Ice thermal storage air conditioning, method, apparatus, and computer readable storage medium

Abstract

The application provides an ice storage air conditioner, method, device and computer readable storage medium, which comprises a water tank, a storage module, an auxiliary ice storage module and a control assembly. The storage module comprises an evaporator, a compressor and a throttling assembly which are sequentially connected, wherein the evaporator is located in the interior of the water tank, the throttling assembly comprises a first end and a second end, a first temperature sensor for detecting the temperature of the water tank is arranged in the water tank, a second temperature sensor for detecting the return gas temperature is arranged in the compressor, and a third temperature sensor for detecting the evaporation temperature is arranged on the surface of the evaporator. The auxiliary ice storage module comprises a first control valve, a second control valve and a liquid storage tank, the liquid storage tank comprises an inlet end and an outlet end, the inlet end is connected with the first end through the first control valve, and the outlet end is connected with the second end through the second control valve. The control assembly is connected with the first temperature sensor, the second temperature sensor, the third temperature sensor, the first control valve and the second control valve respectively.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and more particularly to an ice storage air conditioner, method, apparatus and computer-readable storage medium. Background Technology

[0002] Ice storage air conditioning equipment generally includes a compressor, evaporator, condenser, water tank, and refrigerant. The compressor generates pressure that drives the refrigerant to circulate within the unit, lowering the temperature of the evaporator surface and causing the water in the tank to cool until it freezes, thus achieving the purpose of cold storage.

[0003] Current ice storage air conditioning equipment suffers from poor cooling performance and long ice storage time during the initial ice storage process. This is because the water temperature in the tank is too high, causing the evaporator to overheat and the refrigerant flowing into the evaporator to evaporate completely. Consequently, the evaporator cannot discharge the liquid refrigerant, resulting in no cooling effect, poor cooling efficiency, and a long ice storage time, negatively impacting the user experience. Therefore, shortening the ice storage time of ice storage air conditioning equipment has become an urgent technical problem to be solved. Summary of the Invention

[0004] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention proposes an ice storage air conditioner, method, apparatus, and computer-readable storage medium, which can improve the cooling effect and shorten the ice storage time.

[0005] In a first aspect, embodiments of the present invention provide an ice storage air conditioner, comprising:

[0006] Water tank;

[0007] A cold storage module includes an evaporator, a compressor, and a throttling assembly connected in sequence. The evaporator is located inside the water tank. The throttling assembly includes a first end and a second end. A first temperature sensor for detecting the water tank temperature is installed inside the water tank. A second temperature sensor for detecting the return gas temperature is installed inside the compressor. A third temperature sensor for detecting the evaporation temperature is installed on the surface of the evaporator.

[0008] An auxiliary ice storage module includes a first control valve, a second control valve, and a liquid storage tank. The liquid storage tank includes an inlet end and an outlet end. The inlet end is connected to the first end through the first control valve, and the outlet end is connected to the second end through the second control valve.

[0009] The control component is connected to the first temperature sensor, the second temperature sensor, the third temperature sensor, the first control valve, and the second control valve, respectively.

[0010] The ice storage air conditioner provided according to embodiments of the present invention has at least the following beneficial effects: The ice storage air conditioner uses a compressor to drive refrigerant through a throttling component to the evaporator for heat exchange, reducing the surface temperature of the evaporator and thus lowering the temperature inside the water tank, causing the liquid in the water tank to cool down to freezing and storing cooling capacity. The inlet end of the liquid storage tank is connected to the first end of the throttling component via a first control valve, while the outlet end is connected to the second end of the throttling component via a second control valve. The control component can control the first and second control valves respectively according to the water tank temperature, return gas temperature, and evaporation temperature. When the water tank temperature is high, the control component can control the second control valve to open, so that the refrigerant stored in the liquid storage tank flows sequentially through the outlet end and the second control valve, flowing from the second end of the throttling component into the refrigerant circulation system of the ice storage air conditioner, increasing the refrigerant circulation volume per unit time, increasing the amount of refrigerant flowing through the evaporator, and improving heat exchange efficiency. The control component can also control the opening of the first control valve based on the return gas temperature and evaporation temperature, allowing the refrigerant in the ice storage air conditioner to flow from the first end of the throttling component to the inlet end. This enables the refrigerant to be recovered by the liquid receiver, preventing excessive refrigerant circulation that could increase the compressor's discharge pressure and affect cooling performance. Therefore, by controlling the first and second control valves based on the water tank temperature, return gas temperature, and evaporation temperature respectively, the liquid receiver can release or recover refrigerant, improving cooling performance and shortening the ice storage time of the ice storage air conditioner.

[0011] In the aforementioned ice storage air conditioner, the auxiliary ice storage module further includes an auxiliary throttling device, which is connected in parallel with the throttling component.

[0012] By adding an auxiliary throttling device connected in parallel with the throttling component, the refrigerant flow rate of the ice storage air conditioner per unit time is increased, thereby increasing the refrigerant flow rate through the evaporator. This ensures that the evaporator has sufficient refrigerant for heat exchange, improving heat exchange efficiency, increasing the cold storage speed, and shortening the cold storage time.

[0013] In the aforementioned ice storage air conditioner, one end of the auxiliary throttle is connected to the inlet end through the first control valve, and the other end is connected to the second end through the second control valve.

[0014] With the second control valve open, the refrigerant in the ice storage air conditioner can flow through the auxiliary throttling device, increasing the refrigerant flow rate per unit time and thus accelerating the ice storage speed. With the second control valve closed, the refrigerant cannot circulate through the auxiliary throttling device. Therefore, the refrigerant throttling degree of the ice storage air conditioner is enhanced, lowering the evaporation temperature and improving the heat exchange effect between the refrigerant and the water in the tank at the evaporator, thereby accelerating the ice storage speed.

[0015] In a second aspect, embodiments of the present invention provide a control method for an ice storage air conditioner, applied to the ice storage air conditioner as described in the first aspect embodiment, the control method comprising:

[0016] When both the first control valve and the second control valve are closed, and the ice storage air conditioner has been running for a preset first duration, the water tank temperature is obtained;

[0017] When the water tank temperature is greater than or equal to a preset water temperature threshold, the second control valve is opened to release refrigerant from the storage tank.

[0018] When the second control valve is open for a preset second duration, the return gas temperature and the evaporation temperature are obtained;

[0019] Based on the return gas temperature and the evaporation temperature, the first control valve and the second control valve are controlled to adjust the amount of refrigerant in the internal circulation of the ice storage air conditioner and accelerate the ice storage speed.

[0020] The control method for ice storage air conditioning provided by the embodiments of the present invention has at least the following beneficial effects: When the ice storage air conditioning operates for a preset first duration with both the first and second control valves closed, it can be considered that the ice storage air conditioning has been operating stably. At this time, the water tank temperature is acquired and compared with a preset water temperature threshold. If the water tank temperature is greater than or equal to the water temperature threshold, it indicates that the ice storage air conditioning requires a large amount of cooling capacity to cool the water tank. Therefore, the second control valve is opened, causing the liquid storage tank to release refrigerant into the evaporator, increasing the refrigerant circulation volume per unit time, increasing the amount of refrigerant flowing through the evaporator, improving the cooling effect, and shortening the ice storage time. When the second control valve is open for a preset second duration, it can be considered that the liquid storage tank has released sufficient refrigerant, and the refrigerant circulation volume in the ice storage air conditioning is sufficient. At this time, the return gas temperature and evaporation temperature can be acquired. The current circulating refrigerant volume is determined by the return gas temperature and evaporation temperature, thereby controlling the first and second control valves to allow the liquid storage tank to continue releasing or recovering refrigerant, adjusting the current circulating refrigerant volume, improving heat exchange efficiency, and accelerating the ice storage speed.

[0021] In the above-mentioned control method for ice storage air conditioning, when the water tank temperature is less than a preset water temperature threshold, both the first control valve and the second control valve are kept in the closed state.

[0022] The required refrigerant circulation volume for the current ice storage air conditioner is determined by comparing the water tank temperature and the water temperature threshold. If the water tank temperature is lower than the water temperature threshold, the current ice storage air conditioner is considered to be operating stably with a low evaporation temperature and a moderate refrigerant volume. Therefore, there is no need to adjust the current circulating refrigerant volume.

[0023] In the above-described control method for ice storage air conditioning, controlling the first control valve and the second control valve based on the return gas temperature and the evaporation temperature includes:

[0024] When the difference between the return gas temperature and the evaporation temperature is less than or equal to a preset first refrigeration threshold, the second control valve is closed.

[0025] By comparing the difference between the return gas temperature and the evaporation temperature with the first refrigeration threshold, it is determined whether the amount of refrigerant in the current cycle is sufficient. If the difference between the return gas temperature and the evaporation temperature is less than or equal to the first refrigeration threshold, it can be considered that the amount of refrigerant in the current cycle is sufficient and there is no need to continue adding refrigerant. Therefore, the second control valve is closed to stop the release of refrigerant from the liquid storage tank, so as to avoid excessive refrigerant in the cycle, which would affect the heat exchange efficiency.

[0026] In the above-described control method for ice storage air conditioning, controlling the first control valve and the second control valve based on the return gas temperature and the evaporation temperature includes:

[0027] When the difference between the return gas temperature and the evaporation temperature is greater than the preset first refrigeration threshold, the second control valve is kept in the open state until the difference between the reacquired return gas temperature and the reacquired evaporation temperature is less than or equal to the preset first refrigeration threshold.

[0028] If the difference between the return gas temperature and the evaporation temperature is greater than the first cooling threshold, it can be considered that the current refrigerant quantity in the cycle is insufficient, and the liquid receiver needs to continue releasing refrigerant to increase the amount of refrigerant flowing through the evaporator. Therefore, the second control valve remains open until the current refrigerant quantity in the ice storage air conditioner is sufficient, thereby improving heat exchange efficiency and cooling effect.

[0029] In the above-described control method for ice storage air conditioning, after closing the second control valve, the following steps are included:

[0030] When the second control valve is closed for a preset third duration, a new return gas temperature and a new evaporation temperature are obtained again.

[0031] When the difference between the new return gas temperature and the new evaporation temperature is less than or equal to a preset second refrigeration threshold, the first control valve is opened.

[0032] After the second control valve has been closed for a preset third period, it can be considered that the ice storage air conditioner has stopped releasing refrigerant from the liquid tank and is operating stably. The return gas temperature and evaporation temperature can then be acquired again. The difference between the return gas temperature and the evaporation temperature is compared with the second cooling threshold to determine if the amount of refrigerant circulating in the ice storage air conditioner is excessive. If the amount of circulating refrigerant is excessive, the first control valve is opened, allowing some of the refrigerant flowing from the compressor to flow into the liquid tank for recovery, reducing the amount of circulating refrigerant and preventing compressor overload.

[0033] In the above-described control method for ice storage air conditioning, the step of obtaining a new return air temperature and a new evaporation temperature after the second control valve has been closed for a preset third time includes:

[0034] When the difference between the new return gas temperature and the new evaporation temperature is greater than the preset second refrigeration threshold, the second control valve is kept closed until the difference between the reacquired return gas temperature and the reacquired evaporation temperature is less than or equal to the preset second refrigeration threshold.

[0035] If the difference between the new return gas temperature and the new evaporation temperature is greater than the second refrigeration threshold, the second control valve will remain closed, allowing the liquid storage tank to continue to recover refrigerant from the ice storage air conditioner, reducing the amount of refrigerant in the current cycle until the amount of refrigerant circulating in the ice storage air conditioner is moderate, and the refrigerant flowing through the evaporator can be completely evaporated, maintaining high heat exchange efficiency and shortening the ice storage time.

[0036] In the above-described control method for ice storage air conditioning, after opening the first control valve, the following steps are included:

[0037] When the first control valve is open for a preset fourth time, a new return gas temperature and a new evaporation temperature are obtained again.

[0038] When the difference between the new return gas temperature and the new evaporation temperature is greater than or equal to a preset third refrigeration threshold, the first control valve is closed.

[0039] After the first control valve opens, the liquid receiver begins to recover refrigerant from the ice storage air conditioning cycle. When the first control valve has been open for a preset fourth time, it can be considered that the liquid receiver has recovered a portion of the refrigerant. The cooling capacity of the current ice storage air conditioning cycle is determined by comparing the difference between the return gas temperature and the evaporation temperature with the third cooling threshold. If the current cooling capacity is appropriate, the first control valve is closed to stop the liquid receiver from recovering refrigerant, thus preventing insufficient refrigerant circulation and reduced heat exchange efficiency.

[0040] In the above-mentioned control method for ice storage air conditioning, after the first control valve has been open for a preset fourth time period and a new return air temperature and a new evaporation temperature have been obtained, the method further includes:

[0041] When the difference between the new return gas temperature and the new evaporation temperature is less than a preset third refrigeration threshold, the first control valve remains open until the difference between the reacquired return gas temperature and the reacquired evaporation temperature is greater than or equal to the preset third refrigeration threshold.

[0042] If the difference between the re-acquired return air temperature and the re-acquired evaporation temperature is less than the preset third refrigeration threshold, it indicates that the amount of refrigerant circulating in the current ice storage air conditioner is too large, and the liquid storage tank still needs to continue to recover refrigerant. Therefore, the first control valve is kept open until the difference between the re-acquired return air temperature and the re-acquired evaporation temperature is greater than or equal to the third refrigeration threshold, that is, the amount of refrigerant circulating is moderate.

[0043] In the above-described control method for ice storage air conditioning, after closing the first control valve, the following steps are included:

[0044] When the first control valve is closed for a preset fifth time period, a new water tank temperature is obtained again;

[0045] When the temperature of the new water tank is less than or equal to the preset ice storage temperature, the ice storage air conditioner is controlled to stop operating.

[0046] After the first control valve has been closed for a preset fifth time, it can be considered that the ice storage air conditioner has stabilized and returned to normal ice storage state, with the remaining refrigerant after being recovered by the liquid storage tank. Therefore, the water tank temperature can be re-acquired to determine whether the water tank temperature has dropped to the target ice storage temperature, so as to determine whether the ice storage operation has been completed and control the operation of the ice storage air conditioner.

[0047] Thirdly, embodiments of the present invention provide an operation control device, including a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the control method described in the second aspect of the embodiments above.

[0048] The operation control device provided by the embodiments of the present invention has at least the following beneficial effects: When the ice storage air conditioner operates for a preset first time when both the first and second control valves are closed, it can be considered that the ice storage air conditioner has been operating stably. At this time, the operation control device acquires the water tank temperature and compares it with a preset water temperature threshold. If the water tank temperature is greater than or equal to the water temperature threshold, it indicates that the ice storage air conditioner requires a large amount of cooling capacity to cool the water tank. Therefore, the operation control device controls the second control valve to open, causing the liquid storage tank to release refrigerant into the evaporator, increasing the refrigerant circulation volume per unit time, increasing the amount of refrigerant flowing through the evaporator, improving the cooling effect, and shortening the ice storage time. When the second control valve is open for a preset second duration, it can be assumed that the liquid storage tank has released sufficient refrigerant, and the refrigerant circulation volume in the ice storage air conditioner is sufficient. At this time, the operation control device obtains the return gas temperature and evaporation temperature, and judges the current circulating refrigerant volume based on the return gas temperature and evaporation temperature, thereby controlling the first control valve and the second control valve to make the liquid storage tank continue to release or recover refrigerant, adjust the current circulating refrigerant volume, improve heat exchange efficiency, and accelerate the ice storage speed.

[0049] Fourthly, embodiments of the present invention provide an air conditioner, including the operation control device described in the third aspect of the embodiments above.

[0050] The air conditioner provided by the embodiments of the present invention has at least the following beneficial effects: When the air conditioner operates for a preset first duration with both the first and second control valves closed, it can be considered that the air conditioner has been operating stably. At this time, the water tank temperature is acquired and compared with a preset water temperature threshold. If the water tank temperature is greater than or equal to the water temperature threshold, it indicates that the air conditioner currently requires a large amount of cooling capacity to cool the water tank. Therefore, the air conditioner controls the second control valve to open, causing the liquid receiver to release refrigerant into the evaporator, increasing the refrigerant circulation volume per unit time, increasing the amount of refrigerant flowing through the evaporator, improving the cooling effect, and shortening the ice storage time. When the second control valve is open for a preset second duration, it can be considered that the liquid receiver has released sufficient refrigerant, and the refrigerant circulation volume in the air conditioner is sufficient. At this time, the air conditioner acquires the return air temperature and evaporation temperature, and determines the current circulating refrigerant volume based on the return air temperature and evaporation temperature, thereby controlling the first and second control valves to allow the liquid receiver to continue releasing or recovering refrigerant, adjusting the current circulating refrigerant volume, improving heat exchange efficiency, and accelerating the ice storage speed.

[0051] Fifthly, embodiments of the present invention provide a computer-readable storage medium storing computer-executable instructions for causing a computer to perform the control method described in the second aspect of the embodiments above.

[0052] The computer-readable storage medium provided by the embodiments of the present invention has at least the following beneficial effects: When the ice storage air conditioner operates for a preset first duration with both the first and second control valves closed, it can be considered that the ice storage air conditioner has been operating stably. At this time, the water tank temperature is acquired and compared with a preset water temperature threshold. If the water tank temperature is greater than or equal to the water temperature threshold, it indicates that the ice storage air conditioner requires a large amount of cooling capacity to cool the water tank. Therefore, the second control valve is opened, causing the liquid storage tank to release refrigerant into the evaporator, increasing the refrigerant circulation volume per unit time, increasing the amount of refrigerant flowing through the evaporator, improving the cooling effect, and shortening the ice storage time. When the second control valve is open for a preset second duration, it can be considered that the liquid storage tank has released sufficient refrigerant, and the refrigerant circulation volume in the ice storage air conditioner is sufficient. At this time, the return gas temperature and evaporation temperature can be acquired. The current circulating refrigerant volume is determined by the return gas temperature and evaporation temperature, thereby controlling the first and second control valves to allow the liquid storage tank to continue releasing or recovering refrigerant, adjusting the current circulating refrigerant volume, improving heat exchange efficiency, and accelerating the ice storage speed.

[0053] The computer-readable storage medium provided according to embodiments of the present invention has at least the following beneficial effects: other features and advantages of the invention will be set forth in the following description, and will be apparent in part from the description, or may be learned by practicing the invention. The objects and other advantages of the invention can be realized and obtained by means of the structures particularly pointed out in the description and drawings. Attached Figure Description

[0054] The present invention will be further described below with reference to the accompanying drawings and embodiments;

[0055] Figure 1 This is a schematic diagram of the structure of an ice storage air conditioner provided in an embodiment of the present invention;

[0056] Figure 2 This is a schematic diagram of the structure of an ice storage air conditioner provided in another embodiment of the present invention;

[0057] Figure 3 This is a flowchart of the control method for ice storage air conditioning provided in an embodiment of the present invention;

[0058] Figure 4 yes Figure 3 A detailed flowchart following step S100;

[0059] Figure 5 yes Figure 3 The detailed flowchart of step S400;

[0060] Figure 6 yes Figure 3 The detailed flowchart of step S400;

[0061] Figure 7 yes Figure 5 A detailed flowchart following step S410;

[0062] Figure 8 yes Figure 7 The detailed flowchart following step S411;

[0063] Figure 9 yes Figure 7 The detailed flowchart following step S412;

[0064] Figure 10 yes Figure 9 The detailed flowchart following step S414;

[0065] Figure 11 yes Figure 9 The detailed flowchart following step S415;

[0066] Figure 12 This is a schematic diagram of the operation control device provided in an embodiment of the present invention. Detailed Implementation

[0067] This section will describe in detail specific embodiments of the present invention. Preferred embodiments of the present invention are shown in the accompanying drawings. The purpose of the drawings is to supplement the textual description with graphics, so that people can intuitively and vividly understand each technical feature and overall technical solution of the present invention, but they should not be construed as limiting the scope of protection of the present invention.

[0068] It should be understood that in the description of the embodiments of the present invention, the use of terms such as "first" and "second" is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of technical features indicated, or implicitly indicating the order of the technical features indicated. "At least one" means one or more, and "more than one" means two or more. "At least one of the following" and similar expressions refer to any combination of these items, including any combination of single or multiple items.

[0069] Furthermore, unless otherwise explicitly specified and limited, the term "connection / linkage" should be interpreted broadly, for example, it can be a fixed connection or a movable connection, a detachable connection or a non-detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection or a connection that can communicate with each other; it can be a direct connection or an indirect connection through an intermediate medium.

[0070] In the description of the embodiments of the present invention, the terms "one embodiment / implementation," "another embodiment / implementation," or "some embodiments / implementations," "in the above embodiments / implementations," etc., refer to specific features, structures, materials, or characteristics described in conjunction with embodiments or examples that are included in at least two embodiments or implementations of this disclosure. In this disclosure, the illustrative expressions of the above terms do not necessarily refer to the same illustrative embodiment or implementation. It should be noted that although a logical order is shown in the flowcharts, in some cases, the steps shown or described may be performed in a different order than that shown in the flowcharts.

[0071] It should be noted that the technical features involved in the various embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other.

[0072] This invention provides an ice storage air conditioner, method, apparatus, and computer-readable storage medium. By determining whether the refrigerant circulation volume required by the ice storage air conditioner is sufficient through the water tank temperature, return gas temperature, and evaporation temperature, the first control valve and the second control valve are controlled to release or recover refrigerant from the liquid storage tank to adjust the refrigerant circulation volume in the ice storage air conditioner, improve heat exchange efficiency, enhance cooling effect, and shorten ice storage time.

[0073] The embodiments of the present invention will be further described below with reference to the accompanying drawings.

[0074] Firstly, reference Figure 1 , Figure 1 This is a schematic diagram of the structure of an ice storage air conditioner 200 provided in the first aspect of the present invention.

[0075] The ice storage air conditioner 200 includes a water tank 210, a cold storage module, an auxiliary ice storage module 100, and control components. The cold storage module includes an evaporator 220, a compressor 230, a condenser 240, and a throttling component 250. The compressor 230, condenser 240, throttling component 250, and evaporator 220 are connected sequentially, with the evaporator 220 connected to the compressor 230. The evaporator 220 absorbs heat from the low-pressure liquid refrigerant flowing from the throttling component 250, evaporating it into low-pressure gaseous refrigerant, thus lowering the surface temperature of the evaporator 220. This low-pressure gaseous refrigerant is then circulated to the compressor 230. Since the evaporator 220 is located inside the water tank 210, lowering the surface temperature of the evaporator 220 reduces the water temperature within the water tank 210, achieving the purpose of storing cold energy. The throttling assembly 250 includes a first end 251 and a second end 252, wherein the first end 251 is connected to the evaporator 220 and the second end 252 is connected to the condenser 240.

[0076] The auxiliary ice storage module 100 includes a liquid storage tank 110, a first control valve 120, and a second control valve 130. The liquid storage tank 110 has an inlet end 111 and an outlet end 112, and can store refrigerant. The outlet end 112 of the liquid storage tank 110 is connected to the second control valve 130, which can be connected to a second end 252. Therefore, when the second control valve 130 is open, the refrigerant in the liquid storage tank 110 can flow out from the outlet end 112, pass through the open second control valve 130, and flow from the second end 252 into the ice storage air conditioner 200, thereby increasing the total amount of refrigerant circulating within the ice storage air conditioner 200, increasing the amount of refrigerant flowing through the evaporator 220 per unit time, and improving the heat exchange efficiency of the evaporator 220. The inlet end 111 of the liquid storage tank 110 is connected to the first control valve 120, which can be connected to the first end 251. Therefore, when the first control valve 120 is open and the second control valve 130 is closed, the refrigerant of the ice storage air conditioner 200 can flow out from the first end 251, pass through the first control valve 120, and flow into the liquid storage tank 110 from the inlet end 111. However, since the second control valve 130 is closed, the refrigerant that flows into the liquid storage tank 110 cannot flow out from the outlet end 112 and the second control valve 130, thus achieving the purpose of refrigerant recovery and avoiding excessive refrigerant in the internal circulation of the ice storage air conditioner 200, which would lead to excessively high suction and discharge pressures of the compressor 230 and inhibit heat exchange efficiency.

[0077] Currently, cold storage equipment cycles through ice storage followed by cooling. The ice storage process involves lowering the temperature of the water in tank 210 from room temperature until it freezes. In the initial stage of ice storage, the water temperature in tank 210 is high, making the evaporator 220 prone to overheating. The refrigerant evaporates rapidly upon entering the evaporator 220, resulting in a lack of liquid refrigerant in the portion of the evaporator 220 near the outlet 112. This leads to ineffective heat exchange and low heat exchange efficiency. Furthermore, overheating of the evaporator 220 can cause the return gas temperature of the compressor 230 to rise, increasing the compressor load and further raising the temperature of the evaporator 220, further reducing heat exchange efficiency and prolonging the ice storage time.

[0078] A first temperature sensor is installed in the water tank 210, a second temperature sensor is installed in the compressor 230, and a third temperature sensor is installed in the evaporator 220. The first temperature sensor measures the water temperature of the water tank 210 in its current state, the second temperature sensor measures the return gas temperature of the compressor 230, and the third temperature sensor measures the evaporation temperature of the evaporator 220. In addition, the ice storage air conditioner 200 is also equipped with a control component that can acquire the water tank temperature from the first temperature sensor, the return gas temperature from the second temperature sensor, and the evaporation temperature from the third temperature sensor. The control component can control the first control valve 120 and the second control valve 130 according to the water tank temperature, return gas temperature, and evaporation temperature, thereby adjusting the amount of refrigerant circulating. For example, when the water tank temperature is high, the second control valve 130 is opened and the first control valve 120 is closed, so that the refrigerant in the liquid storage tank 110 flows through the outlet end 112 and the second control valve 130, and flows from the second end 252 to the evaporator 220, increasing the amount of refrigerant circulating in the ice storage air conditioner 200. The amount of refrigerant flowing into the evaporator 220 ensures that the evaporator 220 has sufficient refrigerant for heat exchange, reducing the temperature of the evaporator 220, and at the same time reducing the return gas temperature of the compressor 230, improving the cooling effect and shortening the ice storage time.

[0079] To prevent excessive refrigerant release from the liquid receiver 110, which could lead to excessive refrigerant circulation within the ice storage air conditioner 200 and reduce heat exchange efficiency, the control component can control the second control valve 130 to open based on the evaporation temperature and return gas temperature. This allows the liquid receiver 110 to release refrigerant to the evaporator 220, and then closes the second control valve 130 to stop the refrigerant release from the liquid receiver 110. Consequently, the refrigerant released from the liquid receiver 110 circulates within the ice storage air conditioner 200, and the amount of refrigerant circulating within the ice storage air conditioner 200 is greater than the initial circulation amount. This compensates for the initial insufficient refrigerant amount in the ice storage air conditioner 200, improves the heat exchange efficiency of the evaporator 220, reduces the return gas temperature of the compressor 230, helps to increase the cooling rate of the evaporator 220, and shortens the ice storage time.

[0080] As the ice storage air conditioner 200 continues to operate, the evaporation temperature gradually decreases, and the amount of refrigerant exchanged per unit time in the evaporator 220 gradually decreases and remains stable. Because some refrigerant is released from the liquid receiver 110, the refrigerant circulation volume within the ice storage air conditioner 200 is large, resulting in excessive liquid refrigerant flowing into the evaporator 220. However, the evaporation area of ​​the evaporator 220 is fixed, causing some liquid refrigerant to not evaporate completely. This leads to a gas-liquid mixture of liquid and gaseous refrigerant. When this gas-liquid mixture enters the compressor 230, it causes liquid slugging in the compressor 230, affecting its normal operation. Simultaneously, the large amount of refrigerant circulating within the ice storage air conditioner 200 can easily increase the discharge pressure of the compressor 230, inhibiting heat exchange efficiency. Therefore, based on the comparison between the return gas temperature and the evaporation temperature, the first control valve 120 is opened and the second control valve 130 is closed. This allows the refrigerant in the ice storage air conditioner 200 to flow out from the first end 251, pass through the first control valve 120, and flow into the liquid storage tank 110 through the inlet end 111, achieving the purpose of refrigerant recovery and recovering excess refrigerant circulating within the ice storage air conditioner 200. Closing the first control valve 120 stops the refrigerant recovery in the liquid storage tank 110. After the liquid storage tank 110 recovers a portion of the refrigerant from the ice storage air conditioner 200, the refrigerant circulation volume of the ice storage air conditioner 200 returns to its initial refrigerant volume. The refrigerant flowing through the evaporator 220 is then evaporated, maintaining a high heat exchange efficiency and shortening the ice storage time.

[0081] Based on the water tank temperature, evaporation temperature, and return gas temperature, the first control valve 120 and the second control valve 130 are adjusted so that the liquid storage tank 110 can release refrigerant into the ice storage air conditioner 200. This increases the amount of refrigerant flowing through the evaporator 220 during the initial cold storage stage, improving the cooling effect during the initial cold storage stage. It also allows the liquid storage tank 110 to recover some of the refrigerant in the ice storage air conditioner 200. During the stable cold storage stage, the refrigerant circulation volume is restored to the initial refrigerant volume, maintaining the high heat exchange rate of the evaporator 220 and shortening the ice storage time.

[0082] It should be noted that the ice storage air conditioner 200 includes a water pump 280, a refrigeration heat exchanger 260, and a fan 270. The water pump 280, refrigeration heat exchanger 260, and water tank 210 are interconnected. The water pump 280 transports liquid from the water tank 210 to the refrigeration heat exchanger 260. The low-temperature liquid exchanges heat with the outside air within the refrigeration heat exchanger 260, lowering the temperature of the environment surrounding the refrigeration heat exchanger 260. The heat-exchanged liquid returns to the water tank 210, forming a cycle. The fan 270 is located on one side of the refrigeration heat exchanger 260, and it blows out the low-temperature air surrounding the refrigeration heat exchanger 260, achieving a cooling effect.

[0083] refer to Figure 2 , Figure 2This is a schematic diagram of the structure of an ice storage air conditioner 200 according to another embodiment of the first aspect of the present invention. It is understood that the ice storage air conditioner 200 is also provided with an auxiliary throttling device 140, which can be connected in parallel with the throttling component 250 within the ice storage air conditioner 200. Thus, the refrigerant in the ice storage air conditioner 200 can flow through the auxiliary throttling device 140, increasing the refrigerant flow rate and the amount of refrigerant flowing through the ice storage air conditioner 200 per unit time. This ensures that the evaporator 220 has sufficient refrigerant for heat exchange, improving heat exchange efficiency, enhancing cooling effect, and shortening ice storage time. Both the auxiliary throttling device 140 and the throttling component 250 can be capillary tubes.

[0084] It is understood that the auxiliary throttling device 140 includes a first auxiliary end 141 and a second auxiliary end 142. The first auxiliary end 141 is connected to the first control valve 120, while the second auxiliary end 142 is connected to the second control valve 130. The first auxiliary end 141 is connected to the first end 251 of the throttling assembly 250 and is connected to the inlet end 111 of the liquid receiver 110 via the first control valve 120. Therefore, the on / off state of the first control valve 120 does not affect the flow of refrigerant from the first auxiliary end 141 into the auxiliary throttling device 140. The second auxiliary end 142 is connected to the inlet end 111 of the liquid receiver 110 and is connected to the second end 252 of the throttling assembly 250 via the second control valve 130. Therefore, when the second control valve 130 is closed, refrigerant cannot flow out through the auxiliary throttling device 140 to the evaporator 220. With the second control valve 130 open, refrigerant can flow out from the second auxiliary end 142 of the auxiliary throttle 140, and after passing through the second control valve 130, it flows to the evaporator 220.

[0085] Therefore, when the second control valve 130 is open, the refrigerant in the ice storage air conditioner 200 can simultaneously flow to the evaporator 220 through the throttling component 250 and the auxiliary throttling device 140, increasing the refrigerant flow rate per unit time. Simultaneously, with the second control valve 130 open, the refrigerant in the liquid storage tank 110 also flows to the evaporator 220 through the second control valve 130, increasing the refrigerant quantity in the ice storage air conditioner 200. This results in an increase in the amount of refrigerant flowing through the evaporator 220 per unit time, improving the heat exchange efficiency of the evaporator 220 and shortening the ice storage time.

[0086] When the first control valve 120 and the second control valve 130 are closed, the refrigerant cannot pass through the auxiliary throttling device 140. The refrigerant can only flow to the evaporator 220 through the throttling component 250. This is equivalent to strengthening the throttling of the ice storage air conditioner 200, reducing the temperature of the refrigerant, thereby accelerating the heat exchange between the low-temperature refrigerant and the water inside the water tank 210, and shortening the ice storage time.

[0087] With the first control valve 120 open and the second control valve 130 closed, the refrigerant cannot pass through the auxiliary throttle 140, and the refrigerant in the liquid receiver 110 cannot flow to the evaporator 220. However, the refrigerant of the ice storage air conditioner 200 flows to the inlet 111 of the liquid receiver 110 through the second control valve 130, and can also flow to the evaporator 220 through the throttle assembly 250. Thus, in the process of maintaining the normal cooling of the ice storage air conditioner 200, some refrigerant can be recovered into the liquid receiver 110, reducing the amount of refrigerant circulating in the ice storage air conditioner 200, reducing the discharge pressure of the compressor 230, avoiding liquid slugging, and improving the heat exchange efficiency of the evaporator 220.

[0088] The ice storage air conditioner 200 described in this embodiment of the invention is for the purpose of more clearly illustrating the technical solutions of this embodiment of the invention, and does not constitute a limitation on the technical solutions provided by this embodiment of the invention. Those skilled in the art will know that with the evolution of the ice storage air conditioner 200 and the emergence of new application scenarios, the technical solutions provided by this embodiment of the invention are also applicable to similar technical problems.

[0089] It will be understood by those skilled in the art that Figure 1 and Figure 2 The structure of the ice storage air conditioner 200 shown does not constitute a limitation on the embodiments of the present invention. It may include more or fewer components than shown, or combine certain components, or have different component arrangements.

[0090] Based on the structure of the ice storage air conditioner 200 described above, various embodiments of the control method of the ice storage air conditioner 200 of the present invention are proposed.

[0091] Secondly, referring to Figure 3 , Figure 3 This is a flowchart of a control method for an ice storage air conditioner provided in an embodiment of the present invention. This control method for an ice storage air conditioner can be applied to, for example... Figure 1 or Figure 2 The ice storage air conditioner 200 shown includes, but is not limited to, the following steps in its control method:

[0092] Step S100: When both the first control valve and the second control valve are closed, and the ice storage air conditioner has been running for a preset first time, the water tank temperature is obtained.

[0093] Step S200: When the water tank temperature is greater than or equal to the preset water temperature threshold, open the second control valve to release the refrigerant from the storage tank.

[0094] Step S300: When the second control valve is open for a preset second duration, the return gas temperature and evaporation temperature are obtained.

[0095] In step S400, based on the return gas temperature and the evaporation temperature, the first control valve and the second control valve are controlled to adjust the amount of refrigerant in the internal circulation of the ice storage air conditioner and accelerate the ice storage speed.

[0096] Understandably, after the initial startup of the ice storage air conditioner, if it continues to operate for a preset first duration with both the first and second control valves closed, it can be considered that the ice storage air conditioner is operating stably. At this point, the water tank temperature can be obtained through the first temperature sensor to determine whether the water tank temperature is too high, i.e., whether the ice storage air conditioner currently requires a large amount of cooling capacity to cool the liquid in the water tank. When the water tank temperature is greater than or equal to the preset water temperature threshold, it can be considered that the current water tank temperature is too high, requiring a large amount of cooling capacity to cool the water tank. However, the evaporator is located inside the water tank, and the evaporator temperature is prone to becoming too high. This causes the refrigerant to evaporate rapidly after flowing into the evaporator, leaving the evaporator surface near the outlet without liquid refrigerant flowing through it, resulting in low heat exchange efficiency. Moreover, overheating of the evaporator can easily lead to an increase in the compressor's return gas temperature, increasing the compressor load, which in turn causes the evaporator temperature to continue to rise, further reducing heat exchange efficiency and prolonging the ice storage time. Therefore, when the water tank temperature is greater than or equal to the water temperature threshold, the second control valve is opened, allowing the refrigerant in the storage tank to flow through the outlet end and the second control valve, and then into the evaporator from the second end. This increases the amount of refrigerant circulating in the ice storage air conditioner per unit time, ensuring that there is enough refrigerant flowing into the evaporator for heat exchange, thereby reducing the evaporator temperature, improving heat exchange efficiency, enhancing the cooling effect, and shortening the ice storage time.

[0097] Excessive refrigerant in the internal circulation of an ice storage air conditioner leads to excessive refrigerant flowing into the evaporator. Since the evaporator's evaporation area is fixed, some refrigerant cannot evaporate completely, reducing heat exchange efficiency. This causes some liquid and gaseous refrigerant to form a gas-liquid mixture. When this mixture enters the compressor, it causes liquid slugging, affecting the compressor's normal operation. Furthermore, the compressor's excessive refrigerant circulation places a heavy load on it, resulting in high discharge and return pressures, further inhibiting heat exchange efficiency. However, increasing the refrigerant in the internal circulation of the ice storage air conditioner gradually lowers the evaporator temperature as it runs, reducing the amount of refrigerant needed for heat exchange per unit time. This means the required refrigerant amount gradually decreases back to the initial level. Therefore, it is necessary to reduce the amount of refrigerant in the internal circulation of the ice storage air conditioner to maintain high heat exchange efficiency and shorten the ice storage time.

[0098] Therefore, after the second control valve opens, the ice storage air conditioner operates for a preset second duration, indicating that the liquid storage tank has released sufficient refrigerant. The evaporation temperature and return gas temperature are used to determine if the current refrigerant level in the internal circulation of the ice storage air conditioner is sufficient; that is, the superheat is used to determine if the current refrigerant level is excessive. If the superheat is low, it indicates that the current refrigerant level is too high, requiring refrigerant recovery. Therefore, the first control valve is opened, and the second control valve is closed, causing the refrigerant in the internal circulation of the ice storage air conditioner to flow out from the first end, pass through the first control valve, and flow into the liquid storage tank from the inlet end. This achieves the purpose of refrigerant recovery, reducing the amount of refrigerant in the internal circulation of the ice storage air conditioner, ensuring that the refrigerant flowing through the evaporator is just evaporated, maintaining high heat exchange efficiency, and shortening the ice storage time.

[0099] Therefore, based on the water tank temperature, return air temperature, and evaporation temperature, the first control valve and the second control valve are controlled to adjust the amount of refrigerant circulating in the ice storage air conditioner, so that there is sufficient refrigerant in the evaporator for heat exchange and evaporation, and the refrigerant flowing through the evaporator is completely evaporated, thereby improving heat exchange efficiency and shortening ice storage time.

[0100] Reference Figure 4 , Figure 4 yes Figure 3 The detailed flowchart after step S100 is in Figure 4 In the example, after step S100, there are, but are not limited to, the following steps:

[0101] Step S110: When the water tank temperature is lower than the preset water temperature threshold, both the first control valve and the second control valve are kept closed.

[0102] It is understandable that when the water tank temperature is lower than the water temperature threshold, the cooling capacity required by the ice storage air conditioner is considered to be moderate, and the amount of refrigerant circulating is moderate. Therefore, there is no need to adjust the amount of refrigerant circulating. Thus, maintaining the first control valve closed and the second control valve closed can maintain high heat exchange efficiency.

[0103] Reference Figure 5 , Figure 5 yes Figure 3 The detailed flowchart of step S400 is in Figure 5 In the example, step S400 includes, but is not limited to, the following steps:

[0104] Step S410: When the difference between the return gas temperature and the evaporation temperature is less than or equal to the preset first refrigeration threshold, the second control valve is closed.

[0105] Understandably, the difference between the return gas temperature and the evaporation temperature is the superheat. After the second control valve opens, i.e., after the liquid receiver tank releases refrigerant into the evaporator, if the superheat is less than or equal to the preset first cooling threshold, it can be considered that the current refrigerant quantity in the ice storage air conditioner is sufficient, and there is no need to continue adding refrigerant. Therefore, the second control valve is closed to stop the liquid receiver tank from releasing refrigerant, thus preventing excessive refrigerant in circulation. At this time, the amount of refrigerant circulating in the ice storage air conditioner is greater than the initial amount, ensuring sufficient refrigerant flow through the evaporator, improving the evaporator's heat exchange efficiency, and enhancing the cooling effect.

[0106] It should be noted that ice storage air conditioners can be equipped with an auxiliary throttling device. After the second control valve is closed, the refrigerant cannot pass through the auxiliary throttling device and can only flow to the evaporator through the throttling component. This is equivalent to strengthening the throttling effect of the ice storage air conditioner, lowering the temperature of the refrigerant, thereby accelerating the heat exchange between the low-temperature refrigerant and the liquid inside the water tank and shortening the ice storage time.

[0107] Reference Figure 6 , Figure 6 yes Figure 3 The detailed flowchart of step S400 is in Figure 6 In the example, step S400 includes, but is not limited to, the following steps:

[0108] Step S420: When the difference between the return gas temperature and the evaporation temperature is greater than the preset first refrigeration threshold, the second control valve is kept in the open state until the difference between the reacquired return gas temperature and the reacquired evaporation temperature is less than or equal to the preset first refrigeration threshold.

[0109] Understandably, after the second control valve opens, if the superheat exceeds the first cooling threshold (i.e., the difference between the return gas temperature and the evaporation temperature is large), it can be assumed that the refrigerant quantity in the current ice storage air conditioning cycle is insufficient. The evaporator lacks sufficient refrigerant for heat exchange and evaporation, requiring the liquid receiver to continue releasing refrigerant to increase the refrigerant quantity in the ice storage air conditioning cycle. When the superheat exceeds the first cooling threshold, the second control valve remains open, allowing the liquid receiver to continue replenishing refrigerant. When the second control valve remains open for the preset second duration, the return gas temperature from the second temperature sensor and the evaporation temperature from the third temperature sensor are re-acquired. Using these re-acquired temperatures, a new superheat is calculated. It is then determined whether the new superheat is less than or equal to the first cooling threshold, indicating whether the current refrigerant quantity in the cycle is sufficient. If the new superheat is less than or equal to the first cooling threshold, the current refrigerant quantity in the cycle is sufficient, and the second control valve can be closed to stop the liquid receiver from releasing more refrigerant. If the new superheat is still greater than the first cooling threshold, the second control valve needs to be opened to allow the liquid receiver to continue releasing refrigerant until the amount of refrigerant in the ice storage air conditioning cycle is sufficient, that is, the new superheat is less than or equal to the first cooling threshold, so as to improve the heat exchange efficiency of the evaporator, improve the cooling effect, and shorten the ice storage time.

[0110] Reference Figure 7 , Figure 7 yes Figure 5 The detailed flowchart after step S410 is in Figure 7 In the example, after step S410, there are, but are not limited to, the following steps:

[0111] Step S411: When the second control valve is closed for a preset third time, a new return gas temperature and a new evaporation temperature are obtained again.

[0112] Step S412: When the difference between the new return gas temperature and the new evaporation temperature is less than or equal to the preset second refrigeration threshold, the first control valve is opened.

[0113] Understandably, when the refrigerant quantity in the internal circulation of the ice storage air conditioner is sufficient—that is, the difference between the return air temperature and the evaporation temperature is less than or equal to the first cooling threshold—the second control valve is closed, allowing the ice storage air conditioner to operate with the increased refrigerant quantity. When the ice storage air conditioner operates with a stable increase in refrigerant for a preset third duration (i.e., the second control valve is closed for a preset third duration), it can be considered that the ice storage air conditioner has stabilized, the evaporation temperature has decreased, and the current refrigerant quantity required by the ice storage air conditioner has decreased. Therefore, some refrigerant needs to be recovered. Thus, the return air temperature from the second temperature sensor and the evaporation temperature from the third temperature sensor are obtained again, and the difference between the new return air temperature and the new evaporation temperature is used to determine whether the current circulating refrigerant quantity is excessive. When the difference is less than or equal to the preset second cooling threshold, it indicates that the amount of refrigerant circulating is too much. The first control valve can be opened while the second control valve remains closed, allowing the refrigerant of the ice storage air conditioner to flow out from the first end, through the first control valve, and into the liquid storage tank from the inlet end. This achieves the purpose of refrigerant recovery, reduces the amount of circulating refrigerant, and ensures that the refrigerant flowing through the evaporator is completely evaporated, maintaining high heat exchange efficiency and shortening the ice storage time.

[0114] Reference Figure 8 , Figure 8 yes Figure 7 The detailed flowchart after step S411 is in Figure 8 In the example, after step S411, there are, but are not limited to, the following steps:

[0115] Step S413: When the difference between the new return gas temperature and the new evaporation temperature is greater than the preset second refrigeration threshold, the second control valve is kept closed until the difference between the reacquired return gas temperature and the reacquired evaporation temperature is less than or equal to the preset second refrigeration threshold.

[0116] Understandably, after the second control valve is closed, the difference between the new return gas temperature and the new evaporation temperature is greater than the second refrigeration threshold, indicating that the current refrigerant quantity is sufficient, i.e., the return gas temperature is high. The evaporator still needs a large amount of refrigerant for heat exchange. Therefore, both the second and first control valves are kept closed, so that the ice storage air conditioner operates with the increased refrigerant quantity, ensuring that sufficient refrigerant enters the evaporator for heat exchange, achieving high heat exchange efficiency and shortening the ice storage time.

[0117] As the ice storage air conditioner continues to operate, the evaporator temperature gradually decreases, and the amount of refrigerant used for heat exchange per unit time also gradually decreases. This means the amount of refrigerant required by the evaporator gradually decreases back to its initial level. Therefore, it is necessary to obtain the evaporation temperature and return gas temperature again at a preset third time interval to determine if the current refrigerant requirement of the evaporator has decreased. When the difference between the return gas temperature and the evaporation temperature is less than or equal to the second cooling threshold, it indicates that the return gas temperature is already too low, and the current refrigerant requirement of the evaporator has decreased. Therefore, the amount of refrigerant circulating in the ice storage air conditioner should be reduced to maintain high heat exchange efficiency and shorten the ice storage time.

[0118] Reference Figure 9 , Figure 9 yes Figure 7 The detailed flowchart after step S412 is in Figure 9 In the example, after step S412, there are, but are not limited to, the following steps:

[0119] Step S414: When the first control valve has been open for a preset fourth time, a new return gas temperature and a new evaporation temperature are obtained again.

[0120] Step S415: When the difference between the new return gas temperature and the new evaporation temperature is greater than or equal to the preset third refrigeration threshold, the first control valve is closed.

[0121] Understandably, when the first control valve is open and the second control valve is closed, the refrigerant in the ice storage air conditioner flows into the liquid storage tank through the first end, the first control valve, and the inlet end. The refrigerant in the liquid storage tank cannot flow into the evaporator through the outlet end, the second control valve, and the second end. Therefore, the refrigerant is recovered, reducing the amount of refrigerant circulating in the ice storage air conditioner. Thus, if the time after the first control valve is open reaches a preset fourth time, it can be considered that the liquid storage tank has recovered some of the circulating refrigerant. It is then necessary to obtain the return gas temperature and evaporation temperature again to determine if the amount of refrigerant circulating in the ice storage air conditioner is sufficient, in order to continue or stop refrigerant recovery. If the difference between the new return gas temperature and the new evaporation temperature is greater than or equal to the preset third refrigeration threshold, it indicates that the liquid storage tank has recovered enough refrigerant, and the current amount of refrigerant circulating in the ice storage air conditioner is sufficient. There is no need to continue recovering refrigerant. Therefore, the first control valve is closed to stop the refrigerant from flowing into the liquid storage tank through the first control valve, thus stopping refrigerant recovery, maintaining the high heat exchange efficiency of the ice storage air conditioner, and shortening the ice storage time.

[0122] Reference Figure 10 , Figure 10 yes Figure 9 The detailed flowchart after step S414 is in Figure 10 In the example, after step S414, there are, but are not limited to, the following steps:

[0123] Step S416: When the difference between the new return gas temperature and the new evaporation temperature is less than the preset third refrigeration threshold, the first control valve is kept in the open state until the difference between the reacquired return gas temperature and the reacquired evaporation temperature is greater than or equal to the preset third refrigeration threshold.

[0124] Understandably, after the first control valve has been open for a preset fourth time period, the return gas temperature and evaporation temperature can be measured again to determine whether the liquid receiver has recovered some of the refrigerant. If the difference between the new return gas temperature and the new evaporation temperature is less than the preset third refrigeration threshold, it indicates that the current return gas temperature is low, and the amount of refrigerant circulating in the ice storage air conditioner is relatively large, meaning that the liquid receiver has not recovered enough refrigerant. Therefore, the first control valve needs to remain open to allow the refrigerant to flow into the liquid receiver for recovery.

[0125] If the first control valve remains open for an extended period, resulting in prolonged refrigerant recovery, the amount of refrigerant circulating in the ice storage air conditioner may be insufficient, reducing heat exchange efficiency and prolonging ice storage time. Therefore, after the first control valve opens, the return gas temperature and evaporation temperature are periodically measured to determine if the amount of refrigerant circulating in the ice storage air conditioner is excessive. If the refrigerant level is excessive, refrigerant recovery continues; if the refrigerant level is sufficient, refrigerant recovery is stopped, thus preventing insufficient refrigerant from affecting evaporator heat exchange.

[0126] Reference Figure 11 , Figure 11 yes Figure 9 The detailed flowchart after step S415 is in Figure 11 In the example, after step S415, there are, but are not limited to, the following steps:

[0127] Step S417: When the first control valve has been closed for a preset fifth time period, a new water tank temperature is obtained again.

[0128] Step S418: When the new water tank temperature is less than or equal to the preset ice storage temperature, control the ice storage air conditioner to stop operating.

[0129] Understandably, when the first control valve closes, the liquid storage tank stops recovering refrigerant, indicating that the ice storage air conditioner has resumed its initial refrigerant level. If the first control valve remains closed for a preset five-hour period, it means the ice storage air conditioner is operating stably in normal ice storage mode. Therefore, the water tank temperature can be re-acquired to determine if it has dropped to the target ice storage temperature, thus confirming the completion of the ice storage operation. If the new water tank temperature is less than or equal to the ice storage temperature, it means the liquid in the tank has cooled and frozen, completing the ice storage operation. The ice storage air conditioner can then be shut down to save power. If the new water tank temperature is greater than the ice storage temperature, it means the liquid in the tank has not completely cooled, and the ice storage operation is not complete. The compressor of the ice storage air conditioner must continue to run to continuously cool the liquid in the tank until the water tank temperature is again less than or equal to the ice storage temperature after another preset five-hour interval. At this point, the ice storage air conditioner can be shut down to ensure sufficient ice storage.

[0130] refer to Figure 12 , Figure 12 The present invention provides a schematic diagram of the structure of the operation control device 1200 according to a third aspect embodiment of the present invention. The operation control device 1200 includes: a memory 1210, a processor 1220 and a computer program stored in the memory 1210 and executable on the processor 1220. When the processor 1220 executes the computer program, it implements the control method of the ice storage air conditioner as described in the above embodiment.

[0131] The memory 1210, as a non-transitory computer-readable storage medium, can be used to store non-transitory software programs and non-transitory computer-executable programs, such as the ice storage air conditioner control method in the above embodiments of the present invention. The processor 1220 implements the ice storage air conditioner control method in the above embodiments of the present invention by running the non-transitory software program and instructions stored in the memory 1210.

[0132] The memory 1210 may include a program storage area and a data storage area. The program storage area may store the operating system and application programs required for at least one function; the data storage area may store data required for executing the control method of the ice storage air conditioner in the above embodiments. Furthermore, the memory 1210 may include high-speed random access memory 1210, and may also include non-transitory memory 1210, such as at least one disk storage device, flash memory device, or other non-transitory solid-state storage device. It should be noted that the memory 1210 may optionally include memory 1210 remotely located relative to the processor 1220, and these remote memories 1210 can be connected to the terminal via a network. Examples of such networks include, but are not limited to, the Internet, corporate intranets, local area networks, mobile communication networks, and combinations thereof.

[0133] The non-transient software program and instructions required to implement the ice storage air conditioner control method in the above embodiments are stored in memory. When executed by one or more processors, the ice storage air conditioner control method in the above embodiments is executed, for example, the method described above is executed. Figure 3 Method steps S100 to S400 Figure 4 Method steps S110, Figure 5 Method steps S410, Figure 6 Method steps S420, Figure 7 Method steps S411 to S412 in the middle Figure 8 Method steps S413 Figure 9 Method steps S414 to S415 Figure 10 Method steps S416 and Figure 11 Method steps S417 to S418.

[0134] A fourth aspect of the present invention provides an air conditioner including an operation control device 1200 as provided in the third aspect embodiment. Therefore, when the air conditioner operates for a preset first duration with both the first and second control valves closed, it can be considered that the air conditioner has achieved stable operation. At this time, the water tank temperature is acquired and compared with a preset water temperature threshold. If the water tank temperature is greater than or equal to the water temperature threshold, it indicates that the air conditioner requires a large amount of cooling capacity to cool the water tank. Therefore, the air conditioner controls the second control valve to open, causing the liquid receiver to release refrigerant into the evaporator, increasing the refrigerant circulation volume per unit time, thus increasing the amount of refrigerant flowing through the evaporator, improving the cooling effect, and shortening the ice accumulation time. When the second control valve is open for a preset second duration, it can be assumed that the liquid receiver has released sufficient refrigerant and the refrigerant circulation in the air conditioner is sufficient. At this time, the air conditioner obtains the return air temperature and evaporation temperature, and judges the current refrigerant circulation amount by using the return air temperature and evaporation temperature, thereby controlling the first control valve and the second control valve to make the liquid receiver continue to release or recover refrigerant, adjust the current refrigerant circulation amount, improve heat exchange efficiency, and accelerate ice storage speed.

[0135] A fifth aspect embodiment of the present invention provides a computer-readable storage medium storing computer-executable instructions that can be used to cause a computer to perform the control method of the ice storage air conditioner as described in the second aspect embodiment above, for example, to perform the above-described... Figure 3 Method steps S100 to S400 Figure 4 Method steps S110, Figure 5 Method steps S410, Figure 6 Method steps S420, Figure 7 Method steps S411 to S412, Figure 8 Method steps S413 Figure 9 Method steps S414 to S415 Figure 10 Method steps S416 and Figure 11 Method steps S417 to S418.

[0136] It will be understood by those skilled in the art that all or some of the steps and systems in the methods disclosed above can be implemented as software, firmware, hardware, and suitable combinations thereof. Some or all of the physical components can be implemented as software executed by a processor, such as a central processing unit, digital signal processor, or microprocessor, or as hardware, or as an integrated circuit, such as an application-specific integrated circuit. Such software can be distributed on a computer-readable medium, which may include computer storage media or non-transitory media and communication media or transient media. As is known to those skilled in the art, the term computer storage media includes volatile and non-volatile, removable and non-removable media implemented in any method or technology for storing information such as computer-readable instructions, data structures, program modules, or other data. Computer storage media includes, but is not limited to, RAM, ROM, EEPROM, flash memory or other memory technologies, CD-ROM, digital versatile disc DVD or other optical disc storage, magnetic cartridges, magnetic tape, disk storage or other magnetic storage devices, or any other medium that can be used to store desired information and is accessible to a computer. Furthermore, as is known to those skilled in the art, communication media typically contain computer-readable instructions, data structures, program modules, or other data in modulated data signals such as carrier waves or other transmission mechanisms, and may include any information delivery medium.

[0137] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present invention.

Claims

1. An ice storage air conditioner, characterized in that, include: Water tank; A cold storage module includes an evaporator, a compressor, and a throttling component connected in sequence. The evaporator is located inside the water tank. The throttling component includes a first end and a second end. A first temperature sensor for detecting the water tank temperature is installed inside the water tank. A second temperature sensor for detecting the return gas temperature is installed inside the compressor. A third temperature sensor for detecting the evaporation temperature is installed on the surface of the evaporator. An auxiliary ice storage module includes a first control valve, a second control valve, a liquid storage tank, and an auxiliary throttle. The liquid storage tank includes an inlet end and an outlet end. The inlet end is connected to the first end through the first control valve, and the outlet end is connected to the second end through the second control valve. One end of the auxiliary throttle is connected to the inlet end through the first control valve, and the other end is connected to the second end through the second control valve. The control component is connected to the first temperature sensor, the second temperature sensor, the third temperature sensor, the first control valve, and the second control valve, respectively.

2. A control method for an ice storage air conditioner, characterized in that, The control method, applied to the ice storage air conditioner as described in claim 1, includes: When both the first control valve and the second control valve are closed, and the ice storage air conditioner has been running for a preset first duration, the water tank temperature is obtained; When the water tank temperature is greater than or equal to a preset water temperature threshold, the second control valve is opened to release refrigerant from the storage tank. When the second control valve is open for a preset second duration, the return gas temperature and the evaporation temperature are obtained; Based on the return gas temperature and the evaporation temperature, the first control valve and the second control valve are controlled to adjust the amount of refrigerant in the internal circulation of the ice storage air conditioner and accelerate the ice storage speed.

3. The control method according to claim 2, characterized in that, When the water tank temperature is lower than the preset water temperature threshold, both the first control valve and the second control valve remain closed.

4. The control method according to claim 2, characterized in that, The step of controlling the first control valve and the second control valve based on the return gas temperature and the evaporation temperature includes: When the difference between the return gas temperature and the evaporation temperature is less than or equal to a preset first refrigeration threshold, the second control valve is closed.

5. The control method according to claim 2, characterized in that, The step of controlling the first control valve and the second control valve based on the return gas temperature and the evaporation temperature includes: When the difference between the return gas temperature and the evaporation temperature is greater than the preset first refrigeration threshold, the second control valve is kept in the open state until the difference between the reacquired return gas temperature and the reacquired evaporation temperature is less than or equal to the preset first refrigeration threshold.

6. The control method according to claim 4, characterized in that, After closing the second control valve, the following steps are included: When the second control valve is closed for a preset third duration, a new return gas temperature and a new evaporation temperature are obtained again. When the difference between the new return gas temperature and the new evaporation temperature is less than or equal to a preset second refrigeration threshold, the first control valve is opened.

7. The control method according to claim 6, characterized in that, When the second control valve is closed for a preset third time, and a new return gas temperature and a new evaporation temperature are obtained again, the process includes: When the difference between the new return gas temperature and the new evaporation temperature is greater than the preset second refrigeration threshold, the second control valve is kept closed until the difference between the reacquired return gas temperature and the reacquired evaporation temperature is less than or equal to the preset second refrigeration threshold.

8. The control method according to claim 6, characterized in that, After opening the first control valve, the following steps are included: When the first control valve is open for a preset fourth time, a new return gas temperature and a new evaporation temperature are obtained again. When the difference between the new return gas temperature and the new evaporation temperature is greater than or equal to a preset third refrigeration threshold, the first control valve is closed.

9. The control method according to claim 8, characterized in that, After the first control valve has been open for a preset fourth time period, and a new return gas temperature and a new evaporation temperature are obtained again, the process further includes: When the difference between the new return gas temperature and the new evaporation temperature is less than a preset third refrigeration threshold, the first control valve remains open until the difference between the reacquired return gas temperature and the reacquired evaporation temperature is greater than or equal to the preset third refrigeration threshold.

10. The control method according to claim 8, characterized in that, After closing the first control valve, the following steps are included: When the first control valve is closed for a preset fifth time period, a new water tank temperature is obtained again; When the temperature of the new water tank is less than or equal to the preset ice storage temperature, the ice storage air conditioner is controlled to stop operating.

11. An operation control device, characterized in that, It includes a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor, when executing the computer program, implements the control method as described in any one of claims 2 to 10.

12. An air conditioner, characterized in that, Includes the operation control device as described in claim 11.

13. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores computer-executable instructions for causing a computer to perform the control method as described in any one of claims 2 to 10.

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