Refrigeration system, Refrigeration apparatus

Abstract

The application relates to the technical field of refrigeration equipment, and discloses a refrigeration system and a refrigeration equipment. The refrigeration system comprises a compressor, a first heat exchanger and a second heat exchanger connected in sequence; a regenerator comprising a throttling component and a heat exchange pipeline capable of heat exchange, two ends of the throttling component being connected with an outlet of the first heat exchanger and an inlet of the second heat exchanger in communication, and two ends of the heat exchange pipeline being connected with an outlet of the second heat exchanger and a return gas port of the compressor in communication; a branch pipeline connected in parallel with the throttling component and capable of being controlled to be opened and closed; and an expansion device arranged in the branch pipeline. The branch pipeline is controlled to be opened and closed, when the temperature of refrigerant in the heat exchange pipeline is relatively high, the branch pipeline can be opened, the refrigerant in the branch pipeline does not exchange heat with the heat exchange pipeline, so that the heat exchange pipeline cannot heat the refrigerant in the branch pipeline, and the temperature of the refrigerant in the branch pipeline cannot be increased.

Description

Technical Field

[0001] This application relates to the field of refrigeration equipment technology, specifically to a refrigeration system and refrigeration equipment. Background Technology

[0002] Currently, refrigeration systems, especially cryogenic refrigeration systems, generally suffer from high energy consumption.

[0003] To this end, the related technology discloses a refrigeration system, including: a compressor, a first heat exchanger and a second heat exchanger connected in sequence; a regenerator, including a throttling component and a heat exchange pipeline, wherein the throttling component 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, wherein the throttling component and the heat exchange pipeline are capable of heat exchange.

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

[0005] In the refrigeration system of the relevant technology, during the initial stage of startup, the temperature of the refrigerant in the heat exchange pipeline is relatively high. As a result, when the heat exchange pipeline exchanges heat with the throttling device, the temperature of the refrigerant at the throttling device will increase, thereby reducing the cooling rate of 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 refrigeration system and refrigeration equipment to improve the cooling speed of the refrigeration system.

[0009] According to a first aspect of the present invention, a refrigeration system is provided, comprising: a compressor, a first heat exchanger, and a second heat exchanger connected in sequence; a regenerator including a throttling component capable of heat exchange and a heat exchange pipeline, wherein the two ends of the throttling component are respectively connected to the outlet of the first heat exchanger and the inlet of the second heat exchanger, and the two ends of the heat exchange pipeline are connected to the outlet of the second heat exchanger and the return port of the compressor; a branch pipeline connected in parallel with the throttling component and capable of controlled opening and closing; and an expansion device disposed on the branch pipeline.

[0010] According to a second aspect of the present invention, a refrigeration device is provided, comprising a refrigeration system as described in any of the above embodiments.

[0011] The refrigeration system and refrigeration equipment provided in this disclosure can achieve the following technical effects:

[0012] The branch pipes are opened and closed in a controlled manner. When the refrigerant temperature in the heat exchange pipe is high, the branch pipes can be opened. The refrigerant in the branch pipes does not exchange heat with the heat exchange pipes, so the heat exchange pipes cannot heat the refrigerant in the branch pipes, preventing the refrigerant temperature in the branch pipes from rising. Moreover, the branch pipes are equipped with expansion devices, so the refrigerant can be throttled when flowing through the branch pipes, achieving evaporation of the refrigerant in the second heat exchanger and realizing the cooling function of the refrigeration system. Furthermore, since the heat exchange pipes do not exchange heat with the refrigerant in the branch pipes, the refrigeration system can achieve rapid cooling.

[0013] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0014] 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:

[0015] Figure 1 This is a schematic diagram of a method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0016] Figure 2 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0017] Figure 3 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0018] Figure 4 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0019] Figure 5 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0020] Figure 6 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0021] Figure 7 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0022] Figure 8 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0023] Figure 9 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0024] Figure 10 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0025] Figure 11 This is a schematic diagram illustrating the control of compressor speed according to an embodiment of this disclosure;

[0026] Figure 12 This is a schematic diagram of another method for controlling a refrigeration system provided in an embodiment of this disclosure;

[0027] Figure 13 This is a schematic diagram illustrating the regulation of fan speed according to an embodiment of this disclosure;

[0028] Figure 14 This is a schematic diagram of a device for controlling a refrigeration system provided in an embodiment of this disclosure;

[0029] Figure 15 This is a schematic diagram of another device for controlling a refrigeration system provided in an embodiment of this disclosure;

[0030] Figure 16 This is a schematic diagram of another device for controlling a refrigeration system provided in an embodiment of this disclosure;

[0031] Figure 17 This is a schematic diagram of the structure of a refrigeration system provided in an embodiment of this disclosure;

[0032] Figure 18 This is a schematic diagram of another refrigeration system provided in an embodiment of this disclosure.

[0033] Figure label:

[0034] 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;

[0035] 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;

[0036] 30. Interstage heat exchanger;

[0037] 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;

[0038] 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;

[0039] 160. Device for controlling a refrigeration system; 161. Processor; 162. Memory; 163. Communication interface; 164. Bus. Detailed Implementation

[0040] 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.

[0041] 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.

[0042] Unless otherwise stated, the term "multiple" means two or more.

[0043] 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.

[0044] 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.

[0045] 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.

[0046] Combination Figure 1 As shown, this disclosure provides a method for controlling a refrigeration system, including:

[0047] S100, the processor obtains the space temperature of the storage space corresponding to the cooling system.

[0048] 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.

[0049] Among them, the S200 processor controls the cooling system to enter a rapid cooling mode, including:

[0050] S210, the processor controls the high-temperature stage compressor to run at the set speed of the first high-temperature stage.

[0051] 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.

[0052] 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").

[0053] T1 (where TL is the storage space temperature and T1 is the first temperature threshold) indicates that the storage space temperature meets the preset first temperature condition, meaning the temperature is too high and needs to be rapidly cooled to ensure a low-temperature storage environment for the items. Therefore, in this case, the control T1 = TL + M1, where TL is the target temperature of the low-temperature refrigeration system, ranging from -40℃ to -86℃ (default -80℃), and M1 is the temperature adjustment value for the target temperature of the low-temperature refrigeration system in rapid cooling mode, ranging from -0℃ to -20℃ (default 10℃), with an adjustment step of 1℃.

[0054] 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 high-temperature stage compressor RH2, with a range of 2000 rpm to 5000 rpm, a default value of 5000 rpm, and an adjustment step of 100 rpm.

[0055] 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.

[0056] 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.

[0057] 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.

[0058] After M2, that is, after the temperature of the storage space stabilizes, the high-temperature stage compressor and the low-temperature stage compressor start delay time are controlled according to the temperature of the intermediate heat exchanger. In the rapid cooling mode, M2 is used to control the start delay time of the low-temperature stage compressor after the high-temperature stage compressor starts. This avoids the space temperature from fluctuating. The value range of M2 is 0 to 20 minutes, with a default value of 10 minutes and an adjustment step of 1 minute.

[0059] Combination Figure 2 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0060] S100, the processor obtains the space temperature of the storage space corresponding to the cooling system.

[0061] 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.

[0062] The processor controls the cooling system to enter a rapid cooling mode, including:

[0063] S210, the processor controls the high-temperature stage compressor to run at the set speed of the first high-temperature stage.

[0064] 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.

[0065] T2 (where th is the temperature of the intermediate heat exchanger; T2 is the second temperature threshold, and also the target temperature TH1 of the high-temperature stage refrigeration system in rapid cooling mode) 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 low RL2. In rapid cooling mode, the purpose of setting the low-temperature stage compressor to the highest 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 when the specific heat capacity and temperature difference remain unchanged, increasing the refrigerant flow rate m can increase the cooling capacity, thereby reducing the temperature to the target temperature as quickly as possible. The value range of RL2 is 2000rpm to 5000rpm, with a default value of 5000rpm and an adjustment step of 100rpm. Optionally, the value range of TH1 (small TH1) is -55℃ to 0, with a default value of -25℃ and an adjustment step of 1℃.

[0066] Combination Figure 3 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0067] S100, the processor obtains the space temperature of the storage space corresponding to the cooling system.

[0068] 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.

[0069] The processor controls the cooling system to enter a rapid cooling mode, including:

[0070] S210, the processor controls the high-temperature stage compressor to run at the set speed of the first high-temperature stage.

[0071] S221. When the temperature of the intermediate heat exchanger is less than or equal to the second temperature threshold, the processor controls the low-stage compressor to operate at the first low-stage set speed.

[0072] S222. The processor obtains the new temperature of the intermediate heat exchanger.

[0073] S223. The processor adjusts the operation of the high-stage compressor and the low-stage compressor according to the new temperature of the intermediate heat exchanger.

[0074] 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 on the premise of ensuring the refrigeration temperature, the energy consumption can also be reduced.

[0075] th′≥T3 (th′ is the new temperature of the intermediate heat exchanger, and T3 is the third temperature threshold), which indicates 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 T3 = TH1 + M3, where M3 is the intermediate heat exchanger temperature upward adjustment value in the rapid cooling mode, with a value range of 0 to 20 °C, the default value is 3 °C, and the step size is 1 °C.

[0076] T4 < th′ < T3 (T4 is the fourth temperature threshold), which indicates 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, at the initial stage of cooling, due to the refrigerant heat recovery 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 in 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 reach a relatively stable state quickly. 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.

[0077] When 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, which in turn reduces 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, and at the same time, the refrigerating capacity of the low-temperature stage refrigeration system can be increased.

[0078] 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, not only can sufficient refrigerating capacity be provided, but also the excess of refrigerating capacity can be avoided, and the repeated start and stop of the compressor can be avoided, thereby realizing the reduction of the energy consumption of the refrigeration system.

[0079] M0. That is, after the temperature of the storage space to be stored 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 from 10 seconds to 120 seconds, with a default value of 20 seconds and an adjustment step of 5 seconds.

[0080] When T4 < th′ < T3, when the processor controls both the high-temperature stage compressor and the low-temperature stage compressor to maintain their current speeds unchanged, after the first pre-M5, the low-temperature stage compressor is controlled to operate at its maximum speed RL2. In this way, at 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, which makes the suction temperature of the low-temperature stage compressor decrease, and the discharge temperature decreases simultaneously. The condensation pressure of the low-temperature stage refrigeration system decreases. At this time, the speed of the low-temperature stage compressor can be increased to obtain a larger refrigerating capacity.

[0081] M5 is the time for the compressor speed to be stably maintained in the rapid cooling mode, and its value range is from 5 minutes to 60 minutes, with a default value of 10 minutes and an adjustment step of 5 minutes.

[0082] Combined with Figure 4 As shown, another method for controlling a refrigeration system provided by an embodiment of the present disclosure includes:

[0083] S100, the processor obtains the space temperature of the storage space corresponding to the refrigeration system.

[0084] 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.

[0085] The processor controls the cooling system to enter a rapid cooling mode, including:

[0086] S210, the processor controls the high-temperature stage compressor to run at the set speed of the first high-temperature stage.

[0087] 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.

[0088] S300, the processor re-acquires the temperature of the storage space.

[0089] 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.

[0090] 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.

[0091] 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, at this time, the refrigeration system is controlled to exit the rapid cooling mode. Simultaneously, the high-temperature compressor is controlled. T5 = TL + M6, where M6 is the sensor's 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℃.

[0092] If tl′>T5, it indicates that the temperature of the storage space is too high, requiring further cooling to provide additional 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.

[0093] 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.

[0094] Combination Figure 5 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0095] S500: The processor obtains the temperature of the storage space corresponding to the cooling system.

[0096] In the S600, the processor controls the cooling system to enter normal cooling mode when the ambient temperature meets the second set temperature condition.

[0097] Among them, the S600 processor controls the cooling system to enter normal cooling mode, including:

[0098] S610, the processor controls the high-temperature stage compressor to run at the second high-temperature stage set speed.

[0099] 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.

[0100] 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").

[0101] 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.

[0102] When the refrigeration system enters normal cooling mode, the high-temperature stage compressor is first controlled to operate at the second high-temperature stage set speed, which is equivalent to controlling the high-temperature stage compressor to start. This allows the refrigerant circulation loop of the high-temperature stage compressor to exchange heat with 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 second high-temperature stage set speed is lower than the first high-temperature stage set speed. Optionally, the second high-temperature stage set speed is the maximum RH1 of the high-temperature 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.

[0103] 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 second 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.

[0104] The method for controlling a refrigeration system provided in this disclosure determines whether the storage space requires normal cooling based on its temperature. 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 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.

[0105] 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.

[0106] Temperature thresholds T1 and tl ≥ T12, where tl is the temperature of the storage space, T1 is the first temperature threshold, and T12 is the twelfth temperature threshold. At temperature T1, the refrigeration system does not meet the conditions for entering rapid cooling mode. When the space temperature also satisfies tl ≥ T12, the refrigeration system meets the conditions for entering normal mode.

[0107] T12 = TL + M8, where TL is the target temperature of the low-temperature refrigeration system, ranging from -40℃ to -86℃, with a default value of -80℃. M8 is the adjustment value for the space temperature under normal cooling mode, which is 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℃.

[0108] After M9, that is, after the space temperature stabilizes, the high-temperature stage compressor and the low-temperature stage compressor are controlled according to the temperature of the intermediate heat exchanger. M9 is the start-up delay time of the low-temperature stage compressor after the high-temperature stage compressor starts in normal cooling mode. In this way, the value range of M9 for the storage space is 0 to 20 minutes, the default value is 1 minute, and the adjustment step is 1 minute.

[0109] Combination Figure 6 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0110] S500: The processor obtains the temperature of the storage space corresponding to the cooling system.

[0111] In the S600, the processor controls the cooling system to enter normal cooling mode when the ambient temperature meets the second set temperature condition.

[0112] Among them, the S600 processor controls the cooling system to enter normal cooling mode, including:

[0113] S610, the processor controls the high-temperature stage compressor to run at the second high-temperature stage set speed.

[0114] 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.

[0115] T6 (where th is the temperature of the intermediate heat exchanger; T6 is the sixth temperature threshold, also the target temperature TH2 of the high-temperature stage refrigeration system in normal cooling mode) 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 excessive cooling capacity and energy waste. Optionally, the second low-temperature stage set speed is lower than the first RL1 because: at low speeds, the compressor experiences less mechanical loss, making it easier to achieve a higher COP (Coefficient of Performance, the ratio of energy to heat, or simply energy efficiency ratio), hence operating at the lowest speed. The value range is 2000 rpm to 5000 rpm, with a default value of 2000 rpm and an adjustment step of 100 rpm.

[0116] 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℃.

[0117] Combination Figure 7 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0118] S500: The processor obtains the temperature of the storage space corresponding to the cooling system.

[0119] In the S600, the processor controls the cooling system to enter normal cooling mode when the ambient temperature meets the second set temperature condition.

[0120] Among them, the S600 processor controls the cooling system to enter normal cooling mode, including:

[0121] S610, the processor controls the high-temperature stage compressor to run at the second high-temperature stage set speed.

[0122] 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.

[0123] S622, the processor obtains the new temperature of the intermediate heat exchanger and the new space temperature.

[0124] S623, the processor adjusts the operation of the high-temperature stage compressor based on the new temperature of the intermediate heat exchanger.

[0125] The S624 processor adjusts the operation of the cryogenic stage compressor based on the new space temperature.

[0126] 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.

[0127] 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, allowing it to better match the operating conditions of the low-temperature stage compressor. This means the high-temperature stage compressor can react quickly to changes in the speed of the low-temperature stage compressor, thus improving energy efficiency and reducing consumption in the refrigeration system. M10 refers to obtaining the new temperature of the intermediate heat exchanger after the space temperature has stabilized, which helps reduce the energy consumption of the refrigeration system. M10 is the time interval for adjusting the speed of the high-temperature stage compressor in normal cooling mode, ranging from 10 to 120 seconds, with a default value of 30 seconds and an adjustment step of 5 seconds.

[0128] After M11, the storage space temperature is re-acquired, and the operation of the low-temperature stage compressor is controlled based on this re-acquired temperature. M11 > M10. Thus, after waiting for the sixth set time M11, once the space temperature stabilizes, 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. Therefore, within different timing cycles, the adjustment time interval for the high-temperature stage compressor and the low-temperature stage compressor speed (M11 is the low-temperature stage compressor speed adjustment time interval in normal cooling mode), ranging from 10 seconds to 120 seconds, with a default of 60 seconds and an adjustment step of 5 seconds, is determined.

[0129] Optionally, in S623, the processor adjusts the operation of the high-stage compressor according to the new temperature of the intermediate heat exchanger, including:

[0130] When the new temperature of the intermediate heat exchanger is greater than or equal to the seventh temperature threshold, the processor increases the rotational speed of the high-stage compressor.

[0131] 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 the current rotational speed.

[0132] When the new temperature of the intermediate heat exchanger is less than or equal to the eighth temperature threshold, the processor decreases the rotational speed of the high-stage compressor. th′≥T7 (th′ is the new temperature of the intermediate heat exchanger, and T7 is the seventh temperature threshold), indicating that after the low-stage compressor operates at the second low-stage set rotational speed, the temperature of the intermediate heat exchanger is still relatively high, and the refrigerating capacity is insufficient to provide a low-temperature environment for the storage space. Therefore, at this time, 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, and M12 is the upward adjustment value of the rotational speed of the high-stage compressor in the normal cooling mode, which is greater than or equal to 0. The value range of M12 is 0 to 20°C, with a default value of 3°C and an adjustment step of 1°C.

[0133] T8<th′<T7 (T8 is the eighth temperature threshold), indicating that after the low-stage compressor operates at the second low-stage set rotational speed, the temperature of the intermediate heat exchanger is within the appropriate range. Therefore, at this time, control the high-stage compressor to maintain the current rotational speed unchanged. In this way, by controlling the high-stage pressure T8 = TH2 + M13, where M13 is less than or equal to 0, which is the downward adjustment value of the rotational speed of the high-stage compressor in the normal cooling mode, less than or M13 has a value range of -20°C to 0, with a default value of -3°C and an adjustment step of 1°C.

[0134] th′≤T8, indicating that after the low-stage compressor operates at the second low-stage set rotational speed, the temperature of the intermediate heat exchanger is relatively low, and the refrigerating capacity is excessive. Therefore, at this time, decrease the rotational speed of the high-stage compressor, so as to reduce unnecessary energy consumption.

[0135] 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 rotational speed of the high-stage compressor is adjusted, which can not only provide sufficient refrigerating capacity, but also avoid excessive refrigerating capacity and prevent the compressor from starting and stopping repeatedly, thereby reducing the energy consumption of the refrigeration system.

[0136] In S623, the processor adjusts the operation of the low-stage compressor according to the new space temperature, including:

[0137] 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.

[0138] 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 the current rotational speed.

[0139] 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. tl″≥T10 (tl″ is the new space temperature of the storage space, T10 is the tenth temperature threshold), indicating that the space temperature is relatively high and needs to be reduced. T11<tl″<T10 (T11 is the eleventh temperature threshold), indicating that the space temperature is within the appropriate temperature range, then control the low-temperature stage compressor. tl″≤T11, indicating that the space temperature is relatively low, which will cause waste of cooling capacity, so the rotational speed of the low-temperature compressor is reduced 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. 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, greater than or the range of M14 is from 0 to 5 °C, the default value is 1 °C, and the adjustment step is 0.1 °C.

[0140] 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, less than or the range of M15 is from -5 °C to 0, the default value is -1.5 °C, and the adjustment step is 0.1 °C.

[0141] Combined with Figure 8 As shown, another method for controlling a refrigeration system provided by an embodiment of the present disclosure includes:

[0142] S500, the processor obtains the space temperature of the storage space corresponding to the refrigeration system.

[0143] S600, when the space temperature satisfies the second set temperature condition, the processor controls the refrigeration system to enter the normal cooling mode.

[0144] Among them, S600, the processor controls the refrigeration system to enter the normal cooling mode, including:

[0145] S610, the processor controls the high-temperature stage compressor to operate at the second high-temperature stage set rotational speed.

[0146] S620, the processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the temperature of the intermediate heat exchanger.

[0147] S700, the processor re-acquires the temperature of the storage space.

[0148] The S800 processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the reacquired space temperature.

[0149] 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.

[0150] 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, at this time, the refrigeration system is controlled to exit the normal cooling mode. Simultaneously, the high-temperature stage compressor T9 = TL + M8 can be controlled, where TL is the target temperature of the low-temperature stage refrigeration system, with a value range of -40℃ to -80℃ and a default value of -80℃. 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, with a default value of -1℃ and an adjustment step of 0.1℃.

[0151] If tl′>T9, it means that the storage space has not reached the target space temperature. Then, the operation of the high-temperature compressor and the low-temperature compressor will be readjusted. That is, S622 will be executed again after M10, and S623 will be executed again after the sixth set time M10.

[0152] 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.

[0153] Combination Figure 9 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0154] S500: The processor obtains the temperature of the storage space corresponding to the cooling system.

[0155] In the S600, the processor controls the cooling system to enter normal cooling mode when the ambient temperature meets the second set temperature condition.

[0156] Among them, the S600 processor controls the cooling system to enter normal cooling mode, including:

[0157] S610, the processor controls the high - temperature - stage compressor to operate at the second high - temperature - stage set speed.

[0158] S620, the processor controls the operation of the high - temperature - stage compressor and the low - temperature - stage compressor according to the temperature of the intermediate heat exchanger.

[0159] S700, the processor re - obtains the space temperature of the storage space.

[0160] S800, the processor controls the operation of the high - temperature - stage compressor and the low - temperature - stage compressor according to the re - obtained space temperature.

[0161] S900, after executing S500, when the space temperature of the storage space 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 stop.

[0162] After obtaining the space temperature of the storage space corresponding to the refrigeration system, it is judged whether the space temperature meets the first set - temperature condition and T1, and tl < T12, indicating that the space temperature is relatively low at this time and there is no need for the refrigeration system to provide cooling capacity. Therefore, the high - temperature - stage compressor and the low - temperature - stage compressor are controlled to stop, and at the same time, all the fans can be controlled to stop. In this way, controlling all the compressors and all the fans to stop when refrigeration is not necessary can reduce the energy consumption of the refrigeration system.

[0163] Combined Figure 10 As shown, another method for controlling a refrigeration system provided by an embodiment of the present disclosure includes:

[0164] S500, the processor obtains the space temperature of the storage space corresponding to the refrigeration system.

[0165] S600, when the space temperature meets the second set - temperature condition, the processor controls the refrigeration system to enter the normal cooling mode.

[0166] Among them, for S600, the processor controls the refrigeration system to enter the normal cooling mode, including:

[0167] S610, the processor controls the high - temperature - stage compressor to operate at the second high - temperature - stage set speed.

[0168] S620, the processor controls the operation of the high - temperature - stage compressor and the low - temperature - stage compressor according to the temperature of the intermediate heat exchanger.

[0169] S700, the processor re - obtains the space temperature of the storage space.

[0170] The S800 processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the reacquired space temperature.

[0171] 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.

[0172] 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.

[0173] After the high-temperature and low-temperature compressors are shut down, the storage space temperature is continuously acquired, and it is determined that the new storage space temperature tl″′ ≥ T13 (tl″′ is the new storage space temperature acquired after the compressors are shut down, and T13 is the thirteenth temperature threshold). This indicates whether the storage 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 storage space temperature, the storage space temperature can be reduced to a suitable low temperature range, and the appropriate compressor speed can be matched to avoid excessive cooling capacity, thereby reducing the energy consumption of the refrigeration system.

[0174] 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℃.

[0175] 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:

[0176] S1101, the processor obtains the temperature of the storage space.

[0177] TL+M1; if yes, execute S1103; if no, execute S1113.

[0178] Running on RH2.

[0179] After M2 minutes, when the temperature of the intermediate heat exchanger meets th≤TH1, control the cryogenic stage compressor to run at speed RL2.

[0180] M0 seconds.

[0181] TH1+M3; if yes, execute S1107; if no, execute S1108.

[0182] 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.

[0183] TH1+M4; if yes, execute S1109; if no, execute S1110.

[0184] 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.

[0185] After M5 minutes, control the cryogenic stage compressor to run at speed RL2; then execute S1111.

[0186] TL+M6; if yes, execute S1112; if no, execute S1105.

[0187] S1112, the processor exits rapid cooling mode.

[0188] TL+M8; if yes, execute S1114; if no, execute S1129.

[0189] Running on RH1.

[0190] After M9 minutes, when the temperature of the intermediate heat exchanger meets th≤TH2, control the cryogenic stage compressor to run at speed RL1; then execute S1116 and S1123.

[0191] M10 seconds.

[0192] TH2+M12; if yes, execute S1118; if no, execute S1119.

[0193] S1118, the processor increases the speed of the high-temperature stage compressor, and then executes S1122.

[0194] TH2+M13; if yes, execute S1120; if no, execute S1121.

[0195] S1120, reduce the speed of the high-temperature stage compressor, and then execute S1122.

[0196] S1121, the processor maintains the speed of the high-temperature stage compressor, and then executes S1122.

[0197] TL+M8; if yes, execute S1131; if no, execute S1116 and S1123.

[0198] M11 seconds.

[0199] TL+M14; if yes, execute S1125; if no, execute S1126.

[0200] S1125, the processor increases the speed of the cryogenic stage compressor, and then executes S1122.

[0201] TL+M15; if yes, execute S1127; if no, execute S1128.

[0202] S1127, the processor reduces the speed of the cryogenic stage compressor, and then executes S1122.

[0203] S1128, the processor maintains the speed of the cryogenic stage compressor, and then executes S1122.

[0204] S1129, the processor controls the shutdown of the high-temperature stage compressor, the low-temperature stage compressor, and all fans.

[0205] TL+M7; if yes, execute S1102; if no, execute S1129.

[0206] S1131, Exit normal cooling mode.

[0207] Combination Figure 12 As shown, this disclosure provides another method for controlling a refrigeration system, including:

[0208] 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.

[0209] 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.

[0210] 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.

[0211] By using the method for controlling a refrigeration system provided in the embodiments of the present disclosure, based on the operating state of the high-stage compressor and the outlet temperature of the condenser of the high-stage refrigeration system, the operation of the fan is controlled. The fan speed and the on / off operating state can be automatically adjusted according to the cooling air volume required by the condenser of the high-stage refrigeration system, so that the air volume matches the operating state of the refrigeration system, reducing noise and prolonging the life of the fan at the same time.

[0212] Optionally, in S1200, the processor controls the operation of the fan according to the operating state of the high-stage compressor and the outlet temperature of the condenser, including:

[0213] When the high-stage compressor starts, the processor:

[0214] The processor determines the target fan speed corresponding to the outlet temperature of the condenser of the current high-stage refrigeration system according to the correlation between the outlet temperature of the condenser of the high-stage refrigeration system and the fan speed.

[0215] The processor controls all fans to operate at the target speed.

[0216] The correlation between the outlet temperature of the condenser of the high-stage refrigeration system (hereinafter referred to as "the outlet temperature of the condenser") and the fan speed is pre-stored in the memory of the refrigeration system. When the high-stage compressor starts, it means that the refrigeration system is operating for refrigeration. Then the processor calls the above 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 speed of the fan, and further the air volume required by the refrigeration system is matched, reducing noise.

[0217] 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, when the temperature range ≥ T14, where tc is the outlet temperature of the condenser and T14 is the fourteenth temperature threshold), the corresponding fan speed is the first set speed. When T15 < tc < T14, where T15 is the fifteenth temperature threshold), the corresponding fan speed is the second set speed. When the outlet of the condenser ≤ 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 is matched with different fan speeds, and the fan can be adjusted to an appropriate speed, avoiding insufficient or overshoot of speed adjustment.

[0218] It should be noted that those skilled in the art can divide the temperature range as needed, thereby corresponding to more fan speed settings, so as to more accurately adjust the fan speed.

[0219] T14 = ta + M16, where ta is the ambient temperature and M16 is the upper limit of temperature adjustment, which is greater than or equal to 0. The value range of M16 is 0 to 20℃, with a default value of 4℃ and an adjustment step of 0.5℃.

[0220] T15 = ta + M17, where M17 is the lower limit of temperature adjustment, greater than or equal to 0. The value of M17 ranges from 0℃ to 10℃, with a default value of 2℃ and an adjustment step of 0.5℃.

[0221] After M18, the condenser outlet temperature is reacquired, and based on the reacquired outlet temperature, the fan speed control logic described above is followed. After M18, the condenser outlet temperature is stabilized to ensure the accuracy of subsequent adjustments to the fan speed.

[0222] M18 is the fan speed adjustment time interval, ranging from 10 seconds to 120 seconds, with a default value of 30 seconds and an adjustment step of 5 seconds.

[0223] 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.

[0224] The following will combine Figure 13 The following details the regulation of fan speed in the embodiments of this disclosure:

[0225] S1301, the processor obtains the operating status of the high-temperature stage compressor.

[0226] S1302, the processor determines whether the high-temperature stage compressor has started; if yes, execute S1303, if no, execute S1309. +M16; if yes, execute S1304; if no, execute S1305.

[0227] S1304, the processor controls all fans to run at maximum speed, and then executes S1308.

[0228] +M17; if yes, execute S1306; if no, execute S1307.

[0229] S1306, the processor controls all fans to run at intermediate speed, and then executes S1308.

[0230] S1307, the processor controls all fans to run at the lowest speed, and then executes S1308.

[0231] M18 seconds, then execute S1303.

[0232] S1309, the processor delays for 1 minute, and then executes S1301.

[0233] 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.

[0234] 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.

[0235] 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.

[0236] 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.

[0237] 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.

[0238] 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.

[0239] 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.

[0240] 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.

[0241] 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.

[0242] 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.

[0243] 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.

[0244] 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.

[0245] 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.

[0246] 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.

[0247] 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.

[0248] 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.

[0249] 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.

[0250] 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.

[0251] 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.

[0252] 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.

[0253] 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.

[0254] 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.

[0255] 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.

[0256] 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.

[0257] 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.

[0258] 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).

[0259] 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.

[0260] 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.

[0261] 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.

[0262] 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.

[0263] 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.

[0264] 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.

[0265] 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.

[0266] 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).

[0267] 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.

[0268] The third, fourth, fifth, and sixth heat exchange tubes are all spiral-shaped.

[0269] Optionally, the refrigerant used in the second-stage refrigeration system 20 is miscible with the lubricating oil used in the second-stage compressor 201.

[0270] 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.

[0271] The refrigerant used in the second-stage refrigeration system 20 is R170, and does not include oil return agent.

[0272] The refrigerant used in the first-stage refrigeration system 10 is miscible with the lubricating oil used in the first-stage compressor 101.

[0273] 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.

[0274] The refrigerant used in the first-stage refrigeration system 10 is R290, and does not include oil return agent.

[0275] 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.

[0276] 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.

[0277] 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.

[0278] 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.

[0279] 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.

[0280] 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.

[0281] 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 middle, 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.

[0282] 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.

[0283] Optionally, the second heat exchanger includes an evaporation pipe for supplying refrigerant flow and fins disposed on the evaporation pipe.

[0284] 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.

[0285] 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.

[0286] 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.

[0287] Refrigeration equipment can be refrigerators, freezers, etc. Refrigeration equipment includes an inner liner, which defines a refrigerated space for holding the items being refrigerated.

[0288] 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.

[0289] 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.

[0290] 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.

[0291] 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.

[0292] 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.

[0293] 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.

[0294] 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.

[0295] 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.

[0296] 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.

[0297] The first-stage compressor 101 is used to provide the driving force for the high-temperature refrigerant.

[0298] First-stage precooler 102: Uses air to initially cool the refrigerant in the first-stage refrigeration system 10.

[0299] 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.

[0300] 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.

[0301] 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.

[0302] 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.

[0303] Second-stage compressor 201: used to provide the driving force for the flow of refrigerant in the second-stage refrigeration system 20.

[0304] Second-stage precooler 202: Uses air to initially cool the refrigerant in the second-stage refrigeration system 20.

[0305] 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.

[0306] 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.

[0307] 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.

[0308] The second-stage compressor 201 is equipped with a fan 208 to reduce the surface temperature of the second-stage compressor 201.

[0309] 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 exchanger 108, a second heat exchanger 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 exchanger 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.

[0310] 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.

[0311] (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.

[0312] (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.

[0313] Optionally, such as Figure 17 and Figure 18 As shown, the refrigeration system also includes branch pipes and an expansion device.

[0314] 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.

[0315] 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.

[0316] 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.

[0317] The refrigeration system also includes switches and a processor.

[0318] 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.

[0319] 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.

[0320] 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.

[0321] 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.

[0322] The switch can be a solenoid valve. The expansion device can be an electronic expansion valve, a capillary tube, etc.

[0323] 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.

[0324] 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.

[0325] 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.

[0326] 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.

[0327] 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.

[0328] 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.

[0329] 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.

[0330] 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.

[0331] This disclosure provides a computer-readable storage medium storing computer-executable instructions configured to perform the above-described method for controlling a refrigeration system.

[0332] 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.

[0333] 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.

[0334] 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.

[0335] 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.

[0336] 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 refrigeration system characterized by, The application relates to a refrigeration system. The refrigeration system comprises a compressor, a first heat exchanger and a second heat exchanger connected in sequence. The regenerator comprises a throttling component and a heat exchange pipeline, the two ends of the throttling component are connected with the outlet of the first heat exchanger and the inlet of the second heat exchanger respectively, and the two ends of the heat exchange pipeline are connected with the outlet of the second heat exchanger and the back gas outlet of the compressor. The branch pipeline is connected with the throttling component in parallel and can be controlled to be opened and closed. The expansion device is arranged in the branch pipeline. The switch is arranged in the branch pipeline and is used for controlling the opening and closing of the branch pipeline. The processor is connected with the switch and is configured to control the switch to be opened so as to make the branch pipeline conductive when the outlet temperature of the second heat exchanger is higher than a preset temperature. The compressor comprises a first-stage compressor and a second-stage compressor, the first heat exchanger comprises a first-stage condenser and a first heat exchange part, the second heat exchanger comprises a second heat exchange part and a second-stage evaporator, and the first heat exchange part and the second heat exchange part can exchange heat.

2. The refrigeration system of claim 1, wherein, The regenerator comprises: The first-stage regenerator comprises a first-stage throttling component and a first-stage heat exchange pipeline, the two ends of the first-stage throttling component are connected with the outlet of the first-stage condenser and the inlet of the first heat exchange part respectively, the two ends of the first-stage heat exchange pipeline are connected with the outlet of the first heat exchange part and the back gas outlet of the first-stage compressor respectively, and the first-stage throttling component and the first-stage heat exchange pipeline can exchange heat. The branch pipeline comprises a first-stage branch pipeline, the first-stage branch pipeline is connected with the first-stage throttling component in parallel and can be controlled to be opened and closed. The expansion device comprises a first-stage expansion device, and the first-stage expansion device is arranged in the first-stage branch pipeline. The throttling component comprises a first-stage throttling component, and the heat exchange pipeline comprises a first-stage heat exchange pipeline.

3. The refrigeration system of claim 1, wherein, The regenerator comprises: The second-stage regenerator comprises a second-stage throttling component and a second-stage heat exchange pipeline, the two ends of the second-stage throttling component are connected with the outlet of the second heat exchange part and the inlet of the second-stage evaporator respectively, the two ends of the second-stage heat exchange pipeline are connected with the outlet of the second-stage evaporator and the back gas outlet of the second-stage compressor respectively, and the second-stage throttling component and the second-stage heat exchange pipeline can exchange heat. The branch pipeline comprises a second-stage branch pipeline, the second-stage branch pipeline is connected with the second-stage throttling component in parallel and can be controlled to be opened and closed. The expansion device comprises a second-stage expansion device, and the second-stage expansion device is arranged in the second-stage branch pipeline. The throttling component comprises a second-stage throttling component, and the heat exchange pipeline comprises a second-stage heat exchange pipeline.

4. The refrigeration system of any of claims 1 to 3, wherein, The heat exchange structure comprises a first heat exchange component and a second heat exchange component, the first heat exchange component is connected between the back gas outlet 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 back gas outlet of the compressor. The heat exchange structure comprises:

5. The refrigeration system of claim 4, wherein, ​ The second-stage heat exchange structure comprises a third heat exchange part and a fourth heat exchange part capable of heat exchange, the third heat exchange part is communicated between the exhaust port of the second-stage compressor and the inlet of the second heat exchange part, and the fourth heat exchange part is communicated between the outlet of the second-stage evaporator and the return air port of the second-stage compressor, wherein the first heat exchange member comprises the third heat exchange part, and the second heat exchange member comprises the fourth heat exchange part.

6. The refrigeration system of claim 4 wherein, The heat exchange structure comprises: The first-stage heat exchange structure comprises a fifth heat exchange part and a sixth heat exchange part capable of heat exchange, the fifth heat exchange part is communicated between the exhaust port of the first-stage compressor and the inlet of the first-stage condenser, and the sixth heat exchange part is communicated between the outlet of the first heat exchange part and the return air port of the first-stage compressor, wherein the first heat exchange member comprises the fifth heat exchange part, and the second heat exchange member comprises the sixth heat exchange part.

7. A refrigeration appliance characterized in that, The refrigeration system comprises the refrigeration system according to any one of claims 1 to 6.

8. The refrigeration appliance of claim 7, wherein, The second heat exchanger comprises: The evaporation pipeline has an outer wall surface of a cross section comprising a fitting surface; The refrigeration equipment further comprises: The inner container is fitted with the fitting surface, and the shape of the fitting surface fitted with the inner container is adapted to the fitting surface.

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