A refrigeration system

Abstract

The utility model provides a kind of refrigeration system, which comprises: first channel and second channel, first channel and second channel are communicated first refrigeration circuit and second refrigeration circuit respectively;The first refrigeration circuit comprises: first compressor, a plurality of refrigerant regulating components and refrigeration module;The second refrigeration circuit comprises: second compressor, condenser and throttling pressure reducing device;Wherein, the refrigeration module is constructed into the first flow channel spirally extending from the outer periphery of the refrigeration module to the center of the refrigeration module, and the second flow channel spirally extending from the center of the refrigeration module to the outer periphery of the refrigeration module;The first flow channel and the second flow channel are staggered distributed along the spiral direction, the first flow channel and the second flow channel are communicated, and the flow direction of the refrigerant in the first flow channel is opposite to the flow direction of the refrigerant in the second flow channel.The refrigeration system disclosed in the present application achieves uniform overall temperature of the refrigeration module.

Description

Technical Field

[0001] This utility model relates to the field of three-temperature testing and sorting machine technology, and in particular to a refrigeration system. Background Technology

[0002] Three-temperature testing and sorting machines are specifically designed for IC (Integrated Circuit Chip) testing, capable of testing and sorting chips in high-temperature, room-temperature, and low-temperature environments. Existing three-temperature testing and sorting machines typically preheat or cool the chips to a set test temperature using a preheating device before testing. When performing low-temperature testing, a cooling system is needed to cool the preheating device to the set low-temperature test temperature. The preheating device usually includes a preheating plate to hold the chip, as well as a cooling module and a heating module. These modules preheat or cool the preheating plate to the set test temperature, preheating the chip and preventing a large difference between the initial chip surface temperature and the test temperature during testing.

[0003] However, existing refrigeration systems cannot ensure uniform temperature across the entire refrigeration module when supplying cryogenic refrigerant. This results in a large temperature difference between the central and peripheral areas of the refrigeration module, leading to localized overheating or undercooling. Consequently, the chip temperatures vary across different areas of the preheating plate, failing to meet temperature testing requirements and affecting the accuracy of subsequent test data.

[0004] It should be noted that the above description of the background technology is only for the purpose of providing a clear and complete explanation of the technical solutions of this application and facilitating understanding by those skilled in the art. It should not be assumed that these technical solutions are known to those skilled in the art simply because they have been described in the background technology section of this application. Utility Model Content

[0005] The purpose of this invention is to disclose a refrigeration system that addresses many shortcomings of existing refrigeration modules in refrigeration systems, particularly in achieving uniform overall temperature of the refrigeration module.

[0006] To achieve the above objectives, this utility model provides a refrigeration system, including: a first refrigeration circuit, a second refrigeration circuit, and a heat exchanger, wherein the first refrigeration circuit and the second refrigeration circuit are thermally coupled through the heat exchanger;

[0007] The heat exchanger includes: a first channel and a second channel that are thermally isolated from each other, wherein the first channel and the second channel are respectively connected to the first refrigeration circuit and the second refrigeration circuit;

[0008] The first refrigeration circuit includes: a first compressor, several refrigerant regulating components, and a refrigeration module;

[0009] The second refrigeration circuit includes: a second compressor, a condenser, and a throttling and pressure-reducing device;

[0010] The refrigeration module is configured with a first flow channel extending spirally from the outer periphery of the refrigeration module to the center of the refrigeration module, and a second flow channel extending spirally from the center of the refrigeration module to the outer periphery of the refrigeration module.

[0011] The first flow channel and the second flow channel are staggered along a spiral direction, the first flow channel and the second flow channel are connected, and the refrigerant flow direction in the first flow channel is opposite to the refrigerant flow direction in the second flow channel.

[0012] As a further improvement of this utility model, the refrigeration module is constructed with a spiral-shaped first partition and a second partition, which are staggered along the spiral direction;

[0013] The refrigeration module, together with the first partition and the second partition, respectively encloses the first flow channel and the second flow channel.

[0014] As a further improvement of this utility model, the first dividing part is formed by connecting multiple long strip-shaped first components along a set spiral path, and a 90° angle is formed between two adjacent first components;

[0015] The second partition is formed by connecting multiple elongated second components along a set spiral path, with a 90° angle between two adjacent second components.

[0016] As a further improvement of this utility model, the heat exchanger is configured as a plate heat exchanger, and the first channel and the second channel are configured as alternately stacked plate channels.

[0017] As a further improvement of this utility model, the flow cross-sectional area of ​​the first channel is larger than that of the second channel.

[0018] As a further improvement of this utility model, the first refrigeration circuit further includes: an oil separator disposed between the exhaust port of the first compressor and the inlet end of the first channel, and a pressure regulating valve disposed between the oil separator and the first compressor.

[0019] As a further improvement of this utility model, the refrigerant regulating assembly includes a first solenoid valve, a servo valve, and a capillary tube connected in series.

[0020] As a further improvement of this utility model, the second refrigeration circuit further includes: a drying filter disposed at the outlet end of the condenser and the inlet end of the throttling and pressure reducing device.

[0021] As a further improvement of this utility model, the first refrigeration circuit further includes: a pressure equalization branch disposed between the heat exchanger and the first compressor; the pressure equalization branch includes a second solenoid valve and a bypass pressure reducing valve connected in series.

[0022] Compared with the prior art, the beneficial effects of this utility model are as follows: The refrigerant flows from the outer periphery of the cooling module to the center of the cooling module along a spiral path in the first flow channel. During this process, the refrigerant continuously absorbs heat from the outer periphery to the center of the cooling module, preferentially cooling the outer periphery. After reaching the center of the cooling module, the refrigerant automatically flows from the first flow channel into the second flow channel and flows from the center of the cooling module toward the outer periphery along a spiral path in the second flow channel, cooling the center area of ​​the cooling module again. This ensures that the overall temperature of the cooling module is uniform, avoiding local overheating or undercooling. It also enables the cooling module to uniformly transfer cooling energy to the preheating plate, ensuring a uniform overall temperature of the preheating plate. This allows the preheating plate to reach the set low-temperature test temperature, preventing different temperatures in different areas of the preheating plate from causing different preheating temperatures for the chip, thus meeting temperature test requirements and preventing any impact on the accuracy of subsequent chip test data. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the refrigeration system disclosed in this utility model;

[0024] Figure 2 This is a cross-sectional view of the cooling module. Detailed Implementation

[0025] The present invention will now be described in detail with reference to the embodiments shown in the accompanying drawings. However, it should be noted that these embodiments are not intended to limit the present invention. Equivalent transformations or substitutions in function, method, or structure made by those skilled in the art based on these embodiments are all within the protection scope of the present invention.

[0026] The accompanying drawings in this invention are not strictly drawn to scale, and the specific dimensions of each structure can be determined according to actual needs. The drawings described in this invention are merely structural schematic diagrams.

[0027] Please refer to Figures 1 to 2 A specific implementation of a refrigeration system is disclosed.

[0028] In the prior art, when a three-temperature test sorber needs to test chips, it usually preheats or cools the chips to a set test temperature through a pre-temperature device. When performing a low-temperature (e.g., -55°C) test on chips, it is necessary to cool the pre-temperature device through a refrigeration system to make the pre-temperature device reach the set test temperature (e.g., -55°C). However, when the refrigeration system in the prior art delivers low-temperature refrigerant to the refrigeration module, it is difficult to ensure uniform temperature across the entire refrigeration module, resulting in a large temperature difference between the central area and the peripheral area of the refrigeration module, leading to local overheating or overcooling. As a result, the temperatures of the chips in different areas of the pre-temperature tray are different, which cannot meet the temperature test requirements and affects the data accuracy of subsequent tests.

[0029] The following description specifically takes the pre-temperature device as an example for illustrative explanation. Certainly, it may also be a chip carrying device or other device that requires temperature control for chip test temperature, and the device includes a refrigeration module, which is not limited in this embodiment, but this should not limit the protection scope of the present application.

[0030] Reference Figure 1 to Figure 2 as shown, in this embodiment, the refrigeration system 100 includes: a first refrigeration circuit, a second refrigeration circuit, and a heat exchanger 30.

[0031] The first refrigeration circuit and the second refrigeration circuit are thermally coupled through the heat exchanger 30; the heat exchanger 30 includes a first passage 31 and a second passage 32 that are thermally isolated from each other, and the first passage 31 and the second passage 32 are respectively communicated with the first refrigeration circuit and the second refrigeration circuit; the first refrigeration circuit includes a first compressor 11, a plurality of refrigerant regulating assemblies 12 and a refrigeration module 13; the second refrigeration circuit includes a second compressor 21, a condenser 22 and a throttle pressure reducing device 23; wherein, the refrigeration module 13 is configured with a first flow passage 131 spirally extending from the outer periphery of the refrigeration module 13 to the center of the refrigeration module 13, and a second flow passage 132 spirally extending from the center of the refrigeration module 13 to the outer periphery of the refrigeration module 13; the first flow passage 131 and the second flow passage 132 are alternately distributed along the spiral direction, the first flow passage 131 is communicated with the second flow passage 132, and the flowing direction of the refrigerant in the first flow passage 131 is opposite to the flowing direction of the refrigerant in the second flow passage 132.

[0032] In the first refrigeration circuit, the first compressor 11, the first channel 31, the refrigerant regulating component 12, and the refrigeration module 13 are connected sequentially through pipelines. The inlet end of the first channel 31 is connected to the exhaust port of the second compressor 21 through a pipeline, and the outlet end of the first channel 31 is connected to several refrigerant regulating components 12. The outlet end of the refrigerant regulating component 12 is connected to the refrigeration module 13 through a pipeline. The refrigeration module 13 has an inlet 135 and an outlet 136. The outlet end of the refrigerant regulating component 12 is connected to the inlet 135 of the refrigeration module 13 through a pipeline, and the suction port of the first compressor 11 is connected to the outlet 136 of the refrigeration module 13 through a pipeline. In the second refrigeration circuit, the second compressor 21, condenser 22, throttling and pressure reducing device 23, and second channel 32 are connected in sequence through pipelines. The inlet end of the condenser 22 is connected to the exhaust port of the second compressor 21, the inlet end of the throttling and pressure reducing device 23 is connected to the outlet end of the condenser 22, the inlet end of the second channel 32 is connected to the outlet end of the throttling and pressure reducing device 23, and the outlet end of the second channel 32 is connected to the suction port of the second compressor 21.

[0033] It should be noted that the first channel 31 and the second channel 32 are thermally isolated from each other. Thermal isolation refers to the physical isolation of the refrigerants in the first channel 31 and the second channel 32, preventing the refrigerants in the first channel 31 and the second channel 32 from mixing, while allowing heat transfer.

[0034] When the second refrigeration circuit is working, the second compressor 21 draws in low-temperature, low-pressure refrigerant and compresses it into high-temperature, high-pressure refrigerant. The high-temperature, high-pressure refrigerant gas enters the condenser 22 through a pipeline, where it is cooled by air or water cooling to become high-pressure refrigerant. The high-pressure refrigerant then enters the throttling and depressurizing device 23 (e.g., a thermostatic expansion valve) through a pipeline to depressurize it into low-temperature, low-pressure refrigerant. The low-temperature, low-pressure refrigerant then enters the second channel 32 of the heat exchanger 30 through a pipeline to absorb the heat released by the high-temperature, high-pressure refrigerant in the first channel 31, and then returns to the second compressor 21 through a pipeline. The second refrigeration circuit repeats this cycle continuously.

[0035] When the first refrigeration circuit is working, the first compressor 11 draws in low-temperature, low-pressure refrigerant and compresses it into high-temperature, high-pressure refrigerant. The high-temperature, high-pressure refrigerant enters the first channel 31 of the heat exchanger 30 through a pipeline and releases heat into the second channel 32, exchanging heat with the low-temperature, low-pressure refrigerant in the second channel 32 to cool it into high-pressure refrigerant. After being regulated by the refrigerant regulating component 12, the high-pressure refrigerant forms a low-pressure, low-temperature refrigerant and is transported to the refrigeration module 13. After heat exchange in the refrigeration module 13, it returns to the first compressor 11 through a pipeline, and the first refrigeration circuit repeats in this way. The inlet 135 and outlet 136 of the refrigeration module 13 are respectively connected to the first flow channel 131 and the second flow channel 132, so that the low-pressure, low-temperature refrigerant discharged from the outlet end of the refrigerant regulating component 12 enters the first flow channel 131 through the inlet 135, flows in the first flow channel 131 to the second flow channel 132, and finally returns to the first compressor 11 through the pipeline via the outlet 136 of the refrigeration module 13.

[0036] The refrigerant flows from the outer periphery of the refrigeration module 13 to the center of the refrigeration module 13 along a spiral path in the first flow channel 131. During this process, the refrigerant continuously absorbs heat from the outer periphery to the center of the refrigeration module 13, preferentially cooling the outer periphery of the refrigeration module 13. After the refrigerant reaches the center of the refrigeration module 13, it automatically flows from the first flow channel 131 into the second flow channel 132, and flows from the center of the refrigeration module 13 toward the outer periphery of the refrigeration module 13 along a spiral path in the second flow channel 132, cooling the central area of ​​the refrigeration module 13 again, so that the overall temperature of the refrigeration module 13 is uniform.

[0037] During this process, the temperature of the refrigerant injected into the first flow channel 131 gradually increases, and the heated refrigerant enters the second flow channel 132. Simultaneously, new low-pressure, low-temperature refrigerant is continuously injected into the first flow channel 131, flowing through the refrigerant flow direction within the first flow channel 131 (e.g., ...). Figure 2 The direction indicated by the middle arrow L1) and the refrigerant flow direction within the second flow channel 132 (as shown by the middle arrow L1) are different. Figure 2(In the opposite direction indicated by the middle arrow L2) This causes the refrigerant flowing in the second flow channel 132 to release heat to the new refrigerant in the adjacent first flow channel 131. The refrigerant flowing in the first flow channel 131 and the refrigerant flowing in the second flow channel 132 continuously exchange heat, causing the new refrigerant in the first flow channel 131 to absorb heat, thus preventing the outer periphery of the cooling module 13 from becoming too cold. It also causes the heated refrigerant in the second flow channel 132 to release heat, preventing the central area of ​​the cooling module 13 from becoming too hot. This reduces the temperature difference between the refrigerant in the first flow channel 131 and the refrigerant in the second flow channel 132, ensuring a uniform overall temperature of the cooling module 13 and preventing localized overheating or underheating. This allows the cooling module 13 to uniformly transfer cooling energy to the preheating plate, ensuring a uniform overall temperature of the preheating plate and allowing it to reach the set low-temperature test temperature (e.g., -55℃). This prevents different temperatures in different areas of the preheating plate from causing different preheating temperatures for the chip, thus meeting temperature test requirements and preventing any impact on the accuracy of subsequent chip test data. The refrigerant flowing in the second channel 132 returns to the first compressor 11 through the outlet 136, and so on.

[0038] In some examples, the parameter Figure 2 As shown, the refrigeration module 13 is constructed with a spiral-shaped first partition 133 and a second partition 134, which are staggered along the spiral direction. A first flow channel 131 and a second flow channel 132 are formed between the refrigeration module 13 and the first partition 133 and the second partition 134, respectively. One end of the first partition 133 is connected to the side of the refrigeration module 13, and the other end of the first partition 133 is a free end; one end of the second partition 134 is connected to the side of the refrigeration module 13, and the other end of the second partition 134 is a free end. When the refrigerant enters the first flow channel 131 from the inlet 135, it is guided by the first partition 133 and the second partition 134 to flow along the spiral path to the center of the refrigeration module 13. After absorbing heat, the refrigerant naturally turns from the free end of the first flow channel 131 to the free end of the second flow channel 132. When it flows back in the second flow channel 132, it exchanges heat with the new refrigerant in the adjacent first flow channel 131 through countercurrent flow. The staggered layout of the first partition 133 and the second partition 134 can expand the heat exchange area, thereby reducing the temperature difference in the entire area of ​​the refrigeration module 13 and making the overall temperature of the refrigeration module 13 uniform.

[0039] In some examples, the parameter Figure 2As shown, the first partition 133 is formed by connecting multiple elongated first components 1331 along a predetermined spiral path, with adjacent first components 1331 forming a 90° angle; the second partition 134 is formed by connecting multiple elongated second components 1341 along a predetermined spiral path, with adjacent second components 1341 forming a 90° angle. The multiple elongated first components 1331 along the predetermined spiral path can be welded to form the first partition 133, and the multiple elongated second components 1341 along the predetermined spiral path can be welded to form the second partition 134. When the overall shape of the cooling module 13 is preferably cuboid, any two connected first components 1331 and any two connected second partitions 134 form a 90° angle. By using a 90° angle between any two connected first components 1331 and a 90° angle between any two connected second components 1341, the refrigerant in the first flow channel 131 and the second flow channel 132 can achieve vertical turning during the flow process, thereby forming turbulence. This allows the outer layer of refrigerant flowing against the side wall of the first partition 133 in the first flow channel 131 to mix with the central refrigerant, and the outer layer of refrigerant flowing against the side wall of the second partition 134 in the second flow channel 132 to mix with the central refrigerant. This enables the refrigerant to quickly absorb heat and improves heat exchange efficiency.

[0040] In some examples, the parameter Figure 1 As shown, the heat exchanger 30 is configured as a plate heat exchanger 30, with the first channel 31 and the second channel 32 configured as alternating stacked plate channels. The plate heat exchanger 30 constructs the first channel 31 and the second channel 32 through alternating stacked corrugated plates (not shown) to form a physically isolated dual-channel counter-current heat exchange structure. That is, the refrigerant flows in opposite directions in the first channel 31 and the second channel 32, and the refrigerants in the first channel 31 and the second channel 32 can exchange heat. The refrigerants in the first channel 31 and the second channel 32 are completely isolated by the plates, preventing refrigerant mixing. Simultaneously, efficient heat conduction is achieved through the titanium alloy plates, allowing the refrigerant in the first channel 31 to release heat, which is then absorbed by the refrigerant in the second channel 32.

[0041] In some examples, the flow cross-sectional area of ​​the first channel 31 is larger than that of the second channel 32. This is to reduce the refrigerant flow rate in the first channel 31 and match it to the refrigerant flow rate in the second channel 32 under the same mass flow rate conditions, resulting in smoother refrigerant flow and improved heat exchange efficiency. For example, the ratio of the cross-sectional area of ​​the first channel 31 to the flow cross-sectional area of ​​the second channel 32 can be 1.2 to 1.5:1.

[0042] In some examples, the parameter Figure 1As shown, the first refrigeration circuit also includes: an oil separator 14 disposed between the discharge port of the first compressor 11 and the inlet end of the first channel 31, and a pressure regulating valve 15 disposed between the oil separator 14 and the first compressor 11. The oil separator 14 separates and recovers the lubricating oil from the refrigerant discharged from the first compressor 11 back to the first compressor 11, ensuring the normal operation of the lubrication system, preventing lubricating oil from entering the heat exchanger 30 and affecting its heat exchange performance, and preventing lubricating oil from accumulating in the pipeline and causing blockage. The opening of the pressure regulating valve 15 controls the back pressure at the bottom oil return port of the oil separator 14, ensuring that the separated lubricating oil can stably flow back to the first compressor 11, maintaining a stable back pressure in the oil separator 14. Furthermore, by limiting the return oil flow rate, excessive high-temperature lubricating oil is prevented from flooding into the first compressor 11 at once.

[0043] In some examples, the parameter Figure 1 As shown, the refrigerant regulating assembly 12 includes a first solenoid valve 121, a servo valve 122, and a capillary tube 123 connected in series. The first solenoid valve 121 controls the refrigerant flow, the servo valve 122 regulates the refrigerant flow and pressure, and the capillary tube 123 provides basic throttling and pressure reduction functions. The refrigerant first flows through the first solenoid valve 121, then through the servo valve 122 for precise flow regulation, and finally through the capillary tube 123 for stable pressure reduction. The regulated refrigerant then enters the refrigeration module 13 to ensure that the refrigerant entering the refrigeration module 13 is in an optimal pressure and flow state.

[0044] In some examples, the parameter Figure 1 As shown, the second refrigeration circuit also includes a dryer filter 24 disposed at the outlet end of the condenser 22 and the inlet end of the throttling and pressure-reducing device 23. The dryer filter 24 is used to adsorb moisture in the refrigerant and filter impurities, ensuring the long-term stable operation of the refrigeration system 100.

[0045] In some examples, the parameter Figure 1 As shown, the first refrigeration circuit further includes a pressure equalization branch 16 disposed between the heat exchanger 30 and the first compressor 11; the pressure equalization branch 16 includes a second solenoid valve 161 and a bypass pressure reducing valve 162 connected in series. The inlet end of the pressure equalization branch 16 is connected to the outlet end of the first channel 31 through a pipeline, and the outlet end of the pressure equalization branch 16 is connected to the suction port of the first compressor 11 through a pipeline. When the refrigeration system 100 detects an increase in the suction pressure of the first compressor 11, the second solenoid valve 161 opens, and the bypass pressure reducing valve 162 reduces the pressure of the refrigerant on the high-pressure side and injects it into the low-pressure side to regulate the pressure balance.

[0046] The detailed descriptions listed above are merely specific descriptions of feasible implementations of this utility model, and are not intended to limit the scope of protection of this utility model. All equivalent implementations or modifications made without departing from the spirit of this utility model should be included within the scope of protection of this utility model.

[0047] It will be apparent to those skilled in the art that this invention is not limited to the details of the exemplary embodiments described above, and that it can be implemented in other specific forms without departing from the spirit or essential characteristics of this invention. Therefore, the embodiments should be considered illustrative and non-limiting in all respects, and the scope of this invention is defined by the appended claims rather than the foregoing description. Thus, it is intended that all variations falling within the meaning and scope of equivalents of the claims be included within this invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0048] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. A refrigeration system, characterized in that, include: The system comprises a first refrigeration circuit, a second refrigeration circuit, and a heat exchanger, wherein the first refrigeration circuit and the second refrigeration circuit are thermally coupled through the heat exchanger. The heat exchanger includes: a first channel and a second channel that are thermally isolated from each other, wherein the first channel and the second channel are respectively connected to the first refrigeration circuit and the second refrigeration circuit; The first refrigeration circuit includes: a first compressor, several refrigerant regulating components, and a refrigeration module; The second refrigeration circuit includes: a second compressor, a condenser, and a throttling and pressure-reducing device; The refrigeration module is configured with a first flow channel extending spirally from the outer periphery of the refrigeration module to the center of the refrigeration module, and a second flow channel extending spirally from the center of the refrigeration module to the outer periphery of the refrigeration module. The first flow channel and the second flow channel are staggered along a spiral direction, the first flow channel and the second flow channel are connected, and the refrigerant flow direction in the first flow channel is opposite to the refrigerant flow direction in the second flow channel.

2. The refrigeration system according to claim 1, characterized in that, The refrigeration module is constructed with a spiral-shaped first partition and a second partition, which are staggered along the spiral direction. The refrigeration module, together with the first partition and the second partition, respectively encloses the first flow channel and the second flow channel.

3. The refrigeration system according to claim 2, characterized in that, The first dividing part is formed by connecting multiple elongated first components along a predetermined spiral path, with a 90° angle between two adjacent first components; The second partition is formed by connecting multiple elongated second components along a set spiral path, with a 90° angle between two adjacent second components.

4. The refrigeration system according to claim 1, characterized in that, The heat exchanger is configured as a plate heat exchanger, and the first channel and the second channel are configured as alternately stacked plate channels.

5. The refrigeration system according to claim 4, characterized in that, The cross-sectional area of ​​the first channel is larger than that of the second channel.

6. The refrigeration system according to claim 1, characterized in that, The first refrigeration circuit further includes: an oil separator disposed between the exhaust port of the first compressor and the inlet end of the first channel, and a pressure regulating valve disposed between the oil separator and the first compressor.

7. The refrigeration system according to claim 1, characterized in that, The refrigerant regulating assembly includes a first solenoid valve, a servo valve, and a capillary tube connected in series.

8. The refrigeration system according to claim 1, characterized in that, The second refrigeration circuit further includes a dryer filter disposed at the outlet end of the condenser and the inlet end of the throttling and pressure reducing device.

9. The refrigeration system according to claim 1, characterized in that, The first refrigeration circuit further includes: a pressure equalization branch disposed between the heat exchanger and the first compressor; the pressure equalization branch includes a second solenoid valve and a bypass pressure reducing valve connected in series.

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