Refrigerating system and testing and sorting equipment

Abstract

The utility model relates to a refrigeration system and test sorting equipment, which comprises a first refrigeration module, a second refrigeration module, a third refrigeration module, a fourth refrigeration module, a fifth refrigeration module and a sixth refrigeration module, and is characterized in that the first refrigeration module comprises a first throttle mechanism, a first compressor, a condenser and a first evaporator; the first compressor, the condenser, the first expansion valve and the first evaporator are sequentially communicated to form a first closed loop; the first refrigeration module further comprises a first heat exchange pipeline, one end of the first heat exchange pipeline communicates with the output end of the condenser, and the other end of the first heat exchange pipeline communicates with the input end of the first evaporator. The second refrigeration module comprises a second compressor, a first evaporator, a second expansion valve and a second evaporator which are sequentially communicated to form a second closed loop; the second closed loop comprises a first pipeline arranged between the output end of the second expansion valve and the input end of the second evaporator; the first heat exchange pipeline is thermally coupled with the first pipeline through the first heat exchanger, and a refrigerant of the first heat exchange pipeline is expanded and depressurized through the first throttling mechanism after exchanging heat with the first pipeline.

Description

Technical Field

[0001] The utility model relates to the technical field of temperature control, in particular to a refrigeration system and testing and sorting equipment. Background Art

[0002] The test equipment for electronic components is equipped with a temperature control system, which includes a refrigeration system and a heating system. When testing electronic components, the refrigeration system and the heating system work together to control the temperature of the electronic components. Among the refrigeration systems, the two-stage compression cascade refrigeration system is more common.

[0003] The two-stage compression cascade refrigeration system includes a high-temperature refrigeration module and a low-temperature refrigeration module, and the low-temperature refrigeration module ultimately provides medium-temperature or low-temperature refrigerant. The refrigerant provided by the low-temperature refrigeration module exchanges heat with the electronic components through the load end, so that the electronic components are maintained at the target temperature.

[0004] When the load side requires a higher refrigerant temperature to exchange heat with electronic components, a bypass branch is led out through the exhaust end of the compressor of the low-temperature refrigeration module. The refrigerant in the bypass branch is mixed with the refrigerant in the main circuit after throttling and cooling by the expansion valve to increase the temperature of the refrigerant flowing to the load side. However, this method requires adjusting the ratio of the refrigerant flow between the main circuit and the bypass branch. The bypass branch has a greater impact on the entire low-temperature refrigeration module, and the bypass valve on the bypass branch has a long adjustment cycle, which is prone to temperature fluctuations. At the same time, because the exhaust end of the compressor is connected to the return air end through the bypass branch, it is easy to cause a high pressure at the return air end of the compressor, which is not conducive to the long-term stable operation of the low-temperature compressor. Utility Model Content

[0005] Based on this, it is necessary to provide a refrigeration system and testing and sorting equipment that can improve the above problems.

[0006] A refrigeration system, comprising:

[0007] The first refrigeration module comprises a first throttling mechanism, a first compressor, a condenser and a first evaporator, wherein the first throttling mechanism comprises a first expansion valve; the first compressor, the condenser, the first expansion valve and the first evaporator are sequentially connected to form a first closed loop; the first refrigeration module further comprises a first heat exchange pipeline, one end of the first heat exchange pipeline is connected to the output end of the condenser, and the other end is connected to the input end of the first evaporator;

[0008] The second refrigeration module comprises a second compressor, the first evaporator, a second expansion valve and a second evaporator which are sequentially connected to form a second closed loop; the second closed loop comprises a first pipeline arranged between an output end of the second expansion valve and an input end of the second evaporator;

[0009] The first heat exchanger, the first heat exchange pipeline is thermally coupled with the first pipeline through the first heat exchanger, and the refrigerant in the first heat exchange pipeline is expanded and depressurized through the first throttling mechanism after heat exchange with the first pipeline.

[0010] In one embodiment, the first heat exchange pipeline is arranged independently from the first closed loop;

[0011] One end of the first heat exchange pipeline is connected to the output end of the condenser, and the other end of the first heat exchange pipeline is connected to the input end of the first expansion valve. After the refrigerant in the first heat exchange pipeline exchanges heat with the first pipeline, it is expanded and depressurized through the first expansion valve.

[0012] Alternatively, one end of the first heat exchange pipeline is connected to the output end of the condenser, and the other end of the first heat exchange pipeline is connected to the part of the first closed loop located at the output end of the first expansion valve and the input end of the first evaporator. The first throttling mechanism also includes a third expansion valve, which is arranged on the first heat exchange pipeline. The refrigerant in the first heat exchange pipeline is expanded and reduced in pressure through the third expansion valve after heat exchange with the first pipeline.

[0013] In one embodiment, the refrigeration system comprises a first control valve, which is arranged on the first heat exchange pipeline to control the on-off of the first heat exchange pipeline; and / or

[0014] The refrigeration system also includes a second control valve. The first heat exchange pipeline and the first closed loop form a first intersection and a second intersection. The second control valve is arranged on the first closed loop and located between the first intersection and the second intersection. The second control valve is used to control the on-off of the part of the first closed loop at the first intersection and the second intersection.

[0015] In one embodiment, the first heat exchange pipeline is part of the first closed loop, and the first heat exchange pipeline is connected between the output end of the condenser and the input end of the first expansion valve. The refrigerant in the first heat exchange pipeline is expanded and reduced in pressure through the first expansion valve after heat exchange with the first pipeline.

[0016] In one embodiment, the second refrigeration module further includes a second throttling mechanism, and the second throttling mechanism includes the second expansion valve; the second closed loop includes a second pipeline provided between the output end of the second compressor and the input end of the first evaporator;

[0017] The second refrigeration module also includes a connecting pipe, and the refrigeration system also includes a second heat exchanger. One end of the connecting pipe is connected to the output end of the first evaporator, and the other end is connected to the input end of the second evaporator. The connecting pipe is thermally coupled with the second pipe through the second heat exchanger; the refrigerant in the connecting pipe is expanded and reduced in pressure by the second throttling mechanism and then flows to the second heat exchanger.

[0018] In one embodiment, the communication pipeline is provided independently from the second closed loop;

[0019] Both ends of the communication pipeline are connected to the first pipeline, and the refrigerant in the communication pipeline expands and reduces pressure through the second expansion valve and then flows to the second heat exchanger; or

[0020] The second throttling mechanism also includes a fourth expansion valve, one end of the connecting pipeline is connected to the part of the second closed loop located between the output end of the first evaporator and the input end of the second expansion valve, and the other end is connected to the input end of the second evaporator; the fourth expansion valve is arranged on the connecting pipeline, and the refrigerant in the connecting pipeline expands and reduces pressure through the fourth expansion valve and then flows to the second heat exchanger.

[0021] In one embodiment, the refrigeration system further comprises a third control valve, wherein the third control valve is arranged on the communication pipeline to control the on-off of the communication pipeline; and / or

[0022] The refrigeration system also includes a fourth control valve. The connecting pipeline and the second closed loop have a third intersection and a fourth intersection. The fourth control valve is arranged on the second closed loop and located between the third intersection and the fourth intersection. The fourth control valve is used to control the on-off of the part of the second closed loop located between the third intersection and the fourth intersection.

[0023] In one embodiment, the first pipeline is the connecting pipeline.

[0024] In one embodiment, the first refrigeration module further includes a second heat exchange pipeline independently provided from the first closed loop, one end of the second heat exchange pipeline is connected to the output end of the condenser, and the other end of the second heat exchange pipeline is connected to the input end of the first compressor;

[0025] The refrigeration system also includes a third heat exchanger, and the second closed loop includes a third pipeline arranged between the output end of the second evaporator and the input end of the second compressor; the second heat exchange pipeline is thermally coupled with the third pipeline through the third heat exchanger, and the refrigerant in the second heat exchange pipeline is expanded and reduced in pressure through the first throttling mechanism and then flows to the third heat exchanger.

[0026] In one embodiment, one end of the second heat exchange pipeline is connected to the output end of the first expansion valve, and the other end is connected to the input end of the first compressor, and the refrigerant in the second heat exchange pipeline is expanded and depressurized by the first expansion valve and then flows to the third heat exchanger; or

[0027] One end of the second heat exchange pipeline is connected to the part of the first closed loop located between the output end of the condenser and the input end of the first expansion valve; the first throttling mechanism also includes a throttling device, and the refrigerant in the second heat exchange pipeline expands and reduces pressure through the throttling device and then flows to the third heat exchanger.

[0028] In one embodiment, the refrigeration system further includes a fifth control valve, which is disposed on the second heat exchange pipeline to control the on-off of the second heat exchange pipeline.

[0029] In one embodiment, the first heat exchange pipeline is independently arranged from the first closed loop, both ends of the first heat exchange pipeline are connected to the portion of the first closed loop located between the output end of the condenser and the input end of the first expansion valve, and the first heat exchange pipeline and the first closed loop have a first intersection and a second intersection; one end of the second heat exchange pipeline is connected to the first heat exchange pipeline, and has a fifth intersection with the first heat exchange pipeline;

[0030] The refrigeration system further comprises a first control valve, a second control valve, a fifth control valve and a sixth control valve, wherein the sixth control valve is arranged on the first heat exchange pipeline and is located between the first intersection and the fifth intersection, the first control valve is arranged on the first heat exchange pipeline and is located between the second intersection and the fifth intersection, the second control valve is arranged on the first closed loop and is located between the first intersection and the second intersection, and the fifth control valve is arranged on the second heat exchange pipeline;

[0031] The refrigerant in the first heat exchange pipeline is expanded and reduced in pressure through the first expansion valve after exchanging heat with the first pipeline. The first throttling mechanism also includes a throttling element. The refrigerant in the second heat exchange pipeline is expanded and reduced in pressure through the throttling element and then flows to the third heat exchanger.

[0032] A testing and sorting device comprises the refrigeration system as described above.

[0033] In the above refrigeration system and test and sorting equipment, when the set temperature is relatively high, the refrigerant flows to the first heat exchange pipeline through the condenser, and flows to the first heat exchanger through the first heat exchange pipe. In the first heat exchanger, the refrigerant in the first heat exchange pipeline exchanges heat with the refrigerant in the first pipeline, and the refrigerant in the first heat exchange pipeline expands and depressurizes after the first throttling mechanism and flows to the first evaporator, and the refrigerant in the first pipeline flows to the second evaporator after heat exchange, thereby increasing the temperature of the refrigerant flowing to the second evaporator. That is, it is ensured that the temperature of the refrigerant entering the second evaporator (load) meets the set temperature, so that the refrigeration system meets the high temperature working condition requirements. Compared with the prior art (a bypass branch is drawn out from the exhaust end of the compressor of the low-temperature refrigeration module, and the refrigerant in the bypass branch is mixed with the refrigerant in the main circuit after throttling and cooling by the expansion valve to increase the temperature of the refrigerant flowing to the load end), the refrigeration system of the present application no longer needs to adjust the ratio of the refrigerant flow between the main circuit and the bypass branch, avoids the influence of the bypass branch on the low-temperature refrigeration module, and reduces the fluctuation of the temperature of the second evaporator. At the same time, the exhaust end of the second compressor no longer needs to be connected to the return air end through a bypass branch, which will not cause excessive pressure at the return air end of the second compressor, and is conducive to the long-term stable operation of the low-temperature compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 A schematic diagram of the structure of a refrigeration system provided in one embodiment of the present application;

[0035] Figure 2 A schematic diagram of the structure of a refrigeration system provided in another embodiment of the present application;

[0036] Figure 3 A schematic diagram of the structure of a refrigeration system provided in yet another embodiment of the present application;

[0037] Figure 4 A schematic diagram of the structure of a refrigeration system provided in yet another embodiment of the present application;

[0038] Figure 5 A schematic diagram of the structure of a refrigeration system provided in yet another embodiment of the present application;

[0039] Figure 6 A schematic structural diagram of a refrigeration system provided in yet another embodiment of the present application.

[0040] Description of reference numerals:

[0041] 100. refrigeration system; 10. first refrigeration module; 11. first compressor; 12. condenser; 13. first expansion valve; 14. first evaporator; 15. first heat exchange pipeline; 16. third expansion valve; 17. second heat exchange pipeline; 18. throttling device; 20. second refrigeration module; 21. second compressor; 22. second expansion valve; 23. second evaporator; 24. first pipeline; 25. second pipeline; 26. connecting pipeline; 27. fourth expansion valve; 28. third pipeline; 30. first heat exchanger; 40. first control valve; 50. second control valve; 60. second heat exchanger; 70. third control valve; 80. fourth control valve; 90. third heat exchanger; 110. fifth control valve; 120. sixth control valve; A. first intersection; B. second intersection; C. third intersection; D. fourth intersection; E. fifth intersection. DETAILED DESCRIPTION

[0042] In order to make the above-mentioned purposes, features and advantages of the utility model more obvious and easy to understand, the specific implementation methods of the utility model are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the utility model. However, the utility model can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the utility model, so the utility model is not limited by the specific embodiments disclosed below.

[0043] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0044] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of the present utility model, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0045] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0046] In the present utility model, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature being "above", "above" or "above" a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being "below", "below" or "below" a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0047] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be a central element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used herein are for illustrative purposes only and are not intended to be the only implementation method.

[0048] See also Figure 1 In one embodiment of the present application, a refrigeration system 100 is provided for controlling the temperature of electronic components. Specifically, the electronic components are chips, and the refrigeration system 100 is used to control the temperature of the chips. Of course, in other embodiments, the types of electronic components used for temperature control by the refrigeration system 100 are not limited.

[0049] The refrigeration system 100 includes a first refrigeration module 10, and the first refrigeration module 10 includes a first throttling mechanism, a first compressor 11, a condenser 12 and a first evaporator 14. Among them, the first throttling mechanism includes a first expansion valve 13. The first compressor 11, the condenser 12, the first expansion valve 13 and the first evaporator 14 are connected in sequence to form a first closed loop.

[0050] When the first closed loop is working, the first compressor 11 inhales the high-temperature, low-pressure refrigerant gas output from the output end of the first evaporator 14, compresses the refrigerant into a high-temperature, high-pressure refrigerant gas, and discharges it to the condenser 12 from the exhaust end (output end) of the first compressor 11. When the refrigerant passes through the condenser 12, it is condensed into a medium-temperature, high-pressure refrigerant liquid by the condenser 12, and is expanded and reduced in pressure by the first expansion valve 13 to be a low-temperature, low-pressure refrigerant liquid, and finally outputs the first evaporator 14 again from the input end of the first evaporator 14. When the low-temperature, low-pressure refrigerant liquid enters the first evaporator 14, it can exchange heat with the cooled mechanism, thereby cooling the cooled mechanism. The refrigerant after heat exchange enters the first compressor 11 again from the output end of the first evaporator 14, and the cycle repeats.

[0051] The refrigeration system 100 also includes a second refrigeration module 20, which includes a second compressor 21, a first evaporator 14, a second expansion valve 22 and a second evaporator 23 which are sequentially connected to form a second closed loop. That is, the first evaporator 14 serves as the evaporator of the first refrigeration module 10, and as the condenser of the second refrigeration module 20, the first evaporator 14 is also called an evaporative condenser. At this time, the first refrigeration module 10 is a high-temperature refrigeration module, the second refrigeration module 20 is a low-temperature refrigeration module, and the refrigeration system 100 is a two-stage compression cascade refrigeration system 100. It should be noted that the first evaporator 14 has two input ends and an output end, and the two input ends correspond to the two output ends one by one and are connected to each other. When the first evaporator 14 serves as the evaporator of the first refrigeration module 10, the corresponding input end and output end are respectively connected to the output end of the first expansion valve 13 and the input end of the first compressor 11. When the evaporative condenser is used as the condenser of the second refrigeration module 20 , the corresponding input end and output end are communicated with the output end of the second compressor 21 and the input end of the second expansion valve 22 , respectively.

[0052] Specifically, the first expansion valve 13 is a thermal expansion valve, and the second expansion valve 22 is an electronic expansion valve.

[0053] When the second closed loop is working, the second compressor 21 sucks the high-temperature, low-pressure refrigerant output from the output end of the second evaporator 23, compresses the refrigerant into a high-temperature, high-pressure refrigerant gas, and discharges it from the output end of the second compressor 21 to the first evaporator 14. When the refrigerant passes through the first evaporator 14, it exchanges heat with the refrigerant of the first refrigeration module 10, and is condensed by the first evaporator 14 into a medium-temperature, high-pressure refrigerant liquid, that is, the refrigerant in the first refrigeration circuit plays a role in cooling the refrigerant in the second refrigeration circuit. The medium-temperature, high-pressure refrigerant liquid is expanded and depressurized into a low-temperature, low-pressure refrigerant liquid through the second expansion valve 22, and finally enters the second evaporator 23 again from the output end of the second evaporator 23. When the low-temperature, low-pressure liquid refrigerant enters the second evaporator 23, it can exchange heat with electronic components to control the temperature of the electronic components. The refrigerant after heat exchange enters the second compressor 21 again from the output end of the second evaporator 23, and the cycle repeats.

[0054] Further reading Figure 1 The first refrigeration module 10 further includes a first heat exchange pipeline 15, one end of which is connected to the output end of the condenser 12, and the other end of which is connected to the input end of the first evaporator 14. The second closed loop includes a first pipeline 24, which is connected between the output end of the second expansion valve 22 and the input end of the second evaporator 23. The refrigeration system 100 further includes a first heat exchanger 30, the first heat exchange pipeline 15 is thermally coupled with the first pipeline 24 through the first heat exchanger 30, and the refrigerant in the first heat exchange pipeline 15 is expanded and depressurized through the first throttling mechanism after heat exchange with the first pipeline 24.

[0055] In the refrigeration system 100 provided in the embodiment of the present application, when the set temperature is relatively high, the refrigerant flows to the first heat exchange pipeline 15 through the condenser 12, and then flows to the first heat exchanger 30 through the first heat exchange pipeline 15. In the first heat exchanger 30, the refrigerant in the first heat exchange pipeline 15 exchanges heat with the refrigerant in the first pipeline 24. After the heat exchange, the refrigerant in the first heat exchange pipeline 15 is expanded and depressurized by the first throttling mechanism and then flows to the first evaporator 14. After the heat exchange, the refrigerant in the first pipeline 24 flows to the second evaporator 23, thereby increasing the temperature of the refrigerant flowing to the second evaporator 23. That is, it is ensured that the temperature of the refrigerant entering the second evaporator 23 (load) meets the set temperature, so that the refrigeration system 100 meets the high temperature working condition requirements. Compared with the prior art (a bypass branch is led out through the exhaust end of the compressor of the low-temperature refrigeration module, and the refrigerant in the bypass branch is mixed with the refrigerant in the main circuit after throttling and cooling by the expansion valve to increase the temperature of the refrigerant flowing to the load end), the refrigeration system 100 of the present application no longer needs to adjust the ratio of the refrigerant flow between the main circuit and the bypass branch, avoids the influence of the bypass branch on the low-temperature refrigeration module, and reduces the temperature fluctuation of the second evaporator 23. At the same time, the exhaust end of the second compressor 21 no longer needs to be connected to the return air end through the bypass branch, which will not cause excessive pressure at the return air end of the second compressor 21, which is conducive to the long-term stable operation of the low-temperature compressor.

[0056] It should also be noted here that after the refrigerant in the first heat exchange pipeline 15 exchanges heat with the refrigerant in the first pipeline 24 in the first heat exchanger 30, the temperature of the refrigerant in the first heat exchange pipeline 15 decreases, thereby reducing the superheat of the refrigerant returning to the first compressor 11 and improving the refrigeration capacity of the first refrigeration module 10.

[0057] In some embodiments, see Figure 2 The first heat exchange pipeline 15 is independently arranged from the first closed loop. One end of the first heat exchange pipeline 15 is connected to the output end of the condenser 12, and the other end is connected to the input end of the first expansion valve 13. The refrigerant in the first heat exchange pipeline 15 is expanded and depressurized through the first expansion valve 13 after heat exchange with the first pipeline 24.

[0058] In the above configuration, since the first heat exchange pipeline 15 exists independently of the first closed loop, the first heat exchange pipeline 15 is a bypass branch of the first closed loop. When the set temperature of the refrigeration system 100 is relatively low, the first heat exchange pipeline 15 is controlled to be disconnected and connected, and the first closed loop is connected. At this time, the refrigeration system 100 meets the requirements of operating in the low temperature mode. When the set temperature of the refrigeration system 100 is relatively high, the first closed loop is controlled to be disconnected and connected. At this time, the first heat exchange pipeline 15 is connected, and the refrigerant in the condenser 12 flows to the first heat exchange pipeline 15, and after the first heat exchanger 30 exchanges heat with the refrigerant in the first pipeline 24, it expands and depressurizes through the first throttling mechanism and flows to the first evaporator 14. At this time, the refrigeration system 100 meets the requirements of operating in the high temperature mode. In the low temperature mode, the refrigerant in the condenser 12 expands and depressurizes through the first expansion valve 13 and flows to the first evaporator 14. In the high temperature mode, the refrigerant in the first heat exchange pipeline 15 expands and depressurizes through the first expansion valve 13 and flows to the first evaporator 14. That is, no matter in the low temperature mode or the high temperature mode, the refrigerant is expanded and depressurized through the first expansion valve 13 , thereby simplifying the structure of the refrigeration system 100 .

[0059] Optionally, continue to Figure 1 , the refrigeration system 100 further includes a first control valve 40, which is disposed on the first heat exchange pipeline 15 to control the on-off of the first heat exchange pipeline 15. The refrigeration system 100 further includes a second control valve 50, the first heat exchange pipeline 15 and the first closed loop form a first intersection A and a second intersection B, and the second control valve 50 is disposed on the first closed loop and is located between the first intersection A and the second intersection B. The second control valve 50 is used to control the on-off of the portion of the first closed loop between the first intersection A and the second intersection B. In this way, when the refrigeration system 100 needs to run in low temperature mode, the first control valve 40 is closed and the second control valve 50 is opened; when the refrigeration system 100 needs to run in high temperature mode, the first control valve 40 is opened and the second control valve 50 is closed.

[0060] In some other embodiments, continue to refer to Figure 1 , the first heat exchange pipeline 15 is set independently of the first closed loop. One end of the first heat exchange pipeline 15 is connected to the output end of the condenser 12, and the other end of the first heat exchange pipeline 15 is connected to the part of the first closed loop located at the output end of the first expansion valve 13 and the input end of the first evaporator 14. The first throttling mechanism also includes a third expansion valve 16, which is arranged on the first heat exchange pipeline 15. The refrigerant in the first heat exchange pipeline 15 is expanded and reduced in pressure through the third expansion valve 16 after heat exchange with the first pipeline 24.

[0061] The above configuration can also enable the refrigeration system 100 to meet the operating requirements in low temperature mode and high temperature mode. Different from the above embodiment, in low temperature mode, the refrigerant in the condenser 12 is expanded and depressurized through the first expansion valve 13 and flows to the first evaporator 14, and in high temperature mode, the refrigerant in the first heat exchange pipeline 15 is expanded and depressurized through the third expansion valve 16 and flows to the first evaporator 14. That is, in low temperature mode, the refrigerant is expanded and depressurized through the first expansion valve 13, and in high temperature mode, the refrigerant is expanded and depressurized through the third expansion valve 16, and the two do not affect each other.

[0062] In some other embodiments, see Figure 3 The first heat exchange pipeline 15 is part of the first closed loop, and the first heat exchange pipeline 15 is connected between the output end of the condenser 12 and the input end of the first expansion valve 13. After the first heat exchange pipeline 15 exchanges heat with the first pipeline 24, it is expanded and depressurized through the first expansion valve 13. At this time, the refrigeration system 100 can also operate in the high temperature mode.

[0063] In some embodiments, see Figure 4 , the second refrigeration module 20 further includes a second throttling mechanism, and the second throttling mechanism includes the above-mentioned second expansion valve 22. The second closed loop includes a second pipeline 25 provided between the output end of the second compressor 21 and the input end of the first evaporator 14, the second refrigeration module 20 further includes a connecting pipeline 26, and the refrigeration system 100 further includes a second heat exchanger 60. One end of the connecting pipeline 26 is connected to the output end of the first evaporator 14, and the other end is connected to the input end of the second evaporator 23. The connecting pipeline 26 is thermally coupled with the second pipeline 25 through the second heat exchanger 60. The refrigerant in the connecting pipeline 26 flows to the second heat exchanger 60 after expansion and decompression through the second throttling mechanism. In this way, when the set temperature of the refrigeration system 100 is relatively high, the refrigerant in the first condenser 12 flows to the connecting pipeline 26, and flows to the second heat exchanger 60 after expansion and decompression through the second throttling mechanism. At this time, the refrigeration system 100 meets the requirements of operating in the high temperature mode.

[0064] With the above arrangement, the refrigerant flowing to the second evaporator 23 exchanges heat with the medium-temperature refrigerant after the high-temperature condenser 12 through the first heat exchanger 30, and exchanges heat with the low-temperature exhaust pipe refrigerant through the second heat exchanger 60. The flow rate of the low-temperature refrigerant is regulated by the second throttling mechanism to achieve the set temperature of the refrigerant entering the second evaporator 23 (load).

[0065] In some specific embodiments, the refrigerant flowing to the second evaporator 23 exchanges heat with the low-temperature exhaust pipe refrigerant through the second heat exchanger 60, and then exchanges heat with the medium-temperature refrigerant after the high-temperature condenser 12 through the first heat exchanger 30, so that the temperature of the refrigerant flowing to the second evaporator 23 gradually increases.

[0066] In some embodiments, see Figure 4 The connecting pipe 26 is independently arranged from the second closed loop. Both ends of the connecting pipe 26 are connected to the first pipe 24. The refrigerant in the connecting pipe 26 is expanded and depressurized by the second expansion valve 22 and then flows to the second heat exchanger 60.

[0067] In the above configuration, since the connecting pipe 26 exists independently of the second closed loop, the connecting pipe 26 serves as a bypass branch of the second closed loop. When the set temperature of the refrigeration system 100 is relatively low, the connecting pipe 26 is controlled to be disconnected, and the second closed loop is connected. At this time, the refrigeration system 100 meets the operation requirements in the low temperature mode. When the set temperature of the refrigeration system 100 is relatively high, the second closed loop is controlled to be disconnected, and the connecting pipe 26 is connected. The refrigerant in the first evaporator 14 is expanded and depressurized by the second expansion valve 22 and then all flows to the connecting pipe 26. The refrigerant flowing to the second evaporator 23 exchanges heat with the refrigerant in the low temperature exhaust pipe through the second heat exchanger 60, and then exchanges heat with the medium temperature refrigerant after the high temperature condenser 12 through the first heat exchanger 30, so that the refrigeration system 100 meets the operation requirements in the high temperature mode. Meanwhile, in the low temperature mode, the refrigerant in the first evaporator 14 is expanded and depressurized through the second expansion valve 22 and then flows to the second evaporator 23, and in the high temperature mode, the refrigerant in the first evaporator 14 is expanded and depressurized through the second expansion valve 22 and then flows to the connecting pipe 26. That is, no matter in the low temperature mode or the high temperature mode, the refrigerant is expanded and depressurized through the second expansion valve 22, which simplifies the structure of the refrigeration system 100.

[0068] Optionally, continue to Figure 4 , the refrigeration system 100 further includes a third control valve 70, which is arranged on the connecting line 26 to control the on-off of the connecting line 26. The refrigeration system 100 further includes a fourth control valve 80, and the connecting line 26 and the second closed loop have a third intersection C and a fourth intersection D. The fourth control valve 80 is arranged on the second closed loop and is located between the third intersection C and the fourth intersection D, and the fourth control valve 80 is used to control the on-off of the second closed loop. In this way, when the refrigeration system 100 needs to run in the low temperature mode, the third control valve 70 is closed and the fourth control valve 80 is opened; when the refrigeration system 100 needs to run in the high temperature mode, the third control valve 70 is opened and the fourth control valve 80 is closed.

[0069] In some other embodiments, continue to refer to Figure 1 The second throttling mechanism further includes a fourth expansion valve 27. One end of the connecting pipe 26 is connected to the portion of the second closed loop located between the output end of the first evaporator 14 and the input end of the second expansion valve 22, and the other end is connected to the input end of the second evaporator 23. The fourth expansion valve 27 is provided on the connecting pipe 26. The refrigerant in the connecting pipe 26 expands and reduces pressure through the fourth expansion valve 27 and flows to the second heat exchanger 60.

[0070] The above configuration can also enable the refrigeration system 100 to meet the operation requirements in the low temperature mode and the high temperature mode. At the same time, in the low temperature mode, the refrigerant in the first evaporator 14 expands and depressurizes through the second expansion valve 22 and then flows to the second evaporator 23, and in the high temperature mode, the refrigerant in the first evaporator 14 expands and depressurizes through the fourth expansion valve 27 and then flows to the second evaporator 23. That is, in the low temperature mode, the refrigerant expands and depressurizes through the second expansion valve 22, and in the high temperature mode, the refrigerant expands and depressurizes through the fourth expansion valve 27, and the two do not affect each other.

[0071] In some other embodiments, please refer to Figure 3 , the first pipeline 24 is a connecting pipeline 26. At this time, the connecting pipeline 26 is a part of the second closed loop. At this time, the refrigeration system 100 can also operate in the high temperature mode.

[0072] In some embodiments, see Figure 5 The first refrigeration module 10 further includes a second heat exchange pipeline 17, which is independently arranged from the first closed loop. One end of the second heat exchange pipeline 17 is connected to the output end of the condenser 12, and the other end is connected to the input end of the first compressor 11. The refrigeration system 100 further includes a third heat exchanger 90, and the second closed loop includes a third pipeline 28 arranged between the output end of the second evaporator 23 and the input end of the second compressor 21. The second heat exchange pipeline 17 is thermally coupled with the third pipeline 28 through the third heat exchanger 90, and the refrigerant in the second heat exchange pipeline 17 flows to the third heat exchanger 90 after expansion and decompression through the first throttling mechanism. In this way, when the return air temperature of the second compressor 21 is high, the refrigerant in the condenser 12 flows to the second heat exchange pipeline 17, and after expansion and decompression by the first throttling mechanism, flows to the third heat exchanger 90, and the refrigerant in the second heat exchange pipeline 17 exchanges heat with the refrigerant in the third pipeline 28 in the third heat exchanger 90, thereby achieving the purpose of reducing the return air temperature of the second compressor 21. Compared with the prior art (a bypass branch is set after the second expansion valve 22 and connected to the return air pipe, and the bypass branch will cause the refrigerant entering the second evaporator 23 to be reduced, thereby weakening the refrigeration capacity; a solenoid valve is set on the bypass branch, and the solenoid valve is used to control the mixing of the low-temperature refrigerant after throttling and the high-temperature refrigerant in the return air pipe, and the switch of the solenoid valve will impact the stable operation of the main circuit, which is not conducive to the stable output of the system), it is no longer necessary to lead out a bypass branch from the second expansion valve 22 to reduce the return air temperature, which will not weaken the refrigeration capacity of the low-temperature refrigeration module, and is conducive to the stable operation of the system. At the same time, after passing through the third heat exchanger 90, the temperature of the high-temperature refrigerant increases, which solves the problems of insufficient superheat of the high-temperature refrigeration module and low high-temperature exhaust temperature.

[0073] Continue reading Figure 5The refrigeration system 100 further includes a fifth control valve 110, which is disposed on the second heat exchange pipeline 17 to control the on-off of the second heat exchange pipeline 17. In this way, the second heat exchange pipeline 17 can be connected when needed and disconnected when not needed, and the on-off is controllable.

[0074] See also Figure 6 One end of the second heat exchange pipeline 17 is connected to the output end of the first expansion valve 13, and the other end is connected to the input end of the first compressor 11. The refrigerant in the second heat exchange pipeline 17 is expanded and depressurized by the first expansion valve 13 and then flows to the third heat exchanger 90. In this way, the refrigerant in the first closed loop and the refrigerant in the second heat exchange pipeline 17 are both expanded and depressurized by the first expansion valve 13, which reduces the structural setting of the refrigeration system 100.

[0075] In some other embodiments, continue to refer to Figure 5 , one end of the second heat exchange pipeline 17 is connected to the part of the first closed loop located between the output end of the condenser 12 and the input end of the first expansion valve 13. The first throttling mechanism also includes a throttling device 18, and the refrigerant in the second heat exchange pipeline 17 expands and reduces pressure through the throttling device 18 and then flows to the third heat exchanger 90. In this way, the refrigerant in the first closed loop expands and reduces pressure through the first expansion valve 13, and the refrigerant in the second heat exchange pipeline 17 expands and reduces pressure through the throttling device 18, and they do not affect each other. Optionally, the throttling device 18 is a capillary tube. Of course, in some other embodiments, the throttling device 18 can also be a thermal expansion valve or an electronic expansion valve.

[0076] In some specific implementations, please refer to Figure 5 , the first heat exchange pipeline 15 is independently arranged from the first closed loop, and both ends of the first heat exchange pipeline 15 are connected to the part of the first closed loop located at the output end of the condenser 12 and the input end of the first expansion valve 13. The first heat exchange pipeline 15 and the first closed loop have a first intersection A and a second intersection B, and one end of the second heat exchange pipeline 17 is connected to the first heat exchange pipeline 15 and has a fifth intersection E with the first heat exchange pipeline 15. The refrigeration system 100 also includes a first control valve 40, a second control valve 50, a fifth control valve 110 and a sixth control valve 120. The sixth control valve 120 is arranged on the first heat exchange pipeline 15 and is located between the first intersection A and the fifth intersection E. The first control valve 40 is arranged on the first heat exchange pipeline 15 and is located between the first intersection A and the second intersection B. The second control valve 50 is arranged on the first closed loop and is located between the first intersection A and the second intersection B. The fifth control valve 110 is disposed on the second heat exchange pipeline 17 .

[0077] The refrigerant in the first heat exchange pipeline 15 is expanded and depressurized through the first expansion valve 13 after heat exchange with the first pipeline 24 in the first heat exchanger 30. The first throttling mechanism also includes a throttling device 18, through which the refrigerant in the second heat exchange pipeline 17 is expanded and depressurized and flows to the third heat exchanger 90.

[0078] Further, the connecting line 26 is independently provided from the second closed loop, and both ends of the connecting line 26 are connected to the first line 24. The connecting line 26 and the second closed loop have a third intersection C and a fourth intersection D. The refrigeration system 100 further includes a third control valve 70 and a fourth control valve 80, wherein the third control valve 70 is provided on the connecting line 26, and the fourth control valve 80 is provided on the first line 24 and is located between the third intersection C and the fourth intersection D.

[0079] The operating principle of the refrigeration system 100 provided in the specific embodiment of the present application is as follows:

[0080] Low temperature mode: When the set temperature T1≤T of the refrigeration system 100 (T is the high and low temperature dividing point of the refrigeration system 100, in some embodiments, the high and low temperature dividing point is -40°C, and T1 is -60°C), the first control valve 40, the third control valve 70, the fifth control valve 110 and the sixth control valve 120 are closed, and the second control valve 50 and the fourth control valve 80 are opened. At this time, the flow path of the refrigerant in the high temperature refrigeration module is: the first compressor 11, the condenser 12, the second control valve 50, the first expansion valve 13, the first evaporator 14, and the first compressor 11. The flow path of the refrigerant in the low temperature refrigeration module is: the second compressor 21, the first evaporator 14, the second expansion valve 22, the fourth control valve 80, the second evaporator 23, and the second compressor 21. At this time, the refrigeration system 100 is a conventional operation mode of the two-stage cascade refrigeration system 100, which is mainly used in the working condition when T1 is low temperature.

[0081] High temperature mode: When the set temperature T1 of the refrigeration system 100 is greater than T (in some embodiments, T1 is -20°C), the second control valve 50, the fourth control valve 80 and the fifth control valve 110 are closed, and the first control valve 40, the third control valve 70 and the sixth control valve 120 are opened. At this time, the first heat exchanger 30 and the second heat exchanger 60 participate in heat exchange. The refrigerant flowing to the second evaporator 23 exchanges heat with the refrigerant in the low-temperature exhaust pipe through the second heat exchanger 60, and then exchanges heat with the medium-temperature refrigerant after the high-temperature condenser 12 through the first heat exchanger 30. The low-temperature refrigerant flow is regulated by the second expansion valve 22 to achieve the refrigerant temperature entering the second evaporator 23 reaching the set temperature T1.

[0082] Return air cooling mode:

[0083] When the test temperature required for the second evaporator 23 is high temperature, for example, the required production temperature is 150°C, the temperature of the second evaporator 23 is mainly controlled by the electric heating rod. Generally, when the second evaporator 23 stops working, the refrigeration system 100 needs to be turned on for cooling (the refrigeration system 100 sets the temperature T1≤T during cooling). In the initial stage of the refrigeration system 100, since the refrigeration capacity generated by the system is far lower than the cooling capacity required for cooling the second evaporator 23, it is necessary to monitor the cooling of the low-temperature return air. When the low-temperature return air temperature T2≥T2' (T2' is the control value of the return air temperature of the low-temperature compressor), the first control valve 40 and the third control valve 70 are closed, and the second control valve 50, the fourth control valve 80, the fifth control valve 110 and the sixth control valve 120 are opened, and the second heat exchange pipeline 17 participates in the circulation. The refrigerant flowing out of the condenser 12 of the high-temperature refrigeration module is divided into two paths: one path of the refrigerant is throttled by the throttling device 18 and then passes through the third heat exchanger 90 to exchange heat with the low-temperature return air to reduce the temperature of the low-temperature return air, thereby reducing the exhaust temperature of the low-temperature compressor; the other path flows to the first expansion valve 13 to participate in the refrigeration cycle. Finally, the two paths of refrigerant are mixed and flow back to the high-temperature compressor.

[0084] It should be noted that in some other embodiments, in the high temperature mode of the refrigeration system 100, each control valve may also adopt other opening and closing methods, which are not limited here. For example, in some embodiments, in the high temperature mode, only one heat exchanger may be set to work, and the refrigerant flowing into the second evaporator 23 exchanges heat with the refrigerant in the low temperature exhaust pipe through the second heat exchanger 60 or exchanges heat with the medium temperature refrigerant after the high temperature condenser 12 through the first heat exchanger 30.

[0085] Another embodiment of the present application further provides a test sorting device, comprising the above-mentioned refrigeration system 100. The test sorting device is used to test and sort electronic components. Since the above-mentioned refrigeration system 100 has beneficial effects, the test sorting device including the refrigeration system 100 has the same beneficial effects, which will not be described in detail here.

[0086] The technical features of the above-described embodiments may be arbitrarily combined. To make the description concise, not all possible combinations of the technical features in the above-described embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0087] The above-mentioned embodiments only express several implementation methods of the utility model, and the description is relatively specific and detailed, but it cannot be understood as limiting the scope of the utility model patent. It should be pointed out that for ordinary technicians in this field, several modifications and improvements can be made without departing from the concept of the utility model, which all belong to the protection scope of the utility model. Therefore, the protection scope of the utility model patent shall be based on the attached claims.

Claims

1. A refrigeration system, characterized in that: include: A first refrigeration module (10) comprises a first throttling mechanism, a first compressor (11), a condenser (12) and a first evaporator (14), wherein the first throttling mechanism comprises a first expansion valve (13); the first compressor (11), the condenser (12), the first expansion valve (13) and the first evaporator (14) are connected in sequence to form a first closed loop; the first refrigeration module (10) further comprises a first heat exchange pipeline (15), wherein one end of the first heat exchange pipeline (15) is connected to an output end of the condenser (12), and the other end is connected to an input end of the first evaporator (14); The second refrigeration module (20) comprises a second compressor (21), the first evaporator (14), a second expansion valve (22) and a second evaporator (23) which are sequentially connected to form a second closed loop; the second closed loop comprises a first pipeline (24) provided between an output end of the second expansion valve (22) and an input end of the second evaporator (23); A first heat exchanger (30), wherein the first heat exchange pipeline (15) is thermally coupled to the first pipeline (24) through the first heat exchanger (30), and the refrigerant in the first heat exchange pipeline (15) is expanded and depressurized through the first throttling mechanism after heat exchange with the first pipeline (24).

2. The refrigeration system according to claim 1, characterized in that: The first heat exchange pipeline (15) is arranged independently of the first closed loop; One end of the first heat exchange pipeline (15) is connected to the output end of the condenser (12), and the other end of the first heat exchange pipeline (15) is connected to the input end of the first expansion valve (13); the refrigerant in the first heat exchange pipeline (15) is expanded and depressurized after exchanging heat with the first pipeline (24) through the first expansion valve (13); Alternatively, one end of the first heat exchange pipeline (15) is connected to the output end of the condenser (12), and the other end of the first heat exchange pipeline (15) is connected to a portion of the first closed loop located between the output end of the first expansion valve (13) and the input end of the first evaporator (14). The first throttling mechanism also includes a third expansion valve (16), and the third expansion valve (16) is arranged on the first heat exchange pipeline (15). After the refrigerant in the first heat exchange pipeline (15) exchanges heat with the first pipeline (24), it is expanded and reduced in pressure through the third expansion valve (16).

3. The refrigeration system according to claim 2, characterized in that: The refrigeration system comprises a first control valve (40), wherein the first control valve (40) is arranged on the first heat exchange pipeline (15) to control the on-off of the first heat exchange pipeline (15); and / or The refrigeration system further comprises a second control valve (50), wherein the first heat exchange pipeline (15) and the first closed loop form a first intersection (A) and a second intersection (B), and the second control valve (50) is arranged on the first closed loop and located between the first intersection (A) and the second intersection (B), and the second control valve (50) is used to control the on / off of the portion of the first closed loop located between the first intersection (A) and the second intersection (B).

4. The refrigeration system according to claim 1, characterized in that: The first heat exchange pipeline (15) is a part of the first closed loop, and the first heat exchange pipeline (15) is connected between the output end of the condenser (12) and the input end of the first expansion valve (13). The refrigerant in the first heat exchange pipeline (15) is expanded and depressurized through the first expansion valve (13) after heat exchange with the first pipeline (24).

5. The refrigeration system according to claim 1, characterized in that: The second refrigeration module (20) further comprises a second throttling mechanism, wherein the second throttling mechanism comprises the second expansion valve (22); the second closed loop comprises a second pipeline (25) provided between the output end of the second compressor (21) and the input end of the first evaporator (14); The second refrigeration module (20) also includes a connecting pipe (26), and the refrigeration system also includes a second heat exchanger (60). One end of the connecting pipe (26) is connected to the output end of the first evaporator (14), and the other end is connected to the input end of the second evaporator (23). The connecting pipe (26) is thermally coupled with the second pipe (25) through the second heat exchanger (60); the refrigerant in the connecting pipe (26) is expanded and reduced in pressure by the second throttling mechanism and then flows to the second heat exchanger (60).

6. The refrigeration system according to claim 5, characterized in that: The connecting pipeline (26) is arranged independently of the second closed loop; Both ends of the connecting pipeline (26) are connected to the first pipeline (24), and the refrigerant in the connecting pipeline (26) is expanded and depressurized through the second expansion valve (22) and then flows to the second heat exchanger (60); or The second throttling mechanism also includes a fourth expansion valve (27); one end of the connecting pipe (26) is connected to a portion of the second closed loop located between the output end of the first evaporator (14) and the input end of the second expansion valve (22); the other end is connected to the input end of the second evaporator (23); the fourth expansion valve (27) is arranged on the connecting pipe (26), and the refrigerant in the connecting pipe (26) is expanded and reduced in pressure through the fourth expansion valve (27) and then flows to the second heat exchanger (60).

7. The refrigeration system according to claim 6, characterized in that: The refrigeration system further comprises a third control valve (70), wherein the third control valve (70) is arranged on the connecting pipeline (26) to control the opening and closing of the connecting pipeline (26); and / or The refrigeration system further comprises a fourth control valve (80), the connecting pipeline (26) and the second closed loop have a third intersection (C) and a fourth intersection (D), the fourth control valve (80) is arranged on the second closed loop and is located between the third intersection (C) and the fourth intersection (D), and the fourth control valve (80) is used to control the on / off of the part of the second closed loop located between the third intersection (C) and the fourth intersection (D).

8. The refrigeration system according to claim 5, characterized in that: The first pipeline (24) is the connecting pipeline (26).

9. The refrigeration system according to claim 1, characterized in that: The first refrigeration module (10) further comprises a second heat exchange pipeline (17) which is independently arranged from the first closed loop, one end of the second heat exchange pipeline (17) being connected to the output end of the condenser (12), and the other end of the second heat exchange pipeline (17) being connected to the input end of the first compressor (11); The refrigeration system also includes a third heat exchanger (90), and the second closed loop includes a third pipeline (28) arranged between the output end of the second evaporator (23) and the input end of the second compressor (21); the second heat exchange pipeline (17) is thermally coupled with the third pipeline (28) through the third heat exchanger (90), and the refrigerant in the second heat exchange pipeline (17) is expanded and reduced in pressure through the first throttling mechanism and then flows to the third heat exchanger (90).

10. The refrigeration system according to claim 9, characterized in that: One end of the second heat exchange pipeline (17) is connected to the output end of the first expansion valve (13), and the other end is connected to the input end of the first compressor (11), and the refrigerant in the second heat exchange pipeline (17) is expanded and depressurized through the first expansion valve (13) and then flows to the third heat exchanger (90); or One end of the second heat exchange pipeline (17) is connected to a portion of the first closed loop located between the output end of the condenser (12) and the input end of the first expansion valve (13); the first throttling mechanism also includes a throttling device (18), and the refrigerant in the second heat exchange pipeline (17) is expanded and reduced in pressure through the throttling device (18) and then flows to the third heat exchanger (90).

11. The refrigeration system according to claim 9, characterized in that: The refrigeration system further comprises a fifth control valve (110), wherein the fifth control valve (110) is arranged on the second heat exchange pipeline (17) and is used for controlling the on-off of the second heat exchange pipeline (17).

12. The refrigeration system according to claim 9, characterized in that: The first heat exchange pipeline (15) is arranged independently of the first closed loop, and both ends of the first heat exchange pipeline (15) are connected to the portion of the first closed loop located between the output end of the condenser (12) and the input end of the first expansion valve (13), and the first heat exchange pipeline (15) and the first closed loop have a first intersection point (A) and a second intersection point (B); one end of the second heat exchange pipeline (17) is connected to the first heat exchange pipeline (15), and has a fifth intersection point (E) with the first heat exchange pipeline (15); The refrigeration system further comprises a first control valve (40), a second control valve (50), a fifth control valve (110) and a sixth control valve (120); the sixth control valve (120) is arranged on the first heat exchange pipeline (15) and is located between the first intersection (A) and the fifth intersection (E); the first control valve (40) is arranged on the first heat exchange pipeline (15) and is located between the second intersection (B) and the fifth intersection (E); the second control valve (50) is arranged on the first closed loop and is located between the first intersection (A) and the second intersection (B); and the fifth control valve (110) is arranged on the second heat exchange pipeline (17); The refrigerant in the first heat exchange pipeline (15) is expanded and reduced in pressure through the first expansion valve (13) after exchanging heat with the first pipeline (24). The first throttling mechanism also includes a throttling device (18). The refrigerant in the second heat exchange pipeline (17) is expanded and reduced in pressure through the throttling device (18) and then flows to the third heat exchanger (90).

13. A test sorting device, characterized in that: Comprising a refrigeration system as described in any one of claims 1-12.

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