CN207729861U - A kind of transcritical CO_2 Two-stage Compression supercharging refrigeration system - Google Patents

Abstract

The utility model discloses a kind of Trans-critical cycle CO₂Two-stage Compression is pressurized refrigeration system.It is provided with oil return line between the utility model low pressure compressor and high pressure compressor, the low pressure compressor to pipeline between high pressure compressor is provided with check valve and pressure transmitter, the Intermediate Heat Exchanger is disposed with expansion valve, pressure transmitter and check valve to check valve, the bypass line of the expansion drum to high pressure compressor is provided between high pressure compressor suction duct road.The utility model is reduced the delivery temperature of compressed gas while being reduced restriction loss using Two-stage Compression and expansion drum, while also improving the refrigerating capacity of system to the refrigerant supercooling for entering evaporator using Intermediate Heat Exchanger, improves system performance.

Description

A transcritical CO2 two-stage compression booster refrigeration system

technical field

The utility model relates to the technical field of environmental protection refrigeration, in particular to a transcritical _CO2 two-stage compression and pressurization refrigeration system.

Background technique

With the rapid development of my country's economic level and the gradual increase of people's requirements for living standards, the output and demand of perishable foods (fruits, vegetables, dairy products, etc.) are gradually increasing, and consumers pay more attention to food quality and safety. Also getting higher and higher. This has also led to a huge demand for devices and products such as cold storage and supermarket freezers in the market.

Today's refrigeration system is facing the dual pressure of environmental protection and energy saving and emission reduction. The development and utilization of environmentally friendly refrigerants and energy-saving optimization of refrigeration systems have become a new trend in the development of the refrigeration industry.

At present, most of the refrigeration equipment produced and used in the market, such as cold storages, freezers, and refrigerated trucks, use Freon refrigerants with high global warming potential (GWP), such as R404A, R507C, and R22. In the process of system refrigerant charging and maintenance, refrigerant leakage will inevitably occur, which intensifies the greenhouse effect. In this situation, the natural working substance CO ₂ has been paid attention to again because of its good thermophysical properties. Compared with HCFCs and HFCs refrigerants, _CO2 has obvious advantages: 1) Environmentally friendly refrigerant: GWP is 1, ODP is 0; 2) It has good safety and chemical stability: non-toxic, non-flammable, adaptable Various lubricating oils; 3) Good thermal properties: large cooling capacity per unit volume, low kinematic viscosity; 4) Excellent flow and heat transfer characteristics, which can effectively reduce the size of compressors, heat exchangers and systems. However, due to the low critical temperature (31.1°C) and high critical pressure (7.38MPa) of _CO2 , the operating pressure of the system is high and the throttling loss is large, resulting in the operating efficiency of the _CO2 system being lower than that of the conventional fluorine system, which is also The promotion and development of _CO2 systems are limited.

Therefore, improving the performance and efficiency of _CO2 refrigeration systems has become the main direction of _CO2 system research.

Utility model content

The technical problem to be solved by the utility model is to provide a transcritical CO ₂ two-stage compression pressurized refrigeration system, which can reduce the exhaust gas temperature to a certain extent through the incomplete cooling in the middle of the two-stage compression, and will pass through the gas cooler The refrigerant gas is throttled for gas-liquid separation in the expansion tank, which reduces the gas content of the refrigerant entering the intermediate heat exchanger and evaporator after throttling, reduces the throttling loss, and uses the intermediate heat exchanger to The _CO2 refrigerant in the evaporator is subcooled, which increases the cooling capacity of the system and improves the system performance.

The technical scheme adopted for realizing the purpose of this utility model is:

A transcritical _CO2 two-stage compression booster refrigeration system, low-pressure stage compressor, high-pressure stage compressor, oil separator, gas cooler, expansion tank, dry filter, intermediate heat exchanger, evaporator, gas-liquid separation The devices are connected sequentially through pipelines, an oil return pipeline is arranged between the low pressure compressor and the high pressure compressor, and a check valve one and a pressure transmitter one are arranged in the pipeline between the low pressure compressor and the high pressure compressor, so that The bypass pipeline from the expansion tank to the inlet of the high-pressure compressor is provided with expansion valve 4, pressure transmitter 3 and check valve 3 in sequence, and an expansion valve is provided between the outlet of the gas cooler and the inlet pipeline of the expansion tank Sanhe pressure transmitter 2, the liquid outlet of the expansion tank is connected to the dry filter through the pipeline of the flow meter 2, and the dry filter is connected to two branches respectively, and one branch passes through the solenoid valve 2, the expansion valve 2, and the intermediate heat exchange device, pressure transmitter 4, check valve 2, then connect the pipeline between the outlet of the low-pressure stage compressor and pressure transmitter 1, and the other branch passes through the intermediate heat exchanger, flow meter 1, solenoid valve 1, expansion valve Valve 1, the evaporator, and the gas-liquid separator are connected to the inlet of the low-pressure stage compressor.

_CO2 is the refrigerant for this refrigeration system. The high-temperature and high-pressure _CO2 gas coming out of the gas cooler enters the expansion tank after throttling and reducing pressure through the expansion valve. After throttling, the gas-liquid two-phase refrigerant is separated from gas and liquid in the expansion tank, and the gas in the tank is expanded by the bypass branch. After the valve is depressurized, it is merged into the suction line of the high-pressure compressor. The _CO2 liquid in the tank is dried by a dry filter and then divided into two paths. After subcooling, it is merged into the suction pipeline of the high-pressure stage compressor, and the other refrigerant liquid enters the evaporator through the expansion valve after being subcooled in the intermediate heat exchanger. After absorbing heat in the evaporator, it passes through the gas After the liquid separator is compressed to medium pressure by the low-pressure compressor, it is mixed with the gas in the two branches in the suction line of the high-pressure compressor and then sucked into the high-pressure stage compressor. The high-temperature and high-pressure gas from the high-pressure compressor is separated by oil After entering the gas cooler to cool down, the refrigeration cycle is completed.

Compared with the prior art, the utility model has the advantages and positive effects as follows:

(1) Use CO ₂ as the system refrigerant. Since _CO2 has a GWP of 1 and an ODP of 0, it is an environmentally friendly refrigerant with excellent thermophysical properties. Compared with conventional refrigeration systems, the direct carbon emission is basically 0.

(2) The mode of incomplete cooling in the middle of two-stage compression is used. The exhaust gas from the low-pressure compressor is mixed with the steam from the intermediate heat exchanger and the expansion tank steam throttled by the steam bypass valve to cool down, and then the exhaust gas is compressed by the high-pressure compressor. Compared with the CO ₂ single-stage compression system, In the case of reaching the same exhaust pressure, the exhaust temperature should be lower.

(3) An expansion tank is used in the system. Since the system is equipped with an expansion tank after the air cooler, the throttling pressure difference is reduced, which reduces the throttling loss of the system, and the expansion tank is used for gas-liquid separation, so that the refrigerant at the outlet of the expansion tank is a saturated liquid, greatly reducing The gas content after throttling by the expansion valve is reduced, and the performance coefficient of the system is improved.

(4) Use the intermediate heat exchanger to subcool the refrigerant before entering the evaporator. The use of the intermediate heat exchanger increases the cooling capacity of the system and improves the system performance.

Description of drawings

Fig. 1 is a schematic diagram of the transcritical _CO2 two-stage compression booster refrigeration system described in the utility model.

In the figure: 1. Low-pressure compressor; 1-1. Oil return pipeline; 2. Check valve 1; 3. High-pressure compressor; 4. Oil separator; 5. Gas cooler; 6. Expansion valve 3; 7. Expansion tank; 8. Flow meter two; 9. Dry filter; 10. Solenoid valve two; 11. Expansion valve two; 12. Intermediate heat exchanger; 13. One-way valve two; 14. Flow meter one; 15 .Solenoid valve 1; 16. Expansion valve 1; 17. Evaporator; 18. Gas-liquid separator; 19. Expansion valve 4; 20. Check valve 3; 21. Pressure transmitter 1; 22. Pressure transmitter Two; 23. Pressure transmitter three; 24. Pressure transmitter four.

Detailed ways

The preferred embodiments of the utility model will be described in detail below in conjunction with the accompanying drawings, so that the advantages and characteristics of the utility model can be more easily understood by those skilled in the art, so that the protection scope of the utility model can be defined more clearly .

Figure 1 is a schematic diagram of a transcritical _CO2 two-stage compression refrigeration system provided with a medium and low temperature evaporator according to the present invention. The utility model is composed of a low-pressure compressor 1, an oil return pipeline 1-1, a one-way valve 2, a high-pressure compressor 3, an oil separator 4, a gas cooler 5, an expansion valve 3 6, an expansion tank 7, and a flow meter 2 8. Dry filter 9, Solenoid valve 2 10, Expansion valve 2 11, Intermediate heat exchanger 12, Check valve 2 13, Flow meter 1 14, Solenoid valve 1 15, Expansion valve 1 16, Evaporator 17, Gas-liquid Separator 18, expansion valve four 19, one-way valve three 20, pressure transmitter one 21, pressure transmitter two 22, pressure transmitter three 23, and pressure transmitter four 24. The outlet of the low-pressure compressor, high-pressure compressor, oil separator, gas cooler, expansion tank, dry filter, and intermediate heat exchanger are connected in sequence through pipelines, and an oil return pipe is arranged between the low-pressure compressor and the high-pressure compressor The pipeline between the low-pressure compressor and the high-pressure compressor is provided with a check valve 1 and a pressure transmitter 1, and the bypass pipeline from the expansion tank to the inlet of the high-pressure compressor is sequentially provided with expansion valve 4, Pressure transmitter 3 and one-way valve 3, expansion valve 3 and pressure transmitter 2 are installed between the outlet of the gas cooler and the inlet pipeline of the expansion tank, and the liquid outlet of the expansion tank is connected through the pipeline with flowmeter 2 Dry filter, the dry filter is connected to two branches respectively, and one branch is connected to the outlet of the low-pressure stage compressor and the pressure The pipeline between transmitter 1 and the other branch are connected to the inlet of the low-pressure stage compressor after passing through the intermediate heat exchanger, flow meter 1, solenoid valve 1, expansion valve 1, evaporator, and gas-liquid separator.

The operating principle of a transcritical CO _two -stage compression refrigeration system provided with a medium and low temperature evaporator in this embodiment is:

The high-temperature and high-pressure _CO2 gas coming out of the gas cooler 5 is throttled and depressurized by the expansion valve 3 6 and then enters the expansion tank 7. After throttling, the gas-liquid two-phase refrigerant is separated from the gas and liquid in the expansion tank, and the saturated gas in the tank is discharged from the side. The branch path is depressurized by the expansion valve 4 19 and then merged into the suction line of the high pressure compressor 3. The CO ₂ liquid in the tank is dried by the drying filter 9 and then divided into two paths, and one path is throttled by the expansion valve 2 11 and enters the middle The heat exchanger 12 supercools the refrigerant entering the evaporator, and then merges into the suction line of the high-pressure compressor 3, while the other refrigerant liquid is supercooled by the intermediate heat exchanger 12, and then passes through the expansion valve 16 Throttling into the evaporator 17, after absorbing heat in the evaporator 17, after passing through the gas-liquid separator 18, it is compressed to the medium pressure by the low-pressure compressor 1, and then mixed with the two branch gases in the suction line of the high-pressure compressor 3 After that, it is sucked into the high-pressure stage compressor 3, and the high-temperature and high-pressure gas from the high-pressure compressor 3 passes through the oil separator 4 and then enters the gas cooler 5 to cool down and complete the refrigeration cycle.

The check valve two 13 is to prevent the exhaust pressure of the low-pressure compressor from being higher than the evaporation pressure of the medium temperature evaporator to cause gas backflow; the check valve one 2 is to prevent the bypass vapor pressure from the expansion tank from being higher than The discharge pressure of the low-pressure compressor produces backflow; the check valve three 20 is to prevent the backflow phenomenon caused by the discharge pressure of the low-pressure compressor being higher than the steam bypass pressure of the expansion tank under the condition of abnormal operation of the system .

The oil return pipeline 1-1 is the oil return pipeline of the low-pressure stage compressor, and the oil return pipeline 1-1 is connected with the low-pressure stage compressor 1 and the high-pressure stage compressor 3 respectively.

The pressure transmitter 1 21 is used to compare the value of the pressure transmitter 3 23 in system control to adjust the opening of the expansion valve 4 19 .

The pressure transmitter 2 22 is used to compare with the preset value in the system control to control the opening of the expansion valve 3 6 .

The flow meter two 8 is for recording the total _CO refrigerant flow through the intermediate heat exchanger and the evaporator; the flow meter one 14 is for recording the refrigerant mass flow rate of the evaporator for calculating the refrigerating capacity of the system to It is convenient to adjust the opening degrees of the expansion valve two 11 and the expansion valve one 16 according to actual usage conditions.

The low-pressure and high-pressure compressors described in the utility model are any one of fixed-frequency or variable-frequency scroll compressors, rotor compressors, screw compressors, piston compressors, or other types of compressors. The gas cooler is an air-cooled cooler, water-cooled cooler, evaporative cooler or other coolers. The expansion valve is any one of electronic expansion valve, thermal expansion valve, capillary or orifice throttling, or other throttling devices that can reduce the pressure of the refrigerant.

The above is only an embodiment of the present invention, and does not limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made by using the description of the present invention and the contents of the accompanying drawings, or directly or indirectly used in other related technologies Fields are all included in the scope of patent protection of the present invention in the same way.

Claims (5)

1. A transcritical CO _two- stage compression booster refrigeration system is characterized in that a low-pressure stage compressor, a high-pressure stage compressor, an oil separator, a gas cooler, an expansion tank, a filter drier, an intermediate heat exchanger, The evaporator and the gas-liquid separator are connected sequentially through pipelines, an oil return pipeline is arranged between the low-pressure compressor and the high-pressure compressor, and a check valve and a pressure Transmitter 1, the bypass line from the expansion tank to the inlet of the high-pressure compressor is provided with expansion valve 4, pressure transmitter 3 and check valve 3 in sequence, the outlet of the gas cooler is connected to the inlet of the expansion tank An expansion valve 3 and a pressure transmitter 2 are arranged between them. The liquid outlet of the expansion tank is connected to the dry filter through the pipeline of the flow meter 2. The dry filter is respectively connected to two branches, and one branch passes through the solenoid valve 2 and the expansion tank. Valve 2, intermediate heat exchanger, pressure transmitter 4, and check valve 2 are connected to the pipeline between the outlet of the low-pressure compressor and pressure transmitter 1, and the other branch passes through the intermediate heat exchanger and flowmeter 1 1. Solenoid valve 1, expansion valve 1, evaporator, and gas-liquid separator are connected to the inlet of the low-pressure stage compressor. 2. transcritical CO according to claim ₁ Two-stage compression booster refrigeration system, characterized in that the low-pressure compressor and the high-pressure stage compressor are scroll compressors, rotary compressors, screw compressors with fixed frequency or variable frequency Any one of machine and piston compressor. 3. The transcritical CO _two -stage compression booster refrigeration system according to claim 1, wherein the expansion valve is any one of electronic expansion valve, thermal expansion valve, capillary tube or orifice throttling . 4. The transcritical CO ₂ two-stage compression booster refrigeration system according to claim 1, characterized in that, the intermediate heat exchanger is a plate heat exchanger or a casing heat exchanger. 5. transcritical CO according to claim ₁ Two-stage compression booster refrigeration system, characterized in that, the gas cooler is any one of an air-cooled cooler, a water-cooled cooler, and an evaporative cooler .