A refrigeration system and its control method

Abstract

This invention provides a refrigeration system and its control method. The refrigeration system includes an air circulator, an auxiliary cooling system, and a recirculation structure. The air circulator has a turbine outlet connected to an exhaust channel. The auxiliary cooling system has a condenser. The recirculation structure allows a portion of the exhaust gas in the exhaust channel to absorb the condensation heat released by the condenser, and then the gas, having absorbed the condensation heat, is directed to a first recirculation port and flows into the exhaust channel. According to the technical solution of this invention, a portion of the exhaust gas in the exhaust channel can absorb the condensation heat released by the condenser and its temperature rises under the action of the recirculation structure. This high-temperature gas is directed to the first recirculation port and flows into the exhaust channel, which can heat the exhaust channel and alleviate ice blockage within it. Furthermore, by adding a heat accumulator, the thermal demands of the aircraft under different flight conditions can be met. This effectively prevents ice blockage while also achieving waste heat recovery, greatly improving energy utilization efficiency.

Description

Technical Field

[0001] This invention belongs to the field of refrigeration technology, specifically relating to a refrigeration system and its control method. Background Technology

[0002] Currently, in three-wheeled high-pressure dehumidification air circulation refrigeration systems, engine bleed air is generally used as the high-pressure air source. After being cooled by multiple heat exchangers and turbine expansion, it is introduced into the cabin for cooling. However, under high temperature and high humidity conditions, the air has a very high moisture content. After the air expands and cools down, moisture will be released. Since the turbine outlet temperature is usually below 0°C, the released water is very likely to freeze in the exhaust passage at the turbine outlet, causing ice blockage inside the exhaust passage at the turbine outlet, which seriously affects the system performance. Summary of the Invention

[0003] Therefore, the present invention provides a refrigeration system and its control method, the main technical problem to be solved is: how to alleviate the ice blockage phenomenon in the exhaust passage of the turbine outlet.

[0004] To address the above problems, the present invention provides a refrigeration system comprising an air circulator, an auxiliary cooling system, and a reflux structure.

[0005] The air circulator has a turbine outlet, which is connected to an exhaust passage; the exhaust passage has an exhaust port and a first return port; wherein, along the exhaust direction of the exhaust passage, the first return port is located upstream of the exhaust port.

[0006] The auxiliary cooling system includes a condenser;

[0007] The reflux structure is used to allow a portion of the exhaust gas in the exhaust channel to absorb the condensation heat released by the condenser, and then the gas after absorbing the condensation heat is led to the first reflux port and flows into the exhaust channel.

[0008] In some embodiments, the reflux structure includes a first reflux channel connected in parallel with the exhaust channel; the condenser has a heat exchange channel connected in series with the first reflux channel;

[0009] The reflux structure guides a portion of the exhaust gas from the exhaust channel into the heat exchange channel through the first reflux channel, so as to absorb the condensation heat released by the condenser through the heat exchange channel; the reflux structure also guides the gas that has absorbed the condensation heat to the first reflux port and flows into the exhaust channel through the first reflux channel.

[0010] In some embodiments, the refrigeration system further includes a first pump body disposed on the first return channel, the first pump body being used to drive the gas in the first return channel to flow towards the first return port.

[0011] In some implementations, the first return channel may be opened or closed.

[0012] In some embodiments, the refrigeration system further includes a heat accumulator for recovering the condensation heat released by the condenser;

[0013] The reflux structure is also used to allow a portion of the exhaust gas from the exhaust channel to absorb the heat stored in the heat accumulator, and then guide the heat-absorbed gas to the first reflux port to flow into the exhaust channel.

[0014] In some embodiments, the reflux structure includes a second reflux channel connected in parallel with the exhaust channel;

[0015] The heat accumulator has a heat release channel, which is connected in series with the second return channel;

[0016] The reflux structure guides a portion of the exhaust gas from the exhaust channel into the heat release channel through the second reflux channel, so as to absorb the heat stored in the heat accumulator through the heat release channel; the reflux structure also guides the gas that has absorbed the heat to the first reflux port and flows into the exhaust channel through the second reflux channel.

[0017] In some embodiments, the refrigeration system further includes a second pump body; the second pump body is disposed on the second return channel, and the second pump body is used to drive the gas in the second return channel to flow towards the first return port.

[0018] In some embodiments, when the refrigeration system further includes a first pump body disposed on the first return channel, and the condenser has a heat exchange channel connected in series with the first return channel, the branch connected to the first pump body and the heat exchange channel is a first branch, and the heat accumulator has a heat absorption channel connected in parallel with the first branch, and the two can form a circulation loop.

[0019] In some embodiments, the first return channel has a drain port and a second return port. The first return channel introduces a portion of the exhaust gas from the exhaust channel through the drain port, and the gas that has undergone heat exchange with the refrigerant is led to the first return port and flows into the exhaust channel through the second return port.

[0020] The end of the heat absorption channel connected in parallel with the first branch is the first end, and the other end of the two connected in parallel is the second end;

[0021] The refrigeration system further includes a first switching valve and a second switching valve. The first switching valve is disposed in the channel between the first end and the second return port, and the second switching valve is disposed in the channel between the second end and the outlet port.

[0022] In some embodiments, the heat absorption channel and the heat release channel are the same channel; wherein,

[0023] The channel between the first end and the second return port is a first channel segment, and the first return channel and the second return channel share the first channel segment;

[0024] And / or, the channel between the second end and the drainage port is a second channel segment, and the first return channel and the second return channel share the second channel segment.

[0025] In some implementations, the second return channel may be opened or closed.

[0026] In some embodiments, when the refrigeration system further includes a first pump body disposed on the first return channel, and the condenser has a heat exchange channel connected in series with the first return channel, and the branch connecting the first pump body and the heat exchange channel is a first branch, and the heat accumulator has a heat absorption channel connected in parallel with the first branch,

[0027] The heat absorption channel is located on the second branch of the second return channel. The heat absorption channel is connected in parallel with the first branch through the second branch. The refrigeration system also includes a third switching valve, which is installed on the second branch to control the opening or closing of the second return channel.

[0028] In some embodiments, when the heat absorption channel and the heat release channel are the same channel, and the refrigeration system further includes a second pump body, the second pump body is disposed on the second branch section, and the refrigeration system further includes a fourth switching valve, which is disposed on the first branch.

[0029] The present invention also provides a control method for the above-mentioned refrigeration system, wherein the refrigeration system further includes another condenser, the exhaust channel exhausts through the condensation channel of the other condenser; and the first return channel has a drain port and a second return port, one end of the heat absorption channel and the first branch connected in parallel is the first end, and the other end of the two connected in parallel is the second end; the refrigeration system further includes a first switching valve and a second switching valve, the first switching valve being disposed in the channel between the first end and the second return port, and the second switching valve being disposed in the channel between the second end and the drain port, the control method includes:

[0030] When the refrigeration system is applied to an aircraft and the aircraft is in the climb or cruise phase, if the pressure difference between the two ends of the condensation channel of the other condenser is less than a preset value, then the first and second switching valves are closed, the third and fourth switching valves are opened, and the first or second pump body is activated; otherwise, the first, second, and fourth switching valves are opened, the third switching valve is closed, and the first pump body is activated.

[0031] And / or, when the refrigeration system is applied to an aircraft and the aircraft is in the ground or landing operation phase, if the pressure difference between the two ends of the condensation channel of the other condenser is greater than or equal to a preset value, then the first switch valve, the second switch valve and the third switch valve are opened, the fourth switch valve is closed, and the second pump body is turned on; otherwise, at least one of the first switch valve and the second switch valve is closed.

[0032] The refrigeration system and its control method provided by this invention have the following beneficial effects:

[0033] 1. Part of the exhaust gas in the exhaust channel can absorb the condensation heat released by the condenser and its temperature rises under the action of the reflux structure. The high-temperature gas is then led back to the first reflux port and flows into the exhaust channel, which can heat the exhaust channel and alleviate the ice blockage phenomenon in the exhaust channel.

[0034] 2. When the refrigeration system of the present invention is applied to an aircraft, the addition of a heat accumulator can meet the aircraft's heat demand under different flight conditions, effectively prevent ice blockage, and also realize waste heat recovery, greatly improving energy utilization efficiency. Attached Figure Description

[0035] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0036] Figure 1 This is a structural diagram of a refrigeration system provided in one embodiment of the present invention;

[0037] Figure 2 yes Figure 1 A partial structural diagram of the refrigeration system.

[0038] The attached figures are labeled as follows:

[0039] 1. Turbine outlet; 2. Exhaust passage; 3. Condenser; 4. First return passage; 5. Second return passage; 6. Heat accumulator; 7. First pump body; 8. First switching valve; 9. Second switching valve; 10. Second pump body; 11. Third switching valve; 12. Fourth switching valve; 13. Another condenser; 14. Differential pressure sensor; 15. Primary heat exchanger; 16. Secondary heat exchanger; 17. Regenerator; 18. Water separator; 19. Turbine; 20. Compressor structure; 21. Fan; 22. First throttling device; 23. Intermediate heat exchanger; 24. Second throttling device; 25. Evaporator; 26. Low-pressure compressor; 27. Intermediate chamber; 28. High-pressure compressor; 29. ​​Cooling unit; 31. Heat exchange passage; 61. Heat absorption passage; 62. Heat release passage; 63. Heat storage material; 41. First branch; 42. First channel section; 43. Second channel section; 51. Second branch section; 401. Second return port; 402. Drain port; 403. First end; 404. Second end; 131. Condensation passage of another condenser. Detailed Implementation

[0040] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0041] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0042] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0043] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0044] See also Figure 1-2 As shown, according to an embodiment of the present invention, a refrigeration system is provided, comprising an air circulator, an auxiliary cooling system, and a recirculation structure. The air circulator has a turbine outlet 1, which is connected to an exhaust passage 2, through which exhaust gas is discharged. The exhaust passage has an exhaust port and a first recirculation port 21. The first recirculation port 21 is located upstream of the exhaust port along the exhaust direction of the exhaust passage 2. The auxiliary cooling system has a condenser 3. The recirculation structure is used to allow a portion of the exhaust gas from the exhaust passage 2 to absorb the condensation heat released by the condenser 3, and then guide the heat-absorbed gas to the first recirculation port 21 to flow back into the exhaust passage 2.

[0045] In the example above, a portion of the exhaust gas from exhaust channel 2 absorbs the condensation heat released by condenser 3 under the action of the reflux structure, and its temperature rises. This high-temperature gas is then redirected back to the first reflux port 21 and flows into exhaust channel 2, which can heat exhaust channel 2 and alleviate the ice blockage phenomenon in exhaust channel 2.

[0046] The technical solution of the present invention not only effectively alleviates the ice blockage phenomenon in the exhaust channel 2, but also realizes waste heat recovery, which greatly improves energy utilization efficiency.

[0047] In some embodiments, the first return port 21 and the turbine outlet 1 can be the same port, so that the gas after absorbing heat can flow from the turbine outlet 1 into the exhaust passage 2 to heat and de-ice the entire section of the exhaust passage 2, thereby further improving the de-icing effect of the exhaust passage 2.

[0048] It should be noted here that: (as...) Figure 1 As shown, the refrigeration system of the present invention may further include a turbine 19, a primary heat exchanger 15, a secondary heat exchanger 16, a regenerator 17, a fan 21, a water separator 18, and another condenser 13. The exhaust passage 2 described above exhausts through the condensation passage 131 of the other condenser. The air circulator described above has a compressor structure 20. Hot air from upstream first enters the primary heat exchanger 15 for cooling, then enters the compressor structure 20, is pressurized, and then enters the secondary heat exchanger 16 for a second cooling. The primary heat exchanger 15 and the secondary heat exchanger 16 together form a two-stage heat exchanger. The cold side of the two-stage heat exchanger is cooled by ram air, which originates from the engine's bleed air. The cold side outlet of the two-stage heat exchanger is collected by a ram air switching valve and exhausted through the fan 21. Air exiting from the hot side of the secondary heat exchanger 16 passes through the regenerator 17, then enters the heat exchange channel of another condenser 13 for heat exchange before entering the water separator 18. The water separator 18 separates and discharges the free water in the air. The separated air then enters the regenerator 17 to evaporate any remaining free water, and subsequently enters the turbine 19 for expansion and cooling before entering the exhaust channel 2 from the turbine outlet 1. Finally, it is discharged through the condensation channel 131 of another condenser and sent to the cabin.

[0049] like Figure 1 As shown, the aforementioned auxiliary cooling system also includes a high-pressure compressor 28, a low-pressure compressor 26, an intermediate chamber 27, an intermediate heat exchanger 23, an evaporator 25, a first throttling device 22, and a second throttling device 24. Both the first throttling device 22 and the second throttling device 24 can be expansion valves, etc. The working principle of this auxiliary cooling system is as follows: the outlet of the condenser 3 is divided into two paths. One path (the main path) enters the inner side of the coil of the intermediate heat exchanger 23, and the other path (the branch path) is depressurized by the first throttling device 22 and enters the outer side of the coil of the intermediate heat exchanger 23, cooling the refrigerant flowing through the coil in the main path and increasing the subcooling degree of the main path refrigerant. The cooled refrigerant in the main path is depressurized by the second throttling device 24 and enters the evaporator 25 for evaporation. The evaporated refrigerant gas enters the suction port of the low-pressure compressor 26, is compressed, and then discharged to the intermediate chamber 27. After the refrigerant in the outer branch of the intermediate heat exchanger 23 coil is completely evaporated, it enters the intermediate cavity 27, mixes with the exhaust gas from the low-pressure compressor 26, and then enters the suction port of the high-pressure compressor 28. After compression, it is discharged into the condenser 3 and condensed into liquid refrigerant, thus completing the entire cycle. Throughout the cycle, the evaporator 25 and the cooling unit 29 complete heat exchange in the evaporator 25, achieving cooling of the terminal heat load.

[0050] To achieve the function of the aforementioned reflux structure, in some implementations, such as Figure 2As shown, the aforementioned reflux structure may include a first reflux channel 4, which is connected in parallel with the exhaust channel 2. The aforementioned condenser 3 has a heat exchange channel 31, which is connected in series with the first reflux channel 4. Specifically, the aforementioned reflux structure guides a portion of the exhaust gas from the exhaust channel 2 into the heat exchange channel 31 through the first reflux channel 4, so as to absorb the condensation heat released by the condenser 3 through the heat exchange channel 31. The reflux structure also guides the gas that has absorbed the condensation heat to the first reflux port 21 and flows into the exhaust channel 2 through the first reflux channel 4.

[0051] The condenser 3 has a condensation channel 32. The refrigerant in the auxiliary cooling system flows through the condensation channel 32 to release condensation heat. When part of the exhaust from the exhaust channel 2 flows through the heat exchange channel 31, it can exchange heat with the refrigerant in the condensation channel 32 through the heat exchange channel 31 to absorb the condensation heat released by the refrigerant.

[0052] In the above example, the first return channel 4 can be a pipe structure. The first return channel 4 introduces a portion of the exhaust gas from the exhaust channel 2 into the condenser 3 to absorb the condensation heat, and then guides the gas after absorbing the condensation heat to the first return port 21 to flow into the exhaust channel 2, thereby realizing the function of the aforementioned return structure.

[0053] In some implementations, such as Figure 2 As shown, the aforementioned refrigeration system also includes a first pump body 7, which is disposed on the first return channel 4. The first pump body 7 is used to drive the gas in the first return channel 4 to flow towards the first return port 21. Specifically, the first pump body 7 is used to drive a portion of the exhaust gas in the exhaust channel 2 into the heat exchange channel 31, and to drive the gas in the first return channel 4 that has absorbed condensation heat to flow to the first return port 21 and into the exhaust channel 2.

[0054] In the above example, the first pump body 7 can provide the power for the gas flow in the first return channel 4, which is conducive to the smooth flow of a part of the exhaust gas in the exhaust channel 2 into the heat exchange channel 31, and the gas in the first return channel 4 after absorbing the condensation heat can smoothly flow to the first return port 21 and into the exhaust channel 2.

[0055] In some embodiments, the aforementioned first return channel 4 can be opened or closed, thus allowing for de-icing based on whether the condensing heat released by the condenser 3 is needed. Specifically, when ice blockage occurs in the exhaust channel 2, the first return channel 4 can be opened; otherwise, the first return channel 4 can be closed.

[0056] In some implementations, such as Figure 2As shown, the aforementioned refrigeration system may further include a heat accumulator 6, which is used to recover the condensation heat released by the condenser 3. The reflux structure is also used to allow a portion of the exhaust gas from the exhaust passage 2 to absorb the heat stored in the heat accumulator 6, and then the heat-absorbed gas is directed to the first reflux port 21 and flows into the exhaust passage 2.

[0057] In the example above, a portion of the exhaust gas from the exhaust channel 2 absorbs the heat stored in the heat accumulator 6 under the action of the reflux structure, and the temperature rises. This high-temperature gas is then drawn back into the exhaust channel 2 through the first reflux port 21, which can heat the exhaust channel 2 and alleviate the ice blockage phenomenon in the exhaust channel 2.

[0058] When the aforementioned refrigeration system is applied to an aircraft, the addition of a heat accumulator 6 can meet the aircraft's heat demand under different flight conditions, effectively preventing ice blockage while also recovering waste heat, thus greatly improving energy efficiency.

[0059] To achieve the function of the aforementioned reflux structure, in some implementations, such as Figure 2 As shown, the aforementioned reflux structure may include a second reflux channel 5, which is connected in parallel with the aforementioned exhaust channel 2. The aforementioned heat accumulator 6 has a heat release channel 62, which is connected in series with the second reflux channel 5. The reflux structure guides a portion of the exhaust gas from the exhaust channel 2 into the heat release channel 62 through the second reflux channel 5, so as to absorb the heat stored in the heat accumulator 6 through the heat release channel 62. The reflux structure also guides the heat-absorbed gas to the first reflux port 21 and into the exhaust channel 2 through the second reflux channel 5.

[0060] In the above example, the second return channel 5 can be a pipe structure. The second return channel 5 absorbs the heat stored in the heat accumulator 6 by introducing a portion of the exhaust gas from the exhaust channel 2 into the heat release channel 62 of the heat accumulator 6, and then directs the heat-absorbing gas to the first return port 21 and flows into the exhaust channel 2, thereby realizing the function of the aforementioned return structure.

[0061] In some embodiments, the aforementioned refrigeration system further includes a second pump body 10. The second pump body 10 is disposed on the second return channel 5 and is used to drive the gas in the second return channel 5 to flow towards the first return port 21. Specifically, the second pump body 10 is used to drive a portion of the exhaust gas in the exhaust channel 2 into the heat dissipation channel 62, and to drive the gas in the second return channel 5 that has absorbed heat to flow to the first return port 21 and into the exhaust channel 2.

[0062] In the above example, the second pump body 10 can provide the power for the gas flow in the second return channel 5, which is conducive to the smooth flow of a part of the exhaust gas in the exhaust channel 2 into the heat release channel 62, and the gas that has absorbed heat in the second return channel 5 can smoothly flow to the first return port 21 and into the exhaust channel 2.

[0063] In some implementations, such as Figure 2 As shown, when the refrigeration system also includes a first pump body 7, which is disposed on the first return channel 4, and the condenser 3 has a heat exchange channel 31 connected in series on the first return channel 4, the branch connected to the first pump body 7 and the heat exchange channel 31 is the first branch 41, and the heat accumulator 6 has a heat absorption channel 61, which is connected in parallel with the first branch 41, and the two can form a circulation loop.

[0064] In the above example, since the heat absorption channel 61 of the heat accumulator 6 can form a circulation loop with the heat exchange channel 31 of the condenser 3 and the first pump body 7, when the first pump body 7 is started, it can drive the gas after heat exchange through the heat exchange channel 31 to flow through the heat absorption channel 61 of the heat accumulator 6, so that the heat accumulator 6 can absorb heat and store it through the heat absorption channel 61.

[0065] In some embodiments, the aforementioned heat accumulator 6 includes a heat storage material 63, which can absorb and store heat through the heat absorption channel 61. The heat storage material 63 can also release the stored heat through the heat release channel 62.

[0066] To achieve the effect of forming a circulation loop between the aforementioned heat absorption channel 61 and the first branch 41, in some embodiments, such as... Figure 2 As shown, the aforementioned first return channel 4 may have a drain port 402 and a second return port 401. The drain port 402 may be directly connected to the aforementioned exhaust port 22, and the second return port 401 may be directly connected to the aforementioned first return port 21. The first return channel 4 introduces a portion of the exhaust gas from the exhaust channel 2 through the drain port 402, and introduces the gas after heat exchange with the refrigerant to the first return port 21 and flows into the exhaust channel 2 through the second return port 401. The end of the aforementioned heat absorption channel 61 and the first branch 41 connected in parallel is the first end 403, and the other end of the parallel connection is the second end 404. The refrigeration system of the present invention also includes a first switching valve 8 and a second switching valve 9. The first switching valve 8 is disposed in the channel between the first end 403 and the second return port 401, and the second switching valve 9 is disposed in the channel between the second end 404 and the drain port 402.

[0067] In the above example, when both the first switching valve 8 and the second switching valve 9 are closed, the first pump body 7 is turned on, which allows the heat absorption channel 61 and the first branch 41 to form a circulation loop, thereby achieving the effect of the aforementioned heat absorption channel 61 and the first branch 41 forming a circulation loop.

[0068] In some embodiments, the aforementioned heat absorption channel 61 and heat release channel 62 are the same channel, which simplifies the structure and reduces the cost of the heat accumulator 6.

[0069] Among them, such as Figure 2 As shown, the channel between the first end 403 and the second return port 401 is the first channel segment 42. The first return channel 4 and the second return channel 5 can share the first channel segment 42, which simplifies the structure of the first return channel 4 and the second return channel 5 and reduces costs.

[0070] like Figure 2 As shown, the channel between the aforementioned second end 404 and the drainage port 402 is the second channel segment 43. The aforementioned first return channel 4 and second return channel 5 can share this second channel segment 43, which simplifies the structure of the first return channel 4 and the second return channel 5 and reduces costs.

[0071] In some embodiments, the aforementioned second return channel 5 can be opened or closed, thus allowing for de-icing based on whether the heat stored in the accumulator 6 is needed. Specifically, the second return channel 5 can be opened when ice blockage occurs in the exhaust channel 2; otherwise, it can be closed.

[0072] To achieve the effect of opening or closing the aforementioned second return channel 5, in some embodiments, such as Figure 2 As shown, when the refrigeration system further includes a first pump body 7, which is disposed on the first return channel 4, and the condenser 3 has a heat exchange channel 31 connected in series on the first return channel 4, and the branch connecting the first pump body 7 and the heat exchange channel 31 is the first branch 41, and the heat accumulator 6 has a heat absorption channel 61 connected in parallel with the first branch 41, the heat absorption channel 61 is located on the second branch section 51 of the second return channel 5, and the heat absorption channel 61 is connected in parallel with the aforementioned first branch 41 through the second branch section 51. The refrigeration system also includes a third switching valve 11, which is disposed on the second branch section 51 to control the opening or closing of the second return channel 5.

[0073] In some embodiments, when the aforementioned heat absorption channel 61 and heat release channel 62 are the same channel, and the refrigeration system further includes a second pump body 10, the second pump body 10 is disposed on the second branch section 51, and the refrigeration system further includes a fourth switching valve 12, which is disposed on the first branch 41.

[0074] In the above example, the second pump body 10, the first switching valve 8, the second switching valve 9, the third switching valve 11, and the fourth switching valve 12 work together to allow the second return channel 5 to be opened independently, so that the second return channel 5 can use the heat stored in the heat accumulator 6 to heat and de-ice the exhaust channel 2. Specifically, when it is necessary to use the heat from the heat accumulator 6 to heat and de-ice the exhaust channel 2 independently, the first switching valve 8, the second switching valve 9, and the third switching valve 11 can be opened, and the fourth switching valve 12 can be closed. At this time, the first return channel 4 is closed, allowing the second return channel 5 to be opened independently, so that the heat from the heat accumulator 6 can be used independently to heat and de-ice the exhaust channel 2.

[0075] In some embodiments, the aforementioned first switching valve 8, second switching valve 9, third switching valve 11 and fourth switching valve 12 may all be solenoid valves, etc.

[0076] The present invention also provides a control method for the above-mentioned refrigeration system. When the refrigeration system further includes another condenser 13, the exhaust passage 2 exhausts through the condensation passage 131 of the other condenser; and the first return passage 4 has a drain port 402 and a second return port 401, one end of the heat absorption passage 61 and the first branch 41 connected in parallel is the first end 403, and the other end of the two connected in parallel is the second end 404; the refrigeration system further includes a first switching valve 8 and a second switching valve 9, the first switching valve 8 being disposed in the passage between the first end 403 and the second return port 401, and the second switching valve 9 being disposed in the passage between the second end 404 and the drain port 402, the aforementioned control method includes:

[0077] When the refrigeration system is applied to an aircraft and the aircraft is in the climb or cruise phase, if the pressure difference between the two ends of the condensation channel 131 of the other condenser is less than a preset value, the first switch valve 8 and the second switch valve 9 are closed, the third switch valve 11 and the fourth switch valve 12 are opened, and the first pump body 7 or the second pump body 10 is activated; otherwise, the first switch valve 8, the second switch valve 9 and the fourth switch valve 12 are opened, the third switch valve 11 is closed, and the first pump body 7 is activated.

[0078] In the above example, when the aircraft is in the climb or cruise phase, the auxiliary cooling system is under a large load and generates more waste heat. If there is no ice blockage in the exhaust passage 2, that is, the pressure difference between the two ends of the condensation passage 131 of the other condenser is less than the preset value, the excess condensation heat can be stored in the heat accumulator 6. That is, the first switch valve 8 and the second switch valve 9 are closed, the third switch valve 11 and the fourth switch valve 12 are opened, and the first pump body 7 or the second pump body 10 is turned on. At this time, the heat absorption passage 61 of the heat accumulator and the heat exchange passage 31 of the condenser form a circulation loop. After the gas absorbs the condensation heat of the condenser 3, it releases heat when it flows through the heat absorption passage 61 of the heat accumulator. The heat accumulator 6 absorbs the heat and stores it. If there is ice blockage in the exhaust passage 2, i.e., the pressure difference between the two ends of the condensation passage 131 of the other condenser is greater than or equal to the preset value, then the exhaust passage 2 needs to be heated and de-iced using the waste heat of condensation. That is, the first switch valve 8, the second switch valve 9 and the fourth switch valve 12 are opened, the third switch valve 11 is closed, and the first pump body 7 is turned on. The first pump body 7 drives a part of the exhaust gas in the exhaust passage 2 to flow into the heat exchange passage 31 of the condenser to absorb the condensation heat. Then, the gas after absorbing the condensation heat flows along the first return passage 4 to the first return port 21 and flows into the exhaust passage 2 to heat and de-ic the exhaust passage 2.

[0079] When the refrigeration system is applied to an aircraft and the aircraft is in the ground or landing operation phase, if the pressure difference between the two ends of the condensation channel 131 of the other condenser is greater than or equal to a preset value, the first switch valve 8, the second switch valve 9 and the third switch valve 11 are opened, the fourth switch valve 12 is closed, and the second pump body 10 is turned on; otherwise, at least one of the first switch valve 8 and the second switch valve 9 is closed.

[0080] In the above example, when the aircraft is on the ground or during landing operations, the load on the auxiliary cooling system is relatively small. If ice blockage occurs in exhaust passage 2 (i.e., the pressure difference between the two ends of the condenser passage 131 of the other condenser is greater than or equal to a preset value), the heat stored in the heat accumulator 6 needs to be used to de-ice exhaust passage 2. This involves opening the first switch valve 8, the second switch valve 9, and the third switch valve 11, closing the fourth switch valve 12, and activating the second pump body 10. The second pump body 10 then drives a portion of the exhaust from exhaust passage 2 into the heat release passage 62 of the heat accumulator to absorb the heat stored in the heat accumulator 6. The heated gas then flows along the second return passage 5 to the first return port 21 and back into exhaust passage 2, heating and de-icing exhaust passage 2. If there is no ice blockage in exhaust passage 2 (i.e., the pressure difference between the two ends of the condenser passage 131 of the other condenser is less than a preset value), exhaust passage 2 will discharge normally. This means that at least one of the first switch valve 8 and the second switch valve 9 will be closed, thus closing both the first return passage 4 and the second return passage 5.

[0081] The control method described above enables the heat storage in the heat accumulator 6 to meet the heat requirements under different flight conditions.

[0082] It should be noted that the aforementioned refrigeration system may include a differential pressure sensor 14 to detect the pressure difference between the two ends of the condensation channel 131 of another condenser. In a specific application example, the aforementioned preset value can be 5~9 kPa.

[0083] The refrigeration system of the present invention makes full use of the condensation waste heat in the auxiliary cooling system to provide heat to the air at turbine outlet 1, thereby heating the cold air at turbine outlet 1. In addition, a heat accumulator 6 is added to meet the heat demand of the aircraft under different flight conditions. While effectively preventing ice blockage, it also realizes waste heat recovery, which greatly improves energy utilization efficiency.

[0084] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0085] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A refrigeration system characterized by: The air circulation machine, the auxiliary cooling system and the backflow structure are included. The air circulation machine has a turbine outlet (1) connected with an exhaust passage (2); the exhaust passage has an exhaust port (22) and a first backflow port (21); wherein, along the exhaust direction of the exhaust passage (2), the first backflow port (21) is located on the upstream side of the exhaust port (22). The auxiliary cooling system has a condenser (3). The backflow structure is used for absorbing the condensation heat released by the condenser (3) by part of the exhaust of the exhaust passage (2), and then introducing the gas after absorbing the condensation heat into the exhaust passage (2) at the first backflow port (21). The backflow structure includes a first backflow passage (4) connected with the exhaust passage (2) in parallel; the condenser (3) has a heat exchange passage (31) connected in series on the first backflow passage (4). The backflow structure introduces part of the exhaust of the exhaust passage (2) into the heat exchange passage (31) through the first backflow passage (4) to absorb the condensation heat released by the condenser (3) through the heat exchange passage (31); the backflow structure also introduces the gas after absorbing the condensation heat into the exhaust passage (2) at the first backflow port (21) through the first backflow passage (4).

2. The refrigeration system of claim 1, wherein: A first pump body (7) is further included, which is arranged on the first backflow passage (4) and used for driving the gas in the first backflow passage (4) to flow to the first backflow port (21).

3. The refrigeration system according to claim 1 or 2, characterized in that: The first backflow passage (4) can be opened or closed.

4. The refrigeration system of any of claims 1-2, wherein: A heat accumulator (6) is further included, which is used for recovering the condensation heat released by the condenser (3); The backflow structure is further used for absorbing the heat stored in the heat accumulator (6) by part of the exhaust of the exhaust passage (2), and then introducing the gas after absorbing the heat into the exhaust passage (2) at the first backflow port (21).

5. The refrigeration system according to claim 4, characterized in that: The backflow structure includes a second backflow passage (5) connected with the exhaust passage (2) in parallel; The heat accumulator (6) has a heat release passage (62) connected in series on the second backflow passage (5); The backflow structure introduces part of the exhaust of the exhaust passage (2) into the heat release passage (62) through the second backflow passage (5) to absorb the heat stored in the heat accumulator (6) through the heat release passage (62); the backflow structure also introduces the gas after absorbing the heat into the exhaust passage (2) at the first backflow port (21) through the second backflow passage (5).

6. The refrigeration system of claim 5, wherein: The second pump body (10) is arranged on the second return channel (5) and is used to drive the gas in the second return channel (5) to flow to the first return port (21).

7. The refrigeration system of claim 5 or 6, wherein: When the refrigeration system further comprises a first pump body (7) arranged on the first return channel (4), and the condenser (3) has a heat exchange channel (31) connected in series on the first return channel (4), the first pump body (7) and the heat exchange channel (31) are connected to a first branch (41), the heat storage device (6) has a heat absorption channel (61) connected in parallel with the first branch (41) and capable of forming a circulation loop.

8. The refrigeration system according to claim 7, wherein: the first return channel (4) has a diversion port (402) and a second return port (401), the first return channel (4) introduces a part of the exhaust gas of the exhaust channel (2) through the diversion port (402) and introduces the gas after heat exchange with the refrigerant to the first return port (21) to flow into the exhaust channel (2) through the second return port (401); the heat absorption channel (61) and the first branch (41) are connected in parallel at a first end (403) and a second end (404); the refrigeration system further comprises a first switch valve (8) arranged on a channel between the first end (403) and the second return port (401) and a second switch valve (9) arranged on a channel between the second end (404) and the diversion port (402).

9. The refrigeration system of claim 8, wherein: the heat absorption channel (61) and the heat release channel (62) are the same channel; wherein, the first return channel (4) and the second return channel (5) share the first channel segment (42) between the first end (403) and the second return port (401); and / or, the second end (404) and the diversion port (402) share the second channel segment (43) between the second end (404) and the diversion port (402).

10. The refrigeration system according to any one of claims 5-6, 8-9, wherein: the second return channel (5) is openable or closable.

11. The refrigeration system according to claim 10, wherein: When the refrigeration system further comprises a first pump body (7), the first pump body (7) is arranged on the first return channel (4), the condenser (3) has a heat exchange channel (31) connected in series on the first return channel (4), the first pump body (7) is connected with a first branch (41) of the heat exchange channel (31), the heat storage device (6) has a heat absorption channel (61) connected in parallel with the first branch (41), the heat absorption channel (61) is arranged on a second branch section (51) of the second return channel (5), the heat absorption channel (61) is connected in parallel with the first branch (41) through the second branch section (51), wherein the refrigeration system further comprises a third switch valve (11) arranged on the second branch section (51) to control opening or closing of the second return channel (5).

12. The refrigeration system of claim 11, wherein: When the heat absorption channel (61) and the heat release channel (62) are the same channel, and the refrigeration system further comprises a second pump body (10), the second pump body (10) is arranged on the second branch section (51), and the refrigeration system further comprises a fourth switch valve (12) arranged on the first branch (41).

13. A control method for the refrigeration system of claim 12, characterized in that, When the refrigeration system further comprises another condenser (13), the exhaust channel (2) exhausts through a condensing channel (131) of the another condenser, the first return channel (4) has a flow guide port (402) and a second return port (401), one end of the heat absorption channel (61) and the first branch (41) connected in parallel is a first end (403), and the other end connected in parallel is a second end (404), the refrigeration system further comprises a first switch valve (8) and a second switch valve (9), the first switch valve (8) is arranged on a channel between the first end (403) and the second return port (401), and the second switch valve (9) is arranged on a channel between the second end (404) and the flow guide port (402), the control method comprises: When the refrigeration system is applied to an airplane, and the airplane is in a climbing or cruising operation stage, if a pressure difference between two ends of the condensing channel (131) of the another condenser is less than a preset value, the first switch valve (8) and the second switch valve (9) are closed, the third switch valve (11) and the fourth switch valve (12) are opened, and the first pump body (7) or the second pump body (10) is started; otherwise, the first switch valve (8), the second switch valve (9) and the fourth switch valve (12) are opened, the third switch valve (11) is closed, and the first pump body (7) is started. And / or, when the refrigeration system is applied to an airplane, and the airplane is in the ground or landing operation stage, if the pressure difference between the two ends of the condensing channel (131) of the other condenser is greater than or equal to a preset value, the first switch valve (8), the second switch valve (9) and the third switch valve (11) are opened, the fourth switch valve (12) is closed, and the second pump body (10) is started; otherwise, at least one of the first switch valve (8) and the second switch valve (9) is closed.

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