A heat exchange device

Abstract

This invention relates to a heat exchange device, comprising a frame and an inner liner. The inner liner is rotatably mounted on the frame and includes an outer wall and an inner wall. The inner liner has multiple non-communicating convection chambers along its circumference, each containing a first working fluid. Each convection chamber is equipped with a baffle to divide it into two sub-chambers. Gaps exist between the baffles and both the inner and outer walls, allowing the two sub-chambers to communicate through these gaps. The emissivity of the outer wall facing one sub-chamber is unequal to that of the outer wall facing the other sub-chamber. This heat exchange device breaks free from the Carnot cycle limitation, overcomes the energy efficiency limitations of traditional devices, offers significant drag reduction optimization potential, and achieves a significantly higher COP than traditional devices. The difference in emissivity between the outer walls of the two sub-chambers creates a localized circumferential temperature difference near the gaps, spontaneously forming a stable Bénard circulation within the convection chambers. This enables the unpowered autonomous circulation of the first working fluid, eliminating the need for additional energy-consuming components such as circulation pumps and compressors, thus reducing costs and losses.

Description

Technical Field

[0001] This invention relates to the field of heat exchanger technology, and more particularly to a heat exchanger. Background Technology

[0002] Currently, mainstream refrigeration and heating equipment, including vapor compression, absorption, adsorption, and Stirling systems, are all based on the Carnot cycle and its variants in terms of thermodynamics. The Carnot cycle sets a theoretical limit for the efficiency of heat engines (including refrigerators), known as the Carnot efficiency. The operating efficiency of refrigeration and heating equipment is strictly constrained by the Carnot efficiency, and the actual COP (Coefficient of Performance) can never exceed this Carnot efficiency.

[0003] While the concept of traditional centrifugal refrigeration has been proposed for some time, it has always been considered a form of Carnot cycle implementation in rotating machinery. Its core understanding is that the work done by the motor is used to compress the gas, thus its efficiency has always been considered limited by Carnot efficiency. For example, Chinese patent CN101636621B (invention title "Process and apparatus for transferring heat from a first medium to a second medium") proposes a device that uses a rotating drum to generate a radial temperature gradient for heat transfer. This patent creates a temperature gradient by rotating a large amount of compressible fluid (such as xenon gas). The pressure gradient generated by the rotation is used to drive a secondary thermodynamic cycle (such as a steam cycle) to generate work. Essentially, this still utilizes the temperature difference between a high-temperature heat source and a low-temperature heat source to do work, still following the basic framework of a Carnot cycle or steam cycle, and the overall efficiency remains constrained by Carnot efficiency.

[0004] Therefore, there is an urgent need for a heat exchange device to solve the above-mentioned technical problems. Summary of the Invention

[0005] The purpose of this invention is to provide a heat exchange device to at least solve one of the above-mentioned problems.

[0006] To achieve the above objectives, the present invention provides a heat exchange device, comprising: frame; The inner liner is rotatably mounted on the frame. The inner liner includes an outer wall and an inner wall. The inner liner has multiple non-communicating convection cavities along its circumference. Each convection cavity contains a first working fluid. Each convection cavity is fan-shaped and has a partition to divide it into two sub-cavities. The partition is not connected to the outer wall and the inner wall, so that the two sub-cavities can be connected. The emissivity of the outer wall facing one sub-cavity is not equal to the emissivity of the outer wall facing the other sub-cavity in the same convection cavity.

[0007] Furthermore, a first coating is provided on the outer wall of one of the sub-cavities facing each other, and a second coating is provided on the outer wall of the other sub-cavity within the same convection cavity facing each other; the emissivity of the first coating and the second coating are not equal; or, One of the chambers has a first coating on its outer wall facing the other, and the outer wall of the other chamber in the same convection cavity is polished.

[0008] Furthermore, a heat exchange channel is provided in the axial region of the inner liner. The heat exchange channel is a cooling end, and air can circulate in the heat exchange channel.

[0009] Furthermore, the heat exchange channel includes multiple circumferentially distributed branch channels, which are inclined from the axis of the inner liner to the outer wall of the inner liner along the air flow direction.

[0010] Furthermore, the inner liner also includes a first end cap and a second end cap, the first end cap being connected to the outer wall and the inner wall respectively, the second end cap being connected to the outer wall and the inner wall respectively, and the flow channel being formed on the first end cap, the partition and the second end cap.

[0011] Furthermore, the heat exchange device also includes an airflow drive component, the heat exchange channel has an air inlet and an air outlet, and the airflow drive component is disposed on the air inlet.

[0012] Furthermore, the heat exchange device also includes a housing, which is fixedly installed on the frame, and an inner liner is disposed inside the housing. A sealed heat-conducting cavity is formed between the housing and the inner liner, and a second working fluid is disposed inside the heat-conducting cavity.

[0013] Furthermore, the second working medium is hydrogen.

[0014] Furthermore, the outer shell has a heat transfer cavity in which a third working fluid flows.

[0015] Furthermore, the heat exchange device includes a seal, which is disposed between the outer shell and the inner liner.

[0016] The beneficial effects of this invention are as follows: The heat exchange device provided by the present invention includes a frame and an inner liner. The inner liner is rotatably mounted on the frame and includes an outer wall and an inner wall. The inner liner has multiple non-communicating convection chambers along its circumference. A first working fluid is provided in each convection chamber. Each convection chamber is fan-shaped and has a baffle plate to divide the convection chamber into two sub-chambers. The baffle plate is not connected to the inner wall and the outer wall, that is, there are gaps between the baffle plate and the inner wall and the outer wall so that the two sub-chambers can be connected through the gaps. The emissivity of the outer wall facing one sub-chamber is not equal to the emissivity of the outer wall facing the other sub-chamber.

[0017] The inner tank rotates at high speed on the frame, and a stable and conservative centrifugal force field is formed in multiple convection chambers of the inner tank. A radial temperature gradient is spontaneously formed, with high pressure and high temperature in the area near the outer wall and low pressure and low temperature in the axial area (the area near the inner wall). This radial temperature gradient is maintained by the conservation of angular momentum. Maintaining the temperature gradient does not consume additional work. Except for the acceleration phase when the inner tank is establishing the centrifugal field, the driving source that drives the rotation of the inner tank does not participate in the compression work of the first working fluid. This heat exchange device is free from the Carnot cycle limitation, breaks through the energy efficiency limitation of traditional refrigeration and heating devices, has a large space for drag reduction and optimization, and the actual operating COP (Coefficient of Performance) is much higher than that of traditional refrigeration and heating devices. The difference in emissivity between the outer walls of the two chambers creates a local circumferential temperature difference in the gaps near the outer walls. This local circumferential temperature difference spontaneously forms a stable Bénard circulation within the convection chamber, enabling the unpowered autonomous circulation of the first working fluid. In other words, the self-driven circulation of the first working fluid is enhanced by relying on the radiative temperature difference, eliminating additional energy-consuming components such as circulation pumps and compressors, resulting in a simpler structure and reduced costs and losses. Attached Figure Description

[0018] Figure 1 This is a perspective view of the heat exchange device provided in an embodiment of the present invention; Figure 2 This is a cross-sectional view of the heat exchange device provided in an embodiment of the present invention. Figure 1 ; Figure 3 This is a partial structural diagram of the inner liner provided in an embodiment of the present invention; Figure 4 yes Figure 3 A magnified view of a section at point A in the middle; Figure 5 This is a cross-sectional view of the heat exchange device provided in an embodiment of the present invention. Figure 2 ; Figure 6 This is a side view of the heat exchange device provided in an embodiment of the present invention; Figure 7 This is a perspective view of the heat exchange device provided in an embodiment of the present invention from another angle.

[0019] In the picture: 1. Frame; 11. First support; 12. Second support; 13. Base plate; 2. Inner liner; 21. Convection chamber; 211. Dividing chamber; 212. Gap; 22. Outer wall; 23. Inner wall; 24. First end cap; 25. Second end cap; 26. Partition plate; 27. Chamber plate; 28. Ring plate; 29. ​​Connecting plate; 3. First coating; 4. Second coating; 5. Heat exchange channel; 51. Flow channel; 52. Air inlet; 53. Exhaust port; 6. Airflow drive components; 7. Outer shell; 71. Heat transfer chamber; 72. Liquid inlet; 73. Liquid outlet; 74. Filling port; 75. Shaft hole; 8. Heat-conducting cavity; 9. Sealing components; 10. Shaft; 20. Bearings. Detailed Implementation

[0020] The technical solution of the present invention will be further described below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, only the parts relevant to the present invention are shown in the accompanying drawings, not all of them.

[0021] This invention defines certain directional terms. Unless otherwise stated, the directional terms used, such as "up," "down," "left," "right," "inner," and "outer," are used for ease of understanding and therefore do not constitute a limitation on the scope of protection of this invention.

[0022] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0023] In the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0024] like Figures 1-7As shown, this embodiment provides a heat exchange device for cooling or heating. The heat exchange device includes a frame 1 and an inner liner 2, which is rotatably mounted on the frame 1. The inner liner 2 includes an outer wall 22 and an inner wall 23. The inner liner 2 has multiple non-communicating convection chambers 21 along its circumference. A first working fluid is provided in each convection chamber 21. Each convection chamber 21 is fan-shaped, and each convection chamber 21 is provided with a baffle 26 to divide the convection chamber 21 into two sub-chambers 211. The baffle 26 is not connected to the inner wall 23 and the outer wall 22, that is, there is a gap 212 between the baffle 26 and the inner wall 23 and the outer wall 22, so that the two sub-chambers 211 are connected through the gap 212. The emissivity of the outer wall 22 facing one sub-chamber 211 is not equal to the emissivity of the outer wall 22 facing the other sub-chamber 211.

[0025] Furthermore, the heat exchange device also includes a drive source that drives the inner tank 2 to rotate.

[0026] The inner liner 2 rotates at high speed and uniform speed on the frame 1. Stable and conservative centrifugal force fields are formed in the multiple convection chambers 21 of the inner liner 2, and a radial temperature gradient is spontaneously formed with high pressure and high temperature in the outer edge region (the region near the outer wall 22) and low pressure and low temperature in the axial region (the region near the inner wall 23). The heat in the outer edge region of the inner liner 2 is used for heating, and the heat in the axial region is used for cooling. The radial temperature gradient is maintained by the conservation of angular momentum. Maintaining the temperature gradient does not consume additional work. Except during the acceleration phase when the inner tank 2 is establishing the centrifugal field, the driving source that drives the inner tank 2 to rotate does not participate in the compression work of the first working fluid. This heat exchange device is free from the Carnot cycle limitation, breaks through the energy efficiency limitation of traditional refrigeration and heating devices, has a large space for drag reduction optimization, and its actual operating COP (Coefficient of Performance) is much higher than that of traditional refrigeration and heating devices. The difference in emissivity of the outer walls 22 corresponding to the two sub-cavities 211 will generate a local circumferential temperature difference in the gap 212 near the outer walls 22. This local circumferential temperature difference will spontaneously form a stable Bénard circulation in the convection cavity 21, realizing the unpowered autonomous circulation of the first working fluid. That is, the self-driven circulation of the first working fluid is enhanced by the radiation temperature difference. The Bénard circulation can achieve efficient heat exchange, improve heat exchange efficiency, eliminate additional energy-consuming components such as circulation pumps and compressors, simplify the structure, and reduce costs and losses.

[0027] If there is no difference in emissivity on the outer wall 22 of the inner liner 2, the rotation of the inner liner 2 creates a radial temperature gradient within the convection cavity 21. Due to the viscosity of the first working fluid and the Coriolis force, a Bénard circulation can naturally occur. However, a Bénard circulation may not form between the two sub-cavities 211. The first working fluid forms a Bénard circulation within its own sub-cavity 211. That is, the logarithm of the Bénard circulation may not be the same as the number of convection cavities 21, resulting in a smaller range and lower circulation intensity. The difference in emissivity on the outer wall 22 of the inner liner 2 causes a difference in heat dissipation of the first working fluid through the outer wall 22, creating a localized circumferential temperature difference in the gap 212 near the outer wall 22. The combined effect of the radial and circumferential temperature gradients causes the first working fluid to form a Bénard circulation in the two sub-cavities 211 within the same convection cavity 21. The logarithm of the Bénard circulation is the same as the number of convection cavities 21, expanding the range and increasing the circulation intensity of the Bénard circulation.

[0028] When the inner liner 2 rotates at high speed and uniform speed on the frame 1, the temperature T of the first working fluid at any radius position is calculated according to the following formula: In the formula, T is the temperature of the first working fluid at any radius position of the inner liner 2. m T0 is the highest temperature of the first working fluid in the outer edge region of the inner liner 2, T0 is the lowest temperature of the first working fluid in the axial region of the inner liner 2, M is the relative molecular mass of the first working fluid, ω is the rotational speed of the inner liner 2, i is the molecular degree of freedom of the first working fluid, R is the gas constant, and r0 is the lowest temperature of the first working fluid in the axial region of the inner liner 2. m Let r be the maximum diameter of inner liner 2, r be the radius at the calculated temperature, and r0 be the minimum diameter of inner liner 2.

[0029] The above formula can be modified to obtain: As can be seen from the above variation, the maximum radial temperature difference of the first working fluid inside the inner liner 2 is positively correlated with the rotational speed ω of the inner liner 2 and also positively correlated with the relative molecular mass M of the first working fluid. That is, the greater the rotational speed ω of the inner liner 2, the greater the maximum radial temperature difference of the first working fluid inside the inner liner 2; the smaller the rotational speed ω of the inner liner 2, the smaller the maximum radial temperature difference of the first working fluid inside the inner liner 2. Similarly, the greater the relative molecular mass M of the first working fluid, the greater the maximum radial temperature difference of the first working fluid inside the inner liner 2; the smaller the relative molecular mass M of the first working fluid, the smaller the maximum radial temperature difference of the first working fluid inside the inner liner 2.

[0030] The rotational speed ω of the inner tank 2 directly determines the intensity of the centrifugal field. By adjusting the rotational speed ω of the inner tank 2, the intensity of the centrifugal field is changed, thereby controlling the temperature of the axial region or the outer edge region: the higher the rotational speed ω of the inner tank 2, the more significant the radial temperature and pressure gradient, the lower the temperature of the axial region, the higher the temperature of the outer edge region, and the stronger the cooling power of the axial region / heating power of the outer edge region; the lower the rotational speed ω of the inner tank 2, the gentler the radial temperature and pressure gradient, the closer the temperature of the axial region is to the ambient temperature, and the more moderate the power.

[0031] When the heat exchange device provided in this embodiment is used for heating, the heat in the outer edge region is utilized, while the axial region is prone to frost formation due to low temperature, affecting heat exchange efficiency. When frost formation is severe, reducing the rotation speed of the inner liner 2 weakens the centrifugal field, and the high-temperature heat from the outer edge of the inner liner 2 is transferred to the axial region through the first working fluid circulation. Especially when the rotation speed of the inner liner 2 is low enough, the temperature in the axial region approaches the ambient temperature, thus achieving defrosting. After defrosting, increasing the rotation speed of the inner liner 2 allows the heat exchange device to continue normal operation. In other words, the normal operation mode and the defrosting mode are achieved by adjusting the rotation speed of the inner liner 2.

[0032] The heat exchange device provided in this embodiment can achieve temperature control and defrosting functions simply by adjusting the rotation speed of the inner tank 2. Temperature control no longer relies on complex sensors and valve adjustments, and defrosting does not require additional electric auxiliary heating or defrosting mechanisms. This eliminates the need for additional control and defrosting mechanisms, simplifies the control logic, solves the dual shortcomings of traditional processing and control methods, and reduces energy consumption and failure rate.

[0033] During defrosting control, a preset running time is set. When the heat exchanger runs for the preset time, it automatically enters the defrosting mode. Alternatively, the degree of frost can be indirectly determined by a simple pressure sensor. When the degree of frost reaches the preset defrosting value, the speed of the inner tank 2 is automatically reduced, and the defrosting mode is entered. After defrosting is completed, the speed of the inner tank 2 is automatically increased to resume normal operation. The entire process is completed automatically.

[0034] Since a larger relative molecular mass M of the first working fluid results in a larger maximum radial temperature difference within the inner liner 2, and a smaller relative molecular mass M results in a smaller maximum radial temperature difference, a gas with a relatively large molecular mass should be selected as the first working fluid to increase the radial temperature difference. Factors such as the working temperature, chemical stability, non-toxicity or low toxicity, environmental friendliness, and procurement cost of the first working fluid must also be considered. Under the selected operating conditions, a larger relative molecular mass M of the first working fluid is better. Based on these comprehensive considerations, a fluorine-containing macromolecular gas is selected as the first working fluid.

[0035] The specific type of working medium used varies depending on the operating temperature range. For example, when the operating temperature range is above 0°C, perfluoropropane and trifluoroiodomethane can be chosen as the primary working medium because their boiling points are around -20°C. Both perfluoropropane and trifluoroiodomethane are gases within the operating temperature range, with trifluoroiodomethane having the widest operating temperature range and being the most environmentally friendly gas in terms of relative molecular mass (M). Alternatively, when perfluorobutane is used as the primary working medium, its boiling point is around 0°C, and its optimal operating temperature range is above 10°C.

[0036] The primary working fluid is a low-GWP (Low Global Warming Potential) environmentally friendly macromolecular refrigerant, which poses no risk of ozone layer depletion and has no media emissions throughout the entire process, making it more green and environmentally friendly.

[0037] like Figures 1-5 As shown, the inner liner 2 also includes a first end cap 24 and a second end cap 25. The first end cap 24 is connected to the outer wall 22 and the inner wall 23 respectively, and the second end cap 25 is connected to the outer wall 22 and the inner wall 23 respectively to form a hollow cavity. The hollow cavity is used to divide into multiple convection chambers 21.

[0038] Specifically, the inner liner 2 also includes multiple chamber plates 27, each extending radially and connected to the first end cap 24, the second end cap 25, the inner wall 23, and the outer wall 22, respectively. A convection cavity 21 is formed between adjacent chamber plates 27. Since there are no gaps between the chamber plates 27 and the outer wall 22 and inner wall 23, the convection cavities 21 are not interconnected. More specifically, the chamber plates 27 are uniformly arranged circumferentially along the inner liner 2, ensuring that the multiple convection cavities 21 have the same size. The chamber plates 27 restrict the flow of the first working fluid within its assigned convection cavity 21, preventing it from circumferentially moving into other convection cavities 21, thus forcing the first working fluid to flow axially and radially within its assigned convection cavity 21.

[0039] The convection cavity 21 is completely sealed and filled with a first working fluid. The first working fluid flows only within the convection cavity 21. After the first working fluid is filled into the convection cavity 21, it is permanently sealed with no exposed interfaces and no need for replenishment of the first working fluid, achieving lifetime maintenance-free and zero-leakage operation, thus improving the service life and stability of the inner liner 2. After the inner liner 2 is formed, it undergoes airtightness testing and helium leak testing. First, a vacuum is drawn, and after the first working fluid is quantitatively filled, the sealing holes are permanently sealed to ensure long-term airtightness within the convection cavity 21, preventing leakage of the first working fluid from affecting the Bénard circulation and heat exchange.

[0040] Furthermore, the heat exchange device also includes a rotating shaft 10, with the inner liner 2 mounted on the rotating shaft 10. The rotating shaft 10 is rotatably mounted on the frame 1, and a drive source drives the rotating shaft 10 to rotate, thereby causing the inner liner 2 to rotate.

[0041] Specifically, the rotating shaft 10 and the inner liner 2 are integrally formed.

[0042] Furthermore, the inner liner 2 also includes a connecting plate 29, which is annular. The outer contour of the connecting plate 29 is connected to the inner wall 23, and the inner contour of the connecting plate 29 is connected to the outer wall 22 of the rotating shaft 10.

[0043] Specifically, there are two connecting plates 29, which are flush with the first end plate and the second end plate, respectively, to increase the connection strength.

[0044] Furthermore, the frame 1 includes a base plate 13 and a first support 11, the first support 11 being disposed on the base plate 13, and the rotating shaft 10 being disposed on the first support 11.

[0045] Furthermore, the heat exchange device also includes a bearing 20, the outer ring of which is connected to the first support 11, and the inner ring of which is connected to the rotating shaft 10.

[0046] To create a difference in emissivity on the outer walls 22, a first coating 3 is applied to the outer wall 22 facing one of the sub-cavities 211, and a second coating 4 is applied to the outer wall 22 facing the other sub-cavity 211 within the same convection cavity 21. The emissivity of the first coating 3 and the second coating 4 are not equal; or, One of the sub-cavities 211 has a first coating 3 on its outer wall 22 facing it, and the surface of the outer wall 22 facing the other sub-cavity 211 in the same convection cavity 21 is polished.

[0047] When the inner liner 2 is made of metal, a first coating 3 is provided on the outer wall 22 facing one of the compartments 211, and the surface of the outer wall 22 facing the other compartment 211 within the same convection cavity 21 is polished, resulting in a difference in the emissivity of the outer walls 22 of the two compartments 211 within the same convection cavity 21. Specifically, the first coating 3 is a graphene coating, and the inner liner 2 is preferably a magnesium alloy or an aluminum alloy.

[0048] The first coating 3 and the second coating 4 are set at the same time, so that the surface properties of the outer wall 22 of the inner liner 2 are relatively uniform, which reduces the friction between the inner liner 2 and the second working fluid (mentioned below), extends the service life of the inner liner 2, reduces losses, and improves heat exchange efficiency.

[0049] To increase the intensity of the Bernard circulation, the greater the difference in emissivity between the first coating 3 and the second coating 4, the better.

[0050] Furthermore, the first coating 3 is one or more combinations of carbon-based nanomaterials, transition metal oxides (such as spinel oxides), carbides (such as silicon carbide), borides, or inorganic micro / nano particles (such as titanium dioxide, barium sulfate, and silicon dioxide). The carbon-based nanomaterials can be graphene or carbon nanotubes, the transition metal oxides can be spinel oxides, the carbides can be silicon carbide, and the inorganic micro / nano particles can be titanium dioxide, barium sulfate, or silicon dioxide. The second coating 4 is a metallic material, a doped semiconductor material, a two-dimensional transition metal carbide / nitride, etc.

[0051] Specifically, the first coating 3 is preferably a graphene coating with an emissivity of 0.9-0.98. The second coating 4 is a polished metal coating, preferably made of white metal and polished, specifically polished aluminum alloy with an emissivity of 0.02-0.1. This results in a significant difference in the emissivity of the first coating 3 and the second coating 4, making the temperature difference in the gap 212 near the outer edge of the inner liner 2 more pronounced, forming a circumferential temperature difference, so as to form selective radiation-induced Bénard circulation.

[0052] The two coatings are precisely sprayed in separate zones with neat boundaries, ensuring a stable difference in emissivity between the paired convection cavities 21. The two coatings are designed to withstand high temperatures, resist aging, and have good adhesion, making them suitable for long-term high-speed operation. At the same time, they prevent the two coatings from peeling off, which would affect the circulation intensity.

[0053] In this embodiment, the distribution of the two coatings corresponding to different convection cavities 21 is not limited. The first coating 3 and the second coating 4 can be arranged alternately on the outer wall 22, or other arrangements can be used, as long as the two coatings corresponding to the same convection cavity 21 have a difference in emissivity.

[0054] Furthermore, a heat exchange channel 5 is provided in the axial region of the inner liner 2. The heat exchange channel 5 is the cooling end, and air can circulate within it. The heat exchange channel 5 absorbs heat from the air, and the cooled air is then sent into the cooling space to achieve cooling.

[0055] Furthermore, the heat exchange channel 5 includes multiple circumferentially distributed branch channels 51, which are inclined from the axis of the inner liner 2 toward the outer wall 22 of the inner liner 2 along the air flow direction. The inclined arrangement of the branch channels 51, combined with the high-speed rotation of the inner liner 2, facilitates the direct removal of condensate and defrost water generated during the heat exchange process from the axial area along the air flow direction, avoiding water accumulation that affects heat exchange efficiency. At the same time, it eliminates the need for an additional defrosting mechanism, simplifying the structure.

[0056] Furthermore, the inclination angle of the diversion channel 51 is 1°-3°. By setting an inclination angle of 1°-3°, gravity can be used to allow condensate or defrost water to flow naturally to the lower point, preventing water accumulation and corrosion of the diversion channel 51, and preventing blockage of the diversion channel 51. The inclination angle of 1°-3° ensures effective drainage without affecting the airflow speed, and the additional resistance to the airflow is minimal, preventing airflow turbulence and reducing the overall energy consumption of the diversion channel 51.

[0057] Furthermore, the diversion channel 51 is formed on the first end cover 24, the partition 26, and the second end cover 25. The location of the diversion channel 51 is ingenious. Instead of being directly formed between the inner wall 23 and the rotating shaft 10, the diversion channel 51 is formed on the partition 26 and located at the axial center of the partition 26. This allows the diversion channel 51 to share a wall surface with the convection cavity 21. The first working fluid in the convection cavity 21 can directly exchange heat with the air in the diversion channel 51 through this wall surface, reducing heat exchange loss and improving heat exchange efficiency. Moreover, the fact that the diversion channel 51 is formed on the partition 26 increases the heat exchange area between the first working fluid and the air, further improving heat exchange efficiency.

[0058] The flow channels 51 are formed on the baffle plate 26, so that each flow channel 51 corresponds to the convection cavity 21. The heat exchange in each flow channel 51 does not affect each other, which shortens the heat exchange path, reduces the loss in the heat exchange process, and improves the heat exchange efficiency.

[0059] Furthermore, the heat exchange device also includes an airflow drive 6. The heat exchange channel 5 has an air inlet 52 and an air outlet 53. The airflow drive 6 is disposed on the air inlet 52 and is used to draw air into the heat exchange channel 5.

[0060] Furthermore, the airflow drive 6 can also be provided on the exhaust port 53 to deliver air out of the heat exchange channel 5.

[0061] Specifically, the airflow drive component 6 is a fan. The fan blades guide the airflow into the heat exchange channel 5, reducing airflow resistance and energy consumption.

[0062] Specifically, the airflow drive component 6 is integrally formed with the rotating shaft 10. The rotation of the rotating shaft 10 drives the airflow drive component 6 to rotate, eliminating the need for a separate fan to drive the airflow drive component 6. The airflow drive component 6 autonomously drives air to pass through the heat exchange channel 5, directly convecting the air for heat exchange, reducing heat exchange losses. The air directly contacts the inner liner 2 for heat exchange, eliminating intermediate heat exchange links, reducing multi-stage heat exchange losses, and lowering thermal resistance losses.

[0063] Specifically, the condensate and defrost water generated during the heat exchange process in the distribution channel 51 are thrown out of the heat exchange channel 5 from the exhaust port 53 to ensure smooth airflow. At the same time, centrifugal force is used to quickly throw out the condensate and defrost water to avoid water accumulation affecting heat exchange.

[0064] Furthermore, the inner liner 2, rotating shaft 10, airflow drive component 6, and heat exchange channel 5 are all integrally formed through additive manufacturing. Additive manufacturing can perfectly realize the complex integrated structure of the thin-walled and thin-shell inner liner 2, the internal baffle 26 and chamber plate 27 of the inner liner 2, the gap 212 connecting the two flow chambers, and the heat exchange channel 5 with a small angle gradient. This eliminates the risk of weld leakage, controls the amount of deformation of the inner liner 2 caused by welding, accurately ensures the gradient angle of the flow channel, meets the requirements of high-speed rotation dynamic balance, sealed pressure bearing, and centrifugal water ejection, and greatly improves the structural reliability.

[0065] Of course, other conventional manufacturing methods can also be used, and this embodiment does not limit this to any particular method.

[0066] After the inner liner 2, rotating shaft 10, airflow drive component 6 and heat exchange channel 5 are additively formed, the whole is subjected to high-precision dynamic balancing correction to match the stepless speed regulation condition of 3000-12000rpm, control vibration and noise, and ensure stable operation of the equipment at different speeds.

[0067] The shell wall thickness is determined by strength. Under the premise of meeting the strength requirements, the smaller the shell wall thickness, the smaller the overall self-weight and rotational inertia, which reduces the load and friction loss of the bearing 20 under high-speed rotation, thereby reducing the overall resistance coefficient and improving COP.

[0068] The inner liner is made of a lightweight, high-strength, and thermally conductive material, such as aluminum alloy.

[0069] Furthermore, the drive source adopts a variable frequency motor directly coupled to the shaft 10, supporting stepless speed regulation and adapting to temperature control and defrosting requirements. Before leaving the factory, the speed, shaft temperature, and defrosting effect of the variable frequency motor are calibrated, and the speed range and defrosting speed threshold under different operating conditions are preset to ensure simple control logic, reliable operation, and no need for on-site debugging. The rated speed range of the variable frequency motor is 3000~12000rpm.

[0070] like Figure 1 , Figure 2 , Figures 5-7 As shown, the heat exchange device also includes a housing 7, which is fixedly mounted on the frame 1. An inner liner 2 is disposed inside the housing 7, and a sealed heat-conducting cavity 8 is formed between the housing 7 and the inner liner 2. A second working fluid is disposed inside the heat-conducting cavity 8. The heat from the outer edge region of the inner liner 2 is transferred to the housing 7 through the second working fluid, and the housing 7 is used for heating.

[0071] Furthermore, the frame 1 also includes a second support 12, which is mounted on the base plate 13, and the outer casing 7 is mounted on the second support 12 to support the outer casing 7.

[0072] The uniform gap between the outer wall 22 of the inner liner 2 and the outer shell 7 forms the aforementioned heat-conducting cavity 8. The size of the gap is 2mm-5mm, and the heat-conducting cavity 8 is filled with a second working fluid. A slight positive pressure is maintained inside the heat-conducting cavity 8 to prevent air infiltration, which would increase wind resistance and affect the stability of the rotation speed.

[0073] When selecting a secondary working fluid, it is necessary to consider the resistance generated by the rotation of the inner liner 2, as well as the thermal conductivity and procurement cost of the secondary working fluid. The secondary working fluid needs to balance the triple requirements of drag reduction, heat exchange, and low procurement cost. Therefore, hydrogen, methane, or helium are chosen as the secondary working fluid.

[0074] Preferably, the second working fluid is hydrogen. Hydrogen has the highest thermal conductivity, approximately 0.163~0.174 W / (m·K), which is more than 7 times that of air. The low density and low viscosity of hydrogen can significantly reduce the wind resistance loss of the high-speed rotating inner liner 2 (frictional resistance or viscous resistance, which is about 1 / 14 of air resistance). Simultaneously, relying on convection combined with radiation-induced circulating heat transfer, a composite heat transfer path is constructed, simultaneously addressing the triple requirements of drag reduction, heat exchange, and low procurement cost. Furthermore, although helium's thermal conductivity is slightly lower than hydrogen's, its wind resistance is about 1 / 7 of air resistance, significantly higher than hydrogen's, and its procurement cost is also higher. Methane's thermal conductivity is also lower than hydrogen's, but helium's wind resistance is about 0.56 times that of air, significantly higher than hydrogen's. Therefore, filling with hydrogen is the optimal choice among drag reduction, heat exchange, and low procurement cost.

[0075] If zero resistance is the ultimate goal, vacuuming is the best option. However, heat cannot be conducted through gas in a vacuum; heat can only be transferred through radiation, resulting in extremely low heat dissipation efficiency. Furthermore, vacuuming consumes more energy and requires a higher level of sealing. Therefore, choosing hydrogen as the second working medium is the optimal choice among drag reduction, heat exchange, and low procurement costs.

[0076] Furthermore, a filling port 74 is provided on the outer shell 7, which is connected to the heat conduction cavity 8 for filling the heat conduction cavity 8 with a second working fluid.

[0077] Furthermore, the outer shell 7 has a heat transfer cavity 71, in which a third working fluid flows.

[0078] Furthermore, the third working fluid is water, which needs to be softened before entering the outer casing 7 for circulation, in order to prevent the third working fluid from forming scale inside the outer casing 7 and reducing the heat exchange efficiency.

[0079] Furthermore, the outer casing 7 is provided with a liquid inlet 72 and a liquid outlet 73, both of which are connected to the heat transfer cavity 71.

[0080] Furthermore, the liquid inlet 72 is located at the lower part of the outer shell 7, and the liquid outlet 73 is located at the upper end of the outer shell 7. That is, the circulation of the third working fluid adopts a counter-current layout of bottom inlet and top outlet, which enhances the heat dissipation / heat collection capacity of the outer edge and ensures that the heat transfer cavity 71 of the outer shell 7 is always filled with cooling water, avoiding air stagnation and facilitating exhaust.

[0081] Furthermore, the outer casing 7 is made of aluminum alloy, which has high thermal conductivity, reducing heat loss.

[0082] To further improve heat exchange efficiency, a first coating 3 is provided on the outer wall 22 of the outer shell 7 facing the inner liner 2. The first coating 3 on the outer shell 7 has high emissivity and is used in conjunction with the inner liner 2 with the first coating 3 to further improve heat conduction efficiency and reduce heat loss.

[0083] In order to make the surface properties of the outer wall 22 of the outer shell 7 facing the inner liner 2 relatively uniform, reduce the friction between the outer shell 7 and the second working fluid, extend the service life of the outer shell 7, reduce losses, and improve heat exchange efficiency, a second coating 4 can also be provided on the outer wall 22 of the outer shell 7 facing the inner liner 2. The second coating 4 on the outer shell 7 is opposite to the second coating 4 provided on the inner liner 2, and the thickness of the first coating 3 and the second coating 4 on the outer shell 7 is the same, so as to ensure that the surface properties of the outer wall 22 of the outer shell 7 facing the inner liner 2 are relatively uniform.

[0084] Furthermore, an insulation layer is provided on the outer side of the outer casing 7 to avoid unnecessary heat and cold losses.

[0085] Furthermore, the heat exchange device includes a seal 9, which is provided between the outer shell 7 and the inner liner 2. The seal 9 makes the heat conduction cavity 8 relatively closed, thereby improving the heat exchange efficiency between the inner liner 2 and the outer shell 7.

[0086] Specifically, the inner liner 2 also includes an annular plate 28. The first end cap 24 and the second end cap 25 are both provided with an annular plate 28. The outer shell 7 is provided with a shaft hole 75, which communicates with the heat conduction cavity 8. The annular plate 28 and the shaft hole 75 are sealed by a sealing element 9 so that the heat conduction cavity 8 is relatively closed, thereby improving the heat exchange efficiency between the inner liner 2 and the outer shell 7.

[0087] Furthermore, the rotating shaft 10 passes through the shaft hole 75, and its two ends extending out of the outer casing 7 are respectively connected to the first bracket 11.

[0088] Apart from the acceleration phase of establishing the centrifugal field of the inner liner 2, all the energy consumption of the drive source is used only to overcome wind resistance, friction of bearing 20, sealing resistance, and micro-flow resistance of the working fluid. The energy efficiency is determined by mechanical resistance, wind resistance, flow loss and heat exchange efficiency.

[0089] To reduce wind resistance, an airflow drive component 6 is installed on the air inlet 52. The fan blades of the airflow drive component 6 guide the airflow into the heat exchange channel 5, reducing the airflow resistance and thus reducing the energy consumption of the drive source.

[0090] To minimize the frictional resistance of the bearing 20, the bearing 20 is preferably a magnetic levitation bearing 20 or a high-precision ceramic low-friction bearing 20, thereby reducing the energy consumption of the drive source.

[0091] Since the inner liner 2 rotates while the outer shell 7 remains stationary, the seal 9 and the shaft hole 75 of the outer shell 7 form a static seal, while the seal 9 and the annular plate 28 of the inner liner 2 form a dynamic seal. The static seal requirement is met by the seal 9 pressing against the shaft hole 75 of the outer shell 7. For the dynamic seal, a non-contact labyrinth seal and / or a magnetohydrodynamic seal are selected. The non-contact labyrinth seal increases fluid leakage resistance through a multi-stage meandering flow channel design, rather than blocking flow through solid contact. With no solid contact, no lubrication is required, resulting in extremely low frictional resistance. The magnetohydrodynamic seal is a non-contact dynamic seal that uses a gradient magnetic field to confine the magnetohydrodynamic fluid in the gap between the annular plate 28 and the shaft hole 75, forming a liquid sealing barrier. There is no solid friction, and the frictional torque is only 1 / 10 of that of a contact seal, significantly reducing energy consumption. This sealing method ensures good sealing performance while also reducing sealing resistance.

[0092] To reduce the flow resistance of the working fluid, the first working fluid is preferably a fluorine-containing gas, and the second working fluid is preferably hydrogen.

[0093] The heat exchange device provided in this embodiment can be used as a refrigeration device or a heating device. According to the target temperature of the refrigeration / heat pump, the motor is set to a corresponding speed range. After the speed stabilizes, the temperature of the shaft area can be maintained within the target range. There is no need for complex sensor feedback adjustment. Only a fixed speed range needs to be set according to the target temperature.

[0094] When the heat exchange device provided in this embodiment is used as a refrigeration device, the heat exchange device is generally located in an indoor space. The third working fluid in the heat transfer chamber 71 of the outer shell 7 is connected to the outdoor heat dissipation module. The high-temperature heat in the outer edge region of the inner liner 2 is transferred to the third working fluid through the Bénard circulation and the heat exchange of the second working fluid, and is finally discharged to the outdoor environment. The low temperature in the axial region of the inner liner 2 directly cools the indoor air flowing through it, thereby achieving indoor cooling. The specific operation steps are as follows: The motor drives the inner tank 2 to rotate at a set speed, creating a stable radial temperature gradient in the centrifugal field. This lowers the temperature in the axial region of the inner tank 2. Indoor air is drawn into the heat exchange channel 5 by the fan blades and directly exchanges heat with the wall of the partition plate 26 located in the axial region of the inner tank 2. After cooling, the air is discharged from the exhaust port 53, achieving indoor cooling. The high-temperature heat in the outer edge region of the inner tank 2 is transferred to the third working fluid through the Bénard circulation and the second working fluid. The third working fluid then discharges the heat to the atmosphere through an external radiator. The Bénard circulation drives the first working fluid to circulate continuously, maintaining a long-term low temperature in the axial region of the inner tank 2. Under the combined action of the inclined heat exchange channel 5 and centrifugal force, the condensate generated during the heat exchange process is directly thrown away from the shaft center without the need for additional drainage. When the indoor temperature needs to be adjusted, simply adjust the motor speed: higher speed increases cooling capacity, while lower speed decreases cooling capacity.

[0095] When the heat exchange device provided in this embodiment is used as a heating device, the heat exchange device is generally located in the outdoor environment. The third working fluid in the heat transfer chamber 71 of the outer shell 7 is connected to the indoor heating water system. The low-temperature airflow in the axial region of the inner tank 2 absorbs the residual heat of the outdoor air, and the high-temperature heat in the outer edge region of the inner tank 2 is transported to the room through the heating water system to achieve stable indoor heating. The specific operating steps are as follows: The motor drives the inner tank 2 to rotate at high speed according to the set speed. The centrifugal field forms a stable radial temperature gradient, and the temperature of the axial region of the inner tank 2 decreases and is lower than that of the outdoor environment. Outdoor air is drawn into the heat exchange channel 5 by the fan blades and directly exchanges heat with the wall of the partition 26 located in the axial region of the inner tank 2. The heat of the outdoor air is absorbed by the first working fluid. After the outdoor air cools down, it is sent out from the exhaust port 53. The first working fluid continuously enriches the absorbed heat to the outer edge region of the inner tank 2 through the Bénard circulation. The high temperature heat in the outer edge region of the inner tank 2 is transferred to the third working fluid through the Bénard circulation and the heat exchange of the second working fluid. The third working fluid continuously supplies heat to the room through the indoor heating water circuit to achieve indoor heating. When the outdoor temperature is too low, the core area is prone to frost formation, which affects the heat exchange efficiency. When the frost formation reaches the point where defrosting is required, the motor speed is automatically reduced, the centrifugal field strength is weakened, and the high temperature heat from the outer edge of the inner tank 2 is transferred to the core area. The residual heat from the core area of ​​the inner tank 2 is used to defrost. After defrosting is completed, the motor speed is automatically increased, and the melted frost water is thrown out from the exhaust port 53 by relying on centrifugal force and the inclined design of the heat exchange channel 5, and the equipment resumes normal heating operation. When it is necessary to adjust the indoor heating temperature, simply adjust the motor speed: higher speed increases heating capacity, while lower speed decreases heating capacity.

[0096] The internal structure, circulation direction, and rotation logic of the heat exchanger are completely identical under both operating conditions. Only the installation location and the purpose of the external water circuit need to be changed to switch between refrigeration and heat pump operating conditions. The heat exchanger does not need to be modified, so that the heat exchanger can both cool and heat, reducing the cost of use.

[0097] The rated COP of the heat exchange device provided in this embodiment under different setting conditions is shown in Table 1 below: Table 1 Rated COP of heat exchangers under different setup conditions

[0098] As shown in Table 1, even with different setting conditions, the rated COP of the heat exchange device provided in this embodiment is above 17. In contrast, the operating efficiency of conventional refrigeration or heating equipment in the prior art is strictly constrained by the Carnot efficiency. The COP of conventional refrigeration or heating equipment in the prior art is generally less than 4, and rarely reaches 6. By comparison, the rated COP of the heat exchange device provided in this embodiment is much higher than the COP of conventional refrigeration or heating equipment in the prior art. That is, the heat exchange device provided in this embodiment is free from the Carnot cycle limitation, and its actual operating COP (Coefficient of Performance) is much higher than that of traditional refrigeration and heating devices.

[0099] It should be noted that the rated COP of the heat exchange device provided in this embodiment is affected by many factors, and the rated COP in Table 1 is a typical value.

[0100] Although the present invention has been described in detail above with general descriptions, specific embodiments, and experiments, modifications or improvements can be made to it, which will be obvious to those skilled in the art. Therefore, all such modifications or improvements made without departing from the spirit of the present invention fall within the scope of protection claimed by the present invention.

Claims

1. A heat exchange device, characterized in that, include: Rack (1); The inner liner (2) is rotatably mounted on the frame (1). The inner liner (2) includes an outer wall (22) and an inner wall (23). The inner liner (2) has multiple non-communicating convection cavities (21) along its circumference. The convection cavities (21) contain a first working fluid. Each convection cavity (21) is fan-shaped. Each convection cavity (21) is provided with a partition (26) to divide the convection cavity (21) into two sub-cavities (211). There are gaps (212) between the partition (26) and the outer wall (22) and the inner wall (23) so that the two sub-cavities (211) are connected through the gaps (212). The emissivity of the outer wall (22) facing one of the sub-cavities (211) is not equal to the emissivity of the outer wall (22) facing the other sub-cavity (211) in the same convection cavity (21).

2. The heat exchange device according to claim 1, characterized in that, One of the sub-cavities (211) has a first coating (3) on its outer wall (22) facing the other, and the other sub-cavity (211) in the same convection cavity (21) has a second coating (4) on its outer wall (22) facing the other. The emissivity of the first coating (3) and the second coating (4) are not equal; or, One of the sub-cavities (211) has a first coating (3) on its outer wall (22) facing it, and the surface of the outer wall (22) facing the other sub-cavity (21) in the same convection cavity (21) is polished.

3. The heat exchange device according to claim 1, characterized in that, The inner liner (2) has a heat exchange channel (5) in its axial region. The heat exchange channel (5) is a cooling end and air can circulate in the heat exchange channel (5).

4. The heat exchange device according to claim 3, characterized in that, The heat exchange channel (5) includes a plurality of circumferentially distributed branch channels (51), which are inclined from the axis of the inner liner (2) toward the outer wall (22) of the inner liner (2) along the air flow direction.

5. The heat exchange device according to claim 4, characterized in that, The inner liner (2) also includes a first end cap (24) and a second end cap (25). The first end cap (24) is connected to the outer wall (22) and the inner wall (23) respectively. The second end cap (25) is connected to the outer wall (22) and the inner wall (23) respectively. The diversion channel (51) is opened on the first end cap (24), the partition (26) and the second end cap (25).

6. The heat exchange device according to claim 3, characterized in that, The heat exchange device further includes an airflow drive (6), the heat exchange channel (5) has an air inlet (52) and an exhaust port (53), and the airflow drive (6) is disposed on the air inlet (52).

7. The heat exchange device according to claim 1, characterized in that, The heat exchange device also includes a shell (7), which is fixedly installed on the frame (1). The inner liner (2) is located inside the shell (7). A sealed heat-conducting cavity (8) is formed between the shell (7) and the inner liner (2). A second working fluid is provided in the heat-conducting cavity (8).

8. The heat exchange device according to claim 7, characterized in that, The second working medium is hydrogen.

9. The heat exchange device according to claim 7, characterized in that, The outer shell (7) has a heat transfer cavity (71) in which a third working fluid flows.

10. The heat exchange device according to claim 7, characterized in that, The heat exchange device includes a seal (9), which is provided between the outer shell (7) and the inner liner (2).

Images