Refrigerating system and sorting test equipment

Abstract

The utility model relates to a refrigerating system and a sorting test device, in a high temperature working condition, a refrigerant output by a first condenser passes through a first throttle valve and then enters an evaporator. At the moment, in order to increase the duty ratio of the heating system to the range required by a user, the opening degree of the first throttling valve can be increased, the refrigerant can directly enter the evaporator without the strong throttling effect, and due to the fact that a bypass branch for shunting the refrigerant entering the evaporator does not exist, the flow of the refrigerant entering the evaporator can be greatly increased; therefore, the countermeasure heating capacity of the heating system is improved, and the duty ratio of the heating system is effectively improved. And meanwhile, in order to avoid the situation that the return air temperature of the first compressor is too high or liquid impact is generated, throttling cooling and pressure reduction can be conducted on the refrigerant output by the evaporator through the throttling assembly. Therefore, the refrigerating system can avoid overheating or liquid impact of the first compressor under the condition that the high duty ratio use requirement of the heating system is met, and stable work of the refrigerating system is guaranteed.

Description

Technical Field

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

[0002] Electronic components, especially semiconductor chips, need to be subjected to reliability and stability tests at various ambient temperatures before leaving the factory. The temperature control system for controlling the test temperature includes a refrigeration system and a heating system. When testing electronic components, the temperature of the electronic components is controlled by the cold and heat confrontation between the refrigeration system and the heating system to ensure the accuracy of the test results.

[0003] Since the suction temperature of the refrigeration system needs to be controlled within a suitable range, in high-temperature working conditions, generally, a bypass branch needs to be led out from the condenser of the refrigeration system. The refrigerant flowing through the bypass branch can be mixed with the refrigerant flowing out of the refrigeration load, so as to achieve the purpose of reducing the suction temperature. The bypass branch will divert a part of the refrigerant, resulting in a reduction in the refrigerant entering the refrigeration load and a decrease in the refrigeration capacity, that is, reducing the counteracting heating capacity. In this way, the duty cycle of the heating system will be reduced, and it is often impossible to meet the customer's high-duty-cycle requirements. Summary of the Utility Model

[0004] Based on this, it is necessary to provide a refrigeration system and a sorting and testing device that can effectively improve the duty cycle of the heating system in view of the above problems.

[0005] A refrigeration system capable of cooperating with a heating system to control temperature. The refrigeration system includes a first refrigeration module. The first refrigeration module includes a first compressor, a first condenser, a first throttle valve, an evaporator, and a throttling component. The first compressor, the first condenser, the first throttle valve, the evaporator, and the throttling component are sequentially connected and form a first refrigeration circuit. The input end and the output end of the throttling component are respectively connected to the output end of the evaporator and the suction end of the first compressor.

[0006] In one embodiment, the throttling component includes a first pipeline, an adjusting pipeline, a second pipeline, a third throttle valve, and a heat exchanger. Both the first pipeline and the second pipeline are part of the first refrigeration circuit. The input end of the first pipeline is connected to the output end of the evaporator, the output end of the first pipeline is connected to the input end of the heat exchanger, and the third throttle valve is connected to the first pipeline. The input end of the second pipeline is connected to the air outlet end of the heat exchanger, and the output end of the second pipeline is connected to the suction end of the first compressor. The adjusting pipeline is thermally coupled to the heat exchanger, and the input end of the adjusting pipeline is connected to the first pipeline, and the output end of the adjusting pipeline is connected to the second pipeline.

[0007] In one embodiment, a regulating valve is provided on the regulating pipeline, and the regulating valve is used to regulate the refrigerant flow rate flowing through the regulating pipeline.

[0008] In one embodiment, the regulating valve is set as a throttle valve, and the regulating valve is located between the heat exchanger and the output end of the regulating pipeline.

[0009] In one embodiment, the first refrigeration module further includes a first bypass branch, a first control valve is provided on the first bypass branch, the input end of the first bypass branch is communicated to a part of the first refrigeration return pipeline between the output end of the first condenser and the input end of the evaporator, and the output end of the first bypass branch is communicated with the throttling assembly.

[0010] In one embodiment, the output end of the first bypass branch is communicated with the first pipeline.

[0011] In one embodiment, the output end of the first bypass branch is communicated with the input end of the third throttle valve; the input end of the first bypass branch is communicated to the input end of the first throttle valve, the first control valve is set as a throttle valve, and the refrigerant in the first bypass branch can expand and reduce pressure through the first control valve.

[0012] In one embodiment, the output end of the first bypass branch is communicated with the input end of the third throttle valve; the input end of the first bypass branch is communicated to the output end of the first throttle valve, and the refrigerant in the first bypass branch expands and reduces pressure through the first throttle valve.

[0013] In one embodiment, a second refrigeration module is further included. The second refrigeration module includes a second compressor, a second condenser, a second throttle valve and the first condenser. The second compressor, the second condenser, the second throttle valve and the first condenser are sequentially communicated to form a second refrigeration loop, and the first condenser serves as an evaporation condenser to thermally couple the first refrigeration loop and the second refrigeration loop.

[0014] A sorting and testing device includes a heating system and the refrigeration system according to any one of the above preferred embodiments. The heating system is thermally coupled with the evaporator to jointly control the temperature of electronic components.

[0015] In the above-mentioned refrigeration system and sorting and testing equipment, under high-temperature working conditions, the refrigerant output by the first condenser enters the evaporator after passing through the first throttle valve. At this time, in order to increase the duty cycle of the heating system to the user's required range, the opening of the first throttle valve can be increased. Therefore, the refrigerant can directly enter the evaporator without strong throttling. Since there is no bypass branch to split the refrigerant entering the evaporator, the refrigerant flow rate entering the evaporator can be greatly increased, thereby increasing the counterheating amount of the heating system and effectively increasing the duty cycle of the heating system. At the same time, in order to prevent the suction temperature of the first compressor from being too high or causing liquid slugging, the refrigerant output by the evaporator can be throttled, cooled, and depressurized through the throttling component. Thus, it can be seen that the above-mentioned refrigeration system can avoid overheating or liquid slugging of the first compressor while meeting the usage requirements of a high duty cycle of the heating system, ensuring the stable operation of the refrigeration system. Brief Description of the Drawings

[0016] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only some embodiments of the present application. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings.

[0017] Figure 1 It is a schematic diagram of the pipeline structure of the refrigeration system in a preferred embodiment of the present utility model;

[0018] Figure 2 For Figure 1 It is a schematic diagram of the pipeline structure of the throttling component in the shown refrigeration system;

[0019] Figure 3 For Figure 1 It is an equivalent pipeline schematic diagram of the first refrigeration module in the shown refrigeration system under high-temperature working conditions. Detailed Description of the Embodiments

[0020] In order to make the above-mentioned objects, features, and advantages of the present utility model more obvious and understandable, the following will give a detailed description of the specific embodiments of the present utility model with reference to the drawings. Many specific details are set forth in the following description in order to fully understand the present utility model. However, the present utility model can be implemented in many other ways different from those described herein. Those skilled in the art can make similar improvements without departing from the connotation of the present utility model. Therefore, the present utility model is not limited by the specific embodiments disclosed below.

[0021] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present utility model.

[0022] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In the description of the present utility model, the meaning of "a plurality of" is at least two, such as two, three, etc., unless otherwise specifically and clearly defined.

[0023] In the present utility model, unless otherwise clearly specified and limited, the terms "mounted", "connected", "connected to", "fixed", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the internal communication of two elements or the interaction relationship between two elements, unless otherwise clearly limited. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0024] In the present utility model, unless otherwise clearly specified and limited, the first feature being "on" or "under" the second feature may be 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, the first feature being "above", "over" and "on top of" the second feature may be that the first feature is directly above or obliquely above the second feature, or merely indicates that the first feature has a higher horizontal height than the second feature. The first feature being "under", "beneath" and "underneath" the second feature may be that the first feature is directly below or obliquely below the second feature, or merely indicates that the first feature has a lower horizontal height than the second feature.

[0025] It should be noted that when an element is referred to as "fixed to" or "disposed on" another element, it can be directly on the other element or there may be an intermediate element. When an element is considered to be "connected" to another element, it can be directly connected to the other element or there may be an intermediate element at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used herein are for illustrative purposes only and do not represent the only implementation.

[0026] Please refer to Figure 1 , the present utility model provides a refrigeration system 100 and a sorting and testing device. Among them, the above sorting and testing device includes a heating system (not shown in the figure) and a refrigeration system 100. The heating system and the refrigeration system 100 can act together on the electronic components to be tested to jointly control the temperature of the electronic components.

[0027] The heating system is used to heat the electronic components to be tested, and the refrigeration system 100 is used to cool the electronic components to be tested. The two act together and oppose each other, so that the electronic components to be tested are in different temperature environments such as low temperature, medium temperature and low temperature. Optionally, the electronic components to be tested are semiconductor chips. Of course, the above refrigeration system 100 can also be applied to control the temperature of other types of electronic components.

[0028] The above refrigeration system 100 includes a first refrigeration module 10. Among them, the first refrigeration module 10 includes a first compressor 11, a first condenser 12, a first throttle valve 13, an evaporator 14 and a throttle assembly 15. The first compressor 11, the first condenser 12, the first throttle valve 13, the evaporator 14 and the throttle assembly 15 are connected in sequence to form a first refrigeration circuit. When the first refrigeration module 10 is working, the refrigerant circulates along the first refrigeration circuit. When the refrigerant flows through the evaporator 14, it can evaporate and absorb heat, thereby playing a cooling role. Specifically, the heating system is thermally coupled with the evaporator 14 to jointly control the temperature of the electronic components.

[0029] Furthermore, the input end of the throttle assembly 15 is connected to the output end of the evaporator 14, and the output end of the throttle assembly 15 is connected to the suction end of the first compressor 11. The throttle assembly 15 is used to throttle the refrigerant, thereby reducing the temperature and pressure of the refrigerant output by the evaporator 14 to reduce the suction temperature and suction humidity of the first compressor 11, thereby avoiding too high suction temperature or preventing liquid hammer from occurring to the first compressor 11.

[0030] When the above refrigeration system 100 operates under high temperature conditions (for example, above 50 °C), such as Figure 3As shown, the high-temperature and high-pressure refrigerant discharged from the exhaust end of the first compressor 11 is transported to the first condenser 12; the refrigerant passes through the first condenser 12 and is condensed by the first condenser 12 into a medium-temperature and high-pressure refrigerant; at this time, in order to increase the duty cycle of the heating system to the user's required range, the opening degree of the first throttle valve 13 can be increased, so that the refrigerant enters the evaporator 14 directly in a medium-temperature and high-pressure state without strong throttling; after the refrigerant enters the evaporator 14, it can evaporate and absorb heat, thereby cooling the electronic components. The high-temperature and high-pressure refrigerant after heat exchange is output from the output end of the evaporator 14 and is expanded and depressurized by the throttling assembly 15, so as to obtain a refrigerant with significantly reduced temperature and pressure; the first compressor 11 sucks in the refrigerant output by the throttling assembly 15 and compresses it into a high-temperature and high-pressure refrigerant gas, and cycles in this way.

[0031] The refrigerant output from the first condenser 12 enters the evaporator 14 after passing through the first throttle valve 13, and the opening degree of the first throttle valve 13 can be adjusted to the maximum. Moreover, since there is no bypass branch to split the refrigerant entering the evaporator 14, the refrigerant flow rate entering the evaporator 14 can be greatly increased. In this way, the heating capacity of the heating system can be improved, thereby effectively increasing the duty cycle of the heating system to meet the high-duty-cycle requirements of customers.

[0032] Since the refrigerant does not undergo effective expansion and depressurization and enters the evaporator 14 in a medium-temperature and high-pressure state, the refrigerant after heat exchange in the evaporator 14 will be in a high-temperature and high-pressure state. Therefore, the throttling assembly 15 is needed to throttle the refrigerant output from the evaporator 14 to avoid too high a suction temperature of the first compressor 11. Specifically, the throttling assembly 15 can expand and depressurize the high-temperature and high-pressure refrigerant output from the evaporator 14 by throttling, reducing the pressure while reducing the temperature.

[0033] Moreover, since the evaporation amount of the medium-temperature and high-pressure refrigerant in the evaporator 14 is small, the high-temperature and high-pressure refrigerant output from the evaporator 14 is mainly in a liquid state. Therefore, it is easy to cause the liquid content in the suction gas of the first compressor 11 to exceed the standard, thereby causing liquid hammer to the first compressor 11. To avoid this problem, the throttling assembly 15 needs to increase the evaporation amount of the refrigerant while expanding and depressurizing the high-temperature and high-pressure refrigerant.

[0034] Please refer to Figure 2, in this embodiment, the throttling assembly 15 includes a first pipeline 151, a regulating pipeline 152, a second pipeline 153, a third throttle valve 154 and a heat exchanger 155. Among them, both the first pipeline 151 and the second pipeline 153 are part of the first refrigeration circuit. The input end of the first pipeline 151 is communicated with the output end of the evaporator 14, the output end of the first pipeline 151 is communicated with the input end of the heat exchanger 155, the input end of the second pipeline 153 is communicated with the gas outlet end of the heat exchanger 155, and the output end of the second pipeline 153 is communicated with the suction end of the first compressor 11. Moreover, the third throttle valve 154 is communicated with the first pipeline 151; the regulating pipeline 152 is thermally coupled with the heat exchanger 155, and the input end of the regulating pipeline 152 is communicated with the first pipeline 151, and the output end of the regulating pipeline 152 is communicated with the second pipeline 153.

[0035] That is to say, the high-temperature and high-pressure refrigerant output by the evaporator 14 is divided into two paths. The first path of refrigerant is transported to the first compressor 11 along the first pipeline 151, the heat exchanger 155 and the second pipeline 153, and the second path of refrigerant is transported to the first compressor 11 along the regulating pipeline 152. The first path of refrigerant flowing through the first pipeline 151 expands and reduces pressure through the third throttle valve 154, so as to input the low-temperature and low-pressure first path of refrigerant into the heat exchanger 155. The first path of refrigerant entering the heat exchanger 155 is mainly in a gaseous state. The second path of refrigerant flowing through the regulating pipeline 152 has a higher temperature because it has not undergone expansion and pressure reduction. Therefore, the second path of refrigerant can exchange heat with the first path of refrigerant in the heat exchanger 155, so that the first path of refrigerant in the heat exchanger 155 evaporates, so as to further reduce the liquid content of the first path of refrigerant.

[0036] The gaseous refrigerant evaporated in the heat exchanger 155 is output from the gas outlet end of the heat exchanger 155 to the second pipeline 153, while the liquid refrigerant remains in the heat exchanger 155 and continues to evaporate. The heat exchanger 155 has a certain gas-liquid separation function, so that the refrigerant flowing through the second pipeline 153 is basically all in a gaseous state. After the second path of refrigerant exchanges heat with the first path of refrigerant in the heat exchanger 155, it continues to be transported along the regulating pipeline 152. Finally, the first path of refrigerant and the second path of refrigerant converge into the suction gas of the first compressor 11 in the second pipeline 153. It can be seen that since the refrigerant further evaporates in the heat exchanger 155, the throttling assembly 15 can not only reduce the suction gas temperature of the first compressor 11, but also significantly reduce the suction gas humidity, thereby avoiding liquid slugging of the first compressor 11.

[0037] Further, in this embodiment, a regulating valve 156 is provided on the regulating pipeline 152. The regulating valve 156 is used to regulate the refrigerant flow rate flowing through the regulating pipeline 152. By adjusting the opening degree of the regulating valve 156, the refrigerant flow rate flowing through the regulating pipeline 152 can be controlled, so as to finally adjust the suction gas temperature of the first compressor 11 to ensure that the suction gas temperature is within a suitable range. Specifically, the larger the opening degree of the regulating valve 156, the larger the refrigerant flow rate flowing through the regulating pipeline 152, and the higher the suction gas temperature of the first compressor 11, and vice versa.

[0038] Furthermore, in this embodiment, the regulating valve 156 is set as a throttle valve, and the regulating valve 156 is located between the heat exchanger 155 and the output end of the regulating pipeline 152. In this way, after the second refrigerant circuit completes heat exchange in the heat exchanger 155, it can pass through the regulating valve 156 for expansion and pressure relief, and can also reduce the temperature and liquid content of the second refrigerant circuit to a certain extent, so as to further reduce the suction gas temperature and suction gas humidity.

[0039] Please refer to again Figure 1 , in this embodiment, the first refrigeration module 10 further includes a gas-liquid separator 19. The gas-liquid separator 19 is arranged between the output end of the throttling assembly 15 and the suction end of the first compressor 11.

[0040] The input port of the gas-liquid separator 19 is communicated with the output end of the throttling assembly 15, specifically, the output end of the second pipeline 153, and its output port is communicated with the suction end of the first compressor 11. Therefore, the refrigerant output by the throttling assembly 15 can enter the suction end of the first compressor 11 only after passing through the gas-liquid separator 19. The gas-liquid separator 19 has the function of gas-liquid separation, which can further reduce the suction gas humidity and effectively avoid the suction gas of the first compressor 11 carrying liquid. At the same time, the gas-liquid separator 19 can also play the role of an expansion tank to a certain extent, and is used to store gaseous refrigerant at normal temperature of the system to prevent the system pressure from being too high.

[0041] Specifically, in this embodiment, the first refrigeration module 10 further includes an oil separator 110. The oil separator 110 has an air inlet, an air outlet and an oil return port. The air inlet is communicated with the exhaust end of the first compressor 11, the air outlet is communicated with the input end of the first condenser 12, and the oil return port is communicated with the suction end of the first compressor 11. The oil separator 110 can separate the lubricating oil mixed in the high-temperature and high-pressure refrigerant discharged by the first compressor 11 to obtain relatively pure high-temperature and high-pressure refrigerant and lubricating oil. The pure high-temperature and high-pressure refrigerant is conveyed to the first condenser 12 through the air outlet, and the separated lubricating oil flows back to the first compressor 11 through the oil return port, so as to ensure the safe and efficient operation of the refrigeration system 100.

[0042] The above refrigeration system 100 can also operate under other temperature conditions (for example, below 0°C). At this time, the operating mode of the first refrigeration module 10 is different from that under the above high-temperature conditions. Specifically, the high-temperature and high-pressure refrigerant discharged from the exhaust end of the first compressor 11 is delivered to the first condenser 12; the refrigerant passes through the first condenser 12 and is condensed by the first condenser 12 into a medium-temperature and high-pressure refrigerant; then, the medium-temperature and high-pressure refrigerant passes through the first throttle valve 13 to expand and reduce the pressure to obtain a low-temperature and low-pressure refrigerant; the low-temperature and low-pressure refrigerant can exchange heat with electronic components after entering the evaporator 14, thereby cooling the electronic components. The low-temperature and low-pressure refrigerant is converted into a high-temperature and low-pressure refrigerant after heat exchange in the evaporator 14 and is output from the output end of the evaporator 14; the high-temperature and low-pressure refrigerant is sucked by the first compressor 11 after passing through the throttle assembly 15 and is compressed into a high-temperature and high-pressure refrigerant gas, and so on in a cycle.

[0043] Since the refrigerant output from the output end of the evaporator 14 is in a high-temperature and low-pressure state, the throttling and expansion effects of the throttle assembly 15, specifically the third throttle valve 154 and the regulating valve 156, are relatively weak, which may cause the suction gas temperature or the suction gas humidity of the first compressor 11 to be too high.

[0044] Therefore, in this embodiment, the first refrigeration module 10 further includes a first bypass branch 18. A first control valve 181 is provided on the first bypass branch 18. The input end of the first bypass branch 18 is connected to a part of the first refrigeration return line between the output end of the first condenser 12 and the input end of the evaporator 14, and the output end of the first bypass branch 18 is connected to the throttle assembly 15.

[0045] The first control valve 181 can control the first bypass branch 18 to be opened or closed. Under high-temperature conditions, the first control valve 181 closes the first bypass branch 18, thereby preventing the first bypass branch 18 from diverting the refrigerant entering the evaporator 14 (as Figure 3 shown). Under other temperature conditions, the opening degree of the first control valve 181 can be controlled as needed. At this time, a part of the medium-temperature and high-pressure refrigerant output from the first condenser 12, or a part of the low-temperature and low-pressure refrigerant obtained by the expansion and pressure reduction of the first throttle valve 13, can be partially delivered to the throttle assembly 15 through the first bypass branch 18. By introducing medium-temperature and high-pressure or low-temperature and low-pressure refrigerant into the throttle assembly 15 through the first bypass branch 18, the purpose of controlling the suction gas temperature and the suction gas humidity can be achieved.

[0046] Specifically, when the suction gas temperature of the first compressor 11 is too high, low-temperature and low-pressure refrigerant can be introduced into the throttle assembly 15 through the first bypass branch 18. The low-temperature refrigerant can be mixed with the high-temperature and low-pressure refrigerant output from the evaporator 14 in the throttle assembly 15 and significantly reduce the temperature of the mixed refrigerant, thereby reducing the suction gas temperature of the first compressor 11 and avoiding too high suction gas temperature.

[0047] When the heat exchange capacity of the evaporator 14 is small and the evaporation amount is low, the temperature of the refrigerant output therefrom is relatively low and the humidity is relatively high, which may cause liquid carryover in the suction gas of the first compressor 11. At this time, medium-temperature and high-pressure refrigerant can be introduced into the throttling assembly 15 through the first bypass branch 18, and the temperature of this medium-temperature and high-pressure refrigerant is higher than that of the high-temperature and low-pressure refrigerant output by the evaporator 14. Therefore, the medium-temperature and high-pressure refrigerant introduced into the throttling assembly 15 through the first bypass branch 18 can heat the high-temperature and low-pressure refrigerant output by the evaporator 14, thereby helping to reduce the liquid content in the refrigerant and avoid liquid carryover in the suction gas of the first compressor 11.

[0048] Specifically, the output end of the first bypass branch 18 is connected to the first pipeline 151. More specifically, the output end of the first bypass branch 18 is connected to the input end of the third throttle valve 154. In this way, the refrigerant in the first bypass branch 18 can be expanded and depressurized by the third throttle valve 154 and then input into the heat exchanger 155, reducing the liquid refrigerant content and the refrigerant temperature in the heat exchanger 155.

[0049] In this embodiment, the input end of the first bypass branch 18 is connected to the input end of the first throttle valve 13, and the first control valve 181 is set as a throttle valve, and the refrigerant in the first bypass branch 18 can be expanded and depressurized through the first control valve 181.

[0050] That is, the input end of the first bypass branch 18 is connected to the part of the first refrigeration circuit between the first condenser 12 and the first throttle valve 13. The medium-temperature and high-pressure refrigerant output by the first condenser 12 can be transported to the first pipeline 151 through the first bypass branch 18. When the suction gas temperature of the first compressor 11 is too high, the medium-temperature and high-pressure refrigerant can be expanded and depressurized by the first control valve 181 to obtain low-temperature and low-pressure refrigerant. Therefore, the refrigerant finally transported to the first pipeline 151 through the first bypass branch 18 is in a low-temperature and low-pressure state, which can play a role in reducing the suction gas temperature.

[0051] In addition, in another embodiment, the input end of the first bypass branch 18 is connected to the output end of the first throttle valve 13, and the refrigerant in the first bypass branch 18 is expanded and depressurized by the first throttle valve 13. That is, the input end of the first bypass branch 18 is connected to the part of the first refrigeration circuit between the first throttle valve 13 and the evaporator 14.

[0052] In this way, a part of the low-temperature and low-pressure refrigerant output by the first throttle valve 13 can be transported to the first pipeline 151 through the first bypass branch 18, thereby playing a role in reducing the suction gas temperature. At this time, the first control valve 181 can be an ordinary valve and does not need to have a throttling function.

[0053] In the above embodiment, after the refrigerant in the first bypass branch 18 is expanded and depressurized by the first throttle valve 13 or the first control valve 181 (acting as a throttle valve), it is input to the input end of the third throttle valve 154 on the first pipeline 151, and then enters the heat exchanger 155 after secondary throttle expansion, thereby further reducing the temperature and dryness of the refrigerant input to the first compressor 11 from the second pipeline 153. In addition, in other embodiments, the output end of the first bypass branch 18 may also be connected to the output end of the third throttle valve 154 on the first pipeline 151, so that the refrigerant in the first bypass branch 18 enters the heat exchanger 155 after only one throttle expansion.

[0054] Under other temperature conditions other than high-temperature conditions, the third throttle valve 154 and the regulating valve 156 can be adjusted to the maximum opening degree, and the throttling assembly 15 does not throttle and cool the flowing refrigerant. At this time, by controlling the opening degree of the first control valve 181, the flow rate of the low-temperature and low-pressure refrigerant or the medium-temperature and high-pressure refrigerant entering the throttling assembly 15 can be controlled, so as to precisely adjust the suction temperature of the first compressor 11.

[0055] In addition, in this embodiment, a mixer 16 is provided between the first throttle valve 13 and the evaporator 14 in the first refrigeration circuit. The first refrigeration module 10 further includes a second bypass branch 17 provided with a second control valve 171. One end of the second bypass branch 17 is connected to a part of the first refrigeration circuit between the first compressor 11 and the first condenser 12, and the other end is connected to the mixer 16.

[0056] When the first refrigeration module 10 operates, part of the high-temperature and high-pressure refrigerant discharged from the exhaust end of the first compressor 11 enters the first condenser 12, and the other part can enter the mixer 16 through the second bypass branch 17 and be mixed with the low-temperature and low-pressure refrigerant obtained by expanding and depressurizing through the first throttle valve 13, thereby adjusting the temperature of the refrigerant entering the evaporator 14 and providing the evaporation temperature required by the evaporator 14. By adjusting the opening degree of the second control valve 171, the flow rate of the high-temperature and high-pressure refrigerant entering the mixer 16 can be controlled, so as to adjust the temperature of the refrigerant entering the evaporator 14 as needed. In this way, the applicable working condition temperature range of the above refrigeration system 100 can be expanded.

[0057] Please refer to again Figure 1 , in this embodiment, the refrigeration system 100 further includes a second refrigeration module 20. The second refrigeration module 20 includes a second compressor 21, a second condenser 22, a second throttle valve 23 and the first condenser 12. The second compressor 21, the second condenser 22, the second throttle valve 23 and the first condenser 12 are connected in sequence to form a second refrigeration circuit, and the first condenser 12 serves as an evaporative condenser to thermally couple the first refrigeration circuit and the second refrigeration circuit.

[0058] When the second refrigeration module 20 operates, the second compressor 21 sucks in the high-temperature and low-pressure refrigerant output from the output end of the first condenser 12, compresses the refrigerant into a high-temperature and high-pressure refrigerant, and discharges it from the exhaust end of the second compressor 21 to the second condenser 22. After passing through the second condenser 22, the refrigerant is condensed by the second condenser 22 into a medium-temperature and high-pressure refrigerant, and is expanded and depressurized by the second throttle valve 23 into a low-temperature and low-pressure refrigerant, and finally enters the first condenser 12 and exchanges heat with the refrigerant in the first refrigeration circuit in the first condenser 12 to reduce the temperature of the refrigerant in the first refrigeration circuit. The heat-exchanged refrigerant is output from the first condenser 12 and enters the second compressor 21 again, and so on in a cycle.

[0059] Thus, it can be seen that the refrigerant in the second refrigeration module 20 can cool the refrigerant in the first refrigeration module 10 through the first condenser 12, thereby improving the condensation effect of the first condenser 12 on the refrigerant in the first refrigeration circuit, and further enhancing the overall cooling effect of the refrigeration system 100.

[0060] It can be seen that the first condenser 12 serves as both the condenser of the first refrigeration module 10 and the evaporator of the second refrigeration module 20. Specifically, in the above-mentioned condensing evaporator, that is, the first condenser 12, two groups of independent pipelines can be formed, which are respectively connected to the first refrigeration circuit and the second refrigeration circuit. The refrigerant in the second refrigeration module 20 and the refrigerant in the first refrigeration module 10 will not be mixed. Moreover, the two groups of pipelines share the heat dissipation fins, so that the heat exchange efficiency between the first refrigeration circuit and the second refrigeration circuit is higher. Moreover, the first condenser 12 that simultaneously has the functions of condensation and evaporation can also simplify the structure and reduce the space occupied by the above-mentioned refrigeration system 100.

[0061] In addition, more levels of refrigeration modules such as the third and fourth levels can be set. The remaining multi-level refrigeration modules can adopt the same structure as the second refrigeration module 20. Moreover, the second condenser 22 of the second refrigeration module 20 can be used as the evaporator of the third refrigeration module, and the condenser of the third refrigeration module can be used as the evaporator of the fourth refrigeration module. And so on, a multi-level cooling structure can be formed, thereby further enhancing the overall cooling effect of the refrigeration system 100.

[0062] In the above-mentioned refrigeration system 100 and sorting and testing equipment, under high-temperature working conditions, the refrigerant output by the first condenser 12 enters the evaporator 14 after passing through the first throttle valve 13. At this time, in order to increase the duty ratio of the heating system to the user's required range, the opening degree of the first throttle valve 13 is increased, so the refrigerant can directly enter the evaporator 14 without strong throttling. Moreover, since there is no bypass branch to split the refrigerant entering the evaporator 14, the refrigerant flow rate entering the evaporator 14 can be greatly increased, thereby increasing the heating capacity against heating of the heating system and effectively increasing the duty ratio of the heating system. At the same time, in order to prevent the suction gas temperature of the first compressor 11 from being too high or liquid hammer from occurring, the refrigerant output by the evaporator 14 can be throttled to reduce the temperature and pressure through the throttling component 15. Thus, it can be seen that the above-mentioned refrigeration system 100 can avoid overheating or liquid hammer of the first compressor 11 while meeting the usage requirements of a high duty ratio of the heating system, ensuring the stable operation of the refrigeration system 100.

[0063] The technical features of the above-described embodiments can be combined arbitrarily. For the sake of brevity of description, 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, it should be considered as the scope described in this specification.

[0064] The above-described embodiments only represent several implementation manners of the present invention. The description is relatively specific and detailed, but it should not be construed as a limitation on the scope of the utility model patent. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present invention, several modifications and improvements can still be made, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the utility model patent shall be subject to the appended claims.

Claims

1. A refrigeration system (100) capable of coordinated temperature control with a heating system, characterized in that: The refrigeration system (100) comprises a first refrigeration module (10), wherein the first refrigeration module (10) comprises a first compressor (11), a first condenser (12), a first throttle valve (13), an evaporator (14) and a throttling assembly (15); the first compressor (11), the first condenser (12), the first throttle valve (13), the evaporator (14) and the throttling assembly (15) are connected in sequence to form a first refrigeration circuit; an input end and an output end of the throttling assembly (15) are respectively connected to an output end of the evaporator (14) and a return air end of the first compressor (11).

2. The refrigeration system (100) according to claim 1, characterized in that: The throttling assembly (15) comprises a first pipeline (151), a regulating pipeline (152), a second pipeline (153), a third throttling valve (154) and a heat exchanger (155); the first pipeline (151) and the second pipeline (153) are both part of the first refrigeration circuit; the input end of the first pipeline (151) is connected to the output end of the evaporator (14); the output end of the first pipeline (151) is connected to the input end of the heat exchanger (155); the third throttling valve (154) is connected to the output end of the evaporator (14); the output end of the first pipeline (151) is connected to the input end of the heat exchanger (155); The first pipeline (154) is connected to the first pipeline (151); the input end of the second pipeline (153) is connected to the air outlet end of the heat exchanger (155), and the output end of the second pipeline (153) is connected to the air return end of the first compressor (11); the regulating pipeline (152) is thermally coupled to the heat exchanger (155), and the input end of the regulating pipeline (152) is connected to the first pipeline (151), and the output end of the regulating pipeline (152) is connected to the second pipeline (153).

3. The refrigeration system (100) according to claim 2, characterized in that: The regulating pipeline (152) is provided with a regulating valve (156), and the regulating valve (156) is used to regulate the flow of the refrigerant flowing through the regulating pipeline (152).

4. The refrigeration system (100) according to claim 3, characterized in that: The regulating valve (156) is configured as a throttle valve, and the regulating valve (156) is located between the heat exchanger (155) and the output end of the regulating pipeline (152).

5. The refrigeration system (100) according to claim 2, characterized in that: The first refrigeration module further comprises a first bypass branch (18), on which a first control valve (181) is provided, an input end of the first bypass branch (18) is connected to a portion of the first refrigeration circuit between an output end of the first condenser (12) and an input end of the evaporator (14), and an output end of the first bypass branch (18) is connected to the throttling assembly (15).

6. The refrigeration system (100) according to claim 5, characterized in that: The output end of the first bypass branch (18) is in communication with the first pipeline (151).

7. The refrigeration system (100) according to claim 6, characterized in that: The output end of the first bypass branch (18) is connected to the input end of the third throttle valve (154); the input end of the first bypass branch (18) is connected to the input end of the first throttle valve (13), and the first control valve (181) is set as a throttle valve. The refrigerant in the first bypass branch (18) can be expanded and reduced in pressure through the first control valve (181).

8. The refrigeration system (100) according to claim 6, characterized in that: The output end of the first bypass branch (18) is connected to the input end of the third throttle valve (154); the input end of the first bypass branch (18) is connected to the output end of the first throttle valve (13), and the refrigerant in the first bypass branch (18) is expanded and reduced in pressure through the first throttle valve (13).

9. The refrigeration system (100) according to any one of claims 1 to 8, characterized in that: The invention also includes a second refrigeration module (20), wherein the second refrigeration module (20) includes a second compressor (21), a second condenser (22), a second throttle valve (23) and the first condenser (12); the second compressor (21), the second condenser (22), the second throttle valve (23) and the first condenser (12) are connected in sequence to form a second refrigeration circuit; the first condenser (12) acts as an evaporative condenser to thermally couple the first refrigeration circuit with the second refrigeration circuit.

10. A sorting test device, characterized in that: It comprises a heating system and a refrigeration system (100) as claimed in any one of claims 1 to 9, wherein the heating system is thermally coupled to the evaporator (14) to jointly control the temperature of electronic components.

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