitive pump LS response performance simulation test only with the independent actuator is realized, wherein the tested load-sensitive pump control loop is not provided with a shuttle valve and is only provided with the pressure feedback hose, so that the influence of the response delay of the pressure feedback hose on the LS response performance can be simulated and tested for the pressure feedback hoses with different lengths;
when the independent cut-off reversing valve is disconnected, the tested load sensitive pump, the proportional throttle valve, the highest-level shuttle valve and the pressure feedback hose form a tested load sensitive pump control loop, the LS response performance simulation test of the tested load sensitive pump with at least one sub-actuator in the cascade actuator is realized, and the shuttle valve and the pressure feedback hose exist in the tested load sensitive pump control loop at the same time, so that the influence of the response delay of the tested shuttle valve and the pressure feedback hose with the corresponding length on the LS response performance can be simulated.
In another optional implementation manner, the independent actuator further comprises a cut-off and reversing valve, the cut-off and reversing valve and the proportional overflow valve are connected in parallel, the first parallel node of the cut-off and reversing valve is connected with the outlet of the proportional throttle valve, and when the independent cut-off and reversing valve is disconnected, the cut-off and reversing valve in the independent actuator can be controlled, so that the independent actuator is or is not arranged in a tested load sensitive pump control loop formed by the tested load sensitive pump, the proportional throttle valve, the highest-stage shuttle valve and the pressure feedback hose.
In another optional implementation manner, a second parallel node of a stop reversing valve and a proportional overflow valve in the independent actuator is communicated with an oil tank;
for each sub-actuator, a stop reversing valve and a proportional overflow valve in the sub-actuator are connected in parallel, a first parallel node of the sub-actuator is respectively connected with a corresponding comparison end of a first-stage shuttle valve and a first end of a corresponding hydraulic pump, a second parallel node of the sub-actuator is communicated with the oil tank, and a second end of the hydraulic pump is also communicated with the oil tank.
In another optional implementation mode, the proportional throttle valve is further connected with a cut-off reversing valve in parallel, and when the cut-off reversing valve connected with the proportional throttle valve in parallel and the cut-off reversing valve in the independent actuator are simultaneously opened, unloading of the tested load-sensitive pump is achieved.
In another optional implementation mode, the device further comprises a motor and a torque and rotation speed sensor, wherein the motor drives the sensitive pump to be tested through the torque and rotation speed sensor;
the oil outlet of the tested load sensitive pump is connected with the inlet of the proportional throttle valve sequentially through the one-way valve and the filter;
a stop valve is arranged between an oil inlet of the tested load sensitive pump and the oil tank;
and a second parallel node of a stop reversing valve and a proportional overflow valve in the independent actuator is communicated with the oil tank through a cooler.
In another optional implementation manner, pressure sensors are respectively arranged at an oil outlet of the tested load sensitive pump, an inlet and an outlet of the proportional throttle valve, an LS oil outlet of the tested load sensitive pump, and output ends of shuttle valves of other stages except the highest stage shuttle valve, and each pressure sensor is used for detecting a pressure change condition corresponding to each link, and analyzing the influence of response delay of the shuttle valve and the pressure feedback hose on the LS response performance according to the pressure change condition of each link.
In another optional implementation manner, a first flow meter is arranged between an oil drain port of the tested load-sensitive pump and an oil tank and is used for measuring the oil discharge flow of the tested load-sensitive pump;
a second flowmeter is arranged at the inlet of the proportional throttle valve;
and a third flow meter is arranged at an LS oil port of the tested load sensitive pump.
In another alternative implementation manner, the connecting node of the one-way valve and the filter is communicated with the oil tank through an overflow valve, so that when the pressure of the oil outlet of the tested load-sensitive pump is abnormally increased, the oil is discharged through the overflow valve.
The invention has the beneficial effects that:
the invention can simulate that a single independent actuator without a shuttle valve is connected into a tested load sensitive pump control loop, and also can simulate that one or a plurality of combined sub-actuators with the shuttle valve are connected into the tested load sensitive pump control loop, and a pressure feedback hose is introduced into the tested load sensitive pump control loop, so that the invention can simulate response time, and test the influence of response delay of the shuttle valve and a pipeline on LS response performance when different numbers of combined actuators are connected; in addition, the relief pressure of the connected actuator is adjustable.
Additional advantages, objects, and features of the invention will be set forth in part in the description which follows and in part will become apparent to those having ordinary skill in the art upon examination of the following or may be learned from practice of the invention. The objectives and other advantages of the invention may be realized and attained by the means of the instrumentalities and combinations particularly pointed out hereinafter.
Drawings
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be further described in detail with reference to the accompanying drawings, in which:
FIG. 1 is a schematic diagram of the operation of a load sensitive pump;
FIG. 2 is a schematic diagram of a conventional load-sensitive pump test system;
FIG. 3 is a schematic diagram of another prior art load-sensitive pump test system;
FIG. 4 is a schematic diagram of another prior art load sensitive pump test system configuration;
FIG. 5 is a schematic structural diagram of an embodiment of a load-sensitive pump control loop simulation test system according to the present invention;
FIG. 6 is a schematic structural diagram of another embodiment of a load-sensitive pump control loop simulation test system according to the present invention;
fig. 7 is a schematic structural diagram of a load-sensitive pump control loop simulation test system according to another embodiment of the present invention.
Detailed Description
The embodiments of the present invention are described below with reference to specific embodiments, and other advantages and effects of the present invention will be easily understood by those skilled in the art from the disclosure of the present specification. The invention is capable of other and different embodiments and of being practiced or of being carried out in various ways, and its several details are capable of modification in various respects, all without departing from the spirit and scope of the present invention. It should be noted that the drawings provided in the following embodiments are only for illustrating the basic idea of the present invention in a schematic way, and the features in the following embodiments and examples may be combined with each other without conflict.
Wherein the showings are for the purpose of illustrating the invention only and not for the purpose of limiting the same, and in which there is shown by way of illustration only and not in the drawings in which there is no intention to limit the invention thereto; to better illustrate the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.
Referring to fig. 5, a schematic structural diagram of an embodiment of the load-sensitive pump control loop simulation test system of the present invention is shown. The load-sensitive pump control loop simulation test system can comprise a tested load-sensitive pump, a proportional throttle valve, an independent stop reversing valve, a pressure feedback hose, an independent actuator and a cascade actuator, wherein an oil outlet of the tested load-sensitive pump is connected with an inlet of the proportional throttle valve, an outlet of the proportional throttle valve is connected with the independent actuator and is connected with a pressure feedback oil port LS of the tested load-sensitive pump sequentially through the independent stop reversing valve and the pressure feedback hose, the cascade actuator comprises a plurality of shuttle valves, two comparison ends of a first-stage shuttle valve are respectively connected with corresponding sub-actuators, an output end of the first-stage shuttle valve is connected with one comparison end of a previous-stage shuttle valve, two comparison ends of other higher-stage shuttle valves are respectively connected with output ends of two corresponding shuttle valves in a next stage, and for a highest-stage shuttle valve, one comparison end of the highest-stage shuttle valve is connected with an output end of a next-stage shuttle valve, the other comparison end is connected with an outlet of the proportional throttle valve, and the output end is connected with an LS oil port of the tested load sensitive pump through the pressure feedback hose; each sub actuator comprises a stop reversing valve, a proportional overflow valve and a hydraulic pump; the independent actuator comprises a proportional overflow valve; the proportional overflow valve is used for adjusting the overflow pressure output by the corresponding actuator; the shuttle valve compares the overflow pressure input by the comparison end of the shuttle valve, and selects oil with higher overflow pressure to output; controlling the independent stop reversing valves and the stop reversing valves in the sub actuators to enable the actuators in different numbers in any combination to be connected to the LS oil ports of the tested load sensitive pump through pressure feedback hoses; and a sensor is arranged at a corresponding position, and the influence of the response delay of the shuttle valve and the pressure feedback hose on the LS response performance in the tested load sensitive pump control loop is simulated and tested according to the data detected by the sensor.
In this embodiment, when the independent cut-off and reversing valve is turned on, the tested load sensitive pump, the proportional throttle valve, the independent cut-off and reversing valve and the pressure feedback hose constitute a tested load sensitive pump control loop, so that a test on the LS response performance of the tested load sensitive pump with only the independent actuator is realized, and the tested load sensitive pump control loop is not provided with a shuttle valve and is only provided with the pressure feedback hose, so that the influence of the response delay of the pressure feedback hose on the LS response performance can be simulated and tested for the pressure feedback hoses with different lengths; when the independent cut-off reversing valve is disconnected, the tested load sensitive pump, the proportional throttle valve, the highest-level shuttle valve and the pressure feedback hose form a tested load sensitive pump control loop, the LS response performance simulation test of the tested load sensitive pump with at least one sub-actuator in the cascade actuator is realized, and the shuttle valve and the pressure feedback hose exist in the tested load sensitive pump control loop at the same time, so that the influence of the response delay of the tested shuttle valve and the pressure feedback hose with the corresponding length on the LS response performance can be simulated.
In fig. 5, the cascade actuator has three stages, the lowest stage is a first stage shuttle valve, the middle stage is a second stage shuttle valve (i.e. other higher stage shuttle valves), the highest stage is a highest stage shuttle valve, two first stage shuttle valves are provided, two comparison ends of the first stage shuttle valves are respectively connected with a sub-actuator, two comparison ends of the second stage shuttle valve are respectively connected with output ends of the two first stage shuttle valves, one comparison end of the highest stage shuttle valve is connected with an output end of the second quaternary shuttle valve, the other comparison end is connected with an outlet of the proportional throttle valve, wherein the first stage shuttle valve compares overflow pressures of the corresponding sub-actuators inputted from the two comparison ends thereof, selects oil with higher overflow pressure to output to the second stage shuttle valve, the second stage shuttle valve compares overflow pressures provided by the two first stage shuttle valves, and also selects oil with higher overflow pressure to output to the highest stage shuttle valve, the highest stage shuttle valve compares overflow pressure provided by the second stage shuttle valve with overflow pressure provided by the independent actuator, and selecting oil with higher overflow pressure, and outputting the oil to the LS oil port of the tested load sensitive pump through the pressure feedback hose. The control method comprises the steps that for each sub-actuator, whether the sub-actuator is connected to a tested load sensitive pump control circuit or not can be controlled by controlling a cut-off reversing valve of the sub-actuator, when the cut-off reversing valve is disconnected, the sub-actuator is connected to the tested load sensitive pump control circuit, when the cut-off reversing valve is connected, the sub-actuator is not connected to the tested load sensitive pump control circuit, and therefore the sub-actuators in different numbers and combined at will can be selected to be connected to the tested load sensitive pump control circuit.
When the independent stop reversing valve is disconnected, the above embodiment can only select the access of each sub-actuator, but cannot select whether to access the independent actuator. When the independent stop reversing valve is disconnected, the stop reversing valve in the independent actuator can be controlled, so that the tested load sensitive pump, the proportional throttle valve, the highest-level shuttle valve and the pressure feedback hose form the tested load sensitive pump control loop with or without the independent actuator. Referring to fig. 6, a second parallel node of the cut-off reversing valve and the proportional overflow valve in the independent actuator is communicated with the oil tank; for each sub-actuator, a stop reversing valve and a proportional overflow valve in the sub-actuator are connected in parallel, a first parallel node of the sub-actuator is respectively connected with a corresponding comparison end of a first-stage shuttle valve and a first end of a corresponding hydraulic pump, a second parallel node of the sub-actuator is communicated with the oil tank, and a second end of the hydraulic pump is also communicated with the oil tank.
It can be seen from the above embodiments that the present invention can simulate that a single independent actuator without a shuttle valve is connected to a tested load-sensitive pump control loop, and can also simulate that one or any combination of a plurality of sub-actuators with shuttle valves is connected to the tested load-sensitive pump control loop, and the present invention introduces a pressure feedback hose into the tested load-sensitive pump control loop, so that the present invention can simulate response time, and test the influence of response delay of the shuttle valve and a pipeline on LS response performance when different numbers of actuators in any combination are connected; in addition, the relief pressure of the connected actuator is adjustable.
Referring to fig. 6, a schematic structural diagram of another embodiment of the load-sensitive pump control loop simulation test system of the present invention is shown. In the embodiment shown in fig. 6, the oil outlet of the tested load sensitive pump 5 is connected to the inlet of the proportional throttle valve 13, the outlet of the proportional throttle valve 13 is connected to the independent actuator, and the pressure feedback LS oil port of the tested load sensitive pump 5 is connected to the pressure feedback LS oil port of the tested load sensitive pump sequentially through the independent stop and change valve 19 and the pressure feedback hose 20.
Unlike the embodiment shown in fig. 5, the cascade actuator in the embodiment shown in fig. 6 has only two stages, and there are two shuttle valves 23 and 27, wherein two comparison ends a and b of the shuttle valve 27 are respectively connected with the two sub-actuators, an output end c is connected with one comparison end b of the shuttle valve 23, the other comparison end a of the shuttle valve 23 is connected with the outlet of the proportional throttle valve 13, and the output end c is connected with the LS port of the tested load sensitive pump 5 through the pressure feedback hose 20. As can be seen from fig. 6, the left sub-actuator comprises a proportional overflow valve 25, a cut-off and reversing valve 30 and a hydraulic pump 24, the proportional overflow valve 25 and the cut-off and reversing valve 30 are connected in parallel, and a first parallel node of the proportional overflow valve 25 and the cut-off and reversing valve 30 is respectively connected with a comparison end a of the shuttle valve 27 and one end of the hydraulic pump 24, a second parallel node is communicated with the oil tank 6, and a second end of the hydraulic pump 24 is also communicated with the oil tank 6; the right sub-actuator includes a hydraulic pump 26, a stop/switch valve 31, and a proportional relief valve 29, and similarly, the stop/switch valve 31 and the proportional relief valve 29 are connected in parallel, and a first parallel node thereof is connected to the other comparison end b of the shuttle valve 27 and a first end of the hydraulic pump 28, respectively, a second parallel node thereof communicates with the tank 6, and a second end of the hydraulic pump 28 also communicates with the tank 6. In addition, the independent actuator in fig. 6 comprises a stop and reversing valve 17 and a proportional overflow valve 15, the stop and reversing valve 17 is connected with the proportional overflow valve 15 in parallel, a first parallel node of the stop and reversing valve is connected with the outlet of the proportional throttle valve 13, and a second parallel node of the stop and reversing valve is communicated with the oil tank 6 through a cooler 18.
When the independent cut-off reversing valve 19 is switched on, the tested load-sensitive pump 5, the proportional throttle valve 13, the independent cut-off reversing valve 19 and the pressure feedback hose 20 form a tested load-sensitive pump control loop, a response performance simulation test of the load-sensitive pump LS only with the independent actuator is realized, no shuttle valve exists in the tested load-sensitive pump control loop, and only the pressure feedback hose 20 exists, so that the influence of the response delay of the pressure feedback hose on the LS response performance can be simulated and tested for the pressure feedback hoses 20 with different lengths; when the independent cut-off reversing valve 19 is disconnected, the tested load-sensitive pump 5, the proportional throttle valve 13, the highest-stage shuttle valve 23 and the pressure feedback hose 20 form a tested load-sensitive pump control loop, the LS response performance simulation test of the tested load-sensitive pump with at least one sub-actuator in the cascade actuator is realized, and the shuttle valve and the pressure feedback hose exist in the tested load-sensitive pump control loop at the same time, so that the influence of the response delay of the tested shuttle valve and the corresponding length of the pressure feedback hose on the LS response performance can be simulated. When the independent stop reversing valve 19 is switched off, if the independent actuator and the left side sub-actuator are connected, the stop reversing valves 17 and 30 are controlled to be switched off, the stop reversing valve 31 is switched on, at the moment, the shuttle valve 23 compares overflow pressures provided by the independent actuator and the left side sub-actuator, and the high overflow pressure corresponds to oil liquid through the pressure feedback hose 20 and is output to the LS oil port of the tested load sensitive pump 5; if the independent actuator and the right sub-actuator are connected, the cut-off reversing valves 17 and 31 are controlled to be disconnected, the cut-off reversing valve 30 is connected, at the moment, the shuttle valve 23 compares overflow pressures provided by the independent actuator and the right sub-actuator, and oil liquid corresponding to higher overflow pressure is output to an LS oil port of the tested load sensitive pump 5 through the pressure feedback hose 20; if the left side sub-actuator and the right side sub-actuator are connected, the stop reversing valves 30 and 31 are controlled to be disconnected, the stop reversing valve 17 is connected, the shuttle valve 23 compares the overflow pressures provided by the left side sub-actuator and the left side sub-actuator at the moment, and the high overflow pressure corresponds to oil liquid which is output to the LS oil port of the tested load sensitive pump 5 through the pressure feedback hose 20; if the independent actuator and the left and right side sub-actuators are connected at the same time, the cut-off reversing valves 17, 30 and 31 can be controlled to be disconnected, at the moment, the shuttle valve 27 compares overflow pressures provided by the left side sub-actuator and the right side sub-actuator, oil liquid corresponding to higher overflow pressure is output to the shuttle valve 23, the shuttle valve 23 compares the overflow pressure of the oil liquid input from the comparison end b with the overflow pressure provided by the independent actuator, and the oil liquid corresponding to higher overflow pressure is output to the LS oil port of the tested load sensitive pump 5 through the pressure feedback hose 20; if only the left actuator is switched on, the stop reversing valves 17 and 31 can be switched on, and the stop reversing valve 30 is switched off; if only the right actuator is to be switched on, the cut-off selector valves 17 and 30 can be switched on and the cut-off selector valve 31 can be switched off. Therefore, the independent cut-off and reversing valves, the cut-off and reversing valves in the independent actuators and the cut-off and reversing valves in the sub actuators are controlled, so that different numbers of actuators with any combination of shuttle valves can be connected into the tested load sensitive pump control circuit, or only the independent actuators without the shuttle valves can be connected into the tested load sensitive pump control circuit.
Unlike the embodiment shown in fig. 5, in the embodiment shown in fig. 6, the proportional throttle valve 13 is also connected in parallel with a cut-off and direction-changing valve 14, and when the cut-off and direction-changing valve 14 connected in parallel with the proportional throttle valve 13 and the cut-off and direction-changing valve 17 in the independent actuator are simultaneously switched on, unloading of the tested load-sensitive pump 5 can be realized. According to the invention, the cut-off reversing valve is arranged in parallel with the proportional throttle valve, and the cut-off reversing valve is arranged in parallel with the proportional overflow valve in the independent actuator, so that the two cut-off reversing valves are controlled to be disconnected simultaneously, the tested load sensitive pump can be conveniently and rapidly unloaded, and the test safety and the test efficiency are ensured. In addition, the invention also comprises a motor 1 and a torque and rotation speed sensor 2, wherein the motor 1 drives the sensitive pump to be tested 5 through the torque and rotation speed sensor 2; the oil outlet of the tested load sensitive pump 5 is connected with the inlet of the proportional throttle valve 13 sequentially through the check valve 8 and the filter 10, the oil output from the oil outlet of the tested load sensitive pump 5 forms a pressure difference through the check valve 8, the filter 10 and the proportional throttle valve 13, and the pressure difference can be further adjusted by adjusting the opening degree of the proportional throttle valve 13; a stop valve 4 is arranged between an oil inlet of the tested load sensitive pump 5 and the oil tank 6; and a second parallel node of a stop reversing valve 17 and a proportional overflow valve 15 in the independent actuator is communicated with the oil tank 6 through a cooler 18. The oil outlet of the tested load sensitive pump 5 is provided with a pressure sensor 7, the inlet and the outlet of the proportional throttle valve 13 are respectively provided with pressure sensors 11 and 16, the LS oil port of the tested load sensitive pump 5 is provided with a pressure sensor 22, the output ends of the shuttle valves of other stages except the highest stage are respectively provided with a pressure sensor (for example, the output end c of the shuttle valve 26 in fig. 6 is provided with a pressure sensor 26), each pressure sensor is used for detecting the pressure change condition of each link, and the influence of the response delay of the shuttle valve and the pressure feedback hose on the LS response performance is analyzed according to the pressure change condition of each link. A first flow meter 3 is arranged between an oil drainage port of the tested load sensitive pump 5 and an oil tank 6 and is used for measuring the oil discharge flow of the tested load sensitive pump 5; a second flowmeter 12 is arranged at the inlet of the proportional throttle valve 13 and is used for measuring the flow at the inlet of the proportional throttle valve 13; and a third flow meter 21 is arranged at the LS oil port of the tested load sensitive pump 5 and is used for measuring the flow at the LS oil port of the tested load sensitive pump. According to the invention, by arranging the first flow meter, the oil drainage quantity of the tested load sensitive pump can be accurately measured. And the connecting node of the one-way valve 8 and the filter 10 is communicated with the oil tank 6 through an overflow valve 9, so that when the pressure of the oil outlet of the tested load sensitive pump 5 is abnormally increased, the oil is discharged through the overflow valve 9.
Although the above embodiments can realize that different numbers of sub-actuators in any combination are connected to the tested load-sensitive pump control circuit, since the sub-actuators are connected in a cascade manner through the shuttle valves, each sub-actuator is connected through the same number of shuttle valves, for example, each sub-actuator in fig. 5 needs to be connected to the tested load-sensitive pump control circuit through three shuttle valves. In order to conveniently and individually adjust the number of the shuttle valves passed by each connected sub-actuator, the cascade actuator is further improved. As shown in fig. 7, taking a three-stage cascade actuator as an example, for each shuttle valve except for the third stage shuttle valve, the left comparison end of the left shuttle valve is connected with the first end of the corresponding left three-way valve, the right comparison end of the left shuttle valve is connected with the first end of the corresponding right three-way valve, the second end of the left first-stage shuttle valve corresponding to the left three-way valve is connected with a sub-actuator, the third end is connected with the first end of the vertical three-way valve, the second end of the left first-stage shuttle valve corresponding to the right three-way valve is connected with another sub-actuator, the third end is connected with the second end of the second-stage shuttle valve corresponding to the left three-way valve, the third end of the second-stage shuttle valve, which corresponds to the left three-way valve, is connected with the second end of the vertical three-way valve, the third end of the vertical three-way valve is connected with the left comparison end of the third-stage shuttle valve, the output end of the left first-stage shuttle valve is connected with the third end of the second-stage shuttle valve corresponding to the left three-way valve. For the right first-stage shuttle valve, the second end of the right first-stage shuttle valve, which corresponds to the left three-way valve, is connected with a sub-actuator, the third end of the right first-stage shuttle valve is connected with the second end of the second-stage shuttle valve, which corresponds to the right three-way valve, the second end of the right first-stage shuttle valve, which corresponds to the right three-way valve, is connected with another sub-actuator, the third end of the right first-stage shuttle valve is connected with the third end of the second-stage shuttle valve, which corresponds to the right three-way valve, and the output end of the right first-stage shuttle valve is connected with the third end of the second-stage shuttle valve, which corresponds to the right three-way valve. The second end of the right first-stage shuttle valve corresponding to the left three-way valve is connected with the second end of the left three-way valve corresponding to the left first-stage shuttle valve through a stop reversing valve, and the second end of the right first-stage shuttle valve corresponding to the right three-way valve is connected with the second end of the right three-way valve corresponding to the left first-stage shuttle valve through another stop reversing valve. The right comparison end of the third-stage shuttle valve is connected with the outlet of the proportional throttle valve, and the output end of the third-stage shuttle valve is connected with the tested load sensitive pump through a pressure feedback hose.
Wherein, through controlling each three-way valve and cut-off reversing valve in the cascade actuator, can make the left side comparison end of the third level shuttle valve realize following five kinds of condition: 1) the sub-actuator can be connected into a tested load sensitive pump control loop through the shuttle valve of the third-stage shuttle valve; 2) the sub-actuator can be connected into a tested load sensitive pump control loop through the second-stage shuttle valve and the third-stage shuttle valve; 3) the two sub actuators can be connected into a tested load sensitive pump control loop through the second-stage shuttle valve and the third-stage shuttle valve; 4) the three sub-actuators can be connected into a tested load sensitive pump control loop through the three shuttle valves, namely the first-stage shuttle valve, the second-stage shuttle valve and the third-stage shuttle valve; 5) any number of sub-actuators in the four sub-actuators can be connected to the tested load-sensitive pump control circuit through the three shuttle valves, namely the first-stage shuttle valve, the second-stage shuttle valve and the third-stage shuttle valve, and the method can be realized through the embodiment shown in fig. 5.
When the first condition is realized, which sub-actuator is connected can be firstly determined, and for the first sub-actuator from left to right, the corresponding three-way valve in the cascade actuator is controlled, so that the oil output by the first sub-actuator is provided to the left comparison end of the third-stage shuttle valve through the left three-way valve and the vertical three-way valve corresponding to the left first-stage shuttle valve in sequence; for the second sub-actuator from left to right, controlling a corresponding three-way valve in the cascade actuator to enable oil output by the second sub-actuator to sequentially pass through a right three-way valve corresponding to the first-stage shuttle valve on the left side, a left three-way valve corresponding to the second-stage shuttle valve and a vertical three-way valve to be supplied to a left comparison end of the third-stage shuttle valve; for a third sub-actuator from left to right, controlling a corresponding three-way valve and a corresponding stop reversing valve in the cascade actuator, and enabling oil output by the third sub-actuator to be sequentially provided to a left comparison end of a third-stage shuttle valve through the stop reversing valve, a left three-way valve corresponding to a left first-stage shuttle valve and a vertical three-way valve; and for the fourth sub-actuator from left to right, controlling a corresponding three-way valve and a corresponding stop reversing valve in the cascade actuator, so that the oil output by the fourth sub-actuator sequentially passes through the corresponding stop reversing valve, a right three-way valve corresponding to the left first-stage shuttle valve, a left three-way valve corresponding to the second-stage shuttle valve and a vertical three-way valve and is provided for the left comparison end of the third-stage shuttle valve.
When the second situation is realized, which sub-actuator is connected can be firstly determined, and for the first sub-actuator from left to right, the corresponding three-way valve in the cascade actuator is controlled, so that the oil output by the first sub-actuator sequentially passes through the left three-way valve corresponding to the left first-stage shuttle valve, the vertical three-way valve, the left three-way valve corresponding to the second-stage shuttle valve and is provided for the left comparison end of the third-stage shuttle valve; for the second sub-actuator from left to right, the corresponding three-way valve in the cascade actuator is controlled, so that the oil output by the second sub-actuator is provided to the left comparison end of the third-stage shuttle valve through the right three-way valve corresponding to the left first-stage shuttle valve, the left three-way valve corresponding to the second-stage shuttle valve and the second-stage shuttle valve in sequence; for a third sub-actuator from left to right, controlling a corresponding three-way valve in the cascade actuator to enable oil output by the third sub-actuator to sequentially pass through a left three-way valve corresponding to a right first-stage shuttle valve, a right three-way valve corresponding to a second-stage shuttle valve and the second-stage shuttle valve to be provided for a left comparison end of a third-stage shuttle valve; and for the fourth sub-actuator from left to right, controlling a corresponding three-way valve in the cascade actuator to enable the oil output by the fourth sub-actuator to sequentially pass through a right three-way valve corresponding to the right first-stage shuttle valve, a right three-way valve corresponding to the second-stage shuttle valve and the second-stage shuttle valve to be provided to the left comparison end of the third-stage shuttle valve.
When the third situation is realized, whether the two sub-actuators are connected with the same first-stage shuttle valve or not can be judged firstly, if the two sub-actuators are the same and are the first sub-actuator and the second sub-actuator from left to right, the corresponding three-way valve and the corresponding cut-off reversing valve in the cascade actuator are controlled, oil output by the first sub-actuator is enabled to sequentially pass through the cut-off reversing valve, the left three-way valve corresponding to the first-stage shuttle valve on the right side, the right three-way valve corresponding to the second-stage shuttle valve and be connected with the right comparison end of the second-stage shuttle valve, oil output by the second sub-actuator is enabled to sequentially pass through the right three-way valve corresponding to the first-stage shuttle valve on the left side and the left three-way valve corresponding to the second-stage shuttle valve and be connected with the left comparison end of the third-stage shuttle valve; if the two sub-actuators are the same and are a third sub-actuator and a fourth sub-actuator from left to right, the corresponding three-way valves and the corresponding cut-off reversing valves in the cascade actuator are controlled, so that oil output by the third sub-actuator sequentially passes through the cut-off reversing valve, the left three-way valve corresponding to the left first-stage shuttle valve, the vertical three-way valve and the left three-way valve corresponding to the second-stage shuttle valve to be connected with the left comparison end of the second-stage shuttle valve, oil output by the fourth sub-actuator sequentially passes through the right three-way valve corresponding to the right first-stage shuttle valve and the right three-way valve corresponding to the second-stage shuttle valve to be connected with the right comparison end of the second-stage shuttle valve, and the output end of the second-stage shuttle valve is connected with the left comparison end of the third-stage shuttle valve.
If the two sub-actuators are different and are a first sub-actuator and a third sub-actuator from left to right, the corresponding three-way valves in the cascade actuator are controlled, oil output by the first sub-actuator is connected with the left comparison end of the second stage shuttle valve sequentially through the left first stage shuttle valve corresponding left three-way valve, the vertical three-way valve and the second stage shuttle valve corresponding left three-way valve, the oil output by the third sub-actuator is connected with the right comparison end of the second stage shuttle valve sequentially through the right first stage shuttle valve corresponding left three-way valve and the second stage shuttle valve corresponding right three-way valve, and the output end of the second stage shuttle valve is connected with the left comparison end of the third stage shuttle valve. The other two sub-actuators are not connected to the comparison end of the same shuttle valve, and are similar to the above description, and are not described again.
When the fourth situation is realized, for example, if a first sub-actuator from left to right is connected to a tested load-sensitive pump control loop through two shuttle valves, namely a second-stage shuttle valve and a third-stage shuttle valve, and a third sub-actuator and a fourth sub-actuator are connected to the tested load-sensitive pump control loop through three shuttle valves, namely a first-stage shuttle valve, a second-stage shuttle valve and a third-stage shuttle valve, a corresponding three-way valve in the cascade actuator is controlled, so that the first sub-actuator is connected to a left comparison end of the second-stage shuttle valve sequentially through a left three-way valve corresponding to the first-stage shuttle valve on the left side, a vertical three-way valve and a left three-way valve corresponding to the second-stage shuttle valve; the third sub-actuator corresponds the left side comparison end of the left side first level shuttle valve through the right side first level shuttle valve and connects the left side comparison end of the right side first level shuttle valve, the fourth sub-actuator corresponds the right side comparison end of the right side first level shuttle valve through the right side first level shuttle valve and connects the right side comparison end of the right side first level shuttle valve, the output end of the right side first level shuttle valve corresponds the right side three-way valve through the second level shuttle valve and connects the right side comparison end of the second level shuttle valve, and the output end of the second level shuttle valve connects the left side comparison end of the third level shuttle valve.
If the first shuttle valve from left to right is connected to the tested load sensitive pump control loop through the second-stage shuttle valve and the third-stage shuttle valve, and the second sub actuator and the third sub actuator are connected to the tested load sensitive pump control loop through the first-stage shuttle valve, the second-stage shuttle valve and the third-stage shuttle valve, the corresponding three-way valve and the corresponding cut-off reversing valve in the cascade actuator are controlled, so that the first sub actuator is connected with the left comparison end of the second-stage shuttle valve through the left-side three-way valve corresponding to the first-stage shuttle valve, the vertical three-way valve and the left-side three-way valve corresponding to the second-stage shuttle valve in sequence; the second sub-actuator is connected with the right comparison end of the first-stage shuttle valve through a stop reversing valve and a right three-way valve corresponding to the second-stage shuttle valve on the right side in sequence, the third sub-actuator is connected with the left comparison end of the first-stage shuttle valve on the right side through a left three-way valve corresponding to the first-stage shuttle valve on the right side, the output end of the first-stage shuttle valve on the right side is connected with the right comparison end of the second-stage shuttle valve through a right three-way valve corresponding to the second-stage shuttle valve, and the output end of the second-stage shuttle valve is connected with the left comparison end of the third-stage shuttle valve. According to the embodiments, the cascade actuators are further designed, so that the number of the shuttle valves which pass through when each sub-actuator is connected to the tested load sensitive pump control loop can be adjusted.
Finally, the above embodiments are only intended to illustrate the technical solutions of the present invention and not to limit the present invention, and although the present invention has been described in detail with reference to the preferred embodiments, it will be understood by those skilled in the art that modifications or equivalent substitutions may be made on the technical solutions of the present invention without departing from the spirit and scope of the technical solutions, and all of them should be covered by the claims of the present invention.
Claims (9)
1. A load-sensitive pump control loop simulation test system is characterized by comprising a tested load-sensitive pump, a proportional throttle valve, an independent stop reversing valve, a pressure feedback hose, an independent actuator and a cascade actuator, wherein an oil outlet of the tested load-sensitive pump is connected with an inlet of the proportional throttle valve, an outlet of the proportional throttle valve is connected with the independent actuator and is connected with a pressure feedback LS oil port of the tested load-sensitive pump sequentially through the independent stop reversing valve and the pressure feedback hose, the cascade actuator comprises a plurality of shuttle valves, for a first-stage shuttle valve, two comparison ends of the first-stage shuttle valve are respectively connected with corresponding sub-actuators, an output end of the first-stage shuttle valve is connected with one comparison end of a previous-stage shuttle valve, for other higher-stage shuttle valves, two comparison ends of the first-stage shuttle valve are respectively connected with output ends of corresponding two shuttle valves in a next stage, and for a highest-stage shuttle valve, one comparison end of the pressure feedback hose is connected with the output end of the secondary high-grade shuttle valve, the other comparison end of the pressure feedback hose is connected with the outlet of the proportional throttle valve, and the output end of the pressure feedback hose is connected with the LS oil port of the tested load sensitive pump; each sub actuator comprises a stop reversing valve, a proportional overflow valve and a hydraulic pump; the independent actuator comprises a proportional overflow valve; the proportional overflow valve is used for adjusting the overflow pressure output by the corresponding actuator; the shuttle valve compares the overflow pressure input by the comparison end of the shuttle valve, and selects oil with higher overflow pressure to output;
controlling the independent stop reversing valves and the stop reversing valves in the sub-actuators to enable the actuators of different numbers in any combination to be connected into the LS oil ports of the tested load sensitive pump through pressure feedback hoses; and a sensor is arranged at a corresponding position, and the influence of the response delay of the shuttle valve and the pressure feedback hose on the LS response performance in the tested load sensitive pump control loop is simulated and tested according to the data detected by the sensor.
2. The load-sensitive pump control loop simulation test system according to claim 1, wherein when the independent cut-off and direction-changing valve is turned on, the tested load-sensitive pump, the proportional throttle valve, the independent cut-off and direction-changing valve and the pressure feedback hose form the tested load-sensitive pump control loop, and a test for simulating the response performance of the tested load-sensitive pump LS with only the independent actuator is realized, wherein the tested load-sensitive pump control loop is not provided with a shuttle valve and is provided with only the pressure feedback hose, so that the influence of the response delay of the pressure feedback hose on the LS response performance can be simulated and tested for the pressure feedback hoses with different lengths;
when the independent cut-off reversing valve is disconnected, the tested load-sensitive pump, the proportional throttle valve, the highest-level shuttle valve and the pressure feedback hose form a tested load-sensitive pump control loop, the LS response performance simulation test of the load-sensitive pump with at least one sub-actuator in the cascade actuator is realized, and the shuttle valve and the pressure feedback hose exist in the tested load-sensitive pump control loop at the same time, so that the influence of the response delay of the tested shuttle valve and the pressure feedback hose with the corresponding length on the LS response performance can be simulated.
3. The load-sensitive pump control loop simulation test system according to claim 2, wherein the independent actuator further comprises a cut-off and reversing valve, the cut-off and reversing valve and the proportional overflow valve are connected in parallel, the first parallel node of the cut-off and reversing valve is connected with the outlet of the proportional throttle valve, and when the independent cut-off and reversing valve is disconnected, the cut-off and reversing valve in the independent actuator can be controlled, so that the tested load-sensitive pump control loop formed by the tested load-sensitive pump, the proportional throttle valve, the highest-level shuttle valve and the pressure feedback hose is provided with or without the independent actuator.
4. The load-sensitive pump control loop simulation test system according to claim 3, wherein a second parallel node of a cut-off reversing valve and a proportional overflow valve in the independent actuator is communicated with an oil tank;
for each sub-actuator, a stop reversing valve and a proportional overflow valve in the sub-actuator are connected in parallel, a first parallel node of the sub-actuator is respectively connected with a corresponding comparison end of a first-stage shuttle valve and a first end of a corresponding hydraulic pump, a second parallel node of the sub-actuator is communicated with the oil tank, and a second end of the hydraulic pump is also communicated with the oil tank.
5. The load-sensitive pump control loop simulation test system according to claim 3 or 4, wherein the proportional throttle valve is further connected in parallel with a cut-off reversing valve, and when the cut-off reversing valve connected in parallel with the proportional throttle valve and the cut-off reversing valve in the independent actuator are simultaneously opened, unloading of the tested load-sensitive pump is achieved.
6. The load-sensitive pump control loop simulation test system according to claim 5, further comprising a motor and a torque speed sensor, wherein the motor drives the sensitive pump to be tested through the torque speed sensor;
the oil outlet of the tested load sensitive pump is connected with the inlet of the proportional throttle valve sequentially through the one-way valve and the filter;
a stop valve is arranged between an oil inlet of the tested load sensitive pump and the oil tank;
and a second parallel node of a stop reversing valve and a proportional overflow valve in the independent actuator is communicated with the oil tank through a cooler.
7. The load-sensitive pump control loop simulation test system according to claim 6, wherein pressure sensors are respectively arranged at an oil outlet of the tested load-sensitive pump, an inlet and an outlet of the proportional throttle valve, an LS oil outlet of the tested load-sensitive pump, and output ends of shuttle valves of other stages except the highest stage, and each pressure sensor is used for detecting a pressure change condition of each corresponding link, and analyzing the influence of response delay of the shuttle valve and the pressure feedback hose on the LS response performance according to the pressure change condition of each link.
8. The load-sensitive pump control loop simulation test system according to claim 7, wherein a first flow meter is arranged between an oil drain port of the tested load-sensitive pump and an oil tank and is used for measuring the oil discharge flow of the tested load-sensitive pump;
a second flowmeter is arranged at the inlet of the proportional throttle valve;
and a third flow meter is arranged at an LS oil port of the tested load sensitive pump.
9. The load-sensitive pump control loop simulation test system according to claim 7, wherein a connection node of the check valve and the filter is communicated with the oil tank through an overflow valve so as to discharge oil through the overflow valve when the pressure at the oil outlet of the tested load-sensitive pump is abnormally increased.
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