A heat pump system and a control device and method thereof

Abstract

The application discloses a heat pump system and a control device and method thereof. The device comprises: a collection unit configured to collect indoor humidity and indoor temperature of the heat pump system; and a control unit configured to control at least one of a first throttling element, a second throttling element, a fan valve assembly and an expansion unit according to the indoor humidity and the indoor temperature, so as to control the heat pump system to work in any mode of a cooling and dehumidifying mode, a cooling mode, a constant temperature and dehumidifying mode and a constant temperature and constant humidity mode in a cooling mode. The scheme can save energy consumption by setting an expander and using a set of refrigeration systems to realize independent control of temperature and humidity of the heat pump system in the cooling mode.

Description

Technical Field

[0001] This invention belongs to the field of heat pump system technology, specifically relating to a heat pump system and its control device and method, and more particularly to a heat pump system utilizing expansion and pressurization and its independent temperature and humidity control device and method. Background Technology

[0002] The proposed solutions use dehumidifying fresh air units and sensible heat multi-split systems to handle indoor temperature and humidity. Specifically, temperature and humidity control are achieved using units with different functions. This method requires one set of refrigeration units to control humidity and another set of refrigeration units to control temperature. The two sets of units are independent of each other. Although independent control of temperature and humidity is achieved, the use of two sets of units and two refrigeration units results in higher energy consumption.

[0003] The above content is only used to help understand the technical solution of the present invention and does not represent an admission that the above content is prior art. Summary of the Invention

[0004] The purpose of this invention is to provide a heat pump system and its control device and method to solve the problem that using a dehumidifying fresh air unit for humidity control and a sensible heat multi-split unit for temperature control requires two independent units, resulting in high energy consumption. The invention achieves the effect of energy saving by setting up an expander and using a single refrigeration system to realize independent control of temperature and humidity of the heat pump system in cooling mode.

[0005] This invention provides a control device for a heat pump system, the heat pump system comprising: a compression unit, a four-way valve, a first heat exchanger, a second heat exchanger, a third heat exchanger, and an expansion unit; the exhaust port of the compression unit is connected to a first end of the first heat exchanger via the four-way valve; the second end of the first heat exchanger is divided into two paths, one path passing through a first throttling element, the expansion unit, and the third heat exchanger before being connected to the intake port of the compression unit via the four-way valve, and the other path passing through a second throttling element, the second heat exchanger, and then being connected to the intake port of the compression unit via the four-way valve; The heat pump system's air duct is also equipped with an air valve assembly; the heat pump system's control device includes: a data acquisition unit and a control unit; wherein, the data acquisition unit is configured to acquire the indoor humidity and indoor temperature of the heat pump system; the control unit is configured to control at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit according to the indoor humidity and the indoor temperature, so as to control the heat pump system to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode.

[0006] In some embodiments, the compression unit includes an electric compressor and a mechanically driven compressor; the expansion unit includes an expander and a mechanical drive shaft; wherein the expander is connected to the mechanically driven compressor via the mechanical drive shaft; the exhaust port of the mechanically driven compressor is connected to the intake port of the electric compressor; the exhaust port of the electric compressor is connected to the first port of the four-way valve; the second port of the four-way valve is connected to the first end of the first heat exchanger; the third port of the four-way valve is connected to the intake port of the mechanically driven compressor; the fourth port of the four-way valve is divided into two paths, one connected to the second heat exchanger and the other connected to the third heat exchanger.

[0007] In some embodiments, the heat pump system further includes at least one of a first shut-off valve, a second shut-off valve, a third shut-off valve, a fourth shut-off valve, and a fifth shut-off valve; wherein the third port of the four-way valve is connected to the suction port of the mechanically driven compressor after passing through the first shut-off valve; the third port of the four-way valve is also connected to the suction port of the electric compressor after passing through the second shut-off valve; the second end of the first heat exchanger is divided into two paths after passing through the first throttling element, one path is connected to the second end of the third heat exchanger after passing through the expander and the fifth shut-off valve; the other path is connected to the second end of the third heat exchanger after passing through the third shut-off valve and the fourth shut-off valve; the first end of the third heat exchanger is connected to the fourth port of the four-way valve.

[0008] In some embodiments, the heat pump system further includes: a fan and a duct; the expander is disposed in the expander heat exchange duct; the duct is disposed at the air inlet and air outlet of the expander heat exchange duct; and the fan is disposed in the air inlet duct of the duct.

[0009] In some embodiments, the damper assembly includes: a first damper, a second damper, and a third damper; the first damper is disposed in a first return air duct where the expansion unit is located, and is used to adjust the return air volume of the first return air duct; the first return air duct is an expander heat exchange duct; the second damper is disposed in a second return air duct where the second heat exchanger is located, and is used to adjust the return air volume of the second return air duct; the third damper is disposed in a fresh air duct where the third heat exchanger is located, and is used to adjust the fresh air volume of the fresh air duct.

[0010] In some embodiments, the control unit controls at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit based on the indoor humidity and the indoor temperature to control the heat pump system to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode. This includes: determining, based on the indoor humidity and the indoor temperature, that the heat pump system operates in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode; adjusting at least one of the first throttling element and the second throttling element to control the evaporation temperature of the heat pump system to half the sum of the indoor dry-bulb temperature and dew point temperature of the heat pump system in the cooling mode of any one mode; and adjusting the dehumidification mode of any one mode. The control unit controls the evaporation temperature of the heat pump system to the difference between the dew point temperature of the heat pump system and a first set value; and controls the expansion unit to operate; adjusts the opening of the damper assembly to a set opening value, and then controls at least one of the damper assembly, the first throttling element, and the second throttling element according to the current opening of the damper assembly; wherein, the control unit controls at least one of the damper assembly, the first throttling element, and the second throttling element according to the current opening of the damper assembly, including: if the current opening of the damper assembly is greater than or equal to the first set opening value and less than or equal to the second set opening value, then the damper assembly is adjusted preferentially; if the current opening of the damper assembly is less than the first set opening value or greater than the second set opening value, then at least one of the first throttling element and the second throttling element is adjusted preferentially.

[0011] In some embodiments, the control unit determines, based on the indoor humidity and the indoor temperature, whether the heat pump system operates in cooling mode in cooling mode or in dehumidification mode, cooling mode, constant temperature and dehumidification mode, or constant temperature and constant humidity mode. This includes: when the indoor temperature is greater than a set indoor temperature and the indoor humidity is greater than a set humidity, controlling at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to control the heat pump system to operate in cooling and dehumidification mode, and controlling it at set intervals based on the re-collected indoor humidity and indoor temperature; when the indoor temperature is greater than the set indoor temperature and the indoor humidity is less than or equal to the set humidity, controlling... The system controls at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to operate the heat pump system in a cooling mode; when the indoor temperature is less than or equal to the indoor set temperature and the indoor humidity is greater than the set humidity, the system controls at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to operate the heat pump system in a constant temperature and dehumidification mode; when the indoor temperature is less than or equal to the indoor set temperature and the indoor humidity is less than or equal to the set humidity, the system controls at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to operate the heat pump system in a constant temperature and constant humidity mode.

[0012] In some embodiments, the control unit adjusts the damper assembly by: during temperature control in any mode, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and a second set value, then the corresponding damper in the damper assembly increases its opening by a set degree; if the indoor dry-bulb temperature of the heat pump system is less than the difference between the indoor set temperature and the second set value, then the corresponding damper in the damper assembly decreases its opening by a set degree; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, then... The opening degree of the corresponding air valve in the air valve assembly remains unchanged; during the humidity control process in any mode, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, the opening degree of the corresponding air valve in the air valve assembly increases; if the relative humidity of the heat pump system is less than the difference between the set humidity and the third set value, the opening degree of the corresponding air valve in the air valve assembly decreases; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, the opening degree of the corresponding air valve in the air valve assembly remains unchanged.

[0013] In some embodiments, the control unit adjusts at least one of the first throttling element and the second throttling element, comprising: during temperature control in any mode, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, then the opening degree of the corresponding throttling element in the first throttling element and the second throttling element decreases; if the indoor dry-bulb temperature of the heat pump system is less than the sum of the indoor set temperature and the second set value, and the indoor dry-bulb temperature of the heat pump system is not equal to the difference between the indoor set temperature and the second set value, then the opening degree of the corresponding throttling element in the first throttling element and the second throttling element increases; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, then... The opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged; during the humidity control process in any mode, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements decreases; if the relative humidity of the heat pump system is less than the sum of the set humidity and the third set value, and the relative humidity of the heat pump system is not equal to the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements increases; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged.

[0014] In some embodiments, where the heat pump system further includes at least one of a first shut-off valve, a second shut-off valve, a third shut-off valve, a fourth shut-off valve, and a fifth shut-off valve, the compression unit includes an electric compressor and a mechanically driven compressor, the expansion unit includes an expander, and the air valve assembly includes a first air valve, a second air valve, and a third air valve, the control unit controls the operation of the expansion unit, including: when the heat pump system is operating in a cooling and dehumidification mode in a cooling mode, the refrigerant discharged from the exhaust port of the electric compressor, after passing through the four-way valve and the first heat exchanger, is divided into two refrigerant paths: one path passes through the first... The throttling element controls the evaporation temperature of the heat pump system. At this time, the third and fourth shut-off valves are closed, and the expander expands, driving the mechanically driven compressor to rotate. The airflow is controlled by the first and third air valves. Another refrigerant, after passing through the second throttling element which controls the evaporation temperature of the heat pump system, controls the airflow through the second air valve. After the two refrigerants mix, the first shut-off valve opens and the second shut-off valve closes, achieving two compressions through the mechanically driven compressor and the electric compressor. When the heat pump system is operating in cooling mode, the electric compressor... The refrigerant discharged from the exhaust port of the machine, after passing through the four-way valve and the first heat exchanger, is divided into two refrigerant streams: one stream controls the evaporation temperature of the heat pump system through the first throttling element, at which point the third and fourth shut-off valves are closed, the expander expands and performs work, driving the mechanically driven compressor to rotate, and the airflow is controlled by the first air valve; the other stream controls the evaporation temperature of the heat pump system through the second throttling element, and the airflow is controlled by the second air valve. After the two refrigerant streams are mixed, the first shut-off valve is opened and the second shut-off valve is closed, and the mechanically driven compressor and the electric compressor achieve [the desired effect]. Double compression; when the heat pump system is operating in the constant temperature and dehumidification mode of cooling mode, the refrigerant discharged from the exhaust port of the electric compressor passes through the four-way valve and the first heat exchanger, and then the second throttling element is closed. The refrigerant controls the evaporation temperature of the heat pump system through the first throttling element. At this time, the third and fourth shut-off valves are closed, the expander expands and does work, driving the mechanically driven compressor to rotate. The air volume is controlled by the first and third air valves. By controlling the first shut-off valve to open and the second shut-off valve to close, double compression is achieved through the mechanically driven compressor and the electric compressor.When the heat pump system operates in a constant temperature and humidity mode within the cooling mode, the refrigerant discharged from the exhaust port of the electric compressor passes through the four-way valve and the first heat exchanger. The second throttling element closes, and the refrigerant's evaporation temperature is controlled by the first throttling element. At this time, the third and fourth shut-off valves are closed, and the expander expands, driving the mechanically driven compressor to rotate. The airflow is controlled by the third air valve. The first shut-off valve is closed, and the second shut-off valve is opened, allowing compression to be achieved through the electric compressor.

[0015] In conjunction with the above-described device, the present invention further provides a heat pump system, comprising: a control device for the heat pump system described above.

[0016] In conjunction with the aforementioned heat pump system, the present invention further provides a control method for a heat pump system, comprising: acquiring indoor humidity and indoor temperature of the heat pump system; and controlling at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit based on the indoor humidity and the indoor temperature, so as to control the heat pump system to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode.

[0017] In some embodiments, controlling at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit based on the indoor humidity and the indoor temperature to control the heat pump system to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, includes: determining, based on the indoor humidity and the indoor temperature, that the heat pump system operates in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode; adjusting at least one of the first throttling element and the second throttling element to control the evaporation temperature of the heat pump system to half the sum of the indoor dry-bulb temperature and dew point temperature of the heat pump system in the cooling mode of any one of the following modes; and controlling the dehumidification mode of any one of the following modes: The following steps are taken: controlling the evaporation temperature of the heat pump system to the difference between the dew point temperature of the heat pump system and a first set value; controlling the expansion unit to operate; adjusting the opening degree of the air valve assembly to a set opening degree value, and then controlling at least one of the air valve assembly, the first throttling element, and the second throttling element according to the current opening degree of the air valve assembly; wherein, controlling at least one of the air valve assembly, the first throttling element, and the second throttling element according to the current opening degree of the air valve assembly includes: if the current opening degree of the air valve assembly is greater than or equal to the first set opening degree value and less than or equal to the second set opening degree value, then the air valve assembly is adjusted preferentially; if the current opening degree of the air valve assembly is less than the first set opening degree value or greater than the second set opening value, then at least one of the first throttling element and the second throttling element is adjusted preferentially.

[0018] In some embodiments, determining whether the heat pump system operates in cooling mode in cooling mode, based on the indoor humidity and the indoor temperature, involves controlling at least one of the following modes: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode. This includes: when the indoor temperature is greater than a set indoor temperature and the indoor humidity is greater than a set humidity, controlling at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to control the heat pump system to operate in cooling and dehumidification mode, and controlling this mode at set intervals based on the re-collected indoor humidity and indoor temperature; when the indoor temperature is greater than the set indoor temperature and the indoor humidity is less than or equal to the set humidity, controlling the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to operate in cooling and dehumidification mode. At least one of a throttling element, a second throttling element, the air valve assembly, and the expansion unit is used to control the heat pump system to operate in a cooling mode; when the indoor temperature is less than or equal to the indoor set temperature and the indoor humidity is greater than the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in a constant temperature and dehumidification mode; when the indoor temperature is less than or equal to the indoor set temperature and the indoor humidity is less than or equal to the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in a constant temperature and constant humidity mode.

[0019] In some embodiments, adjusting the damper assembly includes: during temperature control in any mode, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and a second set value, then the corresponding damper in the damper assembly increases its opening by a set degree; if the indoor dry-bulb temperature of the heat pump system is less than the difference between the indoor set temperature and the second set value, then the corresponding damper in the damper assembly decreases its opening by a set degree; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, then the opening of the corresponding damper in the damper assembly remains unchanged; during humidity control in any mode, if the relative humidity of the heat pump system is greater than the sum of the set humidity and a third set value, then the corresponding damper in the damper assembly increases its opening by a set degree; if the relative humidity of the heat pump system is less than the difference between the set humidity and the third set value, then the corresponding damper in the damper assembly decreases its opening by a set degree; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, then the opening of the corresponding damper in the damper assembly remains unchanged.

[0020] In some embodiments, adjusting at least one of the first throttling element and the second throttling element includes: during temperature control in any mode, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, then the opening degree of the corresponding throttling element in the first throttling element and the second throttling element decreases; if the indoor dry-bulb temperature of the heat pump system is less than the sum of the indoor set temperature and the second set value, and the indoor dry-bulb temperature of the heat pump system is not equal to the difference between the indoor set temperature and the second set value, then the opening degree of the corresponding throttling element in the first throttling element and the second throttling element increases; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, then the opening degree of the first throttling element increases. The opening degree of the corresponding throttling element in the first throttling element and the second throttling element remains unchanged; during the humidity control process in any of the modes, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, the opening degree of the corresponding throttling element in the first throttling element and the second throttling element decreases; if the relative humidity of the heat pump system is less than the sum of the set humidity and the third set value, and the relative humidity of the heat pump system is not equal to the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first throttling element and the second throttling element increases; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first throttling element and the second throttling element remains unchanged.

[0021] In some embodiments, where the heat pump system further includes at least one of a first shut-off valve, a second shut-off valve, a third shut-off valve, a fourth shut-off valve, and a fifth shut-off valve, the compression unit includes an electric compressor and a mechanically driven compressor, the expansion unit includes an expander, and the air valve assembly includes a first air valve, a second air valve, and a third air valve, controlling the operation of the expansion unit includes: when the heat pump system is operating in a cooling and dehumidification mode in a cooling mode, the refrigerant discharged from the exhaust port of the electric compressor, after passing through the four-way valve and the first heat exchanger, is divided into two refrigerant paths: one path is controlled by the first throttling element. When the evaporation temperature of the heat pump system reaches a certain level, the third and fourth shut-off valves are closed. The expander expands and performs work, driving the mechanically driven compressor to rotate. The airflow is controlled by the first and third air valves. Another refrigerant, passing through the second throttling element, controls the evaporation temperature of the heat pump system and controls the airflow by the second air valve. After the two refrigerants mix, the first shut-off valve opens and the second shut-off valve closes, achieving two compressions through the mechanically driven compressor and the electric compressor. When the heat pump system is operating in cooling mode, the exhaust gas from the electric compressor... The refrigerant discharged from the outlet, after passing through the four-way valve and the first heat exchanger, is divided into two refrigerant streams: one stream controls the evaporation temperature of the heat pump system through the first throttling element, at which point the third and fourth shut-off valves are closed, the expander expands and performs work, driving the mechanically driven compressor to rotate, and the airflow is controlled by the first air valve; the other stream controls the evaporation temperature of the heat pump system through the second throttling element, and the airflow is controlled by the second air valve. After the two refrigerant streams are mixed, the first shut-off valve is opened and the second shut-off valve is closed, achieving two cycles through the mechanically driven compressor and the electric compressor. Compression; when the heat pump system is operating in the constant temperature and dehumidification mode of the cooling mode, the refrigerant discharged from the exhaust port of the electric compressor passes through the four-way valve and the first heat exchanger, and then the second throttling element is closed. The refrigerant controls the evaporation temperature of the heat pump system through the first throttling element. At this time, the third and fourth shut-off valves are closed, the expander expands and does work, driving the mechanically driven compressor to rotate. The air volume is controlled by the first and third air valves. The first shut-off valve is opened and the second shut-off valve is closed, and two compressions are achieved through the mechanically driven compressor and the electric compressor.When the heat pump system operates in a constant temperature and humidity mode within the cooling mode, the refrigerant discharged from the exhaust port of the electric compressor passes through the four-way valve and the first heat exchanger. The second throttling element closes, and the refrigerant's evaporation temperature is controlled by the first throttling element. At this time, the third and fourth shut-off valves are closed, and the expander expands, driving the mechanically driven compressor to rotate. The airflow is controlled by the third air valve. The first shut-off valve is closed, and the second shut-off valve is opened, allowing compression to be achieved through the electric compressor.

[0022] Therefore, the solution of the present invention, by setting up an expander and using a refrigeration system, combines indoor temperature and humidity, as well as the required set temperature and humidity, to divide the refrigerant into two flow paths, and controls two electronic expansion valves on the two flow paths respectively, to adjust the evaporation temperature of the two paths. By controlling the difference in evaporation temperature, the air can be cooled or dehumidified. Thus, by setting up an expander and using a refrigeration system, the heat pump system can achieve independent control of temperature and humidity in refrigeration mode, which can save energy consumption.

[0023] Other features and advantages of the invention will be set forth in the description which follows, and will be apparent in part from the description, or may be learned by practicing the invention.

[0024] The technical solution of the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the structure of a control device for a heat pump system according to an embodiment of the present invention;

[0026] Figure 2 This is a schematic diagram of an embodiment of the heat pump system utilizing expansion and pressurization according to the present invention;

[0027] Figure 3 This is a schematic diagram of an embodiment of the temperature and humidity independent control air system of the heat pump system utilizing expansion and pressurization of the present invention.

[0028] Figure 4 This is a schematic diagram of the temperature and humidity control judgment process of an embodiment of the independent temperature and humidity control air system of the heat pump system utilizing expansion and pressurization of the present invention.

[0029] Figure 5 This is a flowchart illustrating another embodiment of the independent temperature and humidity control air system of the heat pump system utilizing expansion and pressurization of the present invention. Specifically, it is a flowchart illustrating the method of controlling temperature and humidity using the first air valve, the second air valve, and the third air valve when the air valve opening is between 20% and 80%.

[0030] Figure 6This is a flowchart illustrating another embodiment of the independent temperature and humidity control air system of the heat pump system utilizing expansion and pressurization of the present invention. Specifically, it is a flowchart illustrating the method of controlling temperature and humidity by the first electronic expansion valve and the second electronic expansion valve when the air valve opening is less than 20% and greater than 80%.

[0031] Figure 7 This is a flowchart illustrating an embodiment of the control method for the heat pump system of the present invention;

[0032] Figure 8 This is a schematic flowchart of an embodiment of the method of the present invention, which controls the heat pump system to operate in any one of the following modes: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode.

[0033] Referring to the accompanying drawings, the reference numerals in the embodiments of the present invention are as follows:

[0034] 1-First shut-off valve; 2-Second shut-off valve; 3-First electronic expansion valve; 4-Second electronic expansion valve; 5-Four-way valve; 6-First heat exchanger; 7-Second heat exchanger; 8-Third heat exchanger; 9-Electric compressor; 10-Mechanical transmission compressor; 11-Mechanical transmission shaft; 12-Expander; 13-Expander heat exchange duct; 14-Fan; 15-Air duct; 16-Fourth shut-off valve; 17-First indoor return air control system; 18-Second indoor return air control system; 19-Outdoor fresh air control system; 20-First air valve; 21-Second air valve; 22-Third air valve; 23-Third shut-off valve; 24-Fifth shut-off valve. Detailed Implementation

[0035] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below in conjunction with specific embodiments and corresponding drawings. Obviously, the described embodiments are only a part of the embodiments of this invention, and not all of them. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this invention.

[0036] In solutions that use dehumidifying fresh air units and sensible heat multi-split systems to manage indoor temperature and humidity, the sensible heat multi-split system can be used to heat the indoor temperature during transitional seasons. However, the system in this solution lacks electric heating and a reversing device; it is merely a unidirectional circulation system and cannot achieve the stated air heating function. In other words, this solution lacks a four-way reversing valve and can only achieve either cooling or heating, meaning it can only perform one function and cannot switch between cooling and heating. Furthermore, while the solution describes the supply fan automatically adjusting its airflow based on the indoor temperature, it does not explain how this adjustment is performed.

[0037] According to an embodiment of the present invention, a control device for a heat pump system is provided. See also Figure 1 The diagram shows a structural schematic of an embodiment of the device of the present invention. The heat pump system includes: a compression unit, a four-way valve 5, a first heat exchanger 6, a second heat exchanger 7, a third heat exchanger 8, and an expansion unit. The exhaust port of the compression unit, after passing through the four-way valve 5, is connected to the first end of the first heat exchanger 6. The second end of the first heat exchanger 6 is divided into two paths: one path passes through a first throttling element, the expansion unit, and the third heat exchanger 8, and then through the four-way valve 5 to the intake port of the compression unit; the other path passes through a second throttling element, the second heat exchanger 7, and then through the four-way valve 5 to the intake port of the compression unit. The first throttling element is, for example, a first electronic expansion valve 3, and the second throttling element is, for example, a second electronic expansion valve 4. A damper assembly is also provided in the air duct of the heat pump system.

[0038] The control device of the heat pump system includes: a data acquisition unit and a control unit.

[0039] The acquisition unit is configured to acquire the indoor humidity and indoor temperature of the heat pump system.

[0040] The control unit is configured to control at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit according to the indoor humidity and the indoor temperature, so as to control the heat pump system to operate in any one of the following modes in the cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, thereby achieving at least independent control of temperature and humidity of the heat pump system in the cooling mode.

[0041] This invention provides a heat pump system utilizing expansion and pressurization, along with an independent temperature and humidity control scheme. Using a single refrigeration system, and considering indoor temperature and humidity, as well as the desired set temperature and humidity, the refrigerant is divided into two flow paths. Two electronic expansion valves on each path are controlled to adjust the evaporation temperature of the two paths. By controlling the difference in evaporation temperature, the air conditioner's state is controlled, resulting in either cooling or dehumidification. This achieves independent temperature and humidity control of the heat pump system in cooling mode. By combining the adjustment of the electronic expansion valves to control the evaporation temperature, the adjustment of the airflow control assembly, and the use of an expander, precise temperature and humidity control is achieved while simultaneously saving energy. The combination of electronic expansion valves and airflow control schemes makes the control of temperature and humidity more precise.

[0042] In some embodiments, the compression unit includes an electric compressor 9 and a mechanically driven compressor 10. The expansion unit includes an expander 12 and a mechanical drive shaft 11.

[0043] The expander 12 is connected to the mechanical transmission compressor 10 via the mechanical transmission shaft 11. The exhaust port of the mechanical transmission compressor 10 is connected to the intake port of the electric compressor 9. The exhaust port of the electric compressor 9 is connected to the first port of the four-way valve 5, such as port D of the four-way valve 5.

[0044] The second port of the four-way valve 5, such as port C of the four-way valve 5, is connected to the first end of the first heat exchanger 6. The third port of the four-way valve 5, such as port S of the four-way valve 5, is connected to the suction port of the mechanically driven compressor 10. The third port of the four-way valve 5, such as port S of the four-way valve 5, is connected to the suction port of the electric compressor 9.

[0045] The fourth valve port of the four-way valve 5, such as port E of the four-way valve 5, is divided into two paths: one path connects to the second heat exchanger 7, and the other path connects to the third heat exchanger 8.

[0046] In some embodiments, the heat pump system further includes at least one of a first shut-off valve 1, a second shut-off valve 2, a third shut-off valve 23, a fourth shut-off valve 16, and a fifth shut-off valve 24.

[0047] The third valve port of the four-way valve 5, such as the S port of the four-way valve 5, is connected to the suction port of the mechanical transmission compressor 10 after passing through the first shut-off valve 1.

[0048] The third valve port of the four-way valve 5, like the S port of the four-way valve 5, is connected to the suction port of the electric compressor 9 via the second shut-off valve 2.

[0049] The second end of the first heat exchanger 6, after passing through the first throttling element, splits into two paths. One path passes through the expander 12 and the fifth shut-off valve 24, connecting to the second end of the third heat exchanger 8. The other path passes through the third shut-off valve 23 and the fourth shut-off valve 16, connecting to the second end of the third heat exchanger 8. The first end of the third heat exchanger 8 is connected to the fourth port of the four-way valve 5, such as port E of the four-way valve 5.

[0050] In some embodiments, the heat pump system further includes a fan 14 and a duct 15.

[0051] The expander 12 is disposed in the expander heat exchange duct 13. The air duct 15 is disposed at the air inlet and air outlet of the expander heat exchange duct 13. The fan 14 is disposed in the air inlet pipe of the air duct 15.

[0052] Figure 2 This is a schematic diagram of an embodiment of the heat pump system utilizing expansion and pressurization according to the present invention. Figure 2As shown, the heat pump system utilizing expansion and pressurization includes: a first shut-off valve 1, a second shut-off valve 2, a first electronic expansion valve 3, a second electronic expansion valve 4, a four-way valve 5, a first heat exchanger 6, a second heat exchanger 7, a third heat exchanger 8, an electric compressor 9, a mechanically driven compressor 10, a mechanically driven shaft 11, an expander 12, an expander heat exchange duct 13, a fan 14, a duct 15, a fourth shut-off valve 16, a third shut-off valve 23, and a fifth shut-off valve 24.

[0053] exist Figure 2 In the example shown, the exhaust port of the electric compressor 9 is connected to port D of the four-way valve 5. Port E of the four-way valve 5 splits into two refrigerant flow paths: one refrigerant flow path connects to the first end of the second heat exchanger 7, and the other refrigerant flow path connects to the first end of the third heat exchanger 8. The second end of the second heat exchanger 7 is connected to the second end of the first heat exchanger 6 via the second electronic expansion valve 4. The first end of the first heat exchanger 6 is connected to port C of the four-way valve 5. The second end of the first heat exchanger 6 is connected to the first end of the expander 12 via the first electronic expansion valve 3. The first end of the expander 12 is connected to the second end of the third heat exchanger 8 via the third shut-off valve 23 and the fourth shut-off valve 16. The second end of the third heat exchanger 8 is connected to the second end of the expander 12 via the fifth shut-off valve 24. The expander 12 is located in the expander heat exchange duct 13. The fan 14 and the duct 15 are connected to the air inlet of the expander heat exchange duct 13. The expander heat exchange duct 13 also has an exhaust port.

[0054] exist Figure 2 In the example shown, the suction port of the electric compressor 9 is connected to the S port of the four-way valve 5 via the second shut-off valve 2. The suction port of the electric compressor 9 is also connected to the discharge port of the mechanically driven compressor 10. The suction port of the mechanically driven compressor 10 is connected to the S port of the four-way valve 5 via the first shut-off valve 1. The mechanically driven compressor 10 is connected to the expander 12 via the mechanical drive shaft 11.

[0055] In some embodiments, the damper assembly includes a first damper 20, a second damper 21, and a third damper 22.

[0056] The first air valve 20 is installed in the first return air duct where the expansion unit is located, and is used to adjust the return air volume of the first return air duct. The first return air duct is the expander heat exchange duct 13.

[0057] The second air valve 21 is installed in the second return air duct where the second heat exchanger 7 is located, and is used to adjust the return air volume of the second return air duct.

[0058] The third air valve 22 is installed in the fresh air duct where the third heat exchanger 8 is located, and is used to adjust the fresh air volume of the fresh air duct.

[0059] Figure 3 This is a schematic diagram of an embodiment of the independent temperature and humidity control air system of the present invention, utilizing an expansion-pressurized heat pump system. Figure 3 As shown, the temperature and humidity independent control air system of the heat pump system using expansion and pressurization includes: a first indoor return air control system 17, a second indoor return air control system 18, an outdoor fresh air control system 19, a first air valve 20, a second air valve 21, and a third air valve 22.

[0060] exist Figure 3 In the example shown, a first air valve 20 is installed in the first return air duct of the first indoor return air control system 17. The return air in the first return air duct passes through the first air valve 20 and flows to the expander heat exchange duct 13. In the second return air duct of the second indoor return air control system 18, a second air valve 21 is installed. The return air in the second return air duct passes through the second air valve 21 and flows to the second heat exchanger 7.

[0061] A third air valve 22 is installed in the fresh air duct of the outdoor fresh air control system 19. Fresh air in the fresh air duct passes through the third air valve 22 and flows to the third heat exchanger 8.

[0062] In some embodiments, the indoor humidity includes: indoor relative humidity. The indoor temperature includes: indoor dry-bulb temperature.

[0063] The control unit, based on the indoor humidity and the indoor temperature, controls at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to control the heat pump system to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, including:

[0064] The control unit is further configured to determine, based on the indoor humidity and the indoor temperature, whether the heat pump system operates in cooling mode in any one of the following modes: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, or constant temperature and constant humidity mode.

[0065] The control unit is further configured to adjust at least one of the first throttling element and the second throttling element to control the evaporation temperature of the heat pump system to half the sum of the indoor dry-bulb temperature and dew point temperature of the heat pump system in the cooling mode of any of the modes; and to control the evaporation temperature of the heat pump system to the difference between the dew point temperature of the heat pump system and a first set value in the dehumidification mode of any of the cooling and dehumidification modes, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, to control the evaporation temperature of the heat pump system to half the sum of the indoor dry-bulb temperature and dew point temperature of the heat pump system; and to control the expansion unit to operate in the dehumidification mode of any of the cooling and dehumidification modes, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode.

[0066] The control unit is further configured to adjust the opening of the damper assembly to a set opening value, and then control at least one of the damper assembly, the first throttling element, and the second throttling element according to the current opening of the damper assembly.

[0067] The control unit controls at least one of the air valve assembly, the first throttling element, and the second throttling element according to the current opening degree of the air valve assembly, including: if the current opening degree of the air valve assembly is greater than or equal to a first preset opening value and less than or equal to a second preset opening value, then the air valve assembly is preferentially adjusted; if the current opening degree of the air valve assembly is less than the first preset opening value or greater than the second preset opening value, then at least one of the first throttling element and the second throttling element is preferentially adjusted.

[0068] In the solution of the present invention, Figure 4 This is a schematic diagram of the temperature and humidity control judgment process of an embodiment of the independent temperature and humidity control air system of the heat pump system utilizing expansion and pressurization of the present invention. Figure 5 This is a flowchart illustrating another embodiment of the independent temperature and humidity control air system of the heat pump system utilizing expansion and pressurization of the present invention. Specifically, it is a flowchart illustrating the method of controlling temperature and humidity using the first air valve, the second air valve, and the third air valve when the air valve opening is between 20% and 80%. Figure 6 This is a flowchart illustrating another embodiment of the independent temperature and humidity control air system of the heat pump system utilizing expansion and pressurization of the present invention. Specifically, it is a flowchart illustrating the method of controlling temperature and humidity by the first electronic expansion valve and the second electronic expansion valve when the air valve opening is less than 20% and greater than 80%.

[0069] See Figure 4 , Figure 5 and Figure 6The example shown illustrates a method for independent temperature and humidity control of airflow using an expansion-pressurized heat pump system, including:

[0070] Step 1: Detect the indoor temperature and humidity and compare them with the set temperature and humidity to determine the required mode.

[0071] Step 2: First, adjust the electronic expansion valve, using the cooling mode to control the evaporation temperature at T. z = (Indoor dry bulb temperature T1 + Dew point temperature T) L ) / 2, dehumidification mode controls evaporation temperature T z = Dew point temperature T L -2.

[0072] Step 3: Adjust the opening of the corresponding air valve to 50% to give the air valve an initial state, and then adjust it according to the temperature and humidity. During the temperature and humidity adjustment process, after the air valve has been adjusted to its initial state, it may not be possible to meet the temperature and humidity control requirements by adjusting the air valve alone. Other control methods are required, such as the adjustment methods in steps 4 and 5.

[0073] Step 4: When the damper opening is detected to be between 20% and 80%, damper adjustment should be prioritized.

[0074] Step 5: When the damper opening is detected to be less than 20% or greater than 80%, adjust the electronic expansion valve. In this step, considering that if the damper opening is less than 20%, it will be completely closed, resulting in no airflow, while the airflow change is not particularly significant when the damper opening is 80% or higher, the temperature and humidity can be controlled according to the logic of the electronic expansion valve. If the temperature is lowered, the electronic expansion valve is closed less in increments of -1°C evaporation temperature; if the evaporation temperature is raised, the electronic expansion valve is opened more in increments of +1°C evaporation temperature.

[0075] The present invention combines two adjustment methods—electronic expansion valves and air valves—to achieve temperature and humidity control. In cooling mode, the system controls the evaporation temperature to meet different requirements by adjusting the two electronic expansion valves, controls the airflow by adjusting the air valves, and recovers energy lost due to throttling using an expander.

[0076] Some solutions lack an expander, resulting in energy inefficiency. Furthermore, temperature and humidity control is achieved through a fresh air dehumidifier and multiple indoor units, leading to poor economic efficiency. The installation of multiple indoor units is more complex, with extended refrigerant piping increasing resistance and losses. In contrast, this invention integrates the dehumidification system with the cooling system, return air system, and fresh air system. It controls different evaporation temperatures via an electronic expansion valve to achieve dehumidification or cooling, and simultaneously utilizes the expander to recover some energy, resulting in greater energy savings.

[0077] Other solutions lack an expander, resulting in energy inefficiency. In temperature and humidity control, cooling and dehumidification occur simultaneously during air treatment, preventing separate control of temperature and humidity. The solution of this invention, however, allows for separate cooling or simultaneous cooling and dehumidification processes, enabling precise control of indoor temperature and humidity by adjusting airflow, resulting in more accurate control.

[0078] In some implementations, the control unit determines, based on the indoor humidity and the indoor temperature, whether the heat pump system operates in cooling mode in any of the following modes: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, or constant temperature and constant humidity mode, including any of the following control scenarios:

[0079] The first control scenario: The control unit is further configured to, when the indoor temperature is greater than the set indoor temperature and the indoor humidity is greater than the set humidity, control at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to control the heat pump system to operate in cooling and dehumidification mode, and to control the system at intervals based on the re-collected indoor humidity and indoor temperature, that is, based on the re-collected indoor humidity and indoor temperature, control at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to re-control the heat pump system to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode.

[0080] The second control scenario: The control unit is further configured to control at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to control the heat pump system to operate in cooling mode when the indoor temperature is greater than the indoor set temperature and the indoor humidity is less than or equal to the set humidity.

[0081] The third control scenario: The control unit is further configured to control at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit when the indoor temperature is less than or equal to the indoor set temperature and the indoor humidity is greater than the set humidity, so as to control the heat pump system to operate in a constant temperature and dehumidification mode.

[0082] The fourth control scenario: The control unit is further configured to control at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit when the indoor temperature is less than or equal to the indoor set temperature and the indoor humidity is less than or equal to the set humidity, so as to control the heat pump system to operate in a constant temperature and humidity mode.

[0083] like Figure 4 As shown, the temperature and humidity control judgment process of the independent temperature and humidity control air system using the expansion and pressurization heat pump system, i.e., the temperature and humidity control judgment process in cooling mode, includes:

[0084] Step 11: Detect the indoor dry-bulb temperature T1 and wet-bulb temperature T using an indoor temperature and humidity sensor. w Relative humidity RH1, etc.

[0085] Step 12: Calculate the dew point temperature T L Determine the indoor set temperature Ta and the humidity RHa.

[0086] Among them, the dew point temperature T is obtained. L There are many ways to do it.

[0087] For example, the dew point temperature T can be obtained by querying the enthalpy diagram. L An enthalpy-humidity diagram is a graphical representation of the relationships between various parameters of moist air.

[0088] For example, the dew point temperature T can be calculated using the Maglas formula. L Specifically, the dew point temperature T can be calculated using the following method. L :

[0089] T L =237.3 / (7.5 / (lg(e / 6.11))-1).

[0090] in, It refers to relative humidity, E. S =E0×10 a×t / (b+t) E0 = 6.11 hPa, b = 237.3, a = 7.5, and t is the dry-bulb temperature.

[0091] Step 13: Determine whether the indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta, and determine whether the relative humidity RH1 is greater than the set humidity RHa.

[0092] (1) When it is determined that the indoor dry bulb temperature T1 is greater than the indoor set temperature Ta and the relative humidity RH1 is greater than the set humidity RHa, the heat pump system will enter the cooling + dehumidification mode, and the indoor dry and wet bulb temperatures will be detected every 2 minutes. The system will cycle through the detection and determine the corresponding logic.

[0093] (2) When the indoor dry bulb temperature T1 is greater than the indoor set temperature Ta and the relative humidity RH1 is less than or equal to the set humidity RHa, the heat pump system will switch to cooling mode.

[0094] (3) When it is determined that the indoor dry bulb temperature T1 ≤ indoor set temperature Ta and the relative humidity RH1 > set humidity RHa, the heat pump system will operate in constant temperature + dehumidification mode.

[0095] (4) When the indoor dry bulb temperature T1 is determined to be less than the indoor set temperature Ta and the relative humidity RH1 is less than the set humidity RHa, the heat pump system will operate in constant temperature + constant humidity mode.

[0096] In some embodiments, the control unit adjusts the damper assembly, including any of the following damper assembly adjustment states:

[0097] The first type of damper assembly adjustment: Specifically, the control unit is further configured to, during temperature control in any of the modes, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, then the corresponding damper in the damper assembly increases its opening by a set degree. If the indoor dry-bulb temperature of the heat pump system is less than the difference between the indoor set temperature and the second set value, then the corresponding damper in the damper assembly decreases its opening by a set degree. If the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value, or the difference between the indoor set temperature and the second set value, then the opening of the corresponding damper in the damper assembly remains unchanged.

[0098] The second type of damper assembly adjustment: Specifically, the control unit is further configured to, during humidity control in any of the modes, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, then the corresponding damper in the damper assembly increases its opening by a set degree. If the relative humidity of the heat pump system is less than the difference between the set humidity and the third set value, then the corresponding damper in the damper assembly decreases its opening by a set degree. If the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value, or the difference between the set humidity and the third set value, then the opening of the corresponding damper in the damper assembly remains unchanged.

[0099] like Figure 4 As shown, the temperature and humidity control judgment process of the independent temperature and humidity control air system using the expansion and pressurization heat pump system also includes:

[0100] (5) Air valve control opening conditions: the first indoor return air control system 17 corresponding to the first air valve 20, the second indoor return air control system 18 corresponding to the second air valve 21, and the outdoor fresh air control system 22 corresponding to the third air valve 22. When the corresponding control air system is opened, the air valve logic applies to the three air valves.

[0101] When the detected indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta+1℃, the damper increases its opening by 2% each time, introducing more cooling capacity. When the detected indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta-1℃, the damper decreases its opening by 2% each time. When the detected indoor dry-bulb temperature T1 is equal to the indoor set temperature Ta±1℃, the damper opening remains unchanged.

[0102] (6) Humidity control process damper control methods, including:

[0103] When the detected relative humidity RH1 > the set humidity RHa + 3%, the damper increases its opening by 2% at a time, introducing more cooling capacity. When the detected relative humidity RH1 < the set humidity RHa - 3%, the damper decreases its opening by 2% at a time. When the detected relative humidity RH1 = the set humidity RHa ± 3%, the damper opening remains unchanged.

[0104] like Figure 5 As shown, the temperature control process damper control method includes:

[0105] Step 21: Detect the indoor dry-bulb temperature T1 and wet-bulb temperature T using an indoor temperature and humidity sensor. w Relative humidity RH1.

[0106] Step 22: Calculate the corresponding dew point temperature T L Determine the indoor set temperature Ta and the humidity RHa.

[0107] Step 23: Determine whether the indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta+1℃, and determine whether the relative humidity RH1 is greater than the set humidity RHa+3%.

[0108] When the indoor dry-bulb temperature T1 is detected to be greater than the indoor set temperature Ta+1℃, open the large air valve.

[0109] When the indoor dry-bulb temperature T1 is detected to be equal to the indoor set temperature Ta ± 1℃, the opening of the damper remains unchanged.

[0110] When the indoor dry-bulb temperature T1 is detected to be less than the indoor set temperature Ta+1℃ and the indoor dry-bulb temperature T1 is not equal to the indoor set temperature Ta±1℃, the air valve is closed.

[0111] When the relative humidity RH1 is detected to be greater than the set humidity RHa+3%, open the air valve.

[0112] When the relative humidity RH1 is detected to be equal to the set humidity RHa ± 3%, the opening of the damper remains unchanged.

[0113] When the relative humidity RH1 is detected to be less than the set humidity RHa+3%, and the relative humidity RH1 is not equal to the set humidity RHa±3%, the air valve is closed.

[0114] In some embodiments, the control unit adjusts at least one of the first throttling element and the second throttling element, including any of the following throttling element adjustment settings:

[0115] The first throttling element adjustment scenario: Specifically, the control unit is further configured to, during temperature control in any of the modes, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, then the opening degree of the corresponding throttling element in the first and second throttling elements decreases. If the indoor dry-bulb temperature of the heat pump system is less than the sum of the indoor set temperature and the second set value, and the indoor dry-bulb temperature of the heat pump system is not equal to the difference between the indoor set temperature and the second set value, then the opening degree of the corresponding throttling element in the first and second throttling elements increases; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, then the opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged.

[0116] The second type of throttling element adjustment: Specifically, the control unit is further configured to, during humidity control in any of the modes, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, then the opening degree of the corresponding throttling element in the first and second throttling elements decreases. If the relative humidity of the heat pump system is less than the sum of the set humidity and the third set value, and the relative humidity of the heat pump system is not equal to the difference between the set humidity and the third set value, then the opening degree of the corresponding throttling element in the first and second throttling elements increases; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, then the opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged.

[0117] like Figure 6 As shown, the workflow of the temperature and humidity independent control air system using an expansion-pressurized heat pump system includes:

[0118] Step 31: Detect the indoor dry-bulb temperature T1 and wet-bulb temperature T using an indoor temperature and humidity sensor. w .

[0119] Step 32: Calculate the corresponding dew point temperature T L Determine the indoor set temperature Ta and the humidity RHa.

[0120] Step 33: Determine whether the indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta+1℃, and determine whether the relative humidity RH1 is greater than the set humidity RHa+3%.

[0121] When the indoor dry-bulb temperature T1 is detected to be greater than the indoor set temperature Ta+1℃, the electronic expansion valve is closed.

[0122] When the indoor dry-bulb temperature T1 is detected to be equal to the indoor set temperature Ta ± 1℃, the opening of the electronic expansion valve remains unchanged.

[0123] When the indoor dry-bulb temperature T1 is detected to be less than the indoor set temperature Ta+1℃ and the indoor dry-bulb temperature T1 is not equal to the indoor set temperature Ta±1℃, the electronic expansion valve is opened.

[0124] When the relative humidity RH1 is detected to be greater than the set humidity RHa+3%, the electronic expansion valve is closed.

[0125] When the relative humidity RH1 is detected to be equal to the set humidity RHa ± 3%, the opening of the electronic expansion valve remains unchanged.

[0126] When the relative humidity RH1 is detected to be less than the set humidity RHa+3%, and the relative humidity RH1 is not equal to the set humidity RHa±3%, the electronic expansion valve is opened.

[0127] In some embodiments, where the heat pump system further includes at least one of a first shut-off valve 1, a second shut-off valve 2, a third shut-off valve 23, a fourth shut-off valve 16, and a fifth shut-off valve 24, the compression unit includes an electric compressor 9 and a mechanically driven compressor 10, the expansion unit includes an expander 12, and the air valve assembly includes a first air valve 20, a second air valve 21, and a third air valve 22, the control unit controls the operation of the expansion unit, including any of the following expansion control scenarios:

[0128] The first expansion control scenario: Specifically, the control unit is further configured such that, when the heat pump system is operating in cooling and dehumidification mode, the refrigerant discharged from the exhaust port of the electric compressor 9, after passing through the four-way valve 5 and the first heat exchanger 6, is divided into two refrigerant streams: one stream controls the evaporation temperature of the heat pump system through the first throttling element, at which time the third shut-off valve 23 and the fourth shut-off valve 16 are closed, the expander 12 expands and performs work, driving the mechanically driven compressor 10 to rotate, and the airflow is controlled by the first air valve 20 and the third air valve 22. The other stream controls the evaporation temperature of the heat pump system through the second throttling element, and the airflow is controlled by the second air valve 21. After the two refrigerant streams are mixed, the first shut-off valve 1 is opened and the second shut-off valve 2 is closed, achieving two compressions through the mechanically driven compressor 10 and the electric compressor 9.

[0129] In the solution of this invention, under the cooling mode, the heat pump system's workflow in the cooling + dehumidification mode is as follows: the high-temperature, high-pressure gas discharged from the exhaust port of the electric compressor 9 passes through port D of the four-way valve 5 and enters the outdoor heat exchanger, i.e., the first heat exchanger 6, through port C of the four-way valve 5. After condensation and heat release, it becomes a high-pressure liquid refrigerant, which is divided into two refrigerant paths:

[0130] The first refrigerant, after passing through the first electronic expansion valve 3, has its evaporation temperature controlled to be lower than the indoor dry-bulb temperature and higher than the dew point temperature. This is achieved by initially controlling the evaporation temperature T. z1 = (Indoor dry bulb temperature T1 + Dew point temperature T) L The air flows to the expander 12. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed. At the same time, the fan 14 introduces indoor air through the pipe 15 to exchange heat with the expander. The liquid refrigerant in the expander 12 absorbs heat and expands, becoming gaseous refrigerant. The expansion does work and drives the expander 12. Through the mechanical transmission shaft 11, it drives the mechanical transmission compressor 10 to rotate. The indoor air flowing through the expander 12 is cooled down after exchanging heat with the refrigerant in the expander 12 and is sent back to the room, which plays a role in controlling the indoor temperature. The air volume is controlled by the first air valve 20 to regulate the flow of cold air into the room and balance the excess heat in the room. After the gaseous refrigerant comes out of the expander 12, it enters the third heat exchanger 8 and exchanges heat with the outdoor fresh air through the pipe 19 to pre-cool the fresh air entering the room. The air volume of the fresh air entering the room is controlled by the third air valve 22.

[0131] The other refrigerant, after passing through the second electronic expansion valve 4, undergoes throttling and pressure reduction to control its evaporation temperature below the dew point temperature, such as the initial controller evaporation temperature T. z2 =T L -2, the second heat exchanger 7 exchanges heat with the indoor air through the air duct 18 to achieve the purpose of dehumidification. Similarly, the air volume is controlled by the second air valve 21 to regulate the indoor humidity.

[0132] After the two refrigerants merge, they pass through the E port and S port of the four-way valve 5, and are then drawn into the mechanically driven compressor 10 through the first shut-off valve 1 (at which time the second shut-off valve 2 is closed). They are then compressed twice by the electric compressor 9, thereby increasing the compression ratio of the heat pump system.

[0133] The second expansion control scenario: Specifically, the control unit is further configured such that, when the heat pump system is operating in cooling mode, the refrigerant discharged from the exhaust port of the electric compressor 9, after passing through the four-way valve 5 and the first heat exchanger 6, is divided into two refrigerant streams: one stream controls the evaporation temperature of the heat pump system through the first throttling element, at which time the third shut-off valve 23 and the fourth shut-off valve 16 are closed, the expander 12 expands and performs work, driving the mechanically driven compressor 10 to rotate, and the airflow is controlled by the first air valve 20. The other stream controls the evaporation temperature of the heat pump system through the second throttling element, and the airflow is controlled by the second air valve 21. After the two refrigerant streams mix, the first shut-off valve 1 is opened and the second shut-off valve 2 is closed, achieving two compressions through the mechanically driven compressor 10 and the electric compressor 9.

[0134] In the solution of this invention, in the cooling mode, the working process of the heat pump system in the cooling mode is as follows: the high-temperature and high-pressure gas discharged from the exhaust port of the electric compressor 9 passes through the four-way valve 5 and enters the first heat exchanger 6 through port C of the four-way valve 5. After condensation and heat release, it becomes a high-pressure liquid refrigerant, which is divided into two refrigerant paths:

[0135] The first refrigerant, after passing through the first electronic expansion valve 3, has its evaporation temperature controlled to be lower than the indoor dry-bulb temperature and higher than the dew point temperature. This is achieved by initially controlling the evaporation temperature T. z1 = (Indoor dry bulb temperature T1 + Dew point temperature T) L The air flows to the expander 12. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed. At the same time, the fan 14 introduces indoor air through the pipe 15 to exchange heat with the expander. The liquid refrigerant in the expander 12 absorbs heat and expands, becoming gaseous refrigerant. The expansion does work and drives the expander 12. Through the mechanical transmission shaft 11, it drives the mechanical transmission compressor 10 to rotate. The indoor air flowing through the expander 12 is cooled down after exchanging heat with the refrigerant in the expander 12 and is sent back to the room, which plays a role in controlling the indoor temperature. The air volume is controlled by the first air valve 20 to regulate the flow of cold air into the room and balance the excess heat in the room. After the gaseous refrigerant comes out of the expander 12, it flows through the third heat exchanger 8. At this time, the third air valve 22 in the fresh air duct (i.e. the fresh air duct of the fresh air control system 19) is closed, and fresh air is temporarily not introduced.

[0136] Another refrigerant path passes through the second electronic expansion valve 4, controlling its evaporation temperature to be lower than the indoor dry-bulb temperature and higher than the dew point temperature. This is achieved by initially controlling the evaporation temperature T. z2 = (Indoor dry bulb temperature T1 + Dew point temperature T) L) / 2, the second heat exchanger 7 exchanges heat with the indoor air through the second return air duct where the second indoor return air control system 19 is located, so as to achieve the purpose of cooling. Similarly, the air volume is controlled by the second air valve 21 to adjust and balance the excess heat in the room.

[0137] After the two refrigerants merge, they pass through the E port and S port of the four-way valve 5 and then through the first shut-off valve 1 (at which time the second shut-off valve 2 is closed) and are drawn into the mechanically driven compressor 10. They then pass through the electric compressor 9 to achieve two compressions, thereby increasing the compression ratio of the heat pump system.

[0138] The third expansion control scenario: Specifically, the control unit is further configured such that, when the heat pump system is operating in a constant temperature and dehumidification mode under cooling mode, the refrigerant discharged from the exhaust port of the electric compressor 9 passes through the four-way valve 5 and the first heat exchanger 6, and then the second throttling element is closed. The refrigerant controls the evaporation temperature of the heat pump system through the first throttling element. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed, and the expander 12 expands and performs work, driving the mechanically driven compressor 10 to rotate. The air volume is controlled by the first air valve 20 and the third air valve 22. By controlling the first shut-off valve 1 to open and the second shut-off valve 2 to close, two compressions are achieved through the mechanically driven compressor 10 and the electric compressor 9.

[0139] In cooling mode, the heat pump system's workflow under constant temperature and dehumidification mode is as follows: High-temperature, high-pressure gas discharged from the electric compressor 9's exhaust port passes through the four-way valve 5 and enters the first heat exchanger 6 through port C of the four-way valve 5. After condensation and heat release, it becomes high-pressure liquid refrigerant. At this time, the second electronic expansion valve 4 is fully closed, and the refrigerant flows only through the first electronic expansion valve 3, controlling its evaporation temperature. For example, the initial control of the evaporation temperature T... z2 = Dew point temperature T L-2. The air flows to the expander 12. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed. Simultaneously, the fan 14 introduces indoor air through the pipe 15 to exchange heat with the expander 12. The liquid refrigerant in the expander 12 absorbs heat and expands, becoming gaseous refrigerant. This process simultaneously dehumidifies the air and performs work, driving the expander 12. This, in turn, drives the mechanical compressor 10 to rotate via the mechanical drive shaft 11. The indoor air flowing through the expander 12 experiences reduced humidity after heat exchange with the refrigerant inside and is then returned to the room, thus controlling the indoor humidity. The airflow is controlled by the first air valve 20 to regulate the humidity entering the room. Due to the low evaporation temperature, the refrigerant temperature is lower than the outdoor temperature after heat exchange with the indoor air in the expander heat exchange duct 13. After the gaseous refrigerant comes out of the expander 12, it flows through the third heat exchanger 8. Because the dehumidification process will lower the indoor temperature, the third air valve 22 is opened to introduce outdoor air with a higher temperature to balance the heat removed by dehumidification. The opening degree of the third air valve 22 can be used to control the fresh air flow, thereby regulating the indoor temperature and humidity balance. After passing through the third heat exchanger 8, the refrigerant passes through the E port and S port of the four-way valve 5 and then through the first shut-off valve 1 (at this time, the second shut-off valve 2 is closed) and is drawn into the mechanically driven compressor 10. It then undergoes two compressions through the electric compressor 9 to increase the compression ratio of the heat pump system.

[0140] The fourth expansion control scenario: Specifically, the control unit is further configured such that, when the heat pump system operates in a constant temperature and humidity mode under cooling mode, the refrigerant discharged from the exhaust port of the electric compressor 9 passes through the four-way valve 5 and the first heat exchanger 6. The second throttling element closes, and the refrigerant's evaporation temperature is controlled by the first throttling element. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed. The expander 12 expands and performs work, driving the mechanically driven compressor 10 to rotate. The airflow is controlled by the third air valve 22. The first shut-off valve 1 is closed, and the second shut-off valve 2 is opened, achieving compression through the electric compressor 9.

[0141] In cooling mode, the heat pump system's workflow under constant temperature and humidity mode is as follows: High-temperature, high-pressure gas discharged from the electric compressor 9's exhaust port passes through the four-way valve 5 and enters the first heat exchanger 6 through port C of the four-way valve 5. After condensation and heat release, it becomes high-pressure liquid refrigerant. At this time, the second electronic expansion valve 4 is fully closed, and the refrigerant flows only through the first electronic expansion valve 3, controlling its evaporation temperature to be lower than the indoor dry-bulb temperature and higher than the dew point temperature. For example, the initial control of the evaporation temperature T... z1 = (Indoor dry bulb temperature T1 + Dew point temperature T) LThe refrigerant flows to the third heat exchanger 8 (at this time, the fifth shut-off valve 24 is closed). At this point, the third air valve 22 is opened to introduce outdoor air, controlling the intake air temperature to prevent the indoor temperature from rising further. The opening degree of the third air valve 22 can control the amount of fresh air, thereby regulating the indoor temperature and humidity balance. After passing through the third heat exchanger 8, the refrigerant passes through the E port and S port of the four-way valve 5, and then through the second shut-off valve 2 (at this time, the first shut-off valve 1 is closed) and is drawn into the electric compressor 10, completing one cycle.

[0142] In heating mode, the heat pump system operates as follows: the high-temperature, high-pressure gas discharged from the exhaust port of the electric compressor 9 passes through port D of the four-way valve 5. The high-temperature, high-pressure gaseous refrigerant from port E of the four-way valve 5 enters the second heat exchanger 7 (at this time, the fourth shut-off valve 16 and the fifth shut-off valve 24 are closed, and the first electronic expansion valve 3 is fully closed). After condensation and heat release, it becomes high-pressure liquid refrigerant. It passes through the second electronic expansion valve 4, which throttles and reduces the pressure. It then passes through the first heat exchanger 6 to exchange heat with the outdoor air. The refrigerant passes through port C and port S of the four-way valve 5 and then through the second shut-off valve 2 (at this time, the first shut-off valve 1 is closed) and is drawn into the electric compressor 9, completing one cycle.

[0143] The present invention integrates an expander into the heat pump system, placing it within the return air duct. The expander utilizes the higher temperature of the return air above the indoor air level to provide energy for the refrigerant's expansion and heat absorption, simultaneously processing the indoor air. The expander recovers energy to provide kinetic energy for the compressor, increasing the overall pressure ratio during cooling. By utilizing the expander's expansion work and recovering some energy to provide kinetic energy for the mechanical compressor, throttling losses are reduced. Simultaneously, it cools and dehumidifies the indoor temperature. Thus, by adding an expander, some throttling losses can be recovered, resulting in good energy efficiency. When the expander is engaged, the mechanical compressor performs one compression, and the electric compressor performs a second compression, increasing the overall compression ratio of the heat pump system and improving energy efficiency. Through three heat exchangers in three air ducts, two electronic expansion valves, and air valves within the air ducts, combined with control methods, the temperature and humidity of the indoor air are controlled.

[0144] By adopting the technical solution of this invention, an expander is set up, and a set of refrigeration systems is used. Combining indoor temperature and humidity, as well as the required set temperature and humidity, the refrigerant is divided into two flow paths. Two electronic expansion valves on the two flow paths are controlled respectively to adjust the evaporation temperature of the two paths. By controlling the difference in evaporation temperature, the air can be cooled or dehumidified. Thus, by using a set of refrigeration systems, the heat pump system can achieve independent control of temperature and humidity in refrigeration mode, which can save energy consumption.

[0145] According to an embodiment of the present invention, a heat pump system corresponding to a control device for a heat pump system is also provided. This heat pump system may include the control device for the heat pump system described above.

[0146] Since the processing and functions implemented by the heat pump system in this embodiment are basically the same as those in the embodiments, principles and examples of the aforementioned devices, any details not covered in this embodiment can be found in the relevant descriptions in the aforementioned embodiments, and will not be repeated here.

[0147] By adopting the technical solution of this invention, an expander is set up, and a refrigeration system is used. Combined with indoor temperature and humidity, the required set temperature and humidity, the refrigerant is divided into two flow paths. Two electronic expansion valves on the two flow paths are controlled respectively to adjust the evaporation temperature of the two paths. By controlling the different evaporation temperatures, the air can be cooled or dehumidified. While accurately controlling the temperature and humidity, it can also save energy.

[0148] According to embodiments of the present invention, a control method for a heat pump system corresponding to a heat pump system is also provided, such as... Figure 7 The diagram shows a flow chart of an embodiment of the method of the present invention. The heat pump system includes: a compression unit, a four-way valve 5, a first heat exchanger 6, a second heat exchanger 7, a third heat exchanger 8, and an expansion unit. The exhaust port of the compression unit, after passing through the four-way valve 5, is connected to the first end of the first heat exchanger 6. The second end of the first heat exchanger 6 is divided into two paths: one path passes through a first throttling element, the expansion unit, and the third heat exchanger 8, and then through the four-way valve 5 to the intake port of the compression unit; the other path passes through a second throttling element, the second heat exchanger 7, and then through the four-way valve 5 to the intake port of the compression unit. The first throttling element is, for example, a first electronic expansion valve 3, and the second throttling element is, for example, a second electronic expansion valve 4. A damper assembly is also provided in the air duct of the heat pump system.

[0149] The control method for the heat pump system includes steps S110 and S120.

[0150] In step S110, the indoor humidity and indoor temperature of the heat pump system are collected.

[0151] In step S120, based on the indoor humidity and the indoor temperature, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in any one of the following modes in the cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, thereby achieving at least independent control of temperature and humidity of the heat pump system in the cooling mode.

[0152] This invention provides a heat pump system utilizing expansion and pressurization, along with an independent temperature and humidity control scheme. Using a single refrigeration system, and considering indoor temperature and humidity, as well as the desired set temperature and humidity, the refrigerant is divided into two flow paths. Two electronic expansion valves on each path are controlled to adjust the evaporation temperature of the two paths. By controlling the difference in evaporation temperature, the air conditioner's state is controlled, resulting in either cooling or dehumidification. This achieves independent temperature and humidity control of the heat pump system in cooling mode. By combining the adjustment of the electronic expansion valves to control the evaporation temperature, the adjustment of the airflow control assembly, and the use of an expander, precise temperature and humidity control is achieved while simultaneously saving energy. The combination of electronic expansion valves and airflow control schemes makes the control of temperature and humidity more precise.

[0153] Figure 2 This is a schematic diagram of an embodiment of the heat pump system utilizing expansion and pressurization according to the present invention. Figure 2 As shown, the heat pump system utilizing expansion and pressurization includes: a first shut-off valve 1, a second shut-off valve 2, a first electronic expansion valve 3, a second electronic expansion valve 4, a four-way valve 5, a first heat exchanger 6, a second heat exchanger 7, a third heat exchanger 8, an electric compressor 9, a mechanically driven compressor 10, a mechanically driven shaft 11, an expander 12, an expander heat exchange duct 13, a fan 14, a duct 15, a fourth shut-off valve 16, a third shut-off valve 23, and a fifth shut-off valve 24.

[0154] exist Figure 2 In the example shown, the exhaust port of the electric compressor 9 is connected to port D of the four-way valve 5. Port E of the four-way valve 5 splits into two refrigerant flow paths: one refrigerant flow path connects to the first end of the second heat exchanger 7, and the other refrigerant flow path connects to the first end of the third heat exchanger 8. The second end of the second heat exchanger 7 is connected to the second end of the first heat exchanger 6 via the second electronic expansion valve 4. The first end of the first heat exchanger 6 is connected to port C of the four-way valve 5. The second end of the first heat exchanger 6 is connected to the first end of the expander 12 via the first electronic expansion valve 3. The first end of the expander 12 is connected to the second end of the third heat exchanger 8 via the third shut-off valve 23 and the fourth shut-off valve 16. The second end of the third heat exchanger 8 is connected to the second end of the expander 12 via the fifth shut-off valve 24. The expander 12 is located in the expander heat exchange duct 13. The fan 14 and the duct 15 are connected to the air inlet of the expander heat exchange duct 13. The expander heat exchange duct 13 also has an exhaust port.

[0155] exist Figure 2In the example shown, the suction port of the electric compressor 9 is connected to the S port of the four-way valve 5 via the second shut-off valve 2. The suction port of the electric compressor 9 is also connected to the discharge port of the mechanically driven compressor 10. The suction port of the mechanically driven compressor 10 is connected to the S port of the four-way valve 5 via the first shut-off valve 1. The mechanically driven compressor 10 is connected to the expander 12 via the mechanical drive shaft 11.

[0156] Figure 3 This is a schematic diagram of an embodiment of the independent temperature and humidity control air system of the present invention, utilizing an expansion-pressurized heat pump system. Figure 3 As shown, the temperature and humidity independent control air system of the heat pump system using expansion and pressurization includes: a first indoor return air control system 17, a second indoor return air control system 18, an outdoor fresh air control system 19, a first air valve 20, a second air valve 21, and a third air valve 22.

[0157] exist Figure 3 In the example shown, a first air valve 20 is installed in the first return air duct of the first indoor return air control system 17. The return air in the first return air duct passes through the first air valve 20 and flows to the expander heat exchange duct 13. In the second return air duct of the second indoor return air control system 18, a second air valve 21 is installed. The return air in the second return air duct passes through the second air valve 21 and flows to the second heat exchanger 7.

[0158] A third air valve 22 is installed in the fresh air duct of the outdoor fresh air control system 19. Fresh air in the fresh air duct passes through the third air valve 22 and flows to the third heat exchanger 8.

[0159] In some embodiments, the indoor humidity includes: indoor relative humidity. The indoor temperature includes: indoor dry-bulb temperature.

[0160] The specific process of controlling at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit in step S120, based on the indoor humidity and the indoor temperature, to control the heat pump system to operate in any one of the following modes in the cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, is described in the following exemplary description.

[0161] The following is combined with Figure 8 The schematic diagram shown is a flowchart of an embodiment of the method of the present invention, which controls the heat pump system to operate in any one of the following modes in the cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode. It further illustrates the specific process of controlling the heat pump system to operate in any one of the following modes in the cooling mode in step S120, including steps S210 to S230.

[0162] Step S210: Based on the indoor humidity and the indoor temperature, determine whether the heat pump system operates in cooling mode in any one of the following modes: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, or constant temperature and constant humidity mode.

[0163] Step S220: Adjust at least one of the first throttling element and the second throttling element to control the evaporation temperature of the heat pump system to half the sum of the indoor dry-bulb temperature and dew point temperature of the heat pump system in the cooling mode of any of the modes; and control the evaporation temperature of the heat pump system to the difference between the dew point temperature of the heat pump system and a first set value in the dehumidification mode of any of the cooling and dehumidification modes, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode. That is, in the cooling mode of any of the cooling and dehumidification modes, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, control the evaporation temperature of the heat pump system to half the sum of the indoor dry-bulb temperature and dew point temperature of the heat pump system; and in the dehumidification mode of any of the cooling and dehumidification modes, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, control the evaporation temperature of the heat pump system to the difference between the dew point temperature of the heat pump system and a set temperature value. And control the expansion unit to operate.

[0164] Step S230: After adjusting the opening degree of the air valve assembly to the set opening degree value, control at least one of the air valve assembly, the first throttling element and the second throttling element according to the current opening degree of the air valve assembly.

[0165] The method of controlling at least one of the air valve assembly, the first throttling element, and the second throttling element according to the current opening degree of the air valve assembly includes: if the current opening degree of the air valve assembly is greater than or equal to a first preset opening value and less than or equal to a second preset opening value, then the air valve assembly is adjusted preferentially; if the current opening degree of the air valve assembly is less than the first preset opening value or greater than the second preset opening value, then at least one of the first throttling element and the second throttling element is adjusted preferentially.

[0166] In the solution of the present invention, Figure 4 This is a schematic diagram of the temperature and humidity control judgment process of an embodiment of the independent temperature and humidity control air system of the heat pump system utilizing expansion and pressurization of the present invention. Figure 5 This is a flowchart illustrating another embodiment of the independent temperature and humidity control air system of the heat pump system utilizing expansion and pressurization of the present invention. Specifically, it is a flowchart illustrating the method of controlling temperature and humidity using the first air valve, the second air valve, and the third air valve when the air valve opening is between 20% and 80%. Figure 6This is a flowchart illustrating another embodiment of the independent temperature and humidity control air system of the heat pump system utilizing expansion and pressurization of the present invention. Specifically, it is a flowchart illustrating the method of controlling temperature and humidity by the first electronic expansion valve and the second electronic expansion valve when the air valve opening is less than 20% and greater than 80%.

[0167] See Figure 4 , Figure 5 and Figure 6 The example shown illustrates a method for independent temperature and humidity control of airflow using an expansion-pressurized heat pump system, including:

[0168] Step 1: Detect the indoor temperature and humidity and compare them with the set temperature and humidity to determine the required mode.

[0169] Step 2: First, adjust the electronic expansion valve, using the cooling mode to control the evaporation temperature at T. z = (Indoor dry bulb temperature T1 + Dew point temperature T) L ) / 2, dehumidification mode controls evaporation temperature T z = Dew point temperature T L -2.

[0170] Step 3: Adjust the opening of the corresponding air valve to 50%.

[0171] Step 4: When the damper opening is detected to be between 20% and 80%, damper adjustment should be prioritized.

[0172] Part 5: When the damper opening is detected to be less than 20% or greater than 80%, adjust the electronic expansion valve. If the temperature is lowered, the electronic expansion valve is closed by -1℃ of the evaporation temperature each time; if the evaporation temperature is raised, the electronic expansion valve is opened by +1℃ of the evaporation temperature each time.

[0173] The present invention combines two adjustment methods—electronic expansion valves and air valves—to achieve temperature and humidity control. In cooling mode, the system controls the evaporation temperature to meet different requirements by adjusting the two electronic expansion valves, controls the airflow by adjusting the air valves, and recovers energy lost due to throttling using an expander.

[0174] Some solutions lack an expander, resulting in energy inefficiency. Furthermore, temperature and humidity control is achieved through a fresh air dehumidifier and multiple indoor units, leading to poor economic efficiency. The installation of multiple indoor units is more complex, with extended refrigerant piping increasing resistance and losses. In contrast, this invention integrates the dehumidification system with the cooling system, return air system, and fresh air system. It controls different evaporation temperatures via an electronic expansion valve to achieve dehumidification or cooling, and simultaneously utilizes the expander to recover some energy, resulting in greater energy savings.

[0175] Other solutions lack an expander, resulting in energy inefficiency. In temperature and humidity control, cooling and dehumidification occur simultaneously during air treatment, preventing separate control of temperature and humidity. The solution of this invention, however, allows for separate cooling or simultaneous cooling and dehumidification processes, enabling precise control of indoor temperature and humidity by adjusting airflow, resulting in more accurate control.

[0176] In some implementations, step S210 determines, based on the indoor humidity and the indoor temperature, that the heat pump system operates in cooling mode in any of the following modes: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, including any of the following control situations:

[0177] The first control scenario: When the indoor temperature is greater than the set indoor temperature and the indoor humidity is greater than the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in cooling and dehumidification mode. The control is performed at set intervals based on the re-collected indoor humidity and indoor temperature. That is, based on the re-collected indoor humidity and indoor temperature, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to re-control the heat pump system to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode.

[0178] The second control scenario: When the indoor temperature is greater than the set indoor temperature and the indoor humidity is less than or equal to the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in cooling mode.

[0179] The third control scenario: When the indoor temperature is less than or equal to the set indoor temperature and the indoor humidity is greater than the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in a constant temperature and dehumidification mode.

[0180] The fourth control scenario: When the indoor temperature is less than or equal to the set indoor temperature and the indoor humidity is less than or equal to the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in a constant temperature and humidity mode.

[0181] like Figure 4As shown, the temperature and humidity control judgment process of the independent temperature and humidity control air system using the expansion and pressurization heat pump system, i.e., the temperature and humidity control judgment process in cooling mode, includes:

[0182] Step 11: Detect the indoor dry-bulb temperature T1 and wet-bulb temperature T using an indoor temperature and humidity sensor. w .

[0183] Step 12: Calculate the corresponding dew point temperature T L Determine the indoor set temperature Ta and the humidity RHa.

[0184] Step 13: Determine whether the indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta, and determine whether the relative humidity RH1 is greater than the set humidity RHa.

[0185] (1) When it is determined that the indoor dry bulb temperature T1 is greater than the indoor set temperature Ta and the relative humidity RH1 is greater than the set humidity RHa, the heat pump system will enter the cooling + dehumidification mode, and the indoor dry and wet bulb temperatures will be detected every 2 minutes. The system will cycle through the detection and determine the corresponding logic.

[0186] (2) When the indoor dry bulb temperature T1 is greater than the indoor set temperature Ta and the relative humidity RH1 is less than or equal to the set humidity RHa, the heat pump system will switch to cooling mode.

[0187] (3) When it is determined that the indoor dry bulb temperature T1 ≤ indoor set temperature Ta and the relative humidity RH1 > set humidity RHa, the heat pump system will operate in constant temperature + dehumidification mode.

[0188] (4) When the indoor dry bulb temperature T1 is determined to be less than the indoor set temperature Ta and the relative humidity RH1 is less than the set humidity RHa, the heat pump system will operate in constant temperature + constant humidity mode.

[0189] In some embodiments, adjusting the damper assembly in step S230 includes any of the following damper assembly adjustment states:

[0190] The first type of damper assembly adjustment: During temperature control in any of the stated modes, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, the corresponding damper in the damper assembly increases its opening by the set degree. If the indoor dry-bulb temperature of the heat pump system is less than the difference between the indoor set temperature and the second set value, the corresponding damper in the damper assembly decreases its opening by the set degree. If the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value, or the difference between the indoor set temperature and the second set value, the opening of the corresponding damper in the damper assembly remains unchanged.

[0191] The second type of damper assembly adjustment: During humidity control in any of the above modes, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, the corresponding damper in the damper assembly increases its opening by the set degree. If the relative humidity of the heat pump system is less than the difference between the set humidity and the third set value, the corresponding damper in the damper assembly decreases its opening by the set degree. If the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value, or the difference between the set humidity and the third set value, the opening of the corresponding damper in the damper assembly remains unchanged.

[0192] like Figure 4 As shown, the temperature and humidity control judgment process of the independent temperature and humidity control air system using the expansion and pressurization heat pump system also includes:

[0193] (5) Air valve control opening conditions: the first indoor return air control system 17 corresponding to the first air valve 20, the second indoor return air control system 18 corresponding to the second air valve 21, and the outdoor fresh air control system 22 corresponding to the third air valve 22. When the corresponding control air system is opened, the air valve logic applies to the three air valves.

[0194] When the detected indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta+1℃, the damper increases its opening by 2% each time, introducing more cooling capacity. When the detected indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta-1℃, the damper decreases its opening by 2% each time. When the detected indoor dry-bulb temperature T1 is equal to the indoor set temperature Ta±1℃, the damper opening remains unchanged.

[0195] (6) Humidity control process damper control methods, including:

[0196] When the detected relative humidity RH1 > the set humidity RHa + 3%, the damper increases its opening by 2% at a time, introducing more cooling capacity. When the detected relative humidity RH1 < the set humidity RHa - 3%, the damper decreases its opening by 2% at a time. When the detected relative humidity RH1 = the set humidity RHa ± 3%, the damper opening remains unchanged.

[0197] like Figure 5 As shown, the temperature control process damper control method includes:

[0198] Step 21: Detect the indoor dry-bulb temperature T1 and wet-bulb temperature T using an indoor temperature and humidity sensor. w .

[0199] Step 22: Calculate the corresponding dew point temperature T L Determine the indoor set temperature Ta and the humidity RHa.

[0200] Step 23: Determine whether the indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta+1℃, and determine whether the relative humidity RH1 is greater than the set humidity RHa+3%.

[0201] When the indoor dry-bulb temperature T1 is detected to be greater than the indoor set temperature Ta+1℃, open the large air valve.

[0202] When the indoor dry-bulb temperature T1 is detected to be equal to the indoor set temperature Ta ± 1℃, the opening of the damper remains unchanged.

[0203] When the indoor dry-bulb temperature T1 is detected to be less than the indoor set temperature Ta+1℃ and the indoor dry-bulb temperature T1 is not equal to the indoor set temperature Ta±1℃, the air valve is closed.

[0204] When the relative humidity RH1 is detected to be greater than the set humidity RHa+3%, open the air valve.

[0205] When the relative humidity RH1 is detected to be equal to the set humidity RHa ± 3%, the opening of the damper remains unchanged.

[0206] When the relative humidity RH1 is detected to be less than the set humidity RHa+3%, and the relative humidity RH1 is not equal to the set humidity RHa±3%, the air valve is closed.

[0207] In some embodiments, adjusting at least one of the first throttling element and the second throttling element in step S220 includes any of the following throttling element adjustment settings:

[0208] The first type of throttling element adjustment: During temperature control in any of the stated modes, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, the opening degree of the corresponding throttling element in the first and second throttling elements decreases. If the indoor dry-bulb temperature of the heat pump system is less than the sum of the indoor set temperature and the second set value, and the indoor dry-bulb temperature of the heat pump system is not equal to the difference between the indoor set temperature and the second set value, the opening degree of the corresponding throttling element in the first and second throttling elements increases; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, the opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged.

[0209] The second type of throttling element adjustment: During humidity control in any of the above modes, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements decreases. If the relative humidity of the heat pump system is less than the sum of the set humidity and the third set value, and the relative humidity of the heat pump system is not equal to the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements increases; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged.

[0210] like Figure 6 As shown, the workflow of the temperature and humidity independent control air system using an expansion-pressurized heat pump system includes:

[0211] Step 31: Detect the indoor dry-bulb temperature T1 and wet-bulb temperature T using an indoor temperature and humidity sensor. w .

[0212] Step 32: Calculate the corresponding dew point temperature T L Determine the indoor set temperature Ta and the humidity RHa.

[0213] Step 33: Determine whether the indoor dry-bulb temperature T1 is greater than the indoor set temperature Ta+1℃, and determine whether the relative humidity RH1 is greater than the set humidity RHa+3%.

[0214] When the indoor dry-bulb temperature T1 is detected to be greater than the indoor set temperature Ta+1℃, the electronic expansion valve is closed.

[0215] When the indoor dry-bulb temperature T1 is detected to be equal to the indoor set temperature Ta ± 1℃, the opening of the electronic expansion valve remains unchanged.

[0216] When the indoor dry-bulb temperature T1 is detected to be less than the indoor set temperature Ta+1℃ and the indoor dry-bulb temperature T1 is not equal to the indoor set temperature Ta±1℃, the electronic expansion valve is opened.

[0217] When the relative humidity RH1 is detected to be greater than the set humidity RHa+3%, the electronic expansion valve is closed.

[0218] When the relative humidity RH1 is detected to be equal to the set humidity RHa ± 3%, the opening of the electronic expansion valve remains unchanged.

[0219] When the relative humidity RH1 is detected to be less than the set humidity RHa+3%, and the relative humidity RH1 is not equal to the set humidity RHa±3%, the electronic expansion valve is opened.

[0220] In some embodiments, in step S220, if the heat pump system further includes at least one of a first shut-off valve 1, a second shut-off valve 2, a third shut-off valve 23, a fourth shut-off valve 16, and a fifth shut-off valve 24, the compression unit includes an electric compressor 9 and a mechanically driven compressor 10, the expansion unit includes an expander 12, and the air valve assembly includes a first air valve 20, a second air valve 21, and a third air valve 22, then controlling the expansion unit to operate includes any of the following expansion control situations:

[0221] The first expansion control scenario: When the heat pump system is operating in cooling and dehumidification mode, the refrigerant discharged from the exhaust port of the electric compressor 9, after passing through the four-way valve 5 and the first heat exchanger 6, is divided into two refrigerant streams: one stream controls the evaporation temperature of the heat pump system through the first throttling element, at which time the third shut-off valve 23 and the fourth shut-off valve 16 are closed, the expander 12 expands and performs work, driving the mechanically driven compressor 10 to rotate, and the airflow is controlled by the first air valve 20 and the third air valve 22. The other stream controls the evaporation temperature of the heat pump system through the second throttling element, and the airflow is controlled by the second air valve 21. After the two refrigerant streams mix, the first shut-off valve 1 is opened and the second shut-off valve 2 is closed, achieving two compressions through the mechanically driven compressor 10 and the electric compressor 9.

[0222] In the solution of this invention, under the cooling mode, the heat pump system's workflow in the cooling + dehumidification mode is as follows: the high-temperature, high-pressure gas discharged from the exhaust port of the electric compressor 9 passes through port D of the four-way valve 5 and enters the outdoor heat exchanger, i.e., the first heat exchanger 6, through port C of the four-way valve 5. After condensation and heat release, it becomes a high-pressure liquid refrigerant, which is divided into two refrigerant paths:

[0223] The first refrigerant, after passing through the first electronic expansion valve 3, has its evaporation temperature controlled to be lower than the indoor dry-bulb temperature and higher than the dew point temperature. This is achieved by initially controlling the evaporation temperature T. z1 = (Indoor dry bulb temperature T1 + Dew point temperature T) LThe air flows to the expander 12. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed. At the same time, the fan 14 introduces indoor air through the pipe 15 to exchange heat with the expander. The liquid refrigerant in the expander 12 absorbs heat and expands, becoming gaseous refrigerant. The expansion does work and drives the expander 12. Through the mechanical transmission shaft 11, it drives the mechanical transmission compressor 10 to rotate. The indoor air flowing through the expander 12 is cooled down after exchanging heat with the refrigerant in the expander 12 and is sent back to the room, which plays a role in controlling the indoor temperature. The air volume is controlled by the first air valve 20 to regulate the flow of cold air into the room and balance the excess heat in the room. After the gaseous refrigerant comes out of the expander 12, it enters the third heat exchanger 8 and exchanges heat with the outdoor fresh air through the pipe 19 to pre-cool the fresh air entering the room. The air volume of the fresh air entering the room is controlled by the third air valve 22.

[0224] The other refrigerant, after passing through the second electronic expansion valve 4, undergoes throttling and pressure reduction to control its evaporation temperature below the dew point temperature, such as the initial controller evaporation temperature T. z2 =T L -2, the second heat exchanger 7 exchanges heat with the indoor air through the air duct 18 to achieve the purpose of dehumidification. Similarly, the air volume is controlled by the second air valve 21 to regulate the indoor humidity.

[0225] After the two refrigerants merge, they pass through the E port and S port of the four-way valve 5, and are then drawn into the mechanically driven compressor 10 through the first shut-off valve 1 (at which time the second shut-off valve 2 is closed). They are then compressed twice by the electric compressor 9, thereby increasing the compression ratio of the heat pump system.

[0226] The second expansion control scenario: When the heat pump system is operating in cooling mode, the refrigerant discharged from the exhaust port of the electric compressor 9, after passing through the four-way valve 5 and the first heat exchanger 6, is divided into two refrigerant streams: one stream controls the evaporation temperature of the heat pump system through the first throttling element, at which time the third shut-off valve 23 and the fourth shut-off valve 16 are closed, the expander 12 expands and performs work, driving the mechanically driven compressor 10 to rotate, and the airflow is controlled by the first air valve 20. The other stream controls the evaporation temperature of the heat pump system through the second throttling element, and the airflow is controlled by the second air valve 21. After the two refrigerant streams mix, the first shut-off valve 1 is opened and the second shut-off valve 2 is closed, achieving two compressions through the mechanically driven compressor 10 and the electric compressor 9.

[0227] In the solution of this invention, in the cooling mode, the working process of the heat pump system in the cooling mode is as follows: the high-temperature and high-pressure gas discharged from the exhaust port of the electric compressor 9 passes through the four-way valve 5 and enters the first heat exchanger 6 through port C of the four-way valve 5. After condensation and heat release, it becomes a high-pressure liquid refrigerant, which is divided into two refrigerant paths:

[0228] The first refrigerant, after passing through the first electronic expansion valve 3, has its evaporation temperature controlled to be lower than the indoor dry-bulb temperature and higher than the dew point temperature. This is achieved by initially controlling the evaporation temperature T. z1 = (Indoor dry bulb temperature T1 + Dew point temperature T) L The air flows to the expander 12. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed. At the same time, the fan 14 introduces indoor air through the pipe 15 to exchange heat with the expander. The liquid refrigerant in the expander 12 absorbs heat and expands, becoming gaseous refrigerant. The expansion does work and drives the expander 12. Through the mechanical transmission shaft 11, it drives the mechanical transmission compressor 10 to rotate. The indoor air flowing through the expander 12 is cooled down after exchanging heat with the refrigerant in the expander 12 and is sent back to the room, which plays a role in controlling the indoor temperature. The air volume is controlled by the first air valve 20 to regulate the flow of cold air into the room and balance the excess heat in the room. After the gaseous refrigerant comes out of the expander 12, it flows through the third heat exchanger 8. At this time, the third air valve 22 in the fresh air duct (i.e. the fresh air duct of the fresh air control system 19) is closed, and fresh air is temporarily not introduced.

[0229] Another refrigerant path passes through the second electronic expansion valve 4, controlling its evaporation temperature to be lower than the indoor dry-bulb temperature and higher than the dew point temperature. This is achieved by initially controlling the evaporation temperature T. z2 = (Indoor dry bulb temperature T1 + Dew point temperature T) L ) / 2, the second heat exchanger 7 exchanges heat with the indoor air through the second return air duct where the second indoor return air control system 19 is located, so as to achieve the purpose of cooling. Similarly, the air volume is controlled by the second air valve 21 to adjust and balance the excess heat in the room.

[0230] After the two refrigerants merge, they pass through the E port and S port of the four-way valve 5 and then through the first shut-off valve 1 (at which time the second shut-off valve 2 is closed) and are drawn into the mechanically driven compressor 10. They then pass through the electric compressor 9 to achieve two compressions, thereby increasing the compression ratio of the heat pump system.

[0231] The third expansion control scenario: When the heat pump system operates in constant temperature and dehumidification mode under cooling mode, the refrigerant discharged from the exhaust port of the electric compressor 9 passes through the four-way valve 5 and the first heat exchanger 6. The second throttling element closes, and the refrigerant's evaporation temperature is controlled by the first throttling element. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed. The expander 12 expands and performs work, driving the mechanically driven compressor 10 to rotate. The airflow is controlled by the first air valve 20 and the third air valve 22. By controlling the first shut-off valve 1 to open and the second shut-off valve 2 to close, two compressions are achieved through the mechanically driven compressor 10 and the electric compressor 9.

[0232] In cooling mode, the heat pump system's workflow under constant temperature and dehumidification mode is as follows: High-temperature, high-pressure gas discharged from the electric compressor 9's exhaust port passes through the four-way valve 5 and enters the first heat exchanger 6 through port C of the four-way valve 5. After condensation and heat release, it becomes high-pressure liquid refrigerant. At this time, the second electronic expansion valve 4 is fully closed, and the refrigerant flows only through the first electronic expansion valve 3, controlling its evaporation temperature. For example, the initial control of the evaporation temperature T... z2 = Dew point temperature T L -2. The air flows to the expander 12. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed. Simultaneously, the fan 14 introduces indoor air through the pipe 15 to exchange heat with the expander 12. The liquid refrigerant in the expander 12 absorbs heat and expands, becoming gaseous refrigerant. This process simultaneously dehumidifies the air and performs work, driving the expander 12. This, in turn, drives the mechanical compressor 10 to rotate via the mechanical drive shaft 11. The indoor air flowing through the expander 12 experiences reduced humidity after heat exchange with the refrigerant inside and is then returned to the room, thus controlling the indoor humidity. The airflow is controlled by the first air valve 20 to regulate the humidity entering the room. Due to the low evaporation temperature, the refrigerant temperature is lower than the outdoor temperature after heat exchange with the indoor air in the expander heat exchange duct 13. After the gaseous refrigerant comes out of the expander 12, it flows through the third heat exchanger 8. Because the dehumidification process will lower the indoor temperature, the third air valve 22 is opened to introduce outdoor air with a higher temperature to balance the heat removed by dehumidification. The opening degree of the third air valve 22 can be used to control the fresh air flow, thereby regulating the indoor temperature and humidity balance. After passing through the third heat exchanger 8, the refrigerant passes through the E port and S port of the four-way valve 5 and then through the first shut-off valve 1 (at this time, the second shut-off valve 2 is closed) and is drawn into the mechanically driven compressor 10. It then undergoes two compressions through the electric compressor 9 to increase the compression ratio of the heat pump system.

[0233] The fourth expansion control scenario: When the heat pump system operates in constant temperature and humidity mode under cooling mode, the refrigerant discharged from the exhaust port of the electric compressor 9 passes through the four-way valve 5 and the first heat exchanger 6. The second throttling element closes, and the refrigerant's evaporation temperature is controlled by the first throttling element. At this time, the third shut-off valve 23 and the fourth shut-off valve 16 are closed. The expander 12 expands and performs work, driving the mechanically driven compressor 10 to rotate. The airflow is controlled by the third air valve 22. The first shut-off valve 1 is closed, and the second shut-off valve 2 is opened, achieving compression through the electric compressor 9.

[0234] In cooling mode, the heat pump system's workflow under constant temperature and humidity mode is as follows: High-temperature, high-pressure gas discharged from the electric compressor 9's exhaust port passes through the four-way valve 5 and enters the first heat exchanger 6 through port C of the four-way valve 5. After condensation and heat release, it becomes high-pressure liquid refrigerant. At this time, the second electronic expansion valve 4 is fully closed, and the refrigerant flows only through the first electronic expansion valve 3, controlling its evaporation temperature to be lower than the indoor dry-bulb temperature and higher than the dew point temperature. For example, the initial control of the evaporation temperature T... z1 = (Indoor dry bulb temperature T1 + Dew point temperature T) L The refrigerant flows to the third heat exchanger 8 (at this time, the fifth shut-off valve 24 is closed). At this point, the third air valve 22 is opened to introduce outdoor air, controlling the intake air temperature to prevent the indoor temperature from rising further. The opening degree of the third air valve 22 can control the amount of fresh air, thereby regulating the indoor temperature and humidity balance. After passing through the third heat exchanger 8, the refrigerant passes through the E port and S port of the four-way valve 5, and then through the second shut-off valve 2 (at this time, the first shut-off valve 1 is closed) and is drawn into the electric compressor 10, completing one cycle.

[0235] In heating mode, the heat pump system operates as follows: the high-temperature, high-pressure gas discharged from the exhaust port of the electric compressor 9 passes through port D of the four-way valve 5. The high-temperature, high-pressure gaseous refrigerant from port E of the four-way valve 5 enters the second heat exchanger 7 (at this time, the fourth shut-off valve 16 and the fifth shut-off valve 24 are closed, and the first electronic expansion valve 3 is fully closed). After condensation and heat release, it becomes high-pressure liquid refrigerant. It passes through the second electronic expansion valve 4, which throttles and reduces the pressure. It then passes through the first heat exchanger 6 to exchange heat with the outdoor air. The refrigerant passes through port C and port S of the four-way valve 5 and then through the second shut-off valve 2 (at this time, the first shut-off valve 1 is closed) and is drawn into the electric compressor 9, completing one cycle.

[0236] The present invention integrates an expander into the heat pump system, placing it within the return air duct. The expander utilizes the higher temperature of the return air above the indoor air level to provide energy for the refrigerant's expansion and heat absorption, simultaneously processing the indoor air. The expander recovers energy to provide kinetic energy for the compressor, increasing the overall pressure ratio during cooling. By utilizing the expander's expansion work and recovering some energy to provide kinetic energy for the mechanical compressor, throttling losses are reduced. Simultaneously, it cools and dehumidifies the indoor temperature. Thus, by adding an expander, some throttling losses can be recovered, resulting in good energy efficiency. When the expander is engaged, the mechanical compressor performs one compression, and the electric compressor performs a second compression, increasing the overall compression ratio of the heat pump system and improving energy efficiency. Through three heat exchangers in three air ducts, two electronic expansion valves, and air valves within the air ducts, combined with control methods, the temperature and humidity of the indoor air are controlled.

[0237] Since the processing and functions implemented by the method in this embodiment are basically the same as the embodiments, principles and examples of the aforementioned heat pump system, any details not covered in this embodiment can be found in the relevant descriptions in the aforementioned embodiments, and will not be repeated here.

[0238] The technical solution of this embodiment uses an expander and a refrigeration system. By combining indoor temperature and humidity with the required set temperature and humidity, the refrigerant is divided into two flow paths. Two electronic expansion valves on the two flow paths are controlled to adjust the evaporation temperature of the two paths. By controlling the different evaporation temperatures, the air can be cooled or dehumidified, resulting in good energy-saving effect.

[0239] In summary, it is readily understood by those skilled in the art that, without conflict, the aforementioned advantageous methods can be freely combined and superimposed.

[0240] The above description is merely an embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of the claims of the present invention.

Claims

1. A control device for a heat pump system, characterized in that, The heat pump system includes: a compression unit, a four-way valve (5), a first heat exchanger (6), a second heat exchanger (7), a third heat exchanger (8), and an expansion unit; the exhaust port of the compression unit is connected to the first end of the first heat exchanger (6) via the four-way valve (5); the second end of the first heat exchanger (6) is divided into two paths, one path is connected to the intake port of the compression unit via the first throttling element, the expansion unit, and the third heat exchanger (8), and then via the four-way valve (5); the other path is connected to the intake port of the compression unit via the second throttling element, the second heat exchanger (7), and then via the four-way valve (5); a damper assembly is also provided in the air duct of the heat pump system. The control device for the heat pump system includes: a data acquisition unit and a control unit; wherein, The acquisition unit is configured to acquire the indoor humidity and indoor temperature of the heat pump system; The control unit is configured to control at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit according to the indoor humidity and the indoor temperature, so as to control the heat pump system to operate in any one of the following modes in the cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode. The control unit, based on the indoor humidity and indoor temperature, controls the first throttling element, the second throttling element, the air valve assembly, and the expansion unit to control the heat pump system to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, including: Based on the indoor humidity and the indoor temperature, the heat pump system is determined to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode. Adjust the first throttling element and the second throttling element to control the evaporation temperature of the heat pump system to half the sum of the indoor dry-bulb temperature and the dew point temperature of the heat pump system in the cooling mode of any of the modes; control the evaporation temperature of the heat pump system to the difference between the dew point temperature of the heat pump system and the first set value in the dehumidification mode of any of the modes; and control the expansion unit to work. After adjusting the opening degree of the air valve assembly to the set opening degree value, the air valve assembly, the first throttling element and the second throttling element are controlled according to the current opening degree of the air valve assembly. The control unit controls the air valve assembly, the first throttling element, and the second throttling element according to the current opening degree of the air valve assembly, including: if the current opening degree of the air valve assembly is greater than or equal to a first preset opening value and less than or equal to a second preset opening value, then the air valve assembly is adjusted preferentially; if the current opening degree of the air valve assembly is less than the first preset opening value or greater than the second preset opening value, then the first throttling element and the second throttling element are adjusted preferentially.

2. The control device for the heat pump system according to claim 1, characterized in that, The compression unit includes an electric compressor (9) and a mechanically driven compressor (10); the expansion unit includes an expander (12) and a mechanically driven shaft (11); wherein, The expander (12) is connected to the mechanical transmission compressor (10) via the mechanical transmission shaft (11); the exhaust port of the mechanical transmission compressor (10) is connected to the intake port of the electric compressor (9); the exhaust port of the electric compressor (9) is connected to the first valve port of the four-way valve (5). The second port of the four-way valve (5) is connected to the first end of the first heat exchanger (6); the third port of the four-way valve (5) is connected to the suction port of the mechanical transmission compressor (10); the third port of the four-way valve (5) is connected to the suction port of the electric compressor (9). The fourth port of the four-way valve (5) is divided into two paths, one of which is connected to the second heat exchanger (7), and the other is connected to the third heat exchanger (8).

3. The control device for the heat pump system according to claim 2, characterized in that, The heat pump system further includes at least one of a first shut-off valve (1), a second shut-off valve (2), a third shut-off valve (23), a fourth shut-off valve (16), and a fifth shut-off valve (24); wherein, The third valve port of the four-way valve (5) is connected to the suction port of the mechanical transmission compressor (10) after passing through the first shut-off valve (1); The third valve port of the four-way valve (5) is connected to the suction port of the electric compressor (9) via the second shut-off valve (2); After passing through the first throttling element, the second end of the first heat exchanger (6) is divided into two paths. One path passes through the expander (12) and the fifth shut-off valve (24) and is connected to the second end of the third heat exchanger (8). The other path passes through the third shut-off valve (23) and the fourth shut-off valve (16) and is connected to the second end of the third heat exchanger (8). The first end of the third heat exchanger (8) is connected to the fourth valve port of the four-way valve (5).

4. The control device for the heat pump system according to claim 2, characterized in that, The heat pump system further includes: a fan (14) and a duct (15); The expander (12) is installed in the expander heat exchange duct (13); the air duct (15) is installed at the air inlet and air outlet of the expander heat exchange duct (13); and the fan (14) is installed in the air inlet of the air duct (15).

5. The control device for the heat pump system according to claim 1, characterized in that, The air valve assembly includes: a first air valve (20), a second air valve (21), and a third air valve (22); The first air valve (20) is installed in the first return air duct where the expansion unit is located, and is used to adjust the return air volume of the first return air duct; the first return air duct is the heat exchange air duct (13) of the expander; The second air valve (21) is installed in the second return air duct where the second heat exchanger (7) is located, and is used to adjust the return air volume of the second return air duct; The third air valve (22) is installed in the fresh air duct where the third heat exchanger (8) is located, and is used to adjust the fresh air volume of the fresh air duct.

6. The control device for the heat pump system according to claim 1, characterized in that, The control unit determines, based on the indoor humidity and the indoor temperature, whether the heat pump system operates in cooling mode in any one of the following modes: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, or constant temperature and constant humidity mode. When the indoor temperature is greater than the set indoor temperature and the indoor humidity is greater than the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in cooling and dehumidification mode, and the control is performed at set intervals based on the re-collected indoor humidity and indoor temperature. When the indoor temperature is greater than the indoor set temperature and the indoor humidity is less than or equal to the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in cooling mode. When the indoor temperature is less than or equal to the set indoor temperature and the indoor humidity is greater than the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in a constant temperature and dehumidification mode. When the indoor temperature is less than or equal to the indoor set temperature and the indoor humidity is less than or equal to the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in a constant temperature and humidity mode.

7. The control device for the heat pump system according to claim 1, characterized in that, The control unit adjusts the air valve assembly, including: During temperature control in any of the aforementioned modes, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, the corresponding air valve in the air valve assembly increases its opening by a set degree; if the indoor dry-bulb temperature of the heat pump system is less than the difference between the indoor set temperature and the second set value, the corresponding air valve in the air valve assembly decreases its opening by a set degree; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, the opening of the corresponding air valve in the air valve assembly remains unchanged. During humidity control in any of the aforementioned modes, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, the corresponding air valve in the air valve assembly increases its opening by the set degree; if the relative humidity of the heat pump system is less than the difference between the set humidity and the third set value, the corresponding air valve in the air valve assembly decreases its opening by the set degree; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, the opening of the corresponding air valve in the air valve assembly remains unchanged.

8. The control device for the heat pump system according to claim 1, characterized in that, The control unit adjusts at least one of the first throttling element and the second throttling element, including: During temperature control in any of the aforementioned modes, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, the opening degree of the corresponding throttling element in the first and second throttling elements decreases; if the indoor dry-bulb temperature of the heat pump system is less than the sum of the indoor set temperature and the second set value, and the indoor dry-bulb temperature of the heat pump system is not equal to the difference between the indoor set temperature and the second set value, the opening degree of the corresponding throttling element in the first and second throttling elements increases; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, the opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged. During humidity control in any of the modes, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements decreases; if the relative humidity of the heat pump system is less than the sum of the set humidity and the third set value, and the relative humidity of the heat pump system is not equal to the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements increases; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged.

9. The control device for the heat pump system according to claim 1, characterized in that, In the case where the heat pump system further includes at least one of a first shut-off valve (1), a second shut-off valve (2), a third shut-off valve (23), a fourth shut-off valve (16), and a fifth shut-off valve (24), the compression unit includes an electric compressor (9) and a mechanically driven compressor (10), the expansion unit includes an expander (12), and the air valve assembly includes a first air valve (20), a second air valve (21), and a third air valve (22), the control unit controls the operation of the expansion unit by including: When the heat pump system is operating in cooling and dehumidification mode, the refrigerant discharged from the exhaust port of the electric compressor (9) is divided into two refrigerant streams after passing through the four-way valve (5) and the first heat exchanger (6): one refrigerant stream controls the evaporation temperature of the heat pump system through the first throttling element, at which time the third shut-off valve (23) and the fourth shut-off valve (16) are closed, the expander (12) expands and does work, driving the mechanical transmission compressor (10) to rotate, and the air volume is controlled by the first air valve (20) and the third air valve (22); the other refrigerant stream controls the evaporation temperature of the heat pump system through the second throttling element, and controls the air volume by the second air valve (21); after the two refrigerant streams are mixed, the first shut-off valve (1) is opened and the second shut-off valve (2) is closed, and two compressions are achieved through the mechanical transmission compressor (10) and the electric compressor (9); When the heat pump system is operating in the cooling mode of the refrigeration mode, the refrigerant discharged from the exhaust port of the electric compressor (9) is divided into two refrigerant streams after passing through the four-way valve (5) and the first heat exchanger (6): one refrigerant stream controls the evaporation temperature of the heat pump system through the first throttling element, at which time the third shut-off valve (23) and the fourth shut-off valve (16) are closed, the expander (12) expands and does work, driving the mechanical transmission compressor (10) to rotate, and the air volume is controlled by the first air valve (20); the other refrigerant stream controls the evaporation temperature of the heat pump system through the second throttling element, and controls the air volume by the second air valve (21); after the two refrigerant streams are mixed, the first shut-off valve (1) is opened and the second shut-off valve (2) is closed, and two compressions are achieved through the mechanical transmission compressor (10) and the electric compressor (9); When the heat pump system is operating in the constant temperature and dehumidification mode of the cooling mode, the refrigerant discharged from the exhaust port of the electric compressor (9) passes through the four-way valve (5) and the first heat exchanger (6), and the second throttling element is closed. The refrigerant controls the evaporation temperature of the heat pump system through the first throttling element. At this time, the third shut-off valve (23) and the fourth shut-off valve (16) are closed. The expander (12) expands and does work, driving the mechanical transmission compressor (10) to rotate. The air volume is controlled by the first air valve (20) and the third air valve (22). The first shut-off valve (1) is opened and the second shut-off valve (2) is closed. Two compressions are achieved through the mechanical transmission compressor (10) and the electric compressor (9). When the heat pump system is operating in the constant temperature and humidity mode of the cooling mode, the refrigerant discharged from the exhaust port of the electric compressor (9) passes through the four-way valve (5) and the first heat exchanger (6), and the second throttling element is closed. The refrigerant controls the evaporation temperature of the heat pump system through the first throttling element. At this time, the third shut-off valve (23) and the fourth shut-off valve (16) are closed. The expander (12) expands and does work, driving the mechanical transmission compressor (10) to rotate. The air volume is controlled by the third air valve (22). The first shut-off valve (1) is closed and the second shut-off valve (2) is opened, and compression is achieved by the electric compressor (9).

10. A heat pump system, characterized in that, include: The control device for the heat pump system as described in any one of claims 1 to 9.

11. A control method for a heat pump system as described in claim 10, characterized in that, include: Collect the indoor humidity and indoor temperature of the heat pump system; Based on the indoor humidity and the indoor temperature, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in any one of the following modes in the cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode.

12. The control method for a heat pump system according to claim 11, characterized in that, Based on the indoor humidity and the indoor temperature, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, including: Based on the indoor humidity and the indoor temperature, the heat pump system is determined to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode. Adjust at least one of the first throttling element and the second throttling element to control the evaporation temperature of the heat pump system to half the sum of the indoor dry-bulb temperature and the dew point temperature of the heat pump system in the cooling mode of either mode; control the evaporation temperature of the heat pump system to the difference between the dew point temperature of the heat pump system and a first set value in the dehumidification mode of either mode; and control the expansion unit to operate. After adjusting the opening of the air valve assembly to a set opening value, at least one of the air valve assembly, the first throttling element, and the second throttling element is controlled according to the current opening of the air valve assembly. The method of controlling at least one of the air valve assembly, the first throttling element, and the second throttling element according to the current opening degree of the air valve assembly includes: if the current opening degree of the air valve assembly is greater than or equal to a first preset opening value and less than or equal to a second preset opening value, then the air valve assembly is adjusted preferentially; if the current opening degree of the air valve assembly is less than the first preset opening value or greater than the second preset opening value, then at least one of the first throttling element and the second throttling element is adjusted preferentially.

13. The control method for a heat pump system according to claim 12, characterized in that, Based on the indoor humidity and the indoor temperature, the heat pump system is determined to operate in any one of the following modes in cooling mode: cooling and dehumidification mode, cooling mode, constant temperature and dehumidification mode, and constant temperature and constant humidity mode, including: When the indoor temperature is greater than the set indoor temperature and the indoor humidity is greater than the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in cooling and dehumidification mode, and the control is performed at set intervals based on the re-collected indoor humidity and indoor temperature. When the indoor temperature is greater than the indoor set temperature and the indoor humidity is less than or equal to the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in cooling mode. When the indoor temperature is less than or equal to the set indoor temperature and the indoor humidity is greater than the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in a constant temperature and dehumidification mode. When the indoor temperature is less than or equal to the indoor set temperature and the indoor humidity is less than or equal to the set humidity, at least one of the first throttling element, the second throttling element, the air valve assembly, and the expansion unit is controlled to control the heat pump system to operate in a constant temperature and humidity mode.

14. The control method for a heat pump system according to claim 12, characterized in that, Adjusting the air valve assembly includes: During temperature control in any of the aforementioned modes, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, the corresponding air valve in the air valve assembly increases its opening by a set degree; if the indoor dry-bulb temperature of the heat pump system is less than the difference between the indoor set temperature and the second set value, the corresponding air valve in the air valve assembly decreases its opening by a set degree; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, the opening of the corresponding air valve in the air valve assembly remains unchanged. During humidity control in any of the aforementioned modes, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, the corresponding air valve in the air valve assembly increases its opening by the set degree; if the relative humidity of the heat pump system is less than the difference between the set humidity and the third set value, the corresponding air valve in the air valve assembly decreases its opening by the set degree; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, the opening of the corresponding air valve in the air valve assembly remains unchanged.

15. The control method for a heat pump system according to claim 12, characterized in that, Adjusting at least one of the first throttling element and the second throttling element includes: During temperature control in any of the aforementioned modes, if the indoor dry-bulb temperature of the heat pump system is greater than the sum of the indoor set temperature and the second set value, the opening degree of the corresponding throttling element in the first and second throttling elements decreases; if the indoor dry-bulb temperature of the heat pump system is less than the sum of the indoor set temperature and the second set value, and the indoor dry-bulb temperature of the heat pump system is not equal to the difference between the indoor set temperature and the second set value, the opening degree of the corresponding throttling element in the first and second throttling elements increases; if the indoor dry-bulb temperature of the heat pump system is equal to the sum of the indoor set temperature and the second set value or the difference between the indoor set temperature and the second set value, the opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged. During humidity control in any of the modes, if the relative humidity of the heat pump system is greater than the sum of the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements decreases; if the relative humidity of the heat pump system is less than the sum of the set humidity and the third set value, and the relative humidity of the heat pump system is not equal to the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements increases; if the relative humidity of the heat pump system is equal to the sum of the set humidity and the third set value or the difference between the set humidity and the third set value, the opening degree of the corresponding throttling element in the first and second throttling elements remains unchanged.

16. The control method for a heat pump system according to claim 12, characterized in that, In the case that the heat pump system further includes at least one of a first shut-off valve (1), a second shut-off valve (2), a third shut-off valve (23), a fourth shut-off valve (16), and a fifth shut-off valve (24), the compression unit includes an electric compressor (9) and a mechanically driven compressor (10), the expansion unit includes an expander (12), and the air valve assembly includes a first air valve (20), a second air valve (21), and a third air valve (22), controlling the operation of the expansion unit includes: When the heat pump system is operating in cooling and dehumidification mode, the refrigerant discharged from the exhaust port of the electric compressor (9) is divided into two refrigerant streams after passing through the four-way valve (5) and the first heat exchanger (6): one refrigerant stream controls the evaporation temperature of the heat pump system through the first throttling element, at which time the third shut-off valve (23) and the fourth shut-off valve (16) are closed, the expander (12) expands and does work, driving the mechanical transmission compressor (10) to rotate, and the air volume is controlled by the first air valve (20) and the third air valve (22); the other refrigerant stream controls the evaporation temperature of the heat pump system through the second throttling element, and controls the air volume by the second air valve (21); after the two refrigerant streams are mixed, the first shut-off valve (1) is opened and the second shut-off valve (2) is closed, and two compressions are achieved through the mechanical transmission compressor (10) and the electric compressor (9); When the heat pump system is operating in the cooling mode of the refrigeration mode, the refrigerant discharged from the exhaust port of the electric compressor (9) is divided into two refrigerant streams after passing through the four-way valve (5) and the first heat exchanger (6): one refrigerant stream controls the evaporation temperature of the heat pump system through the first throttling element, at which time the third shut-off valve (23) and the fourth shut-off valve (16) are closed, the expander (12) expands and does work, driving the mechanical transmission compressor (10) to rotate, and the air volume is controlled by the first air valve (20); the other refrigerant stream controls the evaporation temperature of the heat pump system through the second throttling element, and controls the air volume by the second air valve (21); after the two refrigerant streams are mixed, the first shut-off valve (1) is opened and the second shut-off valve (2) is closed, and two compressions are achieved through the mechanical transmission compressor (10) and the electric compressor (9); When the heat pump system is operating in the constant temperature and dehumidification mode of the cooling mode, the refrigerant discharged from the exhaust port of the electric compressor (9) passes through the four-way valve (5) and the first heat exchanger (6), and the second throttling element is closed. The refrigerant controls the evaporation temperature of the heat pump system through the first throttling element. At this time, the third shut-off valve (23) and the fourth shut-off valve (16) are closed. The expander (12) expands and does work, driving the mechanical transmission compressor (10) to rotate. The air volume is controlled by the first air valve (20) and the third air valve (22). The first shut-off valve (1) is opened and the second shut-off valve (2) is closed. Two compressions are achieved through the mechanical transmission compressor (10) and the electric compressor (9). When the heat pump system is operating in the constant temperature and humidity mode of the cooling mode, the refrigerant discharged from the exhaust port of the electric compressor (9) passes through the four-way valve (5) and the first heat exchanger (6), and the second throttling element is closed. The refrigerant controls the evaporation temperature of the heat pump system through the first throttling element. At this time, the third shut-off valve (23) and the fourth shut-off valve (16) are closed. The expander (12) expands and does work, driving the mechanical transmission compressor (10) to rotate. The air volume is controlled by the third air valve (22). The first shut-off valve (1) is closed and the second shut-off valve (2) is opened, and compression is achieved by the electric compressor (9).

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