CN218154885U - Refrigerating unit - Google Patents

Abstract

The utility model discloses a refrigerating unit, which comprises a magnetic suspension compressor, a fluorine pump, an evaporative condenser, an evaporator and a gas-liquid separator; the exhaust port of the magnetic suspension compressor is connected with the inlet of the evaporative condenser; the outlet of the evaporative condenser is connected with the inlet of the evaporator, a throttling device is connected between the outlet of the evaporative condenser and the inlet of the gas-liquid separator, and the gas outlet of the gas-liquid separator is connected with the air suction port of the magnetic suspension compressor; the outlet of the evaporative condenser is also connected with the inlet of the fluorine pump, a throttling device is connected between the outlet of the fluorine pump and the inlet of the evaporator, the outlet of the fluorine pump is connected with the inlet of the evaporator, and the liquid outlet of the gas-liquid separator is connected with the inlet of the evaporative condenser. The refrigeration of the magnetic suspension compressor and the refrigeration of the fluorine pump are combined to realize year-round refrigeration, the operation range of the refrigerating unit can be greatly widened, the reliability of the combined operation of the magnetic suspension centrifugal machine system and the fluorine pump is improved, the magnetic suspension compressor can keep stable operation at a lower condensation temperature, the reliability of the system is improved, and the energy consumption of the system is reduced.

Description

Refrigerating unit

Technical Field

The utility model relates to a refrigeration technology field especially relates to a can satisfy refrigerating unit of year round refrigeration needs.

Background

With the continuous development of communication technology, industry and the like, occasions needing year-round refrigeration are more and more, such as data centers, machine rooms, factories, large public buildings and the like.

Taking a data center as an example, a traditional annual refrigerating unit, a small unit generally adopts a scroll compressor, a medium-large unit generally adopts a screw compressor or a centrifugal compressor, and because of the characteristics of the compressor, the limitation that the compressor cannot refrigerate under the condition of low ambient temperature exists, the refrigerating requirement cannot be met on occasions needing annual refrigeration such as the data center, and the like, and under the condition that the unit cannot be operated in winter, the mode that a cooling tower directly supplies cold is generally adopted, so that the system is relatively complex, the reliability is poor and the energy consumption of the system is high.

Disclosure of Invention

The utility model provides a refrigerating unit can solve among the prior art problem that the annual refrigerating unit system structure is complicated, the reliability is poor, and the energy consumption is high.

In some embodiments of the present application, there is provided a refrigeration unit comprising:

the system comprises a magnetic suspension compressor, a fluorine pump, an evaporative condenser, an evaporator and a gas-liquid separator;

the exhaust port of the magnetic suspension compressor is connected with the inlet of the evaporative condenser;

the outlet of the evaporation condenser is connected with the inlet of the evaporator, a throttling device is connected between the outlet of the evaporation condenser and the inlet of the evaporator, the outlet of the evaporator is connected with the inlet of the gas-liquid separator, and the gas outlet of the gas-liquid separator is connected with the air suction port of the magnetic suspension compressor;

the outlet of the evaporative condenser is further connected with the inlet of the fluorine pump, a throttling device is connected between the inlet of the fluorine pump and the outlet of the fluorine pump, the outlet of the fluorine pump is connected with the inlet of the evaporator, and the liquid outlet of the gas-liquid separator is connected with the inlet of the evaporative condenser.

The refrigeration of the magnetic suspension compressor and the refrigeration of the fluorine pump are combined to realize the year-round refrigeration, so that the operation range of the refrigerating unit can be greatly expanded, and the reliability of the combined operation of the magnetic suspension centrifugal machine system and the fluorine pump is improved; the gas-liquid separator is arranged in the system, and when the running of the fluorine pump system is switched to the running of the compressor system, the risk of damage to the compressor caused by air suction and liquid carrying is avoided; the fluorine pump is arranged at the outlet of the evaporative condenser for the operation of the refrigerating system, so that liquid refrigerant can be ensured to enter the fluorine pump, the operation reliability of the fluorine pump is improved, and the operation reliability of a unit is further improved; the magnetic suspension compressor can keep stable operation at a lower condensation temperature, thereby improving the reliability of the system and reducing the energy consumption of the system.

In some embodiments of the present application, the refrigeration unit further includes a plate heat exchanger, an outlet of the evaporative condenser is connected to an inlet of a first channel of the plate heat exchanger through a first pipeline, and an outlet of the first channel is connected to an inlet of the evaporator; the first pipeline is connected with a branch, an expansion valve is arranged on the branch, one end of the branch is connected to the first pipeline, the other end of the branch is connected with an inlet of a second channel of the plate heat exchanger, and an outlet of the second channel is connected with an air supplementing port of the magnetic suspension compressor; and the outlet of the evaporative condenser is connected with the inlet of the fluorine pump through a second pipeline.

In some embodiments of the present application, the outlet of the first passage and the outlet of the fluorine pump are connected to the same pipe and connected to the inlet of the evaporator through the pipe, the throttling device is provided on the pipe, and the number of the throttling devices is one or two throttling devices are provided in parallel.

In some embodiments of the present application, a first check valve is disposed on the first pipeline, the first check valve is located downstream of a connection point of the branch and the first pipeline, and a second check valve is disposed on a connection pipeline between an outlet of the fluorine pump and an inlet of the evaporator.

In some embodiments of the present application, a third check valve is disposed on a connection pipeline between the exhaust port of the magnetic levitation compressor and the inlet of the evaporative condenser, and a fourth check valve is disposed on a connection pipeline between the liquid outlet of the gas-liquid separator and the inlet of the evaporative condenser.

In some embodiments of the present application, the outlet of the evaporative condenser is further connected with a compressor cooling pipeline, for leading a part of liquid refrigerant of the evaporative condenser to the inside of the magnetic suspension compressor, and cooling the magnetic suspension compressor, one end of the compressor cooling pipeline is connected with the outlet of the evaporative condenser, and the other end of the compressor cooling pipeline is connected with the cooling inlet of the magnetic suspension compressor.

In some embodiments of the present application, the compressor cooling line includes a differential pressure cooling line and a forced cooling line, the forced cooling line is connected in parallel with the differential pressure cooling line, and a refrigerant pump is disposed on the forced cooling line.

In some embodiments of the present application, the compressor cooling pipeline further includes a pressure regulating pipeline, the pressure regulating pipeline is connected in parallel with the differential pressure cooling pipeline and the forced cooling pipeline, and the pressure regulating pipeline is provided with a pressure regulating valve.

In some embodiments of the present application, a sixth check valve is disposed on the differential pressure cooling pipeline, a seventh check valve is disposed on the forced cooling pipeline, and a filter is connected between the compressor cooling pipeline and the cooling inlet of the magnetic suspension compressor.

In some embodiments of this application, vapour and liquid separator's liquid outlet with be connected with the load balance pipeline on the connecting line between evaporative condenser's the import, the one end of load balance pipeline is connected vapour and liquid separator's liquid outlet with on the connecting line between evaporative condenser's the import, the other end is connected the evaporimeter, be equipped with the load balance valve on the load balance pipeline.

Drawings

FIG. 1 illustrates a refrigeration chiller system schematic according to a first embodiment;

fig. 2 illustrates a refrigerant flow diagram of a refrigeration unit operating in summer and transitional seasons according to a first embodiment;

fig. 3 illustrates a refrigerant flow diagram of a refrigeration unit according to a first embodiment when operating in winter;

FIG. 4 shows a schematic diagram of a refrigeration chiller system according to a second embodiment;

fig. 5 shows a refrigerant flow diagram of the refrigeration unit according to the second embodiment when operating in summer and in a transitional season;

fig. 6 illustrates a refrigerant flow diagram when the refrigerator set according to the second embodiment is operated in winter;

FIG. 7 shows a refrigeration chiller system schematic according to a third embodiment;

FIG. 8 is an enlarged view of the portion A of FIG. 7;

fig. 9 illustrates a refrigerant flow diagram when the refrigeration unit operates in summer and in a transitional season according to the third embodiment;

fig. 10 shows a refrigerant flow pattern when the refrigerator set according to the third embodiment is operated in winter.

Reference numerals are as follows: 10-a magnetic suspension compressor, 11-an exhaust port, 12-an air suction port, 13-a cooling inlet, 14-an air supplement port, 20-a fluorine pump, 30-an evaporative condenser, 40-an evaporator, 50-a gas-liquid separator, 51-a gas outlet, 52-a liquid outlet, 60-a throttling device, 70-a plate heat exchanger, 80-a first pipeline, 90-a second pipeline, 100-a branch, 110-an expansion valve, 120-a pipeline, 130-a first check valve, 140-a second check valve, 150-a third check valve, 160-a fourth check valve, 170-a differential pressure cooling pipeline, 180-a forced cooling pipeline, 190-a refrigerant pump, 200-a pressure regulating pipeline, 210-a pressure regulating valve, 220-a sixth check valve, 230-a seventh check valve, 240-a filter, 250-a load balancing pipeline and 260-a load balancing valve.

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts all belong to the protection scope of the present invention.

In the description of the present invention, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are merely for convenience of description and for simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, are not to be construed as limiting the present invention.

The terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.

In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood as a specific case by those skilled in the art.

In the present disclosure, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may comprise direct contact between the first and second features, or may comprise contact between the first and second features not directly. Also, the first feature "on," "above" and "over" the second feature may include the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.

The following disclosure provides many different embodiments or examples for implementing different features of the invention. In order to simplify the disclosure of the present invention, the components and arrangements of specific examples are described below. Of course, they are merely examples and are not intended to limit the present invention. Furthermore, the present disclosure may repeat reference numerals and/or reference letters in the various examples for purposes of simplicity and clarity and do not in itself dictate a relationship between the various embodiments and/or arrangements discussed. In addition, the present disclosure provides examples of various specific processes and materials, but one of ordinary skill in the art may recognize applications of other processes and/or use of other materials.

The utility model discloses well air conditioner carries out the refrigeration cycle of air conditioner through using compressor, condenser, expansion valve and evaporimeter. The refrigeration cycle includes a series of processes involving compression, condensation, expansion, and evaporation to cool or heat an indoor space.

The low-temperature and low-pressure refrigerant enters the compressor, the compressor compresses the refrigerant gas in a high-temperature and high-pressure state, and the compressed refrigerant gas is discharged. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and the heat is released to the ambient environment through the condensation process.

The expansion valve expands the liquid-phase refrigerant in a high-temperature and high-pressure state condensed in the condenser into a low-pressure gas-liquid two-phase refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator can achieve a cooling effect by heat-exchanging with a material to be cooled using latent heat of evaporation of a refrigerant. In the water chilling unit, water flowing through an evaporator exchanges heat with a refrigerant, and cooled water is sent into an indoor tail end (a fan coil or a combined air conditioner) through a water pump arranged in the system, so that the indoor space or equipment is cooled.

In commercial air conditioning systems, it is common to include: the main machine comprises a compressor, a condenser, a throttle valve, an evaporator and other accessories, the tail end comprises a fan, a surface cooler and other functional modules, and the transmission and distribution system comprises a water pump, a water path valve and other accessories.

The main machine realizes the preparation of cold water in the evaporator through reverse Carnot circulation, the water pump conveys the cold water to the tail end, and the tail end cools the indoor space and the equipment; meanwhile, heat is discharged from the condenser and exchanges heat with the outside through air (an air-cooled unit) or water (a water-cooled unit) or an air-water system (an evaporation-cooled unit).

Example one

Fig. 1 shows a schematic diagram of a refrigeration unit system according to a first embodiment. As shown in fig. 1, a refrigerating unit, in particular a refrigerating unit capable of refrigerating year round, comprises a magnetic suspension compressor 10, a fluorine pump 20, an evaporative condenser 30, an evaporator 40 and a gas-liquid separator 50.

The exhaust port 11 of the magnetic suspension compressor 10 is connected with the inlet of the evaporative condenser 30, the outlet of the evaporative condenser 30 is connected with the inlet of the evaporator 40, a throttling device 60 is connected between the outlet of the evaporative condenser 30 and the inlet of the evaporator 40, the outlet of the evaporator 40 is connected with the inlet of the gas-liquid separator 50, and the gas outlet 51 of the gas-liquid separator 50 is connected with the air suction port 12 of the magnetic suspension compressor 10.

The outlet of the evaporative condenser 30 is also connected with the inlet of the fluorine pump 20, a throttling device 60 is also connected between the outlet of the evaporative condenser 30 and the inlet of the fluorine pump 20, the outlet of the fluorine pump 20 is connected with the inlet of the evaporator 40, and the liquid outlet 52 of the gas-liquid separator 50 is connected with the inlet of the evaporative condenser 30.

The magnetic suspension compressor 10 is a magnetic suspension centrifugal compressor, a rotor is suspended in the air by utilizing the magnetic force, so that the rotor is not in mechanical contact with a stator, the rotor drives an impeller to rotate at a high speed, refrigerant gas entering a suction end is driven by the impeller to obtain sufficient speed, and then the speed energy is converted into pressure energy through a diffuser and is discharged out of the compressor.

The evaporator 40 is a shell-and-tube evaporator 40, and may be any of a flooded type, a dry type, and a falling film type, and has a wider application range.

The condenser is an evaporative condenser, and compared with the existing air-cooled condenser, the evaporative condenser 30 has lower condensing temperature (the condensing temperature is lower by more than 5 ℃), and can realize the effect of saving more energy than the air-cooled condenser.

Fig. 2 illustrates a refrigerant flow diagram for a refrigeration unit operating in summer and transitional seasons according to an embodiment one. As shown in fig. 2, when the refrigeration unit of this embodiment operates in summer and in transitional seasons, the magnetic levitation compressor 10 is started to perform mechanical refrigeration, the high-temperature and high-pressure refrigerant gas is discharged from the exhaust port 11 of the magnetic levitation compressor 10, enters the evaporative condenser 30 through the inlet of the evaporative condenser 30 to be condensed into liquid, is throttled and depressurized by the throttling device 60, enters the evaporator 40 to be evaporated into saturated gas, then enters the magnetic levitation compressor 10 through the air suction port 12 of the magnetic levitation compressor 10 after gas-liquid separation by the gas-liquid separator 50, and is then discharged through the exhaust port 11 of the magnetic levitation compressor 10, and the cycle is repeated to achieve refrigeration.

Because the magnetic suspension compressor 10 is an oil-free system, the magnetic suspension compressor can still keep running at a lower condensation temperature, and the problems of complex control logic, poor stability and the like of a unit under the condition that the temperature of a traditional compressor is different in a transition season or in the daytime or at night are solved. For example, when the temperature is high in the prior art, the evaporative condenser 30 supplements water and the fan runs at a high speed; when the temperature is low, the evaporative condenser 30 discharges water, the fan operates at a low speed, and the switching is frequently performed. The lowest operating condensation temperature of the conventional compressor is greatly limited (the condensation temperature is generally above 25 ℃ when the evaporation temperature is 5 ℃), and when the ambient temperature is below 18 ℃, the conventional compressor is difficult to start for refrigeration. And when the evaporation temperature is 5 ℃, the lowest operation condensation temperature of the magnetic suspension centrifugal compressor is more than 10 ℃, namely, when the environment temperature is 5 ℃, the magnetic suspension centrifugal compressor can be started to operate. Therefore, the operation range of the unit is greatly widened.

Meanwhile, the gas-liquid separator 50 is arranged between the evaporator 40 and the magnetic suspension compressor 10, so that gas refrigerant is sucked into the air suction port 12 of the magnetic suspension compressor 10, liquid impact on the magnetic suspension compressor 10 is prevented, and the reliability and the service life of the compressor are improved.

Fig. 3 illustrates a refrigerant flow diagram of a refrigeration unit according to a first embodiment when operating in winter. As shown in fig. 3, when the refrigeration unit of this embodiment operates in winter, the magnetic suspension compressor 10 is stopped, the fluorine pump 20 is started, the refrigerant is driven by the fluorine pump 20 to enter the evaporation condenser 30 for condensation, and then is throttled by the throttling device 60 for depressurization, enters the evaporator 40, is evaporated in the evaporator 40, is separated by the gas-liquid separator, and under the drive of the fluorine pump 20, the liquid refrigerant separated by the gas-liquid separator 50 enters the evaporation condenser 30 again through the liquid outlet 52 of the gas-liquid separator 50, and thus circulates. The refrigerant passing through the evaporative condenser 30 becomes a liquid refrigerant, preventing the fluorine pump 20 from cavitation. Because the power of the fluorine pump 20 is far less than that of the magnetic levitation compressor 10, the energy consumption of the system is greatly reduced.

In this embodiment, the magnetic suspension compressor 10 and the fluorine pump 20 are used for refrigerating, so that the compound year-round refrigeration is realized, the operation range of the refrigerating unit can be greatly expanded, the reliability of the compound operation of the magnetic suspension centrifuge system and the fluorine pump 20 is increased, and the frequent switching is avoided; the gas-liquid separator 50 is arranged in the system, so that when the fluorine pump 20 system is switched to the compressor system, the risk of damage to the compressor caused by air suction and liquid carrying is avoided; the evaporator 40 can be a shell-and-tube evaporator, which can meet the requirement of cooling a larger refrigeration system, and the requirement of the cleanliness of the system is greatly reduced compared with the requirement of a plate; the fluorine pump 20 is arranged at the outlet of the evaporative condenser 30 for the operation of the refrigeration system, so that liquid refrigerant can be ensured to enter the fluorine pump 20, and the operation reliability of the fluorine pump 20 is improved.

Example two

Fig. 4 shows a refrigerating unit system schematic according to a second embodiment. Different from the first embodiment, the refrigeration unit in this embodiment further includes a plate heat exchanger 70, a first channel and a second channel are provided in the plate heat exchanger 70, the outlet of the evaporative condenser 30 is not directly connected to the inlet of the evaporator 40, but is connected to the inlet of the first channel of the plate heat exchanger 70 through a first pipeline 80, and then is connected to the inlet of the evaporator 40 through the outlet of the first channel; meanwhile, the first pipeline 80 is connected with a branch 100, the branch 100 is provided with an expansion valve 110, one end of the branch 100 is connected to the first pipeline 80, the other end of the branch 100 is connected with an inlet of a second channel of the plate heat exchanger 70, and an outlet of the second channel is connected with the air supplement port 14 of the magnetic suspension compressor 10. The outlet of the evaporative condenser 30 is connected to the inlet of the fluorine pump 20 via a second line 90.

Fig. 5 shows a refrigerant flow diagram of the refrigeration unit according to the second embodiment when operating in summer and in a transitional season. As shown in fig. 5, during refrigeration in summer and in transitional seasons, in this embodiment, the plate heat exchanger 70 serves as an economizer, the high-pressure liquid refrigerant from the evaporative condenser 30 first enters the plate heat exchanger 70, and then enters the plate heat exchanger 70 and is divided into two parts, one part enters the branch 100, the high-pressure liquid refrigerant is throttled by the expansion valve 110 on the branch to further cool down and enter the first channel of the plate heat exchanger 70, the other part enters the second channel of the plate heat exchanger 70, the temperature of the liquid refrigerant in the first channel is lower than that of the liquid refrigerant in the second channel, so that heat of the liquid refrigerant in the second channel is absorbed through heat exchange, the liquid refrigerant in the second channel is further cooled, that is, the temperature before throttling of the liquid refrigerant is further reduced, the liquid refrigerant is throttled by the throttling device 60 and then enters the evaporator 40 to be evaporated, and the liquid refrigerant in the first channel enters the magnetic levitation compressor 10 again to be compressed again after heat exchange, and then enters a cycle. By arranging the plate heat exchanger 70 as an economizer, the capacity and efficiency of the unit can be improved, and the power consumption of the magnetic levitation compressor 10 can be reduced.

Fig. 6 shows a refrigerant flow pattern when the refrigerator set according to the second embodiment is operated in winter. As shown in fig. 6, when the refrigeration unit of this embodiment operates in winter, the magnetic levitation compressor 10 is stopped, the fluorine pump 20 is turned on, the refrigerant is driven by the fluorine pump 20 to enter the evaporation condenser 30 from the liquid outlet 52 of the gas-liquid separator 50 for condensation, and then is throttled by the throttle device 60 for pressure reduction, enters the evaporator 40 for evaporation in the evaporator 40, and is separated by the gas-liquid separator 50, and the liquid refrigerant separated by the gas-liquid separator 50 enters the evaporation condenser 30 again through the liquid outlet 52 of the gas-liquid separator 50 under the driving of the fluorine pump 20, and the process is circulated.

In this embodiment, the outlet of the first passage and the outlet of the fluorine pump 20 are connected to the same pipe 120, and are connected to the inlet of the evaporator 40 via the pipe 120, the throttling device 60 is provided on the pipe 120, and the number of the throttling devices 60 is one, or two throttling devices are provided in parallel. When two throttling devices 60 are arranged in parallel, when the magnetic suspension compressor operates in summer and transition seasons, one throttling device 60 can be opened because the pressure difference between the pressure of the exhaust port 11 and the pressure of the air suction port 12 of the magnetic suspension compressor 10 is large and a large flow area is not needed; when the magnetic suspension compressor operates in winter, the pressure difference between the pressure of the exhaust port 11 and the pressure of the air suction port 12 of the magnetic suspension compressor 10 is small, a larger flow area is needed, and the two throttling devices 60 can be opened to improve the throttling and pressure reducing capacity and further improve the energy efficiency of the refrigerating unit in winter. In particular, the throttling means is an expansion valve.

In this embodiment, a first check valve 130 is disposed on the first pipeline 80, the first check valve 130 is located downstream of the connection point of the branch 100 and the first pipeline 80, and a second check valve 140 is disposed on the second pipeline 90, which is the connection line between the outlet of the fluorine pump 20 and the inlet of the evaporator 40, so as to ensure the unidirectional flow of the refrigerant.

Similarly, a third check valve 150 is arranged on a connecting pipeline between the exhaust port 11 of the magnetic suspension compressor 10 and the inlet of the evaporative condenser 30, and a fourth check valve 160 is arranged on a connecting pipeline between the liquid outlet 52 of the gas-liquid separator 50 and the inlet of the evaporative condenser 30.

EXAMPLE III

Fig. 7 shows a schematic diagram of a refrigerating unit system according to a third embodiment, and fig. 8 is an enlarged view of a portion a of fig. 7. As shown in fig. 7, unlike the second embodiment, the outlet of the evaporative condenser 30 in this embodiment is further connected with a compressor cooling line for guiding a part of the liquid refrigerant of the evaporative condenser 30 into the magnetically levitated compressor 10 to cool the magnetically levitated compressor 10. One end of the compressor cooling pipeline is connected with the outlet of the evaporative condenser, and the other end of the compressor cooling pipeline is connected with the cooling inlet 13 of the magnetic suspension compressor 10. Therefore, the magnetic suspension compressor 10 can be effectively cooled when needed, and the magnetic suspension compressor 10 is prevented from being frequently stopped.

Fig. 9 shows a refrigerant flow diagram when the refrigeration unit according to the third embodiment is operated in summer and the transitional season. As shown in fig. 9, when the refrigeration unit of this embodiment performs refrigeration in summer and in transitional seasons, the magnetic levitation compressor 10 is started to perform mechanical refrigeration, the gas of the high-temperature and high-pressure refrigerant is discharged from the exhaust port 11 of the magnetic levitation compressor 10, enters the evaporation condenser 30 through the inlet of the evaporation condenser 30, and is condensed into liquid, the high-pressure liquid refrigerant from the evaporation condenser 30 first enters the plate heat exchanger 70, enters the plate heat exchanger 70 and is divided into two parts, one part enters the branch 100, is throttled by the expansion valve 110 on the branch 100 to further lower the temperature of the high-pressure liquid refrigerant entering the first channel of the plate heat exchanger 70, the other part enters the second channel of the plate heat exchanger 70, the temperature of the liquid refrigerant in the first channel is lower than that of the liquid refrigerant in the second channel, so that the heat of the liquid refrigerant in the second channel is absorbed through heat exchange, the liquid refrigerant in the second channel is further cooled, that the temperature before throttling of the liquid refrigerant is further reduced, and is throttled by the throttling device 60 to enter the evaporator 40 for evaporation, and the liquid refrigerant in the first channel enters the magnetic levitation compressor 10 again for heat exchange and continues to enter the circulation.

When the magnetic levitation compressor 10 needs to be cooled, a part of refrigerant liquid from the evaporative condenser 30 flows back into the compressor through the compressor cooling pipeline to cool the inside of the compressor.

Specifically, the compressor cooling line includes a differential pressure cooling line 170 and a forced cooling line 180, the forced cooling line 180 is connected in parallel with the differential pressure cooling line 170, and a refrigerant pump 190 is disposed on the forced cooling line 180.

In general, a part of the refrigerant liquid from the evaporative condenser 30 is driven by the refrigerant pressure difference and flows back to the compressor through the pressure difference cooling line 170 to cool the inside of the compressor. If the pressure ratio (the ratio of the gas pressure of the exhaust port 11 of the compressor to the gas pressure of the suction port 12 of the compressor) is lower than the preset value (namely, when the outdoor environment temperature is lower), enough refrigerant is difficult to drive to flow back to the compressor only through the refrigerant pressure difference, at the moment, a part of liquid refrigerant at the outlet of the evaporative condenser 30 is forcibly introduced into the compressor through the refrigerant pump 190, namely flows back to the interior of the compressor through the forced cooling pipeline 180 to cool the interior of the compressor, the cooling requirements of the compressor under different working conditions are met, the temperature is effectively reduced, and the magnetic suspension compressor 10 is prevented from being frequently stopped.

As shown in fig. 9, the cooling circuit of the compressor further includes a pressure regulating circuit 200, the pressure regulating circuit 200 is connected in parallel with the differential pressure cooling circuit 170 and the forced cooling circuit 180, and a pressure regulating valve 210 is disposed on the pressure regulating circuit 200.

When cooling is not needed inside the magnetic levitation compressor 10, the internal cooling valve of the compressor is closed and liquid refrigerant does not need to be forcibly pumped into the cooling inlet 13 of the compressor, in order to avoid directly closing the refrigerant pump 190, the pressure regulating valve 210 is opened at this time, so that refrigerant at the outlet of the refrigerant pump 190 can flow back to the suction port of the refrigerant pump 190, and when cooling is needed again on the magnetic levitation compressor 10, the pressure regulating valve 210 is closed, so that the refrigerant pump 190 can forcibly introduce a part of refrigerant into the compressor again. By arranging the pressure regulating pipeline 200 and the pressure regulating valve 210, the refrigerant pump 190 can be prevented from being started and stopped frequently, and the situations that the refrigerant pump 190 is damaged by frequent starting and stopping and the compressor is not cooled in time are avoided.

As also shown in fig. 9, a sixth check valve 220 is disposed on the differential pressure cooling pipeline 170, and a seventh check valve 230 is disposed on the forced cooling pipeline 180, so as to ensure that the unidirectional flow of the refrigerant is realized; a filter 240 is connected between the cooling line of the compressor and the cooling inlet 13 of the magnetic levitation compressor 10 to filter the liquid refrigerant for cooling, and prevent impurities therein from entering the magnetic levitation compressor 10 to damage the compressor.

Fig. 10 shows a refrigerant flow pattern when the refrigerator set according to the third embodiment is operated in winter. As shown in fig. 10, when the refrigeration unit of this embodiment operates in winter, the magnetic suspension compressor 10 is stopped, the fluorine pump 20 is turned on, the refrigerant is driven by the fluorine pump 20 to enter the evaporation condenser 30 from the liquid outlet 52 of the gas-liquid separator 50 for condensation, and then is throttled by the throttling device 60 for depressurization, and enters the evaporator 40 to be evaporated in the evaporator 40, and then is separated by the gas-liquid separator 50, and the liquid refrigerant separated by the gas-liquid separator 50 enters the evaporation condenser 30 again through the liquid outlet 52 of the gas-liquid separator 50 under the driving of the fluorine pump 20, and the process is repeated.

In this embodiment, a load balancing pipeline 250 is connected to a connection pipeline between the liquid outlet 52 of the gas-liquid separator 50 and the inlet of the evaporative condenser 30, one end of the load balancing pipeline 250 is connected to a connection pipeline between the liquid outlet 52 of the gas-liquid separator 50 and the inlet of the evaporative condenser 30, the other end is connected to the evaporator 40, and a load balancing valve 260 is disposed on the load balancing pipeline 250.

Through setting up load balance pipeline 250 and load balance valve 260, in case the magnetic suspension compressor 10 can't fall down the circumstances, open load balance valve 260, make the high-pressure side and the low pressure side intercommunication of magnetic suspension compressor 10, reduce the refrigerating output, prevent frequently to open and stop the compressor, improve compressor life-span and reliability.

In fig. 1 to 10, a right horizontal arrow on the right side of the evaporator 40 indicates a cold water outlet direction, a left horizontal arrow indicates a cold water return direction, a left horizontal arrow on the right lower side of the evaporative condenser 30 indicates a water inlet direction, and the remaining straight arrows indicate a refrigerant flow direction.

In the foregoing description of embodiments, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.

The above is only a specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention should be covered within the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims (10)

1. A refrigeration unit, comprising:

the system comprises a magnetic suspension compressor, a fluorine pump, an evaporative condenser, an evaporator and a gas-liquid separator;

the exhaust port of the magnetic suspension compressor is connected with the inlet of the evaporative condenser;

the outlet of the evaporative condenser is connected with the inlet of the evaporator, a throttling device is connected between the outlet of the evaporative condenser and the inlet of the evaporator, the outlet of the evaporator is connected with the inlet of the gas-liquid separator, and the gas outlet of the gas-liquid separator is connected with the air suction port of the magnetic suspension compressor;

the outlet of the evaporative condenser is further connected with the inlet of the fluorine pump, a throttling device is connected between the inlet of the fluorine pump and the outlet of the fluorine pump, the outlet of the fluorine pump is connected with the inlet of the evaporator, and the liquid outlet of the gas-liquid separator is connected with the inlet of the evaporative condenser.

2. The refrigeration unit as set forth in claim 1 further comprising:

an outlet of the evaporative condenser is connected with an inlet of a first channel of the plate heat exchanger through a first pipeline, and an outlet of the first channel is connected with an inlet of the evaporator; the first pipeline is connected with a branch, an expansion valve is arranged on the branch, one end of the branch is connected to the first pipeline, the other end of the branch is connected with an inlet of a second channel of the plate heat exchanger, and an outlet of the second channel is connected with an air supplementing port of the magnetic suspension compressor; and the outlet of the evaporative condenser is connected with the inlet of the fluorine pump through a second pipeline.

3. The refrigeration unit as set forth in claim 2,

the outlet of the first channel and the outlet of the fluorine pump are connected to the same pipeline, and are connected to the inlet of the evaporator through the pipeline, the throttling device is arranged on the pipeline, and the number of the throttling devices is one or two throttling devices are arranged in parallel.

4. The refrigeration unit as set forth in claim 2,

the first pipeline is provided with a first one-way valve, the first one-way valve is positioned at the downstream of the connection point of the branch and the first pipeline, and a second one-way valve is arranged on a connection pipeline between the outlet of the fluorine pump and the inlet of the evaporator.

5. The refrigeration unit as set forth in claim 1,

and a third one-way valve is arranged on a connecting pipeline between an exhaust port of the magnetic suspension compressor and an inlet of the evaporative condenser, and a fourth one-way valve is arranged on a connecting pipeline between a liquid outlet of the gas-liquid separator and an inlet of the evaporative condenser.

6. The refrigeration unit as set forth in claim 1,

the outlet of the evaporative condenser is also connected with a compressor cooling pipeline for guiding a part of liquid refrigerant of the evaporative condenser to the magnetic suspension compressor to cool the magnetic suspension compressor, one end of the compressor cooling pipeline is connected with the outlet of the evaporative condenser, and the other end of the compressor cooling pipeline is connected with the cooling inlet of the magnetic suspension compressor.

7. The refrigeration unit as set forth in claim 6,

the compressor cooling pipeline comprises a differential pressure cooling pipeline and a forced cooling pipeline, the forced cooling pipeline is connected with the differential pressure cooling pipeline in parallel, and a refrigerant pump is arranged on the forced cooling pipeline.

8. The refrigeration unit as set forth in claim 7,

the compressor cooling pipeline further comprises a pressure regulating pipeline, the pressure regulating pipeline is connected with the differential pressure cooling pipeline and the forced cooling pipeline in parallel, and a pressure regulating valve is arranged on the pressure regulating pipeline.

9. The refrigeration unit as set forth in claim 7,

and a sixth one-way valve is arranged on the differential pressure cooling pipeline, a seventh one-way valve is arranged on the forced cooling pipeline, and a filter is connected between the compressor cooling pipeline and the cooling inlet of the magnetic suspension compressor.

10. The refrigeration unit as set forth in claim 1,

the evaporator is characterized in that a load balancing pipeline is connected to a connecting pipeline between a liquid outlet of the gas-liquid separator and an inlet of the evaporative condenser, one end of the load balancing pipeline is connected to the connecting pipeline between the liquid outlet of the gas-liquid separator and the inlet of the evaporative condenser, the other end of the load balancing pipeline is connected with the evaporator, and a load balancing valve is arranged on the load balancing pipeline.

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