Heat source tower heat pump constant temperature and humidity integrated machine

Abstract

The application discloses a heat source tower heat pump constant temperature and humidity integrated machine, and belongs to the technical field of heat source tower heat pumps. The heat source tower heat pump constant temperature and humidity integrated machine comprises a compressor, a condenser and an indoor unit. The indoor unit is provided with a fresh air inlet, a return air inlet and an air supply outlet. A first evaporator, a mixing area and a second evaporator are sequentially arranged in the air duct of the indoor unit along the airflow direction. The return air inlet is located on the side surface of the indoor unit and faces the mixing area. The outlet of the compressor is connected with the condenser through a refrigerant pipeline. The outlet of the condenser is connected with the first evaporator and the second evaporator through a three-way joint. The first evaporator is used for deep dehumidification of fresh air. The second evaporator is used for secondary cooling and dehumidification of mixed air after the mixing of fresh air and return air. The outlets of the first evaporator and the second evaporator are communicated with the compressor through a three-way joint. The application realizes constant temperature and humidity and constant temperature and dehumidification through three-way precise control, and has the advantages of precise humidity control, energy saving and high efficiency.

Description

Technical Field

[0001] This invention belongs to the field of heat source tower heat pump technology, specifically relating to an integrated heat source tower heat pump constant temperature and humidity control unit. Background Technology

[0002] Currently, heat pump systems with heat source towers are widely used in building HVAC systems due to their high heating efficiency in low-temperature and high-humidity environments. However, for locations requiring constant temperature and humidity, existing heat pump fresh air dehumidifier units generally suffer from the following technical deficiencies: Firstly, most existing heat source tower heat pump units adopt a dual-flow compressor design and are equipped with only a single dehumidification module. This makes it impossible to accurately adjust the dehumidification intensity and heat recovery amount according to changes in indoor heat and humidity load, resulting in severe coupling of temperature and humidity control, low control accuracy, and inability to meet the high-precision constant temperature and humidity requirements.

[0003] Secondly, conventional fresh air dehumidifiers generally adopt a treatment method of mixing fresh air and return air first, and then uniformly dehumidifying them. The outlet air temperature after dehumidification is usually only 10-12℃. In order to meet the indoor supply air temperature requirements, the low-temperature supply air must be fully reheated. The reheat load is large, resulting in a lot of energy waste and a significant reduction in the unit's operating energy efficiency.

[0004] Third, in order to achieve multi-path control and multi-condition adjustment, existing units mostly adopt dual or multiple compressor designs, resulting in complex unit structure, large size, high manufacturing cost, high failure rate, and difficult maintenance. Summary of the Invention

[0005] In view of this, the present invention provides a heat source tower heat pump constant temperature and humidity control integrated machine to solve the above problems.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: A heat pump constant temperature and humidity control unit with a heat source tower includes a compressor, a condenser, and an indoor unit. The indoor unit is equipped with a fresh air inlet, a return air inlet, and a supply air outlet. A first evaporator, a mixing zone, and a second evaporator are sequentially arranged along the airflow direction within the indoor unit's air duct. The return air inlet is located on the side of the indoor unit, directly opposite the mixing zone. The compressor outlet is connected to the condenser via a refrigerant pipeline, and the condenser outlet is connected to the first and second evaporators via a tee. The first evaporator is used for deep dehumidification of the fresh air. The second evaporator is used for secondary cooling and dehumidification of the mixed air after the fresh air and return air are combined. The outlets of the first and second evaporators are connected to the compressor via a tee.

[0007] Furthermore, a first electronic expansion valve is provided on the refrigerant pipeline of the first evaporator to control the evaporation temperature of the first evaporator.

[0008] Furthermore, a second electronic expansion valve is provided on the refrigerant line of the second evaporator to control the refrigerant flow rate of the second evaporator.

[0009] Furthermore, a reheat module is provided in the air duct of the indoor unit after the second evaporator. The reheat module is used to reheat the air supplied after it has been processed by the second evaporator.

[0010] Furthermore, the reheat module is a reheater, and the inlet of the reheater is equipped with a third electronic expansion valve. The inlet of the third electronic expansion valve and the inlet of the second evaporator are connected to the outlet of the second electronic expansion valve through a tee. The outlet of the reheater and the outlet of the compressor are connected to the condenser through a tee.

[0011] Furthermore, the reheat module is a PTC electric heating element.

[0012] Furthermore, a fresh air filtration module is provided at the fresh air inlet, and a return air filtration module is provided at the return air inlet.

[0013] Furthermore, the indoor unit is also equipped with a humidification module to achieve constant temperature humidification function.

[0014] Furthermore, the indoor unit is also equipped with a blower, which is located between the reheat module and the air outlet.

[0015] Furthermore, a one-way valve is provided at the outlet of the first evaporator.

[0016] The beneficial effects of this invention are as follows: 1. Simplified structure and high efficiency: It adopts a single compressor with a liquid-distributing solenoid valve to achieve three-way flow, breaking through the limitations of the existing two-way design. It is equipped with a large and a small dual dehumidification module (first evaporator and second evaporator), which simplifies the structure and makes the operation highly efficient.

[0017] Independent temperature and humidity control: By performing deep dehumidification on the fresh air (first evaporator) and only cooling the mixed air (second evaporator), the purpose of independent temperature and humidity control is achieved, reducing the energy waste of simultaneously performing deep dehumidification and reheating on the fresh air and return air.

[0018] Precise energy saving: Dynamically adjusts the system based on heat conditions. When heat is sufficient, one dehumidifier and one reheater operate simultaneously; when heat is insufficient, both dehumidifier modules operate while heat recovery is reduced. Through precise three-way control, constant temperature humidification and dehumidification are achieved, resulting in significant energy savings.

[0019] High-quality air supply: After deep dehumidification, the fresh air is mixed with the return air, and then undergoes secondary cooling and reheating. The supply air temperature and humidity can accurately reach the set values, avoiding the impact of excessively low or high supply air temperature on comfort. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the provided drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the interior of the indoor unit in Example 1; Figure 2 This is a schematic diagram of the structure of the heat source tower heat pump constant temperature and humidity control integrated machine in Example 1; Figure 3 This is a schematic diagram of the interior of the indoor unit in Example 2; Figure 4 This is a schematic diagram of the structure of the heat source tower heat pump constant temperature and humidity control integrated machine in Example 2; Figure 5 This is a schematic diagram of the interior of the indoor unit in Example 3; Figure 6 This is a schematic diagram of the structure of the heat source tower heat pump constant temperature and humidity control integrated machine in Example 3; In the figure: 1-Compressor, 2-Condenser, 3-Indoor unit, 4-Fresh air inlet, 5-Return air inlet, 6-First evaporator, 7-Second evaporator, 8-Reheater, 9-PTC electric heater, 10-One-way valve, 11-First electronic expansion valve, 12-Second electronic expansion valve, 13-Third electronic expansion valve, 21-Fresh air filter module, 22-Return air filter module, 32-Humidifier module, 34-Blower, 35-Air outlet. Detailed Implementation

[0022] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0023] Example 1

[0024] See attached document Figure 1-2 The heat source tower heat pump constant temperature and humidity control integrated unit disclosed in this embodiment includes a compressor 1, a condenser 2 and an indoor unit 3, which constitute the core refrigerant circulation body and air handling body of the unit.

[0025] The indoor unit 3 is equipped with a fresh air inlet 4, a return air inlet 5, and a supply air outlet 35. The fresh air inlet 4 is located at the air inlet of the indoor unit 3 to introduce fresh outdoor air; the return air inlet 5 is located on the side of the indoor unit 3 to introduce indoor return air; and the supply air outlet 35 is located at the air outlet of the indoor unit 3 to deliver treated air into the room. Inside the air duct of the indoor unit 3, a first evaporator 6, a mixing zone, and a second evaporator 7 are arranged sequentially along the airflow direction. The return air inlet 5 is positioned directly opposite the mixing zone, ensuring that the fresh air treated by the first evaporator 6 and the indoor return air introduced by the return air inlet 5 are fully mixed in the mixing zone before entering the second evaporator 7 for further treatment.

[0026] In the refrigerant circulation loop, the outlet of compressor 1 is connected to the inlet of condenser 2 via a refrigerant pipeline. The outlet of condenser 2 is connected to the inlet of the first evaporator 6 and the inlet of the second evaporator 7 via a T-joint, realizing a dual-path refrigerant flow design for a single compressor. The outlets of the first evaporator 6 and the second evaporator 7 merge via a T-joint and then connect to the inlet of compressor 1, forming a complete closed-loop refrigerant circulation loop. The first evaporator 6 is used for deep dehumidification of the fresh air introduced through the fresh air inlet 4, and the second evaporator 7 is used for secondary cooling of the mixed air after the fresh air and return air are combined.

[0027] In a preferred embodiment, a first electronic expansion valve 11 is provided on the refrigerant pipeline on the inlet side of the first evaporator 6 to precisely control the evaporation temperature of the first evaporator 6, thereby stabilizing and regulating the dehumidification amount of the fresh air deep dehumidification to ensure that the fresh air dehumidification effect meets the design requirements. A second electronic expansion valve 12 is provided on the refrigerant pipeline on the inlet side of the second evaporator 7 to precisely control the refrigerant flow rate of the second evaporator 7, thereby regulating the cooling range of the mixed air to match the set requirements of the supply air temperature.

[0028] In a preferred embodiment, the fresh air inlet 4 is provided with a fresh air filter module 21 on the air inlet side, which is used to filter and purify the introduced outdoor fresh air and remove dust, particulate matter and other impurities in the air; the return air inlet 5 is provided with a return air filter module 22 on the air inlet side, which is used to filter the introduced indoor return air and ensure the cleanliness of the internal components of the air duct and the quality of the supplied air.

[0029] In a preferred embodiment, a humidification module 32 is also provided in the air duct of the indoor unit 3. In this embodiment, the humidification module 32 is located between the mixing zone and the second evaporator 7. It can also be adjusted to a suitable position in front of the air outlet 35 according to the air duct layout. It is used to humidify the air supply when the indoor humidity is lower than the set value, so as to realize the constant temperature humidification function of the unit.

[0030] In a preferred embodiment, the indoor unit 3 is further provided with a blower 34 in the air duct. The blower 34 is located after the second evaporator 7 and before the air outlet 35. It is used to provide power for the air flow in the air duct, ensure the delivery efficiency of fresh air and return air and the static pressure of the air supply, and meet the indoor air supply needs.

[0031] In a preferred embodiment, a one-way valve 10 is provided at the outlet of the first evaporator 6. The one-way valve 10 can prevent refrigerant from flowing back into the first evaporator 6, thereby affecting the deep dehumidification of the fresh air.

[0032] The working principle of this embodiment is as follows: Outdoor fresh air enters indoor unit 3 through fresh air inlet 4, and is first purified and filtered by fresh air filter module 21 before entering the first evaporator 6. The evaporation temperature of the first evaporator 6 is precisely controlled by the first electronic expansion valve 11, so that the fresh air undergoes deep dehumidification treatment in the first evaporator 6. The treated fresh air reaches a dry bulb temperature of 10℃ and a moisture content of 8.5g / kg, and the fresh air dehumidification capacity meets the indoor moisture load design requirements.

[0033] Fresh air that has undergone deep dehumidification enters the mixing zone. Indoor return air is introduced into indoor unit 3 through return air inlet 5, filtered by return air filter module 22, and then enters the mixing zone to fully mix with the low-temperature fresh air. Taking an indoor return air temperature of 26℃ as an example, the temperature of the mixed air is approximately 20℃. The mixed air then enters the second evaporator 7, where the refrigerant flow rate is regulated by the second electronic expansion valve 12 to precisely cool the mixed air, directly reducing its temperature to the set supply air temperature. Finally, it is delivered into the room through air outlet 35 via air supply fan 34.

[0034] When the indoor humidity is lower than the set threshold, the humidification module 32 is activated to humidify the air in the air duct. In conjunction with the temperature control of the second evaporator 7, the unit can achieve constant temperature and humidification operation.

[0035] In this air handling process, the unit performs independent deep dehumidification of the fresh air through the first evaporator 6 and precise cooling of the mixed air through the second evaporator 7. This achieves independent decoupling control of temperature and humidity, completely avoiding the energy waste caused by the traditional unit's unified deep dehumidification of fresh air and return air followed by full reheating, and significantly improving the unit's operating energy efficiency.

[0036] Example 2

[0037] See attached document Figure 3-4 The heat source tower heat pump constant temperature and humidity control integrated machine disclosed in this embodiment has the same main structure as that in embodiment 1. The difference is that a reheat module is also provided in the air duct of the indoor unit 3 after the second evaporator 7. In this embodiment, the reheat module is a reheater 8, which is used to perform precise reheating treatment on the air supplied after the second evaporator 7 to meet the requirements of higher precision air supply temperature control.

[0038] A third electronic expansion valve 13 is installed on the inlet side of the reheater 8. The inlet of the third electronic expansion valve 13 is connected to the inlet of the second evaporator 7 via a T-junction, and then to the outlet of the second electronic expansion valve 12. This allows the reheater 8 and the second evaporator 7 to form a parallel refrigerant branch, which, together with the compressor 1 and the condenser 2, constitutes a third refrigerant branch, achieving three-way refrigerant branch control for a single compressor, breaking through the limitations of traditional dual-branch design. The outlet of the reheater 8 is connected to the outlet of the compressor 1 via a T-junction, forming a complete cycle.

[0039] In this embodiment, the blower 34 is located before the reheater 8 and the air outlet 35, ensuring the power of the air supply while ensuring that the air after reheating is evenly delivered to the room.

[0040] The working principle of this embodiment is as follows: Outdoor fresh air enters indoor unit 3 through fresh air inlet 4, and after being purified by fresh air filter module 21, it enters first evaporator 6. Deep dehumidification is completed by the regulation of first electronic expansion valve 11. The treated fresh air has a dry bulb temperature of 10℃ and a moisture content of 8.5g / kg, which meets the indoor moisture load requirements.

[0041] After deep dehumidification, the fresh air enters the mixing zone and mixes thoroughly with the indoor return air introduced through the return air inlet 5 and filtered by the return air filter module 22. The temperature of the mixed air is approximately 20°C. The mixed air then enters the second evaporator 7, where the refrigerant flow is regulated by the second electronic expansion valve 12 to perform secondary cooling and dehumidification. The treated supply air reaches a dry bulb temperature of 16°C and a relative humidity of 95%, further enhancing the dehumidification effect and meeting the indoor dehumidification needs in high-humidity environments.

[0042] When the user-set supply air temperature is higher than 16℃, the third electronic expansion valve 13 opens, allowing high-temperature refrigerant to enter the reheater 8. This reheats the low-temperature supply air, which has been processed by the second evaporator 7, precisely ensuring the supply air temperature stabilizes at the set value. Finally, the air is delivered into the room via the supply fan 34 and the air outlet 35. When the set supply air temperature is lower than or equal to 16℃, the third electronic expansion valve 13 closes, the reheater 8 stops working, and the supply air is directly delivered into the room via the supply fan 34.

[0043] The unit can dynamically adjust its operating mode according to the system's heat conditions: when the indoor heat load is sufficient and the heat demand is small, it adopts a single-path dehumidification (first evaporator 6) + single-path reheat (reheater 8) operating mode to accurately match the heat and humidity load; when the indoor heat load is insufficient and the humidity load is large, it adopts a dual dehumidification module (first evaporator 6 + second evaporator 7) to operate at full load, while reducing the amount of heat recovery. Through the precise control of the three-path refrigerant diversion, it takes into account both constant temperature dehumidification effect and energy saving.

[0044] Example 3

[0045] See attached document Figure 5-6 The heat source tower heat pump constant temperature and humidity control integrated unit disclosed in this embodiment has the same main structure as that in embodiment 2. The difference is that the reheat module is a PTC electric heater 9, which is used to perform electric auxiliary heating reheating treatment on the supply air after it has been processed by the second evaporator 7, adapting to the supply air temperature control requirements under extreme low temperature conditions and improving the environmental adaptability of the unit.

[0046] In this embodiment, the PTC electric heater 9 is located between the second evaporator 7 and the blower 34. It can precisely adjust the heating power according to the set value of the blower temperature to achieve stepless control of the blower temperature.

[0047] The working principle of this embodiment is as follows: Outdoor fresh air enters indoor unit 3 through fresh air inlet 4, and after being purified by fresh air filter module 21, it enters first evaporator 6. Deep dehumidification is completed by the regulation of first electronic expansion valve 11. The treated fresh air has a dry bulb temperature of 10℃ and a moisture content of 8.5g / kg, which meets the indoor moisture load requirements.

[0048] After deep dehumidification, the fresh air enters the mixing zone and mixes thoroughly with the indoor return air introduced through the return air inlet 5 and filtered by the return air filter module 22. The temperature of the mixed air is approximately 20°C. The mixed air then enters the second evaporator 7, where the refrigerant flow is regulated by the second electronic expansion valve 12 to perform secondary cooling and dehumidification. The treated supply air reaches a dry bulb temperature of 16°C and a relative humidity of 95%, completing the deep dehumidification process.

[0049] When the user-set air supply temperature is higher than 16℃, the PTC electric heater 9 starts and precisely adjusts the heating power according to the difference between the set temperature and the actual air supply temperature. This precisely reheats the low-temperature air supply, ensuring the air supply temperature stabilizes at the set value, and is finally delivered into the room through the air outlet 35 via the air supply fan 34. When the set air supply temperature is lower than or equal to 16℃, the PTC electric heater 9 shuts off, and the air supply is directly delivered into the room via the air supply fan 34.

[0050] This embodiment uses PTC electric heating as the reheat module, which has a simpler structure and more direct control. It can ensure stable control of the supply air temperature under extreme low temperature conditions where the refrigerant system is insufficient, further expanding the applicable operating conditions of the unit.

[0051] The above descriptions are merely specific embodiments of the present invention, and common knowledge regarding the specific structures and characteristics of the solutions is not described in detail here. It should be noted that those skilled in the art can make various modifications and improvements without departing from the structure of the present invention, and these should also be considered within the scope of protection of the present invention. These modifications and improvements will not affect the effectiveness of the implementation of the present invention or the practicality of the patent. The scope of protection claimed in this application should be determined by the content of its claims, and the specific embodiments described in the specification can be used to interpret the content of the claims.

[0052] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the apparatus disclosed in the embodiments, since they correspond to the methods disclosed in the embodiments, the description is relatively simple; relevant parts can be referred to the method section.

[0053] The above description of the disclosed embodiments enables those skilled in the art to make or use the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A heat source tower heat pump constant temperature and humidity control integrated unit, characterized in that, include: The unit comprises a compressor (1), a condenser (2), and an indoor unit (3). The indoor unit (3) is provided with a fresh air inlet (4), a return air inlet (5), and a supply air outlet (35). The air duct of the indoor unit (3) is provided with a first evaporator (6), a mixing zone, and a second evaporator (7) arranged sequentially along the airflow direction. The return air inlet (5) is located on the side of the indoor unit (3) and faces the mixing zone. The outlet of the compressor (1) is connected to the condenser (2) through a refrigerant pipeline. The outlet of the condenser (2) is connected to the first evaporator (6) and the second evaporator (7) through a tee. The first evaporator (6) is used for deep dehumidification of the fresh air. The second evaporator (7) is used for secondary cooling and dehumidification of the mixed air after the fresh air and return air are mixed. The outlets of the first evaporator (6) and the second evaporator (7) are connected to the compressor (1) through a tee.

2. The integrated temperature and humidity control unit for heat source tower heat pumps according to claim 1, characterized in that, The first evaporator (6) is equipped with a first electronic expansion valve (11) on the refrigerant pipeline to control the evaporation temperature of the first evaporator (6).

3. The integrated temperature and humidity control unit for heat source towers and heat pumps according to claim 1, characterized in that, The second evaporator (7) is equipped with a second electronic expansion valve (12) on the refrigerant pipeline to control the refrigerant flow of the second evaporator (7).

4. The integrated temperature and humidity control unit for heat source tower heat pumps according to claim 3, characterized in that, The indoor unit (3) has a reheat module installed in the air duct after the second evaporator (7). The reheat module is used to reheat the air supplied after it has been processed by the second evaporator (7).

5. The integrated temperature and humidity control unit for heat source tower heat pumps according to claim 4, characterized in that, The reheat module is a reheater (8). The inlet of the reheater (8) is provided with a third electronic expansion valve (13). The inlet of the third electronic expansion valve (13) and the inlet of the second evaporator (7) are connected to the outlet of the second electronic expansion valve (12) through a tee. The outlet of the reheater (8) and the outlet of the compressor (1) are connected to the condenser (2) through a tee.

6. The integrated temperature and humidity control unit for heat source tower heat pumps according to claim 4, characterized in that, The reheat module is a PTC electric heater (9).

7. The integrated temperature and humidity control unit for heat source tower heat pumps according to claim 1, characterized in that, A fresh air filter module (21) is provided at the fresh air inlet (4), and a return air filter module (22) is provided at the return air inlet (5).

8. The integrated temperature and humidity control unit for heat source tower heat pumps according to claim 1, characterized in that, The indoor unit (3) is also equipped with a humidification module (32) for achieving constant temperature humidification function.

9. The integrated temperature and humidity control unit for heat pumps and heat source towers according to claim 4, characterized in that, The indoor unit (3) is also provided with a blower (34), which is located between the reheat module and the air outlet (35).

10. The integrated temperature and humidity control unit for heat source tower heat pumps according to claim 1, characterized in that, The outlet of the first evaporator (6) is equipped with a check valve (10).

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