Pump-driven two-phase flow refrigerating system, regulation and control method, electronic equipment and readable storage medium

Abstract

The invention relates to the field of refrigeration, in particular to a pump-driven two-phase flow refrigeration system, a regulation and control method, electronic equipment and a readable storage medium, the pump-driven two-phase flow refrigeration system comprises an evaporator serving as a user unit, after a gas-liquid mixed refrigerant discharged by the evaporator is separated by a gas-liquid separator, a gaseous refrigerant is condensed by a condenser and then conveyed to the evaporator through an injection pump, and the evaporator is connected with the pump-driven two-phase flow refrigeration system. A liquid refrigerant sequentially passes through the liquid storage tank, the main pump and the injection pump and then is conveyed to the evaporator to form refrigerant circulation; a three-way regulating valve is arranged at an outlet of the condenser, and after refrigerant condensed by the condenser is shunted by the three-way regulating valve, one part of the refrigerant is conveyed to the injection pump, and the other part of the refrigerant is conveyed into the liquid storage tank. The cavitation phenomenon of the pump body in the refrigerating system is avoided, and the safety and reliability of the refrigerating system are improved.

Description

Technical Field

[0001] The present invention relates to the field of refrigeration, and in particular to a pump-driven two-phase flow refrigeration system, a control method, an electronic device and a readable storage medium. Background Art

[0002] The pump-driven two-phase flow refrigeration system is a refrigeration system that uses a pump to provide power for liquid refrigerant, sends the liquid refrigerant into the user unit, evaporates inside the user unit, and uses the latent heat of vaporization during the evaporation of the refrigerant to take away the heat of the user unit. The refrigeration system is specifically described in the publication number "CN112197454A", through the injection method of the first-stage jet pump, the liquid jet working medium is used for injection, so that the refrigerant working medium is injected into the jet pump at the outlet of the refrigeration device by the jet working medium, so that the gas of the refrigerant working medium becomes a high-pressure gas, and is separated into gas and liquid by the working medium separator, so that the separated high-pressure steam working medium returns to the refrigeration device, is used for refrigeration after condensation, and the liquid jet working medium returns to the first-stage generator, and the refrigeration cycle is performed again to form a refrigeration circuit, and the circulation of the refrigerant in the user unit is realized by the action of the pump.

[0003] Due to its working characteristics, the pump-driven two-phase flow refrigeration system still has many technical problems to be solved, the most important of which is the "flash and cavitation" phenomenon that is prone to occur in the pump body. Since the refrigerant enters the liquid storage tank or directly enters the pump through the pipeline after condensing in the condenser, the liquid refrigerant should be in a "saturated" state or close to a "saturated" state. After the liquid refrigerant in this state enters the pump body, under the influence of local flow resistance and the speed increase of the water pump impeller, the local pressure of the refrigerant on the impeller surface is reduced, and it is easy to vaporize and flash. After long-term action, it will cause serious "cavitation" to the impeller and other parts of the pump body, which has a fatal impact on the safety and reliability of the refrigeration system, so it needs to be solved urgently. Summary of the invention

[0004] In order to avoid and overcome the technical problems existing in the prior art, the present invention provides a pump-driven two-phase flow refrigeration system, a control method, an electronic device and a readable storage medium. The present invention avoids the occurrence of pump cavitation in the refrigeration system and improves the safety and reliability of the refrigeration system.

[0005] To achieve the above object, the present invention provides the following technical solutions:

[0006] A pump-driven two-phase flow refrigeration system includes an evaporator as a user unit. The gas-liquid mixed refrigerant discharged from the evaporator is separated by a gas-liquid separator, and the gaseous refrigerant is condensed by a condenser and then transported to the evaporator by a jet pump. The liquid refrigerant passes through a liquid storage tank, a main pump and a jet pump in sequence and is then transported to the evaporator to form a refrigerant cycle. A three-way regulating valve is provided at the outlet of the condenser. The refrigerant condensed by the condenser is split by the three-way regulating valve, and one part of it is transported to the jet pump and the other part is transported to the liquid storage tank.

[0007] As a further solution of the present invention: a liquid level sensor and a pressure sensor are installed on the liquid storage tank.

[0008] As a further solution of the present invention: an automatic exhaust valve is installed on the liquid storage tank, and is connected to the inlet of the condenser through the automatic exhaust valve.

[0009] A control method for a pump-driven two-phase flow refrigeration system, comprising the following steps:

[0010] S1, starting the pump-driven two-phase flow refrigeration system;

[0011] S2. Dynamically adjust the diversion mass ratio of the three-way regulating valve according to the operating time of the refrigeration system, so that the ratio x of the refrigerant mass flow directly flowing to the injection pump through the three-way regulating valve and the refrigerant mass flow flowing out of the condenser satisfies the following formula:

[0012]

[0013] in:

[0014] k represents the injection ratio of the injection pump;

[0015] t represents the real-time temperature after the refrigeration system is running;

[0016] φ Ct It represents the latent heat of condensation per unit mass of refrigerant at temperature t;

[0017] φ Et It represents the latent heat of evaporation of unit mass of refrigerant at temperature t;

[0018] ρ lt It represents the density of liquid refrigerant at temperature t;

[0019] ρ wt It represents the density of gaseous refrigerant at temperature t;

[0020] r in Indicates the inlet flow channel radius of the main pump;

[0021] h c represents the convective heat transfer coefficient of the condenser;

[0022] S represents the convection heat transfer area of ​​the condenser;

[0023] q in Indicates the amount of heat absorbed by the evaporator per unit time;

[0024] τ represents the operating time of the refrigeration system;

[0025] C p Indicates the constant pressure specific heat of the refrigerant;

[0026] m represents the total mass of refrigerant in the refrigeration system;

[0027] p eτ represents the pressure at the top of the liquid storage tank at temperature t;

[0028] g represents the acceleration due to gravity;

[0029] e represents a natural constant;

[0030] R represents the radius of the liquid storage tank;

[0031] H0 represents the liquid level in the liquid storage tank when the refrigeration system is started;

[0032] t a Indicates the ambient temperature;

[0033] ρ wta Indicates t a Density of gaseous refrigerant at temperature;

[0034] ρ lta Indicates t a Density of liquid refrigerant at temperature;

[0035] φ Cta Indicates t a The latent heat of condensation per unit mass of refrigerant at temperature;

[0036] H * Indicates the height difference between the bottom of the storage tank and the center of the main pump inlet;

[0037] ∑h S Indicates the resistance loss of the pipeline from the bottom of the liquid storage tank to the inlet of the main pump;

[0038] p Vt Indicates the vapor pressure of the refrigerant at temperature t;

[0039] p A Indicates the minimum difference between the pump inlet pressure and the vapor pressure of the refrigerant required to avoid cavitation in the main pump.

[0040] An electronic device comprises a processor, an input device, an output device and a memory, wherein the processor, the input device, the output device and the memory are connected in sequence, the memory is used to store a computer program, the computer program comprises program instructions, and the processor is configured to call the program instructions to execute the control method of a pump-driven two-phase flow refrigeration system.

[0041] A readable storage medium stores a computer program, wherein the computer program includes program instructions, and when the program instructions are executed by a processor, the processor executes the control method of a pump-driven two-phase flow refrigeration system.

[0042] Compared with the prior art, the present invention has the following beneficial effects:

[0043] 1. The present invention installs a three-way regulating valve in the pump-driven two-phase flow refrigeration system to divert a part of the refrigerant discharged from the condenser into the liquid storage tank, so as to prevent the evaporated gaseous refrigerant from directly entering the main pump and forming cavitation. At the same time, the three-way regulating valve can always keep a certain amount of liquid refrigerant in the liquid storage tank to maintain the working pressure of the main pump inlet. Finally, the suction force formed by the jet pump is used to mix the condensed refrigerant with the refrigerant passing through the main pump to form a refrigerant that can be regarded as a "saturated" state. The refrigerant in this state is sent to the user unit, which is more conducive to the evaporation and heat absorption of the refrigerant, improves the evaporation and heat absorption performance of the refrigerant, avoids the occurrence of pump body cavitation in the refrigeration system, and improves the safety and reliability of the refrigeration system.

[0044] 2. The present invention dynamically adjusts the diversion mass ratio of the three-way regulating valve according to the change of the running time of the refrigeration system. By adjusting the diversion mass, the main pump will never have cavitation phenomenon. BRIEF DESCRIPTION OF THE DRAWINGS

[0045] Figure 1 It is a structural schematic diagram of the present invention.

[0046] In the figure:

[0047] 1. Evaporator; 2. Gas-liquid separator; 3. Condenser; 4. Three-way regulating valve; 5. Liquid storage tank;

[0048] 51. Automatic exhaust valve; 52. Liquid level sensor; 53. Pressure sensor;

[0049] 6. Jet pump; 7. Main pump. DETAILED DESCRIPTION

[0050] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0051] See also Figure 1 In an embodiment of the present invention, a pump-driven two-phase flow refrigeration system includes an evaporator 1. The evaporator 1 serves as a user unit. The refrigerant absorbs heat in the evaporator 1, and part of the liquid refrigerant evaporates into a gas state. The gas-liquid mixed refrigerant enters the gas-liquid separator 2 and is diverted in the gas-liquid separator 2. The diverted gaseous refrigerant enters the condenser 3 and is condensed into a liquid refrigerant under the cooling effect of an external low-temperature fluid. The liquid refrigerant in the gas-liquid separator 2 flows into the liquid storage tank 5 through a pipeline.

[0052] An automatic exhaust valve 51 is provided on the top of the liquid storage tank 5. The gaseous refrigerant flowing into the liquid storage tank 5 is discharged into the inlet of the condenser 3 through the automatic exhaust valve 51, and flows into the condenser 3 in parallel with the gaseous refrigerant discharged through the gas-liquid diverter 2, and condenses to form liquid refrigerant.

[0053] The liquid refrigerant condensed by the condenser 3 is passed into the three-way regulating valve 4 for diversion, wherein a part of the liquid refrigerant is connected to the liquid storage tank 5 through the first outlet of the three-way regulating valve 4, and the other part of the liquid refrigerant is connected to the suction port of the injection pump 6 through the second outlet of the three-way regulating valve 4.

[0054] A liquid level sensor 52 is installed on the liquid storage tank 5 to monitor the liquid level in the liquid storage tank 5 , and the flow rate of the three-way regulating valve 4 is determined according to the monitoring data of the liquid level sensor 52 .

[0055] When the liquid level sensor 52 monitors that the liquid level height (i.e., the refrigerant capacity) in the liquid storage tank 5 meets the requirements, all the liquid refrigerant condensed by the condenser 3 flows into the jet pump 6; when the liquid level sensor 52 detects that the liquid level height (i.e., the liquid capacity) in the liquid storage tank 5 is less than the required value, the three-way regulating valve 4 starts to operate, reducing the refrigerant flow rate flowing into the jet pump 6 and increasing the refrigerant flow rate flowing into the liquid storage tank 5, so that the liquid refrigerant in the liquid storage tank always meets the capacity requirements.

[0056] This part of liquid refrigerant has a relatively high degree of supercooling. The liquid refrigerant provided with conveying power by the main pump 7 at the outlet of the liquid storage tank 5 forms a certain suction force in the jet pump 6, and the suction force is used to send part of the condensed liquid refrigerant into the evaporator 1. The liquid refrigerant sucked into the evaporator 1 is relatively closer to the saturated state, and is mixed with the supercooled refrigerant from the main pump 7 to form a saturated refrigerant or a refrigerant close to the saturated state. The refrigerant in this state enters the evaporator 1 and is more likely to absorb heat using the latent heat of vaporization.

[0057] The steps include:

[0058] S1. Start a pump-driven two-phase flow refrigeration system;

[0059] S2. Dynamically adjust the diversion mass ratio of the three-way regulating valve 4 according to the operation time of the refrigeration system, so that the ratio x of the refrigerant mass flow directly flowing to the injection pump 6 through the three-way regulating valve 4 and the refrigerant mass flow flowing out of the condenser 3 satisfies the following formula:

[0060]

[0061] in:

[0062] k represents the injection ratio of the injection pump 6;

[0063] t represents the real-time temperature after the refrigeration system is running;

[0064] φ Ct It represents the latent heat of condensation per unit mass of refrigerant at temperature t;

[0065] φ Et It represents the latent heat of evaporation of unit mass of refrigerant at temperature t;

[0066] ρ lt It represents the density of liquid refrigerant at temperature t;

[0067] ρ wt It represents the density of gaseous refrigerant at temperature t;

[0068] r in represents the inlet flow channel radius of the main pump 7;

[0069] h c represents the convective heat transfer coefficient of condenser 3;

[0070] S represents the convection heat exchange area of ​​the condenser 3;

[0071] q in Indicates the amount of heat absorbed by evaporator 1 per unit time;

[0072] τ represents the operating time of the refrigeration system;

[0073] Cp Indicates the constant pressure specific heat of the refrigerant;

[0074] m represents the total mass of refrigerant in the refrigeration system;

[0075] p eτ It represents the pressure at the liquid level of the liquid storage tank 5 at temperature t;

[0076] g represents the acceleration due to gravity;

[0077] e represents a natural constant;

[0078] R represents the radius of the liquid storage tank 5;

[0079] H0 represents the liquid level in the liquid storage tank 5 when the refrigeration system is started;

[0080] t a Indicates the ambient temperature;

[0081] ρ wta Indicates t a Density of gaseous refrigerant at temperature;

[0082] ρ lta Indicates t a Density of liquid refrigerant at temperature;

[0083] φ Cta Indicates t a The latent heat of condensation per unit mass of refrigerant at temperature; H * Indicates the height difference between the bottom of the liquid storage tank 5 and the center of the inlet of the main pump 7;

[0084] ∑h S It represents the resistance loss of the pipeline from the bottom of the liquid storage tank to the inlet of the main pump 7; p Vt Indicates the vapor pressure of the refrigerant at temperature t;

[0085] p A It represents the minimum difference between the pump inlet pressure and the vaporization pressure of the refrigerant required to avoid cavitation of the main pump 7.

[0086] The derivation steps of the calculation in step S2 are as follows:

[0087] The initial state when the refrigeration system is started is taken as the "0" moment, that is, the time τ in the initial state is 0; then the heat absorption of the evaporator 1 and the heat release of the condenser in the initial state are both 0kw. At this time, the temperature at each location in the refrigeration system is equal to the ambient temperature, and the liquid level in the storage tank is H0.

[0088] Since the system is running, the evaporator 1 absorbs heat under the constant heat flux boundary condition, that is, dQ in =q in dτ;

[0089] Among them, Q in is the heat absorption of evaporator 1;

[0090] q in is the amount of heat absorbed by evaporator 1 per unit time, which is assumed to be a constant and does not change with time;

[0091] The condenser heat release is a convection boundary condition, that is, dQ out =h c ·S·(tt a )dτ;

[0092] Among them, Q out is the heat release of condenser 3;

[0093] h c represents the convective heat transfer coefficient of condenser 3, which is assumed to be constant and does not change with time;

[0094] S represents the convection heat transfer area of ​​condenser 3, which does not change with time;

[0095] t represents the real-time temperature after the refrigeration system is running;

[0096] t a Indicates the ambient temperature.

[0097] After the system runs for a period of time, it tends to be stable. In order to avoid "cavitation" of the main pump 7, the overall energy during the system operation should meet the following requirements:

[0098] dQ=dQ in -dQ out Formula 1;

[0099] The change in system energy is:

[0100] dQ=C p ·mdt formula 2;

[0101] C p Indicates the constant pressure specific heat of the refrigerant;

[0102] m represents the mass of refrigerant in the system.

[0103] Combined with dQ in , dQ out The expression of and equation 1 and equation 2 can be used to obtain the following relationship:

[0104] S.h c ·(tt a )dτ+C p mdt = q in dτ Equation 3;

[0105] Derivative both sides of the above equation with respect to τ:

[0106]

[0107] Then the solution of equation 4 is:

[0108]

[0109] The refrigerant flow rate ejected from the jet pump outlet is f;

[0110] The refrigerant flow rate flowing out from the bottom of the liquid storage tank 5 is f1;

[0111] The refrigerant flow rate from the three-way regulating valve 4 directly to the injection pump 6 is f2;

[0112] The mass flow rate of the gaseous refrigerant flowing from the gas-liquid separator 2 to the condenser 3 is f3; the mass flow rate of the liquid refrigerant flowing from the gas-liquid separator to the liquid storage tank is f4;

[0113] The refrigerant flow rate from the condenser to the three-way regulating valve 4 is f5;

[0114] The refrigerant flow rate from the three-way regulating valve 4 directly to the liquid storage tank 5 is f6;

[0115] but:

[0116]

[0117] Among them, φ E It indicates the latent heat of evaporation per unit mass of refrigerant;

[0118] φ C It represents the latent heat of condensation per unit mass of refrigerant.

[0119] According to the law of conservation of mass, we can get:

[0120] f=f1+f2=f3+f4 Formula 8;

[0121] f5=f2+f6 Formula 9;

[0122] Assuming that the ratio of the refrigerant mass flow rate flowing directly to the injection pump 6 through the three-way regulating valve 4 to the refrigerant mass flow rate flowing out of the condenser 3 is x, then:

[0123] x=f2 / f5 Formula 10;

[0124] According to the above relationship, we can get:

[0125]

[0126] The injection ratio of the injection pump is k, then:

[0127] k = f2 / f1 Formula 13;

[0128] According to formula 12 and formula 13, we can get:

[0129]

[0130] According to formula 8, we can get:

[0131]

[0132] Since the volume of the gas-liquid separator 2 in the refrigeration system is small, the mass of the refrigerant stored therein accounts for a small proportion. If the mass change of the refrigerant in the gas-liquid separator 2 is ignored, it can be concluded that:

[0133]

[0134] Since the sum of the mass of the refrigerant flowing into the storage tank minus the mass of the refrigerant flowing out of the storage tank is equal to the mass change of the refrigerant in the storage tank, and the gas-liquid interface in the storage tank will change due to the inflow and outflow of the refrigerant, and since the density of the liquid refrigerant is greater than that of the gaseous refrigerant, the mass change in the storage tank can be expressed as the increased mass of the liquid refrigerant minus the mass of the gaseous refrigerant in the corresponding volume.

[0135] Assume that the liquid storage tank is cylindrical with a radius of R and a liquid refrigerant density of ρ l , the density of gaseous refrigerant is ρ w , the real-time liquid level in the liquid storage tank 5 is H; the differential expression of the above mass change relationship is:

[0136] d(f4+f6-f1)=(ρ l -ρ w )·π·R 2 ·dH Formula 17;

[0137] Combining equations 11, 14, 16, and 17, we can obtain:

[0138]

[0139] dQ out and dQ in Substituting the expression into formula 18, we can get:

[0140]

[0141] By taking the derivative of τ on both sides of Equation 19, we can obtain:

[0142]

[0143] Substituting equation 5 into equation 20, we can obtain the ordinary differential equation of the real-time height H of the liquid level in the liquid storage tank with respect to time τ:

[0144]

[0145] The general solution of formula 21 for H is:

[0146]

[0147] When the refrigeration system is in the initial state, τ = 0, H = H0, and is substituted into equation 22, the constant term C1 is obtained:

[0148]

[0149] Substituting equation 23 into equation 22 yields:

[0150]

[0151] When τ→∞, the system reaches equilibrium, at which point Q in∞ =Q out∞ , then we can conclude that: E∞ =φ C∞ , substituting into formula 24, we can get:

[0152]

[0153] Among them, Q in∞ Indicates the amount of heat absorbed by evaporator 1 when the system is running stably;

[0154] Q out∞ Indicates the heat release of condenser 3 when the system is running stably;

[0155] H ∞ Indicates the liquid level in the liquid storage tank 5 when the system is running stably;

[0156] φ E∞ It indicates the latent heat of evaporation of unit mass of refrigerant when the system is running stably;

[0157] φ C∞ It indicates the latent heat of condensation of unit mass of refrigerant when the system is running stably;

[0158] but:

[0159]

[0160] Solved:

[0161]

[0162] Substituting H = H0 into equation 27 when τ = 0 in the initial state of the refrigeration system, we can obtain the constant term C2:

[0163]

[0164] Substituting equation 28 into equation 26 yields:

[0165]

[0166] According to formula 14, we can get:

[0167]

[0168] The pressure at the liquid level in the storage tank is p e , the flow velocity at the liquid surface in the tank is v e , the inlet pressure of the main pump is p s The resistance loss of the pipeline from the bottom of the liquid storage tank to the inlet of the main pump 7 is ∑h S , the inlet velocity of the main pump is v s The height difference between the bottom of the liquid storage tank 5 and the center of the main pump 7 inlet is H * According to Bernoulli's principle, we can get:

[0169]

[0170] Among them, ρ lt It represents the density of liquid refrigerant at temperature t;

[0171] Assume v e =0, then:

[0172]

[0173] Among them, ρ lt It represents the density of liquid refrigerant at temperature t;

[0174] According to formula 30, the pump inlet velocity v S for:

[0175]

[0176] Among them, r in Indicates the inlet flow channel radius of the main pump.

[0177] According to formula 32 and formula 33, we can get:

[0178]

[0179] In order to avoid cavitation of the main pump impeller, the minimum operating pressure of the main pump must be higher than the refrigerant vaporization pressure p V , that is, the main pump inlet pressure must be higher than the refrigerant vaporization pressure p V , then the main pump inlet pressure p S for:

[0180] p S >p V +p AFormula 35;

[0181] p A It represents the minimum difference between the pump inlet pressure and the vaporization pressure of the refrigerant required to avoid cavitation of the main pump 5. This value needs to be calculated based on the pump type flow channel and refrigerant movement characteristics selected in the design and is regarded as a constant.

[0182] According to equation 34 and equation 35, the following equation 36 can be obtained:

[0183]

[0184] According to Formula 36, ​​the relationship between x in step S2 and the operating time of the refrigeration system can be obtained. If the relationship in step S2 is satisfied, the main pump can be free from cavitation.

[0185] Another embodiment of the present application is an electronic device.

[0186] The electronic device may be the mobile device itself, or a stand-alone device independent of the mobile device, which may communicate with the mobile device to receive the collected input signals from the mobile device and send the selected target decision behavior to the mobile device.

[0187] An electronic device includes one or more processors and memory.

[0188] The processor may be a central processing unit (CPU) or other forms of processing units having data processing capabilities and / or instruction execution capabilities, and may control other components in the electronic device to perform desired functions.

[0189] The memory may include one or more computer program products, and the computer program product may include various forms of computer-readable storage media, such as volatile memory and / or non-volatile memory. The volatile memory may include, for example, random access memory (RAM) and / or cache memory (cache), etc. The non-volatile memory may include, for example, read-only memory (ROM), hard disk, flash memory, etc. One or more computer program instructions may be stored on the computer-readable storage medium, and the processor may run the program instructions to implement a control method for a pump-driven two-phase flow refrigeration system of each embodiment of the present application described above.

[0190] In one example, the electronic device may further include: an input device and an output device, and these components are interconnected through a bus system and / or other forms of connection mechanisms. For example, the input device may include various devices such as an on-board diagnostic system (OBD), a camera, an industrial camera, etc. The input device may also include, for example, a keyboard, a mouse, etc. The output device may include, for example, a display, a speaker, a printer, and a communication network and a remote output device connected thereto, etc.

[0191] In addition, the electronic device may further include any other appropriate components according to specific application scenarios.

[0192] Another embodiment of the present application may also be a computer program product, which includes computer program instructions, which, when executed by a processor, enable the processor to execute the calculation steps according to various embodiments of the present application described in the above-mentioned method for controlling a pump-driven two-phase flow refrigeration system in this specification.

[0193] The computer program product may be written in any combination of one or more programming languages ​​to write program codes for performing the operations of the embodiments of the present application, including object-oriented programming languages, such as Java, C++, etc., and conventional procedural programming languages, such as "C" language or similar programming languages. The program code may be executed entirely on the user computing device, partially on the user device, as an independent software package, partially on the user computing device and partially on a remote computing device, or entirely on a remote computing device or server.

[0194] In addition, an embodiment of the present application may also be a computer-readable storage medium having computer program instructions stored thereon, which, when executed by a processor, enables the processor to execute a control method for a pump-driven two-phase flow refrigeration system in this specification.

[0195] The computer readable storage medium can adopt any combination of one or more readable media. The readable medium can be a readable signal medium or a readable storage medium. The readable storage medium can include, for example, but is not limited to, a system, device or device of electricity, magnetism, light, electromagnetic, infrared, or semiconductor, or any combination of the above. More specific examples (non-exhaustive list) of readable storage media include: an electrical connection with one or more wires, a portable disk, a hard disk, a random access memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber, a portable compact disk read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination of the above.

[0196] The basic principles of the present application are described above in conjunction with specific embodiments. However, it should be noted that the advantages, strengths, effects, etc. mentioned in the present application are only examples and not limitations, and it cannot be considered that these advantages, strengths, effects, etc. are required by each embodiment of the present application. In addition, the specific details disclosed above are only for the purpose of illustration and ease of understanding, not for limitation, and the above details do not limit the present application to being implemented by adopting the above specific details.

[0197] The block diagrams of the devices, apparatuses, equipment, and systems involved in this application are only illustrative examples and are not intended to require or imply that they must be connected, arranged, and configured in the manner shown in the block diagram. As will be appreciated by those skilled in the art, these devices, apparatuses, equipment, and systems can be connected, arranged, and configured in any manner. Words such as "including", "comprising", "having", etc. are open words, referring to "including but not limited to", and can be used interchangeably with them. The words "or" and "and" used here refer to the words "and / or" and can be used interchangeably with them, unless the context clearly indicates otherwise. The words "such as" used here refer to the phrase "such as but not limited to", and can be used interchangeably with them.

Claims

1. A pump-driven two-phase flow refrigeration system, characterized in that: The invention comprises an evaporator (1) as a user unit, wherein the gas-liquid mixed refrigerant discharged from the evaporator (1) is separated by a gas-liquid separator (2), the gaseous refrigerant is condensed by a condenser (3) and then transported to the evaporator (1) by a jet pump (6), and the liquid refrigerant is sequentially transported to the evaporator (1) by passing through a liquid storage tank (5), a main pump (7) and a jet pump (6), so as to form a refrigerant cycle; a three-way regulating valve (4) is arranged at the outlet of the condenser (3), and the refrigerant condensed by the condenser (3) is divided by the three-way regulating valve (4), and a part of the refrigerant is transported to the jet pump (6) and the other part is transported to the liquid storage tank (5).

2. A pump-driven two-phase flow refrigeration system according to claim 1, characterized in that: A liquid level sensor (52) and a pressure sensor (53) are installed on the liquid storage tank (5).

3. A pump-driven two-phase flow refrigeration system according to claim 1, characterized in that: An automatic exhaust valve (51) is installed on the liquid storage tank (5), and the liquid storage tank (5) is connected to the inlet of the condenser (3) through the automatic exhaust valve (51).

4. A control method for a pump-driven two-phase flow refrigeration system, characterized in that: The steps include: S1. Start a pump-driven two-phase flow refrigeration system as claimed in any one of claims 1 to 3; S2. Dynamically adjust the diversion mass ratio of the three-way regulating valve (4) according to the operating time of the refrigeration system, so that the ratio x of the mass flow rate of the refrigerant directly flowing to the injection pump (6) through the three-way regulating valve (4) and the mass flow rate of the refrigerant flowing out of the condenser (3) satisfies the following formula: in: k represents the injection ratio of the injection pump (6); t represents the real-time temperature after the refrigeration system is running; φ Ct It represents the latent heat of condensation per unit mass of refrigerant at temperature t; φ Et It represents the latent heat of evaporation of unit mass of refrigerant at temperature t; ρ lt It represents the density of liquid refrigerant at temperature t; ρ wt It represents the density of gaseous refrigerant at temperature t; r in represents the inlet flow channel radius of the main pump (7); h c represents the convective heat transfer coefficient of the condenser (3); S represents the convection heat exchange area of ​​the condenser (3); q in represents the amount of heat absorbed by the evaporator (1) per unit time; τ represents the operating time of the refrigeration system; C p Indicates the constant pressure specific heat of the refrigerant; m represents the total mass of refrigerant in the refrigeration system; p eτ represents the pressure at the top of the liquid storage tank (5) at temperature t; g represents the acceleration due to gravity; e represents a natural constant; R represents the radius of the liquid storage tank (5); H0 represents the liquid level in the liquid storage tank (5) when the refrigeration system is started; t a Indicates the ambient temperature; ρ wta Indicates t a Density of gaseous refrigerant at temperature; ρ lta Indicates t a Density of liquid refrigerant at temperature; φ Cta Indicates t a The latent heat of condensation per unit mass of refrigerant at temperature; H * Indicates the height difference between the bottom of the liquid storage tank (5) and the center of the inlet of the main pump (7); ∑h S Indicates the resistance loss of the pipeline from the bottom of the liquid storage tank to the inlet of the main pump (7); p Vt Indicates the vapor pressure of the refrigerant at temperature t; p A It represents the minimum difference between the pump inlet pressure and the vaporization pressure of the refrigerant required to avoid cavitation of the main pump (7).

5. An electronic device, characterized in that: The invention comprises a processor, an input device, an output device and a memory, wherein the processor, the input device, the output device and the memory are connected in sequence, the memory is used to store a computer program, the computer program comprises program instructions, and the processor is configured to call the program instructions to execute a control method for a pump-driven two-phase flow refrigeration system as claimed in claim 4.

6. A readable storage medium, characterized in that: The storage medium stores a computer program, wherein the computer program includes program instructions, and when the program instructions are executed by the processor, the processor executes the control method for a pump-driven two-phase flow refrigeration system as claimed in claim 4.

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