Integrated double-plate heat exchanger water-cooled brine unit system
Patent Information
- Application Number
- CN202522190671.5
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-10-16
- Publication Date
- 2026-09-22
- Estimated Expiration
- 2035-10-16
AI Technical Summary
[0004]针对传统水冷盐水机组传热效率低，体积庞大笨重，制冷剂充注量大的问题，提出了一种集成双板换结构水冷盐水机组系统
[0009]本实用新型的有益效果在于：本实用新型大幅降低制冷系统的充注量，采用板式蒸发器与板式冷凝器替代传统管壳式换热器，换热效率高，内部容积小，直接降低制冷剂充注量，减少初始成本，并满足环保法规（如低GWP制冷剂要求），降低泄漏风险；板式换热器较传统壳管式换热器体积更小，重量更轻，节省机房空间，降低运输及安装成本；气液分离器与板式蒸发器的直连设计，结合液位精准控制，维持板式蒸发器供液稳定性同时避免低压侧波动导致的压缩机液击风险，确保低温工况下循环可靠性。
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Figure CN224787416U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of refrigeration technology, and in particular to an integrated double-plate heat exchanger structure water-cooled brine unit system. Background Technology
[0002] Water-cooled brine chillers, as one of the core pieces of equipment in industrial refrigeration systems, play a crucial role in many fields such as chemical engineering, pharmaceuticals, food processing, central air conditioning, and cold chain logistics. They are mainly used to produce low-temperature refrigerants (usually brine solutions). Their core working principle follows the refrigeration cycle and mainly consists of four components: a compressor, a condenser, a throttling device (such as an expansion valve), and an evaporator.
[0003] Traditional water-cooled brine chiller units generally use shell-and-tube heat exchangers as both evaporators and condensers. While the structure is mature and reliable, this type of heat exchanger design typically suffers from the following significant technical bottlenecks and shortcomings: 1) Low heat transfer efficiency and bulky size: Shell and tube heat exchangers usually use bare tubes or finned tubes, with a small heat transfer area per unit volume and low heat transfer efficiency. In order to meet the required heat transfer load, the equipment structure is mostly bulky and heavy, occupying a lot of machine room space and significantly increasing transportation and installation costs. 2) Large refrigerant charge: Due to the large internal volume of the shell and tube heat exchanger, the refrigerant charge required for the entire system increases significantly, which not only increases the initial cost, but also becomes a significant disadvantage in the context of increasingly stringent environmental regulations (such as restrictions on the use of refrigerants with high GWP values) and the pursuit of reducing the risk of leakage. Utility Model Content
[0004] To address the problems of low heat transfer efficiency, large size and heavy weight, and large refrigerant charge of traditional water-cooled brine chillers, an integrated double-plate heat exchanger structure water-cooled brine chiller system is proposed.
[0005] The technical solution of this utility model is: an integrated double plate heat exchanger structure water-cooled brine unit system, including a compressor, the outlet of the compressor is connected to the inlet end of an oil separator, the oil separator is connected to the compressor, the exhaust end of the oil separator is connected to the inlet of a plate condenser, and the outlet of the plate condenser is connected to the inlet of a high-pressure tank. It also includes a plate economizer. The outlet of the high-pressure guide tank is divided into two paths. One path connects to the evaporator side inlet of the plate economizer, and the evaporator side return port of the plate economizer connects to the compressor. The other path of the high-pressure guide tank outlet connects to the subcooled side inlet of the plate economizer, and the subcooled side outlet of the plate economizer connects to the bottom inlet of the suction regenerator. The circulating gas outlet of the suction regenerator is connected to the compressor inlet, the refrigerant outlet at the bottom of the gas-liquid separator is connected to the plate evaporator inlet, and the refrigerant inlet at the bottom of the gas-liquid separator is connected to the plate evaporator outlet.
[0006] Preferably, a liquid supply throttling valve is provided on the pipeline between the bottom outlet of the gas-absorbing regenerator and the inlet of the gas-liquid separator; Preferably, the gas-liquid separator is equipped with a liquid level sensor for monitoring the liquid level inside the gas-liquid separator.
[0007] Preferably, it also includes a Venturi tube, the inlet of which is connected to a pipe between the exhaust end of the oil separator and the inlet of the plate condenser; the outlet of the Venturi tube is connected to a pipe between the top outlet of the gas-liquid separator and the circulating gas inlet of the suction regenerator; and the oil return port of the Venturi tube is connected to the oil return port of the gas-liquid separator.
[0008] Preferably, a thermal expansion valve is provided on the pipeline between the high-pressure guide tank and the subcooled side inlet of the plate economizer, and the temperature sensing component of the thermal expansion valve is connected to the pipeline between the evaporator side return port of the plate economizer and the compressor.
[0009] The beneficial effects of this utility model are as follows: This utility model significantly reduces the refrigerant charge of the refrigeration system. It uses plate evaporators and plate condensers to replace traditional shell-and-tube heat exchangers, resulting in high heat exchange efficiency and small internal volume, directly reducing the refrigerant charge, reducing initial costs, and meeting environmental regulations (such as low GWP refrigerant requirements), thus reducing the risk of leakage. The plate heat exchanger is smaller and lighter than traditional shell-and-tube heat exchangers, saving machine room space and reducing transportation and installation costs. The direct connection design between the gas-liquid separator and the plate evaporator, combined with precise liquid level control, maintains the stability of the liquid supply to the plate evaporator while avoiding the risk of compressor liquid slugging caused by low-pressure side fluctuations, ensuring reliable cycle operation under low-temperature conditions. Attached Figure Description
[0010] Figure 1 This is a schematic diagram of the integrated double-plate heat exchanger structure water-cooled brine unit system of this utility model.
[0011] The component names corresponding to the various reference numerals in the diagram are as follows: 1. Compressor; 2. Oil separator; 3. Plate condenser; 4. High-pressure guide tank; 5. Plate economizer; 6. Liquid supply throttle valve; 7. Gas-liquid separator; 71. Liquid level sensor; 8. Plate evaporator; 9. Suction regenerator; 10. Venturi tube; 11. Thermal expansion valve. Detailed Implementation
[0012] The present invention will now be described in detail with reference to the accompanying drawings and specific embodiments. This embodiment is based on the technical solution of the present invention and provides detailed implementation methods and specific operating procedures; however, the scope of protection of the present invention is not limited to the following embodiments.
[0013] refer to Figure 1As shown in the figure, this application discloses an integrated double-plate heat exchanger structure water-cooled brine unit system, including a compressor 1, the outlet of the compressor 1 is connected to the air inlet of an oil separator 2, the oil separator 2 is connected to the oil return port of the compressor 1, the exhaust end of the oil separator 2 is connected to the inlet of a plate condenser 3, and the outlet of the plate condenser 3 is connected to the inlet of a high-pressure tank 4.
[0014] It also includes a plate economizer 5, which includes an evaporator side and a subcooling side. The outlet of the high-pressure guide tank 4 is divided into two paths. One path is connected to the evaporator side inlet of the plate economizer 5, and the evaporator side return port of the plate economizer 5 is connected to the compressor 1. The other path of the outlet of the high-pressure guide tank 4 is connected to the subcooling side inlet of the plate economizer 5, and the subcooling side outlet of the plate economizer 5 is connected to the bottom inlet of the suction regenerator 9.
[0015] The bottom outlet of the suction regenerator 9 is connected to the inlet of the gas-liquid separator 7, the top outlet of the gas-liquid separator 7 is connected to the circulating gas inlet of the suction regenerator 9, the circulating gas outlet of the suction regenerator 9 is connected to the inlet of the compressor 1, the refrigerant outlet at the bottom of the gas-liquid separator 7 is connected to the inlet of the plate evaporator 8, and the refrigerant inlet at the bottom of the gas-liquid separator 7 is connected to the outlet of the plate evaporator 8. The gas-liquid separator 7 is connected to the plate evaporator 8 and forms a refrigerant circulation loop on the side of the plate evaporator 8 through the thermosiphon principle.
[0016] A liquid supply throttling valve 6 is installed on the pipeline between the bottom outlet of the gas-suction regenerator 9 and the inlet of the gas-liquid separator 7.
[0017] The gas-liquid separator 7 is equipped with a liquid level sensor 71 for monitoring the liquid level inside the gas-liquid separator 7.
[0018] The control system adjusts the opening of the liquid supply throttle valve 6 according to the liquid level sensor 71 to maintain a stable liquid level and ensure the stable operation of the gas-liquid separator 7 and the plate evaporator 8 based on the thermosiphon principle.
[0019] It also includes a Venturi tube 10, the inlet of which is connected to the pipe between the exhaust end of the oil separator 2 and the inlet of the plate condenser 3; the outlet of the Venturi tube 10 is connected to the pipe between the top outlet of the gas-liquid separator 7 and the circulating gas inlet of the suction regenerator 9; the oil return port of the Venturi tube 10 is connected to the oil return port of the gas-liquid separator 7; through Bernoulli's principle, the Venturi tube 10 introduces high-pressure exhaust from the compressor 1, and uses the negative pressure generated by the high-pressure gas flow to draw out the lubricating oil in the gas-liquid separator 7 and bring it back to the compressor 1, thereby realizing the recovery of lubricating oil on the low-pressure side of the refrigeration system.
[0020] A thermostatic expansion valve 11 is installed on the pipe between the high-pressure conduit 4 and the subcooled side inlet of the plate economizer 5. The temperature sensing component of the thermostatic expansion valve 11 is connected to the pipe between the evaporator side return port of the plate economizer 5 and the compressor 1. The thermostatic expansion valve 11 is used to cool the refrigerant liquid heading to the evaporator.
[0021] The refrigerant introduced from the high-pressure tank 4 on the evaporator side of the plate economizer 5 is throttled and vaporized by the thermostatic expansion valve 11, absorbing heat to cool the subcooled side. The vaporized refrigerant returns to the economizer interface of the compressor 1 to form a make-up gas cycle, thereby improving refrigeration efficiency. The refrigerant on the subcooled side of the plate economizer 5 is also introduced from the high-pressure tank 4 and finally delivered to the refrigerant inlet of the evaporator 8.
[0022] The specific working principle is as follows: The high-temperature, high-pressure gas discharged from compressor 1 passes through oil separator 2 to separate lubricating oil, then enters plate condenser 3 to condense into liquid, flowing into high-pressure tank 4. The liquid refrigerant in high-pressure tank 4 flows through plate economizer 5 for subcooling, and then enters suction regenerator 9 for further subcooling. After two subcoolings, the liquid refrigerant passes through liquid throttling valve 6 to reduce pressure and enters gas-liquid separator 7. The refrigerant liquid at the bottom of gas-liquid separator 7 flows into plate evaporator 8, absorbs heat from brine, vaporizes to form a gas-liquid mixture, and returns to gas-liquid separator 7. Inside gas-liquid separator 7, the refrigerant liquid settles and re-enters evaporator 8 for circulation; the separated refrigerant gas is superheated by suction regenerator 9 and then drawn into compressor 1, completing the cycle.
[0023] The gas-liquid separator 7 is equipped with a liquid level sensor 71 to monitor the liquid level inside the gas-liquid separator. The control system adjusts the opening of the liquid supply throttle valve 6 according to the liquid level sensor 71 to maintain a stable liquid level and ensure the stable operation of the gas-liquid separator 7 and the plate evaporator 8 based on the thermosiphon principle.
[0024] The beneficial effects are as follows: This utility model significantly reduces the refrigerant charge of the refrigeration system. It replaces the traditional shell-and-tube heat exchanger with a plate evaporator 8 and a plate condenser 3, which has high heat exchange efficiency and small internal volume, directly reducing the refrigerant charge, reducing initial costs, and meeting environmental regulations (such as low GWP refrigerant requirements), thus reducing the risk of leakage. The plate heat exchanger is smaller and lighter than the traditional shell-and-tube heat exchanger, saving machine room space and reducing transportation and installation costs. The direct connection design between the gas-liquid separator 7 and the plate evaporator 8, combined with precise liquid level control, maintains the stability of the liquid supply to the plate evaporator 8 while avoiding the risk of liquid slugging in the compressor 1 caused by low-pressure side fluctuations, ensuring the reliability of the cycle under low-temperature conditions.
[0025] It should be noted that the terms "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating orientation or positional relationships are based on the orientation or positional relationships shown in the accompanying drawings. They are used only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. The terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. "A plurality of" means two or more. "Installed," "connected," and "joined" should be interpreted broadly; for example, they can refer to a fixed connection, a detachable connection, or an integral connection.
[0026] The above description is merely a preferred embodiment of this utility model and is not intended to limit this utility model in any form or substance. It should be noted that those skilled in the art can make various improvements and additions without departing from this utility model, and these improvements and additions should also be considered within the protection scope of this utility model. Any modifications, alterations, and equivalent changes made by those skilled in the art without departing from the spirit and scope of this utility model using the disclosed technical content are equivalent embodiments of this utility model. Furthermore, any modifications, alterations, and evolutions made to the above embodiments based on the essential technology of this utility model are still within the scope of the technical solution of this utility model.
Claims
1. A water-cooled brine chiller system with an integrated double-plate heat exchanger structure, characterized in that, Includes a compressor (1), the outlet of the compressor (1) is connected to the inlet of the oil separator (2), the oil separator (2) is connected to the compressor (1), the exhaust end of the oil separator (2) is connected to the inlet of the plate condenser (3), and the outlet of the plate condenser (3) is connected to the inlet of the high-pressure guide tank (4). It also includes a plate economizer (5), the outlet of the high pressure tank (4) is divided into two paths, one path is connected to the evaporation side inlet of the plate economizer (5), the evaporation side return port of the plate economizer (5) is connected to the compressor (1); the other path of the outlet of the high pressure tank (4) is connected to the subcooling side inlet of the plate economizer (5), and the subcooling side outlet of the plate economizer (5) is connected to the bottom inlet of the suction regenerator (9). The circulating gas outlet of the suction regenerator (9) is connected to the inlet of the compressor (1), the refrigerant outlet at the bottom of the gas-liquid separator (7) is connected to the inlet of the plate evaporator (8), and the refrigerant inlet at the bottom of the gas-liquid separator (7) is connected to the outlet of the plate evaporator (8).
2. The integrated double-plate heat exchanger structure water-cooled brine unit system according to claim 1, characterized in that, A liquid supply throttling valve (6) is provided on the pipeline between the bottom outlet of the gas-absorbing regenerator (9) and the inlet of the gas-liquid separator (7).
3. The integrated double-plate heat exchanger structure water-cooled brine unit system according to claim 1, characterized in that, The gas-liquid separator (7) is equipped with a liquid level sensor (71) for monitoring the liquid level inside the gas-liquid separator (7).
4. The integrated double-plate heat exchanger structure water-cooled brine unit system according to claim 1, characterized in that, It also includes a venturi tube (10), the inlet of which is connected to the pipe between the exhaust end of the oil separator (2) and the inlet of the plate condenser (3); the outlet of the venturi tube (10) is connected to the pipe between the top outlet of the gas-liquid separator (7) and the circulating gas inlet of the gas-absorbing regenerator (9); and the oil return port of the venturi tube (10) is connected to the oil return port of the gas-liquid separator (7).
5. The integrated double-plate heat exchanger structure water-cooled brine unit system according to claim 1, characterized in that, A thermal expansion valve (11) is provided on the pipeline between the high-pressure guide tank (4) and the subcooled side inlet of the plate economizer (5). The temperature sensing component of the thermal expansion valve (11) is connected to the pipeline between the evaporation side return port of the plate economizer (5) and the compressor (1).