CN108223492A - A kind of hydraulic linear motor element seal friction force and viscosity friction coefficient test system and method - Google Patents
A kind of hydraulic linear motor element seal friction force and viscosity friction coefficient test system and method Download PDFInfo
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- 238000000034 method Methods 0.000 title claims abstract description 9
- 238000007789 sealing Methods 0.000 claims abstract description 23
- 238000006073 displacement reaction Methods 0.000 claims abstract description 22
- 230000033001 locomotion Effects 0.000 claims abstract description 16
- 239000007788 liquid Substances 0.000 claims description 30
- 239000002828 fuel tank Substances 0.000 claims description 7
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 6
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- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
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Abstract
本发明属于液压测试技术领域，具体是一种液压直线运动元件密封力及粘性摩擦系数测试系统及方法。解决了解决高水基液压元件粘性摩擦力和粘性摩擦系数大小测试的问题，驱动部分包括滤器I、驱动泵、溢流阀I、电液比例方向阀、液控单向阀I、液控单向阀II、位移传感器和驱动油缸，驱动部分包括滤器I、驱动泵、溢流阀I、电液比例方向阀、液控单向阀I、液控单向阀II、位移传感器和驱动油缸，被测部分包括压力表I、蓄能器I、截止阀I、截止阀II、蓄能器II、压力表II、被测缸、拨片、行程开关I、行程开关II、单向阀I、单向阀II、电液换向阀、溢流阀II、充液泵和过滤器II。本发明可以测量不同压差和运动速度下的密封摩擦阻力和摩擦系数。
The invention belongs to the technical field of hydraulic testing, in particular to a testing system and method for sealing force and viscous friction coefficient of a hydraulic linear motion element. Solved the problem of testing the viscous friction force and viscous friction coefficient of high water-based hydraulic components. The driving part includes filter I, drive pump, overflow valve I, electro-hydraulic proportional directional valve, hydraulic control check valve I, hydraulic control check valve II. Displacement sensor and drive cylinder. The drive part includes filter I, drive pump, relief valve I, electro-hydraulic proportional directional valve, hydraulic control check valve I, hydraulic control check valve II, displacement sensor and drive cylinder. The part includes pressure gauge I, accumulator I, shut-off valve I, shut-off valve II, accumulator II, pressure gauge II, measured cylinder, paddle, travel switch I, travel switch II, one-way valve I, one-way Valve II, electro-hydraulic directional valve, overflow valve II, charge pump and filter II. The invention can measure sealing frictional resistance and frictional coefficient under different pressure differences and moving speeds.
Description
技术领域technical field
本发明属于液压测试技术领域，具体是一种液压直线运动元件密封力及粘性摩擦系数测试系统及方法。The invention belongs to the technical field of hydraulic testing, in particular to a testing system and method for sealing force and viscous friction coefficient of a hydraulic linear motion element.
背景技术Background technique
目前，煤矿液压支架液压系统广泛采用高水基乳化液作为传递介质（95-97%水 +3-5%乳化油混合而成），介质粘度低，液压系统和液压元件内部易泄漏，所以高水基液压元件广泛采用O形圈密封，尤其在液压支架液压缸与液压阀上使用居多。在对液压缸或液压阀进行数学建模时，需要考虑阀芯或液压缸所受的轴向摩擦力。传统的油压阀主要依靠间隙密封，其所受的粘性阻尼力小，但高水基液压元件O形圈所受的粘性摩擦力很大，且与其两端压差和运动速度相关，目前O形圈粘性摩擦力计算都是参考传统的油压阀计算公式进行，计算结果存在较大的误差，从而影响对液压阀或液压缸类元件动态特性的研究。At present, the hydraulic system of coal mine hydraulic supports widely uses high water-based emulsion as the transmission medium (95-97% water + 3-5% emulsified oil mixed), the viscosity of the medium is low, and the hydraulic system and hydraulic components are easy to leak inside, so high water-based hydraulic components O-ring seals are widely used, especially in hydraulic support hydraulic cylinders and hydraulic valves. When mathematically modeling a hydraulic cylinder or hydraulic valve, it is necessary to consider the axial friction force on the spool or hydraulic cylinder. The traditional oil pressure valve mainly relies on the gap seal, which suffers from small viscous damping force, but the viscous friction force suffered by the O-ring of high-water-based hydraulic components is very large, and it is related to the pressure difference between its two ends and the speed of movement. At present, the O-ring The calculation of viscous friction force is carried out with reference to the traditional oil pressure valve calculation formula, and there are large errors in the calculation results, which will affect the research on the dynamic characteristics of hydraulic valves or hydraulic cylinder components.
发明内容Contents of the invention
本发明为了解决解决高水基液压元件粘性摩擦力和粘性摩擦系数大小测试的问题，提供一种液压直线运动元件密封力及粘性摩擦系数测试系统及方法。In order to solve the problem of testing the viscous friction force and viscous friction coefficient of high water-based hydraulic components, the present invention provides a hydraulic linear motion component sealing force and viscous friction coefficient testing system and method.
本发明采取以下技术方案：一种液压直线运动元件密封力及粘性摩擦系数测试系统，包括驱动部分、连接部分和被测部分。The invention adopts the following technical solutions: a testing system for sealing force and viscous friction coefficient of a hydraulic linear motion element, including a driving part, a connecting part and a measured part.
驱动部分包括滤器I、驱动泵、溢流阀I、电液比例方向阀、液控单向阀I、液控单向阀II、位移传感器和驱动油缸，过滤器I与驱动泵连接，驱动泵与电液比例方向阀的P口连接，电液比例方向阀的T口与油箱连接，P口和T口之间并联有溢流阀I，电液比例方向阀的A口和B口分别通过液控单向阀I和液控单向阀II与驱动油缸连接，驱动油缸上设有位移传感器，液控单向阀I的控制口连接液控单向阀II的进液口，液控单向阀II的控制口连接到液控单向阀I的进液口。The driving part includes a filter I, a driving pump, an overflow valve I, an electro-hydraulic proportional directional valve, a hydraulic control check valve I, a hydraulic control check valve II, a displacement sensor and a driving cylinder. The filter I is connected to the driving pump, and the driving pump It is connected to the P port of the electro-hydraulic proportional directional valve, and the T port of the electro-hydraulic proportional directional valve is connected to the oil tank. There is a relief valve I connected in parallel between the P port and the T port, and the A port and the B port of the electro-hydraulic proportional directional valve respectively pass through The hydraulic control check valve I and the hydraulic control check valve II are connected to the driving cylinder, and the driving cylinder is provided with a displacement sensor. The control port of the hydraulic control check valve I is connected to the liquid inlet of the hydraulic control check valve II. The control port of the valve II is connected to the liquid inlet of the hydraulic control check valve I.
连接部分包括转接头I、拉压力传感器和转接头II，转接头I一端与驱动油缸连接，转接头I另一端通过拉压力传感器与转接头II连接。The connection part includes an adapter I, a tension pressure sensor and an adapter II, one end of the adapter I is connected to the drive cylinder, and the other end of the adapter I is connected to the adapter II through the tension pressure sensor.
被测部分包括压力表I、蓄能器I、截止阀I、截止阀II、蓄能器II、压力表II、被测缸、拨片、行程开关I、行程开关II、单向阀I、单向阀II、电液换向阀、溢流阀II、充液泵和过滤器II；被测缸一端与转接头II连接，被测缸的活塞杆端面上固定有拨片，所述被测缸左右两腔通过密封圈隔开，拨片的左、右两端试验台面上分别设置行程开关I和行程开关II，被测缸的a口与蓄能器I连接，蓄能器I上连接有压力表I，c口与蓄能器II连接，蓄能器II上连接有压力表II，被测缸的b口与单向阀II连接，d口与单向阀I连接，蓄能器I和蓄能器II连接有截止阀I和截止阀II；单向阀I、单向阀II分别与电液换向阀的A口和B口连接，电液换向阀P口与T口之间连接有溢流阀II，电液换向阀P口与充液泵连接，充液泵与过滤器II连接，过滤器II与油箱连接，电液换向阀T口直接与油箱连接。The measured part includes pressure gauge I, accumulator I, shut-off valve I, shut-off valve II, accumulator II, pressure gauge II, measured cylinder, paddle, travel switch I, travel switch II, check valve I, One-way valve II, electro-hydraulic reversing valve, overflow valve II, liquid filling pump and filter II; one end of the tested cylinder is connected to the adapter II, and a paddle is fixed on the end surface of the piston rod of the tested cylinder. The left and right chambers of the measuring cylinder are separated by a sealing ring. The travel switch I and the travel switch II are respectively set on the test bench at the left and right ends of the paddle. The a port of the measured cylinder is connected to the accumulator I, and The pressure gauge I is connected, the c port is connected to the accumulator II, the pressure gauge II is connected to the accumulator II, the b port of the measured cylinder is connected to the one-way valve II, and the d port is connected to the one-way valve I to store energy. The stop valve I and the stop valve II are connected to the accumulator I and the accumulator II; the check valve I and the check valve II are respectively connected to the A port and the B port of the electro-hydraulic directional valve, and the P port of the electro-hydraulic directional valve is connected to the T port. Relief valve II is connected between the ports, the P port of the electro-hydraulic reversing valve is connected to the charging pump, the charging pump is connected to the filter II, the filter II is connected to the fuel tank, and the T port of the electro-hydraulic reversing valve is directly connected to the fuel tank .
左转接头和右转接头的左、右两端分别设置有螺纹凸台，左转接头左端的螺纹凸台拧进驱动油缸的活塞杆中的螺纹孔，右端的螺纹凸台拧进拉压力传感器左端的螺纹孔中；右转接头左端的螺纹凸台拧进进拉压力传感器右端的螺纹孔中，右端的螺纹凸台拧进被测油缸的活塞杆中的螺纹孔。The left and right ends of the left and right swivel joints are respectively provided with threaded bosses. The threaded bosses at the left end of the left swivel joints are screwed into the threaded holes in the piston rod of the drive cylinder, and the threaded bosses at the right end are screwed into the tension pressure sensor. In the threaded hole at the left end; the threaded boss at the left end of the right-hand adapter is screwed into the threaded hole at the right end of the pressure sensor, and the threaded boss at the right end is screwed into the threaded hole in the piston rod of the measured oil cylinder.
一种液压直线运动元件密封力及粘性摩擦系数测试方法，包括以下步骤，A method for testing sealing force and viscous friction coefficient of a hydraulic linear motion element, comprising the following steps,
101～测试前，先开启驱动泵和充液泵，并保证蓄能器I和蓄能器II都充有一定压力的氮气；101～Before the test, first turn on the driving pump and the charging pump, and ensure that both the accumulator I and the accumulator II are filled with nitrogen at a certain pressure;
102～调节电液比例方向阀使被测缸恢复到初始位置，即拨片与行程开关I贴合；102~Adjust the electro-hydraulic proportional directional valve to restore the measured cylinder to the initial position, that is, the paddle and the travel switch I fit together;
103～关闭电液比例阀，使驱动油缸停止，此时，打开截止阀I和截止阀II，释放蓄能器内的液体，使被测缸左右两腔液体压力为零，然后再关闭截止阀I和截止阀II，打开电液换向阀分别对被测缸左右两腔充液，直到左右两腔液体压力分别上升到试验需要的压力值时再关闭电液换向阀，充液完成，然后关闭充液泵，降低充液泵引起的振动和压力脉动对测试结果的干扰；103 ~ Close the electro-hydraulic proportional valve to stop the driving cylinder. At this time, open the stop valve I and stop valve II to release the liquid in the accumulator, so that the liquid pressure in the left and right chambers of the measured cylinder is zero, and then close the stop valve I and shut-off valve II, open the electro-hydraulic reversing valve to fill the left and right cavities of the cylinder under test respectively, until the liquid pressure of the left and right cavities respectively rises to the pressure value required for the test, then close the electro-hydraulic reversing valve, and the filling is completed. Then turn off the charging pump to reduce the interference of the vibration and pressure pulsation caused by the charging pump on the test results;
104～开启电液比例方向阀，根据试验需要，可以给电液比例方向阀的放大器输入端输入不同的电流，这样电液比例方向阀的开口量就会不同，流量也不同，驱动油缸的运动速度就会不同；包括匀速条件下测试和变速条件下测试；104～Open the electro-hydraulic proportional directional valve, according to the needs of the test, you can input different currents to the input terminal of the amplifier of the electro-hydraulic proportional directional valve, so that the opening amount and flow rate of the electro-hydraulic proportional directional valve will be different, and the movement of the driving cylinder will be different. The speed will be different; including tests under constant speed conditions and tests under variable speed conditions;
105～在步骤104的测试过程中，由位移传感器记录驱动油缸和被测缸的位移，由拉压力传感器记录传感器的总力F总，,两种工况下的密封圈摩擦力分别为：105～During the testing process in step 104, the displacement sensor records the displacement of the driving cylinder and the measured cylinder, and the total force F of the sensor is recorded by the tension and pressure sensor. The friction force of the sealing ring under the two working conditions is respectively:
匀速条件时： At constant velocity:
摩擦力Fm=F总-（P右-P左）A；Friction force F m = F total - (P right - P left ) A;
粘性摩擦系数：C=；Viscous friction coefficient: C= ;
变速条件时： During shifting conditions:
摩擦力Fm=F总-（P右-P左）A-M；Friction force F m = F total - (P right - P left ) AM ;
粘性摩擦系数：C=；Viscous friction coefficient: C= ;
以上式子中，P左、P右分别为被测缸左右两腔的压力，A为被测缸左右两腔受力面积，为所测位移的导数，即速度，为所测位移的二阶导数，即加速度；In the above formula, Pleft and Pright are the pressures of the left and right cavities of the measured cylinder respectively, and A is the stress area of the left and right cavities of the measured cylinder, is the derivative of the measured displacement, that is, the velocity, is the second derivative of the measured displacement, that is, the acceleration;
106～当拨片碰到行程开关II后，系统停止测量，再重复步骤101-105重新测量。106～When the paddle touches the limit switch II, the system stops measuring, and then repeats steps 101-105 to measure again.
与现有技术相比，本发明能测量不同形式密封圈下的液压缸或液压阀阀芯密封摩擦阻力和摩擦系数，方案简单易行；可以调节密封圈两端压力，测量不同压差下的密封摩擦阻力和摩擦系数；被测部分液压阀阀芯或液压缸的运动速度可控，可测量不同运动速度下的密封摩擦力及摩擦系数。Compared with the prior art, the present invention can measure the sealing friction resistance and friction coefficient of hydraulic cylinders or hydraulic valve spools under different forms of sealing rings, and the scheme is simple and feasible; the pressure at both ends of the sealing ring can be adjusted to measure the friction coefficient under different pressure differences. Seal friction resistance and friction coefficient; the movement speed of the hydraulic valve spool or hydraulic cylinder under test can be controlled, and the seal friction force and friction coefficient at different movement speeds can be measured.
附图说明Description of drawings
图1为本发明的原理图；Fig. 1 is a schematic diagram of the present invention;
图中：1-过滤器I，2-驱动泵，3-溢流阀I，4-电液比例方向阀，5-液控单向阀I，6-液控单向阀II，7-位移传感器，8-驱动油缸，9-转接头I，10-拉压力传感器，11-转接头II，12-压力表I，13-蓄能器I，14-截止阀I，15-截止阀II，16-蓄能器II，17-压力表II，18-被测缸，19-紧固螺钉，20-拨片，21-行程开关I，22-行程开关II，23-单向阀I，24-单向阀II，25-电液换向阀，26-溢流阀II，27-充液泵，28-过滤器II。In the figure: 1-filter I, 2-drive pump, 3-relief valve I, 4-electro-hydraulic proportional directional valve, 5-hydraulic control check valve I, 6-hydraulic control check valve II, 7-displacement Sensor, 8-drive cylinder, 9-adapter I, 10-pull pressure sensor, 11-adapter II, 12-pressure gauge I, 13-accumulator I, 14-stop valve I, 15-stop valve II, 16-accumulator II, 17-pressure gauge II, 18-tested cylinder, 19-fastening screw, 20-paddle, 21-travel switch I, 22-travel switch II, 23-one-way valve I, 24 - one-way valve II, 25 - electro-hydraulic reversing valve, 26 - overflow valve II, 27 - filling pump, 28 - filter II.
具体实施方式Detailed ways
如图1所示，一种液压直线运动元件密封力及粘性摩擦系数测试系统，包括驱动部分、连接部分和被测部分，驱动部分包括滤器I1、驱动泵2、溢流阀I3、电液比例方向阀4、液控单向阀I5、液控单向阀II6、位移传感器7和驱动油缸8，过滤器I1与驱动泵2连接，驱动泵2与电液比例方向阀4的P口连接，电液比例方向阀4的T口与油箱连接，P口和T口之间并联有溢流阀I3，电液比例方向阀4的A口和B口分别通过液控单向阀I5和液控单向阀II6与驱动油缸8连接，驱动油缸8上设有位移传感器7，液控单向阀I5的控制口连接液控单向阀II6的进液口，液控单向阀II6的控制口连接到液控单向阀I5的进液口。As shown in Figure 1, a hydraulic linear motion element sealing force and viscous friction coefficient testing system includes a driving part, a connecting part and a measured part. The driving part includes a filter I1, a driving pump 2, an overflow valve I3, an electro-hydraulic proportional Directional valve 4, hydraulic control check valve I5, hydraulic control check valve II6, displacement sensor 7 and drive cylinder 8, filter I1 is connected to drive pump 2, drive pump 2 is connected to port P of electro-hydraulic proportional directional valve 4, The T port of the electro-hydraulic proportional directional valve 4 is connected to the fuel tank, and a relief valve I3 is connected in parallel between the P port and the T port. The one-way valve II6 is connected with the driving cylinder 8, the driving cylinder 8 is provided with a displacement sensor 7, the control port of the hydraulic control one-way valve I5 is connected with the liquid inlet of the hydraulic control one-way valve II6, and the control port of the hydraulic control one-way valve II6 Connect to the liquid inlet of hydraulic control check valve I5.
连接部分包括转接头I9、拉压力传感器10和转接头II11，转接头I9一端与驱动油缸8连接，转接头I9另一端通过拉压力传感器10与转接头II11连接。The connection part includes an adapter I9, a tension pressure sensor 10 and an adapter II11. One end of the adapter I9 is connected to the drive cylinder 8, and the other end of the adapter I9 is connected to the adapter II11 through the tension pressure sensor 10.
被测部分包括压力表I12、蓄能器I13、截止阀I14、截止阀II15、蓄能器II16、压力表II17、被测缸18、拨片20、行程开关I21、行程开关II22、单向阀I23、单向阀II24、电液换向阀25、溢流阀II26、充液泵27和过滤器II28；被测缸18一端与转接头II11连接，被测缸18的活塞杆端面上固定有拨片20，所述被测缸18左右两腔通过密封圈隔开，拨片20的左、右两端试验台面上分别设置行程开关I21和行程开关II22，单向阀I23、单向阀II24分别与电液换向阀25的A口和B口连接，电液换向阀25P口与T口之间连接有溢流阀II26，电液换向阀25P口与充液泵27连接，充液泵27与过滤器II28连接，过滤器II28与油箱连接，电液换向阀25T口直接与油箱连接。The measured part includes pressure gauge I12, accumulator I13, shut-off valve I14, shut-off valve II15, accumulator II16, pressure gauge II17, tested cylinder 18, paddle 20, travel switch I21, travel switch II22, check valve I23, one-way valve II24, electro-hydraulic reversing valve 25, overflow valve II26, liquid filling pump 27 and filter II28; one end of the tested cylinder 18 is connected with the adapter II11, and the end surface of the piston rod of the tested cylinder 18 is fixed with The paddle 20, the left and right cavities of the measured cylinder 18 are separated by a sealing ring, and the left and right ends of the paddle 20 are respectively provided with a travel switch I21 and a travel switch II22 on the test bench, and a one-way valve I23 and a one-way valve II24 They are respectively connected to the A port and the B port of the electro-hydraulic reversing valve 25, and the overflow valve II26 is connected between the 25P port and the T port of the electro-hydraulic reversing valve, and the 25P port of the electro-hydraulic reversing valve is connected to the filling pump 27, and the filling The liquid pump 27 is connected with the filter II28, the filter II28 is connected with the fuel tank, and the 25T port of the electro-hydraulic reversing valve is directly connected with the fuel tank.
所述液控单向阀I5、液控单向阀II6组合，其中，液控单向阀I5的控制口连接液控单向阀II6的进液口，液控单向阀II6的控制口连接到液控单向阀I5的进液口，两个液控单向阀构成一个双向锁，连接在驱动缸8与电液比例方向阀4之间，能保证驱动缸停留在任意位置时对被测部分的蓄能器I13或蓄能器II16进行充液。The combination of the hydraulic control check valve I5 and the hydraulic control check valve II6, wherein the control port of the hydraulic control check valve I5 is connected to the liquid inlet of the hydraulic control check valve II6, and the control port of the hydraulic control check valve II6 is connected to To the liquid inlet of the hydraulic control check valve I5, the two hydraulic control check valves form a two-way lock, which is connected between the drive cylinder 8 and the electro-hydraulic proportional directional valve 4, which can ensure that the drive cylinder stays in any position for the The accumulator I13 or accumulator II16 of the measuring part is filled with liquid.
所述电液比例方向阀4为油介质阀，能够通过调节阀芯开度来调节流量，达到调节驱动油缸运动速度的目的。The electro-hydraulic proportional directional valve 4 is an oil medium valve, which can adjust the flow rate by adjusting the opening of the valve core to achieve the purpose of adjusting the moving speed of the driving oil cylinder.
所述位移传感器7为非接触式传感器，分为移动测量杆和外壳。移动测量杆右端与驱动油缸8活塞杆通过螺纹连接在一起，传感器外壳安装在驱动缸左壁端面上。驱动油缸8与移动测量杆具有相等的运动速度。The displacement sensor 7 is a non-contact sensor, which is divided into a moving measuring rod and a casing. The right end of the moving measuring rod is threadedly connected with the 8 piston rods of the drive cylinder, and the sensor housing is installed on the end face of the left wall of the drive cylinder. The driving cylinder 8 has the same speed of motion as the moving measuring rod.
所述转接头分为转接头I9和转接头II11，两个转接头左右两端分别设置螺纹凸台。转接头I9左端螺纹凸台拧进驱动油缸8的活塞杆中的螺纹孔，右端螺纹凸台拧进拉压力传感器10左端的螺纹孔中。转接头II11左端螺纹凸台拧进进拉压力传感器10右端的螺纹孔中，右端螺纹凸台拧进被测油缸18的活塞杆中的螺纹孔。这样，在更换不同的力传感器后，只需更换转接头即可，而不用重新设置驱动油缸8和被测缸18上的螺纹孔。The adapter is divided into adapter I9 and adapter II11, and the left and right ends of the two adapters are respectively provided with threaded bosses. The threaded boss at the left end of the adapter I9 is screwed into the threaded hole in the piston rod of the drive cylinder 8, and the threaded boss at the right end is screwed into the threaded hole at the left end of the pressure sensor 10. The threaded boss at the left end of the adapter II11 is screwed into the threaded hole at the right end of the pull pressure sensor 10, and the threaded boss at the right end is screwed into the threaded hole in the piston rod of the measured oil cylinder 18. In this way, after replacing different force sensors, it is only necessary to replace the adapter without resetting the threaded holes on the driving cylinder 8 and the measured cylinder 18 .
所述被测缸18左右两腔靠密封圈隔开，且密封圈可以为各种不同结构形式，所述被测缸18的活塞杆右端设置螺纹孔，用紧固螺钉19将拨片20压紧固定在被测缸18的右端面，所述拨片20的左右两端试验台面上分别设置行程开关I21、行程开关II22，当被测缸向右移动碰到行程开关II22时即停止，当被测缸向左移动碰到行程开关I21时即停止。The left and right chambers of the measured cylinder 18 are separated by a sealing ring, and the sealing ring can be in various structural forms. The right end of the piston rod of the measured cylinder 18 is provided with a threaded hole, and the pick 20 is pressed by a fastening screw 19. Tightly fixed on the right end face of the measured cylinder 18, the left and right ends of the paddle 20 are respectively provided with a travel switch I21 and a travel switch II22 on the test bench. When the measured cylinder moves to the right and touches the travel switch II22, it stops. The measured cylinder stops when it moves to the left and touches the travel switch I21.
所述单向阀I23、单向阀II24连接在被测缸18与电液换向阀25之间，所述电液换向阀25控制分别能控制左右蓄能器I13、蓄能器II16的充液，所述单向阀I23与被测缸18右腔连通，所述单向阀II24与被测缸18左腔连通。所述蓄能器I13、蓄能器II14分别与被测缸18的左右两腔连通，所述蓄能器容积与被测缸完整行程容积之比应大于等于10:1，保证被测缸在左右移动时，蓄能器I13、蓄能器II16内部的液体压力基本保持不变，实现恒压测量。所述蓄能器I13入口端并联压力表I12，用来测量蓄能器I13的充液压力；所述蓄能器II16入口端并联压力表II17，用来测量蓄能器II16的充液压力。所述截止阀I14连接在蓄能器13和液箱之间，所述截止阀II15连接在蓄能器16和液箱之间，在每次充液之前，先将截止阀I14、截止阀II15打开将蓄能器I13、蓄能器II16的压力释放后再关闭截止阀I14、截止阀II15实现充液。充液结束后，在测量时，可以将充液泵27关闭，减小和降低充液泵引起的振动和压力脉动，降低对测量精确度的不良影响。The one-way valve I23 and the one-way valve II24 are connected between the measured cylinder 18 and the electro-hydraulic reversing valve 25, and the electro-hydraulic reversing valve 25 controls the left and right accumulators I13 and II16 respectively. Filled with liquid, the one-way valve I23 communicates with the right chamber of the measured cylinder 18, and the one-way valve II24 communicates with the left chamber of the measured cylinder 18. The accumulator I13 and the accumulator II14 are respectively communicated with the left and right chambers of the measured cylinder 18, and the ratio of the volume of the accumulator to the complete stroke volume of the measured cylinder should be greater than or equal to 10:1 to ensure that the measured cylinder is When moving left and right, the liquid pressure inside the accumulator I13 and the accumulator II16 remains basically unchanged, realizing constant pressure measurement. The inlet of the accumulator I13 is connected in parallel with a pressure gauge I12 for measuring the filling pressure of the accumulator I13; the inlet of the accumulator II16 is connected in parallel with a pressure gauge II17 for measuring the filling pressure of the accumulator II16. The shut-off valve I14 is connected between the accumulator 13 and the liquid tank, and the shut-off valve II15 is connected between the accumulator 16 and the liquid tank. Before each liquid filling, the shut-off valve I14, the shut-off valve II15 Open and release the pressure of the accumulator I13 and the accumulator II16 and then close the shut-off valve I14 and the shut-off valve II15 to realize liquid filling. After the liquid filling is completed, the liquid filling pump 27 can be turned off during the measurement, so as to reduce and reduce the vibration and pressure pulsation caused by the liquid filling pump, and reduce the adverse effect on the measurement accuracy.
测试步骤或方法：Test steps or methods:
1、测试前，先开启驱动泵2和充液泵27，并保证蓄能器I13和蓄能器II16都充有一定压力的氮气。1. Before the test, first turn on the driving pump 2 and the charging pump 27, and ensure that both the accumulator I13 and the accumulator II16 are filled with nitrogen at a certain pressure.
2、先调节电液比例方向阀4使被测缸18恢复到初始位置，即拨片20与左边行程开关I21贴合。2. First adjust the electro-hydraulic proportional directional valve 4 to restore the measured cylinder 18 to the initial position, that is, the paddle 20 is in contact with the left travel switch I21.
3、关闭电液比例阀4，使驱动油缸8停止。此时，先打开截止阀I14和截止阀II15，释放蓄能器内的液体，使被测缸18左右两腔（左右蓄能器）液体压力为零。然后再关闭截止阀I14和截止阀II15，打开电液换向阀25分别对被测缸18左右两腔（左右蓄能器）充液，直到左右两腔液体压力（P左、P右，其中P左<P右）分别上升到试验需要的压力值时再关闭电液换向阀25，充液完成，这样就能保证被测缸18上的密封件左右两边的压力不一样，实现不同压差下的密封力测试。然后关闭充液泵27，降低充液泵引起的振动和压力脉动对测试结果的干扰。3. Close the electro-hydraulic proportional valve 4 to stop the drive cylinder 8. At this time, first open the shut-off valve I14 and the shut-off valve II15 to release the liquid in the accumulator, so that the liquid pressure in the left and right chambers of the measured cylinder 18 (the left and right accumulators) is zero. Then close the shut-off valve I14 and shut-off valve II15, open the electro-hydraulic reversing valve 25 to fill the left and right cavities (left and right accumulators) of the measured cylinder 18, until the liquid pressure of the left and right cavities (P left , P right , where P left < P right ) respectively rise to the pressure value required by the test, then close the electro-hydraulic reversing valve 25, and the liquid filling is completed, so that the pressure on the left and right sides of the seal on the tested cylinder 18 can be guaranteed to be different, and different pressures can be realized. Poor sealing force test. Then close the charging pump 27 to reduce the interference of the vibration and pressure pulsation caused by the charging pump on the test results.
4、开启电液比例方向阀4，根据试验需要，可以给电液比例方向阀4的放大器输入端输入不同的电流，这样电液比例方向阀4的开口量就会不同，流量也不同，驱动油缸8的运动速度就会不同。采用电液比例阀4的好处是能够使驱动油缸8有不同的速度，实现不同工况下的测量：4. Turn on the electro-hydraulic proportional directional valve 4. According to the needs of the test, different currents can be input to the input terminal of the amplifier of the electro-hydraulic proportional directional valve 4. In this way, the opening amount and the flow rate of the electro-hydraulic proportional directional valve 4 will be different. The speed of motion of oil cylinder 8 will be different. The advantage of using the electro-hydraulic proportional valve 4 is that it can make the drive cylinder 8 have different speeds, and realize the measurement under different working conditions:
匀速条件下测试。若输入端的输入电流是常数，那么驱动油缸8和被测缸18就会以某一速度匀速运动，如果调整常数值，那就可以实现不同速度下的匀速测试。 Tested under constant speed conditions. If the input current at the input end is constant, then the driving cylinder 8 and the tested cylinder 18 will move at a certain speed at a constant speed. If the constant value is adjusted, the constant speed test at different speeds can be realized.
变速条件下测试。例如给输入端的输入电流是正弦曲线，那流量、驱动油缸8和被测缸18都会呈正弦曲线形式。而变速条件下与匀速条件下的密封力是不相等的。 Tested under variable speed conditions. For example, if the input current to the input terminal is sinusoidal, then the flow rate, the driving cylinder 8 and the measured cylinder 18 will all be sinusoidal. The sealing force under variable speed conditions is not equal to that under constant speed conditions.
5、在步骤4的测试过程中，由位移传感器7记录驱动油缸8和被测缸18的位移（微分后就是速度），由拉压力传感器10记录传感器的总力F总。那么两种工况下的密封圈摩擦力分别为：5. During the test in step 4, the displacement sensor 7 records the displacement of the driving cylinder 8 and the measured cylinder 18 (speed after differentiation), and the pull pressure sensor 10 records the total force F of the sensor. Then the friction force of the sealing ring under the two working conditions are:
匀速条件时 At constant speed
摩擦力Fm=F总-（P右-P左）AFriction force F m = F total - (P right - P left ) A
粘性摩擦系数：C= Viscous friction coefficient: C=
变速条件时 When changing gears
摩擦力Fm=F总-（P右-P左）A-M Friction force F m = F total - (P right - P left ) AM
粘性摩擦系数：C= Viscous friction coefficient: C=
以上式子中，P左、P右分别为被测缸18左右两腔的压力，A为被测缸18左右两腔受力面积，为所测位移的导数（即速度），为所测位移的二阶导数（即加速度）。In the above formula, P left and P right are the pressures of the left and right chambers of the measured cylinder 18 respectively, and A is the stress area of the left and right chambers of the measured cylinder 18, is the derivative of the measured displacement (i.e. velocity), is the second derivative of the measured displacement (i.e. acceleration).
6、当拨片20碰到行程开关II22后，系统停止测量。再重复步骤1-5重新测量。6. When the paddle 20 touches the limit switch II22, the system stops measuring. Repeat steps 1-5 again to measure again.
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