CN103471829A - Test stand of multi-way valve of hydraulic excavator - Google Patents
Test stand of multi-way valve of hydraulic excavator Download PDFInfo
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- CN103471829A CN103471829A CN2013104017030A CN201310401703A CN103471829A CN 103471829 A CN103471829 A CN 103471829A CN 2013104017030 A CN2013104017030 A CN 2013104017030A CN 201310401703 A CN201310401703 A CN 201310401703A CN 103471829 A CN103471829 A CN 103471829A
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- 238000005259 measurement Methods 0.000 abstract description 7
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Abstract
The invention relates to the technical field of engineering machinery and discloses a test stand of a multi-way valve of a hydraulic excavator. The test stand comprises a hydraulic system which comprises a main power oil unit, a guide oil supplying unit, as analog loading unit, a cooling and filtering unit, an oil returning unit and an oil supplying tank, and a measurement and control system which comprises an industrial personal computer and a PLC. The test stand of the multi-way valve of the hydraulic excavator overcomes the defects of an existing multi-way valve testing stand effectively, and can simulate the actual working condition of the multi-way valve of the excavator better, achieve multi-union simultaneous testing of the multi-way vale, and carry out comprehensive testing on the performance of the multi-way valve of the excavator.
Description
Technical field
The present invention relates to technical field of engineering machinery, particularly relate to a kind of hydraulic excavator banked direction control valves testing table.
Background technology
Excavator is machine the most complicated in engineering machinery, hydraulic system is the most important system of excavator, and banked direction control valves is as the core component of excavator hydraulic system, it is responsible for the hydraulic oil from oil pump output is distributed according to need to each execution unit, and guarantee the sequentially-operating of each topworks of excavator and the harmony of composite move, so the test that the excavator banked direction control valves is correlated with is very important.Although nowadays some testing tables about banked direction control valves are arranged, these testing tables consider two problems that mainly contain: the firstth, and the actual condition of simulation excavator banked direction control valves that can not be real; The secondth, can not carry out multi-joint test simultaneously to banked direction control valves.So just cause the banked direction control valves performance parameter that tests out inaccurate, thereby affect the operating performance of excavator.
Summary of the invention
Goal of the invention: technical matters to be solved by this invention is for the deficiencies in the prior art, a kind of hydraulic excavator banked direction control valves testing table is provided, and the present invention not only can realize being detected simultaneously but also can simulating more truly the excavator actual condition banked direction control valves is multi-joint.
In order to solve the problems of the technologies described above, the invention discloses a kind of hydraulic excavator banked direction control valves testing table, comprise hydraulic system and TT&C system, wherein hydraulic system is used to the test of banked direction control valves that power and oil sources are provided, the commutation of realization to each spool of banked direction control valves, and can be loaded to banked direction control valves simulation excavator practical working situation;
TT&C system is responsible for each unit motor, solenoid directional control valve and proportional pressure control valve etc. are controlled, and the data of output are gathered, storage and showing in real time, but also taking into account the security of system, realize the monitoring to some key states in system.
In the present invention, described hydraulic system comprises active force oil unit, guide's oil supply unit, the simulation loading unit that connects respectively described banked direction control valves, oil return unit and supply reservoir, active force oil unit, guide's oil supply unit and oil return unit connect supply reservoir simultaneously.
In the present invention, described active force oil unit comprises the first strainer filter, main fuel feeding variable output pump, the first filtrator, the first plug-in mounting retaining valve and the first flow meter that pipeline connects successively, wherein main fuel feeding variable output pump coaxially connects variable-frequency motor, and be communicated with described supply reservoir, the first flow meter connects the oil-in of banked direction control valves; Pipeline between first flow meter and banked direction control valves is provided with the first tensimeter; The bypass simultaneously of main fuel feeding variable output pump connects main fuel feeding proportional pressure control valve, and main fuel feeding proportional pressure control valve is communicated with the oil return opening of banked direction control valves.
In the present invention, described guide's oil supply unit comprises the second strainer filter, the first fixed displacement pump, the first filtrator and the second plug-in mounting retaining valve that pipeline connects successively, and wherein fixed displacement pump coaxially connects motor, and fixed displacement pump is communicated with supply reservoir; The second plug-in mounting retaining valve connects the first proportional pressure-reducing valve and the second proportional pressure-reducing valve simultaneously, and the first proportional pressure-reducing valve connects the first solenoid directional control valve and banked direction control valves successively, and the second proportional pressure-reducing valve connects the second solenoid directional control valve and banked direction control valves successively; The endpiece of the first proportional pressure-reducing valve and the second proportional pressure-reducing valve is connected respectively the second tensimeter, the 3rd tensimeter; The fixed displacement pump bypass connects electromagnetic relief valve, and electromagnetic relief valve connects oil return opening, the first solenoid directional control valve and second solenoid directional control valve of supply reservoir, banked direction control valves simultaneously.
In the present invention, described oil return unit comprises proportional pressure control valve, the first hand stop valve, the second hand stop valve, the second fine filter, the 7th tensimeter, the 4th flowmeter and leakage measuring instrumentation device, the oil return opening of banked direction control valves is divided into three tunnels, the first via connects supply reservoir by the leakage measuring instrumentation device, the second tunnel is connected supply reservoir by the first hand stop valve with proportional pressure control valve, Third Road directly connects supply reservoir by the second hand stop valve, wherein at common the 7th tensimeter that connects of the oil inlet end on three tunnels; The endpiece of proportional pressure control valve and the second hand stop valve is connected this 4th flowmeter and the second fine filter jointly successively; The second fine filter is connected in fuel tank.
In the present invention, described simulation loading unit comprises simulated solution cylinder pressure end load unit and simulation motor end loading unit.
Simulated solution cylinder pressure end load unit comprises the first electricity liquid ratio relief valve, the 3rd plug-in mounting retaining valve, the second electricity liquid ratio relief valve, the 4th plug-in mounting retaining valve, the 4th tensimeter, the 5th tensimeter, the second flowmeter; The oil outlet end of the first electricity liquid ratio relief valve connects the second flowmeter, and the second flowmeter connects the oil inlet end of the 4th plug-in mounting retaining valve, and the oil outlet end of the oil inlet end of the first electricity liquid ratio relief valve and the 4th inserted valve is connected to respectively first of tested banked direction control valves and loads hydraulic fluid port; Simultaneously, the oil outlet end of the second electricity liquid ratio relief valve connects the second flowmeter, the second flowmeter connects the oil inlet end of the 3rd plug-in mounting retaining valve, and the oil outlet end of the oil inlet end of the second electricity liquid ratio relief valve and the 3rd plug-in mounting retaining valve is connected to respectively first of tested banked direction control valves and loads hydraulic fluid port; First loads hydraulic fluid port connects respectively the 4th tensimeter and the 5th tensimeter.
Simulation motor end loading unit comprises oil motor, shaft coupling, torque loader, the 6th tensimeter, the 3rd flowmeter, the oil inlet end of oil motor and oil outlet end are connected to respectively second of tested banked direction control valves and load hydraulic fluid port, and torque loader is connected with oil motor by shaft coupling; The oil inlet end of motor is connecting the 6th tensimeter and the 3rd flowmeter successively.In the present invention, comprise the cold filtration unit that connects supply reservoir, the cold filtration unit comprises the 3rd strainer filter, the second fixed displacement pump, motor, refrigeratory and the first fine filter be communicated with successively; Wherein the first fine filter is connected supply reservoir separately with the 3rd strainer filter, and the second fixed displacement pump connects motor, and the second fixed displacement pump is connected in the pipeline between refrigeratory and the first fine filter by Manual pilot formula surplus valve simultaneously.
In the present invention, supply reservoir is provided with vent valve.
In the present invention, supply reservoir is provided with thermometer.
In the present invention, TT&C system comprises industrial computer and PLC controller, wherein industrial computer is for detecting respectively banked direction control valves and active force oil unit, guide's oil supply unit, the simulation loading unit, pressure and flow velocity between oil return unit and cold filtration unit, connecting respectively each tensimeter, flowmeter and speed pickup, and to the first electricity liquid ratio relief valve, the second electricity liquid ratio relief valve, the proportional pressure control valve of oil return unit, frequency converter in the variable-frequency motor of main fuel feeding variable output pump group, main fuel feeding proportional pressure control valve, the first proportional pressure-reducing valve, and second proportional pressure-reducing valve controlled,
The PLC controller is for connecting and control the first pressure switch in the motor of main fuel feeding variable output pump, the motor in the first fixed displacement pump group, the motor in the second fixed displacement pump group, the first solenoid directional control valve in guide's oil supply unit and the second solenoid directional control valve, cold filtration unit and the second pressure switch in the oil return unit.
TT&C system is exported corresponding pressure and flow by the control to elements such as motor, valves, and, in conjunction with data acquisition and processing unit, completes automatic collection, demonstration and processing to test figure.
Compared with prior art, beneficial effect of the present invention is:
1, with the load of the shaft end of torque loader simulation excavator rotary motor and running motor, rather than all with proportional pressure control valve, carry out simulation loading, so not only can simplified structure, reduce costs, can also simulate more realistically the actual condition of excavator;
2, can realize the sequentially-operating of banked direction control valves simply connected and multi-joint composite move by each switch operation of guide's oil supply unit, so just can realize banked direction control valves is carried out to multi-joint test simultaneously, improve the fiduciary level of test;
3, leakage rate is measured and is adopted the measuring cup method of testing, with speed pickup, collects leakage rate, then according to Q=VA, calculates leakage rate.So not only increase measurement range and also saved the measurement of time, reduced error, improved the accuracy of test;
4, in guide's oil supply unit, accumulator is installed, wherein store pilot pressure oil, be used for simulating the excavator actual condition, while occurring the guide for shortage of oil in the situations such as actuating mechanism of excavating machine composite move, accumulator can be used as supplementary, prevents from testing carrying out smoothly;
5, all retaining valves in this testing table hydraulic system all change the plug-in mounting retaining valve into, can allow like this system responses accelerate, and quiet dynamic perfromance improves, and leakage rate reduces, and the plug-in mounting retaining valve is more suitable for large flow rate working conditions simultaneously, more can meet the requirement of excavator;
6, due near water intaking inconvenience testing table, therefore this experimental bench system adopts air-cooled, with the motor driving fan, carry out cooling, be provided with Manual pilot formula surplus valve simultaneously in this cooling unit, can carry out the manual adjustments reversal valve according to Current Temperatures and reach whether need cooling purpose, there is energy-saving effect.
The accompanying drawing explanation
Below in conjunction with the drawings and specific embodiments, the present invention is done further and illustrates, above-mentioned and/or otherwise advantage of the present invention will become apparent.
The structured flowchart of the excavator banked direction control valves testing table that Fig. 1 provides for the embodiment of the present invention.
The excavator banked direction control valves testing table hydraulic system principle figure that Fig. 2 provides for the embodiment of the present invention.
The leakage measuring instrumentation device schematic diagram that Fig. 3 provides for the embodiment of the present invention.
The torque loader schematic diagram that Fig. 4 provides for the embodiment of the present invention.
The excavator banked direction control valves testing bench control system schematic diagram that Fig. 5 provides for the embodiment of the present invention.
Embodiment
The invention discloses a kind of hydraulic excavator banked direction control valves testing table, as Fig. 1, comprise hydraulic system and TT&C system.The test that wherein hydraulic system is banked direction control valves provides power and oil sources, realizes the commutation to each spool of banked direction control valves, and can be loaded banked direction control valves, simulation excavator practical working situation; TT&C system is responsible for each unit motor, solenoid directional control valve and proportional pressure control valve etc. are controlled, and the data that sensor is spread out of are gathered, storage and demonstration in real time, but also taking into account the security of system, the monitoring of realization to some key states in system, whether as stifled as filtrator, whether oil level is too high.
Wherein excavator banked direction control valves testing table hydraulic system principle figure as shown in Figure 2, comprises active force oil unit, guide's oil supply unit, simulation loading unit, cold filtration unit, oil return unit, supply reservoir; Excavator banked direction control valves testing bench control system schematic diagram as shown in Figure 5, comprises industrial computer, the PLC controller.
Wherein as shown in Figure 2, supply reservoir 1 is enclosed air pressure fuel tank, prevents that the hydraulic pump suction is empty and cause cavitation to damage, store fluid in fuel tank, vent valve 41 also is installed at an upper portion thereof, and when the fuel tank preload pressure surpasses predetermined value, vent valve 41 is opened exhaust automatically.
Wherein as shown in Figure 2, active force oil unit comprises: the first strainer filter 3, hand stop valve 4, main fuel feeding variable output pump 5, variable-frequency motor 6, main fuel feeding proportional pressure control valve 7, the first filtrator 8, the first plug-in mounting retaining valves 9, first flow meter 10, the first tensimeters 11.After setting up the pressure of good main fuel feeding proportional pressure control valve 7, the oil suction from supply reservoir 1 of main fuel feeding variable output pump, by way of the first strainer filter 3 and hand stop valve 4, the fluid of discharging through main fuel feeding variable output pump 5 is again through the first filtrator 8 and the first plug-in mounting retaining valve 9, finally enter the oil inlet P mouth of tested banked direction control valves, when force value, during higher than the set pressure of proportional pressure control valve 7, fluid will directly advance to be connected to scavenge pipe fuel tank last time of banked direction control valves T mouth from proportional pressure control valve 7 overflows.Be provided with first flow meter 10 and the first tensimeter 11 on the oil-in be connected with tested banked direction control valves at plug-in mounting retaining valve 9, for flow and the pressure of testing oil-in, be convenient to test and setting to banked direction control valves.
At the pump inlet port, the first strainer filter 3 is installed, both can have been made all elements of system be protected, can guarantee larger through-current capability again, prevent hole; The first filtrator 8 is installed pumping hydraulic fluid port, is can be used as supplementing of the first strainer filter 3, further fluid is filtered, keep the clean of fluid.As Fig. 2 the first filtrator 8 also is installed in parallel a surplus valve, and the oil pipe that is connected to the surplus valve entrance end is the Temin color, so just can judge once fluid be arranged through surplus valve, just knowing that the first filtrator 8 has stopped up need to be to its cleaning or by its replacing.
Active force oil unit provides power and oil sources for whole pilot system, effectively ensures carrying out smoothly of test.
Wherein as shown in Figure 2, guide's oil supply unit of this figure comprises two, i.e. two guide's oil circuits, specifically comprise: the second strainer filter 19, hand stop valve 20, the first fixed displacement pumps 21, motor 22, electromagnetic relief valve 23, the second filtrators 24, the second plug-in mounting retaining valve 25, accumulator 26, the first proportional pressure-reducing valves 27, the second proportional pressure-reducing valve 30, the first solenoid directional control valve 29, the second solenoid directional control valves 32, the second tensimeter 28, the three tensimeters 31.Two reversing oil circuit ends that the first solenoid directional control valve 29 is controlled commutation connect respectively guide's hydraulic fluid port a1 of tested banked direction control valves, b1, and two reversing oil circuit ends that the second solenoid directional control valve 32 is controlled commutation connect respectively guide's hydraulic fluid port a2 of tested banked direction control valves, b2.After having set up the pressure of electromagnetic relief valve 23, fixed displacement pump 21 oil suction from supply reservoir 1, approach the second strainer filter 19 and hand stop valve 20, the fluid of discharging through fixed displacement pump 21 is first through the second filtrator 24, again through the second plug-in mounting retaining valve 25, then divide two oil circuits to flow through respectively the first proportional pressure-reducing valve 27 and the second proportional pressure-reducing valve 30, fluid after proportional pressure-reducing valve 27 flows to the oil-in of the first solenoid directional control valve 29, fluid after proportional pressure-reducing valve 30 flows to the oil-in of the second solenoid directional control valve 32, the oil return opening of the first solenoid directional control valve 29 and the second solenoid directional control valve 32 all is connected on the oil pipe that is connected to banked direction control valves T mouth, when pressure during higher than the set pressure of electromagnetic relief valve 23, fluid will directly overflow to from electromagnetic relief valve oil pipe fuel tank last time be connected with banked direction control valves T mouth.Endpiece at proportional pressure-reducing valve 27 and proportional pressure-reducing valve 30 is provided with respectively the second tensimeter 28 and the 3rd tensimeter 31, is used for measuring the pressure of banked direction control valves guide hydraulic fluid port, is convenient to test and setting to banked direction control valves.
Effect respectively with the first strainer filter 3 of the second strainer filter 19 and the second filtrator 24 is identical with the effect of the first filtrator 8, repeats no more here.On the oil pipe of the endpiece of plug-in mounting retaining valve 25, an accumulator 26 has been installed, wherein store pilot pressure oil, its effect is for simulating the excavator actual condition, while occurring the guide for shortage of oil in the situations such as actuating mechanism of excavating machine composite move, accumulator 26 can be used as supplementary, the carrying out smoothly of warranty test.By regulating the top hole pressure of proportional pressure-reducing valve 27 and proportional pressure-reducing valve 30, the pressure differential of proportion of utilization reduction valve endpiece and banked direction control valves pilot unit oil return opening can make the banked direction control valves spool move the effect that reaches commutation, and the commutation by the first solenoid directional control valve 29 and the second solenoid directional control valve 32 can make the banked direction control valves spool move commutation to another direction.
Guide's oil supply unit is as AFS Auxiliary Fuel Supply System, is commutation for controlling the banked direction control valves spool, with this, simulates the difference action of controlling excavator.
Wherein as shown in Figure 2, the simulation loading unit comprises simulated solution cylinder pressure end load unit and simulation motor end loading unit, and hydraulic cylinder can be scraper bowl cylinder, swing arm cylinder or the dipper cylinder on excavator, and motor can be running motor or rotary motor.
Simulated solution cylinder pressure end load unit comprises the first electromagnetic proportion relief valve 43, the three plug-in mounting retaining valve 44, the second electricity liquid ratio relief valve 46, the four plug-in mounting retaining valve 47, the second flowmeter 45, the four tensimeter 42, the five tensimeters 48.The oil outlet end of the first electricity liquid ratio relief valve 43 is connected in the oil inlet end of the 4th plug-in mounting retaining valve 47, and the oil outlet end of the oil inlet end of the first electricity liquid ratio relief valve 43 and the 4th inserted valve 47 is connected to respectively the loading hydraulic fluid port A1 of tested banked direction control valves, B1; The oil outlet end of the second electricity liquid ratio relief valve 46 is connected in the oil inlet end of the 3rd plug-in mounting retaining valve 44, and the oil outlet end of the oil inlet end of the second electricity liquid ratio relief valve 46 and the 3rd plug-in mounting retaining valve is connected to respectively the loading hydraulic fluid port B1 of tested banked direction control valves, A1.The 4th tensimeter 42, the five tensimeter 48, the second flowmeters 45 are set respectively on loading oil circuit, are measured for the flow to this loading oil circuit and pressure, be convenient to test and setting to banked direction control valves.
Simulated solution cylinder pressure end load unit is combined by electricity liquid ratio relief valve and plug-in mounting retaining valve, based on Redundancy Design thought, adopt biaxial loadings, when the loading of one of them direction goes wrong, can't affect the carrying out of test, the force value of by industrial computer, setting up proportional pressure control valve can be simulated some actual conditions of excavator banked direction control valves.
Simulation motor end loading unit comprises: the 6th tensimeter 49, the three flowmeters 50, oil motor 53, shaft coupling 52, torque loader 51.The oil inlet end of oil motor 53 and oil outlet end are connected to respectively another loading hydraulic fluid port A2 of tested banked direction control valves, B2, and torque loader 51 is connected with oil motor 53 by shaft coupling 52.Be provided with the 6th tensimeter 49 and the 3rd flowmeter 50 in oil circuit, measured for the flow to this loading oil circuit and pressure, be convenient to the tests and measurements to banked direction control valves.
Simulation motor end loading unit torque loader simulation loading, torque loader 51 is structure as shown in Figure 4, this torque loader is to utilize the principle of friction force transmitting torque to design, by bolt 513, torque loader is fixed on test-bed, the length of bolt 513 can be selected as required, then adjusting bolt 511 can be regulated friction plate structure 512, sets different torque values, reaches the effect that motor end is loaded.Not only simplify the structure by this torque loader simulation loading, reduced cost, also simulate more truly the actual condition of excavator.Torque loader can adopt existing structure, as long as realize that moment of torsion loads.
The simulation loading unit carries out simulation loading to this banked direction control valves experimental bench system, just can simulate the actual condition of excavator banked direction control valves by the torque loader of regulating the electricity liquid ratio relief valve in simulated solution cylinder pressure end load unit and simulate in the motor end loading unit respectively, as composition operation, straight line action etc., be convenient to test and setting to banked direction control valves.
Wherein, as Fig. 2, the oil return unit comprises three junior units, is respectively direct oil return box unit, the back pressure unit, the leakage measuring instrumentation unit, specifically comprise proportional pressure control valve 13, the first hand stop valves 14, the second hand stop valve 15, leakage measuring instrumentation device 17, the second fine filter 2, the second pressure switches 55, the 7th tensimeter 12, the four flowmeters 16.
Only need to open direct oil return box unit when carrying out the tests such as banked direction control valves straight line moving, close hand stop valve 14 and hand stop valve 171, open hand stop valve 15, by the fluid of main fuel feeding variable output pump 5 and fixed displacement pump 21 outputs directly from the oil pipe oil return case of the T hydraulic fluid port of banked direction control valves, be provided with the 4th flowmeter 16 in loop, for measuring the flow on oil return line, be convenient to test and setting to banked direction control valves.The second pressure switch 55 has been installed on the second fine filter 2, once fine filter stops up, will have been given the alarm, needed change fine filter or cleaned.
Need to open the back pressure unit when tests such as being simulated descending movable arm of excavator needs back pressure, close hand stop valve 15 and hand stop valve 171, open hand stop valve 14.Now fluid will meet the back pressure requirement of each operating mode from proportional pressure control valve 13 oil return casees by the force value of setting surplus valve, be provided with the 7th tensimeter 12 in loop,, measure each back pressure value by the 7th tensimeter 12, realize test and setting to banked direction control valves.
Need to open the leakage measuring instrumentation unit when carrying out Leak Off Test (LOT), because the scope of the leakage rate of banked direction control valves is 10～2500mL/min, the range of a flowmeter can not meet the demands, the cost of two flowmeters will improve, so adopt the graduated cylinder method of testing in this test, the measurement mechanism schematic diagram as shown in Figure 3, comprise hand stop valve 171, graduated cylinder 172, hand stop valve 173 and the speed pickup 174 that is arranged on graduated cylinder oil-feed place, speed pickup connects transmitter, industrial computer successively.First open hand stop valve 173 during test, empty the fluid in graduated cylinder, then close stop valve 173, then open stop valve 171, fluid flows into graduated cylinder from leaking oil-in, when fluid arrives the overflow vent position, to enter supply reservoir from overflow vent, the Negotiation speed sensor is measured the speed that flows to of fluid, and the floorage of establishing graduated cylinder is A, the speed of measuring is V, leakage rate Q=VA.This graduated cylinder mensuration has not only increased measurement range, has reduced cost, and does not need Measuring Time in process of the test, has reduced the error of test, has improved accuracy.
Wherein as shown in Figure 2, the cold filtration unit comprises: the 3rd strainer filter 33, hand stop valve 34, motor 35, the second fixed displacement pumps 36, motor 37, Manual pilot formula surplus valve 38, refrigeratory 39, the first fine filter 40, the first pressure switches 54, thermometer 18.Due to experimental field inconvenience water intaking, so this experiment adopts air-cooled cooling method.At the trial, observe the temperature of thermometer 18, when temperature is greater than 46 while spending, fluid is through the 3rd strainer filter 33 and hand stop valve 34 from fixed displacement pump 36 outputs, and now Manual pilot formula surplus valve 38 is not worked, just in as Fig. 2 state, fluid directly passes through motor 37, then by refrigeratory 39, motor just drives fan and refrigeratory is carried out air-cooled like this, reaches the cooling last fluid of effect and returns supply reservoir 1.When temperature is less than 46 while spending, the manual adjustments reversal valve, fluid will be directly from Manual pilot formula surplus valve output oil return case from fixed displacement pump 36 outputs.
The first fine filter 40 is identical with the effect of the second fine filter 2, repeats no more here.
The cold filtration unit is an independently unit, it has independent filtering system, it will coordinate the filtrator in main oil supply unit and guide's oil supply unit to carry out work, it has independent cooling device, the temperature range that it can keep the fluid in fuel tank subscribing, thereby improve the accuracy of test, reduce the leakage of fluid.
In this testing table hydraulic system, all retaining valves are all changed and make the plug-in mounting retaining valve, system responses is accelerated, quiet dynamic perfromance improves, and leakage rate reduces, and the plug-in mounting retaining valve is more suitable for large flow rate working conditions simultaneously, more can meet the requirement of excavator.
Only below two of excavator banked direction control valves test bed testing banked direction control valves in Fig. 2 to be loaded to the test specification of hydraulic fluid port and guide's hydraulic fluid port, if in the time of need to testing banked direction control valves multi-joint simultaneously, only need on every loading hydraulic fluid port to be measured, increase again one group of corresponding loading unit, it should be noted that, excavate action when the test increased for excavator, just increase simulated solution cylinder pressure end load unit; For walking or revolution, just increase simulation motor end loading unit when the test increased.After having increased loading unit, accordingly, increase again one group of corresponding guide's oil circuit and get final product on every guide's hydraulic fluid port to be measured.So it is a plurality of that loading oil circuit of the present invention and guide's oil circuit have, can to the multi-joint loading hydraulic fluid port of banked direction control valves, be tested simultaneously simultaneously, simulate more realistically the actual condition of excavator banked direction control valves, improved reliability and the accuracy of test.
Wherein as shown in Figure 5, excavator banked direction control valves testing bench control system comprises PLC controller and industrial computer.
The testing bench control schematic diagram is to draw on the basis of testing table hydraulic schematic diagram, consider two figure are combined and can make integral body seem too too fat to move, so two figure separately are introduced, for convenient, understand, the element numbers in Fig. 5 is all directly to continue to use the element numbers of the correspondence in Fig. 2.
The PLC controller is connected in main motor 5, guide's fuel feeding motor 21 and cooling motor 36 successively as shown in Figure 5, and PLC controls and also is connected in solenoid directional control valve 29 and 32, and PLC controls and also is connected to the pressure switch 55,54 in oil return unit and cold filtration unit simultaneously.It is exactly to be convenient to PLC they are operated that these elements are connected on PLC, is controlling the carrying out of test.
Industrial computer is connected in frequency converter, proportional pressure-reducing valve 27 and 30, electricity liquid ratio relief valve 43 and 46, the proportional pressure control valve 13 in proportional pressure control valve 7, variable-frequency motor simultaneously as shown in Figure 5, these valves and frequency converter are connected on industrial computer, be to be convenient to industrial computer they are carried out to corresponding Numerical Control, thereby be convenient to the carrying out of test.
Industrial computer also is connected in the first tensimeter 11, the second tensimeter 28, the 3rd tensimeter 31, the 4th tensimeter 42, the 5th tensimeter 48, the 6th tensimeter 49, the 7th tensimeter 12, first flow meter 10, the second flowmeter 45, the 3rd flowmeter 50, the 4th flowmeter 16 and speed pickup 174 simultaneously as shown in Figure 5, by these tensimeters,, flowmeter and speed pickup are connected on industrial computer is to be convenient to industrial computer collect the data of export by converter by these tensimeters, flowmeter and speed pickup and process accordingly.
In the concrete application process of the present invention, the banked direction control valves performance test is comprised:
1, the guide oil mouth pressure is measured
Test method: start guide's oil feed pump 21, electromagnetic relief valve 23 obtains electric, the second solenoid directional control valve 32 and solenoid directional control valve 35 left end electromagnet simultaneously electric, then by industrial computer, the input signal of proportional pressure-reducing valve 27 and proportional pressure-reducing valve 30 is adjusted to maximum pressure value p1, now regulate electromagnetic relief valve until the reading of the second tensimeter 28 and the 3rd tensimeter 31 all shows p1, then lower gradually the force value of proportional pressure-reducing valve 27 and proportional pressure-reducing valve 30, the indicating value of observing the second tensimeter 28 and the 3rd tensimeter 31 changes.By regulating proportional pressure-reducing valve 27 and proportional pressure-reducing valve 30 electric signal, record the value of the second tensimeter 28 and the 3rd tensimeter 31.Subject is changed another direction, same test.
2, the impact test of load variations on (simply connected) flow
This test comprises two, and loading unit carrys out simulated solution cylinder pressure end load with electricity liquid ratio relief valve respectively, simulates motor end with torque loader and loads.
Simulated solution cylinder pressure end load unit:
Test method: the first solenoid directional control valve 29 left ends obtain electric, and manual adjustments electromagnetic relief valve 23 is to working pressure, and 21 pairs of guide's oil circuit fuel feeding of guide's oil feed pump are commutated to the banked direction control valves subject.Industrial computer adjusted master, supply oil-overflow valve 7 to working pressure, 5 pairs of subject fuel feeding of main oil feed pump, the on-load pressure of regulating continuously electricity liquid ratio relief valve 43 or electricity liquid ratio relief valve 46 changes, open stop valve 15 and record first flow meter 10, the second flowmeter 45, the four flowmeters 16, the first tensimeter 11, the value of the 4th tensimeter 42, the five tensimeters 48, do load-flow curve.The subject commutation, do same test.
Simulation motor end loading unit:
Test method: the second solenoid directional control valve 32 left ends obtain electric, and manual adjustments electromagnetic relief valve 23 is to working pressure, and 21 pairs of guide's oil circuit fuel feeding of guide's oil feed pump are commutated to the banked direction control valves subject.Industrial computer adjusted master, supply oil-overflow valve 7 to working pressure, 5 pairs of subject fuel feeding of main oil feed pump, regulate continuously the bolt 511 on torque loader, on-load pressure is changed, open stop valve 15, record first flow meter 10, the 3rd flowmeter 50, the four flowmeter 16, the first tensimeters 11, the 6th tensimeter 49, do load-flow curve.The subject commutation, do same test.
3, the impact test of load variations on (multi-joint) flow
The first solenoid directional control valve 29 and the second solenoid directional control valve 32 left ends obtain electric, and manual adjustments electromagnetic relief valve 23 is to working pressure, and 21 pairs of guide's oil circuit fuel feeding of guide's oil feed pump are commutated to two subjects of banked direction control valves.Industrial computer adjusted master, supply oil-overflow valve 7 to working pressure, 5 pairs of two subject fuel feeding of main oil feed pump, the on-load pressure of regulating continuously electricity liquid ratio relief valve 43 or electricity liquid ratio relief valve 46 changes, regulate continuously the bolt 511 on torque loader simultaneously, also make on-load pressure change, open stop valve 15, record first flow meter 10, the second flowmeter 45, the three flowmeters 50, the 4th flowmeter 16, the first tensimeter 11, the four tensimeter 42, the five tensimeters 48, the value of the 6th tensimeter 49, do load-flow curve.Two subjects commutate simultaneously, do same test.
3, back pressure test
Test method: when swing arm connection or revolution connection etc. is tested, need to carry out back pressure test.To, according to schematic diagram to wherein one describing, with simulated solution cylinder pressure end load unit, carry out test simulation swing arm connection herein.At first the first solenoid directional control valve 29 obtains electric commutation, guide's oil feed pump 21 is opened fuel feeding, regulate proportional pressure-reducing valve 27, to the swing arm connection pressure of stipulating, swing arm is joined to the spool commutation, then open 5 pairs of banked direction control valves swing arm alliance oil of main oil feed pump, and close the stop valve 171 in the oil return unit, stop valve 15, open stop valve 14, finally by industrial computer, regulate the different value of proportional pressure control valve 13, by the 7th tensimeter 12, record force value.
4, Leak Off Test (LOT)
Test method: the internal leakage that this experiment respectively joins neutral position and commutation position to banked direction control valves is tested.Because test principle figure only draws two, so below will only describe two in figure, the test of other connection by that analogy.Before measuring internal leakage, first open 173 stop valves, after emptying the graduated cylinder inner fluid, again it is closed, when measuring internal leakage, the flow of system only need to meet test request, there is no need to input large flow.
While testing the neutral position internal leakage, each connection of tested valve is all in neutral position, loading hydraulic fluid port A1 from banked direction control valves, B1, A2, B2 passes into the oil of different pressures, this pressure is regulated by loading unit electromagnetic proportion relief valve and torque loader, except the T mouth, other hydraulic fluid port is blocked entirely, and block stop valve 14 and stop valve 15 in the oil return unit, open stop valve 171, the fluid now leaked out will enter graduated cylinder 172 from leakage measuring instrumentation device oil-in, then Negotiation speed sensor 174 is measured the speed of flow liquid, be designated as V, if the floorage of graduated cylinder is A, leakage rate Q=VA,
When test commutates the position internal leakage, open main fuel feeding variable output pump 5, by regulating proportional pressure control valve 7 from banked direction control valves P mouth input different pressures, except the T mouth, other hydraulic fluid port is blocked entirely, and concrete measuring method is the same constantly with measurement neutral position internal leakage, repeats no more here.
The invention provides a kind of hydraulic excavator banked direction control valves testing table; method and the approach of this technical scheme of specific implementation are a lot; the above is only the preferred embodiment of the present invention; should be understood that; for those skilled in the art; under the premise without departing from the principles of the invention, can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.In the present embodiment not clear and definite each ingredient all available prior art realized.
Claims (10)
1. a hydraulic excavator banked direction control valves testing table, is characterized in that, comprises hydraulic system and TT&C system, wherein hydraulic system is used to the test of banked direction control valves that power and oil sources are provided, the commutation of realization to each spool of banked direction control valves, and can be loaded to banked direction control valves simulation excavator practical working situation;
TT&C system is for monitoring the duty of hydraulic system corresponding component.
2. a kind of hydraulic excavator banked direction control valves testing table according to claim 1, it is characterized in that, described hydraulic system comprises active force oil unit, guide's oil supply unit, the simulation loading unit that connects respectively described banked direction control valves, oil return unit and supply reservoir, active force oil unit, guide's oil supply unit and oil return unit connect supply reservoir simultaneously.
3. a kind of hydraulic excavator banked direction control valves testing table according to claim 2, it is characterized in that, described active force oil unit comprises main fuel feeding variable output pump, the first plug-in mounting retaining valve and the first flow meter that pipeline connects successively, wherein main fuel feeding variable output pump coaxially connects variable-frequency motor, and be communicated with described supply reservoir, the first flow meter connects the oil-in of banked direction control valves; Pipeline between first flow meter and banked direction control valves is provided with the first tensimeter; The bypass simultaneously of main fuel feeding variable output pump connects main fuel feeding proportional pressure control valve, and main fuel feeding proportional pressure control valve is communicated with the oil return opening of banked direction control valves.
4. a kind of hydraulic excavator banked direction control valves testing table according to claim 3, it is characterized in that, described guide's oil supply unit comprises the first fixed displacement pump and the second plug-in mounting retaining valve that pipeline connects successively, and wherein fixed displacement pump coaxially connects motor, and fixed displacement pump is communicated with supply reservoir; The second plug-in mounting retaining valve connects the first proportional pressure-reducing valve and the second proportional pressure-reducing valve simultaneously, and the first proportional pressure-reducing valve connects the first solenoid directional control valve and banked direction control valves successively, and the second proportional pressure-reducing valve connects the second solenoid directional control valve and banked direction control valves successively; The fixed displacement pump bypass connects electromagnetic relief valve, and electromagnetic relief valve connects oil return opening, the first solenoid directional control valve and second solenoid directional control valve of supply reservoir, banked direction control valves simultaneously.
5. a kind of hydraulic excavator banked direction control valves testing table according to claim 4, it is characterized in that, described oil return unit comprises proportional pressure control valve, the first hand stop valve, the second hand stop valve and leakage measuring instrumentation device, the oil return opening of banked direction control valves is divided into three tunnels, the first via connects supply reservoir by the leakage measuring instrumentation device, the second tunnel is connected supply reservoir by the first hand stop valve with proportional pressure control valve, and Third Road directly connects supply reservoir by the second hand stop valve.
6. a kind of hydraulic excavator banked direction control valves testing table according to claim 5, is characterized in that, described simulation loading unit comprises simulated solution cylinder pressure end load unit and simulation motor end loading unit;
Simulated solution cylinder pressure end load unit comprises the first electricity liquid ratio relief valve, the 3rd plug-in mounting retaining valve, the second electricity liquid ratio relief valve, the 4th plug-in mounting retaining valve; The oil outlet end of the first electricity liquid ratio relief valve connects the oil inlet end of the 4th plug-in mounting retaining valve, and the oil outlet end of the oil inlet end of the first electricity liquid ratio relief valve and the 4th inserted valve is connected to respectively first of tested banked direction control valves and loads hydraulic fluid port; Simultaneously, the oil outlet end of the second electricity liquid ratio relief valve connects the oil inlet end of the 3rd plug-in mounting retaining valve, and the oil outlet end of the oil inlet end of the second electricity liquid ratio relief valve and the 3rd plug-in mounting retaining valve is connected to respectively first of tested banked direction control valves and loads hydraulic fluid port;
Simulation motor end loading unit comprises oil motor, shaft coupling and torque loader, and the oil inlet end of oil motor and oil outlet end are connected to respectively second of tested banked direction control valves and load hydraulic fluid port, and torque loader is connected with oil motor by shaft coupling.
7. a kind of hydraulic excavator banked direction control valves testing table according to claim 6, it is characterized in that, comprise the cold filtration unit that connects supply reservoir, the cold filtration unit comprises the 3rd strainer filter, the second fixed displacement pump, motor, refrigeratory and the first fine filter be communicated with successively; Wherein the first fine filter is connected supply reservoir separately with the 3rd strainer filter, and the second fixed displacement pump connects motor, and the second fixed displacement pump is connected in the pipeline between refrigeratory and the first fine filter by Manual pilot formula surplus valve simultaneously.
8. a kind of hydraulic excavator banked direction control valves testing table according to claim 2, is characterized in that, supply reservoir is provided with vent valve.
9. a kind of hydraulic excavator banked direction control valves testing table according to claim 2, is characterized in that, supply reservoir is provided with thermometer.
10. a kind of hydraulic excavator banked direction control valves testing table according to claim 7, it is characterized in that, TT&C system comprises industrial computer and PLC controller, wherein industrial computer is for detecting respectively banked direction control valves and active force oil unit, guide's oil supply unit, the simulation loading unit, pressure and flow velocity between oil return unit and cold filtration unit, and to the first electricity liquid ratio relief valve, the second electricity liquid ratio relief valve, the proportional pressure control valve of oil return unit, frequency converter in the variable-frequency motor of main fuel feeding variable output pump, main fuel feeding proportional pressure control valve, the first proportional pressure-reducing valve, and second proportional pressure-reducing valve controlled, the PLC controller is for connecting and control the first pressure switch in the motor of main fuel feeding variable output pump, the motor in the first fixed displacement pump, the motor in the second fixed displacement pump, the first solenoid directional control valve in guide's oil supply unit and the second solenoid directional control valve, cold filtration unit and the second pressure switch in the oil return unit.
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