CN113669241B - Liquid piston compressor control system - Google Patents
Liquid piston compressor control system Download PDFInfo
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- CN113669241B CN113669241B CN202110925606.6A CN202110925606A CN113669241B CN 113669241 B CN113669241 B CN 113669241B CN 202110925606 A CN202110925606 A CN 202110925606A CN 113669241 B CN113669241 B CN 113669241B
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- 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
- F04B49/002—Hydraulic systems to change the pump delivery
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- 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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/008—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being a fluid transmission link
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/32—Hydrogen storage
Abstract
The invention discloses a liquid piston compressor control system, wherein electromagnetic valves are respectively arranged on an air inlet pipeline and an exhaust pipeline which are communicated with a gas compression cavity of a liquid piston compressor, an oil inlet of a first electromagnetic proportional speed regulating valve is respectively communicated with an oil outlet of a one-way variable hydraulic pump, an oil inlet of a two-position two-way electromagnetic directional valve and an oil inlet of an overflow valve through pipelines, an oil outlet of a second electromagnetic proportional speed regulating valve, an oil outlet of the two-position two-way electromagnetic directional valve and an oil outlet of the overflow valve are respectively communicated with an oil tank, an oil inlet of the one-way variable hydraulic pump is connected to oil through an oil pipe to form a pressure stabilizing buffer structure, the action mode of a liquid piston and a solid piston is changed, the follow-up property between the liquid piston and a gas piston can be effectively controlled and ensured in the process that the piston moves from an upper dead center to a lower dead center, a gas-liquid two-phase interface is stabilized, and the clearance volume generated in the working process of the compressor is reduced, the high-efficiency and stable operation of the compressor is realized, and the adaptability of the liquid piston compressor to wide working conditions is improved.
Description
Technical Field
The application belongs to the technical field of compressors, and particularly relates to a liquid piston compressor control system.
Background
The development of the world faces the double challenges of huge and environmental problems, and hydrogen energy is regarded as an important way for solving the energy problem in the new century as a zero-emission, pollution-free and sustainable green energy. In a plurality of application fields of hydrogen, a hydrogen fuel cell automobile is expected to become a first breakthrough and an important outlet of the hydrogen energy industry, become an optimal technical route of a new energy automobile, and also become an important development strategy of the future automobile industry in China. The development of mature, stable, safe, reliable and efficient high-pressure hydrogenation station equipment is the premise and the basis of the development of the hydrogen fuel cell automobile industry.
Taking a hydrogen station for transporting gas by a tank car as an example, the main equipment comprises a gas discharging column, a compressor, a hydrogen storage tank, a filling machine, a pipeline, a control system, a nitrogen purging device, a diffusing device, a safety monitoring device and the like. According to statistics, the cost of the compressor accounts for about 30% of the total construction cost of the hydrogenation station, the compressor is the second major factor of the failure of the hydrogenation station, the compressor is related to 22% of maintenance events, 28% of safety accidents and 25% of hydrogen leakage, and the compressor is an important component of the hydrogenation station. At present, diaphragm compressors are mainly used in hydrogenation stations, and a small amount of liquid-driven piston compressors and crank-connecting rod type reciprocating piston compressors are also used. The service life of a core component membrane of the diaphragm compressor is only 500-2000 hours at present, and large displacement cannot be realized; the liquid-driven piston compressor can only realize smaller displacement and has the problem that hydrogen is polluted by hydraulic oil; the traditional piston compressor is immature at present, and the biggest obstacle is that a high-pressure sealing friction pair cannot be effectively solved. Therefore, an innovative compression technology with better performance is important for promoting the development of the hydrogenation industry and accelerating the entry of hydrogen fuel cell automobiles into the market.
The advent of liquid piston compressors has provided a new idea for solving this problem. Compared with the traditional hydrogen compressor, the liquid piston compressor uses special liquid to construct a liquid piston for gas compression, and the liquid can hardly be compressed and has extremely low vapor pressure, so that hydrogen can not be polluted in the compression process; because of good cooling effect, the compression process is close to isothermal compression, and the temperature of the compressor can be reduced, thereby improving the reliability and saving the energy consumption; the liquid piston compressor is driven by hydraulic pressure, has few moving parts, has a simple structure compared with a common compressor, and can be used for a long time without maintenance. Based on the advantages, the liquid piston compressor is expected to become a good solution for hydrogen pressurization of a future high-pressure hydrogen station.
The commercial application of large-emission hydrogen stations in the future requires hydrogen compressors with higher gas supply capacity. For liquid piston compressors, higher operating frequencies are required. Due to the existence of liquid in the cylinder of the liquid piston compressor, the liquid is difficult to follow the motion of the solid piston due to high-speed motion under the condition of no control, and the follow-up property of the liquid piston and the solid piston cannot be maintained. At the moment, the gas-liquid two-phase interface cannot be maintained stably, and a part of working medium gas is wrapped by liquid and is difficult to be discharged at the exhaust stage, so that the clearance of the cylinder is continuously increased along with the operation of the compressor, the exhaust volume is reduced, and the working efficiency of the liquid piston compressor is seriously influenced.
Disclosure of Invention
The invention aims to provide a control system of a liquid piston compressor, which overcomes the defects of the prior art.
In order to achieve the purpose, the invention adopts the following technical scheme:
the control system of the liquid piston compressor comprises a gas compression assembly and a hydraulic assembly, wherein the gas compression assembly is connected with the hydraulic assembly through a hydraulic pipeline;
the gas compression assembly comprises a gas inlet pipeline and a gas outlet pipeline which are communicated with a gas compression cavity of the liquid piston compressor, and the gas inlet pipeline and the gas outlet pipeline are both provided with electromagnetic valves;
the hydraulic system comprises an oil tank, a one-way variable hydraulic pump, a two-position two-way electromagnetic directional valve, an overflow valve, a first electromagnetic proportional speed regulating valve, a two-position three-way electromagnetic directional valve and a second electromagnetic proportional speed regulating valve;
an oil inlet of the first electromagnetic proportional speed regulating valve is respectively communicated with an oil outlet of the one-way variable hydraulic pump, an oil inlet of the two-position two-way electromagnetic directional valve and an oil inlet of the overflow valve through pipelines, an oil outlet of the first electromagnetic proportional speed regulating valve is communicated with an oil inlet of the two-position three-way electromagnetic directional valve through an oil pipe, a working oil port of the two-position three-way electromagnetic directional valve is communicated with an oil cavity of a hydraulic cylinder of the liquid piston compressor through the oil pipe, and an oil return port of the two-position three-way electromagnetic directional valve is communicated with an oil inlet of the second electromagnetic proportional speed regulating valve through the oil pipe; an oil outlet of the second electromagnetic proportional speed regulating valve, an oil outlet of the two-position two-way electromagnetic directional valve and an oil outlet of the overflow valve are communicated to an oil tank, and an oil inlet of the one-way variable hydraulic pump is connected to the oil tank through an oil pipe.
Furthermore, an electromagnetic valve, a gas filter, a first check valve, a first pressure reducing valve and an air inlet pipeline electromagnetic valve are sequentially arranged on the air inlet pipeline, and one end of the air inlet pipeline electromagnetic valve is communicated with a gas compression cavity of the liquid piston compressor.
Furthermore, the exhaust pipeline is sequentially provided with an exhaust valve, a second pressure reducing valve and a second one-way valve, one end of the second one-way valve is connected with the exhaust pipeline, and one end of the exhaust valve is communicated to a gas compression cavity of the liquid piston compressor.
Further, the liquid piston compressor comprises a cylinder body and a piston arranged in the cylinder body, a cavity at one end of the piston in the cylinder body is a gas compression cavity, a cavity at the other end of the piston in the cylinder body is a hydraulic cylinder oil cavity, the gas compression cavity is provided with a pressure sensor and a temperature sensor, and the piston at one end of the gas compression cavity is provided with ionic liquid.
Furthermore, an oil pipe of the one-way variable hydraulic pump communicated to the oil tank is provided with a first liquid filter, and one end of the one-way variable hydraulic pump is connected with a servo motor.
Furthermore, a working oil port of the two-position two-way electromagnetic directional valve is connected with an oil tank through a hydraulic pipeline, and the other end of the overflow valve is connected with the oil tank through the hydraulic pipeline.
Furthermore, a hydraulic cooler is arranged on an oil outlet pipeline of the second electromagnetic proportional speed regulating valve.
Further, an oil outlet of the second electromagnetic proportional speed regulating valve is connected with an oil inlet of the hydraulic cooler through a tenth hydraulic pipeline.
Furthermore, the oil outlet end of the hydraulic cooler is connected with a second liquid filter.
Furthermore, an oil outlet of the hydraulic cooler is connected with an oil inlet of a second liquid filter, and an oil outlet of the second liquid filter is connected with an oil tank.
Compared with the prior art, the invention has the following beneficial technical effects:
the invention relates to a control system of a liquid piston compressor, which is characterized in that an air inlet pipeline and an exhaust pipeline which are communicated with a gas compression cavity of the liquid piston compressor are respectively provided with an electromagnetic valve, and meanwhile, a hydraulic system comprises an oil tank, a one-way variable hydraulic pump, a two-position two-way electromagnetic directional valve, an overflow valve, a first electromagnetic proportional speed regulating valve, a two-position three-way electromagnetic directional valve and a second electromagnetic proportional speed regulating valve; an oil inlet of a first electromagnetic proportional speed regulating valve is communicated with an oil outlet of a one-way variable hydraulic pump, an oil inlet of a two-position two-way electromagnetic directional valve and an oil inlet of an overflow valve through pipelines respectively, an oil outlet of the first electromagnetic proportional speed regulating valve is communicated with an oil inlet of the two-position three-way electromagnetic directional valve through an oil pipe, a working oil port of the two-position three-way electromagnetic directional valve is communicated with an oil cavity of a hydraulic cylinder of a liquid piston compressor through the oil pipe, and an oil return port of the two-position three-way electromagnetic directional valve is communicated with an oil inlet of a second electromagnetic proportional speed regulating valve through the oil pipe; the oil outlet of the second electromagnetic proportional speed regulating valve, the oil outlet of the two-position two-way electromagnetic directional valve and the oil outlet of the overflow valve are communicated to an oil tank, the oil inlet of the one-way variable hydraulic pump is connected to oil through oil pipes to form a pressure stabilizing buffer structure, the action mode of a liquid piston and a solid piston is changed, the follow-up property between the liquid piston and a gas piston can be effectively controlled and guaranteed in the process that the piston moves from an upper dead point to a lower dead point, a gas-liquid two-phase interface is stabilized, the clearance volume generated in the working process of the compressor is reduced, and the efficient and stable operation of the compressor is realized.
Furthermore, a hydraulic system composed of hydraulic elements such as a first electromagnetic proportional speed regulating valve, a second electromagnetic proportional speed regulating valve, a two-position three-way electromagnetic directional valve, a one-way variable hydraulic pump and the like can effectively regulate the movement speed of the piston in real time according to the running state of the compressor by controlling the flow of hydraulic oil, and regulate the movement of the piston according to the gas-liquid two-phase movement characteristic, so that the gas-liquid two-phase interface control is realized, the liquid piston is kept relatively stable in the high-speed running process of the compressor, the high-efficiency stable work of the compressor at a high rotating speed can be realized, and an effective way is provided for improving the air displacement of the liquid piston compressor.
Furthermore, the pressure reducing valve and the one-way valve are arranged on the exhaust pipeline and the air inlet pipeline respectively, so that gas can be effectively prevented from flowing backwards, and the safety of the compression process is improved.
Drawings
Fig. 1 is a schematic view of a compressor according to an embodiment of the present invention.
In the figure, 1-oil tank, 2-first hydraulic pipeline, 3-first liquid filter, 4-second hydraulic pipeline, 5-one-way variable hydraulic pump, 6-servo motor, 7-third hydraulic pipeline, 8-fourth hydraulic pipeline, 9-two-position two-way electromagnetic directional valve, 10-fifth hydraulic pipeline, 11-sixth hydraulic pipeline, 12-overflow valve, 13-seventh hydraulic pipeline, 14-first electromagnetic proportional speed regulating valve, 15-eighth hydraulic pipeline, 16-two-position three-way electromagnetic directional valve, 17-ninth hydraulic pipeline, 18-second electromagnetic proportional speed regulating valve, 19-tenth hydraulic pipeline, 20-hydraulic cooler, 21-eleventh hydraulic pipeline, 22-second liquid filter, 23-twelfth hydraulic pipeline, 24-a thirteenth hydraulic pipeline, 25-a hydraulic cylinder oil chamber, 26-hydraulic oil, 27-a solid piston, 28-ionic liquid, 29-a gas compression chamber, 30-an electromagnetic valve, 31-a gas filter, 32-a first one-way valve, 33-a first pressure reducing valve, 34-an air inlet pipeline electromagnetic valve, 35-an air inlet pipeline, 36-a pressure sensor, 37-a temperature sensor, 38-an exhaust valve, 39-a second pressure reducing valve, 40-a second one-way valve and 41-an exhaust pipeline.
Detailed Description
The invention is described in further detail below with reference to the accompanying drawings:
the present invention will be further described with reference to the following examples. The following description is only a part of the embodiments of the present invention, and not all embodiments. All embodiments of the gas obtained by a person skilled in the art without any inventive work based on the embodiments of the present invention belong to the protection scope of the present invention.
As shown in fig. 1, a liquid piston compressor control system, a gas compression assembly and a hydraulic assembly, wherein the gas compression assembly is connected with the hydraulic assembly through a pipeline;
the gas compressor component comprises a gas inlet pipeline, a gas exhaust pipeline, a gas compression cavity and a hydraulic cylinder oil cavity;
the air inlet pipeline comprises an electromagnetic valve 30, an air filter 31, a first one-way valve 32, a first pressure reducing valve 33 and an air inlet pipeline electromagnetic valve 34, wherein the electromagnetic valve 30 is connected with one end of the air filter 31 through a pipeline, the other end of the air filter 31 is connected with one end of the first one-way valve 32 through a pipeline, the other end of the first one-way valve 32 is connected with one end of the first pressure reducing valve 33 through a pipeline, the other end of the first pressure reducing valve 33 is connected with one end of the air inlet pipeline electromagnetic valve 34 through a pipeline, and the air inlet pipeline electromagnetic valve 34 is installed on the air compression cavity 29 and is directly connected with the air compression cavity 29;
the exhaust pipeline comprises an exhaust valve 38, a second pressure reducing valve 39 and a second one-way valve 40, the exhaust valve 38 is installed on the gas compression cavity 29, one end of the exhaust valve is directly connected with the gas compression cavity 29, the other end of the exhaust valve 38 is connected with one end of the second pressure reducing valve 39 through a pipeline, and the other end of the second pressure reducing valve 39 is connected with one end of the second one-way valve 40 through a pipeline;
the liquid piston compressor comprises a cylinder body and a piston 27 arranged in the cylinder body, a gas compression cavity 29 is communicated with the hydraulic cylinder oil cavity 25 and is separated by the piston 27, a pressure sensor 36 and a temperature sensor 37 are installed at the upper part of the gas compression cavity 29, ionic liquid 28 is arranged on the piston, and the hydraulic cylinder oil cavity 25 is connected with the two-position three-way electromagnetic directional valve 16 through a thirteenth hydraulic pipeline 24;
the hydraulic system comprises an oil tank 1, a first liquid filter 3, a one-way variable hydraulic pump 5, a servo motor 6, a two-position two-way electromagnetic directional valve 9, an overflow valve 12, a first electromagnetic proportional speed regulating valve 14, a two-position three-way electromagnetic directional valve 16, a second electromagnetic proportional speed regulating valve 18, a hydraulic cooler 20 and a second liquid filter 22;
the oil tank 1 is connected with one end of a first liquid filter 3 through a first hydraulic pipeline 2, the other end of the first liquid filter 3 is connected with an oil suction port of a one-way variable hydraulic pump 5 through a second hydraulic pipeline 4, one end of the one-way variable hydraulic pump 5 is connected with a servo motor 6, an oil discharge port of the one-way variable hydraulic pump 5 is connected with an oil inlet of a two-position two-way electromagnetic directional valve 9 through a fourth hydraulic pipeline 8, an oil discharge port of the one-way variable hydraulic pump 5 is connected with one end of an overflow valve 12 through a sixth hydraulic pipeline 11, and an oil discharge port of the one-way variable hydraulic pump 5 is connected with one end of a first electromagnetic proportional speed regulating valve 14 through a third hydraulic pipeline 7;
a working oil port of the two-position two-way electromagnetic directional valve 9 is connected with the oil tank 1 through a fifth hydraulic pipeline 10, and the other end of the overflow valve 12 is connected with the oil tank 1 through a seventh hydraulic pipeline 13;
the two-position three-way electromagnetic directional valve 16 comprises three interfaces which are respectively an oil inlet, an oil return port and a working oil port, the oil inlet of the two-position three-way electromagnetic directional valve 16 is connected with the other end of the first electromagnetic proportional speed regulating valve 14 through an eighth hydraulic pipeline 15, the working oil port of the two-position three-way electromagnetic directional valve 16 is connected with an oil cavity of the hydraulic cylinder through a thirteenth hydraulic pipeline 24, and the oil return port of the two-position three-way electromagnetic directional valve 16 is connected with one end of the second electromagnetic proportional speed regulating valve 18 through a ninth hydraulic pipeline 17;
the other end of the second electromagnetic proportional speed regulating valve 18 is connected with one end of a hydraulic cooler 20 through a tenth hydraulic pipeline 19, the other end of the hydraulic cooler 20 is connected with one end of a second liquid filter 22 through an eleventh hydraulic pipeline 21, and the other end of the second liquid filter 22 is connected with the oil tank 1 through a twelfth hydraulic pipeline 23.
The working principle of the invention is as follows:
before the compressor starts to work, the set pressure of the overflow valve 12 is set in advance to serve as the maximum working pressure of the hydraulic system, and the first electromagnetic proportional speed regulating valve 14 and the second electromagnetic proportional speed regulating valve 18 are adjusted to set initial flow so as to control the movement speed of the piston 27; the two-position two-way electromagnetic directional valve 9 is positioned at a right control position, so that an oil inlet pipeline of the hydraulic system is communicated with the oil tank 1 and is in a pressure relief state; the two-position three-way electromagnetic directional valve 16 is positioned at a right control position, and an oil return pipeline of the hydraulic system is communicated with an oil cavity 25 of the hydraulic cylinder; the intake line solenoid valve 32 is in a closed state.
And (3) a gas suction process: the servo motor 6 is started, and the unidirectional variable hydraulic pump 5 starts to work; the air inlet pipeline electromagnetic valve 34 is opened, and hydrogen enters the air inlet pipeline and reaches the air inlet pipeline electromagnetic valve 34 through the gas filter 31, the first check valve 32 and the first pressure reducing valve 33; at the moment, the oil cavity 25 of the hydraulic cylinder is communicated with the oil tank 1, the gas pressure in the gas compression cavity is greater than the oil pressure in the oil cavity 25 of the hydraulic cylinder, the piston 27 moves downwards under the action of the oil-gas pressure difference, and the hydraulic oil 26 in the oil cavity 25 of the hydraulic cylinder enters the oil tank 1 through an oil return pipeline; meanwhile, the gas pressure in the gas compression chamber 29 is continuously reduced, and when the pressure in the gas compression chamber 29 is lower than the inlet pressure set by the inlet line solenoid valve 34, the inlet line solenoid valve 34 is opened, and hydrogen gas enters the gas compression chamber 29.
And (3) compression and exhaust processes: the two-position two-way electromagnetic directional valve 9 is switched to a left control position, an oil inlet pressure relief pipeline is cut off, and the pressure of hydraulic oil is increased and stabilized under the set pressure of an overflow valve 12 under the action of a one-way variable hydraulic pump 5; when the gas pressure in the gas compression cavity 29 is higher than the exhaust pressure set by the exhaust valve 38, the exhaust valve 38 is opened, the high-pressure gas enters the exhaust pipeline 41, passes through the exhaust valve 38, the second reducing valve 39 and the second check valve 40, is discharged and enters a lower device or a user using end.
The hydraulic system comprises the hydraulic elements such as the first electromagnetic proportional speed regulating valve, the second electromagnetic proportional speed regulating valve, the two-position three-way electromagnetic directional valve, the one-way variable hydraulic pump and the like, can effectively regulate the movement speed of the piston in real time according to the running state of the compressor by controlling the flow of hydraulic oil, and regulate the movement of the piston according to the gas-liquid two-phase movement characteristic, thereby realizing the control of a gas-liquid two-phase interface, ensuring that the liquid piston keeps relatively stable in the high-speed running process of the compressor, realizing the efficient and stable work of the compressor at high rotating speed and providing an effective way for the gas displacement lifting of the liquid piston compressor.
Claims (10)
1. The control system of the liquid piston compressor is characterized by comprising a gas compression assembly and a hydraulic assembly, wherein the gas compression assembly is connected with the hydraulic assembly through the liquid piston compressor;
the liquid piston compressor comprises a cylinder body and a piston (27) arranged in the cylinder body, wherein a cavity body at one end of the piston (27) in the cylinder body is a gas compression cavity (29), and a cavity body at the other end of the piston in the cylinder body is a hydraulic cylinder oil cavity (25); the gas compression assembly comprises a gas inlet pipeline and a gas outlet pipeline which are communicated with a gas compression cavity (29) of the liquid piston compressor, and the gas inlet pipeline and the gas outlet pipeline are respectively provided with an electromagnetic valve;
the hydraulic assembly comprises an oil tank (1), a one-way variable hydraulic pump (5), a two-position two-way electromagnetic directional valve (9), an overflow valve (12), a first electromagnetic proportional speed regulating valve (14), a two-position three-way electromagnetic directional valve (16) and a second electromagnetic proportional speed regulating valve (18);
an oil inlet of a first electromagnetic proportional speed regulating valve (14) is respectively communicated with an oil outlet of a one-way variable hydraulic pump (5), an oil inlet of a two-position two-way electromagnetic directional valve (9) and an oil inlet of an overflow valve (12) through pipelines, an oil outlet of the first electromagnetic proportional speed regulating valve (14) is communicated with an oil inlet of a two-position three-way electromagnetic directional valve (16) through an oil pipe, a working oil port of the two-position three-way electromagnetic directional valve (16) is communicated with a hydraulic cylinder oil cavity (25) of a liquid piston compressor through an oil pipe, and an oil return port of the two-position three-way electromagnetic directional valve (16) is communicated with an oil inlet of a second electromagnetic proportional speed regulating valve (18) through an oil pipe; an oil outlet of the second electromagnetic proportional speed regulating valve (18), an oil outlet of the two-position two-way electromagnetic directional valve (9) and an oil outlet of the overflow valve (12) are communicated to the oil tank (1), and an oil inlet of the one-way variable hydraulic pump (5) is connected to the oil tank (1) through an oil pipe.
2. The liquid piston compressor control system as claimed in claim 1, characterized in that the air inlet pipeline is provided with an electromagnetic valve (30), a gas filter (31), a first check valve (32), a first pressure reducing valve (33) and an air inlet pipeline electromagnetic valve (34) in sequence, and one end of the air inlet pipeline electromagnetic valve (34) is communicated with a gas compression cavity of the liquid piston compressor.
3. The control system of the liquid piston compressor as claimed in claim 1, wherein the exhaust pipeline is sequentially provided with an exhaust valve (38), a second pressure reducing valve (39) and a second one-way valve (40), one end of the second one-way valve (40) is connected with an exhaust pipeline (41), and one end of the exhaust valve (38) is communicated to a gas compression cavity of the liquid piston compressor.
4. A liquid piston compressor control system according to claim 1, characterized in that a pressure sensor and a temperature sensor are installed on the gas compression chamber (29), and an ionic liquid (28) is installed on the piston located at one end of the gas compression chamber (29).
5. The control system of the liquid piston compressor as claimed in claim 1, characterized in that a first liquid filter (3) is arranged on an oil pipe of the unidirectional variable hydraulic pump (5) communicated to the oil tank (1), and one end of the unidirectional variable hydraulic pump (5) is connected with a servo motor (6).
6. The control system of the liquid piston compressor as claimed in claim 1, wherein the working oil port of the two-position two-way electromagnetic directional valve (9) is connected with the oil tank (1) through a hydraulic pipeline, and the other end of the overflow valve (12) is connected with the oil tank (1) through a hydraulic pipeline.
7. A control system of a liquid piston compressor according to claim 1, characterized in that the oil outlet pipe of the second electromagnetic proportional speed regulating valve (18) is provided with a hydraulic cooler (20).
8. The liquid piston compressor control system according to claim 1, characterized in that the oil outlet of the second electromagnetic proportional speed regulating valve (18) is connected with the oil inlet of the hydraulic cooler (20) through a tenth hydraulic conduit.
9. A liquid piston compressor control system according to claim 7, characterized in that a second liquid filter (22) is connected to the oil outlet end of the hydraulic cooler (20).
10. A liquid piston compressor control system according to claim 9, characterised in that the oil outlet of the hydraulic cooler (20) is connected to the oil inlet of a second liquid filter (22), and the oil outlet of the second liquid filter (22) is connected to the oil tank (1).
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| CN202110925606.6A CN113669241B (en) | 2021-08-12 | 2021-08-12 | Liquid piston compressor control system |
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| CN202110925606.6A CN113669241B (en) | 2021-08-12 | 2021-08-12 | Liquid piston compressor control system |
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| CN114215725B (en) * | 2021-12-14 | 2023-08-04 | 西安交通大学 | Two-stage compression diaphragm compressor system |
| CN115288996B (en) * | 2022-09-19 | 2023-07-21 | 中国石油大学(华东) | Performance test device for simulating ionic liquid hydrogen compressor |
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