A multi-stage radially rotating cylinder liquid piston reciprocating compressor

Abstract

A multi-stage radially rotating cylinder liquid piston reciprocating compressor relates to the field of compressor design and manufacturing, comprising a compressor housing, a compression assembly, a control assembly, a cooling circulation system, a gas-liquid processing device, a purging device and a safety protection device; the inner cylinder body of the compression assembly is arranged in an outer cylinder body, a transmission shaft is fixed in the center hole of the inner cylinder body, and the center of the inner cylinder body is concentrically arranged with the geometric center of the outer cylinder body; a plurality of mounting holes are evenly distributed radially and radially along the outer edge surface of the inner cylinder body, and the mounting holes are arranged from the inside to the outside in sequence. The choke plug is connected to the outer cylinder body and a retainer on the side wall thereof through the bearing, and conducting holes are opened in the cylinder chamber along the axis direction of the inner cylinder body, and the conducting holes are connected to the control assembly; through the control and regulation of the control assembly, a single compressor can realize a multi-stage series or multi-cylinder parallel compression process, thereby realizing multi-stage and multiple compressions.

Description

Technical Field

[0001] The present application relates to the field of compressor design and manufacture, and in particular to a multi-stage radially rotating cylinder liquid piston reciprocating compressor. Background Art

[0002] As is known, compressors are divided into two categories according to their working principles: volumetric type and speed type. Among them, volumetric compressors rely on pistons or rotors that move back and forth (reciprocating) or rotate (rotary) in the cylinder to reduce the working volume and increase the gas pressure, which is called a reciprocating compressor or a rotary compressor. At the same time, reciprocating compressors are divided into two categories: reciprocating piston compressors and reciprocating diaphragm compressors. The main advantages of reciprocating piston compressors are wide application pressure range, high efficiency and strong adaptability. However, there are the following defects: 1. The overall size and weight are large; 2. There are many vulnerable parts such as air valves, support rings, piston rings and packings; 3. In order to extend the operating cycle, the compressor cylinder chamber needs to be lubricated with oil, and there is inevitably contamination of the compressed gas by lubricating oil or wear particles; 4. The packing seal cost is high and the reliability is low in high-pressure or leaky gas applications; 5. The compressing high-pressure gas, leaky gas, high-purity gas or rare and precious gas has poor applicability. Although reciprocating diaphragm compressors can avoid such problems, they have shortcomings such as small exhaust flow and short life of key components (diaphragms), which restrict their application development.

[0003] With the emergence of a new material, ionic liquid (a salt composed of organic cations and inorganic or organic anions), the development of traditional reciprocating piston compressors has ushered in a new transformation. Ionic liquids have the advantages of low vapor pressure, low solubility, high decomposition temperature, high thermal stability, high viscosity index and low compressibility, which provide conditions for the innovation of reciprocating piston compressors. The ionic liquid compressor was first proposed by Linde Kryotechnik AG in Germany. Its product features are: the static compressor cylinder is arranged vertically; the power adopts a hydraulic system, and the hydraulically driven piston drives the ionic liquid to reciprocate up and down in the cylinder. The suction and exhaust compression process of the compressor is completed through the action of the one-way valves at the inlet and exhaust ports at the top of the cylinder. The ionic liquid compressor manufactured by Linde for hydrogen filling stations is much more compact than the standard reciprocating compressor. However, the multi-stage compression process required still requires multiple "vertically arranged cylinders" to be completed by series operation, and the system is relatively complex. For liquid piston compressors, how to conveniently realize the multi-stage compression process needs to be explored. At the same time, the upper limit of the operating frequency of this type of compressor is low, which limits its promotion and application in more fields.

[0004] The patent publication number is CN111365210A, the application publication date is 2020.07.03, and the patent name is: A high-efficiency boosted zero-clearance ionic liquid compressor with precisely adjustable piston stroke; the patent publication number is CN111365211A, and the application publication date is 2020.07.03. A swing-reversing two-stage boosted zero-clearance ionic liquid compressor; the patent publication number is CN111365212A, and the application publication date is 2020.07.03, and the patent name is: A three-stage boosted zero-clearance ionic liquid compressor with real-time adjustable phase difference. Both adopt: the static compressor cylinder is arranged vertically; a hydraulic oil station is used as the power source, and the reversing component is used to switch the hydraulic drive oil circuit. The hydraulically driven solid piston pushes the ionic liquid to reciprocate up and down in the cylinder, and the suction and exhaust compression process of the compressor is completed through the action of the one-way valves at the air inlet and exhaust ports on the top of the cylinder. The above patents face the same problems as Linde's patents. At the same time, because their hydraulic systems use valve control, the system power loss is relatively large and the energy consumption is relatively high.

[0005] The patent publication number is CN101243258A, the application date is 2006.07.25, and the publication (announcement) date is 2008.08.13. The patent name is a pistonless compressor. It proposes a pistonless compressor that is arranged along the axial direction of the inclined disk and rotates along the central axis of the inclined disk. The piston produces a reciprocating motion along the axial direction of the central axis of the rotation and drives the ionic liquid to complete the gas compression in the cylinder. The gas path is opened and closed by the distribution plate. In order to complete the suction process, the compressor needs to be equipped with a pre-boosting screw compressor on the inlet pipeline. The patent uses an ionic liquid piston to independently complete the gas compression process. In terms of operation mode, pump control replaces valve control. The overall structure is more compact and has positive significance in concept; but due to the limitations of the structural design, the pistonless compressor is difficult to meet the application requirements of large displacement. Summary of the invention

[0006] In order to overcome the deficiencies in the background technology, the present application discloses a multi-stage radially rotating cylinder liquid piston reciprocating compressor with compact structure, excellent rigidity, balanced power and reliable operation.

[0007] In order to achieve the application purpose, this application adopts the following technical solutions:

[0008] A multi-stage radially rotating cylinder liquid piston reciprocating compressor, comprising a compressor housing, a compression assembly, a control assembly, a cooling circulation system, a gas-liquid processing device, a purge device and a safety protection device; the compression assembly and the control assembly are located inside the compressor housing, and the cooling circulation system, the gas-liquid processing device, the purge device and the safety protection device are located outside the compressor housing;

[0009] The compression assembly includes a transmission shaft, an inner cylinder, a liquid piston, a choke, a bearing, a retainer and an outer cylinder; the inner cylinder is arranged in the outer cylinder, a transmission shaft is fixed in the center hole of the inner cylinder, the outer cylinder is in a circular ring shape, the inner wall of the outer cylinder is a continuous closed-loop wavy surface, and the inner cylinder center and the outer cylinder geometric center are arranged concentrically during assembly; a plurality of mounting holes are evenly distributed radially and radially along the outer edge of the inner cylinder, and the mounting holes are arranged from the inside to the outside in order to form a cylinder chamber, a compressed liquid, a choke and a bearing, so that a number of cylinder chambers are formed to be radially distributed on the outer edge of the inner cylinder along the transmission shaft, the choke is connected to the outer cylinder and the retainer on the side wall thereof through the bearing, and a through hole is opened in the cylinder chamber along the axis direction of the inner cylinder in each mounting hole, and the through hole is connected to the control assembly;

[0010] Furthermore, external power is transmitted to the inner cylinder body through the transmission shaft, and the inner cylinder body performs synchronous rotational motion with the transmission shaft. With the help of the continuous closed-loop wavy surface on the inner wall of the outer cylinder body, the rotation of the inner cylinder body is converted into radial reciprocating motion of the compressed liquid, the baffle plug and the bearing in the mounting hole. When the inner cylinder body performs rotational motion, the compressed liquid in the cylinder chamber is subjected to centrifugal force, which limits the flow of the compressed liquid and forms the liquid piston in the cylinder chamber and on the surface of the baffle plug.

[0011] Furthermore, the continuous closed-loop waveform surface on the inner wall of the outer cylinder is evenly distributed in the circumferential direction, and the waveform surface consists of a rising section and a descending section. A complete rising section and a descending section correspond to a complete process of gas compression, and the number of periodic changes in the radius of the waveform surface in the circumferential direction is a positive integer.

[0012] Furthermore, the center lines of the cylinder chambers in the mounting hole of the inner cylinder body are evenly distributed in a radial shape and are distributed in the same plane or different planes of the inner cylinder body radial direction. The number of cylinder chambers is twice the number of periodic changes of the radius of the waveform surface in the circumferential direction. n times, n is a positive integer.

[0013] Furthermore, at least two cylinders synchronously participate in the gas compression cycle process of each stage of the compressor, and the working processes of these two cylinders are opposite, that is, when the first cylinder of the same compression stage is performing the liquid suction and air intake process, the other cylinder of the same compression stage is performing the exhaust and liquid discharge process; when the first cylinder of the same compression stage is performing the exhaust and liquid discharge process, the other cylinder of the same compression stage is performing the liquid suction and air intake process.

[0014] Furthermore, the transmission shaft is a single-piece integral forging structure and is rigidly directly connected to the center hole of the inner cylinder body through a key.

[0015] Furthermore, the cross-sectional area of ​​the flow blocking plug and the cross-sectional area of ​​the liquid piston are designed to be equal or unequal. At the same time, due to the fluidity of the liquid, the cylinder chamber and the guide hole flow channel through which the liquid piston flows are streamlined.

[0016] Furthermore, the liquid piston, the baffle plug and the bearing of the compression assembly rotate at high speed and participate in radial reciprocating motion during the gas compression process. The bearing is a roller bearing or a sliding bearing. When the bearing is a roller bearing, a columnar box groove is provided at the end of the baffle plug to cover the surface of the roller bearing with a columnar structure, and the axial through hole of the core of the baffle plug leads to the cylindrical working surface of the roller bearing. The mating surface between the retainer and the roller bearing is a conical surface or a cylindrical surface; when the bearing is a sliding bearing, its connecting end adopts a ball head with a neck structure, and a U-shaped groove is provided at the connecting end of the baffle plug, and a ball groove is provided at the bottom of the U-shaped groove. The ball groove is connected to the sliding bearing of the ball head with a neck structure, and the sliding end of the sliding bearing forms an arc-shaped sliding mating surface with the inner wall of the outer cylinder body, and the retainer is provided on the inner wall of the outer cylinder body to form an annular contact band edge with the sliding bearing, and a groove is provided on the mating surface of the sliding end of the sliding bearing, and the axial through hole of the baffle plug and the axial through hole of the core of the sliding bearing are both connected to the groove opened on the sliding mating surface.

[0017] The control assembly includes a diverter plate arranged in the compressor housing and a liquid inlet channel, an air inlet channel and an exhaust channel on the compressor housing. The diverter plate is arranged between the inner cylinder body and the compressor housing, and the diverter plate is installed on the inner wall of the compressor housing. The contact surface of the diverter plate and the inner cylinder body is tightly fitted. A plurality of groups of interfaces corresponding to the conduction holes are provided on the side of the diverter plate fitted with the inner cylinder body. Each group of interfaces is distributed in an arc shape on concentric circles on the diverter plate. Each group of interfaces includes a liquid inlet interface L, an air inlet interface G and an exhaust interface M in sequence. The plurality of groups of interfaces are sorted in sequence. Each group of interfaces after sorting corresponds to a certain level of the compression sequence, that is, the liquid inlet interface Ln, the air inlet interface Gn and the exhaust interface Mn of the nth group of interfaces correspond to the nth level of the compression sequence.

[0018] Furthermore, the liquid inlet interface L, the air inlet interface G of the first group and the exhaust interface M of the last group are through holes in the axial direction of the diverter disk, and the remaining interfaces are not through holes in the axial direction, the outer end of the liquid inlet channel on the compressor housing is connected to the liquid supply pipeline of the cooling circulation system, and the inner end is connected to the liquid inlet interface L of each group of interfaces on the diverter disk, the outer end of the air inlet channel on the compressor housing is connected to the gas-liquid mixer through the compressor inlet pipe, and the inner end is connected to the air inlet interface G in the first group of interfaces corresponding to the first stage on the diverter disk, the outer end of the exhaust channel on the compressor housing is connected to the gas-liquid separator through the compressor outlet pipe, and the inner end is connected to the exhaust interface M in the last group of interfaces corresponding to the last stage on the diverter disk;

[0019] Furthermore, the number of compression stages of the compressor is related to the number of compressions per cylinder per revolution of the compressor and the control method of the diverter disk. The number of compressions per cylinder per revolution of the compressor is equal to the number of cycles of change of the radius of the corrugated surface of the inner wall of the outer cylinder body. In order to realize the compression process of the compressor in multi-stage series or multi-cylinder parallel connection, it is necessary to combine and match the connection relationship of each group of intake interfaces G and exhaust interfaces M in the diverter disk. When the compressor needs to operate in a multi-stage series mode, the exhaust interface of the previous group and the intake interface of the next group are connected in the diverter disk. They are connected through channels, that is, M1 of the first sequence is connected with G2 of the second sequence, M2 of the second sequence is connected with G3 of the third sequence, and so on, M(n-1) of the n-1th sequence is connected with Gn of the nth sequence, so as to realize n-stage compression and boosting of the compressor; when the compressor needs to operate in a multi-cylinder parallel mode, all the intake interfaces G of each group that need to operate in parallel are connected through channels in the diverter disk, and all the exhaust interfaces M of each group that need to operate in parallel are connected through channels in the diverter disk.

[0020] Furthermore, when the inner cylinder body rotates, the liquid piston generates radial reciprocating motion in the cylinder chamber, and the reciprocating motion causes the working volume of the cylinder chamber to change. At the same time, the cylinder chamber is cyclically connected with the liquid inlet interface L, air inlet interface G and exhaust interface M of each group of interfaces on the diverter disk through the conducting hole, and a dynamic and static sealing surface is formed between the diverter disk and the inner cylinder body, thereby preventing leakage of gas or liquid.

[0021] The cooling circulation system comprises a liquid reservoir, a cooler, a cooler bypass valve, a filter, a liquid supply pump, a pump safety valve, an overflow valve and a liquid supply pipe check valve. The liquid reservoir is used to collect the compressed liquid and the lubricating medium leaked from each sealing pair. The compressed liquid and the lubricating medium are uniformly ionic liquids. The ionic liquid is drawn out from the liquid reservoir, and is pressurized by the liquid supply pump after passing through the flange A interface of the liquid reservoir, the cooler with a cooler bypass valve, and the filter in sequence. The pressurized compressed liquid is divided into two paths: one is the compressor liquid supply pipeline, and the pipeline is provided with a liquid supply pipe check valve, and the liquid supply pipe check valve is passed through the pipeline C The interfaces are connected to the liquid inlet channel in the compressor housing and the liquid inlet interface L in the diverter disk in turn; the other is the compressor spray pipeline, which passes through the mixer check valve and the mixer regulating valve and enters the gas-liquid mixer on the compressor inlet pipe. The compressor intake air and the ionic liquid are mixed into a two-phase fluid in the gas-liquid mixer and then enter the compressor inlet; a pump safety valve is provided at the outlet of the liquid supply pump, and the outlet pipeline of the pump safety valve is connected to the flange B interface of the liquid storage tank; an overflow valve is provided at the high point of the entire cooling circulation system, and the overflow valve outlet is discharged back to the liquid storage tank through the flange B interface.

[0022] The gas-liquid processing device includes a gas-liquid mixer, a mixer regulating valve, a mixer non-return valve, a gas-liquid separator, a separator hydraulic control valve and a damping circulation valve. The liquid spraying pipeline from the compressor cooling circulation system is connected to the mixer non-return valve, the mixer non-return valve is connected to the mixer regulating valve, and the outlet of the mixer regulating valve is connected to the liquid spraying pipeline inlet of the gas-liquid mixer; the inlet pipeline of the gas-liquid mixer is connected to the inlet pipeline of the compressor, the outlet pipeline of the gas-liquid mixer is connected to the air inlet channel in the compressor housing, and the air inlet channel in the compressor housing is connected to the air inlet interface G in the diverter disk; the exhaust interface M in the diverter disk is connected to the exhaust channel in the compressor housing, the exhaust channel in the compressor housing is connected to the inlet pipeline of the gas-liquid separator, the liquid outlet of the gas-liquid separator is connected to the inlet pipeline of the separator hydraulic control valve, the outlet pipeline of the separator hydraulic control valve is connected to the inlet pipeline of the damping circulation valve, the outlet pipeline of the damping circulation valve is discharged to the fuselage liquid storage tank through the flange D interface, and the gas outlet of the gas-liquid separator is connected to the outside of the boundary.

[0023] The purging device includes a purge and a discharge one-way valve. The air inlet end of the purge is connected to an external air source, and the exhaust end of the purge is connected to a compressor housing. A purge discharge pipeline is also provided on the compressor housing. The purge discharge pipeline is connected to an external discharge system, and a discharge one-way valve is provided on the purge discharge pipeline.

[0024] Furthermore, the purge medium of the purger is an inert gas.

[0025] The safety protection device is provided outside the compressor housing, the air inlet end of the safety protection device is connected to the compressor housing, and the air outlet end of the safety protection device is connected to the external exhaust system.

[0026] Furthermore, the safety protection device uses a bursting disc or a relief valve.

[0027] Due to the adoption of the above technical solution, the present invention has the following beneficial effects:

[0028] 1. The liquid piston reciprocating compressor described in the present invention has multiple cylinder chambers distributed radially along the transmission shaft at the outer edge of the inner cylinder body, which is conducive to realizing a large-sized cylinder chamber, and the overall structure is compact, which can easily meet the demand of the liquid piston compressor for increasing the exhaust flow rate; the compressed liquid in the inner cylinder body forms a liquid piston under the action of centrifugal force, eliminating the influence of multiple adverse factors on the liquid piston after the "vertical arrangement of the cylinder" in the prior art, and broadening the application field of the liquid piston reciprocating compressor.

[0029] 2. The liquid piston reciprocating compressor described in the present invention can complete multiple gas compression processes per rotation of the liquid piston. Through the control and regulation of the control assembly, a single compressor can realize a multi-stage series or multi-cylinder parallel compression process, and a single compressor can conveniently realize multi-stage and multiple compression.

[0030] 3. Compared with the liquid piston compressors in the prior art, the liquid piston reciprocating compressor of the present invention adopts a mechanical direct-connected direct-drive working mode for the compressor cylinder, which eliminates the hydraulic drive system commonly used in the prior art, simplifies the whole machine matching, and improves the transmission efficiency, so the compressor structure is novel; compared with the traditional reciprocating piston compressor, this machine is a piston-free and air valve-free design, which minimizes the types of vulnerable parts of the piston compressor, extends the life of vulnerable parts, reduces operating costs, and has a long trouble-free operation period.

[0031] 4. The liquid piston reciprocating compressor described in the present invention has a short axial dimension of the whole machine, a small shaft support span, a high overall rigidity of the drive shaft and the inner cylinder body, a compact compressor structure, and more reliable operation; the multiple cylinders arranged radially symmetrically have good dynamic balance during operation, a small radial load, and almost no axial load, so the compressor runs more stably.

[0032] 5. The liquid piston reciprocating compressor described in the present invention uses ionic liquid as the compression liquid, which can fully cool the compressed gas. The present invention realizes a nearly isothermal gas compression process and achieves high gas compression efficiency.

[0033] 6. The liquid piston reciprocating compressor described in the present invention uses a liquid piston to block the leakage of the compressed gas, and utilizes the good sealing performance of a specific liquid to replace and solve the material science problem in the field of high-pressure contact seals, making the compressor suitable for the compression of high-pressure gases or gases that are prone to leakage; the liquid piston uses a compressed liquid that does not dissolve the compressed gas and is separated from the gas without residue, making the compressor suitable for the compression of high-purity gases and rare and precious gases, avoiding the contamination of the compressed gas by traditional compressor lubricating oil or wear particles. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 It is a schematic diagram of the radial structure of the compressor of the present invention.

[0035] Figure 2 It is a schematic diagram of the axial structure of the compressor of the present invention.

[0036] Figure 3 It is a schematic diagram of the left side structure of the three-stage series compression diverter disk of the present invention.

[0037] Figure 4 It is a schematic diagram of the right side structure of the three-stage series compression diverter disk of the present invention.

[0038] Figure 5 It is a schematic diagram of the left side structure of the two-stage series double-stage compression diverter disk of the present invention.

[0039] Figure 6 It is a schematic diagram of the right side structure of the two-stage series double-stage compression diverter disk of the present invention.

[0040] Figure 7 It is a schematic diagram of the compressor system and pipeline flow of the present invention.

[0041] In the figure: 1. compressor housing; 2. transmission shaft; 3. inner cylinder; 4. liquid piston; 5. choke; 6. bearing; 7. retainer; 8. outer cylinder; 9. guide hole; 10. diverter plate; 11. air inlet channel; 12. exhaust channel; 13. liquid inlet channel; 14. gas-liquid separator; 15. separator hydraulic control valve; 16. damping circulation valve; 17. purge; 18. discharge non-return valve; 19. safety protection device; 20. gas-liquid mixer; 21. mixer regulating valve; 22. mixer non-return valve; 23. liquid reservoir; 24. cooler; 25. cooler bypass valve; 26. filter; 27. liquid supply pump; 28. pump safety valve; 29. ​​overflow valve; 30. liquid supply pipe non-return valve; 31. cylinder chamber. DETAILED DESCRIPTION

[0042] The present invention is further described below in conjunction with the accompanying drawings and specific embodiments. It should be noted that the embodiments are only specific descriptions of the present invention, and their purpose is to allow those skilled in the art to better understand the technical solution of the present application, and should not be regarded as limiting the present invention.

[0043] Example 1

[0044] Implement three-stage compression six-cylinder radial rotating cylinder liquid piston reciprocating compressor, such as Figures 1 to 4 , Figure 7 As shown, it includes a compressor housing 1, a compression assembly, a control assembly, a cooling circulation system, a gas-liquid processing device, a purge device and a safety protection device 19; the compression assembly and the control assembly are located inside the compressor housing 1, and the cooling circulation system, the gas-liquid processing device, the purge device and the safety protection device 19 are located outside the compressor housing 1;

[0045] The compression assembly includes a transmission shaft 2, an inner cylinder 3, a liquid piston 4, a choke 5, a bearing 6, a retainer 7 and an outer cylinder 8; the inner cylinder 3 is arranged in the outer cylinder 8, the transmission shaft 2 is fixed in the center hole of the inner cylinder 3, the outer cylinder 8 is annular, and the inner wall of the outer cylinder 8 is a continuous closed-loop wavy surface. When assembled, the center of the inner cylinder 3 and the geometric center of the outer cylinder 8 are concentrically arranged; a plurality of mounting holes are evenly distributed radially and radially along the outer edge surface of the inner cylinder 3, and the mounting holes are arranged from the inside to the outside. The outside is the cylinder chamber 31, the compressed liquid, the choke 5 and the bearing 6 in sequence, so that a number of cylinder chambers 31 are formed and distributed radially along the transmission shaft 2 on the outer edge of the inner cylinder body 3. The choke 5 is connected to the outer cylinder body 8 and the retainer 7 on the side wall through the bearing 6. In each mounting hole, a through hole 9 is opened in the cylinder chamber 31 along the axial direction of the inner cylinder body 3, and the through hole 9 is connected to the control assembly; the transmission shaft 2 is a single-piece integral forging structure, and is rigidly directly connected to the center hole of the inner cylinder body 3 through a key;

[0046] The radius of the waveform surface changes periodically in the circumferential direction of rotation. The waveform surface consists of an ascending section and a descending section. A complete ascending section and a descending section correspond to a complete process of gas compression. The liquid piston 4 can complete multiple gas compression processes per rotation, and the number of periodic changes in the radius of the surface is equal to the number of gas compressions per cylinder per rotation of the compressor. In this way, under the coordination of the control assembly, a single compressor can realize a multi-stage series or multi-cylinder parallel compression process, and a single compressor can realize multi-stage and multiple compressions. The number of compression stages of the compressor in this embodiment is three, so the number of gas compressions per cylinder per rotation of a single machine must be greater than or equal to three times, that is, the number of periodic changes in the radius of the waveform surface in the circumferential direction of rotation must be greater than or equal to three times. In this embodiment, the number of periodic changes in the radius of the waveform surface is three times;

[0047] The wavy curved surface on the inner wall of the outer cylinder body 8 is uniformly distributed in the circumferential direction; the center lines of the cylinder chambers 31 in the mounting hole of the inner cylinder body 3 are uniformly distributed in a radial shape and are distributed in the same radial plane of the inner cylinder body 3. The total number of cylinder chambers 31 in the mounting hole is six;

[0048] The cross-sectional area of ​​the flow blocking plug 5 is designed to be equal to that of the liquid piston 4. In some preferred embodiments, the cross-sectional area of ​​the flow blocking plug 5 and that of the liquid piston 4 may be designed to be unequal. At the same time, due to the fluidity of the liquid, the cylinder chamber 31 and the flow passage of the guide hole 9 through which the liquid piston 4 flows are in a streamlined form.

[0049] The liquid piston 4 is formed by using an ionic liquid. The ionic liquid has the characteristics of low vapor pressure, low solubility, high decomposition temperature, high thermal stability, high viscosity index and low compressibility. Therefore, the ionic liquid can block the leakage of the compressed gas. The sealing performance of the ionic liquid can solve the material science problem in the field of high-pressure contact sealing. This embodiment is suitable for the compression of high-pressure gas or gas that is easy to leak, and is also suitable for the compression process of high-purity gas or rare and precious gas. Since the ionic liquid can fully cool the compressed gas, this embodiment can achieve near-isothermal compression and achieve high gas compression efficiency. The ionic liquid can also be used instead of the lubricating medium of the compressor. This embodiment can achieve operation without lubricating oil in the cylinder.

[0050] The liquid piston 4, the choke 5 and the bearing 6 of the compression assembly rotate at high speed and participate in radial reciprocating motion during the gas compression process. The bearing 6 is a roller bearing. The end of the choke 5 is provided with a columnar groove covering the surface of the roller bearing of the columnar structure. The axial through hole in the core of the choke 5 leads to the cylindrical working surface of the roller bearing. The mating surface of the retainer 7 and the roller bearing is a conical surface or a cylindrical surface.

[0051] The working principle of the gas compression cycle in the compression assembly is as follows:

[0052] When the transmission shaft 2 drives the inner cylinder body 3 to rotate, the inertial centrifugal force generated by the bearing 6, the choke 5 and the compressed liquid, the reaction force applied by the outer cylinder body 8 and the retainer 7, and the gas force of the cyclic pressure change in the cylinder chamber 31 work together, wherein the compressed liquid forms a liquid piston 4 under the action of the inertial centrifugal force; as the inner cylinder body 3 rotates, with the help of the continuous closed-loop wavy surface on the inner wall of the outer cylinder body 8, the rotation of the inner cylinder body 3 is converted into the radial reciprocating motion of the liquid piston 4, the choke 5 and the bearing 6 in the mounting hole; when the liquid piston 4 moves in the direction of the centrifugal force, the volume of the working chamber of the cylinder chamber 31 increases, and the liquid and gas suction processes are completed sequentially; The cylinder body 3 continues to rotate, and the inner wall of the compressor outer cylinder body 8 pushes the bearing 6, the baffle plug 5 and the liquid piston 4 to move toward the rotation center of the inner cylinder body 3. The volume of the working chamber of the cylinder chamber 31 becomes smaller, completing the exhaust and liquid discharge process. With the help of the three-periodic changes in the radius of the waveform surface in the circumferential direction, as the inner cylinder body 3 rotates, each cylinder will complete three gas compression cycles per revolution. Since the total number of compressor cylinder chambers 31 is six, and the cylinder chambers 31 and the waveform surface are evenly distributed in the circumferential direction, there are two cylinders synchronously participating in the gas compression process of each stage of the compressor at the same time, and the working processes of these two cylinders are opposite.

[0053] The process of the six working cylinders in the compression assembly working in coordination and sequence is as follows:

[0054] In this embodiment, the six cylinder chambers 31 are numbered X1, X2, Y1, Y2, Z1, and Z2 in sequence according to the rotation direction of the inner cylinder body 3. It can be seen from the above working principle that the working process of the six cylinder chambers 31 is: when X1 is performing the first-stage liquid suction and air intake process, X2 is performing the first-stage exhaust and liquid discharge process, and so on, Y1 is performing the second-stage liquid suction and air intake process, Y2 is performing the second-stage exhaust and liquid discharge process, Z1 is performing the third-stage liquid suction and air intake process, and Z2 is performing the third-stage exhaust and liquid discharge process; further, the working processes of the six cylinder chambers 31 correspond to each other in time and function, that is, when X2 is performing the first-stage exhaust and liquid discharge process, Y1 is performing the second-stage air intake process, and at this time, X2 and Y1 are connected through the diverter plate 10. The arc-shaped interface is connected and synchronously controlled. When Y2 is performing the second-stage exhaust and liquid discharge process, Z1 is performing the third-stage air intake process. At this time, Y2 and Z1 are connected and synchronously controlled through the arc-shaped interface on the diverter disk 10; further, as the inner cylinder body 3 rotates, when X1 rotates to the original position of X2, X1 begins to repeat the original working process of X2, and performs the first-stage exhaust and liquid discharge. By analogy, at this time, X2 begins to repeat the original working process of Y1, and performs the second-stage liquid intake and air intake..., Z2 begins to repeat the original working process of X1, and performs the first-stage liquid intake and air intake, until the inner cylinder body 3 rotates one circle and returns to the starting position. In this way, the six cylinder chambers 31 of X1, X2, Y1, Y2, Z1 and Z2 work in coordination with each other to complete the three compression processes of the gas in sequence.

[0055] The relationship between the various forces in the compression assembly is as follows:

[0056] The liquid piston 4 and the choke plug 5 in the compression assembly generate interaction forces with the outer cylinder body 8 and the retainer 7 on the side wall thereof through the bearing 6. The typical relationship between the various forces is: when the inner cylinder body 3 rotates, the liquid piston 4, the choke plug 5 and the bearing 6 in the inner cylinder body 3 will generate inertial centrifugal force, and the outer cylinder body 8 and the retainer 7 restrict their movement and exert a reaction force on them. At the same time, the gas with cyclic pressure changes in the cylinder chamber 31 will also exert gas force on the liquid piston 4, the choke plug 5 and the bearing 6. Therefore, the force on the liquid piston 4, the choke plug 5 and the bearing 6 is the vector superposition of the gas force and the inertial centrifugal force of each component;

[0057] The flow control setting of the flow divider plate 10 in the control assembly is as follows:

[0058] The diverter plate 10 is arranged between the inner cylinder body 3 and the compressor housing 1, and the diverter plate 10 is installed on the inner wall of the compressor housing 1. The contact surface of the diverter plate 10 and the inner cylinder body 3 fits tightly. On the diverter plate 10 side of the fitting surface, multiple groups of interfaces are provided on the annular surface corresponding to the through hole 9 of the cylinder chamber 31. Each group of interfaces includes one liquid inlet interface L, one air inlet interface G and one exhaust interface M. All these interfaces in contact with the surface of the inner cylinder body 3 are distributed in arc shape on the concentric circles on the diverter plate 10. The multiple groups of interfaces are sorted in sequence according to the adjacent relationship, and each group of interfaces after sorting corresponds to a certain level of the compression sequence, as shown in the attached figure. Figure 3-4 As shown, the first stage of the compressor corresponds to the liquid inlet interface L1, the air inlet interface G1, and the exhaust interface M1 of the first group, the second stage of the compressor corresponds to the liquid inlet interface L2, the air inlet interface G2, and the exhaust interface M2 of the second group, and the third stage of the compressor corresponds to the liquid inlet interface L3, the air inlet interface G3, and the exhaust interface M3 of the third group. The liquid inlet interfaces L of all compression stages are connected through channels in the diverter disk 10, that is, in the diverter disk 10, L1, L2, and L3 are connected through channels, and at the same time, the exhaust interface of the previous group is connected to the air inlet interface of the next group through channels, that is, M1 is connected to G2, M2 is connected to G3, and the liquid inlet interface L1, the air inlet interface G1 and the exhaust interface M3 are connected. There is a through hole in the axial direction of the diverter disk 10, so on the contact surface between the diverter disk 10 and the compressor housing 1, a liquid inlet interface L1, an air inlet interface G1 and an exhaust interface M3 are left on the diverter disk 10 side; the outer end of the liquid inlet channel 13 on the compressor housing 1 is connected to the liquid supply pipeline of the cooling circulation system, and the inner end is connected to the liquid inlet interface L1 on the diverter disk 10, the outer end of the air inlet channel 11 on the compressor housing 1 is connected to the gas-liquid mixer 20 through the compressor inlet pipe, and the inner end is connected to the air inlet interface G1 on the diverter disk 10, the outer end of the exhaust channel 12 on the compressor housing 1 is connected to the gas-liquid separator 14 through the compressor outlet pipe, and the inner end is connected to the exhaust interface M3 on the diverter disk 10.

[0059] In the above embodiment, the compressor realizes three-stage series compression, and the corresponding flow dividing control setting of the flow dividing plate 10 is as above; when the compressor needs to realize multi-cylinder parallel compression, such as adopting "two parallel cylinders in the first stage and one single cylinder in the second stage, a total of two-stage compression", then as shown in the attached Figure 5-6As shown, the corresponding control setting of the diverter disk 10 is as follows: the liquid inlet interfaces L of all compression stages are connected through channels in the diverter disk 10, that is, in the diverter disk 10, L1, L2, and L3 are connected through channels, and the air intake interfaces G1 and G2 of the first group and the second group of interfaces corresponding to the first stage of the compressor are connected through channels in the diverter disk 10, that is, at this time, the inner end of the air intake channel 11 on the compressor housing 1 is connected to the air intake interface G1 on the diverter disk 10, and a connection relationship is established between the air intake channel 11 and G2, and the exhaust interfaces M1 and M2 of the first group and the second group of interfaces corresponding to the first stage of the compressor are connected through channels in the diverter disk 10, and the channels arranged on the diverter disk 10 do not interfere with each other, and the exhaust interface of the first stage is connected to the air intake interface of the second stage through channels, that is, M1, M2 and G3 are all connected, and the undescribed content in this setting case is consistent with the corresponding description in the embodiment.

[0060] When the inner cylinder body 3 rotates, the liquid piston 4 generates radial reciprocating motion in the cylinder chamber 31. The reciprocating motion causes the working volume of the cylinder chamber 31 to change. At the same time, the cylinder chamber 31 is cyclically connected with the liquid inlet interface L, the air inlet interface G and the exhaust interface M of each group on the diverter plate 10 in sequence through the conducting hole 9. The fitting surface between the diverter plate 10 and the inner cylinder body 3 forms a dynamic and static contact surface, which is perpendicular to the transmission shaft 2 of the compressor. At the same time, the contact surface on the inner cylinder body 3 is the rotating side, and the contact surface on the diverter plate 10 is the stationary side. There is a sealing medium between the dynamic and static contact surfaces, so a dynamic and static sealing surface is formed between the diverter plate 10 and the inner cylinder body 3, and the dynamic and static sealing surface prevents the leakage of gas or liquid.

[0061] The coordinated working process of the compression assembly and the control assembly is as follows:

[0062] In this embodiment, as shown in the attached Figure 1-4As shown, there are six cylinder chambers 31 on the inner cylinder body 3. When the inner cylinder body 3 rotates, the position point where the radius of the waveform surface corresponding to X1, Y1, and Z1 changes from decreasing to increasing is taken as the starting point. At this time, its liquid piston 4 starts to move centrifugally, and the working volume of X1, Y1, and Z1 starts to increase. At the same time, the radius of the waveform surface corresponding to X2, Y2, and Z2 changes from increasing to decreasing, and its liquid piston 4 starts to move centripetally, and the working volume of X2, Y2, and Z2 starts to decrease; when the through holes 9 of X1, Y1, and Z1 are connected to the liquid inlet interfaces L1, L2, and L3 in the diverter plate 10 respectively , the ionic liquid from the cooling circulation system supply pipe begins to be injected into X1, Y1, and Z1, and the liquid absorption process of the cylinder chamber 31 begins. During the liquid absorption process, the working volume of X1, Y1, and Z1 continues to increase until the through hole 9 of X1, Y1, and Z1 is disconnected from the diverter plate 10, and the liquid absorption process ends; and in this process, due to the centripetal movement of the X2, Y2, and Z2 liquid piston 4, the working volume of X2, Y2, and Z2 begins to decrease, and the gas is compressed in X2, Y2, and Z2 and the pressure continues to increase. The pressure increase process continues until the entire gas compression process ends; as the inner cylinder body 3 continues to The radius of the waveform surface corresponding to X1, Y1, and Z1 continues to rotate, and the radius of the waveform surface corresponding to X1, Y1, and Z1 continues to increase. When the through holes 9 of X1, Y1, and Z1 are connected to the air inlet interfaces G1, G2, and G3 of the shunt disk 10, respectively, the air intake process of X1, Y1, and Z1 begins. At the same time, the radius of the waveform surface corresponding to X2, Y2, and Z2 continues to decrease, and the through holes 9 of X2, Y2, and Z2 are connected to the exhaust interfaces M1, M2, and M3 of the shunt disk 10, respectively. In this way, the exhaust and liquid discharge process of X2, Y2, and Z2 starts synchronously with the air intake process of X1, Y1, and Z1, and the gas is discharged from the air intake channel 1. 1 and the G1 interface in the diverter disk 10 continuously flow into X1. Since M1 and G2 are connected inside the diverter disk 10, the gas-liquid mixed phase compressed medium flows out from X2, flows through the M1 interface and G2 interface of the diverter disk 10 in sequence, and is continuously injected into Y1. At the same time, since M2 and G3 are connected inside the diverter disk 10, the gas-liquid mixed phase compressed medium flows out from Y2, flows through the M2 interface and G3 interface of the diverter disk 10 in sequence, and is continuously injected into Z1. Finally, the gas-liquid mixed phase compressed medium flows out from Z2 and is continuously discharged into the exhaust channel 12 through the M3 interface of the diverter disk 10.As the liquid pistons 4 of X1, Y1, Z1 continue to move centrifugally, the working volumes of X1, Y1, Z1 continue to increase, and the air intake process of X1, Y1, Z1 continues until the radius of the corresponding waveform surface changes from increasing to decreasing. At this time, the through holes 9 of X1, Y1, Z1 are disconnected from the air inlet interfaces G1, G2, G3 in the diverter disk 10, and the air intake process of X1, Y1, Z1 ends. At the same time, the liquid pistons 4 of X2, Y2, Z2 continue to move centripetally, and the working volumes of X2, Y2, Z2 continue to decrease. When the radius of the waveform surface corresponding to X2, Y2, Z2 changes from decreasing to increasing, the through holes 9 of X2, Y2, Z2 are disconnected from the interfaces M1, M2, M3 in the diverter disk 10, and the exhaust and liquid discharge process of X2, Y2, Z2 is the same as that of X1, Y1, Z1. The suction process ends synchronously; as the inner cylinder body 3 continues to rotate, when X1, Y1, and Z1 rotate to the original position of X2, Y2, and Z2, X1, Y1, and Z1 begin to repeat the original working process of X2, Y2, and Z2, and so on, X1, Y1, and Z1 will rotate to the original position of Y1, Z1, and X1, the original position of Y2, Z2, and X2, the original position of Z1, X1, and Y1, and the original position of Z2, X2, and Y2, until returning to the starting point of X1, Y1, and Z1. During this period, different positional relationships correspond to specific working processes of gas compression. So far, the six working cylinders X1, X2, Y1, Y2, Z1, and Z2 have completed the three-stage pressurization of the gas and the compression process of six times per revolution in sequence under the coordination of the control assembly. ;

[0063] The cooling circulation system provides operating conditions for the heat balance, system lubrication and cooling flushing of the compressor. The liquid supply pump 27 serves as a power source to provide circulation power for the cooling circulation system. The liquid reservoir 23 is used to collect the compressed liquid (ionic liquid) and the lubricating medium (ionic liquid) leaked from each sealing pair. The compressed liquid and the lubricating medium are uniformly ionic liquid; the ionic liquid is drawn out from the liquid reservoir 23, and is pressurized by the liquid supply pump 27 after passing through the flange A interface of the liquid reservoir 23, the cooler 24 with the cooler bypass valve 25, and the filter 26 in sequence. The pressurized ionic liquid is divided into two paths: one is the compressor liquid supply pipeline, and the liquid supply pipe check valve 30 is set on the pipeline. The liquid supply pipe check valve 30 is connected to the liquid inlet channel 13 and the diverter plate 1 in the compressor housing 1 in sequence through the pipeline C interface. 0; the other is the compressor spray pipeline, which passes through the mixer check valve 22 and the mixer regulating valve 21 and enters the gas-liquid mixer 20 on the compressor inlet pipeline. The compressor intake air and the ionic liquid are mixed into a two-phase fluid in the gas-liquid mixer 20 and then enter the compressor inlet; a pump safety valve 28 is provided at the outlet of the liquid supply pump 27, and the outlet pipeline of the pump safety valve 28 is connected to the flange B interface of the liquid storage tank 23; an overflow valve 29 is provided at the high point of the entire cooling circulation system, and the outlet of the overflow valve 29 is discharged back to the liquid storage tank 23 through the flange B interface.

[0064] The gas-liquid processing device is a pre-processing and post-processing device for the inlet and outlet gases of the compressor, wherein the gas-liquid mixer 20 is located on the compressor intake pipe to achieve gas-liquid mixing of the compressor intake gas and the compressed liquid; and the gas-liquid separator 14 is located on the compressor exhaust pipe to achieve the separation function of the compressor exhaust gas and the compressed liquid;

[0065] The liquid spraying pipeline from the compressor cooling circulation system is connected to the mixer check valve 22, the mixer check valve 22 is connected to the mixer regulating valve 21, the outlet of the mixer regulating valve 21 is connected to the liquid spraying pipeline inlet of the gas-liquid mixer 20; the inlet pipeline of the gas-liquid mixer 20 is connected to the compressor inlet pipeline, the outlet pipeline of the gas-liquid mixer 20 is connected to the air intake channel 11 in the compressor housing 1, and the air intake channel 11 in the compressor housing 1 is connected to the air intake interface G1 in the diverter plate 10;

[0066] Furthermore, the compressed liquid (ionic liquid) from the cooling circulation system liquid supply pump 27 enters the mixer regulating valve 21 after passing through the mixer check valve 22, and the compressed liquid (ionic liquid) at the outlet of the mixer regulating valve 21 enters the gas-liquid mixer 20. The compressor intake air and the compressed liquid are mixed into a two-phase fluid in the gas-liquid mixer 20, and then enter the compressor intake channel 11 and the intake interface G1;

[0067] The exhaust interface M3 in the diverter disk 10 is connected to the exhaust channel 12 in the compressor housing 1, the exhaust channel 12 in the compressor housing 1 is connected to the inlet pipe of the gas-liquid separator 14, the liquid outlet of the gas-liquid separator 14 is connected to the inlet pipe of the separator hydraulic control valve 15, the outlet pipe of the separator hydraulic control valve 15 is connected to the inlet pipe of the damping circulation valve 16, the outlet pipe of the damping circulation valve 16 is discharged to the fuselage liquid storage tank 23 through the flange D interface, and the gas outlet of the gas-liquid separator 14 is connected to the outside of the boundary.

[0068] Furthermore, the gas-liquid two-phase fluid from the compressor exhaust port M3 and the exhaust channel 12 enters the gas-liquid separator 14, and the compressed liquid (ionic liquid) separated by the gas-liquid separator 14 is discharged to the fuselage liquid storage tank 23 in the cooling circulation system after passing through the separator hydraulic control valve 15 and the damping circulation valve 16; the gas separated by the gas-liquid separator 14 is sent to the outside of the boundary;

[0069] The gas-liquid mixer 20 adopts a countercurrent structure; the mixer regulating valve 21 provides a stable injection pressure for the gas-liquid mixer 20; the gas-liquid separator 14 adopts a coalescing structure; the separator liquid control valve 15 works in a continuous mode, and continuously monitors, controls and adjusts the liquid level of the gas-liquid separator 14.

[0070] In order to prevent the process gas from leaking out of the compression assembly and causing safety risks, the purge device performs positive pressure purge protection on the inside of the compressor casing 1 when the compressor is in operation or non-operation state; the positive pressure purge protection maintains the pressure inside the casing slightly higher than the external atmospheric pressure; the air inlet end of the purge device 17 is connected to the external air source, and the exhaust end of the purge device 17 is connected to the compressor casing 1. At the same time, a purge discharge pipe is provided on the compressor casing 1, and a discharge check valve 18 is provided on the purge discharge pipe, which is connected to the external discharge system after the discharge check valve 18; in this embodiment, nitrogen is used as the purge gas source; the purge device 17 works in a continuous operation mode, and when the compressor is located in an explosive hazardous place, the purge device 17 is preferably a pneumatic type; in this embodiment, a continuous operation fully pneumatic purge device 17 is selected.

[0071] The safety protection device 19 is used to protect the compressor from overpressure in an accident state. It can maintain the working pressure in the compressor casing 1 within a safe range. When the pressure in the casing exceeds the safety limit, it will be safely discharged to protect the safety of the entire compressor; the air inlet end of the safety protection device 19 is connected to the compressor casing 1, and the exhaust end of the safety protection device 19 is connected to the external discharge system; the safety protection device 19 can use a bursting disc or a relief valve, and a relief valve is used in this embodiment; the air inlet end of the relief valve is connected to the compressor casing 1, and the exhaust end of the relief valve is connected to the external discharge system.

[0072] Parts of the present invention not described in detail are prior art.

[0073] The embodiments selected herein for the purpose of disclosing the invention are currently considered to be suitable, but it should be understood that the invention is intended to include all changes and modifications of the embodiments that fall within the scope of the concept and invention.

Claims

1. A multi-stage radially rotating cylinder liquid piston reciprocating compressor, comprising a compressor housing, a compression assembly, a control assembly, a cooling circulation system, a gas-liquid processing device, a purge device and a safety protection device, characterized in that: The compression assembly and control assembly are located inside the compressor housing, and the cooling circulation system, gas-liquid processing device, purge device and safety protection device are located outside the compressor housing; The compression assembly includes a transmission shaft, an inner cylinder, a liquid piston, a choke, a bearing, a retainer and an outer cylinder; the inner cylinder is arranged in the outer cylinder, the transmission shaft is fixed in the center hole of the inner cylinder, the outer cylinder is in a circular ring shape, the inner wall of the outer cylinder is a continuous closed loop uniformly distributed wavy surface, and the inner cylinder center and the outer cylinder geometric center are arranged concentrically during assembly; a plurality of mounting holes are evenly distributed radially and radially along the outer edge of the inner cylinder, and the mounting holes are arranged from the inside to the outside in order of cylinder chambers, compressed liquid, chokes and bearings, so that a number of cylinder chambers are formed and distributed radially on the outer edge of the inner cylinder along the transmission shaft, and the chokes are connected to the outer cylinder through bearings. The cylinder body and the retainer on the side wall are connected, and a through hole is opened in the cylinder chamber along the axis direction of the inner cylinder body in each mounting hole, and the through hole is connected with the control assembly. When the inner cylinder body performs synchronous rotational motion with the transmission shaft, the rotation of the inner cylinder body is converted into radial reciprocating motion of the compressed liquid, the choke plug and the bearing in the mounting hole by means of the continuous closed-loop wavy surface on the inner wall of the outer cylinder body. At the same time, the compressed liquid in the cylinder chamber is subjected to the centrifugal force, which limits the flow of the compressed liquid and forms the liquid piston in the cylinder chamber and on the surface of the choke plug. The liquid piston adopts ionic liquid and is used to block the leakage of the compressed gas. The control assembly includes a diverter plate arranged in the compressor housing and a liquid inlet channel, an air inlet channel and an exhaust channel on the compressor housing. The diverter plate is arranged between the inner cylinder body and the compressor housing, and the diverter plate is installed on the inner wall of the compressor housing. The contact surface of the diverter plate and the inner cylinder body is tightly fitted. A plurality of groups of interfaces corresponding to the conduction holes are arranged on the side of the diverter plate fitted with the inner cylinder body. Each group of interfaces is distributed in an arc shape on the concentric circles on the diverter plate. Each group of interfaces includes a liquid inlet interface L, an air inlet interface G and an exhaust interface M in sequence. The plurality of groups of interfaces are arranged in sequence. Each group of interfaces after arrangement corresponds to a certain level of the compression sequence, namely, the liquid inlet interface Ln, the air inlet interface G and the exhaust interface M of the nth group. Gn and the exhaust port Mn correspond to the nth stage of the compression sequence respectively; the number of compression stages of the compressor is related to the number of compressions per cylinder per revolution of the compressor and the control method of the diverter plate. The number of compressions per cylinder per revolution of the compressor is equal to the number of cycles of change of the radius of the corrugated surface of the inner wall of the outer cylinder body; when the compressor needs to operate in a multi-stage series mode, the exhaust port of the previous group of sequences and the intake port of the next group of sequences are connected through a channel in the diverter plate, that is, M1 of the first group of sequences is connected to G2 of the second group of sequences, and M2 of the second group of sequences is connected to G3 of the third group of sequences, and so on, M(n-1) of the n-1th group of sequences is connected to Gn of the nth group of sequences, so as to realize the n-stage compression and supercharging of the compressor; When the compressor needs to operate in multi-cylinder parallel mode, all the groups of air intake interfaces G that need to operate in parallel are connected through channels in the diverter disk, and all the groups of air exhaust interfaces M that need to operate in parallel are connected in sequence through channels in the diverter disk.

2. The multi-stage radially rotating cylinder liquid piston reciprocating compressor according to claim 1 is characterized in that: The corrugated surface of the inner wall of the outer cylinder body is composed of an ascending section and a descending section. A complete ascending section and a descending section correspond to a complete process of gas compression. The number of periodic changes of the radius of the corrugated surface in the circumferential direction is a positive integer. The center lines of the cylinder chambers are distributed in the same plane or different planes of the radial direction of the inner cylinder body. The number of cylinder chambers is twice the number of periodic changes of the radius of the corrugated surface in the circumferential direction. n Times, n is a positive integer, and at least two cylinders simultaneously participate in the gas compression cycle process of each stage of the compressor.

3. The multi-stage radially rotating cylinder liquid piston reciprocating compressor according to claim 1, characterized in that: The cross-sectional area of ​​the choke plug and the cross-sectional area of ​​the liquid piston are designed to be equal or unequal. At the same time, due to the fluidity of the liquid, the cylinder chamber and the guide hole flow channel through which the liquid piston flows are streamlined.

4. The multi-stage radially rotating cylinder liquid piston reciprocating compressor according to claim 1, characterized in that: The liquid piston, the choke and the bearing of the compression assembly rotate at high speed and participate in radial reciprocating motion during the gas compression process. The bearing is a roller bearing or a sliding bearing. When the bearing is a roller bearing, a columnar box groove is provided at the end of the choke to cover the surface of the roller bearing with a columnar structure, and the axial through hole of the core of the choke leads to the cylindrical working surface of the roller bearing. The mating surface of the retainer and the roller bearing is a conical surface or a cylindrical surface; when the bearing is a sliding bearing, its connecting end adopts a ball head with a neck structure, and a U-shaped groove is provided at the connecting end of the choke, and a ball groove is provided at the bottom of the U-shaped groove. The ball groove is connected to the sliding bearing of the ball head with a neck structure, and the sliding end of the sliding bearing forms an arc-shaped sliding mating surface with the inner wall of the outer cylinder body, and the retainer is provided on the inner wall of the outer cylinder body to form an annular contact band edge with the sliding bearing, and a groove is provided on the sliding end mating surface of the sliding bearing, and the axial through hole of the choke and the axial through hole of the core of the sliding bearing are both connected to the groove opened on the sliding mating surface.

5. The multi-stage radially rotating cylinder liquid piston reciprocating compressor according to claim 3 is characterized in that: The liquid inlet interface L, the air inlet interface G of the first group of multiple groups of interfaces and the exhaust interface M of the last group are through holes in the axial direction of the diverter disk, and the remaining interfaces are not through holes in the axial direction. The outer end of the liquid inlet channel on the compressor casing is connected to the liquid supply pipeline of the cooling circulation system, and the inner end is connected to the liquid inlet interface L of each group of interfaces on the diverter disk. The outer end of the air inlet channel on the compressor casing is connected to the gas-liquid mixer through the compressor inlet pipe, and the inner end is connected to the air inlet interface G in the first group of interfaces corresponding to the first stage on the diverter disk. The outer end of the exhaust channel on the compressor casing is connected to the gas-liquid separator through the compressor outlet pipe, and the inner end is connected to the exhaust interface M in the last group of interfaces corresponding to the last stage on the diverter disk.

6. The multi-stage radially rotating cylinder liquid piston reciprocating compressor according to claim 1, characterized in that: The cooling circulation system includes a liquid reservoir, a cooler, a cooler bypass valve, a filter, a liquid supply pump, a pump safety valve, an overflow valve and a liquid supply pipe check valve. The liquid reservoir is used to collect compressed liquid and lubricating medium leaked from each sealing pair. The compressed liquid and the lubricating medium are uniformly ionic liquids. The ionic liquid is drawn out from the liquid reservoir and pressurized by the liquid supply pump through the flange A interface of the liquid reservoir, the cooler with a cooler bypass valve, and the filter. The pressurized compressed liquid is divided into two paths: one is the compressor liquid supply pipeline, and a liquid supply pipe check valve is arranged on the pipeline. The liquid supply pipe check valve is connected to the compressor through the pipeline C interface. It is connected to the liquid inlet channel in the compressor housing and the liquid inlet interface L in the diverter disk in sequence; the other is the compressor spray pipeline, which passes through the mixer check valve and the mixer regulating valve and enters the gas-liquid mixer on the compressor inlet pipe. The compressor intake air and the ionic liquid are mixed into a two-phase fluid in the gas-liquid mixer and then enter the compressor inlet; a pump safety valve is provided at the outlet of the liquid supply pump, and the outlet pipeline of the pump safety valve is connected to the flange B interface of the liquid storage tank; an overflow valve is provided at the high point of the entire cooling circulation system, and the overflow valve outlet is discharged back to the liquid storage tank through the flange B interface.

7. The multi-stage radially rotating cylinder liquid piston reciprocating compressor according to claim 1, characterized in that: The gas-liquid processing device includes a gas-liquid mixer, a mixer regulating valve, a mixer non-return valve, a gas-liquid separator, a separator hydraulic control valve and a damping circulation valve. The liquid spraying pipeline from the compressor cooling circulation system is connected to the mixer non-return valve, the mixer non-return valve is connected to the mixer regulating valve, and the outlet of the mixer regulating valve is connected to the liquid spraying pipeline inlet of the gas-liquid mixer; the inlet pipeline of the gas-liquid mixer is connected to the inlet pipeline of the compressor, the outlet pipeline of the gas-liquid mixer is connected to the air inlet channel in the compressor housing, and the air inlet channel in the compressor housing is connected to the air inlet interface G in the diverter disk; the exhaust interface M in the diverter disk is connected to the exhaust channel in the compressor housing, the exhaust channel in the compressor housing is connected to the inlet pipeline of the gas-liquid separator, the liquid outlet of the gas-liquid separator is connected to the inlet pipeline of the separator hydraulic control valve, the outlet pipeline of the separator hydraulic control valve is connected to the inlet pipeline of the damping circulation valve, the outlet pipeline of the damping circulation valve is discharged to the fuselage liquid storage tank through the flange D interface, and the gas outlet of the gas-liquid separator is connected to the outside of the boundary.

8. The multi-stage radially rotating cylinder liquid piston reciprocating compressor according to claim 1, characterized in that: The purge device includes a purger and a discharge one-way valve. The air inlet end of the purger is connected to an external air source, and the exhaust end of the purger is connected to a compressor housing. A purge discharge pipe is also provided on the compressor housing. The purge discharge pipe is connected to an external discharge system, and a discharge one-way valve is provided on the purge discharge pipe.

9. The multi-stage radially rotating cylinder liquid piston reciprocating compressor according to claim 1, characterized in that: A safety protection device is arranged outside the compressor housing, an air inlet end of the safety protection device is connected with the compressor housing, and an exhaust end of the safety protection device is connected with an external exhaust system.

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