Refrigeration cycle system capable of realizing low humidity

Abstract

The utility model discloses a refrigeration cycle system can realize low humidity, include: compressor compressor, condenser, liquid storage tank, drying filter, first solenoid valve, second solenoid valve, third solenoid valve, first expansion valve, first liquid mirror, second expansion valve, second liquid mirror, dehumidification heat exchange unit, first heat exchange module, second heat exchange module, pressure regulating valve and oil separator. The utility model relates to refrigeration technical field, specifically provide a kind of for solving the problem that dehumidification process is accompanied by significant temperature fluctuation, and dehumidification efficiency is low and cannot realize low humidity environment.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration technology, specifically to a refrigeration cycle system that can achieve low humidity. Background Technology

[0002] In the field of plant cultivation, plant incubators need to provide precise temperature and humidity environments for different types of plants and different developmental stages of the same plant. The temperature needs to be stable within a specific optimal growth range, and the humidity needs to be precisely controlled according to the physiological needs of the plant.

[0003] In existing technologies, temperature control in plant cultivation boxes can be precisely adjusted, but humidity control still has significant shortcomings. The core problem lies in the traditional evaporator dehumidification technology used in the dehumidification process, specifically in the following two aspects:

[0004] 1. In existing technologies, when dehumidifying via an evaporator, the evaporator's operating temperature must be lower than the temperature under conventional refrigeration conditions to achieve water vapor condensation. This low temperature can cause the temperature inside the incubator to drop below the set value, resulting in temperature fluctuations. Plant growth requires extremely high temperature stability, and temperature fluctuations can easily trigger physiological disorders in plants, such as poor root development and yellowing leaves, severely affecting the cultivation effect.

[0005] 2. In existing evaporator dehumidification technologies, a water film easily forms between the evaporator fins due to the surface tension of condensate, and this water film cannot detach on its own. This water film significantly reduces the heat exchange efficiency of the evaporator, leading to a decrease in dehumidification capacity. It can only handle high humidity air with a relative humidity above 50%. When the air humidity is below 50%, the dehumidification effect drops significantly, failing to meet the needs of some plants (such as drought-tolerant flowers and succulents) for low humidity environments below 40%. Furthermore, high humidity environments easily breed mold, causing plant diseases. Utility Model Content

[0006] The technical problem to be solved by this invention is to address the issues of significant temperature fluctuations during the dehumidification process and the inability to achieve a low-humidity environment due to low dehumidification efficiency.

[0007] To solve the above-mentioned technical problems, this utility model provides the following technical solution:

[0008] This utility model proposes a refrigeration cycle system capable of achieving low humidity, comprising:

[0009] A compressor is used to compress refrigerant into high-temperature, high-pressure gas.

[0010] The condenser, connected to the outlet of the compressor, is used to condense the high-temperature, high-pressure gaseous refrigerant into a high-temperature, high-pressure liquid refrigerant and release heat to the outside through a condenser fan;

[0011] A liquid storage tank, connected to the outlet of the condenser, is used to store subcooled liquid refrigerant;

[0012] A dryer filter, connected to the outlet of the liquid storage tank, is used to remove impurities and moisture from the refrigerant;

[0013] The valve control unit includes a first solenoid valve, a second solenoid valve, and a third solenoid valve. The inlets of the first and second solenoid valves are connected to the outlet of the dryer filter, and the inlet of the third solenoid valve is connected to the outlet of the compressor.

[0014] The first throttling unit includes a first expansion valve and a first sight glass, wherein the inlet of the first sight glass is connected to the outlet of the first solenoid valve, and the inlet of the first expansion valve is connected to the outlet of the first sight glass.

[0015] The second throttling unit includes a second expansion valve and a second sight glass. The inlet of the second sight glass is connected to the outlet of the second solenoid valve, and the inlet of the second expansion valve is connected to the outlet of the second sight glass.

[0016] The dehumidification and heat exchange unit includes a first heat exchange module for realizing a cooling function and a second heat exchange module for realizing a low humidity dehumidification function. The inlet of the first heat exchange module is connected to the outlet of the first expansion valve, and the inlet of the second heat exchange module is connected to the outlet of the second expansion valve.

[0017] The pressure regulating valve has its inlet connected to the outlet of the first heat exchange module, the outlet of the second heat exchange module, and the outlet of the third solenoid valve, respectively, and its outlet connected to the inlet of the compressor. It is used to regulate the system return gas pressure and prevent damage to the compressor.

[0018] Preferably, an oil separator is provided between the outlet of the pressure regulating valve and the inlet of the compressor to separate the lubricating oil carried in the refrigerant gas and send it back to the compressor.

[0019] Preferably, the first heat exchange module is a finned copper tube assembly, used to increase the heat exchange area through the fins to achieve cooling of the air inside the chamber; the second heat exchange module is a six-finless exposed copper tube assembly, used to condense water vapor in the air through the low temperature of the copper tube surface, reducing the relative humidity of the air inside the chamber to below 40%; in addition, the second heat exchange module is correspondingly provided with a drainage unit, used to collect and drain the condensate formed on the surface of the second heat exchange module. The condensate falls off naturally under the action of gravity and is discharged from the chamber by the drainage system. The drainage unit is preferably a PVC drainage pipe.

[0020] Preferably, the six exposed copper tubes in the second heat exchange module are arranged in two rows, with the upper row close to the first heat exchange module and containing two copper tubes, and the lower row containing four copper tubes. Of the four copper tubes in the lower row, two correspond vertically to the two copper tubes in the upper row to form a core heat exchange area to cope with the high wind speed in the center of the air duct. The other two are symmetrically distributed on both sides of the core heat exchange area to dehumidify both sides of the airflow.

[0021] Preferably, the first heat exchange module and the second heat exchange module are integrated in the same evaporator housing, and the evaporator housing is provided with a refrigerant flow interface, which includes:

[0022] The refrigerant inlet and outlet for refrigeration mode corresponding to the first heat exchange module, and the refrigerant inlet and outlet for dehumidification mode corresponding to the second heat exchange module.

[0023] Preferably, in the refrigeration mode, one end of the refrigerant inlet is connected to the outlet of the first expansion valve of the first throttling unit, and the other end is connected to the refrigerant input end of the first heat exchange module; in the refrigeration mode, one end of the refrigerant outlet is connected to the refrigerant output end of the first heat exchange module, and the other end is connected to the inlet of the pressure regulating valve; in the dehumidification mode, one end of the refrigerant inlet is connected to the outlet of the second expansion valve of the second throttling unit, and the other end is connected to the refrigerant input end of the second heat exchange module; in the dehumidification mode, one end of the refrigerant outlet is connected to the refrigerant output end of the second heat exchange module, and the other end is connected to the inlet of the pressure regulating valve.

[0024] Preferably, the condenser is a tube-fin condenser, the liquid storage tank is a horizontal liquid storage tank, and the dryer filter is a dryer filter with a filter screen.

[0025] The present invention proposes a refrigeration cycle system capable of achieving low humidity. The beneficial effects achieved by adopting the above structure are as follows:

[0026] 1. The cooling and deep dehumidification functions are assigned to two independent heat exchange modules. By switching the operating conditions of the valve control unit, the dehumidification operation no longer affects the main refrigeration circuit, thus solving the temperature fluctuation problem caused by dehumidification in traditional systems.

[0027] 2. By using a finless exposed copper tube structure and optimizing the copper tube arrangement, the problems of low dehumidification efficiency and inability to achieve low humidity are solved. The problem of condensation forming a water film and affecting heat exchange is completely avoided. The heat exchange efficiency remains high, thus enabling the air humidity to be stably reduced to below 40% RH, meeting the higher standard of low humidity requirements.

[0028] 3. At the same time, by integrating the second heat exchange module with the first heat exchange module in the same housing, the integrated design ensures that the system size is compatible with traditional equipment. It has the advantages of low cost, easy implementation and strong adaptability, which can effectively improve the temperature and humidity control accuracy of the plant incubator and provide a stable and suitable environment for plant growth.

[0029] 4. The system is equipped with a pressure regulating valve and an oil separator, which effectively protects the compressor and ensures the stability and reliability of the system in long-term operation. Attached Figure Description

[0030] The accompanying drawings are provided to further illustrate the present invention and form part of the specification. They are used together with the embodiments of the present invention to explain the present invention, but do not constitute a limitation thereof. In the drawings:

[0031] Figure 1 This is a schematic diagram of the overall composition of a refrigeration cycle system that can achieve low humidity according to this application;

[0032] Figure 2 This is a schematic diagram of the dehumidification and heat exchange unit in this application. Figure 1 ;

[0033] Figure 3 This is a schematic diagram of the dehumidification and heat exchange unit in this application. Figure 2 ;

[0034] Figure 4 for Figure 2 The right view;

[0035] Among them, 1. Compressor, 2. Condenser, 3. Liquid storage tank, 4. Dryer filter, 5. First solenoid valve, 6. Second solenoid valve, 7. Third solenoid valve, 8. First expansion valve, 9. First sight glass, 10. Second expansion valve, 11. Second sight glass, 12. Dehumidification heat exchange unit, 13. First heat exchange module, 14. Second heat exchange module, 15. Pressure regulating valve, 16. Oil separator;

[0036] 17. Evaporator shell; 18. Refrigerant inlet for refrigeration mode; 19. Refrigerant outlet for refrigeration mode; 20. Refrigerant inlet for dehumidification mode; 21. Refrigerant outlet for dehumidification mode. Detailed Implementation

[0037] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present utility model. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the protection scope of the present utility model.

[0038] It should be noted that the terms “front,” “back,” “left,” “right,” “up,” and “down” used in the following description refer to the directions shown in the attached diagram, while the terms “inside” and “outside” refer to the directions toward or away from the geometric center of a specific component, respectively.

[0039] Example 1

[0040] like Figure 1 As shown, this embodiment provides a refrigeration cycle system capable of achieving low humidity, mainly including a compressor 1, a condenser 2, a liquid receiver 3, a dryer filter 4, a first solenoid valve 5, a second solenoid valve 6, a third solenoid valve 7, a first throttling unit composed of a first sight glass 9 and a first expansion valve 8, a second throttling unit composed of a second sight glass 11 and a second expansion valve 10, a dehumidification heat exchange unit 12, and a pressure regulating valve. An oil separator 16 is provided between the outlet of the pressure regulating valve and the inlet of the compressor 1.

[0041] The structure of the dehumidification and heat exchange unit 12 is as follows: Figures 2 to 4 As shown, it includes an integrated housing. The upper part of the housing contains a first heat exchange module 13, which consists of finned copper tubes and is used for cooling. The lower part of the housing contains a second heat exchange module 14, which consists of six finless exposed copper tubes and is specifically used for dehumidification.

[0042] like Figure 3 As shown, the six copper pipes are arranged in two rows: two pipes are placed in the upper row near the first heat exchange module 13, and four pipes are placed in the lower row. Of the four pipes in the lower row, the middle two are roughly aligned vertically with the two in the upper row, forming a dense core heat exchange area to handle the higher wind speed at the center of the duct. The remaining two pipes are symmetrically distributed on both sides of this core area to dehumidify the airflow on both sides. Furthermore, because the wind speed in the middle is slightly higher than on the left and right sides, the humidity reduction when air passes through the middle section is slightly less than on the left and right sides. Therefore, two copper pipes are placed in the middle to ensure that the humidity of the air passing through the middle section can also be reduced to a certain level.

[0043] Example 2

[0044] Based on Embodiment 1, this embodiment provides a structural composition of a dehumidification heat exchange unit 12, which includes a first heat exchange module 13 and a second heat exchange module 14 integrated in the same evaporator housing 17. The evaporator housing is provided with four refrigerant flow ports, including:

[0045] The first heat exchange module 13 has a refrigerant inlet 18 and a refrigerant outlet 19 for refrigeration mode, and the second heat exchange module 14 has a refrigerant inlet 20 and a refrigerant outlet 21 for dehumidification mode.

[0046] Furthermore, one end of the refrigerant inlet 18 in the refrigeration mode is connected to the outlet of the first expansion valve 8 of the first throttling unit, and the other end is connected to the refrigerant input end of the first heat exchange module 13; one end of the refrigerant outlet 19 in the refrigeration mode is connected to the refrigerant output end of the first heat exchange module 13, and the other end is connected to the inlet of the pressure regulating valve; one end of the refrigerant inlet 20 in the dehumidification mode is connected to the outlet of the second expansion valve 10 of the second throttling unit, and the other end is connected to the refrigerant input end of the second heat exchange module 14; one end of the refrigerant outlet 21 in the dehumidification mode is connected to the refrigerant output end of the second heat exchange module 14, and the other end is connected to the inlet of the pressure regulating valve.

[0047] The system operates in the following modes:

[0048] When the set temperature is lower than the internal temperature, heat needs to be removed from the cabinet. In this case, the cooling mode should be activated.

[0049] The first solenoid valve 5 is open, while the second solenoid valve 6 and the third solenoid valve 7 are closed. The refrigerant circulates along the path of compressor 1 → condenser 2 → liquid receiver 3 → dryer filter 4 → first solenoid valve 5 → first sight glass 9 → first expansion valve 8 → refrigerant inlet 18 for refrigeration mode → first heat exchange module 13 → refrigerant outlet 19 for refrigeration mode → pressure regulating valve 13 → oil separator 14 → compressor 1. Specifically, compressor 1 compresses the refrigerant into a high-temperature, high-pressure gas. When it flows through condenser 2, it condenses into a high-temperature, high-pressure liquid. At the same time, it releases heat to the outside through the condenser fan. Then it is cooled into a subcooled liquid refrigerant. After passing through liquid receiver 3, dryer filter 4, first solenoid valve 5, and first sight glass 9, it is adiabatically throttled in the first expansion valve 8 to become a low-pressure liquid refrigerant. It evaporates into a low-temperature gas in the evaporator (first heat exchange module 13), absorbing heat from the outside. Through air circulation, it exchanges heat with the gas inside the chamber, thereby achieving the purpose of cooling. The low-pressure refrigerant that flows out is drawn into the compressor 1 through the pressure regulating valve 15, and the cycle continues to work, thereby achieving cooling inside the box.

[0050] Further, refer to Figure 2 and Figure 4As shown, when the system needs to operate in cooling mode, the refrigerant enters the cooling refrigerant inlet 18 controlled by a solenoid valve. After passing through the evaporator, it exchanges heat with the outside environment through the fins. The fins expand the contact area with the outside environment, and the fan further improves the heat exchange efficiency. Finally, it flows out from the cooling refrigerant outlet 19 and returns to the compressor. When the system needs to operate in dehumidification mode, the refrigerant enters the dehumidification refrigerant inlet 20 controlled by a solenoid valve. After contacting the outside air, the fan power is reduced, and the airflow speed is decreased. In this case, the contact time between the air and the copper pipes is longer, allowing for sufficient heat exchange. Because there are no fins, the surface temperature of the copper pipes is lower, much lower than the dew point temperature of the air. Water vapor in the air condenses on the copper pipes, and the condensate does not form a water film that affects the heat exchange efficiency. Finally, the refrigerant flows out from the outlet 2 and returns to the compressor, while the condensate is discharged from the system through pipes. Under this dehumidification condition, because the contact area between the air and the copper pipe is small and the wind speed is low during the dehumidification process, the air can be dehumidified to the maximum extent while having little impact on the system temperature.

[0051] When the temperature reaches the set value, the first solenoid valve 5 and the second solenoid valve 6 close, while the third solenoid valve 7 opens. At this time, the high-pressure gas flowing out of the compressor 1 flows directly to the heat exchanger, where it undergoes condensation. Then, it flows back to the compressor 1 through the pressure regulating valve 15, which prevents excessive return pressure from damaging the compressor's internal components. Afterward, the second solenoid valve 6 closes, and the first solenoid valve 5 and the third solenoid valve 7 open alternately. The evaporation and condensation of the refrigerant in the evaporator alternate, providing heat counterbalancing within the evaporator and maintaining a stable temperature.

[0052] When dehumidification is required, the second solenoid valve 6 opens, while the first solenoid valve 5 and the third solenoid valve 7 close. The refrigerant circulates through the following path: compressor 1 → condenser 2 → receiver 3 → dryer filter 4 → second solenoid valve 6 → second sight glass 11 → second expansion valve 10 → refrigerant inlet 20 for dehumidification → second heat exchange module 14 → refrigerant outlet 21 for dehumidification → pressure regulating valve 13 → oil separator 14 → compressor 1. The dehumidification module (second heat exchange module 14) consists of six bare copper tubes without fins. The refrigerant evaporates in the copper tubes, absorbing most of the heat. The surface temperature is much lower than the dew point temperature of the air, causing water vapor in the air to condense on the copper tubes. Because there are no fins, the condensate does not form a water film, thus reducing the humidity to below 40%. The condensate falls off naturally under gravity, and a drainage system drains the water out of the chamber. Because the copper tubes are not surrounded by fins, the heat exchange area is greatly reduced, and it does not affect the internal temperature during the initial process.

[0053] The surface temperature of the second heat exchange module 14 is extremely low, causing water vapor in the air to quickly condense into water droplets and drip down, which are then discharged through the drain pipe below (not shown in the figure), achieving deep dehumidification with minimal impact on the internal temperature. Under this dehumidification condition, due to the small contact area between the air and the copper pipe and the low air velocity during dehumidification, the air can be dehumidified to the maximum extent while having a minimal impact on the system temperature.

[0054] Insulation / Oil Return Mode: The third solenoid valve 7 is open, while the first solenoid valve 5 and the second solenoid valve 6 are closed. High-temperature, high-pressure refrigerant flows directly from compressor 1 through the third solenoid valve 7 to pressure regulating valve 13, and then returns to compressor 1. This mode is used to maintain system pressure when cooling is not required, preventing frequent compressor starts and stops or poor oil return.

[0055] It should be noted that, in this document, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, material, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, material, or apparatus.

[0056] Unless otherwise expressly specified and limited, the terms "set up," "install," "connect," and "link" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0057] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A refrigeration cycle system capable of achieving low humidity, characterized by, include: Compressor (1), used to compress refrigerant into high-temperature and high-pressure gas; The condenser (2) is connected to the outlet of the compressor (1) and is used to condense the high-temperature and high-pressure gaseous refrigerant into a high-temperature and high-pressure liquid refrigerant and release heat to the outside through the condenser fan; A liquid storage tank (3) is connected to the outlet of the condenser (2) and is used to store subcooled liquid refrigerant; A dryer filter (4) is connected to the outlet of the liquid storage tank (3) and is used to remove impurities and moisture from the refrigerant; The valve control unit includes a first solenoid valve (5), a second solenoid valve (6) and a third solenoid valve (7). The inlets of the first solenoid valve (5) and the second solenoid valve (6) are connected to the outlet of the dryer filter (4), and the inlet of the third solenoid valve (7) is connected to the outlet of the compressor (1). The first throttling unit includes a first expansion valve (8) and a first sight glass (9). The inlet of the first sight glass (9) is connected to the outlet of the first solenoid valve (5), and the inlet of the first expansion valve (8) is connected to the outlet of the first sight glass (9). The second throttling unit includes a second expansion valve (10) and a second sight glass (11). The inlet of the second sight glass (11) is connected to the outlet of the second solenoid valve (6), and the inlet of the second expansion valve (10) is connected to the outlet of the second sight glass (11). The dehumidification heat exchange unit (12) includes a first heat exchange module (13) for realizing the cooling function and a second heat exchange module (14) for realizing the low humidity dehumidification function. The inlet of the first heat exchange module (13) is connected to the outlet of the first expansion valve (8), and the inlet of the second heat exchange module (14) is connected to the outlet of the second expansion valve (10). The pressure regulating valve (15) has its inlet connected to the outlet of the first heat exchange module (13), the outlet of the second heat exchange module (14), and the outlet of the third solenoid valve (7), respectively, and its outlet connected to the inlet of the compressor (1). It is used to regulate the return gas pressure of the system and prevent the compressor (1) from being damaged.

2. The refrigeration cycle system capable of achieving low humidity according to claim 1, characterized in that: An oil separator (16) is also provided between the outlet of the pressure regulating valve (15) and the inlet of the compressor (1) for separating the lubricating oil carried in the refrigerant gas and sending it back to the compressor (1).

3. A refrigeration cycle system capable of achieving low humidity according to claim 2, characterized in that: The first heat exchange module (13) is a finned copper tube assembly, which is used to increase the heat exchange area through fins and achieve cooling of the air inside the box; the second heat exchange module (14) is a six-finless exposed copper tube assembly, which is used to condense water vapor in the air through the low temperature of the copper tube surface and reduce the relative humidity of the air inside the box.

4. A refrigeration cycle system capable of achieving low humidity according to claim 3, characterized in that: The arrangement of the six exposed copper tubes in the second heat exchange module (14) is as follows: they are divided into two rows, with the upper row close to the first heat exchange module (13), and two copper tubes are set in the upper row and four copper tubes are set in the lower row. Among the four copper tubes in the lower row, two of them correspond to the two copper tubes in the upper row in the vertical direction to form the core heat exchange area, and the other two are symmetrically distributed on both sides of the core heat exchange area.

5. A refrigeration cycle system capable of achieving low humidity according to claim 4, characterized in that: The first heat exchange module (13) and the second heat exchange module (14) are integrated in the same evaporator housing (17), and the evaporator housing (17) is provided with a refrigerant flow interface, which includes: The refrigerant inlet (18) and refrigerant outlet (19) for refrigeration mode corresponding to the first heat exchange module (13), and the refrigerant inlet (20) and refrigerant outlet (21) for dehumidification mode corresponding to the second heat exchange module (14).

6. The low humidity achievable refrigeration cycle system according to claim 5, wherein: The refrigerant inlet (18) in the refrigeration mode is connected at one end to the outlet of the first expansion valve (8) of the first throttling unit and at the other end to the refrigerant input end of the first heat exchange module (13); the refrigerant outlet (19) in the refrigeration mode is connected at one end to the refrigerant output end of the first heat exchange module (13) and at the other end to the inlet of the pressure regulating valve (15); the refrigerant inlet (20) in the dehumidification mode is connected at one end to the outlet of the second expansion valve (10) of the second throttling unit and at the other end to the refrigerant input end of the second heat exchange module (14); the refrigerant outlet (21) in the dehumidification mode is connected at one end to the refrigerant output end of the second heat exchange module (14) and at the other end to the inlet of the pressure regulating valve (15).

7. A refrigeration cycle system capable of achieving low humidity according to claim 1, characterized in that: The condenser (2) is a tube-fin condenser, the liquid storage tank (3) is a horizontal liquid storage tank, and the dryer filter (4) is a dryer filter with a filter screen.

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