CN108005993B - Electrohydraulic actuator for gas flow regulating system of reciprocating compressor - Google Patents
Electrohydraulic actuator for gas flow regulating system of reciprocating compressor Download PDFInfo
- Publication number
- CN108005993B CN108005993B CN201711172945.1A CN201711172945A CN108005993B CN 108005993 B CN108005993 B CN 108005993B CN 201711172945 A CN201711172945 A CN 201711172945A CN 108005993 B CN108005993 B CN 108005993B
- Authority
- CN
- China
- Prior art keywords
- sealing
- nitrogen
- oil
- cylinder body
- ring
- 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.)
- Active
Links
- 230000001105 regulatory effect Effects 0.000 title claims description 8
- 238000007789 sealing Methods 0.000 claims abstract description 199
- 239000007789 gas Substances 0.000 claims abstract description 19
- 238000000034 method Methods 0.000 claims abstract description 11
- 230000008569 process Effects 0.000 claims abstract description 11
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 164
- 229910052757 nitrogen Inorganic materials 0.000 claims description 85
- 230000003068 static effect Effects 0.000 claims description 16
- 230000009471 action Effects 0.000 claims description 8
- 229920000049 Carbon (fiber) Polymers 0.000 claims description 3
- 229910000831 Steel Inorganic materials 0.000 claims description 3
- 230000004888 barrier function Effects 0.000 claims description 3
- 239000004917 carbon fiber Substances 0.000 claims description 3
- VNTLIPZTSJSULJ-UHFFFAOYSA-N chromium molybdenum Chemical compound [Cr].[Mo] VNTLIPZTSJSULJ-UHFFFAOYSA-N 0.000 claims description 3
- QJGQUHMNIGDVPM-UHFFFAOYSA-N nitrogen group Chemical group [N] QJGQUHMNIGDVPM-UHFFFAOYSA-N 0.000 claims description 3
- -1 polytetrafluoroethylene Polymers 0.000 claims description 3
- 229920001343 polytetrafluoroethylene Polymers 0.000 claims description 3
- 239000004810 polytetrafluoroethylene Substances 0.000 claims description 3
- 239000010959 steel Substances 0.000 claims description 3
- 238000007790 scraping Methods 0.000 claims description 2
- 239000010720 hydraulic oil Substances 0.000 abstract description 5
- 230000002457 bidirectional effect Effects 0.000 abstract description 4
- 230000007246 mechanism Effects 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 72
- 238000013461 design Methods 0.000 description 6
- 230000004044 response Effects 0.000 description 6
- 239000012530 fluid Substances 0.000 description 4
- 238000003780 insertion Methods 0.000 description 3
- 230000037431 insertion Effects 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- RWSOTUBLDIXVET-UHFFFAOYSA-N Dihydrogen sulfide Chemical compound S RWSOTUBLDIXVET-UHFFFAOYSA-N 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 239000010727 cylinder oil Substances 0.000 description 1
- 230000008021 deposition Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 229910001873 dinitrogen Inorganic materials 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000002360 explosive Substances 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 125000004435 hydrogen atom Chemical class [H]* 0.000 description 1
- 229910000037 hydrogen sulfide Inorganic materials 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 231100000572 poisoning Toxicity 0.000 description 1
- 230000000607 poisoning effect Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 239000004576 sand Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 231100000331 toxic Toxicity 0.000 description 1
- 230000002588 toxic effect Effects 0.000 description 1
- 239000002341 toxic gas Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1414—Characterised by the construction of the motor unit of the straight-cylinder type with non-rotatable piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B51/00—Testing machines, pumps, or pumping installations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1457—Piston rods
- F15B15/1461—Piston rod sealings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1471—Guiding means other than in the end cap
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/202—Externally-operated valves mounted in or on the actuator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Compressor (AREA)
- Sealing Devices (AREA)
Abstract
The invention relates to the technical field of compressor air quantity regulation, and particularly discloses an electro-hydraulic actuating mechanism for a reciprocating compressor air quantity regulation system. The device has good sealing performance, can realize the bidirectional sealing of hydraulic oil and process media in the compressor cylinder, has no external leakage, and can effectively isolate dangerous gases in the compressor cylinder.
Description
Technical Field
The invention belongs to the technical field of compressor air quantity adjustment, and particularly relates to an electrohydraulic actuator for a reciprocating compressor air quantity adjustment system.
Background
The stepless air volume regulating system for the reciprocating compressor consists of a hydraulic system, an electrohydraulic actuator and a control system. The electrohydraulic actuator receives control system signals, and controls the opening and closing time of the air inlet valve of the compressor through hydraulic transmission, so that stepless regulation of the air quantity of the compressor in a certain range is realized, and the quality of the dynamic performance of the electrohydraulic actuator greatly influences the air quantity regulation of the compressor, thereby influencing the energy consumption of the compressor.
The requirements of the current reciprocating compressor air quantity stepless regulating system on the electrohydraulic actuator mainly comprise the following points: 1) Fast response characteristics: in a stepless compressor air flow regulating system, a high-speed electrohydraulic actuator is required to drive an air inlet valve unloader to act at a specific moment so as to open or close an air inlet valve plate. Generally, when the main shaft rotation speed r=300 r/min of the compressor is adopted, the reciprocating working period t=200 ms of the piston of the compressor is adopted, wherein the compression stroke duration of the piston is about T/2=100 ms, and from the viewpoint of real-time control, in order to enable the valve plate of the air valve to be opened and closed in time so as to realize stepless regulation of the discharge capacity of the compressor, the response time of the electro-hydraulic actuator must be limited within 20 ms; 2) High reliability and long life characteristics: in the normal maintenance period of the compressor, the host needs to continuously run, and in the normal case, the annual average fault-free running time of the compressor is 8000h, taking a reciprocating piston compressor with the rotating speed of 300r/min as an example, the annual average switching times of the high-speed electrohydraulic actuator is about 1.45 hundred million times, and the parameters are very great challenges to the service life and the reliability of the electrohydraulic actuator; 3) High-pressure gas-liquid two-phase sealing: the high-speed electrohydraulic actuator for the large reciprocating compressor has very severe sealing performance requirement, and firstly has high sealing requirement, because the process medium of the reciprocating compressor is usually flammable and explosive gas such as hydrogen, methane and the like or highly toxic gas such as hydrogen sulfide and the like, after the gas-liquid two-phase sealing part leaks, the oil in the actuator leaks and is brought into a compressor cylinder, and hydraulic oil is subjected to chemical change in the high-temperature and high-pressure environment in the cylinder, so that carbon deposition is generated at the air valve of the compressor, and the normal operation of the compressor is endangered. Meanwhile, the gas in the cylinder can also reversely flow into the actuator, under the toxic working condition, the process medium can enter the oil tank of the hydraulic system along with the hydraulic oil, and the space of the oil tank is communicated with the atmosphere, so that the process medium can be directly leaked to the outside, and poisoning accidents can be caused after the process medium is inhaled by a human body. And secondly, the medium pressure is high, the normal pressure of hydraulic oil is 10MPa, and the pressure of a compressor process medium is up to 15MPa. Finally, the service life of the sealing surface is high, and the high-frequency long-time running condition brings high requirements to the wear resistance of the sealing auxiliary sealing surface and the sealing piece.
In order to solve the above problems, it is needed to design an electrohydraulic actuator with high response and high reliability, which can meet the use requirement of an adjusting system under the working condition of high frequency and high pressure.
Disclosure of Invention
The invention aims to provide an electrohydraulic actuator for a reciprocating compressor air quantity adjusting system, which is used for realizing stepless adjustment of the compressor air quantity under the working condition of high frequency and high pressure.
The technical scheme of the invention is as follows:
an electrohydraulic actuator is used for a gas quantity regulating system of a reciprocating compressor and comprises an electromagnetic valve, a hydraulic cylinder, a nitrogen sealing device and a temperature sensor;
the electromagnetic valve is arranged above the hydraulic cylinder and is fixedly connected with the hydraulic cylinder through four fastening screws;
the electromagnetic valve is provided with a port A, a port P and a port T;
the hydraulic cylinder comprises an upper cylinder body, a lower cylinder body, a piston sleeve, a piston rod, a hydraulic rod, a first sealing guide support, a second sealing guide support, a third sealing guide support and an oil scraper ring support;
the upper cylinder body is arranged above the lower cylinder body, and the upper cylinder body and the lower cylinder body are fixedly connected through an inner hexagonal cylindrical head screw;
a rodless cavity A and a rod cavity B are arranged in the upper cylinder body, and the rodless cavity A and the rod cavity B are coaxial;
the upper end surface of the upper cylinder body is provided with a working oil port which is communicated with the through port A and the rodless cavity A;
an oil inlet and an oil outlet are arranged on the side surface of the upper cylinder body, wherein the oil inlet is communicated with the through hole P, and the oil outlet is communicated with the through hole T;
an inserting through hole is axially formed in the upper cylinder body and the lower cylinder body, and a threaded inserting type temperature sensor is arranged in the inserting through hole;
the piston is sleeved in the rodless cavity A and is connected with the upper cylinder body through threads;
one end of the piston rod is arranged in the piston sleeve, a gap exists between the piston rod and the piston sleeve, and the other end of the piston rod is positioned in the rod cavity B;
an annular balance groove is formed in the outer side of the piston rod, vortex is formed in the groove when oil flows through the balance groove, so that the oil is converted from a laminar state to a turbulent mixing state, and a resistance barrier is formed;
an oil drain port and a gas drain port are arranged on the side surface of the lower cylinder body, and the oil drain port can guide the leakage oil at the sealing position of the piston gap back to the oil tank;
an annular sealing cavity C is arranged in the sealing guide support II and is communicated with the air leakage port;
a first sealing guide support, a second sealing guide support and a third sealing guide support are sequentially arranged in the lower cylinder body from top to bottom, and three radial static seals are respectively formed between the first sealing guide support, the second sealing guide support and the inner wall of the lower cylinder body through three O-shaped rings II;
the sealing guide support I, the sealing guide support II and the sealing guide support III are hollow cylinder shapes and are coaxial;
the inner wall of the sealing guide support I is provided with a groove I and a guide groove I, the combined sealing ring I is arranged in the groove I, and the guide belt I is arranged in the guide groove I;
a groove II and a groove III are formed in the inner wall of the sealing guide support II, the combined sealing ring II is arranged in the groove II, and the combined sealing ring III is arranged in the groove III;
a groove IV and a guide groove II are arranged on the inner wall of the sealing guide support III, the combined sealing ring IV is arranged in the groove IV, and the guide belt II is arranged in the guide groove II;
the side wall of the sealing guide support II is provided with an air leakage hole which is communicated with the air leakage hole on the side surface of the lower cylinder body;
the oil scraper ring is supported at the outlet of the lower part of the lower cylinder body and is connected with the lower cylinder body through threads;
the nitrogen seal device is arranged below the lower cylinder body and comprises a nitrogen seal oil scraper ring support, a nitrogen seal device connecting frame and a nitrogen seal guide support;
the nitrogen seal oil scraper ring support, the nitrogen seal device connecting frame and the nitrogen seal guide support are hollow structures and are coaxial;
an O-shaped ring IV is arranged between the nitrogen sealing device connecting frame and the lower cylinder body, the nitrogen sealing device connecting frame is fixedly connected with the lower cylinder body through a fastening screw, the O-shaped ring IV is compressed to form an axial static seal, and an air cavity D is arranged in the nitrogen sealing device connecting frame;
the nitrogen seal oil scraper ring is supported below the nitrogen seal device connecting frame and is connected with the nitrogen seal oil scraper ring through threads;
the nitrogen seal sealing guide support is arranged in the nitrogen seal device connecting frame;
one end of the hydraulic rod is positioned in the rod cavity B, is contacted with one end of the piston rod, and the other end of the hydraulic rod passes through the first sealing guide support, the first sealing cavity C, the second sealing guide support, the third sealing guide support, the oil scraper ring support, the nitrogen sealing device connecting frame, the nitrogen sealing guide support and the nitrogen sealing oil scraper ring support and then is positioned below the nitrogen sealing device;
the first combined sealing ring, the second combined sealing ring, the third combined sealing ring, the fourth combined sealing ring, the fifth combined sealing ring, the sixth combined sealing ring, the seventh combined sealing ring and the eighth combined sealing ring are composed of O-shaped rings and slip rings.
An O-shaped ring I is arranged at the joint of the upper cylinder body and the lower cylinder body, so that axial static seal is realized, and leakage of oil in the rod cavity B is prevented.
And a high-pressure sealing ring is arranged at the joint of the piston sleeve and the upper cylinder body to form static seal.
And an O-shaped ring III is arranged at the joint of the nitrogen seal sealing guide support and the nitrogen seal device connecting frame to form static seal.
A combined sealing ring V is arranged at the matching position of the oil scraper ring support and the hydraulic rod, and a combined sealing ring V is arranged at the matching position of the nitrogen-sealed oil scraper ring support and the hydraulic rod.
And a combined sealing ring six, a combined sealing ring seven 33, a guiding belt three and a guiding belt four are arranged at the joint of the nitrogen seal guiding support and the hydraulic rod and are used for separating nitrogen in the air cavity D from a process medium in the cylinder of the reciprocating compressor.
And an inflation inlet is arranged on the side wall of the nitrogen sealing device connecting frame and is used for inflating nitrogen with certain pressure into the air cavity D.
The piston rod and the piston sleeve are made of chromium-molybdenum steel, and have hardness difference.
The slip ring is made of polytetrafluoroethylene containing carbon fibers.
When the inside of the electromagnetic valve is switched to the P-A passage, oil enters from the oil inlet, flows through the P-A passage of the electromagnetic valve, flows into the rodless cavity A from the working oil port, drives the piston rod and the hydraulic rod to overcome the external load force at the rod end, and completes the opening action;
when the inside of the electromagnetic valve is switched to the A-T passage, under the action of load counter force, the piston rod and the hydraulic rod linearly move in the opposite direction and reset, and oil in the rodless cavity A flows through the A-T passage of the electromagnetic valve from the working oil port and returns to the oil tank from the oil outlet.
The invention has the remarkable effects that:
according to the electrohydraulic actuator, in the sealing structure design, the hydraulic cylinder adopts the sealing structure of the multiple slip ring type combined sealing ring and the additional guide ring, so that the electrohydraulic actuator has the advantages of small friction coefficient, wear resistance and good sealing performance, and can realize bidirectional sealing of hydraulic oil and process media in the cylinder of the compressor without external leakage. On the basis of the sealing structure, the nitrogen sealing device is designed, so that dangerous gas in the compressor cylinder can be effectively isolated. The sealing ring is not used at the sealing position of the piston of the hydraulic cylinder, and the sealing is realized through a tiny gap between the matching surfaces, so that the friction resistance of the oil cylinder is greatly reduced, the mutual abrasion among parts is avoided, and the response frequency, the dynamic friction force and other dynamic characteristics of the hydraulic cylinder are greatly improved, and the service life of the hydraulic cylinder is greatly prolonged. On overall structure design, the hydraulic cylinder piston adopts split type design, and the part dismouting is more convenient, has improved the centering of piston simultaneously. The actuating mechanism adopts unique solenoid valve and pneumatic cylinder integral type design, need not connecting tube, and the installation is simple, and overall structure overall arrangement is compacter, and is difficult for leaking, simultaneously, has improved system response speed. In addition, through the temperature sensor who installs in the pneumatic cylinder, still can real-time supervision compressor cylinder internal gas temperature, avoid nitrogen sealing device and hydraulic rod end department's sealing washer to produce inefficacy because of the high temperature, guaranteed seal structure's reliability. The test proves that the opening and closing time of the hydraulic cylinder is less than 15ms, the continuous operation of not less than 8000 hours in one year can be satisfied, and the work is stable.
Drawings
FIG. 1 is a schematic left side view of an electro-hydraulic actuator;
FIG. 2 is a right side schematic view of an electro-hydraulic actuator;
FIG. 3 is a schematic diagram of a hydraulic cylinder;
FIG. 4 is a schematic view of a lower cylinder seal structure of a hydraulic cylinder;
fig. 5 is an enlarged schematic view of the structure at I in fig. 4.
In the figure: 1-an electromagnetic valve; 2-a hydraulic cylinder; 3-nitrogen sealing device; 4-a temperature sensor; 5-an upper cylinder; 6-a lower cylinder; 7-a piston sleeve; 8-a piston rod; 9-a hydraulic rod; 10-sealing guide support I; 11-sealing guide support II; 12-sealing guide support III; 13-oil scraper ring support; 14-oil inlet; 15, a working oil port; 16-an oil outlet; 17-an oil drain port; 18-hexagon socket head cap screw; 19-fastening a screw; 20-a high-pressure sealing ring; 21-O-ring I; a second 22-O-shaped ring; a 23-O-ring; 24-slip rings; 25-a first guide belt; 26-a combined sealing ring I; 27-a second combined sealing ring; 28-a combined sealing ring III; 29-a combined sealing ring IV; 30-combining a sealing ring V; 31-a second guide belt; 32-a combined sealing ring six; 33-a combined sealing ring seven; 34-a third guide belt; 35-a guide belt IV; 36-a gas leakage port; 37-combined sealing ring eight; 38-nitrogen seal oil scraper ring support; 39-nitrogen sealing device connection frame; 40-nitrogen seal sealing guide support; 41-an inflation inlet; 42-O-shaped ring III; and a 43-O-shaped ring IV.
Detailed Description
The invention will be described in further detail with reference to the accompanying drawings and specific examples.
An electro-hydraulic actuator for a gas amount regulating system of a reciprocating compressor as shown in fig. 1 and 2 comprises an electromagnetic valve 1, a hydraulic cylinder 2, a nitrogen sealing device 3 and a temperature sensor 4.
The electromagnetic valve 1 is arranged above the hydraulic cylinder 2 and is fixedly connected with the hydraulic cylinder 2 through four fastening screws 19. The solenoid valve 1 is provided with a port a, a port P and a port T. The solenoid valve 1 can be selected from various commercial products meeting the requirements of the invention.
As shown in fig. 3, the hydraulic cylinder 2 includes an upper cylinder body 5, a lower cylinder body 6, a piston sleeve 7, a piston rod 8, a hydraulic rod 9, a seal guide support one 10, a seal guide support two 11, a seal guide support three 12 and a scraper ring support 13.
The upper cylinder body 5 is arranged above the lower cylinder body 6, and the upper cylinder body and the lower cylinder body are fixedly connected through an inner hexagonal cylindrical head screw 18. A rodless cavity A and a rod-containing cavity B are arranged in the upper cylinder body 5, and the rodless cavity A and the rod-containing cavity B are coaxial. An O-shaped ring I21 is arranged at the joint of the upper cylinder body 5 and the lower cylinder body 6, so that axial static seal is realized, and the leakage of oil in the rod cavity B is prevented.
An oil port 15 is arranged on the upper end surface of the upper cylinder body 5 and is communicated with the through port A and the rodless cavity A. An oil inlet 14 and an oil outlet 16 are arranged on the side face of the upper cylinder body 5, wherein the oil inlet 14 is communicated with the through hole P, and the oil outlet 16 is communicated with the through hole T.
An insertion through hole is axially formed in the upper cylinder body 5 and the lower cylinder body 6, and a threaded insertion type temperature sensor 4 is installed in the insertion through hole and is used for measuring the temperature of the three O-shaped rings 22 and the temperature of gas in the compressor cylinder.
The piston sleeve 7 is arranged in the rodless cavity A and is connected with the upper cylinder body 5 through threads, and a high-pressure sealing ring 20 is arranged at the joint of the piston sleeve 7 and the upper cylinder body 5 to form static seal. One end of the piston rod 8 is arranged in the piston sleeve 7, a gap exists between the piston rod and the piston sleeve, and the other end of the piston rod 8 is positioned in the rod cavity B. In the action process of the hydraulic cylinder 2, the piston sleeve 7 and the piston rod 8 move mutually, and the leakage quantity is controlled by reasonably designing the length and the width of the gap so as to achieve the aim of sealing. When high-pressure oil flows through the gap, an oil film is formed, and lubrication and supporting functions can be achieved. The piston rod 8 and the piston sleeve 7 are made of materials with small dynamic and static friction coefficients, large hardness and certain hardness difference, such as chromium-molybdenum steel.
The outside of piston rod 8 is equipped with annular balance groove, and when fluid flowed through the balance groove, can form the vortex in the groove, makes fluid change from laminar state to turbulent mixing state and forms the resistance barrier to form the throttle to fluid, and make it produce as big pressure loss as possible, reduce the leakage. Because of errors in the geometric shape and coaxiality of the parts, working high-pressure oil is asymmetrically distributed in the sealing gap to form hydraulic clamping force, and friction force between dynamic sealing pairs is increased. Through setting up the balancing tank for radial oil pressure that acts on the piston rod 8 outside tends to balance, and piston rod 8 and piston sleeve 7 can be automatic centering, because concentric ring seam leak is more than eccentric ring seam little, and the centering of sealed vice part can also reduce the leakage quantity of fluid, further improves sealing performance.
An oil drain port 17 and an air drain port 36 are arranged on the side face of the lower cylinder body 6, and the oil drain port 17 can guide the leaked oil at the sealing position of the piston gap back to the oil tank.
The lower cylinder body 6 is internally provided with a first sealing guide support 10, a second sealing guide support 11 and a third sealing guide support 12 from top to bottom in sequence, and three radial static seals are respectively formed with the inner wall of the lower cylinder body 6 through three second O-shaped rings 22. The sealing guide support I10, the sealing guide support II 11 and the sealing guide support III 12 are hollow cylindrical shapes and coaxial.
An annular sealing cavity C is arranged in the sealing guide support II 11 and is communicated with the air leakage port 36.
As shown in fig. 4 and 5, a groove one and a guide groove one are formed in the inner wall of the seal guide support one 10, a combined seal ring one 26 is arranged in the groove one, and a guide belt one 25 is arranged in the guide groove one. The inner wall of the sealing guide support II 11 is provided with a groove II and a groove III, the combined sealing ring II 27 is arranged in the groove II, and the combined sealing ring III 28 is arranged in the groove III. The inner wall of the sealing guide support three 12 is provided with a groove four and a guide groove two, the combined sealing ring four 29 is arranged in the groove four, and the guide belt two 31 is arranged in the guide groove two. The first guide belt 25 and the second guide belt 31 are used for righting the hydraulic rod 9.
And a gas leakage hole is arranged on the side wall of the second sealing guide support 11 and is communicated with a gas leakage hole 36 on the side surface of the lower cylinder body 6, so that gas leaked from the second combined sealing ring 27, the third combined sealing ring 28 and the fourth combined sealing ring 29 and residual oil leaked from the first combined sealing ring 26 can be recovered.
The slip ring 24 is made of polytetrafluoroethylene containing carbon fibers, and has the advantages of low friction coefficient, high wear resistance and extrusion resistance and good sealing performance. The compressive elastic counter force of the O-ring 23 provides the sliding sealing surface of the slip ring 24 with additional compressive stress necessary to ensure sealing.
The oil scraper ring support 13 is arranged at the lower outlet of the lower cylinder body 6 and is connected with the lower cylinder body 6 through threads.
The nitrogen sealing device 3 is arranged below the lower cylinder body 6 and comprises a nitrogen sealing oil scraping ring support 38, a nitrogen sealing device connecting frame 39 and a nitrogen sealing guiding support 40. The nitrogen seal oil scraper ring support 38, the nitrogen seal device connecting frame 39 and the nitrogen seal guide support 40 are hollow structures and coaxial. The nitrogen sealing device connecting frame 39 is fixedly connected with the lower cylinder body 6 through a fastening screw, meanwhile, the O-shaped ring IV 43 is pressed to form an axial static seal, and an air cavity D is arranged in the nitrogen sealing device connecting frame 39.
The nitrogen seal oil scraper ring support 38 is arranged below the nitrogen seal device connecting frame 39, and the nitrogen seal oil scraper ring support and the nitrogen seal oil scraper ring are connected through threads.
The nitrogen seal guiding support 40 is arranged in the nitrogen seal device connecting frame 39, and an O-shaped ring III 42 is arranged at the joint of the nitrogen seal guiding support 40 and the nitrogen seal device connecting frame 39 to form static seal.
One end of the hydraulic rod 9 is positioned in the rod cavity B and is contacted with one end of the piston rod 8, and the other end passes through the sealing guide support I10, the sealing cavity C, the sealing guide support II 11, the sealing guide support III 12, the oil scraper ring support 13, the nitrogen sealing device connecting frame 39, the nitrogen sealing guide support 40 and the nitrogen sealing oil scraper ring support 38 and then is positioned below the nitrogen sealing device 3.
A combined sealing ring V30 is arranged at the matching position of the oil scraper ring support 13 and the hydraulic rod 9, and a combined sealing ring V37 is arranged at the matching position of the nitrogen-sealed oil scraper ring support 38 and the hydraulic rod 9, so that the sealing of high-pressure gas in the hydraulic cylinder can be realized, dirt and impurities such as dust and sand in the external environment can be prevented from entering the actuating mechanism, and the abrasion of equipment is reduced.
And a combined sealing ring six 32, a combined sealing ring seven 33, a guide belt three 34 and a guide belt four 35 are arranged at the matching position of the nitrogen seal sealing guide support 40 and the hydraulic rod 9 and are used for separating nitrogen in the air cavity D from a process medium in the cylinder of the reciprocating compressor.
The first combined sealing ring 26, the second combined sealing ring 27, the third combined sealing ring 28, the fourth combined sealing ring 29, the fifth combined sealing ring 30, the sixth combined sealing ring 32, the seventh combined sealing ring 33 and the eighth combined sealing ring 37 are all composed of the O-shaped ring 23 and the slip ring 24.
An air charging port 41 is provided on the side wall of the nitrogen sealing device connecting frame 39 for charging nitrogen gas with a certain pressure into the air chamber D.
When the inside of the electromagnetic valve 1 is switched to the P-A passage, oil enters from the oil inlet 14, flows through the P-A passage of the electromagnetic valve 1, flows into the rodless cavity A from the working oil port 15, drives the piston rod 8 and the hydraulic rod 9 to overcome the external load force at the rod end, and completes the opening action. When the inside of the electromagnetic valve 1 is switched to the A-T passage, the piston rod 8 and the hydraulic rod 9 linearly move in the opposite direction and reset under the action of load counterforce, and the oil in the rodless cavity A flows through the A-T passage of the electromagnetic valve 1 from the working oil port 15 and returns to the oil tank from the oil outlet 16. Based on the above, the cyclic opening and closing actions of the hydraulic cylinder 2 are completed.
According to the invention, a non-contact special structural design is adopted at the sealing position of the piston of the hydraulic cylinder, and a sealing structure of a sliding ring type bidirectional combined sealing ring and a guide belt is adopted at the hydraulic rod, so that bidirectional sealing of gas and oil at two sides of a rod end can be realized, the sealing performance is excellent, the friction resistance is small, the response speed is high, and the use requirement of an adjusting system can be met under the working condition of high frequency and high pressure.
Claims (10)
1. An electrohydraulic actuator for a reciprocating compressor gas flow regulating system, characterized by: comprises an electromagnetic valve (1), a hydraulic cylinder (2), a nitrogen sealing device (3) and a temperature sensor (4);
the electromagnetic valve (1) is arranged above the hydraulic cylinder (2) and is fixedly connected with the hydraulic cylinder (2) through four fastening screws (19);
a through port A, a through port P and a through port T are arranged on the electromagnetic valve (1);
the hydraulic cylinder (2) comprises an upper cylinder body (5), a lower cylinder body (6), a piston sleeve (7), a piston rod (8), a hydraulic rod (9), a sealing guide support I (10), a sealing guide support II (11), a sealing guide support III (12) and an oil scraper ring support (13);
the upper cylinder body (5) is arranged above the lower cylinder body (6), and the upper cylinder body and the lower cylinder body are fixedly connected through an inner hexagonal cylindrical head screw (18);
a rodless cavity A and a rod-containing cavity B are arranged in the upper cylinder body (5), and the rodless cavity A and the rod-containing cavity B are coaxial;
the upper end surface of the upper cylinder body (5) is provided with a working oil port (15) which is communicated with the through port A and the rodless cavity A;
an oil inlet (14) and an oil outlet (16) are arranged on the side surface of the upper cylinder body (5), wherein the oil inlet (14) is communicated with the through hole P, and the oil outlet (16) is communicated with the through hole T;
an inserting through hole is axially formed in the upper cylinder body (5) and the lower cylinder body (6), and a threaded inserting temperature sensor (4) is arranged in the inserting through hole;
the piston sleeve (7) is arranged in the rodless cavity A and is connected with the upper cylinder body (5) through threads;
one end of the piston rod (8) is arranged in the piston sleeve (7), a gap exists between the piston rod and the piston sleeve, and the other end of the piston rod (8) is positioned in the rod cavity B;
an annular balance groove is formed in the outer side of the piston rod (8), vortex is formed in the groove when oil flows through the balance groove, so that the oil is converted from a laminar flow state to a turbulent flow mixing state, and a resistance barrier is formed;
an oil drain port (17) and an air drain port (36) are arranged on the side surface of the lower cylinder body (6), and the oil drain port (17) can guide the leakage oil at the sealing position of the piston gap back to the oil tank;
an annular sealing cavity C is arranged in the sealing guide support II (11), and the sealing cavity C is communicated with the air leakage port (36);
a first sealing guide support (10), a second sealing guide support (11) and a third sealing guide support (12) are sequentially arranged in the lower cylinder body (6) from top to bottom, and three radial static seals are formed between the three sealing guide supports and the inner wall of the lower cylinder body (6) through three second O-shaped rings (22);
the sealing guide support I (10), the sealing guide support II (11) and the sealing guide support III (12) are hollow cylindrical shapes and are coaxial;
the inner wall of the sealing guide support I (10) is provided with a groove I and a guide groove I, the combined sealing ring I (26) is arranged in the groove I, and the guide belt I (25) is arranged in the guide groove I;
the inner wall of the sealing guide support II (11) is provided with a groove II and a groove III, the combined sealing ring II (27) is arranged in the groove II, and the combined sealing ring III (28) is arranged in the groove III;
a groove IV and a guide groove II are arranged on the inner wall of the sealing guide support III (12), a combined sealing ring IV (29) is arranged in the groove IV, and a guide belt II (31) is arranged in the guide groove II;
the side wall of the sealing guide support II (11) is provided with a gas leakage hole which is communicated with a gas leakage hole (36) on the side surface of the lower cylinder body (6);
the oil scraper ring support (13) is arranged at the outlet below the lower cylinder body (6) and is connected with the lower cylinder body (6) through threads;
the nitrogen sealing device (3) is arranged below the lower cylinder body (6) and comprises a nitrogen sealing oil scraping ring support (38), a nitrogen sealing device connecting frame (39) and a nitrogen sealing guiding support (40);
the nitrogen seal oil scraper ring support (38), the nitrogen seal device connecting frame (39) and the nitrogen seal guide support (40) are hollow structures and coaxial;
an O-shaped ring IV (43) is arranged between the nitrogen sealing device connecting frame (39) and the lower cylinder body (6), the nitrogen sealing device connecting frame (39) is fixedly connected with the lower cylinder body (6) through a fastening screw, meanwhile, the O-shaped ring IV (43) is pressed to form an axial static seal, and an air cavity D is arranged in the nitrogen sealing device connecting frame (39);
the nitrogen seal oil scraper ring support (38) is arranged below the nitrogen seal device connecting frame (39), and the nitrogen seal oil scraper ring support and the nitrogen seal oil scraper ring are connected through threads;
the nitrogen seal sealing guide support (40) is arranged in the nitrogen seal device connecting frame (39);
one end of the hydraulic rod (9) is positioned in the rod cavity B, is contacted with one end of the piston rod (8), and passes through the sealing guide support I (10), the sealing cavity C, the sealing guide support II (11), the sealing guide support III (12), the oil scraper ring support (13), the nitrogen sealing device connecting frame (39), the nitrogen sealing guide support (40) and the nitrogen sealing oil scraper ring support (38) to be positioned below the nitrogen sealing device (3);
the first combined sealing ring (26), the second combined sealing ring (27), the third combined sealing ring (28) and the fourth combined sealing ring (29) are composed of an O-shaped ring (23) and a slip ring (24).
2. An electro-hydraulic actuator as defined in claim 1, wherein: an O-shaped ring I (21) is arranged at the joint of the upper cylinder body (5) and the lower cylinder body (6) to realize axial static seal and prevent oil in the rod cavity B from leaking.
3. An electro-hydraulic actuator as defined in claim 2, wherein: the connecting part of the piston sleeve (7) and the upper cylinder body (5) is provided with a high-pressure sealing ring (20) to form static seal.
4. An electro-hydraulic actuator as claimed in claim 3, wherein: and an O-shaped ring III (42) is arranged at the joint of the nitrogen seal guide support (40) and the nitrogen seal device connecting frame (39) to form static seal.
5. An electro-hydraulic actuator as defined in claim 4, wherein: a combined sealing ring five (30) is arranged at the matching position of the oil scraper ring support (13) and the hydraulic rod (9), and a combined sealing ring eight (37) is arranged at the matching position of the nitrogen seal oil scraper ring support (38) and the hydraulic rod (9).
6. An electro-hydraulic actuator as defined in claim 5, wherein: and a combined sealing ring six (32), a combined sealing ring seven (33), a guiding belt three (34) and a guiding belt four (35) are arranged at the matching position of the nitrogen sealing guiding support (40) and the hydraulic rod (9) and are used for separating nitrogen in the air cavity D from a process medium in the cylinder of the reciprocating compressor.
7. An electro-hydraulic actuator as defined in claim 6, wherein: an inflation inlet (41) is arranged on the side wall of the nitrogen sealing device connecting frame (39) and is used for inflating nitrogen with certain pressure into the air cavity D.
8. An electro-hydraulic actuator as defined in claim 7, wherein: the piston rod (8) and the piston sleeve (7) are made of chromium-molybdenum steel, and the hardness of the piston rod and the piston sleeve is poor.
9. An electro-hydraulic actuator as defined in claim 8, wherein: the slip ring (24) is made of polytetrafluoroethylene containing carbon fibers.
10. An electro-hydraulic actuator as defined in claim 9, wherein: when the inside of the electromagnetic valve (1) is switched to a P-A passage, oil enters from an oil inlet (14), flows through the P-A passage of the electromagnetic valve (1), flows into the rodless cavity A through a working oil port (15), drives a piston rod (8) and a hydraulic rod (9) to overcome the external load force at the rod end, and completes the opening action;
when the inside of the electromagnetic valve (1) is switched to the A-T passage, under the action of load counter force, the piston rod (8) and the hydraulic rod (9) linearly move in the opposite direction and reset, and oil in the rodless cavity A flows through the A-T passage of the electromagnetic valve (1) from the working oil port (15) and returns to the oil tank from the oil outlet (16).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711172945.1A CN108005993B (en) | 2017-11-22 | 2017-11-22 | Electrohydraulic actuator for gas flow regulating system of reciprocating compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711172945.1A CN108005993B (en) | 2017-11-22 | 2017-11-22 | Electrohydraulic actuator for gas flow regulating system of reciprocating compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108005993A CN108005993A (en) | 2018-05-08 |
| CN108005993B true CN108005993B (en) | 2023-12-15 |
Family
ID=62053448
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711172945.1A Active CN108005993B (en) | 2017-11-22 | 2017-11-22 | Electrohydraulic actuator for gas flow regulating system of reciprocating compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108005993B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109654006A (en) * | 2018-12-26 | 2019-04-19 | 江西资生科技有限公司 | Stepless amount regulating system and method |
| CN111042622B (en) * | 2019-12-31 | 2024-07-12 | 成都辟思航空科技有限公司 | Inflatable easy-to-fold rod |
| CN113374682B (en) * | 2021-07-15 | 2022-05-13 | 西南石油大学 | Fracturing pump fluid end plunger hole seal structure |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1182314A (en) * | 1997-09-01 | 1999-03-26 | Japan Steel Works Ltd:The | Displacement adjusting device of displacement reciprocating compressor |
| CN202946734U (en) * | 2012-11-20 | 2013-05-22 | 富阳派沃阀门有限公司 | Nitrogen-sealed valve |
| CN203978771U (en) * | 2014-08-08 | 2014-12-03 | 山东易阳石化节能装备有限公司 | A kind of stepless tolerance adjustment actuating mechanism of essential safe type clearance of reciprocating compressor |
| CN205013264U (en) * | 2015-10-05 | 2016-02-03 | 天华化工机械及自动化研究设计院有限公司 | Compressor tolerance infinitely variable control system |
| CN207609641U (en) * | 2017-11-22 | 2018-07-13 | 北京航天石化技术装备工程有限公司 | A kind of electrohydraulic actuator for reciprocating compressor amount regulating system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201865889U (en) * | 2010-11-30 | 2011-06-15 | 赖梦超 | Clearance stepless adjustment actuator of reciprocating compressor |
-
2017
- 2017-11-22 CN CN201711172945.1A patent/CN108005993B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1182314A (en) * | 1997-09-01 | 1999-03-26 | Japan Steel Works Ltd:The | Displacement adjusting device of displacement reciprocating compressor |
| CN202946734U (en) * | 2012-11-20 | 2013-05-22 | 富阳派沃阀门有限公司 | Nitrogen-sealed valve |
| CN203978771U (en) * | 2014-08-08 | 2014-12-03 | 山东易阳石化节能装备有限公司 | A kind of stepless tolerance adjustment actuating mechanism of essential safe type clearance of reciprocating compressor |
| CN205013264U (en) * | 2015-10-05 | 2016-02-03 | 天华化工机械及自动化研究设计院有限公司 | Compressor tolerance infinitely variable control system |
| CN207609641U (en) * | 2017-11-22 | 2018-07-13 | 北京航天石化技术装备工程有限公司 | A kind of electrohydraulic actuator for reciprocating compressor amount regulating system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108005993A (en) | 2018-05-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107202174B (en) | Novel double-sealing type dome valve | |
| CN101806363B (en) | High-pressure high-temperature two-way balance stop valve | |
| CN108005993B (en) | Electrohydraulic actuator for gas flow regulating system of reciprocating compressor | |
| CN103982671A (en) | Floating ball valve | |
| CN117432813B (en) | Spring type multi-stage throttling emptying valve | |
| CN107061834B (en) | Built-in driving axial-flow type regulating valve | |
| CN111828685A (en) | Isolated two-position three-way valve | |
| CN111503279A (en) | High-temperature-resistant switch valve device | |
| CN112178209A (en) | Bellows type ultra-low temperature pneumatic stop valve | |
| CN103727254B (en) | A kind of High Temperature High Pressure self balancing modulating valve | |
| CN201731153U (en) | High-pressure low-temperature gas check valve | |
| CN207609641U (en) | A kind of electrohydraulic actuator for reciprocating compressor amount regulating system | |
| CN219345116U (en) | Leakage-free plug-in type hydraulic control one-way valve | |
| CN203730808U (en) | High-temperature and high-pressure self-balancing control valve | |
| CN103982674A (en) | Top-mounting fixation ball valve | |
| CN202381720U (en) | Unidirectional pressure self-balance stop valve | |
| CN105134991A (en) | Novel cock valve | |
| CN204900910U (en) | Novel plug valve | |
| CN201269345Y (en) | Gas-fluid type piston valve | |
| CN201034184Y (en) | Standing ball valve seat structure | |
| CN210510342U (en) | Hydraulic anti-pollution valve for hydraulic ultrahigh-pressure water | |
| CN203516830U (en) | High-pressure balanced type three-way control valve | |
| CN203322297U (en) | Elastic self-sealing butterfly valve | |
| CN103244694B (en) | Piston type zero leakage stop valve | |
| CN208185119U (en) | Emulsion Piston for pump compound sealing mechanism |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |