A wide-temperature dynamic variable temperature liquid cooling device

Abstract

This utility model relates to a wide-temperature dynamic variable-temperature liquid cooling device. The exhaust from the high-temperature stage compressor is split into two paths after passing through the condenser. One path is sent to the first compression side of the evaporator via a control valve and an electronic expansion valve. The exhaust from the first compression side is then connected back to the high-temperature stage compressor via a pressure regulating valve. The other path is connected to the first hot end of the condenser-evaporator via a liquid supply solenoid valve. The exhaust from the first hot end is then returned to the high-temperature stage compressor. The exhaust from the low-temperature stage compressor is sent to the other hot end of the condenser-evaporator. The exhaust from the other hot end is connected to the other compression side of the evaporator via a low-temperature liquid supply solenoid valve and a low-temperature electronic expansion valve. The exhaust from the other compression side is then connected back to the low-temperature stage compressor for return gas. The load liquid supply is sent through a water tank and a liquid supply pump set. One path is connected to the load side of the evaporator via a refrigeration solenoid valve, and the other path is connected to the load side outlet of the evaporator via a forced-cooling solenoid valve and a forced-cooling air-cooled heat exchanger. The return liquid pipe is connected to the load via a return liquid control valve. This device has a simple structure and can meet the requirements for efficient and precise real-time temperature adjustment over a wide temperature range.

Description

Technical Field

[0001] This utility model relates to a liquid cooling device, specifically a wide-temperature dynamic variable temperature liquid cooling device. Background Technology

[0002] With the development of liquid cooling technology, liquid cooling systems are applicable to more and more environments. For some occasions with a large range of ambient temperature changes, traditional single-compression refrigeration liquid cooling systems can meet adaptive control by adding compressors of the same specifications or adjusting the compressor power. However, this results in a large control range, poor response efficiency and refrigeration accuracy, and high energy consumption and low reliability when the compression refrigeration power is adjusted significantly. Summary of the Invention

[0003] This invention provides a wide-temperature dynamic variable temperature liquid cooling device with a simple structure that can meet the requirements of efficient and high-precision real-time temperature adjustment over a wide temperature range.

[0004] The technical solution adopted by this utility model is: a wide-temperature dynamic variable-temperature liquid cooling device, including a compression refrigeration unit, the compression refrigeration unit connected to an evaporator, the evaporator connected to a load via a return liquid pipe, the load returning to the evaporator via a supply liquid pipe, and a water tank and a supply liquid pump set installed on the supply liquid pipe. The characteristic feature is that the compression refrigeration unit includes a high-temperature stage compressor and a low-temperature stage compressor. The exhaust gas from the high-temperature stage compressor is split into two paths after passing through the condenser. One path is sent to the first compression side of the evaporator via a high-temperature evaporation control valve and a high-temperature electronic expansion valve. The gas discharged from the first compression side of the evaporator is returned to the high-temperature stage compressor via an evaporation pressure regulating valve. The other path is connected to the first hot section of the condenser evaporator via a high-temperature supply liquid solenoid valve. The condenser evaporator's hot end is connected to the high-temperature stage compressor's return gas via a check valve; the low-temperature stage compressor's exhaust gas is sent to the condenser evaporator's other hot end, and the condenser evaporator's other hot end is connected to the evaporator's other compression side via a low-temperature liquid supply solenoid valve and a low-temperature electronic expansion valve; the evaporator's other compression side is connected to the low-temperature stage compressor's return gas; the load liquid supply is sent through a water tank, and a liquid supply pipe is connected to the bottom of the water tank. The liquid supply pipe is split into two paths after the liquid supply pump set. One path is connected to the evaporator's load side inlet via a refrigeration solenoid valve, and the other path is connected to the evaporator's load side outlet or the return liquid pipe via a forced cooling solenoid valve and one or more forced cooling air-cooled heat exchangers. The return liquid pipe is connected to the load via a return liquid control valve.

[0005] The exhaust gas from the high-temperature stage compressor is also connected back to the high-temperature stage compressor return gas via a high-temperature energy regulating valve.

[0006] The exhaust gas from the cryogenic stage compressor is also connected back to the cryogenic stage compressor return gas via a cryogenic energy regulating valve.

[0007] The other hot section of the condenser-evaporator is split into two paths: one path connects to the other compression side of the evaporator via a low-temperature liquid supply solenoid valve and a low-temperature electronic expansion valve, and the other path connects to the return gas of the low-temperature stage compressor via a return liquid supply solenoid valve.

[0008] The exhaust gas from the cryogenic compressor is split into two paths after passing through the pre-cooling condenser. One path is sent to the other hot section of the condenser-evaporator, and the other path is connected to the return gas from the cryogenic compressor via a pressure regulating valve.

[0009] The exhaust gas from the cryogenic compressor is split into two paths after passing through the pre-cooling condenser. One path is sent to the other hot section of the condenser-evaporator, and the other path is connected to the return gas from the cryogenic compressor via a pressure regulating valve.

[0010] The exhaust gas from the high-temperature stage compressor is divided into three paths after passing through the condenser. The first path is sent to the compression side of the evaporator via the high-temperature evaporation control valve and the high-temperature electronic expansion valve. The second path is connected to the hot section of the condenser evaporator via the high-temperature liquid supply solenoid valve. The third path is connected to the return gas from the high-temperature stage compressor via the liquid injection solenoid valve.

[0011] The return liquid control valve of the return liquid pipe is followed by a fine filter and then splits into two paths. One path is connected to the load via a return liquid flow sensor, a return liquid temperature sensor, and a return liquid pressure sensor. The other path is connected to the water tank via a bypass valve. The load output is sent to the water tank via a supply liquid pressure sensor, a supply liquid temperature sensor, and a supply liquid flow sensor.

[0012] A pressure relief solenoid valve is connected in parallel to the bypass valve.

[0013] A recovery pipeline branches off from the return liquid pressure sensor, and the recovery pipeline connects to the water tank via a recovery pump.

[0014] The beneficial effects of this utility model are: 1. When the temperature inside the water tank is higher than the ambient temperature by a certain amount, only the forced cooling solenoid valve is opened. The high-temperature stage and low-temperature stage compressors do not work. The coolant in the water tank is sent to one or more forced cooling heat exchangers through the liquid supply pump group for forced air cooling. This can meet the cooling liquid supply to the evaporator, while effectively taking into account the precision control and playing an energy-saving role when the ambient temperature is relatively low.

[0015] 2. When the temperature inside the water tank is lower than the ambient temperature by a certain amount, the forced cooling solenoid valve closes and the refrigeration solenoid valve opens. Based on the temperature difference between the water tank and the ambient temperature, the low-temperature stage compressor operates when the temperature difference is small, and the high-temperature stage compressor operates simultaneously when the temperature difference is large. The refrigerant delivered by the high-temperature stage compressor is sent to the condenser-evaporator after passing through the condenser, where it is cooled together with the refrigerant delivered by the low-temperature stage compressor. After being efficiently condensed by the condenser-evaporator, the refrigerant delivered by the low-temperature stage compressor enters the other compression side of the evaporator, where it exchanges heat with the coolant returning and supplying liquid to the load. Combined with the refrigerant delivered by the high-temperature stage compressor being separated after passing through the condenser and sent to one compression side of the evaporator, the two compression sides perform superimposed refrigeration, which can meet the needs of wide-temperature variable-temperature cooling and high-precision cooling with large temperature differences.

[0016] 3. Both the low-temperature stage compressor and the high-temperature stage compressor are equipped with adjustable return gas compressors. The low-temperature stage compressor is equipped with a pressure regulating valve and a return liquid supply solenoid valve connected to the compressor. The high-temperature stage compressor is equipped with a spray solenoid valve connected to the compressor. This comprehensive control of compressor load fluctuations ensures stable exhaust and return gas under extreme temperature difference conditions and energy consumption control. When the pressure in the return liquid pipe is too high, the pressure is released directly to the drain tank through a bypass valve or a pressure relief solenoid valve. The return liquid pipe also returns coolant to the water tank via a recovery pump through a recovery pipeline, ensuring the stability of the coolant in the load pipeline. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the structure of this utility model.

[0018] In the diagram: 1. Load, 2. Liquid supply pipe, 3. Liquid supply pressure sensor, 4. Liquid supply temperature sensor, 5. Liquid supply flow sensor, 6. Water tank, 7. Liquid supply pump assembly, 8. Forced cooling solenoid valve, 9. Forced cooling heat exchanger, 10. Refrigeration solenoid valve, 11. Evaporator, 12. High-temperature compressor, 13. Condenser, 14. High-temperature evaporation control valve, 15. High-temperature electronic expansion valve, 16. Evaporation pressure regulating valve, 17. High-temperature liquid supply solenoid valve, 18. Liquid injection solenoid valve, 19. Condenser / evaporator, 20. Check valve, 11. Low temperature. 21. Primary compressor; 22. Pre-cooling condenser; 23. Pressure regulating valve; 24. Low-temperature liquid supply solenoid valve; 25. Low-temperature electronic expansion valve; 26. Return liquid supply solenoid valve; 27. Return electronic expansion valve; 28. Low-temperature energy regulating valve; 29. ​​High-temperature energy regulating valve; 30. Return liquid pipe; 31. Fine filter; 32. Differential pressure sensor; 33. Return liquid pressure sensor; 34. Return liquid temperature sensor; 35. Return liquid flow sensor; 36. Recovery pipeline; 37. Recovery pump; 38. Bypass valve; 39. Pressure relief solenoid valve. Detailed Implementation

[0019] The following explanation, in conjunction with the accompanying drawings, will provide further details.

[0020] Figure 1As shown: A wide-temperature dynamic variable-temperature liquid cooling device includes a high-temperature stage compressor 12 and a low-temperature stage compressor 21. The exhaust gas from the high-temperature stage compressor 21 is divided into three paths after passing through the condenser 13. The first path is sent to the compression side of the evaporator 11 via the high-temperature evaporation control valve 14 and the high-temperature electronic expansion valve 15. The gas discharged from the compression side of the evaporator 11 is returned to the high-temperature stage compressor 12 via the evaporation pressure regulating valve 16. The second path is connected to the hot end of the condenser-evaporator 19 via the high-temperature liquid supply solenoid valve 17. The gas discharged from the hot end of the condenser-evaporator 19 is returned to the high-temperature stage compressor 12 via the check valve 20. The third path is... The liquid injection solenoid valve 18 is connected back to the high-temperature stage compressor 12 for return gas; the exhaust gas from the low-temperature stage compressor 21 is split into two paths after passing through the pre-cooling condenser 22. One path is connected back to the low-temperature stage compressor 21 for return gas via the pressure regulating valve 23, and the other path is sent to the other hot end of the condenser-evaporator 19. The other hot end of the condenser-evaporator 19 is split into two paths. One path is connected to the other compression side of the evaporator 11 via the low-temperature liquid supply solenoid valve 24 and the low-temperature electronic expansion valve 25. The other compression side of the evaporator 11 sends the gas back to the low-temperature stage compressor 21 for return gas, and the other path is connected back to the low-temperature stage compressor 21 for return gas via the return liquid supply solenoid valve 26.

[0021] The load side of the evaporator 11 is connected to the load via the return liquid pipe 30. A fine filter 31 with a differential pressure sensor 32 is installed on the return liquid pipe 30, and the filter splits into three paths after the fine filter. One path is equipped with a return liquid flow sensor 35, a return liquid temperature sensor 34, and a return liquid pressure sensor 33, and is connected to the load 1 and the recovery pipe 36 respectively. The recovery pipe 36 is connected to the water tank 6 via the recovery pump 37. The load 1 is connected to the supply liquid pipe 2. The water tank 6 is installed on the supply liquid pipe 2. The supply liquid pressure sensor 3, the supply liquid temperature sensor 4, and the supply liquid flow sensor 5 are installed sequentially on the supply liquid pipe 2 between the load 1 and the water tank 6. The water tank 6 sends out the liquid through the supply liquid pump group 7 and then splits into two paths. One path is sent to the inlet of the load side of the evaporator 11 via the refrigeration solenoid valve 10, and the other path is connected to the return liquid pipe of the load side outlet of the evaporator 11 via the forced cooling solenoid valve 8 and one or more forced cooling heat exchangers 9.

[0022] In this embodiment, the exhaust gas from the high-temperature stage compressor 12 is also connected back to the high-temperature stage compressor return gas via the high-temperature energy regulating valve 29. The exhaust gas from the low-temperature stage compressor 21 is also connected back to the low-temperature stage compressor return gas via the low-temperature energy regulating valve 28.

[0023] In this embodiment, each valve, pump, and sensor is connected to a controller, which is also connected to an external temperature and humidity sensor, thereby controlling the electrical start and stop. This technology is prior art in liquid cooling technology and will not be described in detail in this application and the accompanying drawings.

[0024] In this embodiment, the liquid supply pump group adopts a parallel structure of multiple pumps and check valves. This technology belongs to the prior art and will not be described in detail in this application and the accompanying drawings.

[0025] In this embodiment, the compressor refrigeration unit is equipped with a dryer filter, oil separator, gas-liquid separator, compressor exhaust and return gas pressure and temperature sensors and controllers, and each pipeline is equipped with control valves and check valves for on / off and check valve control structures. The water tank is equipped with liquid level, exhaust, electric heating, water filling and drainage structures, etc., which are all existing conventional technologies and will not be described in detail in this application and the accompanying drawings.

[0026] Based on this embodiment, after returning to the liquid supply solenoid valve 26, a return electronic expansion valve 27 can also be set to connect back to the cryogenic compressor 21 for gas return.

Claims

1. A wide-temperature dynamic variable-temperature liquid cooling device, comprising a compressor refrigeration unit, the compressor refrigeration unit being connected to an evaporator, the evaporator being connected to a load via a return liquid pipe, the load returning to the evaporator via a supply liquid pipe, and a water tank and a supply liquid pump set being installed on the supply liquid pipe, characterized in that: The refrigeration unit includes a high-temperature stage compressor and a low-temperature stage compressor. The exhaust from the high-temperature stage compressor is split into two paths after passing through the condenser. One path is sent to the first compression side of the evaporator via a high-temperature evaporation control valve and a high-temperature electronic expansion valve. The exhaust from the first compression side of the evaporator is then connected back to the high-temperature stage compressor return gas via an evaporation pressure regulating valve. The other path is connected to the first hot end of the condenser-evaporator via a high-temperature liquid supply solenoid valve. The exhaust from the first hot end of the condenser-evaporator is then connected back to the high-temperature stage compressor return gas via a check valve. The exhaust from the low-temperature stage compressor is sent to the other hot end of the condenser-evaporator. The exhaust from the other hot end of the condenser-evaporator is connected to the other compression side of the evaporator via a low-temperature liquid supply solenoid valve and a low-temperature electronic expansion valve. The exhaust from the other compression side of the evaporator is then connected back to the low-temperature stage compressor return gas. The load liquid supply is sent through a water tank. A liquid supply pipe is connected to the bottom of the water tank. The liquid supply pipe is split into two paths after the liquid supply pump set. One path is connected to the load side inlet of the evaporator via a refrigeration solenoid valve. The other path is connected to the load side outlet of the evaporator or to the return liquid pipe via a forced cooling solenoid valve and one or more forced cooling air-cooled heat exchangers. The return liquid pipe is connected to the load via a return liquid control valve.

2. The wide-temperature dynamic variable-temperature liquid cooling device according to claim 1, characterized in that: The exhaust gas from the high-temperature stage compressor is also connected back to the high-temperature stage compressor return gas via a high-temperature energy regulating valve.

3. The wide-temperature dynamic variable-temperature liquid cooling device according to claim 1, characterized in that: The exhaust gas from the cryogenic stage compressor is also connected back to the cryogenic stage compressor return gas via a cryogenic energy regulating valve.

4. A wide-temperature dynamic variable-temperature liquid cooling device according to claim 1 or 3, characterized in that: The other hot section of the condenser-evaporator is split into two paths: one path connects to the other compression side of the evaporator via a low-temperature liquid supply solenoid valve and a low-temperature electronic expansion valve, and the other path connects to the return gas of the low-temperature stage compressor via a return liquid supply solenoid valve.

5. The wide-temperature dynamic variable temperature liquid cooling device according to claim 1, characterized in that: The exhaust gas from the cryogenic compressor is split into two paths after passing through the pre-cooling condenser. One path is sent to the other hot section of the condenser-evaporator, and the other path is connected to the return gas from the cryogenic compressor via a pressure regulating valve.

6. The wide-temperature dynamic variable temperature liquid cooling device according to claim 4, characterized in that: The exhaust gas from the cryogenic compressor is split into two paths after passing through the pre-cooling condenser. One path is sent to the other hot section of the condenser-evaporator, and the other path is connected to the return gas from the cryogenic compressor via a pressure regulating valve.

7. The wide-temperature dynamic variable temperature liquid cooling device according to claim 1, characterized in that: The exhaust gas from the high-temperature stage compressor is divided into three paths after passing through the condenser. The first path is sent to the compression side of the evaporator via the high-temperature evaporation control valve and the high-temperature electronic expansion valve. The second path is connected to the hot section of the condenser evaporator via the high-temperature liquid supply solenoid valve. The third path is connected to the return gas from the high-temperature stage compressor via the liquid injection solenoid valve.

8. The wide-temperature dynamic variable temperature liquid cooling device according to claim 1, characterized in that: The return liquid control valve of the return liquid pipe is followed by a fine filter and then splits into two paths. One path is connected to the load via a return liquid flow sensor, a return liquid temperature sensor, and a return liquid pressure sensor. The other path is connected to the water tank via a bypass valve. The load output is sent to the water tank via a supply liquid pressure sensor, a supply liquid temperature sensor, and a supply liquid flow sensor.

9. A wide-temperature dynamic variable-temperature liquid cooling device according to claim 8, characterized in that: A pressure relief solenoid valve is connected in parallel to the bypass valve.

10. A wide-temperature dynamic variable-temperature liquid cooling device according to claim 8, characterized in that: A recovery pipeline branches off from the return liquid pressure sensor, and the recovery pipeline connects to the water tank via a recovery pump.

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