CN213480643U - Heat pump system and air conditioning equipment - Google Patents
Heat pump system and air conditioning equipment Download PDFInfo
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- CN213480643U CN213480643U CN202022683539.5U CN202022683539U CN213480643U CN 213480643 U CN213480643 U CN 213480643U CN 202022683539 U CN202022683539 U CN 202022683539U CN 213480643 U CN213480643 U CN 213480643U
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Abstract
The present disclosure provides a heat pump system and an air conditioning apparatus. Wherein, the heat pump system includes: the heat exchanger comprises a compressor, a first indoor heat exchanger, a second indoor heat exchanger, a first outdoor heat exchanger, a second outdoor heat exchanger and a valve assembly. The valve component is respectively connected with an exhaust port and an air suction port of the compressor, a first end of the first indoor heat exchanger, a first end of the second indoor heat exchanger, a first end of the first outdoor heat exchanger and a first end of the second outdoor heat exchanger, and a second end of the first indoor heat exchanger and a second end of the second indoor heat exchanger are connected with a second end of the first outdoor heat exchanger and a second end of the second outdoor heat exchanger through connecting pipelines. The system and the equipment disclosed by the invention realize independent adjustability of indoor temperature and indoor humidity, and improve adjustability of indoor air outlet temperature under the condition of reducing energy consumption, thereby obtaining ideal indoor humidity and temperature.
Description
Technical Field
The disclosure relates to the technical field of air conditioning equipment, in particular to a heat pump system and air conditioning equipment.
Background
With the development of modern social economy, people have higher and higher requirements on the temperature and humidity of air in industrial production environment, and the application field of constant-temperature and constant-humidity environment control equipment is wider and wider. At present, the mainstream constant temperature and humidity machine is basically provided with an electric heating function. When the constant temperature and humidity machine is used, when the indoor humidity is higher than the set humidity and the indoor temperature is lower than or equal to the set temperature, the electric heating function is started to avoid temperature overshoot, and the electric heating system performs indoor heating work; when the indoor temperature is lower than the set temperature, the temperature needs to be raised, but the constant temperature and humidity can cause the problem that the outdoor heat exchanger frosts and defrosts, so that the temperature fluctuation can not meet the requirement, and the indoor electric heating is used for adjusting the temperature at the moment. However, if heating is performed using an electric heating system, the power consumption of the constant temperature and humidity machine increases, and the energy efficiency decreases.
In order to reduce power consumption, the related art known to the inventors proposes a method of using a high-temperature (70 to 90 ℃) heat source discharged from a compressor to activate a reheater, thereby reheating the reheater, thereby reducing power consumption. However, in the dehumidification and reheating mode, in order to ensure the dehumidification effect, the adjustability of the indoor air outlet temperature is not high, and ideal indoor humidity and temperature cannot be obtained.
It is noted that the information disclosed in this background section of the invention is only for enhancement of understanding of the general background of the invention, and should not be taken as an acknowledgement or any form of suggestion that this information constitutes prior art already known to a person skilled in the art.
Disclosure of Invention
The inventor researches and discovers that the problem that the indoor air outlet temperature adjustability is not high in the dehumidification and reheating mode exists in the related technology.
In view of this, the embodiments of the present disclosure provide a heat pump system and an air conditioning apparatus, which can reduce energy consumption and improve adjustability of outlet air temperature.
Some embodiments of the present disclosure provide a heat pump system, comprising:
a compressor;
a first indoor heat exchanger and a second indoor heat exchanger;
a first outdoor heat exchanger and a second outdoor heat exchanger; and
the valve assembly is used for controlling the flow direction and the on-off of the refrigerant to form a refrigerant loop;
the valve assembly is respectively connected with an exhaust port and an air suction port of the compressor, a first end of the first indoor heat exchanger, a first end of the second indoor heat exchanger, a first end of the first outdoor heat exchanger and a first end of the second outdoor heat exchanger, and a second end of the first indoor heat exchanger and a second end of the second indoor heat exchanger are connected with a second end of the first outdoor heat exchanger and a second end of the second outdoor heat exchanger through connecting pipelines.
In some embodiments, the outdoor heat exchanger further comprises a first outdoor fan and a second outdoor fan, the first outdoor fan and the first outdoor heat exchanger are located in the first air duct, the second outdoor fan and the second outdoor heat exchanger are located in the second air duct, and the first air duct and the second air duct are independently arranged.
In some embodiments, the outdoor heat exchanger further comprises a liquid storage tank, a first end of the liquid storage tank is connected with the connecting pipeline, a second end of the liquid storage tank is connected with a second end of the first outdoor heat exchanger and a second end of the second outdoor heat exchanger, a first expansion valve is arranged in a passage of the second end of the first outdoor heat exchanger connected with the second end of the liquid storage tank, and a second expansion valve is arranged in a passage of the second end of the second outdoor heat exchanger connected with the second end of the liquid storage tank.
In some embodiments, a third expansion valve is disposed in a passage of the second end connection pipe of the first indoor heat exchanger, and a fourth expansion valve is disposed in a passage of the second end connection pipe of the second indoor heat exchanger.
In some embodiments, the air conditioner further comprises an indoor side fan, the first indoor heat exchanger and the second indoor heat exchanger are located in the same air duct, and indoor side return air generated by the indoor side fan sequentially passes through the second indoor heat exchanger and the first indoor heat exchanger.
In some embodiments, a valve assembly comprises:
the first control valve is used for controlling the on-off of the air suction port of the compressor and the first end of the second indoor heat exchanger;
the second control valve is used for controlling the on-off of the air suction port of the compressor and the first end of the first outdoor heat exchanger;
the third control valve is used for controlling the on-off of the air suction port of the compressor and the first end of the second outdoor heat exchanger;
the fourth control valve is used for controlling the connection and disconnection between the exhaust port of the compressor and the first end of the second indoor heat exchanger;
the fifth control valve is used for controlling the connection and disconnection between the exhaust port of the compressor and the first end of the first outdoor heat exchanger;
the sixth control valve is used for controlling the connection and disconnection between the exhaust port of the compressor and the first end of the second outdoor heat exchanger; and
and the seventh control valve is used for controlling the on-off of the exhaust port of the compressor and the first end of the first indoor heat exchanger.
In some embodiments, the first indoor heat exchanger further comprises a throttling element disposed in a passage between a suction port of the compressor and the second end of the first indoor heat exchanger.
In some embodiments, further comprising:
a first stop valve provided in a passage between the valve assembly and the first end of the first outdoor heat exchanger;
the second stop valve is arranged in a passage between the valve component and the first end of the second outdoor heat exchanger;
a third stop valve provided in the connecting line.
In some embodiments, the air conditioner comprises an indoor unit and an outdoor unit, wherein the indoor unit comprises a compressor, a first indoor heat exchanger, a second indoor heat exchanger and a valve assembly, and the outdoor unit comprises a first outdoor heat exchanger, a second outdoor heat exchanger and a liquid storage tank.
Some embodiments of the present disclosure provide an air conditioning apparatus including the aforementioned heat pump system.
Therefore, according to the embodiment of the disclosure, by arranging the two indoor heat exchangers and the two outdoor heat exchangers, in the dehumidification and reheating mode, the two outdoor heat exchangers can respectively and independently distribute the refrigerants passing through the two indoor heat exchangers, so that the independent adjustment of the indoor temperature and humidity is realized, the adjustability of the indoor outlet air temperature is improved under the condition of reducing the energy consumption, and the ideal indoor humidity and temperature are obtained.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description, serve to explain the principles of the disclosure.
The present disclosure may be more clearly understood from the following detailed description, taken with reference to the accompanying drawings, in which:
FIG. 1 is a schematic diagram of a heat pump system refrigerant flow path in a cooling/dehumidification mode in accordance with some embodiments of the heat pump system of the present disclosure;
FIG. 2 is a schematic diagram of a heat pump system refrigerant flow path in a first dehumidification and reheat mode in accordance with some embodiments of the heat pump system of the present disclosure;
FIG. 3 is a schematic diagram of a heat pump system refrigerant flow path in a second dehumidification and reheat mode in accordance with some embodiments of the heat pump system of the present disclosure;
FIG. 4 is a schematic diagram of a heat pump system refrigerant flow path in a third dehumidification and reheat mode in accordance with some embodiments of the heat pump system of the present disclosure;
fig. 5 is a schematic view of a refrigerant flow path of a heat pump system in a first heating mode according to some embodiments of the heat pump system of the present disclosure;
fig. 6 is a schematic view of a refrigerant flow path of a heat pump system in a second heating mode according to some embodiments of the heat pump system of the present disclosure;
fig. 7 is a schematic view of a refrigerant flow path of a heat pump system in a first defrosting mode according to some embodiments of the heat pump system of the present disclosure;
fig. 8 is a schematic view of a refrigerant flow path of a heat pump system in a second defrost mode according to some embodiments of the heat pump system disclosed herein.
Description of the reference numerals
1. A compressor; 2. a first control valve; 3. a second control valve; 4. an eighth control valve; 5. a third control valve; 6. a fourth control valve; 7. a fifth control valve; 8. a ninth control valve; 9. a sixth control valve; 10. a seventh control valve; 11. a first indoor heat exchanger; 12. a second indoor heat exchanger; 13. an indoor side fan; 14. a third expansion valve; 15. a fourth expansion valve; 16. a throttling element; 17. a first shut-off valve; 18. a second stop valve; 19. a third stop valve; 20. a first outdoor heat exchanger; 21. a second outdoor heat exchanger; 22. a first expansion valve; 23. a second expansion valve; 24. a liquid storage tank; 25. a first outdoor fan; 26. a second outdoor fan; 100. an indoor unit; 200. an outdoor unit.
Detailed Description
Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and is in no way intended to limit the disclosure, its application, or uses. The present disclosure may be embodied in many different forms and is not limited to the embodiments herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art. It should be noted that: the relative arrangement of parts and steps, the composition of materials, numerical expressions and numerical values set forth in these embodiments are to be construed as merely illustrative, and not as limitative, unless specifically stated otherwise.
The use of "first," "second," and similar terms in this disclosure is not intended to indicate any order, quantity, or importance, but rather are used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that the element preceding the word covers the element listed after the word, and does not exclude the possibility that other elements are also covered. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.
In the present disclosure, when a specific device is described as being located between a first device and a second device, there may or may not be intervening devices between the specific device and the first device or the second device. When a particular device is described as being coupled to other devices, the particular device may be directly coupled to the other devices without intervening devices or may be directly coupled to the other devices with intervening devices.
All terms used in the present disclosure have the same meaning as understood by one of ordinary skill in the art to which the present disclosure belongs, unless otherwise specifically defined. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail, but are intended to be part of the specification where appropriate.
As shown in connection with fig. 1-8, some embodiments of the present disclosure provide a heat pump system, including: the air conditioner comprises a compressor 1, a first indoor heat exchanger 11, a second indoor heat exchanger 12, a first outdoor heat exchanger 20, a second outdoor heat exchanger 21 and a valve assembly, wherein the valve assembly is used for controlling the flow direction and the on-off of a refrigerant to form a refrigerant loop. The functions of cooling, heating and the like can be realized by controlling the action of the valve component. The first indoor heat exchanger 11, the second indoor heat exchanger 12, the first outdoor heat exchanger 20, and the second outdoor heat exchanger 21 may be various heat exchangers.
As shown in fig. 1, the valve assembly is connected to an air outlet and an air inlet of the compressor 1, a first end of the first indoor heat exchanger 11, a first end of the second indoor heat exchanger 12, a first end of the first outdoor heat exchanger 20, and a first end of the second outdoor heat exchanger 21, respectively, and a second end of the first indoor heat exchanger 11 and a second end of the second indoor heat exchanger 12 are connected to a second end of the first outdoor heat exchanger 20 and a second end of the second outdoor heat exchanger 21 through connecting lines.
The heat pump system is usually cool in the air sent out under the dehumidification function, and needs to be reheated for air supply, through the action of the control valve assembly, as shown in fig. 2 to 4, the refrigerant output by the exhaust port of the compressor 1 can enter the first indoor heat exchanger 11, the refrigerant output by the first indoor heat exchanger 11 enters the refrigerant loop of the heat pump system through the connecting pipeline, the dehumidification and reheating are realized while the basic function of the heat pump system is kept, and when the indoor humidity is greater than the set humidity and the indoor temperature is less than or equal to the set temperature, in order to avoid the temperature overshoot, the condensation heat generated by the first indoor heat exchanger 11 is utilized for the reheating air supply. The air is reheated by using the condensation heat generated by the first indoor heat exchanger 11, so that the air reheating function during dehumidification is realized, and the electric heating system is more economical and energy-saving.
In the exemplary embodiment, by arranging the two indoor heat exchangers and the two outdoor heat exchangers, the two outdoor heat exchangers can respectively and independently distribute the refrigerants passing through the two indoor heat exchangers in the dehumidification and reheating mode, so that the indoor temperature and humidity can be independently adjusted, the adjustability of the indoor outlet air temperature is improved under the condition of reducing energy consumption, and ideal indoor humidity and temperature can be obtained.
In order to realize that the heat dissipating capacities of the two outdoor heat exchangers can be respectively and independently adjusted, in some embodiments, as shown in fig. 1 to 8, the heat pump system further includes a first outdoor fan 25 and a second outdoor fan 26, the first outdoor fan 25 and the first outdoor heat exchanger 20 are located in the first air duct, the second outdoor fan 26 and the second outdoor heat exchanger 21 are located in the second air duct, and the first air duct and the second air duct are independently arranged.
In some embodiments, as shown in fig. 1 to 8, the heat pump system further includes a liquid storage tank 24, a first end of the liquid storage tank 24 is connected to the connecting pipeline, a second end of the liquid storage tank 24 is connected to the second end of the first outdoor heat exchanger 20 and the second end of the second outdoor heat exchanger 21, a first expansion valve 22 is disposed in a path of the second end of the first outdoor heat exchanger 20 connected to the second end of the liquid storage tank 24, and a second expansion valve 23 is disposed in a path of the second end of the second outdoor heat exchanger 21 connected to the second end of the liquid storage tank 24. The first expansion valve 22 and the second expansion valve 23 receive the liquefied high-temperature high-pressure refrigerant and convert the refrigerant into a low-temperature low-pressure liquid refrigerant, and the liquid storage tank 24 temporarily stores the refrigerant to ensure stable operation of the heat pump system.
In order to switch the modes, as shown in fig. 1 to 8, in some embodiments, a third expansion valve 14 is disposed in a path of the second end connection pipeline of the first indoor heat exchanger 11, and a fourth expansion valve 15 is disposed in a path of the second end connection pipeline of the second indoor heat exchanger 12. The third expansion valve 14 and the fourth expansion valve 15 receive the liquefied high-temperature high-pressure refrigerant and convert the refrigerant into a low-temperature low-pressure liquid refrigerant, and the liquid storage tank 24 temporarily stores the refrigerant to ensure stable operation of the heat pump system.
In some embodiments, as shown in fig. 1 to 8, the heat pump system further includes an indoor fan 13, the first indoor heat exchanger 11, and the second indoor heat exchanger 12 are located in the same air duct, and indoor return air generated by the indoor fan 13 passes through the second indoor heat exchanger 12 and the first indoor heat exchanger 11 in sequence.
As one implementation of the valve assembly, in some embodiments, as shown in fig. 1-8, the valve assembly comprises: the air conditioner comprises a first control valve 2, a second control valve 3, a third control valve 5, a fourth control valve 6, a fifth control valve 7, a sixth control valve 9 and a seventh control valve 10, wherein the first control valve 2 is used for controlling the connection and disconnection between an air suction port of a compressor 1 and a first end of a second indoor heat exchanger 12; the second control valve 3 is used for controlling the on-off of the air suction port of the compressor 1 and the first end of the first outdoor heat exchanger 20; the third control valve 5 is used for controlling the on-off of the suction port of the compressor 1 and the first end of the second outdoor heat exchanger 21; the fourth control valve 6 is used for controlling the on-off of the exhaust port of the compressor 1 and the first end of the second indoor heat exchanger 12; the fifth control valve 7 is used for controlling the on-off of the exhaust port of the compressor 1 and the first end of the first outdoor heat exchanger 20; the sixth control valve 9 is used for controlling the on-off between the exhaust port of the compressor 1 and the first end of the second outdoor heat exchanger 21; the seventh control valve 10 is used for controlling the on-off between the exhaust port of the compressor 1 and the first end of the first indoor heat exchanger 11.
In some embodiments, as shown in fig. 1 to 8, the valve assembly further includes an eighth control valve 4 and a ninth control valve 8, the eighth control valve 4 is used for controlling the on-off of the suction port of the compressor 1 and the first end of the second indoor heat exchanger 12, the ninth control valve 8 is used for controlling the on-off of the exhaust port of the compressor 1 and the first end of the second indoor heat exchanger 12, and the on-off of the eighth control valve 4 is consistent with the on-off control of the first control valve 2, and can be used as a backup mechanism for the first control valve 2, so as to prevent the system from being inoperable when the first control valve 2 fails, and ensure the operation stability of the system. Similarly, the on-off of the ninth control valve 8 is consistent with the on-off control of the fourth control valve 6, and the ninth control valve can be used as a standby mechanism of the fourth control valve 6 to prevent the system from being incapable of working when the fourth control valve 6 fails, so that the running stability of the system is ensured. In some embodiments, these control valves include solenoid valves that are energized and de-energized. Compared with an electric ball valve, the electromagnetic valve only has one-way flow and one-way pressure bearing, has lower requirements on the electromagnetic valve and has higher implementability.
In some embodiments, as shown in fig. 1 to 8, the heat pump system further includes a throttling element 16 disposed in a passage between a suction port of the compressor 1 and the second end of the first indoor heat exchanger 11. In some embodiments, the throttling element 16 comprises a capillary tube or the like. The throttling element 16 connects the second port of the first indoor heat exchanger 11 and the air suction port of the compressor 1, so that the first indoor heat exchanger 11 can be switched to the low-pressure side in the refrigeration/dehumidification mode, and meanwhile, the liquid refrigerant in the first indoor heat exchanger is discharged, and the problem that the first indoor heat exchanger 11 stores liquid is avoided.
In some embodiments, as shown in fig. 1 to 8, the heat pump system further includes a first stop valve 17, a second stop valve 18, and a third stop valve 19, wherein the first stop valve 17 is disposed in a passage between the valve assembly and the first end of the first outdoor heat exchanger 20; the second stop valve 18 is arranged in a passage between the valve assembly and the first end of the second outdoor heat exchanger 21; a third shut-off valve 19 is provided in the connecting line.
In some embodiments, the heat pump system includes an indoor unit 100 and an outdoor unit 200, the indoor unit 100 includes a compressor 1, a first indoor heat exchanger 11, a second indoor heat exchanger 12, and a valve assembly, and the outdoor unit 200 includes a first outdoor heat exchanger 20, a second outdoor heat exchanger 21, and a liquid storage tank 24, that is, in this embodiment, the compressor 1 is disposed in the indoor unit and the liquid storage tank is disposed in the outdoor unit.
The control process of the heat pump system of the present disclosure is as follows:
determining an operation mode of the heat pump system;
the operation of the valve assembly in the heat pump system is controlled according to a preset control strategy and based on the operation mode.
The operation mode comprises the following steps: at least one of a cooling/dehumidifying mode, a first dehumidifying and reheating mode, a second dehumidifying and reheating mode, a third dehumidifying and reheating mode, a first heating mode, a second heating mode, a first defrosting mode, and a second defrosting mode.
When the operation mode is the cooling/dehumidifying mode, the fifth control valve 7, the sixth control valve 9 and the first control valve 2 are controlled to be conducted, so that the exhaust port of the compressor 1 is communicated with the first end of the first outdoor heat exchanger 20 and the first end of the second outdoor heat exchanger 21, respectively, and the suction port of the compressor 1 is communicated with the first end of the second indoor heat exchanger 12.
As shown in fig. 1, in the cooling/dehumidifying mode, the refrigerant discharged from the discharge port of the compressor 1 does not pass through the first indoor heat exchanger 11, and the first indoor heat exchanger 11 does not operate. One path of refrigerant discharged from the discharge port of the compressor 1 passes through the fifth control valve 7, the first stop valve 17, the first outdoor heat exchanger 20, the first expansion valve 22, the receiver 24, the third stop valve 19, the fourth expansion valve 15, the second indoor heat exchanger 12, and the first control valve 2, and is returned to the suction port of the compressor 1. The other path of the refrigerant discharged from the discharge port of the compressor 1 passes through the sixth control valve 9, the second stop valve 18, the second outdoor heat exchanger 21, the second expansion valve 23, the receiver tank 24, the third stop valve 19, the fourth expansion valve 15, the second indoor heat exchanger 12, and the first control valve 2, and is returned to the suction port of the compressor 1.
When the operation mode is the first dehumidification and reheating mode, the seventh control valve 10, the first control valve 2, the fifth control valve 7 and the sixth control valve 9 are controlled to be conducted, so that the exhaust port of the compressor 1 is communicated with the first end of the first indoor heat exchanger 11, the first end of the first outdoor heat exchanger 20 and the first end of the second outdoor heat exchanger 21, respectively, and the suction port of the compressor 1 is communicated with the first end of the second indoor heat exchanger 12.
As shown in fig. 2, in the first dehumidification and reheating mode, the first refrigerant discharged from the discharge port of the compressor 1 passes through the seventh control valve 10, the first indoor heat exchanger 11, the third expansion valve 14, the fourth expansion valve 15, the second indoor heat exchanger 12, and the first control valve 2, and is returned to the suction port of the compressor 1. The first indoor heat exchanger 11 generates condensation heat, and the second indoor heat exchanger 12 performs dehumidification. The second refrigerant discharged from the discharge port of the compressor 1 passes through the fifth control valve 7, the first stop valve 17, the first outdoor heat exchanger 20, the first expansion valve 22, the liquid storage tank 24, the third stop valve 19, the fourth expansion valve 15, the second indoor heat exchanger 12 and the first control valve 2, and returns to the suction port of the compressor 1; the third refrigerant path discharged from the discharge port of the compressor 1 passes through the sixth control valve 9, the second stop valve 18, the second outdoor heat exchanger 21, the second expansion valve 23, the accumulator 24, the third stop valve 19, the fourth expansion valve 15, the second indoor heat exchanger 12, and the first control valve 2, and is returned to the suction port of the compressor 1.
When the operation mode is the second dehumidification and reheat mode, the seventh control valve 10, the first control valve 2, the fifth control valve 7 and the third control valve 5 are controlled to be opened, so that the exhaust port of the compressor 1 is communicated with the first end of the first indoor heat exchanger 11 and the first end of the first outdoor heat exchanger 20, respectively, and the suction port of the compressor 1 is communicated with the first end of the second outdoor heat exchanger 21 and the first end of the second indoor heat exchanger 12, respectively.
As shown in fig. 3, in the second dehumidification and reheating mode, the first refrigerant discharged from the discharge port of the compressor 1 enters the first indoor heat exchanger 11, the third expansion valve 14, the fourth expansion valve 15, the second indoor heat exchanger 12, and the first control valve 2 through the seventh control valve 10, and returns to the suction port of the compressor 1. The first indoor heat exchanger 11 generates condensation heat, and the second indoor heat exchanger 12 performs cooling and dehumidification. The second refrigerant discharged from the discharge port of the compressor 1 passes through the fifth control valve 7, the first stop valve 17, the first outdoor heat exchanger 20, the first expansion valve 22, the second expansion valve 23, the second outdoor heat exchanger 21, the second stop valve 18, and the third control valve 5, and is returned to the suction port of the compressor 1.
When the operation mode is the third dehumidification and reheat mode, the seventh control valve 10, the first control valve 2, the sixth control valve 9 and the second control valve 3 are controlled to be opened, so that the exhaust port of the compressor 1 is communicated with the first end of the first indoor heat exchanger 11 and the first end of the second outdoor heat exchanger 21, respectively, and the suction port of the compressor 1 is communicated with the first end of the first outdoor heat exchanger 20 and the first end of the second indoor heat exchanger 12, respectively.
As shown in fig. 4, in the third dehumidification and reheating mode, the first refrigerant discharged from the discharge port of the compressor 1 enters the first indoor heat exchanger 11, the third expansion valve 14, the fourth expansion valve 15, the second indoor heat exchanger 12, and the first control valve 2 through the seventh control valve 10, and returns to the suction port of the compressor 1. The first indoor heat exchanger 11 generates condensation heat, and the second indoor heat exchanger 12 performs cooling and dehumidification. The second refrigerant discharged from the discharge port of the compressor 1 passes through the sixth control valve 9, the second stop valve 18, the second outdoor heat exchanger 21, the second expansion valve 23, the first expansion valve 22, the second outdoor heat exchanger 21, the second stop valve 18, and the second control valve 3, and returns to the suction port of the compressor 1.
When the operation mode is the first heating mode, the seventh control valve 10, the fourth control valve 6, the second control valve 3 and the third control valve 5 are controlled to be opened, so that the discharge port of the compressor 1 is communicated with the first end of the first indoor heat exchanger 11 and the first end of the second indoor heat exchanger 12, respectively, and the suction port of the compressor 1 is communicated with the first end of the first outdoor heat exchanger 20 and the first end of the second outdoor heat exchanger 21, respectively.
As shown in fig. 5, in the first heating mode, the first refrigerant discharged from the discharge port of the compressor 1 enters the first indoor heat exchanger 11 through the seventh control valve 10, and then enters the accumulator 24 through the third expansion valve 14 and the third stop valve 19. The first indoor heat exchanger 11 generates condensation heat. The second refrigerant path discharged from the discharge port of the compressor 1 enters the second indoor heat exchanger 12 through the fourth control valve 6, and enters the accumulator 24 through the fourth expansion valve 15 and the third stop valve 19. The second indoor heat exchanger 12 generates condensation heat. One path of refrigerant output by the liquid storage tank 24 passes through the second expansion valve 23, the second outdoor heat exchanger 21, the second stop valve 18 and the third control valve 5 and returns to the suction port of the compressor 1; the other path of refrigerant output from the accumulator 24 passes through the first expansion valve 22, the first outdoor heat exchanger 20, the first stop valve 17 and the second control valve 3, and returns to the suction port of the compressor 1.
When the operation mode is the second heating mode, the fourth control valve 6, the second control valve 3 and the third control valve 5 are controlled to be conducted, so that the discharge port of the compressor 1 is communicated with the first end of the second indoor heat exchanger 12, and the suction port of the compressor 1 is communicated with the first end of the first outdoor heat exchanger 20 and the first end of the second outdoor heat exchanger 21, respectively.
As shown in fig. 6, in the second heating mode, the refrigerant discharged from the discharge port of the compressor 1 does not pass through the first indoor heat exchanger 11, and the first indoor heat exchanger 11 does not operate. The refrigerant discharged from the discharge port of the compressor 1 enters the second indoor heat exchanger 12 through the fourth control valve 6, and enters the accumulator 24 through the fourth expansion valve 15 and the third stop valve 19. The second indoor heat exchanger 12 generates condensation heat. One path of refrigerant output by the liquid storage tank 24 passes through the second expansion valve 23, the second outdoor heat exchanger 21, the second stop valve 18 and the third control valve 5 and returns to the suction port of the compressor 1; the other path of refrigerant output from the accumulator 24 passes through the first expansion valve 22, the first outdoor heat exchanger 20, the first stop valve 17 and the second control valve 3, and returns to the suction port of the compressor 1.
When the operation mode is the first defrosting mode, the fourth control valve 6, the sixth control valve 9 and the second control valve 3 are controlled to be conducted, so that the exhaust port of the compressor 1 is communicated with the first end of the second indoor heat exchanger 12 and the first end of the second outdoor heat exchanger 21, respectively, and the suction port of the compressor 1 is communicated with the first end of the first outdoor heat exchanger 20.
As shown in fig. 7, in the first defrosting mode, the refrigerant discharged from the discharge port of the compressor 1 does not pass through the first indoor heat exchanger 11, and the first indoor heat exchanger 11 does not operate. The first path of refrigerant discharged from the exhaust port of the compressor 1 enters the second indoor heat exchanger 12 through the fourth control valve 6, enters the liquid storage tank 24 through the fourth expansion valve 15 and the third stop valve 19, and the second indoor heat exchanger 12 generates condensation heat. The refrigerant output from the accumulator 24 passes through the first expansion valve 22, the first outdoor heat exchanger 20, the first stop valve 17 and the second control valve 3, and returns to the suction port of the compressor 1. The second refrigerant discharged from the discharge port of the compressor 1 passes through the second stop valve 18, the second outdoor heat exchanger 21, and the second expansion valve 23, and then passes through the first expansion valve 22, the first outdoor heat exchanger 20, the first stop valve 17, and the second control valve 3, and returns to the suction port of the compressor 1, thereby performing defrosting of the second outdoor heat exchanger.
When the operation mode is the second frost removal mode, the fourth control valve 6, the fifth control valve 7 and the third control valve 5 are controlled to be conducted, so that the exhaust port of the compressor 1 is communicated with the first end of the second indoor heat exchanger 12 and the first end of the first outdoor heat exchanger 20 respectively, and the suction port of the compressor 1 is communicated with the first end of the second outdoor heat exchanger 21.
As shown in fig. 8, in the second defrosting mode, the refrigerant discharged from the discharge port of the compressor 1 does not pass through the first indoor heat exchanger 11, and the first indoor heat exchanger 11 does not operate. The first path of refrigerant discharged from the exhaust port of the compressor 1 enters the second indoor heat exchanger 12 through the fourth control valve 6, enters the liquid storage tank 24 through the fourth expansion valve 15 and the third stop valve 19, and the second indoor heat exchanger 12 generates condensation heat. The refrigerant output from the accumulator 24 passes through the second expansion valve 23, the second outdoor heat exchanger 21, the second stop valve 18 and the third control valve 5, and returns to the suction port of the compressor 1. The second refrigerant discharged from the discharge port of the compressor 1 passes through the first cutoff valve 17, the first outdoor heat exchanger 20, and the first expansion valve 22, and then passes through the second expansion valve 23, the second outdoor heat exchanger 21, the second cutoff valve 18, and the third control valve 5, and returns to the suction port of the compressor 1, thereby performing the defrosting process of the first outdoor heat exchanger.
When the indoor has cold load or wet load, the system firstly enters a refrigeration/dehumidification mode, the functional relation of the difference value between the indoor environment temperature and the set temperature can be used for representing the cold load, and the functional relation of the difference value between the indoor moisture content and the set moisture content can be used for representing the wet load. When the moisture load is larger than the cooling load, for example, the moisture content is not lower than the set value, but the indoor temperature is already lower than the set value, the first dehumidification and reheating mode is entered.
When the heat exchange amount of the indoor heat exchanger is the maximum in the first dehumidification and reheating mode and the indoor moisture load requirement is not met, the second dehumidification and reheating mode is entered, and as shown in fig. 3, the heat exchange amount of the first indoor heat exchanger 11 is increased by reducing the first outdoor heat exchanger 20; by increasing the heat exchange amount of the second outdoor heat exchanger 21, the heat exchange amount of the second indoor heat exchanger 12 is reduced. Or enter a third dehumidification and reheating mode, as shown in fig. 4, by reducing the heat exchange amount of the second outdoor heat exchanger 21, the heat exchange amount of the first indoor heat exchanger 11 is increased; by increasing the heat exchange amount of the first outdoor heat exchanger 20, the heat exchange amount of the second indoor heat exchanger 12 is reduced. The two outdoor heat exchangers can respectively and independently distribute the refrigerants passing through the two indoor heat exchangers, so that the indoor temperature and humidity can be independently adjusted, the adjustability of the indoor air outlet temperature is improved under the condition of reducing energy consumption, and ideal indoor humidity and temperature are obtained.
When the operation mode is the second dehumidification and reheating mode, the heat exchange amount of the first outdoor heat exchanger 20 is reduced when the indoor humidity is reduced to the preset humidity and the indoor temperature is lower than the preset temperature. This control increases the heat exchange amount of the first indoor heat exchanger 11, thereby increasing the indoor temperature.
After the preset time, if the indoor temperature is still lower than the preset temperature, the working frequency of the compressor 1 and the heat exchange quantity of the second outdoor heat exchanger 21 are increased, so that the heat exchange quantity of the first indoor heat exchanger 11 is further increased through control, the indoor temperature is increased, the heat exchange quantity of the second indoor heat exchanger 12 is increased due to the increase of the compressor frequency, the heat dissipation quantity of the second indoor heat exchanger 12 is kept unchanged through the increase of the heat exchange quantity of the second outdoor heat exchanger 21, and the indoor humidity is kept unchanged.
When the indoor humidity is reduced to the preset humidity and the indoor temperature is lower than the preset temperature in the state that the operation mode is the third dehumidification and reheating mode, the heat exchange amount of the second outdoor heat exchanger 21 is reduced. This control increases the heat exchange amount of the first indoor heat exchanger 11, thereby increasing the indoor temperature.
After the preset time, if the indoor temperature is still less than the preset temperature, the working frequency of the compressor 1 and the heat exchange amount of the first outdoor heat exchanger 20 are increased, so that the heat exchange amount of the first indoor heat exchanger 11 is further increased by controlling, and the indoor temperature is increased.
When the indoor heat load is required, a first heating mode or a second heating mode is entered, and the first defrosting mode or the second defrosting mode is triggered according to the condition face whether the corresponding outdoor heat exchanger needs defrosting or not.
When the indoor temperature is lower than the set temperature, the temperature needs to be raised, but the heat pump system has the problem that the outdoor heat exchanger frosts and defrosts, so that the temperature fluctuation can not meet the requirement, and defrosting is needed at the moment. The heat pump system uses the double-chamber outer side heat exchanger, adopts the first defrosting mode and the second defrosting mode to realize asynchronous defrosting, and the indoor side heat exchanger still keeps a high-pressure state during defrosting, keeps the heat output of the indoor side, and reduces the fluctuation of the indoor temperature caused by the fact that the indoor side heat exchanger does not heat during defrosting of the common heat pump air conditioner.
Some embodiments of the present disclosure provide an air conditioning apparatus including the aforementioned heat pump system. In some embodiments, the air conditioning apparatus is a heat pump type thermostat and humidistat, or the like.
Thus, various embodiments of the present disclosure have been described in detail. Some details that are well known in the art have not been described in order to avoid obscuring the concepts of the present disclosure. It will be fully apparent to those skilled in the art from the foregoing description how to practice the presently disclosed embodiments.
Although some specific embodiments of the present disclosure have been described in detail by way of example, it should be understood by those skilled in the art that the foregoing examples are for purposes of illustration only and are not intended to limit the scope of the present disclosure. It will be understood by those skilled in the art that various changes may be made in the above embodiments or equivalents may be substituted for elements thereof without departing from the scope and spirit of the present disclosure. The scope of the present disclosure is defined by the appended claims.
Claims (10)
1. A heat pump system, comprising:
a compressor (1);
a first indoor heat exchanger (11) and a second indoor heat exchanger (12);
a first outdoor heat exchanger (20) and a second outdoor heat exchanger (21); and
the valve assembly is used for controlling the flow direction and the on-off of the refrigerant to form a refrigerant loop;
the valve assembly is respectively connected with an exhaust port and a suction port of the compressor (1), a first end of the first indoor heat exchanger (11), a first end of the second indoor heat exchanger (12), a first end of the first outdoor heat exchanger (20) and a first end of the second outdoor heat exchanger (21), and a second end of the first indoor heat exchanger (11) and a second end of the second indoor heat exchanger (12) are connected with a second end of the first outdoor heat exchanger (20) and a second end of the second outdoor heat exchanger (21) through connecting pipelines.
2. The heat pump system of claim 1, further comprising a first outdoor fan (25) and a second outdoor fan (26), wherein the first outdoor fan (25) and the first outdoor heat exchanger (20) are located in a first air duct, the second outdoor fan (26) and the second outdoor heat exchanger (21) are located in a second air duct, and the first air duct and the second air duct are independently provided.
3. The heat pump system according to claim 2, further comprising a liquid storage tank (24), wherein a first end of the liquid storage tank (24) is connected to the connecting pipeline, a second end of the liquid storage tank is connected to a second end of the first outdoor heat exchanger (20) and a second end of the second outdoor heat exchanger (21), a first expansion valve (22) is disposed in a passage of the second end of the first outdoor heat exchanger (20) connected to the second end of the liquid storage tank (24), and a second expansion valve (23) is disposed in a passage of the second end of the second outdoor heat exchanger (21) connected to the second end of the liquid storage tank (24).
4. A heat pump system according to claim 3, wherein a third expansion valve (14) is provided in a path in which the second end of the first indoor heat exchanger (11) is connected to the connection pipe, and a fourth expansion valve (15) is provided in a path in which the second end of the second indoor heat exchanger (12) is connected to the connection pipe.
5. The heat pump system according to claim 1, further comprising an indoor side fan (13), wherein the indoor side fan (13), the first indoor heat exchanger (11) and the second indoor heat exchanger (12) are located in the same air duct, and indoor side return air generated by the indoor side fan (13) passes through the second indoor heat exchanger (12) and the first indoor heat exchanger (11) in sequence.
6. The heat pump system of claim 5, wherein the valve assembly comprises:
the first control valve (2) is used for controlling the on-off of an air suction port of the compressor (1) and the first end of the second indoor heat exchanger (12);
the second control valve (3) is used for controlling the on-off of a suction port of the compressor (1) and the first end of the first outdoor heat exchanger (20);
the third control valve (5) is used for controlling the on-off of a suction port of the compressor (1) and the first end of the second outdoor heat exchanger (21);
the fourth control valve (6) is used for controlling the on-off of an exhaust port of the compressor (1) and the first end of the second indoor heat exchanger (12);
the fifth control valve (7) is used for controlling the on-off of the exhaust port of the compressor (1) and the first end of the first outdoor heat exchanger (20);
the sixth control valve (9) is used for controlling the on-off of the exhaust port of the compressor (1) and the first end of the second outdoor heat exchanger (21); and
and the seventh control valve (10) is used for controlling the on-off of the exhaust port of the compressor (1) and the first end of the first indoor heat exchanger (11).
7. The heat pump system according to claim 5, further comprising a throttling element (16) provided in a passage between a suction port of the compressor (1) and the second end of the first indoor heat exchanger (11).
8. The heat pump system of claim 1, further comprising:
a first shut-off valve (17) provided in a passage between the valve assembly and a first end of the first outdoor heat exchanger (20);
a second shutoff valve (18) disposed in a passage between the valve assembly and a first end of the second outdoor heat exchanger (21);
a third shut-off valve (19) provided in the connecting line.
9. The heat pump system according to claim 1, comprising an indoor unit (100) and an outdoor unit (200), wherein the indoor unit (100) comprises the compressor (1), the first indoor heat exchanger (11), the second indoor heat exchanger (12) and the valve assembly, and wherein the outdoor unit (200) comprises the first outdoor heat exchanger (20), the second outdoor heat exchanger (21) and a liquid storage tank (24).
10. An air conditioning apparatus comprising the heat pump system according to any one of claims 1 to 9.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202022683539.5U CN213480643U (en) | 2020-11-18 | 2020-11-18 | Heat pump system and air conditioning equipment |
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| CN202022683539.5U CN213480643U (en) | 2020-11-18 | 2020-11-18 | Heat pump system and air conditioning equipment |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112303954A (en) * | 2020-11-18 | 2021-02-02 | 珠海格力电器股份有限公司 | Heat pump system, control method and device thereof, air conditioning equipment and storage medium |
| CN114923228A (en) * | 2022-05-25 | 2022-08-19 | 青岛海信日立空调系统有限公司 | Central air conditioner |
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2020
- 2020-11-18 CN CN202022683539.5U patent/CN213480643U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112303954A (en) * | 2020-11-18 | 2021-02-02 | 珠海格力电器股份有限公司 | Heat pump system, control method and device thereof, air conditioning equipment and storage medium |
| CN112303954B (en) * | 2020-11-18 | 2024-04-26 | 珠海格力电器股份有限公司 | Heat pump system, control method and device thereof, air conditioning equipment and storage medium |
| CN114923228A (en) * | 2022-05-25 | 2022-08-19 | 青岛海信日立空调系统有限公司 | Central air conditioner |
| CN114923228B (en) * | 2022-05-25 | 2023-10-31 | 青岛海信日立空调系统有限公司 | Central air conditioner |
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