Constant-temperature air outlet dehumidification heat pump system

Abstract

The utility model discloses a constant-temperature air outlet dehumidification heat pump system which comprises a compressor, a condenser and an evaporator which are connected to form a refrigerant circulation loop and further comprises a first flow distribution adjusting device, a heat using device and a control device. The heat utilization device and the condenser are arranged between the compressor and the evaporator in parallel; the inlet end of the first flow distribution adjusting device is connected with the outlet end of the compressor through a pipeline, the first outlet end of the first flow distribution adjusting device is connected with the condenser through a pipeline, and the second outlet end of the first flow distribution adjusting device is connected to the heat using device through a pipeline. The control device is connected with the first flow distributing and adjusting device and controls the opening degree of the first flow distributing and adjusting device according to the return air temperature so as to control the amount of refrigerants entering the condenser and the heat using device. According to the constant-temperature air outlet dehumidification heat pump system, high-precision temperature and humidity cooperative control is achieved, temperature fluctuation is reduced, meanwhile, the energy efficiency ratio and the system stability are improved, the high-end scene requirement is met, and the stability under the complex working condition is improved.

Description

Technical Field

[0001] This utility model relates to the field of heat pump technology, and in particular to a constant temperature air outlet dehumidification heat pump system. Background Technology

[0002] Traditional constant temperature air outlet dehumidification heat pump systems all use refrigeration with electric auxiliary heating. When the room needs heating, a high-power electric heater needs to be turned on. When the room load is low and refrigeration and dehumidification are needed, a high-power electric heater is turned on for heat compensation. Due to the high operating power, not only are the requirements for electrical control equipment high, but the power consumption during operation is also high, which is not energy-saving. Especially when dehumidification is needed during the heating process, a separate electric heating compensation is required, and the system's energy consumption is high.

[0003] There are similar approaches on the market, using reheat condensers installed after the evaporator. However, this approach cannot control the heat of the supplied air, resulting in inaccurate room temperature and low comfort. Another approach uses multiple condensers installed in series, controlling heat dissipation through the airflow of one of the condensers. However, series-connected condensers cannot achieve full heat recovery, resulting in some heat loss.

[0004] With the increasing demand for precise temperature and humidity control in industries such as industry, agriculture, medicine, and high-end laboratories, the limitations of traditional dehumidification equipment in terms of energy efficiency ratio, temperature and humidity coordinated control capability, and operational stability are gradually becoming apparent. Utility Model Content

[0005] The technical problem to be solved by this utility model is to provide a constant temperature air outlet dehumidification heat pump system.

[0006] The technical solution adopted by this utility model to solve its technical problem is: constructing a constant temperature outlet dehumidification heat pump system. It includes a compressor, a condenser, and an evaporator connected in a refrigerant circulation loop. The constant temperature outlet dehumidification heat pump system further includes a first flow distribution and regulating device, a heat-using device, and a control device. The heat-using device is connected in parallel with the condenser between the compressor and the evaporator. The inlet end of the first flow distribution and regulating device is connected to the outlet end of the compressor via a pipe, the first outlet end of the first flow distribution and regulating device is connected to the condenser via a pipe, and the second outlet end of the first flow distribution and regulating device is connected to the heat-using device via a pipe. The control device is connected to the first flow distribution and regulating device and controls the opening degree of the first flow distribution and regulating device according to the return air temperature to control the amount of refrigerant entering the condenser and the heat-using device.

[0007] Furthermore, the heat-using device includes a pool water heating device and / or an air heating device arranged in parallel with the condenser between the compressor and the evaporator.

[0008] Furthermore, the heating device includes the pool water heating device and the air heating device; the constant temperature air outlet dehumidification heat pump system also includes a second flow distribution and regulating device; the inlet end of the second flow distribution and regulating device is connected to the second outlet end of the first flow distribution and regulating device through a pipe, the first outlet end of the second flow distribution and regulating device is connected to the air heating device through a pipe, and the second outlet end of the second flow distribution and regulating device is connected to the pool water heating device through a pipe; the control device is connected to the second flow distribution and regulating device to control the amount of refrigerant entering the air heating device and the pool water heating device.

[0009] Furthermore, the first flow distribution regulating device and the second flow distribution regulating device are proportional three-way valves. The opening degree of the proportional three-way valve is adjusted in real time by the control device according to the return air temperature monitored by the temperature sensor, so as to control the refrigerant flow direction and flow rate.

[0010] Furthermore, the condenser includes an outdoor heat dissipation device located outdoors; the air heating device is located indoors.

[0011] Furthermore, the refrigerant outlet of the pool water heating device is connected to the inlet of the corresponding third one-way check valve via a pipe, the refrigerant outlet of the air heating device is connected to the inlet of the corresponding second one-way check valve via a pipe, the outlet of the third one-way check valve is connected to the corresponding third flow switch device, the outlet of the second one-way check valve is connected to the corresponding second flow switch device, and the second flow switch device and the third flow switch device are connected to the inlet of the compressor via pipes.

[0012] Furthermore, the refrigerant outlet of the condenser is connected via a pipe to the inlet of a corresponding first one-way check valve, the outlet of the first one-way check valve is connected to a corresponding first flow switch device, and the first flow switch device is connected via a pipe to the inlet of the compressor.

[0013] Furthermore, the constant temperature air outlet dehumidification heat pump system also includes a liquid receiver, and an electronic expansion valve and a filter are provided between the liquid receiver and the evaporator.

[0014] Furthermore, the refrigerant outlet of the pool water heating device is connected to the liquid storage tank via a pipeline. A fourth one-way check valve is installed between the pool water heating device and the liquid storage tank. The refrigerant outlet of the pool water heating device is connected to the inlet of the fourth one-way check valve, and the inlet of the liquid storage tank is connected to the outlet of the fourth one-way check valve. The air heating device is connected to the liquid storage tank via a pipeline. A fifth one-way check valve is installed between the air heating device and the liquid storage tank. The refrigerant outlet of the air heating device is connected to the inlet of the fifth one-way check valve, and the inlet of the liquid storage tank is connected to the outlet of the fifth one-way check valve.

[0015] Furthermore, the refrigerant outlet of the outdoor heat dissipation device is connected to the liquid receiver via a pipe. A sixth one-way check valve is provided between the outdoor heat dissipation device and the liquid receiver. The refrigerant outlet of the outdoor heat dissipation device is connected to the inlet of the sixth one-way check valve, and the inlet of the liquid receiver is connected to the outlet of the sixth one-way check valve.

[0016] The implementation of this utility model has the following beneficial effects: The constant temperature air outlet dehumidification heat pump system adopts a flow distribution and adjustment device, which aims to achieve high-precision temperature and humidity coordinated control, reduce temperature fluctuations, and at the same time improve the energy efficiency ratio and system stability, meet the needs of high-end scenarios, and improve stability under complex working conditions. Attached Figure Description

[0017] To more clearly illustrate the technical solution of this utility model, the present utility model will be further described below in conjunction with the accompanying drawings and embodiments. It should be understood that the following drawings only show some embodiments of this utility model and should not be considered as a limitation of the scope. For those skilled in the art, other related drawings can be obtained from these drawings without creative effort. In the drawings:

[0018] Figure 1 This is a schematic diagram of the structure of a constant temperature air outlet dehumidification heat pump system in some embodiments of this utility model;

[0019] Figure 2 This is a schematic diagram of the structure of a constant temperature air outlet dehumidification heat pump system in some embodiments of this utility model;

[0020] Figure 3 This is a structural schematic diagram of a constant temperature air outlet dehumidification heat pump system in some embodiments of this utility model; and

[0021] Figure 4 This is a control principle diagram of a constant temperature air outlet dehumidification heat pump system in some embodiments of this utility model.

[0022] Explanation of reference numerals in the attached drawings: 01-Compressor; 02-Evaporator; 03-Electronic expansion valve; 04-Filter; 05-Liquid receiver; 06-First proportional three-way valve; 07-Second proportional three-way valve; 08-Pool water heating device; 09-Air heating device; 10-Condenser; 11-First one-way check valve; 12-Second one-way check valve; 13-Third one-way check valve; 14-Fourth one-way check valve; 15-Fifth one-way check valve; 16-Sixth one-way check valve; 17-First control valve; 18-Second control valve; 19-Third control valve; 20-Fourth control valve; 21-First flow switch device; 22-Second flow switch device; 23-Third flow switch device. Detailed Implementation

[0023] To provide a clearer understanding of the technical features, objectives, and effects of this utility model, the specific embodiments of this utility model are now described in detail with reference to the accompanying drawings. In the following description, it should be understood that the orientations or positional relationships indicated by terms such as "front," "rear," "upper," "lower," "left," "right," "longitudinal," "horizontal," "vertical," "horizontal," "top," "bottom," "inner," "outer," "head," and "tail" are based on the orientations or positional relationships shown in the accompanying drawings, and are constructed and operated in a specific orientation. They are only for the convenience of describing this technical solution and do not indicate that the device or component referred to must have a specific orientation; therefore, they should not be construed as limitations on this utility model.

[0024] It should also be noted that, unless otherwise explicitly specified and limited, terms such as "installation," "connection," "joining," "fixing," and "setting" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; 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; they can refer to the internal communication of two components or the interaction between two components. When an component is referred to as being "on" or "below" another component, the component can be located "directly" or "indirectly" on the other component, or there may be one or more intermediary components. The terms "first," "second," "third," etc., are only for the convenience of describing this technical solution and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, features defined with "first," "second," "third," etc., may explicitly or implicitly include one or more of that feature. For those skilled in the art, the specific meaning of the above terms in this utility model can be understood according to the specific circumstances.

[0025] In the following description, specific details such as particular system structures and techniques are set forth for illustrative purposes and not for limitation, in order to provide a thorough understanding of the embodiments of the present invention. However, those skilled in the art will understand that the present invention can be implemented in other embodiments without these specific details. In other instances, detailed descriptions of well-known systems, apparatuses, circuits, and methods are omitted so as not to obscure the description of the present invention with unnecessary detail.

[0026] Please see Figure 1 This utility model shows a structural schematic diagram of a constant temperature air outlet dehumidification heat pump system.

[0027] In some embodiments, a constant-temperature outlet dehumidification heat pump system is provided, which includes a compressor 01. In this embodiment, the compressor can be a variable frequency compressor, which controls the refrigerant flow by adjusting the speed to adapt to different load requirements and improve energy efficiency.

[0028] A variable frequency compressor (VFD) is a compressor that uses variable frequency drive (VFD) technology, allowing its speed to be adjusted in real time according to the system load (typically with a frequency range of 15 Hz to 120 Hz and a speed of 1500 RPM to 9000 RPM). Compared to a fixed frequency compressor (which operates at a fixed speed), VFD technology achieves flexible capacity output by changing the compressor's "operating frequency." Motor speed control: The frequency of the input current is adjusted by the VFD to control the speed of a permanent magnet synchronous motor (PMSM) or asynchronous motor. Capacity adjustment: Changes in speed directly affect the compressor's suction and discharge pressure, thus dynamically matching cooling / heating demands. This VFD compressor includes: a permanent magnet synchronous motor, a VFD driver, a pressure sensor, and a temperature sensor. The pressure sensor monitors the discharge / suction pressure in real time and feeds feedback to the control system to adjust the speed. The temperature sensor monitors the evaporator O2 / condenser I0 temperature in real time and feeds feedback to the control system to adjust the temperature, preventing overheating or overcooling. The VFD driver converts AC power into variable frequency current, feeding feedback to the control system to adjust relevant parameters, and integrates a PID algorithm to achieve precise control.

[0029] This constant-temperature outlet dehumidification heat pump system also has a first flow distribution regulating device and / or a second flow distribution regulating device, which are proportional three-way valves. The proportional three-way valves dynamically adjust the refrigerant flow direction and flow distribution, enabling flexible switching between cooling, heating, and mixed modes. Port 1 of the second proportional three-way valve 07 is connected to a heating device (such as a pool water heating device 08 or an air heating device 09). Port 2 (outlet end) of the first proportional three-way valve 06 is connected to the condenser 10. Port 3 of the first proportional three-way valve 06 is connected to the output end of the variable frequency compressor 01. By controlling the opening degree of the first proportional three-way valve 06, the connection degree of ports 1 (outlet end), 2 (outlet end), and 3 (inlet end) is controlled, thereby controlling the refrigerant flow and enabling flexible switching between various modes.

[0030] Please see Figure 2 and Figure 3 This utility model illustrates another structural schematic diagram of a constant temperature outlet dehumidification heat pump system. In this embodiment, there is one heat-using device, which can be a pool water heating device or an air heating device. Port 1 (outlet end) of the first proportional three-way valve 06 is connected to the heat-using device (such as pool water heating device 08 or air heating device 09). Port 2 (outlet end) of the first proportional three-way valve 06 is connected to the condenser 10. Port 3 (inlet end) of the first proportional three-way valve 06 is connected to the output end of the variable frequency compressor 01.

[0031] Please see Figure 4 This utility model illustrates the control principle diagram of a constant temperature air outlet dehumidification heat pump system.

[0032] See also Figure 1 , 2 3 and Figure 4 In some embodiments, a constant-temperature supply air dehumidification heat pump system is provided, which uses temperature sensors to collect return air temperature and supply air temperature to meet calculation requirements. The return air temperature is set to 28°C, with a control accuracy of ±0.1°C. When the current return air temperature is between 27.9°C and 28.1°C, the opening degree of the first proportional three-way valve 06 and / or the second proportional three-way valve 07 remains unchanged. If the current return air temperature is below 27.9°C, it is determined that there is insufficient heat in the air and the temperature is trending downwards. Therefore, the opening degree of the first proportional three-way valve 06 and / or the second proportional three-way valve 07 is reduced, increasing the refrigerant mass flow for air heating and decreasing the refrigerant mass flow for outdoor heat dissipation. This results in more heat being introduced into the air for heating, raising the air temperature. Conversely, if the current return air temperature is higher than 28.1℃, it is determined that there is too much heat in the air and the temperature is on the rise. Therefore, the opening degree of the first proportional three-way valve 06 and / or the second proportional three-way valve 07 is increased, the refrigerant mass flow for air heating is reduced, the refrigerant mass flow for outdoor heat dissipation is increased, the heat input into the air for heating is reduced, and the air temperature drops.

[0033] The core algorithm of PID is as follows: Out = Kp*e + Ki*∫e + Kd*△e;

[0034] Kp = settable constant, e = error value (target value - current value);

[0035] Ki = a settable constant, ∫e = error integral (target value - previous current value + target value - current value);

[0036] Kd = a settable constant, Δe = ((target value - current value this time) - (target value - current value two times ago)). Differential control uses the difference between the error at the current time and the previous time to predict the future. If the difference is positive, it is considered that the error is gradually increasing, and the control intensity needs to be increased to reduce the error. If the error is negative, the error is gradually decreasing, and the control intensity can be smaller to allow the target to reach the specified value smoothly and gradually.

[0037] The controller acquires temperature data once per scan cycle and sets a constant K. p =1,K i =2,K d =3;

[0038] In the first scan cycle, the return air temperature T1 = 27.5℃.

[0039] During the second scan cycle, the return air temperature T2 = 27.0℃.

[0040] Out2=1*(28-27)+2*(28-27.5+28-27)+3*((28-27)-(28-27.5))

[0041] =1+3+1.5 =5.5,

[0042] In the third scan cycle, the return air temperature T3 = 26.5℃.

[0043] Out3=1*(28-26.5)+2*(28-27+28-26.5)+3*((28-26.5)-(28-27))

[0044] =1.5 + 5 + 1.5 = 8,

[0045] In the 4th scan cycle, the return air temperature T4 = 26.0℃.

[0046] Out4=1*(28-26)+2*(28-26.5+28-26)+3*((28-26)-(28-26.5))

[0047] =2+7+1.5=10.5.

[0048] The system continuously scans and updates its calculations. The larger the OUT value, the greater the amount of air that needs to be heated. The first proportional three-way valve 06 and / or the second proportional three-way valve 07 will reduce their opening degree, increasing the refrigerant mass flow for air heating and decreasing the refrigerant mass flow for outdoor heat dissipation. This results in more heat being transferred into the air for heating, thus raising the air temperature.

[0049] In some embodiments, the return air temperature is set to 27°C, and the control accuracy is set to ±0.1°C. When the current return air temperature is between 26.9°C and 27.1°C, the opening degree of the first proportional three-way valve 06 and / or the second proportional three-way valve 07 remains unchanged. If the current return air temperature is below 26.9°C, it is determined that there is insufficient heat in the air and the temperature is trending downwards. The opening degree of the first proportional three-way valve 06 and / or the second proportional three-way valve 07 is reduced, increasing the refrigerant mass flow for air heating and decreasing the refrigerant mass flow for outdoor heat dissipation. This results in more heat being introduced into the air for heating, thus raising the air temperature. Conversely, if the current return air temperature is above 27.1°C, it is determined that there is excessive heat in the air and the temperature is trending upwards. The opening degree of the first proportional three-way valve 06 and / or the second proportional three-way valve 07 is increased, decreasing the refrigerant mass flow for air heating and increasing the refrigerant mass flow for outdoor heat dissipation. This results in less heat being introduced into the air for heating, thus lowering the air temperature.

[0050] The core algorithm of PID is as follows: Out = Kp*e + Ki*∫e + Kd*△e;

[0051] Kp = settable constant, e = error value (target value - current value);

[0052] Ki = a settable constant, ∫e = error integral (target value - previous current value + target value - current value);

[0053] Kd = a settable constant, Δe = ((target value - current value this time) - (target value - current value two times ago)). Differential control uses the difference between the error at the current time and the previous time to predict the future. If the difference is positive, it is considered that the error is gradually increasing, and the control intensity needs to be increased to reduce the error. If the error is negative, the error is gradually decreasing, and the control intensity can be smaller to allow the target to reach the specified value smoothly and gradually.

[0054] The controller acquires temperature data once per scan cycle and sets a constant K. p =1,K i =2,K d =3;

[0055] In the first scan cycle, the return air temperature T1 = 26.5℃.

[0056] During the second scan cycle, the return air temperature T2 = 26.0℃.

[0057] Out2=1*(27-26)+2*(27-26.5+27-26)+3*((27-26)-(27-26.5))

[0058] =1+3+1.5=5.5,

[0059] In the third scan cycle, the return air temperature T3 = 25.5℃.

[0060] Out3=1*(27-25.5)+2*(27-26+27-25.5)+3*((27-25.5)-(27-26))

[0061] =1.5 + 5 + 1.5 = 8,

[0062] In the 4th scan cycle, the return air temperature T4 = 25.0℃.

[0063] Out4=1*(27-25)+2*(27-25.5+27-25)+3*((27-25)-(27-25.5))

[0064] =2+7+1.5=10.5.

[0065] The system continuously scans and updates its calculations. The larger the OUT value, the greater the amount of air that needs to be heated. The first proportional three-way valve 06 and / or the second proportional three-way valve 07 will reduce their opening degree, increasing the refrigerant mass flow for air heating and decreasing the refrigerant mass flow for outdoor heat dissipation. This results in more heat being transferred into the air for heating, thus raising the air temperature.

[0066] In some embodiments, a constant-temperature outlet dehumidification heat pump system includes a compressor 01, a condenser 10, and an evaporator 02 connected in a refrigerant circulation loop. The system also includes a first flow distribution regulating device, a heat-using device, and a control device. The flow distribution regulating device can be a proportional three-way valve with one inlet end and two outlet ends. The heat-using device is connected in parallel with the condenser 10 between the compressor 01 and the evaporator 02. This parallel design allows the constant-temperature outlet dehumidification heat pump system to recover and utilize condensation heat as a heat source, reducing additional heating energy consumption. Combined with the intelligent distribution of the flow regulating device, waste heat is converted into effective heat energy while dehumidifying, achieving high-precision temperature and humidity coordinated control, and simultaneously improving the energy efficiency ratio and system stability.

[0067] The inlet of the first proportional three-way valve 06 is connected to the outlet of the compressor 01 via a pipe. The first outlet of the first proportional three-way valve 06 is connected to the condenser 10 via a pipe, and the second outlet of the first proportional three-way valve 06 is connected to the heat-using device via a pipe. The control device is connected to the first proportional three-way valve 06 and controls the opening of the first proportional three-way valve 06 according to the return air temperature to control the amount of refrigerant entering the condenser 10 and the heat-using device. This constant temperature outlet dehumidification heat pump system uses temperature sensors to collect the return air temperature and the supply air temperature to meet calculation requirements. If the return air temperature is set to m℃, with a range of 10℃-30℃ and preferred values ​​of 27℃ and 28℃, and a control accuracy of ±0.1℃, when the current return air temperature is between m-0.1℃ and m+0.1℃, the proportional three-way valve maintains its current opening. If the return air temperature is below m-0.1℃, the program determines that there is insufficient heat in the air and the temperature is trending downwards. The proportional three-way valve will reduce its opening, increasing the refrigerant mass flow for air heating and decreasing the refrigerant mass flow for outdoor heat dissipation, resulting in more heat being transferred to the air for heating and raising the air temperature. Conversely, if the return air temperature is below m+0.1℃, the program determines that there is excessive heat in the air and the temperature is trending upwards. The proportional three-way valve will increase its opening, decreasing the refrigerant mass flow for air heating and increasing the refrigerant mass flow for outdoor heat dissipation, resulting in less heat being transferred to the air for heating and a decrease in the air temperature. The first proportional three-way valve 06 dynamically distributes the refrigerant flow, enabling parallel operation of dehumidification and heating functions.

[0068] During dehumidification, some refrigerant enters the condenser 10 to release heat for heating, avoiding excessive cooling caused by traditional dehumidification. This allows for precise maintenance of the target ambient temperature, significantly improving the synchronicity of temperature and humidity control and the accuracy of temperature control. The control device adjusts the refrigerant distribution ratio in real time based on return air temperature feedback, enabling rapid response to changes in ambient temperature and humidity. For example, in low-temperature and high-humidity conditions in winter, it automatically increases the refrigerant flow of the heating device to enhance heating capacity; in summer, it prioritizes condensation dehumidification efficiency, achieving energy-saving operation that adapts to different operating conditions. The modular design of the heating device supports functional expansion, allowing connection to terminal equipment such as floor radiant heating, domestic hot water storage tanks, pool water heating devices 08, and air heating devices 09 to meet diverse heating needs. The dual-path refrigerant distribution architecture reserves interfaces for future integration of other heat recovery modules. When the return air temperature is set to 28℃ and the control accuracy is set to ±0.1℃, and the current return air temperature is between 27.9℃ and 28.1℃, the opening of the proportional three-way valve remains unchanged. If the current return air temperature is below 27.9℃, it is determined that there is insufficient heat in the air and the temperature is trending downwards. The opening degree of the proportional three-way valve will be reduced, increasing the refrigerant mass flow for air heating and decreasing the refrigerant mass flow for outdoor heat dissipation. This results in more heat being transferred into the air for heating, raising the air temperature. Conversely, if the current return air temperature is above 28.1℃, it is determined that there is excessive heat in the air and the temperature is trending upwards. The opening degree of the proportional three-way valve will be increased, decreasing the refrigerant mass flow for air heating and increasing the refrigerant mass flow for outdoor heat dissipation. This results in less heat being transferred into the air for heating, lowering the air temperature. In some embodiments, the return air temperature is set to 27℃, with a control accuracy of ±0.1℃. When the current return air temperature is between 26.9℃ and 27.1℃, the current opening degree of the proportional three-way valve remains unchanged. If the current return air temperature is below 26.9℃, it is determined that there is insufficient heat in the air and the temperature is trending downwards. The opening degree of the proportional three-way valve will be reduced, increasing the refrigerant mass flow for air heating and decreasing the refrigerant mass flow for outdoor heat dissipation. This results in more heat being transferred into the air for heating, raising the air temperature. Conversely, if the current return air temperature is above 27.1℃, it is determined that there is excessive heat in the air and the temperature is trending upwards. The opening degree of the proportional three-way valve will be increased, decreasing the refrigerant mass flow for air heating and increasing the refrigerant mass flow for outdoor heat dissipation. This results in less heat being transferred into the air for heating, lowering the air temperature.

[0069] In some embodiments, the inlet end of the second proportional three-way valve 07 is connected to the second outlet end of the first proportional three-way valve 06 via a pipeline, the first outlet end of the second proportional three-way valve 07 is connected to the heat-using device via a pipeline, and the second outlet end of the second proportional three-way valve 07 is also connected to the heat-using device via a pipeline. Through the cascaded control of the two-stage flow distribution regulating devices, the system can achieve dual dynamic regulation of the flow rate of the heat-using device. The second proportional three-way valve 07 performs secondary flow distribution based on the output state of the first proportional three-way valve 06, further improving the control accuracy of refrigerant flow and heat. The configuration of the dual regulating valves allows the system to independently adjust the flow ratio of each branch according to real-time operating conditions. When the ambient humidity changes, the two devices can quickly and collaboratively adjust the flow input of the heat-using device, reducing overheating or insufficient dehumidification caused by temperature and humidity fluctuations, and reducing ineffective energy consumption. Similarly, if needed, users can perform multi-stage cascaded control based on the flow distribution regulating devices and proportional three-way valves according to actual applications, such as three-stage cascaded control, four-stage cascaded control, and other multi-stage cascaded control.

[0070] In some embodiments, the first and second flow distribution regulating devices are proportional three-way valves. The opening degree of the proportional three-way valve is adjusted in real time by the control device based on the return air temperature monitored by the temperature sensor to control the refrigerant flow direction and flow rate. The integrated design of the three-way valve directly reduces the number of pipe bends and optimizes the pipe design. The second proportional three-way valve 07 simultaneously regulates the refrigerant flow rate and direction through a single valve body, avoiding the delay problem of conventional multi-valve coordinated control. Based on real-time feedback from the temperature sensor, the control device directly adjusts the refrigerant distribution ratio in the heating device (such as diverting it to the bypass circuit or other heating devices), achieving high-precision control with a temperature fluctuation range of ≤±0.1℃, significantly improving dehumidification stability.

[0071] In some embodiments, the constant temperature outlet dehumidification heat pump system includes a compressor 01, a condenser 10, and an evaporator 02 connected in a refrigerant circulation loop. The constant temperature outlet dehumidification heat pump system also includes a first flow distribution regulating device, a heat-using device, and a control device. The heat-using device is arranged in parallel with the condenser 10 between the compressor 01 and the evaporator 02. The inlet end of the first flow distribution regulating device is connected to the outlet end of the compressor 01 through a pipe, the first outlet end of the first flow distribution regulating device is connected to the condenser 10 through a pipe, and the second outlet end of the first flow distribution regulating device is connected to the heat-using device through a pipe. The control device is connected to the first flow distribution regulating device and controls the opening degree of the first flow distribution regulating device according to the return air temperature to control the amount of refrigerant entering the condenser 10 and the heat-using device.

[0072] In some embodiments, the heating device includes a pool water heating device 08 and an air heating device 09; the constant temperature air outlet dehumidification heat pump system also includes a second flow distribution and regulating device; the inlet end of the second flow distribution and regulating device is connected to the second outlet end of the first flow distribution and regulating device via a pipe, the first outlet end of the second flow distribution and regulating device is connected to the air heating device 09 via a pipe, and the second outlet end of the second flow distribution and regulating device is connected to the pool water heating device 08 via a pipe; a control device is connected to the second flow distribution and regulating device to control the amount of refrigerant entering the air heating device 09 and the pool water heating device 08. Direct heating of the pool water can maintain a constant water temperature, which is suitable for swimming pools, hot springs and other scenarios, improving the user experience. By circulating heating, heat loss is reduced, resulting in lower energy consumption compared to traditional external heating methods (such as gas boilers). It also avoids water temperature fluctuations that lead to microbial growth and reduces the risk of water pollution. Direct heating of the air is suitable for enclosed spaces (such as greenhouses and workshops), shortening the heating time. Through the design of the air duct, the temperature distribution within the space is made uniform, avoiding local overheating or cold areas. Heating the air in high humidity environments reduces the risk of surface condensation and protects equipment or building structures.

[0073] In some embodiments, the constant temperature air outlet dehumidification heat pump system further includes a condenser 10, which includes an outdoor heat dissipation device installed outdoors; the air heating device 09 is installed indoors. The outdoor environment typically offers greater space and airflow conditions, allowing for natural convection or wind-assisted heat dissipation, reducing reliance on mechanical fans and improving heat dissipation efficiency. By directly discharging heat to the external environment, heat accumulation inside the equipment is avoided, especially in high-temperature environments, effectively preventing thermal runaway and ensuring stable equipment operation. Transferring heat dissipation needs outdoors reduces the space occupied inside the equipment or in the server room, making it suitable for space-sensitive scenarios such as laboratories and base stations.

[0074] In some embodiments, the refrigerant outlet of the pool water heating device 08 is connected via a pipe to the inlet of the corresponding third one-way check valve 13, and the refrigerant outlet of the air heating device 09 is connected via a pipe to the inlet of the corresponding second one-way check valve 12. The outlet of the third one-way check valve 13 is connected to the corresponding third flow switch device 23, and the outlet of the second one-way check valve 12 is connected to the corresponding second flow switch device 22. The second flow switch device 22 and the third flow switch device 23 are connected to the inlet of the compressor 01 via pipes. The inlet and outlet of both the pool water heating device 08 and the air heating device 09 are refrigerant pipes. By configuring independent one-way check valves for the pool water heating device 08 and the air heating device 09 respectively, cross-contamination or pressure fluctuations caused by backflow of different media (liquid water and gaseous fluid) in the pipes can be effectively prevented, ensuring the independent operation of the two heat exchange systems and avoiding energy efficiency loss or equipment failure caused by mutual interference between systems. Each branch is equipped with an independent flow switch device, which can independently adjust the flow rate of the pool water circulation and air circulation according to actual needs. The one-way check valve prevents backflow and liquid slugging when compressor 01 stops. Combined with the flow switch's on / off control, it effectively avoids idling or overload at the compressor 01 inlet, significantly extending compressor 01's lifespan and reducing system pressure fluctuations caused by abnormal flow. When a circuit requires maintenance, isolation can be achieved by closing the corresponding flow switch, eliminating the need for a complete system shutdown and improving maintenance efficiency. This architecture supports independent start / stop of pool water heating and air heating functions, allowing for flexible configuration of operating modes based on specific application scenarios (such as pool temperature and humidity control systems, industrial heat pump systems, etc.).

[0075] The second flow switch device 22 and the third flow switch device 23 can be used to control the refrigerant in the pipes of the pool water heating device 08 and the air heating device 09 to flow back to the compressor 01. Thus, when the second flow switch device 22 and the third flow switch device 23 are not working, the refrigerant in the pipes of the second flow switch device 22 and the third flow switch device 23 is flowed back to the compressor 01 to avoid insufficient refrigerant during cooling.

[0076] In some embodiments, the condenser 10 is connected via a pipe to the inlet of a corresponding first one-way check valve 11, and the outlet of the first one-way check valve 11 is connected to a corresponding first flow switch device 21. The first flow switch device 21 is connected via a pipe to the inlet of the compressor 01. The one-way check valve effectively blocks the reverse flow of refrigerant when the compressor 01 is stopped. When the compressor 01 stops running, system pressure imbalance may cause high-temperature, high-pressure refrigerant to backflow into the compressor 01, causing liquid slugging (liquid refrigerant directly entering the compression chamber, causing mechanical damage). The physical one-way conduction characteristic of the check valve can completely eliminate this risk, significantly improving the reliability of the compressor 01 and extending the service life of core components.

[0077] When the first flow switch device 12 is turned on, the refrigerant in the condenser 10 pipe can be returned to the compressor 01, and the flow rate into the receiver 05 and evaporator 02 can be controlled as needed, thereby controlling the cooling capacity.

[0078] In some embodiments, the refrigerant outlet of the pool water heating device 08 is connected to the liquid storage tank 05 via a pipeline. A fourth one-way check valve 14 is installed between the pool water heating device 08 and the liquid storage tank 05. The refrigerant outlet of the pool water heating device 08 is connected to the inlet of the fourth one-way check valve 14, and the inlet of the liquid storage tank 05 is connected to the outlet of the fourth one-way check valve 14. An air heating device 09 is connected to the liquid storage tank 05 via a pipeline. A fifth one-way check valve 15 is installed between the air heating device 09 and the liquid storage tank 05. The refrigerant outlet of the air heating device 09 is connected to the inlet of the fifth one-way check valve 15, and the inlet of the liquid storage tank 05 is connected to the outlet of the fifth one-way check valve 15. The two heating devices are connected to the same liquid storage tank through their respective independent valves, achieving a modular configuration of the heat source. The system can independently start and stop either heating device without affecting the operation of the other, facilitating phased adjustment of the heat load (e.g., prioritizing air heating in winter), and improving control accuracy and response efficiency. The check valve effectively blocks the reverse pressure relief path of the liquid reservoir 05, preventing system pressure fluctuations caused by sudden load changes. For example, when the pool water heating device 08 stops momentarily, the valve automatically closes to prevent the high-temperature fluid in the liquid reservoir 05 from flowing back into the pump body, maintaining stable pressure in the circulation pipeline and extending equipment life.

[0079] In some embodiments, the refrigerant outlet of the outdoor heat dissipation device is connected to the liquid receiver 05 via a pipe. A sixth one-way check valve 16 is installed between the outdoor heat dissipation device and the liquid receiver 05. The refrigerant outlet of the outdoor heat dissipation device is connected to the inlet of the sixth one-way check valve 16, and the inlet of the liquid receiver 05 is connected to the outlet of the sixth one-way check valve 16. This design, through the mechanical isolation function of the one-way check valve, ensures system safety while achieving refined thermal energy management, enhanced equipment protection, and optimized operation and maintenance costs. It is particularly suitable for ground source heat pumps, air conditioning circulation systems, or industrial cooling scenarios with high requirements for temperature stability.

[0080] In some embodiments, the constant temperature outlet dehumidification heat pump system further includes a liquid receiver 05. An electronic expansion valve 03 and a filter 04 are installed between the liquid receiver 05 and the evaporator 02. The electronic expansion valve 03 dynamically adjusts the refrigerant flow rate by monitoring the superheat of the evaporator 02 in real time, ensuring that the evaporator 02 is always in optimal heat exchange condition. Compared to traditional capillary tubes, its variable opening characteristic can adapt to changes in system load, reduce ineffective throttling losses, and further improve the system's energy efficiency ratio, especially showing significant energy savings during high and low temperature switching. The filter 04 uses a multi-layer metal filter screen (such as 304 stainless steel + copper alloy) and a magnetic adsorption structure, which can effectively intercept particles such as welding slag, oxide scale, and metal debris (filtration accuracy up to 50μm), preventing impurities from entering the evaporator fins and causing localized blockage. The dual components work together to form a graded protection: the filter 04 intercepts large particulate impurities beforehand, and the electronic expansion valve 03, through PWM control, prevents liquid refrigerant from flowing back to the compressor 01, further reducing the risk of liquid slugging in the compressor 01. The system's mean time between failures (MTBF) has been improved, making it particularly suitable for highly corrosive conditions such as ammonia refrigeration.

[0081] It is understood that the above embodiments only illustrate preferred embodiments of the present utility model, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the present utility model patent. It should be noted that for those skilled in the art, the above technical features can be freely combined, and several modifications and improvements can be made without departing from the concept of the present utility model, all of which fall within the protection scope of the present utility model. Therefore, all equivalent transformations and modifications made within the scope of the claims of the present utility model should fall within the coverage of the claims of the present utility model.

Claims

1. A constant-temperature air outlet dehumidification heat pump system, comprising a compressor (01), a condenser (10), and an evaporator (02) connected in a refrigerant circulation loop, characterized in that, The constant temperature air outlet dehumidification heat pump system also includes a first flow distribution and regulation device, a heat-using device, and a control device; The heat-using device is connected in parallel with the condenser (10) between the compressor (01) and the evaporator (02); The inlet end of the first flow distribution regulating device is connected to the outlet end of the compressor (01) via a pipe, the first outlet end of the first flow distribution regulating device is connected to the condenser (10) via a pipe, and the second outlet end of the first flow distribution regulating device is connected to the heat-using device via a pipe. The control device is connected to the first flow distribution regulating device and controls the opening of the first flow distribution regulating device according to the return air temperature, so as to control the amount of refrigerant entering the condenser (10) and the heat-using device.

2. The constant temperature air outlet dehumidification heat pump system according to claim 1, characterized in that, The heat-using device includes a pool water heating device (08) and / or an air heating device (09) connected in parallel with the condenser (10) between the compressor (01) and the evaporator (02).

3. The constant temperature air outlet dehumidification heat pump system according to claim 2, characterized in that, The heat-using device includes the pool water heating device (08) and the air heating device (09); The constant temperature air outlet dehumidification heat pump system also includes a second flow distribution and adjustment device; The inlet end of the second flow distribution regulating device is connected to the second outlet end of the first flow distribution regulating device via a pipe. The first outlet end of the second flow distribution regulating device is connected to the air heating device (09) via a pipe. The second outlet end of the second flow distribution regulating device is connected to the pool water heating device (08) via a pipe. The control device is connected to the second flow distribution regulating device to control the amount of refrigerant entering the air heating device (09) and the pool water heating device (08).

4. The constant temperature air outlet dehumidification heat pump system according to claim 3, characterized in that, The first flow distribution regulating device and the second flow distribution regulating device are proportional three-way valves. The opening degree of the proportional three-way valve is adjusted in real time by the control device according to the return air temperature monitored by the temperature sensor, so as to control the refrigerant flow direction and flow rate.

5. The constant temperature air outlet dehumidification heat pump system according to claim 3, characterized in that, The condenser (10) includes an outdoor heat dissipation device installed outdoors; The air heating device (09) is installed indoors.

6. The constant temperature air outlet dehumidification heat pump system according to claim 3, characterized in that, The refrigerant outlet of the pool water heating device (08) is connected to the inlet of the corresponding third one-way check valve (13) via a pipe. The refrigerant outlet of the air heating device (09) is connected to the inlet of the corresponding second one-way check valve (12) via a pipe. The outlet of the third one-way check valve (13) is connected to the corresponding third flow switch device (23). The outlet of the second one-way check valve (12) is connected to the corresponding second flow switch device (22). The second flow switch device (22) and the third flow switch device (23) are connected to the inlet of the compressor (01) via pipes.

7. The constant temperature air outlet dehumidification heat pump system according to claim 5, characterized in that, The refrigerant outlet of the condenser (10) is connected to the inlet of the corresponding first one-way check valve (11) via a pipe. The outlet of the first one-way check valve (11) is connected to the corresponding first flow switch device (21). The first flow switch device (21) is connected to the inlet of the compressor (01) via a pipe.

8. The constant temperature air outlet dehumidification heat pump system according to claim 1, characterized in that: The constant temperature air outlet dehumidification heat pump system also includes a liquid storage tank (05), and an electronic expansion valve (03) and a filter (04) are provided between the liquid storage tank (05) and the evaporator (02).

9. The constant temperature air outlet dehumidification heat pump system according to claim 8, characterized in that, The refrigerant outlet of the pool water heating device (08) is connected to the reservoir (05) via a pipeline. A fourth one-way check valve (14) is provided between the pool water heating device (08) and the reservoir (05). The refrigerant outlet of the pool water heating device (08) is connected to the inlet of the fourth one-way check valve (14), and the inlet of the reservoir (05) is connected to the outlet of the fourth one-way check valve (14). The air heating device (09) is connected to the reservoir (05) via a pipeline. A fifth one-way check valve (15) is provided between the air heating device (09) and the reservoir (05). The refrigerant outlet of the air heating device (09) is connected to the inlet of the fifth one-way check valve (15), and the inlet of the reservoir (05) is connected to the outlet of the fifth one-way check valve (15).

10. The constant temperature air outlet dehumidification heat pump system according to claim 7, characterized in that, The refrigerant outlet of the outdoor heat dissipation device is connected to the liquid reservoir (05) via a pipe. A sixth one-way check valve (16) is provided between the outdoor heat dissipation device and the liquid reservoir (05). The refrigerant outlet of the outdoor heat dissipation device is connected to the inlet of the sixth one-way check valve (16), and the inlet of the liquid reservoir (05) is connected to the outlet of the sixth one-way check valve (16).

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