Air conditioner

Abstract

Disclosed is an air conditioner (1). In the air conditioner (1), when the air conditioner (1) operates in a cooling and water heating mode, a target frequency is determined on the basis of a first frequency of a compressor (100) satisfying a cooling condition and a second frequency of the compressor (100) satisfying a water heating condition, so as to control the compressor (100) to work at the target frequency, thereby adjusting the frequency of the compressor (100) on the basis of a cooling requirement and a water heating requirement. Thus, when the air conditioner (1) operates in the cooling and water heating mode, the waste of energy in the air conditioner (1) caused by excess capacity of the compressor (100) for cooling and water heating is avoided, and insufficient user comfort caused by insufficient capacity of the compressor (100) for cooling and water heating is also avoided.

Description

air conditioner

[0001] This application claims priority to Chinese patent application No. 202411827428.3, filed on December 11, 2024; and to Chinese patent application No. 202422533328.1, filed on October 18, 2024, the entire contents of which are incorporated herein by reference. Technical Field

[0002] This disclosure relates to the field of air conditioning technology, and in particular to an air conditioner. Background Technology

[0003] To meet users' daily hot water needs, the air conditioner has been upgraded to produce hot water in addition to its cooling and heating functions. The air conditioner can be connected to a water tank to produce domestic hot water. Summary of the Invention

[0004] An air conditioner is provided according to some embodiments of this disclosure. The air conditioner includes: a compressor, including an air inlet and an air outlet; an indoor heat exchanger for exchanging heat with indoor air via refrigerant; an outdoor heat exchanger, a first end of which is connected to a first end of the indoor heat exchanger, for exchanging heat between outdoor air and refrigerant; a water tank heat exchanger, a first end of which is connected to both the first ends of the indoor and outdoor heat exchangers, for exchanging heat between water and refrigerant; and a control valve assembly, including a first control valve unit, a second control valve unit, and a third control valve unit, wherein the first control valve unit is disposed at the air outlet of the compressor and the outdoor heat exchanger. Between the second ends of the heat exchanger, a second control valve unit is disposed between the compressor outlet and the second end of the water tank heat exchanger, and a third control valve unit is disposed between the first end of the water tank heat exchanger and the first end of the indoor heat exchanger and the first end of the outdoor heat exchanger; a controller is used to control the control valve group to change the flow direction of the refrigerant output from the outlet; the controller is also used to determine the first frequency corresponding to the compressor meeting the cooling conditions and the second frequency corresponding to the compressor meeting the hot water conditions when the air conditioner is operating in the cooling-to-hot water mode, determine the target frequency based on the first frequency and the second frequency, and control the compressor to operate at the target frequency. Attached Figure Description

[0005] Figure 1 is a structural diagram of an air conditioner provided in some embodiments of this disclosure.

[0006] Figure 2 is a structural diagram of an air conditioner provided in some embodiments of this disclosure.

[0007] Figure 3 is a connection structure diagram of the controller of an air conditioner provided in some embodiments of this disclosure.

[0008] Figure 4 is a refrigerant flow diagram under the cooling and hot water production mode provided in some embodiments of this disclosure.

[0009] Figure 5 is another embodiment of the air conditioner provided in some embodiments of this disclosure.

[0010] Figure 6 is a graph showing the correspondence between the variation amplitude of the water tank temperature difference and the frequency adjustment value provided in some embodiments of this disclosure.

[0011] Figure 7 is a structural diagram of an air conditioner provided according to some embodiments of the present disclosure.

[0012] Figure 8 is a structural diagram of an air conditioner in a cooling state according to some embodiments of the present disclosure.

[0013] Figure 9 is a structural diagram of an air conditioner in heating mode according to some embodiments of the present disclosure.

[0014] Figure 10 is a structural diagram of an air conditioner in hot water production state according to some embodiments of the present disclosure.

[0015] Figure 11 is a structural diagram of an air conditioner in a first cooling and hot water production state according to some embodiments of the present disclosure.

[0016] Figure 12 is a structural diagram of an air conditioner in heating or hot water production state according to some embodiments of the present disclosure.

[0017] Figure 13 is a structural diagram of an air conditioner in defrost mode according to some embodiments of the present disclosure.

[0018] Figure 14 is a structural diagram of an air conditioner in the second cooling and hot water production stage according to some embodiments of the present disclosure.

[0019] Figure 15 is a structural diagram of an air conditioner in the third cooling and hot water production stage according to some embodiments of the present disclosure. Detailed Implementation

[0020] The following description, in conjunction with the accompanying drawings, clearly and completely describes some embodiments of this disclosure. Obviously, the described embodiments are merely some, not all, of the embodiments of this disclosure. All other embodiments obtained by those skilled in the art based on the embodiments provided in this disclosure are within the scope of protection of this disclosure.

[0021] This disclosure provides an air conditioner, as shown in FIG1. ​​The air conditioner 1 may include a compressor 100. The compressor 100 has an air inlet 110 and an air outlet 120. The air conditioner 1 may include an outdoor heat exchanger 200 for exchanging heat with outdoor air. The air conditioner 1 may include an indoor heat exchanger 300 for exchanging heat with indoor air using refrigerant flowing out of the compressor 100. In some embodiments, as shown in FIG2, a first end of the indoor heat exchanger 300 is connected to a first end of the outdoor heat exchanger 200. In this way, refrigerant can flow from the first end of the outdoor heat exchanger 200 to the indoor heat exchanger 300, or refrigerant can also flow from the first end of the indoor heat exchanger 300 to the outdoor heat exchanger 200, thereby switching the mode of the air conditioner 1 so that the indoor heat exchanger 300 can act as a condenser or an evaporator, thereby achieving indoor cooling or heating.

[0022] In some embodiments, as shown in FIG1, the air conditioner 1 may include a water tank heat exchanger 400, which is used for heat exchange with water in a water tank 710. A first end of the water tank heat exchanger 400 is connected to a first end of both an indoor heat exchanger 300 and an outdoor heat exchanger 200. Thus, refrigerant flowing from the first end of the water tank heat exchanger 400 can flow to the outdoor heat exchanger 200 and / or the indoor heat exchanger 300. Specifically, when the refrigerant flows simultaneously to both the outdoor heat exchanger 200 and the indoor heat exchanger 300, the refrigerant flowing from the water tank heat exchanger 400 is divided in two, meaning the flow rate of refrigerant flowing to either the indoor heat exchanger 300 or the outdoor heat exchanger 200 is only half the flow rate of refrigerant in the water tank heat exchanger 400. Therefore, in this case, the hot water production capacity is greater than the cooling capacity, or the hot water production capacity is greater than the heating capacity. When the refrigerant flows only to the outdoor heat exchanger 200 or the indoor heat exchanger 300, that is, the flow rate of the refrigerant that exchanges heat in the water tank heat exchanger 400 is equal to or similar to the flow rate of the refrigerant that flows to the indoor heat exchanger 300 or the outdoor heat exchanger 200. Therefore, at this time, the hot water production capacity is equivalent to the cooling capacity, or the hot water production capacity is equivalent to the heating capacity.

[0023] In some embodiments, as shown in Figures 1 and 2, the air conditioner 1 may include a control valve assembly, which is connected to the air inlet 110, the air outlet 120, the outdoor heat exchanger 200, the indoor heat exchanger 300, and the water tank heat exchanger 400, respectively. For example, the control valve assembly can control the flow direction of the refrigerant and perform one of the following functions: cooling function, heating function, cooling and hot water function, heating and hot water function, hot water function, defrosting mode, etc. In some embodiments, as shown in Figures 1 and 2, the control valve assembly may include a first control valve unit 5, which is disposed between the air inlet 110 and the air outlet 120 of the compressor 100 and the second end of the outdoor heat exchanger 200. In this way, the refrigerant can flow from the outlet 120 of the compressor 100 to the first control valve unit 5, and then through the first control valve unit 5 to the outdoor heat exchanger 200; or, the refrigerant can flow from the outdoor heat exchanger 200 through the first control valve unit 5 to the inlet 110 of the compressor 100. Thus, by controlling the first control valve unit 5, it is possible to control whether the refrigerant flows through the outdoor heat exchanger 200, and the order or direction of its flow through the outdoor heat exchanger 200, thereby controlling the outdoor heat exchanger 200 to act as a condenser or an evaporator.

[0024] In some embodiments, as shown in FIG2, the first control valve unit 5 may also be connected to the second end of the indoor heat exchanger 300, so that the refrigerant flowing out of the indoor heat exchanger 300 can flow directly to the compressor 100 through the first control valve unit 5, or the refrigerant flowing out of the compressor 100 can first flow to the indoor heat exchanger 300 through the first control valve unit 5, thereby controlling the flow direction of the refrigerant flowing through the indoor heat exchanger 300.

[0025] In some embodiments, the first control valve unit 5 may include at least two control valves connected in series or in parallel to change the flow direction of refrigerant between the compressor 100 and the outdoor heat exchanger 200. For example, as shown in FIG2, the first control valve unit 5 may include a four-way valve 51 and a three-way valve 52. The D port of the four-way valve 51 is connected to the outlet 120 of the compressor 100. The C port of the four-way valve 51 is connected to the second port of the three-way valve 52. The E port of the four-way valve 51 is connected to the second end of the indoor heat exchanger 300. The S port of the four-way valve 51 is connected to the inlet 110 of the compressor 100 through a gas-liquid separator 910. The first port of the three-way valve 52 is connected to the second end of the outdoor heat exchanger 200. The second port of the three-way valve 52 is connected to the C port of the four-way valve 51. The third port of the three-way valve 52 is connected to the S port of the four-way valve 51. It is also connected to the inlet 110 of the compressor 100 through the gas-liquid separator 910.

[0026] The gas-liquid separator 910 can be used to store the liquid refrigerant flowing to the air inlet 110 of the compressor 100, which can ensure that the refrigerant supply in the air conditioner 1 is sufficient, so as to ensure that the air conditioner 1 operates more reliably.

[0027] In some embodiments, as shown in Figures 1 and 2, the control valve assembly may include a second control valve unit 7, which is disposed between the air inlet 110 and air outlet 120 of the compressor 100 and the second end of the water tank heat exchanger 400. In this way, refrigerant can flow from the air outlet 120 of the compressor 100 to the second control valve unit 7, and then through the second control valve unit 7 to the water tank heat exchanger 400, thereby allowing the refrigerant to release heat to the domestic water through the water tank heat exchanger 400 to heat the domestic water; alternatively, the refrigerant can also flow from the water tank heat exchanger 400 to the second control valve unit 7, and then through the second control valve unit 7 to the air inlet 110 of the compressor 100, thus flowing into the compressor 100.

[0028] In some embodiments, the second control valve unit 7 may include at least two control valves, which may be connected in series or in parallel to change the flow direction and flow rate of refrigerant between the compressor and the water tank heat exchanger 400. For example, as shown in FIG2, the second control valve unit 7 may include a first solenoid valve 71 and a second solenoid valve 72. The first end of the first solenoid valve 71 is connected to the outlet 120 of the compressor 100 and the D port of the four-way valve, respectively. The second end of the first solenoid valve 71 is connected to the second end of the water tank heat exchanger 400. The first end of the second solenoid valve 72 is connected to the inlet 110 of the compressor 100 through the gas-liquid separator 910. At the same time, the first end of the second solenoid valve 72 is also connected to the third port of the three-way valve and the S end of the four-way valve. The second end of the second solenoid valve 72 is connected to the second end of the water tank heat exchanger 400.

[0029] In some embodiments, as shown in Figures 1 and 2, the control valve assembly may include a third control valve unit 6, which is disposed between the first end of the water tank heat exchanger 400 and the first end of the indoor heat exchanger 300 and the first end of the outdoor heat exchanger 200. Thus, refrigerant can flow from the water tank heat exchanger 400 and through the third control valve unit 6 to the indoor heat exchanger 300 or the outdoor heat exchanger 200; or, after flowing from the indoor heat exchanger 300, the refrigerant can flow through the third control valve unit 6 to the outdoor heat exchanger 200, i.e., without passing through the water tank heat exchanger 400; or, after flowing from the outdoor heat exchanger 200, the refrigerant can flow through the third control valve unit 6 to the indoor heat exchanger 300 and / or the water tank heat exchanger 400. The third control valve unit 6 controls the flow of refrigerant through one or more of the water tank heat exchanger 400, indoor heat exchanger 300, and outdoor heat exchanger 200, as well as the order in which the refrigerant flows through the water tank heat exchanger 400, indoor heat exchanger, and outdoor heat exchanger. This allows the outdoor heat exchanger 200 to act as a condenser or evaporator, or the indoor heat exchanger to act as a condenser or evaporator, or the water tank heat exchanger 400 to act as a condenser or evaporator.

[0030] In some embodiments, the third control valve unit 6 may include at least two control valves, which may be connected in series or in parallel to change the flow direction and flow rate of refrigerant between the indoor heat exchanger 300, the outdoor heat exchanger 200, and the water tank heat exchanger 400. For example, as shown in FIG2, the third control valve unit 6 may include a first electronic expansion valve 61, a second electronic expansion valve 62, a third electronic expansion valve 63, and a fourth electronic expansion valve 64. The first electronic expansion valve 61 is connected to the first end of the outdoor heat exchanger 200 and the main inlet of the economizer 800. The second electronic expansion valve 62 is connected to the first end of the water tank heat exchanger 400 and the inlet of the liquid receiver 920. The outlet of the liquid receiver 920 is connected to the main inlet of the economizer 800. The third electronic expansion valve 63 is connected to the main outlet of the economizer 800 and the first end of the indoor heat exchanger 300. One port of the fourth electronic expansion valve 64 is connected to the pipe between the third electronic expansion valve 63 and the main inlet of the economizer 800, and the other port of the fourth electronic expansion valve 64 is connected to the auxiliary inlet of the economizer 800. The economizer 800 is used to adapt to the enthalpy-increasing compressor, which can improve the heating performance in low-temperature environments. It increases the suction enthalpy of the compressor 100 by recovering part of the refrigerant's energy, thereby improving the heating capacity and energy efficiency ratio of the air conditioner 1. The liquid receiver 920 can be used to store the liquid refrigerant flowing to the outdoor heat exchanger 200.

[0031] In some embodiments, as shown in FIG3, the air conditioner 1 may include a controller 10, which is electrically connected to the compressor 100 and the control valve group (not shown in FIG1) to control the operating frequency of the compressor 100 and the on or off state of the control valve group, thereby realizing the control of the flow rate and direction of the refrigerant.

[0032] In some embodiments, as shown in FIG2, the air conditioner 1 may include a water tank 710 and a water pump 720. The water tank 710 and a water tank heat exchanger 400 are connected to form a water passage. The water pump 720 is disposed in the water passage. The water tank 710 is used to store domestic water, and the water pump 720 is used to draw water from the water tank 710 to the water tank heat exchanger 400, so that the water tank heat exchanger 400 heats the water by exchanging heat with a refrigerant, and then the hot water is discharged through the water tank 710.

[0033] In some embodiments, based on the structure of the air conditioner 1 shown in FIG2, when the air conditioner 1 is operating in cooling mode, the C and D terminals of the four-way valve 51 are connected, the E and S terminals of the four-way valve 51 are connected, the first solenoid valve 71 is closed, and the second solenoid valve 72 is closed. The first and second ports of the three-way valve 52 are connected, the third electronic expansion valve 63 and the first electronic expansion valve 61 are open, and the second electronic expansion valve 62 and the fourth electronic expansion valve 64 are closed. At this time, after the refrigerant is discharged from the outlet 120 of the compressor 100, it passes through the four-way valve 51, the three-way valve 52, the outdoor heat exchanger 200, the third electronic expansion valve 63, the economizer 800, the liquid receiver 920, the first electronic expansion valve 61, the indoor heat exchanger 300, the four-way valve 51, the gas-liquid separator 910, and finally enters the compressor 100 through the inlet 110 of the compressor 100.

[0034] In some embodiments, when the air conditioner 1 is operating in heating mode, the C and S terminals of the four-way valve 51 are connected, the E and D terminals are connected, the first solenoid valve 71 is closed, and the second solenoid valve 72 is closed. The first and second ports of the three-way valve 52 are connected, the third electronic expansion valve 63, the first electronic expansion valve 61, and the fourth electronic expansion valve 64 are open, and the second electronic expansion valve 62 is closed. At this time, after the refrigerant is discharged from the outlet 120 of the compressor 100, it passes through the four-way valve 51, the indoor heat exchanger 300, the first electronic expansion valve 61, the liquid receiver 920, and the economizer 800. After the refrigerant flows out of the economizer 800, part of the refrigerant passes through the third electronic expansion valve 63, the outdoor heat exchanger 200, the three-way valve 52, the four-way valve 51, and the gas-liquid separator 910, and finally enters the compressor 100 through the inlet 110 of the compressor 100; the other part of the refrigerant passes through the fourth electronic expansion valve 64 and the economizer 800, and finally enters the compressor 100 through the gas filler 130 of the compressor 100.

[0035] In some embodiments, when the air conditioner 1 is operating in heating / hot water mode, the C and S terminals of the four-way valve 51 are connected, the E and D terminals are connected, the first solenoid valve 71 is open, and the second solenoid valve 72 is closed. The first and second ports of the three-way valve 52 are connected, and the first electronic expansion valve 61, the second electronic expansion valve 62, the third electronic expansion valve 63, and the fourth electronic expansion valve 64 are open. At this time, after the refrigerant is discharged from the outlet 120 of the compressor 100, part of the refrigerant passes through the four-way valve 51, the indoor heat exchanger 300, the first electronic expansion valve 61, the liquid receiver 920, and the economizer 800. The other part of the refrigerant passes through the first solenoid valve 71, the water tank heat exchanger 400, and the second electronic expansion valve 62. After the two refrigerant flows merge, they enter the third electronic expansion valve 63, the outdoor heat exchanger 200, the three-way valve 52, the four-way valve 51, and the gas-liquid separator 910. Finally, they enter the compressor 100 through the inlet 110. Among them, the refrigerant that flows through the economizer 800, after flowing out of the economizer 800, part of it merges with the refrigerant that flows through the water tank heat exchanger 400 and enters the third electronic expansion valve 63. The other part passes through the fourth electronic expansion valve 64 and the economizer 800. Finally, it enters the compressor 100 through the air supply port 130.

[0036] In some embodiments, when the air conditioner 1 is operating in hot water mode, the C and D terminals of the four-way valve 51 are connected, and the E and S terminals are connected. The first solenoid valve 71 is open, and the second solenoid valve 72 is closed. The first and third ports of the three-way valve 52 are connected, the third electronic expansion valve 63 and the second electronic expansion valve 62 are open, and the first electronic expansion valve 61 and the fourth electronic expansion valve 64 are closed. At this time, after the refrigerant is discharged from the air outlet 120 of the compressor 100, it passes through the first solenoid valve 71, the water tank heat exchanger 400, the second electronic expansion valve 62, the third electronic expansion valve 63, the outdoor heat exchanger 200, the three-way valve 52, and the gas-liquid separator 910, and finally enters the compressor 100 through the air inlet 110.

[0037] In some embodiments, when the air conditioner 1 is operating in defrost mode, the C and D terminals of the four-way valve 51 are connected, the E and S terminals are connected, the first solenoid valve 71 is closed, and the second solenoid valve 72 is open. The first and second ports of the three-way valve 52 are connected, the third electronic expansion valve 63 and the second electronic expansion valve 62 are open, and the first electronic expansion valve 61 and the fourth electronic expansion valve 64 are closed.

[0038] At this time, after the refrigerant is discharged from the outlet 120 of the compressor 100, it passes through the four-way valve 51, the three-way valve 52, the outdoor heat exchanger 200, the third electronic expansion valve 63, the second electronic expansion valve 62, the water tank heat exchanger 400, the second solenoid valve 72, and the gas-liquid separator 910, and finally enters the compressor 100 through the inlet 110 of the compressor 100.

[0039] In some embodiments, when the air conditioner 1 is operating in cooling and hot water mode, the following situations can be distinguished based on the relationship between its cooling capacity and hot water production capacity:

[0040] In scenario one, when the cooling capacity is less than the hot water capacity, terminals C and D of the four-way valve 51 are connected, and terminals E and S are connected. The first solenoid valve 71 is open, and the second solenoid valve 72 is closed. Ports 1 and 3 of the three-way valve 52 are connected, and the first electronic expansion valve 61, the second electronic expansion valve 62, and the third electronic expansion valve 63 are open, while the fourth electronic expansion valve 64 is closed. At this time, after the refrigerant is discharged through the outlet 120 of the compressor 100, as shown in Figure 4, it passes through the water tank heat exchanger 400 and the second electronic expansion valve 62. Part of the refrigerant then passes through the liquid storage tank 920, the economizer 800, the third electronic expansion valve 63, the indoor heat exchanger 300, and the four-way valve 51, while the other part passes through the first electronic expansion valve 61, the outdoor heat exchanger 200, and the three-way valve 52. The two refrigerant streams converge and enter the gas-liquid separator 910, and then enter the compressor 100.

[0041] In scenario two, when the cooling capacity is equivalent to the hot water capacity, terminals C and D of the four-way valve 51 are connected, and terminals E and S are connected. The first solenoid valve 71 is open, and the second solenoid valve 72 is closed. Ports 1 and 2 of the three-way valve 52 are connected, and the second electronic expansion valve 62 and the first electronic expansion valve 61 are open, while the third electronic expansion valve 63 and the fourth electronic expansion valve 64 are closed. At this time, after the refrigerant is discharged from the outlet 120 of the compressor 100, it passes through the water tank heat exchanger 400, the second electronic expansion valve 62, the economizer 800, the liquid receiver 920, the first electronic expansion valve 61, the indoor heat exchanger 300, the four-way valve 51, and the gas-liquid separator 910, and finally enters the compressor 100 through the inlet 110.

[0042] In scenario three, when the cooling capacity exceeds the hot water capacity, terminals C and D of the four-way valve 51 are connected, and terminals E and S are connected. The first solenoid valve 71 opens, and the second solenoid valve 72 closes. Ports 1 and 2 of the three-way valve 52 are connected, and the third electronic expansion valve 63, the second electronic expansion valve 62, and the first electronic expansion valve 61 open, while the fourth electronic expansion valve 64 closes. After the refrigerant is discharged from the outlet 120 of the compressor 100, part of the refrigerant passes through the four-way valve 51, the three-way valve 52, the outdoor heat exchanger 200, and the third electronic expansion valve 63, while the other part passes through the water tank heat exchanger 400 and the second electronic expansion valve 62. The two refrigerant streams merge and then pass through the liquid receiver 920, the economizer 800, the first electronic expansion valve 61, the indoor heat exchanger 300, the four-way valve 51, and the gas-liquid separator 910, finally entering the compressor 100 through the inlet 110. The cooling capacity is determined based on the difference between the real-time indoor temperature and the target indoor temperature, while the hot water production capacity is determined based on the difference between the real-time outlet water temperature and the target outlet water temperature.

[0043] As can be seen from the above structure, because the air conditioner 1 has added a water tank 710 and a water tank heat exchanger 400 as a source of domestic hot water, during the simultaneous operation of cooling and hot water production, the refrigerant discharged from the outlet 120 of the compressor 100 needs to pass through the water tank heat exchanger 400 first, and then through the indoor heat exchanger 300 and the outdoor heat exchanger 200. That is, it will prioritize heating the domestic water in the water tank 710. However, when the load under cooling conditions and the load under hot water production conditions change, the air conditioner 1 cannot adjust the capacity distribution of the water tank 710 and the terminal, which may result in insufficient or excessive capacity in a certain mode, affecting the user's comfort and potentially causing energy waste.

[0044] This disclosure provides an air conditioner 1 in some embodiments. When the air conditioner 1 is operating in cooling and hot water mode, a target frequency is determined based on a first frequency of the compressor 100 that meets cooling conditions and a second frequency that meets hot water conditions. The compressor 100 is then controlled to operate at the target frequency, thereby adjusting the frequency of the compressor 100 according to cooling and hot water demand. Since the final operating frequency of the compressor 100 is determined based on the first and second frequencies, the air conditioner 1, when operating in cooling and hot water mode, can avoid energy waste caused by excessive cooling and hot water production capacity of the compressor 100, while also avoiding insufficient user comfort caused by insufficient cooling and hot water production capacity of the compressor 100.

[0045] In some embodiments, based on the structure of the air conditioner 1 shown in any of Figures 1, 2 and 3, the controller 10 of the air conditioner 1 can be configured to perform the following steps: Step S101, when the operating mode of the air conditioner 1 is cooling and hot water production mode, determine a first frequency corresponding to the cooling condition of the compressor 100, and determine a second frequency corresponding to the hot water production condition of the compressor 100; Step S102, determine a target frequency based on the first frequency and the second frequency, and control the compressor 100 to operate at the target frequency.

[0046] When air conditioner 1 operates in cooling mode, sufficient refrigerant needs to flow through the indoor heat exchanger 300 to ensure that the indoor heat exchanger 300 can reduce the real-time indoor temperature to the target indoor temperature after heat exchange with the refrigerant. The refrigerant flow rate is related to the operating conditions of air conditioner 1. Therefore, the aforementioned cooling conditions refer to the operating conditions of air conditioner 1 that enable the indoor temperature to be reduced to the target indoor temperature. The operating conditions include the operating parameters of the target components, which include one or more of the compressor 100, indoor heat exchanger 300, outdoor heat exchanger 200, and water tank heat exchanger 400.

[0047] When air conditioner 1 is operating in hot water mode, sufficient refrigerant needs to flow through the water tank heat exchanger 400 to ensure that the water tank heat exchanger 400 can adjust the real-time outlet water temperature to the target outlet water temperature after heat exchange with the refrigerant. The refrigerant flow rate is related to the operating conditions of air conditioner 1. Therefore, the aforementioned hot water production conditions refer to the operating conditions of air conditioner 1 that enable the real-time outlet water temperature to be adjusted to the target outlet water temperature. The operating conditions include the operating parameters of the target components, which include one or more of the compressor 100, indoor heat exchanger 300, outdoor heat exchanger 200, and water tank heat exchanger 400.

[0048] It should be noted that if the operating frequency of the compressor 100 is insufficient to meet the requirements for cooling or hot water production, then no matter how the operating parameters of other components are adjusted, the air conditioner 1 will not be able to meet the cooling or hot water production requirements. For example, if the frequency of the compressor 100 cannot allow more and faster refrigerant to flow to the indoor heat exchanger 300, then the indoor heat exchanger 300 cannot perform heat exchange with sufficient refrigerant, and the indoor temperature cannot drop to the user's desired temperature. Similarly, if the frequency of the compressor 100 cannot allow more and faster refrigerant to flow to the water tank heat exchanger 400, then the water tank heat exchanger 400 cannot perform heat exchange with sufficient refrigerant, thus preventing the domestic water in the water tank 710 from being heated to the set temperature, and failing to meet the user's domestic water usage needs.

[0049] Therefore, the controller 10 can determine a first frequency corresponding to the compressor 100 meeting the cooling conditions, and a second frequency corresponding to the compressor 100 meeting the hot water production conditions. The first frequency corresponding to the cooling conditions refers to the compressor's operating frequency at which the indoor temperature is reduced to the target indoor temperature, and the second frequency corresponding to the hot water production conditions refers to the compressor's operating frequency at which the real-time outlet water temperature is adjusted to the target outlet water temperature.

[0050] In some embodiments, the target frequency can be the maximum value of the first frequency and the second frequency. For example, when the user requires the real-time indoor temperature to reach the target indoor temperature, the real-time outlet water temperature also needs to reach the target outlet water temperature. In this case, the controller 10 needs to determine the maximum frequency of the first frequency and the second frequency as the target frequency, so that the operating frequency of the compressor 100 can simultaneously meet the cooling and hot water production conditions, thereby improving the user experience.

[0051] In other embodiments, the target frequency can be calculated based on the first frequency and the second frequency. For example, if the target frequency is the average of the sum of the first frequency and the second frequency, then when the value of the first frequency required by the compressor to meet the cooling conditions is greater than the value of the second frequency required to meet the hot water conditions, the compressor 100 can reduce the indoor temperature to the target indoor temperature while still having additional energy to heat domestic water, thereby reducing the energy consumption of the air conditioner 1.

[0052] In some embodiments, the operation of the air conditioner 1 can be divided into an initial operating stage and a normal operating stage. The initial operating stage refers to the gradual transition of the air conditioner 1 from a non-operating state to a normal operating state when it is first started. During this stage, it is necessary to determine the initial operating frequency of the compressor 100 to control the compressor 100 to operate at the initial operating frequency, thereby ensuring the normal start-up and operation of the air conditioner 1. After the compressor 100 has been operating at the initial operating frequency for a period of time, the air conditioner 1 will enter the normal operating stage. During the normal operating stage, the controller 10 needs to adjust the operating frequency of the compressor 100 in real time according to the operating parameters during operation, such as the water tank temperature and the outlet water temperature of the water tank heat exchanger 400.

[0053] Therefore, in some embodiments, when the controller 10 specifically executes step S102, it may include the following steps: Step S1021, when the compressor 100 is in the initial working stage of the cooling and hot water production mode, determine the first initial frequency corresponding to the cooling condition and the second initial frequency corresponding to the hot water production condition of the compressor 100. Step S1022, determine the target initial frequency based on the first initial frequency and the second initial frequency, and control the compressor 100 to operate at the target initial frequency. It should be noted that, in the initial working stage of the air conditioner 1, the controller 10 determines the target initial frequency based on the first initial frequency corresponding to the cooling condition and the second initial frequency corresponding to the hot water production condition, which can ensure that the compressor 100 can meet the cooling and hot water production conditions in the initial working stage, thereby improving the heat exchange response.

[0054] When air conditioner 1 operates in the initial stage of cooling / hot water mode, controller 10 needs to determine the first initial frequency under cooling conditions and the second initial frequency under hot water conditions. However, in cooling / hot water mode, since the refrigerant flows through the water tank heat exchanger 400 and then through the indoor heat exchanger 300, the operating parameters of the indoor heat exchanger 300 under cooling conditions and the operating parameters of the water tank heat exchanger 400 under hot water conditions will affect each other. That is, if the initial frequency of the compressor is calculated based solely on the operating parameters of the indoor heat exchanger 300 and the current indoor temperature, it cannot be guaranteed that the refrigerant reaching the indoor heat exchanger 300 after flowing through the water tank heat exchanger 400 will still be able to maintain cooling operation. Therefore, when calculating the first and second initial frequencies, it is necessary to consider the influence of indoor temperature under cooling conditions and the influence of outlet water temperature under hot water conditions.

[0055] In some embodiments, the determination of the first initial frequency may include: the controller 10 determining the first initial frequency based on the rated cooling frequency and a first set of temperature correction coefficients; the first set of temperature correction coefficients includes one or more of the following: outdoor temperature correction coefficient, outlet water temperature difference correction coefficient, and inlet water temperature correction coefficient. It should be noted that when the air conditioner 1 operates in cooling-to-hot-water mode, the cooling demand of the air conditioner 1 is affected by the outdoor temperature, the outlet water temperature difference under hot water conditions, and the inlet water temperature. Therefore, when calculating the first initial frequency under cooling conditions, the controller 10 needs to consider the influence of the outdoor temperature, the outlet water temperature difference under hot water conditions, and the inlet water temperature. That is, when calculating the first initial frequency, in addition to the rated cooling frequency, a first set of temperature correction coefficients, including one or more of the following: outdoor temperature correction coefficient, outlet water temperature difference correction coefficient, and inlet water temperature correction coefficient, needs to be added.

[0056] When the first set of temperature correction coefficients includes the outdoor temperature correction coefficient, the outlet water temperature difference correction coefficient, and the inlet water temperature correction coefficient, the calculation formula for the first initial frequency Fre_aim is: Fre_aim = (Kao * CAPC_rate * K_Tr * K_△TSC * K_TW + Kbo) / 100. Wherein, CAPC_rate is the nominal rated cooling frequency of air conditioner 1, in W; K_Tr is the outdoor temperature correction coefficient; K_△TSC is the outlet water temperature difference correction coefficient; K_TW is the inlet water temperature correction coefficient; Kao is the coefficient of performance (COP); and Kbo is the cooling constant. The outdoor temperature correction coefficient is obtained by controller 10 based on the preset correspondence between the outdoor temperature and the outdoor temperature correction coefficient, as well as the real-time outdoor temperature. The outdoor temperature can be detected by a temperature sensor installed on the outer surface of the outdoor heat exchanger 200.

[0057] In some embodiments, the correspondence between outdoor temperature Tr and outdoor temperature correction factor K_Tr is shown in Table 1.

[0058] Table 1

[0059] Among them, the outlet water temperature difference correction coefficient is obtained by the controller 10 based on the correspondence between the preset outlet water temperature difference and the outlet water temperature difference correction coefficient, as well as the real-time outlet water temperature difference.

[0060] In some embodiments, the correspondence between the outlet water temperature difference ΔTWSC and the outlet water temperature difference correction coefficient K_ΔTSC is shown in Table 2.

[0061] Table 2

[0062] Where △TWSC=TWS-TW_out, TW_out is the real-time outlet water temperature, TWS is the target outlet water temperature, and T_OFFSETC is the corresponding saturation temperature under the set operating pressure. The inlet water temperature correction coefficient is obtained by the controller 10 based on the preset correspondence between the inlet water temperature and the inlet water temperature correction coefficient, as well as the real-time inlet water temperature.

[0063] In some embodiments, the correspondence between the inlet water temperature TW_in and the inlet water temperature correction coefficient K_TW of the water tank heat exchanger 400 is shown in Table 3.

[0064] Table 3

[0065] It should be noted that by correcting the rated cooling frequency according to the first set of temperature correction coefficients, a first initial frequency that matches the cooling demand and the heat exchange demand of domestic water can be obtained, so that the air conditioner 1 can take into account the influence of outdoor temperature, outlet water temperature and inlet water temperature on the heat exchange demand in the initial working stage of cooling mode, so as to simultaneously meet the cooling demand and the hot water demand.

[0066] In some embodiments, the determination of the second initial frequency may include: the controller 10 determining the second initial frequency based on a reference initial frequency and a second set of temperature correction coefficients; the second set of temperature correction coefficients includes one or more of an outdoor temperature difference correction coefficient and a water tank temperature difference correction coefficient. It should be noted that, since the air conditioner 1 operates in cooling-to-hot-water mode, the hot water demand of the air conditioner 1 is affected by the difference between the outdoor temperature and the water tank temperature. Therefore, when calculating the second initial frequency under hot water conditions, the controller 10 needs to consider the influence of the outdoor temperature and the water tank temperature difference. That is, when calculating the second initial frequency, in addition to the reference initial frequency under hot water conditions, the controller 10 also needs to add a second set of temperature correction coefficients, including an outdoor temperature difference correction coefficient and / or a water tank temperature difference correction coefficient. The outdoor temperature difference refers to the difference between the real-time outdoor temperature and the reference outdoor temperature; the water tank temperature difference refers to the difference between the real-time water tank temperature and the target water tank temperature, and / or the difference between the real-time water tank temperature and the reference water tank temperature.

[0067] Therefore, in some embodiments, when the second set of temperature correction coefficients includes the outdoor temperature difference correction coefficient and the water tank temperature difference correction coefficient, the calculation formula for the second initial frequency F_D_start can be F_D_start=F_D_base*K_Tr+K_Tk+K_TkS, where F_D_base is the reference initial frequency, usually 50Hz; K_Tr is the correction coefficient obtained based on the difference between the real-time outdoor temperature and the reference outdoor temperature; K_Tk is the correction coefficient obtained based on the difference between the real-time water tank temperature and the reference water tank temperature; and K_TkS is the correction coefficient obtained based on the difference between the real-time water tank temperature and the target water tank temperature. K_Tr is obtained by the controller 10 based on the preset correspondence between the outdoor temperature difference ΔTr and the outdoor temperature difference correction coefficient K_Tr, and the real-time outdoor temperature difference. The real-time outdoor temperature difference is the difference between the real-time outdoor temperature Tr and the reference outdoor temperature Tr_base, where Tr_base is usually 20℃.

[0068] In some embodiments, the correspondence between the outdoor temperature difference ΔTr and the outdoor temperature difference correction coefficient K_Tr is shown in Table 4.

[0069] Table 4

[0070] Wherein, K_Tk is obtained by the controller 10 based on the correspondence between the preset water tank temperature difference ΔTk and the water tank temperature difference correction coefficient K_Tk, as well as the real-time water tank temperature difference. The real-time water tank temperature difference is the difference between the real-time water tank temperature Tk and the reference water tank temperature Tk_base.

[0071] In some embodiments, the correspondence between the water tank temperature difference ΔTk and the water tank temperature difference correction coefficient K_Tk is shown in Table 5.

[0072] Table 5

[0073] Wherein, K_TkS is obtained by the controller 10 based on the correspondence between the preset water tank temperature difference ΔTkS and the water tank temperature difference correction coefficient K_TkS, as well as the real-time water tank temperature difference. The real-time water tank temperature difference is the difference between the target water tank temperature TkS and the real-time water tank temperature.

[0074] In some embodiments, the correspondence between the water tank temperature difference ΔTkS and the water tank temperature difference correction coefficient K_TkS is shown in Table 6.

[0075] Table 6

[0076] It should be noted that by correcting the reference initial frequency according to the second set of temperature correction coefficients, a second initial frequency matching the water output requirements can be obtained. This allows the air conditioner 1 to consider the impact of outdoor temperature and water tank temperature on hot water demand during the initial operation phase of hot water production mode, making the second initial frequency more closely aligned with the current heat exchange conditions of the air conditioner 1. The method for determining the target initial frequency can refer to the method for determining the target frequency described above. For example, after obtaining the first and second initial frequencies, the controller 10 uses the maximum value of the first and second initial frequencies as the target initial frequency, thereby ensuring that the compressor 100's operating frequency can simultaneously meet the requirements of both the initial operation phase of cooling and the initial operation phase of hot water production, improving the user experience.

[0077] In some embodiments, after the controller 10 determines the target initial frequency, the controller 10 further performs the following steps: Step S1023, when the compressor 100 operates at the target initial frequency for a preset duration, the compressor 100 enters the normal operation phase. The controller 10 determines a first operating frequency corresponding to the cooling conditions in the current frequency adjustment cycle, and a second operating frequency corresponding to the hot water production conditions in the current frequency adjustment cycle. Step S1024, the controller 10 determines the target operating frequency for the current frequency adjustment cycle based on the first and second operating frequencies, and controls the compressor 100 to operate at the target operating frequency in the current frequency adjustment cycle. It should be noted that, since the air conditioner 1 needs to perform both cooling and hot water production simultaneously when operating in cooling and hot water production mode, the frequency adjustment cycle of the controller 10 when adjusting the frequency according to the cooling conditions must be equal to the frequency adjustment cycle when adjusting the frequency according to the hot water production conditions, thereby ensuring the reliable operation of the air conditioner 1.

[0078] After the air conditioner 1 operates at the target initial frequency for a period of time, the controller 10 periodically adjusts the operating frequency of the compressor 100. This allows the air conditioner 1 to respond promptly to the real-time frequency changes under cooling and hot water conditions, enabling the compressor 100's frequency to dynamically change and adapt to these conditions in real time. It should be noted that the compressor 100 is in normal operating condition when the target initial frequency has been determined and the operating time at that frequency has reached a preset duration. The moment the compressor 100 begins to enter normal operating condition can be either when the operating time at the target initial frequency reaches the preset duration or later.

[0079] It should be noted that by determining the compressor 100 frequency during the initial and normal operating phases of the cooling and hot water mode, it can be ensured that the compressor 100's operating frequency can consistently meet the cooling and hot water needs throughout the entire cooling and hot water mode operation, whether in the initial or normal operating phase, thus improving the user experience.

[0080] The method for determining the target operating frequency of the current frequency adjustment cycle can refer to the method for determining the target frequency described above. For example, after obtaining the first operating frequency and the second operating frequency of the current frequency adjustment cycle, the maximum value of the first and second operating frequencies is taken as the target initial frequency. This ensures that the operating frequency of the compressor 100 can simultaneously meet the needs of the initial operating stage of cooling and the initial operating stage of hot water production in the current frequency adjustment cycle, thereby improving the user experience.

[0081] In some embodiments, the controller 10 determines the first operating frequency by: obtaining a first frequency adjustment value within the current frequency adjustment cycle, and then adjusting the current frequency of the compressor according to the first frequency adjustment value to obtain the first operating frequency of the compressor. Wherein, in order for the air conditioner 1 to continuously meet both cooling and hot water production conditions simultaneously, the first frequency adjustment value may be obtained based on operating parameters that enable the air conditioner 1 to meet both cooling and hot water production conditions, including outlet water temperature and / or indoor temperature.

[0082] In some embodiments, when the air conditioner 1 is operating in cooling and hot water mode, if the operating frequency of the compressor 100 is insufficient to support the cooling and hot water conditions, the indoor temperature will not be able to drop to the target temperature, and the outlet water temperature of the water tank heat exchanger 400 will not be able to rise to the target outlet water temperature. That is, the difference between the real-time indoor temperature and the target indoor temperature, and the difference between the real-time outlet water temperature and the target outlet water temperature will increase simultaneously. Therefore, the controller 10 can characterize the cooling effect based on the difference between the real-time outlet water temperature of the water tank heat exchanger 400 and the target outlet water temperature. When the difference between the outlet water temperature of the water tank heat exchanger 400 and the target outlet water temperature is large, it indicates that the cooling effect is poor. When the difference between the outlet water temperature of the water tank heat exchanger 400 and the target outlet water temperature is small, it indicates that the cooling effect is good.

[0083] Therefore, in some embodiments, as shown in FIG3, the air conditioner 1 may further include a first temperature sensor 13, which is connected to the controller 10. The first temperature sensor 13 is used to detect the real-time outlet water temperature of the water tank heat exchanger 400. The controller 10 can be used to obtain the real-time outlet water temperature detected by the first temperature sensor 13 in the current frequency adjustment cycle when the compressor 100 is in the normal operation stage; determine the outlet water temperature difference between the target outlet water temperature and the real-time outlet water temperature; obtain a first frequency adjustment value based on the outlet water temperature difference; and adjust the current operating frequency of the compressor 100 according to the first frequency adjustment value to obtain the first operating frequency corresponding to the current frequency adjustment cycle.

[0084] In some embodiments, the location of the first temperature sensor 13 can be set by those skilled in the art according to actual conditions. For example, the first temperature sensor 13 can be set at the outlet of the water tank heat exchanger 400, as shown in FIG7, to detect the temperature of the water flowing from the water tank heat exchanger 400 to the water tank 710 in real time. The target outlet water temperature is the ideal outlet water temperature value set by the user. The user can input the target outlet water temperature value through the control panel of the air conditioner 1, and then the control panel sends the target outlet water temperature value to the controller 10, so that the controller 10 adjusts the operating parameters of the air conditioner 1, thereby stabilizing the real-time outlet water temperature of the water tank heat exchanger 400 at the target outlet water temperature. The formula for calculating the outlet water temperature difference is: Outlet water temperature difference = Real-time outlet water temperature - Target outlet water temperature, indicating how much the real-time outlet water temperature needs to rise or fall to reach the target outlet water temperature.

[0085] It should be noted that, because within each frequency adjustment cycle, when the frequency of compressor 100 cannot meet the conditions for cooling and hot water production, the temperature difference between the outlet water temperature of the water tank heat exchanger 400 and the target outlet water temperature will exceed a certain value. Therefore, if the temperature difference between the real-time outlet water temperature and the target outlet water temperature exceeds a certain value, controller 10 needs to adjust the frequency of compressor 100 to reduce the difference between the outlet water temperature of water tank heat exchanger 400 and the target outlet water temperature. Conversely, when the frequency of compressor 100 can meet the conditions for cooling and hot water production, the temperature difference between the outlet water temperature of water tank heat exchanger 400 and the target outlet water temperature will be less than a certain value. In this case, controller 10 may not need to change the frequency of compressor 100 or may only adjust the frequency of compressor 100 by a small amount. Therefore, there can be a positive correlation between the outlet water temperature difference and the first frequency adjustment value; that is, the larger the outlet water temperature difference, the larger the first frequency adjustment value.

[0086] Therefore, in some embodiments, technicians can pre-set the correspondence between the outlet water temperature difference and the first frequency adjustment value, so that when the controller 10 determines the first frequency adjustment value, it can directly obtain the first frequency adjustment value based on the correspondence and the outlet water temperature difference in the current frequency adjustment cycle.

[0087] In some embodiments, since the operating frequency of the compressor 100 has a corresponding operating frequency range, the controller 10 cannot exceed the operating frequency range when adjusting the operating frequency of the compressor 100. Therefore, the first frequency adjustment value of two consecutive frequency adjustment cycles cannot be too high. So the controller 10 can also determine the first frequency adjustment value based on the change amplitude between the outlet water temperature difference of two adjacent frequency adjustment cycles, thereby ensuring that after adjusting the frequency of the compressor 100 according to the first frequency adjustment value, the frequency of the compressor 100 will always be within the operating frequency range of the compressor.

[0088] In some embodiments, the controller 10 can be used to obtain the real-time outlet water temperature detected by the first temperature sensor 13 in the current frequency adjustment cycle when the compressor 100 is in normal operation; determine the outlet water temperature difference between the target outlet water temperature and the real-time outlet water temperature; obtain a first frequency adjustment value based on the change amplitude of the outlet water temperature difference corresponding to the current frequency adjustment cycle compared to the outlet water temperature difference of the previous frequency adjustment cycle; and adjust the current operating frequency of the compressor 100 according to the first frequency adjustment value to obtain the first operating frequency corresponding to the current frequency adjustment cycle.

[0089] In some embodiments, when obtaining the first frequency adjustment value based on the change amplitude of the outlet water temperature difference, it may be based on the correspondence between the change amplitude of the outlet water temperature difference and the frequency adjustment value.

[0090] In some embodiments, the correspondence between the change amplitude of the outlet water temperature difference and the frequency adjustment value is shown in Table 7.

[0091] Table 7

[0092] Wherein, the outlet water temperature difference ΔTW = real-time outlet water temperature TW_out - target outlet water temperature TWS; the change amplitude ΔTW(n) = [TW_out(n) - TWS(n)] - [TW_out(n-1) - TWS(n-1)], that is, the difference between ΔTW in the current frequency adjustment cycle and ΔTW in the previous frequency adjustment cycle; ΔF is the first frequency adjustment value. Wherein, when calculating the first frequency adjustment cycle, ΔTW(1) = 0.

[0093] In some embodiments, when the controller 10 adjusts the frequency of the compressor 100, it needs to do so based on the current outlet water temperature difference. When the current outlet water temperature difference is large and the change amplitude of the outlet water temperature difference in two adjacent frequency adjustment cycles is also large, a certain value needs to be added to the frequency adjustment value corresponding to the change amplitude. Therefore, the correspondence between the current outlet water temperature difference, the change amplitude of the outlet water temperature difference, and the frequency adjustment value can be set to better match the current outlet water conditions.

[0094] In some embodiments, the correspondence between the current outlet water temperature difference, the amplitude of the change in outlet water temperature difference, and the frequency adjustment value is shown in Table 8.

[0095] Table 8

[0096] Wherein, the outlet water temperature difference ΔTW = real-time outlet water temperature TW_out - target outlet water temperature TWS; ΔTW(n) = [TW_out(n) - TWS(n)] - [TW_out(n-1) - TWS(n-1)], which is the difference between ΔTW in the current frequency adjustment cycle and ΔTW in the previous frequency adjustment cycle. When calculating the first frequency adjustment cycle, ΔTW(1) = 0; ΔF is the first frequency adjustment value.

[0097] In some embodiments, the duration of each frequency adjustment cycle can be determined based on the outlet water temperature difference. That is, during actual calculation, the duration of the current frequency adjustment cycle is calculated based on the outlet water temperature difference in the previous frequency adjustment cycle. Then, within the current frequency adjustment cycle, the frequency of the compressor 100 is adjusted according to the outlet water temperature difference. This allows for dynamic adaptation of the compressor 100's operating frequency by reducing the duration of the frequency adjustment cycle when the outlet water temperature difference is large and increasing the duration when the outlet water temperature difference is small.

[0098] In some embodiments, the relationship between the outlet water temperature difference ΔTW and the frequency adjustment period T can be shown in Table 9:

[0099] Table 9

[0100] Wherein, the outlet water temperature difference ΔTW = real-time outlet water temperature TW_out - target outlet water temperature TWS. It should be noted that adjusting the frequency of compressor 100 based on the change in the difference between the real-time outlet water temperature and the target outlet water temperature can ensure that the frequency of compressor 100 in cooling mode can also meet the target outlet water temperature requirement, guaranteeing the user's water needs and improving the user experience.

[0101] In some embodiments, the controller 10 may determine the second operating frequency by: obtaining a second frequency adjustment value within the current frequency adjustment cycle, and then adjusting the current frequency of the compressor according to the second frequency adjustment value to obtain the second operating frequency of the compressor. Wherein, in order to ensure that the air conditioner 1 can consistently meet the hot water production conditions, the second frequency adjustment value may be obtained based on operating parameters that enable the air conditioner 1 to meet the hot water production conditions, including the water tank temperature and / or the outlet water temperature.

[0102] When the air conditioner 1 is operating in hot water mode, if the operating frequency of the compressor 100 cannot meet the hot water production conditions, the real-time outlet water temperature of the water tank heat exchanger 400 will not be maintained at the target outlet water temperature. One factor affecting the inability to maintain the real-time outlet water temperature at the target outlet water temperature is the low temperature in the water tank. This causes the compressor 100 to supply more refrigerant to the water tank heat exchanger 400 so that the water tank heat exchanger 400 has enough energy to achieve heat exchange and thus heat the domestic water. Therefore, the temperature in the water tank is an important factor affecting the hot water production effect of the air conditioner 1.

[0103] Therefore, in some embodiments, the air conditioner 1 may further include a water tank 710 and a second temperature sensor 14. The water tank 710 is connected to a water tank heat exchanger 400, and the second temperature sensor 14 is connected to a controller 10. The second temperature sensor 14 is used to detect the real-time water tank temperature of the water tank 710. The controller 10 can be used to obtain the real-time water tank temperature detected by the second temperature sensor 14 in the current frequency adjustment cycle when the compressor 100 is in normal operation, determine the water tank temperature difference between the target water tank temperature and the real-time water tank temperature; obtain a second frequency adjustment value based on the water tank temperature difference; and adjust the current operating frequency of the compressor 100 based on the second frequency adjustment value to obtain the second operating frequency corresponding to the current frequency adjustment cycle.

[0104] In some embodiments, the second temperature sensor 14 can be installed inside the water tank, as shown in Figure 5, or it can be installed in the connecting pipe between the water tank heat exchanger and the water tank.

[0105] In some embodiments, the second temperature sensor 14 and the first temperature sensor 13 may be the same temperature sensor or different temperature sensors. The target water tank temperature may be an ideal water tank temperature value set by the user. The user can input the target water tank temperature value through the control panel of the air conditioner 1, and the control panel will then send the target water tank temperature value to the controller 10, so that the controller 10 can adjust the operating parameters of the air conditioner 1 to stabilize the real-time temperature in the water tank 710 at the target water tank temperature value.

[0106] The formula for calculating the water tank temperature difference is: Water tank temperature difference = Real-time water tank temperature - Target water tank temperature, indicating how much the real-time water tank temperature needs to rise or fall to reach the target water tank temperature. It should be noted that, because within each frequency adjustment cycle, when the compressor 100's frequency cannot meet the hot water production requirements, the temperature difference between water tank 710 and the target water tank temperature will be greater than a certain value. Therefore, if the temperature difference between the real-time and target water tank temperatures is greater than a certain value, the controller 10 needs to adjust the compressor 100's frequency to reduce the difference between the real-time and target water tank temperatures. Conversely, when the compressor 100's frequency meets the hot water production requirements, the temperature difference between the real-time and target water tank temperatures will be less than a certain value. In this case, the controller 10 can either not change the compressor 100's frequency or only adjust the compressor 100's frequency by a small amount. Therefore, there can be a positive correlation between the water tank temperature difference and the second frequency adjustment value, that is, the larger the water tank temperature difference, the larger the second frequency adjustment value.

[0107] Therefore, in some embodiments, technicians can pre-set the correspondence between the water tank temperature difference and the second frequency adjustment value, so that when the controller 10 determines the second frequency adjustment value, it can directly obtain the second frequency adjustment value based on the correspondence and the water tank temperature difference in the current frequency adjustment cycle.

[0108] In some embodiments, since the operating frequency of the compressor 100 has a corresponding operating frequency range, the controller 10 cannot exceed the operating frequency range when adjusting the operating frequency of the compressor 100. Therefore, the second frequency adjustment value cannot be too high for two consecutive cycles. Thus, the controller 10 can also determine the second frequency adjustment value based on the change amplitude between the water tank temperature difference between two adjacent frequency adjustment cycles, thereby ensuring that after adjusting the frequency of the compressor 100 according to the second frequency adjustment value, the frequency of the compressor 100 will always be within the operating frequency range of the compressor.

[0109] In some embodiments, the controller 10 can be used to acquire the real-time water tank temperature detected by the second temperature sensor 14 in the current frequency adjustment cycle when the compressor 100 is in normal operation, determine the water tank temperature difference between the target water tank temperature and the real-time water tank temperature; obtain a second frequency adjustment value based on the change amplitude of the water tank temperature difference corresponding to the current frequency adjustment cycle compared to the water tank temperature difference in the previous frequency adjustment cycle; and adjust the current operating frequency of the compressor 100 according to the second frequency adjustment value to obtain the second operating frequency corresponding to the current frequency adjustment cycle. Wherein, when the controller 10 obtains the second frequency adjustment value based on the change amplitude of the water tank temperature difference, it may be based on the correspondence between the change amplitude of the water tank temperature difference and the frequency adjustment value. This correspondence can be set by those skilled in the art according to actual conditions, and this embodiment does not impose any limitations.

[0110] In some embodiments, the correspondence between the change amplitude of the water tank temperature difference and the frequency adjustment value is shown in Figure 6. Wherein, ΔTDW = TKS - TKL, the compensation value is 0 by default, ΔTDW is the change amplitude of the water tank temperature difference, TKS is the target water tank temperature, and TKL is the water tank temperature.

[0111] In Figure 6, intervals 1 to 6 are divided in ascending order of ΔTDW value. The ΔTDW value is smallest in interval 1 and largest in interval 6. After ΔTDW rises from interval 1 to interval 2, the second frequency adjustment value is the first value. After ΔTDW falls from interval 2 to interval 1, the second frequency adjustment value is the second value. The first and second values ​​are different. The same applies when ΔTDW switches between other intervals.

[0112] In some embodiments, in interval 6: if the frequency rises from interval 5 to interval 6 and remains in interval 6 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +10Hz; if the frequency remains in interval 6 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +8Hz.

[0113] In some embodiments, in interval 5: if the frequency rises from interval 4 to interval 5 and remains in interval 5 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +9Hz; if the frequency remains in interval 5 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +7Hz; if the frequency falls from interval 6 to interval 5 and remains in interval 5 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +6Hz.

[0114] In some embodiments, in interval 4: if the frequency rises from interval 3 to interval 4 and remains in interval 4 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +8Hz; if the frequency remains in interval 4 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +6Hz; if the frequency falls from interval 5 to interval 4 and remains in interval 4 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +5Hz.

[0115] In some embodiments, in interval 3: if the frequency rises from interval 2 to interval 3 and remains in interval 3 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +7Hz; if the frequency remains in interval 3 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +5Hz; if the frequency falls from interval 4 to interval 3 and remains in interval 3 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +4Hz.

[0116] In some embodiments, in interval 2: if the frequency rises from interval 1 to interval 2 and remains in interval 2 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +6Hz; if the frequency remains in interval 2 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +4Hz; if the frequency falls from interval 3 to interval 2 and remains in interval 2 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +3Hz.

[0117] In some embodiments, in interval 1: if the frequency drops from interval 2 to interval 1 and remains in interval 1 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +2Hz; if the frequency remains in interval 1 for one consecutive frequency adjustment cycle, the second frequency adjustment value is +1Hz.

[0118] In some embodiments, due to the error in the second temperature sensor 14 when detecting the real-time water tank temperature of the water tank 710, a corresponding compensation value needs to be added when setting the target water tank temperature, i.e., TKS + compensation value. However, the water tank 710 has a corresponding maximum temperature limit, so the value after adding the corresponding compensation value needs to be less than the maximum temperature of the water tank 710, i.e., the change amplitude of the water tank temperature difference ΔTDW = min[TKS + compensation value, TKSTOP] - TKL, where TKSTOP is the maximum temperature of the water tank 710. It should be noted that adjusting the frequency of the compressor 100 according to the change value of the difference between the real-time water tank temperature and the target water tank temperature can ensure that the compressor 100 can provide a sufficient frequency to heat the water in the water tank 710, so that the temperature in the water tank 710 is always maintained at the target water tank temperature, so that the water tank heat exchanger 400 reduces the energy consumed when heating the water flowing out of the water tank 710, effectively realizing the hot water production mode.

[0119] In some embodiments, the controller 10 can also be used to exit the cooling / hot water mode when the air conditioner 1 meets the termination conditions. The termination conditions may include the air conditioner 1 reaching a preset operating threshold, receiving a mode switching command (indicating a switch from cooling / hot water mode to another mode), or the compressor 100 failing to operate normally at one or more target frequencies. It should be noted that when the controller 10 adjusts the refrigerant flow to the water tank heat exchanger 400 and the indoor heat exchanger 300, in addition to adjusting the compressor's operating frequency, it can also adjust the refrigerant flow by adjusting the opening degree of each control valve in the control valve group. However, since control valves with adjustable openings are costly, and adjusting all control valves in the control valve group would increase the controller 10's control load, only some control valves in the control valve group can be configured as adjustable-opening control valves. This reduces component costs while still achieving refrigerant flow adjustment to the water tank heat exchanger 400 and the indoor heat exchanger 300. Adjustable-opening control valves include, for example, electronic expansion valves.

[0120] In some embodiments, the target control valve unit in the control valve assembly may include the electronic expansion valve whose opening can be adjusted by the controller 10, and the target control valve unit may be one or more of the first control valve unit 5, the second control valve unit 7, and the third control valve unit 6. For example, one or more of the first electronic expansion valve 61, the second electronic expansion valve 62, the third electronic expansion valve 63, and the fourth electronic expansion valve 64 in FIG2 may be electronic expansion valves whose opening can be adjusted by the controller 10.

[0121] If the control valve in the first control valve unit 5 includes an electronic expansion valve whose opening is adjusted by the controller 10, the controller 10 can adjust the refrigerant flowing from the outdoor heat exchanger 200 and / or the indoor heat exchanger 300 to the compressor 100 under cooling and hot water conditions by adjusting the opening of the electronic expansion valve in the first control valve unit 5. Since the capacity of the refrigerant circulating in the air conditioner 1 is constant, the refrigerant flow rate output from the outlet 120 of the compressor 100 can be further adjusted when the refrigerant input through the air inlet 110 of the compressor 100 decreases or increases.

[0122] If the control valve of the second control valve unit 7 includes an electronic expansion valve whose opening is adjusted by the controller 10, the controller 10 can adjust the refrigerant flow from the compressor 100 to the water tank heat exchanger 400 under cooling and hot water conditions by adjusting the opening of the electronic expansion valve of the second control valve unit 7. Since the capacity of the refrigerant circulating in the air conditioner 1 is constant, if the refrigerant input through the air inlet 110 of the compressor 100 decreases or increases, the refrigerant flow output from the air outlet 120 of the compressor 100 in the next refrigerant cycle can be further adjusted.

[0123] If the control valve of the third control valve unit 6 includes an electronic expansion valve whose opening is adjusted by the controller 10, the controller 10 can adjust the refrigerant flowing from the water tank heat exchanger 400 to the outdoor heat exchanger 200 and / or the indoor heat exchanger 300 under cooling and hot water conditions by adjusting the opening of the electronic expansion valve. Since the capacity of the refrigerant circulating in the air conditioner 1 is constant, the refrigerant flow rate output from the air outlet 120 of the compressor 100 can be further adjusted when the refrigerant input through the air inlet 110 of the compressor 100 decreases or increases.

[0124] In some embodiments, when the controller 10 needs to control the opening degree of multiple electronic expansion valves in the control valve group, the controller 10 can control different electronic expansion valves in the control valve group according to different opening degree control strategies. For example, the control valve group includes electronic expansion valve A, electronic expansion valve B, and electronic expansion valve C. When controlling the opening degree of electronic expansion valve A, electronic expansion valve B, and electronic expansion valve C, the controller 10 can control the opening degree of electronic expansion valve A according to a first opening degree control strategy, control the opening degree of electronic expansion valve B according to a second opening degree control strategy, and control the opening degree of electronic expansion valve C according to a third opening degree control strategy to achieve targeted opening degree control, thereby improving the operational reliability of the compressor. The first opening degree control strategy, the second opening degree control strategy, and the third opening degree control strategy are different.

[0125] In some embodiments, the opening control strategy of the controller 10 may include, after the target electronic expansion valve is powered on, first controlling the target electronic expansion valve to conduct according to a first opening value, and after the conduction time reaches a preset time, conducting according to a second opening value, wherein the first opening value and the second opening value are different, and the target electronic expansion valve is one or more of a plurality of electronic expansion valves in the control valve group; or, the opening control strategy may also include, after the target electronic expansion valve is powered on, controlling the target electronic expansion valve to maintain conduction at a third opening value; or, the opening control strategy may also include, after the target electronic expansion valve is powered on, controlling the target electronic expansion valve to adjust its opening in real time according to the real-time operating efficiency of the compressor.

[0126] In some embodiments, to ensure that the air conditioner 1 can continuously meet the hot water production requirements, the opening degree of the target electronic expansion valve connected between the water tank heat exchanger 400, the outdoor heat exchanger 200, and the indoor heat exchanger 300 can be adjusted according to the real-time operating efficiency of the compressor after the refrigerant flows out of the water tank heat exchanger 400. For example, for the second electronic expansion valve 62, the controller 10 can adjust the opening degree according to the real-time operating efficiency of the compressor. Since the second electronic expansion valve 62 is close to the refrigerant output end of the water tank heat exchanger 400, adjusting the opening degree of the second electronic expansion valve 62 according to the real-time operating efficiency of the compressor can more quickly limit the flow of refrigerant to the outdoor heat exchanger 200 and / or the indoor heat exchanger 300.

[0127] In some embodiments, in order to reduce the control load of the controller 10, only the second electronic expansion valve 62 can be set as the target electronic expansion valve whose opening is adjusted according to the real-time operating efficiency of the compressor. Other electronic expansion valves can be turned on according to a fixed opening value after power-on. Other electronic expansion valves include the first electronic expansion valve 61, the third electronic expansion valve 63, and the fourth electronic expansion valve 64.

[0128] In some embodiments, since the exhaust superheat of the compressor 100 is used to characterize the real-time operating efficiency of the compressor 100, if the exhaust superheat of the compressor 100 is too high, it means that the real-time operating efficiency of the compressor 100 is low. Therefore, when the controller 10 adjusts the opening of the target electronic expansion valve according to the real-time operating efficiency of the compressor 100, it can adjust the opening based on the real-time exhaust superheat of the compressor 100. The specific adjustment value of the opening can be determined based on the real-time exhaust superheat of the compressor 100, thereby ensuring that the operating efficiency of the compressor 100 is maintained at the target level. That is, in some embodiments, as shown in FIG3, the air conditioner 1 also includes a third temperature sensor 15 and a pressure sensor 16. The controller 10 is connected to the third temperature sensor 15 and the pressure sensor, respectively. The third temperature sensor 15 is used to detect the exhaust temperature of the compressor 100. The pressure sensor 16 is used to detect the exhaust pressure of the compressor 100. The controller 10 can also be used to perform the following steps: Step S103, when the air conditioner 1 is in cooling / hot water mode, obtain the exhaust temperature detected by the third temperature sensor 15 and the exhaust pressure detected by the pressure sensor 16; Step S104, obtain the saturation temperature corresponding to the exhaust pressure, and determine the exhaust superheat based on the exhaust temperature and the saturation temperature; Step S105, adjust the opening of the target electronic expansion valve based on the exhaust superheat. It should be noted that saturation temperature refers to the temperature at which a substance reaches dynamic equilibrium between liquid (or gaseous) and vapor states under a specific pressure. That is, at the saturation temperature, the evaporation rate of the liquid and the condensation rate of the vapor are equal, and no phase change occurs. For the same substance, the saturation temperature is only associated with a specific saturation pressure. That is, for a given pressure, there is only one specific temperature at which the substance is saturated. Therefore, when calculating the saturation temperature, it is necessary to measure the current exhaust pressure and then obtain the corresponding saturation temperature by consulting a thermodynamic property table or chart.

[0129] Discharge superheat refers to the difference between the discharge temperature (gas refrigerant temperature) of compressor 100 and its saturation temperature at the current discharge pressure. Discharge superheat reflects the degree to which the discharge temperature of compressor 100 exceeds its corresponding saturation temperature under actual pressure conditions. The calculation process for discharge superheat may include: 1. Obtaining the discharge temperature; 2. Obtaining the discharge pressure and finding the saturation temperature of the refrigerant at that discharge pressure by querying a preset correspondence between discharge pressure and saturation temperature. Different refrigerants have different correspondences; 3. Calculating the discharge superheat using the following formula: Discharge Superheat = Discharge Temperature - Saturation Temperature.

[0130] In some embodiments, the third temperature sensor 15 can be installed at the discharge pipe of the compressor 100, as shown in FIG. 7, or at the inlet of the condenser, to obtain the discharge temperature of the compressor 100. In some embodiments, the pressure sensor 16 can be installed at the discharge pipe of the compressor 100, as shown in FIG. 5, or at the inlet of the condenser, to obtain the discharge pressure of the compressor 100. It should be noted that when adjusting the opening of the target electronic expansion valve according to the discharge superheat, if the discharge superheat is too large, it indicates that the operating efficiency of the compressor is too low. At this time, it is necessary to increase the opening of the electronic expansion valve to improve the operating efficiency of the compressor 100 to a normal level. Therefore, the discharge superheat and the opening of the electronic expansion valve are positively correlated, that is, the greater the discharge superheat, the greater the opening of the electronic expansion valve. Technicians can preset the correspondence between the discharge superheat and the opening of the electronic expansion valve, so that when the controller 10 determines the discharge superheat, it can directly obtain the target opening of the electronic expansion valve in the current opening adjustment cycle according to the correspondence and the real-time discharge superheat in the current opening adjustment cycle.

[0131] In other embodiments, the controller 10 may adjust the opening of the electronic expansion valve according to the exhaust superheat, and may include one of the following adjustment methods:

[0132] In one adjustment method, the controller 10 adjusts the opening of the electronic expansion valve based on the difference between the exhaust superheat in two adjacent opening adjustment cycles. Since the difference between the exhaust superheat in two adjacent opening adjustment cycles reflects the trend of exhaust superheat change, adjusting the opening based on this trend can mitigate the change in exhaust superheat and ensure the normal operation of the compressor 100. For example, if the difference between the exhaust superheat in the current opening adjustment cycle and the exhaust superheat in the previous opening adjustment cycle is positive, it indicates that the exhaust superheat of the compressor 100 is gradually increasing, so the opening of the electronic expansion valve needs to be increased to reduce the exhaust superheat. Conversely, if the difference between the exhaust superheat in the current opening adjustment cycle and the exhaust superheat in the previous opening adjustment cycle is negative, it indicates that the exhaust superheat of the compressor 100 is gradually decreasing, so the opening of the electronic expansion valve needs to be decreased to increase the exhaust superheat.

[0133] In adjustment method two, controller 10 can adjust the opening of the electronic expansion valve according to the superheat difference of the current opening adjustment cycle. The superheat difference is the difference between the target exhaust superheat and the real-time exhaust superheat. That is, controller 10 can also be used for:

[0134] Based on the real-time exhaust temperature and real-time saturation temperature of the compressor 100 in the current opening adjustment cycle, the real-time exhaust superheat corresponding to the current opening adjustment cycle is determined. The superheat difference between the target exhaust superheat and the real-time exhaust superheat corresponding to the current opening adjustment cycle is determined, and the opening of the electronic expansion valve is adjusted according to the superheat difference corresponding to the current opening adjustment cycle.

[0135] It should be noted that the target exhaust superheat can be used to characterize the temperature of the gaseous refrigerant discharged by the compressor 100 when the air conditioner 1 can operate normally in cooling and hot water conditions. That is, in the process of controlling the opening of the electronic expansion valve according to the exhaust superheat, the real-time exhaust superheat should be compared with the target superheat. If the real-time exhaust superheat is lower than the target exhaust superheat, it means that the temperature of the gaseous refrigerant discharged by the compressor 100 is low, the refrigerant flow is too large, and the refrigerant cannot fully exchange heat with the compressor 100. In this case, the opening of the electronic expansion valve is reduced to decrease the refrigerant flow, thereby increasing the exhaust superheat of the compressor 100 and avoiding the problem of the compressor 100's exhaust superheat being too low. If the exhaust superheat is higher than the target exhaust superheat, it means that the temperature of the gaseous refrigerant discharged by the compressor 100 is high, the refrigerant flow is too small, and the refrigerant exchanges heat excessively with the compressor 100. In this case, the opening of the electronic expansion valve is increased to increase the refrigerant flow, thereby reducing the exhaust superheat of the compressor 100 and avoiding the problem of the compressor 100's exhaust superheat being too high.

[0136] In some embodiments, when obtaining the opening adjustment value based on the superheat difference, the opening adjustment value corresponding to the current opening adjustment cycle can be obtained based on the correspondence between the superheat difference and the opening adjustment value, as well as the superheat difference corresponding to the current opening adjustment cycle. Then, the opening of the electronic expansion valve can be adjusted based on the opening adjustment value corresponding to the current opening adjustment cycle.

[0137] In some embodiments, the target exhaust superheat can be fixed by those skilled in the art according to actual conditions. For example, the technician can preset the target exhaust superheat range to 15°C-20°C. When the real-time exhaust superheat is lower than the lower limit of the target superheat range, the opening of the electronic expansion valve needs to be reduced; while when the real-time exhaust superheat is higher than the upper limit of the target superheat range, the opening of the electronic expansion valve needs to be increased.

[0138] In other embodiments, the target exhaust superheat can be calculated in real time during each opening adjustment cycle. Since the air conditioner 1 operates in cooling / hot water mode, to ensure the normal operation of the compressor 100, the exhaust superheat is mainly affected by the operating frequency of the compressor 100, the cooling conditions of the air conditioner 1, and the hot water production conditions. Therefore, when designing the target exhaust superheat of the compressor 100, one or more of the compressor 100's current operating frequency, outdoor temperature, and outlet water temperature need to be considered. Thus, the target exhaust superheat corresponding to the current opening adjustment cycle can be determined based on the compressor 100's current operating frequency and a third set of temperature correction coefficients. The third set of temperature correction coefficients includes one or more of the outlet water temperature correction coefficient and the outdoor temperature correction coefficient. The outdoor temperature correction coefficient can be obtained based on a preset correspondence between the outdoor temperature and the outdoor temperature correction constant, as well as the real-time outdoor temperature.

[0139] In some embodiments, the correspondence between outdoor temperature Tr and outdoor temperature correction constant e2_C_DSH1 is shown in Table 10.

[0140] Table 10

[0141] Here, e2_C_DSH11, e2_C_DSH12, e2_C_DSH13, and e2_C_DSH14 represent different values. The outlet water temperature correction coefficient can be obtained based on the preset correspondence between the outlet water temperature and the outlet water temperature correction constant, as well as the real-time outlet water temperature.

[0142] In some embodiments, the correspondence between the outlet water temperature Tw_out and the outlet water temperature correction constant e2_B_DSH1 is shown in Table 11.

[0143] Table 11

[0144] Among them, e2_B_DSH11, e2_B_DSH12, e2_B_DSH13 and e2_B_DSH14 represent different values.

[0145] In some embodiments, when the third set of temperature correction coefficients includes an outlet water temperature correction coefficient and an outdoor temperature correction coefficient, the formula for calculating the target exhaust superheat DSHobjH can be: DSHobjH=(FreqDrv×e2_K_DSH1+e2_B_DSH1)*e2_C_DSH1. Where FreqDrv is the current frequency of compressor 100, e2_K_DSH1 is a correction coefficient related to the frequency of compressor 100, e2_B_DSH1 is the outlet water temperature correction constant, and e2_C_DSH1 is the outdoor temperature correction coefficient.

[0146] In the third adjustment method, the controller 10 can adjust the opening of the electronic expansion valve according to the difference between the superheat difference corresponding to two adjacent opening adjustment cycles. The superheat difference is the difference between the target exhaust superheat and the real-time exhaust superheat. That is, the controller 10 can also be used to: determine the real-time exhaust superheat corresponding to the current opening adjustment cycle according to the real-time exhaust temperature and saturation temperature of the compressor 100 in the current opening adjustment cycle, determine the superheat difference between the target exhaust superheat and the real-time exhaust superheat, and adjust the opening of the electronic expansion valve according to the superheat difference corresponding to the current opening adjustment cycle and the superheat difference corresponding to the previous opening adjustment cycle.

[0147] It should be noted that, since the opening of the electronic expansion valve has a corresponding opening adjustment range, the controller 10 cannot exceed the opening adjustment range when adjusting the opening of the electronic expansion valve. Therefore, the opening adjustment value cannot be too high for two consecutive opening adjustment cycles. Thus, the controller 10 can also determine the opening adjustment value based on the change amplitude between the superheat difference of two adjacent opening adjustment cycles, thereby ensuring that after adjusting the opening of the electronic expansion valve according to the opening adjustment value, the opening of the electronic expansion valve will always be within the opening adjustment range.

[0148] In some embodiments, when the controller 10 adjusts the opening of the electronic expansion valve based on the difference between the superheat difference between two adjacent cycles, it can first determine the target opening adjustment value based on the correspondence between the preset superheat difference and the opening adjustment value, as well as the real-time superheat difference, and then adjust the opening of the electronic expansion valve based on the target opening adjustment value.

[0149] In some embodiments, the correspondence between the preset superheat difference Q and the opening adjustment value ΔH is shown in Table 12, wherein the superheat difference Q = ΔSSH(n) - ΔSSH(n-1), and ΔSSH(n) is the difference between the exhaust superheat corresponding to the current opening adjustment cycle and the target exhaust superheat.

[0150] Table 12

[0151] In some embodiments, when adjusting the opening of the electronic expansion valve, if the superheat difference corresponding to the opening adjustment cycle is large, a certain value needs to be added to the current opening adjustment value to further reduce the exhaust superheat of the compressor 100. Therefore, a correspondence can be set between the superheat difference corresponding to two adjacent opening adjustment cycles, the superheat difference corresponding to the current opening adjustment cycle, and the opening adjustment value, so as to better fit the current working conditions of the compressor 100.

[0152] In some embodiments, the correspondence between the superheat difference between two adjacent opening adjustment cycles, the superheat difference between the current opening adjustment cycle, and the opening adjustment value is shown in Table 13.

[0153] Table 13

[0154] In some embodiments, the opening adjustment of the electronic expansion valve is subject to certain limitations due to the influence of the current opening degree and the current exhaust temperature. Specifically, when the target parameter of the air conditioner 1 is at a preset limit adjustment threshold, the opening degree of the electronic expansion valve is adjusted according to the preset limit adjustment rules. The target parameter includes the current opening degree of the electronic expansion valve and / or the current exhaust temperature. The preset limit adjustment rules include the minimum value of the opening adjustment value corresponding to each opening adjustment cycle, the minimum value of the target opening degree corresponding to each opening adjustment cycle, the reduction of the duration of the opening adjustment cycle, and the opening adjustment value corresponding to each opening adjustment cycle being one or more of the preset thresholds.

[0155] In some embodiments, the preset limit adjustment rules may include: when the current opening degree of the electronic expansion valve is less than or equal to 110 steps, the minimum value of the opening degree adjustment corresponding to each opening degree adjustment cycle is a first preset number of steps, that is, the number of steps to adjust the opening degree adjustment corresponding to each opening degree adjustment cycle to a smaller value is not allowed to exceed the first preset number of steps, the first preset number of steps being, for example, 2 steps; this restriction is lifted after the actual number of steps > 120 steps; and / or, when the current exhaust temperature Tcomp > 95°C, the minimum value of the target opening degree corresponding to each opening degree adjustment cycle is the current number of steps, that is, the number of steps of the electronic expansion valve is not allowed to be adjusted to a smaller value, and normal control is restored when Tcomp < 90°C; and / or, when the current exhaust temperature Tcomp > 97°C, the opening degree adjustment value corresponding to each opening degree adjustment cycle is a preset threshold, that is, the number of steps of the electronic expansion valve is increased by a second preset number of steps per cycle, the second preset number of steps being, for example, +15 steps, once the additional step control is entered, the duration of each subsequent opening degree adjustment cycle is shortened to 1 / 2 of the duration of the previous opening degree adjustment cycle, and normal control is restored when Tcomp < 92°C.

[0156] As shown in FIG7, an air conditioner 1 is provided according to an embodiment of the present disclosure. The air conditioner 1 may include a compressor 100 having an air inlet 110 and an air outlet 120. In some embodiments, as shown in FIG7, the air conditioner 1 may further include a gas-liquid separator 910, which may be connected before the air inlet 110.

[0157] In some embodiments, as shown in FIG7, the air conditioner 1 may include an outdoor heat exchanger 200 for exchanging heat with outdoor air. In some embodiments, as shown in FIG7, the air conditioner 1 may include an indoor heat exchanger 300 for exchanging heat with indoor air. For example, one end of the indoor heat exchanger 300 is connected to one end of the outdoor heat exchanger 200. In this way, refrigerant can flow from one end of the outdoor heat exchanger 200 to the indoor heat exchanger 300, or refrigerant can flow from one end of the indoor heat exchanger 300 to the outdoor heat exchanger 200, thereby enabling the air conditioner 1 to switch modes so that the indoor heat exchanger 300 can act as a condenser or an evaporator for cooling or heating the room.

[0158] In some embodiments, as shown in FIG7, the air conditioner 1 may include a water tank heat exchanger 400, which is used for heat exchange with domestic water.

[0159] For example, one end of the water tank heat exchanger 400 can be connected to one end of the indoor heat exchanger 300 and one end of the outdoor heat exchanger 200, respectively.

[0160] In some embodiments, as shown in FIG7, the air conditioner 1 may include a control valve assembly, which is connected to the air inlet 110, the air outlet 120, the other end of the outdoor heat exchanger 200, the other end of the indoor heat exchanger 300, and the other end of the water tank heat exchanger 400, respectively, to control at least one of the outdoor heat exchanger 200, the indoor heat exchanger 300, and the water tank heat exchanger 400 to act as a condenser, and at least one of them to act as an evaporator. For example, the control valve assembly can control the flow of refrigerant so that the outdoor heat exchanger 200 acts as a condenser and the indoor heat exchanger 300 acts as an evaporator, thereby providing indoor cooling; or, the indoor heat exchanger 300 can act as a condenser and the outdoor heat exchanger 200 can act as an evaporator, thereby providing indoor heating; or, the water tank heat exchanger 400 can act as a condenser and the indoor heat exchanger 300 can act as an evaporator, thereby providing indoor cooling while heating domestic water; or, the water tank heat exchanger 400 and the indoor heat exchanger 300 can both act as condensers and the outdoor heat exchanger 200 can act as an evaporator, thereby providing indoor heating while heating domestic water.

[0161] In some embodiments, as shown in FIG7, the control valve assembly may include a first multi-way valve 510, which is connected to the outlet 120, the inlet 110, the other end of the outdoor heat exchanger 200, and the other end of the indoor heat exchanger 300. In this way, refrigerant can flow from the outlet 120 of the compressor 100 to the first multi-way valve 510, and then through the first multi-way valve 510 to the outdoor heat exchanger 200 or the indoor heat exchanger 300. Thus, the first multi-way valve 510 can control whether the refrigerant flows through the outdoor heat exchanger 200 and the indoor heat exchanger 300, and control the order in which the refrigerant flows through them, thereby controlling whether the outdoor heat exchanger 200 and the indoor heat exchanger 300 act as a condenser or an evaporator.

[0162] In some embodiments, as shown in FIG7, the control valve assembly may further include a second multi-way valve 520, which is connected to the outlet 120, the inlet 110, and the other end of the water tank heat exchanger 400. In this way, refrigerant can flow from the outlet 120 of the compressor 100 to the second multi-way valve 520, and then through the second multi-way valve 520 to the water tank heat exchanger 400, thereby allowing the refrigerant to release heat to the domestic water through the water tank heat exchanger 400 to heat the domestic water; alternatively, the refrigerant can also flow from the water tank heat exchanger 400 to the second multi-way valve 520 and then back into the compressor 100 through the second multi-way valve 520.

[0163] In some embodiments, as shown in FIG8, the first multi-way valve 510 can control the outlet 120 to connect with the other end of the outdoor heat exchanger 200, and the other end of the indoor heat exchanger 300 to connect with the inlet 110. In this way, the high-temperature refrigerant flowing from the outlet 120 of the compressor 100 can flow to the outdoor heat exchanger 200 through the first multi-way valve 510. At this time, the outdoor heat exchanger 200 can act as a condenser, meaning the refrigerant can first release heat to the outside through the outdoor heat exchanger 200. Furthermore, at this time, the indoor heat exchanger 300 can act as an evaporator, allowing the refrigerant to absorb indoor heat before flowing back to the compressor through the first multi-way valve 510.

[0164] In some embodiments, as shown in FIG9, the first multi-way valve 510 can control the outlet 120 to be connected to the other end of the indoor heat exchanger 300, and the other end of the outdoor heat exchanger 200 to be connected to the inlet 110. In this way, the high-temperature refrigerant flowing out of the outlet 120 of the compressor 100 can flow to the indoor heat exchanger 300 through the first multi-way valve 510. At this time, the indoor heat exchanger 300 can act as a condenser, that is, the refrigerant can first release heat to the room through the indoor heat exchanger 300. At this time, the outdoor heat exchanger 200 can act as an evaporator, and the refrigerant can absorb heat from the outdoor air through the outdoor heat exchanger 200 and then flow back to the compressor through the first multi-way valve 510.

[0165] In some embodiments, the second multi-way valve 520 can selectively connect the other end of the water tank heat exchanger 400 to the outlet 120 or the inlet 110. For example, the second multi-way valve 520 can connect the other end of the water tank heat exchanger 400 to the outlet 120, as shown in Figures 10, 11, and 12. In this way, the refrigerant flowing out of the compressor 100 can flow to the water tank heat exchanger 400 through the second multi-way valve 520, and then the water tank heat exchanger 400 can heat the domestic water. Alternatively, the second multi-way valve 520 can connect the other end of the water tank heat exchanger 400 to the inlet 110, as shown in Figure 13. In this way, the refrigerant can absorb the heat of the domestic water through the water tank heat exchanger 400 and then flow back to the compressor. At this time, the heat of the domestic water can be used to defrost the outdoor heat exchanger 200. Therefore, the air conditioner 1 in this embodiment can not only cool or heat the room independently, but also heat domestic water while cooling the room, or heat domestic water while heating the room, resulting in a better user experience. Furthermore, the control valve assembly has a simpler structure, which simplifies the piping layout of the air conditioner 1, making the air conditioner 1 more structurally simple and facilitating mode switching. Thus, the air conditioner 1 according to this embodiment can simultaneously heat and heat water, as well as simultaneously cool and heat water, and features a simple connection structure and easy mode switching.

[0166] In some embodiments of this disclosure, as shown in FIG7, the first multi-way valve 510 may include a first interface 511 connected to the outlet 120. Refrigerant flowing from the outlet 120 of the compressor 100 can flow to the first multi-way valve 510 through the first interface 511. In some embodiments, as shown in FIG7, the first multi-way valve 510 may include a second interface 512 connected to the other end of the outdoor heat exchanger 200. Refrigerant flowing through the first multi-way valve 510 can flow to the outdoor heat exchanger 200 through the second interface 512, or the refrigerant can flow from the other end of the outdoor heat exchanger 200 to the second interface 512 and then flow back to the compressor 100 through the first multi-way valve 510. In some embodiments, as shown in FIG7, the first multi-way valve 510 may include a third interface 513 connected to the inlet 110. In this way, the refrigerant flowing through the first multi-way valve 510 can flow to the air inlet 110 through the third port 513, and then flow back to the compressor 100, realizing refrigerant circulation in the air conditioner 1. In some embodiments, the first multi-way valve 510 may include a fourth port 514, which is connected to the other end of the indoor heat exchanger 300. In this way, the refrigerant flowing through the first multi-way valve 510 can flow to the indoor heat exchanger 300 through the fourth port 514, or the refrigerant can also flow from the other end of the indoor heat exchanger 300 to the fourth port 514, and then flow back to the compressor 100 through the first multi-way valve 510.

[0167] In some embodiments, the first multi-way valve 510 can be a four-way valve. The first multi-way valve 510 has a switchable first state and a second state, as shown in FIG8. When the first multi-way valve 510 is in the first state, the first port 511 is connected to the second port 512, and the third port 513 is connected to the fourth port 514.

[0168] Therefore, the refrigerant flowing from the outlet 120 of the compressor 100 can flow sequentially through the first port 511 and the second port 512 to the outdoor heat exchanger 200. At this time, the outdoor heat exchanger 200 can act as an evaporator, allowing the refrigerant to release heat to the outdoor air. Similarly, the refrigerant flowing from the indoor heat exchanger 300 can flow sequentially through the fourth port 514 and the third port 513 back to the compressor. At this time, the indoor heat exchanger 300 can act as an evaporator, allowing the refrigerant to absorb heat from the room, thus achieving indoor cooling.

[0169] In some embodiments, as shown in FIG9, when the first multi-way valve 510 is in the second state, the first port 511 is connected to the fourth port 514, and the third port 513 is connected to the second port 512. Thus, the refrigerant flowing from the outlet 120 of the compressor 100 can flow sequentially through the first port 511 and the fourth port 514 to the indoor heat exchanger 300. At this time, the indoor heat exchanger 300 can act as an evaporator, and the refrigerant can release heat into the room through the indoor heat exchanger 300 to achieve heating for the room. Similarly, the refrigerant flowing from the outdoor heat exchanger 200 can flow sequentially through the second port 512 and the third port 513 back to the compressor. At this time, the outdoor heat exchanger 200 can act as an evaporator, and the refrigerant can absorb heat from the outdoor air through the outdoor heat exchanger 200 and then flow back to the compressor 100.

[0170] In some embodiments of this disclosure, as shown in FIG7, the second multi-way valve 520 may include a fifth port 521, which is connected to the outlet 120. Thus, refrigerant flowing from the outlet 120 can flow to the second multi-way valve 520 through the fifth port 521. In some embodiments, as shown in FIG7, the second multi-way valve 520 may include a sixth port 522, which is connected to the inlet 110. Thus, refrigerant flowing through the second multi-way valve 520 can flow to the inlet 110 through the sixth port 522, and then flow back to the compressor 100, achieving refrigerant circulation.

[0171] In some embodiments, as shown in FIG7, the second multi-way valve 520 may include a seventh port 523, which is connected to the other end of the water tank heat exchanger 400. Thus, refrigerant flowing through the second multi-way valve 520 can flow to the water tank heat exchanger 400 through the seventh port 523, and then heat domestic water through the water tank heat exchanger 400; alternatively, refrigerant flowing through the water tank heat exchanger 400 can also flow to the second multi-way valve 520 through the seventh port 523, and then flow back to the compressor 100 through the second multi-way valve 520.

[0172] In some embodiments, the second multi-way valve 520 can be a three-way valve. The second multi-way valve 520 has switchable third and fourth states, as shown in FIG10. When the second multi-way valve 520 is in the third state, the seventh port 523 is connected to the fifth port 521. In this way, the high-temperature refrigerant flowing out of the outlet 120 of the compressor 100 can flow sequentially through the fifth port 521 and the seventh port 523 and flow to the water tank heat exchanger 400. At this time, the high-temperature refrigerant can release heat to the domestic water through the water tank heat exchanger 400 to heat the domestic water. Then, the refrigerant flowing out of the water tank heat exchanger 400 can flow to the outdoor heat exchanger 200 or the indoor heat exchanger 300 to absorb heat through the outdoor heat exchanger 200 or the indoor heat exchanger 300 and then flow back to the compressor 100, and the air conditioner 1 completes the hot water production cycle.

[0173] In some embodiments, as shown in FIG13, when the second multi-way valve 520 is in the fourth state, the seventh port 523 is connected to the sixth port 522. In this way, the refrigerant flowing through the water tank heat exchanger 400 can also flow through the seventh port 523 to the second multi-way valve 520, and then flow back to the compressor 100 through the second multi-way valve 520. At this time, the air conditioner 1 can absorb the heat of the domestic water through the water tank heat exchanger 400 to defrost the outdoor heat exchanger 200 with the heat of the domestic water.

[0174] In some specific embodiments of this disclosure, as shown in FIG7, the control valve assembly may further include a first on-off valve 530, which is connected between the second interface 512 and the other end of the outdoor heat exchanger 200. Thus, the first on-off valve 530 can control the on / off connection between the second interface 512 and the other end of the outdoor heat exchanger 200. For example, when the outdoor heat exchanger 200 needs to act as an evaporator or condenser, the first on-off valve 530 can be opened. At this time, the refrigerant flowing through the first multi-way valve 510 can flow to the outdoor heat exchanger 200 through the first on-off valve 530, or the refrigerant flowing out of the outdoor heat exchanger 200 can also flow to the first multi-way valve 510 through the first on-off valve 530, and then flow back into the compressor 100.

[0175] In some embodiments, as shown in FIG7, the control valve group may further include a second on-off valve 540, which is connected between the other end of the outdoor heat exchanger 200 and the air inlet 110. Thus, the second on-off valve 540 can control the opening and closing of the connection between the other end of the outdoor heat exchanger 200 and the air inlet 110. That is, the refrigerant flowing through the outdoor heat exchanger 200 can also directly flow back to the compressor through the second on-off valve 540. For example, when the first multi-way valve 510 is in the first state, the air inlet 110 and the first on-off valve 530 are not connected. At this time, the second on-off valve 540 can be opened to ensure that the refrigerant can flow back to the compressor 100 normally, realizing the circulation of the refrigerant and ensuring the normal operation of the air conditioner 1. This results in a more reasonable structural design.

[0176] In some embodiments of this disclosure, as shown in FIG7, the air conditioner 1 may further include a first throttling element 610. One end of the first throttling element 610 is connected to one end of the outdoor heat exchanger 200, and the other end of the first throttling element 610 is connected to one end of the indoor heat exchanger 300 and one end of the water tank heat exchanger 400, respectively. The first throttling element 610 may be an electronic expansion valve. With this configuration, the refrigerant flowing through the indoor heat exchanger 300 or the water tank heat exchanger 400 can be throttled and cooled by the first throttling element 610 before flowing to the outdoor heat exchanger 200. That is, when the indoor heat exchanger 300 or the water tank heat exchanger 400 acts as a condenser and the outdoor heat exchanger 200 acts as an evaporator, the refrigerant flowing to the outdoor heat exchanger 200 can be throttled and cooled by the first throttling element 610 before flowing into the outdoor heat exchanger 200, and absorb heat from the outdoor air through the outdoor heat exchanger 200, which is beneficial to improving the efficiency of the refrigerant absorbing heat through the outdoor heat exchanger 200.

[0177] In some embodiments, as shown in FIG7, the air conditioner 1 may further include a second throttling element 620. One end of the second throttling element 620 is connected to one end of the water tank heat exchanger 400, and the other end of the second throttling element 620 is connected to one end of the outdoor heat exchanger 200 and one end of the indoor heat exchanger 300, respectively. The second throttling element 620 may be an electronic expansion valve. With this configuration, the refrigerant flowing out of the outdoor heat exchanger 200 or the indoor heat exchanger 300 can be throttled and cooled by the second throttling element 620 before flowing to the water tank heat exchanger 400. That is, when the indoor heat exchanger 300 or the outdoor heat exchanger 200 acts as a condenser and the water tank heat exchanger 400 acts as an evaporator, the refrigerant flowing to the water tank heat exchanger 400 can be throttled and cooled by the second throttling element 620 before flowing into the water tank heat exchanger 400, and absorbs heat from the domestic water through the water tank heat exchanger 400, which is beneficial to improving the efficiency of the refrigerant absorbing heat through the water tank heat exchanger 400.

[0178] In some embodiments, as shown in FIG7, the air conditioner 1 may further include a third throttling element 630. One end of the third throttling element 630 is connected to one end of the indoor heat exchanger 300, and the other end of the third throttling element 630 is connected to one end of the outdoor heat exchanger 200 and one end of the water tank heat exchanger 400, respectively. The third throttling element 630 may be an electronic expansion valve. With this configuration, the refrigerant flowing out of the outdoor heat exchanger 200 or the water tank heat exchanger 400 can be throttled and cooled by the third throttling element 630 before flowing to the indoor heat exchanger 300. That is, when the water tank heat exchanger 400 or the outdoor heat exchanger 200 acts as a condenser and the indoor heat exchanger 300 acts as an evaporator, the refrigerant flowing to the indoor heat exchanger 300 can be throttled and cooled by the third throttling element 630 before flowing into the indoor heat exchanger 300, and absorbs heat from the indoor air through the indoor heat exchanger 300, which is beneficial to improving the efficiency of heat absorption by the refrigerant through the indoor heat exchanger 300.

[0179] In some embodiments of this disclosure, as shown in FIG8, the air conditioner 1 has a cooling state, and when the air conditioner 1 is in the cooling state, the first multi-way valve 510 is in the first state and the second multi-way valve 520 is in the fourth state, the first on-off valve 530 and the first throttling element 610 are open, the third throttling element 630 is open and throttles, and the second on-off valve 540 and the second throttling element 620 are closed. Therefore, the high-temperature refrigerant flowing out of the outlet 120 of the compressor 100 can flow to the first on / off valve 530 through the first port 511 and the second port 512, and then to the outdoor heat exchanger 200 through the first on / off valve 530. At this time, the high-temperature refrigerant can release heat to the outdoor air through the outdoor heat exchanger 200. The refrigerant flowing out of the outdoor heat exchanger 200 can flow to the third throttling element 630 through the first throttling element 610. After the refrigerant is throttled and cooled by the third throttling element 630, it flows to the indoor heat exchanger 300 and absorbs heat from the indoor air through the indoor heat exchanger 300, thereby reducing the indoor temperature and achieving indoor cooling. Next, the refrigerant flows out of the indoor heat exchanger 300 and flows to the inlet 110 through the fourth port 514 and the third port 513 in sequence, so as to flow back into the compressor 100 and realize the cooling cycle of the air conditioner 1.

[0180] In some embodiments, as shown in FIG9, the air conditioner 1 may also have a heating state, and when the air conditioner 1 is in the heating state, the first multi-way valve 510 is in the second state and the second multi-way valve 520 is in the fourth state, the first on-off valve 530 and the third throttling element 630 are open, the first throttling element 610 is open and throttles, and the second on-off valve 540 and the second throttling element 620 are closed.

[0181] Therefore, the high-temperature refrigerant flowing out of the outlet 120 of the compressor 100 can flow to the indoor heat exchanger 300 through the first interface 511 and the fourth interface 514. At this time, the high-temperature refrigerant can release heat into the room through the indoor heat exchanger 300 to heat the indoor air and achieve heating for the room. Then, the refrigerant flowing out of the indoor heat exchanger 300 can flow to the first throttling element 610 through the third throttling element 630. After the refrigerant is throttled and cooled by the first throttling element 610, it flows to the outdoor heat exchanger 200 and absorbs heat from the outdoor air through the outdoor heat exchanger 200. Next, the refrigerant flows out of the outdoor heat exchanger 200 and flows to the inlet 110 through the second interface 512 and the third interface 513 in sequence to flow back into the compressor 100, realizing the heating cycle of the air conditioner 1.

[0182] Additionally, it should be noted that when the air conditioner 1 is in heating mode, the first on / off valve 530 can be closed and the second on / off valve 540 can be opened, or the first on / off valve 530 and the second on / off valve 540 can be opened simultaneously.

[0183] In some embodiments, as shown in FIG10, the air conditioner 1 may also have a hot water production state. When the air conditioner 1 is in the hot water production state, the first multi-way valve 510 is in the first state and the second multi-way valve 520 is in the third state. The second on-off valve 540 and the second throttling element 620 are open, the first throttling element 610 is open and throttles, and the first on-off valve 530 and the third throttling element 630 are closed. Therefore, the high-temperature refrigerant flowing out of the outlet 120 of the compressor 100 can flow to the water tank heat exchanger 400 through the fifth interface 521 and the seventh interface 523. At this time, the high-temperature refrigerant can release heat into the domestic water through the water tank heat exchanger 400 to heat the domestic water. Then, the refrigerant flowing out of the water tank heat exchanger 400 can flow to the first throttling element 610 through the second throttling element 620. After the refrigerant is throttled and cooled by the first throttling element 610, it flows to the outdoor heat exchanger 200 and absorbs heat from the outdoor air through the outdoor heat exchanger 200. Next, the refrigerant flows out of the outdoor heat exchanger 200 and flows to the inlet 110 through the second interface 512 and the third interface 513 in sequence to flow back into the compressor 100, realizing the hot water production cycle of the air conditioner 1.

[0184] Additionally, it should be noted that when the air conditioner 1 is in hot water production mode, the first multi-way valve 510 can also be in the second state, and the second multi-way valve 520 in the third state, opening the first on-off valve 530 and the second throttling element 620. The first throttling element 610 is open and throttles the flow, while the second on-off valve 540 and the third throttling element 630 are closed. Alternatively, when the air conditioner 1 is in hot water production mode, the first multi-way valve 510 can also be in the second state, and the second multi-way valve 520 in the third state, opening the first on-off valve 530, the second on-off valve 540, and the second throttling element 620. The first throttling element 610 is open and throttles the flow, while the third throttling element 630 is closed.

[0185] In some embodiments, as shown in FIG11, the air conditioner 1 may also have a first cooling and hot water state. When the air conditioner 1 is in the first cooling and hot water state, the first multi-way valve 510 is in the first state and the second multi-way valve 520 is in the third state. The second throttling element 620 is open, the third throttling element 630 is open and throttles, and the first on-off valve 530, the second on-off valve 540 and the first throttling element 610 are closed. Therefore, the high-temperature refrigerant flowing out of the outlet 120 of the compressor 100 can flow to the water tank heat exchanger 400 through the fifth interface 521 and the seventh interface 523. At this time, the high-temperature refrigerant can release heat into the domestic water through the water tank heat exchanger 400 to heat the domestic water. Then, the refrigerant flowing out of the water tank heat exchanger 400 can flow to the third throttling element 630 through the second throttling element 620. After the refrigerant is throttled and cooled by the third throttling element 630, it flows to the indoor heat exchanger 300 and absorbs heat from the indoor air through the indoor heat exchanger 300 to reduce the indoor temperature and achieve cooling for the room. Next, the refrigerant flows out of the indoor heat exchanger 300 and flows to the inlet 110 through the fourth interface 514 and the third interface 513 in sequence to flow back into the compressor 100, realizing the first cooling and hot water cycle of the air conditioner 1.

[0186] In some embodiments, as shown in FIG12, the air conditioner 1 may also have a heating / hot water production state. When the air conditioner 1 is in the heating / hot water production state, the first multi-way valve 510 is in the second state and the second multi-way valve 520 is in the third state. The first on-off valve 530, the second throttling element 620, and the third throttling element 630 are open, the first throttling element 610 is open and throttles, and the second on-off valve 540 is closed. Thus, the high-temperature refrigerant flowing out of the outlet 120 of the compressor 100 can be divided into two parts. One part of the refrigerant flows to the water tank heat exchanger 400 through the fifth interface 521 and the seventh interface 523. At this time, the high-temperature refrigerant can release heat into the domestic water through the water tank heat exchanger 400 to heat the domestic water. Then, the refrigerant flowing out of the water tank heat exchanger 400 can flow to the first throttling element 610 through the second throttling element 620. The other part of the refrigerant can flow to the indoor heat exchanger 300 through the first interface 511 and the fourth interface 514. At this time, the high-temperature refrigerant can flow to the indoor heat exchanger 300 through the indoor heat exchanger 300. The refrigerant 300 releases heat into the room to heat the indoor air, thus providing heating. The refrigerant flowing from the indoor heat exchanger 300 then flows through the third throttling element 630 to the first throttling element 610. After the two refrigerants merge, they are throttled and cooled by the first throttling element 610 before flowing to the outdoor heat exchanger 200. The outdoor heat exchanger 200 absorbs heat from the outdoor air. The refrigerant then flows out from the outdoor heat exchanger 200 and sequentially through the second port 512 and the third port 513 to the air inlet 110, returning to the compressor 100, thus achieving the heating and hot water circulation of the air conditioner 1. Furthermore, it should be noted that when the air conditioner 1 is in heating or hot water production mode, the first on / off valve 530 can be closed and the second on / off valve 540 can be opened, or both valves can be opened simultaneously.

[0187] In some embodiments, as shown in FIG13, the air conditioner 1 may also have a defrost state. When the air conditioner 1 is in the defrost state, the first multi-way valve 510 is in the first state and the second multi-way valve 520 is in the fourth state. The first on-off valve 530 and the first throttling element 610 are open, the second throttling element 620 is open and throttles, and the second on-off valve 540 and the third throttling element 630 are closed. Thus, when it is necessary to defrost the outdoor heat exchanger 200, the air conditioner 1 can be switched to the defrost state. At this time, the refrigerant flowing out of the outlet 120 of the compressor 100 can flow through the first interface 511 and the second interface 512 to the first on-off valve 530, and then through the first on-off valve 530 to the outdoor heat exchanger 200. At this time, the high-temperature refrigerant can flow through the outdoor heat exchanger 200 and heat the outdoor heat exchanger 200 to achieve defrosting of the outdoor heat exchanger 200. Then the refrigerant flowing out of the outdoor heat exchanger 200... The refrigerant can flow from the first throttling element 610 to the second throttling element 620. After being throttled and cooled by the second throttling element 620, the refrigerant flows to the water tank heat exchanger 400 and absorbs the heat from the domestic water. The heat from the domestic water can then be used to defrost the outdoor heat exchanger 200. Next, the refrigerant flows out of the water tank heat exchanger 400 and flows through the seventh port 523 and the fifth port 521 to the air inlet 110 in sequence, so as to flow back into the compressor 100 and realize the defrosting cycle of the air conditioner 1.

[0188] In some embodiments of this disclosure, as shown in FIG14, the air conditioner 1 also has a second cooling-to-hot water state. When the air conditioner 1 is in the second cooling-to-hot water state, the first multi-way valve 510 is in the first state and the second multi-way valve 520 is in the third state. The second on-off valve 540 and the second throttling element 620 are open, the first throttling element 610 and the third throttling element 630 are open and throttle, and the first on-off valve 530 is closed. Therefore, the high-temperature refrigerant flowing out of the outlet 120 of the compressor 100 can flow to the water tank heat exchanger 400 through the fifth port 521 and the seventh port 523. At this time, the high-temperature refrigerant can release heat into the domestic water through the water tank heat exchanger 400 to heat the domestic water. Then, the refrigerant flowing out of the water tank heat exchanger 400 can be divided into two parts: one part of the refrigerant flows through the second throttling element 620 to the third throttling element 630. After the refrigerant is throttled and cooled by the third throttling element 630, it flows to the indoor heat exchanger 300, where it absorbs heat from the indoor air to reduce the indoor temperature. The refrigerant first cools the room. Then, it flows out of the indoor heat exchanger 300 and flows to the air inlet 110 through the fourth port 514 and the third port 513 in sequence. Another part of the refrigerant flows to the first throttling element 610 through the second throttling element 620. After the refrigerant is throttled and cooled by the first throttling element 610, it flows to the outdoor heat exchanger 200 and absorbs heat from the outdoor air. Then, the refrigerant flows out of the outdoor heat exchanger 200 and flows to the air inlet 110 through the second on / off valve 540 to flow back into the compressor 100, realizing the second cooling and hot water cycle of the air conditioner 1.

[0189] It should be noted that, compared to the first cooling / hot water mode, when air conditioner 1 is in the second cooling / hot water mode, some of the refrigerant flowing out of the water tank heat exchanger 400 will flow to the outdoor heat exchanger 200, where it will absorb heat from the outside air before flowing back to the compressor 100. Therefore, when the heating demand for domestic hot water is high, or the indoor cooling demand is low, air conditioner 1 can be switched to the second cooling / hot water mode. In this way, the heat released through the water tank heat exchanger 400 can be replenished by the outdoor heat exchanger 200 absorbing heat from the outdoor air, without increasing the cooling capacity of the indoor heat exchanger 300, resulting in a better user experience.

[0190] In some embodiments, as shown in FIG15, the air conditioner 1 may also have a third cooling and hot water state. When the air conditioner 1 is in the third cooling and hot water state, the first multi-way valve 510 is in the first state and the second multi-way valve 520 is in the third state. The first on-off valve 530, the first throttling element 610 and the second throttling element 620 are open, the third throttling element 630 is open and throttles, and the second on-off valve 540 is closed.

[0191] Therefore, the high-temperature refrigerant flowing out of the outlet 120 of the compressor 100 can be divided into two parts: one part of the refrigerant can flow to the water tank heat exchanger 400 through the fifth port 521 and the seventh port 523. At this time, the high-temperature refrigerant can release heat into the domestic water through the water tank heat exchanger 400 to heat the domestic water. Then, the refrigerant flowing out of the water tank heat exchanger 400 flows to the third throttling element 630 through the second throttling element 620. The other part of the refrigerant can flow to the first on / off valve 530 through the first port 511 and the second port 512, and then flow to the outdoor heat exchanger 200 through the third on / off valve. This part of the refrigerant can... The outdoor heat exchanger 200 absorbs heat from the outdoor air. Then, the refrigerant flows out of the outdoor heat exchanger 200 and can flow through the first throttling element 610 to the third throttling element 630. After the two parts of refrigerant merge, they are throttled and cooled by the third throttling element 630 before flowing to the indoor heat exchanger 300. The indoor heat exchanger 300 absorbs heat from the indoor air to lower the indoor temperature and achieve cooling for the room. Next, the refrigerant flows out of the indoor heat exchanger 300 and flows through the fourth interface 514 and the third interface 513 to the air inlet 110 in sequence, so as to flow back into the compressor 100, realizing the third cooling and hot water cycle of the air conditioner 1.

[0192] It should be noted that, compared to the first cooling / hot water mode, when air conditioner 1 is in the third cooling / hot water mode, a portion of the refrigerant flowing from compressor 100 will flow to outdoor heat exchanger 200. There, it absorbs heat from the outside air before flowing to indoor heat exchanger 300. Therefore, when the heating demand for domestic hot water is low, or the indoor cooling demand is high, air conditioner 1 can be switched to the third cooling / hot water mode. This allows more heat from the refrigerant to be released to the outside through outdoor heat exchanger 200, and the low-temperature refrigerant can then absorb more heat from the indoor air through indoor heat exchanger 300, thereby increasing the cooling capacity of indoor heat exchanger 300 and meeting the indoor cooling demand.

[0193] In some embodiments of this disclosure, as shown in FIG7, the air conditioner 1 may further include an economizer 800, and the compressor 100 may also be provided with an air inlet 130. The economizer 800 has a first heat exchange channel 810 and a second heat exchange channel 820 that exchange heat with each other. One end of the first heat exchange channel 810 is connected to one end of the outdoor heat exchanger 200, and the other end of the first heat exchange channel 810 is connected to one end of the indoor heat exchanger 300 and one end of the water tank heat exchanger 400, respectively. One end of the second heat exchange channel 820 is connected to one end of the first heat exchange channel 810, and the other end of the second heat exchange channel 820 is connected to the air inlet 130. The air conditioner 1 may further include a fourth throttling element 640, one end of the fourth throttling element 640 is connected to one end of the first heat exchange channel 810, and the other end of the fourth throttling element 640 is connected to one end of the second heat exchange channel 820. The fourth throttling element 640 may be a solenoid valve. Thus, when the outside temperature is low and the air conditioner 1 is heating the room, the liquid refrigerant flowing out of the indoor heat exchanger 300 flows to the first heat exchange channel 810. The liquid refrigerant flowing out of the first heat exchange channel 810 can be divided into two parts. One part of the liquid refrigerant can flow to the outdoor heat exchanger 200 through the first throttling element 610 to absorb heat from the outdoor air. The other part of the liquid refrigerant can flow to the fourth throttling element 640. After being throttled and cooled by the fourth throttling element 640, this part of the refrigerant flows into the second heat exchange channel 820. At this time, the refrigerant in the first heat exchange channel 810 and the refrigerant in the second heat exchange channel 820 can exchange heat to reduce the temperature of the refrigerant in the first heat exchange channel 810. Then, the refrigerant flowing out of the second heat exchange channel 820 can flow to the air inlet 130 and flow into the compressor 100 through the air inlet 130. This configuration allows the refrigerant flowing back to the compressor 100 from the air inlet 130 to replenish the compressor 100 and increase its enthalpy, thereby improving the compressor 100's operating efficiency. Furthermore, after the liquid refrigerant in the first heat exchange channel 810 exchanges heat with the refrigerant in the second heat exchange channel 820, the temperature of the refrigerant in the second channel will further decrease, thus improving the efficiency of the refrigerant in absorbing outdoor air through the outdoor heat exchanger 200.

[0194] In some embodiments of this disclosure, as shown in FIG7, the air conditioner 1 may further include a liquid storage tank 920, one end of which may be connected to the first heat exchange channel 810, and the other end of which may be connected to the second throttling element 620 and the third throttling element 630 respectively.

[0195] In some embodiments of this disclosure, as shown in FIG7, the air conditioner 1 further includes a water tank module 700. In some embodiments, as shown in FIG7, the water tank module 700 may include a water tank 710, which is used to store domestic water and has an inlet 711 and an outlet 712. In some embodiments, as shown in FIG7, the water tank module 700 may include an internal heat exchanger (not shown in the figure), which is disposed inside the water tank 710 and used for heat exchange with the domestic water in the water tank 710. In some embodiments, as shown in FIG7, the water tank module 700 may include a water pump 720, and the internal heat exchanger and the water pump 720 are connected.

[0196] In some embodiments, as shown in FIG7, the water tank heat exchanger 400 may have a fifth heat exchange channel 410 and a sixth heat exchange channel 420 for mutual heat exchange. One end of the fifth heat exchange channel 410 is connected to the second multi-way valve 520, and the other end of the fifth heat exchange channel 410 is connected to one end of the outdoor heat exchanger 200 and one end of the indoor heat exchanger 300, respectively. The sixth heat exchange channel 420 is connected in series with the internal heat exchanger and the water pump 720. With this configuration, the refrigerant flowing through the fifth heat exchange channel 410 can exchange heat with the refrigerant flowing through the sixth heat exchange channel 420, thereby allowing the water tank heat exchanger 400 to release heat to the water tank module 700 or absorb heat from the water tank module 700.

[0197] As shown in Figure 7, an air conditioner 1 is described according to some embodiments of the present disclosure. The air conditioner 1 may include a compressor 100 having an inlet 110 and an outlet 120. The air conditioner 1 may include a gas-liquid separator 910, which may be connected before the air inlet 110. The air conditioner 1 may include an outdoor heat exchanger 200, an indoor heat exchanger 300, and a water tank heat exchanger 400.

[0198] In some embodiments, as shown in FIG7, the air conditioner 1 may include a control valve assembly, which is connected to the air inlet 110, the air outlet 120, the other end of the outdoor heat exchanger 200, the other end of the indoor heat exchanger 300, and the other end of the water tank heat exchanger 400, respectively, to control at least one of the outdoor heat exchanger 200, the indoor heat exchanger 300, and the water tank heat exchanger 400 to act as a condenser, and at least one of them to act as an evaporator.

[0199] In some embodiments, as shown in FIG7, the control valve group may include a first multi-way valve 510, which is connected to the air outlet 120, the air inlet 110, the other end of the outdoor heat exchanger 200, and the other end of the indoor heat exchanger 300, respectively.

[0200] In some embodiments, as shown in FIG7, the control valve group may further include a second multi-way valve 520, which is connected to the outlet 120, the inlet 110 and the other end of the water tank heat exchanger 400, respectively.

[0201] In some embodiments, as shown in FIG8, the first multi-way valve 510 can control the refrigerant flowing out of the outlet 120 to flow sequentially through the outdoor heat exchanger 200 and the indoor heat exchanger 300.

[0202] In some embodiments, as shown in FIG9, the first multi-way valve 510 can control the refrigerant flowing out of the outlet 120 to flow sequentially through the indoor heat exchanger 300 and the outdoor heat exchanger 200.

[0203] In some embodiments, as shown in Figures 10, 11 and 12, the second multi-way valve 520 can control the flow of refrigerant from the outlet 120 to the water tank heat exchanger 400.

[0204] In some embodiments, as shown in FIG13, the second multi-way valve 520 can control the flow of refrigerant flowing through the water tank heat exchanger 400 to the air inlet 110.

[0205] Therefore, the air conditioner 1 in this embodiment can not only cool or heat the room independently, but also heat domestic water while cooling the room, or heat domestic water while heating the room, resulting in a better user experience. Moreover, the structure of the control valve group is simpler, which helps to simplify the pipeline layout of the air conditioner 1. The structure of the air conditioner 1 is simpler, which facilitates mode switching of the air conditioner 1.

[0206] The air conditioner 1 in this disclosure performs a refrigeration cycle by using a compressor 100, a condenser, an expansion valve, and an evaporator. The refrigeration cycle includes a series of processes involving compression, condensation, expansion, and evaporation, and supplies refrigerant to the conditioned and heat-exchanged air.

[0207] Compressor 100 compresses refrigerant gas under high temperature and high pressure and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and the heat is released to the surrounding environment through the condensation process.

[0208] The expansion valve expands the high-temperature, high-pressure liquid refrigerant condensed in the condenser into a low-pressure liquid refrigerant. The evaporator evaporates the expanded refrigerant in the expansion valve and returns the low-temperature, low-pressure refrigerant gas to the compressor 100. The evaporator achieves a cooling effect by utilizing the latent heat of refrigerant evaporation to exchange heat with the material being cooled. Throughout the cycle, the air conditioner 1 can regulate the temperature and humidity of the indoor space via the indoor heat exchanger 300.

[0209] Those skilled in the art will understand that the scope of this disclosure is not limited to the specific embodiments described above, and that modifications and substitutions can be made to certain elements of the embodiments without departing from the spirit of this disclosure. The scope of this disclosure is limited by the appended claims.

Claims

1. An air conditioner, the air conditioner comprising: The compressor includes an air inlet and an air outlet; Indoor heat exchangers are used to exchange heat with indoor air via refrigerant; An outdoor heat exchanger, the first end of which is connected to the first end of the indoor heat exchanger, is used to exchange heat between outdoor air and the refrigerant. A water tank heat exchanger, the first end of which is connected to the first end of the indoor heat exchanger and the first end of the outdoor heat exchanger respectively, the water tank heat exchanger being used to exchange heat between water and the refrigerant. The control valve assembly includes a first control valve unit, a second control valve unit, and a third control valve unit. The first control valve unit is disposed between the air inlet and outlet of the compressor and the second end of the outdoor heat exchanger. The second control valve unit is disposed between the air inlet and outlet of the compressor and the second end of the water tank heat exchanger. The third control valve unit is disposed between the first end of the water tank heat exchanger, the first end of the indoor heat exchanger, and the first end of the outdoor heat exchanger. A controller is used to control the control valve assembly to change the flow direction of the refrigerant output from the outlet. The controller is further configured to, when the air conditioner is in cooling and hot water operation mode, determine a first frequency corresponding to the compressor meeting the cooling conditions and a second frequency corresponding to the compressor meeting the hot water conditions, determine a target frequency based on the first frequency and the second frequency, and control the compressor to operate at the target frequency.

2. The air conditioner as claimed in claim 1, wherein the controller is further configured to obtain the maximum frequency of the first frequency and the second frequency, and determine the maximum frequency as the target frequency.

3. The air conditioner as described in claim 1 or 2, wherein the controller is further configured to, when the compressor is in the initial working stage of the cooling and hot water production mode, determine a first initial frequency corresponding to the compressor meeting the cooling conditions, and determine a second initial frequency corresponding to the compressor meeting the hot water production conditions, determine a target initial frequency based on the first initial frequency and the second initial frequency, and control the compressor to operate at the target initial frequency; The controller is further configured to: when the compressor operates at the target initial frequency for a preset duration, the compressor enters a normal operating phase; determine a first operating frequency corresponding to the compressor meeting the cooling conditions in the current frequency adjustment cycle; determine a second operating frequency corresponding to the compressor meeting the hot water production conditions in the current frequency adjustment cycle; determine a target operating frequency for the current frequency adjustment cycle based on the first operating frequency and the second operating frequency; and control the compressor to operate at the target operating frequency in the current frequency adjustment cycle.

4. The air conditioner as described in claim 3, further comprising a first temperature sensor, the first temperature sensor being connected to the controller; The first temperature sensor is used to detect the real-time outlet water temperature of the water tank heat exchanger; The controller is further configured to, when the compressor is in normal operation, obtain the real-time outlet water temperature detected by the first temperature sensor in the current frequency adjustment cycle, determine the outlet water temperature difference between the target outlet water temperature and the real-time outlet water temperature, and obtain a first frequency adjustment value based on the change amplitude of the outlet water temperature difference corresponding to the current frequency adjustment cycle compared to the outlet water temperature difference of the previous frequency adjustment cycle; and to adjust the current operating frequency of the compressor based on the first frequency adjustment value to obtain the first operating frequency corresponding to the current frequency adjustment cycle.

5. The air conditioner as described in claim 3 or 4, wherein the air conditioner further comprises a water tank and a second temperature sensor, the water tank being connected to the water tank heat exchanger, and the second temperature sensor being connected to the controller; The second temperature sensor is used to detect the real-time water temperature of the water tank; The controller is further configured to, when the compressor is in normal operation, acquire the real-time water tank temperature detected by the second temperature sensor in the current frequency adjustment cycle, determine the water tank temperature difference between the target water tank temperature and the real-time water tank temperature, and obtain a second frequency adjustment value based on the change amplitude of the water tank temperature difference corresponding to the current frequency adjustment cycle compared to the water tank temperature difference in the previous frequency adjustment cycle; and to adjust the current operating frequency of the compressor based on the second frequency adjustment value to obtain the second operating frequency corresponding to the current frequency adjustment cycle.

6. The air conditioner as described in any one of claims 3-5, wherein the duration of each frequency adjustment cycle is determined based on the outlet water temperature difference.

7. The air conditioner as claimed in claim 3, wherein the controller is further configured to determine a first initial frequency based on the rated cooling frequency and a first set of temperature correction coefficients; The first set of temperature correction coefficients comprises: One or more of the following: outdoor temperature correction factor, outlet water temperature difference correction factor, and inlet water temperature correction factor.

8. The air conditioner of claim 7, wherein the controller is further configured to determine the second initial frequency based on a reference initial frequency and a second set of temperature correction coefficients; The second set of temperature correction coefficients comprises: One or more of the outdoor temperature difference correction factor and the water tank temperature difference correction factor.

9. The air conditioner according to any one of claims 1-8, wherein the third control valve unit includes a target electronic expansion valve, the target electronic expansion valve being connected to a first end of the water tank heat exchanger, a first end of the indoor heat exchanger, and a first end of the outdoor heat exchanger respectively; the air conditioner further includes a third temperature sensor and a pressure sensor; The third temperature sensor is used to detect the exhaust temperature of the compressor; The pressure sensor is used to detect the discharge pressure of the compressor; The controller is further configured to, when the air conditioner is operating in a cooling / hot water mode, obtain the exhaust temperature detected by the third temperature sensor and the exhaust pressure detected by the pressure sensor, determine the saturation temperature of the refrigerant corresponding to the exhaust pressure based on the exhaust pressure, determine the exhaust superheat based on the exhaust temperature and the saturation temperature, and adjust the opening of the target electronic expansion valve based on the exhaust superheat.

10. The air conditioner as claimed in claim 9, wherein the controller is further configured to determine the real-time exhaust superheat corresponding to the current opening adjustment cycle based on the real-time exhaust temperature and real-time exhaust pressure of the compressor in the current opening adjustment cycle, determine the superheat difference between the target exhaust superheat and the real-time exhaust superheat corresponding to the current opening adjustment cycle, and adjust the opening of the target electronic expansion valve based on the superheat difference between the current opening adjustment cycle and the superheat difference between the previous opening adjustment cycle.

11. The air conditioner as described in claim 10, wherein the target exhaust superheat corresponding to the current opening adjustment cycle is determined based on the current operating frequency of the compressor and the third set of temperature correction coefficients; The third set of temperature correction factors includes one or more of the outlet water temperature correction factor and the outdoor temperature correction factor.

12. An air conditioner, comprising: The compressor has an air inlet and an air outlet; Outdoor heat exchanger, used for heat exchange with outdoor air; An indoor heat exchanger is used for heat exchange with indoor air, and one end of the indoor heat exchanger is connected to one end of the outdoor heat exchanger. A water tank heat exchanger is used for heat exchange with domestic water, and one end of the water tank heat exchanger is connected to one end of the indoor heat exchanger and one end of the outdoor heat exchanger respectively. A control valve assembly is connected to the air inlet, the air outlet, the other end of the outdoor heat exchanger, the other end of the indoor heat exchanger, and the other end of the water tank heat exchanger, respectively, to control at least one of the outdoor heat exchanger, the indoor heat exchanger, and the water tank heat exchanger to act as a condenser, and at least one of them to act as an evaporator. The control valve assembly includes: A first multi-way valve is connected to the air outlet, the air inlet, the other end of the outdoor heat exchanger, and the other end of the indoor heat exchanger, respectively. The second multi-way valve is connected to the air outlet, the air inlet and the other end of the water tank heat exchanger respectively; Wherein, the first multi-way valve controls the air outlet to be connected to the other end of the outdoor heat exchanger, and the other end of the indoor heat exchanger to be connected to the air inlet; or controls the air outlet to be connected to the other end of the indoor heat exchanger, and the other end of the outdoor heat exchanger to be connected to the air inlet; and The second multi-way valve controls the other end of the water tank heat exchanger to selectively connect to the air outlet or the air inlet.

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