WO2019047968A1 - 用于油压减振器阻尼阀试验的测试模块和系统及试验方法 - Google Patents

用于油压减振器阻尼阀试验的测试模块和系统及试验方法 Download PDF

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Publication number
WO2019047968A1
WO2019047968A1 PCT/CN2018/105002 CN2018105002W WO2019047968A1 WO 2019047968 A1 WO2019047968 A1 WO 2019047968A1 CN 2018105002 W CN2018105002 W CN 2018105002W WO 2019047968 A1 WO2019047968 A1 WO 2019047968A1
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WIPO (PCT)
Prior art keywords
assembly
test
valve
oil
guide
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PCT/CN2018/105002
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English (en)
French (fr)
Inventor
王文林
周梓荣
曹晓畅
尹玲
林小夏
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东莞理工学院
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Application filed by 东莞理工学院 filed Critical 东莞理工学院
Priority to US16/627,770 priority Critical patent/US10935468B2/en
Publication of WO2019047968A1 publication Critical patent/WO2019047968A1/zh

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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M17/00—Testing of vehicles
    • G01M17/007—Wheeled or endless-tracked vehicles
    • G01M17/04—Suspension or damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/3264—Arrangements for indicating, e.g. fluid level; Arrangements for checking dampers
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/003—Machine valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/12—Fluid damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/0047—Measuring, indicating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/185—Bitubular units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/3207—Constructional features
    • F16F9/3235—Constructional features of cylinders
    • F16F9/3242—Constructional features of cylinders of cylinder ends, e.g. caps

Definitions

  • the utility model relates to an integrated test module, an automatic measurement and control system and a test method capable of testing a dynamic characteristic of a hydraulic damper damping valve in a high and low temperature environment, belonging to a hydraulic component testing device and a hydraulic component testing technology. , hydraulic damper product testing technology field.
  • the oil damper is an important component of modern railway vehicles such as high-speed rail, which plays an important role in the stability and comfort of the vehicle system.
  • the damper valve is also a key component inside the oil damper, and its performance is on the oil.
  • the damping characteristics of the pressure damper play a decisive role. Therefore, it is important to test the dynamic characteristics of the oil damper damping valve and understand its performance and indicators.
  • high-speed rail may require operation from high-cold areas (below -40 ° C) to high temperature areas in one day, then the high- and low-temperature dynamic characteristics test for hydraulic damper damping valve has become a New topic.
  • test system for testing the "flow-pressure characteristic" of a piston valve of an automobile damper.
  • the test system has the following characteristics:
  • a complete hydraulic system including hydraulic pump, various hydraulic control valves and fuel tanks is used to supply oil to the piston valve, so the system is complicated and bulky.
  • a set of oil temperature control system including refrigeration and heating devices was specially designed to maintain the constant oil temperature of the system.
  • This test method is feasible at normal temperature, but it is not feasible to use the above method at high and low temperatures, especially at low temperatures. Because at low temperatures, such as below -30 ° C, the general hydraulic pump can not effectively absorb oil, many hydraulic control valves, pipelines can not work properly, let alone effective and accurate related tests; in addition, in high and low temperature test In the temperature control of the hydraulic system of the entire hydraulic system, it is neither convenient nor energy-saving.
  • the automatic measurement and control system can excite the modular test device by servo drive, input various excitation signals including step, sawtooth wave, etc., and the parameters are adjustable. To test the dynamic characteristics of the damping valve.
  • the automatic measurement and control system can not only automatically control the temperature and excitation signal input of the modular test device, but also automatically test the physical quantity such as temperature, pressure and flow of the oil through the tested damping valve, and then test the data. Process, save, and output.
  • a test module for testing dynamic characteristics of a hydraulic damper damping valve comprising a storage cylinder assembly, a guide assembly, a guide exhaust plate, a pressure cylinder, a piston-piston rod assembly, a hydraulic oil, a bottom valve assembly, Pressure cylinder gasket, bottom valve gasket, oil guide plate assembly, magnet, oil return assembly, skeleton oil seal, screw cap and dust seal.
  • the oil deflector assembly is coupled to a reservoir assembly, the oil deflector assembly is placed in a bottom portion of the cylinder assembly cylinder, the bottom valve gasket is placed over the oil guide assembly base, and the bottom valve assembly is placed Above the bottom valve gasket, the pressure cylinder gasket is placed in an annular groove on the valve body of the bottom valve assembly, the pressure cylinder is placed above the pressure cylinder gasket, the guide exhaust plate Placed on the pressure cylinder, the guide assembly is placed on the guide venting plate, and the guide assembly is engaged by the internal thread on the cylinder of the sump assembly cylinder, and the guide assembly is screwed down.
  • the guide exhaust plate, the pressure cylinder, the pressure cylinder gasket and the bottom valve assembly are press-fitted in the cylinder of the oil storage cylinder assembly; the skeleton oil seal, the screw cover, the outer circle of the dust seal and the guide assembly are connected
  • the inner circle is connected with the piston-piston rod assembly; the outer circumference of the piston-piston rod assembly is connected to the inner circumference of the pressure cylinder, and can slide relative to each other, and the piston rod passes through the guide assembly, the skeleton oil seal, the screw cover and the dustproof
  • the inner hole of the ring protrudes backward; the upper part of the oil return assembly and the pressure cylinder tube , And a lower oil guide plate assembly; said magnet assembly and the oil guide plate; said chamber is filled with hydraulic oil between the pressure chamber and the cylinder bore more than two thirds of the reserve tube assembly and a pressure cylinder.
  • the sump assembly includes an outer cylinder, a stern end coupling, the two forming a unitary container by welding; the sump assembly including a base and a rib; the bottom valve assembly including a screw cap The tower spring, the valve plate and the valve body, the screw cap passes through the tower spring and the valve piece, and the external thread at the bottom thereof is engaged with the internal thread on the valve body to form an integral assembly.
  • the guide assembly includes a guide body, a tested damping valve, a safety valve, a pressure sensor, a pressure sensor end seal, a temperature sensor, a temperature sensor end seal, a guide wear ring, and a Glyd ring.
  • the damper valve under test includes an adjustment screw cap, a screw cap lock ring, a regulating washer, a spring, a spool, and a valve seat.
  • the lower outer cylinder of the valve seat and the mounting hole of the guide body are tightly fitted, and the valve seat is generally pressed into the mounting hole by a special tool; the valve core is placed on the upper part of the valve seat and can slide in the mounting hole; the spring is placed on the upper part of the valve core In the spring seat, an adjusting washer is placed between the spring and the valve core; the adjusting screw cover is placed on the spring, and an adjusting washer is placed between the adjusting screw cover and the spring; the external thread and the guide of the adjusting screw cover are The inner thread of the body mounting hole is engaged, and the pre-compression amount of the spring can be adjusted by rotating the adjusting screw cover; the anti-loose sealing ring of the screw cover is generally made of rubber material, and is sleeved on the outer circumference of the adjusting screw cover to prevent loosening and sealing.
  • the safety valve adopts the same structure as the tested damping valve, but has different valve seats; the safety valve usually does not open, and opens under special working conditions such as excessive pressure to protect.
  • the pressure sensor and the temperature sensor are fixed on the guide body by the external thread of the end and the thread of the guide body; the end face seal of the pressure sensor is between the pressure sensor and the guide body.
  • the temperature sensor end face seal is between the temperature sensor and the guide body, and both of them function as a seal.
  • the guiding wear ring and the Glyd ring are respectively placed in the circular groove of the inner circle of the guide body, respectively, for guiding wear resistance and sealing action.
  • the piston-piston rod assembly includes a piston rod, a piston valve assembly, a piston, a piston glyph ring, a piston guide wear ring, a hexagonal flower countersunk head screw, and a piston exhaust plate.
  • the lower part of the piston rod passes through the piston valve cover, the piston valve wave spring and the piston valve valve piece in sequence, and the external thread is engaged with the internal thread of the piston inner hole through the external thread, thereby forming the piston rod, the piston valve assembly and the piston as a whole;
  • the outer circumference of the piston cooperates with the inner wall of the pressure cylinder, the piston can slide up and down along the inner wall of the pressure cylinder, and the piston glys ring and the piston guide wear ring are placed between the outer circumference of the piston and the inner wall of the pressure cylinder, respectively
  • the upper part of the piston rod protrudes through the inner hole of the guide assembly, the skeleton oil seal, the screw cover and the dust seal; the skeleton oil seals the oil and seal on the piston rod
  • the oil return assembly includes a return oil seal ring, a retaining ring, a return oil pipe joint, and a return oil pipe.
  • the oil return seal ring is placed on the retaining ring, and the oil return seal ring and the retaining ring are fixed on the pressure cylinder tube through the inner circle and the outer circle of the pressure cylinder tube; the oil return pipe joint is fixed on the hole of the retaining ring; the oil return pipe The upper portion is fixed to the oil return pipe joint and the lower portion is inserted into the rib plate of the oil guide plate assembly.
  • the test module is placed on a test rig including a high and low temperature chamber, and is excited by a servo actuator to test the dynamic characteristics of the damper valve under test. .
  • the automatic measurement and control system comprises a test bench, the aforementioned test module, a servo actuator component, a power source, a measurement and control cabinet, a power cabinet, a measurement and control signal, a weak electric cable, a strong electric cable, and a power transmission hose.
  • the test rig is mainly composed of a base, a high and low temperature box mounting bracket, a high and low temperature box, a column, a position adjustable beam, a beam position adjusting device, a beam fastener, a modular test device mounting joint, and a servo.
  • the actuator mounting block is constructed.
  • the base is made of cast iron or steel.
  • the column is the main bearing part of the gantry.
  • the lower part is connected by bolt or bolt and the base.
  • the test rig is in the form of two-column or four-column structure.
  • the position adjustable beam can be in the column. After sliding up and down and adjusting the position of the beam, the beam can be fixed on the column by fasteners; the lower part of the high and low temperature box mounting bracket is connected with the base, and the upper part is connected with the high and low temperature box, and the high and low temperature box is fixed on the base. .
  • test method of the aforementioned test module and automatic measurement and control system through the human machine interface and the test management module in the automatic test system host computer management software, the parameter setting is first performed, and then the system automatically performs the test; due to the modular test device The travel time is limited. In most cases, the test is usually carried out in a combination of automatic and manual operation. On the one hand, it is safe and reliable, on the other hand, it is easy to test and control, and obtain the desired test results.
  • the above method is a brand-new test principle and method, which effectively solves the problem that the method of supplying oil to the test valve by using a complicated hydraulic system cannot be tested effectively or not in a high or low temperature environment.
  • test module Based on the automatic measurement and control system of the invented test module, not only can the test temperature be conveniently and accurately controlled, but also the test module can be excited by the servo drive method under the desired ambient temperature condition, thereby detecting the test damping valve. Dynamic characteristics, and post-processing, saving and outputting test data; due to the automatic measurement and control system, the modular design and integration method are adopted in the hardware, and only the pluggable high-voltage cable and the measurement and control signal are adopted between the modules of the system. The weak electrical cable and the power transmission hose are interconnected, making installation, commissioning, movement and management of the equipment very convenient.
  • FIG. 1 is a schematic structural view of a test module for testing a dynamic characteristic of a hydraulic damper damping valve in the present application.
  • FIG. 2 is a schematic structural view of a guide assembly inside the test module.
  • Figure 3 is a cross-sectional view taken along line A-A of Figure 2;
  • Figure 4 is a cross-sectional view taken along line B-B of Figure 2;
  • Figure 5 is a structural schematic view and working principle diagram of the tested damping valve of Figure 3.
  • Figure 6 is a schematic structural view and working principle diagram of the safety valve of Figure 4.
  • Figure 7 is a schematic view showing the structure of the piston-piston rod assembly inside the test module.
  • Figure 8 is a schematic diagram of the operation of the test module.
  • FIG. 9 is a schematic structural view of an automatic measurement and control system for testing the dynamic characteristics of a hydraulic damper damping valve in the present application.
  • FIG. 10 is a schematic diagram of the measurement and control of the automatic measurement and control system described in the present application.
  • FIG. 11 is a schematic diagram showing the software structure of the automatic measurement and control system described in the present application.
  • Fig. 12 is a schematic diagram showing the step response normalization curve and the performance indexes of the dynamic characteristic test of the hydraulic damper damping valve in the present application.
  • Fig. 13 is a schematic view showing the sawtooth wave response curve of the dynamic characteristic test of the hydraulic damper damping valve in the present application.
  • Test module for dynamic characteristic test of oil pressure damper damping valve 2. Oil storage cylinder assembly; 21, outer cylinder tube; 22. Oil cylinder end coupling member; 3. Guide member; 31, guide body 32, the test damping valve; 321, the adjustment screw cover; 322, adjusting the screw cover anti-loose sealing ring; 323, adjusting the gasket; 324, the tested damping valve spring; 325, the tested damping valve spool; Test damper valve seat; 33, guide bearing wear ring; 34, guide glyph ring; 35, pressure sensor face seal ring; 36, pressure sensor; 37, safety valve; 371, safety valve adjustment screw cap; Safety valve adjustment screw cap anti-loose sealing ring; 373, safety valve adjusting gasket; 374, safety valve spring; 375, safety valve spool; 376, safety valve seat; 38, temperature sensor end seal; 39, temperature Sensor; 4, guide exhaust plate; 5, pressure cylinder; 6, piston-piston rod assembly; 61, piston rod; 62, piston valve assembly; 621, piston valve cover; 622,
  • the test module comprises a storage cylinder assembly 2, a guide assembly 3, a guide exhaust plate 4, a pressure cylinder 5, a piston-piston rod assembly 6, a hydraulic oil 7, a bottom valve assembly 8, a pressure cylinder gasket 9, and a bottom.
  • the valve gasket 10 the oil guide plate assembly 11, the magnet 12, the oil return assembly 13, the skeleton oil seal 14, the screw cap 15, and the dust seal 16.
  • the oil guide plate assembly 3 is connected to the oil storage cylinder assembly 2, the oil guide plate assembly 3 is placed at the bottom in the cylinder of the oil storage cylinder assembly 2, and the bottom valve gasket 10 is placed above the base of the oil guide plate assembly 11, the bottom valve assembly 8 is placed above the bottom valve gasket 10, the pressure cylinder gasket 9 is placed in an annular groove on the valve body of the bottom valve assembly 8, and the pressure cylinder 5 is placed above the pressure cylinder gasket 9 to guide the exhaust
  • the plate 4 is placed above the pressure cylinder 5, and the guide assembly 3 is placed above the guide venting plate 4, and the guide assembly 3 is screwed down by the external thread and the internal thread on the cylinder of the sump assembly 2
  • the guide assembly 3 presses the guide exhaust plate 4, the pressure cylinder 5, the pressure cylinder gasket 9 and the bottom valve assembly 8 into the cylinder of the oil storage cylinder assembly 2; the skeleton oil seal 14, the screw cover 15,
  • the outer circumference of the dust seal 16 is connected to the guide assembly 3, and the inner circle is connected with the piston-
  • the outer circumference of the piston-piston rod assembly 6 is connected to the inner circle of the pressure cylinder 5, and can slide relative to each other.
  • the rod extends through the inner hole of the guide assembly 3, the skeleton oil seal 14, the screw cap 15 and the dust seal 16; the upper portion of the oil return assembly 13 is connected to the pressure cylinder 5, The lower portion is connected to the oil guiding plate assembly 11; the magnet 12 is connected to the oil guiding plate assembly 11; the hydraulic oil 7 is filled between the inner cavity of the pressure cylinder 5 and more than two thirds of the storage cylinder assembly 2 and the pressure cylinder 5 Capacitance.
  • the oil storage cylinder assembly 2 includes an outer cylinder tube 21 and a cylinder end coupling member 22, which are integrally formed by welding;
  • the oil guiding plate assembly 11 includes an oil guiding plate base 111 and an oil guiding plate rib 112.
  • the oil plate assembly 11 is placed at the bottom of the oil sump assembly 2; the bottom valve gasket 10 is placed over the base 111 of the oil guide plate assembly 11.
  • the foot valve assembly 8 includes a bottom valve screw cover 81, a bottom valve tower spring 82, a bottom valve valve piece 83, and a bottom valve body 84.
  • the screw cap 81 passes through the tower spring 82 and the valve plate 83, and the external thread at the bottom thereof engages with the internal thread on the valve body 84 to form an integral assembly, and the bottom valve assembly 8 is placed above the bottom valve gasket 10.
  • the pressure cylinder gasket 9 is made of copper and placed in the annular groove on the bottom valve body 84.
  • the pressure cylinder 5 is placed on the pressure cylinder gasket 9.
  • the pressure cylinder When the pressure cylinder 5 is pressed by an external force, the pressure cylinder
  • the cartridge gasket 9 acts as a seal.
  • the guide member 3 is moved up and down by the external thread on the outer circumference thereof and the internal thread on the outer cylinder 21 of the reservoir assembly 2, and the lower end surface thereof is fitted to the upper end surface of the pressure cylinder 5.
  • the pressure cylinder 5 is pressed between the guide assembly 3 and the bottom valve assembly 8, and at this time, the inside of the pressure cylinder 5 forms a working cavity, the pressure cylinder
  • An external oil reservoir is formed between the outer portion of the cylinder 5 and the outer cylinder tube 21 of the oil storage cylinder assembly 2; the hydraulic oil 7 is filled with the working chamber and more than two thirds of the oil storage chamber; the guide exhaust plate 4 is made of copper.
  • the material is pressed between the guide assembly 3 and the pressure cylinder 5, one for sealing, and the other to isolate the air bubbles from being introduced into the guide assembly 3, particularly the tested damping valve 32.
  • the guide assembly 3 includes a guide body 31, a tested damping valve 32, a guide guide wear ring 33, a guide glyph ring 34, a pressure sensor end seal 35, a pressure sensor 36, and safety. Valve 37, temperature sensor face seal 38 and temperature sensor 39.
  • the tested damping valve 32 includes an adjusting screw cap 321, an adjusting screw cap sealing ring 322, an adjusting washer 323, a spring 324, a spool 325, and a valve seat 326.
  • the lower outer cylinder of the damper valve seat 326 and the mounting hole on the guide body 31 are tightly fitted, and the valve seat can be pressed into the mounting hole by a special tool;
  • the valve core 325 is placed on the upper part of the valve seat 326, and can be The mounting hole slides;
  • the tested damping valve spring 324 is placed in the spring seat at the upper portion of the spool 325, and an adjusting washer 323 is placed between the spring 324 and the spool 325;
  • the adjusting screw cap 321 is placed on the spring 324,
  • An adjusting washer 323 is disposed between the adjusting screw cap 321 and the spring 324; the external thread of the adjusting screw cap 321 and the thread of the mounting hole 31 are engaged, and the adjusting screw cap 321 can adjust the pre-com
  • the thickness of the pressing oil film between the valve core and the valve seat is ⁇ 1
  • the flow rate through the damping hole is Q 1 , if the diameter, length and seat surface of the damping hole are changed.
  • the safety valve 37 has the same structure and principle as the tested damping valve 32 except that the safety valve seat 376 having the unloading function is employed.
  • the safety valve 37 is generally not opened, but only opened under special working conditions such as excessive pressure, and the modular test device is protected; the safety valve spool 375 and the safety valve seat 376 are squeezed.
  • the thickness of the oil film is ⁇ 2 and the unloading flow rate is Q 2 .
  • the pressure sensor 36 and the temperature sensor 39 are fixed on the guide body 31 by the external thread of the end and the internal thread of the guide body 31; the pressure sensor end face seal 35 is between the pressure sensor 36 and the guide body 31, and the temperature The sensor face seal 38 is between the temperature sensor 39 and the guide body 31, both of which function as a seal.
  • the guide guide wear ring 33 and the guide glyph ring 34 are placed in the circular groove in the inner circumference of the guide body 31, respectively, for guiding wear resistance and high pressure sealing.
  • the piston-piston rod assembly 6 includes a piston rod 61, a piston valve assembly 62, a piston 63, a piston glyph ring 64, a piston guide wear ring 65, a hexagonal flower countersunk head screw 66, and a piston exhaust plate 67. .
  • the lower part of the piston rod passes through the piston valve cover 621, the piston valve wave spring 6622 and the piston valve valve piece 623 in sequence, and is engaged with the internal thread of the piston inner hole through the external thread thereof, thereby the piston rod 61, the piston valve assembly 62 and
  • the piston 65 is formed integrally; the outer circumference of the piston 65 is engaged with the inner wall of the pressure cylinder 5, the piston 65 is slidable up and down along the inner wall of the pressure cylinder 5, and the piston glys ring 66 and the piston guide wear ring 67 are placed. Between the outer circumference of the piston 65 and the inner wall of the pressure cylinder 5, sealing and guiding wear are respectively performed.
  • the upper portion of the piston rod 61 extends through the inner hole of the guide assembly 3, the skeleton oil seal 14, the screw cap 15 and the dust seal 16; the skeleton oil seal 14 acts to scrape and seal the piston rod 61, and the dust seal 16
  • the dust is prevented from being brought into the modular test device by the piston rod 61, and the screw cap 15 is fixed by the external thread on the screw and the internal thread on the guide body 31, and the skeleton oil seal 14 and the dust seal 16 are fixed; the hydraulic oil 7 It is filled with working chambers and more than two-thirds of the oil storage chamber.
  • the piston-piston rod assembly 6 divides the working cavity inside the pressure cylinder 5 into an upper working chamber and a lower working chamber; the hexagonal pattern countersunk screw 66 passes through the piston exhaust plate 67 and the bottom of the piston rod 61 The inner bore thread is engaged to secure the piston vent plate 67 to the lower portion of the piston 63 to isolate the air bubbles and prevent gas from being carried from the lower working chamber into the upper working chamber.
  • the piston-piston rod assembly 6 becomes a mechanical oil supply mechanism for supplying oil to the tested damping valve 32 in the guide bearing assembly 3, and controls the up and down movement speed of the oil supply mechanism.
  • the law can control the oil supply flow rate and the regularity; the temperature sensor 39 and the pressure sensor 36 can respectively detect the test temperature and the oil inlet pressure of the tested damping valve 32.
  • the oil of the tested damping valve 32 and the safety valve 37 can flow back to the oil storage chamber through the oil return passage in the guide; when the piston rod 61 moves up and down, the piston valve assembly 62 and the bottom valve assembly 8 cooperate with each other, so that The hydraulic oil circulates between the working chamber and the oil reservoir.
  • the oil return assembly 13 includes an oil return seal 131, a retaining ring 132, a return oil pipe joint 133, and a return oil pipe 134.
  • the oil return seal 131 is placed on the retaining ring 132.
  • the oil return seal 131 and the retaining ring 132 are fixed to the pressure cylinder through the inner circle thereof and the outer circle of the pressure cylinder 5; the oil return pipe joint 133 is fixed in the block.
  • the upper portion of the oil return pipe 134 is fixed to the oil return pipe joint 133, and the lower portion is inserted into the rib 112 of the oil guide plate assembly 11.
  • the piston-piston rod assembly 6 becomes a mechanical oil supply mechanism for supplying oil to the tested damping valve 32 in the guide bearing assembly 3, and the pressurized oil 7 passes through the tested damping valve 32 and passes through the inside of the guide body 31.
  • the oil return hole (solid arrow E2 in Fig. 8) flows out; the oil return assembly 13 directs the system oil return directly to the bottom of the oil storage cylinder assembly 2, avoiding mixing of the hydraulic oil and the upper air of the oil storage cylinder; the magnet 12 is placed in the oil return The bottom of the assembly 13 and the side walls of the ribs absorb the metal particles in the system return oil. If the safety valve 37 is opened, the oil is also discharged back to the oil reservoir through the oil return hole and the oil return assembly 13 inside the guide body 31.
  • the oil supply flow rate and the regularity can be controlled; and the pressure sensor and the temperature of the tested damping valve 32 can be respectively detected by the pressure sensor 36 and the temperature sensor 39.
  • the pressurized oil 7 flows out through the oil-receiving hole 32 (solid arrow C2 in Fig. 8) passing through the test damper valve 32, and then flows back to the bottom of the oil storage chamber through the oil return assembly 13. If the safety valve 37 is opened, the oil is also discharged back to the bottom of the oil reservoir through the oil return hole and the oil return assembly 13 inside the guide body 31.
  • the above technical solution integrates hydraulic oil, oil supply mechanism (piston-piston rod assembly), tested damping valve and sensor into a small test device like a hydraulic shock absorber product, forming an integrated test module.
  • the entire test module can be conveniently placed in the high and low temperature chamber, so that the oil temperature of the tested damping valve can be effectively and accurately controlled.
  • the problem of using the complex hydraulic system in the prior art to supply the oil to the tested damping valve cannot be effectively or not tested in high and low temperature environments is solved.
  • FIG. 9 to 11 illustrate an embodiment of an automatic measurement and control system for the dynamic characteristic test of a hydraulic damper damping valve of the present application.
  • This embodiment includes the aforementioned test module, test bench 17, hydraulic servo actuator 18, hydraulic station 19, measurement and control cabinet 20, power cabinet 21, measurement and control signals and weak electric cable 22, high-voltage cable 23 and hydraulic hose bundle 24 .
  • the test stand 17 includes a test stand base 171, a test module mounting joint 172, a high and low temperature box mounting bracket 173, a high and low temperature tank 174, a column 175, a beam position adjusting cylinder 176, a force sensor 177, a position adjustable beam 178, and a beam tight Firmware 179 and hydraulic servo actuator mounting block 1710.
  • the base 171 adopts a cast iron structure and has a large weight, which is the basis of the entire gantry; the column 175 is the main bearing member of the gantry, and the lower part thereof is connected by a bolt and a base 171, and the test gantry adopts a two-column structure; the position can be adjusted
  • the beam 178 can slide up and down on the column 175, and the position of the beam is adjusted by the beam position adjusting cylinder 176.
  • the adjustable beam 178 can be adjusted according to the length of the test module 1, the site condition and the set driving stroke. Position; After the position of the beam 178 is adjusted, the cylinder 176 can be adjusted by hydraulically locking the beam position on the one hand, and the beam 178 can be fixed on the column 175 by the beam fastener 179 on the other hand.
  • the lower portion of the high and low temperature tank mounting bracket 173 is connected to the base 171, and the upper portion is connected to the high and low temperature chamber 174, and the high and low temperature chamber 174 is fixed to the base 171.
  • the embodiment 1 of the test module is placed vertically in the high and low temperature chamber 174 of the test rig 17, and both the upper and lower rods can protrude from the high and low temperature chamber through the through holes in the box, between the through hole and the rod
  • the gap is provided with an insulated, sealed object that does not hinder the relative movement;
  • the upper end of the first embodiment of the test module is coupled to the force sensor 177 via the mounting joint 172, and the force sensor 177 is activated by the hydraulic servo actuator assembly 18.
  • the cylinder piston rod 184 is connected, and the lower end of the test module is connected to the base 171 of the test rig 17 through a mounting joint 172.
  • the hydraulic servo actuator assembly 18 includes a displacement sensor 181, a cylinder 182, an electro-hydraulic servo valve 183, and a cylinder rod 184, wherein the displacement sensor 181 is used to test the dynamic displacement of the piston rod 184 of the cylinder;
  • the actuator assembly 18 is fixed as an integral part by the servo actuator mounting block 1710 to the position of the test stand 17 on the adjustable beam 178.
  • the servo actuator assembly 18 is coupled to the hydraulic station 19 by a hydraulic hose bundle 24 that is hydraulically powered by a hydraulic station 19 that drives the tensile or compression motion of the test module 1 in a controlled manner to thereby dampen Test of valve dynamics.
  • the measurement and control cabinet 20 includes a measurement and control cabinet cabinet 201, a display 202, a button and display panel 203, a keyboard box 204, a printer 205, a controller 206, a host computer 207, and a power supply and secondary meter 208.
  • the measuring and controlling cabinet is the device for inputting, controlling signal output and processing, saving and outputting the test information in the automatic measurement and control system for the dynamic characteristic test of the hydraulic shock absorber damping valve.
  • Various industrial control components and equipment are installed. And arranged on the measuring and controlling cabinet cabinet 201.
  • the power cabinet 21 mainly includes a power cabinet cabinet 211, a voltmeter 212, an ammeter 213, and an air switch module 214.
  • the power cabinet is the device for inputting and outputting power in the automatic measurement and control system for the dynamic characteristics test of the oil damper damping valve.
  • Various power and industrial control components are installed and arranged on the cabinet of the electric cabinet. .
  • the automatic measurement and control system for the dynamic characteristics test of the oil damper damping valve adopts modular design and integration method in hardware. It can be divided into four modules in the macroscopic aspect: test bench integrated module, hydraulic station 19, measuring and controlling cabinet 20 and a power cabinet 21, wherein the test rig integrated module is an integrated body of the test rig 17, the test module 1, and the servo actuator assembly 18.
  • the measurement and control cabinet 20 is connected through the measurement and control signal and the weak electric cable 221, the strong electric cable 231 and the strong electric cabinet 21, and is connected to the test rig 17 through the measurement and control signal and the weak electric cable 222, and is connected to the hydraulic station 19 through the measurement and control signal and the weak electric cable 223;
  • the electric cabinet 21 is connected to the hydraulic station 19 via a strong electric cable 232, and is connected to the test rig 17 through a strong electric cable 233;
  • the test rig 17 is connected to the hydraulic station 19 via a hydraulic hose bundle 24, and the hydraulic hose bundle 24 includes a hydraulic pressure
  • the servo actuator assembly 18 and the two beam position adjustment cylinders 176 supply oil to the hose.
  • the four modules are connected to each other only through pluggable type measurement and control signals and weak electric cables, strong electric cables and hydraulic power transmission hoses. To move the equipment, simply unplug the cables and hoses.
  • the automatic measurement and control system for the dynamic characteristics test of the oil damper damping valve is based on the modern computer measurement and control principle, and uses the upper and lower position machine communication measurement and control mode to work.
  • the signals of pressure, flow rate and oil temperature of the hydraulic system of the displacement sensor 181, the force sensor 177, the pressure sensor 36, the temperature sensor 39 and the hydraulic station 19 are conditioned by the signal conditioning module, and then input into the AD/DA board inside the controller 206.
  • the switch quantity signals such as the monitoring switch quantity signal, the system button operation and the emergency stop operation in the hydraulic station 19 are also input to the DIO industrial control board; the CPU of the controller 206 passes the information processing, and the AD/DA board is passed on the one hand.
  • the servo amplifier and the electro-hydraulic servo valve 183 are driven to control the cylinder 182, and the intermediate relay is driven by the DIO industrial control board, the hydraulic pump motor, various hydraulic control solenoid valves, oil temperature control solenoid valves and Heaters, strong electrical contacts, various indicators and alarms are controlled for on and off.
  • the operation information can be input to the controller 206 at the same time.
  • the controller 206 can communicate with the host computer 207 through a communication protocol such as USB, RS-232, etc., and send the collected data to the host computer 207 for post-processing, and the host computer 207 finally exchanges information with the tester through the human-machine interface and the printer.
  • a communication protocol such as USB, RS-232, etc.
  • the software system of the automatic measurement and control system for the dynamic characteristics test of the oil damper damping valve is based on the Visual C++ environment programming development of Visual Studio.Net, which is divided into the controller measurement and control software and the upper computer management software.
  • the measurement and control software and the host computer management software exchange data through serial data communication.
  • the controller measurement and control software is responsible for system data acquisition, hardware drive and hardware management.
  • the software structure includes data acquisition module, signal library, control module, data communication module and hardware calibration maintenance module.
  • the signal library includes step function, simple harmonics and Various signal functions, such as triangular waves, can be used by the controller to drive the servo actuators in a relevant manner.
  • the upper computer management software is responsible for the test management and test data post-processing.
  • the software structure includes the test management module, the data communication module, the data processing module and the database module.
  • the management software accepts manual parameter setting and control commands through the man-machine interface, such as test date and time, tester, test category, test automatic or manual control, etc., through data communication, on the one hand, the hardware in the measurement and control system can be managed, and the other In terms of the data collected by the controller, after performing various post-processing on the data, the information such as the result is saved in a database or outputted through a human-machine interface or a printer.
  • the data processing module mainly includes error analysis, interpolation analysis, graphic curve drawing and test report processing output of the test data; the test "database file” can be output as a standard DATA file or an Excel file for more complicated data by other professional software. analysis.
  • FIG. 12 to 13 illustrate an embodiment of a test method for the dynamic characteristic test of a hydraulic damper damping valve of the present application. The embodiment is tested based on the embodiments of the aforementioned test module and automatic measurement and control system.
  • the test module 1 is installed in the high and low temperature chamber 174 of the test rig 17, and the desired ambient temperature of the high and low temperature chamber, for example, -30 ° C, is maintained at a constant temperature for 24 hours after the ambient temperature reaches the target temperature.
  • the hydraulic servo actuator assembly 18 is manually operated to compress the test module 1 to the shortest position and pause; the drive signal function for the hydraulic servo actuator assembly 18 is selected as a step signal (Fig. 12), the test module 1 is excited, that is, the test module 1 is quickly pulled to the target speed, and then pulled at a constant speed for a period of time, and finally stopped quickly; the compression test can also perform the same test, the operation method is the same as the method of stretching stroke;
  • the “automatic measurement and control system” performs data acquisition and data post-processing of the damping valve dynamic characteristics, and finally saves and outputs the test results.
  • Fig. 12 is a schematic diagram showing the step response normalization curve and the performance indexes of the dynamic characteristic test of the hydraulic damper damping valve in the present application.
  • v(t) is the input step signal normalization curve
  • P(t) is the normalized curve of the response of the tested damping valve inlet pressure at the step signal input.
  • t 1 , t 2 and t 3 are respectively The response time, peak time and transition time of the tested damping valve
  • ⁇ P is the pressure overshoot
  • e is the steady state error.
  • the test module 1 is excited, that is, the test module 1 is pulled to the target speed in a linear incremental manner, and then quickly stopped;
  • the compression test can also perform the same test, and the operation method is the same as the method of stretching the stroke;
  • the measurement and control system performs data acquisition and data processing of the damping valve dynamic characteristics, and finally saves and outputs the test results.
  • Fig. 13 is a schematic view showing the sawtooth wave response curve of the dynamic characteristic test of the hydraulic damper damping valve in the present application.
  • v e (t) is the curve of the sawtooth signal of the tension stroke input
  • P e (t) is the response curve of the inlet pressure of the stroke of the tested damping valve under the input of the sawtooth signal; as can be seen from the figure, After the valve is opened, the pressure is weakly increased (equivalent to unloading). When the input speed is quickly stopped, the tested damping valve cannot be closed quickly, and the closing time lags behind the sawtooth end time.
  • v c (t) is the compression stroke input sawtooth signal curve (indicated by the dotted line)
  • P c (t) is the response curve of the compression stroke of the tested damping valve inlet pressure under the sawtooth signal input.

Abstract

一种能在高、低温环境下，对油压减振器阻尼阀进行动态特性试验的测试模块（1），以及基于该测试模块（1）的自动测试系统和试验方法。该测试模块（1）包括储油缸组件（2）、导承组件（3）、导承排气板（4）、压力缸筒（5）、活塞-活塞杆组件（6）、液压油（7）、底阀组件（8）、压力缸筒垫片（9）、底阀垫片（10）、导油板组件（11）、磁铁（12）、回油组件（13）、骨架油封（14）、螺盖（15）和防尘圈（16），该测试模块（1）采用一体化设计原理将液压油（7）、供油机构、被试阻尼阀（32）及传感器集成在一起，整个测试模块（1）可以放置在高低温箱（174）内，可以方便、有效、准确解决对被试阻尼阀（32）油温进行控制的问题。

Description

用于油压减振器阻尼阀试验的测试模块和系统及试验方法
本申请要求于2017年09月11日提交中国专利局，申请号为201710810850.1、发明名称为“用于油压减振器阻尼阀试验的测试模块和系统及试验方法”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及一种能在高、低温环境下，对油压减振器阻尼阀进行动态特性试验的一体化测试模块、自动测控系统及试验方法，属于液压元器件试验设备、液压元器件试验技术、液压阻尼器产品试验技术领域。
背景技术
油压减振器是现代铁道车辆如高铁上的重要部件，对车辆系统的运动稳定性和舒适性起着重要作用，而阻尼阀又是油压减振器内部的关键器件，其性能对油压减振器的阻尼特性起决定性的作用。因此，对油压减振器阻尼阀进行动态特性试验、了解其性能和指标具有重要意义。此外，随着现代高铁技术的发展，高铁可能要求在一天内从高寒地区(-40℃以下)运行到高温地区，那么针对油压减振器阻尼阀的高、低温动态特性试验又成为了一个新的课题。
目前，不论是从铁道油压减振器的产品标准、试验台，还是从其阻尼特性辨识研究，国际上尚无关于油压减振器阻尼阀动态特性试验、特别是在高低温环境下进行动态特性试验的现有技术。
现有技术中介绍了一种测试汽车减振器活塞阀“流量-压力特性”的试验系统，该试验系统有如下特点：
(1)采用“离线”试验方式，即活塞阀被集成在一个专用的测试装置里面，而不是被直接集成在汽车减振器产品里面进行“在线”试验。
(2)采用了包括液压泵、各种液压控制阀、油箱在内的一整套液压系统向活塞阀供油的方式，因此系统复杂、体积庞大。
(3)专门设计了一套包括制冷、加热装置在内的油温控制系统，以维持系统油温的恒定。这种试验方式在常温下是可行的，但在高低温、特别是在低温条件下运用上述方法是不可行的。因为在低温、譬如-30℃以下时，一般液压泵已不能有效吸油，很多液压控制阀、管路不能正常工作，更不用说有效、准确地进行相关试验了；再者，在高、低温试验中，对整个液压系统液压油进行温度控制，既不方便又不节能。
(4)只能测试活塞阀的“流量-压力特性”，不能测试其响应、启闭等动态特性和指标。
为了能在高、低温环境下，对油压减振器阻尼阀进行动态特性试验，现 有技术中的常规试验方法不可行，因此必须发明一种全新的试验原理和试验模块、自动测控系统和试验方法。该发明必须具体解决以下技术问题：
(1)采用一体化设计原理将油液、供油机构、被试阻尼阀及传感器集成在一个类似油压减振器产品的小的测试模块内，整个模块可以放置在高低温箱内，这样就可以方便、有效、准确解决对被试阻尼阀温度控制的问题。
(2)在高温或低温条件下，自动测控系统能通过伺服驱动方式对模块化的测试装置进行激振，输入包括阶跃、锯齿波等在内的各种激振信号，而且参数可调，以测试阻尼阀的动态特性。
(3)自动测控系统不但能自动控制模模块化的测试装置的温度、激振信号输入，还能自动测试通过被试阻尼阀油液的温度、压力、流量等物理量，并将测试数据进行后处理、保存和输出。
发明内容
本申请采用以下技术方案：
一种用于油压减振器阻尼阀动态特性试验的测试模块，包括储油缸组件、导承组件、导承排气板、压力缸筒、活塞-活塞杆组件、液压油、底阀组件、压力缸筒垫片、底阀垫片、导油板组件、磁铁、回油组件、骨架油封、螺盖和防尘圈。所述导油板组件和储油缸组件连接，导油板组件被放置在储油缸组件缸筒内的底部，所述底阀垫片放置在导油板组件底座之上，所述底阀组件放置在底阀垫片之上，所述压力缸筒垫片放置在底阀组件阀体上的环形槽内，所述压力缸筒放置在压力缸筒垫片之上，所述导承排气板放置在压力缸筒之上，所述导承组件放置在导承排气板之上，导承组件通过其外螺纹和储油缸组件缸筒上的内螺纹咬合，向下拧紧时，导承组件将导承排气板、压力缸筒、压力缸筒垫片和底阀组件压紧固定在储油缸组件缸筒内；所述骨架油封、螺盖、防尘圈的外圆和导承组件连接，内圆和活塞-活塞杆组件连接；所述活塞-活塞杆组件的活塞外圆与压力缸筒内圆连接，可以相对滑动，活塞杆穿过导承组件、骨架油封、螺盖和防尘圈的内孔后而伸出；所述回油组件上部和压力缸筒连接，下部和导油板组件连接；所述磁铁和导油板组件连接；所述液压油被充满压力缸筒内腔和三分之二以上的储油缸组件和压力缸筒之间的容腔。
另一方面，所述储油缸组件包括外缸筒、储油缸端部联结件，二者通过焊接形成一个整体容器；所述导油板组件包括底座和肋板；所述底阀组件包括螺盖、塔簧、阀片和阀体，螺盖穿过塔簧和阀片，通过其底部的外螺纹和阀体上的内螺纹咬合，形成一个整体组件。
另一方面，所述导承组件包括导承体、被试阻尼阀、安全阀、压力传感器、压力传感器端面密封圈、温度传感器、温度传感器端面密封圈、导向耐磨环和格莱圈。被试阻尼阀包括调节螺盖、螺盖防松密封环、调节垫片、弹簧、阀芯和阀座。阀座的下部外圆柱体和导承体安装孔为紧配合，阀座一般通过 专用工具被压入安装孔；阀芯放置在阀座上部，可以在安装孔内滑动；弹簧放置在阀芯上部的弹簧座内，在弹簧和阀芯之间放置有调节垫片；调节螺盖放置在弹簧之上，在调节螺盖和弹簧之间放置有调节垫片；调节螺盖的外螺纹和导承体安装孔内螺纹咬合，转动调节螺盖可以调节弹簧的预压缩量；螺盖防松密封环一般采用橡胶类材料，套在调节螺盖外圆周上，起防松、密封的作用。
另一方面，所述安全阀采用了与被试阻尼阀相同的结构，但具有不同的阀座；安全阀通常不会打开，在特殊工况如压力超标情况下开启，起保护作用。
另一方面，所述压力传感器、温度传感器均通过其端部外螺纹和导承体内螺纹咬合而固定在导承体上；所述压力传感器端面密封圈处于压力传感器和导承体之间，所述温度传感器端面密封圈处于温度传感器和导承体之间，它们均起密封作用。
另一方面，所述导向耐磨环、格莱圈分别放置在导承体内圆的环形槽内，分别起导向耐磨和密封作用。
另一方面，所述活塞-活塞杆组件包括活塞杆、活塞阀组件、活塞、活塞格莱圈、活塞导向耐磨环、内六角花型沉头螺钉和活塞排气板。活塞杆下部按顺序穿过活塞阀挡盖、活塞阀波形弹簧和活塞阀阀片后，通过其外螺纹与活塞内孔的内螺纹咬合，从而将活塞杆、活塞阀组件和活塞组成一个整体；活塞的外圆和压力缸筒的内壁配合，活塞可沿着压力缸筒内壁上、下滑动，活塞格莱圈和活塞导向耐磨环被放置在活塞外圆和压力缸筒内壁之间，分别起密封和导向耐磨的作用，所述活塞杆的上部穿过导承组件内孔、骨架油封、螺盖和防尘圈后而伸出；所述骨架油封起对活塞杆刮油和密封作用，防尘圈防止灰尘被活塞杆带入模块化的测试装置，螺盖通过其上的外螺纹和导承上的内螺纹咬合，对骨架油封和防尘圈起固定作用。
另一方面，所述回油组件包括回油密封圈、挡圈、回油管接头和回油管。回油密封圈放置在挡圈之上，回油密封圈和挡圈通过其内圆与压力缸筒外圆配合而固定在压力缸筒上；回油管接头固定在挡圈的孔上；回油管上部固定在回油管接头上，下部插入导油板组件的肋板内。
使用如前述测试模块进行高低温动态特性试验的自动测控系统，将前述测试模块放置在包括高低温箱的试验台架上，采用伺服作动器进行激振，从而测试被试阻尼阀的动态特性。
另一方面，所述自动测控系统包括试验台架、前述测试模块、伺服作动器组件、动力源、测控柜、强电柜、测控信号及弱电电缆、强电电缆以及动力输送软管。
另一方面，所述试验台架主要由底座、高低温箱安装支架、高低温箱、立柱、位置可调整横梁、横梁位置调整装置、横梁紧固件、模块化的测试装置安装接头和伺服作动器安装块构成。
另一方面，底座采用铸铁或钢结构，立柱是台架的主要承力件，其下部通 过插销或螺栓和底座连接，试验台架采用两柱或四柱结构的形式；位置可调整横梁可以在立柱上上下滑动，横梁位置调整好以后，可以通过紧固件将横梁在立柱上予以固定；所述高低温箱安装支架下部和底座连接，上部和高低温箱连接，将高低温箱固定在底座上。
使用如前述测试模块和自动测控系统的试验方法，通过自动测试系统上位机管理软件中的人机界面和试验管理模块，首先进行参数设定，然后由系统自动进行试验；由于模块化的测试装置的行程有限，在大部分情况下往往采取自动和手动操作相结合的方式进行试验，一方面安全可靠，另一方面便于试验控制、取得所期望的试验结果。
采用本申请的技术方案可以产生如下技术效果：
(1)发明了关于油压减振器阻尼阀动态特性试验、特别是在高低温环境下进行动态特性试验的新技术。
(2)采用一体化设计原理将液压油、供油机构、被试阻尼阀及传感器集成在一个类似油压减振器产品的小的测试模块内，这样整个测试模块可以被放置在高低温箱内，这样就可以方便、有效、准确解决对被试阻尼阀温度控制的问题。
以上方法是一种全新的试验原理和方法，有效解决了采用复杂液压系统向被试阀供油的方法不能有效地或不能在高、低温环境下进行试验的问题。
(3)基于所发明测试模块的自动测控系统，不但能够方便、准确控制试验温度，还能在期望的环境温度条件下，通过伺服驱动方式对测试模块进行激振，从而检测被试阻尼阀的动态特性，并将测试数据进行后处理、保存和输出；由于该自动测控系统，在硬件上采用了模块化设计、集成方法，系统各模块之间仅通过可插拔型强电电缆、测控信号及弱电电缆和动力输送软管相互连接，使得安装调试、移动和管理设备非常方便。
(4)基于所发明测试模块和自动测控系统的试验方法，非常方便输入譬如包括阶跃、锯齿波等在内的各种伺服激振信号，而且参数可调，使得针对被试阻尼阀动态特性的试验变得方便、准确，并且丰富的后处理函数可以获得任意期望的动态特性曲线、指标数据输出。
附图简述
图1是本申请中用于油压减振器阻尼阀动态特性试验的测试模块的结构示意图。
图2是所述测试模块里面导承组件的结构示意图。
图3是图2的A-A剖面示意图。
图4是图2的B-B剖面示意图。
图5是图3中被试阻尼阀的结构示意图和工作原理图。
图6是图4中安全阀的结构示意图和工作原理图。
图7是所述测试模块里面活塞-活塞杆组件的结构示意图。
图8是所述测试模块的工作原理图。
图9是本申请中用于油压减振器阻尼阀动态特性试验的自动测控系统的结构示意图。
图10是本申请中所述自动测控系统的测控原理图。
图11是本申请中所述自动测控系统的软件结构示意图。
图12是本申请中油压减振器阻尼阀动态特性试验阶跃响应归一化曲线及各性能指标示意图。
图13是本申请中油压减振器阻尼阀动态特性试验锯齿波响应曲线示意图。
图中各标号表示：
1、用于油压减振器阻尼阀动态特性试验的测试模块；2、储油缸组件；21、外缸筒；22、储油缸端部联结件；3、导承组件；31、导承体；32、被试阻尼阀；321、调节螺盖；322、调节螺盖防松密封环；323、调节垫片；324、被试阻尼阀弹簧；325、被试阻尼阀阀芯；326、被试阻尼阀阀座；33、导承导向耐磨环；34、导承格莱圈；35、压力传感器端面密封圈；36、压力传感器；37、安全阀；371、安全阀调节螺盖；372、安全阀调节螺盖防松密封环；373、安全阀调节垫片；374、安全阀弹簧；375、安全阀阀芯；376、安全阀阀座；38、温度传感器端面密封圈；39、温度传感器；4、导承排气板；5、压力缸筒；6、活塞-活塞杆组件；61、活塞杆；62、活塞阀组件；621、活塞阀挡盖；622、活塞阀波形弹簧；623、活塞阀阀片；63、活塞；64、活塞格莱圈；65、活塞导向耐磨环；66、内六角花型沉头螺钉；67、活塞排气板；7、液压油；8、底阀组件；81、底阀螺盖；82、底阀塔簧；83、底阀阀片；84、底阀阀体；9、压力缸筒垫片；10、底阀垫片；11、导油板组件；111、导油板底座；112、导油板肋板；12、磁铁；13、回油组件；131、回油密封圈；132、挡圈；133、回油管管接头；134、回油管；14、骨架油封；15、螺盖；16、防尘圈；17、试验台架；171、试验台架底座；172、测试模块安装接头；173、高低温箱安装支架；174、高低温箱；175、立柱；176、横梁位置调整油缸；177、力传感器；178、位置可调整横梁；179、横梁紧固件；1710、液压伺服作动器安装块；18、液压伺服作动器组件；181、位移传感器；182、作动缸；183、电液伺服阀；184、作动缸活塞杆；19、液压站；20、测控柜；201、测控柜柜体；202、显示器；203、按钮与显示灯面板；204、键盘盒；205、打印机；206、控制器；207、上位计算机；208、电源及二次仪表；21、强电柜；211、强电柜柜体；212、电压表；213、电流表；214、空气开关模块；22、测控信号及弱电电缆；221、测控柜与强电柜连接测控信号及弱电电缆；222、测控柜与试验台架连接测控信号及弱电电缆；223、测控柜与液压站连接测控信号及弱电电缆；23、强电电缆；231、强电柜与测控柜连接强电电缆；232、强电柜与液压站连接强电电缆；233、强电柜与试验台架连接强电电缆；24、液压软管束。
具体实施方式
以下结合说明书附图和具体实施例对本申请作进一步详细说明。
图1至图8示出了本申请一种用于油压减振器阻尼阀动态特性试验的测试模块的一种实施例。该测试模块包括储油缸组件2、导承组件3、导承排气板4、压力缸筒5、活塞-活塞杆组件6、液压油7、底阀组件8、压力缸筒垫片9、底阀垫片10、导油板组件11、磁铁12、回油组件13、骨架油封14、螺盖15和防尘圈16。导油板组件3和储油缸组件2连接，导油板组件3被放置在储油缸组件2缸筒内的底部，底阀垫片10放置在导油板组件11的底座之上，底阀组件8放置在底阀垫片10之上，压力缸筒垫片9放置在底阀组件8阀体上的环形槽内，压力缸筒5放置在压力缸筒垫片9之上，导承排气板4放置在压力缸筒5之上，导承组件3放置在导承排气板4之上，导承组件3通过其外螺纹和储油缸组件2缸筒上的内螺纹咬合，向下拧紧时，导承组件3将导承排气板4、压力缸筒5、压力缸筒垫片9和底阀组件8压紧固定在储油缸组件2缸筒内；骨架油封14、螺盖15、防尘圈16的外圆和导承组件3连接，内圆和活塞-活塞杆组件6连接；活塞-活塞杆组件6的活塞外圆与压力缸筒5的内圆连接，可以相对滑动，活塞杆穿过导承组件3、骨架油封14、螺盖15和防尘圈16的内孔后而伸出；回油组件13的上部和压力缸筒5连接，下部和导油板组件11连接；磁铁12和导油板组件11连接；液压油7被充满压力缸筒5的内腔和三分之二以上的储油缸组件2和压力缸筒5之间的容腔。
参见图1储油缸组件2包括外缸筒21、储油缸端部联结件22，二者通过焊接形成一个整体容器；导油板组件11包括导油板底座111、导油板肋板112，导油板组件11放置在储油缸组件2的底部；底阀垫片10则放置在导油板组件11的底座111之上。
底阀组件8包括底阀螺盖81、底阀塔簧82、底阀阀片83和底阀阀体84。螺盖81穿过塔簧82和阀片83，通过其底部的外螺纹和阀体84上的内螺纹咬合，形成一个整体组件，底阀组件8放置在底阀垫片10之上。
压力缸筒垫片9采用铜材，放置在底阀阀体84上环形槽内，压力缸筒5放置在压力缸筒垫片9之上，当压力缸筒5被外力压紧时，压力缸筒垫片9起密封作用。
导承组件3通过其外圆周上的外螺纹和储油缸组件2的外缸筒21上的内螺纹咬合而上下运动，其下部端面和压力缸筒5上部端面配合。当向下紧固导承组件3时，压力缸筒5被压紧在导承组件3和底阀组件8之间，此时压力缸筒5的内部便形成了一个工作容腔，压力缸筒5的外部和储油缸组件2的外缸筒21之间便形成了一个储油腔；液压油7被充满工作容腔和三分之二以上的储油腔；导承排气板4采用铜材，被压紧在导承组件3和压力缸筒5之间，一是起密封作用，二是起隔离气泡、防止气体被带入导承组件3特别是被试阻尼阀32之中。
参见图3-图4，导承组件3包括导承体31、被试阻尼阀32、导承导向耐磨环33、导承格莱圈34、压力传感器端面密封圈35、压力传感器36、安全阀37、温度传感器端面密封圈38和温度传感器39。
参见图5，被试阻尼阀32包括调节螺盖321、调节螺盖防松密封环322、调节垫片323、弹簧324、阀芯325和阀座326。被试阻尼阀阀座326的下部外圆柱体和导承体31上的安装孔为紧配合，阀座可通过专用工具被压入安装孔；阀芯325放置在阀座326的上部，可以在安装孔内滑动；被试阻尼阀弹簧324放置在阀芯325上部的弹簧座内，在弹簧324和阀芯325之间放置有调节垫片323；调节螺盖321放置在弹簧324之上，在调节螺盖321和弹簧324之间放置有调节垫片323；调节螺盖321的外螺纹和导承体31安装孔内螺纹咬合，转动调节螺盖321可以调节弹簧324的预压缩量；调节螺盖防松密封环322采用合成橡胶材料，套在调节螺盖321外圆周上，起防松、密封的作用。
当被试阻尼阀被高压液流打开时，设阀芯和阀座之间挤压油膜的厚度为δ 1，设通过阻尼孔的流量为Q 1，如果改变阻尼孔直径、长度以及阀座表面环形槽的参数，即可以对具有不同参数的阻尼阀进行动态特性测试。
参见图6，安全阀37除了采用具有卸荷功能的安全阀阀座376之外，其余结构和原理与被试阻尼阀32完全一样。在试验中，安全阀37一般不会打开，只是在特殊工况如压力超标情况下才开启，对模块化的测试装置起保护作用；安全阀阀芯375和安全阀阀座376之间挤压油膜的厚度为δ 2，卸荷流量为Q 2。
压力传感器36、温度传感器39均通过其端部外螺纹和导承体31内螺纹咬合而固定在导承体31上；压力传感器端面密封圈35处于压力传感器36和导承体31之间，温度传感器端面密封圈38处于温度传感器39和导承体31之间，它们均起密封作用。
导承导向耐磨环33、导承格莱圈34均放置在导承体31内圆的环形槽内，分别起导向耐磨和高压密封作用。
参见图7，活塞-活塞杆组件6包括活塞杆61、活塞阀组件62、活塞63、活塞格莱圈64、活塞导向耐磨环65、内六角花型沉头螺钉66和活塞排气板67。活塞杆下部按顺序穿过活塞阀挡盖621、活塞阀波形弹簧6622和活塞阀阀片623后，通过其外螺纹与活塞内孔的内螺纹咬合，从而将活塞杆61、活塞阀组件62和活塞65组成一个整体；活塞65的外圆和压力缸筒5的内壁配合，活塞65可沿着压力缸筒5的内壁上、下滑动，活塞格莱圈66和活塞导向耐磨环67被放置在活塞65的外圆和压力缸筒5的内壁之间，分别起密封和导向耐磨的作用。
活塞杆61的上部穿过导承组件3的内孔、骨架油封14、螺盖15和防尘圈16后而伸出；骨架油封14起对活塞杆61刮油和密封作用，防尘圈16防止灰尘被活塞杆61带入模块化的测试装置，螺盖15通过其上的外螺纹和导 承体31上的内螺纹咬合，对骨架油封14和防尘圈16起固定作用；液压油7被充满工作容腔和三分之二以上的储油腔。
活塞-活塞杆组件6将压力缸筒5里面的工作容腔分隔成上工作容腔和下工作容腔；内六角花型沉头螺钉66穿过活塞排气板67后，与活塞杆61底部内孔螺纹咬合，从而将活塞排气板67固定在活塞63的下部，起隔离气泡、防止气体从下工作容腔被带入到上工作容腔的作用。
当活塞杆61被外力驱动上、下运动时，活塞-活塞杆组件6便成为了一个向导承组件3里面的被试阻尼阀32供油的机械式供油机构，控制供油机构上下运动速度及规律，即可控制供油流量及规律；通过温度传感器39、压力传感器36可分别检测出被试阻尼阀32的试验温度、进油压力。
被试阻尼阀32和安全阀37的出油均可通过导承里面的回油通道流回储油腔；活塞杆61上、下运动时，活塞阀组件62和底阀组件8相互配合，使得液压油在工作容腔和储油腔之间循环流动。
参见图1，回油组件13包括回油密封圈131、挡圈132、回油管管接头133和回油管134。回油密封圈131放置在挡圈132之上，回油密封圈131和挡圈132通过其内圆与压力缸筒5的外圆配合而固定在压力缸筒上；回油管接头133固定在挡圈132的孔上；回油管134上部固定在回油管管接头133上，下部插入导油板组件11的肋板112内。
当活塞杆61被外力驱动向上运动时(图8中实线箭头所示方向)，活塞63上的通孔由于被活塞阀阀片623密封住，活塞63上方的工作容腔便形成了高压；同时底阀阀片83由于活塞63的上抽作用而向上运动，造成底阀阀体84上的通孔被打开，储油缸组件2里面的液压油被吸入(图8中实线箭头E1)到活塞63下方的工作容腔，起体积补偿作用。
因此，此时活塞-活塞杆组件6便成为了一个向导承组件3里面被试阻尼阀32供油的机械式供油机构，压力油7通过被试阻尼阀32、经过导承体31里面的回油孔(图8中实线箭头E2)流出；回油组件13将系统回油直接引导进入储油缸组件2底部，避免了液压油和储油缸上部空气的混合；磁铁12被放置在回油组件13的底部和肋板侧壁，可吸附系统回油中的金属颗粒物。如果安全阀37被打开，其出油也是经过导承体31里面的回油孔和回油组件13流回储油腔。
控制供油机构的运动速度和规律，即可控制供油流量和规律；通过压力传感器36、温度传感器39可分别检测出被试阻尼阀32的进油压力和温度。
当活塞杆61被外力驱动向下运动时(图8中虚线箭头所示方向)，底阀阀片83由于活塞63的下压作用而将底阀阀体84上的通孔关闭，同时活塞阀阀片623向上运动，活塞63上的通孔被打开，造成活塞63下方工作容腔里面的液压油被压入到其上方工作容腔(图8中虚线箭头C1)，因此活塞63的上、下工作容腔都形成了高压。
同样，压力油7通过被试阻尼阀32、经过导承体31里面的回油孔(图8 中实线箭头C2)流出，然后经过回油组件13流回储油腔底部。如果安全阀37被打开，其出油也是经过导承体31里面的回油孔和回油组件13流回储油腔底部。
上述技术方案将液压油、供油机构(活塞-活塞杆组件)、被试阻尼阀及传感器集成在了一个类似油压减振器产品的小的测试装置内，形成了一个一体化的测试模块。这样整个测试模块可以被方便地放置在高低温箱内，这样就可以有效、准确地控制被试阻尼阀的油温。解决了现有技术中采用复杂液压系统向被试阻尼阀供油方法不能有效地或不能在高、低温环境下进行试验的问题。
图9至图11示出了本申请用于油压减振器阻尼阀动态特性试验的自动测控系统的一种实施例。该实施例包括前述测试模块、试验台架17、液压伺服作动器18、液压站19、测控柜20、强电柜21、测控信号及弱电电缆22、强电电缆23和液压软管束24。
试验台架17包括试验台架底座171、测试模块安装接头172、高低温箱安装支架173、高低温箱174、立柱175、横梁位置调整油缸176、力传感器177、位置可调整横梁178、横梁紧固件179和液压伺服作动器安装块1710。
底座171采用铸铁结构，重量较大，是整个台架的基础；立柱175是台架的主要承力件，其下部通过螺栓和底座171连接，试验台架采用两柱结构的形式；位置可调整横梁178可以在立柱175上上下滑动，横梁位置采用横梁位置调整油缸176进行动力方式调整，在准备试验时，可以根据测试模块1的长度、现场情况和设定驱动行程，调整可调整横梁178的位置；当横梁178位置调整好以后，一方面可以通过液压控制锁紧横梁位置调整油缸176，另一方面通过横梁紧固件179将横梁178在立柱175上予以固定。
高低温箱安装支架173下部和底座171连接，上部和高低温箱174连接，将高低温箱174固定在底座171上。
测试模块的实施例1竖直放置在试验台架17的高低温箱174内，其上部和下部杆件均可通过箱体上的通孔伸出高低温箱，在通孔和杆件之间的间隙处，设有不妨碍相对运动的隔热、密封物体；测试模块的实施例1的上端通过安装接头172与力传感器177连接，力传感器177再与液压伺服作动器组件18的作动缸活塞杆184连接，测试模块的下端通过安装接头172与试验台架17的底座171连接。
液压伺服作动器组件18包括位移传感器181、作动缸182、电液伺服阀183和作动缸活塞杆184，其中位移传感器181用来测试作动缸活塞杆184的动态位移；液压伺服作动器组件18作为一个整体部件由伺服作动器安装块1710固定在试验台架17的位置可调整横梁178上.
伺服作动器组件18通过液压软管束24和液压站19连接，液压伺服作动器组件18由液压站19提供液压动力，按控制规律驱动测试模块1的拉伸或者压缩运动，从而进行阻尼阀动态特性的试验。
测控柜20包括测控柜柜体201、显示器202、按钮与显示灯面板203、键盘盒204、打印机205、控制器206、上位计算机207和电源及二次仪表208。测控柜是本申请用于油压减振器阻尼阀动态特性试验的自动测控系统中的传感器信息输入、控制信号输出以及测试结果处理、保存和输出的装置，各种工控元器件、设备均安装、布置在测控柜柜体201上。
强电柜21主要包括强电柜柜体211、电压表212、电流表213和空气开关模块214。强电柜是本申请用于油压减振器阻尼阀动态特性试验的自动测控系统中的电力输入、输出的装置，各种电力和工控元器件均安装、布置在强电柜柜体上211。
用于油压减振器阻尼阀动态特性试验的自动测控系统在硬件上采用模块化设计、集成方法，其在宏观上可分为四个模块：试验台架集成模块、液压站19、测控柜20和强电柜21，其中试验台架集成模块是试验台架17、测试模块1和伺服作动器组件18的集成体。
测控柜20通过测控信号及弱电电缆221、强电电缆231和强电柜21连接，通过测控信号及弱电电缆222和试验台架17连接，通过测控信号及弱电电缆223和液压站19连接；强电柜21通过强电电缆232和液压站19连接，通过强电电缆233和试验台架17连接；试验台架17通过液压软管束24和液压站19连接，液压软管束24包括向液压伺服作动器组件18和两个横梁位置调整油缸176供油的软管。
所述四个模块之间仅通过可插拔型测控信号及弱电电缆、强电电缆和液压动力输送软管相互连接，如需移动装备，只需拔掉电缆、软管即可。
参见图10，用于油压减振器阻尼阀动态特性试验的自动测控系统基于现代计算机测控原理，采用上、下位机通讯测控的方式进行工作。将位移传感器181、力传感器177、压力传感器36、温度传感器39以及液压站19液压系统的压力、流量和油温等信号，经过信号调理模块调理后，输入控制器206里面的AD/DA板卡，同时将液压站19中的监控开关量信号、系统按钮操作、急停操作等开关量信号也输入到DIO工控板卡；控制器206的CPU通过信息处理后，一方面通过AD/DA板卡驱动伺服放大器和电液伺服阀183，从而对作动缸182实施控制，另一方面通过DIO工控板卡驱动中间继电器，对液压站油泵电机、各种液压控制电磁阀、油温控制电磁阀和加热器、强电接触器、各种指示灯和报警器进行通断控制。针对电源的按钮操作和急停操作在对电源进行直接控制的情况下，同时可将操作信息输入控制器206。
控制器206可以通过USB、RS-232等通讯协议与上位计算机207进行通讯，将采集的数据送到上位计算机207进行后处理，上位计算机207最后通过人机界面、打印机与试验人员进行信息交互。
参见图11，用于油压减振器阻尼阀动态特性试验的自动测控系统的软件系统基于Visual Studio.Net的Visual C++环境编程开发，宏观上分为控制器测控软件和上位机管理软件，控制器测控软件和上位机管理软件通过串行数据 通讯进行数据交互。
控制器测控软件负责系统的数据采集、硬件驱动和硬件管理，软件结构包括数据采集模块、信号库、控制模块、数据通讯模块和硬件标定维护模块；信号库包括如阶跃函数、简谐波和三角波等各种信号函数，控制器可以运用这些信号函数对伺服作动器进行相关规律的驱动。
上位机管理软件负责试验管理和试验数据后处理，软件结构包括试验管理模块、数据通讯模块、数据处理模块和数据库模块。管理软件通过人机界面接受人工参数设定和控制指令，譬如试验日期时间、试验员、试验类别、试验自动还是手动控制等，通过数据通讯一方面可对测控系统中的硬件进行管理，另一方面可以获得控制器采集的数据，在对数据进行各种后处理以后，将结果等信息保存在数据库或通过人机界面、打印机进行信息输出。
数据处理模块主要包括对试验数据的误差分析、插值分析、图形曲线绘制和试验报告的处理输出；试验“数据库文件”可以以标准DATA文件或者Excel文件输出，供其它专业软件进行更为复杂的数据分析。
图12至图13示出了本申请用于油压减振器阻尼阀动态特性试验的试验方法的一种实施例，实施例基于前述测试模块和自动测控系统的实施例进行试验。
将测试模块1安装在试验台架17的高低温箱174内，设定所期望的高低温箱的环境温度，譬如-30℃，在环境温度达到目标温度后，保持恒温24小时。
(1)试验开始时，先手动操作液压伺服作动器组件18，将测试模块1压缩至接近最短的位置、暂停；选取对液压伺服作动器组件18的驱动信号函数为阶跃信号(图12)，对测试模块1进行激振，即快速拉动测试模块1至目标速度，然后匀速拉动一段时间，最后迅速停止；压缩回程也可以进行同样试验，操作方法与拉伸行程时方法一样；运用“自动测控系统”进行阻尼阀动态特性数据采集和数据后处理，最后将试验结果保存和输出。
图12是本申请中油压减振器阻尼阀动态特性试验阶跃响应归一化曲线及各性能指标示意图。图中v(t)是输入阶跃信号归一化曲线，P(t)是被试阻尼阀进口压力在阶跃信号输入下响应的归一化曲线，t 1、t 2、t 3分别是被试阻尼阀的响应时间、峰值时间和过渡过程时间，ΔP是压力超调量，e是稳态误差。
(2)对油压减振器阻尼阀进行锯齿波响应动态特性试验可以观察阻尼阀的启闭特性。试验开始时，先手动操作液压伺服作动器组件18，将测试模块1压缩至接近最短的位置、暂停；选取对液压伺服作动器组件18的驱动信号函数为锯齿波(也称三角波)信号(图13)，对测试模块1进行激振，即线性递增方式拉动测试模块1至目标速度，然后迅速停止；压缩回程也可以进行同样试验，操作方法与拉伸行程时方法一样；运用“自动测控系统”进行阻尼阀动态特性数据采集和数据处理，最后将试验结果保存和输出。
图13是本申请中油压减振器阻尼阀动态特性试验锯齿波响应曲线示意 图。图中v e(t)是拉伸行程输入锯齿波信号曲线，P e(t)是拉伸行程被试阻尼阀进口压力在锯齿波信号输入下的响应曲线；从图中可以看出，被试阻尼阀在开阀后，压力呈弱增长方式(相当于卸荷)，当输入速度迅速停止后，被试阻尼阀又不能迅速关闭，其关闭时间滞后于锯齿波终止时间。
图中v c(t)是压缩行程输入锯齿波信号曲线(用虚线表示)，P c(t)是压缩行程被试阻尼阀进口压力在锯齿波信号输入下的响应曲线。

Claims (9)

  1. 一种用于油压减振器阻尼阀试验的测试模块，其特征在于：测试模块包括储油缸组件、导承组件、导承排气板、压力缸筒、活塞-活塞杆组件、液压油、底阀组件、压力缸筒垫片、底阀垫片、导油板组件、磁铁、回油组件、骨架油封、螺盖和防尘圈，所述导油板组件和储油缸组件连接，导油板组件被放置在储油缸组件缸筒内的底部，所述底阀垫片放置在导油板组件底座之上，所述底阀组件放置在底阀垫片之上，所述压力缸筒垫片放置在底阀组件阀体上的环形槽内，所述压力缸筒放置在压力缸筒垫片之上，所述导承排气板放置在压力缸筒之上，所述导承组件放置在导承排气板之上，导承组件通过其外螺纹和储油缸组件缸筒上的内螺纹咬合，向下拧紧时，导承组件将导承排气板、压力缸筒、压力缸筒垫片和底阀组件压紧固定在储油缸组件缸筒内；所述骨架油封、螺盖、防尘圈的外圆和导承组件连接，内圆和活塞-活塞杆组件连接；所述活塞-活塞杆组件的活塞外圆与压力缸筒内圆连接，可以相对滑动，活塞杆穿过导承组件、骨架油封、螺盖和防尘圈的内孔后而伸出；所述回油组件上部和压力缸筒连接，下部和导油板组件连接；所述磁铁和导油板组件连接；所述液压油被充满压力缸筒内腔和三分之二以上的储油缸组件和压力缸筒之间的容腔；所述导承组件包括导承体、被试阻尼阀、安全阀、压力传感器、压力传感器端面密封圈、温度传感器、温度传感器端面密封圈、导向耐磨环、格莱圈，所述压力传感器、温度传感器均通过其端部外螺纹和导承体内螺纹咬合而固定在导承体上；所述压力传感器端面密封圈处于压力传感器和导承体之间，所述温度传感器端面密封圈处于温度传感器和导承体之间，所述导向耐磨环、格莱圈分别放置在导承体内圆的环形槽内，被试阻尼阀包括调节螺盖、螺盖防松密封环、调节垫片、弹簧、阀芯和阀座，阀座的下部外圆柱体和导承体安装孔为紧配合，阀座通过专用工具被压入安装孔；阀芯放置在阀座上部，可以在安装孔内滑动；弹簧放置在阀芯上部的弹簧座内，在弹簧和阀芯之间放置有调节垫片；调节螺盖放置在弹簧之上，在调节螺盖和弹簧之间放置有调节垫片；调节螺盖的外螺纹和导承体安装孔内螺纹咬合，转动调节螺盖可以调节弹簧的预压缩量；螺盖防松密封环套在调节螺盖外圆周上，安全阀采用了与被试阻尼阀相同的结构，但具有不同的阀座。
  2. 如权利要求1所述的测试模块，其特征在于，所述储油缸组件包括外缸筒、储油缸端部联结件，二者通过焊接形成一个整体容器；所述导油板组件包括底座、肋板，导油板组件放置在储油缸组件底部；所述底阀垫片放置在导油板组件的底座上。
  3. 如权利要求1所述的测试模块，其特征在于，所述底阀组件包括螺盖、塔簧、阀片和阀体，螺盖穿过塔簧和阀片，通过其底部的外螺纹和阀体上的内螺纹咬合，形成一个整体组件，底阀组件放置在底阀垫片之上。
  4. 一种使用如前述权利要求1-3任一所述的测试模块进行高低温动态特性试验的自动测控系统，将前述测试模块放置在包括高低温箱的试验台架 上，采用伺服作动器进行激振，从而测试被试阻尼阀的动态特性。
  5. 如权利要求4所述的自动测控系统，其特征在于：所述自动测控系统包括试验台架、前述测试模块、伺服作动器组件、动力源、测控柜、强电柜、测控信号及弱电电缆、强电电缆以及动力输送软管，所述试验台架主要由底座、高低温箱安装支架、高低温箱、立柱、位置可调整横梁、横梁位置调整装置、横梁紧固件、测试模块安装接头和伺服作动器安装块构成；
    自动测控系统在硬件上采用模块化设计、集成方法，其在宏观上可分为四个模块：试验台架集成模块、动力源、测控柜和强电柜，其中试验台架集成模块是试验台架、前述测试模块和伺服作动器组件的集成体；所述四个模块之间仅通过可插拔型测控信号及弱电电缆、强电电缆和动力输送软管相互连接，如需移动装备，只需拔掉电缆、拆掉动力输送软管即可。
  6. 如权利要求5所述的自动测控系统，其特征在于：底座采用铸铁或钢结构，立柱是台架的主要承力件，其下部通过插销或螺栓和底座连接，试验台架采用两柱或四柱结构的形式；位置可调整横梁可以在立柱上上下滑动，横梁位置调整好以后，可以通过紧固件将横梁在立柱上予以固定，所述高低温箱安装支架下部和底座连接，上部和高低温箱连接，将高低温箱固定在底座上。
  7. 如权利要求5所述的自动测控系统，其特征在于：所述测试模块可放置在试验台架的高低温箱内，其两端杆件均可通过箱体上的通孔伸出高低温箱，在通孔和杆件之间的间隙处，设有不妨碍相对运动的隔热、密封物体；测试模块的一端通过安装接头与力传感器连接，力传感器再与驱动装置连接，测试模块的另一端通过安装接头与试验台架连接。
  8. 如权利要求5所述的自动测控系统，其特征在于：所述伺服作动器组件包括位移传感器、作动装置和伺服控制装置，由伺服作动器安装块固定在试验台架上，其中位移传感器用来测试作动器的动态位移；伺服作动器组件采用液压、气压或伺服电机驱动的方式，驱动测试模块的拉伸或者压缩运动；伺服作动器组件由液压站、气站或电源提供动力，伺服作动器通过液压软管、气管或者电缆与动力源连接；伺服作动器安装在试验台架的位置可调整横梁上，从而在上方驱动测试模块；伺服作动器也可以安装在试验台架的底座上，从而在下方驱动测试模块，当测试模块被水平横向放置在高低温箱内、实验台架采用横向设计或可倾摆方式设计时，伺服驱动装置从横向驱动测试模块。
  9. 采用如权利要求4-8任一所述的自动测试系统的试验方法，将所述测试模块安装在试验台架的高低温箱内，设定高低温箱的环境温度，在环境温度达到目标温度后，保持恒温24小时及以上；选取伺服作动器驱动信号函数，对测试模块进行激振，运用所述自动测控系统进行阻尼阀动态特性数据采集和数据后处理，最后将试验结果保存和输出。
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