Control method and device for microchannel heat exchangers in air conditioning, air conditioning

Abstract

This application relates to the field of refrigeration system technology, and discloses a control method for an air conditioning microchannel heat exchanger, comprising: obtaining the superheat of a first flow channel and a second flow channel; determining the superheat range in which the superheat of the first flow channel and the second flow channel respectively reside; and controlling the refrigerant flow rate of the first flow channel and the second flow channel according to the control strategy corresponding to the superheat range in which the first flow channel and the second flow channel respectively reside. In this application, the pressure loss of the refrigerant in the microchannel heat exchanger can be reduced, making the pressure loss of the refrigerant match the heat exchange area through which it flows, thereby improving heat exchange performance. This application also discloses a control device for an air conditioning microchannel heat exchanger and an air conditioner.

Description

Technical Field

[0001] This application relates to the field of refrigeration system technology, such as a control method and device for an air conditioning microchannel heat exchanger, and an air conditioner. Background Technology

[0002] Currently, a heat exchanger is an energy-saving device that enables heat transfer between two or more fluids at different temperatures. In a heat exchanger, heat is transferred from the higher-temperature fluid to the lower-temperature fluid. The main factor affecting the heat exchanger's performance is the contact area between the refrigerant and the heat exchanger. Therefore, to improve the heat exchanger's performance, it is usually achieved by increasing the design of the contact area between the refrigerant and the heat exchanger.

[0003] A novel microchannel flat tube heat exchanger with internal teeth exists in the related technology. It includes two parallel and vertically arranged manifolds, with several parallel and laterally arranged heat exchange flat tubes between the manifolds. Heat dissipation fins are provided between adjacent heat exchange flat tubes, contacting the tubes. The key feature is that the heat exchange flat tubes are flat tubes, and the tube body has a heat exchange channel group arranged along its width direction. The heat exchange channel group includes two side heat exchange channels located on opposite sides of the tube body along its width direction and arranged corresponding to each other. The two side heat exchange channels have the same shape and size, and the two side channels... Several intermediate heat exchange channels are arranged at equal intervals between the heat exchange channels. Each intermediate heat exchange channel is a rectangular structure with the same shape and size. Both ends of the side heat exchange channels and intermediate heat exchange channels are connected to the manifold. The inner side of the side heat exchange channels and intermediate heat exchange channels near the outer circumferential surface of the flat tube body is provided with heat exchange internal teeth. The remaining inner side of the side heat exchange channels and intermediate heat exchange channels without heat exchange internal teeth is straight. The heat exchange internal teeth of the side heat exchange channels near the upper and lower surfaces of the flat tube body and the heat exchange internal teeth of the intermediate heat exchange channels near the upper and lower surfaces of the flat tube body are arranged correspondingly to each other.

[0004] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art:

[0005] Although the heat exchange area of ​​the refrigerant is increased by setting the internal teeth of the heat exchanger, the pressure drop of the heat exchanger is also increased. The pressure loss of the refrigerant in the flow channel is large, the surface temperature of the heat exchanger rises, and the heat exchange temperature difference decreases. Therefore, even if the heat exchange area is increased, the heat exchange effect is relatively poor.

[0006] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0007] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0008] This disclosure provides a control method and device for an air conditioner microchannel heat exchanger, and an air conditioner, to reduce the pressure loss of the refrigerant in the microchannel heat exchanger, so that the pressure loss of the refrigerant matches the heat exchange area through which it flows, thereby improving the heat exchange performance.

[0009] In some embodiments, a control method for an air conditioning microchannel heat exchanger includes:

[0010] Obtain the superheat of the first and second flow channels;

[0011] Determine the superheat range of the first and second flow channels respectively;

[0012] The refrigerant flow rate of the first and second flow channels is controlled according to the control strategies corresponding to the superheat ranges of the first and second flow channels, respectively.

[0013] Optionally, determining the superheat range of the first flow channel and the second flow channel respectively includes: determining that the superheat of the first flow channel is in any one of the first superheat range, the second superheat range, and the third superheat range; determining that the superheat of the second flow channel is in any one of the fourth superheat range, the fifth superheat range, and the sixth superheat range; wherein, the maximum value in the first superheat range is less than the minimum value in the second superheat range, the maximum value in the second superheat range is less than the minimum value in the third superheat range; the maximum value in the fourth superheat range is less than the minimum value in the fifth superheat range, and the maximum value in the fifth superheat range is less than the minimum value in the sixth superheat range.

[0014] Optionally, the refrigerant flow rate of the first flow channel can be controlled according to the control strategy corresponding to the superheat range in which the first flow channel is located, including: reducing the refrigerant flow rate of the first flow channel when the superheat of the first flow channel is in the first superheat range; keeping the refrigerant flow rate of the first flow channel unchanged when the superheat of the first flow channel is in the second superheat range; and increasing the refrigerant flow rate of the first flow channel when the superheat of the first flow channel is in the third superheat range.

[0015] Optionally, the refrigerant flow rate of the second flow channel can be controlled according to the control strategy corresponding to the superheat range in which the second flow channel is located, including: reducing the refrigerant flow rate of the second flow channel when the superheat range of the second flow channel is in the fourth superheat range; keeping the refrigerant flow rate of the second flow channel unchanged when the superheat range of the second flow channel is in the fifth superheat range; and increasing the refrigerant flow rate of the second flow channel when the superheat range of the second flow channel is in the sixth superheat range.

[0016] Optionally, obtaining the superheat of the first flow channel and the second flow channel includes: obtaining a first temperature and a first pressure at the outlet end of the first flow channel, and determining the superheat of the first flow channel based on the first temperature and the first pressure; obtaining a second temperature and a second pressure at the outlet end of the second flow channel, and determining the superheat of the second flow channel based on the second temperature and the second pressure.

[0017] Optionally, the control method for the air conditioning microchannel heat exchanger further includes: periodically closing and opening the inlet end of the first flow channel.

[0018] Optionally, controlling the inlet end of the first flow channel to periodically close and open includes: controlling the inlet end of the first flow channel to close, and obtaining the closing duration of the inlet end of the first flow channel, and controlling the inlet end to open again after the closing duration reaches a first set duration; obtaining the opening duration of the inlet end of the first flow channel, and controlling the inlet end to close again after the opening duration reaches a second set duration.

[0019] Optionally, during a first set duration of closing the inlet end of the first flow channel, the method further includes controlling the air conditioning compressor to operate at a reduced frequency.

[0020] In some embodiments, the control device for an air conditioning microchannel heat exchanger includes: a processor and a memory storing program instructions, the processor being configured to execute the control method for an air conditioning microchannel heat exchanger described above when the program instructions are executed.

[0021] In some embodiments, an air conditioner includes: a microchannel heat exchanger and a control device for the air conditioner microchannel heat exchanger according to the above embodiments. The microchannel heat exchanger includes a first flow channel and a second flow channel. The inner wall of the first flow channel is provided with heat exchange internal teeth, and the inner wall of the second flow channel is smoothly disposed. The control device for the air conditioner microchannel heat exchanger according to the above embodiments is installed on the housing of the air conditioner.

[0022] The control method and apparatus for air conditioning microchannel heat exchangers and the air conditioner provided in this disclosure can achieve the following technical effects:

[0023] By incorporating a first and second flow channel in a microchannel heat exchanger, the first flow channel features internal heat exchange teeth on its inner wall, increasing the heat exchange area for the refrigerant flowing through it. The second flow channel has a smooth inner wall, resulting in a relatively smaller pressure drop for the refrigerant flowing through it. By acquiring the superheat of the first and second flow channels and implementing a control strategy corresponding to their respective superheat ranges, the refrigerant flow rate in both channels can be precisely controlled. This allows for more refined control of the refrigerant flow rate in the first and second flow channels, thereby reducing the refrigerant pressure drop in the microchannel heat exchanger and ensuring that the pressure drop matches the heat exchange area, thus improving heat exchange performance.

[0024] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0025] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein:

[0026] Figure 1 This is a schematic diagram of a control method for an air conditioning microchannel heat exchanger provided in an embodiment of this disclosure;

[0027] Figure 2 This is a schematic diagram of another control method for an air conditioning microchannel heat exchanger provided in an embodiment of this disclosure;

[0028] Figure 3 This is a schematic diagram of another control method for an air conditioning microchannel heat exchanger provided in an embodiment of this disclosure;

[0029] Figure 4 This is a schematic diagram of a control device for an air conditioning microchannel heat exchanger provided in an embodiment of this disclosure;

[0030] Figure 5 This is a schematic diagram of the structure of a microchannel heat exchanger provided in an embodiment of this disclosure;

[0031] Figure 6 This is a schematic diagram of the structure of the inner walls of the first and second flow channels provided in the embodiments of this disclosure;

[0032] Figure 7 This is a schematic diagram of the structure of the housing provided in an embodiment of this disclosure;

[0033] Figure 8 This is a schematic diagram of a refrigeration system provided in an embodiment of this disclosure;

[0034] Figure 9This is a schematic diagram of another microchannel heat exchanger provided in an embodiment of this disclosure.

[0035] Figure label:

[0036] 100. Processor; 101. Memory; 102. Communication Interface; 103. Bus; 200. Control device for air conditioning microchannel heat exchanger; 300. Microchannel heat exchanger; 301. Heat exchanger internal teeth; 310. First flow channel; 311. First connecting pipe; 312. Third connecting pipe; 313. First electronic expansion valve; 314. First 315. Third manifold; 320. Second flow channel; 321. Second connecting pipe; 322. Fourth connecting pipe; 323. Second electronic expansion valve; 324. Second manifold; 325. Fourth manifold; 330. Third flow channel; 331. Fifth connecting pipe; 332. Sixth connecting pipe; 333. Fifth manifold; 334. Sixth manifold; 335. Third electronic expansion valve; 400. Housing; 500. Compressor; 600. Condenser; 700. Throttling device. Detailed Implementation

[0037] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0038] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0039] Unless otherwise stated, the term "multiple" means two or more.

[0040] The term "correspondence" can refer to an association or binding relationship. The correspondence between A and B means that there is an association or binding relationship between A and B.

[0041] In this embodiment of the disclosure, smart home appliances refer to home appliances formed by introducing microprocessors, sensor technology and network communication technology into home appliances. They have the characteristics of intelligent control, intelligent sensing and intelligent application. The operation of smart home appliances often relies on the application and processing of modern technologies such as the Internet of Things, the Internet and electronic chips. For example, smart home appliances can be connected to electronic devices to enable users to remotely control and manage smart home appliances.

[0042] In the disclosed embodiments, the terminal device refers to an electronic device with wireless connectivity. The terminal device can communicate with the aforementioned smart home appliances via the internet, or directly via Bluetooth, Wi-Fi, or other methods. In some embodiments, the terminal device may be, for example, a mobile device, a computer, or an in-vehicle device built into a hovercraft, or any combination thereof. Mobile devices may include, for example, mobile phones, smart home devices, wearable devices, smart mobile devices, virtual reality devices, or any combination thereof. Wearable devices may include, for example, smartwatches, smart bracelets, pedometers, etc.

[0043] Combination Figure 1 As shown, in some embodiments, a control method for an air conditioning microchannel heat exchanger includes:

[0044] S01, the processor obtains the overheating of the first and second flow channels;

[0045] S02, the processor determines the superheat range of the first flow channel and the second flow channel respectively;

[0046] S03, the processor controls the refrigerant flow rate of the first and second flow channels according to the control strategy corresponding to the superheat range of the first and second flow channels respectively.

[0047] The control method for an air conditioning microchannel heat exchanger provided in this disclosure involves setting a first flow channel and a second flow channel in the microchannel heat exchanger. The inner wall of the first flow channel has heat exchange internal teeth, which increases the heat exchange area of ​​the refrigerant flowing through it. The inner wall of the second flow channel is smooth, resulting in a relatively small pressure drop of the refrigerant flowing through it. By acquiring the superheat of the first and second flow channels and using a control strategy corresponding to the superheat range of the first and second flow channels, the flow rate of the refrigerant flowing through the first and second flow channels is controlled. This allows for more precise control of the refrigerant flow rate in the first and second flow channels, thereby reducing the pressure drop of the refrigerant in the microchannel heat exchanger and matching the pressure drop of the refrigerant with the heat exchange area, thus improving heat exchange performance.

[0048] Optionally, the processor determines the superheat range in which the first flow channel and the second flow channel are located, including: the processor determining that the superheat of the first flow channel is in any one of the first superheat range, the second superheat range, and the third superheat range; the processor determining that the superheat of the second flow channel is in any one of the fourth superheat range, the fifth superheat range, and the sixth superheat range; wherein, the maximum value in the first superheat range is less than the minimum value in the second superheat range, the maximum value in the second superheat range is less than the minimum value in the third superheat range; the maximum value in the fourth superheat range is less than the minimum value in the fifth superheat range, and the maximum value in the fifth superheat range is less than the minimum value in the sixth superheat range. Thus, six superheat ranges are set up, one for the first superheat range, one for the second, one for the third, one for the fourth, one for the fifth, and one for the sixth. The superheat of the first flow channel corresponds to these ranges, and the superheat of the second flow channel corresponds to these ranges. Each superheat range corresponds to a specific control strategy. The refrigerant flow rate of the first and second flow channels is controlled according to the control strategy corresponding to the superheat range in which they are located. This allows for more precise control of the refrigerant flow rate in the first and second flow channels, ensuring that the pressure loss of the refrigerant matches the heat exchange area it flows through, thereby reducing pressure loss and improving heat exchange performance.

[0049] In one embodiment, the processor controls the refrigerant flow rate of the first flow channel according to a control strategy corresponding to the superheat range of the first flow channel. This includes: reducing the refrigerant flow rate of the first flow channel when the superheat of the first flow channel is in a first superheat range; maintaining the refrigerant flow rate of the first flow channel unchanged when the superheat of the first flow channel is in a second superheat range; and increasing the refrigerant flow rate of the first flow channel when the superheat of the first flow channel is in a third superheat range. Thus, when the superheat of the first flow channel is in a relatively small first superheat range, the superheat of the first flow channel is low, which may result in excessive refrigerant evaporation. Therefore, reducing the refrigerant flow rate of the first flow channel allows for sufficient evaporation of the refrigerant, increasing the superheat of the first flow channel and thereby improving heat exchange performance. When the superheat of the first flow channel is in a moderate second superheat range, the superheat of the first flow channel is suitable, and the heat exchange performance is good, eliminating the need to adjust the refrigerant flow rate of the first flow channel. When the superheat of the first flow channel is in the relatively high third superheat range, the superheat of the first flow channel is large, the refrigerant in the first flow channel evaporates excessively, the amount of liquid refrigerant remaining in the first flow channel is small, and the heat exchange area of ​​the first flow channel is not fully utilized. Therefore, increasing the refrigerant flow rate of the first flow channel and increasing the amount of liquid refrigerant in the first flow channel can improve the heat exchange performance.

[0050] Specifically, the first superheat range is less than 1°C; the second superheat range is greater than or equal to 1°C and less than or equal to 2°C; and the third superheat range is greater than 2°C. Thus, when the superheat of the first flow channel is less than 1°C, there is too much refrigerant in the first flow channel, resulting in insufficient evaporation and poor heat exchange performance. When the superheat of the first flow channel is greater than or equal to 1°C and less than or equal to 2°C, the heat exchange performance of the first flow channel is better, and the refrigerant flow rate in the first flow channel can be kept constant. When the superheat of the first flow channel is greater than 2°C, there is too little liquid refrigerant in the first flow channel, resulting in poor utilization of the heat exchange area; therefore, the refrigerant flow rate in the first flow channel should be increased. Because the inner wall of the first flow channel has internal heat exchange teeth, the heat exchange efficiency is relatively higher, but the pressure loss of the refrigerant is also higher, resulting in a relatively smaller amount of refrigerant required to achieve the same heat exchange capacity in the first flow channel. Therefore, by keeping the refrigerant flow rate constant within the second superheat range, the refrigerant flow rate in the first flow channel can be appropriately reduced when the same heat exchange capacity is achieved in the first flow channel, thereby reducing pressure loss and also reducing the refrigerant charge of the refrigeration system, thus lowering costs.

[0051] Specifically, the processor reduces the refrigerant flow rate in the first channel by controlling the opening degree of the first electronic expansion valve corresponding to the first channel to decrease; the processor increases the refrigerant flow rate in the first channel by controlling the opening degree of the first electronic expansion valve corresponding to the first channel to increase.

[0052] In another embodiment, the processor controls the refrigerant flow rate of the second flow channel according to a control strategy corresponding to the superheat range of the second flow channel. This includes: reducing the refrigerant flow rate of the second flow channel when the superheat of the second flow channel is in the fourth superheat range; maintaining the refrigerant flow rate of the second flow channel unchanged when the superheat of the second flow channel is in the fifth superheat range; and increasing the refrigerant flow rate of the second flow channel when the superheat of the second flow channel is in the sixth superheat range. Thus, when the superheat of the second flow channel is in the relatively small fourth superheat range, the superheat of the second flow channel is low, which may result in insufficient evaporation of the refrigerant. Therefore, reducing the refrigerant flow rate of the second flow channel allows for sufficient evaporation of the refrigerant, increasing the superheat of the second flow channel and thus improving heat exchange performance. When the superheat of the second flow channel is in the moderate fifth superheat range, the superheat of the second flow channel is suitable, and the heat exchange performance is good, so there is no need to adjust the refrigerant flow rate of the second flow channel. When the superheat of the second flow channel is in the relatively high sixth superheat range, the superheat of the second flow channel is large, the refrigerant in the second flow channel evaporates excessively, the amount of liquid refrigerant remaining in the second flow channel is small, and the heat exchange area of ​​the second flow channel is not fully utilized. Therefore, increasing the refrigerant flow rate of the second flow channel and increasing the amount of liquid refrigerant in the second flow channel can improve the heat exchange performance.

[0053] Specifically, the fourth superheat range is less than 0.1℃; the fifth superheat range is greater than or equal to 0.1℃ and less than or equal to 1℃; and the sixth superheat range is greater than 1℃. Thus, when the superheat of the second channel is less than 0.1℃, there is too much refrigerant in the second channel, resulting in insufficient evaporation and poor heat exchange performance. When the superheat of the second channel is greater than or equal to 0.1℃ and less than or equal to 1℃, the heat exchange performance of the second channel is better, and the refrigerant flow rate in the second channel should be kept constant. When the superheat of the second channel is greater than 1℃, there is too little liquid refrigerant in the second channel, resulting in poor utilization of the heat exchange area; therefore, the refrigerant flow rate in the second channel should be increased. To fully utilize the heat exchange efficiency of the second channel, the optimal outlet superheat when the refrigerant at the outlet of the second channel is in a gaseous state is 0℃. However, when the superheat is 0℃, the refrigerant at the outlet may be in a gas-liquid two-phase state. Therefore, when the superheat of the second flow channel is set in the fifth superheat range, the refrigerant flow rate of the second flow channel is kept constant to ensure that the refrigerant at the outlet of the second flow channel is in a gaseous state. This ensures both the heat exchange capacity of the second flow channel and prevents the compressor from drawing in liquid refrigerant at the return gas end.

[0054] Specifically, the processor reduces the refrigerant flow rate in the second channel by controlling the opening degree of the second electronic expansion valve corresponding to the second channel to decrease; the processor increases the refrigerant flow rate in the second channel by controlling the opening degree of the second electronic expansion valve corresponding to the second channel to increase.

[0055] In one embodiment, the processor obtains the superheat of the first and second flow channels by: obtaining a first temperature and a first pressure at the outlet of the first flow channel, and determining the superheat of the first flow channel based on the first temperature and the first pressure; and obtaining a second temperature and a second pressure at the outlet of the second flow channel, and determining the superheat of the second flow channel based on the second temperature and the second pressure. This improves the accuracy of the superheat of the first and second flow channels by obtaining the first temperature and the first pressure at the outlet of the first flow channel, and by obtaining the second temperature and the second pressure at the outlet of the second flow channel, thereby enabling more precise control of the refrigerant flow rates in the first and second flow channels.

[0056] Specifically, the processor acquires the first temperature and first pressure at the outlet of the first flow channel by acquiring the first temperature detected by the temperature sensor and the first pressure detected by the pressure sensor at the outlet of the first flow channel.

[0057] Specifically, the processor acquires the second temperature and the second pressure at the outlet of the second flow channel by acquiring the second temperature detected by the temperature sensor and the second pressure detected by the pressure sensor at the outlet of the second flow channel.

[0058] Combination Figure 2 As shown, in another embodiment, a control method for an air conditioning microchannel heat exchanger includes:

[0059] S01, the processor obtains the overheating of the first and second flow channels;

[0060] S02, the processor determines the superheat range of the first flow channel and the second flow channel respectively;

[0061] S03, the processor controls the refrigerant flow rate of the first and second flow channels according to the control strategy corresponding to the superheat range of the first and second flow channels respectively;

[0062] S04, the processor controls the inlet end of the first flow channel to periodically close and open.

[0063] The control method for an air conditioning microchannel heat exchanger provided in this embodiment addresses the issue of a large pressure drop in the gaseous refrigerant flowing through the first channel (which has internal heat exchange teeth) and the second channel (which has a smooth inner wall). This pressure drop negatively impacts the heat exchange efficiency of the microchannel heat exchanger. Therefore, it is necessary to control the flow of gaseous refrigerant through the second channel and liquid refrigerant through the first channel. Furthermore, since the gaseous refrigerant has a relatively high velocity, the inlet of the first channel is periodically closed and opened to allow the faster-flowing gaseous refrigerant to enter the second channel first. This increases the flow rate of gaseous refrigerant in the second channel, further reducing the pressure drop and ensuring the pressure drop matches the heat exchange area, thus improving heat exchange performance.

[0064] Optionally, the processor controls the inlet of the first flow channel to periodically close and open, including: the processor controls the inlet of the first flow channel to close, and obtains the closing duration of the inlet of the first flow channel, and controls the inlet to open again after the closing duration reaches a first set duration; the processor obtains the opening duration of the inlet of the first flow channel, and controls the inlet to close again after the opening duration reaches a second set duration. In this way, the processor first controls the inlet of the first flow channel to close, then controls the inlet to open again after the closing duration reaches the first set duration, and then controls the inlet to close again after the opening duration reaches the second set duration, causing the inlet of the first flow channel to form a periodic opening and closing. The relatively fast-flowing gaseous refrigerant flows first into the second flow channel for heat exchange. This increases the flow rate of gaseous refrigerant in the second flow channel and increases the flow rate of liquid refrigerant in the first flow channel, thereby further reducing the pressure loss of the refrigerant in the microchannel heat exchanger, matching the pressure loss of the refrigerant with the heat exchange area it flows through, and improving heat exchange performance.

[0065] Specifically, the processor controls the inlet end of the first flow channel to close, obtains the closing duration of the inlet end of the first flow channel, and controls the inlet end to open again after the closing duration reaches a first set duration; the processor obtains the opening duration of the inlet end of the first flow channel, and controls the inlet end to close again after the opening duration reaches a second set duration, including: the processor controls the first electronic expansion valve at the inlet end of the first flow channel to close for a first set duration and then open again, and then close again after opening for a second set duration.

[0066] For example, the first set duration is 10 seconds, and the second set duration is 10 minutes. Since the first flow channel is also the main heat exchange channel of the microchannel heat exchanger, it undertakes the main heat exchange work. Therefore, the duration of its closure should not be too long, otherwise it will affect the heat exchange performance of the microchannel heat exchanger and increase the pressure within the system. Therefore, setting the closure duration of the first flow channel to 10 seconds and the opening duration to 10 minutes can both increase the flow rate of the gaseous refrigerant in the second flow channel and ensure the heat exchange performance of the microchannel heat exchanger.

[0067] Optionally, during a first set time period during which the processor controls the inlet of the first flow channel to close, the processor further includes controlling the air conditioning compressor to operate at a reduced frequency. In this way, when the processor controls the inlet of the first flow channel to close, the microchannel heat exchanger only circulates refrigerant through the second flow channel, causing the system pressure to rise. Therefore, controlling the compressor to reduce its frequency lowers the system pressure, ensuring stable operation of the refrigeration system.

[0068] Specifically, the processor controls the air conditioner compressor to operate at a reduced frequency, including: the processor controls the air conditioner compressor to operate at a frequency lower than a first set frequency.

[0069] Specifically, when the inlet of the first channel is opened, the processor controls the compressor's operating frequency to increase to a second set frequency. Thus, when the inlet of the first channel is open, the refrigerant flow rate in the microchannel heat exchanger increases, thereby controlling the compressor to operate at a higher frequency and ensuring the heat exchange capacity of the microchannel heat exchanger.

[0070] Combination Figure 3 As shown, in another embodiment, a control method for an air conditioning microchannel heat exchanger includes:

[0071] S01, the processor obtains the overheating of the first and second flow channels;

[0072] S02, the processor determines the superheat range of the first flow channel and the second flow channel respectively;

[0073] S03, the processor controls the refrigerant flow rate of the first and second flow channels according to the control strategy corresponding to the superheat range of the first and second flow channels respectively;

[0074] S05, when the processor determines that the refrigerant in the air conditioning system is a non-azeotropic refrigerant, it controls the inlet end of the first flow channel to close and the inlet end of the third flow channel to open.

[0075] The control method for a microchannel heat exchanger in an air conditioner provided in this embodiment addresses the issue of a high gas content in the refrigerant system. When a non-azeotropic refrigerant is charged into the system, the components with lower boiling points evaporate into gas first due to their different boiling points. When the refrigerant flows through the first channel, whose inner wall is entirely equipped with heat exchange teeth, the gaseous refrigerant content is high, increasing pressure loss and reducing the heat exchange efficiency of the first channel. Therefore, when the processor determines that a non-azeotropic refrigerant is being charged into the system, it closes the first channel and opens the third channel. Since the first half of the inner wall of the third channel has heat exchange teeth while the second half is smooth, the higher gas content in the second half reduces the resistance of the third channel, thereby decreasing pressure loss and improving heat exchange efficiency.

[0076] Optionally, while controlling the inlet of the first flow channel to close and the inlet of the third flow channel to open, the processor acquires the superheat of the third flow channel; determines the superheat range of the second and third flow channels respectively; and controls the refrigerant flow of the second and third flow channels according to the control strategy corresponding to the superheat range of the second and third flow channels respectively.

[0077] Optionally, the third flow channel corresponds to the seventh superheat interval, the eighth superheat interval, and the ninth superheat interval. The processor determines which of the seven, eight, and ninth superheat intervals the superheat interval of the third flow channel is located in; wherein, the maximum value in the seventh superheat interval is less than the minimum value in the eighth superheat interval, and the maximum value in the eighth superheat interval is less than the minimum value in the ninth superheat interval.

[0078] Optionally, when the superheat range of the third flow channel is in the seventh superheat range, the processor reduces the refrigerant flow rate of the third flow channel; when the superheat range of the third flow channel is in the eighth superheat range, the processor keeps the refrigerant flow rate of the third flow channel unchanged; when the superheat range of the third flow channel is in the ninth superheat range, the processor increases the refrigerant flow rate of the third flow channel.

[0079] Optionally, when the first flow channel is closed and the third flow channel is open, the processor controls the inlet of the third flow channel to periodically open and close. Since the first half of the inner wall of the third flow channel has heat exchange internal teeth and the second half is a smooth inner wall, while the second flow channel has a smooth inner wall, a large flow of gaseous refrigerant in the third flow channel would result in a significant pressure drop, affecting the heat exchange efficiency of the microchannel heat exchanger. Therefore, it is necessary to control the flow of gaseous refrigerant primarily through the second flow channel and liquid refrigerant primarily through the third flow channel. Furthermore, the gaseous refrigerant has a relatively high velocity; therefore, controlling the periodic opening and closing of the inlet of the third flow channel allows the relatively faster-flowing gaseous refrigerant to flow first into the second flow channel, increasing the flow rate of gaseous refrigerant in the second flow channel. This further reduces the pressure drop of the refrigerant in the microchannel heat exchanger, matching the pressure drop with the heat exchange area, and improving heat exchange performance.

[0080] Combination Figure 4 As shown, this disclosure provides a control device 200 for an air conditioning microchannel heat exchanger, including a processor 100 and a memory 101. Optionally, the device may further include a communication interface 102 and a bus 103. The processor 100, communication interface 102, and memory 101 can communicate with each other via the bus 103. The communication interface 102 can be used for information transmission. The processor 100 can call logical instructions in the memory 101 to execute the control method for the air conditioning microchannel heat exchanger described in the above embodiment.

[0081] Furthermore, the logic instructions in the aforementioned memory 101 can be implemented as software functional units and, when sold or used as independent products, can be stored in a computer-readable storage medium.

[0082] The memory 101, as a computer-readable storage medium, can be used to store software programs and computer-executable programs, such as program instructions / modules corresponding to the methods in the embodiments of this disclosure. The processor 100 executes functional applications and data processing by running the program instructions / modules stored in the memory 101, thereby implementing the control method for the air conditioning microchannel heat exchanger in the above embodiments.

[0083] The memory 101 may include a program storage area and a data storage area. The program storage area may store the operating system and applications required for at least one function; the data storage area may store data created based on the use of the terminal device. Furthermore, the memory 101 may include high-speed random access memory and may also include non-volatile memory.

[0084] Combination Figure 5-9As shown, this disclosure provides an air conditioner, including a microchannel heat exchanger 300 and a control device 200 for the air conditioner microchannel heat exchanger described in the above embodiment. The microchannel heat exchanger 300 includes a first flow channel 310 and a second flow channel 320; wherein, the inner wall of the first flow channel 310 is provided with heat exchange internal teeth 301, and the inner wall of the second flow channel 320 is smoothly disposed; the control device 200 for the air conditioner microchannel heat exchanger described in the above embodiment is mounted on the housing 400 of the air conditioner. The mounting relationship described herein is not limited to placement inside the product, but also includes mounting connections with other components of the product, including but not limited to physical connections, electrical connections, or signal transmission connections. Those skilled in the art will understand that the control device 200 for the air conditioner microchannel heat exchanger can be adapted to feasible product bodies to achieve other feasible embodiments.

[0085] Optionally, the length of the first flow channel 310 is less than the length of the second flow channel 320. In this way, since the inner wall of the first flow channel 310 is provided with heat exchange internal teeth 301, while the inner wall of the second flow channel 320 is smooth, and the refrigerant evaporates and absorbs heat, changing from a liquid to a gaseous state, when flowing through the first and second flow channels 310 and 320 respectively, a large pressure drop will occur when the gaseous refrigerant flows through the first flow channel 310 with a larger flow path. Therefore, setting the length of the first flow channel 310 to be less than the length of the second flow channel 320 increases the heat exchange area within the first flow channel 310 while shortening the refrigerant flow path and reducing the refrigerant pressure drop.

[0086] Optionally, the microchannel heat exchanger 300 further includes: a first connecting pipe 311, a second connecting pipe 321, a third connecting pipe 312, and a fourth connecting pipe 322. The first connecting pipe 311 is connected to the input end of the first flow channel 310, the second connecting pipe 321 is connected to the input end of the second flow channel 320, the third connecting pipe 312 is connected to the output end of the first flow channel 310, and the fourth connecting pipe 322 is connected to the output end of the second flow channel 320. A first electronic expansion valve 313 is connected to the first connecting pipe 311, and a second electronic expansion valve 323 is connected to the second connecting pipe 321. Thus, by connecting the first connecting pipe 311 and the third connecting pipe 312 to the input and output ends of the first flow channel 310 respectively, the refrigerant flows into the first flow channel 310 through the first connecting pipe 311, evaporates and vaporizes, and then flows out through the third connecting pipe 312. The flow rate of the refrigerant in the first flow channel 310 is adjusted by regulating the opening of the first electronic expansion valve 313 in the first connecting pipe 311. By setting the second connecting pipe 321 and the fourth connecting pipe 322 to connect the input end and the output end of the second flow channel 320 respectively, the refrigerant flows into the second flow channel 320 through the second connecting pipe 321, evaporates and vaporizes, and then flows out through the fourth connecting pipe 322. The flow rate of the refrigerant in the second flow channel 320 is adjusted by adjusting the opening of the second electronic expansion valve 323 in the second connecting pipe 321.

[0087] Optionally, pressure sensors and temperature sensors are provided on both the third connecting pipe 312 and the fourth connecting pipe 322. This allows for real-time monitoring of the refrigerant temperature flowing out of the third connecting pipe 312 and the pressure within the first flow channel 310, and the same applies to the refrigerant temperature flowing out of the fourth connecting pipe 322 and the pressure within the second flow channel 320. This facilitates accurate calculation of the superheat in both the first and second flow channels 310.

[0088] Optionally, multiple first flow channels 310 and multiple second flow channels 320 are provided, and the multiple first flow channels 310 and multiple second flow channels 320 are arranged alternately. The input ends of the multiple first flow channels 310 are all connected to the first connecting pipe 311, the output ends of the multiple first flow channels 310 are all connected to the third connecting pipe 312, the input ends of the multiple second flow channels 320 are all connected to the second connecting pipe 321, and the output ends of the multiple second flow channels 320 are all connected to the fourth connecting pipe 322. In this way, by setting multiple first flow channels 310 and multiple second flow channels 320 alternately, the refrigerant flow rate can be increased, thereby improving the heat exchange effect.

[0089] Optionally, the microchannel heat exchanger 300 further includes: a first manifold 314, a second manifold 324, a third manifold 315, and a fourth manifold 325. The input ends of multiple first flow channels 310 are all connected to the first manifold 314, the output end of the first connecting pipe 311 is also connected to the first manifold 314, the output ends of multiple first flow channels 310 are all connected to the third manifold 315, and the input end of the third connecting pipe 312 is also connected to the third manifold 315; the input ends of multiple second flow channels 320 are all connected to the second manifold 324, the output end of the second connecting pipe 321 is also connected to the second manifold 324, the output ends of multiple second flow channels 320 are all connected to the fourth manifold 325, and the input end of the fourth connecting pipe 322 is also connected to the fourth manifold 325. Thus, since multiple first flow channels 310 and second flow channels 320 are provided, to ensure that the refrigerant can be evenly distributed into multiple first flow channels 310 and second flow channels 320, and that the refrigerant evaporated in the first flow channels 310 and second flow channels 320 can be concentrated and collected into the third connecting pipe 312 and the fourth connecting pipe 322, a first manifold 314 and a third manifold 315 are provided in cooperation. The refrigerant flowing out of the first connecting pipe 311 is evenly distributed into multiple first flow channels 310 through the first manifold 314, and the refrigerant evaporated in multiple first flow channels 310 is concentrated and collected into the third manifold 315 and flows into the third connecting pipe 312. A second manifold 324 and a fourth manifold 325 are provided in cooperation. The refrigerant flowing out of the second connecting pipe 321 is evenly distributed into multiple second flow channels 320 through the second manifold 324, and the refrigerant evaporated in multiple second flow channels 320 is collected and flows out into the fourth manifold 325, and then flows into the fourth connecting pipe 322.

[0090] Understandably, the air conditioner also includes a compressor 500, a condenser 600, and a throttling device 700. The exhaust pipe and return pipe of the compressor 500 are connected to the microchannel heat exchanger 300 and the condenser 600 through a four-way valve. The throttling device 700 is connected between the microchannel heat exchanger 300 and the condenser 600. The compressor 500, the condenser 600, the microchannel heat exchanger 300, and the throttling device 700 together constitute the refrigeration system of the air conditioner, which will not be elaborated here.

[0091] Optionally, the microchannel heat exchanger 300 further includes a third flow channel 330. A portion of the inner wall of the third flow channel 330 is smooth, while the remaining portion has heat exchange internal teeth 301. The smooth inner wall portion of the third flow channel 330 is located near its output end, while the portion with the heat exchange internal teeth 301 is located near its input end. Thus, when a non-azeotropic refrigerant is charged into the refrigeration system, components with lower boiling points will evaporate into a gaseous state first as they flow through the microchannel heat exchanger 300. As the refrigerant flows through the first flow channel 310, a significant pressure drop occurs in the latter half of the first flow channel 310, affecting the heat exchange effect. Therefore, by providing the third flow channel 330, when the refrigerant is a non-azeotropic refrigerant, the refrigerant is controlled to flow to both the second flow channel 320 and the third flow channel 330, further reducing the pressure loss of the refrigerant at high dryness levels and improving the heat exchange effect.

[0092] Optionally, the microchannel heat exchanger 300 further includes: a fifth connecting pipe 331, a sixth connecting pipe 332, a fifth manifold 333, and a sixth manifold 334. Multiple third flow channels 330 are provided, and the inlet of each of the multiple third flow channels 330 is connected to the fifth manifold 333, and the outlet of each of the multiple third flow channels 330 is connected to the sixth manifold 334. The outlet of the fifth connecting pipe 331 is also connected to the fifth manifold 333, and the inlet of the sixth connecting pipe 332 is also connected to the sixth manifold 334. A third electronic expansion valve 335 is connected to the fifth connecting pipe 331. In this way, the refrigerant flows from the fifth connecting pipe 331 to the fifth manifold 333, and then is evenly distributed through the fifth manifold 333 into the multiple third flow channels 330. The refrigerant evaporated and vaporized in the multiple third flow channels 330 converges and flows into the sixth connecting pipe 332, and then from the sixth connecting pipe 332 to the sixth manifold 334. The refrigerant flow rate of the third flow channel 330 is adjusted by the third electronic expansion valve 335 installed in the fifth connecting pipe 331.

[0093] Understandably, the first connecting pipe 311, the second connecting pipe 321, and the fifth connecting pipe 331 of the microchannel heat exchanger 300 are all inlet connecting pipes, while the third connecting pipe 312, the fourth connecting pipe 322, and the sixth connecting pipe 332 are all outlet connecting pipes. The refrigerant can flow in from the first connecting pipe 311 and the second connecting pipe 321, or the second connecting pipe 321 and the fifth connecting pipe 331, according to the heat exchange requirements, and flow out from the third connecting pipe 312 and the fourth connecting pipe 322, or the third connecting pipe 312 and the sixth connecting pipe 332 after heat exchange.

[0094] This disclosure provides a computer-readable storage medium storing computer-executable instructions configured to execute the above-described control method for an air conditioning microchannel heat exchanger.

[0095] The aforementioned computer-readable storage medium may be a transient computer-readable storage medium or a non-transitory computer-readable storage medium.

[0096] The technical solutions of this disclosure can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes one or more instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute all or part of the steps of the method described in this disclosure. The aforementioned storage medium can be a non-transitory storage medium, including: a USB flash drive, a portable hard drive, a read-only memory (ROM), a random access memory (RAM), a magnetic disk, or an optical disk, and other media capable of storing program code; it can also be a transient storage medium.

[0097] The foregoing description and accompanying drawings fully illustrate embodiments of this disclosure to enable those skilled in the art to practice them. Other embodiments may include structural, logical, electrical, procedural, and other changes. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included in or replace parts and features of other embodiments. Moreover, the terminology used in this application is for describing embodiments only and is not intended to limit the claims. As used in the description of embodiments and claims, the singular forms “a,” “an,” and “the” are intended to equally include the plural forms unless the context clearly indicates otherwise. Similarly, the term “and / or” as used in this application means including one or more of the associated listed items and all possible combinations thereof. Additionally, when used in this application, the term "comprise" and its variations "comprises" and / or "comprising" refer to the presence of stated features, integrals, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components, and / or groups thereof. Without further limitations, an element defined by the phrase "comprises a..." does not exclude the presence of other identical elements in the process, method, or apparatus that includes said element. In this document, each embodiment may focus on the differences from other embodiments, and similar or identical parts between embodiments can be referred to mutually. For methods, products, etc., disclosed in the embodiments, if they correspond to the method section disclosed in the embodiments, the relevant parts can be referred to the description of the method section.

[0098] Those skilled in the art will recognize that the units and algorithm steps of the various examples described in conjunction with the embodiments disclosed herein can be implemented in electronic hardware, or a combination of computer software and electronic hardware. Whether these functions are implemented in hardware or software depends on the specific application and design constraints of the technical solution. Those skilled in the art can use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of the embodiments of this disclosure. Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the specific working processes of the systems, devices, and units described above can be referred to the corresponding processes in the foregoing method embodiments, and will not be repeated here.

[0099] The methods and products (including but not limited to devices and equipment) disclosed in the embodiments herein can be implemented in other ways. For example, the device embodiments described above are merely illustrative. For instance, the division of units may be merely a logical functional division, and in actual implementation, there may be other division methods. For example, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. In addition, the coupling or direct coupling or communication connection between the shown or discussed units may be through some interfaces, and the indirect coupling or communication connection between devices or units may be electrical, mechanical, or other forms. The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units, that is, they may be located in one place or distributed across multiple network units. Some or all of the units may be selected to implement this embodiment according to actual needs. Furthermore, the functional units in the embodiments of this disclosure may be integrated into one processing unit, or each unit may exist physically separately, or two or more units may be integrated into one unit.

[0100] The flowcharts and block diagrams in the accompanying drawings illustrate the architecture, functionality, and operation of possible implementations of systems, methods, and computer program products according to embodiments of this disclosure. In this regard, each block in a flowchart or block diagram may represent a module, segment, or portion of code containing one or more executable instructions for implementing a specified logical function. In some alternative implementations, the functions marked in the blocks may occur in a different order than that shown in the drawings. For example, two consecutive blocks may actually be executed substantially in parallel, and they may sometimes be executed in reverse order, depending on the functions involved. In the descriptions corresponding to the flowcharts and block diagrams in the accompanying drawings, the operations or steps corresponding to different blocks may also occur in a different order than disclosed in the description, and sometimes there is no specific order between different operations or steps. For example, two consecutive operations or steps may actually be executed substantially in parallel, and they may sometimes be executed in reverse order, depending on the functions involved. Each block in a block diagram and / or flowchart, and combinations of blocks in a block diagram and / or flowchart, can be implemented using a dedicated hardware-based system that performs the specified function or action, or using a combination of dedicated hardware and computer instructions.

Claims

1. A control method for an air conditioning microchannel heat exchanger, characterized in that, The microchannel heat exchanger includes a first flow channel and a second flow channel; wherein the inner wall of the first flow channel is provided with heat exchange internal teeth, and the inner wall of the second flow channel is smoothly arranged. Control methods include: Obtain the superheat of the first and second flow channels; Determine the superheat range of the first and second flow channels respectively; The refrigerant flow rate of the first and second flow channels is controlled according to the control strategy corresponding to the superheat range of the first and second flow channels, respectively.

2. The method according to claim 1, characterized in that, Determine the superheat range of the first and second flow channels, respectively, including: Determine that the superheat of the first flow channel falls within any one of the first superheat interval, the second superheat interval, and the third superheat interval; Determine that the superheat of the second flow channel falls within any one of the fourth, fifth, and sixth superheat intervals; Among them, the maximum value in the first superheat interval is less than the minimum value in the second superheat interval, the maximum value in the second superheat interval is less than the minimum value in the third superheat interval, the maximum value in the fourth superheat interval is less than the minimum value in the fifth superheat interval, and the maximum value in the fifth superheat interval is less than the minimum value in the sixth superheat interval.

3. The method according to claim 2, characterized in that, The refrigerant flow rate of the first flow channel is controlled according to the control strategy corresponding to the superheat range of the first flow channel, including: When the superheat of the first flow channel is in the first superheat range, reduce the refrigerant flow rate of the first flow channel; When the superheat of the first flow channel is in the second superheat range, the refrigerant flow rate of the first flow channel remains constant. When the superheat of the first flow channel is in the third superheat range, increase the refrigerant flow rate of the first flow channel.

4. The method according to claim 2, characterized in that, The refrigerant flow rate of the second flow channel is controlled according to the control strategy corresponding to the superheat range in which the second flow channel is located, including: When the superheat of the second flow channel is in the fourth superheat range, reduce the refrigerant flow rate of the second flow channel; When the superheat of the second flow channel is in the fifth superheat range, the refrigerant flow rate of the second flow channel remains constant. When the superheat of the second flow channel is in the sixth superheat range, increase the refrigerant flow rate of the second flow channel.

5. The method according to claim 1, characterized in that, Obtaining the superheat of the first and second flow channels includes: Obtain the first temperature and first pressure at the outlet end of the first flow channel, and determine the superheat of the first flow channel based on the first temperature and first pressure; Obtain the second temperature and second pressure at the outlet end of the second flow channel, and determine the superheat of the second flow channel based on the second temperature and second pressure.

6. The method according to any one of claims 1 to 5, characterized in that, Also includes: The inlet end of the first flow channel is controlled to periodically close and open.

7. The method according to claim 6, characterized in that, Controlling the periodic closing and opening of the inlet end of the first flow channel includes: The inlet end of the first flow channel is controlled to close, and the closing duration of the inlet end of the first flow channel is obtained. After the closing duration reaches the first set duration, the inlet end is controlled to open again. Obtain the opening duration of the inlet end of the first flow channel, and control the inlet end to close again after the opening duration reaches the second set duration.

8. The method according to claim 7, characterized in that, Within a first predetermined time period during which the inlet end of the first flow channel is closed, the following is also included: Control the air conditioner compressor to operate at a reduced frequency.

9. A control device for an air conditioning microchannel heat exchanger, comprising a processor and a memory storing program instructions, characterized in that, The processor is configured to execute, when running program instructions, the control method for an air conditioning microchannel heat exchanger as described in any one of claims 1 to 8.

10. An air conditioner, characterized in that, include: A microchannel heat exchanger includes a first flow channel and a second flow channel; wherein the inner wall of the first flow channel is provided with heat exchange internal teeth, and the inner wall of the second flow channel is smoothly arranged. The control device for an air conditioning microchannel heat exchanger as claimed in claim 9 is mounted on the housing of the air conditioner.

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