CN219368027U

CN219368027U - Fluorine pump refrigerating system

Info

Publication number: CN219368027U
Application number: CN202223357666.1U
Authority: CN
Inventors: 孙伟; 宋鹏杰; 黄柏良; 吴波; 张宏济
Original assignee: Huawei Digital Power Technologies Co Ltd
Current assignee: Huawei Digital Power Technologies Co Ltd
Priority date: 2022-12-12
Filing date: 2022-12-12
Publication date: 2023-07-18
Anticipated expiration: 2032-12-12

Abstract

The embodiment of the application provides a fluorine pump refrigerating system, which comprises a refrigerant circulating system composed of a first heat exchanger, a gas-liquid separation device, a compressor, a second heat exchanger, a pressure reducing device and a fluorine pump; compared with the traditional compressor refrigeration, when the outdoor temperature is higher, the compressor and the fluorine pump of the system carry out linkage refrigeration, so that the energy efficiency of the fluorine pump refrigeration system can be improved.

Description

Fluorine pump refrigerating system

Technical Field

The embodiment of the application relates to the field of energy, in particular to a fluorine pump refrigerating system.

Background

The air conditioner of the machine room needs to be refrigerated all the year round, and along with the development of the times, the requirement of the air conditioner of the machine room for high energy efficiency is increased day by day, and the air conditioner energy efficiency index of the machine room has become an important index for the construction of a data center. The current fluorine pump air conditioning system has energy efficiency advantage when the outdoor temperature is low, but when the outdoor temperature is high, the working mode is still the traditional compressor refrigeration mode, so the energy efficiency of the fluorine pump air conditioning system cannot be improved essentially. When the outdoor temperature is high, how to improve the energy efficiency of the fluorine pump air conditioning system is a problem to be solved.

Disclosure of Invention

The application provides a fluorine pump refrigerating system, which can improve the energy efficiency of the fluorine pump refrigerating system.

In a first aspect, there is provided a fluorine pump refrigeration system comprising: a first heat exchanger 100, a gas-liquid separation device 110, a compressor 120, a second heat exchanger 130, a pressure reducing device 140, and a fluorine pump 150. The first heat exchanger 100 includes a fifth interface 102 and a sixth interface 104, and is configured to heat a refrigerant input from the fifth interface and output the heated refrigerant from the sixth interface 104; the gas-liquid separation device 110 includes a first port 112, a second port 114, a third port 116, and a fourth port 118, and the gas-liquid separation device 110 is configured to separate a gaseous refrigerant and a liquid refrigerant received from the first port 112, output the gaseous refrigerant from the second port 114, and output the liquid refrigerant from the fourth port 118, and the first port 112 is connected to the sixth port 104; the compressor 120 includes a first input port 122 and a first output port 124, the compressor 120 is configured to compress a refrigerant input from the first input port 122, and output the compressed refrigerant from the first output port 124, and the first input port 122 is connected to the second interface 114; the second heat exchanger 130 includes a seventh port 132 and an eighth port 134, the second heat exchanger 130 is configured to cool the refrigerant inputted from the seventh port 132 and output the cooled refrigerant from the eighth port 134, and the seventh port 132 is connected to the first output port 124; the pressure reducing device 140 includes a ninth port 142 and a tenth port 144, the pressure reducing device 140 is configured to reduce the pressure of the refrigerant inputted from the ninth port, and output the reduced pressure of the refrigerant from the tenth port 144, the ninth port 142 is connected to the eighth port 134, and the tenth port 144 is connected to the third port 116; the fluorine pump includes a second input port 152 and a second output port 154, and outputs the refrigerant inputted from the second input port 152 to the fifth interface 102 of the first heat exchanger through the second output port 154, and the second input port 152 is connected to the fourth interface 118.

In the present application, the refrigerant may be referred to as a refrigerant, and may be changed between a liquid state and a gas state.

Specifically, "the first heat exchanger is used to heat the refrigerant inputted from the fifth port" may be understood as that the refrigerant inputted from the fifth port absorbs heat in the room in the first heat exchanger 100.

Specifically, "the second heat exchanger 130 is used for cooling the refrigerant input from the seventh port 132" may be understood as that the refrigerant input from the seventh port 132 radiates heat to the environment in the second heat exchanger 130.

In the present application, "the first port 112 is connected to the sixth port 104" and "the first input port 122 is connected to the second port 114" are understood to mean that the sixth port 104 is connected to the first input port 122, that is, the first heat exchanger 100 is in communication with the compressor 120 via the gas-liquid separation device 110.

Similarly, "the ninth port 142 is connected to the eighth port 134, and the tenth port 144 is connected to the third port 116" may be understood as that the eighth port 134 is connected to the third port 116, that is, the second heat exchanger 130 is in communication with the gas-liquid separation device 110 via the pressure reducing device 140.

Other similar communication conditions may be referred to in the above description and will not be repeated here.

According to the fluorine pump refrigerating system provided by the application, when the outdoor temperature is higher, the refrigerating mode of linkage of the fluorine pump and the compressor can be adopted for refrigerating, so that the energy consumption of the compressor can be reduced, and the energy efficiency of the fluorine pump refrigerating system is improved.

Alternatively, the first interface 112 and the third interface 116 may be the same interface, so as to reduce the number of openings of the gas separation device 110 and reduce the processing cost.

With reference to the first aspect, in certain implementation manners of the first aspect, the system further includes: a first three-way directional control valve 160, the first three-way directional control valve 160 including a first port 162, a second port 164, and a third port 166, the first port 112 being connected to the sixth port 104 including: the sixth port 104 is connected to the first port 162, the second port 164 is connected to the first port 112, and the first three-way selector valve 160 is configured to output the heated refrigerant from the second port 164 to the first port 112 of the gas-liquid separator 110, or the first three-way selector valve 160 is configured to output the heated refrigerant from the third port 166 to the seventh port 132 of the second heat exchanger 130.

Specifically, "the sixth port 104 is connected to the first port 162, the second port 164 is connected to the first port 112" may be understood as that the first heat exchanger 100 communicates with the gas-liquid separation device 110 via the first three-way directional valve 160.

When the outdoor temperature is low (for example, the outdoor temperature is less than 10 ℃), the first three-way reversing valve 160 can control the heated refrigerant to be output from the third port 166 to the seventh port 132 of the second heat exchanger 130, so that the fluorine pump refrigerating system adopts a fluorine pump refrigerating mode, and the natural cold source is utilized for cooling, thereby improving the energy efficiency of the fluorine pump refrigerating system; when the outdoor temperature is high (for example, the outdoor temperature is higher than 10 ℃), the first three-way reversing valve 160 can control the heated refrigerant to be output from the second port 164 to the first port 112 of the gas-liquid separation device 110, so that the fluorine pump refrigeration system adopts a refrigeration mode of linkage of the fluorine pump and the compressor, and the energy efficiency of the fluorine pump refrigeration system can still be improved.

By the fluorine pump refrigerating system, according to the actual room temperature condition, the fluorine pump refrigerating system can adopt the mode with the highest energy efficiency to perform refrigeration.

With reference to the first aspect, in certain implementation manners of the first aspect, the system further includes: a shut-off valve 180 connected in series with the compressor 120, the shut-off valve 180 controlling opening and closing of the compressor 120.

Besides the first three-way reversing valve can control whether the compressor 120 needs to be started or not, the opening and closing of the compressor 120 can be controlled through the opening and closing of the stop valve connected in series on the management of the compressor 120, and the working mode of the fluorine pump refrigerating system can be flexibly controlled.

With reference to the first aspect, in certain implementation manners of the first aspect, the system further includes: a second three-way directional control valve 170, the second three-way directional control valve 170 including a fourth port 172, a fifth port 174, and a sixth port 176, the tenth port 144 being connected to the third port 116, including: the tenth port 144 is connected to the fourth port 172, the sixth port 176 is connected to the third port 116, and the second three-way selector valve 170 is configured to output the depressurized refrigerant from the sixth port 176 to the third port 116 of the gas-liquid separator 110, or the second three-way selector valve 170 is configured to output the depressurized refrigerant from the fifth port 174 to the fifth port 102 of the first heat exchanger 110.

Specifically, "the tenth port 144 is connected to the fourth port 172, the sixth port 176 is connected to the third port 116" may be understood as that the pressure reducing device 140 communicates with the gas-liquid separation device 110 via the second three-way directional valve 170.

In the normal operation mode, the fluorine pump is a normal operation device, the second three-way reversing valve 170 may control the depressurized refrigerant to be outputted from the sixth port 176 to the third port 116 of the gas-liquid separation device 110, and further, the gas-liquid separation device 110 may supply the refrigerant to the fluorine pump 150. When the fluorine pump is a normal operation device, the energy efficiency of the fluorine pump refrigerating system can be improved; when the fluorine pump fails, the second three-way reversing valve 170 may control the depressurized refrigerant to be outputted from the fifth port 174 to the fifth port 102 of the first heat exchanger 100, so as to ensure a cooling effect.

Through the fluorine pump refrigerating system, when the fluorine pump fails, the normal refrigerating effect can be ensured, and the application flexibility of the fluorine pump refrigerating system is improved.

With reference to the first aspect, in some implementations of the first aspect, the gas-liquid separation device 110 outputs a pure liquid refrigerant through the fourth port 118.

By the separation function of the gas-liquid separation device 110, the pure liquid refrigerant in the lower part of the gas-liquid separation device 110 is input to the first heat exchanger 100 through the fluorine pump 150.

By inputting pure liquid refrigerant into the first heat exchanger 100, the problem of low heat exchange efficiency of the first heat exchanger 100 caused by uneven temperature distribution of the existing refrigerant in a gas-liquid two-phase mixed state when the refrigerant passes through the first heat exchanger 100 can be solved. By the system, the refrigerant distribution and the temperature distribution in the first heat exchanger 100 can be more uniform, and the heat exchange efficiency of the first heat exchanger 100 is improved by more than 30%.

With reference to the first aspect, in some implementations of the first aspect, the gas-liquid separation device 110 outputs a saturated gaseous refrigerant through the second port 114.

In the case where the pure liquid refrigerant is input to the fifth interface 102 of the first heat exchanger 100, the superheated gaseous refrigerant output from the sixth interface 104 of the first heat exchanger 100 may be changed into a saturated gaseous refrigerant or a refrigerant in a gas-liquid two-phase mixed state, so as to reduce the superheat degree of the outlet of the first heat exchanger 100.

The saturated gaseous refrigerant or the refrigerant in a gas-liquid two-phase mixture state output from the first heat exchanger 100 is separated by the gas-liquid separation device 110, and the saturated gaseous refrigerant at the lower part of the gas-liquid separation device 110 is input to the compressor 120 through the second interface 114.

The superheated gaseous refrigerant input by the compressor 120 is changed into saturated gaseous refrigerant, so that the exhaust temperature of the compressor 120 is reduced by 12 ℃, the rotation speed is reduced by 10%, the energy efficiency is improved by more than 15%, and the cooling capacity (coefficient of performance, COP) obtained by the unit power consumption of the fluorine pump refrigerating system is improved by more than 8%.

With reference to the first aspect, in certain implementations of the first aspect, the compressor 120 is connected in parallel with the fluorine pump 150.

By the reversing action of the first three-way reversing valve 160 and the second three-way reversing valve 170, the compressor 120 and the fluorine pump 150 can be connected in parallel, so that a proper working mode can be selected for refrigeration according to the actual outdoor temperature condition.

With reference to the first aspect, in certain implementations of the first aspect, the compressor 120, the gas-liquid separation device 110, the second heat exchanger 130, and the fluorine pump 150 are installed outdoors, and the first heat exchanger 100 is installed indoors.

The fluorine pump and the compressor are arranged outdoors, so that the pipeline resistance can be overcome through a long link of the fluorine pump, and the compressor can be reduced to work against the pipeline resistance.

With reference to the first aspect, in certain implementations of the first aspect, the system further includes a controller that controls the operating frequency of the fluorine pump 150 to automatically adjust within a first range if the outdoor temperature is less than a first threshold; alternatively, if the outdoor temperature is greater than the first threshold, the controller controls the operating frequency of the fluorine pump 150 to be increased from the original first frequency to the second frequency, and the controller controls the operating frequency of the compressor 120 to be increased from the original third frequency to the fourth frequency.

Specifically, when the outdoor temperature is high, the amount of cold demand increases; when the outdoor temperature is low, the amount of cold demand decreases.

One way to achieve this is that when the system detects an increase in the liquid level of the gas-liquid separation device 110, the amount of cold required is reduced; when the system detects a decrease in the liquid level of the gas-liquid separation device 110, the amount of cold demand increases.

Alternatively, when the system detects that the temperature of the outlet refrigerant of the first heat exchanger 100 increases, the amount of cold required increases; when the system detects a decrease in the temperature of the outlet refrigerant of the first heat exchanger 100, the amount of cooling required decreases.

Specifically, the first threshold may be flexibly set according to the actual environment in which the fluorine pump refrigeration system is located, which is not limited in this application.

Additionally, as the cooling capacity demand of the system increases, the system may be stabilized by increasing the operating frequency of the compressor 120 and the fluorine pump 150; when the cooling demand of the system is reduced, the system may be stabilized by reducing the operating frequency of the compressor 120 and the fluorine pump 150.

Specifically, whether the system is stable may be determined in two ways:

First kind: whether the liquid level of the gas-liquid separation device 110 is changed. If the liquid level of the gas-liquid separation device 110 is reduced, it is indicated that the cooling capacity requirement of the system is increased; if the liquid level of the gas-liquid separation device 110 increases, this indicates that the cooling demand of the system decreases.

Second kind: the first heat exchanger 100 outputs the superheat degree of the refrigerant. If the superheat degree of the refrigerant output by the first heat exchanger 100 increases, the cooling capacity requirement of the system increases; if the superheat of the refrigerant output from the first heat exchanger 100 is reduced, this indicates that the cooling demand of the system is reduced.

When the amount of change in the cooling demand is less than the first threshold, the controller can automatically adjust the frequency of the fluorine pump 150 to ensure the stability of the system.

With reference to the first aspect, in certain implementations of the first aspect, the system includes at least one compressor 120, and/or at least one fluorine pump 150, and/or at least one first heat exchanger 100, and/or at least one second heat exchanger 130, wherein the at least one compressor 120 is connected in parallel, the at least one fluorine pump 150 is connected in parallel, the at least one first heat exchanger 100 is connected in parallel, and the at least one second heat exchanger 130 is connected in parallel.

Specifically, the correspondence among the compressor 120, the fluorine pump 150, the first heat exchanger 100, and the second heat exchanger 130 may be one-to-one, one-to-many, many-to-one, and many-to-many, which is not limited in this application.

The fluorine pump refrigeration system may include different numbers of the compressor 120, the fluorine pump 150, the first heat exchanger 100, and the second heat exchanger 130, thereby improving flexibility of system design.

Drawings

Fig. 1 is a system architecture diagram of a fluorine pump mode or a compressor mode.

Fig. 2 is a system architecture diagram of a mixed mode.

Fig. 3 is a schematic configuration diagram of an example of the fluorine pump refrigeration system of the present application.

Fig. 4 is a schematic block diagram of another example of a fluorine pump refrigeration system of the present application.

Fig. 5 shows a system architecture diagram of a fluorine pump cooling mode provided in the present application.

Fig. 6 shows an example of a pressure enthalpy diagram of the fluorine pump cooling mode provided in the present application.

Fig. 7 shows a system architecture diagram of a coupled refrigeration mode of a fluorine pump compressor provided herein.

Fig. 8 shows an example of a pressure enthalpy diagram of the compressor linked refrigeration mode of the fluorine pump provided in the present application.

Fig. 9 shows a system architecture diagram of a compressor refrigeration mode provided herein.

Fig. 10 shows an example of a pressure enthalpy diagram of the compressor refrigeration mode provided herein.

Fig. 11 shows an example of a system architecture diagram of a multiple system provided in the present application.

Fig. 12 shows a schematic diagram of a system control strategy provided in the present application.

Fig. 13 shows a schematic diagram of another system control strategy provided herein.

Fig. 14 shows a system architecture diagram in a water cooling scenario provided in the present application.

Fig. 15 shows an overall architecture diagram of a water cooling scenario provided in the present application.

Fig. 16 shows a system architecture diagram in an air-cooled scenario provided in the present application.

Fig. 17 shows a whole machine architecture diagram in an air cooling scenario provided by the present application.

Detailed Description

The technical solutions in the present application will be described below with reference to the accompanying drawings.

FIG. 1 shows a current fluorine pump air conditioning system, when the outdoor temperature is greater than 15 ℃, the compressor mode is turned on, i.e. the check valve 1 is controlled to be closed and the check valve 2 is controlled to be opened; when the outdoor temperature is less than 10 ℃, a fluorine pump mode is started, namely the check valve 1 is controlled to be opened and the check valve 2 is controlled to be closed; when the outdoor temperature is between 10 ℃ and 15 ℃, the mixed mode of the compressor and the fluorine pump working simultaneously is started, namely the check valve 1 and the check valve 2 are controlled to be closed.

Next, a refrigerating operation in the compressor mode and a refrigerating operation in the fluorine pump mode will be described in detail.

During the refrigeration operation in the compressor mode, a large amount of heat is absorbed when the liquid changes from a liquid state to a gas state, so that the ambient temperature is reduced, and the process is called liquid vaporization heat absorption for short. During this process, a great deal of heat is absorbed by the vaporization of the freon refrigerant.

The change in substance from liquid to gas is not only temperature dependent but also pressure dependent. The higher the temperature or the lower the pressure, the liquid is easy to vaporize into gas, and the heat is absorbed; the lower the temperature or the higher the pressure, the easier the gas liquefies into a liquid, giving off heat.

The compressor, evaporator, condenser, and throttle valve are referred to as four major components of the refrigeration system. The present application describes a refrigeration operation in a compressor mode by taking a compressor, an evaporator, a condenser and a throttle valve as examples, but the refrigeration operation in the compressor mode also involves other devices, and the present application is not limited thereto.

The compressor and the condenser are installed in an outdoor unit of the air conditioner, and the evaporator is installed in an indoor unit of the air conditioner.

In general, the refrigeration process can be divided into the following four stages.

The first stage: this stage is accomplished within the compressor. The compressor sucks the gas refrigerant sent from the evaporator, compresses the gas refrigerant, and then changes the gas refrigerant into high-temperature and high-pressure gas. This process is extremely short, and the heat of the warmed gas is hardly transferred to the outside, so this stage is called an adiabatic compression stage.

And a second stage: this stage is done in the condenser. The compressor sends a high-temperature and high-pressure refrigerant into the condenser, and the high-temperature and high-pressure refrigerant is cooled in the condenser. This phase is called the isothermal compression phase, in which the change of gas phase to liquid phase occurs and the temperature inside the condenser is constant. The task of transferring the heat absorbed in the room to the outside is also accomplished at this stage.

And a third stage: this stage is done at the throttle valve. The throttle valve serves to throttle and reduce the pressure so that the refrigerant becomes a low-pressure and low-temperature state. This stage is called an adiabatic expansion stage because it takes a short time and cannot absorb external heat.

Fourth stage: this stage is accomplished in the evaporator. Since the tube diameter of the evaporator is much larger than that of the throttle valve, the pressure of the refrigerant suddenly becomes small and the temperature thereof also drops sharply. The refrigerant with lower temperature enters the evaporator to change from indoor heat absorption to high-temperature and high-pressure state until complete vaporization so that the refrigerant is rapidly evaporated. This stage is called isothermal expansion stage, since the temperature inside the evaporator is constant at this stage. The task of absorbing indoor heat is also accomplished at this stage.

The high-temperature and high-pressure gas in the evaporator returns to the compressor again, and the processes from the first stage to the fourth stage are repeated, so that refrigeration is repeatedly circulated.

In summary, the flow direction of the refrigerant in the refrigeration process is: the refrigerant flows from the discharge pipe of the compressor to the condenser of the outdoor unit and is sent to the evaporator of the indoor unit through the throttle valve. Then, the refrigerant flows from the air pipe of the evaporator to the air return pipe of the compressor.

In the refrigerating working process of the fluorine pump mode, because the outdoor temperature is low, abundant cold sources exist in nature, and the energy-saving effect can be achieved by adopting a natural cooling mode.

Specifically, when in the fluorine pump mode, the fluorine pump forces liquid refrigerant to flow through the evaporator, the liquid refrigerant absorbs heat from the hot indoor air, and a small portion of the refrigerant absorbs heat to vaporize. The refrigerant liquid with bubbles circulates into the condenser, and then releases the heat carried by the refrigerant liquid into the outdoor atmosphere, and the refrigerant becomes supercooled liquid after releasing heat. Thus, the outdoor cold air can cool the indoor hot air by continuously working.

When the outdoor temperature is between 10 ℃ and 15 ℃, the mixed mode of the compressor and the fluorine pump which are simultaneously operated is started, and the compressor and the fluorine pump are used for refrigerating in series connection, as shown in figure 2.

In summary, when the outdoor temperature of the current fluorine pump air conditioning system is high, the conventional compressor refrigeration mode is still adopted, and the energy efficiency of the fluorine pump air conditioning system cannot be improved essentially. In addition, when the temperature is low or high, the compressor and the fluorine pump cannot be operated simultaneously, so that the frequency of use during the period is reduced, and the advantages of the device cannot be fully exerted.

In order to solve the above problems, the present application provides a fluorine pump refrigeration system, as shown in fig. 3.

The fluorine pump refrigeration system shown in fig. 3 includes a first heat exchanger 100, a gas-liquid separation device 110, a compressor 120, a second heat exchanger 130, a pressure reducing device 140, and a fluorine pump 150.

The first heat exchanger 100 includes a fifth interface 102 and a sixth interface 104. The refrigerant is input to the first heat exchanger 100 through the fifth interface; the refrigerant absorbs heat in the room in the first heat exchanger 100, or the first heat exchanger 100 heats the inputted refrigerant; the first heat exchanger 100 outputs the heated refrigerant from the sixth port 104.

Specifically, the refrigerant outputted from the sixth port 104 may be a saturated gaseous refrigerant or a gas-liquid mixed refrigerant.

The gas-liquid separation device 110 includes a first port 112, a second port 114, a third port 116, and a fourth port 118. The first port 112 is connected to the sixth port, and the refrigerant outputted from the sixth port 104 is inputted to the gas-liquid separator 110 from the first port.

Specifically, the gas-liquid separation device 110 performs gas-liquid separation on the refrigerant inputted from the first port. The gas-liquid separator 110 has an upper portion that is a gaseous refrigerant and a lower portion that is a liquid refrigerant. The gaseous refrigerant at the upper part of the gas-liquid separation device 110 is input to the first input port 122 of the compressor through the second interface 114, and the liquid refrigerant at the lower part of the gas-liquid separation device 110 is input to the second input port 152 of the fluorine pump 150 through the fourth interface 118.

The compressor 120 includes a first input port 122 and a first output port 124. The first inlet 122 receives the gaseous refrigerant from the upper portion of the gas-liquid separator 110 of the second port 114. Specifically, the gaseous refrigerant in the upper portion of the gas-liquid separation device 110 is a saturated gaseous refrigerant.

The compressor 120 compresses the input saturated gaseous refrigerant and outputs the compressed high-temperature and high-pressure gaseous refrigerant through the first output port 124.

The second heat exchanger 130 includes a seventh interface 132 and an eighth interface 134. The second heat exchanger 130 receives the high-temperature and high-pressure gaseous refrigerant outputted from the first output port 124 through the seventh interface 132, cools the inputted high-temperature and high-pressure gaseous refrigerant, and outputs the cooled refrigerant from the eighth interface 134.

The pressure relief device 140 includes a ninth interface 142 and a tenth interface 144. The pressure reducing device 140 receives the cooled refrigerant from the eighth port 134 through the ninth port 142, reduces the pressure of the cooled refrigerant, and outputs the reduced pressure refrigerant from the tenth port 144.

Specifically, the pressure reducing device 140 reduces the pressure of the cooled refrigerant to further reduce the temperature of the refrigerant so as to cool the refrigerant as much as possible into a liquid refrigerant.

The gas-liquid separation device 110 receives the refrigerant from the tenth port 144 through the third port 116, and performs gas-liquid separation. The gas-liquid separation device 110 inputs the lower portion of the pure liquid refrigerant to the fluorine pump 150 through the fourth port 118.

The fluorine pump 150 includes a second input port 152 and a second output port 154, and the fluorine pump 150 forcibly flows the liquid refrigerant inputted from the second input port 152 into the first heat exchanger 100 through the second output port 154 so that the refrigerant absorbs heat in the first heat exchanger 100 to complete the circulation cooling.

When the outdoor temperature is higher, the energy consumption of the compressor can be reduced by adopting the mode of linkage refrigeration of the fluorine pump and the compressor. When the outdoor temperature is lower, the fluorine pump refrigerating system can utilize a natural cold source to refrigerate, namely, a fluorine pump refrigerating mode can be started. Or when the fluorine pump fails, in order to ensure the refrigerating effect, a compressor refrigerating mode can be started to perform refrigeration. As shown in fig. 4.

Another fluorine pump refrigeration system is provided, as shown in fig. 4.

The refrigeration system shown in fig. 4 may further include a first three-way reversing valve 160, a second three-way reversing valve 170, a shut-off valve 180, etc. on the basis of the refrigeration system shown in fig. 3.

The first three-way reversing valve 160 includes a first port 162, a second port 164, and a third port 166. The first port 162 of the first three-way reversing valve 160 is an input, and the second port 164 and the third port 166 are two outputs.

The first three-way reversing valve 160 is used for controlling the refrigerant output from the sixth port 104 to be input to the gas-liquid separation device 110 through the second port 164, or the refrigerant output from the sixth port 104 to be input to the second heat exchanger 130 through the third port 166.

When the first three-way switching valve 160 controls the refrigerant outputted from the sixth port 104 to be inputted to the second heat exchanger 130 through the third port 166 and the shut-off valve 180 is closed, the compressor 120 is not started, and the fluorine pump refrigeration system is operated by using the fluorine pump.

The second three-way reversing valve 170 includes a fourth port 172, a fifth port 174, and a sixth port 176. The fourth port 172 of the second three-way reversing valve 170 is an input and the fifth port 174 and the sixth port 176 are two outputs.

The second three-way switching valve 170 is used to control the refrigerant outputted from the tenth port 144 to be inputted to the first heat exchanger 100 through a fifth port 174, or the refrigerant outputted from the tenth port 144 to be inputted to the gas-liquid separation device 110 through a sixth port 176.

When the second three-way switching valve 170 is used to control the refrigerant outputted from the tenth port 144 to be inputted to the first heat exchanger 100 through the fifth port 174, the fluorine pump 150 is not started, and the fluorine pump refrigeration system is operated using a compressor.

It should be noted that the second three-way reversing valve 170 is used to control the refrigerant output from the tenth port 144 to be input to the first heat exchanger 100 through the fifth port 174, and is used in the case of failure of the fluorine pump. Normally, the fluorine pump is a normal operation device of the fluorine pump refrigeration system.

In different cases, the system can be changed into three modes of operation by adjusting the orientation of the shut-off valve 180, the first three-way diverter valve 160, and the second three-way diverter valve 170 in the system shown in fig. 4: 1. a fluorine pump cooling mode; 2. a fluorine pump compressor linkage refrigeration mode; 3. compressor cooling mode.

Hereinafter, the present application describes the operation in the three modes in detail, using an accumulator or a gas-liquid separator as an example of the gas-liquid separator 110, using an evaporator as an example of the first heat exchanger 100, using a condenser as an example of the second heat exchanger 130, using an electronic expansion valve as an example of the pressure reducing device 140, using the three-way selector valve 1 as an example of the first three-way selector valve 160, using the three-way selector valve 2 as an example of the second three-way selector valve 170.

The application is described by taking air cooling temperature control of a data center as an example. When the outdoor temperature is lower than 15 ℃, starting a fluorine pump refrigeration mode; when the outdoor temperature is higher than 15 ℃, starting a fluorine pump compressor linkage refrigeration mode; when the fluorine pump fails, the compressor refrigeration mode may be activated.

In this system the fluorine pump is a very operating device and the compressor is a very operating device.

The three modes of operation described above are described in detail below, as shown in fig. 5 for the 1 st mode of operation.

By closing the stop valve and adjusting the directions of the three-way steering valve 1 and the three-way steering valve 2, the fluorine pump air conditioning system can realize that the 1 st fluorine pump refrigeration mode is adopted. The dotted line portion of the fluorine pump air conditioning system shown in fig. 5 is an unnecessary portion in the 1 st operation mode.

Specifically, the input end of the evaporator is connected with the output end of the fluorine pump, and the fluorine pump forces the liquid refrigerant to flow through the evaporator. The liquid refrigerant absorbs heat of indoor hot air in the evaporator, and evaporates. The output end of the evaporator is connected with the input end of the condenser, and the evaporator sends the evaporated refrigerant into the condenser. Therefore, the process from the state point 3 to the state point 1 in fig. 5 is the evaporation process of the refrigerant.

The condenser condenses the refrigerant liquid with bubbles, releases heat carried by the refrigerant to the outdoor atmosphere, and the refrigerant becomes supercooled liquid after heat release. The output end of the condenser is connected with the input end of the electronic expansion valve. Therefore, the process from the state point 1 to the state point 2 in fig. 5 is a condensation process of the refrigerant.

When the refrigerant passes through the electronic expansion valve, the electronic expansion valve can throttle the refrigerant, the pressure of the throttled refrigerant is reduced, and the refrigerant is in a low-temperature and low-pressure state.

The output end of the electronic expansion valve is connected with the input end of the three-way steering valve 2, and the output end of the three-way steering valve 2 is connected with the input end of the liquid reservoir. The refrigerant passing through the electronic expansion valve further flows to the accumulator through the three-way diverter valve 2.

Specifically, the liquid reservoir may be a gas-liquid separator that separates an inflow liquid refrigerant from a gas refrigerant, and the gas-liquid separation of the liquid reservoir is integrated. In general, the accumulator is referred to as an accumulator in the fluorine pump cooling mode, and as a gas-liquid separator in the fluorine pump compressor linked cooling mode.

The output end of the liquid reservoir is connected with the input end of the fluorine pump, the liquid reservoir sends the stored liquid refrigerant into the input end of the fluorine pump, and the fluorine pump forces the liquid refrigerant to flow into the evaporator. Thus, the process from state point 2 to state point 3 in fig. 5 is a fluorine pump pressurization process of the fluorine pump.

Through the above-mentioned circulation, it is possible to cool the indoor hot air with the outdoor cold air.

The pressure enthalpy diagram of the fluorine pump air conditioning system adopting the 1 st fluorine pump refrigeration mode is shown as 5.

The operation and the refrigerant state corresponding to the state points shown in fig. 6 are shown in table 1 below.

TABLE 1

State point	Working process	Refrigerant state
			1 to 2	Condensation process	The gaseous state changes into liquid state
2 to 3	Fluorine pump pressurization process	Liquid state
			3 to 1	Evaporation process	The liquid state changes into the gas state

For the 2 nd mode of operation, as shown in fig. 7.

By opening the stop valve and adjusting the directions of the three-way steering valve 1 and the three-way steering valve 2, the linkage refrigeration mode of the fluorine pump air conditioning system adopting the 2 nd fluorine pump compressor can be realized. The dotted line portion of the fluorine pump air conditioning system shown in fig. 7 is an unnecessary portion in the operation mode of fig. 2.

Specifically, the input end of the compressor is connected with the output end of the gas-liquid separator, the output end of the gas-liquid separator inputs saturated gas at the upper part of the gas-liquid separator into the compressor, and the gas at the state point 1 is saturated gas.

The compressor compresses the sucked saturated gas to become high-temperature and high-pressure gas. The pressure in the process compressor increases and the enthalpy of the refrigerant also increases. Therefore, the process of the status point 1 to the status point 2 in fig. 7 is a compression process of the compressor. The output of compressor is connected with the input of stop valve, and the output of stop valve is connected with the input of condenser. The compressor sends high-temperature high-pressure gas refrigerant into the condenser.

The high-temperature and high-pressure gas refrigerant is cooled in the condenser. In this process the condenser transfers heat from the room to the outside. Therefore, the process from the status point 2 to the status point 3 in fig. 7 is a condensation process of the condenser. The pressure in the process condenser is unchanged, but the enthalpy of the refrigerant decreases during cooling.

The output end of the condenser is connected with the input end of the electronic expansion valve, the electronic expansion valve throttles the condensed refrigerant, the pressure of the refrigerant suddenly decreases, the temperature of the refrigerant also rapidly decreases, and the refrigerant can be changed into a low-pressure and low-temperature state. Thus, the process from the state point 3 to the state point 4 in fig. 7 is a throttle process of the electronic expansion valve.

The output end of the electronic expansion valve is connected with the input end of the three-way steering valve 2, the output end of the three-way steering valve 2 is connected with the input end of the gas-liquid separator, and the refrigerant in a low-pressure and low-temperature state after being throttled by the electronic expansion valve enters the gas-liquid separator to realize the separation of the gaseous refrigerant and the liquid refrigerant. Therefore, the process from the state point 4 to the state point 5 in fig. 7 is a separation process of the gaseous refrigerant and the liquid refrigerant of the gas-liquid separator.

The output end of the gas-liquid separator is connected with the input end of the fluorine pump, the gas-liquid separator sends the stored liquid refrigerant into the input end of the fluorine pump, and the fluorine pump forces the liquid refrigerant to flow into the evaporator. Therefore, the process from the state point 5 to the state point 6 in fig. 7 is a pressurizing process of the refrigerant by the fluorine pump.

The output end of the fluorine pump is connected with the input end of the evaporator, the fluorine pump sends the pressurized liquid refrigerant into the evaporator of the indoor unit, and the liquid refrigerant absorbs indoor heat for evaporation. The output end of the evaporator is connected with the input end of the three-way steering valve 1, and the output end of the three-way steering valve 1 is connected with the input end of the gas-liquid separator. The output end of the evaporator inputs a gas-liquid two-phase refrigerant with a certain superheat degree into the gas-liquid separator through the three-way steering valve 1, so as to realize the separation of a gaseous refrigerant and a liquid refrigerant. Therefore, the process from the status point 6 to the status point 7 in fig. 7 is the evaporation process of the evaporator.

The output end of the gas-liquid separator inputs the saturated gas of the upper part of the gas-liquid separator to the compressor again, and thus, the process from the state point 7 to the state point 1 in fig. 7 is a separation process of the gas-liquid separator. By the reciprocating circulation, the outdoor cold air can cool the indoor hot air.

The pressure enthalpy diagram of the fluorine pump air conditioning system adopting the 2 nd fluorine pump compressor linkage refrigeration mode is shown as 7.

The operation and the refrigerant state corresponding to the state points shown in fig. 8 are shown in table 2 below.

TABLE 2

State point	Working process	Refrigerant state
			1	Saturated gas	Saturated gaseous state
1 to 2	Compression process	Supersaturated gaseous state
			2 to 3	Condensation process	The gaseous state changes into liquid state
3 to 4	Throttling process	The liquid state is changed into a gas-liquid mixed state
			4 to 5	Gas-liquidSeparation process	The mixed state of the gas and the liquid changes into liquid state
5 to 6	Fluorine pump pressurization process	Liquid state
			6 to 7	Evaporation process	The liquid state is changed into a gas-liquid mixed state
7 to 1	Gas-liquid separation process	The mixed state of the gas and the liquid changes into the gaseous state

By using the above-mentioned compressor linkage refrigeration mode of the fluorine pump, the refrigerant at the input end of the evaporator is changed from a gas-liquid mixed state into a 100% liquid-phase refrigerant, and the refrigerant at the output end of the evaporator is changed from a supersaturated gas state into a saturated gas state or a gas-liquid mixed state, so that the problems of uneven refrigerant distribution, uneven evaporation temperature distribution and low evaporation efficiency when the refrigerant passes through the evaporator can be solved.

For the 3 rd mode of operation, as shown in fig. 9.

By opening the stop valve and adjusting the directions of the three-way steering valve 1 and the three-way steering valve 2, the 3 rd compressor refrigeration mode of the fluorine pump air conditioning system can be realized. The dotted line portion of the fluorine pump air conditioning system shown in fig. 9 is an unnecessary portion in the 3 rd operation mode.

Specifically, the input end of the compressor is connected with the output end of the gas-liquid separator, and the output end of the gas-liquid separator inputs supersaturated gas at the upper part of the gas-liquid separator into the compressor, and the gas at the state point 1 is the supersaturated gas.

The compressor compresses the sucked supersaturated gas to become high-temperature and high-pressure gas. The pressure in the process compressor increases and the enthalpy of the refrigerant also increases. Therefore, the process of the status point 1 to the status point 2 in fig. 9 is a compression process of the compressor. The output of compressor is connected with the input of stop valve, and the output of stop valve is connected with the input of condenser. The compressor sends high-temperature high-pressure gas refrigerant into the condenser.

The high-temperature and high-pressure gas refrigerant is cooled in the condenser. In this process the condenser transfers heat from the room to the outside. Therefore, the process from the status point 2 to the status point 3 in fig. 9 is a condensation process of the condenser. The pressure in the process condenser is unchanged, but the enthalpy of the refrigerant decreases during cooling.

The output end of the condenser is connected with the input end of the electronic expansion valve, the electronic expansion valve throttles the condensed refrigerant, the pressure of the refrigerant suddenly decreases, the temperature of the refrigerant also rapidly decreases, and the refrigerant can be changed into a low-pressure and low-temperature state. Therefore, the process from the state point 3 to the state point 4 in fig. 9 is a throttle process of the electronic expansion valve.

The output end of the electronic expansion valve is connected with the input end of the three-way steering valve 2, the output end of the three-way steering valve 2 is connected with the input end of the evaporator, the low-pressure low-temperature-state gas-liquid mixed-state refrigerant throttled by the electronic expansion valve enters the evaporator, and the gas-liquid mixed-state refrigerant absorbs indoor heat for evaporation. Therefore, the process from the status point 4 to the status point 1 in fig. 9 is the evaporation process of the evaporator.

And the output end of the gas-liquid separator inputs the supersaturated gas at the upper part of the gas-liquid separator into the compressor again. By the reciprocating circulation, the outdoor cold air can cool the indoor hot air.

The above-mentioned fluorine pump air conditioning system adopts the pressure enthalpy chart of the 3 rd kind of compressor refrigeration mode as shown in 9.

The operation and the refrigerant state corresponding to the state points shown in fig. 10 are shown in table 3 below.

TABLE 3 Table 3

State point	Working process	Refrigerant state
			1	Supersaturated gas	Supersaturated gaseous state
1 to 2	Compression process	Supersaturated gaseous state
			2 to 3	Condensation process	The gaseous state changes into liquid state
3 to 4	Throttling process	The liquid state is changed into a gas-liquid mixed state
			4 to 1	Evaporation process	The mixed state of the gas and the liquid changes into the gaseous state

When the outdoor temperature is lower than 15 ℃, starting a fluorine pump refrigeration mode; and when the outdoor temperature is higher than 15 ℃, starting a fluorine pump compressor linkage refrigeration mode. In this system the fluorine pump is a very operating device and the compressor is a very operating device. Therefore, the problems of low energy efficiency, low compressor energy efficiency, high exhaust temperature of the compressor and high rotating speed of the compressor of the traditional fluorine pump air conditioning system when the outdoor temperature is high can be solved. Compared with the traditional compressor refrigerating system, the fluorine pump refrigerating system has the advantages that the refrigerating capacity (coefficient of performance, COP) obtained by unit power consumption is improved by more than 8%, the compressor efficiency is improved by more than 15%, the exhaust temperature of the compressor is reduced by 12 ℃, and the rotating speed of the compressor is reduced by 10%.

In addition, the compressor is circulated in a short circuit, so that the pipeline resistance is low, and the work of the compressor for overcoming the pipeline resistance can be reduced; and the fluorine pump circulation is long-way, and the pipeline resistance of the long-way and the fluorine pump are provided.

Additionally, the fluorine pump and the compressor in the fluorine pump refrigerating system are connected in parallel, and when the fluorine pump fails, the compressor refrigerating mode can be started.

The fluorine pump air conditioning system of the present application may be a system including one compressor, one fluorine pump, one condenser, and one evaporator, or may be a system including a plurality of compressors, a plurality of fluorine pumps, a plurality of condensers, and a plurality of evaporators, as shown in fig. 11.

The compressors are connected in parallel, the fluorine pumps are connected in parallel, the condensers are connected in parallel, the evaporators are connected in parallel, and the fluorine pumps and the evaporators can be connected in parallel in one-to-one, one-to-many, many-to-one and many-to-many modes.

The working process of the fluorine pump air conditioning system provided by the application is described in detail above, and the system control strategy of the fluorine pump air conditioning system is described below.

According to the fluorine pump air conditioning system, the frequency of the compressor and the frequency of the fluorine pump can be adjusted according to the liquid level state of the liquid reservoir or the gas-liquid separator and the superheat degree of the outlet of the evaporator, so that the fluorine pump air conditioning system can reach a stable state.

When the cooling capacity requirement of the system is in a stable state or slightly fluctuates, the liquid level of the liquid reservoir or the gas-liquid separator is kept unchanged, the frequency of the compressor is kept constant, and the frequency of the fluorine pump has a certain adjustment margin W1. As shown in fig. 12.

The frequency of the fluorine pump can be automatically adjusted within the frequency range of W1, so that the superheat degree of the refrigerant at the output end of the evaporator is 0, and the refrigerant at the output end of the evaporator is ensured to be in a saturated gaseous state.

When the cooling capacity demand of the system is increased, the fluorine pump cannot ensure that the superheat degree of the refrigerant at the output end of the evaporator is 0 in the range of the adjustment margin W1, the consumption of the refrigerant is increased, the liquid level of the liquid reservoir is reduced, and the outlet temperature of the evaporator is overheated. At this time, the fluorine pump and the compressor need to be increased in frequency, so that the fluorine pump air conditioning system is in a stable state.

Similarly, when the cooling capacity requirement of the system increases, the fluorine pump cannot guarantee the superheat degree of the refrigerant at the output end of the evaporator to be 0 in the range of the adjustment margin W1, the consumption of the refrigerant is reduced, the liquid level of the liquid reservoir rises, and the outlet temperature of the evaporator cannot guarantee the superheat degree. At this time, the fluorine pump and the compressor need to be down-converted, so that the fluorine pump air conditioning system is in a stable state.

Possible cooling scenarios for a condenser in a fluorine pump air conditioning system are described below.

First scenario: in a water cooling scene, the condenser is a water cooling plate type heat exchanger, and a system architecture diagram in the water cooling scene is shown in fig. 14.

In this scenario, the operation of the fluorine pump air conditioning system is described above, and will not be described again here. The operation of the water-cooled plate heat exchanger will be described.

The cold source of the plate heat exchanger is provided by the cooling water tower shown in fig. 14, and the spraying of the cooling water tower is started all the year round. When the outdoor temperature is higher than a certain temperature (for example, higher than 10 ℃), the fluorine pump air conditioning system starts a fluorine pump compressor linkage refrigeration mode, and the cooling water tower can cool water to the wet bulb temperature so as to provide a cold source for the fluorine pump air conditioning system. The water flow path provided by the cooling water tower is shown as a complete machine schematic diagram in a water cooling scene shown in fig. 15, water in the water tank flows into the plate heat exchanger through the water pump, and heat in the plate heat exchanger is taken away. The water output from the plate heat exchanger is conveyed to a spraying system, and returns to the water tank through the spraying system. The water dissipates heat through a fan in the spraying process, and is changed into cooling water again.

In addition to the water flow path, as shown in the overall schematic diagram of the water cooling scenario in fig. 15, the circuit for compressing the refrigerant includes a low-pressure refrigerant flow path and a high-pressure refrigerant flow path. The pipeline from the liquid reservoir to the compressor is a low-pressure refrigerant flow path; the pipeline from the compressor to the plate heat exchanger and from the plate heat exchanger to the throttle valve is a high-pressure refrigerant flow path; the pipeline from the throttle valve to the liquid storage device is a low-pressure refrigerant flow path. The liquid storage device sends the low-pressure pure liquid refrigerant into the indoor machine room through the fluorine pump, and the low-pressure pure liquid refrigerant absorbs indoor heat in the indoor machine room to evaporate. The indoor machine room sends the evaporated gas-liquid two-phase mixed refrigerant into the liquid storage device for gas-liquid separation, as shown in fig. 15, into the machine room refrigerant flow path. In addition, the fan of the indoor machine room blows the cooled air into the room.

When the outdoor temperature is lower than a certain temperature (for example, lower than 10 ℃), the fluorine pump air conditioning system starts a fluorine pump refrigerating mode, and the refrigerant coming out of the indoor machine room is directly sent into the plate heat exchanger for cooling through the three-way reversing valve, so that the refrigerant flow path in the fluorine pump mode in winter is shown in fig. 15, and the energy-saving effect is achieved. The cooling water tower is characterized in that the opening degree of a flow regulating valve at the output end of the plate heat exchanger is regulated, so that the temperature of the water tank is maintained above 0 ℃ and the water tank is not frozen, as shown in fig. 14.

The second scenario: in the air cooling scene, the condenser is an air cooling fin tube type heat exchanger, and a system architecture diagram in the air cooling scene is shown in fig. 16.

In this scenario, the operation of the fluorine pump air conditioning system is described above, and will not be described again here. The working process of the air-cooled fin tube heat exchanger is described.

When the outdoor temperature is higher than a certain temperature (for example, higher than 10 ℃), the fluorine pump air conditioning system starts a fluorine pump compressor linkage refrigeration mode, and the fan timely dissipates heat by accelerating the air flow around the air-cooled fin tube type heat exchanger.

Fig. 17 shows a schematic diagram of the whole machine in an air-cooled scenario, in which the circuit for compressing the refrigerant includes a low-pressure refrigerant flow path and a high-pressure refrigerant flow path. The pipeline from the liquid reservoir to the compressor is a low-pressure refrigerant flow path; the pipeline from the compressor to the fin-tube heat exchanger and from the fin-tube heat exchanger to the throttle valve is a high-pressure refrigerant flow path; the pipeline from the throttle valve to the liquid storage device is a low-pressure refrigerant flow path. The liquid storage device sends the low-pressure pure liquid refrigerant into the indoor machine room through the fluorine pump, and the low-pressure pure liquid refrigerant absorbs indoor heat in the indoor machine room to evaporate. The indoor machine room sends the evaporated gas-liquid two-phase mixed refrigerant into the liquid storage device for gas-liquid separation, as shown in fig. 17, into the machine room refrigerant flow path. In addition, the fan of the indoor machine room blows the cooled air into the room.

When the outdoor temperature is lower than a certain temperature (for example, lower than 10 ℃), the fluorine pump air conditioning system starts a fluorine pump refrigerating mode, and the refrigerant coming out of the indoor machine room is directly sent into the air-cooled fin tube type heat exchanger for cooling through the three-way reversing valve, so that the energy-saving effect is achieved through a refrigerant flow path in the fluorine pump mode in winter as shown in fig. 17.

Those of ordinary skill in the art will appreciate that the various illustrative elements and algorithm steps described in connection with the embodiments disclosed herein may be implemented as electronic hardware, or combinations of computer software and electronic hardware. Whether such functionality is implemented as hardware or software depends upon the particular application and design constraints imposed on the solution. Skilled artisans may implement the described functionality in varying ways for each particular application, but such implementation decisions should not be interpreted as causing a departure from the scope of the present application.

It will be clear to those skilled in the art that, for convenience and brevity of description, specific working procedures of the above-described systems, apparatuses and units may refer to corresponding procedures in the foregoing method embodiments, and are not repeated herein.

In the several embodiments provided in this application, it should be understood that the disclosed systems, devices, and methods may be implemented in other manners. For example, the apparatus embodiments described above are merely illustrative, e.g., the division of the units is merely a logical function division, and there may be additional divisions when actually implemented, e.g., multiple units or components may be combined or integrated into another system, or some features may be omitted or not performed. Alternatively, the coupling or direct coupling or communication connection shown or discussed with each other may be an indirect coupling or communication connection via some interfaces, devices or units, which may be in electrical, mechanical or other form.

The units described as separate units may or may not be physically separate, and units shown as units may or may not be physical units, may be located in one place, or may be distributed on a plurality of network units. Some or all of the units may be selected according to actual needs to achieve the purpose of the solution of this embodiment.

In addition, each functional unit in each embodiment of the present application may be integrated in one processing unit, or each unit may exist alone physically, or two or more units may be integrated in one unit.

The foregoing is merely specific embodiments of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art can easily think about changes or substitutions within the technical scope of the present application, and the changes and substitutions are intended to be covered by the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.

Claims

1. A fluorine pump refrigeration system, the system comprising:

the first heat exchanger comprises a fifth interface and a sixth interface, and is used for heating the refrigerant input from the fifth interface and outputting the heated refrigerant from the sixth interface;

The gas-liquid separation device comprises a first interface, a second interface, a third interface and a fourth interface, and is used for separating gaseous refrigerant and liquid refrigerant received from the first interface, outputting the gaseous refrigerant from the second interface and outputting the liquid refrigerant from the fourth interface, and the first interface is connected with the sixth interface;

the compressor comprises a first input port and a first output port, the compressor is used for compressing the refrigerant input from the first input port and outputting the compressed refrigerant from the first output port, and the first input port is connected with the second interface;

the second heat exchanger comprises a seventh interface and an eighth interface, the second heat exchanger is used for cooling the refrigerant input from the seventh interface and outputting the cooled refrigerant from the eighth interface, and the seventh interface is connected with the first output port;

the decompression device comprises a ninth interface and a tenth interface, the decompression device is used for decompressing the refrigerant input from the ninth interface and outputting the decompressed refrigerant from the tenth interface, the ninth interface is connected with the eighth interface, and the tenth interface is connected with the third interface;

The fluorine pump comprises a second input port and a second output port, wherein the fluorine pump is used for outputting the refrigerant input from the second input port to the fifth interface of the first heat exchanger through the second output port, and the second input port is connected with the fourth interface.

2. The system of claim 1, wherein the system further comprises:

the first three-way reversing valve comprises a first port, a second port and a third port, wherein the first port is connected with the sixth port and comprises: the sixth interface is connected with the first interface, the second interface is connected with the first interface, the first three-way reversing valve is used for outputting the heated refrigerant from the second interface to the first interface of the gas-liquid separation device, or the first three-way reversing valve is used for outputting the heated refrigerant from the third interface to the seventh interface of the second heat exchanger.

3. The system of claim 2, wherein the system further comprises:

and the stop valve is connected with the compressor in series and is used for controlling the opening and closing of the compressor.

4. A system according to claim 3, wherein the system further comprises:

The second three-way reversing valve comprises a fourth port, a fifth port and a sixth port, and the tenth interface is connected with the third interface and comprises: the tenth port is connected with the fourth port, the sixth port is connected with the third port, the second three-way reversing valve is used for outputting the depressurized refrigerant from the sixth port to the third port of the gas-liquid separation device, or the second three-way reversing valve is used for outputting the depressurized refrigerant from the fifth port to the fifth port of the first heat exchanger.

5. The system of any one of claims 1 to 4, wherein the gas-liquid separation device outputs a pure liquid refrigerant through the fourth port.

6. The system of any one of claims 1 to 4, wherein the gas-liquid separation device outputs a saturated gaseous refrigerant through the second port.

7. The system of any one of claims 1 to 4, wherein the compressor is connected in parallel with the fluorine pump.

8. The system of any one of claims 1 to 4, wherein the compressor, the gas-liquid separation device, the second heat exchanger, the fluorine pump are installed outdoors, and the first heat exchanger is installed indoors.

9. The system of any one of claims 1 to 4, further comprising a controller,

if the outdoor temperature is less than a first threshold value, the controller controls the operating frequency of the fluorine pump to be adjusted within a first range; or alternatively, the process may be performed,

and if the outdoor temperature is higher than the first threshold value, the controller controls the working frequency of the fluorine pump to be increased from the first frequency to the second frequency, and controls the working frequency of the compressor to be increased from the third frequency to the fourth frequency.

10. The system of claim 9, wherein the system comprises at least one of the compressors, and/or at least one of the fluorine pumps, and/or at least one of the first heat exchangers, and/or at least one of the second heat exchangers,

the at least one compressor is connected in parallel, the at least one fluorine pump is connected in parallel, the at least one first heat exchanger is connected in parallel, and the at least one second heat exchanger is connected in parallel.