Water source heat pump heat exchange method and compact water source heat pump system

Abstract

This invention discloses a water source heat pump heat exchange method and a compact water source heat pump system. The method is applied to a compact water source heat pump system, which includes an aluminum plate-fin heat exchanger, an electronic expansion valve, and a refrigerant compressor. The aluminum plate-fin heat exchanger has a capillary trickle flow control structure on its inner side, with a front heat exchange structure and a rear heat exchange structure located on its front and rear sides, respectively. This invention maximizes the use of the internal space of the equipment, achieving a continuous and efficient transition of refrigerant states (temperature, pressure, phase), making the state transition of the refrigerant smoother during functional conversion, reducing energy loss caused by improper component matching in traditional distributed systems, fully leveraging the high-efficiency heat transfer potential of the plate-fin structure throughout the entire process, achieving efficient synergy and low-loss operation of the core refrigeration components, and possessing a full-condition adaptive mechanism, thus enhancing the overall energy efficiency and reliability of the heat exchange system.

Description

Technical Field

[0001] This invention relates to the field of water source heat pump technology, and in particular to a water source heat pump heat exchange method and a compact water source heat pump system. Background Technology

[0002] With increasing global focus on energy efficiency and environmental protection, water source heat pumps, as a highly efficient and energy-saving heating and cooling system, have been widely adopted. However, existing water source heat pumps face numerous problems in practical operation. Traditional water source heat pumps typically employ large-volume heat exchange devices, such as shell-and-tube heat exchangers, which not only occupy a large area but also incur high installation and maintenance costs. In space-constrained locations, such as small commercial buildings and apartments in cities, they are often unsuitable for installation. Furthermore, traditional throttling devices lack sufficient precision in regulating refrigerant flow according to different operating conditions, leading to reduced system energy efficiency. Furthermore, existing heat exchange devices often cannot operate adaptively under all operating conditions. In different seasons and under different ambient temperature and humidity conditions, the requirements for heat exchange efficiency and refrigerant state of heat pump systems vary, and traditional heat exchange devices are difficult to meet the needs of these complex operating conditions, further affecting the overall performance of water source heat pumps.

[0003] Therefore, it is necessary to develop a water source heat pump heat exchange method and a compact water source heat pump system to solve the problems of large size, low throttling control accuracy, and inability to adapt to all operating conditions of existing water source heat pumps, and to improve the overall performance and energy utilization efficiency of water source heat pumps. Summary of the Invention

[0004] The technical problem to be solved by this invention is to address the shortcomings of the prior art by providing a water source heat pump heat exchange method and a compact water source heat pump system. Through the integrated design of the aluminum plate-fin heat exchange device and the heat pump system, the external dimensions and installation positions of each component are rationally planned to maximize the use of the internal space of the equipment, reduce the overall volume of the water source heat pump, and achieve continuous and efficient transition of refrigerant state (temperature, pressure, phase). This allows for a smoother transition of refrigerant state during functional conversion, reduces energy loss caused by improper component matching in traditional decentralized systems, fully utilizes the high-efficiency heat transfer potential of the plate-fin structure throughout the entire process, and achieves efficient synergy and low-loss operation of the core refrigeration components.

[0005] To achieve the above objectives, this application provides the following technical solution: A water source heat pump heat exchange method is disclosed, applied to a compact water source heat pump system. The compact water source heat pump system includes an aluminum plate-fin heat exchanger, an electronic expansion valve, and a refrigerant compressor. The aluminum plate-fin heat exchanger has a capillary flow control structure on its inner side. A front heat exchange structure and a rear heat exchange structure are respectively located on the front and rear sides of the capillary flow control structure. The front and rear heat exchange structures each have a condensation zone and an evaporation zone, and fluid channels are provided within both the condensation and evaporation zones. The method includes the following steps: S1, refrigerant circulation heat exchange, including: S1.1. First-stage gaseous refrigerant is introduced into the condensation zone. In the condensation zone, the first-stage gaseous refrigerant undergoes a liquefaction reaction, and its state changes to the second-stage liquid refrigerant. Heat is released during the liquefaction reaction, and heat exchange is achieved with the heat exchange structure in front.

[0006] S1.2 The second-stage liquid refrigerant is output from the capillary flow control structure to the condensation area and sent to the electronic expansion valve. The capillary flow control structure, in conjunction with the electronic expansion valve, reduces the pressure and throttles the second-stage liquid refrigerant, transforming it into the third-stage mist refrigerant.

[0007] S1.3. The third-stage mist refrigerant is introduced into the evaporation zone. In the evaporation zone, the third-stage mist refrigerant undergoes a vaporization reaction and its state changes to the fourth-stage gaseous refrigerant. During the vaporization reaction, heat is absorbed and heat is exchanged with the heat exchange structure behind it.

[0008] S1.4. The fourth-stage gaseous refrigerant output from the evaporation zone is introduced into the refrigerant compressor. In the refrigerant compressor, the fourth-stage gaseous refrigerant is compressed and its state is transformed into the first-stage gaseous refrigerant, so that the first-stage gaseous refrigerant flows back to the condensation zone for heat exchange.

[0009] S2. A first fluid is introduced into the fluid channel in front of the aluminum plate-fin heat exchanger, and the first fluid exchanges heat with the heat exchange structure in front.

[0010] S3. A second fluid is introduced into the fluid channel behind the aluminum plate-fin heat exchanger, and the second fluid exchanges heat with the heat exchange structure behind it.

[0011] S4. Monitor the operating parameters of the refrigerant, first fluid, and second fluid in the aluminum plate-fin heat exchanger, including their heat load, pressure, and phase state. Adjust the flow area of ​​the internal flow channels of the capillary flow control structure to control the heat exchange efficiency of the front and rear heat exchange structures.

[0012] In S1, the temperature of the gaseous refrigerant in the first stage is 80℃~120℃, and the absolute pressure is 1.8MPa~2.6MPa; the temperature of the liquid refrigerant in the second stage is 40℃~55℃, and the absolute pressure is 1.8MPa~2.6MPa; the temperature of the mist refrigerant in the third stage is -15℃~5℃, and the absolute pressure is 0.4MPa~0.8MPa; and the temperature of the gaseous refrigerant in the fourth stage is 5℃~20℃, and the absolute pressure is 0.4MPa~0.8MPa.

[0013] The condensation area is located inside the front heat exchange structure, and the evaporation area is located inside the rear heat exchange structure. The front heat exchange structure performs the function of a condenser, and the rear heat exchange structure performs the function of an evaporator. The front heat exchange structure and the rear heat exchange structure are centrally symmetrically distributed on both sides of the capillary flow control structure.

[0014] The specific steps of S4 are as follows: S4.1 Data acquisition, including: Multiple temperature sensors are used to collect real-time temperature change data of the refrigerant, the first fluid, and the second fluid during their transport within the aluminum plate-fin heat exchanger.

[0015] Multiple pressure sensors are used to acquire real-time pressure change data of refrigerant, first fluid, and second fluid during the transport process within the aluminum plate-fin heat exchanger.

[0016] Multiple fluid phase analyzers are used to monitor the phase changes of the refrigerant, the first fluid, and the second fluid in real time during the transport process within the aluminum plate-fin heat exchanger.

[0017] S4.2 Data Processing: The collected temperature change data, pressure change data, and phase change status are fed back to the control module. The control module preprocesses the received data, including filtering and calibration operations, to eliminate noise and errors in the data. Then, the data is analyzed through a specific algorithm model to extract the operating parameters of the phase change status of the refrigerant, the first fluid, and the second fluid during the transportation process in the aluminum plate-fin heat exchanger, and the parameters are displayed in real time on the display module.

[0018] S4.3, Internal flow channels of the capillary flow control structure: Based on the extracted operating parameters and a preset intelligent control algorithm, the control module generates control commands to adjust the capillary flow control structure. The capillary flow control structure then automatically adjusts the flow area of ​​its internal channels according to the control commands.

[0019] Preferably, the first fluid and the second fluid flow in the same direction and are arranged opposite to the flow direction of the refrigerant; the refrigerant's transport trajectory inside the aluminum plate-fin heat exchanger is zigzag.

[0020] The initial temperature of the first fluid is lower than the temperature of the heat exchange structure in front, causing the first fluid to absorb heat and be heated before being discharged.

[0021] The initial temperature of the second fluid is higher than that of the heat exchange structure behind it, causing the second fluid to absorb heat and cool down before being discharged.

[0022] This invention also provides a compact water source heat pump system. The compact water source heat pump system employs the aforementioned water source heat pump heat exchange method. The aluminum plate-fin heat exchanger device has alternating vertically stacked refrigerant channels and fluid channels, with adjacent refrigerant channels and fluid channels sharing a partition. The capillary flow control structure includes multiple capillary throttling devices, which are alternating vertically stacked with multiple partitions. The capillary throttling device located between two partitions divides the refrigerant channel into an independent first refrigerant channel and a second refrigerant channel. Similarly, the capillary throttling device located between two partitions divides the fluid channel into an independent first fluid channel and a second fluid channel.

[0023] All the input ends of the first fluid channels are connected to housing 1; all the output ends of the first fluid channels are connected to housing 2; all the input ends of the second fluid channels are connected to housing 8; all the output ends of the second fluid channels are connected to housing 9; all the input ends of the first refrigerant channels are connected to housing 3; all the output ends of the first refrigerant channels are connected to housing 4; all the input ends of the second refrigerant channels are connected to housing 6; all the output ends of the second refrigerant channels are connected to housing 7; all the input ends of the capillary throttles are connected to housing 4; and all the output ends of the capillary throttles are connected to housing 5.

[0024] The electronic expansion valve is located on the first connecting pipe between housing five and housing six.

[0025] The refrigerant compressor is located on the second connecting pipe between housing seven and housing three.

[0026] Preferably, heat exchange fins are provided in the first refrigerant channel, the second refrigerant channel, the first fluid channel, and the second fluid channel, and the multi-layer baffles and heat exchange fins are alternately stacked.

[0027] Preferably, the top ends of the first and second housings are respectively provided with a first fluid inlet pipe and a first fluid outlet pipe; the top ends of the eighth and ninth housings are respectively provided with a second fluid inlet pipe and a second fluid outlet pipe; the top ends of the third and fifth housings are respectively provided with a first refrigerant inlet pipe and a first refrigerant outlet pipe; and the top ends of the sixth and seventh housings are respectively provided with a second refrigerant inlet pipe and a second refrigerant outlet pipe. The first refrigerant outlet pipe and the second refrigerant inlet pipe are connected by a first connecting pipe, and the second refrigerant outlet pipe and the first refrigerant inlet pipe are connected by a second connecting pipe.

[0028] Preferably, a monitoring module is composed of a temperature sensor, a pressure sensor, and a fluid phase analyzer. The number of temperature sensors, pressure sensors, and fluid phase analyzers is set to nine, and the nine monitoring modules are installed one-to-one in the cavities of housing 1, housing 2, housing 3, housing 4, housing 5, housing 6, housing 7, housing 8, and housing 9.

[0029] Preferably, there is one and only one capillary throttle between each pair of adjacent partitions, and the flow channel of the capillary throttle is configured as a DC micro capillary through-hole, with both ends of the DC micro capillary through-hole penetrating the capillary throttle.

[0030] Preferably, a solenoid valve is provided inside the DC micro capillary through-hole, and a pump for pumping fluid is provided at the input end of both the first fluid input pipe and the second fluid input pipe, and a pump for pumping refrigerant is provided on both the first connecting pipe and the second connecting pipe.

[0031] The control module is electrically connected to the display module. The input and output terminals of the control module are equipped with an A / D converter and a D / A converter, respectively. Multiple monitoring modules are electrically connected to the A / D converter, and multiple pumps, electronic expansion valves, refrigerant compressors, and solenoid valves are electrically connected to the D / A converter.

[0032] The present invention has the following beneficial effects: By integrating the design of aluminum plate-fin heat exchangers and heat pump systems, the external dimensions and installation positions of each component are rationally planned to maximize the use of internal space and reduce the overall volume of the water source heat pump. This enables continuous and efficient transition of refrigerant states (temperature, pressure, phase), allowing for smoother state transitions during refrigerant functional conversion. It also reduces energy losses caused by improper component matching in traditional distributed systems, fully leveraging the high-efficiency heat transfer potential of the plate-fin structure throughout the entire process. This achieves efficient synergy and low-loss operation of the core refrigeration components and features a full-condition adaptive mechanism, ensuring that the water source heat pump maintains high heat exchange efficiency under various operating conditions, improving energy utilization efficiency, and enhancing the overall energy efficiency and reliability of the heat exchange system.

[0033] By optimizing the capillary flow control structure, the degree of throttling can be dynamically adjusted according to parameters such as refrigerant flow rate and pressure under different operating conditions, achieving more precise pressure reduction and throttling. This avoids problems such as poor throttling effect and reduced system efficiency that occur when the operating conditions change in traditional fixed throttling methods. The refrigerant and fluid can exchange heat efficiently in different channels, and the material and shape of the aluminum alloy heat-conducting plate increase the heat transfer area and agitate the fluid to enhance heat transfer.

[0034] By adopting a modular design concept, the water source heat pump system is divided into multiple functional modules. Each module can be produced and assembled independently, which facilitates transportation and on-site installation. At the installation site, the installation of the water source heat pump can be completed simply by connecting and debugging the various modules, which greatly improves installation efficiency and reduces equipment maintenance costs. Attached Figure Description

[0035] Figure 1 The system flowchart of the water source heat pump heat exchange method provided by the present invention is shown.

[0036] Figure 2 This is a schematic diagram of the overall structure of the compact water source heat pump system provided by the present invention.

[0037] Figure 3 This is a first-view perspective perspective view of the combined structure of the aluminum plate-fin heat exchanger and the transfer box in this invention.

[0038] Figure 4 This is a second-view perspective perspective view of the combined structure of the aluminum plate-fin heat exchanger and the transfer box in this invention.

[0039] Figure 5 This is a schematic diagram of the heat exchange fin distribution structure in this invention.

[0040] Figure 6 For the present invention Figure 5 Enlarged view of a local structure.

[0041] Figure 7 The schematic diagram of the working control principle of the compact water source heat pump system provided by the present invention.

[0042] In the diagram: Aluminum plate-fin heat exchanger - 1; Front edge seal - 101; Rear edge seal - 102; Side seal - 103; Refrigerant channel - 2; First refrigerant channel - 201; Second refrigerant channel - 202; Fluid channel - 3; First fluid channel - 301; Second fluid channel - 302; Baffle - 4; Capillary throttling device - 5; Heat exchange fins - 6; Box 1 - 7; Box 2 - 8; Box 3 - 9; Box 4 - 10; Box 5 - 11; Box 6 - 12; Box 7 - 13; Box 8 - 14; Box 9 - 15; First connecting pipe - 1 6; Second connecting pipe - 17; Monitoring module - 18; Temperature sensor - 181; Pressure sensor - 182; Fluid phase analyzer - 183; Control module - 19; Display module - 20; First fluid input pipe - 21; First fluid output pipe - 22; Second fluid input pipe - 23; Second fluid output pipe - 24; First refrigerant input pipe - 25; First refrigerant output pipe - 26; Second refrigerant input pipe - 27; Second refrigerant output pipe - 28; Pump - 29; Electronic expansion valve - 30; Refrigerant compressor - 31; Overflow channel - 32. Detailed Implementation

[0043] The present invention will now be described in further detail with reference to the accompanying drawings and specific preferred embodiments.

[0044] In the description of this invention, it should be understood that the terms "left side," "right side," "upper part," "lower part," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention 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. "First," "second," etc., do not indicate the importance of the components, and therefore should not be construed as a limitation of this invention. The specific dimensions used in this embodiment are only for illustrating the technical solution and do not limit the scope of protection of this invention.

[0045] like Figure 1 and Figure 2 As shown, a water source heat pump heat exchange method is applied to a compact water source heat pump system. The compact water source heat pump system includes an aluminum plate-fin heat exchanger 1, an electronic expansion valve 30, and a refrigerant compressor 31. A capillary flow control structure is provided inside the aluminum plate-fin heat exchanger 1. A front heat exchange structure and a rear heat exchange structure are respectively located on the front and rear sides of the capillary flow control structure, and the front and rear heat exchange structures are centrally symmetrically distributed on both sides of the capillary flow control structure. The front and rear heat exchange structures each have a condensation zone and an evaporation zone, and fluid channels are provided within both the condensation and evaporation zones. The method includes the following steps: S1, refrigerant circulation heat exchange, including: S1.1. First-stage gaseous refrigerant is introduced into the condensation zone. The temperature of the first-stage gaseous refrigerant (which is in a high-temperature, high-pressure state after being discharged from the refrigerant compressor 31) is 80℃~120℃ (slightly different for different refrigerants, such as R410A, which can reach 100℃~120℃), and the absolute pressure is 1.8MPa~2.6MPa. In the condensation zone, the first-stage gaseous refrigerant undergoes a liquefaction reaction, transforming into the second-stage liquid refrigerant. The temperature of the second-stage liquid refrigerant (which is in a medium-temperature, medium-pressure state after the liquefaction reaction) is 40℃~55℃ (close to the ambient temperature + condensing temperature difference), and the absolute pressure is 1.8MPa~2.6MPa (the condensing pressure is constant and consistent with the pressure of the high-temperature, high-pressure stage). Heat is released during the liquefaction reaction, achieving heat exchange with the front heat exchange structure. The front heat exchange structure performs the function of a condenser.

[0046] S1.2 The second-stage liquid refrigerant is output from the condensation area through the capillary flow control structure and sent to the electronic expansion valve 30. The capillary flow control structure, in conjunction with the electronic expansion valve 30, reduces the pressure and throttles the second-stage liquid refrigerant, transforming it into the third-stage mist refrigerant. The temperature of the third-stage mist refrigerant (which is in a low-temperature and low-pressure state after pressure reduction and throttling) is -15℃ to 5℃ (corresponding to the boiling point under evaporation pressure), and the absolute pressure is 0.4MPa to 0.8MPa.

[0047] S1.3. The third-stage mist refrigerant is introduced into the evaporation zone. In the evaporation zone, the third-stage mist refrigerant undergoes a vaporization reaction and its state changes to the fourth-stage gaseous refrigerant. The temperature of the fourth-stage gaseous refrigerant is 5℃~20℃ (slightly higher than the evaporation temperature, "superheated gas"), and the absolute pressure is 0.4MPa~0.8MPa (the evaporation pressure is constant and consistent with the pressure in the low-temperature and low-pressure stage).

[0048] Note: Specific values ​​may vary for different refrigerants (such as R22, R32, R410A).

[0049] The vaporization reaction absorbs heat, which is then exchanged with the subsequent heat exchange structure. The subsequent heat exchange structure functions as an evaporator.

[0050] S1.4. The fourth-stage gaseous refrigerant output from the evaporation zone is introduced into the refrigerant compressor 31. In the refrigerant compressor 31, the fourth-stage gaseous refrigerant is compressed and its state is transformed into the first-stage gaseous refrigerant, so that the first-stage gaseous refrigerant flows back to the condensation zone for heat exchange.

[0051] Specifically, when the compact water source heat pump system is working, the configuration of this structure is as follows: The pump 29 corresponding to the first refrigerant input pipe 25 is started, and the refrigerant is pumped from the third housing 9 into the first refrigerant channel 201. Then it is sent into the fifth housing 11 through the internal channels of the fourth housing 10 and the capillary throttle 5. It then passes through the first connecting pipe 16 and is processed by the electronic expansion valve 30 before entering the second refrigerant channel 202 from the sixth housing 12. After being delivered to the seventh housing 13, it flows back to the third housing 9 through the second connecting pipe 17. After being converted by the refrigerant compressor 31, it undergoes a heat exchange cycle.

[0052] S2. A first fluid is introduced into the first fluid channel 301 in front of the aluminum plate-fin heat exchanger 1, and the first fluid exchanges heat with the heat exchange structure in front.

[0053] Specifically, when the compact water source heat pump system is working, the configuration of this structure is as follows: The pump 29, connected to the first fluid inlet pipe 21 and the second fluid inlet pipe 23, is started to pump the first fluid from the first housing 7 into the first fluid channel 301. The first fluid indirectly contacts the first-stage gaseous refrigerant in the first refrigerant channel 201 for heat exchange. After absorbing heat, the first fluid heats up and then enters the second housing 8 and is discharged from the first fluid outlet pipe 22. For example, cold water enters and hot water exits.

[0054] S3. A second fluid is introduced into the second fluid channel 302 behind the aluminum plate-fin heat exchanger 1, and the second fluid exchanges heat with the heat exchange structure behind it.

[0055] Specifically, when the compact water source heat pump system is working, the configuration of this structure is as follows: The second fluid is pumped from housing 8 (14) into the second fluid channel 302. The second fluid exchanges heat with the third-stage mist refrigerant in the second refrigerant channel 202. After absorbing heat, the second fluid cools down and then enters housing 9 (15) and is discharged from the second fluid outlet pipe 24. For example, cold water enters and chilled water exits.

[0056] The first fluid and the second fluid flow in the same direction, but are set opposite to the flow direction of the refrigerant; the refrigerant’s transport trajectory inside the aluminum plate-fin heat exchanger 1 is zigzag.

[0057] The initial temperature of the first fluid is lower than the temperature of the heat exchange structure in front, causing the first fluid to absorb heat and be heated before being discharged.

[0058] The initial temperature of the second fluid is higher than that of the heat exchange structure behind it, causing the second fluid to absorb heat and cool down before being discharged.

[0059] S4. Monitor the operating parameters of the refrigerant, first fluid, and second fluid in the aluminum plate-fin heat exchanger 1, including their heat load, pressure, and phase state. Adjust the flow area of ​​the internal flow channel of the capillary flow control structure to control the heat exchange efficiency of the front and rear heat exchange structures.

[0060] The specific steps are as follows: S4.1 Data acquisition, including: Multiple temperature sensors 181 are used to collect real-time temperature change data of the refrigerant, the first fluid, and the second fluid during the transportation process within the aluminum plate-fin heat exchanger 1.

[0061] Multiple pressure sensors 182 are used to acquire real-time pressure change data of refrigerant, first fluid and second fluid during the transportation process in aluminum plate fin heat exchanger 1.

[0062] Multiple fluid phase analyzers 183 are used to monitor the phase changes of the refrigerant, the first fluid, and the second fluid in real time during the transport process within the aluminum plate-fin heat exchanger 1.

[0063] S4.2 Data Processing: The collected temperature change data, pressure change data, and phase change status are fed back to the control module 19. The control module 19 preprocesses the received data, including filtering and calibration operations, to eliminate noise and errors in the data. Then, it analyzes the data through a specific algorithm model to extract the operating parameters of the phase change status of the refrigerant, the first fluid, and the second fluid during the transportation process in the aluminum plate-fin heat exchanger 1, and displays them in real time on the display module 20.

[0064] S4.3, Internal flow channels of the capillary flow control structure: Based on the extracted operating parameters and a preset intelligent control algorithm, the control module 19 generates control commands for adjusting the capillary flow control structure, thereby controlling the capillary flow control structure to automatically adjust the flow area of ​​its internal channels according to the control commands.

[0065] Specifically, the larger the flow area of ​​the internal channels of the capillary-microflow control structure, the faster the refrigerant circulation speed. Correspondingly, the heat exchange efficiency between the first fluid and the preceding heat exchange structure, and between the second fluid and the following heat exchange structure, is higher. Under different ambient temperatures and heat load requirements, the refrigerant flow rate is precisely controlled by adaptively adjusting the flow area of ​​the internal channels of the capillary-microflow control structure. The refrigerant flow rate is adjusted in real time according to different operating conditions, ensuring that the system maintains optimal operating conditions under various circumstances. This not only improves the system's energy utilization efficiency and reduces energy consumption, but also enhances the system's stability and reliability, and reduces equipment maintenance costs. This system can automatically adjust its functions and operating modes under different seasons and environmental conditions, achieving adaptive operation under all operating conditions.

[0066] like Figures 2 to 6As shown, the present invention also provides a compact water source heat pump system. In this system, employing the aforementioned water source heat pump heat exchange method, the aluminum plate-fin heat exchanger 1 has vertically alternating refrigerant channels 2 and fluid channels 3. Adjacent refrigerant channels 2 and fluid channels 3 share a partition 4. The partition 4 serves to separate the channels and support the overall heat dissipation structure within the aluminum plate-fin heat exchanger 1. The capillary flow control structure includes multiple capillary throttling devices 5, which are vertically alternating with the partition 4. A capillary throttle 5 located between two partitions 4 divides the refrigerant channel 2 into two independent refrigerant channels 201 and 202. Similarly, a capillary throttle 5 located between two partitions 4 divides the fluid channel 3 into two independent fluid channels 301 and 302. The input ends of all first fluid channels 301 are connected to housing 1 7, and the output ends of all first fluid channels 301 are connected to housing 2 8. The input ends of all second fluid channels 302 are connected to housing 8 14, and the output ends of all second fluid channels 302 are connected to housing 9 15. The input ends of channel 201 are connected to housing 3 9; the output ends of all first refrigerant channels 201 are connected to housing 4 10; the input ends of all second refrigerant channels 202 are connected to housing 6 12; the output ends of all second refrigerant channels 202 are connected to housing 7 13; the input ends of all capillary throttles 5 are connected to housing 4 10; and the output ends of all capillary throttles 5 are connected to housing 5 11. The electronic expansion valve 30 is located on the first connecting pipe 16 between housing 5 11 and housing 6 12. The refrigerant compressor 31 is located on the second connecting pipe 17 between housing 7 13 and housing 3 9.

[0067] Boxes 1-7, 2-8, 3-9, 4-10, 5-11, 6-12, 7-13, 8-14, and 9-15 are all transshipment box structures.

[0068] The system, composed of the above-described structure, integrates the condenser, capillary tube, and evaporator into a compact plate-fin structure, shortening the length of refrigerant piping and optimizing heat loss and pressure reduction during refrigerant transmission. By rationally designing the dimensions and installation positions of each component, the internal space of the equipment is maximized, reducing the overall volume of the water source heat pump. It enables continuous and efficient transitions in refrigerant state (temperature, pressure, phase), such as allowing the condensed high-pressure liquid to directly pass through the capillary structure within the plate fins for throttling before entering adjacent evaporation zones, reducing energy loss during function switching. Simultaneously, the efficient heat transfer characteristics of the plate fins cover the entire process, improving overall heat exchange efficiency.

[0069] With its compact structural design and integrated heat exchange device, the water source heat pump is significantly smaller than traditional water source heat pumps, saving considerable installation space. This makes water source heat pumps more convenient to use in various space-constrained locations, such as small commercial buildings and apartments, thus expanding their application range.

[0070] Furthermore, in the above technical solution, heat exchange fins 6 are provided in the first refrigerant channel 201, the second refrigerant channel 202, the first fluid channel 301, and the second fluid channel 302, and the multi-layer partitions 4 are alternately stacked with the heat exchange fins 6. In the embodiment provided in this application, the outer sides of the first refrigerant channel 201, the second refrigerant channel 202, the first fluid channel 301, and the second fluid channel 302 are blocked by the front sealing strip 101, the rear sealing strip 102, the side sealing strip 103, and the capillary throttling device 5, so that the aluminum plate-fin heat exchange device 1 is formed into an integral structure by brazing. The partition 4 is set as a thin aluminum alloy plate, and the outer shells of the front sealing strip 101, the rear sealing strip 102, the side sealing strip 103, and the capillary throttling device 5 are all made of aluminum composite material. The heat exchange fins 6 include multiple aluminum alloy heat-conducting plates, and the multiple aluminum alloy heat-conducting plates are brazed with the front heat exchange structure and the rear heat exchange structure into an integral structure. The aluminum alloy heat-conducting plate adopts a one-piece stamped wave-shaped structure, with overflow channels 32 pre-reserved within the multiple aluminum alloy heat-conducting plates of the heat exchange fins 6 for the passage of refrigerant and fluid. An efficient channel structure is formed between adjacent partitions 4, allowing the refrigerant and fluid to exchange heat efficiently in different channels. Furthermore, the material and shape of the aluminum alloy heat-conducting plate increase the heat transfer area and agitate the fluid, enhancing heat transfer. Aluminum alloy has excellent thermal conductivity, effectively improving heat exchange efficiency. Simultaneously, the lightweight nature of aluminum alloy makes the entire heat exchange device more compact, reducing installation and transportation costs. Moreover, the highly corrosion-resistant aluminum alloy material has good corrosion resistance, adapting to different water qualities and environmental conditions, extending the service life of the equipment.

[0071] Furthermore, in the above technical solution, the top ends of housing 1 (7) and housing 2 (8) are respectively provided with a first fluid input pipe 21 and a first fluid output pipe 22; the top ends of housing 8 (14) and housing 9 (15) are respectively provided with a second fluid input pipe 23 and a second fluid output pipe 24; the top ends of housing 3 (9) and housing 5 (11) are respectively provided with a first refrigerant input pipe 25 and a first refrigerant output pipe 26; the top ends of housing 6 (12) and housing 7 (13) are respectively provided with a second refrigerant input pipe 27 and a second refrigerant output pipe 28; the first refrigerant output pipe 26 and the second refrigerant input pipe 27 are connected by a first connecting pipe 16; and the second refrigerant output pipe 28 and the first refrigerant input pipe 25 are connected by a second connecting pipe 17.

[0072] Furthermore, in the above technical solution, a monitoring module 18 is composed of one temperature sensor 181, one pressure sensor 182, and one fluid phase analyzer 183. The number of temperature sensors 181, pressure sensors 182, and fluid phase analyzers 183 is set to nine. These nine monitoring modules 18 are correspondingly installed in the cavities of enclosures 1-7, 2-8, 3-9, 4-10, 5-11, 6-12, 7-13, 8-14, and 9-15. The monitoring modules 18 can also diagnose faults in real time and provide early warnings, ensuring the safe operation of the system.

[0073] Furthermore, in the above technical solution, there is one and only one capillary throttle 5 between each pair of adjacent partitions 4. The flow channel of the capillary throttle 5 is configured as a DC micro capillary through-hole, and both ends of the DC micro capillary through-hole penetrate the capillary throttle 5. The DC micro capillary through-hole increases the contact area with the refrigerant and optimizes the flow channel resistance characteristics. Multiple capillary throttles 5 are stacked vertically to form an integrated capillary flow control structure. A leading edge seal 101, a trailing edge seal 102, and a side seal 103 are provided between two adjacent partitions 4. The leading edge seal 101 and the trailing edge seal 102 are located at the front and rear edges of the partition 4, respectively, and the side seals 103 are distributed on both sides of the partition 4. The vertical height of the leading edge seal 101, the trailing edge seal 102, the side seals 103, and the aluminum alloy heat-conducting plate is consistent and equal to the thickness of the capillary throttle 5.

[0074] like Figure 7 As shown, a solenoid valve is installed inside the DC micro capillary through-hole. Pumps 29 for pumping fluid are installed at the input ends of the first fluid input pipe 21 and the second fluid input pipe 23. Pumps 29 for pumping refrigerant are installed on the first connecting pipe 16 and the second connecting pipe 17. The connection end of the control module 19 is electrically connected to the display module. The input and output ends of the control module 19 are respectively equipped with an A / D converter and a D / A converter. Multiple monitoring modules 18 are electrically connected to the A / D converter. Multiple pumps 29, electronic expansion valves 30, refrigerant compressors 31 and solenoid valves are electrically connected to the D / A converter.

[0075] The circuits and controls involved in this invention are all existing technologies and will not be described in detail here.

[0076] This system incorporates a full-condition adaptive adjustment mechanism to achieve precise control of refrigerant flow. It adjusts the refrigerant flow in real time according to different operating conditions, ensuring the unit maintains optimal operation under various conditions (such as different ambient temperatures and different heat load requirements). This not only improves the system's energy efficiency and reduces energy consumption but also enhances system stability and reliability, reducing equipment maintenance costs.

[0077] This system adopts a modular design concept, dividing the water source heat pump system into multiple functional modules. Each module can be independently manufactured and assembled, facilitating transportation and on-site installation. At the installation site, the installation of the water source heat pump can be completed simply by connecting and debugging the various modules, greatly improving installation efficiency.

[0078] Specifically, the water source heat pump system is divided into multiple functional modules. Heat exchange fins 6, capillary throttling devices 5, leading edge seals 101, trailing edge seals 102, and side seals 103 are fabricated according to a modular design concept. Independent refrigerant channels 2 and fluid channels 3 are formed by brazing. Multiple refrigerant channels 2 and multiple fluid channels 3 are alternately stacked vertically to form an integrated aluminum plate-fin heat exchange device 1. This structure adopts a three-state integrated design, integrating the condenser, capillary tube, and evaporator into a compact structure, while also featuring an integrated capillary throttling control structure. Optimizing the capillary throttling control structure allows for dynamic adjustment of the throttling degree based on refrigerant flow rate, pressure, and other parameters under different operating conditions, achieving more precise pressure reduction and throttling, avoiding problems such as poor throttling effect and decreased system efficiency that occur with traditional fixed throttling methods when operating conditions change.

[0079] Through integrated design, the refrigerant's state transition during functional conversion is smoother, reducing energy loss caused by improper component matching in traditional distributed systems. This fully leverages the high-efficiency heat transfer potential of the plate-fin structure throughout the entire process, achieving efficient synergy and low-loss operation of the core refrigeration components. The overall structure of the water source heat pump is optimized, with key components such as the condenser, capillary tube, and evaporator integrated into a three-state, all-condition adaptive aluminum plate-fin heat exchanger arranged in a compact layout. The compressor and heat exchanger are placed adjacent to each other, shortening the length of refrigerant piping and reducing heat loss and pressure drop during refrigerant transmission. Simultaneously, by rationally designing the external dimensions and installation positions of each component, the internal space of the equipment is maximized, reducing the overall volume of the water source heat pump. This significant reduction in size compared to traditional water source heat pumps allows for easier application in various space-constrained locations, such as small commercial buildings and apartments, expanding the application range of water source heat pumps.

[0080] The highly efficient integrated capillary throttling control device enables precise control of refrigerant flow, adjusting it in real time according to different operating conditions to ensure optimal system performance under various circumstances. This improves energy efficiency, reduces energy consumption, enhances system stability and reliability, and reduces equipment maintenance costs. Compared to existing micro-throttling channels, this system offers more efficient throttling and higher energy utilization. It reduces ineffective pressure drop losses and improves system response speed and stability, effectively suppressing refrigerant pulsation and reducing energy dissipation, especially in high-vibration environments such as aerospace. Experimental verification shows that within a temperature range of -40℃ to 150℃, the throttling efficiency of this device is improved by more than 20%, further enhancing the overall energy efficiency and reliability of the heat exchange system.

[0081] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited to the described embodiments. For those skilled in the art, various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present invention, and these variations still fall within the protection scope of the present invention.

Claims

1. A water source heat pump heat exchange method, characterized in that: The method is applied to a compact water source heat pump system, which includes an aluminum plate-fin heat exchanger (1), an electronic expansion valve (30), and a refrigerant compressor (31). The aluminum plate-fin heat exchanger (1) has a capillary flow control structure on its inner side. A front heat exchange structure and a rear heat exchange structure are respectively provided on the front and rear sides of the capillary flow control structure. The front heat exchange structure and the rear heat exchange structure are respectively provided with a condensation area and an evaporation area. Fluid channels are provided in both the condensation area and the evaporation area. The method includes the following steps: S1, refrigerant circulation heat exchange, including: S1.

1. First-stage gaseous refrigerant is introduced into the condensation zone. In the condensation zone, the first-stage gaseous refrigerant undergoes a liquefaction reaction and its state changes to the second-stage liquid refrigerant. Heat is released during the liquefaction reaction, and heat exchange is achieved with the heat exchange structure in front. S1.2, The second stage liquid refrigerant is output from the capillary flow control structure to the condensation area and sent to the electronic expansion valve (30). The capillary flow control structure, together with the electronic expansion valve (30), reduces the pressure and throttles the refrigerant, so that the second stage liquid refrigerant is transformed into the third stage mist refrigerant. S1.

3. The third-stage mist refrigerant is introduced into the evaporation zone. In the evaporation zone, the third-stage mist refrigerant undergoes a vaporization reaction and its state changes to the fourth-stage gaseous refrigerant. During the vaporization reaction, heat is absorbed and heat is exchanged with the heat exchange structure behind it. S1.

4. The fourth stage gaseous refrigerant output from the evaporation zone is fed into the refrigerant compressor (31). In the refrigerant compressor (31), the fourth stage gaseous refrigerant is compressed and its state is changed to the first stage gaseous refrigerant, so that the first stage gaseous refrigerant flows back to the condensation zone for heat exchange. S2. The first fluid is introduced into the fluid channel in front of the aluminum plate fin heat exchanger (1), and the first fluid exchanges heat with the heat exchange structure in front. S3. A second fluid is introduced into the fluid channel behind the aluminum plate fin heat exchanger (1), and the second fluid exchanges heat with the heat exchange structure behind it. S4. Monitor the operating parameters of the heat load, pressure and phase state of the internal refrigerant, first fluid and second fluid in the aluminum plate fin heat exchanger (1), adjust the flow area of ​​the internal flow channel of the capillary flow control structure, and control the heat exchange efficiency of the front heat exchange structure and the rear heat exchange structure.

2. The water source heat pump heat exchange method according to claim 1, characterized in that: In S1, the temperature and absolute pressure parameters for the refrigerant's state transition process are as follows: The temperature of the gaseous refrigerant in the first stage is 80℃~120℃, and the absolute pressure is 1.8MPa~2.6MPa; The temperature of the liquid refrigerant in the second stage is 40℃~55℃, and the absolute pressure is 1.8MPa~2.6MPa; The temperature of the third-stage mist refrigerant is -15℃ to 5℃, and the absolute pressure is 0.4MPa to 0.8MPa. The temperature of the gaseous refrigerant in the fourth stage is 5℃~20℃, and the absolute pressure is 0.4MPa~0.8MPa.

3. The water source heat pump heat exchange method according to claim 2, characterized in that: The specific steps for S4 are as follows: S4.1 Data acquisition, including: Multiple temperature sensors (181) are used to collect real-time temperature change data of refrigerant, first fluid and second fluid during the transportation process in aluminum plate fin heat exchanger (1); Multiple pressure sensors (182) are used to acquire real-time pressure change data of refrigerant, first fluid and second fluid during the transportation process in aluminum plate fin heat exchanger (1); Multiple fluid phase analyzers (183) were used to monitor the phase changes of the refrigerant, the first fluid and the second fluid in real time during the transport process in the aluminum plate-fin heat exchanger (1); S4.2 Data Processing: The collected temperature change data, pressure change data and phase change status are fed back to the control module (19). The control module (19) preprocesses the received data, including filtering and calibration operations, to eliminate noise and errors in the data. Then, the data is analyzed through a specific algorithm model to extract the working condition parameters of the phase change status of the refrigerant, the first fluid and the second fluid during the transportation process in the aluminum plate fin heat exchanger (1), and the parameters are displayed in real time on the display module (20). S4.3, Internal flow channels of the capillary flow control structure: The control module (19) generates control instructions for adjusting the capillary flow control structure based on the extracted operating parameters and the preset intelligent control algorithm. The control module (19) automatically adjusts the flow area of ​​its internal flow channel according to the control instructions.

4. The water source heat pump heat exchange method according to claim 3, characterized in that: The first fluid and the second fluid flow in the same direction and are set opposite to the flow direction of the refrigerant; the refrigerant’s transport trajectory inside the aluminum plate-fin heat exchanger (1) is Z-shaped. The initial temperature of the first fluid is lower than the temperature of the heat exchange structure in front, causing the first fluid to absorb heat and be heated before being discharged. The initial temperature of the second fluid is higher than that of the heat exchange structure behind it, causing the second fluid to absorb heat and cool down before being discharged.

5. A compact water source heat pump system, employing the water source heat pump heat exchange method as described in claim 4, characterized in that: The aluminum plate fin heat exchanger (1) is provided with alternating refrigerant channels (2) and fluid channels (3) in the vertical direction. Adjacent refrigerant channels (2) and fluid channels (3) share a partition (4). The front heat exchange structure performs the function of a condenser, and the rear heat exchange structure performs the function of an evaporator. The front heat exchange structure and the rear heat exchange structure are centrally symmetrically distributed on both sides of the capillary flow control structure. The capillary flow control structure includes multiple capillary throttling devices (5), and the multiple capillary throttling devices (5) are alternately superimposed with multiple baffles (4) in the vertical direction. The capillary throttling device (5) located between two baffles (4) divides the refrigerant channel (2) into a first refrigerant channel (201) and a second refrigerant channel (202) that are independent of each other. The capillary throttling device (5) located between two baffles (4) divides the fluid channel (3) into a first fluid channel (301) and a second fluid channel (302) that are independent of each other. The input ends of all first fluid channels (301) are connected to housing 1 (7), the output ends of all first fluid channels (301) are connected to housing 2 (8), the input ends of all second fluid channels (302) are connected to housing 8 (14), the output ends of all second fluid channels (302) are connected to housing 9 (15), the input ends of all first refrigerant channels (201) are connected to housing 3 (9), the output ends of all first refrigerant channels (201) are connected to housing 4 (10), the input ends of all second refrigerant channels (202) are connected to housing 6 (12), the output ends of all second refrigerant channels (202) are connected to housing 7 (13), the input ends of all capillary throttles (5) are connected to housing 4 (10), and the output ends of all capillary throttles (5) are connected to housing 5 (11). The electronic expansion valve (30) is located on the first connecting pipe (16) between housing five (11) and housing six (12); The refrigerant compressor (31) is located on the second connecting pipe (17) between housing seven (13) and housing three (9).

6. The compact water source heat pump system according to claim 5, characterized in that: Heat exchange fins (6) are provided in the first refrigerant channel (201), the second refrigerant channel (202), the first fluid channel (301), and the second fluid channel (302), and the multi-layer baffle (4) and the heat exchange fins (6) are alternately stacked.

7. The compact water source heat pump system according to claim 5, characterized in that: The top of the first box (7) and the second box (8) are respectively provided with a first fluid input pipe (21) and a first fluid output pipe (22). The top of the eighth box (14) and the ninth box (15) are respectively provided with a second fluid input pipe (23) and a second fluid output pipe (24). The top of the third box (9) and the fifth box (11) are respectively provided with a first refrigerant input pipe (25) and a first refrigerant output pipe (26). The top of the sixth box (12) and the seventh box (13) are respectively provided with a second refrigerant input pipe (27) and a second refrigerant output pipe (28). The first refrigerant output pipe (26) and the second refrigerant input pipe (27) are connected by a first connecting pipe (16). The second refrigerant output pipe (28) and the first refrigerant input pipe (25) are connected by a second connecting pipe (17).

8. The compact water source heat pump system according to claim 5, characterized in that: A temperature sensor (181), a pressure sensor (182), and a fluid phase analyzer (183) are used as monitoring modules (18). The number of temperature sensors (181), pressure sensors (182), and fluid phase analyzers (183) is set to nine. The nine monitoring modules (18) are installed one-to-one in the inner cavities of the first (7), second (8), third (9), fourth (10), fifth (11), sixth (12), seventh (13), eighth (14), and ninth (15) boxes.

9. The compact water source heat pump system according to claim 8, characterized in that: There is one and only one capillary throttle (5) between each pair of adjacent partitions (4). The flow channel of the capillary throttle (5) is configured as a DC micro capillary through hole, and the two ends of the DC micro capillary through hole pass through the capillary throttle (5).

10. The compact water source heat pump system according to claim 9, characterized in that: The DC micro capillary through-hole is equipped with a solenoid valve. The input ends of the first fluid input pipe (21) and the second fluid input pipe (23) are both equipped with pumps (29) for pumping fluid. The first connecting pipe (16) and the second connecting pipe (17) are both equipped with pumps (29) for pumping refrigerant. The connection end of the control module (19) is electrically connected to the display module. The input and output ends of the control module (19) are respectively equipped with an A / D converter and a D / A converter. Multiple monitoring modules (18) are electrically connected to the A / D converter. Multiple pumps (29), electronic expansion valves (30), refrigerant compressors (31) and solenoid valves are electrically connected to the D / A converter.

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