Evaporator heat pump direct expansion dehumidification device

Abstract

The utility model provides an evaporator heat pump direct expansion dehumidification device, which relates to the technical field of industrial dehumidification, a dehumidification component, which includes at least two stages of wheels connected by cavities and an air inlet duct connecting the moisture absorption areas of the multi-stage wheels and an exhaust duct connecting the dehumidification areas required by the wheels; and a heat recovery component, which includes an evaporator installed in the corresponding wheel front air inlet cavity and a condenser installed in the last stage and away from the remaining wheel cavities, a pipe loop with built-in refrigerant is formed between the condenser and the corresponding evaporators of each stage, and the refrigerant absorbing heat in the pipe refluxes to heat the condenser; the refrigerant absorbs the heat of the first-stage evaporator and the second-stage evaporator and flows to the condenser in the form of gas, the condenser transfers heat to the exhaust air, and the refrigerant flows to the first-stage evaporator and the second-stage evaporator again to absorb heat, so that the heat of the fresh air and the return air is fully utilized to dehumidify the regeneration area of ​​the wheel, and the energy loss required for heating the regeneration area of ​​the wheel is greatly reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of industrial dehumidification, in particular to an evaporator heat pump direct expansion dehumidification device. Background Art

[0002] The production process of lithium batteries has very strict requirements on the humidity of the workshop environment. Some workshops require the dew point to be lower than -40℃. The battery production yield is closely related to the workshop humidity. Problems such as battery swelling and leakage are related to excessive water content in the air. In order to improve the production yield and reduce costs, it is very important to control the workshop humidity within a reasonable range. Among the dehumidification solutions, the rotary dehumidification solution is the most widely used in the lithium battery production industry. The humid air flowing through the rotary wheel is fully adsorbed by the special material of the rotary wheel under the action of the water vapor pressure difference, achieving the purpose of deep dehumidification.

[0003] In the prior art, in order to achieve the continuous and stable dehumidification function of the rotor, the rotor needs to be regenerated to remove the moisture in the rotor so that it regains its moisture absorption capacity. Generally, the regeneration air needs to be heated to above 120°C to evaporate the moisture in the rotor and then discharge the moisture through the exhaust system. This method can quickly and effectively remove moisture from the rotor, but it consumes a lot of energy. Therefore, the regeneration process consumes a lot of energy, resulting in insufficient utilization of energy. Utility Model Content

[0004] In order to solve the above technical problems, the utility model uses refrigerant to absorb the heat of the primary evaporator and the secondary evaporator, and transfers heat to the exhaust air through the condenser to reduce the energy loss required for the rotary dehumidification. The specific technical solution is as follows:

[0005] An evaporator heat pump direct expansion dehumidification device includes a dehumidification component, including at least two stages of wheels connected by cavities, an air inlet duct connecting the moisture absorption areas of the multi-stage wheels, and an exhaust duct connecting the dehumidification areas required by the wheels; and a heat recovery component, including an evaporator installed in the corresponding front air inlet cavity of the wheel and a condenser installed in the last stage and away from the remaining wheel cavities, a pipe loop with built-in refrigerant is formed between the condenser and the corresponding stages of the evaporator, and the refrigerant that absorbs heat in the pipe refluxes to heat the condenser.

[0006] Preferably, the dehumidification component includes a primary wheel and a secondary wheel, and the moisture absorption area and the required dehumidification area of ​​the primary wheel and the secondary wheel are the primary wheel regeneration area and the secondary wheel regeneration area, and the primary wheel adsorption area and the secondary wheel adsorption area respectively.

[0007] Preferably, the secondary rotor is further divided into a secondary rotor heat recovery zone, and a cavity toward the secondary rotor heat recovery zone is connected between the cavity before the air inlet of the secondary rotor and the air inlet of the condenser.

[0008] Preferably, the heat recovery component further includes a compressor and a three-way valve, the compressor is installed on the pipe loop between the condenser and each stage of the evaporators, and the three-way valve is installed on the pipeline node of two adjacent evaporators.

[0009] Preferably, an economizer is installed on the pipeline between the three-way valve and the primary evaporator, and the gas pipeline of the economizer merges into the compressor.

[0010] It can be seen from the above technical solutions that the utility model has the following beneficial effects:

[0011] By setting up a condenser, the refrigerant absorbs the heat of the primary evaporator and the secondary evaporator and flows to the condenser in the form of gas. The condenser transfers heat to the exhaust air. After the heat is dissipated, the refrigerant becomes liquid again and flows to the primary evaporator and the secondary evaporator to absorb heat again. The heat of the fresh air and the return air is fully utilized to dehumidify the regeneration area of ​​the rotor, greatly reducing the energy loss required for heating the regeneration area of ​​the rotor.

[0012] By adjusting the refrigerant evaporation ratio in the economizer, the subcooling of the refrigerant entering the primary evaporator can be controlled, so that the primary evaporator can still maintain a good heat exchange effect in the low temperature environment in winter, and the environmental adaptability of the heat pump at different temperatures can be improved.

[0013] The fresh air is heated by the first-stage rotor and then mixed with the return air at a constant temperature. The second-stage evaporator recovers the mixed air with a small temperature change, which can maintain a reasonable heat exchange temperature difference and maximize the heat exchange efficiency. The heat sources of the heat pump come from the fresh air and the mixed air respectively, and different heat exchange configurations are used for different heat sources, which ensures the stability of the heat source of the heat pump, effectively increases the condensation temperature, and reduces the regeneration energy consumption; the regenerated air is heated by the rotor waste heat, preheated by the condenser, and electrically heated. In the scenario of large temperature rise, the temperature difference of a single heating is reduced through staged heating, thereby further improving the energy utilization efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 It is a structural schematic diagram of the dehumidification system of the utility model.

[0015] In the figure: 1. Fresh air; 2. Return air; 3. Supply air; 4. Exhaust air; 5. Primary rotor regeneration zone; 6. Primary rotor adsorption zone; 7. Secondary rotor regeneration zone; 8. Secondary rotor adsorption zone; 9. Secondary rotor heat recovery zone; 10. Primary evaporator; 11. Secondary evaporator; 12. Compressor; 13. Condenser; 14. Expansion valve; 15. Economizer; 16. Supply air fan; 17. Rear surface cooler; 18. Secondary electric auxiliary heater; 19. Exhaust fan; 20. Primary electric auxiliary heater; 21. Throttle valve; 22. Three-way valve. DETAILED DESCRIPTION

[0016] The following is a detailed description of the present invention in conjunction with the accompanying drawings and specific embodiments. Before describing in detail the technical solutions of each embodiment of the present invention, the nouns and terms involved are explained. In this specification, components with the same name or the same number represent similar or identical structures and are only for illustrative purposes.

[0017] Conventional heat pump direct expansion coupling schemes can recycle heat from a single location, for example, using the heat of the fresh air in the front cooler to preheat the regeneration air. However, this scheme is greatly restricted by the ambient temperature and the heating effect is very limited under low temperature conditions. Some heat pump coupling schemes install a heat pump on the exhaust side to recover heat energy for preheating the regeneration air, but are greatly affected by the regeneration exhaust air temperature and air volume, and the heat source is unstable.

[0018] like Figure 1 As shown, an evaporator heat pump direct expansion dehumidification device includes a dehumidification component, which includes at least two stages of rotors connected by cavities and an air inlet duct connecting the moisture absorption areas of the multi-stage rotors and an exhaust duct connecting the dehumidification areas required by the rotors; and a heat recovery component, which includes an evaporator installed in the corresponding rotor front air inlet cavity and a condenser 13 installed in the last stage and away from the remaining rotor cavities. A pipe loop with built-in refrigerant is formed between the condenser 13 and the corresponding evaporators of each stage, and the refrigerant absorbing heat in the pipe refluxes to heat the condenser 13. Among them, a two-stage rotor is preferably used, which is divided into a primary rotor and a secondary rotor. A primary evaporator 10 and a secondary evaporator 11 are respectively installed on the cavities corresponding to the primary rotor and the secondary rotor, and the end of the primary evaporator 10 away from the primary rotor is connected to the external environment of fresh air 1 through the cavity.

[0019] Among them, the dehumidification component includes a primary rotor and a secondary rotor. The moisture absorption area and the required dehumidification area of ​​the primary rotor and the secondary rotor are respectively the primary rotor regeneration area 5 and the secondary rotor regeneration area 7, the primary rotor adsorption area 6 and the secondary rotor adsorption area 8. The fresh air 1 passes through the primary rotor adsorption area 6 and the secondary rotor adsorption area 8 respectively to achieve dehumidification. As the rotor rotates, the rotor rotates the adsorption area to the regeneration area. The branch of the outlet end of the secondary evaporator 11 forms exhaust air 4. After the temperature of the exhaust air 4 increases, it flows through the regeneration area. The exhaust air 4 dries the regeneration area through the cavity. The moisture in the regeneration area flows out to the outside with the exhaust air 4, thereby achieving the repeated dehumidification effect of the rotor, which not only reduces the temperature of the fresh air 1, but also fully uses the heat of the fresh air 1 for dehumidification in the regeneration area.

[0020] The pipeline of fresh air 1 is connected to the C port of the primary evaporator 10 and flows out from the D port of the primary evaporator 10. The cooled fresh air 1 passes through the primary rotor adsorption zone 6. The primary rotor adsorption zone 6 adsorbs and dehumidifies the water vapor of the fresh air 1 and heats the fresh air 1 at the same time. The dehumidified and heated fresh air 1 flows into the C port of the secondary evaporator 11 again. The secondary evaporator 11 cools the fresh air 1 and discharges it from the D port. After passing through the secondary evaporator 11, the fresh air 1 is divided into supply air 3 and exhaust air 4. The supply air 3 is discharged into the room and is suitable for the production workshop environment of lithium batteries. After the exhaust air 4 is heated by the condenser 13, it passes through the regeneration zone of the secondary rotor and the regeneration zone of the primary rotor in turn. The heated exhaust air 4 dehumidifies the secondary rotor and the primary rotor, reduces the moisture content in the regeneration zone 7 of the secondary rotor and the regeneration zone 5 of the primary rotor, and heats the secondary rotor and the primary rotor at the same time. Finally, the exhaust air 4 and the water vapor are discharged outdoors, and the cycle repeats.

[0021] The C port and the D port of the primary evaporator 10 and the secondary evaporator 11 mentioned above represent the air inlet and the air outlet respectively, and the refrigerant inlet and outlet represent the A port and the B port respectively, which are all prior arts.

[0022] In order to improve the temperature raising effect of the exhaust air 4, the secondary rotor is also provided with a secondary rotor heat recovery zone 9, and the secondary rotor is also divided into a secondary rotor heat recovery zone 9. A cavity toward the secondary rotor heat recovery zone 9 is connected between the cavity before the secondary rotor air inlet and the air inlet of the condenser 13 to provide air volume for the exhaust air 4. Among them, the secondary rotor heat recovery zone 9 is the area after dehumidification in the secondary wheel regeneration zone 7, so there is still residual heat in the secondary rotor heat recovery zone 9, which can preheat part of the fresh air 1 of the secondary evaporator 11 and improve the temperature raising effect of the exhaust air 4.

[0023] In order to improve the effect of heat transfer of refrigerant, the heat recovery component also includes a compressor 12 and a three-way valve 22. The compressor 12 is installed on the pipe loop of the condenser 13 and the first-level evaporator 10 and the second-level evaporator 11. The three-way valve 22 is installed on the pipe nodes corresponding to the first-level evaporator 10 and the second-level evaporator 11. The pipeline between the second-level evaporator 11 and the three-way valve 22 is provided with an expansion valve 14; the compressor 12 compresses the refrigerant into a high-temperature and high-pressure refrigerant, and then releases heat and cools in the condenser 13, and then passes through the three-way valve 22 to be divided into two paths. One path of refrigerant flows into the expansion valve 14, and after expansion and pressure reduction, enters the second-level evaporator 11 to evaporate and absorb heat. The fully evaporated gaseous refrigerant returns to the compressor 12 for recompression; the other path of refrigerant flows into the first-level evaporator 10 to evaporate and absorb heat. The fully evaporated gaseous refrigerant returns to the compressor 12 for recompression.

[0024] In order to further improve the heat exchange effect of the refrigerant, an economizer 15 is arranged on the pipeline between the three-way valve 22 and the primary evaporator 10. The economizer 15 flows the liquid refrigerant into the primary evaporator 10, and merges with the evaporated refrigerant of the primary evaporator 10 and the secondary evaporator 11 into the compressor 12; part of the refrigerant inside the economizer 15 directly evaporates and absorbs heat, thereby increasing the supercooling degree of the remaining refrigerant, and the supercooled refrigerant enters the primary evaporator 10 to evaporate and absorb heat. The fully evaporated refrigerant in the primary evaporator 10 merges with the evaporated refrigerant in the economizer 15 and returns to the compressor 12. A throttle valve 21 is arranged on the discharge outlet pipeline of the economizer 15.

[0025] In the present embodiment, when the ambient temperature is high, the throttle valve 21 between the economizer 15 and the compressor 12 is closed, the economizer 15 does not provide subcooling, and all the refrigerant evaporates and absorbs heat in the primary evaporator 10, thereby increasing the amount of heat absorbed by the evaporator, thereby improving the heat exchange capacity in a high temperature and high humidity environment, reducing the temperature of the fresh air 1 while providing a higher temperature rise for the compressor 12, thereby reducing the energy consumption of the dehumidification system.

[0026] In the low-temperature environment scenario of this embodiment, the throttle valve 21 between the economizer 15 and the compressor 12 is fully opened, and the economizer 15 provides the maximum supercooling, so that the temperature of the refrigerant in the primary evaporator 10 is low enough, and the heat of the low-temperature air can still be effectively absorbed in the low-temperature environment, thereby improving the heat exchange capacity in the low-temperature environment, providing more temperature rise for the compressor 12 as much as possible, and reducing the energy consumption of the dehumidification system.

[0027] Furthermore, by adjusting the evaporation amount of the refrigerant inside the economizer 15 and the opening of the throttle valve 21 between the economizer 15 and the compressor 12, this embodiment can adapt to application requirements under different temperature scenarios and reduce the energy consumption of the dehumidification system while ensuring the dehumidification effect.

[0028] An air supply fan 16 is provided on the cavity where the fresh air 1 flows to the air supply 3 , and an exhaust fan 19 is provided on the cavity where the exhaust air 4 flows. The air supply fan 16 and the exhaust fan 19 are used to increase the power of the fresh air 1 and the exhaust air 4 respectively.

[0029] A cavity opening is provided on the cavity between the primary rotor and the secondary rotor, and the cavity opening is used for the return air 2 to enter. The return air 2 is merged into the cavity of the primary rotor adsorption area 6. The return air 2 belongs to the indoor wind and is used to pump the indoor air to make full use of the indoor temperature to achieve dehumidification and cooling of the indoor temperature again. The fresh air 1 and the return air 2 are mixed to form a mixed wind, and the mixed wind flows into the secondary evaporator 11 through the air supply fan 16 for cooling treatment.

[0030] The primary rotor regeneration area 5 and the secondary rotor regeneration area 7 are respectively provided with a primary electric auxiliary heater 20 and a secondary electric auxiliary heater 18 along the side opposite to the wind direction. The primary electric auxiliary heater 20 and the secondary electric auxiliary heater 18 are installed on the cavity corresponding to the primary rotor and the secondary rotor. A rear surface cooler 17 is also provided on the cavity flowing through the secondary rotor adsorption area 8. After the fresh air 1 is cooled by the primary evaporator 10, it enters the primary rotor adsorption area 6 for dehumidification under the drive of the air supply fan 16. Then, the fresh air 1 heated by the rotor is mixed with the return air 2 of the workshop at a constant temperature. The mixed air is cooled by the secondary evaporator 11 and enters the secondary rotor adsorption area 8 for depth. After dehumidification, the dry hot processed air is cooled by the rear surface cooler 17 before entering the production workshop to prevent the supply air 3 from having too high a temperature after passing through the secondary wheel, which would affect the temperature range inside the workshop; driven by the exhaust fan 19, part of the mixed air flows into the secondary wheel heat recovery zone 9, and after preheating, enters the condenser 13 to be further heated, and then is heated to the regeneration temperature by the secondary electric auxiliary heater 18, and then enters the secondary wheel regeneration zone 7. The humid hot regenerated air flows out of the secondary wheel and is heated again to the regeneration temperature by the primary electric auxiliary heater 20, and then enters the primary wheel regeneration zone 5. Finally, the regenerated air is discharged after completing the regeneration of the two-stage wheels.

[0031] The above-described embodiments are merely descriptions of preferred embodiments of the present invention, and are not intended to limit the scope of the present invention. Without departing from the design spirit of the present invention, various modifications and improvements made to the technical solutions of the present invention by ordinary technicians in this field should all fall within the protection scope determined by the claims of the present invention.

Claims

1. An evaporator heat pump direct expansion dehumidification device, characterized in that: include: The dehumidifying element comprises at least two stages of rotors connected by cavities, an air inlet duct connected to the moisture absorption area of ​​the multi-stage rotors, and an air outlet duct connected to the dehumidification area required by the rotors; as well as The heat recovery component comprises an evaporator installed in the corresponding rotor front air inlet cavity and a condenser (13) installed in the last stage and away from the remaining rotor cavities. A pipe loop with built-in refrigerant is formed between the condenser (13) and the corresponding evaporators at each stage. The refrigerant that absorbs heat in the pipe refluxes to increase the temperature of the condenser (13).

2. The evaporator heat pump direct expansion dehumidification device according to claim 1, characterized in that: The dehumidifying element comprises a primary rotor and a secondary rotor, wherein the moisture absorption area and the required dehumidification area of ​​the primary rotor and the secondary rotor are respectively a primary rotor regeneration area (5) and a secondary rotor regeneration area (7), a primary rotor adsorption area (6) and a secondary rotor adsorption area (8).

3. The evaporator heat pump direct expansion dehumidification device according to claim 2, characterized in that: The secondary rotor is further divided into a secondary rotor heat return zone (9), and a cavity toward the secondary rotor heat return zone (9) is connected between the cavity before the air inlet of the secondary rotor and the air inlet of the condenser (13).

4. The evaporator heat pump direct expansion dehumidification device according to claim 2, characterized in that: The heat recovery component also includes a compressor (12) and a three-way valve (22). The compressor (12) is installed on the pipe loop between the condenser (13) and each stage of the evaporators. The three-way valve (22) is installed on the pipe node of two adjacent evaporators.

5. The evaporator heat pump direct expansion dehumidification device according to claim 4, characterized in that: A primary evaporator (10) and a secondary evaporator (11) are respectively installed on the cavities corresponding to the primary rotor and the secondary rotor, an economizer (15) is installed on the pipeline between the three-way valve (22) and the primary evaporator (10), and a gas pipeline of the economizer (15) merges into the compressor (12).

6. The evaporator heat pump direct expansion dehumidification device according to claim 1, characterized in that: An air supply fan (16) is installed on the rotors between adjacent stages and the cavity of the evaporator; and an air exhaust fan (19) is arranged on the cavity between the adjacent rotors.

7. The evaporator heat pump direct expansion dehumidification device according to claim 2, characterized in that: The cavities of the first-stage rotor and the second-stage rotor are provided with cavity openings, and the cavity openings are used for the return air (2) to enter.

8. The evaporator heat pump direct expansion dehumidification device according to claim 2, characterized in that: The first-stage rotor regeneration zone (5) and the second-stage rotor regeneration zone (7) are respectively provided with a first-stage electric auxiliary heater (20) and a second-stage electric auxiliary heater (18) along the side opposite to the wind direction, and the first-stage electric auxiliary heater (20) and the second-stage electric auxiliary heater (18) are installed on the cavities corresponding to the first-stage rotor and the second-stage rotor.

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