Four-season all fresh air dehumidifier based on variable frequency heat pump

Abstract

The utility model discloses a four-season all fresh air dehumidifier based on a variable frequency heat pump, and relates to the field of four-season all fresh air dehumidifiers. The system comprises a first direct-current inverter compressor, a first high-pressure gauge, an oil separator, a four-way valve and a first fin heat exchanger, and is provided with the first direct-current inverter compressor, the first high-pressure gauge, the oil separator, the four-way valve, the first fin heat exchanger, a condensation fan, a first one-way valve, a first liquid storage device and a first stop valve. Wherein the first direct-current inverter compressor is combined with the high-low voltage controller to dynamically adjust the operation frequency and start and stop of the parallel unit, and the seasonal energy efficiency ratio is remarkably increased; the first plate type energy saver is linked with the subcooler, the refrigerating capacity and the heating capacity are synchronously improved through a refrigerant subcooling technology, and the system energy efficiency is optimized; through the synergistic effect of the structures, the technical problems that traditional equipment is serious in condensation heat waste, limited in temperature control range and low in low-temperature dehumidification efficiency are effectively solved.

Description

Technical Field

[0001] This utility model relates to the field of all-season fresh air dehumidifiers, specifically an all-season fresh air dehumidifier based on a variable frequency heat pump. Background Technology

[0002] A fresh air dehumidifier is an advanced air handling device that integrates fresh air introduction, air filtration, and humidity regulation. It can effectively improve indoor air quality and create a healthy and comfortable living or working environment for users.

[0003] Currently, traditional heat pump dehumidifiers primarily dehumidify by lowering the air dew point through a refrigeration cycle. In winter, they dehumidify by heating the fresh air. However, when using condensation heat recovery and reheating in high-humidity summer environments, traditional equipment is limited by fixed-frequency compressors and lacks precise condensation heat control devices. It cannot dynamically adjust the condensation heat ratio based on real-time humidity. Therefore, traditional systems can only supplement heat through external electric heating, resulting in low condensation heat utilization and a significant increase in additional energy consumption. At the same time, the unrecovered waste heat from the condenser is directly discharged into the environment, causing heat energy waste and exacerbating the equipment's heat dissipation burden. Ultimately, this leads to a significant decrease in the system's energy efficiency ratio, making it difficult to achieve stable and comfortable stepless temperature control. Utility Model Content

[0004] Based on this, the purpose of this utility model is to provide a new type of all-season fresh air dehumidifier based on variable frequency heat pump, so as to solve the technical problems of traditional equipment, such as low seasonal energy efficiency ratio due to fixed compressor frequency, serious heat energy waste caused by insufficient condensation heat recovery, limited reheat temperature adjustment range that cannot meet dynamic temperature and humidity requirements, and imbalance between dehumidification and heating efficiency under low temperature conditions in winter.

[0005] To achieve the above objectives, this utility model provides the following technical solution: a seasonal fresh air dehumidifier based on a variable frequency heat pump, comprising: a first DC variable frequency compressor, a first high-pressure gauge, an oil separator, a four-way valve, a first finned heat exchanger, a condenser fan, a first one-way valve, a first liquid receiver, a first shut-off valve, a first dryer filter, a first plate-type energy saver, a first throttling valve, a second one-way valve, a second finned heat exchanger, a blower, a first airflow separator, a first low-pressure gauge, a high and low pressure controller, a second shut-off valve, a solenoid valve, a second throttling valve, a third one-way valve, a fourth one-way valve, a first electric valve, a subcooler, a fifth one-way valve, and a second electric valve;

[0006] The four-way valve is connected to the first DC inverter compressor, the oil separator, the first finned heat exchanger, and the second finned heat exchanger.

[0007] The first high-pressure gauge monitors the discharge pressure of the first DC inverter compressor, the first low-pressure gauge monitors its suction pressure, and the high-low pressure controller receives the pressure signal and adjusts the operating frequency.

[0008] The subcooler is connected to the outlet pipe of the first finned heat exchanger, and the condensation heat recovery ratio is adjusted by the fifth check valve and the second electric valve.

[0009] The first electric valve is located at the outlet branch of the first finned heat exchanger to control the switching of the low-temperature heating mode.

[0010] By adopting the above technical solutions, and by integrating a four-way valve to switch between cooling / heating modes, a high and low pressure controller to dynamically adjust the compressor frequency, and a subcooler and electric valve to coordinate the control of the condensation heat recovery ratio, efficient dehumidification and wide-temperature-range air supply can be achieved in all four seasons, solving the problems of heat energy waste and limited temperature control range in traditional equipment.

[0011] Furthermore, the first DC inverter compressor is sequentially connected to an oil separator, a four-way valve, and a first finned heat exchanger. It is then connected to a first liquid receiver via a first check valve, and then connected to a first plate-type energy saver via a first shut-off valve and a first dryer filter. Subsequently, it is connected to a second finned heat exchanger via a first throttle valve and a second check valve, and finally returns to the first airflow separator and the first DC inverter compressor via a four-way valve, effectively forming a refrigeration cycle path.

[0012] By adopting the above technical solution, the path of the refrigerant flowing sequentially through the compressor, condenser, throttling device and evaporator is clearly defined. By using the plate-type energy-saving device to enhance subcooling efficiency, the refrigeration cycle is ensured to be efficient and stable, and the dehumidification capacity is improved.

[0013] Furthermore, the first DC inverter compressor is sequentially connected to the oil separator, the four-way valve, and the second finned heat exchanger, then connected to the first plate-type energy saver via the second one-way valve, and then connected to the first finned heat exchanger via the second throttle valve, and finally returned to the first airflow separator and the first DC inverter compressor via the four-way valve, effectively forming a heating cycle path.

[0014] By adopting the above technical solution, the heating path switches the flow direction of the four-way valve, allowing the evaporator and condenser to interchange functions. Combined with the coordinated control of the energy saver and the throttling valve, the stability and efficiency of low-temperature heating are improved.

[0015] Furthermore, the first plate-type energy saver improves cooling and heating efficiency through refrigerant and is connected to a high and low pressure controller to achieve adaptive pressure regulation.

[0016] By adopting the above technical solutions, the plate-type energy saver simultaneously improves cooling and heating efficiency through refrigerant subcooling technology, and achieves energy efficiency optimization by dynamically adjusting the system pressure with high and low pressure controllers.

[0017] Furthermore, the outlet air temperature of the blower is controlled by a second electric valve to regulate the heat recovery of the subcooler, achieving continuous adjustment from 12℃ to 50℃.

[0018] By adopting the above technical solution, the heat recovery of the subcooler is adjusted by the second electric valve, and the air supply temperature can be continuously and steplessly adjusted from 12℃ to 50℃ to meet diverse temperature control needs.

[0019] Furthermore, the third check valve prevents refrigerant backflow between the first finned heat exchanger and the first throttle valve, and the fourth check valve restricts the flow direction of the branch of the second finned heat exchanger.

[0020] By adopting the above technical solution, the third and fourth check valves respectively restrict the refrigerant backflow and branch flow direction, ensuring the isolation of the cooling / heating cycle path and improving system stability.

[0021] Furthermore, the second shut-off valve and the first electric valve work together to control the opening and closing of the bypass branch of the heating cycle.

[0022] By adopting the above technical solution, the second shut-off valve and the first electric valve work together to control the heating bypass branch, preventing evaporator frost under low temperature conditions and ensuring continuous and stable operation.

[0023] In summary, the present invention has the following main advantages:

[0024] This invention incorporates a first DC inverter compressor, a first high-pressure gauge, an oil separator, a four-way valve, a first finned heat exchanger, a condenser fan, a first one-way valve, a first liquid receiver, and a first shut-off valve. The first DC inverter compressor, in conjunction with a high- and low-pressure controller, dynamically adjusts the operating frequency and starts / stops parallel units, significantly improving seasonal energy efficiency. A first plate-type energy saver is linked with the subcooler, using refrigerant subcooling technology to simultaneously increase cooling and heating capacity, optimizing system energy efficiency. A second electric valve works in tandem with the subcooler to precisely adjust the condensation heat recovery ratio, achieving stepless adjustment of the supply air temperature over a wide range of 12℃ to 50℃. The four-way valve and the first electric valve combine for switching, supporting efficient operation in both cooling and heating modes, ensuring stable heat pump heating and dehumidification under low-temperature winter conditions. Third, fourth, and fifth one-way valves respectively restrict refrigerant backflow and branch flow, ensuring system circulation stability. The synergistic effect of these structures effectively solves the technical problems of severe condensation heat waste, limited temperature control range, and low low-temperature dehumidification efficiency in traditional equipment. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the overall system structure of this utility model.

[0026] In the diagram: 1. First DC inverter compressor; 2. First high-pressure gauge; 3. Oil separator; 4. Four-way valve; 5. First finned heat exchanger; 6. Condenser fan; 7. First check valve; 8. First liquid receiver; 9. First shut-off valve; 10. First dryer filter; 11. First plate-type energy saver; 12. First throttle valve; 13. Second check valve; 14. Second finned heat exchanger; 15. Blower; 16. First airflow separator; 17. First low-pressure gauge; 18. High and low pressure controller; 19. Second shut-off valve; 20. Solenoid valve; 21. Second throttle valve; 22. Third check valve; 23. Fourth check valve; 24. First electric valve; 25. Subcooler; 26. Fifth check valve; 27. Second electric valve. Detailed Implementation

[0027] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0028] A type of all-season fresh air dehumidifier based on variable frequency heat pump, such as Figure 1 As shown, it includes: a first DC inverter compressor 1, a first high-pressure gauge 2, an oil separator 3, a four-way valve 4, a first finned heat exchanger 5, a condenser fan 6, a first check valve 7, a first liquid receiver 8, a first shut-off valve 9, a first dryer filter 10, a first plate-type energy saver 11, a first throttle valve 12, a second check valve 13, a second finned heat exchanger 14, a blower 15, a first airflow separator 16, a first low-pressure gauge 17, a high and low pressure controller 18, a second shut-off valve 19, a solenoid valve 20, a second throttle valve 21, a third check valve 22, a fourth check valve 23, a first electric valve 24, a subcooler 25, a fifth check valve 26, and a second electric valve 27.

[0029] The four-way valve 4 connects to the first DC inverter compressor 1, the oil separator 3, the first finned heat exchanger 5, and the second finned heat exchanger 14.

[0030] The first high pressure gauge 2 monitors the discharge pressure of the first DC inverter compressor 1, the first low pressure gauge 17 monitors its suction pressure, and the high and low pressure controller 18 receives the pressure signal and adjusts the operating frequency.

[0031] The subcooler 25 is connected to the outlet pipe of the first finned heat exchanger 5, and the condensation heat recovery ratio is adjusted by the fifth check valve 26 and the second electric valve 27.

[0032] The first electric valve 24 is located on the outlet branch of the first finned heat exchanger 5 to control the switching of the low-temperature heating mode. It is achieved by setting up the first DC inverter compressor 1, the four-way valve 4, the subcooler 25, the fifth one-way valve 26, and the second electric valve 27. The four-way valve 4 is connected to the compressor 1, the oil separator 3, and the two finned heat exchangers 5 / 14 to realize the switching of the cooling / heating mode. The first high-pressure gauge 2 and the first low-pressure gauge 17 monitor the system pressure, and the high and low pressure controller 18 dynamically adjusts the frequency of the compressor 1. The subcooler 25 is connected to the outlet pipe of the first finned heat exchanger 5. The flow direction is restricted by the fifth one-way valve 26, the second electric valve 27 adjusts the condensation heat recovery ratio, and the first electric valve 24 controls the opening and closing of the low-temperature heating branch, ultimately realizing the improvement of heat recovery utilization rate and stable operation in all seasons.

[0033] See Figure 1 The first DC inverter compressor 1 is sequentially connected to the oil separator 3, the four-way valve 4, and the first finned heat exchanger 5. It is then connected to the first liquid receiver 8 via the first check valve 7, and then to the first plate-type energy saver 11 via the first shut-off valve 9 and the first dryer filter 10. Subsequently, it is connected to the second finned heat exchanger 14 via the first throttle valve 12 and the second check valve 13. Finally, it returns to the first airflow separator 16 and the first DC inverter compressor 1 via the four-way valve 4, effectively forming a refrigeration cycle path. The first plate-type energy saver 11 improves the heat absorption efficiency of the evaporator by subcooling the refrigerant. Combined with the pressure adaptive adjustment of the high and low pressure controller 18, it ensures that the cooling capacity and energy efficiency ratio are significantly optimized.

[0034] See Figure 1 The first DC inverter compressor 1 is sequentially connected to the oil separator 3, the four-way valve 4, and the second finned heat exchanger 14. It is then connected to the first plate-type energy saver 11 via the second one-way valve 13, and then connected to the first finned heat exchanger 5 via the second throttle valve 21. Finally, it returns to the first airflow separator 16 and the first DC inverter compressor 1 via the four-way valve 4, effectively forming a heating cycle path. The second finned heat exchanger 14 acts as a condenser to heat the fresh air, while the first finned heat exchanger 5 acts as an evaporator to absorb heat from the air. The first plate-type energy saver 11 increases the refrigerant subcooling, and the second throttle valve 21 optimizes the pressure difference under heating conditions, ensuring efficient dehumidification in low-temperature environments.

[0035] See Figure 1 The first plate-type energy-saving device 11 improves cooling and heating efficiency through refrigerant and is connected to the high and low pressure controller 18 to achieve adaptive pressure regulation. The first plate-type energy-saving device 11 reduces the enthalpy value at the evaporator inlet through subcooled refrigerant, thereby improving the heat absorption capacity of the cooling cycle; in the heating cycle, it further reduces the condenser outlet temperature, increasing the heating temperature difference. The high and low pressure controller 18 dynamically adjusts the compressor 1 frequency and the throttle valve opening based on the signals from the first high pressure gauge 2 and the first low pressure gauge 17 to ensure stable system pressure and avoid efficiency loss caused by insufficient subcooling.

[0036] See Figure 1 The outlet air temperature of the blower 15 is controlled by the second electric valve 27 to regulate the heat recovery of the subcooler 25, achieving continuous adjustment from 12℃ to 50℃. The second electric valve 27 controls the opening of the branch of the subcooler 25, adjusting the condensed heat discharged from the first finned heat exchanger 5 to the subcooler 25. The reheated air is then output by the blower 15, and its temperature can be continuously adjusted within the range of 12℃ to 50℃. The fifth one-way valve 26 prevents backflow in the heat recovery branch, ensuring precise and controllable heat distribution and avoiding the increased energy consumption caused by the reliance on external electric heating in traditional equipment.

[0037] See Figure 1 The third one-way valve 22 prevents refrigerant backflow between the first finned heat exchanger 5 and the first throttling valve 12. The fourth one-way valve 23 restricts the flow direction of the branch of the second finned heat exchanger 14. The third one-way valve 22 is located between the first finned heat exchanger 5 and the first throttling valve 12 to prevent high-pressure refrigerant from backflowing to the evaporator in the refrigeration cycle. The fourth one-way valve 23 is located at the outlet of the second finned heat exchanger 14 to restrict the refrigerant from flowing unidirectionally into the first plate-type energy saver 11 in the heating cycle, avoiding path conflicts when switching modes and ensuring the tightness of the cycle logic.

[0038] See Figure 1 The second shut-off valve 19 and the first electric valve 24 work together to control the opening and closing of the bypass branch of the heating cycle. The second shut-off valve 19 is located at the outlet of the first liquid receiver 8, and the first electric valve 24 is located at the outlet branch of the first finned heat exchanger 5. The two work together to control the bypass flow of the heating cycle. During low-temperature heating, the first electric valve 24 opens to divert part of the refrigerant, reducing the risk of evaporator frosting; the second shut-off valve 19 regulates the main flow to maintain system pressure balance and ensure heating efficiency and dehumidification stability.

[0039] The implementation principle of this embodiment is as follows: In summer and spring / autumn, the first DC inverter compressor 1 automatically adjusts its frequency according to the fresh air load, driving the refrigerant to flow sequentially through the oil separator 3 and the four-way valve 4 to switch to the first finned heat exchanger 5 as a condenser to release heat. The condensation heat is recovered through the subcooler 25 and used for reheating the air supply. After being subcooled by the first liquid receiver 8 and the first plate energy saver 11, the refrigerant is depressurized through the first throttle valve 12 and enters the second finned heat exchanger 14 as an evaporator to absorb heat and dehumidify, and finally returns to the compressor to complete the cycle. The second electric valve 27 dynamically adjusts the heat recovery ratio of the subcooler 25 to achieve continuous control of the air supply temperature from 12℃ to 50℃.

[0040] In winter, the four-way valve 4 switches the flow direction, the second finned heat exchanger 14 acts as a condenser to heat the fresh air, and the first finned heat exchanger 5 acts as an evaporator to absorb heat from the air; the first electric valve 24 and the second shut-off valve 19 work together to control the low-temperature heating branch to prevent the evaporator from frosting; the first plate-type energy saver 11 increases the refrigerant subcooling and works with the second throttling valve 21 to optimize heating efficiency.

[0041] The multi-system parallel control can automatically start and stop and match the frequency according to the heat and humidity load. The high and low pressure controller 18 monitors the system pressure in real time through the first high pressure gauge 2 and the first low pressure gauge 17 to ensure that the one-way valves of each branch limit backflow and maintain circulation stability. The four-way valve 4 switches the cooling / heating path. Combined with the load response of the variable frequency compressor 1, the subcooling efficiency enhancement of the energy saver 11 and the heat recovery regulation of the subcooler 25, it can achieve efficient dehumidification in all seasons and precise air delivery in a wide temperature range.

[0042] Although embodiments of the present invention have been shown and described, these specific embodiments are merely explanations of the present invention and are not intended to limit the invention. The specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. After reading this specification, those skilled in the art may make modifications, substitutions, and variations to the embodiments as needed without departing from the principles and spirit of the present invention, provided that such modifications, substitutions, and variations are within the scope of the claims of the present invention and are protected by patent law.

Claims

1. A seasonal fresh air dehumidifier based on a variable frequency heat pump, characterized in that: include, First DC inverter compressor (1), first high pressure gauge (2), oil separator (3), four-way valve (4), first finned heat exchanger (5), condenser fan (6), first check valve (7), first liquid receiver (8), first shut-off valve (9), first dryer filter (10), first plate energy saver (11), first throttle valve (12), second check valve (13), second finned heat exchanger (14), blower (15), first airflow separator (16), first low pressure gauge (17), high and low pressure controller (18), second shut-off valve (19), solenoid valve (20), second throttle valve (21), third check valve (22), fourth check valve (23), first electric valve (24), subcooler (25), fifth check valve (26), second electric valve (27); The four-way valve (4) is connected to the first DC inverter compressor (1), the oil separator (3), the first finned heat exchanger (5) and the second finned heat exchanger (14). The first high pressure gauge (2) monitors the discharge pressure of the first DC inverter compressor (1), the first low pressure gauge (17) monitors its suction pressure, and the high and low pressure controller (18) receives the pressure signal and adjusts the operating frequency. The subcooler (25) is connected to the outlet pipe of the first finned heat exchanger (5), and the condensation heat recovery ratio is adjusted by the fifth check valve (26) and the second electric valve (27). The first electric valve (24) is located on the outlet branch of the first finned heat exchanger (5) to control the switching of the low-temperature heating mode.

2. The variable frequency heat pump four-season full fresh air dehumidifier based on claim 1, characterized in that: The first DC inverter compressor (1) is connected in sequence to the oil separator (3), the four-way valve (4), and the first finned heat exchanger (5). It is connected to the first liquid receiver (8) via the first check valve (7), and then connected to the first plate energy saver (11) via the first shut-off valve (9) and the first dryer filter (10). Subsequently, it is connected to the second finned heat exchanger (14) via the first throttle valve (12) and the second check valve (13). Finally, it returns to the first airflow separator (16) and the first DC inverter compressor (1) via the four-way valve (4), effectively forming a refrigeration cycle path.

3. The variable frequency heat pump four-season full fresh air dehumidifier based on claim 1, characterized in that: The first DC inverter compressor (1) is connected in sequence to the oil separator (3), the four-way valve (4), and the second finned heat exchanger (14). It is connected to the first plate energy saver (11) through the second one-way valve (13), and then connected to the first finned heat exchanger (5) through the second throttle valve (21). Finally, it returns to the first airflow separator (16) and the first DC inverter compressor (1) through the four-way valve (4), effectively forming a heating cycle path.

4. The variable frequency heat pump four-season all-fresh air dehumidifier based on claim 1, characterized in that: The first plate-type energy saver (11) improves the cooling and heating efficiency through refrigerant and is connected to the high and low pressure controller (18) to achieve pressure adaptive regulation.

5. The all-season fresh air dehumidifier based on a variable frequency heat pump according to claim 1, characterized in that: The outlet temperature of the blower (15) is controlled by the second electric valve (27) to control the heat recovery of the subcooler (25), thereby achieving continuous adjustment from 12°C to 50°C.

6. The all-season fresh air dehumidifier based on a variable frequency heat pump according to claim 1, characterized in that: The third check valve (22) prevents refrigerant backflow between the first finned heat exchanger (5) and the first throttle valve (12), and the fourth check valve (23) restricts the flow direction of the branch of the second finned heat exchanger (14).

7. The all-season fresh air dehumidifier based on a variable frequency heat pump according to claim 1, characterized in that: The second shut-off valve (19) and the first electric valve (24) work together to control the opening and closing of the bypass branch of the heating cycle.

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