Method and apparatus for controlling a refrigeration system, refrigeration system, refrigeration appliance, computer readable storage medium

Abstract

The application relates to the refrigeration technical field, and discloses a method for controlling a refrigeration system, the refrigeration system comprising a high-temperature stage compressor, a low-temperature stage compressor and an intermediate heat exchanger; the method comprising: acquiring the space temperature of a storage space corresponding to the refrigeration system; in the case that the space temperature satisfies a second set temperature condition, controlling the refrigeration system to enter a normal cooling mode; wherein controlling the refrigeration system to enter the normal cooling mode comprises: controlling the high-temperature stage compressor to operate at a second high-temperature stage set rotating speed; and controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the temperature of the intermediate heat exchanger. The space temperature is adjusted in real time by controlling the rotating speeds of the high-temperature stage compressor and the low-temperature stage compressor, the number of start-stop times of the compressors is reduced, the problem of excessive refrigeration capacity is solved, and the energy consumption of the refrigeration system is reduced. The application also discloses a device for controlling a refrigeration system, a refrigeration system, a refrigeration equipment and a computer readable storage medium.

Description

Technical Field

[0001] This application relates to the field of refrigeration technology, such as a method and apparatus for controlling a refrigeration system, a refrigeration system, refrigeration equipment, and a computer-readable storage medium. Background Technology

[0002] In the biological or medical fields, different biological materials need to be stored in different temperature zones depending on their activity retention requirements. For example, cell tissues are typically preserved long-term in a frozen environment at -80°C.

[0003] Currently, cascade refrigeration equipment typically controls the high-temperature and low-temperature compressors to operate at fixed speeds. When the target temperature is reached, the compressors are shut down. When the temperature rises to a higher level, the compressors are restarted.

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

[0005] The compressors in this technology operate at a fixed speed, and the frequent starting of the compressors leads to high energy consumption in the refrigeration system.

[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 method and apparatus for controlling a refrigeration system, a refrigeration system, a refrigeration device, and a computer-readable storage medium to reduce the energy consumption of the refrigeration system.

[0009] In some embodiments, the refrigeration system includes: a high-temperature stage compressor, a low-temperature stage compressor, and an intermediate heat exchanger; the method for controlling the refrigeration system includes: acquiring the space temperature of the storage space corresponding to the refrigeration system; and controlling the refrigeration system to enter a normal cooling mode when the space temperature meets a second set temperature condition; wherein controlling the refrigeration system to enter the normal cooling mode includes: controlling the high-temperature stage compressor to operate at a second high-temperature stage set speed; and controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the temperature of the intermediate heat exchanger.

[0010] In some embodiments, the apparatus for controlling a refrigeration system includes a processor and a memory storing program instructions, the processor being configured to execute the aforementioned method for controlling a refrigeration system when the program instructions are executed.

[0011] In some embodiments, the refrigeration system includes: a high-temperature stage compressor, a low-temperature stage compressor, and an intermediate heat exchanger; and, as described above, a device for controlling the refrigeration system, communicatively connected to the high-temperature stage compressor and the low-temperature stage compressor.

[0012] In some embodiments, the refrigeration device includes a refrigeration system as described above.

[0013] In some embodiments, the computer-readable storage medium stores program instructions that, when executed, perform the aforementioned method for controlling the refrigeration system.

[0014] The method and apparatus for controlling a refrigeration system, the refrigeration system, the refrigeration equipment, and the computer-readable storage medium provided in the embodiments of this disclosure can achieve the following technical effects:

[0015] Based on the temperature of the storage space corresponding to the refrigeration system, it is determined whether the storage space requires normal cooling. If the space temperature meets the second set temperature condition, the refrigeration system is controlled to enter normal cooling mode. First, the high-temperature stage compressor is controlled to operate at a lower second high-temperature stage set speed to achieve normal cooling. Then, the speeds of the high-temperature stage compressor and the low-temperature stage compressor are controlled based on the temperature of the intermediate heat exchanger. The temperature of the intermediate heat exchanger can characterize the cooling temperature of the storage space by the refrigeration system. By controlling the speeds of the high-temperature stage compressor and the low-temperature stage compressor, the space temperature is adjusted in real time, reducing the number of compressor start-stops and the excess cooling capacity caused by operating at a fixed speed, thereby reducing the energy consumption of the refrigeration system.

[0016] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0017] 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:

[0018] Figure 1 This is a schematic diagram of a method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0019] Figure 2 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0020] Figure 3 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0021] Figure 4 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0022] Figure 5 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0023] Figure 6 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0024] Figure 7 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0025] Figure 8 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0026] Figure 9 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0027] Figure 10 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0028] Figure 11 This is a schematic diagram illustrating the control of compressor speed according to an embodiment of this disclosure;

[0029] Figure 12 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0030] Figure 13 This is a schematic diagram illustrating the regulation of fan speed according to an embodiment of this disclosure;

[0031] Figure 14 This is a schematic diagram of a device for controlling a refrigeration system provided in an embodiment of this disclosure;

[0032] Figure 15 This is a schematic diagram of another device for controlling a refrigeration system provided in an embodiment of this disclosure;

[0033] Figure 16 This is a schematic diagram of another device for controlling a refrigeration system provided in an embodiment of this disclosure;

[0034] Figure 17 This is a schematic diagram of the structure of a refrigeration system provided in an embodiment of this disclosure;

[0035] Figure 18 This is a schematic diagram of another refrigeration system provided in an embodiment of this disclosure.

[0036] Figure label:

[0037] 100. Refrigeration system; 10. First-stage refrigeration system; 101. First-stage compressor; 102. First-stage precooler; 103. First-stage anti-condensation pipe; 104. First-stage heat exchange structure; 1041. Fifth heat exchange section; 1042. Sixth heat exchange section; 105. First-stage condenser; 106. First-stage dryer filter; 107. First-stage regenerator; 1071. First-stage throttling component; 1072. First-stage heat exchange piping; 108. First heat exchange section; 109. First-stage gas-liquid separator; 110. First-stage branch piping; 111. First-stage expansion device; 112. First-stage switch;

[0038] 20. Second-stage refrigeration system; 201. Second-stage compressor; 202. Second-stage precooler; 203. Second-stage heat exchange structure; 2031. Third heat exchange section; 2032. Fourth heat exchange section; 204. Second heat exchange section; 205. Second-stage dryer filter; 206. Second-stage regenerator; 2061. Second-stage throttling component; 2062. Second-stage heat exchange piping; 207. Second-stage evaporator; 208. Fan; 209. Second-stage branch piping; 210. Second-stage expansion device; 211. Second-stage switch;

[0039] 30. Interstage heat exchanger;

[0040] 140. A device for controlling a refrigeration system; 1401. A first acquisition module; 1402. A first control module; 1412. A first control submodule; 1422. A second control submodule;

[0041] 150. A device for controlling a refrigeration system; 1501. A second acquisition module; 1502. A second control module; 1512. A third control submodule; 1522. A fourth control submodule;

[0042] 160. Device for controlling a refrigeration system; 161. Processor; 162. Memory; 163. Communication interface; 164. Bus. Detailed Implementation

[0043] 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.

[0044] 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.

[0045] Unless otherwise stated, the term "multiple" means two or more.

[0046] In this embodiment of the disclosure, the character " / " indicates that the objects before and after it are in an "or" relationship. For example, A / B means: A or B.

[0047] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0048] 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.

[0049] Combination Figure 1 As shown, this disclosure provides a method for controlling a refrigeration system, including:

[0050] S100, the processor obtains the space temperature of the storage space corresponding to the cooling system.

[0051] S200: When the ambient temperature is greater than or equal to a first temperature threshold, the processor controls the cooling system to enter a rapid cooling mode.

[0052] Among them, the S200 processor controls the cooling system to enter a rapid cooling mode, including:

[0053] S210, the processor controls the high-temperature stage compressor to run at the set speed of the first high-temperature stage.

[0054] The S220 processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the temperature of the intermediate heat exchanger.

[0055] The refrigeration system is installed on the refrigeration equipment. Optionally, the refrigeration equipment is a refrigerator, freezer, low-temperature storage box, etc. The refrigeration system is a cascade refrigeration system, including a high-temperature stage compressor, a low-temperature stage compressor, and an intermediate heat exchanger. The storage space corresponding to the refrigeration system is the storage space of the refrigeration equipment, such as the interior space of a refrigerator, the interior space of a freezer, or the interior space of a low-temperature storage box. The processor of the refrigeration system is communicatively connected to a temperature sensor located in the storage space to obtain the space temperature. A temperature sensor is installed at the outlet of the low-temperature stage refrigerant of the intermediate heat exchanger, and the processor of the refrigeration system is communicatively connected to this temperature sensor to obtain the outlet temperature of the low-temperature stage refrigerant of the intermediate heat exchanger (hereinafter referred to as the "temperature of the intermediate heat exchanger").

[0056] The processor compares the acquired space temperature with a preset first temperature threshold. If tl ≥ T1 (tl is the space temperature of the storage space, and T1 is the first temperature threshold), meaning the space temperature meets the preset first temperature condition, it indicates that the temperature of the storage space is too high and needs to be rapidly cooled to ensure a low-temperature storage environment for the items. Therefore, at this time, the refrigeration system is controlled to enter rapid cooling mode. Optionally, T1 = TL + M1, where TL is the target temperature of the low-temperature refrigeration system, with a value range of -40℃ to -86℃, a default value of -80℃, and an adjustment step of 1℃; M1 is the temperature adjustment value of the target temperature of the low-temperature refrigeration system in rapid cooling mode, with a value range of -0 to -20℃, a default value of 10℃, and an adjustment step of 1℃.

[0057] When the refrigeration system enters the rapid cooling mode, the high-temperature stage compressor is first controlled to operate at the set speed of the first high-temperature stage. This allows heat exchange between the refrigerant circulation loop of the high-temperature stage compressor and the refrigerant circulation loop of the low-temperature stage compressor, enabling the low-temperature stage compressor's refrigerant circulation loop to reach a lower cooling temperature. Optionally, the set speed of the first high-temperature stage is the maximum speed RH2 of the high-temperature stage compressor, ranging from 2000 rpm to 5000 rpm, with a default value of 5000 rpm and an adjustment step of 100 rpm.

[0058] The temperature of the intermediate heat exchanger reflects the final cooling temperature of the storage space, thus determining whether the low-temperature storage requirements of the items can be met. Therefore, after the high-temperature stage compressor operates at the first high-temperature stage set speed, the processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the temperature of the intermediate heat exchanger, so that the temperature of the intermediate heat exchanger matches the cooling demand.

[0059] The method for controlling a refrigeration system provided in this disclosure determines whether the storage space needs rapid cooling based on its temperature. If the temperature is greater than or equal to a first temperature threshold, indicating a high storage space temperature, the refrigeration system is controlled to enter a rapid cooling mode. First, the high-temperature stage compressor is controlled to operate at a first high-temperature stage set speed to achieve rapid cooling. Then, the speeds of the high-temperature stage compressor and the low-temperature stage compressor are controlled based on the temperature of the intermediate heat exchanger. The temperature of the intermediate heat exchanger characterizes the refrigeration temperature of the storage space. By controlling the speeds of the high-temperature stage compressor and the low-temperature stage compressor, the space temperature is adjusted in real time, reducing the number of compressor start-ups and shutdowns and the excess cooling capacity caused by operating at a fixed speed, thereby reducing the energy consumption of the refrigeration system.

[0060] Furthermore, by intelligently adjusting the refrigeration system using the above logic, it is possible to prevent excessively high compressor discharge / return temperatures caused by abnormal temperatures, while also improving the pressure state within the system and enhancing system reliability.

[0061] Optionally, after controlling the high-temperature stage compressor to run at the first high-temperature stage set speed for a second set time M2, that is, after the temperature of the storage space has stabilized, the operation of the high-temperature stage compressor and the low-temperature stage compressor is controlled according to the temperature of the intermediate heat exchanger. The second set time M2 is the start-up delay time of the low-temperature stage compressor after the high-temperature stage compressor starts in rapid cooling mode. This can avoid misadjustment caused by adjusting the compressor before the space temperature is stable, which helps to reduce the energy consumption of the refrigeration system. Optionally, the value range of the second set time M2 is 0 to 20 minutes, the default value is 10 minutes, and the adjustment step is 1 minute.

[0062] Combination Figure 2 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0063] S100, the processor obtains the space temperature of the storage space corresponding to the cooling system.

[0064] S200: When the ambient temperature is greater than or equal to a first temperature threshold, the processor controls the cooling system to enter a rapid cooling mode.

[0065] The processor controls the cooling system to enter a rapid cooling mode, including:

[0066] S210, the processor controls the high-temperature stage compressor to run at the set speed of the first high-temperature stage.

[0067] S221, when the temperature of the intermediate heat exchanger is less than or equal to the second temperature threshold, the processor controls the cryogenic stage compressor to run at the first cryogenic stage set speed.

[0068] The processor compares the temperature of the intermediate heat exchanger with the second temperature threshold. If th ≤ T2 (where th is the temperature of the intermediate heat exchanger and T2 is the second temperature threshold, also the target temperature TH1 of the high-temperature stage refrigeration system in rapid cooling mode), it indicates that the space temperature is low, and the cooling capacity is sufficient to maintain the low-temperature environment of the storage space. Therefore, the low-temperature stage compressor is controlled to operate at the first low-temperature stage set speed to avoid energy waste caused by excessive cooling capacity. Optionally, the first low-temperature stage set speed is the maximum speed RL2 of the low-temperature stage compressor. In rapid cooling mode, the purpose of setting the low-temperature stage compressor to the maximum speed is to maximize the low-temperature stage refrigerant flow rate. Since the heat calculation formula Q = cmΔt (where Q is heat, c is the specific heat capacity of the object, m is the mass of the object, and Δt is the temperature difference), it can be seen that, with the specific heat capacity and temperature difference remaining unchanged, increasing the refrigerant flow rate m can increase the cooling capacity, thereby reducing the temperature to the target temperature as quickly as possible.

[0069] Optionally, RL2 ranges from 2000 rpm to 5000 rpm, with a default value of 5000 rpm and an adjustment step of 100 rpm. Optionally, TH1 is less than or equal to 0. Optionally, TH1 ranges from -55℃ to 0, with a default value of -25℃ and an adjustment step of 1℃.

[0070] Combination Figure 3 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0071] S100, the processor obtains the space temperature of the storage space corresponding to the cooling system.

[0072] S200: When the ambient temperature is greater than or equal to a first temperature threshold, the processor controls the cooling system to enter a rapid cooling mode.

[0073] The processor controls the cooling system to enter a rapid cooling mode, including:

[0074] S210, the processor controls the high-temperature stage compressor to run at the set speed of the first high-temperature stage.

[0075] S221, when the temperature of the intermediate heat exchanger is less than or equal to the second temperature threshold, the processor controls the cryogenic stage compressor to run at the first cryogenic stage set speed.

[0076] S222, the processor obtains the new temperature of the intermediate heat exchanger.

[0077] S223, the processor adjusts the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the new temperature of the intermediate heat exchanger.

[0078] The processor obtains the new temperature of the intermediate heat exchanger, and then adjusts the operation of the high-stage compressor and the low-stage compressor according to the new temperature. In this way, the operation of the high-stage compressor and the low-stage compressor is matched with the temperature of the intermediate heat exchanger, and the energy consumption can be reduced while ensuring the refrigeration temperature.

[0079] Optionally, if the new temperature satisfies th'≥T3 (th' is the new temperature of the intermediate heat exchanger, and T3 is the third temperature threshold), it means that after the low-stage compressor operates at the first low-stage set speed, the temperature of the intermediate heat exchanger is still relatively high, and the refrigeration capacity is insufficient to provide a low-temperature environment for the storage space. Therefore, at this time, the speed of the low-stage compressor is reduced, and the speed of the high-stage compressor is increased. In this way, reducing the speed of the low-stage compressor can reduce the refrigerant flow rate of the low-stage refrigeration system, thereby reducing the refrigeration capacity required for the low-stage flow path in the intermediate heat exchanger, reducing the heat load of the high-stage flow path, and reducing the temperature of the intermediate heat exchanger; at the same time, increasing the speed of the high-stage compressor can increase the refrigerant flow rate of the high-stage refrigeration system, thereby increasing the refrigeration capacity in the high-stage flow path of the intermediate heat exchanger, and further reducing the temperature of the intermediate heat exchanger. Optionally, T3 = TH1 + M3, where M3 is the upward adjustment value of the intermediate heat exchanger temperature in the rapid cooling mode, and its value range is 0 to 20 °C, the default value is 3 °C, and the step size is 1 °C.

[0080] If the new temperature satisfies T4<th'<T3 (T4 is the fourth temperature threshold), it means that after the low-stage compressor operates at the first low-stage set speed, the temperature of the intermediate heat exchanger is within the appropriate range. Therefore, at this time, it is controlled that both the high-stage compressor and the low-stage compressor maintain their current speeds unchanged. In this way, in the initial stage of cooling, due to the refrigerant regenerative heat of the regenerator, the suction temperature of the low-stage compressor is relatively high when it starts initially, which will cause the discharge temperature to be relatively high, and thus it is easy to cause a thermal protection phenomenon of the low-stage compressor. When the temperature of the intermediate heat exchanger is stable within a certain temperature range, the evaporation pressure of the high-stage refrigeration system and the condensation pressure of the low-stage refrigeration system can quickly reach a relatively stable state, thereby avoiding the problem of thermal protection of the low-stage compressor. Optionally, T4 = TH1 + M4, where M4 is the lower limit of the intermediate heat exchanger temperature adjustment in the rapid cooling mode, which is less than or equal to 0. Optionally, the value range of M4 is -20 °C to 0, the default value is -3 °C, and the adjustment step size is 1 °C.

[0081] If the new temperature satisfies th' ≤ T4, it indicates that after the low-temperature stage compressor operates at the first low-temperature stage set speed, the temperature of the intermediate heat exchanger is relatively low and the refrigerating capacity is excessive. Therefore, at this time, the speed of the high-temperature stage compressor is reduced and the speed of the low-temperature stage compressor is increased. In this way, when the temperature of the intermediate heat exchanger is relatively low, the condensation pressure of the low-temperature stage refrigeration system is reduced, thereby reducing the heat load of the high-temperature stage flow path in the intermediate heat exchanger. At this time, the refrigerating capacity of the high-temperature stage refrigeration system can be reduced while increasing the refrigerating capacity of the low-temperature stage refrigeration system.

[0082] In this way, by means of the preset third temperature threshold and fourth temperature threshold, it is judged whether the new temperature of the intermediate heat exchanger is within the appropriate temperature range, and based on the judgment result, the speeds of the high-temperature stage compressor and the low-temperature stage compressor are adjusted. In this way, sufficient refrigerating capacity can be provided and refrigerating capacity surplus can be avoided, and repeated start and stop of the compressor can be avoided, so as to reduce the energy consumption of the refrigeration system.

[0083] Optionally, after the processor controls the low-temperature stage compressor to operate at the first low-temperature stage set speed, after a third set duration M0, that is, after the temperature of the storage space stabilizes, the new temperature of the intermediate heat exchanger is obtained, which is beneficial to reducing the energy consumption of the refrigeration system. M0 is the time interval for adjusting the speed of the system compressor in the rapid cooling mode, and its value range is 10 seconds to 120 seconds, the default value is 20 seconds, and the adjustment step is 5 seconds.

[0084] Optionally, when the new temperature satisfies T4 < th' < T3 and the processor controls both the high-temperature stage compressor and the low-temperature stage compressor to maintain their current speeds unchanged, after a first preset duration M5, the low-temperature stage compressor is controlled to operate at its maximum speed RL2. In this way, in the initial stage of cooling, due to the refrigerant heat regeneration of the regenerator, the suction temperature of the low-temperature stage compressor is relatively high when it starts initially, which will cause the discharge temperature to be relatively high, and thus it is easy to cause a thermal protection phenomenon in the low-temperature stage compressor. When the temperature of the intermediate heat exchanger stabilizes within a certain temperature range, the evaporation pressure of the high-temperature stage refrigeration system and the condensation pressure of the low-temperature stage refrigeration system can reach a relatively stable state quickly, thus avoiding the problem of thermal protection of the low-temperature stage compressor. As the system operates, the heat regeneration temperature of the low-temperature stage refrigeration system decreases, resulting in a decrease in the suction temperature of the low-temperature stage compressor, a simultaneous decrease in the discharge temperature, and a decrease in the condensation pressure of the low-temperature stage refrigeration system. At this time, the speed of the low-temperature stage compressor can be increased to obtain a larger refrigerating capacity. ​​​​​​​​

[0087] S100, the processor obtains the space temperature of the storage space corresponding to the cooling system.

[0088] S200: When the ambient temperature is greater than or equal to a first temperature threshold, the processor controls the cooling system to enter a rapid cooling mode.

[0089] The processor controls the cooling system to enter a rapid cooling mode, including:

[0090] S210, the processor controls the high-temperature stage compressor to run at the set speed of the first high-temperature stage.

[0091] The S220 processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the temperature of the intermediate heat exchanger.

[0092] S300, the processor re-acquires the temperature of the storage space.

[0093] In the S400, the processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the reacquired space temperature.

[0094] After the high-temperature and low-temperature compressors are operated based on the temperature control of the intermediate heat exchanger, the space temperature of the storage space is re-acquired. Then, based on the re-acquired space temperature, the operation of the high-temperature and low-temperature compressors is readjusted. In this way, negative feedback regulation can be performed through the real-time temperature and target temperature of the space to adjust the compressor speed in real time, achieve optimal cooling capacity, and avoid unnecessary energy loss.

[0095] Optionally, if tl' ≤ T5 (tl' is the new temperature of the storage space, and T5 is the fifth temperature threshold), it indicates that the space temperature is too low, which may cause the temperature sensor to fail to detect the temperature properly. Therefore, in this case, the refrigeration system is controlled to exit the rapid cooling mode, and the high-temperature and low-temperature compressors are also controlled to shut down. Optionally, T5 = TL + M6, where M6 is the sensor shutdown temperature adjustment value in rapid cooling mode, less than or equal to 0. The value range of M6 is -10℃ to 0, with a default value of -2℃ and an adjustment step of 1℃.

[0096] If tl'>T5, it indicates that the temperature of the storage space is too high and needs to be cooled again to provide cooling capacity. Therefore, the temperature of the intermediate heat exchanger is re-acquired, and based on this re-acquired temperature, the operation of the high-temperature stage compressor and the low-temperature stage compressor is controlled, i.e., S220 is re-executed.

[0097] In this way, based on the reacquired space temperature and the temperature of the intermediate heat exchanger, the operation of the high-temperature compressor and the low-temperature compressor is cyclically controlled. By controlling the changes in the compressor speed, the cooling capacity is dynamically stabilized, avoiding frequent start-stop of the compressor, thereby reducing the energy consumption of the refrigeration system.

[0098] Combination Figure 5 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0099] S500: The processor obtains the temperature of the storage space corresponding to the cooling system.

[0100] In the S600, the processor controls the cooling system to enter normal cooling mode when the ambient temperature meets the second set temperature condition.

[0101] Among them, the S600 processor controls the cooling system to enter normal cooling mode, including:

[0102] S610, the processor controls the high-temperature stage compressor to run at the second high-temperature stage set speed.

[0103] The S620 processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the temperature of the intermediate heat exchanger.

[0104] The refrigeration system is installed on the refrigeration equipment. Optionally, the refrigeration equipment is a refrigerator, freezer, low-temperature storage box, etc. The refrigeration system is a cascade refrigeration system, including a high-temperature stage compressor, a low-temperature stage compressor, and an intermediate heat exchanger. The storage space corresponding to the refrigeration system is the storage space of the refrigeration equipment, such as the interior space of a refrigerator, the interior space of a freezer, or the interior space of a low-temperature storage box. The processor of the refrigeration system is communicatively connected to a temperature sensor located in the storage space to obtain the space temperature. A temperature sensor is installed at the outlet of the low-temperature stage refrigerant of the intermediate heat exchanger, and the processor of the refrigeration system is communicatively connected to this temperature sensor to obtain the outlet temperature of the low-temperature stage refrigerant of the intermediate heat exchanger (hereinafter referred to as the "temperature of the intermediate heat exchanger").

[0105] The processor determines whether the acquired space temperature meets the pre-set second temperature condition. If it does, it means the current storage space needs cooling, but the space temperature is not significantly different from the target temperature, so rapid cooling is not necessary, otherwise it could easily cause temperature overshoot. Therefore, the processor controls the cooling system to enter normal cooling mode.

[0106] When controlling the refrigeration system to enter the normal cooling mode, first control the high-stage compressor to operate at the second high-stage set speed, which is equivalent to controlling the high-stage compressor to start. In this way, the refrigerant circulation circuit where the high-stage compressor is located can exchange heat with the refrigerant circulation circuit where the low-stage compressor is located, so that the refrigerant circulation circuit where the low-stage compressor is located can reach a lower refrigeration temperature. Optionally, the second high-stage set speed is less than the first high-stage set speed. Optionally, the second high-stage set speed is the minimum speed RH1 of the high-stage compressor, with a value range of 2000 rpm to 5000 rpm, a default value of 2000 rpm, and an adjustment step of 100 rpm.

[0107] The temperature of the intermediate heat exchanger can reflect the final refrigeration temperature of the storage space, and thus it can be judged whether the requirements for low-temperature storage of items can be met. Therefore, after the high-stage compressor operates at the second high-stage set speed, the processor controls the operation of the high-stage compressor and the low-stage compressor according to the temperature of the intermediate heat exchanger, so that the temperature of the intermediate heat exchanger can match the refrigeration demand.

[0108] Adopt the method for controlling the refrigeration system provided by the embodiment of the present disclosure. Based on the space temperature of the storage space corresponding to the refrigeration system, judge whether the storage space needs normal cooling. If the space temperature meets the second set temperature condition, control the refrigeration system to enter the normal cooling mode. First, control the high-stage compressor to operate at a smaller second high-stage set speed to achieve normal cooling. Then, based on the temperature of the intermediate heat exchanger, control the speeds of the high-stage compressor and the low-stage compressor. Since the temperature of the intermediate heat exchanger can represent the refrigeration temperature of the refrigeration system for the storage space, the space temperature is adjusted in real time by controlling the speeds of the high-stage compressor and the low-stage compressor, reducing the start-stop times of the compressor and the excess refrigeration capacity caused by operating at a fixed speed, thereby reducing the energy consumption of the refrigeration system.

[0109] In addition, by performing intelligent adjustment on the refrigeration system through the above logic, it is possible to prevent the exhaust / suction temperature of the compressor from being too high due to abnormal temperature, and at the same time improve the pressure state in the system and enhance the system reliability.

[0110] Optionally, the second set temperature condition includes: tl < T1 and tl ≥ T12, where tl is the space temperature of the storage space, T1 is the first temperature threshold, and T12 is the twelfth temperature threshold. When the space temperature meets tl < T1, the refrigeration system does not meet the condition for entering the rapid cooling mode. When the space temperature also meets tl ≥ T12, the refrigeration system meets the condition for entering the normal mode.

[0111] Optionally, T12 = TL + M8, where TL is the target temperature of the cryogenic refrigeration system, ranging from -40℃ to -86℃, with a default value of -80℃ and an adjustment step of 1℃; M8 is the adjustment value for the space temperature under normal cooling mode, less than or equal to 0. The value of M8 ranges from -5℃ to 0, with a default value of -1℃ and an adjustment step of 0.1℃.

[0112] Optionally, after the processor controls the high-temperature stage compressor to run at the second high-temperature stage set speed for the fourth set duration M9, that is, after the space temperature stabilizes, the operation of the high-temperature stage compressor and the low-temperature stage compressor is controlled according to the temperature of the intermediate heat exchanger. The fourth set duration M9 is the delay time for the low-temperature stage compressor to start after the high-temperature stage compressor starts in normal cooling mode. This avoids erroneous adjustments caused by adjusting the compressor before the storage space temperature has stabilized, which helps reduce the energy consumption of the refrigeration system. Optionally, the value range of the fourth set duration M9 is 0 to 20 minutes, with a default value of 1 minute and an adjustment step of 1 minute.

[0113] Combination Figure 6 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0114] S500: The processor obtains the temperature of the storage space corresponding to the cooling system.

[0115] In the S600, the processor controls the cooling system to enter normal cooling mode when the ambient temperature meets the second set temperature condition.

[0116] Among them, the S600 processor controls the cooling system to enter normal cooling mode, including:

[0117] S610, the processor controls the high-temperature stage compressor to run at the second high-temperature stage set speed.

[0118] S621, when the temperature of the intermediate heat exchanger is less than or equal to the sixth temperature threshold, the processor controls the cryogenic stage compressor to run at the second cryogenic stage set speed.

[0119] The temperature of the intermediate heat exchanger is compared with the sixth temperature threshold. If th ≤ T6 (th is the temperature of the intermediate heat exchanger; T6 is the sixth temperature threshold, which is also the target temperature TH2 of the high-temperature stage refrigeration system in normal cooling mode), it indicates that the temperature of the storage space is low, and the cooling capacity is sufficient to maintain the low-temperature storage space. Therefore, the low-temperature stage compressor is controlled to operate at the second low-temperature stage set speed to avoid energy waste due to excessive cooling capacity. Optionally, the second low-temperature stage set speed is lower than the first low-temperature stage set speed. Optionally, the second low-temperature stage set speed is the lowest speed RL1 of the low-temperature stage compressor. This is because: at low speeds, the compressor generates less mechanical loss, making it easier to achieve a higher COP value (Coefficient of Performance, the conversion ratio between energy and heat, or simply energy efficiency ratio), hence the lowest speed is used. The value range is 2000 rpm to 5000 rpm, with a default value of 2000 rpm and an adjustment step of 100 rpm.

[0120] Optionally, T6 is the target temperature TH2 of the high-temperature stage refrigeration system in normal cooling mode, which is less than or equal to 0. The value range of TH2 is -55℃ to 0, with a default value of -30℃ and an adjustment step of 1℃.

[0121] Combination Figure 7 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0122] S500: The processor obtains the temperature of the storage space corresponding to the cooling system.

[0123] In the S600, the processor controls the cooling system to enter normal cooling mode when the ambient temperature meets the second set temperature condition.

[0124] Among them, the S600 processor controls the cooling system to enter normal cooling mode, including:

[0125] S610, the processor controls the high-temperature stage compressor to run at the second high-temperature stage set speed.

[0126] S621, when the temperature of the intermediate heat exchanger is less than or equal to the sixth temperature threshold, the processor controls the cryogenic stage compressor to run at the second cryogenic stage set speed.

[0127] S622, the processor obtains the new temperature of the intermediate heat exchanger and the new space temperature.

[0128] S623, the processor adjusts the operation of the high-temperature stage compressor based on the new temperature of the intermediate heat exchanger.

[0129] The S624 processor adjusts the operation of the cryogenic stage compressor based on the new space temperature.

[0130] Under normal adjustment conditions, the temperature of the intermediate heat exchanger has a higher priority than the ambient temperature. When these two temperatures conflict, the compressor speed should be adjusted based on the intermediate heat exchanger temperature. Therefore, after controlling the cryogenic stage compressor to operate at the second cryogenic stage set speed, when adjusting the compressor speed, the compressor speed should first be adjusted based on the intermediate heat exchanger, and then based on the ambient temperature.

[0131] When adjusting the compressor, the operation of the high-temperature stage compressor is adjusted first, followed by the low-temperature stage compressor. This is because it is desirable for the high-temperature stage compressor to have a faster frequency change cycle, allowing it to respond more quickly than the low-temperature stage compressor. Essentially, the high-temperature stage compressor is controlled for cooling before the low-temperature stage compressor is controlled for cooling. The high-temperature stage compressor is more sensitive than the low-temperature stage compressor, enabling it to better match the operating conditions of the low-temperature stage compressor. Thus, the high-temperature stage compressor reacts quickly to changes in the speed of the low-temperature stage compressor, resulting in faster energy savings and reduced consumption in the refrigeration system.

[0132] Optionally, after the processor controls the low-temperature stage compressor to run at the second low-temperature stage set speed, it waits for a fifth set time M10, i.e., until the space temperature stabilizes, before acquiring the new temperature of the intermediate heat exchanger, which helps reduce the energy consumption of the refrigeration system. Optionally, M10 is the time interval for adjusting the speed of the high-temperature stage compressor in normal cooling mode, with a value range of 10 to 120 seconds, a default value of 30 seconds, and an adjustment step of 5 seconds.

[0133] Optionally, after the processor controls the low-temperature stage compressor to run at the second low-temperature stage set speed, it re-acquires the space temperature of the storage space after a sixth set time M11, and controls the operation of the low-temperature stage compressor based on the re-acquired space temperature. M11 > M10. This way, after waiting for the space temperature to stabilize after the sixth set time M11, the speed of the low-temperature stage compressor is adjusted based on the space temperature, which helps reduce the energy consumption of the refrigeration system. Thus, within different timing cycles, the high-temperature stage compressor and the low-temperature stage compressor are independently controlled, thereby achieving refrigeration to bring the space temperature of the storage space to the target temperature. Optionally, M11 is the time interval for adjusting the speed of the low-temperature stage compressor in normal cooling mode, with a value range of 10 seconds to 120 seconds, a default of 60 seconds, and an adjustment step of 5 seconds.

[0134] Optionally, S623, the processor adjusts the operation of the high-temperature stage compressor based on the new temperature of the intermediate heat exchanger, including:

[0135] When the processor increases the speed of the high-temperature stage compressor when the new temperature of the intermediate heat exchanger is greater than or equal to the seventh temperature threshold.

[0136] When the new temperature of the intermediate heat exchanger is less than the seventh temperature threshold and greater than the eighth temperature threshold, the processor controls the high-stage compressor to maintain its current speed.

[0137] When the new temperature of the intermediate heat exchanger is less than or equal to the eighth temperature threshold, the processor reduces the speed of the high-stage compressor.

[0138] If the new temperature of the intermediate heat exchanger satisfies th'≥T7 (th' is the new temperature of the intermediate heat exchanger, and T7 is the seventh temperature threshold), it indicates that after the low-stage compressor operates at the second low-stage set speed, the temperature of the intermediate heat exchanger is still relatively high, and the cooling capacity is insufficient to provide a low-temperature environment for the storage space. Therefore, at this time, the speed of the high-stage compressor is increased to increase the cooling capacity. Optionally, T7 = TH2 + M12, where TH2 is the target temperature of the high-stage refrigeration system in the normal cooling mode, with a value range of -55°C to 0°C, a default value of -30°C, and an adjustment step of 1°C; M12 is the upward adjustment value of the high-stage compressor speed in the normal cooling mode, which is greater than or equal to 0. The value range of M12 is 0 to 20°C, a default value of 3°C, and an adjustment step of 1°C.

[0139] If the new temperature of the intermediate heat exchanger satisfies T8<th'<T7 (T8 is the eighth temperature threshold), it indicates that after the low-stage compressor operates at the second low-stage set speed, the temperature of the intermediate heat exchanger is within the appropriate range. Therefore, at this time, the processor controls the high-stage compressor to maintain its current speed unchanged. In this way, by controlling the high-stage compressor to maintain a relatively stable speed, the space temperature is stabilized. Optionally, T8 = TH2 + M13, where M13 is less than or equal to 0 and is the downward adjustment value of the high-stage compressor speed in the normal cooling mode, which is less than or equal to 0. The value range of M13 is -20°C to 0°C, a default value of -3°C, and an adjustment step of 1°C.

[0140] If the new temperature of the intermediate heat exchanger satisfies th'≤T8, it indicates that after the low-stage compressor operates at the second low-stage set speed, the temperature of the intermediate heat exchanger is relatively low and the cooling capacity is excessive. Therefore, at this time, the speed of the high-stage compressor is reduced, so as to reduce unnecessary energy consumption.

[0141] In this way, by presetting the seventh temperature threshold and the eighth temperature threshold, it is judged whether the new temperature of the intermediate heat exchanger is within the appropriate range, and based on the judgment result, the speed of the high-stage compressor is adjusted, which can not only provide sufficient cooling capacity, but also avoid excessive cooling capacity and avoid repeated start and stop of the compressor, thereby reducing the energy consumption of the refrigeration system.

[0142] S623. The processor adjusts the operation of the low-stage compressor according to the new space temperature, including:

[0143] When the new space temperature is greater than or equal to the tenth temperature threshold, the processor increases the rotational speed of the low-temperature stage compressor.

[0144] When the new space temperature is less than the tenth temperature threshold and greater than the eleventh temperature threshold, the processor controls the low-temperature stage compressor to maintain its current rotational speed.

[0145] When the new space temperature is less than or equal to the eleventh temperature threshold, the processor decreases the rotational speed of the low-temperature stage compressor.

[0146] If tl”≥T10 (tl” is the new space temperature of the storage space, and T10 is the tenth temperature threshold), it indicates that the space temperature is relatively high and the space temperature needs to be decreased, so the rotational speed of the low-temperature stage compressor is increased. If T11<tl”<T10 (T11 is the eleventh temperature threshold), it indicates that the space temperature is within the appropriate temperature range, so the processor controls the low-temperature stage compressor to maintain its current rotational speed unchanged to keep the space temperature at the current level. If tl”≤T11, it indicates that the space temperature is relatively low, which will cause waste of cooling capacity, so the rotational speed of the low-temperature compressor is decreased to reduce the generation of cooling capacity and can also ensure a low-temperature storage environment. Thus, by adjusting the rotational speed of the low-temperature compressor based on the new space temperature, the space temperature of the storage space can be maintained within an appropriate low-temperature range, and the situation of excessive or insufficient cooling capacity can be reduced, thereby reducing the energy consumption of the refrigeration system.

[0147] Optionally, T10 = TL + M14, where M14 is the upward adjustment temperature value of the target temperature of the low-temperature stage refrigeration system in the normal cooling mode, and is greater than or equal to 0. The value range of M14 is from 0 to 5 °C, the default value is 1 °C, and the adjustment step is 0.1 °C.

[0148] Optionally, T11 = TL + M15, where M15 is the downward adjustment temperature value of the target temperature of the low-temperature stage refrigeration system in the normal cooling mode, and is less than or equal to 0. The value range of M15 is from -5 °C to °C, the default value is -1.5 °C, and the adjustment step is 0.1 °C.

[0149] Combined Figure 8 As shown, the embodiments of the present disclosure provide another method for controlling a refrigeration system, including:

[0150] S500, the processor obtains the space temperature of the storage space corresponding to the refrigeration system.

[0151] S600, when the space temperature meets the second set temperature condition, the processor controls the refrigeration system to enter the normal cooling mode.

[0152] Among them, S600, the processor controls the refrigeration system to enter the normal cooling mode, including:

[0153] S610, the processor controls the high-temperature stage compressor to run at the second high-temperature stage set speed.

[0154] The S620 processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the temperature of the intermediate heat exchanger.

[0155] S700, the processor re-acquires the temperature of the storage space.

[0156] The S800 processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the reacquired space temperature.

[0157] After the high-temperature and low-temperature compressors are operated based on the temperature control of the intermediate heat exchanger, the space temperature of the storage space is reacquired. Then, based on the reacquired space temperature, the operation of the high-temperature and low-temperature compressors is readjusted. In this way, through multiple cycles of adjustment of the high-temperature and low-temperature compressors, temperature overshoot and repeated start-stop of the compressors are avoided, and the space temperature can be gradually stabilized at the target temperature with low energy consumption.

[0158] Optionally, if tl' ≤ T9 (tl' is the new temperature of the storage space, and T9 is the ninth temperature threshold), it indicates that the space temperature is too low, which may cause the temperature sensor to fail to detect the temperature properly. Therefore, in this case, the refrigeration system is controlled to exit the normal cooling mode, and the high-temperature compressor and low-temperature compressor can also be stopped. Optionally, T9 = TL + M8, where TL is the target temperature of the low-temperature refrigeration system, with a value range of -40℃ to -80℃, a default value of -80℃, and an adjustment step of 1℃; M8 is the temperature adjustment value of the storage space under normal cooling mode, less than or equal to 0. The value range of M8 is -5℃ to 0, a default value of -1℃, and an adjustment step of 0.1℃.

[0159] If tl'>T9, it indicates that the storage space has not reached the target space temperature. In this case, the operation of the high-temperature stage compressor and the low-temperature stage compressor will be readjusted, i.e., S622 and S623 will be executed again. Optionally, S622 will be executed again after a fifth set time interval M10, and S623 will be executed again after a sixth set time interval M10.

[0160] The ultimate goal is to adjust the storage space temperature to the target temperature. Therefore, after adjusting the speed of the high-temperature compressor and the low-temperature compressor once, it is beneficial to determine whether the speed of the high-temperature compressor and the low-temperature compressor needs to be adjusted again based on the space temperature. This will help to accurately control the compressor speed and the space temperature.

[0161] Combination Figure 9 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0162] S500, the processor obtains the space temperature of the storage space corresponding to the refrigeration system.

[0163] S600, when the space temperature meets the second set temperature condition, the processor controls the refrigeration system to enter the normal cooling mode.

[0164] Among them, for S600, the processor controls the refrigeration system to enter the normal cooling mode, including:

[0165] S610, the processor controls the high-temperature stage compressor to operate at the second set speed of the high-temperature stage.

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[0175] S610, the processor controls the high-temperature stage compressor to run at the second high-temperature stage set speed.

[0176] The S620 processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the temperature of the intermediate heat exchanger.

[0177] S700, the processor re-acquires the temperature of the storage space.

[0178] The S800 processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the reacquired space temperature.

[0179] S900: After executing S500, if the storage space temperature does not meet the first set temperature condition for entering the rapid cooling mode and does not meet the second set temperature condition for entering the normal cooling mode, the processor controls the high-temperature stage compressor and the low-temperature stage compressor to shut down.

[0180] S1000: When the new space temperature is greater than or equal to the thirteenth temperature threshold, the processor controls the cooling system to selectively enter either rapid cooling mode or normal cooling mode, depending on the temperature range of the new space temperature.

[0181] After the high-temperature and low-temperature compressors are shut down, the storage space temperature is continuously acquired, and it is determined whether the new space temperature meets the conditions for compressor startup. If tl”' ≥ T13 (tl”' is the new space temperature acquired after the compressor stops, and T13 is the thirteenth temperature threshold), it indicates that the storage space temperature has risen to a higher temperature. Then, it is determined whether the new space temperature tl”' meets the first or second set temperature condition, i.e., steps S100 to S200 and S500 to S600 are executed, thereby controlling the refrigeration system to selectively enter either rapid cooling mode or normal cooling mode. In this way, by matching the refrigeration system to rapid cooling or normal cooling based on the new space temperature, the space temperature can be reduced to a suitable low temperature range, and an appropriate compressor speed can be matched to avoid excessive cooling capacity, thereby reducing the energy consumption of the refrigeration system.

[0182] Optionally, T13 = TL + M7, where M7 is the compressor's upper limit temperature for starting, which is greater than or equal to 0. The value of M7 ranges from 0 to 5℃, with a default value of 1℃ and an adjustment step of 0.1℃.

[0183] The following will combine Figure 11 (The top is located on the left side of the drawing), specifically illustrating the control of compressor speed in the embodiments of this disclosure:

[0184] S1101, the processor obtains the temperature of the storage space.

[0185] S1102, the processor determines whether the space temperature satisfies tl≥TL+M1; if yes, then execute S1103; if no, then execute S1113.

[0186] S1103, the processor controls the high-temperature stage compressor to run at speed RH2.

[0187] S1104, after the processor waits for M2 minutes, when the temperature of the intermediate heat exchanger meets th≤TH1, it controls the cryogenic stage compressor to run at speed RL2.

[0188] S1105, processor timer M0 seconds.

[0189] S1106, the processor determines whether the temperature of the intermediate heat exchanger satisfies th≥TH1+M3; if yes, then execute S1107; if no, then execute S1108.

[0190] S1107, the processor reduces the speed of the low-temperature stage compressor and increases the speed of the high-temperature stage compressor; then it executes S1111.

[0191] S1108, the processor determines whether the temperature of the intermediate heat exchanger satisfies th≤TH1+M4; if yes, then execute S1109; if no, then execute S1110.

[0192] S1109, the processor reduces the speed of the high-temperature stage compressor and increases the speed of the low-temperature stage compressor; then it executes S1111.

[0193] S1110, the processor maintains the speed of the high-temperature stage compressor and the low-temperature stage compressor; after waiting for M5 minutes, it controls the low-temperature stage compressor to run at speed RL2; then it executes S1111.

[0194] S1111, the processor determines whether the space temperature satisfies tl≤TL+M6; if yes, then execute S1112; if no, then execute S1105.

[0195] S1112, the processor exits rapid cooling mode.

[0196] S1113, the processor determines whether the space temperature satisfies tl≥TL+M8; if yes, then execute S1114; if no, then execute S1129.

[0197] S1114, the processor controls the high-temperature stage compressor to run at speed RH1.

[0198] S1115, after the processor waits for M9 minutes, when the temperature of the intermediate heat exchanger meets th≤TH2, it controls the cryogenic stage compressor to run at speed RL1; then it executes S1116 and S1123.

[0199] S1116, processor timer M10 seconds.

[0200] S1117, the processor determines whether the temperature of the intermediate heat exchanger satisfies th≥TH2+M12; if yes, then execute S1118; if no, then execute S1119.

[0201] S1118, the processor increases the speed of the high-temperature stage compressor, and then executes S1122.

[0202] S1119, the processor determines whether the temperature of the intermediate heat exchanger satisfies th≤TH2+M13; if yes, then execute S1120; if no, then execute S1121.

[0203] S1120, reduce the speed of the high-temperature stage compressor, and then execute S1122.

[0204] S1121, the processor maintains the speed of the high-temperature stage compressor, and then executes S1122.

[0205] S1122, the processor determines whether the space temperature satisfies tl≤TL+M8; if yes, then execute S1131; if no, then execute S1116 and S1123.

[0206] S1123, processor timer M11 seconds.

[0207] S1124, the processor determines whether the space temperature satisfies tl≥TL+M14; if yes, then execute S1125; if no, then execute S1126.

[0208] S1125, the processor increases the speed of the cryogenic stage compressor, and then executes S1122.

[0209] S1126, the processor determines whether the space temperature satisfies tl≤TL+M15; if yes, then execute S1127; if no, then execute S1128.

[0210] S1127, the processor reduces the speed of the cryogenic stage compressor, and then executes S1122.

[0211] S1128, the processor maintains the speed of the cryogenic stage compressor, and then executes S1122.

[0212] S1129, the processor controls the shutdown of the high-temperature stage compressor, the low-temperature stage compressor, and all fans.

[0213] S1130, the processor determines whether the space temperature satisfies tl≥TL+M7; if yes, then execute S1102; if no, then execute S1129.

[0214] S1131, Exit normal cooling mode.

[0215] Combination Figure 12 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0216] S1100, the processor obtains the operating status of the high-temperature stage compressor and the outlet temperature of the condenser of the high-temperature stage refrigeration system.

[0217] The S1200 processor controls the operation of the fan based on the operating status of the high-temperature stage compressor and the outlet temperature of the condenser in the high-temperature stage refrigeration system.

[0218] The processor of the refrigeration system acquires the operating status of the high-temperature stage compressor to determine whether it should start. Simultaneously, the processor obtains the condenser outlet temperature via a temperature sensor located at the condenser outlet of the high-temperature stage refrigeration system. Then, based on the operating status of the high-temperature stage compressor and the condenser outlet temperature, the processor controls the operation of the fan. This is because the fan is directly connected to the condenser of the high-temperature stage refrigeration system and has no direct relationship with the condenser of the low-temperature stage refrigeration system. The condenser of the low-temperature stage refrigeration system is equivalent to the evaporator of the high-temperature stage refrigeration system. The operating conditions of the high-temperature stage refrigeration system affect the operating conditions of the low-temperature stage refrigeration system, and the fan affects the operating conditions of the high-temperature stage refrigeration system. Therefore, the fan operation is controlled based on the operating status of the high-temperature stage compressor and the condenser outlet temperature of the high-temperature stage refrigeration system.

[0219] The method for controlling a refrigeration system provided in this disclosure controls the operation of the fan based on the operating status of the high-temperature compressor and the outlet temperature of the condenser of the high-temperature refrigeration system. It can automatically adjust the fan speed and on / off operating status according to the cooling air volume required by the condenser of the high-temperature refrigeration system, thereby matching the air volume with the operating status of the refrigeration system, reducing noise and extending the fan life.

[0220] Optionally, in the S1200, the processor controls the operation of the fan based on the operating status of the high-temperature stage compressor and the outlet temperature of the condenser, including:

[0221] The processor is operating under the condition that the high-temperature compressor is started:

[0222] The processor determines the target fan speed corresponding to the current condenser outlet temperature of the high-temperature refrigeration system based on the correlation between the condenser outlet temperature and the fan speed.

[0223] The processor controls all fans to run at the target speed.

[0224] The storage of the refrigeration system pre-stores the correlation between the outlet temperature of the condenser of the high-temperature stage refrigeration system (hereinafter referred to as "the outlet temperature of the condenser") and the fan speed. When the high-temperature stage compressor starts, it indicates that the refrigeration system is operating for refrigeration. Then the processor calls the above-mentioned correlation to determine the target fan speed corresponding to the outlet temperature of the condenser, and controls all fans to operate at the target fan speed. In this way, the outlet temperature of the condenser is matched with the fan speed, thereby matching the air volume required by the refrigeration system and reducing noise.

[0225] Optionally, the correlation between the outlet temperature of the condenser and the fan speed includes one or more corresponding relationships between the outlet temperature and the fan speed. Specifically, different temperature ranges are pre-divided, and different temperature ranges correspond to different fan speeds. Optionally, the larger the upper limit value of the temperature range, the higher the corresponding fan speed. Specifically, when the outlet temperature of the condenser is greater than or equal to the fourteenth temperature threshold (tc≥T14, tc is the outlet temperature of the condenser, T14 is the fourteenth temperature threshold), the corresponding fan speed is the first set speed. When the outlet temperature of the condenser is less than the fourteenth temperature threshold and greater than the fifteenth temperature threshold (T15<tc<T14, T15 is the fifteenth temperature threshold), the corresponding fan speed is the second set speed. When the outlet temperature of the condenser is less than or equal to the fifteenth temperature threshold (tc≤T15), the corresponding fan speed is the third set speed. Among them, the first set speed is greater than the third set speed, and the third set speed is greater than the second set speed. Optionally, the first set speed is the highest speed of the fan, the second set speed is the lowest speed of the fan, and the third set speed is the intermediate speed between the highest speed and the lowest speed. In this way, the outlet temperature of the condenser matches different fan speeds, which can adjust the fan to an appropriate speed and avoid insufficient or overshoot of speed adjustment.

[0226] It should be noted that those skilled in the art can divide more temperature ranges according to needs, and then correspond to more gears of fan speeds, so as to more accurately adjust the fan speed.

[0227] Optionally, T14 = ta + M16, where ta is the ambient temperature, M16 is the upper limit value of temperature adjustment, and is greater than or equal to 0. The value range of M16 is 0 to 20°C, the default value is 4°C, and the adjustment step is 0.5°C.

[0228] Optionally, T15 = ta + M17, where M17 is the lower limit value of temperature adjustment, and is greater than or equal to 0. The value range of M17 is 0°C to 10°C, the default value is 2°C, and the adjustment step is 0.5°C.

[0229] Optionally, after controlling all fans to operate at the target fan speed, the processor starts timing. After the seventh set time M18, the condenser outlet temperature is reacquired, and based on the reacquired outlet temperature, the speed of all fans is controlled according to the fan speed control logic described above. The specific control logic is detailed in S1200 above and will not be repeated here. This allows the condenser outlet temperature to stabilize after the seventh set time M18, ensuring the accuracy of subsequent fan speed adjustments.

[0230] Optionally, M18 is the fan speed regulation time interval, ranging from 10 seconds to 120 seconds, with a default value of 30 seconds and an adjustment step of 5 seconds.

[0231] Optionally, if the high-temperature stage compressor is not running, the processor will re-determine whether the high-temperature stage compressor is running at an eighth set interval, and control the fan speed based on the condenser outlet temperature. Optionally, the eighth set interval is 1 to 2 minutes. This continuously monitors the compressor's operating status, allowing for precise control of the fan speed.

[0232] The following will combine Figure 13 The following details the regulation of fan speed in the embodiments of this disclosure:

[0233] S1301, the processor obtains the operating status of the high-temperature stage compressor.

[0234] S1302, the processor determines whether the high-temperature stage compressor has started; if yes, it executes S1303, otherwise it executes S1309.

[0235] S1303, the processor determines whether the condenser outlet temperature satisfies tc≥ta+M16; if yes, then execute S1304; if no, then execute S1305.

[0236] S1304, the processor controls all fans to run at maximum speed, and then executes S1308.

[0237] S1305, the processor determines whether the condenser outlet temperature satisfies tc≤ta+M17; if yes, then execute S1306; if no, then execute S1307.

[0238] S1306, the processor controls all fans to run at intermediate speed, and then executes S1308.

[0239] S1307, the processor controls all fans to run at the lowest speed, and then executes S1308.

[0240] S1308, the processor timestamp M18 seconds, and then executes S1303.

[0241] S1309, the processor delays for 1 minute, and then executes S1301.

[0242] Optionally, the fan speed control logic provided in this embodiment can be integrated with the compressor speed control logic in the rapid cooling mode and the compressor speed control logic in the normal cooling mode (e.g., Figure 11 Simultaneous operation of the compressor and fan allows for matched control, reducing unnecessary energy consumption and improving system response speed and control accuracy. Furthermore, by designing different control modes and coupling the compressor and fan for different operating conditions, system reliability can be improved.

[0243] Combination Figure 14 As shown in the figure, this disclosure provides an apparatus 140 for controlling a refrigeration system, including a first acquisition module 1401 and a first control module 1402. The first acquisition module 1401 is configured to acquire the space temperature of the storage space corresponding to the refrigeration system. The first control module 1402 is configured to control the refrigeration system to enter a rapid cooling mode when the space temperature is greater than or equal to a first temperature threshold.

[0244] The first control module 1402 includes a first control submodule 1412 and a second control submodule 1422. The first control submodule 1412 is configured to control the high-temperature stage compressor to operate at a first high-temperature stage set speed. The second control submodule 1422 is configured to control the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the temperature of the intermediate heat exchanger.

[0245] The device 140 for controlling a refrigeration system provided in this embodiment determines whether the storage space needs rapid cooling based on the space temperature corresponding to the refrigeration system. If the space temperature is greater than or equal to a first temperature threshold, it indicates that the storage space temperature is high, and the refrigeration system is controlled to enter a rapid cooling mode. First, the high-temperature stage compressor is controlled to run at the first high-temperature stage set speed to achieve rapid cooling. Then, the speeds of the high-temperature stage compressor and the low-temperature stage compressor are controlled based on the temperature of the intermediate heat exchanger. The temperature of the intermediate heat exchanger can characterize the cooling temperature of the storage space by the refrigeration system. By controlling the speeds of the high-temperature stage compressor and the low-temperature stage compressor, the space temperature is adjusted in real time, reducing the number of compressor start-ups and shutdowns and the excess cooling capacity caused by running at a fixed speed, thereby reducing the energy consumption of the refrigeration system.

[0246] Combination Figure 15As shown in the figure, this disclosure provides an apparatus 150 for controlling a refrigeration system, including a second acquisition module 1501 and a second control module 1502. The second acquisition module 1501 is configured to acquire the space temperature of the storage space corresponding to the refrigeration system. The second control module 1502 is configured to control the refrigeration system to enter a normal cooling mode when the space temperature meets a second set temperature condition.

[0247] The second control module 1502 includes a third control submodule 1512 and a fourth control submodule 1522. The third control submodule 1512 is configured to control the high-temperature stage compressor to operate at a second high-temperature stage set speed. The fourth control submodule 1522 is configured to control the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the temperature of the intermediate heat exchanger.

[0248] The apparatus 150 for controlling a refrigeration system provided in this embodiment determines whether the storage space requires normal cooling based on the space temperature corresponding to the refrigeration system. If the space temperature meets a second set temperature condition, the refrigeration system is controlled to enter a normal cooling mode. First, the high-temperature stage compressor is controlled to operate at a lower second high-temperature stage set speed to achieve normal cooling. Then, the speeds of the high-temperature stage compressor and the low-temperature stage compressor are controlled based on the temperature of the intermediate heat exchanger. The temperature of the intermediate heat exchanger can characterize the cooling temperature of the storage space by the refrigeration system. By controlling the speeds of the high-temperature stage compressor and the low-temperature stage compressor, the space temperature is adjusted in real time, reducing the number of compressor start-ups and shutdowns and the excess cooling capacity caused by operating at a fixed speed, thereby reducing the energy consumption of the refrigeration system.

[0249] Combination Figure 16 As shown, this embodiment of the disclosure provides a device 160 for controlling a refrigeration system, including a processor 161 and a memory 162. Optionally, the device 160 may further include a communication interface 163 and a bus 164. The processor 161, communication interface 163, and memory 162 can communicate with each other via the bus 164. The communication interface 163 can be used for information transmission. The processor 161 can call logical instructions in the memory 162 to execute the method for controlling the refrigeration system described in the above embodiment.

[0250] Furthermore, the logic instructions in the aforementioned memory 162 can be implemented as software functional units and, when sold or used as independent products, can be stored in a computer-readable storage medium.

[0251] The memory 162, 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 161 executes functional applications and data processing by running the program instructions / modules stored in the memory 162, that is, it implements the method for controlling the refrigeration system in the above embodiments.

[0252] The memory 162 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 created based on the use of the terminal device. Furthermore, the memory 162 may include high-speed random access memory and may also include non-volatile memory.

[0253] Combination Figure 17 and Figure 18 As shown, this embodiment of the present disclosure provides a refrigeration system 100, including: a compressor, a first heat exchanger, and a second heat exchanger connected in sequence via refrigerant pipelines.

[0254] The first heat exchanger functions as a condenser, and the second heat exchanger functions as an evaporator. The refrigerant flowing from the compressor condenses in the first heat exchanger and evaporates in the second heat exchanger.

[0255] The heat exchange system also includes a heat exchange structure, which includes a first heat exchange component and a second heat exchange component capable of heat exchange. The first heat exchange component is connected between the exhaust port of the compressor and the inlet of the first heat exchanger, and the second heat exchange component is connected between the outlet of the second heat exchanger and the return port of the compressor.

[0256] The first and second heat exchange components can exchange heat, allowing the refrigerant flowing out of the second heat exchanger to exchange heat with the refrigerant flowing out of the compressor's discharge port. This allows the lubricating oil mixed in the refrigerant flowing out of the second heat exchanger to be heated by the refrigerant flowing out of the compressor's discharge port. The heated oil becomes more fluid and flows back to the compressor, thus eliminating the need for an oil separator.

[0257] Compared to the first heat exchange component being located between the outlet of the first heat exchanger and the inlet of the second heat exchanger, when the first heat exchange component is located between the exhaust port of the compressor and the inlet of the first heat exchanger, the refrigerant temperature in the first heat exchange component is higher. This allows for better heating of the refrigerant in the second heat exchange component, and the oil mixed in the refrigerant can also be heated better, ensuring that the oil can flow back into the compressor and that the refrigeration system can still operate normally even without an oil separator.

[0258] Optionally, such as Figure 17As shown, the compressor includes a first-stage compressor 101 and a second-stage compressor 201; the first heat exchanger includes a first-stage condenser 105 and a second heat exchange section 204; the second heat exchanger includes a first heat exchange section 108 and a second-stage evaporator 207; the first heat exchange section 108 and the second heat exchange section 204 are capable of heat exchange; the first-stage refrigeration system 10 includes the first-stage compressor 101, the first-stage condenser 105, and the first heat exchange section 108 connected in sequence; the second-stage refrigeration system 20 includes the second-stage compressor 201, the second heat exchange section 204, and the second-stage evaporator 207 connected in sequence.

[0259] The first-stage compressor 101 is also the high-temperature stage compressor in the aforementioned method for controlling the refrigeration system. The first-stage refrigeration system 10 is also the high-temperature stage refrigeration system in the aforementioned method for controlling the refrigeration system. The second-stage compressor 201 is also the low-temperature stage compressor in the aforementioned method for controlling the refrigeration system. The second-stage refrigeration system 20 is also the low-temperature stage refrigeration system in the aforementioned method for controlling the refrigeration system.

[0260] The refrigeration system is divided into a first-stage refrigeration system 10 and a second-stage refrigeration system. The first heat exchange section 108 and the second heat exchange section 204 can exchange heat, thereby allowing the refrigerant in the first heat exchange section 108 to cool the refrigerant in the second heat exchange section 204, lowering the temperature of the refrigerant in the second heat exchange section 204, and enabling the second-stage refrigeration system 20 to reach a lower refrigeration temperature. In other words, while achieving the same refrigeration temperature, the refrigeration system of this application can reduce energy consumption.

[0261] Optionally, the heat exchange structure includes a second-stage heat exchange structure 203, which includes a third heat exchange section 2031 and a fourth heat exchange section 2032 capable of heat exchange. The third heat exchange section 2031 is connected between the exhaust port of the second-stage compressor 201 and the inlet of the second heat exchange section 204, and the fourth heat exchange section 2032 is connected between the outlet of the second-stage evaporator 207 and the return port of the second-stage compressor 201. The first heat exchange component includes the third heat exchange section 2031, and the second heat exchange component includes the fourth heat exchange section 2032.

[0262] Heat exchange can occur between the third heat exchange section 2031 and the fourth heat exchange section 2032, allowing the refrigerant flowing out of the second-stage evaporator 207 to exchange heat with the refrigerant flowing out of the second-stage compressor 201. This also allows the lubricating oil mixed in the refrigerant flowing out of the second-stage evaporator 207 to be heated by the refrigerant flowing out of the second-stage compressor 201. The heated oil becomes more fluid and flows back to the second-stage compressor 201, thus eliminating the need for an oil separator.

[0263] Optionally, the third heat exchange section 2031 includes a third heat exchange tube, the two ends of which are respectively connected to the exhaust port of the second-stage compressor 201 and the inlet of the second heat exchange section 204.

[0264] The fourth heat exchange section 2032 includes a fourth heat exchange tube, the two ends of which are connected to the outlet of the second-stage evaporator 207 and the return port of the second-stage compressor 201, respectively.

[0265] Heat exchange between the third and fourth heat exchange tubes is achieved by either placing the third heat exchange tube outside the fourth heat exchange tube or placing the fourth heat exchange tube outside the third heat exchange tube.

[0266] The third heat exchange tube is sleeved on the outside of the fourth heat exchange tube. For example, the third heat exchange tube is a copper tube with an inner diameter of 12mm and the fourth heat exchange tube is a copper tube with an inner diameter of 4mm. The refrigerant flowing out of the second-stage compressor 201 passes through the third heat exchange tube (the gap between the outer wall of the third heat exchange tube and the inner wall of the fourth heat exchange tube), the second heat exchange section 204 and the second-stage evaporator 207, and then flows back to the second-stage compressor 201 through the fourth heat exchange tube.

[0267] Alternatively, the fourth heat exchange tube may be sleeved on the outside of the third heat exchange tube. For example, the third heat exchange tube may be a copper tube with an inner diameter of 4 mm and the fourth heat exchange tube may be a copper tube with an inner diameter of 12 mm. The refrigerant flowing out of the second-stage compressor 201 passes through the third heat exchange tube, the second heat exchange section 204 and the second-stage evaporator 207, and then flows back to the second-stage compressor 201 through the fourth heat exchange tube (the gap between the outer wall of the third heat exchange tube and the inner wall of the fourth heat exchange tube).

[0268] The third and / or fourth heat exchange tubes are corrugated tubes. The corrugation of the tubes enhances the turbulence of the refrigerant, effectively reduces the boundary layer thickness during refrigerant flow, and enhances the heat exchange effect between the third and fourth heat exchange tubes.

[0269] Optionally, such as Figure 17 As shown, the heat exchange structure includes a first-stage heat exchange structure 104, which includes a fifth heat exchange section 1041 and a sixth heat exchange section 1042 capable of heat exchange. The fifth heat exchange section 1041 is connected between the exhaust port of the first-stage compressor 101 and the inlet of the first-stage condenser 105, and the sixth heat exchange section 1042 is connected between the outlet of the first heat exchange section 108 and the return port of the first-stage compressor 101. The first heat exchange component includes the fifth heat exchange section 1041, and the second heat exchange component includes the sixth heat exchange section 1042.

[0270] Heat exchange is possible between the fifth heat exchange section 1041 and the sixth heat exchange section 1042, allowing the refrigerant flowing out of the first heat exchange section 108 to exchange heat with the refrigerant flowing out of the first-stage compressor 101. This allows the lubricating oil mixed in the refrigerant flowing out of the first heat exchange section 108 to be heated by the refrigerant flowing out of the first-stage compressor 101. The heated oil has increased fluidity and flows back to the first-stage compressor 101, thus eliminating the need for an oil separator.

[0271] Optionally, the fifth heat exchange section 1041 includes a fifth heat exchange tube, the two ends of which are respectively connected to the exhaust port of the first-stage compressor 101 and the inlet of the first-stage condenser 105.

[0272] The sixth heat exchange section 1042 includes a sixth heat exchange tube, the two ends of which are connected to the outlet of the first heat exchange section 108 and the return port of the first stage compressor 101, respectively.

[0273] Heat exchange between the fifth and sixth heat exchange tubes is achieved by either placing the fifth heat exchange tube outside the sixth heat exchange tube or placing the sixth heat exchange tube outside the fifth heat exchange tube.

[0274] The fifth heat exchange tube is sleeved on the outside of the sixth heat exchange tube. For example, the fifth heat exchange tube is a copper tube with an inner diameter of 12 mm and the sixth heat exchange tube is a copper tube with an inner diameter of 4 mm. The refrigerant flowing out of the first stage compressor 101 passes through the fifth heat exchange tube (the gap between the outer wall of the fifth heat exchange tube and the inner wall of the sixth heat exchange tube), the first stage condenser 105, and the first heat exchange section 108, and then flows back to the first stage compressor 101 through the sixth heat exchange tube.

[0275] Alternatively, the sixth heat exchange tube may be sleeved on the outside of the fifth heat exchange tube. For example, the fifth heat exchange tube may be a copper tube with an inner diameter of 4 mm and the sixth heat exchange tube may be a copper tube with an inner diameter of 12 mm. The refrigerant flowing out of the first-stage compressor 101 passes through the fifth heat exchange tube, the first-stage condenser 105, and the first heat exchange section 108, and then flows back to the first-stage compressor 101 through the sixth heat exchange tube (the gap between the outer wall surface of the fifth heat exchange tube and the inner wall surface of the sixth heat exchange tube).

[0276] The fifth and / or sixth heat exchange tubes are corrugated tubes. The corrugation of the corrugated tubes enhances the turbulence of the refrigerant, which can effectively reduce the boundary layer thickness during the refrigerant flow process and enhance the heat exchange effect between the fifth and sixth heat exchange tubes.

[0277] The third, fourth, fifth, and sixth heat exchange tubes are all spiral-shaped.

[0278] Optionally, the refrigerant used in the second-stage refrigeration system 20 is miscible with the lubricating oil used in the second-stage compressor 201.

[0279] The lubricating oil can dissolve well in the refrigerant, so the refrigerant can carry the lubricating oil to flow in the second-stage refrigeration system 20. Due to the presence of the second-stage heat exchange structure 203, the lubricating oil flowing out of the second-stage evaporator 207 can be reheated by the third heat exchange section 2031, which improves the fluidity of the lubricating oil and ensures that the lubricating oil flows back to the second-stage compressor 201.

[0280] The refrigerant used in the second-stage refrigeration system 20 is R170, and does not include oil return agent.

[0281] The refrigerant used in the first-stage refrigeration system 10 is miscible with the lubricating oil used in the first-stage compressor 101.

[0282] The lubricating oil can dissolve well in the refrigerant, so the refrigerant can carry the lubricating oil to flow in the first-stage refrigeration system 10. Due to the presence of the first-stage heat exchange structure 104, the lubricating oil flowing out from the first heat exchange section 108 can be reheated by the fifth heat exchange section 1041, which improves the fluidity of the lubricating oil and ensures that the lubricating oil flows back to the first-stage compressor 101.

[0283] The refrigerant used in the first-stage refrigeration system 10 is R290, and does not include oil return agent.

[0284] Optionally, the refrigeration system also includes a regenerator, which includes a throttling device and a heat exchange pipeline. The throttling device is connected between the outlet of the first heat exchanger and the inlet of the second heat exchanger, and the heat exchange pipeline is connected between the outlet of the second heat exchanger and the return port of the compressor. The throttling device and the heat exchange pipeline are capable of heat exchange.

[0285] On the one hand, the refrigerant flowing out of the outlet of the second heat exchanger exchanges heat with the throttling device as it flows through the heat exchange pipeline, absorbing the temperature of the throttling device and increasing the temperature of the refrigerant flowing out of the outlet of the second heat exchanger, further enhancing the fluidity of the lubricating oil in the refrigerant. On the other hand, the refrigerant in the heat exchange pipeline can cool the refrigerant in the throttling device, reducing the temperature of the refrigerant in the throttling device, thereby reducing the energy consumption of the refrigeration system.

[0286] The heat exchange pipeline is located upstream of the heat exchange structure, meaning that the refrigerant flowing out of the heat exchange pipeline first passes through the second heat exchange component and then flows back to the compressor's return port.

[0287] The refrigerant temperature in the first heat exchange component is higher than that in the throttling component. Therefore, if the heat exchange pipeline is located downstream of the heat exchange structure, the refrigerant temperature will be higher after exchanging heat with the first heat exchange component in the second heat exchange component. When it flows through the heat exchange pipeline and exchanges heat with the throttling component, the heat exchange capacity will be reduced or no heat exchange will occur.

[0288] like Figure 17As shown, the regenerator includes a first-stage regenerator 107 and a second-stage regenerator 206. The first-stage regenerator 107 includes a first-stage throttling component 1071 and a first-stage heat exchange pipe 1072, and the second-stage regenerator 206 includes a second-stage throttling component 2061 and a second-stage heat exchange pipe 2062. The throttling component includes the first-stage throttling component 1071 and the second-stage throttling component 2061, and the heat exchange pipe includes the first-stage heat exchange pipe 1072 and the second-stage heat exchange pipe 2062.

[0289] The first-stage regenerator 107 is installed in the first-stage refrigeration system 10, and the second-stage regenerator 206 is installed in the second-stage refrigeration system 20.

[0290] The two ends of the first-stage throttling component 1071 are respectively connected to the outlet of the first-stage condenser 105 and the inlet of the first heat exchange section 108, such as... Figure 17 In this configuration, the two ends of the first-stage heat exchange pipeline 1072 are connected to the outlet of the first heat exchange section 108 and the return port of the first-stage compressor 101, respectively. For example... Figure 18 In the process, the two ends of the first-stage heat exchange pipeline 1072 are connected to the outlet of the first heat exchange section 108 and the inlet of the sixth heat exchange section 1042, respectively.

[0291] The two ends of the second-stage throttling component 2061 are respectively connected to the outlet of the second heat exchange section 204 and the inlet of the second-stage evaporator 207, such as... Figure 17 and Figure 18 In the middle, the two ends of the second-stage heat exchange pipeline 2062 are connected to the outlet of the second-stage evaporator 207 and the inlet of the fourth heat exchange section 2032, respectively.

[0292] Optionally, the second heat exchanger includes an evaporation pipe for supplying refrigerant flow and fins disposed on the evaporation pipe.

[0293] There are multiple evaporation pipes, each extending horizontally. These multiple evaporation pipes are arranged sequentially from top to bottom, and adjacent evaporation pipes are connected. Furthermore, the distance between adjacent evaporation pipes increases from top to bottom.

[0294] Higher-temperature air has a lower density, so it sits above lower-temperature air. Therefore, the heat exchange between the upper air and the evaporator pipes is stronger, while the heat exchange between the lower air and the evaporator pipes is relatively weaker. To address this, the distance between adjacent evaporator pipes at the top is small, while the distance between adjacent evaporator pipes at the bottom is large—that is, the evaporator pipes are denser at the top and sparser at the bottom. This arrangement fully utilizes the heat from the upper air, ensuring sufficient heat exchange between the upper evaporator pipes and the air, thus improving the heat exchange efficiency of the evaporator.

[0295] It is understandable that multiple evaporation pipes can also be evenly arranged, that is, the distance between two adjacent evaporation pipes is equal along the top-to-bottom direction.

[0296] Refrigeration equipment can be refrigerators, freezers, etc. Refrigeration equipment includes an inner liner, which defines a refrigerated space for holding the items being refrigerated.

[0297] The outer wall surface of the evaporator pipe cross-section includes a contact surface. The refrigeration equipment also includes an inner liner. The contact surface is located on the outer wall surface of the inner liner and is in contact with it, thereby achieving heat exchange between the evaporator pipe and the inner liner. The shape of the part of the inner liner that contacts the contact surface is adapted to the contact surface to increase the contact area between the evaporator pipe and the inner liner and improve the heat exchange effect between them.

[0298] For example, the contact surface is flat, and the area on the inner liner that contacts the contact surface is also flat. The contact of these two flat surfaces increases the contact area between the evaporator pipe and the inner liner. Furthermore, the flat contact surface reduces the flow area and internal volume of the evaporator pipe, further enhancing heat exchange between the refrigerant and the inner liner. The outer wall of the evaporator pipe's cross-section also includes an arc-shaped surface, with both ends connected to the ends of the contact surface. In this case, the cross-section of the evaporator pipe can be D-shaped.

[0299] For example, the bonding surface is an arc surface, and the part of the inner liner that is used to bond with the bonding surface is also an arc surface that bends in the same direction as the bonding surface. The two arc surfaces are bonded together, increasing the contact area between the evaporator pipe and the inner liner.

[0300] like Figure 17 As shown, the first-stage refrigeration system 10 includes a first-stage compressor 101, a first-stage precooler 102, a first-stage anti-condensation pipe 103, a first-stage condenser 105, a first-stage dryer filter 106, a first-stage throttling component 1071, a first-stage heat exchange section 108, a first-stage heat exchange pipeline 1072, and a first-stage gas-liquid separator 109, arranged sequentially along the flow direction of the refrigerant.

[0301] like Figure 18 As shown, the first-stage refrigeration system 10 includes a first-stage compressor 101, a first-stage precooler 102, a first-stage anti-condensation pipe 103, a fifth heat exchange section 1041, a first-stage condenser 105, a first-stage dryer filter 106, a first-stage throttling component 1071, a first heat exchange section 108, a first-stage heat exchange pipeline 1072, a first-stage gas-liquid separator 109, and a sixth heat exchange section 1042, arranged sequentially along the refrigerant flow direction.

[0302] like Figure 17 and Figure 18As shown, the second-stage refrigeration system 20 includes a second-stage compressor 201, a second-stage precooler 202, a third heat exchange section 2031, a second heat exchange section 204, a second-stage dryer filter 205, a second-stage throttling component 2061, a second-stage evaporator 207, a second-stage heat exchange pipeline 2062, and a fourth heat exchange section 2032, arranged sequentially along the flow direction of the refrigerant.

[0303] For the first-stage condenser 105, the first-stage condenser 105 is connected to the first heat exchange section 108 through the first-stage throttling component 1071. The refrigerant flowing out of the first-stage condenser 105 flows through the first heat exchange section 108, and the first heat exchange section 108 cools the refrigerant of the second-stage refrigeration system 20.

[0304] The first heat exchange section 108 and the second heat exchange section 204 together constitute the interstage heat exchanger 30, which can be an intermediate plate heat exchanger. The interstage heat exchanger 30 is also the intermediate heat exchanger in the aforementioned method for controlling the refrigeration system. The interstage heat exchanger 30 is a counter-current heat exchanger, in which the refrigerant flows in opposite directions in the first heat exchange section 108 and the second heat exchange section 204. The refrigerant in the first-stage refrigeration system 10, after being throttled by the first-stage throttling component 1071, cools the refrigerant in the second-stage refrigeration system 20 through counter-current heat exchange (first heat exchange section 108). The cooled refrigerant in the second-stage refrigeration system 20 is connected to the second-stage evaporator 207 through the second-stage throttling component 2061.

[0305] The second-stage evaporator 207 is a heat exchanger arranged from top to bottom with denser layers at the top and sparser layers at the bottom. The second-stage evaporator 207 absorbs heat from the refrigeration space. The refrigerant enters the second-stage evaporator 207 from the evaporation pipe located at the top and flows out of the second-stage evaporator 207 from the evaporation pipe located at the bottom.

[0306] The first-stage compressor 101 is used to provide the driving force for the high-temperature refrigerant.

[0307] First-stage precooler 102: Uses air to initially cool the refrigerant in the first-stage refrigeration system 10.

[0308] First-stage anti-condensation pipe 103: Used to cool the refrigerant in the first-stage refrigeration system 10 and prevent condensation at the opening of the refrigerator or freezer.

[0309] First-stage dryer filter 106: used to dry the refrigerant in the first-stage refrigeration system 10, and at the same time filter the refrigerant before it enters the first-stage throttling component 1071.

[0310] First-stage regenerator 107: This is a structure in which the first-stage heat exchange pipeline 1072 is nested within the first-stage throttling component 1071. It is used to cool the first-stage throttling component 1071 while increasing the temperature of the refrigerant returning to the first-stage compressor 101. For example, the first-stage heat exchange pipeline 1072 uses a copper tube with an inner diameter of 6mm, and the first-stage throttling component 1071 uses a capillary tube with a diameter of 1mm.

[0311] First-stage gas-liquid separator 109: Used to separate gas and liquid refrigerant to ensure that the refrigerant returned to the first-stage compressor 101 is gas.

[0312] Second-stage compressor 201: used to provide the driving force for the flow of refrigerant in the second-stage refrigeration system 20.

[0313] Second-stage precooler 202: Uses air to initially cool the refrigerant in the second-stage refrigeration system 20.

[0314] Second-stage heat exchange structure 203: used to further cool the refrigerant in the second-stage refrigeration system 20 before it enters the second heat exchange section 204, while increasing the refrigerant temperature of the second-stage compressor 201.

[0315] Second-stage regenerator 206: This is a structure in which the second-stage heat exchange pipeline 2062 is nested with the second-stage throttling component 2061. It is used to cool the second-stage throttling component 2061 while increasing the temperature of the refrigerant returning to the second-stage compressor 201. For example, the second-stage heat exchange pipeline 2062 uses a copper tube with an inner diameter of 6mm, and the second-stage throttling component 2061 uses a capillary tube with a diameter of 1mm.

[0316] Second-stage dryer filter 205: used to dry the refrigerant in the second-stage refrigeration system 20, while filtering the refrigerant before it enters the second-stage throttling component 2061.

[0317] The second-stage compressor 201 is equipped with a fan 208 to reduce the surface temperature of the second-stage compressor 201.

[0318] This application improves the cooling capacity of the second-stage refrigeration system 20 by setting up a first-stage refrigeration system 10, a second-stage refrigeration system 20, a first heat exchange section 108, a second heat exchange section 204, a regenerator, and a heat exchange structure. This enables the second-stage refrigeration system 20 to achieve ultra-low temperature refrigeration and fully utilizes the cooling capacity of the first-stage refrigeration system 10, the cooling capacity of the first throttling component, and the cooling capacity of the third heat exchange section 2031. As a result, the number of start-ups and shutdowns of the first-stage compressor 101 and the second-stage compressor 201 can be reduced, the power of the first-stage compressor 101 and the second-stage compressor 201 can be reduced, the start-up time of the first-stage compressor 101 and the second-stage compressor 201 can be reduced, and the operating conditions of the first-stage compressor 101 and the second-stage compressor 201, such as exhaust temperature and / or pressure, and suction temperature and / or pressure, can be improved.

[0319] Specifically, (1) the first-stage refrigeration system 10 and the second-stage refrigeration system 20 are respectively equipped with a first-stage regenerator 107 and a second-stage regenerator 206. The second-stage regenerator 206 utilizes the cold energy at the outlet of the second-stage evaporator 207, which increases the amount of low-temperature liquid after the second-stage throttling component 2061 throttles, thereby increasing the refrigeration capacity of the second-stage refrigeration system 20 and improving the system COP.

[0320] (2) By adding a first-stage regenerator 107, a second-stage regenerator 206, a first-stage heat exchange structure 104, and a second-stage heat exchange structure 203, excess cooling capacity is effectively utilized, while reducing the risk of liquid carryover during the return of the first-stage compressor 101 and the second-stage compressor 201.

[0321] (3) The oil separator is eliminated in the second-stage refrigeration system 20, and the second-stage refrigeration system 20 only uses R170 refrigerant, excluding the oil return agent. The cross-section of the evaporation pipe of the second-stage evaporator 207 is D-shaped, which can reduce the internal volume of the evaporation pipe. With a certain amount of refrigerant charged into the second-stage refrigeration system 20, the second-stage evaporator 207 can be filled with liquid refrigerant, achieving a full liquid state. The excess liquid in the second-stage evaporator 207 can be evaporated in the second-stage heat exchange pipe 2062 using the second-stage throttling component 2061. Thus, the refrigerant in the second-stage evaporator 207 can more easily carry the lubricating oil from the second-stage evaporator 207 back to the second-stage compressor 201. The lubricating oil can be POE (ester oil). Secondly, the second-stage refrigeration system 20 selects a refrigerant that is miscible with the lubricating oil. Finally, the problem of "oil return" of the second-stage compressor 201 is also solved under the condition that the second-stage refrigeration system 20 only uses refrigerant and does not use the oil return agent.

[0322] Optionally, such as Figure 17 and Figure 18 As shown, the refrigeration system also includes branch pipes and an expansion device.

[0323] The branch pipe is connected in parallel with the throttling device and can be opened and closed in a controlled manner; the expansion device is located in the branch pipe.

[0324] The expansion device enables the first heat exchanger to function as a condenser and the second heat exchanger to function as an evaporator when the branch pipes are connected, thus realizing the refrigeration function of the refrigeration system.

[0325] When the refrigerant temperature in the heat exchange pipe is high, the branch pipe can be opened. The refrigerant in the branch pipe does not exchange heat with the heat exchange pipe, so the heat exchange pipe cannot heat the refrigerant in the branch pipe and will not cause the refrigerant temperature in the branch pipe to rise. Therefore, the refrigeration system can achieve rapid cooling and avoid the cooling speed at start-up being affected by the setting of the regenerator.

[0326] The refrigeration system also includes switches and a processor.

[0327] The switch is located on the branch pipe and is used to control the opening and closing of the branch pipe; the processor is connected to the switch and is configured to control the switch to open when the outlet temperature of the second heat exchanger is higher than the preset temperature.

[0328] When the outlet temperature of the second heat exchanger is higher than the preset temperature, the temperature of the refrigerant in the heat exchange pipeline will also be higher. For example, if the refrigerant temperature in the heat exchange pipeline exceeds the refrigerant temperature at the throttling device, the heat exchange between the heat exchange pipeline and the throttling device will cause the refrigerant temperature in the throttling device to rise, thus slowing down the cooling speed. At this time, the processor control switch is turned on, and the branch pipeline is opened. The refrigerant flowing out of the outlet of the first heat exchanger does not pass through the throttling device, but flows into the second heat exchanger through the branch pipeline and the expansion device, achieving rapid cooling.

[0329] When the temperature of the refrigerant in the heat exchange pipeline drops to a level where heat exchange between the heat exchange pipeline and the throttling device will not cause the temperature of the refrigerant in the throttling device to rise, the control branch pipeline is closed, and the refrigerant at the outlet of the first heat exchanger flows into the second heat exchanger through the throttling device.

[0330] The processor can control the opening and closing of the switch based on the outlet temperature of the second heat exchanger, or based on the operating time. For example, the switch is turned on during the preset operating time, and turned off when the operating time exceeds the preset time.

[0331] The switch can be a solenoid valve. The expansion device can be an electronic expansion valve, a capillary tube, etc.

[0332] The branch pipeline includes a first-stage branch pipeline 110, which is connected in parallel with the first-stage throttling component 1071 and can be controlled to open and close. The expansion device includes a first-stage expansion device 111, which is located in the first-stage branch pipeline 110. The switch includes a first-stage switch 112, which is located in the first-stage branch pipeline 110 and is used to control the opening and closing of the first-stage branch pipeline 110.

[0333] The first-stage refrigeration system 10 is equipped with a first-stage branch pipe 110 and a first-stage expansion device 111. When the refrigerant temperature in the first-stage heat exchange pipe 1072 is high, the first-stage switch 112 is opened to open the first-stage branch pipe 110, so that the refrigerant flowing out of the outlet of the first-stage condenser 105 flows into the first heat exchange section 108 through the first-stage branch pipe 110 instead of passing through the first-stage throttling device 1071, thus achieving rapid cooling. As the refrigeration system operates, the refrigerant temperature in the first-stage heat exchange pipe 1072 decreases. When it decreases to a certain level (e.g., below the refrigerant temperature in the first-stage throttling device 1071), the first-stage switch 112 is closed, the first-stage branch pipe 110 is disconnected, and the refrigerant flowing out of the outlet of the first-stage condenser 105 flows into the first heat exchange section 108 through the first-stage throttling device 1071.

[0334] The branch pipeline includes a second-level branch pipeline 209, which is connected in parallel with the second-level throttling component 2061 and can be opened and closed in a controlled manner; the expansion device includes a second-level expansion device 210, which is located in the second-level branch pipeline 209.

[0335] The second-stage refrigeration system 20 is equipped with a second-stage branch pipe 209 and a second-stage expansion device 210. When the refrigerant temperature in the second-stage heat exchange pipe 2062 is high, the second-stage switch 211 is opened to open the second-stage branch pipe 209, so that the refrigerant flowing out of the outlet of the second heat exchange section 204 flows into the second-stage evaporator 207 through the second-stage branch pipe 209 instead of passing through the second-stage throttling device 2061, thus achieving rapid cooling. As the refrigeration system operates, the refrigerant temperature in the second-stage heat exchange pipe 2062 decreases. When it decreases to a certain level (e.g., below the refrigerant temperature in the second-stage throttling device 2061), the second-stage switch 211 is closed, the second-stage branch pipe 209 is disconnected, and the refrigerant flowing out of the outlet of the second heat exchange section 204 flows into the second-stage evaporator 207 through the second-stage throttling device 2061.

[0336] An embodiment of the second aspect of this application provides a refrigeration device, including a refrigeration system as described in any of the above embodiments.

[0337] The refrigeration device provided in the second aspect of this application, since it includes the refrigeration system as described in any of the above embodiments, has all the beneficial effects of the refrigeration system as described in any of the above embodiments, and will not be repeated here.

[0338] The foregoing description and accompanying drawings fully illustrate embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural 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 or substituted for parts and features of other embodiments. Embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

[0339] This disclosure provides a refrigeration device, including the refrigeration system as described above. Devices 140 and 150 (160) for controlling the refrigeration system are communicatively connected to the high-temperature stage compressor, low-temperature stage compressor, and fan of the aforementioned refrigeration system to control the speed and start / stop of the high-temperature stage compressor, low-temperature stage compressor, and fan. Device 150 (160) for controlling the refrigeration system is mounted on the refrigeration device. The mounting relationship described herein is not limited to placement inside the refrigeration device, but also includes mounting connections with other components of the refrigeration device, including but not limited to physical connections, electrical connections, or signal transmission connections. Those skilled in the art will understand that device 150 (160) for controlling the refrigeration system can be adapted to feasible product bodies to achieve other feasible embodiments.

[0340] This disclosure provides a computer-readable storage medium storing computer-executable instructions configured to perform the above-described method for controlling a refrigeration system.

[0341] 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, such as a USB flash drive, external hard drive, read-only memory (ROM), random access memory (RAM), magnetic disk, or optical disk, etc., and other media capable of storing program code.

[0342] 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.

[0343] 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.

[0344] 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.

[0345] 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 method for controlling a refrigeration system, characterized by, The refrigeration system comprises: a high-temperature stage compressor, a low-temperature stage compressor and an intermediate heat exchanger; the method comprises: obtaining the space temperature of the storage space corresponding to the refrigeration system; in the case that the space temperature meets a second set temperature condition, controlling the refrigeration system to enter a normal cooling mode; wherein, controlling the refrigeration system to enter the normal cooling mode comprises: controlling the high-temperature stage compressor to operate at a second high-temperature stage set rotating speed; controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the temperature of the intermediate heat exchanger; controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the temperature of the intermediate heat exchanger comprises: in the case that the temperature of the intermediate heat exchanger is less than or equal to a sixth temperature threshold, controlling the low-temperature stage compressor to operate at a second low-temperature stage set rotating speed; after controlling the low-temperature stage compressor to operate at the second low-temperature stage set rotating speed, controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the temperature of the intermediate heat exchanger further comprises: obtaining a new temperature of the intermediate heat exchanger and a new space temperature; adjusting the operation of the high-temperature stage compressor according to the new temperature of the intermediate heat exchanger; adjusting the operation of the low-temperature stage compressor according to the new space temperature.

2. The method of claim 1, wherein, adjusting the operation of the high-temperature stage compressor according to the new temperature of the intermediate heat exchanger comprises: in the case that the new temperature of the intermediate heat exchanger is greater than or equal to a seventh temperature threshold, increasing the rotating speed of the high-temperature stage compressor; in the case that the new temperature of the intermediate heat exchanger is less than the seventh temperature threshold and greater than an eighth temperature threshold, controlling the high-temperature stage compressor to maintain the current rotating speed; in the case that the new temperature of the intermediate heat exchanger is less than or equal to the eighth temperature threshold, decreasing the rotating speed of the high-temperature stage compressor.

3. The method of claim 1, wherein, adjusting the rotating speed of the low-temperature stage compressor according to the new space temperature comprises: in the case that the new space temperature is greater than or equal to a tenth temperature threshold, increasing the rotating speed of the low-temperature stage compressor; in the case that the new space temperature is less than the tenth temperature threshold and greater than an eleventh temperature threshold, controlling the low-temperature stage compressor to maintain the current rotating speed; in the case that the new space temperature is less than or equal to the eleventh temperature threshold, decreasing the rotating speed of the low-temperature stage compressor.

4. The method according to any one of claims 1 to 3, characterized in that, after controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the temperature of the intermediate heat exchanger, the method further comprises: re-obtaining the space temperature of the storage space; controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the re-obtained space temperature.

5. The method of claim 4, wherein, controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the re-obtained space temperature comprises: in the case that the re-obtained space temperature is less than or equal to a ninth temperature threshold, controlling the refrigeration system to exit the normal cooling mode; in the case that the re-obtained space temperature is greater than the ninth temperature threshold, re-adjusting the operation of the high-temperature stage compressor and the low-temperature stage compressor.

6. The method according to any one of claims 1 to 3, characterized in that, the second set temperature condition comprises: the space temperature is less than a first temperature threshold and greater than or equal to a twelfth temperature threshold.

7. The method according to any one of claims 1 to 3, characterized in that, after obtaining the space temperature of the storage space corresponding to the refrigeration system, the method further comprises: In a case where the space temperature of the storage space does not satisfy the first set temperature condition for entering the fast cooling mode and does not satisfy the second set temperature condition for entering the normal cooling mode, the high-temperature stage compressor and the low-temperature stage compressor are controlled to be stopped.

8. The method of claim 7, wherein, After the high-temperature stage compressor and the low-temperature stage compressor are controlled to be stopped, the method further comprises: In a case where the new space temperature is greater than or equal to the thirteenth temperature threshold, according to a temperature range in which the new space temperature is located, the refrigeration system is selectively controlled to enter the fast cooling mode or the normal cooling mode.

9. An apparatus for controlling a refrigeration system, comprising a processor and a memory having stored therein program instructions, wherein, The processor is configured to execute the method for controlling the refrigeration system as claimed in any one of claims 1 to 8 when the program instructions are executed.

10. A refrigeration system characterized by, Comprise: a high-temperature stage compressor, a low-temperature stage compressor and an intermediate heat exchanger; and, The device for controlling the refrigeration system as claimed in claim 9 is in communication connection with the high-temperature stage compressor and the low-temperature stage compressor.

11. A refrigeration appliance characterized in that, Comprise the refrigeration system as claimed in claim 10.

12. A computer readable storage medium storing program instructions, wherein the program instructions comprise instructions for causing a computer to perform the method of any one of claims 1-11. The program instructions, when executed, cause the computer to execute the method for controlling the refrigeration system as claimed in any one of claims 1 to 8.

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