CN1180233C - Hydraulic energy source equipment - Google Patents
Hydraulic energy source equipment Download PDFInfo
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- CN1180233C CN1180233C CNB021312354A CN02131235A CN1180233C CN 1180233 C CN1180233 C CN 1180233C CN B021312354 A CNB021312354 A CN B021312354A CN 02131235 A CN02131235 A CN 02131235A CN 1180233 C CN1180233 C CN 1180233C
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Abstract
The present invention discloses a hydraulic energy source device which can work under the environment of ultrahigh temperature or lower temperature. The device comprises two sets of high-temperature pump groups which are connected in parallel. Each set comprises a high-temperature jar, an oil inlet one-way valve, a normal-temperature drive jar and an oil outlet one-way valve. Each set of high-temperature pump group completes oil intake and oil discharge by that the normal-temperature drive jar is connected with a proportion reversing valve by a pipeline, the other end of the pipeline which penetrates through the proportion reversing valve is connected with a normal-temperature hydraulic source, and a piston of the high-temperature jar moves following the movement of a piston of the normal-temperature drive jar. The device controls the flux and the pressure of the normal-temperature hydraulic source supplying to the normal-temperature jar by that the opening size of the proportion reversing valve is determined by a computer, and uses a single neuron which is suitable for proportional integral differential control to compensate the dynamic state of a system. By indication of actual measurement of a test, the device reaches the target that output pressure is 28MPa, output flux is 60 L/Min, pressure fluctuation is less than 10%, medium temperature is up to 160 DEG C, and low temperature reaches minus 60 DEG C.
Description
Technical field
The present invention relates to a kind of pump carries out the performance test of hydraulic pressure component under particular job environment device, more particularly being meant a kind of is hydraulic energy source equipment under-60 ℃～160 ℃ the working environment in temperature, belongs to the fluid control technology field.
Background technology
The hydraulic pressure component is widely used in fields such as machinery, traffic, Aero-Space, and its performance quality can directly influence the quality and the performance of entire equipment.For the reliability that guarantees that it is worked under some rugged surroundings, need under particular job environment, carry out performance test to some hydraulic pressure component, therefore need provide this particular job environment and the equipment of testing.As the hydraulic pressure component of aerospace field, require it under high temperature (as up to 160 ℃) or low temperature (as subzero 60 ℃) actuating medium and working environment, stablize with constant hydraulic pressure and hydraulic flow and carry out work.Just need carry out carrying out performance test under corresponding environment and the corresponding medium temperature to these components, to guarantee its reliable operation on ground.
The multicolumn plug rotary pump hydraulic energy source equipment (seeing also shown in Figure 1) of present usefulness, in Fig. 1, its basic structure is: 9 plungers 112 are evenly distributed in the axial hole of rotary cylinder-block 113, and can be free to slide therein, swash plate 108 maintains static with valve plate 117, transmission shaft 114 driven rotary cylinder bodies 113 and plunger 112 rotations, plunger 112 bulbs have piston shoes and abut against on the swash plate 108, during rotary cylinder-block 113 rotations, plunger 112 is reciprocating in the axial hole of rotary cylinder-block 113, because swash plate 108 has the oblique angle, so plunger 112 half cycles are in the oil suction state, in addition half cycle is in the state of buying oil, and it communicates with the low pressure oilhole of valve plate 117 during oil suction, and it communicates with the high pressure oilhole of valve plate 117 and connects the high-pressure output tube road when buying oil.This structure has more pair of friction components, and plunger 112 has pair of friction components with rotary cylinder-block 113 holes, and head piston shoes and swash plate 108 have 9 pair of friction components, and rotary cylinder-block 113 has pair of friction components with valve plate 117.The pair of friction components gap is very little, when can not form oil film, will produce dry friction, even burn, so this pump can not bear superhigh temperature and ultralow temperature operating mode.Because the high speed rotating of plunger, oil viscosity is very little under the high temperature, and oil pump can not to form oil film impaired because of friction vice division chief, and oil viscosity is very big equally at low temperatures, makes plunger suction sky cause the hole.
Summary of the invention
The purpose of this invention is to provide a kind of hydraulic energy source equipment that under-60 ℃～160 ℃ environment, carries out hydraulic pressure component dependable performance property testing, this device greatly reduces the pair of friction components of oil pump, test performance reliability height, and data computation is accurate, easy and simple to handle, simple in structure, with low cost.
Hydraulic energy source equipment of the present invention, the high-temperature pump group of forming by two groups of first high temperature cylinders 1 in parallel, the second high temperature cylinder 201, first in line check valve 2, second in line check valve 202, the first normal temperature driving cylinder 3, the second normal temperature driving cylinder, 203, first fuel-displaced retaining valve 11, the second fuel-displaced retaining valve 211, first proportional reversing valve 4, second proportional reversing valves 204, and normal temperature hydraulic power source 5, test block 6, electrohydraulic controller 7, computing machine 8, oil sump tank 9, oil feeding reservoirs 10, heat exchanger 12, pressure transducer 13, surplus valve 14 formations; Wherein, the control signal electric current that is loaded on first proportional reversing valve 4 and second proportional reversing valve 204 is provided through current controller 7 by computing machine 8 outputs, the current signal of first proportional reversing valve 4 and second proportional reversing valve 204 is triangular wave forms, and its phase differential is 90 degree; Described first in line check valve, 2 one ends are connected on the first high temperature cylinder 1 through pipeline, the other end is connected on the oil feeding reservoirs 10 through pipeline, described first fuel-displaced retaining valve 11 1 ends are connected on the first high temperature cylinder 1 through pipeline, the other end connects by test specimen 6 through pipeline, on heat exchanger 12 and the oil sump tank 9, the described first normal temperature driving cylinder 3 links to each other with normal temperature hydraulic power source 5 with first proportional reversing valve 4 by pipeline, described oil sump tank 9 is communicated with between the oil feeding reservoirs 10 filtration unit being arranged, described computing machine 8 sends command signal, via output current after electrohydraulic controller 7 power amplifications to first proportional reversing valve 4, described surplus valve 14 1 ends are connected in the exit point of system promptly by the front of test specimen 6, the other end is connected on the pipeline of oil sump tank 9, described pressure transducer 13 1 ends are connected in by on test specimen 6 exit points, and the voltage of the other end is exported to the testing pump origin system pressure interface of electrohydraulic controller 7; Described another high-temperature pump group second in line check valve 202 1 ends are connected on the second high temperature cylinder 201 through pipeline, the other end is connected on the oil feeding reservoirs 10 through pipeline, second fuel-displaced retaining valve 211 1 ends are connected on the second high temperature cylinder 201 through pipeline, the other end is on pipeline connects by test specimen 6, heat exchanger 12 and oil sump tank 9, and the second normal temperature driving cylinder 203 links to each other with normal temperature hydraulic power source 5 with second proportional reversing valve 204 by pipeline.
Described hydraulic energy source equipment, the medium temperature of this device are-60 ℃～160 ℃, and high temperature can reach 160 ℃, and low temperature can reach-60.
Described hydraulic energy source equipment, its computing machine 8 adopts single neuron adaptive PID control method, utilize neurogenic weights to change, come dynamic compensation is done by system from change three scale-up factors of PID suitablely, designed suitable certainly dynamic compensation control program, the dead band characteristic of first proportional reversing valve 4 and second proportional reversing valve 204 has been carried out dynamic compensation.
Described hydraulic energy source equipment, the normal temperature actuating medium circulates in the pipeline between the first normal temperature driving cylinder 3 and the second normal temperature driving cylinder, 203 normal temperature hydraulic power sources and the fuel tank all the time, and the hot operation medium circulates in high temperature piston pump, pipeline and high temperature fuel tank all the time, has realized the isolation of normal temperature medium and high-temperature medium.
Described hydraulic energy source equipment, the delivery rate waveform of pump has the waveform identical with control signal, and the resultant flow of twin-tub output can be coordinated control by computing machine 8.
Described hydraulic energy source equipment, output pressure are 28Mpa, and delivery rate is 60L/Min, and pressure fluctuation is＜10%.
Described hydraulic energy source equipment, the O-ring seal that uses in the first high temperature cylinder and the second high temperature cylinder is resistant to elevated temperatures fluoroplastic rubber seal.
The present invention compares with multicolumn plug rotary pump, not only friction pair significantly reduces, and enlarge markedly because of size, volume and the friction pair contact area of the used pump of the present invention, the pumping source movement velocity reduces greatly, so help high temperature resistant, reduce the friction that oil viscosity causes, prolonged mission life.This invention is simple in structure, helps safeguarding and maintenance that cost is low.Add and adopt computing machine to compensate and control, eliminated the output pressure pulsation that dead band because of commutation, proportioning valve, dynamic deferred and leakage etc. cause, guaranteed the constant of output pressure.
Description of drawings
Fig. 1 is the principle assumption diagram of multicolumn plug rotary pump.
Fig. 2 is a structured flowchart of the present invention.
Fig. 3 (a) and (b) are that the phase differential that is added on the proportional reversing valve of the present invention is that 90 marking currents of spending are schemed over time.
Fig. 4 (a) and (b) are that two pump group delivery rates of the present invention are schemed over time.
Fig. 5 is the measured curve figure of the system's output pressure after the compensation of the present invention.
Fig. 6 is the measured curve figure of the system's output pressure before the compensation of the present invention.
Among the figure: 1. the first high temperature cylinder, 2. first in line check valves, 3. first normal temperature driving cylinders, 4. first proportional reversing valves, 5. normal temperature hydraulic power sources 6. are by test specimen 7. electrohydraulic controllers 8. computers 9. oil sump tanks 10. oil feeding reservoirs 11. first oil outlet one-way valves 12. heat exchangers 13. pressure sensors 14. overflow valves 201. second high temperature cylinders 202. second in line check valves 203. second normal temperature driving cylinders 204. second proportional reversing valves 211. second oil outlet one-way valves
Specific embodiment
The present invention is described in further detail below in conjunction with accompanying drawing.
In Fig. 2, the high-temperature pump group of top is by the first high temperature cylinder 1, first in line check valve 2 of two parallel connections, the first fuel-displaced retaining valve 11 of two parallel connections and the first normal temperature driving cylinder 3 are formed, described two first in line check valves 2 that link to each other with the first high temperature cylinder 1 are connected on the oil feeding reservoirs 10 through pipeline, described two first fuel-displaced retaining valves 11 that link to each other with the first high temperature cylinder 1 are connected on the oil sump tank 9 through output channel, on this pipeline, be provided with by test specimen 6, the measuring point of pressure transducer 13, the contact of surplus valve 14, the O-ring seal that uses in the described first high temperature cylinder 1 are with the special high-temperature resistant rubber system of fluoroplastic; The described first normal temperature driving cylinder 3 links to each other with first proportional reversing valve 4 by pipeline, and the other end of first proportional reversing valve 4 links to each other with normal temperature hydraulic power source 5 by pipeline again.When computing machine 8 is exported control signals when the power electric current of electrohydraulic controller 7 amplifications is loaded on first proportional reversing valve 4, first proportional reversing valve 4 is opened, 5 of normal temperature hydraulic power sources are pressed into hydraulic oil in the first normal temperature driving cylinder 3, thereby make the piston motion of the first normal temperature driving cylinder 3 and promote the piston motion of the first high temperature cylinder 1, such as, left, this moment, first in line check valve 2 was opened, and oil is inhaled into the right-hand member of the first high temperature cylinder 1 from oil feeding reservoirs 10; When the first normal temperature driving cylinder 3 with the first high temperature cylinder 1 pull to reverse direction promptly to the right the time the first fuel-displaced retaining valve 11 of the first high temperature cylinder, 1 bottom open, the first high temperature cylinder 1 is squeezed into connection by the output channel of test specimen 6 with the fluid in it by the first fuel-displaced retaining valve 11, and fluid is by being turned back to oil sump tank 9 behind the test specimen 6.Equally, the high-temperature pump group of described bottom is by the second high temperature cylinder 201, second in line check valve 202 of two parallel connections, the second fuel-displaced retaining valve 211 of two parallel connections and the second normal temperature driving cylinder 203 are formed, meanwhile, when marking current is loaded on second proportional reversing valve 204, second proportional reversing valve 204 is opened, normal temperature hydraulic power source 5 is pressed into hydraulic oil in the second normal temperature driving cylinder 203, thereby make the piston motion in the second normal temperature driving cylinder 203, promote the piston motion of the second high temperature cylinder 201 simultaneously, this moment, fluid entered in the second high temperature cylinder 201 from second in line check valve 202, then the second high temperature cylinder 201 retracts along with returning of the second normal temperature driving cylinder 203, then the fluid in the second high temperature cylinder 201 enters and the output channel that is linked to each other by test specimen 6 by the second fuel-displaced retaining valve 211, constant pressure hydraulic oil with last group of fluid stack formation test specimen 6 needed high temperature or low temperature, by being got back to oil sump tank 9 by the fluid of test specimen 6, in fact oil sump tank 9 is communicated with through filtration unit with oil feeding reservoirs 10.The signal that loads on first proportional reversing valve 4 and second proportional reversing valve 204 is the form of triangular wave, and first proportional reversing valve 4 is 90 degree with phasic difference mutually on second proportional reversing valve 204.
Circulate in the pipeline of normal temperature actuating medium between the first normal temperature driving cylinder 3 and the second normal temperature driving cylinder 203 and normal temperature hydraulic power source 5 in the present invention, and the hot operation medium circulates in the first high temperature cylinder 1 and the second high temperature cylinder 201 and pipeline and high temperature fuel tank, like this, realized the isolation of normal temperature actuating medium and hot operation medium by normal temperature driving cylinder and high temperature piston pump.Normal temperature hydraulic power source 5 provides power as the work pumping source of reality, drive the high-temperature pump group and realize reciprocating action, the first normal temperature driving cylinder 3, the second normal temperature driving cylinder 203 and the first high temperature cylinder 1, the second high temperature cylinder 201 that becomes one of therefore connecting mechanically just becomes genuine isolated hydraulic pump.
Why adopting two groups of hydraulic isolation cylinders in parallel at pump source system of the present invention, is because the pump source system of single group hydraulic cylinder can produce bigger pressure fluctuation.
Further specifying the present invention below is how to solve the pulsation of output pressure and eliminate commutation, proportional reversing valve dead band, dynamic deferred and leakage contribution.
The coordination control of computing machine:
The pressure substantially constant of physical shock when high-temperature pump group piston rod commutates and the output of maintenance system, we adopt the measure-alike high-temperature pump group of two nested structures to compose in parallel the high temperature pumping source as mentioned above, as shown in Figure 2.Current input signal i is loaded into respectively on separately first proportional reversing valve 4 and second proportional reversing valve 204 with the form of triangular wave, realizes adjusting to high-temperature pump group movement velocity by the aperture of regulating first proportional reversing valve 4 and second proportional reversing valve 204.Rational phase differential is promptly 90 ° if the triangular wave input signal of two high-temperature pump groups can have certain, the big physical shock that in the time of then not only can eliminating the commutation of pump group piston rod the high-temperature pump group is produced, compression shock that produces in the time of also can eliminating the piston rod commutation and the pressure fluctuation situation that makes pump source system obtain weakening, and have improved the serviceability and the mission life of pump source system well.With preferable situation is example, and the period T of triangular wave and amplitude A can be determined by the stroke cycle parameter of tested pressurized strut and the rating curve of proportioning valve.The waveform of the input control signal of proportional reversing valve as shown in Figure 3.For electro-hydraulic proportional valve, in certain pressure differential range, fluid flow and the proportional relation of control signal by first proportional reversing valve 4 and second proportional reversing valve, 204 restrictions, if therefore first proportional reversing valve 4 and second proportional reversing valve 204 are input as triangular wave, the variation that then flows into the flow of high-temperature pump group first normal temperature driving cylinder 3 and the second normal temperature driving cylinder, 203 fluid also should be the triangular wave form.Do not consider the situation such as compression, leakage of fluid, then according to the flow equation of hydraulic cylinder
Q＝AV
In the formula, A is the useful area in hydraulic cylinder works chamber, so the movement velocity V of hydraulic cylinder piston rod and fluid flow Q are proportional, finally the fluid flow of each high-temperature pump group discharge all is the triangular wave that is proportionate relationship with input control signal.And the waveform of the delivery rate of two pump groups has the phase differential identical with the control signal waveform.At this moment the rule of flow separately of two high-temperature pump groups as shown in Figure 4.The total delivery rate Q of the pump source system of double pump group is by Q
1, Q
2Stack, as seen from the figure: Q
1, Q
2After the stack, can make system's total flow keep the weighing apparatus definite value.Like this, the pressure fluctuation that is caused by the high-temperature pump group in theory just has been eliminated.Here computing machine coordination control is crux, if the triangular wave waveform input signal and the phase coordination of two high-temperature pump groups are bad, output pressure will have than great fluctuation process.
The dead area compensation of proportional reversing valve:
As shown in Figure 4, Q
1, Q
2Stack, when phase phasic difference 90 is spent, can obtain the flow output of constant in theory, but in actual pump source system various non-ideal conditions may appear, as nonlinear characteristics such as the dead band of the compressibility of fluid, leakage, proportioning valve and system dynamics etc., these can both cause the pulsation of system output stream amount and pressure.
Influence in numerous non-linear factors of system's output pressure, having the greatest impact of proportional reversing valve dead band characteristic weakens the proportioning valve dead band will be improved system effectively to the influence of system's output pressure output characteristics.
Can carry out static compensation to the dead band according to the size in proportional reversing valve dead band, fairly simple, it is effective that the response time is not had the system of high requirement.If but the command signal frequency is higher, when particularly requiring system's output that the instruction input is realized that the some point is followed, because the proportioning valve dead band is bigger usually, the frequency range of valve is lower again, make valve need the long period by the dead band, therefore for speed control, when changing direction of motion, will make system produce bigger tracking error.In addition, when the output pressure of valve and flow changed, the dead band value of valve also changed.Therefore, the static compensation in employing proportioning valve dead band can not be applicable to the situation of high precision and high response speed.The present invention adopts proportioning valve dead band dynamic compensation, according to system's input difference signal e and dead area compensation signal U of difference rate of change signal delta e output with output, is by the online definite variation dead area compensation value of computing machine promptly.Computing machine has been stored the fine compensation value that obtains under the different operating modes automatically, can directly call the dead area compensation value of storage when meeting identical operating mode next time.
Computer control:
This system requirements realizes that to the instruction triangular wave point point follows, but because the parameter of system dynamics and two hydraulic cylinders, proportioning valve and friction etc. can not be identical, thereby movement velocity can not be just the same.Need consider certain control strategy for this reason, improve the output performance of system.
Experimental result shows, simple PID (Proportional Integral Differential) control, i.e. and ratio, integration, differential control all has certain effect to system dynamics compensation, precision.But system itself has non-linear and time variation, and output characteristics is not very good.The advantage of the existing neural network of single adaptive neuron, can adapt to the requirement of control in real time of quick process again, network structure is also simple, so the present invention adopts single neuron adaptive PID control strategy, utilize neuronic weights to change, from change three scale-up factors of PID suitablely, obtained desirable output pressure characteristic.
The measured curve of the system's output pressure before Fig. 5, Fig. 6 illustrate the compensation back respectively and compensate, compensation back pressure surge meets the hydraulic energy source technical standard less than 8%.
Model machine of the present invention has carried out comprehensive test, and the pressure surge of output meets the GB requirement, and this equipment successfully is used for the performance test of the hydraulic unit ultralow temperature-60 ℃ of certain model aircraft to the component of 150 ℃ of high temperature.
Device of the present invention is easy to operate, simple in structure, with low cost.
Claims (3)
1, a kind of hydraulic energy source equipment, comprise two groups of first high temperature cylinders (1) in parallel, the second high temperature cylinder (201), first in line check valve (2), second in line check valve (202), the first normal temperature driving cylinder (3), the second normal temperature driving cylinder (203), the first fuel-displaced retaining valve (11), the second fuel-displaced retaining valve (211), first proportional reversing valve (4), the high-temperature pump group that second proportional reversing valve (204) is formed, and normal temperature hydraulic power source (5), by test specimen (6), electrohydraulic controller (7), computing machine (8), oil sump tank (9), oil feeding reservoirs (10), heat exchanger (12), pressure transducer (13), surplus valve (14), wherein, the control signal electric current that is loaded on first proportional reversing valve (4) and second proportional reversing valve (204) is provided through current controller (7) by computing machine (8) output, the current signal of first proportional reversing valve (4) and second proportional reversing valve (204) is the triangular wave form, its phase differential is 90 degree, it is characterized in that: described first in line check valve (2) one ends are connected on the first high temperature cylinder (1) through pipeline, and the other end is connected on the oil feeding reservoirs (10) through pipeline; Described first fuel-displaced retaining valve (11) one ends are connected on the first high temperature cylinder (1) through pipeline, and the other end is on pipeline connects by test specimen (6), heat exchanger (12) and oil sump tank (9); The described first normal temperature driving cylinder (3) links to each other with normal temperature hydraulic power source (5) with first proportional reversing valve (4) by pipeline; Between the same oil feeding reservoirs of described oil sump tank (9) (10) filtration unit is arranged and be communicated with; Described computing machine (8) sends command signal, via output current after electrohydraulic controller (7) power amplification on first proportional reversing valve (4) and second proportional reversing valve (204); The exit point that described surplus valve (14) one ends are connected in system is promptly by the front of test specimen (6), and the other end is connected on the pipeline of oil sump tank (9); Described pressure transducer (13) one ends are connected in by on test specimen (6) exit point, and the voltage of the other end is exported to the testing pump origin system pressure interface of electrohydraulic controller (7); Described another high-temperature pump group second in line check valve (202) one ends are connected on the second high temperature cylinder (201) through pipeline, the other end is connected on the oil feeding reservoirs (10) through pipeline, second fuel-displaced retaining valve (211) one ends are connected on the second high temperature cylinder (201) through pipeline, the other end is on pipeline connects by test specimen (6), heat exchanger (12) and oil sump tank (9), and the second normal temperature driving cylinder (203) links to each other with normal temperature hydraulic power source (5) with second proportional reversing valve (204) by pipeline; Described computing machine (8) adopts single neuron adaptive PID control method, utilize neurogenic weights to change, come dynamic compensation is done by system from change three scale-up factors of PID suitablely, designed suitable certainly dynamic compensation control program, the dead band characteristic of first proportional reversing valve (4) and second proportional reversing valve (204) has been carried out dynamic compensation; The medium temperature of described device is-60 ℃～160 ℃.
2, hydraulic energy source equipment according to claim 1 is characterized in that: this device output pressure is 28Mpa, and delivery rate is 60L/Min, and pressure fluctuation is＜10%.
3, hydraulic energy source equipment according to claim 1 is characterized in that: the O-ring seal that uses in the first high temperature cylinder (1) and the second high temperature cylinder (201) is resistant to elevated temperatures fluoroplastic rubber seal.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB021312354A CN1180233C (en) | 2002-09-19 | 2002-09-19 | Hydraulic energy source equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB021312354A CN1180233C (en) | 2002-09-19 | 2002-09-19 | Hydraulic energy source equipment |
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| CN1400455A CN1400455A (en) | 2003-03-05 |
| CN1180233C true CN1180233C (en) | 2004-12-15 |
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| CNB021312354A Expired - Fee Related CN1180233C (en) | 2002-09-19 | 2002-09-19 | Hydraulic energy source equipment |
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Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101915666A (en) * | 2010-07-07 | 2010-12-15 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Test method and system for reliability of swing mechanism based on power recovery technology |
| CN102129247B (en) * | 2010-12-23 | 2012-09-26 | 重庆角羽科技有限公司 | Comprehensive detection method and detection system for automotive hydraulic automatic transmission control assembly |
| CN102169053B (en) * | 2010-12-24 | 2012-07-25 | 重庆青山工业有限责任公司 | Hydraulic control loop of high/low-temperature test bed for automatic transmission valve |
| DE102012005224A1 (en) * | 2012-03-15 | 2013-09-19 | Festo Ag & Co. Kg | Fluid system and method of operating a fluid system |
| CN103364028B (en) * | 2012-03-29 | 2015-12-09 | 北汽福田汽车股份有限公司 | For the data acquisition system (DAS) of dump truck hydraulic lifting |
| CN104632785A (en) * | 2014-12-04 | 2015-05-20 | 黑龙江大学 | Hydraulic testing system based on computer intelligent control and testing method thereof |
| CN105718696B (en) * | 2016-02-02 | 2019-07-05 | 成都欧迅科技股份有限公司 | A kind of deep-sea production tree electrichydraulic control valve group list electricity low pressure reversing valve designs method |
| CN107882790A (en) * | 2017-11-10 | 2018-04-06 | 中航飞机起落架有限责任公司 | A kind of isolated high/low temperature hydraulic system and its control method |
| CN110259743B (en) * | 2019-06-24 | 2021-02-19 | 绍兴文理学院 | Hydraulic cylinder independent control system of rock triaxial creep testing machine |
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