A gas-liquid-solid coupling dynamics simulation method and system for a diaphragm compressor system

Abstract

A method and system for simulating the gas-liquid-solid coupled dynamics of a diaphragm compressor system. The method includes summarizing different diaphragm compressor physical models for specific application scenarios based on actual needs; modularizing the physical model into gas circuit systems, oil circuit systems, diaphragm motion, auxiliary components, and other heat and mass transfer components; programming and parameter setting using the AMESim language, an advanced modeling and simulation platform for engineering systems, to implement diaphragm compressor simulation calculations in AMESim; verifying the AMESim simulation calculation results, optimizing and adjusting the parameters of the diaphragm compressor physical model through comparative analysis to ensure that the diaphragm compressor physical model meets actual operating conditions; using the diaphragm compressor physical model that meets actual operating conditions, solving related problems based on simulation needs, and optimizing the diaphragm compressor system or structure. The present invention can replicate the complex working process of the gas-liquid-solid coupled operation of a diaphragm compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of diaphragm compressors, and in particular to a gas-liquid-solid coupling dynamics simulation method and system for a diaphragm compressor system. Background Art

[0002] A diaphragm compressor is a positive displacement compressor that uses a diaphragm to separate the oil and gas sides. Its operating principle is: a motor drives the crankshaft and connecting rod, driving the piston in reciprocating motion to increase and reduce the pressure of the high-pressure oil. The high-pressure oil then pushes the diaphragm to compress and discharge the gas. Due to their excellent sealing properties and high compression ratio, diaphragm compressors are widely used in the hydrogen energy industry, especially in hydrogen refueling stations.

[0003] Maintaining a dynamic balance of hydraulic oil mass within the compressor chamber is a major challenge during the development and design of diaphragm compressors due to the compressibility and potential leakage of hydraulic oil. Current diaphragm compressor development and design primarily relies on the optimal selection of components, including the plunger charge pump and relief valve, to ensure proper operation. Furthermore, the hydraulic oil pressure and hydrogen pressure in a diaphragm compressor fluctuate in tandem, and variations in the hydraulic oil mass within the oil chamber directly impact the compressor's overall displacement and safety. Therefore, conducting thorough experimental verification during the development of new diaphragm compressor models is both costly and inherently risky. Due to the flammable and leaky nature of hydrogen as a small molecule, many key parameters are either unavailable or poorly measured. Furthermore, the operation of a diaphragm compressor involves gas-liquid-solid coupling, including diaphragm deformation, gas compression, hydraulic oil compression, and drive mechanism motion. Reproducing the complex operation of a diaphragm compressor using only theoretical research or numerical calculations is difficult. Current three-dimensional simulations of diaphragm compressors cannot simultaneously account for the complex multi-phase coupling of the relief valve, plunger pump, inlet and exhaust valves, and diaphragm motion. Therefore, how to predict and simulate the performance of diaphragm compressors is a difficult problem that is difficult to overcome in the current research and development of diaphragm compressors. Summary of the Invention

[0004] The purpose of the present invention is to address the problems in the above-mentioned prior art and provide a method and system for simulating the gas-liquid-solid coupling dynamics of a diaphragm compressor system, so as to fill the defect that it is difficult to reproduce the complex working process of the gas-liquid-solid coupling of a diaphragm compressor by only using theoretical research or numerical calculation, and provide new technical support for the research and development of new models of diaphragm compressors.

[0005] In order to achieve the above object, the present invention has the following technical solutions:

[0006] A gas-liquid-solid coupled dynamics simulation method for a diaphragm compressor system, comprising:

[0007] Summarize different diaphragm compressor physical models in specific application scenarios based on actual needs;

[0008] Modularize the gas system, oil system, diaphragm movement, auxiliary components and other heat and mass transfer components of the diaphragm compressor physical model;

[0009] According to the physical model of the diaphragm compressor after modular partitioning, the advanced modeling and simulation platform for engineering systems AMESim language is used for programming and parameter setting, and the simulation calculation of the diaphragm compressor is realized in AMESim;

[0010] Verify the simulation calculation results of AMESim, and optimize and adjust the parameters of the diaphragm compressor physical model through comparative analysis to make the diaphragm compressor physical model meet the actual operating conditions;

[0011] Use a physical model of a diaphragm compressor that meets actual operating conditions to solve related problems based on simulation requirements and optimize the selection and design of the diaphragm compressor system or structure.

[0012] As a preferred solution, when summarizing different diaphragm compressor physical models in specific application scenarios based on actual needs, the actual needs include component selection and optimization design, compressor fault diagnosis, system simulation and optimization, performance prediction and verification, and research and development of new ultra-high pressure models.

[0013] As a preferred solution, the diaphragm compressor physical model includes a diaphragm compressor integrated module composed of a hydraulic cylinder drive module, a plunger pump module, a relief valve module, an intake valve module, an exhaust valve module, a hydraulic cylinder module, a diaphragm motion module, a pneumatic cylinder module and a follower valve module, as well as a data acquisition module and a data transmission module;

[0014] The hydraulic cylinder drive module is used to simulate the process of the diaphragm compressor simulating the crank-connecting rod mechanism driving the piston movement;

[0015] The plunger pump module and the overflow valve module are used to simulate the oil inlet and oil outlet processes of the diaphragm compressor cylinder respectively;

[0016] The hydraulic cylinder module is used to simulate the effective volume movement of hydraulic oil in the diaphragm compressor cylinder.

[0017] As a preferred solution, the physical model of the diaphragm compressor after modular partitioning is written and parameterized using the AMESim language, an advanced modeling and simulation platform for engineering systems. When the simulation calculation of the diaphragm compressor is implemented in AMESim, the piston movement in the hydraulic cylinder drive module is directly driven by the crank-connecting rod mechanism, and the motion law of the piston is described by the following formula:

[0018]

[0019] Where: x is the piston displacement; φ is the crankshaft angle; r is the crankshaft radius; λ is the ratio of the crankshaft radius r to the connecting rod length l; ν is the piston speed; ω is the angular velocity;

[0020] By converting the above mathematical formula into AMESim modular modeling and simulation language, a hydraulic cylinder drive module is formed and then connected to the hydraulic cylinder module.

[0021] As a preferred solution, the plunger movement of the plunger pump module is directly driven by the crank-connecting rod mechanism and its own spring structure, but there is a phase angle with the piston movement in the hydraulic cylinder drive module. The plunger movement law is described by the following formula:

[0022]

[0023] Where: x zs is the displacement of the plunger pump plunger; r is the radius of the plunger drive eccentric wheel; θ is the rotation angle of the plunger drive eccentric wheel; a is the eccentric distance of the plunger pump drive eccentric wheel; v zs is the speed of the plunger pump plunger;

[0024] The plunger-driven eccentric is described by its phase difference with the crankshaft rotation:

[0025]

[0026] Where: The phase difference between the rotation angle of the plunger-driven eccentric and the rotation angle of the crankshaft;

[0027] By converting the above mathematical formula into AMESim modular modeling and simulation language, a plunger pump module is formed and then connected with the hydraulic cylinder module.

[0028] As a preferred solution, the instantaneous flow of the relief valve module is determined by the relief valve opening, the pressure difference on both sides of the relief valve and the medium properties, and is described by the following formula:

[0029]

[0030] Where: q oil is the instantaneous flow of the overflow valve; C df is the overflow valve inlet flow coefficient; D f is the inlet diameter of the relief valve;

[0031] Δx f is the relief valve core lift; ρ is the hydraulic oil density; p oil is the oil pressure in the cavity; k s is the spring stiffness of the overflow valve; Δx spring is the compression amount of the overflow valve spring; p cis the pressure inside the relief valve core; C db is the overflow valve outlet flow coefficient; D b is the outlet diameter of the relief valve;

[0032] Simplify the above mathematical formula and regard the pressure of the relief valve core as atmospheric pressure, then:

[0033]

[0034] By converting the above mathematical formula into AMESim modular modeling and simulation language, an overflow valve module is formed and then connected to the hydraulic cylinder module.

[0035] As a preferred solution, the intake valve module and the exhaust valve module are used to simulate the intake and exhaust processes of the diaphragm compressor air cavity volume respectively, and the pneumatic cylinder module is used to simulate the gas compression process caused by the change of the diaphragm compressor air cavity volume;

[0036] The valve spool movement in the intake and exhaust valve modules is described by the following equation:

[0037]

[0038] Where: M v is the valve core mass; H vc is the displacement of the intake valve core; H vd is the exhaust valve core displacement; κ v is the flow coefficient; p gs is the pressure in the intake pipe; p g A is the pressure in the air chamber of the diaphragm compressor; v K is the flow area of ​​the valve core; ν H is the spring stiffness of the valve core; ν0 is the spring pre-compression amount;

[0039] By converting the above mathematical formulas into AMESim modular modeling and simulation language, an intake valve module and an exhaust valve module are formed, which are then connected to the pneumatic cylinder module.

[0040] As a preferred solution, by simulating the hydraulic oil entering from the plunger pump module and being discharged from the overflow valve module, the hydraulic pressure is applied to the diaphragm of the diaphragm compressor in the hydraulic cylinder module to drive the diaphragm movement in the diaphragm motion module, thereby realizing the establishment of the liquid phase flow process of the diaphragm compressor; by simulating the gas volume in the pneumatic cylinder module to change under the drive of the diaphragm motion module, thereby causing the gas pressure change in the pneumatic cylinder module and the movement of the intake valve module and the exhaust valve module, thereby realizing the establishment of the gas phase flow process of the diaphragm compressor; by simulating the liquid phase flow process of the diaphragm compressor through the diaphragm motion module to drive the gas phase flow process, thereby realizing the establishment of the gas-liquid-solid coupling process of the diaphragm compressor;

[0041] The relationship between the maximum deflection of the diaphragm center and the volume of the diaphragm cavity of a single-index diaphragm compressor is described by the following formula:

[0042]

[0043] Where: V q is the semi-cavity volume under the maximum center deflection of the diaphragm; R is the diaphragm cavity radius; W0 is the maximum deflection of the diaphragm center; z is the diaphragm cavity index coefficient; since the change in the diaphragm center deflection caused by diaphragm movement is linearly related to the change in diaphragm cavity volume, the movement of the diaphragm surface is replaced by a reciprocating cylinder model, and the above formula is converted into the AMESim modular modeling and simulation language to form a diaphragm motion module, which is connected with the hydraulic cylinder module and the pneumatic cylinder module, thereby realizing the establishment of a gas-liquid-solid coupling dynamic model of the diaphragm compressor system based on AMESim.

[0044] As a preferred solution, the diaphragm compressor integrated module includes a first-stage diaphragm compressor integrated module and a second-stage diaphragm compressor integrated module; the first-stage diaphragm compressor integrated module and the second-stage diaphragm compressor integrated module are the overall component integration of two single-stage diaphragm compressors, except that the unit node parameter settings are different, the first-stage diaphragm compressor integrated module adopts a relief valve module, and the second-stage diaphragm compressor integrated module adopts a follower valve module;

[0045] The spool valve module is described by the following formula:

[0046]

[0047] Where: q oil,ylvalve is the flow rate of the servo valve; C dv is the flow coefficient of the oil outlet of the servo valve; D f is the outlet diameter of the servo valve; p gas,d is the exhaust pressure in the first-stage diaphragm compressor integrated module;

[0048] The exhaust pressure in the first-stage diaphragm compressor integrated module controls the opening and closing characteristics of the servo valve model in the second-stage diaphragm compressor integrated module through the data transmission module, thereby realizing the overflow function of the servo valve model. The above formula is converted into the AMESim modular modeling and simulation language, integrated into the second-stage diaphragm compressor integrated module, and coordinated with other modules to establish the gas-liquid-solid coupling dynamic model of the diaphragm compressor system with servo valve based on AMESim.

[0049] The output data from the first-stage diaphragm compressor integrated module and the second-stage diaphragm compressor integrated module are analyzed and modulated, and finally output to the user end through the data acquisition module.

[0050] A diaphragm compressor system gas-liquid-solid coupled dynamics simulation system, comprising:

[0051] Demand summary module, used to summarize different diaphragm compressor physical models in specific application scenarios based on actual needs;

[0052] Physical model partitioning module, used to modularize and partition the diaphragm compressor physical model into gas circuit system, oil circuit system, diaphragm movement, auxiliary components and other heat and mass transfer components;

[0053] AMESim simulation calculation module is used to write and set parameters based on the modular partitioned diaphragm compressor physical model using the AMESim language, an advanced modeling and simulation platform for engineering systems, to implement simulation calculations of the diaphragm compressor in AMESim;

[0054] The physical model optimization and adjustment module is used to verify the simulation calculation results of AMESim. Through comparative analysis, the parameters of the diaphragm compressor physical model are optimized and adjusted to make the diaphragm compressor physical model meet the actual operating conditions.

[0055] The physical model selection and design module is used to use the physical model of the diaphragm compressor that meets the actual operating conditions, solve related problems based on simulation requirements, and optimize the selection and design of the diaphragm compressor system or structure.

[0056] Compared with the prior art, the present invention has at least the following beneficial effects:

[0057] Based on actual needs, different diaphragm compressor physical models for specific application scenarios are summarized. The resulting diaphragm compressor physical model is modularly partitioned into the gas system, oil system, diaphragm movement, auxiliary components, and other heat and mass transfer components for subsequent debugging and simulation operation. The model is then written and parameterized using the AMESim language, an advanced modeling and simulation platform for engineering systems, to implement simulation calculations of the diaphragm compressor in AMESim. The AMESim simulation calculation results are verified by comparing with other reliable data sets. Through comparative analysis, the parameters of the diaphragm compressor physical model are optimized and adjusted to ensure that the diaphragm compressor physical model meets actual operating conditions. Finally, the diaphragm compressor physical model that meets actual operating conditions is used to solve related problems based on simulation requirements and optimize the selection and design of the diaphragm compressor system or structure. The present invention enables the study of the performance characteristics of diaphragm compressors as a whole or as components, as well as oil or gas circuits, as well as simulation calculations of gas-liquid-solid three-phase coupling. This effectively addresses the drawback of traditional methods that make it difficult to reproduce the gas-liquid-solid coupling process of diaphragm compressors. The simulation results are reasonable and accurate, and can be used to guide the development of new diaphragm compressor models and the performance evaluation, analysis, and fault diagnosis of existing models in a variety of specific application scenarios. The present invention's gas-liquid-solid coupling dynamics simulation method for diaphragm compressor systems has good operability and reliability in the actual R&D and design process, and can be used to guide the design and development work of diaphragm compressor practitioners. BRIEF DESCRIPTION OF THE DRAWINGS

[0058] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the specific embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0059] Figure 1 This is a flow chart of a method for simulating the gas-liquid-solid coupled dynamics of a diaphragm compressor system according to an embodiment of the present invention;

[0060] Figure 2 Schematic diagram of a gas-liquid-solid coupled dynamics simulation model of a single-stage diaphragm compressor system according to an embodiment of the present invention;

[0061] Figure 3 This is a diagram showing the simulation results of the diaphragm movement of a single-stage diaphragm compressor system according to an embodiment of the present invention;

[0062] Figure 4 This is a simulation result diagram of the oil pressure and air pressure changes of a single-stage diaphragm compressor system according to an embodiment of the present invention;

[0063] Figure 5 This is a diagram showing the simulation results of the opening and closing conditions and flow characteristics of the plunger pump of a single-stage diaphragm compressor system according to an embodiment of the present invention;

[0064] Figure 6 Graph showing the simulation results of the opening and closing conditions and flow characteristics of the overflow valve of a single-stage diaphragm compressor system according to an embodiment of the present invention;

[0065] Figure 7 Schematic diagram of a gas-liquid-solid coupled dynamics simulation model of a two-stage diaphragm compressor system according to an embodiment of the present invention;

[0066] Figure 8 This is a diagram showing the two-stage oil pressure simulation results of a two-stage diaphragm compressor system according to an embodiment of the present invention;

[0067] Figure 9 This is a diagram showing the simulation results of the diaphragm movement of a two-stage diaphragm compressor system according to an embodiment of the present invention;

[0068] Figure 10 This is a diagram showing the simulation results of the opening and closing conditions of the plunger pump and the overflow valve and the flow characteristics of the gas-liquid-solid coupling dynamics simulation of the two-stage diaphragm compressor system according to an embodiment of the present invention;

[0069] In the attached figure: 1-hydraulic cylinder drive module; 2-plunger pump module; 3-overflow valve module; 4-intake valve module; 5-exhaust valve module; 6-hydraulic cylinder module; 7-diaphragm movement module; 8-pneumatic cylinder module; 9-follow-up valve module; J1-first-stage diaphragm compressor integrated module; J2-second-stage diaphragm compressor integrated module; J3-data acquisition module; J4-data transmission module. DETAILED DESCRIPTION

[0070] The technical solutions of the present invention will be clearly and completely described below in conjunction with the embodiments. Obviously, the embodiments described are only a part of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0071] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense. For example, it can be fixedly connected, detachably connected, or integrally connected; it can be mechanically connected or electrically connected; it can be directly connected, or indirectly connected through an intermediate medium, or it can be internally connected between two components, or it can be wirelessly connected or wired. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances. In addition, the technical features involved in the embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other.

[0072] Example 1

[0073] See also Figure 1 A method for simulating gas-liquid-solid coupled dynamics of a diaphragm compressor system according to an embodiment of the present invention includes:

[0074] S1. Summarize different diaphragm compressor physical models in specific application scenarios based on actual needs;

[0075] S2. Modularize and partition the diaphragm compressor physical model into gas system, oil system, diaphragm movement, auxiliary components and other heat and mass transfer components;

[0076] S3. Based on the physical model of the diaphragm compressor after modular partitioning, the advanced modeling and simulation platform for engineering systems AMESim is used to write and set parameters, and the simulation calculation of the diaphragm compressor is realized in AMESim;

[0077] S4. Verify the simulation calculation results of AMESim, and optimize and adjust the parameters of the diaphragm compressor physical model through comparative analysis to make the diaphragm compressor physical model meet the actual operating conditions;

[0078] S5. Use a physical model of the diaphragm compressor that meets actual operating conditions to solve related problems based on simulation requirements and optimize the selection and design of the diaphragm compressor system or structure.

[0079] In one possible implementation, step S1 summarizes the component types and diaphragm compressor system assemblies required for actual simulation needs. Specific actual needs include: component selection and optimization design, compressor fault diagnosis, system simulation and optimization, performance prediction and verification, and research and development of new ultra-high pressure models.

[0080] The AMESim simulation method described above enables prediction and overall evaluation of diaphragm compressor performance. This allows simulation models to reflect diaphragm compressor operating characteristics before hardware system design and fabrication, reducing risks and the number of physical tests required. AMESim (Advanced Modeling Environment for performing Simulation of engineering systems) is an advanced modeling and simulation platform for engineering systems. The AMESim modeling process is presented through an intuitive graphical interface, allowing users to create, expand, or modify models without having to learn a specialized programming language. AMESim provides a standard, standardized secondary development platform, allowing users to write their own code for custom modeling and integrate their custom models into the AMESim model library. AMESim offers multiple simulation modes, including dynamic, steady-state, discontinuous, continuous, and batch simulation, enabling users to perform dynamic analysis, parameter optimization, and steady-state analysis. AMESim also offers tools for linearization, modal analysis, spectrum analysis, and model simplification, greatly facilitating user analysis and system optimization. AMESim has an intelligent solver for algorithms, which can automatically select the best integration algorithm from a variety of optional algorithms based on the mathematical characteristics of the model built by the user, and dynamically switch the integration algorithm and adjust the integration step size according to the characteristics of the system at different simulation moments to shorten the simulation time and improve the simulation accuracy.

[0081] The physical model of the diaphragm compressor described in the embodiment of the present invention includes a diaphragm compressor integrated module composed of a hydraulic cylinder drive module 1, a plunger pump module 2, a relief valve module 3, an intake valve module 4, an exhaust valve module 5, a hydraulic cylinder module 6, a diaphragm movement module 7, a pneumatic cylinder module 8 and a follower valve module 9, as well as a data acquisition module J3 and a data transmission module J4.

[0082] like Figure 2As shown, the gas-liquid-solid coupled dynamic simulation model of a single-stage diaphragm compressor system according to an embodiment of the present invention includes: a hydraulic cylinder drive module 1, a plunger pump module 2, a relief valve module 3, an intake valve module 4, an exhaust valve module 5, a hydraulic cylinder module 6, a diaphragm motion module 7, and a pneumatic cylinder module 8. Specifically, the hydraulic drive module 1 simulates the process of piston movement driven by the crankshaft-connecting rod mechanism; the plunger pump module 2 and the relief valve module 3 simulate the oil intake and discharge processes of the diaphragm compressor cylinder, respectively; and the hydraulic cylinder module 6 simulates the effective volumetric movement of the hydraulic oil in the diaphragm compressor cylinder. This completes the modeling of the diaphragm compressor hydraulic drive system. The intake valve module 4 and the exhaust valve module 5 simulate the intake and exhaust processes of the diaphragm compressor air chamber, respectively; and the pneumatic cylinder module 8 simulates the gas compression process caused by the change in the diaphragm compressor air chamber volume. This completes the modeling of the diaphragm compressor pneumatic system. The diaphragm motion module 7 simulates the process of the diaphragm compressor hydraulic drive system driving the diaphragm compressor pneumatic system. This realizes the movement of the diaphragm compressor diaphragm and the gas-liquid-solid coupled process.

[0083] When implementing the simulation calculation of the diaphragm compressor in AMESim, the piston movement in the hydraulic cylinder drive module 1 is directly driven by the crank-connecting rod mechanism. The motion law of the piston is described by the following formula:

[0084]

[0085] Where: x is the piston displacement; φ is the crankshaft angle; r is the crankshaft radius; λ is the ratio of the crankshaft radius r to the connecting rod length l; v is the piston speed; ω is the angular velocity;

[0086] By converting the above mathematical formula into AMESim modular modeling and simulation language, a hydraulic cylinder drive module 1 is formed, which is then connected to the hydraulic cylinder module 6.

[0087] The plunger motion of the plunger pump module 2 is directly driven by the crank-connecting rod mechanism and its own spring structure, but there is a phase angle with the piston motion in the hydraulic cylinder drive module 1. The plunger motion law is described by the following formula:

[0088]

[0089] Where: x zs is the displacement of the plunger pump plunger; r is the radius of the plunger drive eccentric wheel; θ is the rotation angle of the plunger drive eccentric wheel; a is the eccentric distance of the plunger pump drive eccentric wheel; v zs is the speed of the plunger pump plunger;

[0090] The plunger-driven eccentric is described by its phase difference with the crankshaft rotation:

[0091]

[0092] Where: The phase difference between the rotation angle of the plunger-driven eccentric and the rotation angle of the crankshaft;

[0093] By converting the above mathematical formula into AMESim modular modeling and simulation language, a plunger pump module 2 is formed, which is then connected to the hydraulic cylinder module 6.

[0094] The instantaneous flow of the relief valve module 3 is determined by the relief valve opening, the pressure difference on both sides of the relief valve and the medium properties. The flow of the direct-acting relief valve can be described by the following formula:

[0095]

[0096] Where: q oil is the instantaneous flow of the overflow valve; C df is the overflow valve inlet flow coefficient; D f is the inlet diameter of the relief valve;

[0097] Δx f is the relief valve core lift; ρ is the hydraulic oil density; p oil is the oil pressure in the cavity; k s is the spring stiffness of the overflow valve; Δx spring is the compression amount of the overflow valve spring; p c is the pressure inside the relief valve core; C db is the overflow valve outlet flow coefficient; D b is the outlet diameter of the relief valve;

[0098] Simplify the above mathematical formula and regard the pressure of the relief valve core as atmospheric pressure, then:

[0099]

[0100] By converting the above mathematical formula into AMESim modular modeling and simulation language, the overflow valve module 3 is formed and then connected to the hydraulic cylinder module 6.

[0101] Furthermore, the movement of the valve cores in the intake valve module 4 and the exhaust valve module 5 is described by the following formula:

[0102]

[0103] Where: M ν is the valve core mass; H νc is the displacement of the intake valve core; H νd is the exhaust valve core displacement; κ ν is the flow coefficient; p gs is the pressure in the intake pipe; p g A is the pressure in the air chamber of the diaphragm compressor; ν K is the flow area of ​​the valve core;ν H is the spring stiffness of the valve core; ν0 is the spring pre-compression amount;

[0104] By converting the above mathematical formula into AMESim modular modeling simulation language, an intake valve module 4 and an exhaust valve module 5 are formed, which are then connected to a pneumatic cylinder module 8 .

[0105] By simulating the hydraulic oil entering from the plunger pump module 2 and being discharged from the overflow valve module 3, the liquid pressure is applied to the diaphragm of the diaphragm compressor in the hydraulic cylinder module 6, driving the diaphragm movement in the diaphragm motion module 7, thereby realizing the establishment of the liquid phase flow process of the diaphragm compressor; by simulating the gas volume in the pneumatic cylinder module 8 changing under the drive of the diaphragm motion module 7, thereby causing the gas pressure in the pneumatic cylinder module 8 to change and the movement of the intake valve module 4 and the exhaust valve module 5, thereby realizing the establishment of the gas phase flow process of the diaphragm compressor; by simulating the liquid phase flow process of the diaphragm compressor through the diaphragm motion module 7 to drive the gas phase flow process, thereby realizing the establishment of the gas-liquid-solid coupling process of the diaphragm compressor.

[0106] The relationship between the maximum deflection of the diaphragm center and the volume of the diaphragm cavity of a single-index diaphragm compressor is described by the following formula:

[0107]

[0108] Where: V q is the semi-cavity volume under the maximum center deflection of the diaphragm; R is the diaphragm cavity radius; W0 is the maximum center deflection of the diaphragm; z is the diaphragm cavity index coefficient; since the change in the diaphragm center deflection caused by diaphragm movement is linearly related to the change in diaphragm cavity volume, the movement of the diaphragm surface is replaced by a reciprocating cylinder model, and the above formula is converted into the AMESim modular modeling and simulation language to form a diaphragm motion module 7, which is connected to the hydraulic cylinder module 6 and the pneumatic cylinder module 8, thereby realizing the establishment of a gas-liquid-solid coupling dynamic model of the diaphragm compressor system based on AMESim.

[0109] Furthermore, according to the actual structural and operating parameters of the single-stage diaphragm compressor operating conditions, including intake pressure of 6.2 MPa, exhaust pressure of 22.1 MPa, speed of 420 rpm, membrane cavity diameter of 70 mm, plunger pump plunger diameter of 20 mm, plunger pump plunger stroke of 10 mm, and crank radius of 200 mm, the parameters of different modules were set and calculated according to the actual physical model parameters in the AMESim software.

[0110] like Figure 3As shown, through the above method and parameter settings, the movement of the center position of the diaphragm of the diaphragm compressor is simulated and calculated in the diaphragm motion module 7 simulated by AMESim. It can be seen that the diaphragm of the diaphragm compressor can reach the wall of the diaphragm compressor air cavity without hitting the set oil cavity wall, which belongs to the normal operating condition.

[0111] like Figure 4 As shown, through the above method and parameter settings, the simulation calculation in the pneumatic cylinder module 8 and the hydraulic cylinder module 6 simulated by AMESim shows that the oil pressure and air pressure of the single-stage diaphragm compressor have the same trend of change with the crank angle. During the working time when the relief valve core is open, the oil pressure in the diaphragm compressor cavity is higher than the air pressure, which is consistent with the actual operation of the diaphragm compressor.

[0112] like Figures 5 and 6 As shown, through the above method and parameter settings, the opening and closing characteristics and flow characteristics of the plunger pump and the relief valve are simulated and calculated in the plunger pump module 2 and the relief valve module 3 simulated by AMESim. It can be seen that the plunger pump and the relief valve will only open when the pressure in the oil chamber is higher than the set valve core opening pressure.

[0113] In summary, through the analysis of the above-mentioned AMESim simulation calculation model, simulation method and simulation results, it is possible to study the oil pressure and air pressure following characteristics of single-stage diaphragm compressors, and study the diaphragm movement and plunger pump and overflow valve flow characteristics, so as to guide the development and research purpose of new models.

[0114] Example 2

[0115] Another embodiment of the present invention provides an AMESim-based two-stage diaphragm compressor system gas-liquid-solid coupling dynamics simulation model and simulation method, which are used for simulating the change characteristics of the two-stage oil pressure coupling of the two-stage diaphragm compressor. Unlike the above-mentioned embodiment 1, the simulation model described in this embodiment is targeted at the two-stage diaphragm compressor, and the specific simulation requirement in its simulation method is the simulation study of the change characteristics of the two-stage oil pressure coupling. Its specific physical model is changed from a single-stage compressor to a two-stage diaphragm compressor, and its first-stage diaphragm compressor exhaust pressure is equal to the second-stage diaphragm compressor intake pressure. Its first-stage diaphragm compressor oil overflow model is the same as that of embodiment 1, using a relief valve structure, while its second-stage diaphragm compressor oil overflow model uses a follower valve structure.

[0116] like Figure 7As shown, the diaphragm compressor integrated module in the gas-liquid-solid coupled dynamics simulation model of the two-stage diaphragm compressor system according to the embodiment of the present invention includes a first-stage diaphragm compressor integrated module J1 and a second-stage diaphragm compressor integrated module J2; the first-stage diaphragm compressor integrated module J1 and the second-stage diaphragm compressor integrated module J2 are the overall component integrations of two single-stage diaphragm compressors. In addition to the different unit node parameter settings, the first-stage diaphragm compressor integrated module J1 adopts the overflow valve module 3, and the second-stage diaphragm compressor integrated module J2 adopts the servo valve module 9; the servo valve module 9 is described by the following formula:

[0117]

[0118] Where: q oil,ylvalve is the flow rate of the servo valve; C dv is the flow coefficient of the oil outlet of the servo valve; D f is the outlet diameter of the servo valve; p gas,d is the exhaust pressure in the first-stage diaphragm compressor integrated module J1;

[0119] The exhaust pressure in the first-stage diaphragm compressor integrated module J1 controls the opening and closing characteristics of the servo valve model in the second-stage diaphragm compressor integrated module J2 through the data transmission module J4, thereby realizing the overflow function of the servo valve model. The above formula is converted into the AMESim modular modeling and simulation language, connected to the second-stage diaphragm compressor integrated module J2, and coordinated with other modules to realize the establishment of the gas-liquid-solid coupling dynamic model of the diaphragm compressor system with servo valve based on AMESim.

[0120] The output data from the first-stage diaphragm compressor integrated module J1 and the second-stage diaphragm compressor integrated module J2 are analyzed and modulated, and finally output to the demand user end through the data acquisition module J3.

[0121] Furthermore, the first-stage intake pressure was set to 1.7 MPa, the intermediate pressure was set to 6.3 MPa, and the exhaust pressure was set to 22.1 MPa, and the gas-liquid-solid coupling dynamic simulation calculation based on AMESim was performed on a two-stage diaphragm compressor product.

[0122] like Figure 8 As shown in FIG, through the above model and parameter settings, the two-stage oil pressure change characteristic curve of the two-stage diaphragm compressor is obtained by simulation calculation in the data output acquisition module J3 of the AMESim simulation; Figure 9 As shown in Figure 2, considering the compressibility of the hydraulic oil, both the primary and secondary diaphragms hit the cylinder wall, which is a normal operating condition; Figure 10 As shown, the first-level plunger pump, the second-level plunger pump, the first-level overflow valve, and the second-level overflow valve are opened in sequence, and the results are reasonable and meet the preset research requirements.

[0123] The gas-liquid-solid coupling dynamics simulation model and calculation method of the diaphragm compressor system based on AMESim in the present invention have good operability and reliability in the actual research and development design process, and can guide the design and development work of diaphragm compressor practitioners.

[0124] Another embodiment of the present invention further provides a gas-liquid-solid coupled dynamics simulation system for a diaphragm compressor system, comprising:

[0125] Demand summary module, used to summarize different diaphragm compressor physical models in specific application scenarios based on actual needs;

[0126] Physical model partitioning module, used to modularize and partition the diaphragm compressor physical model into gas system, oil system, diaphragm movement, auxiliary components and other heat and mass transfer components;

[0127] AMESim simulation calculation module is used to write and set parameters based on the modular partitioned diaphragm compressor physical model using the AMESim language, an advanced modeling and simulation platform for engineering systems, to implement simulation calculations of the diaphragm compressor in AMESim;

[0128] The physical model optimization and adjustment module is used to verify the simulation calculation results of AMESim. Through comparative analysis, the parameters of the diaphragm compressor physical model are optimized and adjusted to make the diaphragm compressor physical model meet the actual operating conditions.

[0129] The physical model selection and design module is used to use the physical model of the diaphragm compressor that meets the actual operating conditions, solve related problems based on simulation requirements, and optimize the selection and design of the diaphragm compressor system or structure.

[0130] An embodiment of the present invention further provides an electronic device, characterized by comprising:

[0131] A memory storing at least one instruction; and a processor executing the instruction stored in the memory to implement the gas-liquid-solid coupled dynamic simulation method of the diaphragm compressor system.

[0132] An embodiment of the present invention further provides a computer-readable storage medium storing a computer program. When the computer program is executed by a processor, the gas-liquid-solid coupled dynamic simulation method of the diaphragm compressor system is implemented.

[0133] Exemplarily, the instructions stored in the memory may be divided into one or more modules / units, which are stored in a computer-readable storage medium and executed by the processor to implement the gas-liquid-solid coupled dynamic simulation method for a diaphragm compressor system of the present invention. The one or more modules / units may be a series of computer-readable instruction segments capable of performing specific functions, which are used to describe the execution process of the computer program in the server.

[0134] The electronic device may be a computing device such as a smartphone, laptop, PDA, or cloud server. The electronic device may include, but is not limited to, a processor and memory. Those skilled in the art will appreciate that the electronic device may include more or fewer components, or a combination of certain components, or different components. For example, the electronic device may also include input / output devices, network access devices, buses, and the like.

[0135] The processor may be a central processing unit (CPU), other general-purpose processors, digital signal processors (DSP), application-specific integrated circuits (ASIC), field-programmable gate arrays (FPGA), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. The general-purpose processor may be a microprocessor or any conventional processor, etc.

[0136] The memory may be an internal storage unit of the server, such as a hard disk or memory of the server. The memory may also be an external storage device of the server, such as a plug-in hard disk equipped on the server, a Smart Media Card (SMC), a Secure Digital (SD) card, a Flash Card, etc. Furthermore, the memory may include both an internal storage unit of the server and an external storage device. The memory is used to store the computer-readable instructions and other programs and data required by the server. The memory may also be used to temporarily store data that has been output or is about to be output.

[0137] It should be noted that the information interaction, execution process, etc. between the above-mentioned module units are based on the same concept as the method embodiment. Their specific functions and technical effects can be found in the method embodiment part and will not be repeated here.

[0138] Those skilled in the art can clearly understand that, for the convenience and brevity of description, only the division of the above-mentioned functional units and modules is used as an example for illustration. In actual applications, the above-mentioned functions can be distributed and completed by different functional units and modules as needed, that is, the internal structure of the device can be divided into different functional units or modules to complete all or part of the functions described above. The functional units and modules in the embodiment can be integrated into one processing unit, or each unit can exist physically alone, or two or more units can be integrated into one unit. The above-mentioned integrated unit can be implemented in the form of hardware or in the form of software functional units. In addition, the specific names of the functional units and modules are only for the convenience of distinguishing each other, and are not used to limit the scope of protection of this application. The specific working process of the units and modules in the above-mentioned system can refer to the corresponding process in the aforementioned method embodiment, and will not be repeated here.

[0139] If the integrated unit is implemented in the form of a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the present application implements all or part of the processes in the above-mentioned embodiment method by instructing the relevant hardware through a computer program. The computer program can be stored in a computer-readable storage medium. When the computer program is executed by a processor, it can implement the steps of the above-mentioned various method embodiments. Among them, the computer program includes computer program code, which can be in source code form, object code form, executable file or some intermediate form. The computer-readable medium can at least include: any entity or device that can carry the computer program code to the camera / terminal device, a recording medium, a computer memory, a read-only memory (ROM), a random access memory (RAM), an electrical carrier signal, a telecommunications signal and a software distribution medium. For example, a USB flash drive, a mobile hard disk, a magnetic disk or an optical disk.

[0140] In the above embodiments, the description of each embodiment has its own focus. For parts that are not described or recorded in detail in a certain embodiment, reference can be made to the relevant description of other embodiments.

[0141] The above-described embodiments are only used to illustrate the technical solutions of the present application, rather than to limit them. Although the present application has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. These modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the various embodiments of the present application, and should all be included in the scope of protection of the present application.

Claims

1. A gas-liquid-solid coupled dynamics simulation method for a diaphragm compressor system, characterized in that: include: Summarize different diaphragm compressor physical models in specific application scenarios based on actual needs; Modularize the gas system, oil system, diaphragm movement, auxiliary components and other heat and mass transfer components of the diaphragm compressor physical model; According to the physical model of the diaphragm compressor after modular partitioning, the advanced modeling and simulation platform for engineering systems AMESim language is used for programming and parameter setting, and the simulation calculation of the diaphragm compressor is realized in AMESim; Verify the simulation calculation results of AMESim, and optimize and adjust the parameters of the diaphragm compressor physical model through comparative analysis to make the diaphragm compressor physical model meet the actual operating conditions; Use a physical model of the diaphragm compressor that meets actual operating conditions to solve related problems based on simulation requirements and optimize the selection and design of the diaphragm compressor system or structure; The diaphragm compressor physical model includes a diaphragm compressor integrated module composed of a hydraulic cylinder drive module (1), a plunger pump module (2), a relief valve module (3), an intake valve module (4), an exhaust valve module (5), a hydraulic cylinder module (6), a diaphragm motion module (7), a pneumatic cylinder module (8) and a follower valve module (9), as well as a data acquisition module (J3) and a data transmission module (J4); The hydraulic cylinder drive module (1) is used to simulate the process of the diaphragm compressor simulating the crank-connecting rod mechanism driving the piston movement; The plunger pump module (2) and the overflow valve module (3) are used to simulate the oil inlet and oil outlet processes of the diaphragm compressor cylinder respectively; The hydraulic cylinder module (6) is used to simulate the effective volume movement process of the hydraulic oil in the diaphragm compressor cylinder; By simulating the hydraulic oil entering from the plunger pump module (2) and being discharged from the overflow valve module (3), the hydraulic pressure is applied to the diaphragm of the diaphragm compressor in the hydraulic cylinder module (6), driving the diaphragm in the diaphragm motion module (7) to move, thereby realizing the establishment of the liquid phase flow process of the diaphragm compressor; by simulating the gas volume in the pneumatic cylinder module (8) changing under the drive of the diaphragm motion module (7), thereby causing the gas pressure in the pneumatic cylinder module (8) to change and the movement of the intake valve module (4) and the exhaust valve module (5), thereby realizing the establishment of the gas phase flow process of the diaphragm compressor; by simulating the liquid phase flow process of the diaphragm compressor through the diaphragm motion module (7) to drive the gas phase flow process, thereby realizing the establishment of the gas-liquid-solid coupling process of the diaphragm compressor; The relationship between the maximum deflection of the diaphragm center and the volume of the diaphragm cavity of a single-index diaphragm compressor is described by the following formula: Where: is the half-cavity volume under the maximum central deflection of the diaphragm; is the membrane cavity radius; is the maximum deflection at the center of the diaphragm; is the membrane cavity index coefficient; since the change in the diaphragm center deflection caused by the diaphragm movement is linearly related to the change in the membrane cavity volume, the movement of the diaphragm surface is replaced by a reciprocating cylinder model, and the above formula is converted into the AMESim modular modeling and simulation language to form a diaphragm movement module (7), which is connected to the hydraulic cylinder module (6) and the pneumatic cylinder module (8), thereby realizing the establishment of the gas-liquid-solid coupling dynamic model of the diaphragm compressor system based on AMESim.

2. The gas-liquid-solid coupled dynamics simulation method for a diaphragm compressor system according to claim 1, characterized in that: When summarizing different diaphragm compressor physical models in specific application scenarios based on actual needs, the actual needs include component selection and optimization design, compressor fault diagnosis, system simulation and optimization, performance prediction and verification, and research and development of new ultra-high pressure models.

3. The gas-liquid-solid coupled dynamics simulation method for a diaphragm compressor system according to claim 1, characterized in that: The physical model of the diaphragm compressor after modular partitioning is written and parameterized using the AMESim language, an advanced modeling and simulation platform for engineering systems. When the simulation calculation of the diaphragm compressor is realized in AMESim, the piston movement in the hydraulic cylinder drive module (1) is directly driven by the crank-connecting rod mechanism, and the motion law of the piston is described by the following formula: Where: is the piston displacement; is the crankshaft angle; is the crankshaft radius; Crankshaft radius and connecting rod length The ratio of is the piston speed; is the angular velocity; By converting the above mathematical formula into AMESim modular modeling and simulation language, a hydraulic cylinder drive module (1) is formed, which is then connected to the hydraulic cylinder module (6).

4. The gas-liquid-solid coupled dynamics simulation method for a diaphragm compressor system according to claim 3, characterized in that: The plunger movement of the plunger pump module (2) is directly driven by the crank-connecting rod mechanism and its own spring structure, but there is a phase angle with the piston movement in the hydraulic cylinder drive module (1). The plunger movement law is described by the following formula: Where: is the displacement of the plunger pump plunger; is the radius of the plunger driving eccentric; The rotation angle of the eccentric wheel driven by the plunger; The eccentricity of the eccentric wheel driving the plunger pump; is the speed of the plunger pump plunger; The plunger-driven eccentric is described by its phase difference with the crankshaft rotation: Where: The phase difference between the rotation angle of the plunger-driven eccentric and the rotation angle of the crankshaft; By converting the above mathematical formula into AMESim modular modeling and simulation language, a plunger pump module (2) is formed, which is then connected to the hydraulic cylinder module (6).

5. The gas-liquid-solid coupled dynamics simulation method for a diaphragm compressor system according to claim 4, characterized in that: The instantaneous flow rate of the overflow valve module (3) is determined by the overflow valve opening, the pressure difference on both sides of the overflow valve and the medium properties, and is described by the following formula: Where: is the instantaneous flow of the relief valve; is the overflow valve inlet flow coefficient; is the inlet diameter of the relief valve; is the relief valve core lift; is the hydraulic oil density; is the oil pressure in the cavity; is the spring stiffness of the relief valve; is the compression amount of the relief valve spring; is the pressure inside the relief valve core; is the outlet flow coefficient of the relief valve; is the outlet diameter of the relief valve; Simplify the above mathematical formula and regard the pressure of the relief valve core as atmospheric pressure, then: By converting the above mathematical formula into AMESim modular modeling and simulation language, an overflow valve module (3) is formed, which is then connected to the hydraulic cylinder module (6).

6. The gas-liquid-solid coupled dynamics simulation method for a diaphragm compressor system according to claim 5, characterized in that: The air intake valve module (4) and the air exhaust valve module (5) are used to simulate the air intake and exhaust processes of the diaphragm compressor air cavity volume, respectively, and the pneumatic cylinder module (8) is used to simulate the gas compression process caused by the change of the air cavity volume of the diaphragm compressor; The movement of the valve cores in the intake valve module (4) and the exhaust valve module (5) is described by the following equation: Where: is the valve core quality; is the displacement of the intake valve core; is the exhaust valve core displacement; is the flow coefficient; is the pressure in the intake pipe; is the pressure in the air cavity of the diaphragm compressor; is the flow area of ​​the valve core; is the spring stiffness of the valve core; is the spring pre-compression amount; By converting the above mathematical formula into AMESim modular modeling and simulation language, an intake valve module (4) and an exhaust valve module (5) are formed, and then connected to the pneumatic cylinder module (8).

7. The gas-liquid-solid coupled dynamics simulation method for a diaphragm compressor system according to claim 1, characterized in that: The diaphragm compressor integrated module includes a first-stage diaphragm compressor integrated module (J1) and a second-stage diaphragm compressor integrated module (J2); the first-stage diaphragm compressor integrated module (J1) and the second-stage diaphragm compressor integrated module (J2) are the overall component integration of two single-stage diaphragm compressors, and except for the different unit node parameter settings, the first-stage diaphragm compressor integrated module (J1) adopts a relief valve module (3), and the second-stage diaphragm compressor integrated module (J2) adopts a follower valve module (9); The follow-up valve module (9) is described by the following formula: Where: is the flow rate of the servo valve; is the flow coefficient of the oil outlet of the servo valve; is the outlet diameter of the servo valve; is the exhaust pressure in the first-stage diaphragm compressor integrated module (J1); The exhaust pressure in the first-stage diaphragm compressor integrated module (J1) controls the opening and closing characteristics of the servo valve model in the second-stage diaphragm compressor integrated module (J2) through the data transmission module (J4), thereby realizing the overflow function of the servo valve model. The above formula is converted into the AMESim modular modeling and simulation language, connected to the second-stage diaphragm compressor integrated module (J2), and coordinated with other modules to realize the establishment of the gas-liquid-solid coupling dynamic model of the diaphragm compressor system with servo valve based on AMESim. The output data from the first-stage diaphragm compressor integrated module (J1) and the second-stage diaphragm compressor integrated module (J2) are analyzed and modulated, and finally output to the demand user end through the data acquisition module (J3).

8. A diaphragm compressor system gas-liquid-solid coupling dynamics simulation system, characterized in that: include: Demand summary module, used to summarize different diaphragm compressor physical models in specific application scenarios based on actual needs; Physical model partitioning module, used to modularize and partition the diaphragm compressor physical model into gas system, oil system, diaphragm movement, auxiliary components and other heat and mass transfer components; AMESim simulation calculation module is used to write and set parameters based on the modular partitioned diaphragm compressor physical model using the AMESim language, an advanced modeling and simulation platform for engineering systems, to implement simulation calculations of the diaphragm compressor in AMESim; The physical model optimization and adjustment module is used to verify the simulation calculation results of AMESim. Through comparative analysis, the parameters of the diaphragm compressor physical model are optimized and adjusted to make the diaphragm compressor physical model meet the actual operating conditions. The physical model selection and design module is used to use the physical model of the diaphragm compressor that meets the actual operating conditions, solve related problems according to simulation requirements, and optimize the selection and design of the diaphragm compressor system or structure; The diaphragm compressor physical model includes a diaphragm compressor integrated module composed of a hydraulic cylinder drive module (1), a plunger pump module (2), a relief valve module (3), an intake valve module (4), an exhaust valve module (5), a hydraulic cylinder module (6), a diaphragm motion module (7), a pneumatic cylinder module (8) and a follower valve module (9), as well as a data acquisition module (J3) and a data transmission module (J4); The hydraulic cylinder drive module (1) is used to simulate the process of the diaphragm compressor simulating the crank-connecting rod mechanism driving the piston movement; The plunger pump module (2) and the overflow valve module (3) are used to simulate the oil inlet and oil outlet processes of the diaphragm compressor cylinder respectively; The hydraulic cylinder module (6) is used to simulate the effective volume movement process of the hydraulic oil in the diaphragm compressor cylinder; By simulating the hydraulic oil entering from the plunger pump module (2) and being discharged from the overflow valve module (3), the hydraulic pressure is applied to the diaphragm of the diaphragm compressor in the hydraulic cylinder module (6), driving the diaphragm in the diaphragm motion module (7) to move, thereby realizing the establishment of the liquid phase flow process of the diaphragm compressor; by simulating the gas volume in the pneumatic cylinder module (8) changing under the drive of the diaphragm motion module (7), thereby causing the gas pressure in the pneumatic cylinder module (8) to change and the movement of the intake valve module (4) and the exhaust valve module (5), thereby realizing the establishment of the gas phase flow process of the diaphragm compressor; by simulating the liquid phase flow process of the diaphragm compressor through the diaphragm motion module (7) to drive the gas phase flow process, thereby realizing the establishment of the gas-liquid-solid coupling process of the diaphragm compressor; The relationship between the maximum deflection of the diaphragm center and the volume of the diaphragm cavity of a single-index diaphragm compressor is described by the following formula: Where: is the half-cavity volume under the maximum central deflection of the diaphragm; is the membrane cavity radius; is the maximum deflection at the center of the diaphragm; is the membrane cavity index coefficient; since the change in the diaphragm center deflection caused by the diaphragm movement is linearly related to the change in the membrane cavity volume, the movement of the diaphragm surface is replaced by a reciprocating cylinder model, and the above formula is converted into the AMESim modular modeling and simulation language to form a diaphragm movement module (7), which is connected to the hydraulic cylinder module (6) and the pneumatic cylinder module (8), thereby realizing the establishment of the gas-liquid-solid coupling dynamic model of the diaphragm compressor system based on AMESim.

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