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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- CN108223492A CN108223492A CN201810008911.7A CN201810008911A CN108223492A CN 108223492 A CN108223492 A CN 108223492A CN 201810008911 A CN201810008911 A CN 201810008911A CN 108223492 A CN108223492 A CN 108223492A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
Abstract
The invention belongs to technical field of hydraulic test, specifically a kind of hydraulic linear motor element sealing force and viscosity friction coefficient test system and method.It solves the problems, such as to solve high water base fluid pressure element viscous friction and the test of viscosity friction coefficient size, drive part includes filter I, transfer tube, overflow valve I, electrohydraulic proportional directional valve, hydraulic control one-way valve I, hydraulic control one-way valve II, displacement sensor and drive cylinder, drive part includes filter I, transfer tube, overflow valve I, electrohydraulic proportional directional valve, hydraulic control one-way valve I, hydraulic control one-way valve II, displacement sensor and drive cylinder, tested part includes pressure gauge I, accumulator I, shut-off valve I, shut-off valve II, accumulator II, pressure gauge II, tested cylinder, plectrum, travel switches I, travel switches I I, check valve I, check valve II, electro-hydraulic reversing valve, overflow valve II, charging pump and filter II.The present invention can measure seal friction resistance and friction coefficient under different pressure differences and movement velocity.
Description
Technical field
The invention belongs to technical field of hydraulic test, specifically a kind of hydraulic linear motor element sealing force and viscous friction
Coefficient tests system and method.
Background technology
At present, the widely used high-water-based emulsion of coal mine hydraulic supporting hydraulic system is as transfer medium（95-97% water+
3-5% oil emulsions mix）, dielectric viscosity is low, easily leakage inside hydraulic system and Hydraulic Elements, so high water base fluid pressure member
The widely used seal with O ring of part, it is especially in the majority with being used on hydraulic valve in hydraulic support hydraulic cylinder.To hydraulic cylinder or hydraulic valve
When carrying out mathematical modeling, need to consider spool or the axial friction suffered by hydraulic cylinder.Traditional oil pressure valve relies primarily on gap
Sealing, suffered by viscous damping forces it is small, but high water base fluid pressure element O-ring suffered by viscous friction it is very big, and with its two
Side pressure difference is related to movement velocity, and O-ring viscous friction, which calculates, at present is carried out with reference to traditional oil pressure valve calculation formula,
Result of calculation is there are larger error, so as to influence the research to hydraulic valve or hydraulic cylinder class component dynamic characteristic.
Invention content
The present invention in order to solve solve high water base fluid pressure element viscous friction and viscosity friction coefficient size test ask
Topic provides a kind of hydraulic linear motor element sealing force and viscosity friction coefficient test system and method.
The present invention takes following technical scheme：A kind of hydraulic linear motor element sealing force and viscosity friction coefficient test system
System, including drive part, coupling part and tested part.
Drive part includes filter I, transfer tube, overflow valve I, electrohydraulic proportional directional valve, hydraulic control one-way valve I, fluid-control one-way
Valve II, displacement sensor and drive cylinder, filter I are connect with transfer tube, and the P mouths of transfer tube and electrohydraulic proportional directional valve are even
It connects, the T mouths of electrohydraulic proportional directional valve are connect with fuel tank, and overflow valve I, the A of electrohydraulic proportional directional valve are parallel between P mouthfuls and T mouthfuls
Mouthful and B mouthfuls connect respectively by hydraulic control one-way valve I and hydraulic control one-way valve II with drive cylinder, drive cylinder is equipped with displacement sensing
Device, the inlet of the control mouth connection hydraulic control one-way valve II of hydraulic control one-way valve I, the control mouth of hydraulic control one-way valve II are connected to hydraulic control
The inlet of check valve I.
Coupling part includes adapter I, pull pressure sensor and adapter II, and adapter I one end is connect with drive cylinder,
The adapter I other ends are connect by pull pressure sensor with adapter II.
Tested part includes pressure gauge I, accumulator I, shut-off valve I, shut-off valve II, accumulator II, pressure gauge II, is tested
Cylinder, plectrum, travel switches I, travel switches I I, check valve I, check valve II, electro-hydraulic reversing valve, overflow valve II, charging pump and mistake
Filter II；Tested cylinder one end is connect with adapter II, and plectrum, the tested cylinder or so are fixed in the piston rod end face of tested cylinder
Two chambers are separated by sealing ring, and travel switches I and travel switches I I, quilt are set respectively on the left and right both ends experiment table top of plectrum
The a mouths for surveying cylinder are connect with accumulator I, and I, c mouthfuls of pressure gauge is connected on accumulator I and is connect with accumulator II, is connected on accumulator II
Pressure gauge II is connected to, the b mouths of tested cylinder are connect with check valve II, and d mouthfuls connect with check valve I, and accumulator I is connected with accumulator II
There are shut-off valve I and shut-off valve II；Check valve I, check valve II are connect respectively with the A of electro-hydraulic reversing valve mouths and B mouthfuls, electro-hydraulic reversing valve
Overflow valve II is connected between P mouthfuls and T mouthfuls, P mouthfuls of electro-hydraulic reversing valve is connect with charging pump, and charging pump is connect with filter II, mistake
Filter II is connect with fuel tank, and T mouthfuls of electro-hydraulic reversing valve is directly connect with fuel tank.
The left and right both ends of left-hand rotation connector and right-hand rotation connector are respectively arranged with screw boss, and the screw thread of left-hand rotation connector left end is convex
Platform is screwed into the threaded hole in the piston rod of drive cylinder, and the screw boss of right end is screwed into the threaded hole of pull pressure sensor left end
In；The screw boss of right-hand rotation connector left end is screwed into the threaded hole of pull pressure sensor right end, and the screw boss of right end is screwed into
Threaded hole in the piston rod of tested oil cylinder.
A kind of hydraulic linear motor element sealing force and viscosity friction coefficient test method, include the following steps,
Before 101~test, transfer tube and charging pump are first opened, and ensure accumulator I and accumulator II all filled with certain pressure
Nitrogen；
102~adjusting electrohydraulic proportional directional valve makes tested cylinder be restored to initial position, i.e. plectrum is bonded with travel switches I；
103~electro-hydraulic proportional valve is closed, stop drive cylinder, at this point, opening shut-off valve I and shut-off valve II, discharge accumulator
Interior liquid, it is zero to make tested cylinder or so two chamber fluid pressures, then turns off shut-off valve I and shut-off valve II, opens electro-hydraulic change
To valve respectively to tested cylinder or so two chamber filling liquids, when two chamber fluid pressures of left and right rise to the pressure value for testing needs respectively
Electro-hydraulic reversing valve is turned off, filling liquid is completed, and is then shut off charging pump, and vibration and pressure fluctuation are to test caused by reducing charging pump
As a result interference；
104~electrohydraulic proportional directional valve is opened, according to experiment needs, the amplifier in of electrohydraulic proportional directional valve can be given defeated
Enter different electric currents, the amount of opening of such electrohydraulic proportional directional valve will be different, and flow is also different, the movement velocity of drive cylinder
It will be different；Including being tested under test and Variable Velocity Condition under the conditions of at the uniform velocity；
105~in the test process of step 104, the displacement of drive cylinder and tested cylinder is recorded by displacement sensor, by tension and compression
Force snesor records the total power F of sensorAlways, the sealing ring frictional force under two kinds of operating modes is respectively：
At the uniform velocity condition when：
Frictional force Fm=FAlways-（PIt is right-PIt is left）A；
Viscosity friction coefficient：C=；
During Variable Velocity Condition：
Frictional force Fm=FAlways-（PIt is right-PIt is left）A-M；
Viscosity friction coefficient：C=；
In above equation, PIt is left、PIt is rightThe pressure of respectively tested cylinder or so two chambers, A are tested cylinder or so two chamber forced areas,For
The derivative of measured displacement, i.e. speed,For the second dervative of measured displacement, i.e. acceleration；
106~after plectrum meets travel switches I I, system stops measuring, and repeats step 101-105 and remeasures.
Compared with prior art, the hydraulic cylinder that can be measured under different form sealing ring or hydraulic valve seal spool of the invention rub
It wipes resistance and friction coefficient, scheme is simple and practicable；Sealing ring pressure at two ends can be adjusted, measures the seal friction under different pressure differences
Resistance and friction coefficient；The movement velocity of tested section hydraulic valve core or hydraulic cylinder is controllable, can measure under different motion speed
Seal friction force and friction coefficient.
Description of the drawings
Fig. 1 is the principle of the present invention figure；
In figure：1- filters I, 2- transfer tube, 3- overflow valves I, 4- electrohydraulic proportional directional valve, 5- hydraulic control one-way valves I, 6- hydraulic control list
To valve II, 7- displacement sensors, 8- drive cylinders, 9- adapters I, 10- pull pressure sensor, 11- adapters II, 12- pressure
Table I, 13- accumulators I, 14- shut-off valve I, 15- shut-off valve II, 16- accumulator II, 17- pressure gauge II, 18- are tested cylinder, and 19- is tight
Gu screw, 20- plectrums, 21- travel switches Is, the electro-hydraulic commutation of 22- travel switches Is I, 23- check valve I, 24- check valve II, 25-
Valve, 26- overflow valves II, 27- charging pump, 28- filters II.
Specific embodiment
As shown in Figure 1, a kind of hydraulic linear motor element sealing force and viscosity friction coefficient test system, including driving portion
Divide, coupling part and tested part, drive part include filter I1, transfer tube 2, overflow valve I3, electrohydraulic proportional directional valve 4, liquid
Control check valve I5, hydraulic control one-way valve II6, displacement sensor 7 and drive cylinder 8, filter I1 are connect with transfer tube 2, transfer tube 2
It is connect with the P mouths of electrohydraulic proportional directional valve 4, the T mouths of electrohydraulic proportional directional valve 4 are connect with fuel tank, are parallel between P mouthfuls and T mouthfuls
Overflow valve I3, the A mouths of electrohydraulic proportional directional valve 4 and B mouthfuls pass through hydraulic control one-way valve I5 and hydraulic control one-way valve II6 and driving oil respectively
Cylinder 8 connects, and drive cylinder 8 is equipped with displacement sensor 7, the control mouth connection hydraulic control one-way valve II6 of hydraulic control one-way valve I5 into
Liquid mouth, the control mouth of hydraulic control one-way valve II6 are connected to the inlet of hydraulic control one-way valve I5.
Coupling part includes adapter I9, pull pressure sensor 10 and adapter II11, adapter I9 one end and driving oil
Cylinder 8 connects, and the adapter I9 other ends are connect by pull pressure sensor 10 with adapter II11.
Tested part includes pressure gauge I12, accumulator I13, shut-off valve I14, shut-off valve II15, accumulator II16, pressure
Table II 17, tested cylinder 18, plectrum 20, travel switches I 21, travel switches I I22, check valve I23, check valve II24, electro-hydraulic commutation
Valve 25, overflow valve II26, charging pump 27 and filter II28；Tested 18 one end of cylinder is connect with adapter II11, is tested cylinder 18
Plectrum 20 is fixed in piston rod end face, tested 18 or so two chamber of cylinder is separated by sealing ring, the left and right both ends of plectrum 20
Travel switches I 21 and travel switches I I22 are set respectively on experiment table top, check valve I23, check valve II24 are changed respectively with electro-hydraulic
It is connected to the A mouths and B mouthfuls of valve 25, overflow valve II26,25P mouthfuls of electro-hydraulic reversing valve is connected between 25P mouthfuls and T mouthfuls of electro-hydraulic reversing valve
It is connect with charging pump 27, charging pump 27 is connect with filter II28, and filter II28 is connect with fuel tank, 25T mouthfuls of electro-hydraulic reversing valve
Directly it is connect with fuel tank.
The hydraulic control one-way valve I5, hydraulic control one-way valve II6 are combined, wherein, the control mouth connection hydraulic control of hydraulic control one-way valve I5
The inlet of check valve II6, the control mouth of hydraulic control one-way valve II6 are connected to the inlet of hydraulic control one-way valve I5, two hydraulic control lists
A reversible lock is formed to valve, is connected between driving cylinder 8 and electrohydraulic proportional directional valve 4, can guarantee that driving cylinder rests on arbitrarily
Filling liquid is carried out to the accumulator I13 or accumulator II16 that are tested part during position.
The electrohydraulic proportional directional valve 4 is oil medium valve, can adjust flow by adjusting spool aperture, reach adjusting
The purpose of drive cylinder movement velocity.
Institute's displacement sensors 7 are noncontacting proximity sensor, are divided into traverse measurement bar and shell.Traverse measurement bar right end with
8 piston rod of drive cylinder is together by a threaded connection, and sensor outer housing is mounted on driving cylinder left wall end face.Drive cylinder 8
There is equal movement velocity with traverse measurement bar.
The adapter is divided into adapter I9 and adapter II11, and two adapter left and right ends are threaded convex respectively
Platform.Adapter I9 left end screw boss is screwed into the threaded hole in the piston rod of drive cylinder 8, and right end screw boss is screwed into pressure
In the threaded hole of 10 left end of sensor.Adapter II11 left end screw boss is screwed into the threaded hole into 10 right end of pull pressure sensor
In, right end screw boss is screwed into the threaded hole in the piston rod of tested oil cylinder 18.In this way, after different force snesors is replaced,
Adapter is only needed to change, and without resetting the threaded hole in drive cylinder 8 and tested cylinder 18.
18 or so two chamber of tested cylinder is separated by sealing ring, and sealing ring can be various different structure forms, described
The piston rod right end of tested cylinder 18 is threaded hole, and plectrum 20 is pressed abd fixed on to the right end of tested cylinder 18 with trip bolt 19
Face, the plectrum 20 left and right ends experiment table top on travel switches I 21, travel switches I I22 are set respectively, when tested cylinder to
It moves right and stops when meeting travel switches I I22, stop when tested cylinder, which is moved to the left, encounters travel switches I 21.
The check valve I23, check valve II24 are connected between tested cylinder 18 and electro-hydraulic reversing valve 25, the electro-hydraulic commutation
Valve 25 controls the filling liquid that can control left and right accumulator I13, accumulator II16 respectively, the check valve I23 and tested 18 right chamber of cylinder
Connection, the check valve II24 are connected with tested 18 left chamber of cylinder.The accumulator I13, accumulator II14 respectively with tested cylinder 18
The connection of left and right two chamber, the ratio between the accumulator volume and tested cylinder complete stroke volume should be greater than equal to 10:1, ensure tested
When moving left and right, the fluid pressure inside accumulator I13, accumulator II16 is held essentially constant cylinder, realizes that constant pressure measures.Institute
Accumulator I13 arrival end parallel connection pressure gauge I12 are stated, for measuring the supercharging pressure of accumulator I13；The accumulator II16 entrances
End pressure gauge II17 in parallel, for measuring the supercharging pressure of accumulator II16.The shut-off valve I14 is connected to accumulator 13 and liquid
Between case, the shut-off valve II15 is connected between accumulator 16 and liquid case, before each filling liquid, first by shut-off valve I14, cut
Only valve II15 turns off shut-off valve I14, shut-off valve II15 realization after opening the pressure release by accumulator I13, accumulator II16
Filling liquid.After filling liquid, when measuring, charging pump 27 can be closed, reduce and reduce vibration and pressure caused by charging pump
Pulsation, reduces the harmful effect to measuring accuracy.
Testing procedure or method：
1st, before testing, transfer tube 2 and charging pump 27 are first opened, and ensure accumulator I13 and accumulator II16 all filled with a level pressure
The nitrogen of power.
2nd, first adjusting electrohydraulic proportional directional valve 4 makes tested cylinder 18 be restored to initial position, i.e. plectrum 20 is opened with left side stroke
Close I21 fittings.
3rd, electro-hydraulic proportional valve 4 is closed, stops drive cylinder 8.At this point, first opening shut-off valve I14 and shut-off valve II15, release
The liquid in accumulator is put, makes 18 or so two chamber of tested cylinder（Left and right accumulator）Fluid pressure is zero.Then shut-off valve is turned off
I14 and shut-off valve II15 opens electro-hydraulic reversing valve 25 respectively to being tested 18 or so two chamber of cylinder（Left and right accumulator）Filling liquid, until a left side
Right two chamber fluid pressures（PIt is left、PIt is right, wherein PIt is left<PIt is right）Electro-hydraulic reversing valve is turned off when rising to the pressure value that experiment needs respectively
25, filling liquid is completed, this ensures that the pressure of sealing element the right and left on tested cylinder 18 is different, is realized under different pressure differences
Sealing force test.Charging pump 27 is then shut off, reduces vibration and interference of the pressure fluctuation to test result caused by charging pump.
4th, electrohydraulic proportional directional valve 4 is opened, according to experiment needs, the amplifier of electrohydraulic proportional directional valve 4 can be given to input
End inputs different electric currents, and the amount of opening of such electrohydraulic proportional directional valve 4 will be different, and flow is also different, the fortune of drive cylinder 8
Dynamic speed will be different.Benefit using electro-hydraulic proportional valve 4 is that drive cylinder 8 can be made to have different speed, realizes different works
Measurement under condition：
It is tested under the conditions of at the uniform velocity.If the input current of input terminal is constant, then drive cylinder 8 and tested cylinder 18 will be with
A certain speed uniform motion, if adjustment constant value, that can realize the at the uniform velocity test under friction speed.
It is tested under Variable Velocity Condition.Such as to the input current of input terminal be sine curve, that flow, 8 and of drive cylinder
Tested cylinder 18 all can be in sinusoidal form.And under Variable Velocity Condition at the uniform velocity under the conditions of sealing force be unequal.
5th, in the test process of step 4, the displacement of drive cylinder 8 and tested cylinder 18 is recorded by displacement sensor 7（Differential
It is exactly speed afterwards）, the total power F of sensor is recorded by pull pressure sensor 10Always.Sealing ring frictional force point under so two kinds of operating modes
It is not：
At the uniform velocity condition when
Frictional force Fm=FAlways-（PIt is right-PIt is left）A
Viscosity friction coefficient：C=
During Variable Velocity Condition
Frictional force Fm=FAlways-（PIt is right-PIt is left）A-M
Viscosity friction coefficient：C=
In above equation, PIt is left、PIt is rightThe respectively pressure of 18 or so two chamber of tested cylinder, A are 18 or so two chamber forced area of tested cylinder,Derivative for measured displacement（That is speed）,Second dervative for measured displacement（That is acceleration）.
6th, after plectrum 20 meets travel switches I I22, system stops measuring.Step 1-5 is repeated to remeasure.
Claims (3)
1. a kind of hydraulic linear motor element sealing force and viscosity friction coefficient test system, it is characterised in that：Including driving portion
Point, coupling part and tested part,
Drive part includes filter I（1）, transfer tube（2）, overflow valve I（3）, electrohydraulic proportional directional valve（4）, hydraulic control one-way valve I
（5）, hydraulic control one-way valve II（6）, displacement sensor（7）And drive cylinder（8）, filter I（1）With transfer tube（2）Connection, driving
Pump（2）With electrohydraulic proportional directional valve（4）P mouths connection, electrohydraulic proportional directional valve（4）T mouths connect with fuel tank, P mouthfuls and T mouths
Between be parallel with overflow valve I（3）, electrohydraulic proportional directional valve（4）A mouths and B mouthfuls pass through hydraulic control one-way valve I respectively（5）With hydraulic control list
To valve II（6）With drive cylinder（8）Connection, drive cylinder（8）It is equipped with displacement sensor（7）, hydraulic control one-way valve I（5）Control
Donsole connection hydraulic control one-way valve II（6）Inlet, hydraulic control one-way valve II（6）Control mouth be connected to hydraulic control one-way valve I（5）'s
Inlet；
Coupling part includes adapter I（9）, pull pressure sensor（10）With adapter II（11）, adapter I（9）One end is with driving
Dynamic oil cylinder（8）Connection, adapter I（9）The other end passes through pull pressure sensor（10）With adapter II（11）Connection；
Tested part includes pressure gauge I（12）, accumulator I（13）, shut-off valve I（14）, shut-off valve II（15）, accumulator II
（16）, pressure gauge II（17）, tested cylinder（18）, plectrum（20）, travel switches I（21）, travel switches I I（22）, check valve I
（23）, check valve II（24）, electro-hydraulic reversing valve（25）, overflow valve II（26）, charging pump（27）With filter II（28）；Tested cylinder
（18）One end and adapter II（11）Connection is tested cylinder（18）Piston rod end face on be fixed with plectrum（20）, the tested cylinder
（18）Two chambers of left and right are separated by sealing ring, plectrum（20）Left and right both ends experiment table top on travel switches I is set respectively（21）
With travel switches I I（22）, it is tested cylinder（18）A mouths and accumulator I（13）Connection, accumulator I（13）On be connected with pressure gauge I
（12）, c mouthfuls and accumulator II（16）Connection, accumulator II（16）On be connected with pressure gauge II（17）, it is tested cylinder（18）B mouths with
Check valve II（24）Connection, d mouthfuls and check valve I（23）Connection, accumulator I（13）With accumulator II（16）It is connected with shut-off valve I
（14）With shut-off valve II（15）；Check valve I（23）, check valve II（24）Respectively with electro-hydraulic reversing valve（25）A mouths and B mouthful companies
It connects, electro-hydraulic reversing valve（25）Overflow valve II is connected between P mouthfuls and T mouthfuls（26）, electro-hydraulic reversing valve（25）P mouthfuls and charging pump（27）
Connection, charging pump（27）With filter II（28）Connection, filter II（28）It is connect with fuel tank, electro-hydraulic reversing valve（25）T mouthfuls straight
It connects and is connect with fuel tank.
2. hydraulic linear motor element sealing force according to claim 1 and viscosity friction coefficient test system, feature
It is：Left-hand rotation connector（9）With right-hand rotation connector（11）Left and right both ends be respectively arranged with screw boss, left-hand rotation connector（9）Left end
Screw boss is screwed into drive cylinder（8）Piston rod in threaded hole, the screw boss of right end is screwed into pull pressure sensor（10）
In the threaded hole of left end；Right-hand rotation connector（11）The screw boss of left end is screwed into pull pressure sensor（10）The threaded hole of right end
In, the screw boss of right end is screwed into tested oil cylinder（18）Piston rod in threaded hole.
3. a kind of hydraulic linear motor element sealing force as claimed in claim 2 and viscosity friction coefficient test method, special
Sign is：Include the following steps,
Before 101~test, transfer tube is first opened（2）And charging pump（27）, and ensure accumulator I（13）With accumulator II（16）All
Nitrogen filled with certain pressure；
102~adjusting electrohydraulic proportional directional valve（4）Make tested cylinder（18）It is restored to initial position, i.e. plectrum（20）With travel switch
I（21）Fitting；
103~closing electro-hydraulic proportional valve（4）, make drive cylinder（8）Stop, at this point, opening shut-off valve I（14）With shut-off valve II
（15）, the liquid in accumulator is discharged, makes tested cylinder（18）Two chamber fluid pressures of left and right are zero, then turn off shut-off valve I
（14）With shut-off valve II（15）, open electro-hydraulic reversing valve（25）Respectively to being tested cylinder（18）Two chamber filling liquids of left and right, until left and right two
Chamber fluid pressure turns off electro-hydraulic reversing valve when rising to the pressure value that experiment needs respectively（25）, filling liquid complete, be then shut off
Charging pump（27）, reduce vibration and interference of the pressure fluctuation to test result caused by charging pump；
104~unlatching electrohydraulic proportional directional valve（4）, according to experiment needs, electrohydraulic proportional directional valve can be given（4）Amplifier it is defeated
Enter end and input different electric currents, such electrohydraulic proportional directional valve（4）Amount of opening will be different, flow is also different, drive cylinder
（8）Movement velocity will be different；Including being tested under test and Variable Velocity Condition under the conditions of at the uniform velocity；
105~in the test process of step 104, by displacement sensor（7）Record drive cylinder（8）With tested cylinder（18）Position
It moves, by pull pressure sensor（10）Record the total power F of sensorAlways, the sealing ring frictional force under two kinds of operating modes is respectively：
At the uniform velocity condition when：
Frictional force Fm=FAlways-（PIt is right-PIt is left）A；
Viscosity friction coefficient：C=；
During Variable Velocity Condition：
Frictional force Fm=FAlways-（PIt is right-PIt is left）A-M；
Viscosity friction coefficient：C=；
In above equation, PIt is left、PIt is rightRespectively tested cylinder（18）The pressure of two chambers of left and right, A are tested cylinder（18）Two chamber stress of left and right
Area,For the derivative of measured displacement, i.e. speed,For the second dervative of measured displacement, i.e. acceleration；
106~work as plectrum（20）Meet travel switches I I（22）Afterwards, system stops measuring, and repeats step 101-105 and surveys again
Amount.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810008911.7A CN108223492A (en) | 2018-01-04 | 2018-01-04 | A kind of hydraulic linear motor element seal friction force and viscosity friction coefficient test system and method |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810008911.7A CN108223492A (en) | 2018-01-04 | 2018-01-04 | A kind of hydraulic linear motor element seal friction force and viscosity friction coefficient test system and method |
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| CN108223492A true CN108223492A (en) | 2018-06-29 |
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| CN201810008911.7A Pending CN108223492A (en) | 2018-01-04 | 2018-01-04 | A kind of hydraulic linear motor element seal friction force and viscosity friction coefficient test system and method |
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Cited By (3)
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| CN109707698A (en) * | 2019-01-11 | 2019-05-03 | 佛山市顺德区中意液压有限公司 | Measure the device of hydraulic piston mechanism frictional force |
| CN110030232A (en) * | 2019-05-29 | 2019-07-19 | 太原科技大学 | A kind of Moveable horizontal cylinder bench |
| CN112343893A (en) * | 2020-12-16 | 2021-02-09 | 太重集团榆次液压工业(济南)有限公司 | Hydraulic cylinder sealing element testing system and testing method |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109707698A (en) * | 2019-01-11 | 2019-05-03 | 佛山市顺德区中意液压有限公司 | Measure the device of hydraulic piston mechanism frictional force |
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| CN110030232A (en) * | 2019-05-29 | 2019-07-19 | 太原科技大学 | A kind of Moveable horizontal cylinder bench |
| CN112343893A (en) * | 2020-12-16 | 2021-02-09 | 太重集团榆次液压工业(济南)有限公司 | Hydraulic cylinder sealing element testing system and testing method |
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