Refrigeration system, Refrigeration apparatus

Abstract

This application relates to the field of refrigeration equipment technology, and discloses a refrigeration system and refrigeration equipment. The refrigeration system includes: a compressor, a first heat exchanger, and a second heat exchanger connected in sequence; a heat exchange structure including a first heat exchange component and a second heat exchange component capable of heat exchange, the first heat exchange component being connected between the compressor's exhaust port and the first heat exchanger's inlet, and the second heat exchange component being connected between the second heat exchanger's outlet and the compressor's return port. Lubricating oil mixed in the refrigerant flowing out of the second heat exchanger can be heated by the refrigerant flowing out of the compressor's exhaust port. After being heated, the oil's fluidity increases, and the oil flows back to the compressor, thereby eliminating the need for an oil separator.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of refrigeration equipment, in particular to a refrigeration system and a refrigeration equipment. BACKGROUND

[0002] At present, the refrigeration system, especially the ultra-low temperature refrigeration system, has the problem of high energy consumption.

[0003] Therefore, the related technology discloses a cascade refrigeration system, which simultaneously uses an evaporator in one loop as a condenser for cooling refrigerant in another loop, thereby reducing the energy consumption of the refrigeration system.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related technology:

[0005] The refrigeration system in the related technology needs to be provided with an oil separator, resulting in high cost of the refrigeration system.

[0006] It should be noted that the information disclosed in the above background section is only used to strengthen the understanding of the background of the present application, and therefore can include information that does not constitute prior art known to those of ordinary skill in the art. SUMMARY

[0007] In order to have a basic understanding of some aspects of the disclosed embodiments, the following is a simple summary. The summary is not a general review, nor is it intended to determine the key / important components or to delineate the protection scope of these embodiments, but as a prelude to the detailed description below.

[0008] The embodiments of the present disclosure provide a refrigeration system and a refrigeration equipment to solve the problem of high cost of the refrigeration system caused by the need to set an oil separator in the refrigeration system in the related technology.

[0009] According to a first aspect of the embodiments of the present application, a refrigeration system is provided, comprising: a compressor, a first heat exchanger and a second heat exchanger connected in sequence; a heat exchange structure comprising a first heat exchange member and a second heat exchange member capable of heat exchange, the first heat exchange member being communicated between the exhaust port of the compressor and the inlet of the first heat exchanger, and the second heat exchange member being communicated between the outlet of the second heat exchanger and the return gas port of the compressor.

[0010] According to a second aspect of the embodiments of the present application, a refrigeration equipment is provided, comprising the refrigeration system according to any one of the above embodiments.

[0011] The refrigeration system and the refrigeration equipment provided by the embodiments of the present disclosure can achieve the following technical effects:

[0012] The first heat exchange component and the second heat exchange component can exchange heat, so that the refrigerant flowing out of the second heat exchanger can exchange heat with the refrigerant flowing out of the discharge port of the compressor. In this way, the lubricating oil mixed in the refrigerant flowing out of the second heat exchanger can be heated by the refrigerant flowing out of the discharge port of the compressor, and the oil is heated to enhance the flowability, and the oil is returned to the compressor, so that the oil separator can be cancelled.

[0013] The foregoing general description and the following description are merely exemplary and explanatory and are not intended to limit the application. BRIEF DESCRIPTION OF DRAWINGS

[0014] One or more embodiments are illustrated by way of example with reference to the accompanying drawings, which are schematic and are not intended to be limiting of the embodiments, in which like reference numerals refer to like elements in the various figures and in which:

[0015] Figure 1 is a schematic diagram of a method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0016] Figure 2 is a schematic diagram of another method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0017] Figure 3 is a schematic diagram of another method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0018] Figure 4 is a schematic diagram of another method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0019] Figure 5 is a schematic diagram of another method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0020] Figure 6 is a schematic diagram of another method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0021] Figure 7 is a schematic diagram of another method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0022] Figure 8 is a schematic diagram of another method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0023] Figure 9 is a schematic diagram of another method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0024] Figure 10 is a schematic diagram of another method for controlling a refrigeration system provided by an embodiment of the present disclosure;

[0025] Figure 11 is a schematic diagram of the regulation of the compressor speed provided by the embodiments of the present disclosure;

[0026] Figure 12 is a schematic diagram of another method for controlling a refrigeration system provided by the embodiments of the present disclosure;

[0027] Figure 13 is a schematic diagram of the regulation of the fan speed provided by the embodiments of the present disclosure;

[0028] Figure 14 is a schematic diagram of a device for controlling a refrigeration system provided by the embodiments of the present disclosure;

[0029] Figure 15 is a schematic diagram of another device for controlling a refrigeration system provided by the embodiments of the present disclosure;

[0030] Figure 16 is a schematic diagram of another device for controlling a refrigeration system provided by the embodiments of the present disclosure;

[0031] Figure 17 is a structural schematic diagram of a refrigeration system provided by the embodiments of the present disclosure;

[0032] Figure 18 is a structural schematic diagram of another refrigeration system provided by the embodiments of the present disclosure.

[0033] Reference signs:

[0034] 100, refrigeration system; 10, first-stage refrigeration system; 101, first-stage compressor; 102, first-stage pre-cooler; 103, first-stage anti-dew tube; 104, first-stage heat exchange structure; 1041, fifth heat exchange part; 1042, sixth heat exchange part; 105, first-stage condenser; 106, first-stage dry filter; 107, first-stage regenerator; 1071, first-stage throttling part; 1072, first-stage heat exchange pipeline; 108, first heat exchange part; 109, first-stage gas-liquid separator; 110, first-stage branch pipeline; 111, first-stage expansion device; 112, first-stage switch;

[0035] 20, second-stage refrigeration system; 201, second-stage compressor; 202, second-stage pre-cooler; 203, second-stage heat exchange structure; 2031, third heat exchange part; 2032, fourth heat exchange part; 204, second heat exchange part; 205, second-stage dry filter; 206, second-stage regenerator; 2061, second-stage throttling part; 2062, second-stage heat exchange pipeline; 207, second-stage evaporator; 208, fan; 209, second-stage branch pipeline; 210, second-stage expansion device; 211, second-stage switch;

[0036] 30. interstage heat exchanger;

[0037] 140. An apparatus for controlling a refrigeration system; 1401. A first obtaining module; 1402. A first control module; 1412. A first control submodule; 1422. A second control submodule;

[0038] 150. An apparatus for controlling a refrigeration system; 1501. A second obtaining module; 1502. A second control module; 1512. A third control submodule; 1522. A fourth control submodule;

[0039] 160. An apparatus for controlling a refrigeration system; 161. A processor; 162. A memory; 163. A communication interface; 164. A bus. DETAILED DESCRIPTION

[0040] In order to enable a more detailed understanding of the features and technical content of the embodiments of the present disclosure, the implementation of the embodiments of the present disclosure is described in detail below, and the attached drawings are used for reference only and do not limit the embodiments of the present disclosure. In the following technical description, in order to facilitate explanation, through multiple details, a sufficient understanding of the disclosed embodiments is provided. However, one or more embodiments can still be implemented without these details. In other cases, in order to simplify the drawings, well-known structures and devices can be simplified.

[0041] The terms "first", "second", and the like in the specification and claims of the embodiments of the present disclosure and the above-mentioned drawings are used to distinguish similar objects, and do not necessarily describe a specific order or sequence. It should be understood that the data thus used can be interchanged under appropriate circumstances, so that the embodiments of the present disclosure described herein can be implemented. In addition, the terms "include" and "have" and any variations thereof are intended to cover non-exclusive inclusion.

[0042] Unless otherwise specified, the term "a plurality of" means two or more.

[0043] In the embodiments of the present disclosure, the character " / " represents an "or" relationship between the preceding and following objects. For example, A / B represents: A or B.

[0044] The term "and / or" is a description of the association relationship between objects, which means that there can be three relationships. For example, A and / or B means: A or B, or, A and B, the three relationships.

[0045] The term "corresponding" can refer to an association relationship or a binding relationship, A corresponding to B means that there is an association relationship or a binding relationship between A and B.

[0046] In combination Figure 1As shown, the embodiment of the present disclosure provides a method for controlling a refrigeration system, comprising:

[0047] S100, the processor acquires the space temperature of the storage space corresponding to the refrigeration system.

[0048] S200, the processor controls the refrigeration system to enter the rapid cooling mode when the space temperature is greater than or equal to the first temperature threshold.

[0049] Wherein, S200, the processor controls the refrigeration system to enter the rapid cooling mode, comprising:

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

[0051] S220, 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.

[0052] The refrigeration system is installed in a refrigeration device. Optionally, the refrigeration device is a refrigerator, a freezer, a low-temperature storage box, etc. The refrigeration system is a cascade refrigeration system, comprising 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 device, such as the in-box space of the refrigerator, the in-cabinet space of the freezer, and the in-box space of the low-temperature storage box. The processor of the refrigeration system is in communication connection with the temperature sensor arranged in the storage space to acquire the space temperature of the storage space. The outlet of the low-temperature stage refrigerant of the intermediate heat exchanger is provided with a temperature sensor, and the processor of the refrigeration system is in communication connection with the temperature sensor to acquire 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 (T1 is the space temperature of the storage space, T1 is the first temperature threshold), that is, the space temperature meets the pre-set first set temperature condition, which indicates that the temperature of the storage space is too high and needs to be rapidly cooled to ensure the low-temperature storage environment of the goods. Therefore, at this time, the control is T1=TL+M1, wherein TL is the target temperature of the low-temperature stage refrigeration system, the value range is -40℃ to -86℃, and the default is -80℃, and M1 is the temperature adjustment value of the target temperature of the low-temperature stage refrigeration system in the rapid cooling mode, the value range is -0 to -20℃, and the default is 10℃, and the adjustment step is 1℃.

[0054] When the refrigeration system enters the rapid cooling mode, the high-temperature stage compressor is first controlled to operate at a first high-temperature stage set speed. In this way, the refrigerant circulation loop in which the high-temperature stage compressor is located can exchange heat with the refrigerant circulation loop in which the low-temperature stage compressor is located, so that the refrigerant circulation loop in which the low-temperature stage compressor is located can reach a lower refrigeration temperature. Alternatively, the first high-temperature stage set speed is the high-temperature stage compression RH2, and the value range is 2000 rpm to 5000 rpm, and the default value is 5000 rpm per minute, and the adjustment step is 100 rpm.

[0055] The temperature of the intermediate heat exchanger can reflect the refrigeration temperature of the final storage space, and thus it can be determined whether the storage space can meet the demand of the goods for low-temperature storage. 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 according to the temperature of the intermediate heat exchanger, so that the temperature of the intermediate heat exchanger can match the refrigeration demand.

[0056] The method for controlling the refrigeration system provided by the embodiment of the present disclosure is used to determine whether the storage space needs rapid cooling based on the space temperature of the storage space corresponding to the refrigeration system. If the space temperature is greater than or equal to a first temperature threshold, it indicates that the temperature of the storage space is relatively high, and the refrigeration system is controlled to enter the rapid cooling mode. The high-temperature stage compressor is first controlled to operate at a first high-temperature stage set speed to achieve rapid cooling. Then, the speed of the high-temperature stage compressor and the low-temperature stage compressor is controlled based on the temperature of the intermediate heat exchanger. The temperature of the intermediate heat exchanger can represent the refrigeration temperature of the storage space by the refrigeration system. The space temperature is adjusted in real time by controlling the speed of the high-temperature stage compressor and the low-temperature stage compressor, the number of start / stop of the compressor is reduced, and the refrigeration capacity caused by the fixed speed operation is excessive, so as to reduce the energy consumption of the refrigeration system.

[0057] In addition, the refrigeration system is intelligently adjusted by the above-mentioned logic, which can prevent the exhaust / back gas temperature of the compressor from being too high due to abnormal temperature, and can also improve the pressure state in the system and improve the reliability of the system.

[0058] After M2, that is, after the temperature of the storage space stabilizes, the speed of the high-temperature stage compressor and the low-temperature stage compressor is controlled according to the temperature of the intermediate heat exchanger. M2 is the delay time length of the start of the low-temperature stage compressor after the start of the high-temperature stage compressor in the rapid cooling mode. In this way, the space temperature can be avoided. The value range of M2 is 0 to 20 minutes, the default value is 10 minutes, and the adjustment step is 1 minute.

[0059] In combination with Figure 2 As shown in FIG. 1, the embodiment of the present disclosure provides another method for controlling a refrigeration system, which comprises:

[0060] S100, a processor acquires the space temperature of the storage space corresponding to the refrigeration system.

[0061] S200, the processor controls the refrigeration system to enter a rapid cooling mode when the space temperature is greater than or equal to a first temperature threshold.

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

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

[0064] S221, the processor controls the low-temperature stage compressor to operate at a first low-temperature stage set speed when the temperature of the intermediate heat exchanger is less than or equal to a second temperature threshold.

[0065] T2 (th is the temperature of the intermediate heat exchanger; T2 is the second temperature threshold, which is also the target temperature TH1 of the high-temperature stage refrigeration system in the rapid cooling mode), indicating that the space temperature is low, and the cooling capacity at this time is sufficient to maintain the low-temperature environment of the storage space. Therefore, the low-temperature stage compressor is controlled to operate at a 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 the rapid cooling mode, the purpose of the low-temperature stage compressor taking the highest speed is to make the low-temperature stage refrigerant flow as large as possible, because according to the heat calculation formula Q = cmΔt (where Q is the heat, c is the specific heat capacity of the object, m is the mass of the object, and Δt is the temperature difference), under the condition that the specific heat capacity and the temperature difference are constant, increasing the refrigerant flow m can increase the refrigeration capacity, so as to quickly drop to the target temperature. The value range of RL2 is 2000 rpm to 5000 rpm, and the default value is 5000 rpm, and the adjustment step is 100 rpm. Optionally, TH1 is less than TH1, and the value range of TH1 is -55°C to 0, and the default value is -25°C, and the adjustment step is 1°C.

[0066] In combination with Figure 3 As shown in the figure, the embodiment of the present 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 refrigeration system.

[0068] S200, the processor controls the refrigeration system to enter a rapid cooling mode when the space temperature is greater than or equal to a first temperature threshold.

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

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

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

[0072] S222, the processor acquires a new temperature of the intermediate heat exchanger.

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

[0074] The processor acquires a new temperature of the intermediate heat exchanger, and then adjusts the running of the high-temperature stage compressor and the low-temperature stage compressor according to the new temperature. In this way, the running of the high-temperature stage compressor and the low-temperature stage compressor is matched with the temperature of the intermediate heat exchanger, so that the energy consumption can be reduced under the premise of ensuring the refrigeration temperature.

[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-temperature stage compressor runs at the first low-temperature stage set speed, the temperature of the intermediate heat exchanger is still high, and the refrigerating capacity is insufficient to provide a low-temperature environment for the storage space. Therefore, at this time, the speed of the low-temperature stage compressor is reduced, and the speed of the high-temperature stage compressor is increased. In this way, reducing the speed of the low-temperature stage compressor can reduce the refrigerant flow of the low-temperature stage refrigeration system, so that the required refrigerating capacity of the low-temperature stage flow path in the intermediate heat exchanger is reduced, the heat load of the high-temperature stage flow path is reduced, and the temperature of the intermediate heat exchanger is reduced. At the same time, increasing the speed of the high-temperature stage compressor can increase the refrigerant flow of the high-temperature stage refrigeration system, so that the refrigerating capacity of the high-temperature stage flow path in the intermediate heat exchanger is increased, and the temperature of the intermediate heat exchanger is T3=TH1+M3, where M3 is an intermediate heat exchanger temperature adjustment value in the rapid cooling mode, and the value range is 0 to 20℃, the default value is 3℃, and the step is 1℃.

[0076] T4<th'<T3 (T4 is the fourth temperature threshold), which indicates that after the low-temperature stage compressor runs at the first low-temperature stage set speed, the temperature of the intermediate heat exchanger is in an appropriate range. Therefore, at this time, the high-temperature stage compressor and the low-temperature stage compressor are controlled to maintain the current speed unchanged. In this way, in the initial stage of cooling, due to the refrigerant heat recovery of the regenerator, the suction temperature of the low-temperature stage compressor is high when it is initially started, which can cause the exhaust temperature to be high, thereby easily causing the low-temperature stage compressor to have a thermal protection phenomenon. When the temperature of the intermediate heat exchanger is stable 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 quickly reach a relatively stable state, and T4=TH1+M4, where M4 is an intermediate heat exchanger temperature adjustment lower limit value in the rapid cooling mode, and is less than or equal to 0. Alternatively, the value range of M4 is -20℃ to 0, the default value is -3℃, and the adjustment step is 1℃.

[0077] th'≤T4, which indicates that after the low-temperature stage compressor runs at the first low-temperature stage set rotating speed, the temperature of the intermediate heat exchanger is relatively low, and the refrigerating capacity is excessive. Therefore, at this time, the rotating speed of the high-temperature stage compressor is reduced, and the rotating speed of the low-temperature stage compressor is increased. In this way, when the temperature of the intermediate heat exchanger is relatively low, the condensing pressure of the low-temperature stage refrigerating system is reduced, and then the heat load of the high-temperature stage flow path in the intermediate heat exchanger is reduced. At this time, the refrigerating capacity of the high-temperature stage refrigerating system can be reduced, and the refrigerating capacity of the low-temperature stage refrigerating system can be increased.

[0078] In this way, by using the third temperature threshold value and the fourth temperature threshold value, it is determined whether the new temperature of the intermediate heat exchanger is within the appropriate temperature range, and the rotating speeds of the high-temperature stage compressor and the low-temperature stage compressor are adjusted based on the determination result. In this way, sufficient refrigerating capacity can be provided, and excessive refrigerating capacity can be avoided, and the compressor can be prevented from being repeatedly started and stopped, so that the energy consumption of the refrigerating system is reduced.

[0079] M0, that is, after the temperature of the storage space stabilizes, the new temperature of the intermediate heat exchanger is obtained, which is beneficial to reducing the energy consumption of the refrigerating system. M0 is the system compressor rotating speed adjustment time interval in the rapid cooling mode, and the value range is 10 seconds to 120 seconds, and the default value is 20 seconds, and the adjustment step is 5 seconds.

[0080] T4<th'<T3, after the first pre-M5, the processor controls the low-temperature stage compressor to run at the highest rotating speed RL2 while the high-temperature stage compressor and the low-temperature stage compressor are maintained at the current rotating speed. In this way, in the initial stage of cooling, due to the refrigerant heat recovery of the regenerator, the suction temperature of the low-temperature stage compressor is relatively high when the low-temperature stage compressor is initially started, which can cause the exhaust temperature to be relatively high, thereby easily causing the low-temperature stage compressor to have a thermal protection phenomenon. When the temperature of the intermediate heat exchanger stabilizes within a certain temperature range, the evaporation pressure of the high-temperature stage refrigerating system and the condensing pressure of the low-temperature stage refrigerating system can quickly reach a relatively stable state, thereby avoiding the problem of thermal protection of the low-temperature stage compressor. With the operation of the system, the heat recovery temperature of the low-temperature stage refrigerating system decreases, the suction temperature of the low-temperature stage compressor decreases, the exhaust temperature decreases, and the condensing pressure of the low-temperature stage refrigerating system decreases. At this time, the rotating speed of the low-temperature stage compressor can be increased to obtain a larger refrigerating capacity.

[0081] M5 is the compressor rotating speed stable maintenance time in the rapid cooling mode, and the value range is 5 minutes to 60 minutes, and the default value is 10 minutes, and the adjustment step is 5 minutes.

[0082] In combination with Figure 4 As shown in FIG. 1, the embodiment of the present disclosure provides another method for controlling a refrigerating system, which comprises the following steps.

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

[0084] S200, the processor controls the refrigeration system to enter the rapid cooling mode when the space temperature is greater than or equal to the first temperature threshold.

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

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

[0087] S220, 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.

[0088] S300, the processor reacquires the space temperature of the storage space.

[0089] S400, the processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the reacquired space temperature.

[0090] After controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor based on the temperature 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 stage compressor and the low-temperature stage compressor is re-regulated. In this way, real-time temperature feedback adjustment can be performed based on the real-time temperature and the target temperature of the space, the speed of the compressor can be adjusted in real time, the best refrigeration capacity can be obtained, and unnecessary energy loss can be avoided.

[0091] tl'≤T5 (tl' is the new space temperature of the storage space, and T5 is the fifth temperature threshold), indicating that the space temperature is too low, which may cause the temperature sensor to fail to normally detect the temperature. Therefore, at this time, the refrigeration system is controlled to exit the rapid cooling mode, and the high-temperature stage compressor is also controlled to T5=TL+M6, where M6 is a sensor shutdown temperature adjustment value in the rapid cooling mode, less than or equal to 0. The value range of M6 is -10℃ to 0, and the default value is -2℃, and the adjustment step is 1℃.

[0092] tl'>T5, indicating that the space temperature of the storage space is relatively high and needs to be cooled again to provide cold capacity. Then, the temperature of the intermediate heat exchanger is reacquired, and the operation of the high-temperature stage compressor and the low-temperature stage compressor is controlled according to the reacquired temperature of the intermediate heat exchanger, that is, S220 is re-executed.

[0093] In this way, the operation of the high-temperature stage compressor and the low-temperature stage compressor is controlled in cycles based on the reacquired space temperature and the temperature of the intermediate heat exchanger, the dynamic stability of the refrigeration capacity is achieved by controlling the speed change of the compressor, the frequent start and stop of the compressor is avoided, and the energy consumption of the refrigeration system is reduced.

[0094] In combination with Figure 5 As shown in FIG. 8, another method for controlling a refrigeration system is provided, including:

[0095] S500, the processor acquires a space temperature of a storage space corresponding to the refrigeration system.

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

[0097] S600, the processor controls the refrigeration system to enter a normal cooling mode, comprising:

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

[0099] S620, the processor controls the high-temperature stage compressor and the low-temperature stage compressor according to the temperature of the intermediate heat exchanger.

[0100] The refrigeration system is installed in a refrigeration device. Optionally, the refrigeration device is a refrigerator, a freezer, a low-temperature storage box, or the like. The refrigeration system is a cascade refrigeration system, comprising a high-temperature stage compressor, a low-temperature stage compressor, and an intermediate heat exchanger. The storage space corresponding to the refrigeration system is a storage space of the refrigeration device, such as an in-box space of a refrigerator, an in-cabinet space of a freezer, or an in-box space of a low-temperature storage box. The processor of the refrigeration system is in communication connection with a temperature sensor arranged in the storage space to acquire a space temperature of the storage space. An outlet of the low-temperature stage refrigerant of the intermediate heat exchanger is provided with a temperature sensor, and the processor of the refrigeration system is in communication connection with the temperature sensor to acquire an outlet temperature of the low-temperature stage refrigerant of the intermediate heat exchanger (hereinafter referred to as “temperature of the intermediate heat exchanger”).

[0101] The processor determines whether the acquired space temperature meets a second set temperature condition. If yes, it indicates that the current storage space needs to be cooled, but the space temperature and the target temperature are not very different, and fast cooling is not required, otherwise temperature overshoot is likely to occur. Therefore, the refrigeration system is controlled to enter a normal cooling mode.

[0102] When the refrigeration system enters the normal cooling mode, the high-temperature stage compressor is first controlled to operate at a second high-temperature stage set speed, which is equivalent to turning on the high-temperature stage compressor. In this way, the refrigerant circulation loop in which the high-temperature stage compressor is located can exchange heat with the refrigerant circulation loop in which the low-temperature stage compressor is located, so that the refrigerant circulation loop in which the low-temperature stage compressor is located can reach a lower refrigeration temperature. Optionally, the second high-temperature stage set speed is less 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, and the value range is 2000 rpm to 5000 rpm, and the default value is 2000 rpm, and the adjustment step is 100 rpm.

[0103] The temperature of the intermediate heat exchanger can reflect the refrigeration temperature of the final storage space, and thus it can be determined whether the low-temperature storage requirement of the goods can be met. Therefore, after the high-temperature stage compressor runs at the second high-temperature stage set speed, the processor controls the running of the high-temperature stage compressor and the low-temperature stage compressor according to the temperature of the intermediate heat exchanger, so that the temperature of the intermediate heat exchanger can match the refrigeration requirement.

[0104] By using the method for controlling the refrigeration system provided in the embodiments of the present disclosure, whether the storage space needs ordinary cooling is determined based on the space temperature of the storage space corresponding to the refrigeration system. If the space temperature meets the second set temperature condition, the refrigeration system is controlled to enter the ordinary cooling mode. The high-temperature stage compressor is first controlled to run at a smaller second high-temperature stage set speed to achieve ordinary 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 represent the refrigeration 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, the number of start / stop of the compressor is reduced, and the refrigeration capacity caused by running at a fixed speed is reduced, so that the energy consumption of the refrigeration system is reduced.

[0105] In addition, by intelligently adjusting the refrigeration system through the above logic, the excessively high exhaust gas / back gas temperature of the compressor caused by temperature abnormalities can be prevented, and the pressure state in the system can be improved, and the reliability of the system can be improved.

[0106] T1, and tl≥T12, wherein tl is the space temperature of the storage space, T1 is a first temperature threshold, and T12 is a twelfth temperature threshold. When T1, the refrigeration system does not meet the condition for entering the rapid cooling mode. When the space temperature also meets tl≥T12, the refrigeration system meets the condition for entering the ordinary mode.

[0107] T12=TL+M8, wherein TL is the target temperature of the low-temperature stage refrigeration system, and the value range is -40℃ to -86℃, and the default value is -80℃, and M8 is the adjustment value of the space temperature in the ordinary cooling mode, and is less than or equal to 0. The value range of M8 is -5℃ to 0, and the default value is -1℃, and the adjustment step is 0.1℃.

[0108] After M9, that is, after the space temperature stabilizes, the speeds of 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 delay time length of starting the low-temperature stage compressor after starting the high-temperature stage compressor in the ordinary cooling mode. In this way, the M9 of the storage space can be avoided. The value range of M9 is 0 to 20 minutes, and the default value is 1 minute, and the adjustment step is 1 minute.

[0109] In combination with Figure 6 As shown in FIG. 1, the embodiments of the present disclosure provide another method for controlling a refrigeration system, which comprises:

[0110] S500, the processor acquires a space temperature of a storage space corresponding to the refrigeration system.

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

[0112] S600, the processor controls the refrigeration system to enter a normal cooling mode, comprising:

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

[0114] S621, the processor controls the low-temperature stage compressor to operate at a second low-temperature stage set rotating speed when the temperature of the intermediate heat exchanger is less than or equal to a sixth temperature threshold.

[0115] T6(th is the temperature of the intermediate heat exchanger; T6 is the sixth temperature threshold, which is also the target temperature TH2 of the high-temperature stage refrigeration system in the normal cooling mode), indicating that the temperature of the storage space is relatively low, and the cold quantity at this time is sufficient to maintain the low-temperature storage space. Then, the low-temperature stage compressor is controlled to operate at the second low-temperature stage set rotating speed to avoid energy waste caused by excessive cold quantity. Alternatively, the second low-temperature stage set rotating speed is less than the first RL1, because: since the mechanical loss of the compressor is less at a low rotating speed, a higher COP (Coefficient Of Performance, energy and heat conversion ratio, simply referred to as energy efficiency ratio) value can be obtained, so the compressor is operated at the lowest rotating speed. The value range is 2000 rpm to 5000 rpm, the default value is 2000 rpm, and the adjustment step is 100 rpm.

[0116] T6 is the target temperature TH2 of the high-temperature stage refrigeration system in the normal cooling mode, which is less than or equal to 0. The value range of TH2 is -55°C to 0, the default value is -30°C, and the adjustment step is 1°C.

[0117] In combination with Figure 7 As shown in the figure, the embodiment of the present disclosure provides another method for controlling a refrigeration system, comprising:

[0118] S500, the processor acquires a space temperature of a storage space corresponding to the refrigeration system.

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

[0120] S600, the processor controls the refrigeration system to enter a normal cooling mode, comprising:

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

[0122] S621, the processor controls the low-temperature stage compressor to operate at the second low-temperature stage set speed in the case that the temperature of the intermediate heat exchanger is less than or equal to the sixth temperature threshold.

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

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

[0125] S624, the processor adjusts the operation of the low-temperature stage compressor according to the new space temperature.

[0126] In the case of normal adjustment, the priority of the temperature of the intermediate heat exchanger is higher than that of the space temperature, and when the two temperatures conflict, the speed of the compressor needs to be adjusted in priority according to the temperature of the intermediate heat exchanger. Therefore, after the low-temperature stage compressor is controlled to operate at the second low-temperature stage set speed, the speed of the compressor is adjusted, and the compressor is adjusted based on the intermediate heat exchanger first, and then adjusted based on the space temperature.

[0127] When adjusting the compressor, the operation of the high-temperature stage compressor is adjusted first, and then the operation of the low-temperature stage compressor is adjusted, because it is desired that the frequency of the high-temperature stage compressor changes faster, so that the high-temperature stage compressor responds faster than the low-temperature stage compressor. That is, the high-temperature stage compressor is controlled to refrigerate after the low-temperature stage compressor is controlled to refrigerate, the high-temperature stage compressor is more sensitive than the low-temperature stage compressor, and the high-temperature stage compressor can be more matched to the working condition of the low-temperature stage compressor, so that the high-temperature stage compressor changes faster, and when the speed of the low-temperature stage compressor changes, the high-temperature stage compressor can quickly respond, thereby being more conducive to energy saving and consumption reduction of the refrigeration system. M10, that is, after the space temperature stabilizes, the new temperature of the intermediate heat exchanger is obtained, which is conducive to reducing the energy consumption of the refrigeration system. M10 is the system high-temperature stage compressor speed adjustment time interval in the normal cooling mode, and the value range is 10 to 120 seconds, and the default value is 30 seconds, and the adjustment step is 5 seconds.

[0128] After M11, the space temperature of the storage space is reacquired, and the operation of the low-temperature stage compressor is controlled based on the reacquired space temperature. M11>M10. In this way, after waiting for the sixth set time M11, the space temperature stabilizes, and then the speed of the low-temperature stage compressor is adjusted based on the space temperature, which is conducive to reducing the energy consumption of the refrigeration system. Thus, in different timing periods, the high-temperature stage compressor and the low-temperature stage compressor are adjusted, and M11 is the low-temperature stage compressor speed adjustment time interval in the normal cooling mode, and the value range is 10 to 120 seconds, and the default value is 60 seconds, and the adjustment step is 5 seconds.

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

[0130] The processor increases the rotation speed of the high-temperature stage compressor when the new temperature of the intermediate heat exchanger is greater than or equal to a seventh temperature threshold.

[0131] The processor controls the high-temperature stage compressor to maintain the current rotation speed when the new temperature of the intermediate heat exchanger is less than the seventh temperature threshold and greater than an eighth temperature threshold.

[0132] The processor reduces the rotation speed of the high-temperature stage compressor when the new temperature of the intermediate heat exchanger is less than or equal to the eighth temperature threshold. th'≥T7 (th' is the new temperature of the intermediate heat exchanger, and T7 is the seventh temperature threshold), which means that after the low-temperature stage compressor operates at the second low-temperature stage set rotation speed, the temperature of the intermediate heat exchanger is still high, and the refrigeration 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-temperature stage refrigeration system in the normal cooling mode, and the value range is -55℃ to 0, and M12 is the high-temperature stage compressor rotation speed adjustment value in the normal cooling mode, which is greater than or equal to 0. The value range of M12 is 0 to 20℃, and the default value is 3℃, and the adjustment step is 1℃.

[0133] T8<th'<T7 (T8 is the eighth temperature threshold), which means that after the low-temperature stage compressor operates at the second low-temperature stage set rotation speed, the temperature of the intermediate heat exchanger is in an appropriate range. Therefore, at this time, the high-temperature stage compressor is controlled to maintain the current rotation speed unchanged, so that the current rotation speed of the high-temperature stage compressor is controlled, and the rotation speed of the low-temperature stage compressor is controlled to be the second low-temperature stage set rotation speed, thereby reducing unnecessary energy consumption. T8=TH2+M13, where M13 is less than or equal to 0, which is the high-temperature stage compressor rotation speed adjustment value in the normal cooling mode, and is less than or equal to 0. The value range of M13 is -20℃ to 0, the default value is -3℃, and the adjustment step is 1℃.

[0134] th'≤T8, which means that after the low-temperature stage compressor operates at the second low-temperature stage set rotation speed, the temperature of the intermediate heat exchanger is low, and the refrigeration capacity is excessive. Therefore, at this time, the rotation speed of the high-temperature stage compressor is reduced, so as to reduce unnecessary energy consumption.

[0135] In this way, by pre-setting the seventh temperature threshold and the eighth temperature threshold, it is judged whether the new temperature of the intermediate heat exchanger is in an appropriate range, and the rotation speed of the high-temperature stage compressor is adjusted based on the judgment result, so as to provide sufficient refrigeration capacity, avoid excessive refrigeration capacity, and avoid repeated start and stop of the compressor, thereby reducing the energy consumption of the refrigeration system.

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

[0137] The processor increases the rotation speed of the low-temperature stage compressor when the new space temperature is greater than or equal to a tenth temperature threshold.

[0138] The processor controls the low-temperature stage compressor to maintain the current rotation speed when the new space temperature is less than the tenth temperature threshold and greater than an eleventh temperature threshold.

[0139] The processor decreases the rotation speed of the low-temperature stage compressor when the new space temperature is less than or equal to the eleventh temperature threshold. Tl"≥T10 (Tl" is the new space temperature of the storage space, and T10 is the tenth temperature threshold), which indicates that the space temperature is high, and the rotation speed of the low-temperature stage compressor needs to be reduced. T11<tl"<T10 (T11 is the eleventh temperature threshold), which indicates that the space temperature is within an appropriate temperature range, and the rotation speed of the low-temperature stage compressor is controlled. tl"≤T11, which indicates that the space temperature is low, and the rotation speed of the low-temperature stage compressor is reduced to reduce the generation of cold energy and ensure the low-temperature storage environment. In this way, the rotation speed of the low-temperature stage compressor is adjusted 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 cold energy can be reduced, thereby reducing the energy consumption of the refrigeration system. T10=TL+M14, where M14 is an upper adjustment temperature value of the target temperature of the low-temperature stage refrigeration system in the normal cooling mode, greater than or equal to M14, and the value range of M14 is 0 to 5℃, the default value is 1℃, and the adjustment step is 0.1℃.

[0140] T11=TL+M15, where M15 is a lower adjustment temperature value of the target temperature of the low-temperature stage refrigeration system in the normal cooling mode, less than or equal to M15, and the value range of M15 is -5℃ to 0, the default value is -1.5℃, and the adjustment step is 0.1℃.

[0141] In combination Figure 8 As shown in the drawings, the embodiments of the present disclosure provide another method for controlling a refrigeration system, comprising:

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

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

[0144] In S600, the processor controls the refrigeration system to enter the normal cooling mode, comprising:

[0145] S610, the processor controls the high-temperature stage compressor to operate at a second high-temperature stage set rotation 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 reacquires the space temperature of the storage space.

[0148] S800, the processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the reacquired space temperature.

[0149] After controlling the operation of the high-temperature stage compressor and the low-temperature stage compressor based on 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 stage compressor and the low-temperature stage compressor is re-regulated. In this way, through multiple cycles of regulating the high-temperature stage compressor and the low-temperature stage compressor, temperature overshoot and repeated start-stop of the compressor are avoided, and the space temperature can be gradually stabilized at the target temperature while consuming low energy.

[0150] tl'≤T9 (tl' is the new space temperature of the storage space, and T9 is the ninth temperature threshold), indicating that the space temperature is too low, which may cause the temperature sensor to fail to normally detect the temperature. Therefore, at this time, the refrigeration system is controlled to exit the normal cooling mode, and the high-temperature stage compressor can also be controlled as follows: T9=TL+M8, wherein TL is the target temperature of the low-temperature stage refrigeration system, and the value range is -40℃ to -80℃, and the default value is -80℃; M8 is a temperature adjustment value of the storage space in the normal cooling mode, and is less than or equal to 0. The value range of M8 is -5℃ to 0, and the default value is -1℃, and the adjustment step is 0.1℃.

[0151] tl'>T9, indicating that the storage space has not reached the target space temperature, so the operation of the high-temperature stage compressor and the low-temperature stage compressor is re-regulated, that is, M10 is executed again after S622, and M10 is executed again after S623.

[0152] The space temperature of the storage space is adjusted to the target temperature, which is the ultimate goal. Therefore, after one round of adjustment of the rotation speed of the high-temperature stage compressor and the low-temperature stage compressor, whether the rotation speed of the high-temperature stage compressor and the low-temperature stage compressor needs to be adjusted again is judged based on the space temperature, which is beneficial to accurately regulate the rotation speed of the compressor and accurately adjust the space temperature.

[0153] In combination with Figure 9 As shown in FIG. 8, the embodiment of the present disclosure provides another method for controlling a refrigeration system, which comprises the following steps:

[0154] S500, the processor acquires the space temperature of the storage space corresponding to the refrigeration system.

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

[0156] In S600, the processor controls the refrigeration system to enter the normal cooling mode, which comprises the following steps:

[0157] S610, the processor controls the high-temperature stage compressor to run at a second high-temperature stage setting speed.

[0158] S620, the processor controls the running 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 reacquires the space temperature of the storage space.

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

[0161] S900, after S500 is performed, the processor controls the high-temperature stage compressor and the low-temperature stage compressor to stop running in a case where the space temperature of the storage space does not meet the first setting temperature condition for entering the rapid cooling mode and does not meet the second setting temperature condition for entering the normal cooling mode.

[0162] After the space temperature of the storage space corresponding to the refrigeration system is acquired, it is judged whether the space temperature meets the first setting temperature condition and T1 and tl < T12. It is indicated that the space temperature at this time is relatively low and does not need to be provided with cold energy by the refrigeration system. Therefore, the high-temperature stage compressor and the low-temperature stage compressor are controlled to stop running, and all the fans can be controlled to stop running. In this way, all the compressors and all the fans are controlled to stop running in the case where refrigeration is not necessary, and the energy consumption of the refrigeration system can be reduced.

[0163] In combination with Figure 10 As shown in the figure, another method for controlling a refrigeration system is provided in the embodiments of the present disclosure, which comprises the following steps:

[0164] S500, a processor acquires a space temperature of a storage space corresponding to a refrigeration system.

[0165] S600, the processor controls the refrigeration system to enter a normal cooling mode in a case where the space temperature meets a second setting temperature condition.

[0166] In S600, the processor controls the refrigeration system to enter the normal cooling mode, which comprises the following steps:

[0167] S610, the processor controls the high-temperature stage compressor to run at a second high-temperature stage setting speed.

[0168] S620, the processor controls the running 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 reacquires the space temperature of the storage space.

[0170] S800, the processor controls the operation of the high-temperature stage compressor and the low-temperature stage compressor according to the reacquired space temperature.

[0171] S900, after the execution of S500, the processor controls the high-temperature stage compressor and the low-temperature stage compressor to be stopped in the case that the space temperature of the storage space does not meet the first set temperature condition for entering the fast cooling mode and does not meet the second set temperature condition for entering the normal cooling mode.

[0172] S1000, the processor controls the refrigeration system to selectively enter the fast cooling mode or the normal cooling mode according to the temperature range in which the new space temperature is located in the case that the new space temperature is greater than or equal to the thirteenth temperature threshold.

[0173] After the high-temperature stage compressor and the low-temperature stage compressor are controlled to be stopped, the space temperature of the storage space is continuously acquired, and it is judged whether the new space temperature tl''' meets the first set temperature condition or the second set temperature condition, that is, S100 to S200 and S500 to S600 are executed, and then the refrigeration system is controlled to selectively enter the fast cooling mode or the normal cooling mode. In this way, the refrigeration system is matched to run the fast cooling or the normal cooling based on the new space temperature, which can not only realize the reduction of the space temperature to a suitable low-temperature range, but also match the suitable compressor speed to avoid the excess of refrigeration capacity, thereby reducing the energy consumption of the refrigeration system.

[0174] T13 = TL + M7, wherein M7 is a compressor start-up upper limit temperature value and is greater than or equal to 0. The value range of M7 is 0 to 5℃, the default value is 1℃, and the adjustment step is 0.1℃.

[0175] The embodiments of the present disclosure will be described below in combination with Figure 11 (top, left side of the drawing), the regulation of the compressor speed by the embodiments of the present disclosure will be specifically described:

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

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

[0178] RH2 is run.

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

[0180] M0 seconds.

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

[0182] S1107, the processor reduces the rotation speed of the low-temperature stage compressor and increases the rotation speed of the high-temperature stage compressor; and then S1111 is executed.

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

[0184] S1109, the processor reduces the rotation speed of the high-temperature stage compressor and increases the rotation speed of the low-temperature stage compressor; and then S1111 is executed.

[0185] M5 minutes later, the low-temperature stage compressor is controlled to operate at the rotation speed RL2; and then S1111 is executed.

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

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

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

[0189] RH1 is operated.

[0190] M9 minutes later, when the temperature of the intermediate heat exchanger satisfies th≤TH2, the low-temperature stage compressor is controlled to operate at the rotation speed RL1; and then S1116 and S1123 are executed.

[0191] M10 seconds.

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

[0193] S1118, the processor increases the rotation speed of the high-temperature stage compressor; and then S1122 is executed.

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

[0195] S1120, the rotation speed of the high-temperature stage compressor is reduced; and then S1122 is executed.

[0196] S1121, the processor maintains the rotation speed of the high-temperature stage compressor; and then S1122 is executed.

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

[0198] M11 seconds.

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

[0200] S1125, the processor increases the rotation speed of the low-temperature stage compressor, and then performs S1122.

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

[0202] S1127, the processor reduces the rotation speed of the low-temperature stage compressor, and then performs S1122.

[0203] S1128, the processor maintains the rotation speed of the low-temperature stage compressor, and then performs S1122.

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

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

[0206] S1131, exit the normal cooling mode.

[0207] In combination Figure 12 As shown in the figure, the embodiment of the present disclosure provides another method for controlling a refrigeration system, comprising:

[0208] S1100, the processor acquires the running state of the high-temperature stage compressor and the outlet temperature of the condenser of the high-temperature stage refrigeration system.

[0209] S1200, the processor controls the running of the fan according to the running state of the high-temperature stage compressor and the outlet temperature of the condenser of the high-temperature stage refrigeration system.

[0210] The processor of the refrigeration system acquires the running state of the high-temperature stage compressor to determine whether the high-temperature stage compressor is started. At the same time, the processor acquires the outlet temperature of the condenser through the temperature sensor arranged at the outlet of the condenser of the high-temperature stage refrigeration system. Then, the running of the fan is controlled according to the running state of the high-temperature stage compressor and the outlet temperature of the condenser of the high-temperature stage refrigeration system. This is because: the fan is directly related 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 working condition of the high-temperature stage refrigeration system affects the working condition of the low-temperature stage refrigeration system; the fan affects the working condition of the high-temperature stage refrigeration system; therefore, the running of the fan is controlled based on the running state of the high-temperature stage compressor and the outlet temperature of the condenser of the high-temperature stage refrigeration system.

[0211] The method for controlling the refrigeration system provided by the embodiment of the present disclosure controls the operation of the fan based on the operating state of the high-temperature stage compressor and the outlet temperature of the condenser of the high-temperature stage refrigeration system, and can automatically adjust the rotating speed of the fan and the on-off operating state according to the required cooling air volume of the condenser of the high-temperature stage refrigeration system, so that the air volume matches the operating state of the refrigeration system, reduces the noise, and prolongs the service life of the fan.

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

[0213] When the high-temperature stage compressor is started, the processor:

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

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

[0216] The correlation between the outlet temperature of the condenser of the high-temperature stage refrigeration system and the rotating speed of the fan is pre-stored in the storage of the refrigeration system. When the high-temperature stage compressor is started, it indicates that the refrigeration system is operating refrigeration, and the processor calls the above correlation to determine the target rotating speed of the fan corresponding to the outlet temperature of the condenser, and controls all the fans to operate at the target rotating speed. In this way, the outlet temperature of the condenser is matched with the rotating speed of the fan, and then the required air volume of the refrigeration system is matched, and the noise is reduced.

[0217] Optionally, the correlation between the outlet temperature of the condenser and the rotating speed of the fan comprises one or more corresponding relationships between the outlet temperature and the rotating speed of the fan. Specifically, different temperature ranges are pre-divided, and different temperature ranges correspond to different rotating speeds of the fan. Optionally, when the temperature tc is greater than or equal to a fourteenth temperature threshold T14, the corresponding rotating speed of the fan is a first set rotating speed. When T15 < tc < T14, T15 is a fifteenth temperature threshold, the corresponding rotating speed of the fan is a second set rotating speed. When the outlet temperature of the condenser is less than or equal to T15, the corresponding rotating speed of the fan is a third set rotating speed. Wherein, the first set rotating speed is greater than the third set rotating speed, and the third set rotating speed is greater than the second set rotating speed. Optionally, the first set rotating speed is the highest rotating speed of the fan, the second set rotating speed is the lowest rotating speed of the fan, and the third set rotating speed is an intermediate rotating speed between the highest rotating speed and the lowest rotating speed. In this way, the outlet temperature of the condenser matches different rotating speeds of the fan, which can adjust the fan to an appropriate rotating speed, avoiding insufficient or excessive adjustment of the rotating speed.

[0218] It should be noted that the person skilled in the art can divide more temperature ranges according to the needs, and then correspond to the speed of the fan of more gears, so as to more accurately adjust the speed of the fan.

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

[0220] T15 = ta + M17, wherein M17 is the lower limit of temperature adjustment, and is greater than or equal to 0. The value range of M17 is 0-10℃, the default value is 2℃, and the adjustment step is 0.5℃.

[0221] After M18, the outlet temperature of the condenser is reacquired, and based on the reacquired outlet temperature, the speed of the fan is controlled according to the foregoing. After M18, the outlet temperature of the condenser tends to be stable, so as to ensure the accuracy of the subsequent adjustment of the speed of the fan.

[0222] M18 is the time interval of fan speed regulation, and the value range is 10-120 seconds, the default value is 30 seconds, and the adjustment step is 5 seconds.

[0223] Optionally, the processor determines whether the high-temperature stage compressor is started again at an eighth set time interval under the condition that the high-temperature stage compressor is not started, and controls the speed of the fan in combination with the outlet temperature of the condenser. Optionally, the eighth set time interval is 1-2 minutes. In this way, the running state of the compressor is continuously monitored, so as to accurately control the speed of the fan.

[0224] The following will be combined with Figure 13 , the regulation of the speed of the fan by the embodiment of the present disclosure will be specifically explained:

[0225] S1301, the processor acquires the running state of the high-temperature stage compressor.

[0226] S1302, the processor determines whether the high-temperature stage compressor is started; if yes, S1303 is executed, and if no, S1309 is executed.

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

[0228] S1305, the processor determines whether the outlet temperature of the condenser is greater than T14 + M16; if yes, S1306 is executed; and if no, S1307 is executed.

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

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

[0231] M18 seconds, and then performs S1303.

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

[0233] Optionally, the control logic of the fan speed provided in this embodiment can be simultaneously run with the control logic of the compressor speed in the rapid cooling mode and the control logic of the compressor speed in the ordinary cooling mode (as described above). Figure 11 In this way, the compressor and fan matching control can reduce unnecessary energy consumption and improve system response speed and control accuracy. Moreover, by designing different control modes, the compressor and fan are coupled and controlled for different working conditions, which can improve the reliability of the system.

[0234] As shown in Figure 14 The embodiment of the present disclosure provides a device 140 for controlling a refrigeration system, comprising: 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 comprises: 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 run 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 according to the temperature of the intermediate heat exchanger.

[0236] By using the device 140 for controlling a refrigeration system provided in the embodiment of the present disclosure, whether the storage space needs rapid cooling is determined based on the space temperature of the storage space corresponding to the refrigeration system. If the space temperature is greater than or equal to the first temperature threshold, it means that the temperature of the storage space is high, and the refrigeration system is controlled to enter the rapid cooling mode. The high-temperature stage compressor is first controlled to run 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 can represent the refrigeration 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, the number of start-stop of the compressor is reduced, and the excess refrigeration capacity caused by running at a fixed speed is reduced, thereby reducing the energy consumption of the refrigeration system.

[0237] As shown in Figure 15As shown, the embodiment of the present disclosure provides a device 150 for controlling a refrigeration system, comprising: a second acquisition module 1501 and a second control module 1502. The second acquisition module 1501 is configured to acquire a space temperature of a 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 comprises: 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 according to the temperature of the intermediate heat exchanger.

[0239] By using the device 150 for controlling a refrigeration system provided by the embodiment of the present disclosure, whether the storage space needs normal cooling is determined based on the space temperature of the storage space corresponding to the refrigeration system. If the space temperature meets the second set temperature condition, the refrigeration system is controlled to enter the normal cooling mode. The high-temperature stage compressor is first controlled to operate at a smaller 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 represent the refrigeration 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, the number of start-stop of the compressors is reduced, and the excess refrigeration capacity caused by the fixed speed operation is reduced, so as to reduce the energy consumption of the refrigeration system.

[0240] In combination Figure 16 As shown, the embodiment of the present disclosure provides a device 160 for controlling a refrigeration system, comprising a processor 161 and a memory 162. Optionally, the device 160 can further comprise a communication interface 163 and a bus 164. The processor 161, the communication interface 163, and the memory 162 can complete mutual communication through the bus 164. The communication interface 163 can be used for information transmission. The processor 161 can invoke the logic instructions in the memory 162 to execute the method for controlling a refrigeration system of the above-mentioned embodiments.

[0241] In addition, the logic instructions in the memory 162 described above can be implemented in the form of a software functional unit and sold or used as an independent product, which can be stored in a computer readable storage medium.

[0242] The memory 162 can be used to store software programs, computer executable programs, such as program instructions / modules corresponding to the method in the embodiments of the present disclosure. The processor 161 executes the functions of the application and data processing, that is, implements the method for controlling the refrigeration system in the above embodiments by running the program instructions / modules stored in the memory 162.

[0243] The memory 162 can include a program storage area and a data storage area, wherein the program storage area can store an operating system and application programs required by at least one function; the data storage area can store data created according to the use of the terminal device, etc. In addition, the memory 162 can include a high-speed random access memory, and can also include a non-volatile memory.

[0244] In combination with Figure 17 and Figure 18 As shown in the above embodiments, the present disclosure provides a refrigeration system 100, comprising: a compressor, a first heat exchanger and a second heat exchanger connected in sequence through refrigerant pipelines.

[0245] The first heat exchanger serves as a condenser, and the second heat exchanger serves as an evaporator. The refrigerant flowing out of the compressor is condensed in the first heat exchanger and evaporated in the second heat exchanger.

[0246] The heat exchange system further comprises a heat exchange structure, the heat exchange structure comprising a first heat exchange member and a second heat exchange member capable of heat exchange, the first heat exchange member being communicated between the exhaust port of the compressor and the inlet of the first heat exchanger, and the second heat exchange member being communicated between the outlet of the second heat exchanger and the return port of the compressor.

[0247] The first heat exchange member and the second heat exchange member are capable of heat exchange, so that the refrigerant flowing out of the outlet of the second heat exchanger can exchange heat with the refrigerant flowing out of the exhaust port of the compressor. In this way, the lubricating oil mixed in the refrigerant flowing out of the second heat exchanger can be heated by the refrigerant flowing out of the exhaust port of the compressor, and the oil becomes more fluid after being heated, and the oil flows back to the compressor, so that the oil separator can be cancelled.

[0248] Compared with the case that the first heat exchange member is arranged between the outlet of the first heat exchanger and the inlet of the second heat exchanger, when the first heat exchange member is arranged between the exhaust port of the compressor and the inlet of the first heat exchanger, the temperature of the refrigerant in the first heat exchange member is higher, so that the refrigerant in the second heat exchange member can be better heated, and the oil mixed in the refrigerant can also be better heated, so as to ensure that the oil can flow back to the compressor, and ensure that the refrigeration system can still operate normally without the oil separator.

[0249] Optionally, as Figure 17As shown, the compressor comprises a first-stage compressor 101 and a second-stage compressor 201, the first heat exchanger comprises a first-stage condenser 105 and a second heat exchange part 204, the second heat exchanger comprises a first heat exchange part 108 and a second-stage evaporator 207, and the first heat exchange part 108 and the second heat exchange part 204 are capable of heat exchange; the first-stage refrigeration system 10 comprises the first-stage compressor 101, the first-stage condenser 105, and the first heat exchange part 108 connected in sequence; and the second-stage refrigeration system 20 comprises the second-stage compressor 201, the second heat exchange part 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 method for controlling a refrigeration system described above. The first-stage refrigeration system 10 is also the high-temperature stage refrigeration system in the method for controlling a refrigeration system described above. The second-stage compressor 201 is also the low-temperature stage compressor in the method for controlling a refrigeration system described above. The second-stage refrigeration system 20 is also the low-temperature stage refrigeration system in the method for controlling a refrigeration system described above.

[0251] The refrigeration system is divided into a first-stage refrigeration system 10 and a second-stage refrigeration system. The first heat exchange part 108 and the second heat exchange part 204 are capable of heat exchange, so that the refrigerant in the first heat exchange part 108 can cool the refrigerant in the second heat exchange part 204, reduce the temperature of the refrigerant in the second heat exchange part 204, and enable the second-stage refrigeration system 20 to achieve a lower refrigeration temperature. In other words, in the case where the second-stage refrigeration system 20 can achieve the same refrigeration temperature, the refrigeration system of the present application can reduce energy consumption.

[0252] Optionally, the heat exchange structure comprises a second-stage heat exchange structure 203, the second-stage heat exchange structure 203 comprises a third heat exchange part 2031 and a fourth heat exchange part 2032 capable of heat exchange, the third heat exchange part 2031 is connected between the exhaust port of the second-stage compressor 201 and the inlet of the second heat exchange part 204, and the fourth heat exchange part 2032 is connected between the outlet of the second-stage evaporator 207 and the return port of the second-stage compressor 201, wherein the first heat exchange member comprises the third heat exchange part 2031, and the second heat exchange member comprises the fourth heat exchange part 2032.

[0253] The third heat exchange part 2031 and the fourth heat exchange part 2032 are capable of heat exchange, so that the refrigerant flowing out of the outlet of the second-stage evaporator 207 can exchange heat with the refrigerant flowing out of the exhaust port of the second-stage compressor 201. In this way, the lubricating oil mixed in the refrigerant flowing out of the second-stage evaporator 207 can be heated by the refrigerant flowing out of the exhaust port of the second-stage compressor 201, and the oil has enhanced fluidity after being heated, and the oil flows back to the second-stage compressor 201, so that the oil separator can be cancelled.

[0254] Optionally, the third heat exchange part 2031 comprises a third heat exchange pipe, two ends of the third heat exchange pipe are respectively connected with the exhaust port of the second stage compressor 201 and the inlet of the second heat exchange part 204.

[0255] The fourth heat exchange part 2032 comprises a fourth heat exchange pipe, two ends of the fourth heat exchange pipe are respectively connected with the outlet of the second stage evaporator 207 and the return air port of the second stage compressor 201.

[0256] The third heat exchange pipe is sleeved outside the fourth heat exchange pipe or the fourth heat exchange pipe is sleeved outside the third heat exchange pipe, so as to realize heat exchange between the third heat exchange pipe and the fourth heat exchange pipe.

[0257] The third heat exchange pipe is sleeved outside the fourth heat exchange pipe, for example, the third heat exchange pipe is a copper pipe with an inner diameter of 12 mm, and the fourth heat exchange pipe is a copper pipe with an inner diameter of 4 mm, the refrigerant flowing out of the second stage compressor 201 passes through the third heat exchange pipe (the gap between the outer wall surface of the third heat exchange pipe and the inner wall surface of the fourth heat exchange pipe), the second heat exchange part 204 and the second stage evaporator 207, and then flows back to the second stage compressor 201 through the fourth heat exchange pipe.

[0258] Or the fourth heat exchange pipe is sleeved outside the third heat exchange pipe, for example, the third heat exchange pipe is a copper pipe with an inner diameter of 4 mm, and the fourth heat exchange pipe is a copper pipe with an inner diameter of 12 mm, the refrigerant flowing out of the second stage compressor 201 passes through the third heat exchange pipe, the second heat exchange part 204 and the second stage evaporator 207, and then flows back to the second stage compressor 201 through the fourth heat exchange pipe (the gap between the outer wall surface of the third heat exchange pipe and the inner wall surface of the fourth heat exchange pipe).

[0259] The third heat exchange pipe and / or the fourth heat exchange pipe is a corrugated pipe, the corrugation of the corrugated pipe is arranged to enhance the disturbance to the refrigerant, which can effectively reduce the boundary layer thickness in the refrigerant flow process and enhance the heat exchange effect between the third heat exchange pipe and the fourth heat exchange pipe.

[0260] Optionally, as shown in Figure 17 The heat exchange structure comprises a first stage heat exchange structure 104, the first stage heat exchange structure 104 comprises a fifth heat exchange part 1041 and a sixth heat exchange part 1042 capable of heat exchange, the fifth heat exchange part 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 part 1042 is connected between the outlet of the first heat exchange part 108 and the return air port of the first stage compressor 101, wherein the first heat exchange member comprises the fifth heat exchange part 1041, and the second heat exchange member comprises the sixth heat exchange part 1042.

[0261] The fifth heat exchange part 1041 and the sixth heat exchange part 1042 can exchange heat, so that the refrigerant flowing out of the first heat exchange part 108 can exchange heat with the refrigerant flowing out of the exhaust port of the first stage compressor 101. In this way, the lubricating oil mixed in the refrigerant flowing out of the first heat exchange part 108 can be heated by the refrigerant flowing out of the exhaust port of the first stage compressor 101, and the oil is heated to enhance the flowability, and the oil is returned to the first stage compressor 101, so that the oil separator can be cancelled.

[0262] Optionally, the fifth heat exchange part 1041 comprises a fifth heat exchange pipe, and the two ends of the fifth heat exchange pipe are respectively connected with the exhaust port of the first stage compressor 101 and the inlet of the first stage condenser 105.

[0263] The sixth heat exchange part 1042 comprises a sixth heat exchange pipe, and the two ends of the sixth heat exchange pipe are respectively connected with the outlet of the first heat exchange part 108 and the back gas port of the first stage compressor 101.

[0264] The fifth heat exchange pipe is sleeved outside the sixth heat exchange pipe, or the sixth heat exchange pipe is sleeved outside the fifth heat exchange pipe, so as to realize the heat exchange between the fifth heat exchange pipe and the sixth heat exchange pipe.

[0265] The fifth heat exchange pipe is sleeved outside the sixth heat exchange pipe, for example, the fifth heat exchange pipe is a copper pipe with an inner diameter of 12 mm, and the sixth heat exchange pipe is a copper pipe with an inner diameter of 4 mm. The refrigerant flowing out of the first stage compressor 101 passes through the fifth heat exchange pipe (the gap between the outer wall surface of the fifth heat exchange pipe and the inner wall surface of the sixth heat exchange pipe), the first stage condenser 105 and the first heat exchange part 108, and then flows back to the first stage compressor 101 through the sixth heat exchange pipe.

[0266] Or the sixth heat exchange pipe is sleeved outside the fifth heat exchange pipe, for example, the fifth heat exchange pipe is a copper pipe with an inner diameter of 4 mm, and the sixth heat exchange pipe is a copper pipe with an inner diameter of 12 mm. The refrigerant flowing out of the first stage compressor 101 passes through the fifth heat exchange pipe, the first stage condenser 105 and the first heat exchange part 108, and then flows back to the first stage compressor 101 through the sixth heat exchange pipe (the gap between the outer wall surface of the fifth heat exchange pipe and the inner wall surface of the sixth heat exchange pipe).

[0267] The fifth heat exchange pipe and / or the sixth heat exchange pipe are corrugated pipes. The corrugation of the corrugated pipe enhances the disturbance to the refrigerant, effectively reduces the boundary layer thickness in the flow process of the refrigerant, and enhances the heat exchange effect between the fifth heat exchange pipe and the sixth heat exchange pipe.

[0268] The third heat exchange pipe, the fourth heat exchange pipe, the fifth heat exchange pipe and the sixth heat exchange pipe are all in spiral shape.

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

[0270] The lubricating oil can be well dissolved in the refrigerant, so that the refrigerant can drive the lubricating oil to flow in the second refrigeration system 20, and due to the presence of the second heat exchange structure 203, the lubricating oil flowing out of the second evaporator 207 can be heated again by the third heat exchange part 2031, improving the flowability of the lubricating oil and ensuring that the lubricating oil flows back to the second compressor 201.

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

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

[0273] The lubricating oil can be well dissolved in the refrigerant, so that the refrigerant can drive the lubricating oil to flow in the first refrigeration system 10, and due to the presence of the first heat exchange structure 104, the lubricating oil flowing out of the first heat exchange part 108 can be heated again by the fifth heat exchange part 1041, improving the flowability of the lubricating oil and ensuring that the lubricating oil flows back to the first compressor 101.

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

[0275] Optionally, the refrigeration system further comprises a heat exchanger, the heat exchanger comprising a throttling component and a heat exchange pipeline, the throttling component being connected between the outlet of the first heat exchanger and the inlet of the second heat exchanger, and the heat exchange pipeline being connected between the outlet of the second heat exchanger and the return gas port of the compressor, the throttling component and the heat exchange pipeline being 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 component when flowing through the heat exchange pipeline, absorbs the temperature of the throttling component, increases the temperature of the refrigerant flowing out of the outlet of the second heat exchanger, and further enhances the flowability 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 component, thereby reducing the temperature of the refrigerant in the throttling component and reducing the energy consumption of the refrigeration system.

[0277] The heat exchange pipeline is located upstream of the heat exchange structure, i.e. the refrigerant flowing out of the heat exchange pipeline first passes through the second heat exchange component and then flows back to the return gas port of the compressor.

[0278] The temperature of the refrigerant in the first heat exchange component is higher than the temperature of the refrigerant in the throttling component, so if the heat exchange pipeline is located downstream of the heat exchange structure, the temperature of the refrigerant after heat exchange with the first heat exchange component in the second heat exchange component will be relatively high, and when the refrigerant flows through the heat exchange pipeline and exchanges heat with the throttling component, the heat exchange amount will be reduced or heat exchange cannot be performed.

[0279] As shown in FIG. 1, the refrigeration system comprises a first refrigeration system 10 and a second refrigeration system 20. Figure 17As shown, the heat regenerator comprises a first-stage heat regenerator 107 and a second-stage heat regenerator 206. The first-stage heat regenerator 107 comprises a first-stage throttling component 1071 and a first-stage heat exchange pipeline 1072, and the second-stage heat regenerator 206 comprises a second-stage throttling component 2061 and a second-stage heat exchange pipeline 2062. The throttling components comprise the first-stage throttling component 1071 and the second-stage throttling component 2061, and the heat exchange pipelines comprise the first-stage heat exchange pipeline 1072 and the second-stage heat exchange pipeline 2062.

[0280] The first-stage heat regenerator 107 is arranged in the first-stage refrigeration system 10, and the second-stage heat regenerator 206 is arranged 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 part 108. Figure 17 The two ends of the first-stage heat exchange pipeline 1072 are respectively connected to the outlet of the first heat exchange part 108 and the gas return port of the first-stage compressor 101. Figure 18 The two ends of the first-stage heat exchange pipeline 1072 are respectively connected to the outlet of the first heat exchange part 108 and the inlet of the sixth heat exchange part 1042.

[0282] The two ends of the second-stage throttling component 2061 are respectively connected to the outlet of the second heat exchange part 204 and the inlet of the second-stage evaporator 207. Figure 17 The two ends of the second-stage heat exchange pipeline 2062 are respectively connected to the outlet of the second-stage evaporator 207 and the inlet of the fourth heat exchange part 2032. Figure 18

[0283] Optionally, the second heat regenerator comprises an evaporation pipeline for refrigerant flow and fins arranged on the evaporation pipeline.

[0284] The number of evaporation pipelines is multiple, each evaporation pipeline extends along a horizontal plane, and the multiple evaporation pipelines are arranged in a top-down direction, adjacent two evaporation pipelines are connected, and the distance between adjacent two evaporation pipelines in the top-down direction increases.

[0285] Air with a higher temperature has a smaller density, so air with a higher temperature is located above air with a lower temperature. Therefore, the heat exchange capacity of the upper air with the evaporation pipeline is strong, and the heat exchange capacity of the lower air with the evaporation pipeline is relatively weak. Therefore, the distance between adjacent two evaporation pipelines at the top is small, and the distance between adjacent two evaporation pipelines at the bottom is large, that is, the evaporation pipeline is arranged in a top dense and bottom sparse manner, which can fully utilize the heat of the top air, so that the evaporation pipeline at the top fully exchanges heat with the air, and the heat exchange effect of the evaporator is improved.

[0286] It can be understood that the multiple evaporation pipelines can also be uniformly arranged, that is, the distance between adjacent two evaporation pipelines in the top-down direction is equal.​

[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, in sequence along the flow direction of the refrigerant, a second stage compressor 201, a second stage pre-cooler 202, a third heat exchange section 2031, a second heat exchange section 204, a second stage dry filter 205, a second stage throttling component 2061, a second stage evaporator 207, a second stage heat exchange pipe 2062, and a fourth heat exchange section 2032.

[0294] For the first stage condenser 105, the first stage condenser 105 is connected with a first heat exchange section 108 through a 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 jointly constitute an inter-stage heat exchanger 30, which can be an intermediate plate heat exchanger. The inter-stage heat exchanger 30 is also the intermediate heat exchanger in the method for controlling the refrigeration system described above. The inter-stage heat exchanger 30 is a counterflow heat exchanger, and the flow directions of the refrigerants in the first heat exchange section 108 and the second heat exchange section 204 are opposite. 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 counterflow heat exchange (the first heat exchange section 108), and the refrigerant in the second stage refrigeration system 20 after being cooled 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 the top being dense and the bottom being sparse. The second stage evaporator 207 absorbs heat in the refrigeration space, and the refrigerant enters the second stage evaporator 207 from the evaporation pipe at the top and flows out of the second stage evaporator 207 from the evaporation pipe at the bottom.

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

[0298] The first stage pre-cooler 102 is used to preliminarily cool the refrigerant in the first stage refrigeration system 10 by using air.

[0299] The first stage anti-dew pipe 103 is used to cool the refrigerant in the first stage refrigeration system 10 and prevent condensation of the cabinet door of the refrigerator or the freezer.

[0300] The first stage dry filter 106 is used to dry the refrigerant in the first stage refrigeration system 10 and filter the refrigerant before entering the first stage throttling component 1071.

[0301] The first-stage regenerator 107 is a structure in which the first-stage throttling component 1071 is nested in the first-stage heat exchange pipeline 1072, and is used to cool the first-stage throttling component 1071 and increase the temperature of the refrigerant returned to the first-stage compressor 101. For example, the first-stage heat exchange pipeline 1072 is a copper pipe with an inner diameter of 6 mm, and the first-stage throttling component 1071 is a capillary tube with a diameter of 1 mm.

[0302] The first-stage gas-liquid separator 109 is used to separate the gas-liquid two-phase refrigerant and ensure that the refrigerant returned to the first-stage compressor 101 is in a gas phase.

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

[0304] The second-stage pre-cooler 202 is used to preliminarily cool the refrigerant in the second-stage refrigeration system 20 by using air.

[0305] The second-stage heat exchange structure 203 is used to further cool the refrigerant in the second-stage refrigeration system 20 before entering the second heat exchange part 204, and to increase the temperature of the refrigerant of the second-stage compressor 201.

[0306] The second-stage regenerator 206 is a structure in which the second-stage throttling component 2061 is nested in the second-stage heat exchange pipeline 2062, and is used to cool the second-stage throttling component 2061 and increase the temperature of the refrigerant returned to the second-stage compressor 201; for example, the second-stage heat exchange pipeline 2062 is a copper pipe with an inner diameter of 6 mm, and the second-stage throttling component 2061 is a capillary tube with a diameter of 1 mm.

[0307] The second-stage drying filter 205 is used to dry the refrigerant in the second-stage refrigeration system 20 and filter the refrigerant before entering the second-stage throttling component 2061.

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

[0309] The present application improves the refrigeration capacity of the second-stage refrigeration system 20 by arranging the first-stage refrigeration system 10, the second-stage refrigeration system 20, the first heat exchange part 108, the second heat exchange part 204, the regenerator and the heat exchange structure, so that the second-stage refrigeration system 20 can realize ultra-low temperature refrigeration. Moreover, the cold capacity of the first-stage refrigeration system 10, the cold capacity of the first throttling component and the cold capacity of the third heat exchange part 2031 are fully utilized, so that the start-stop times 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, such as the exhaust temperature and / or pressure and the suction temperature and / or pressure, of the first-stage compressor 101 and the second-stage compressor 201 can be improved.

[0310] Specifically, (1) the first-stage refrigeration system 10 and the second-stage refrigeration system 20 are respectively provided with the first-stage regenerator 107 and the second-stage regenerator 206. The second-stage regenerator 206 utilizes the cold energy at the outlet of the second-stage evaporator 207, so that the amount of low-temperature liquid after throttling by the second-stage throttling component 2061 is increased, the refrigerating capacity of the second-stage refrigeration system 20 is increased, and the COP of the system is improved.

[0311] (2) By increasing the first-stage regenerator 107, the second-stage regenerator 206, the first-stage heat exchange structure 104, and the second-stage heat exchange structure 203, the excess cold energy is effectively utilized, and the risk of liquid carry-over of the return gas of the first-stage compressor 101 and the second-stage compressor 201 is reduced.

[0312] (3) The oil separator is removed from the second-stage refrigeration system 20, and the second-stage refrigeration system 20 only utilizes R170 refrigerant and does not include oil return agent. The cross section of the evaporation pipeline of the second-stage evaporator 207 adopts a D shape to reduce the internal volume of the evaporation pipeline. In the case that the amount of refrigerant injected into the second-stage refrigeration system 20 is constant, the second-stage evaporator 207 can be filled with liquid refrigerant to achieve a full-liquid state, and the excess liquid in the second-stage evaporator 207 can be evaporated in the second-stage heat exchange pipeline 2062 by the second-stage throttling component 2061. Thus, the refrigerant in the second-stage evaporator 207 can more easily drive the lubricating oil back to the second-stage compressor 201 from the second-stage evaporator 207. The lubricating oil can be POE (ester oil), and the second-stage refrigeration system 20 can be selected to use a refrigerant that is miscible with the lubricating oil. Finally, under the condition that the second-stage refrigeration system 20 only uses refrigerant and does not use oil return agent, the problem of "oil return" of the second-stage compressor 201 is also solved.

[0313] Optionally, as shown in Figure 17 and Figure 18 , the refrigeration system further comprises a branch pipeline and an expansion device.

[0314] The branch pipeline is connected in parallel with the throttling component and can be controlled to be opened or closed; the expansion device is arranged in the branch pipeline.

[0315] The arrangement of the expansion device enables the first heat exchanger to perform the function of a condenser and the second heat exchanger to perform the function of an evaporator when the branch pipeline is conducted, i.e., the refrigeration function of the refrigeration system can be realized.

[0316] When the temperature of the refrigerant in the heat exchange pipeline is relatively high, the branch pipeline can be opened, and the refrigerant in the branch pipeline is not heat-exchanged 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 will not be increased. Therefore, the rapid refrigeration of the refrigeration system can be realized, and the refrigeration speed at the start of the refrigeration system is not affected by the arrangement of the regenerator.

[0317] The refrigeration system further comprises a switch and a processor.

[0318] The switch is arranged in the branch pipeline and is used for controlling opening and closing of the branch pipeline; the processor is connected with the switch and is configured to control the switch to be opened in a case that the outlet temperature of the second heat exchanger is higher than a preset temperature.

[0319] In a case that the outlet temperature of the second heat exchanger is higher than the preset temperature, the temperature of the refrigerant in the heat exchange pipeline is also higher, for example, the temperature of the refrigerant in the heat exchange pipeline exceeds the temperature of the refrigerant at the throttling component, at this time, heat exchange between the heat exchange pipeline and the throttling component causes the temperature of the refrigerant in the throttling component to rise, thereby slowing down the refrigeration speed. At this time, the processor controls the switch to be opened, and the branch pipeline is turned on, at this time, the refrigerant flowing out of the outlet of the first heat exchanger does not pass through the throttling component, but passes through the branch pipeline and flows into the second heat exchanger through the expansion device, thereby realizing rapid refrigeration.

[0320] In a case that the temperature of the refrigerant in the heat exchange pipeline is reduced to a temperature at which heat exchange between the heat exchange pipeline and the throttling component does not cause the temperature of the refrigerant in the throttling component to rise, the branch pipeline is controlled to be closed, and the refrigerant at the outlet of the first heat exchanger flows into the second heat exchanger through the throttling component.

[0321] The processor can control opening and closing of the switch according to the outlet temperature of the second heat exchanger, or can control opening and closing of the switch according to the length of time of starting, for example, the switch is controlled to be opened within a preset starting time; when the starting exceeds the preset time, the switch is controlled to be closed.

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

[0323] The branch pipeline comprises a first-stage branch pipeline 110, the first-stage branch pipeline 110 is connected with a first-stage throttling component 1071 in parallel and can be controlled to be opened and closed. The expansion device comprises a first-stage expansion device 111, the first-stage expansion device 111 is arranged in the first-stage branch pipeline 110. The switch comprises a first-stage switch 112, the first-stage switch 112 is arranged in the first-stage branch pipeline 110 and is used for controlling opening and closing of the first-stage branch pipeline 110.

[0324] The first-stage refrigeration system 10 is provided with a first-stage branch pipeline 110 and a first-stage expansion device 111. When the temperature of the refrigerant in the first-stage heat exchange pipeline 1072 is relatively high, the first-stage switch 112 is controlled to be opened, so that the first-stage branch pipeline 110 is conducted, and the refrigerant flowing out of the outlet of the first-stage condenser 105 flows into the first heat exchange part 108 through the first-stage branch pipeline 110 instead of the first-stage throttling part 1071, thereby realizing rapid refrigeration. With the operation of the refrigeration system, the temperature of the refrigerant in the first-stage heat exchange pipeline 1072 decreases, and when the temperature decreases to a certain extent (for example, lower than the temperature of the refrigerant in the first-stage throttling part 1071), the first-stage switch 112 is controlled to be closed, so that the first-stage branch pipeline 110 is disconnected, and the refrigerant flowing out of the outlet of the first-stage condenser 105 flows into the first heat exchange part 108 through the first-stage throttling part 1071.

[0325] The branch pipeline includes a second-stage branch pipeline 209, which is connected in parallel with the second-stage throttling part 2061 and can be controlled to be opened and closed. The expansion device includes a second-stage expansion device 210, which is arranged in the second-stage branch pipeline 209.

[0326] The second-stage refrigeration system 20 is provided with the second-stage branch pipeline 209 and the second-stage expansion device 210. When the temperature of the refrigerant in the second-stage heat exchange pipeline 2062 is relatively high, the second-stage switch 211 is controlled to be opened, so that the second-stage branch pipeline 209 is conducted, and the refrigerant flowing out of the outlet of the second heat exchange part 204 flows into the second-stage evaporator 207 through the second-stage branch pipeline 209 instead of the second-stage throttling part 2061, thereby realizing rapid refrigeration. With the operation of the refrigeration system, the temperature of the refrigerant in the second-stage heat exchange pipeline 2062 decreases, and when the temperature decreases to a certain extent (for example, lower than the temperature of the refrigerant in the second-stage throttling part 2061), the second-stage switch 211 is controlled to be closed, so that the second-stage branch pipeline 209 is disconnected, and the refrigerant flowing out of the outlet of the second heat exchange part 204 flows into the second-stage evaporator 207 through the second-stage throttling part 2061.

[0327] The embodiment of the second aspect of the application provides a refrigeration device, which comprises the refrigeration system according to any one of the above embodiments.

[0328] The refrigeration device provided by the embodiment of the second aspect of the application has all the beneficial effects of the refrigeration system according to any one of the above embodiments, and details are not repeated here.

[0329] The above description and drawings suffice to fully enable one skilled in the art to practice the embodiments of the present disclosure. Other embodiments can include structural and other changes. The embodiments are merely representative of the possible variations. Individual components and functions are optional unless explicitly required, and the order of operations can be varied. Portions and features of some embodiments can be included in, or substituted for, portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the drawings, and can be varied in many ways. The scope of the present disclosure is limited only by the claims appended hereto.

[0330] The embodiments of the present disclosure provide a refrigeration equipment comprising the refrigeration system as described above. The device 140, 150 (160) for controlling the refrigeration system is in communication connection with the high-temperature stage compressor, the low-temperature stage compressor and the fan of the refrigeration system as described above, so as to control the rotation speed and start-stop of the high-temperature stage compressor, the low-temperature stage compressor and the fan. The device 150 (160) for controlling the refrigeration system is installed on the refrigeration equipment. The installation relationship described herein is not limited to being placed inside the refrigeration equipment, but also includes installation connection with other components of the refrigeration equipment, including but not limited to physical connection, electrical connection or signal transmission connection, etc. Those skilled in the art can understand that the device 150 (160) for controlling the refrigeration system can be adapted to a feasible product body, thereby realizing other feasible embodiments.

[0331] The embodiments of the present disclosure provide a computer readable storage medium, which stores computer executable instructions, and the computer executable instructions are configured to execute the method for controlling the refrigeration system.

[0332] The technical solutions of the embodiments of the present disclosure can be embodied in the form of a software product. The computer software product is stored in a storage medium, and includes one or more instructions to make a computer device (which can be a personal computer, a server, or a network device, etc.) execute all or part of the steps of the method described in the embodiments of the present disclosure. The storage medium described above can be a non-transitory storage medium, such as a U disk, a mobile hard disk, a read-only memory (ROM), a random access memory (RAM), a magnetic disk or an optical disk, etc.

[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] In the embodiments disclosed herein, the disclosed methods, products (including but not limited to apparatuses, devices, etc.), can be implemented in other manners. For example, the described apparatus embodiments can be implemented only in a form of a logical function, and can be implemented by using a manner such as software (for example, application program) or the like. In some embodiments, a plurality of units or components can be combined or integrated into another system, or some features can be ignored or not executed. In addition, the displayed or discussed coupling or direct coupling or indirect coupling between different units, or the coupling or direct coupling or indirect coupling between the displayed or discussed communication connections can be in a form of electrical, mechanical or other forms.

[0336] The flowcharts and block diagrams in the drawings show the possible implementation architectures, functions and operations of the system, method and computer program product according to the embodiments of the present disclosure. In this regard, each block in the flowcharts or block diagrams can represent a module, a program segment or a part of code containing one or more executable instructions for implementing the specified logical function. In some alternative implementations, the functions noted in the blocks can occur in an order different from that noted in the drawings. For example, two consecutive blocks can actually be executed substantially in parallel, and sometimes they can be executed in reverse order, depending on the functions involved. In the descriptions corresponding to the flowcharts and block diagrams in the drawings, the operations or steps corresponding to different blocks can also occur in an order different from that disclosed in the descriptions, and sometimes there is no specific order between different operations or steps. For example, two consecutive operations or steps can actually be executed substantially in parallel, and sometimes they can be executed in reverse order, depending on the functions involved. Each block in the block diagrams and / or flowcharts, and the combination of blocks in the block diagrams and / or flowcharts, can be implemented by a dedicated hardware-based system that performs the specified functions or actions, or can be implemented by a combination of dedicated hardware and computer instructions.

Claims

1. A refrigeration system characterized by, Comprise: The compressor, the first heat exchanger and the second heat exchanger are connected in sequence; The heat exchange structure comprises a first heat exchange member and a second heat exchange member capable of heat exchange, the first heat exchange member is communicated between the exhaust port of the compressor and the inlet of the first heat exchanger, and the second heat exchange member is communicated between the outlet of the second heat exchanger and the return air port of the compressor; The compressor comprises a first stage compressor and a second stage compressor, the first heat exchanger comprises a first stage condenser and a second heat exchange part, the second heat exchanger comprises a first heat exchange part and a second stage evaporator, the first heat exchange part and the second heat exchange part can exchange heat; The first stage refrigeration system comprises a first stage compressor, a first stage condenser and a first heat exchange part connected in sequence; The second stage refrigeration system comprises a second stage compressor, a second heat exchange part and a second stage evaporator connected in sequence; The refrigerant used by the second stage refrigeration system is mutually soluble with the lubricating oil used by the second stage compressor; And / or the refrigerant used by the first stage refrigeration system is mutually soluble with the lubricating oil used by the first stage compressor.

2. The refrigeration system of claim 1, wherein, The heat exchange structure comprises: 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.

3. The refrigeration system according to claim 2, wherein The third heat exchange part comprises a third heat exchange pipe, and the two ends of the third heat exchange pipe are communicated with the exhaust port of the second stage compressor and the inlet of the second heat exchange part respectively; The fourth heat exchange part comprises a fourth heat exchange pipe, and the two ends of the fourth heat exchange pipe are communicated with the outlet of the second stage evaporator and the return air port of the second stage compressor respectively; Wherein, the third heat exchange pipe is sleeved outside the fourth heat exchange pipe or the fourth heat exchange pipe is sleeved outside the third heat exchange pipe, and the third heat exchange pipe and / or the fourth heat exchange pipe are corrugated pipes.

4. The refrigeration system of claim 1, 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.

5. The refrigeration system according to claim 4, wherein The fifth heat exchange part comprises a fifth heat exchange pipe, and the two ends of the fifth heat exchange pipe are communicated with the exhaust port of the first stage compressor and the inlet of the first stage condenser respectively; The sixth heat exchange part comprises a sixth heat exchange pipe, and the two ends of the sixth heat exchange pipe are communicated with the outlet of the first heat exchange part and the return air port of the first stage compressor respectively; Wherein, the fifth heat exchange pipe is sleeved outside the sixth heat exchange pipe or the sixth heat exchange pipe is sleeved outside the fifth heat exchange pipe, and the fifth heat exchange pipe and / or the sixth heat exchange pipe are corrugated pipes.

6. The refrigeration system of any of claims 1-5, wherein, Also comprise: The heat regenerator comprises a throttling component and a heat exchange pipeline, the throttling component is connected between the outlet of the first heat exchanger and the inlet of the second heat exchanger, the heat exchange pipeline is connected between the outlet of the second heat exchanger and the return gas port of the compressor, the throttling component and the heat exchange pipeline can exchange heat, and the heat exchange pipeline is located upstream of the heat exchange structure.

7. The refrigeration system of any of claims 1-5, wherein, The second heat exchanger comprises: The evaporation pipelines are arranged in sequence and communicated in the top-down direction, and the distance between adjacent two evaporation pipelines increases in the top-down direction.

8. A refrigeration appliance characterized in that, A refrigeration system comprising a refrigeration system as claimed in any one of claims 1 to 7.

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