CN203404164U - Test equipment for testing durability of sealing element of hydraulic cylinder - Google Patents
Test equipment for testing durability of sealing element of hydraulic cylinder Download PDFInfo
- Publication number
- CN203404164U CN203404164U CN201320493686.3U CN201320493686U CN203404164U CN 203404164 U CN203404164 U CN 203404164U CN 201320493686 U CN201320493686 U CN 201320493686U CN 203404164 U CN203404164 U CN 203404164U
- Authority
- CN
- China
- Prior art keywords
- cylinder
- oil
- pressure
- seal
- tested
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Landscapes
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
The utility model discloses test equipment for testing the durability of a sealing element of a hydraulic cylinder. The test equipment comprises the tested hydraulic cylinder, a driving unit (100) used for driving a piston rod of the tested hydraulic cylinder to make reciprocating rectilinear movement, and a pressure oil supplying unit (200). A first annular groove used for placing of a piston sealing element (401) and/or a second annular groove used for placing of a piston rod sealing element (301) are/is arranged inside the tested hydraulic cylinder. The pressure oil supplying unit comprises a pressure cylinder (201), an oil tank (202) and a reversing valve (203). A working cavity of the pressure cylinder is connected with the oil tank through the reversing valve, a high pressure cavity of the pressure cylinder is connected with the oil tank through an oil inlet, and an oil outlet of the high pressure cavity of the pressure cylinder is connected with the first annular groove and/or the second annular groove. According to the test equipment for testing the durability of the sealing element of the hydraulic cylinder, the pressure of pressure oil is increased through the pressure cylinder, the pressure of the pressure oil can reach 50Mpa, the requirement for imitation working condition test pressure is met, and therefore the true working condition of the sealing element of the hydraulic cylinder can be simulated.
Description
Technical field
The utility model relates to the testing installation of Sealing, particularly, relates to a kind of testing installation for test fluid cylinder pressure seal durability.
Background technique
The quality of hydraulic cylinder sealing element durability directly affects the reliability of engineering machinery, therefore in the urgent need to hydraulic cylinder sealing element durability test machine.At present, domestic existing hydraulic cylinder sealing element testing machine can only carry out the sealability comparative trial of Sealing and the experiments of sealing performance of Part load parameter, can not all operating modes of simulated solution cylinder pressure (pressure, speed, temperature parameter) carry out the test of seal durability, the result of test can not reflect hydraulic cylinder sealing element actual conditions comprehensively, and practical reference value is limited.
CN101315311A discloses a kind of energy-saving hydraulic sealing experimental bench, and as shown in Figure 1, this Laboratory Furniture forms by testing oil hydraulic cylinder, experiment Driven by Hydraulic Cylinder loop and loading loop three parts.Experiment oil hydraulic cylinder is comprised of left cylinder cap 2, left guide sleeve 3, cylinder barrel 5, piston 15, piston rod 9, right guide sleeve 19, right cylinder cap 20, wherein: piston 15, left guide sleeve 3 and right guide sleeve 19 are contained in cylinder barrel 5; The central position of the external cylindrical surface of piston has an annular groove, and there is the first radial direction through hole a through this Pocket Machining, in the both sides of this groove, be all processed with the multiple tracks annular groove for mounting support ring and the first tested seal element 16, the first tested seal element 16 paired mounting are in groove both sides, on piston rod 9, be processed with the radial hole b and the axial bore c that are interconnected, radial hole b is connected with the first radial direction through hole a on piston; The neutral position of left guide sleeve 3 endoporus cylndrical surface has an annular groove, and there is the second radial direction through hole d through this Pocket Machining, in the both sides of this groove, be all processed with for the multiple tracks annular groove of the first supporting ring 13 and the second tested seal element 14 is installed, the second tested seal element 14 paired mounting are in groove both sides.Experiment Driven by Hydraulic Cylinder loop is comprised of elements such as variable displacement pump 23, safety valve 24, the first filter 25, the first solenoid directional control valves 22.Load loop and comprise metering pump 26, relief valve 27, the second filter 29, the second solenoid directional control valve 28, the first accumulator 6, the second accumulator 10 and stop valve.In addition, reference character 1 in this NM accompanying drawing 1 represents proximity detector, 4,7,8,11,21 represent respectively the first stop valve, the second stop valve, the 3rd stop valve, the 4th stop valve and the 5th stop valve, 18 represent the second supporting ring, 17 represent the 3rd tested seal element, and 12 represent the first dust ring.
The working procedure of this Laboratory Furniture is as follows: before experiment, first the first tested seal element 16 and tested seal element 14,17 are loaded on respectively on piston 15 and left and right guide sleeve 3,19; Stop valve 4,6,8,11,21 is all opened, operation solenoid directional control valve 28 is introduced pressure oil liquid in the annular groove of piston 15 and left and right guide sleeve 3,19, and the first accumulator 6 and the second accumulator 10 are carried out to topping up, when oil liquid pressure reaches setting value, stop valve 8,21 is closed, by accumulator, make tested seal element place keep the force value setting, at this moment, control the first solenoid directional control valve 22 and make piston 15 drive piston rod 9 to do axially reciprocating in cylinder barrel 5; Stop valve 7,8 or stop valve 11,21 are all closed, by observing the variation of relevant pressure table indication numerical value or indicated numerical value, detect the sealability of tested seal element.
In addition, stop valve 7,11 is closed, other stop valve 4,8,21 is all opened, make solenoid directional control valve 28 in meta, and according to the given time delay of automatical control system, make electromagnetic relief valve 27 constantly electric and dead electricity, can carry out variable load shock test in short-term to tested seal element.
Moreover, by automatical control system, make solenoid directional control valve 28 when meta, can make all tested seal elements be under same induced pressure and test; Make solenoid directional control valve 28 when left position or right position, can make the tested seal element at piston place and the tested seal element at piston rod place be in different induced pressures and test.
The defect of above-mentioned energy-saving hydraulic sealing experimental bench is: the pressure that (1) loads loop is static or variable load is in short-term impacted, and the pressure that loads loop cannot reach the stress level of real working condition, therefore this hydraulic sealing experimental bench cannot be simulated the real working condition of hydraulic cylinder sealing element, and can only carry out by observing the variation of relevant pressure table indication numerical value or indicated numerical value the sealability comparative trial of Sealing; (2) owing to being that hydraulic oil by flowing in cylinder barrel 5 comes piston rod 9 to do axially reciprocating, and the hydraulic oil flowing in cylinder barrel 5 may be penetrated in the annular groove at tested seal element 14,16,17 places, thereby affect the test of seal element sealability, so cause the conformity of test conditions bad, affect the accuracy of test result; (3) above-mentioned energy-saving hydraulic sealing experimental bench can not imitate all operating modes of oil hydraulic cylinder (pressure, speed, temperature parameter) and carries out the test of seal durability; (4), by above-mentioned energy-saving hydraulic sealing experimental bench, organization plan that can not optimization hydraulic cylinder sealing element, can not optimization cylinder barrel and the related process parameter of piston rod.
Model utility content
The purpose of this utility model is to provide a kind of testing installation for test fluid cylinder pressure seal durability that can simulate the real working condition of hydraulic cylinder sealing element.
To achieve these goals, the utility model provides a kind of testing installation for test fluid cylinder pressure seal durability, this testing installation comprises tested oil hydraulic cylinder, for driving the piston rod of described tested oil hydraulic cylinder, do driver element and the pressure oil liquid feeding unit of linear reciprocating motion, in described tested oil hydraulic cylinder, be provided with for laying the first ring connected in star of piston seal and/or for laying the second annular groove of piston rod seal component, wherein, described pressure oil liquid feeding unit comprises pressurized cylinder, fuel tank and selector valve, the active chamber of described pressurized cylinder is connected with described fuel tank by described selector valve, the filler opening of the hyperbaric chamber of described pressurized cylinder is connected with described fuel tank, the oil outlet of the hyperbaric chamber of described pressurized cylinder is connected with described first ring connected in star and/or described the second annular groove.
Preferably, between the pressure hydraulic fluid port of described selector valve and described fuel tank, be connected with the first oil pump and the first one-way valve; Between the return opening of described selector valve and described fuel tank, be connected with the second one-way valve; Between the filler opening of the hyperbaric chamber of described pressurized cylinder and described fuel tank, be connected with the second oil pump and the 3rd one-way valve.
Preferably, pressure hydraulic fluid port and the oil circuit between described fuel tank of described selector valve are oil-feed oil circuit, are connected with the first pressure gauge, accumulator and the first relief valve between described oil-feed oil circuit and described fuel tank.
Preferably, between the repairing oil circuit between the filler opening of the hyperbaric chamber of described pressurized cylinder and described fuel tank and described fuel tank, be connected with the second relief valve and the second pressure gauge.
Preferably, between the oil outlet of the hyperbaric chamber of described pressurized cylinder and described first ring connected in star and/or described the second annular groove, be connected with pressure transducer.
Preferably, between the oil outlet of the hyperbaric chamber of described pressurized cylinder and described first ring connected in star and/or described the second annular groove, be connected with the first switch valve; Oil circuit between the oil outlet of the hyperbaric chamber of described pressurized cylinder and described first ring connected in star and/or described the second annular groove is connected to described fuel tank by the branch road of draining the oil, described in drain the oil on branch road and be connected with second switch valve.
Preferably, described pressure oil liquid feeding unit also comprises cooling unit, and the filler opening of this cooling unit is connected with described fuel tank respectively with oil outlet; Between described fuel tank and described cooling unit, be connected with fine filter.
Preferably, described driver element is variable speed drive units.
Preferably, described tested oil hydraulic cylinder comprises the tested cylinder of piston rod seal component and the tested cylinder of piston seal, described driver element comprises shift drive mechanism, eccentric shaft, eccentric wheel, connecting rod, slide block, for supporting the bearing support of described eccentric shaft and for guiding the guiding pairs of the motion of described slide block, described shift drive mechanism is used for driving described eccentric shaft to be rotated, described eccentric wheel is fixedly set on described eccentric shaft, one end of described connecting rod and described eccentric wheel pivot joint, one end pivot joint of the other end of described connecting rod and described slide block, the other end of described slide block is connected between the first piston bar of the tested cylinder of described piston rod seal component and the second piston rod of the tested cylinder of described piston seal.
Preferably, described driver element also comprises link, the two ends of this link are connected with the second piston rod of the tested cylinder of described piston seal with the first piston bar of the tested cylinder of described piston rod seal component by pull pressure sensor respectively, and described slide block is connected with described link.
Preferably, described link comprise main body and respectively with two bulbs of the two ends ball-joint of this main body, described two bulbs are connected with the second piston rod of the tested cylinder of described piston seal with the first piston bar of the tested cylinder of described piston rod seal component by described pull pressure sensor respectively, and described slide block is connected with the main body of described link.
Preferably, the tested cylinder of the tested cylinder of described piston rod seal component and piston seal arranges respectively in pairs, described link is connected between the tested cylinder of corresponding described piston rod seal component and the tested cylinder of piston seal, described driver element also comprises coupling shaft, this coupling shaft is connected between the tested cylinder of described piston rod seal component of paired setting and two described links of the tested cylinder of piston seal, and described slide block is fixedly connected with described coupling shaft.
Preferably, described tested oil hydraulic cylinder comprises the tested cylinder of piston rod seal component and the tested cylinder of piston seal, wherein:
The tested cylinder of described piston rod seal component comprises first piston bar and guiding body, described guiding body is set on described first piston bar, in the interior perimeter surface of described guiding body, be provided with for laying described second annular groove of described piston rod seal component, described piston rod seal component is used for the clearance seal between described first piston bar and described guiding body, on described guiding body, be provided with the first pressure oil liquid entrance being connected with the oil outlet of the hyperbaric chamber of described pressurized cylinder, this the first pressure oil liquid entrance communicates with the space between described first piston bar and described guiding body, the inside of described first piston bar is formed with the first space, on described first piston bar, be provided with the first temperature adjustment liquid inlet and the first temperature adjustment liquid outlet that are all communicated with described the first space,
The tested cylinder of described piston seal comprises the second piston rod and cylinder body, the cock body of described the second piston rod is arranged in described cylinder body, the body of rod of described the second piston rod stretches out from described cylinder body, on the outer surface of described cock body, be provided with for laying the described first ring connected in star of described piston seal, described piston seal is used for the clearance seal between described cock body and described cylinder body, on the described body of rod, be provided with the second pressure oil liquid entrance being connected with the oil outlet of the hyperbaric chamber of described pressurized cylinder, this the second pressure oil liquid entrance communicates with the space between described cock body and described cylinder body, on the outer surface of described cylinder body, be provided with outside sandwich, between this outside sandwich and described cylinder body, be formed with second space, on described outside sandwich, be provided with the second temperature adjustment liquid inlet and the second temperature adjustment liquid outlet,
Described testing installation also comprises for supplying the liquid supply device of temperature adjustment liquid, the outlet of this liquid supply device is connected with the second temperature adjustment liquid inlet with described the first temperature adjustment liquid inlet respectively, and the import of this liquid supply device is connected with the second temperature adjustment liquid outlet with described the first temperature adjustment liquid outlet respectively.
Preferably, described liquid supply device is cold-hot integrated machine.
Preferably, between the import of described liquid supply device and described the first temperature adjustment liquid outlet and between the import of described liquid supply device and described the second temperature adjustment liquid outlet, be connected with the first temperature transducer.
Preferably, the bottom of described guiding body is provided with the first leakage being communicated with the inner space of described guiding body and collects mouth; The bottom of described cylinder body is provided with the second leakage being communicated with the inner space of described cylinder body and collects mouth.
In the utility model, by pressurized cylinder, improve the pressure of pressure oil liquid, make the pressure of pressure oil liquid can reach 50Mpa, meet the requirement of imitative working condition tests pressure, in addition, the trend of hydraulic oil that changes the active chamber of pressurized cylinder by selector valve changes the size of pressure that is fed to the pressure oil liquid of described first ring connected in star and/or described the second annular groove from hyperbaric chamber, thereby to first ring connected in star and/or the second annular groove, provide imitative operating mode impulse test pressure oil liquid, the real working condition of simulation hydraulic cylinder sealing element.
Other feature and advantage of the present utility model partly in detail are described the embodiment subsequently.
Accompanying drawing explanation
Accompanying drawing is to be used to provide further understanding of the present utility model, and forms a part for specification, is used from explanation the utility model, but does not form restriction of the present utility model with embodiment one below.In the accompanying drawings:
Fig. 1 is the structural representation of existing energy-saving hydraulic sealing experimental bench;
Fig. 2 is the schematic diagram of the hydraulic system of the testing installation for test fluid cylinder pressure seal durability that provides of the utility model;
Fig. 3 is that the master of the mechanical structure part of the testing installation for test fluid cylinder pressure seal durability that provides of the utility model looks schematic diagram;
Fig. 4 is the schematic top plan view of the mechanical structure part of the testing installation for test fluid cylinder pressure seal durability that provides of the utility model;
Fig. 5 is the schematic side view of the mechanical structure part of the testing installation for test fluid cylinder pressure seal durability that provides of the utility model;
Fig. 6 is the structural representation of the tested cylinder of piston rod seal component of the testing installation for test fluid cylinder pressure seal durability that provides of the utility model;
Fig. 7 is a kind of structural representation of mode of execution of the tested cylinder of piston seal of the testing installation for test fluid cylinder pressure seal durability that provides of the utility model;
Fig. 8 is the structural representation of another kind of mode of execution of the tested cylinder of piston seal of the testing installation for test fluid cylinder pressure seal durability that provides of the utility model.
Description of reference numerals
1: proximity detector; 2: left cylinder cap; 3: left guide sleeve; 4: the first stop valves; 5: cylinder barrel; 6: the first accumulators; 7: the second stop valves; 8: the three stop valves; 9: piston rod; 10: the second accumulators; 11: the four stop valves; 12: the first dust rings; 13: the first supporting rings; 14: the second tested seal elements; 15: piston; 16: the first tested seal elements; 17: the three tested seal elements; 18: the second supporting rings; 19: right guide sleeve; 20: right cylinder cap; 21: the five stop valves; 22: the first solenoid directional control valves; 23: variable displacement pump; 24: safety valve; 25: the first filters; 26: metering pump; 27: relief valve; 28: the second solenoid directional control valves; 29: the second filters; A: the first radial direction through hole; B: radial hole; C: axial bore; D: the second radial direction through hole; 30: liquid supply device; 31: the first temperature transducers; 100: driver element; 101: coupling shaft; 102: link; 103: eccentric shaft; 104: eccentric wheel; 105: slide block; 106: connecting rod; 107: bearing support; 108: guiding pairs; 109: the three bearings; 110: the four bearings; 111: pull pressure sensor; 112: variable speed electric motors, particularly; 113: speed reducer; 114: the first coupling; 115: the second coupling; 116: the first bearings; 117: the second bearings; 118: fixed base; 200: pressure oil liquid feeding unit; 201: pressurized cylinder; 202: fuel tank; 203: selector valve; 204: the first oil pumps; 205: the first one-way valves; 206: inlet oil filter; 207: the first pressure gauges; 208: accumulator; 209: the first relief valves; 210: the second oil pumps; 211: the three one-way valves; 212: the second relief valves; 213: the second pressure gauges; 214: pressure transducer; 215: the first switch valves; 216: the branch road of draining the oil; 217: cooling unit; 218: fine filter; 219: the three switch valves; 220: the four switch valves; 221: the five switch valves; 222: liquid level liquid thermometer; 223: the second temperature transducers; 224: air-strainer; 225: liquid level relay; 226: second switch valve; 227: the second one-way valves; 228: return filter; 300: the tested cylinder of piston rod seal component; 301: piston rod seal component; 302: first piston bar; 303: guiding body; 304: the first pressure oil liquid entrances; 305: the first spaces; 306: the first temperature adjustment liquid inlets; 307: the first temperature adjustment liquid outlets; Leak at 308: the first and collect mouth; 309: the three annular grooves; 310: pressure oil liquid supply passage; 311: the Fourth Ring connected in stars; 312: the first guidance tapes; 313: the second dust rings; 400: the tested cylinder of piston seal; 401: piston seal; 402: the second piston rods; 402a: cock body; 402b: the body of rod; 402c: boss; 403: cylinder body; 404: the second pressure oil liquid entrances; 405: outside sandwich; 406: the second temperature adjustment liquid inlets; 407: the second temperature adjustment liquid outlets; Leak at 408: the second and collect mouth; 409: second space; 410: axial passage; 411: radial passage; 412: the five rings connected in stars; 413: nut; 414:O shape seal ring; 415: the second guidance tapes; 416: end cap; 500: stand; 501: panel; 502: base plate; 503: support frame; P: pressure hydraulic fluid port; T: return opening; A: the first actuator port; B: the second actuator port.
Embodiment
Below in conjunction with accompanying drawing, embodiment of the present utility model is elaborated.Should be understood that, embodiment described herein only, for description and interpretation the utility model, is not limited to the utility model.
In the utility model, in the situation that not doing contrary explanation, the noun of locality of use is as undefined in the working state of the testing installation for test fluid cylinder pressure seal durability that " upper and lower " normally provides at the utility model.
As shown in Figures 2 to 5, the utility model provides a kind of testing installation for test fluid cylinder pressure seal durability, this testing installation comprises tested oil hydraulic cylinder, for driving the piston rod of described tested oil hydraulic cylinder, do driver element 100 and the pressure oil liquid feeding unit 200 of linear reciprocating motion, in described tested oil hydraulic cylinder, be provided with for laying the first ring connected in star of piston seal 401 and/or for laying the second annular groove of piston rod seal component 301, wherein, described pressure oil liquid feeding unit 200 comprises pressurized cylinder 201, fuel tank 202 and selector valve 203, the active chamber of described pressurized cylinder 201 is connected with described fuel tank 202 by described selector valve 203, the filler opening of the hyperbaric chamber of described pressurized cylinder 201 is connected with described fuel tank 202, the oil outlet of the hyperbaric chamber of described pressurized cylinder 201 is connected with described first ring connected in star and/or described the second annular groove.
Like this, at driver element 100, drive the piston rod of tested oil hydraulic cylinder to carry out in the process of linear reciprocating motion, by pressure oil liquid feeding unit 200 to for laying the first ring connected in star of piston seal 401 and/or providing imitative operating mode impulse test pressure oil liquid for laying the second annular groove of piston rod seal component 301, particularly, by pressurized cylinder 201, improve the pressure of pressure oil liquid, make the pressure of pressure oil liquid can reach 50Mpa or required test pressure, meet the requirement of imitative working condition tests pressure, in addition, the trend of hydraulic oil that changes the active chamber of pressurized cylinder 201 by selector valve 203 changes the size of pressure that is fed to the pressure oil liquid of described first ring connected in star and/or described the second annular groove from hyperbaric chamber, thereby provide imitative operating mode impulse test pressure oil liquid to first ring connected in star and/or the second annular groove, the real working condition of simulation hydraulic cylinder sealing element.
As shown in Figure 2, the cross-section area of the hyperbaric chamber of pressurized cylinder 201 is less than the cross-section area of the low-pressure cavity of pressurized cylinder 201, thereby reaches the object that improves oil liquid pressure in hyperbaric chamber.In addition, the to-and-fro motion of piston rod need keep synchronizeing with the commutation of selector valve, to realize the pulse pressurization to tested hydraulic cylinder sealing element, and can carry out by approach switch the interlock of control piston bar and selector valve, this kind of control mode is conventionally known to one of skill in the art, do not repeat them here.
Preferably, between the pressure hydraulic fluid port P of described selector valve 203 and described fuel tank 202, be connected with the first oil pump 204 and the first one-way valve 205.Like this, by the first oil pump 204, the fluid in fuel tank 202 can be pumped into the pressure hydraulic fluid port P of selector valve 203; The first one-way valve 205 is back to fuel tank 202 for preventing fluid.In addition, between the pressure hydraulic fluid port P of selector valve 203 and fuel tank 202, be also connected with inlet oil filter 206 and the 3rd switch valve (for example ball valve) 219.Inlet oil filter 206 is for filtering entering the fluid of the pressure hydraulic fluid port P of selector valve 203, to avoid impurity to enter in selector valve 203; The 3rd switch valve 219 is for the break-make of oil circuit control easily.
Preferably, be connected with the second one-way valve 227 between the oil return inlet T of described selector valve 203 and described fuel tank 202, this second one-way valve 227 is for improving the commutation stability of pressurized cylinder 201.In addition, between the oil return inlet T of described selector valve 203 and described fuel tank 202, be also connected with return filter 228, this return filter 228 is for filtering the fluid that is back to fuel tank 202.
Preferably, between the filler opening of the hyperbaric chamber of described pressurized cylinder 201 and described fuel tank 202, be connected with the second oil pump 210 and the 3rd one-way valve 211.Like this, by the second oil pump 210, the fluid in fuel tank 202 can be pumped in the hyperbaric chamber of pressurized cylinder 201, with the hyperbaric chamber discontinuous to pressurized cylinder 201, supplement fluid; The 3rd one-way valve 211 is back to fuel tank 202 for preventing fluid.In addition, between the filler opening of the hyperbaric chamber of pressurized cylinder 201 and fuel tank 202, be also connected with the 4th switch valve (for example ball valve) 220, with the break-make of oil circuit control easily.
Pressure hydraulic fluid port P and the oil circuit between described fuel tank 202 of described selector valve 203 are oil-feed oil circuit, and the oil circuit between the oil return inlet T of described selector valve 203 and described fuel tank 202 is oil return circuit.Preferably, between described oil-feed oil circuit and described fuel tank 202, be connected with the first pressure gauge 207, accumulator 208 and the first relief valve 209.Particularly, the first pressure gauge 207, accumulator 208 and the first relief valve 209 can be connected between the pressure hydraulic fluid port P and the first one-way valve 205 of selector valve 203 of oil-feed oil circuit, between second one-way valve 227 and return filter 228 of oil return circuit; The first pressure gauge 207 can be arranged between accumulator 208 and the first relief valve 209.Like this, by the first pressure gauge 207, can detect the oil liquid pressure of oil-feed oil circuit, and fluctuate or by the first relief valve 209, the unnecessary fluid in oil-feed oil circuit overflowed back to fuel tank 202 by accumulator 208 minimizing oil circuit oil liquid pressures, thereby realize safety and the pressure adjusting of oil-feed oil circuit.In addition, the first relief valve 209 can be taked various suitable forms, for example common relief valve or proportional pressure control valve, or adopt the relief valve of these two kinds of forms.In addition, between accumulator 208 and described oil-feed oil circuit, can also be connected with the 5th switch valve (for example ball valve) 221, to control easily the break-make of accumulator 208.
Preferably, between the repairing oil circuit between the filler opening of the hyperbaric chamber of described pressurized cylinder 201 and described fuel tank 202 and described fuel tank 202, be connected with the second relief valve 212 and the second pressure gauge 213.Particularly, the second relief valve 212 and the second pressure gauge 213 can be connected between second oil pump 210 and the 3rd one-way valve 211 of repairing oil circuit.Like this, the oil liquid pressure that can detect in repairing oil circuit by the second pressure gauge 213, when too high with the oil liquid pressure in repairing oil circuit, by the second relief valve 212, the fluid in repairing oil circuit is overflowed back to fuel tank 202, thereby make the oil liquid pressure of repairing oil circuit reach predetermined pressure.
In order to measure the test pressure with pilot pressure fluid to being fed to the pressure of the pressure oil liquid of described first ring connected in star and/or described the second annular groove easily, preferably, between the oil outlet of the hyperbaric chamber of described pressurized cylinder 201 and described first ring connected in star and/or described the second annular groove, be connected with pressure transducer 214.
Preferably, between the oil outlet of the hyperbaric chamber of described pressurized cylinder 201 and described first ring connected in star and/or described the second annular groove, be connected with the first switch valve (for example ball valve) 215; Oil circuit between the oil outlet of the hyperbaric chamber of described pressurized cylinder 201 and described first ring connected in star and/or described the second annular groove is connected to described fuel tank 202 by the branch road 216 of draining the oil, described in drain the oil on branch road 216 and be connected with second switch valve (for example ball valve) 226.Like this, while overhauling when the tested oil hydraulic cylinder of dismounting or to the oil feeding line between the oil outlet of the hyperbaric chamber of pressurized cylinder 201 and first ring connected in star and/or the second annular groove, second switch valve 226 can be opened, so that the fluid in tested oil hydraulic cylinder and oil feeding line flows back to fuel tank 202, then the first switch valve 215 cuts out, thereby facilitate the dismounting of tested oil hydraulic cylinder and the maintenance of oil feeding line.
Preferably, described pressure oil liquid feeding unit 200 also comprises cooling unit 217, and the filler opening of this cooling unit 217 is connected with described fuel tank 202 respectively with oil outlet; Between described fuel tank 202 and described cooling unit 217, be connected with fine filter 218.Like this, by cooling unit 217, can guarantee the oil temperature requirement of fluid in fuel tank 202, by fine filter 218, can guarantee the turbidity test requirement of fluid in fuel tank 202.Cooling unit 217 can suitably be selected, and for example cooling unit 217 can be oil cooling machine.
In addition, be by above-mentioned mechanical driver element 100(rather than as prior art by the driver element of hydraulic type) come the first piston bar 302 of the tested cylinder 300 of driven plunger shaft seal and the second piston rod 402 of the tested cylinder 400 of piston seal to carry out linear reciprocating motion, so can not affect the test of the sealability of piston rod seal component 301 and piston seal 401, thereby the conformity of proof test condition and the accuracy of test result.
Preferably, described driver element 100 also comprises link 102, the two ends of this link 102 are connected with the first piston bar 302 of the tested cylinder 300 of described piston rod seal component and the second piston rod 402 of the tested cylinder 400 of described piston seal by pull pressure sensor 111 respectively, and described slide block 105 is connected with described link 102.Like this, by pull pressure sensor 111, can measure the surface friction drag of first piston bar 302 and the second piston rod 402, be conducive to optimize the related process parameter of organization plan and cylinder barrel and the piston rod of hydraulic cylinder sealing element.In order to make link 102 have certain activity surplus, facilitate link 102 to drive the first piston bar 302 of the tested cylinder 300 of piston rod seal component and the second piston rod 402 of the tested cylinder 400 of piston seal to carry out straight line motion, preferably, described link 102 comprise main body (not shown) and respectively with two bulb (not shown)s of the two ends ball-joint of this main body, these two bulbs are connected with the first piston bar 302 of the tested cylinder 300 of described piston rod seal component and the second piston rod 402 of the tested cylinder 400 of described piston seal by described pull pressure sensor 111 respectively, described slide block 105 is connected with the main body of described link 102.Particularly, pull pressure sensor 111 can be threaded with the first piston bar 302 of link 102, the tested cylinder 300 of described piston rod seal component and the second piston rod 402 of the tested cylinder 400 of described piston seal.
In order can to measure the tested cylinder 300 of many covers piston rod seal component and the tested cylinder 400 of piston seal simultaneously, preferably, the tested cylinder 400 of the tested cylinder 300 of described piston rod seal component and piston seal arranges respectively in pairs, described link 102 is connected between the tested cylinder 300 of corresponding described piston rod seal component and the tested cylinder 400 of piston seal, described driver element 100 also comprises coupling shaft 101, this coupling shaft 101 is connected between the tested cylinder 300 of described piston rod seal component of paired setting and two described links 102 of the tested cylinder 400 of piston seal, described slide block 105 is fixedly connected with described coupling shaft 101.Coupling shaft 101 can be fixedly connected with link 102 by fastening piece (such as locating stud, bolt etc.), and coupling shaft 101 is connected to the middle part of link 102 conventionally.Slide block 105 can be connected to the middle part of coupling shaft 101, and slide block 105 can be fixedly connected with coupling shaft 101 by fastening piece (such as locating stud, bolt etc.).
In addition, as shown in Figure 2, the oil outlet of the hyperbaric chamber of the pressurized cylinder 201 of pressure oil liquid feeding unit 200 can be fed to the tested cylinder 300 of each piston rod seal component and the tested cylinder 400 of piston seal by pressure oil liquid by many (being four (C0, C1, C2, C3) in the mode of execution shown in Fig. 2) fuel feeding branch roads.
Described shift drive mechanism can suitably be selected.In order to control the speed of shift drive mechanism easily, preferably, described shift drive mechanism comprises variable speed electric motors, particularly 112 and the speed reducer 113 being mutually in transmission connection.Variable speed electric motors, particularly 112 for example can be connected with speed reducer 113 by the first coupling 114, and speed reducer 113 can be connected with eccentric shaft 103 by the second coupling 115 then.In process of the test, can regulate by electrical control system the rotating speed of variable speed electric motors, particularly 112, thereby realize the test speed of the tested cylinder 300 of piston rod seal component and the tested cylinder 400 imitative operating mode 0-1m/s of piston seal.
As shown in Figures 3 to 5, eccentric wheel 104 can be two, and can be fixedly set on two eccentric shafts 103 by fastening piece, and connecting rod 106 is arranged between two eccentric wheels 104.Bearing support 107 is two, to provide stable support to eccentric shaft 103.
In addition, guiding pairs 108 can be taked various suitable structures, as long as can guide shoe 105, make slide block 105 drive the first piston bar 302 of the tested cylinder 300 of described piston rod seal component and the second piston rod 402 of the tested cylinder 400 of described piston seal to carry out linear reciprocating motion.
In addition, in order to facilitate the installation of tested oil hydraulic cylinder and driver element 100, preferably, the testing installation for test fluid cylinder pressure seal durability that the utility model provides also comprises stand 500, and described tested oil hydraulic cylinder and driver element 100 are arranged on described stand 500.For convenient, arrange, as shown in Figures 3 to 5, preferably, described stand 500 comprise panel 501, base plate 502 with for being fixedly connected with the support frame 503 of described panel 501 and base plate 502, the tested cylinder 300 of described piston rod seal component, the tested cylinder 400 of piston seal and guiding pairs 108 are arranged on described panel 501, and described shift drive mechanism (for example variable speed electric motors, particularly 112 and speed reducer 113) and bearing support 107 are arranged on described base plate 502.Panel 501, base plate 502 and support frame 503 can be mutually permanently connected by the mode of welding.The tested cylinder 300 of piston rod seal component can be arranged on panel 501 by the first bearing 116, and the tested cylinder 400 of piston seal can be arranged on panel 501 by the second bearing 117, and guiding pairs 108 can be arranged on panel 501 by fixed base 118.Variable speed electric motors, particularly 112 can be arranged on base plate 502 by the 3rd bearing 109, and speed reducer 113 can be arranged on base plate 502 by the 4th bearing 110, and bearing support 107 can be arranged on base plate 502 by the mode that is fastenedly connected or welds.The concrete mounting type of the tested cylinder 300 of piston rod seal component, the tested cylinder 400 of piston seal, guiding pairs 108, variable speed electric motors, particularly 112 and speed reducer 113 is conventionally known to one of skill in the art, does not repeat them here.
As mentioned above, described tested oil hydraulic cylinder can comprise the tested cylinder 300 of piston rod seal component and the tested cylinder 400 of piston seal.
As shown in Figure 6, according to a kind of preferred implementation of the present utility model, the tested cylinder 300 of described piston rod seal component comprises first piston bar 302 and guiding body 303, described guiding body 303 is set on described first piston bar 302, in the interior perimeter surface of described guiding body 303, be provided with for laying described second annular groove of described piston rod seal component 301, described piston rod seal component 301 is for by the clearance seal between described first piston bar 302 and described guiding body 303, on described guiding body 303, be provided with the first pressure oil liquid entrance 304 being connected with the oil outlet of the hyperbaric chamber of described pressurized cylinder 201, this the first pressure oil liquid entrance 304 communicates with the space between described first piston bar 302 and described guiding body 303, the inside of described first piston bar 302 is formed with the first space 305, on described first piston bar 302, be provided with the first temperature adjustment liquid inlet 306 and the first temperature adjustment liquid outlet 307 that are all communicated with described the first space 305.
As shown in Figure 7 and Figure 8, according to a kind of preferred implementation of the present utility model, the tested cylinder 400 of described piston seal comprises the second piston rod 402 and cylinder body 403, the cock body 402a of described the second piston rod 402 is arranged in described cylinder body 403, the body of rod 402b of described the second piston rod 402 stretches out from described cylinder body 403, on the outer surface of described cock body 402a, be provided with for laying the described first ring connected in star of described piston seal 401, described piston seal 401 is for by the clearance seal between described cock body 402a and described cylinder body 403, on described body of rod 402b, be provided with the second pressure oil liquid entrance 404 being connected with the oil outlet of the hyperbaric chamber of described pressurized cylinder 201, this the second pressure oil liquid entrance 404 communicates with the space between described cock body 402a and described cylinder body 403, on the outer surface of described cylinder body 403, be provided with outside sandwich 405, between this outside sandwich 405 and described cylinder body 403, be formed with second space 409, on described outside sandwich 405, be provided with the second temperature adjustment liquid inlet 406 and the second temperature adjustment liquid outlet 407.
As shown in Figure 2, described testing installation also comprises for supplying the liquid supply device 30 of temperature adjustment liquid, the outlet of this liquid supply device 30 is connected with the second temperature adjustment liquid inlet 406 with described the first temperature adjustment liquid inlet 306 respectively, and the import of this liquid supply device 30 is connected with the second temperature adjustment liquid outlet 407 with described the first temperature adjustment liquid outlet 307 respectively.In the mode of execution shown in Fig. 2, four road B0, B1, B2, B3 are arranged in the outlet of liquid supply device 30, are connected respectively with the temperature adjustment liquid inlet of four tested cylinders with pipeline; Four road A0, A1, A2, A3 are arranged in the import of liquid supply device 30, are connected respectively with the temperature adjustment liquid outlet of four tested cylinders with pipeline, form each tested cylinder circulating temperature-regulating loop.
According to the tested cylinder 300 of the piston rod seal component of above-mentioned preferred implementation, in first space 305 that can utilize liquid supply device 30 to form in the inside of first piston bar 302, pass into the test ambient temperature that temperature adjustment liquid changes tested oil hydraulic cylinder, thus the operating ambient temperature of Reality simulation operating mode.In addition, above-mentioned method of temperature control can adapt to various test ambient temperature, the restriction of the ambient temperature that is not put to the test, so test variety range is wider, applicability is good, and without increasing experimentation cost.Moreover above-mentioned method of temperature control energy loss is less, temperature adjustment is quick, temperature stabilization, and stability and test efficiency that can proof test condition.
According to the tested cylinder 400 of the piston seal of above-mentioned preferred implementation, in the second space 409 that can utilize liquid supply device 30 to form, pass into the test ambient temperature that temperature adjustment liquid changes tested oil hydraulic cylinder between outside sandwich 405 and cylinder body 403, thus the operating ambient temperature of Reality simulation operating mode.In addition, above-mentioned method of temperature control can adapt to various test ambient temperature, the restriction of the ambient temperature that is not put to the test, so test variety range is wider, applicability is good, and without increasing experimentation cost.Moreover above-mentioned method of temperature control energy loss is less, temperature adjustment is quick, temperature stabilization, and stability and test efficiency that can proof test condition.
Described temperature adjustment liquid can be various liquid, for example water or fluid.
In order to measure with Control experiment ambient temperature the temperature of the temperature adjustment liquid in the tested cylinder 300 of piston rod seal component and the tested cylinder 400 of piston seal easily, preferably, between the import of described liquid supply device 30 and described the first temperature adjustment liquid outlet 307 and between the import of described liquid supply device 30 and described the second temperature adjustment liquid outlet 407, be connected with the first temperature transducer 31.
Other preferred following structural features of the tested cylinder 300 of piston rod seal component.
In order easily the pressure oil liquid leaking in guiding body 303 via piston rod seal component 301 to be collected, to analyze the durability of piston rod seal component 301 and to carry out comparative trial, and can realize directly perceived, quantitative measurment to letting out in tested piston rod seal component 301, preferably, the bottom of described guiding body 303 is provided with the first leakage being communicated with the inner space of described guiding body 303 and collects mouth 308.The first set-up mode that leaks collection mouth 308 is conventionally known to one of skill in the art, does not repeat them here.In the mode of execution shown in Fig. 6, it is two that mouth 308 is collected in the first leakage, these two first leakages are collected mouth 308 and are separately positioned on for laying the both sides of two the second annular grooves of piston rod seal component 301, thereby respectively the pressure oil liquid leaking by two piston rod seal components 301 are collected.In order easily the pressure oil liquid of leakage to be directed to the first leakage, collect mouth 308, preferably, in the interior perimeter surface of described guiding body 303, be provided with and described first leakage collection mouthful 308 the 3rd annular grooves 309 that are communicated with.
In order to regulate equably the test ambient temperature of tested oil hydraulic cylinder, and facilitate the setting of the first temperature adjustment liquid inlet 306 and the first temperature adjustment liquid outlet 307, preferably, described first piston bar 302 formation are run through along the axial direction of described first piston bar 302 in described the first space 305, and described the first temperature adjustment liquid inlet 306 and the first temperature adjustment liquid outlet 307 are separately positioned on the two ends of described first piston bar 302.In addition, on the outer surface at the two ends of first piston bar 302, be provided with screw thread, to be connected easily with for supplying the import and export of the liquid supply device 30 of temperature adjustment liquid.
Preferably, described the second annular groove is two.Like this, two identical or different piston rod seal components 301 can be installed in two the second annular grooves.When two piston rod seal components 301 are different, can carry out comparative trial.
Pressure oil liquid can flow to the second annular groove for laying piston rod seal component 301 so that the durability of piston rod seal component 301 is tested by various suitable modes.According to a kind of preferred implementation of the present utility model, on described guiding body 303, be provided with the pressure oil liquid supply passage 310 extending along the radial direction of this guiding body 303 and the Fourth Ring connected in star 311 being communicated with this pressure oil liquid supply passage 310, wherein: two described the second annular grooves lay respectively at the both sides of described Fourth Ring connected in star 311, described the first pressure oil liquid entrance 304 is communicated with described pressure oil liquid supply passage 310, described pressure oil liquid supply passage 310 is communicated with the space between described first piston bar 302 and described guiding body 303 by described Fourth Ring connected in star 311.Fourth Ring connected in star 311 needn't be too wide, and for example the width of Fourth Ring connected in star 311 can be 10 millimeters.Like this, owing to only having the seldom hydraulic oil of amount to be present in two less spaces between tested piston rod seal component 301 in process of the test, so the impact of deaeration on test conditions effectively in process of the test, improves the correctness of test result greatly.In addition, during due to test, only need to the Fourth Ring connected in star 311 a small amount of hydraulic oil of supply, not need a large amount of hydraulic oil by the first pressure oil liquid entrance 304, so in the disassembly process of testing installation of the present utility model, in the Renewal process of Sealing and can effectively reduce the pollution of hydraulic oil to environment in process of the test, greatly improve the working environment of tester.
For the ease of first piston bar 302 is guided, preferably, between the outer surface of described first piston bar 302 and the interior perimeter surface of described guiding body 303, be provided with the first guidance tape 312.In the mode of execution shown in Fig. 6, the first guidance tape 312 is two, and these two the first guidance tapes 312 are separately positioned between two described the second annular grooves and Fourth Ring connected in star.Particularly, can in the interior perimeter surface of guiding body 303, annular groove be set, and the first guidance tape 312 is arranged in this annular groove.
Preferably, between the interior perimeter surface at the two ends of described guiding body 303 and the outer surface of described first piston bar 302, be provided with the second dust ring 313, thereby prevent that outside dust from entering into the space between guiding body 303 and first piston bar 302.Particularly, can in the interior perimeter surface of guiding body 303, annular groove be set, and the second dust ring 313 is arranged in this annular groove.
Other preferred following structural features of the tested cylinder 400 of piston seal.
In order easily the pressure oil liquid leaking in cylinder body 403 via piston seal 401 to be collected, to analyze the durability of piston seal 401 and to carry out comparative trial, and can realize directly perceived, quantitative measurment to letting out in tested piston seal 401, preferably, the bottom of described cylinder body 403 is provided with the second leakage being communicated with the inner space of described cylinder body 403 and collects mouth 408.The second set-up mode that leaks collection mouth 408 is conventionally known to one of skill in the art, does not repeat them here.In the mode of execution shown in Fig. 7 and Fig. 8, it is two that mouth 408 is collected in the second leakage, these two second leakages are collected mouth 408 and are separately positioned on for laying the both sides of two first ring connected in stars of piston seal 401, thereby the pressure oil liquid respectively two piston seals 401 by two cock body 402a being leaked is collected.
Preferably, described first ring connected in star is two.Like this, can in two first ring connected in stars, lay two piston seals 401 tests.Two piston seals 401 can be identical Sealing, can be also different Sealings.When two piston seals 401 are different Sealing, can carry out comparative trial.
Pressure oil liquid can flow to first ring connected in star for laying piston seal 401 so that the durability of piston seal 401 is tested by various suitable modes.According to a kind of preferred implementation of the present utility model, on described the second piston rod 402, be provided with axial passage 410, radial passage 411 and the five rings connected in star 412 being communicated with this radial passage 411, wherein: two described first ring connected in stars lay respectively at the both sides of described five rings connected in star 412, described the second pressure oil liquid entrance 404 is communicated with described axial passage 410, described axial passage 410 is communicated with described radial passage 411, described radial passage 411 is communicated with the space between described cock body 402a and described cylinder body 403 by described five rings connected in star 412.Axial passage 410 is arranged on the central position of the second piston rod 402 conventionally.Five rings connected in star 412 needn't be too wide, and for example the width of five rings connected in star 412 can be 10 millimeters.Like this, owing to only having the seldom hydraulic oil of amount to be present in two less spaces between tested piston seal 401 in process of the test, so the impact of deaeration on test conditions effectively in process of the test, improves the correctness of test result greatly.In addition, during due to test, only need to the five rings connected in star 412 a small amount of hydraulic oil of supply, not need a large amount of hydraulic oil by the second pressure oil liquid entrance 404, so in the disassembly process of testing installation of the present utility model, in the Renewal process of Sealing and can effectively reduce the pollution of hydraulic oil to environment in process of the test, greatly improve the working environment of tester.
The cock body 402a of the second piston rod 402 and body of rod 402b can be monolithic construction, can be also split-type structural.In the mode of execution shown in Fig. 7, cock body 402a and the body of rod 402b of the second piston rod 402 form monolithic construction.In the mode of execution shown in Fig. 8, cock body 402a and the body of rod 402b of the second piston rod 402 form split-type structural.As shown in Figure 8, the second piston rod 402 comprises two cock body 402a and a body of rod 402b, and two cock body 402a are enclosed within the upper and backstop of body of rod 402b on the boss 402c of body of rod 402b, and lock by nut 413.In addition, in order to prevent that fluid, from the clearance leakage between body of rod 402b and cock body 402a, is also provided with O-ring seals 414 between body of rod 402b and cock body 402a.
For the ease of the second piston rod 402 is guided, preferably, between the outer surface of described cock body 402a and the interior perimeter surface of described cylinder body 403, be provided with the second guidance tape 415.In the mode of execution shown in Fig. 7 and Fig. 8, for laying the both sides of the described first ring connected in star of described piston seal 401, be provided with described the second guidance tape 415.Particularly, can on the outer surface of cock body 402a, annular groove be set, and the second guidance tape 415 is arranged in this annular groove.
In order to limit easily the movement position of cock body 402a, preferably, the two ends of described cylinder body 403 are removably connected with respectively end cap 416, and this end cap 416 is inserted in described cylinder body 403 to limit the movement position of described cock body 402a.The mode that end cap 416 for example can be threaded connection is connected to the two ends of cylinder body 403.
In order to heat cylinder body 403 equably or cooling, with the test ambient temperature of simulated solution cylinder pressure more truly, preferably, described outside sandwich 405 arranges around described cylinder body 403.Outside sandwich 405 can be arranged on the outer surface of cylinder body 403 by various suitable modes, and for example outside sandwich 405 can be welded on the outer surface of cylinder body 403.In addition, outside sandwich 405 can adopt various suitable materials, for example metallic material.
According to a kind of preferred implementation of the present utility model, described the second temperature adjustment liquid inlet 406 and the second temperature adjustment liquid outlet 407 are separately positioned on bottom and the top and spaced apart along the axial direction of described cylinder body 403 of described outside sandwich 405.Particularly, as shown in Figure 7 and Figure 8, the second temperature adjustment liquid inlet 406 and the second temperature adjustment liquid outlet 407 are probably arranged on the diagonally opposing corner position of outside sandwich 405.Like this, can increase the flow path of temperature adjustment liquid, more equably the outer surface of cylinder body 403 be heated.
In addition, the testing installation for test fluid cylinder pressure seal durability that the utility model provides also comprises electrical control system, and the formation of this electrical control system is conventionally known to one of skill in the art.For example, this electrical control system can be comprised of forceful electric power, weakness control section, be mainly used in realizing the electrical control for the testing installation of test fluid cylinder pressure seal durability, the setting of test parameters, the collection of data-signal and processing, the demonstration of test pressure, speed, temperature and test number (TN), and demonstration, storage and the output print of test pressure-time graph, surface friction drag-time graph.
In addition,, in the utility model, the structure of each hydraulic element and annexation are conventionally known to one of skill in the art, do not repeat them here.
As shown in Fig. 2 to Fig. 8, the testing installation for test fluid cylinder pressure seal durability that the utility model embodiment provides is when work, by pressure oil liquid feeding unit 200, to the second annular groove of the tested cylinder 300 of piston rod seal component and the first ring connected in star of the tested cylinder 400 of piston seal, pass into pressure oil liquid respectively, and measure by the pressure of 214 pairs of pressure oil liquids of pressure transducer; By driver element 100, the first piston bar 302 of the tested cylinder 300 of driven plunger shaft seal and the second piston rod 402 of the tested cylinder 400 of piston seal are done linear reciprocating motion respectively; By liquid supply device 30, in the first space 305 of the first piston bar 302 of the tested cylinder 300 of piston rod seal component and in the outside sandwich 405 of the tested cylinder 400 of piston seal and the second space 409 between cylinder body 403, pass into temperature adjustment liquid respectively, thereby change the test ambient temperature of tested oil hydraulic cylinder, and the temperature of the temperature adjustment liquid flowing out from the first space 305 and second space 409 by 31 pairs of the first temperature transducers is measured.In addition, in process of the test, can measure by the surface friction drag of 111 pairs of first piston bars 302 of pull pressure sensor and the second piston rod 402.Moreover, in process of the test, can collect mouthful the 308 and second leakage by the first leakage and collect mouth 408 respectively to leaking the fluid in guiding body 303 via piston rod seal component 301 and collecting via the fluid of piston seal 401 leakages in cylinder body 403, to analyze the durability of piston rod seal component 301 and piston seal 401 and to carry out comparative trial.
The testing installation for test fluid cylinder pressure seal durability that the utility model embodiment provides possesses following advantage:
(1) can improve by pressurized cylinder 201 pressure of pressure oil liquid, make the pressure of pressure oil liquid can reach 50Mpa or test required pressure, meet the requirement of imitative working condition tests pressure, in addition, the trend of hydraulic oil that changes the active chamber of pressurized cylinder 201 by selector valve 203 changes the size of pressure that is fed to the pressure oil liquid of described first ring connected in star and/or described the second annular groove from hyperbaric chamber, realize the oil liquid pressure height circulation change of pressurized cylinder hyperbaric chamber, thereby provide imitative operating mode impulse test pressure oil liquid to first ring connected in star and/or the second annular groove, the real working condition of simulation hydraulic cylinder sealing element,
(2) be by above-mentioned mechanical driver element 100(rather than as prior art by the driver element of hydraulic type) come the first piston bar 302 of the tested cylinder 300 of driven plunger shaft seal and the second piston rod 402 of the tested cylinder 400 of piston seal to carry out linear reciprocating motion, so can not affect the test of the sealability of piston rod seal component 301 and piston seal 401, thereby the conformity of proof test condition and the accuracy of test result;
(3) testing installation for test fluid cylinder pressure seal durability that the utility model embodiment provides can imitate all operating modes of oil hydraulic cylinder (pressure of pressure oil liquid, the movement velocity of hydraulic cylinder piston rod, test ambient temperature parameter) and carry out that the imitative operating mode durability of Sealing is qualitative, quantitative test, detects the actual life of hydraulic cylinder sealing element;
(4) according to the tested cylinder 300 of the piston rod seal component of the utility model preferred implementation, in first space 305 that can utilize liquid supply device 30 to form in the inside of first piston bar 302, pass into the test ambient temperature that temperature adjustment liquid changes tested oil hydraulic cylinder, thus the operating ambient temperature of Reality simulation operating mode; According to the tested cylinder 400 of the piston seal of the utility model preferred implementation, in the second space 409 that can utilize liquid supply device 30 to form, pass into the test ambient temperature that temperature adjustment liquid changes tested oil hydraulic cylinder between outside sandwich 405 and cylinder body 403, thus the operating ambient temperature of Reality simulation operating mode; In addition, above-mentioned method of temperature control can adapt to various test ambient temperature, the restriction of the ambient temperature that is not put to the test, so test variety range is wider, applicability is good, and without increasing experimentation cost; Moreover above-mentioned method of temperature control energy loss is less, temperature adjustment is quick, temperature stabilization, and stability and test efficiency that can proof test condition;
(5) by pull pressure sensor 111, can measure the surface friction drag of first piston bar 302 and the second piston rod 402; By the first leakage, collecting mouthful the 308 and second leakage collection mouth 408 can be respectively to leaking the fluid in guiding body 303 and collecting via the fluid of piston seal 401 leakages in cylinder body 403 via piston rod seal component 301, thereby quantitative measurment is carried out in the leakage to piston rod seal component 301 and piston seal 401, thereby be conducive to optimize the related process parameter that meets the hydraulic cylinder sealing element of engineering machinery working condition requirement and be conducive to optimize organization plan and cylinder barrel and the piston rod of hydraulic cylinder sealing element, and then extend the working life of oil hydraulic cylinder.
Below describe by reference to the accompanying drawings preferred implementation of the present utility model in detail; but; the utility model is not limited to the detail in above-mentioned mode of execution; within the scope of technical conceive of the present utility model; can carry out multiple simple variant to the technical solution of the utility model, these simple variant all belong to protection domain of the present utility model.
It should be noted that in addition each the concrete technical characteristics described in above-mentioned embodiment, in reconcilable situation, can combine by any suitable mode.For fear of unnecessary repetition, the utility model is to the explanation no longer separately of various possible compound modes.
In addition, between various mode of execution of the present utility model, also can carry out combination in any, as long as it is without prejudice to thought of the present utility model, it should be considered as content disclosed in the utility model equally.
Claims (16)
1. the testing installation for test fluid cylinder pressure seal durability, this testing installation comprises tested oil hydraulic cylinder, for driving the piston rod of described tested oil hydraulic cylinder, do driver element (100) and the pressure oil liquid feeding unit (200) of linear reciprocating motion, in described tested oil hydraulic cylinder, be provided with for laying the first ring connected in star of piston seal (401) and/or for laying the second annular groove of piston rod seal component (301), it is characterized in that, described pressure oil liquid feeding unit (200) comprises pressurized cylinder (201), fuel tank (202) and selector valve (203), the active chamber of described pressurized cylinder (201) is connected with described fuel tank (202) by described selector valve (203), the filler opening of the hyperbaric chamber of described pressurized cylinder (201) is connected with described fuel tank (202), the oil outlet of the hyperbaric chamber of described pressurized cylinder (201) is connected with described first ring connected in star and/or described the second annular groove.
2. the testing installation for test fluid cylinder pressure seal durability according to claim 1, it is characterized in that, between the pressure hydraulic fluid port (P) of described selector valve (203) and described fuel tank (202), be connected with the first oil pump (204) and the first one-way valve (205); Between the return opening (T) of described selector valve (203) and described fuel tank (202), be connected with the second one-way valve (227); Between the filler opening of the hyperbaric chamber of described pressurized cylinder (201) and described fuel tank (202), be connected with the second oil pump (210) and the 3rd one-way valve (211).
3. the testing installation for test fluid cylinder pressure seal durability according to claim 2, it is characterized in that, the pressure hydraulic fluid port (P) of described selector valve (203) and the oil circuit between described fuel tank (202) are oil-feed oil circuit, are connected with the first pressure gauge (207), accumulator (208) and the first relief valve (209) between described oil-feed oil circuit and described fuel tank (202).
4. the testing installation for test fluid cylinder pressure seal durability according to claim 2, it is characterized in that, between the repairing oil circuit between the filler opening of the hyperbaric chamber of described pressurized cylinder (201) and described fuel tank (202) and described fuel tank (202), be connected with the second relief valve (212) and the second pressure gauge (213).
5. the testing installation for test fluid cylinder pressure seal durability according to claim 1, it is characterized in that, between the oil outlet of the hyperbaric chamber of described pressurized cylinder (201) and described first ring connected in star and/or described the second annular groove, be connected with pressure transducer (214).
6. the testing installation for test fluid cylinder pressure seal durability according to claim 1, it is characterized in that, between the oil outlet of the hyperbaric chamber of described pressurized cylinder (201) and described first ring connected in star and/or described the second annular groove, be connected with the first switch valve (215); Oil circuit between the oil outlet of the hyperbaric chamber of described pressurized cylinder (201) and described first ring connected in star and/or described the second annular groove is connected to described fuel tank (202) by the branch road of draining the oil (216), described in drain the oil on branch road (216) and be connected with second switch valve (226).
7. the testing installation for test fluid cylinder pressure seal durability according to claim 1, it is characterized in that, described pressure oil liquid feeding unit (200) also comprises cooling unit (217), and the filler opening of this cooling unit (217) is connected with described fuel tank (202) respectively with oil outlet; Between described fuel tank (202) and described cooling unit (217), be connected with fine filter (218).
8. the testing installation for test fluid cylinder pressure seal durability according to claim 1, is characterized in that, described driver element (100) is variable speed drive units.
9. the testing installation for test fluid cylinder pressure seal durability according to claim 8, it is characterized in that, described tested oil hydraulic cylinder comprises the tested cylinder of piston rod seal component (300) and the tested cylinder of piston seal (400), described driver element (100) comprises shift drive mechanism, eccentric shaft (103), eccentric wheel (104), connecting rod (106), slide block (105), be used for supporting the bearing support (107) of described eccentric shaft (103) and for guiding the guiding pairs (108) of the motion of described slide block (105), described shift drive mechanism is used for driving described eccentric shaft (103) to be rotated, described eccentric wheel (104) is fixedly set on described eccentric shaft (103), one end of described connecting rod (106) and described eccentric wheel (104) pivot joint, one end pivot joint of the other end of described connecting rod (106) and described slide block (105), the other end of described slide block (105) is connected between the first piston bar (302) of the tested cylinder of described piston rod seal component (300) and second piston rod (402) of the tested cylinder of described piston seal (400).
10. the testing installation for test fluid cylinder pressure seal durability according to claim 9, it is characterized in that, described driver element (100) also comprises link (102), the two ends of this link (102) are connected with the first piston bar (302) of the tested cylinder of described piston rod seal component (300) and second piston rod (402) of the tested cylinder of described piston seal (400) by pull pressure sensor (111) respectively, and described slide block (105) is connected with described link (102).
11. testing installations for test fluid cylinder pressure seal durability according to claim 10, it is characterized in that, described link (102) comprise main body and respectively with two bulbs of the two ends ball-joint of this main body, described two bulbs are connected with the first piston bar (302) of the tested cylinder of described piston rod seal component (300) and second piston rod (402) of the tested cylinder of described piston seal (400) by described pull pressure sensor (111) respectively, and described slide block (105) is connected with the main body of described link (102).
12. testing installations for test fluid cylinder pressure seal durability according to claim 10, it is characterized in that, the tested cylinder of described piston rod seal component (300) and the tested cylinder of piston seal (400) arrange respectively in pairs, described link (102) is connected between the tested cylinder of corresponding described piston rod seal component (300) and the tested cylinder of piston seal (400), described driver element (100) also comprises coupling shaft (101), this coupling shaft (101) is connected between the tested cylinder of described piston rod seal component (300) of paired setting and two described links (102) of the tested cylinder of piston seal (400), described slide block (105) is fixedly connected with described coupling shaft (101).
13. testing installations for test fluid cylinder pressure seal durability according to claim 1, is characterized in that, described tested oil hydraulic cylinder comprises the tested cylinder of piston rod seal component (300) and the tested cylinder of piston seal (400), wherein:
The tested cylinder of described piston rod seal component (300) comprises first piston bar (302) and guiding body (303), described guiding body (303) is set on described first piston bar (302), in the interior perimeter surface of described guiding body (303), be provided with for laying described second annular groove of described piston rod seal component (301), described piston rod seal component (301) is for by the clearance seal between described first piston bar (302) and described guiding body (303), on described guiding body (303), be provided with the first pressure oil liquid entrance (304) being connected with the oil outlet of the hyperbaric chamber of described pressurized cylinder (201), this the first pressure oil liquid entrance (304) communicates with the space between described first piston bar (302) and described guiding body (303), the inside of described first piston bar (302) is formed with the first space (305), on described first piston bar (302), be provided with the first temperature adjustment liquid inlet (306) and the first temperature adjustment liquid outlet (307) that are all communicated with described the first space (305),
The tested cylinder of described piston seal (400) comprises the second piston rod (402) and cylinder body (403), the cock body (402a) of described the second piston rod (402) is arranged in described cylinder body (403), the body of rod (402b) of described the second piston rod (402) stretches out from described cylinder body (403), on the outer surface of described cock body (402a), be provided with for laying the described first ring connected in star of described piston seal (401), described piston seal (401) is for by the clearance seal between described cock body (402a) and described cylinder body (403), on the described body of rod (402b), be provided with the second pressure oil liquid entrance (404) being connected with the oil outlet of the hyperbaric chamber of described pressurized cylinder (201), this the second pressure oil liquid entrance (404) communicates with the space between described cock body (402a) and described cylinder body (403), on the outer surface of described cylinder body (403), be provided with outside sandwich (405), between this outside sandwich (405) and described cylinder body (403), be formed with second space (409), on described outside sandwich (405), be provided with the second temperature adjustment liquid inlet (406) and the second temperature adjustment liquid outlet (407),
Described testing installation also comprises the liquid supply device (30) for supplying temperature adjustment liquid, the outlet of this liquid supply device (30) is connected with the second temperature adjustment liquid inlet (406) with described the first temperature adjustment liquid inlet (306) respectively, and the import of this liquid supply device (30) is connected with the second temperature adjustment liquid outlet (407) with described the first temperature adjustment liquid outlet (307) respectively.
14. testing installations for test fluid cylinder pressure seal durability according to claim 13, is characterized in that, described liquid supply device (30) is cold-hot integrated machine.
15. testing installations for test fluid cylinder pressure seal durability according to claim 13, it is characterized in that, between the import of described liquid supply device (30) and described the first temperature adjustment liquid outlet (307) and between the import of described liquid supply device (30) and described the second temperature adjustment liquid outlet (407), be connected with the first temperature transducer (31).
16. testing installations for test fluid cylinder pressure seal durability according to claim 13, it is characterized in that, the bottom of described guiding body (303) is provided with the first leakage being communicated with the inner space of described guiding body (303) and collects mouthful (308); The bottom of described cylinder body (403) is provided with the second leakage being communicated with the inner space of described cylinder body (403) and collects mouthful (408).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320493686.3U CN203404164U (en) | 2013-08-13 | 2013-08-13 | Test equipment for testing durability of sealing element of hydraulic cylinder |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320493686.3U CN203404164U (en) | 2013-08-13 | 2013-08-13 | Test equipment for testing durability of sealing element of hydraulic cylinder |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203404164U true CN203404164U (en) | 2014-01-22 |
Family
ID=49940102
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320493686.3U Expired - Lifetime CN203404164U (en) | 2013-08-13 | 2013-08-13 | Test equipment for testing durability of sealing element of hydraulic cylinder |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203404164U (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103410810A (en) * | 2013-08-13 | 2013-11-27 | 湖南特力液压有限公司 | Testing device for testing durability of sealing parts of hydraulic cylinder |
| CN105020193A (en) * | 2014-12-28 | 2015-11-04 | 高铁检测仪器（东莞）有限公司 | Oil pressure control system |
| CN105673621A (en) * | 2016-03-01 | 2016-06-15 | 浙江大学 | Multi-working-condition comprehensive simulation test system for reciprocating seal of aviation actuator |
| CN105716963A (en) * | 2016-04-28 | 2016-06-29 | 北京中汽寰宇机动车检验中心有限公司 | Comprehensive testing system for high-temperature pulse of steering power hose of motor vehicle |
| CN106194900A (en) * | 2016-08-30 | 2016-12-07 | 武汉理工大学 | A kind of hydraulic reciprocating seals dynamic property detection device and design |
| CN107132169A (en) * | 2016-02-29 | 2017-09-05 | 江苏金德建筑工程质量检测研究有限公司 | A kind of impervious test system for supporting mobile interchange and cloud platform |
| CN109253130A (en) * | 2018-10-10 | 2019-01-22 | 武汉科技大学 | Reciprocation sealing basic test system and test method |
| CN110296829A (en) * | 2019-07-03 | 2019-10-01 | 清华大学 | A kind of high-voltage high-speed reciprocation sealing experiment test platform |
| CN112555208A (en) * | 2020-12-10 | 2021-03-26 | 重庆大学 | Hydraulic device suitable for ultrahigh pressure precision force loading and step control method |
| CN116025615A (en) * | 2023-03-29 | 2023-04-28 | 山东柏远复合材料科技股份有限公司 | Hydraulic cylinder barrel durability testing device |
| CN117145834A (en) * | 2023-10-23 | 2023-12-01 | 莱州兴达液压机械科技有限公司 | Oil cylinder sealing piece test bed |
-
2013
- 2013-08-13 CN CN201320493686.3U patent/CN203404164U/en not_active Expired - Lifetime
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103410810A (en) * | 2013-08-13 | 2013-11-27 | 湖南特力液压有限公司 | Testing device for testing durability of sealing parts of hydraulic cylinder |
| CN105020193A (en) * | 2014-12-28 | 2015-11-04 | 高铁检测仪器（东莞）有限公司 | Oil pressure control system |
| CN107132169A (en) * | 2016-02-29 | 2017-09-05 | 江苏金德建筑工程质量检测研究有限公司 | A kind of impervious test system for supporting mobile interchange and cloud platform |
| CN105673621A (en) * | 2016-03-01 | 2016-06-15 | 浙江大学 | Multi-working-condition comprehensive simulation test system for reciprocating seal of aviation actuator |
| CN105716963A (en) * | 2016-04-28 | 2016-06-29 | 北京中汽寰宇机动车检验中心有限公司 | Comprehensive testing system for high-temperature pulse of steering power hose of motor vehicle |
| CN105716963B (en) * | 2016-04-28 | 2019-04-12 | 中机寰宇认证检验有限公司 | A kind of motor turning power hose high temperature pulse integrated test system |
| CN106194900B (en) * | 2016-08-30 | 2018-03-16 | 武汉理工大学 | A kind of hydraulic reciprocating sealing dynamic property detection means and design |
| CN106194900A (en) * | 2016-08-30 | 2016-12-07 | 武汉理工大学 | A kind of hydraulic reciprocating seals dynamic property detection device and design |
| CN109253130A (en) * | 2018-10-10 | 2019-01-22 | 武汉科技大学 | Reciprocation sealing basic test system and test method |
| CN109253130B (en) * | 2018-10-10 | 2020-09-11 | 武汉科技大学 | Reciprocating seal foundation test system and test method |
| CN110296829A (en) * | 2019-07-03 | 2019-10-01 | 清华大学 | A kind of high-voltage high-speed reciprocation sealing experiment test platform |
| CN112555208A (en) * | 2020-12-10 | 2021-03-26 | 重庆大学 | Hydraulic device suitable for ultrahigh pressure precision force loading and step control method |
| CN116025615A (en) * | 2023-03-29 | 2023-04-28 | 山东柏远复合材料科技股份有限公司 | Hydraulic cylinder barrel durability testing device |
| CN117145834A (en) * | 2023-10-23 | 2023-12-01 | 莱州兴达液压机械科技有限公司 | Oil cylinder sealing piece test bed |
| CN117145834B (en) * | 2023-10-23 | 2024-01-05 | 莱州兴达液压机械科技有限公司 | Oil cylinder sealing piece test bed |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103410810B (en) | Testing device for testing durability of sealing parts of hydraulic cylinder | |
| CN203404164U (en) | Test equipment for testing durability of sealing element of hydraulic cylinder | |
| CN106194900B (en) | A kind of hydraulic reciprocating sealing dynamic property detection means and design | |
| CN201265573Y (en) | Test bed for hydraulic cylinder | |
| CN101949800B (en) | Pressing-twisting multi-shaft loading testing machine | |
| CN104006034B (en) | Hydraulic servo variable-load loading test bench | |
| CN112556936B (en) | Hydraulic sealing comprehensive experiment table and experiment method | |
| CN103939421B (en) | A kind of method for testing fatigue for hydraulic cylinder and device | |
| CN204783953U (en) | Energy -conserving test device of synthesis of solenoid valve and pneumatic cylinder reliability | |
| CN201475088U (en) | Novel hydraulic test bench | |
| CN104458466A (en) | Friction performance testing device for slipper pair of high-pressure axial plunger pump | |
| CN103352900A (en) | Heavy-duty mining dump vehicle hydraulic oil cylinder/hydraulic valve test table | |
| CN113008718A (en) | Axial plunger pump flow distribution pair test device and method | |
| CN102564860A (en) | Rotating joint durability testing principle and full-automatic testing machine | |
| CN113484014B (en) | Examination test system for dynamic sealing performance of sealing ring | |
| CN105181205A (en) | High-pressure high-speed axial piston pump piston pair four-axis force testing device | |
| CN107063698A (en) | A kind of mechanism for testing, platform and the method for testing of the side-mounted changeable air valve of internal combustion engine | |
| CN105298989A (en) | Fault simulation hydraulic control system for electro-hydraulic servo system | |
| CN115899022B (en) | Internally curved motor stator guide rail-plunger assembly impact load testing device | |
| CN112178009A (en) | Electro-hydraulic actuator performance test experiment table | |
| CN204177693U (en) | High pressure axial plunger pump Slipper coupling friction performance testing device | |
| Bhaumik et al. | Design & development of test rig for investigation of contact mechanics phenomena in reciprocating hydraulic seals | |
| CN103257041B (en) | Cylinder head gasket mechanical fatigue simulation test device and method | |
| CN205280391U (en) | Auto -lock swing hydraulic press performance testing platform | |
| CN214118631U (en) | Novel hydraulic test bed |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term |
Granted publication date: 20140122 |
|
| CX01 | Expiry of patent term |