Refrigeration system

Abstract

The utility model relates to a refrigerating system which comprises a first refrigerating module, the first refrigerating module comprises a first compressor, a first condenser and a first evaporator which are sequentially communicated to form a first refrigerating loop, and a throttling element is further arranged on the part, between the output end of the first evaporator and the input end of the first compressor, of the first refrigerating loop. And the throttling element is used for increasing the pressure of a refrigerant in the first evaporator. The refrigerating system can be matched with a heating system to meet the operation requirement under the high-temperature working condition. Meanwhile, the refrigerant entering the first evaporator is in a two-phase state, the temperature of the refrigerant in the two-phase state is not prone to change in the evaporation heat absorption process, and even if the refrigerant is in an overheat state at the output end of the first evaporator, the superheat degree is greatly reduced compared with the scheme in the prior art; the temperature distribution uniformity of the refrigerant in the first evaporator is greatly improved, so that the temperature uniformity of the first evaporator is improved, and the production requirement is met.

Description

Technical Field

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

[0002] With the development of economy and the progress of society, electronic components are widely used in various fields. Before electronic components are put into use, their reliability and stability under various ambient temperatures need to be tested. The test equipment generally includes a refrigeration system and a heating system. The refrigeration system is used as a cold source, and the heating system is used as a heat source. The temperature of the test environment is controlled by the heat and cold confrontation between the heat source and the cold source.

[0003] In order to meet the test requirements of low-temperature working conditions, the evaporator of the test equipment is generally set after the electronic expansion valve is throttled. At this time, the refrigerant flowing in the evaporator is in a low-pressure and low-temperature state. When the test equipment needs to move under high-temperature working conditions, the low-pressure and low-temperature refrigerant in the flow channel will cause excessive cooling capacity. If the heating system power is insufficient, it will be difficult for the entire temperature control system to operate stably.

[0004] In traditional technology, a bypass electronic expansion valve is set up in the refrigeration system to bypass the high-temperature and high-pressure refrigerant discharged from the exhaust end of the compressor to the input end of the evaporator to increase the temperature of the evaporator, and the temperature of the evaporator is controlled by adjusting the opening of the bypass electronic expansion valve. However, in this way, the high-temperature gaseous refrigerant discharged from the compressor bypasses the input end of the evaporator, which greatly increases the liquid inlet at the input end of the evaporator, and even enters the evaporator in an overheated state. After entering the evaporator to absorb heat, the superheat at the output end of the evaporator will further increase, making the temperature uniformity of the evaporator poor and difficult to meet production needs. Utility Model Content

[0005] Based on this, it is necessary to provide a refrigeration system that can improve the temperature uniformity of the evaporator to meet production needs in order to address the problem that the temperature uniformity of the evaporator of the traditional refrigeration system is poor under high temperature conditions and it is difficult to meet production needs.

[0006] A refrigeration system includes a first refrigeration module, wherein the first refrigeration module includes a first compressor, a first condenser and a first evaporator which are connected in sequence to form a first refrigeration circuit. A throttling device is also provided on the portion of the first refrigeration circuit between the output end of the first evaporator and the input end of the first compressor, and the throttling device is used to increase the pressure of the refrigerant in the first evaporator.

[0007] In the above-mentioned refrigeration system, under the action of the throttling element, the saturation temperature corresponding to the refrigerant in the first evaporator is relatively large, the temperature difference between the first evaporator and the electronic components will be greatly reduced, and the heat exchange will be greatly reduced. Even if the power of the heating system is not high, the refrigeration system can cooperate with the heating system to meet the operation requirements under high temperature conditions. At the same time, the refrigerant entering the first evaporator is in a two-phase state, that is, the refrigerant in the first evaporator exchanges heat with the electronic components in a two-phase state. The temperature of the two-phase refrigerant is not easy to change during the evaporation and heat absorption process. Even if the refrigerant is in an overheated state at the output end of the first evaporator, the overheating degree is greatly reduced compared with the solution in the prior art. The uniformity of the temperature distribution of the refrigerant in the first evaporator is greatly improved, so that the temperature uniformity of the first evaporator is improved, thereby meeting the production needs.

[0008] In one embodiment, the first refrigeration module also includes a first bypass line, one end of the first bypass line is connected to a portion of the first refrigeration circuit between the first evaporator and the throttling device, and the other end of the first bypass line is connected to a portion of the first refrigeration circuit between the throttling device and the first compressor; a first control valve is provided on the first bypass line.

[0009] In one of the embodiments, a first expansion valve is further provided on a portion of the first refrigeration circuit between the first condenser and the first evaporator.

[0010] In one embodiment, the first refrigeration module also includes a second bypass line, one end of the second bypass line is connected to a portion of the first refrigeration circuit between the first condenser and the first expansion valve, and the other end of the second bypass line is connected to a portion of the first refrigeration circuit between the first expansion valve and the first evaporator; a second control valve is provided on the second bypass line.

[0011] In one embodiment, the throttling element includes at least one of a thermal expansion valve, an electronic expansion valve and a capillary tube.

[0012] In one embodiment, the refrigeration system further includes a superheating mechanism, and the superheating mechanism is used to increase the superheat degree of the refrigerant flowing to the first compressor.

[0013] In one embodiment, the superheating mechanism includes a connecting pipe and a second expansion valve, one end of the connecting pipe is connected to a portion of the first refrigeration circuit located between the first compressor and the first condenser, and the other end of the connecting pipe is connected to a portion of the first refrigeration circuit located between the throttling element and the first compressor or to a portion of the first refrigeration circuit located between the first condenser and the first evaporator;

[0014] The second expansion valve is arranged on the connecting pipeline. The refrigerant from the first compressor to the superheating mechanism is expanded and depressurized by the second expansion valve and then converges with the refrigerant in the first refrigeration circuit to increase the superheat of the refrigerant flowing to the first compressor.

[0015] In one of the embodiments, the superheating mechanism is thermally coupled to a portion of the first refrigeration circuit between the throttling element and the first compressor to increase the superheat of the refrigerant flowing to the first compressor.

[0016] In one embodiment, the refrigeration system further includes a second refrigeration module, the second refrigeration module includes a second compressor, a second condenser, a third expansion valve and a second evaporator which are sequentially connected to form a second refrigeration circuit; the second evaporator is integrated with the first condenser to form an evaporative condenser;

[0017] The superheating mechanism includes a heat exchanger and a heat exchange pipeline, one end of the heat exchange pipeline is connected to the output end of the second compressor of the second refrigeration circuit, and the other end is connected to the input end of the third expansion valve of the second refrigeration circuit; the heat exchange pipeline is thermally coupled with the part of the first refrigeration circuit located between the throttling device and the first compressor through the heat exchanger.

[0018] In one embodiment, the heat exchange pipeline is arranged independently from the second refrigeration circuit.

[0019] In one embodiment, the second refrigeration circuit also includes a third control valve, which is arranged between the output end of the second compressor and the input end of the third expansion valve, one end of the heat exchange pipeline is connected to the part of the second refrigeration circuit located between the second compressor and the third control valve, and the other end is connected to the part of the second refrigeration circuit located between the third control valve and the third expansion valve. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 A schematic diagram of a refrigeration system provided in one embodiment of the present application;

[0021] Figure 2 A schematic diagram of a refrigeration system provided in another embodiment of the present application;

[0022] Figure 3 A schematic diagram of a refrigeration system provided in yet another embodiment of the present application;

[0023] Figure 4 A schematic diagram of a refrigeration system provided in yet another embodiment of the present application;

[0024] Figure 5A schematic diagram of a refrigeration system provided in yet another embodiment of the present application;

[0025] Figure 6 A schematic diagram of a refrigeration system provided in accordance with another embodiment of the present application.

[0026] Description of reference numerals:

[0027] 100. Refrigeration system; 10. First refrigeration module; 11. First compressor; 12. First condenser; 13. First evaporator; 14. Throttle; 15. First bypass pipeline; 16. First control valve; 17. First expansion valve; 18. Second bypass pipeline; 19. Second control valve; 110. Oil separator; 120. First filter dryer; 130. Mixing tank; 20. Overheating mechanism; 21. Connecting pipeline; 22. Second expansion valve; 23. Heat exchanger; 24. Heat exchange pipeline; 30. Second refrigeration module; 31. Second compressor; 32. Second condenser; 33. Third expansion valve; 34. Second evaporator; 35. Third control valve; 40. Coolant circuit; 41. Cold source; 42. Coolant pipeline. DETAILED DESCRIPTION

[0028] 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.

[0029] 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.

[0030] 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.

[0031] 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.

[0032] 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.

[0033] 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.

[0034] See also Figure 1 In one embodiment of the present application, a refrigeration system 100 is provided for refrigerating electronic components, so as to cooperate with a heating system to control the temperature of the electronic components. Specifically, the electronic components are chips, and the refrigeration system 100 is used for refrigerating the chips, so as to cooperate with a heating system to control the temperature of the chips. Of course, in other embodiments, there is no limitation on the types of electronic components that the refrigeration system 100 is used for refrigeration.

[0035] The refrigeration system 100 includes a first refrigeration module 10, which includes a first compressor 11, a first condenser 12 and a first evaporator 13 which are connected in sequence to form a first refrigeration circuit. Among them, the first evaporator 13 is used to exchange heat with electronic components (direct contact heat exchange can be possible, or indirect heat exchange can be possible). When the first refrigeration module 10 is working, the high-temperature and low-pressure refrigerant gas enters the first compressor 11 through the input end of the first compressor 11, and the first compressor 11 compresses the high-temperature and low-pressure refrigerant into a high-temperature and high-pressure refrigerant, which is discharged from the output end of the first compressor 11 to the first condenser 12. When the refrigerant passes through the first condenser 12, it is condensed by the first condenser 12 into a medium-temperature and high-pressure refrigerant.

[0036] In the present application, a throttling device 14 is further provided on the first refrigeration circuit between the output end of the first evaporator 13 and the output end of the first compressor 11 . The throttling device 14 is used to increase the pressure of the refrigerant in the first evaporator 13 .

[0037] Since the throttling device 14 can increase the pressure of the refrigerant in the first evaporator 13, the medium-temperature and high-pressure refrigerant flowing out of the first condenser 12 is still in a high-pressure state after flowing to the first evaporator 13. Compared with the situation where the medium-temperature and high-pressure refrigerant liquid flows to the first evaporator 13 after being throttled by the throttling mechanism, the position of the first evaporator 13 changes from the low-pressure side to the high-pressure side. The pressure on the high-pressure side is much greater than that on the low-pressure side, and the corresponding saturation temperature is larger. At this time, the temperature difference between the first evaporator 13 and the electronic components will be greatly reduced, and the heat exchange will be greatly reduced. Even if the power of the heating system is not high, the refrigeration system 100 can cooperate with the heating system to meet the operating requirements under high-temperature conditions.

[0038] At the same time, the high-temperature and high-pressure refrigerant flowing out of the first compressor 11 passes through the first condenser 12 to release heat and become a two-phase state. It flows directly to the first evaporator 13 for evaporation and heat absorption without passing through the throttling mechanism. Then the refrigerant entering the first evaporator 13 is in a two-phase state, that is, the refrigerant in the first evaporator 13 exchanges heat with the electronic components in a two-phase state. The temperature of the two-phase refrigerant is not easy to change during the evaporation and heat absorption process (the refrigerant pressure in the first evaporator 13 is large and the saturation temperature is high. The high saturation temperature can avoid the transformation from liquid to gas as much as possible, thereby avoiding the refrigerant from becoming overheated after absorbing heat in the first evaporator 13). Even if the refrigerant is in an overheated state at the output end of the first evaporator 13, the degree of overheat is greatly reduced compared with the solution in the prior art, and the uniformity of the temperature distribution of the refrigerant in the first evaporator 13 is greatly improved, so that the temperature uniformity of the first evaporator 13 is improved, thereby meeting the demand for temperature uniformity in production.

[0039] It should be noted here that the refrigerant flows out through the first evaporator 13 and enters the throttling device 14 for throttling. The refrigerant after throttling is still in a superheated state. The superheated refrigerant enters the input end of the first compressor 11 to complete the refrigeration cycle.

[0040] Furthermore, the first refrigeration module 10 further includes an oil separator 110, which is disposed between the first compressor 11 and the first condenser 12, and can separate the lubricating oil in the high-pressure steam discharged from the first compressor to ensure safe and efficient operation of the first refrigeration module 10. A first drying filter 120 is also disposed between the oil separator 110 and the first condenser 12, and the first drying filter 120 plays a role in filtering impurities.

[0041] See also Figure 2 The first refrigeration module 10 further includes a first bypass line 15, one end of the first bypass line 15 is connected to a portion of the first refrigeration circuit between the first evaporator 13 and the throttling device 14, and the other end of the first bypass line 15 is connected to a portion of the first refrigeration circuit between the throttling device 14 and the first compressor 11. A first control valve 16 is provided on the first bypass line 15. In some embodiments, the first control valve 16 is a solenoid valve. In other embodiments, the type of the first control valve 16 is not limited. A first expansion valve 17 is also provided on a portion of the first refrigeration circuit between the first condenser 12 and the first evaporator 13.

[0042] In the above arrangement, when the first control valve 16 is operated to close, the first bypass line 15 bypasses the throttle 14, and the throttle 14 does not participate in throttling at this time. The high-temperature low-pressure refrigerant flowing out of the first evaporator 13 flows to the first compressor 11 through the first bypass line 15. The first compressor 11 compresses the high-temperature low-pressure refrigerant into a high-temperature high-pressure refrigerant, and the high-temperature high-pressure refrigerant is discharged from the output end of the first compressor 11 to the first condenser 12. When the refrigerant passes through the first condenser 12, it is condensed into a medium-temperature high-pressure refrigerant by the first condenser 12. The medium-temperature high-pressure refrigerant is expanded and reduced in pressure to a low-temperature low-pressure refrigerant through the first expansion valve 17, and enters the first evaporator 13 from the input end of the first evaporator 13. When the low-temperature low-pressure refrigerant enters the first evaporator 13, it performs heat exchange with the electronic components. The refrigerant after heat exchange enters the first compressor 11 from the output end of the first evaporator 13, and the cycle repeats. At this time, the low-temperature working condition requirements can be met, that is, the requirements for low-temperature control of electronic components can be met.

[0043] It should be noted that the temperature that the electronic components need to reach under low temperature conditions is lower than the temperature that the electronic components need to reach under high temperature conditions. In some specific embodiments, the temperature that the electronic components need to reach under low temperature conditions is less than 0°, such as -60°, and the temperature that the electronic components need to reach under high temperature conditions is greater than 0°, such as 50°. Of course, in other specific embodiments, the temperatures of low temperature conditions and high temperature conditions are not specifically limited.

[0044] When the first control valve 16 is disconnected, the first bypass line 15 is cut off, and the throttling device 14 participates in throttling. At this time, the first expansion valve 17 is equivalent to the primary throttling mechanism, and the throttling device 14 is equivalent to the secondary throttling mechanism. Since the throttling device 14 can increase the pressure of the refrigerant in the first evaporator 13, the pressure of the refrigerant in the first evaporator 13 is relatively high (close to the high-pressure end). When the pressure of the refrigerant is high, the corresponding saturation temperature is also high, which can meet the requirements of high-temperature working conditions (the temperature under this working condition is lower than the temperature when only the throttling device 14 is throttled without the throttling of the first expansion valve 17), that is, it can meet the requirements of high-temperature control of electronic components. At the same time, the refrigerant flowing out of the first condenser 12 is in a supercooled state or a two-phase state, and it is still in a two-phase state after throttling by the primary throttling mechanism. The refrigerant in this state enters the first evaporator 13 for evaporation and heat absorption. Since the refrigerant is in a two-phase state, the temperature of the evaporation and heat absorption process will not change, and the temperature uniformity of the first evaporator 13 is greatly improved compared with the existing technical solutions.

[0045] It should be noted that the inlet temperature of the first evaporator 13 can be adjusted by adjusting the opening of the first expansion valve 17. For example, when the inlet temperature is lower than the set temperature, the opening of the first expansion valve 17 is reduced, and when the inlet temperature is higher than the set temperature, the opening of the first expansion valve 17 is increased, so that the inlet temperature of the first evaporator 13 is stabilized within the set temperature range.

[0046] In some embodiments, see Figure 1 and Figure 2 In some other embodiments, the throttling member 14 may be a capillary tube. Figure 3 The throttling device 14 can also be a thermal expansion valve or an electronic expansion valve, and when the throttling device 14 is a thermal expansion valve or an electronic expansion valve, the opening of the throttling device 14 is adjustable. By adjusting the opening of the throttling device 14, it can cooperate with the first expansion valve 17 to make the liquid inlet temperature within the preset temperature range.

[0047] In some embodiments, see Figure 4The first refrigeration module 10 further includes a second bypass line 18, one end of the second bypass line 18 is connected to the first refrigeration circuit between the first condenser 12 and the first expansion valve 17, and the other end of the second bypass line 18 is connected to the first refrigeration circuit between the first expansion valve 17 and the first evaporator 13. A second control valve 19 is provided on the second bypass line 18. In some specific embodiments, the second control valve 19 is a solenoid valve. It is conceivable that in other embodiments, the type of the second control valve 19 is not limited.

[0048] When the first control valve 16 is closed and the second control valve 19 is disconnected, the first refrigeration module 10 operates in the same principle as a conventional refrigeration module, and the refrigeration system 100 can meet the requirements of low temperature working conditions. When the first control valve 16 and the second control valve 19 are both disconnected, the first expansion valve 17 acts as a primary throttling mechanism and the throttling member 14 acts as a secondary throttling mechanism, and the refrigeration system 100 can meet the requirements of high temperature working conditions. When the first control valve 16 is disconnected and the second control valve 19 is closed, the first expansion valve 17 is bypassed by the second bypass line 18, and the refrigeration system 100 can meet the requirements of higher temperature working conditions.

[0049] Furthermore, when the refrigeration system 100 needs to operate under high temperature conditions, the refrigerant state at the output end of the first evaporator 13 may be in a two-phase state, and the refrigerant after throttling by the throttling device 14 may still be in a two-phase state. The two-phase refrigerant enters the first compressor 11 and there is a risk of liquid hammering of the first compressor 11, thereby causing damage to the compressor. In some embodiments, the refrigeration system 100 also includes an overheating mechanism 20, which is used to increase the superheat of the refrigerant flowing to the first compressor 11. When it is detected that the suction superheat of the first compressor 11 is too low, the overheating mechanism 20 can heat the temperature of the refrigerant flowing to the first compressor 11 to increase its superheat, thereby avoiding the risk of liquid hammering of the first compressor 11 and ensuring the stable operation of the refrigeration system 100. At the same time, in the prior art, the refrigerant entering the first evaporator 13 is in an overheated state, and the superheat further increases after absorbing heat in the first evaporator 13, resulting in very large suction superheat and exhaust superheat of the first compressor 11, and the reliability of the compressor is reduced. In the present application, the refrigerant entering the first evaporator 13 is in a two-phase state, and the suction superheat of the first compressor 11 is controlled by the overheating mechanism 20. The suction superheat of the first compressor 11 can be greatly reduced compared with the existing scheme, and within a reasonable range, the reliability of the compressor operation can be greatly improved.

[0050] In some embodiments, see Figure 4The superheating mechanism 20 includes a connecting pipe 21 and a second expansion valve 22. One end of the connecting pipe 21 is connected to the portion of the first refrigeration circuit located between the first compressor 11 and the first condenser 12, and the other end of the connecting pipe 21 is connected to the portion of the first refrigeration circuit located between the throttling device 14 and the first compressor 11. The second expansion valve 22 is arranged on the connecting pipe 21. After the refrigerant from the first compressor 11 to the superheating mechanism 20 is expanded and depressurized by the second expansion valve 22, it converges with the refrigerant of the first refrigeration circuit to increase the superheat of the refrigerant flowing to the first compressor 11. Specifically, the second expansion valve 22 can be a capillary tube or a thermal expansion valve, etc.

[0051] According to the above arrangement, when it is detected that the suction superheat of the first compressor 11 is too low, the high-temperature refrigerant at the output end of the first compressor 11 flows to the connecting pipe 21, and the second expansion valve 22 on the connecting pipe 21 is used for expansion and pressure reduction of the refrigerant. The refrigerant after expansion and pressure reduction can converge with the refrigerant in the first refrigeration circuit, thereby increasing the superheat of the refrigerant flowing to the first compressor 11, so that the suction temperature of the first compressor 11 is within a reasonable range.

[0052] In some other embodiments, see Figure 5 , one end of the connecting pipe 21 can also be arranged to be connected to the part of the first refrigeration circuit located between the first compressor 11 and the first condenser 12, and the other end of the connecting pipe 21 can be arranged to be connected to the part of the first refrigeration circuit located between the first expansion valve 17 and the first evaporator 13. At this time, when it is detected that the suction superheat of the first compressor 11 is too low, the high-temperature refrigerant at the output end of the first compressor 11 flows to the connecting pipe 21, and the second expansion valve 22 on the connecting pipe 21 is used for the expansion and decompression of the refrigerant. The refrigerant after expansion and decompression can converge with the refrigerant in the first refrigeration circuit, and flow to the first compressor 11 after passing through the first evaporator 13, so that the suction temperature of the first compressor 11 is within a reasonable range. Further, a mixing tank 130 is provided on the first refrigeration circuit, and the refrigerant in the connecting pipe 21 and the refrigerant in the first refrigeration circuit can be mixed in the mixing tank 130 and then enter the first evaporator 13 to ensure the temperature uniformity of the refrigerant in the first evaporator 13. Of course, in some other embodiments, the first refrigeration module 10 can also omit the mixing tank 130, which is not limited here.

[0053] In some further embodiments, the superheating mechanism 20 is thermally coupled to a portion of the first refrigeration circuit between the throttling member 14 and the first compressor 11 to increase the superheat of the refrigerant flowing to the first compressor 11. Thus, when it is detected that the suction superheat of the first compressor 11 is too low, the superheating mechanism 20 is thermally coupled to a portion of the first refrigeration circuit between the throttling member 14 and the first compressor 11, so that the superheat of the refrigerant flowing to the first compressor 11 is increased, so that the suction temperature of the first compressor 11 is within a reasonable range.

[0054] In some specific embodiments, the superheating mechanism 20 includes a heater, which is used to heat the refrigerant flowing through the portion of the first refrigeration circuit between the throttling member 14 and the first compressor 11, thereby increasing the superheat of the refrigerant flowing to the first compressor 11, so that the suction temperature of the first compressor 11 is within a reasonable range. Specifically, the heater can be an electric heater.

[0055] In some embodiments, see Figure 6 , the refrigeration system 100 also includes a second refrigeration module 30, which includes a second compressor 31, a second condenser 32, a third expansion valve 33 and a second evaporator 34 which are connected in sequence to form a second refrigeration circuit. The second evaporator 34 is integrated with the first condenser 12 to form an evaporative condenser. At this time, the refrigeration system 100 is a two-stage compression cascade refrigeration system, the second refrigeration module 30 is a high-temperature refrigeration module, and the first refrigeration module 10 is a low-temperature refrigeration module. When the second refrigeration circuit is working, the second compressor 31 sucks the high-temperature and low-pressure refrigerant gas output from the output end of the evaporative condenser, compresses the refrigerant into a high-temperature and high-pressure refrigerant gas, and discharges it from the output end of the second compressor 31 to the second condenser 32. When the refrigerant passes through the second condenser 32, it is condensed into a medium-temperature and high-pressure refrigerant liquid by the second condenser 32, and is expanded and reduced in pressure into a low-temperature and low-pressure refrigerant liquid by the third expansion valve 33, and finally input into the evaporative condenser again from the input end of the evaporative condenser. When the low-temperature and low-pressure liquid refrigerant enters the evaporative condenser, it performs heat exchange with the first refrigeration circuit. The refrigerant after heat exchange enters the second compressor 31 again from the output end of the evaporative condenser, and the cycle repeats.

[0056] The superheating mechanism 20 includes a heat exchanger 23 and a heat exchange pipeline 24, one end of the heat exchange pipeline 24 is connected to the output end of the second compressor 31 of the second refrigeration circuit, and the other end is connected to the input end of the third expansion valve 33 of the second refrigeration circuit. The heat exchange pipeline 24 is thermally coupled with the part of the first refrigeration circuit located between the throttling member 14 and the first compressor 11 through the heat exchanger 23. The heat exchanger 23 can be a plate heat exchanger or a shell and tube heat exchanger. In this way, the relatively high temperature refrigerant of the second refrigeration circuit can flow through the heat exchange pipeline 24, and when it flows through the heat exchanger 23, it can heat the refrigerant in the first refrigeration circuit, thereby increasing the superheat of the refrigerant flowing to the first compressor 11, so that the suction temperature of the first compressor 11 is within a reasonable range.

[0057] In some specific implementations, please refer to Figure 1-Figure 3 The heat exchange pipeline 24 is independently arranged from the second refrigeration circuit. Thus, the arrangement of the heat exchange pipeline 24 will not interfere with the normal operation of the second refrigeration circuit. Figure 6 , the heat exchange line 24 can also serve as a part of the second refrigeration circuit.

[0058] Further, both ends of the heat exchange pipeline 24 are connected to the portion of the second refrigeration circuit located between the second condenser 32 and the third expansion valve 33. Of course, in some other embodiments, one end of the heat exchange pipeline 24 can be connected to the portion of the second refrigeration circuit located between the second compressor 31 and the second condenser 32, and the other end can be connected to the portion of the second refrigeration circuit located between the second condenser 32 and the third expansion valve 33, which is not limited here.

[0059] For further information, see Figure 1-Figure 3 , the second refrigeration circuit also includes a third control valve 35, which is arranged on the second refrigeration circuit between the output end of the second compressor 31 and the input end of the third expansion valve 33. One end of the heat exchange line 24 is connected to the part of the second refrigeration circuit located between the second compressor 31 and the third expansion valve 33, and the other end is connected to the part of the second refrigeration circuit located between the third control valve 35 and the third expansion valve 33. In this way, when it is detected that the suction superheat of the first compressor 11 is too low, the third control valve 35 is operated to be closed, and the refrigerant in the second refrigeration circuit flows through the heat exchange line 24 and heats the refrigerant in the first refrigeration circuit, thereby increasing the superheat of the refrigerant flowing to the first compressor 11, so that the suction temperature of the first compressor 11 is within a reasonable range. When it is detected that the suction superheat of the first compressor 11 is appropriate, the third control valve 35 is operated to be opened, and the refrigerant will not flow to the heat exchange line 24, and the second refrigeration circuit works normally.

[0060] In some embodiments, see Figure 6The refrigeration system 100 further includes a cold source 41 and a cold medium pipeline 42 which are sequentially connected to form a cold medium loop 40, and the cold medium pipeline 42 is thermally coupled to the second condenser 32. The cold medium can flow to the cold medium pipeline 42 through the cold source 41 to dissipate heat in the second condenser 32, and the cold medium after heat dissipation can flow back to the cold source 41 through the cold medium pipeline 42, and the cycle is repeated.

[0061] 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.

[0062] 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: The invention comprises a first refrigeration module (10), wherein the first refrigeration module (10) comprises a first compressor (11), a first condenser (12) and a first evaporator (13) which are connected in sequence to form a first refrigeration circuit, and a throttling device (14) is also provided on the part of the first refrigeration circuit between the output end of the first evaporator (13) and the input end of the first compressor (11), wherein the throttling device (14) is used to increase the pressure of the refrigerant in the first evaporator (13).

2. The refrigeration system according to claim 1, characterized in that: The first refrigeration module (10) further comprises a first bypass pipeline (15), one end of which is connected to a portion of the first refrigeration circuit between the first evaporator (13) and the throttling device (14), and the other end of which is connected to a portion of the first refrigeration circuit between the throttling device (14) and the first compressor (11); a first control valve (16) is provided on the first bypass pipeline (15).

3. The refrigeration system according to claim 1 or 2, characterized in that: A first expansion valve (17) is also provided on a portion of the first refrigeration circuit between the first condenser (12) and the first evaporator (13).

4. The refrigeration system according to claim 3, characterized in that: The first refrigeration module (10) further comprises a second bypass pipeline (18), one end of the second bypass pipeline (18) being connected to a portion of the first refrigeration circuit between the first condenser (12) and the first expansion valve (17), and the other end of the second bypass pipeline (18) being connected to a portion of the first refrigeration circuit between the first expansion valve (17) and the first evaporator (13); a second control valve (19) is provided on the second bypass pipeline (18).

5. The refrigeration system according to claim 1, characterized in that: The throttling element (14) comprises at least one of a thermal expansion valve, an electronic expansion valve and a capillary tube.

6. The refrigeration system according to claim 1, characterized in that: The refrigeration system further comprises a superheating mechanism (20), wherein the superheating mechanism (20) is used to increase the superheat degree of the refrigerant flowing to the first compressor (11).

7. The refrigeration system according to claim 6, characterized in that: The superheating mechanism (20) comprises a connecting pipe (21) and a second expansion valve (22), one end of the connecting pipe (21) being connected to a portion of the first refrigeration circuit located between the first compressor (11) and the first condenser (12), and the other end of the connecting pipe (21) being connected to a portion of the first refrigeration circuit located between the throttling element (14) and the first compressor (11) or being connected to a portion of the first refrigeration circuit located between the first condenser (12) and the first evaporator (13); The second expansion valve (22) is arranged on the connecting pipe (21). After the refrigerant from the first compressor (11) flows to the superheating mechanism (20) and is expanded and reduced in pressure by the second expansion valve (22), it converges with the refrigerant in the first refrigeration circuit to increase the superheat of the refrigerant flowing to the first compressor (11).

8. The refrigeration system according to claim 6, characterized in that: The superheating mechanism (20) is thermally coupled to a portion of the first refrigeration circuit located between the throttling element (14) and the first compressor (11) to increase the superheat of the refrigerant flowing to the first compressor (11).

9. The refrigeration system according to claim 8, characterized in that: The refrigeration system further comprises a second refrigeration module (30), wherein the second refrigeration module (30) comprises a second compressor (31), a second condenser (32), a third expansion valve (33) and a second evaporator (34) which are sequentially connected to form a second refrigeration circuit; the second evaporator (34) and the first condenser (12) are integrated into one body to form an evaporative condenser; The superheating mechanism (20) includes a heat exchanger (23) and a heat exchange pipeline (24); one end of the heat exchange pipeline (24) is connected to the output end of the second compressor (31) of the second refrigeration circuit, and the other end is connected to the input end of the third expansion valve (33) of the second refrigeration circuit; the heat exchange pipeline (24) is thermally coupled to a portion of the first refrigeration circuit located between the throttling device (14) and the first compressor (11) through the heat exchanger (23).

10. The refrigeration system according to claim 9, characterized in that: The heat exchange pipeline (24) is arranged independently from the second refrigeration circuit.

11. The refrigeration system according to claim 10, characterized in that: The second refrigeration circuit also includes a third control valve (35), which is arranged between the output end of the second compressor (31) and the input end of the third expansion valve (33). One end of the heat exchange pipeline (24) is connected to the part of the second refrigeration circuit located between the second compressor (31) and the third control valve (35), and the other end is connected to the part of the second refrigeration circuit located between the third control valve (35) and the third expansion valve (33).

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