A heat exchanger based on textured flow channels and microchannels

Abstract

The present invention discloses a heat exchanger based on textured flow channels and microchannels. The heat exchanger based on textured flow channels and microchannels includes a fixed tube, a heat exchange tube, a drive module, a deformation module and a heat exchange module: a plurality of heat exchange tubes are distributed in parallel and are all connected to the fixed tube; the drive module includes a drive motor and a screw, and the screw is connected to the drive motor by transmission; the deformation module is connected to the screw by transmission and the movement direction is parallel to the extension direction of the screw; the heat exchange module includes a support ring, a slip ring and a heat exchange component, the support ring is fixedly connected to the heat exchange tube, the slip ring is connected to the deformation module by transmission and the movement direction is parallel to the extension direction of the heat exchange tube, and the heat exchange component is rotatably connected to the support ring and is connected to the slip ring by transmission. In the embodiment of the present application, the deformation module is linked with the heat exchange module, and the heat exchange component realizes deformation from fixed to outward expansion, which prolongs the frosting time; enhances disturbance, increases heat exchange efficiency; and improves the reliability, heat dissipation and stability of the heat exchanger.

Description

Technical Field

[0001] The present invention relates to the field of heat exchange technology, and in particular to a heat exchanger based on textured flow channels and microchannels. Background Art

[0002] Heat exchangers are devices that generate and output cooling in refrigeration systems. Their heat exchange efficiency directly impacts the performance and economic efficiency of the refrigeration unit. Fin-and-tube heat exchangers are the most commonly used in unitary air conditioning units. Microchannel heat exchangers used in cooling and heating systems improve heat exchange efficiency. Their tiny channels allow for more uniform refrigerant flow within the heat exchanger, thereby increasing heat transfer efficiency. This design enables the heat exchanger to absorb and release heat more efficiently, improving cooling and heating performance.

[0003] In the prior art, although heat exchange can be achieved through heat exchange microchannels, the fins are fixed in place during the heat exchange process. Therefore, it is difficult to achieve large-area displacement heat exchange during heat exchange, the heat exchange flow area is small, the heat exchange efficiency is greatly reduced, and frost and other phenomena will occur as the use time increases. The above problems seriously limit the development of microchannel heat exchangers in the field of refrigeration and heating, and thus a heat exchanger structure combining textured flow channels and fish-scale microchannels has been invented. At the same time, most of the heat exchangers containing fins today are single vertically inserted fixed fins. The fins and tubes are integrated, and the fin shape is mostly a whole piece. Although the secondary surface is expanded and the heat transfer resistance is reduced, there is also a problem of weak disturbance of the external gas, which makes the boundary layer thicker, resulting in weak mixing of the cold and hot fluids, resulting in reduced heat transfer performance of the fluid along the flow direction. Therefore, this patent proposes and constructs fins with different micro-textured flow channels on the inside and outside. The fluid enhances the disturbance through the microchannels, so that the thermal boundary layer can be periodically interrupted and redeveloped, thereby maximizing the use of the fin space to enhance heat exchange.

[0004] In summary, the existing heat exchanger has the technical problem of difficulty in achieving large-area displacement heat exchange, small heat exchange flow area, significant decrease in heat exchange efficiency, and frost occurring as the use time increases. Summary of the Invention

[0005] The purpose of this application is to overcome the above-mentioned technical deficiencies and propose a heat exchanger based on textured flow channels and microchannels to solve the technical problems in the existing technology that it is difficult to achieve large-area displacement heat exchange during heat exchange, the heat exchange flow area is small, the heat exchange efficiency is greatly reduced, and frosting will occur with increasing use time.

[0006] In order to achieve the above technical objectives, this application adopts the following technical solutions:

[0007] The present application provides a heat exchanger based on textured flow channels and microchannels, including a fixed tube, a heat exchange tube, a drive module, a deformation module, and a heat exchange module:

[0008] Fixed pipe;

[0009] a heat exchange tube, wherein a plurality of the heat exchange tubes are distributed in parallel and are all connected to the fixed tube;

[0010] A drive module, comprising a drive motor and a screw, wherein the drive motor is in driving connection with the screw;

[0011] A deformation module, wherein the deformation module is in driving connection with the screw, and the screw drives the deformation module to reciprocate along the screw;

[0012] The heat exchange module includes a support ring, a slip ring and a heat exchange component. The support ring is fixedly connected to the heat exchange tube, the slip ring is transmission-connected to the deformation module, the deformation module drives the slip ring to reciprocate along the heat exchange tube, the heat exchange component is rotationally connected to the support ring and transmission-connected to the slip ring, the slip ring drives one end of the heat exchange component to move away from or toward the heat exchange tube, and the other end of the heat exchange component rotates around the support ring as the axis.

[0013] In some embodiments of the present application, the deformation module includes a sleeve recess, a first sleeve rod, a push plate and a push rod. The sleeve recess is connected to the screw rod in a transmission manner and the movement direction is parallel to the extension direction of the screw rod. The first sleeve rod is rotatably connected to the sleeve recess through a connecting shaft. The push plate is rotatably connected to the first sleeve rod through a push shaft. The movement direction of the push rod is parallel to the extension direction of the heat exchange tube.

[0014] In some embodiments of the present application, a frame plate is further included, wherein the frame plate is fixedly connected to one side of the fixed tube, and the inner wall of the frame plate is rotatably connected to the screw rod.

[0015] In some embodiments of the present application, the number of the heat exchange modules is multiple groups, and the multiple heat exchange tubes are arranged in sequence and at equal intervals, and each group of the heat exchange modules is evenly sleeved on one of the heat exchange tubes.

[0016] In some embodiments of the present application, the multiple heat exchange modules on two adjacent heat exchange tubes are staggered.

[0017] In some embodiments of the present application, a diverter pipe is further included, which is arranged opposite to the fixed pipe and is respectively connected to the plurality of heat exchange pipes.

[0018] In some embodiments of the present application, the heat exchange assembly includes a support rod, a second set of rods, a push rod, an inner heat exchange fin, a hinged sleeve and a support rod, the support rod is fixedly connected to the slip ring, one end of the second set of rods is rotatably connected to the support rod, the push rod is rotatably connected to the other end of the second set of rods, the inner heat exchange fin is fixedly connected to the push rod, the support rod is fixedly connected to the support ring, and the hinged sleeve is rotatably connected to the support rod and fixedly connected to the inner heat exchange fin.

[0019] In some embodiments of the present application, textured channels are provided on the inner and outer surfaces of the inner heat exchange fins, the textured channels include a plurality of mutually staggered sub-channels, and the textured channels include a circular micro-column texture.

[0020] In some embodiments of the present application, the heat exchange assembly also includes a linkage push rod, a third set of rods, a push shaft, an external heat exchange fin, a sleeve rotating block and a support shaft. The linkage push rod is fixedly connected to the slip ring, the third set of rods is rotatably connected to the linkage push rod, the external heat exchange fin and the slip ring respectively, the push shaft is rotatably connected to the third set of rods, the external heat exchange fin is fixedly connected to the push shaft, the sleeve rotating block is fixedly connected to the external heat exchange fin, and the support shaft is rotatably connected to the sleeve rotating block and fixedly connected to the support ring.

[0021] In some embodiments of the present application, textured channels are provided on the inner and outer surfaces of the external heat exchange fins, and the textured channels include a plurality of mutually staggered sub-channels, and the textured channels include rectangular, triangular, and diamond-shaped micro-column textures.

[0022] Compared with the existing technology, the technical solution provided by this application brings the following beneficial technical effects:

[0023] The embodiment of the present application links the deformation module with the heat exchange module, so that the internal and external heat exchange components can be deformed from fixed to outward expansion, thereby extending the frosting time; enhancing the disturbance, thereby increasing the heat exchange efficiency; achieving a breakthrough application of microchannel heat exchange, realizing large-area displacement heat exchange, and significantly improving the reliability, heat dissipation and stability of the microchannel heat exchanger in the field of refrigeration and heating. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the technical solutions in this application, the following briefly introduces the drawings required for use in the embodiments:

[0025] Figure 1 Schematic diagram of the structure of a heat exchanger based on textured flow channels and microchannels provided in an embodiment of the present application;

[0026] Figures 2A and 2B This is a structural diagram of a deformation module provided in an embodiment of the present application;

[0027] Figures 3A and 3B This is a schematic structural diagram of a heat exchange module provided in an embodiment of the present application;

[0028] Figures 4A and 4B This is a schematic structural diagram of a heat exchange assembly provided in an embodiment of the present application;

[0029] Figures 5A and 5B This is a schematic structural diagram of a textured flow channel provided in an embodiment of the present application;

[0030] Figures 6A and 6B This is a temperature distribution cloud diagram of a heat exchange component provided in an embodiment of the present application;

[0031] Figures 7A and 7B This is a velocity distribution cloud diagram of a heat exchange component provided in an embodiment of the present application;

[0032] Figures 8A to 8C This is a temperature distribution cloud, velocity distribution cloud map, and streamline map of a heat exchange component at different opening angles provided in an embodiment of the present application.

[0033] Reference numerals:

[0034] 1-fixed tube, 2-heat exchange tube, 3-drive motor, 4-screw, 5-support ring, 6-slip ring, 7-sleeve recess, 8-connecting shaft, 9-first set of rods, 10-push shaft, 11-push plate, 12-push rod, 13-frame plate, 14-diverter pipe, 15-support rod, 16-second set of rods, 17-push rod, 18-inner heat exchange fin, 19-hinge sleeve, 20-support rod, 21-linked push rod, 22-third set of rods, 23-push shaft, 24-outer heat exchange fin, 25-sleeve rotating block, 26-support shaft. DETAILED DESCRIPTION

[0035] In order to make the purpose, technical solutions and advantages of this application more clearly understood, the present application is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this application and are not intended to limit this application.

[0036] Those skilled in the art will understand that in this specification, the wording "including" is an open-ended expression, which means that the described features exist but does not exclude other features. The directional words "up", "down", "left", "right", etc. are exemplary directions based on the drawings. Features defined as "first" and "second" implicitly include one or more of the features. Singular expressions can also be used in the plural. "Multiple" means two or more. The terms "installed", "connected", and "connected" can be fixed connections, detachable connections, or integrated connections; they can be directly connected, or indirectly connected through an intermediate medium, or they can be internal connections between two elements. In addition, "connected" can include wireless connections.

[0037] The purpose of this application is to overcome the above-mentioned technical deficiencies and propose a heat exchanger based on textured flow channels and microchannels to solve the technical problems in the existing technology that it is difficult to achieve large-area displacement heat exchange during heat exchange, the heat exchange flow area is small, the heat exchange efficiency is greatly reduced, and frosting will occur with increasing use time.

[0038] In order to achieve the above technical objectives, this application adopts the following technical solutions:

[0039] This application provides a heat exchanger based on textured flow channels and microchannels, such as Figure 1 As shown, Figure 1 This is a structural schematic diagram of a heat exchanger based on textured flow channels and microchannels provided in an embodiment of the present application.

[0040] A heat exchanger based on textured flow channels and microchannels includes a fixed tube 1, a heat exchange tube 2, a drive module, a deformation module, and a heat exchange module:

[0041] Fixed tube 1;

[0042] Heat exchange tubes 2, wherein a plurality of heat exchange tubes 2 are distributed in parallel and are all connected to the fixed tube 1;

[0043] A driving module, comprising a driving motor 3 and a screw 4, wherein the driving motor 3 is in driving connection with the screw 4;

[0044] A deformation module, the deformation module is in transmission connection with the screw 4, and the screw drives the deformation module to reciprocate along the screw 4;

[0045] The heat exchange module includes a support ring 5, a slip ring 6 and a heat exchange component. The support ring 5 is fixedly connected to the heat exchange tube 2, and the slip ring 6 is transmission-connected to the deformation module. The deformation module drives the slip ring to reciprocate along the heat exchange tube 2. The heat exchange component is rotationally connected to the support ring 5 and transmission-connected to the slip ring 6. The slip ring 6 drives one end of the heat exchange component to move away from or close to the heat exchange tube 2, and the other end of the heat exchange component rotates around the support ring 5 as the axis.

[0046] The embodiment of the present application links the deformation module with the heat exchange module, so that the internal and external heat exchange components can be deformed from fixed to outward expansion, thereby extending the frosting time; the inner and outer surfaces of the internal and external heat exchange components contain textured microchannels, which enhances the disturbance and thus increases the heat exchange efficiency; a breakthrough application of the microchannel heat exchanger is achieved, realizing large-area displacement heat exchange, and significantly improving the reliability, heat dissipation and stability of the microchannel heat exchanger in the field of refrigeration and heating.

[0047] Since the first end of the heat exchange component in this application is rotatably connected to the support ring 5 and the second end is transmission-connected to the slip ring 6, after the slip ring 6 drives the second end of the heat exchange component to expand outward, the fluid channel of the heat exchange module flows along the diversion pipe 14 to the fixed pipe 1. When the heat exchange medium passes through the second end of the previous heat exchange component and then passes through the first end of the next heat exchange component, the fluid channel presents the characteristics of a large inlet and a small outlet, thereby accelerating the flow rate of the medium in the channel, improving the heat exchange effect, and reducing the impact of the medium on the component. Among them, the Venturi effect points out that when gas or liquid flows in a Venturi tube, due to the continuity equation, the velocity reaches the maximum value and the static pressure reaches the minimum value at the narrowest point of the pipe. Based on the Bernoulli principle, when the flow is at equal height, the greater the flow rate, the smaller the pressure, which makes the heat dissipation efficiency higher and the fluid impact smaller.

[0048] like Figures 2A and 2B As shown, Figures 2A and 2B This is a structural diagram of a deformation module provided in an embodiment of the present application; Figure 2B yes Figure 2A A partial diagram of .

[0049] In some embodiments of the present application, the deformation module includes a sleeve recess 7, a first sleeve rod 9, a push plate 11 and a push rod 12. The sleeve recess 7 is transmission-connected to the screw 4 and the movement direction is parallel to the extension direction of the screw 4. The first sleeve rod 9 is rotationally connected to the sleeve recess 7 through a connecting shaft 8. The push plate 11 is rotationally connected to the first sleeve rod 9 through a push shaft 10. The movement direction of the push rod 12 is parallel to the extension direction of the heat exchange tube 2.

[0050] In some embodiments of the present application, a frame plate 13 is further included. The frame plate 13 is fixedly connected to one side of the fixed tube 1 , and the inner wall of the frame plate 13 is rotatably connected to the screw rod 4 .

[0051] In this embodiment, a frame plate 13 is welded in front of the fixed tube 1, and a screw 4 is rotatably connected to the inner wall of the frame plate 13. A drive motor 3 for driving the screw 4 to rotate is fixedly installed at the bottom end of the frame plate 13; a linkage deformation module is provided on the outer wall of the screw 4; the deformation module includes a sleeve concave block 7 threadedly arranged on the outer wall of the screw 4, and a connecting shaft 8 is welded on one side of the inner wall of the sleeve concave block 7, and a first sleeve rod 9 is rotatably connected to the outer wall of the connecting shaft 8; a push shaft 10 is rotatably connected to the inner wall of the first sleeve rod 9 near its bottom end, and the A push plate 11 is welded to one end of the push shaft 10, and a plurality of push rods 12 are fixedly connected to one side of the push plate 11 in sequence from top to bottom. A heat exchange tube 2 welded to the fixed tube 1 is provided on one side of each push rod 12, and a plurality of slip rings 6 are fixedly connected to the outer wall of the push rod 12; a plurality of support rods 15 are installed on the inner wall of the slip ring 6, and a support ring 5 is provided on one side of each slip ring 6, and the support ring 5 is fixedly connected to the heat exchange tube 2, and the outer wall of the support rod 15 is provided with an internal shape-changing heat exchange component; an external shape-changing heat exchange component is provided on one side of the support rod 15.

[0052] The slip ring 6 is fixed to the next support ring 5 by a fixing ring, so that the slip ring 6 and the support ring 5 are easy to fix and easy to remove and replace.

[0053] In some embodiments of the present application, the heat exchange modules are in multiple groups, and the multiple heat exchange tubes 2 are arranged in sequence and at equal intervals, and each group of heat exchange modules is evenly sleeved on one heat exchange tube 2.

[0054] The sleeve recess 7 is slidably connected to the frame plate 13, and the outer wall of the sleeve recess 7 and the inner wall of the frame plate 13 are polished and ground; the frame plate 13 and the sleeve recess 7 are both made of stainless steel, and the heat exchange tubes 2 are arranged in equal intervals from top to bottom, and the heat exchange tubes 2 are made of copper.

[0055] In some embodiments of the present application, the multiple heat exchange modules on two adjacent heat exchange tubes 2 are staggered.

[0056] In some embodiments of the present application, a diverter pipe 14 is further included. The diverter pipe 14 is arranged opposite to the fixed pipe 1 and is connected to the plurality of heat exchange pipes 2 respectively.

[0057] In this embodiment, the heat exchange modules are staggered to avoid interference with each other during deployment.

[0058] A diverter pipe 14 is installed at the other end of the fixed pipe 1 , and the plurality of heat exchange tubes 2 are fixedly connected to the diverter pipe 14 .

[0059] like Figures 3A and 3B As shown, Figures 3A and 3B This is a schematic structural diagram of a heat exchange module provided in an embodiment of the present application; Figure 3A In the contracted state, Figure 3B In the expanded state.

[0060] In some embodiments of the present application, the heat exchange assembly includes a support rod 15, a second set of rods 16, a push rod 17, an inner heat exchange fin 18, a hinged sleeve block 19 and a support rod 20, the support rod 15 is fixedly connected to the slip ring 6, one end of the second set of rods 16 is rotatably connected to the support rod 15, the push rod 17 is rotatably connected to the other end of the second set of rods 16, the inner heat exchange fin 18 is fixedly connected to the push rod 17, the support rod 20 is fixedly connected to the support ring 5, and the hinged sleeve block 19 is rotatably connected to the support rod 20 and fixedly connected to the inner heat exchange fin 18.

[0061] The internal shape-changing heat exchange component includes a second set of rods 16 rotatably arranged on the outer wall of the support rod 15; the inner wall of the second set of rods 16 is rotatably connected to a push rod 17 near its top end, and one end of the push rod 17 is welded with a fish-scale shaped internal heat exchange fin 18, and a hinged sleeve block 19 is fixedly installed on one side of the fish-scale shaped internal heat exchange fin 18; the inner wall of the hinged sleeve block 19 is rotatably connected to a support rod 20, and the support rod 20 is fixedly connected to the support ring 5.

[0062] like Figures 4A and 4B As shown, Figures 4A and 4B This is a schematic structural diagram of a heat exchange assembly provided in an embodiment of the present application; Figure 4A For the internal heat exchange fin 18, Figure 4B It is the external heat exchange fin 24.

[0063] In some embodiments of the present application, textured channels are provided on the inner and outer surfaces of the inner heat exchange fins 18 , and the textured channels include a plurality of mutually staggered sub-channels, and the textured channels include a circular micro-column texture.

[0064] In some embodiments of the present application, the heat exchange assembly also includes a linkage push rod 2112, a third set of rods 22, a driving shaft 23, an external heat exchange fin 24, a sleeve rotating block 25 and a support shaft 26. The linkage push rod 2112 is fixedly connected to the slip ring 6, and the third set of rods 22 is rotatably connected to the linkage push rod 2112, the external heat exchange fin 24 and the slip ring 6 respectively. The driving shaft 23 is rotatably connected to the third set of rods 22, the external heat exchange fin 24 is fixedly connected to the driving shaft 23, the sleeve rotating block 25 is fixedly connected to the external heat exchange fin 24, and the support shaft 26 is rotatably connected to the sleeve rotating block 25 and fixedly connected to the support ring 5.

[0065] The external shape-changing heat-dissipating assembly includes a linkage push rod 2112 provided on one side of the support rod 15; the linkage push rod 2112 is fixedly connected to the slip ring 6, and the outer wall of the linkage push rod 2112 is rotatably connected to the third set of rods 22;

[0066] A driving shaft 23 is rotatably connected to the inner wall of the third sleeve rod 22 near its top end, and a fish-scale-shaped external heat exchange fin 24 is fixedly installed on one end of the driving shaft 23. A sleeve rotating block 25 is welded to one side of the fish-scale-shaped external heat exchange fin 24; a support shaft 26 is rotatably connected to the inner wall of the sleeve rotating block 25, and the support shaft 26 is welded to the support ring 5.

[0067] The fish-scale external heat exchange fins 24 and the slip ring 6 are both rotatably connected to the third set of rods 22 .

[0068] When the internal shape changes heat, the slip ring 6 drives the multiple support rods 15 to move leftward. The support rods 15 carry the second set of rods 16 to move leftward, and the second set of rods 16 drives the push rod 17 to move leftward. The push rod 17 drives the fish-scale internal heat exchange fins 18 to rotate, which in turn drives the hinged sleeve 19 to rotate. The hinged sleeve 19 rotates along the outer wall of the support rod 20. With the support ring 5 supporting the support rod 20, the multiple fish-scale internal heat exchange fins 18 can achieve outward expansion and flow displacement like fish scales.

[0069] External deformation transfers heat. When the slip ring 6 moves leftward, it simultaneously drives the multiple linked push rods 2112 to the left, which in turn drives the third set of rods 22 to the left. The third set of rods 22 rotates the propeller shaft 23, which in turn rotates the fish-scale external heat exchange fins 24. The fish-scale external heat exchange fins 24, in turn, rotate the sleeve rotating block 25. The sleeve rotating block 25 rotates on the outer wall of the support shaft 26, allowing the multiple fish-scale external heat exchange fins 24 to expand and deform outward. This allows the multiple fish-scale external heat exchange fins 24 to shift position and exchange heat, expanding the heat exchange area.

[0070] The specific steps are:

[0071] Step 1: The refrigerant is diverted to the multiple heat exchange tubes 2 through the diverter tube 14 and passes through the multiple fish-scale shaped inner heat exchange fins 18 and the multiple fish-scale shaped outer heat exchange fins 24 on the heat exchange tubes 2 for heat exchange operation.

[0072] Step 2: During the linked deformation, the drive motor 3 activates the forward rotation of the screw 4. The screw 43 drives the sleeve recess 7 downward under the force of the thread transmission. The sleeve recess 7 slides down along the inner wall of the frame plate 13. Simultaneously, the sleeve recess 7 drives the connecting shaft 8 downward, and the connecting shaft 8 drives the first sleeve rod 9 downward to move the push shaft 10. The push shaft 10 carries the push plate 11 downward, and the push plate 11 drives the multiple push rods 12 to move left. The push rods 12 drive the multiple slip rings 6 to move left synchronously. The slip rings 6 slide leftward along the outer wall of the heat exchange tube 2, and the multiple slip rings 6 move left synchronously.

[0073] Step 3: When the internal shape changes heat, the slip ring 6 drives the multiple support rods 15 to move leftward. The support rods 15 carry the second set of rods 16 to move leftward, and the second set of rods 16 drives the push rod 17 to move leftward. The push rod 17 drives the fish-scale internal heat exchange fins 18 to rotate, which in turn drives the hinged sleeve 19 to rotate. The hinged sleeve 19 rotates along the outer wall of the support rod 20. With the support ring 5 supporting the support rod 20, the multiple fish-scale internal heat exchange fins 18 can achieve outward expansion and flow displacement like fish scales.

[0074] Step 4: External deformation and heat transfer: As the slip ring 6 moves leftward, it simultaneously drives the multiple linked push rods 2112 to the left, which in turn drives the third set of rods 22 to the left. The third set of rods 22 rotates the propeller shaft 23, which in turn rotates the fish-scale external heat exchange fins 24. The fish-scale external heat exchange fins 24 then rotate the sleeve rotating block 25. The sleeve rotating block 25 rotates on the outer wall of the support shaft 26, allowing the multiple fish-scale external heat exchange fins 24 to expand and deform outward. This allows the multiple fish-scale external heat exchange fins 24 to shift position and exchange heat, expanding the heat exchange area.

[0075] The plurality of support rods 15 are arranged in a circular ring at equal intervals, and the vertical cross-section shapes of the support rods 15 and the support rods 20 are both set to be circular; the plurality of fish-scale shaped internal heat exchange fins 18 are arranged in a circular ring at equal intervals, and the fish-scale shaped internal and external heat exchange fins 24 are both made of copper.

[0076] like Figures 5A and 5B As shown, Figures 5A and 5B This is a structural schematic diagram of a textured flow channel provided in an embodiment of the present application. Figure 5A is the textured flow channel of the inner fin, Figure 5B It is the textured flow channel of the outer fin.

[0077] In some embodiments of the present application, textured channels are provided on the inner and outer surfaces of the external heat exchange fins 24 , and the textured channels include a plurality of mutually staggered sub-channels, and the textured channels include rectangular, triangular, and diamond-shaped micro-column textures.

[0078] The fish-scale inner and outer heat exchange fins 24 both include textured flow channels. The inner and outer sides of the fish-scale inner heat exchange fins 18 are added with cross-V-shaped micro-channels, and the inner and outer sides of the fish-scale outer heat exchange fins 24 are added with diamond-shaped and triangular micro-channels. The flow channels are symmetrically distributed along the center of the fins. By adding textured flow channels, fluid disturbance is enhanced and the fin space is maximized to enhance heat exchange.

[0079] Regarding the choice of microtexture shape: The microchannel is generally V-shaped. ① Its unique geometry guides the fluid through multiple deflections, generating secondary flow and double vortices within the channel around the microtexture. This fluid disturbance significantly breaks up the boundary layer, enhancing convective heat transfer between the fluid and the wall, thereby improving the heat transfer coefficient. ② Compared to linear or parallel channel designs, the V-shaped channel increases the contact area between the fluid and the heat exchanger wall by changing its geometry, effectively increasing the heat transfer area per unit volume, thereby maximizing the use of the fin space for enhanced heat transfer. ③ The V-shaped structure achieves more uniform fluid distribution within the heat exchanger, reducing temperature gradients caused by local flow deviations. This uniformity optimizes the overall thermal performance of the heat exchanger and avoids efficiency losses caused by local overheating or insufficient cooling. ④ The high turbulence of the V-shaped channel prevents particles and impurities in the fluid from adhering to the channel, reducing the formation of dirt and deposits. This not only extends the maintenance cycle of the heat exchanger but also maintains high-efficiency heat transfer performance over the long term.

[0080] The outer layer is an arc-shaped fin, so the designed microtexture contains rectangular and triangular microcolumns with an inclination angle of β=70°, as well as diamond-shaped microcolumns. The inclination angle improves the heat transfer factor and friction factor compared to the vertical structure. At the same time, the rectangular, triangular and diamond-shaped microcolumns have a sharper shape, which enables them to form a stronger disturbance effect when the fluid flows. Along the entire microchannel, horseshoe-shaped vortices and wake vortices will be generated around each rectangular, diamond and triangular microcolumn. The emergence of these longitudinal structures is induced by the interaction between the primary flow and the microcolumns, which helps to break the thermal boundary layer of the fluid and enhance convective heat transfer. The efficient heat transfer enables the cold fluid to achieve the fastest heat exchange effect.

[0081] The inner fin design retains its main structure of micro-rectangular column microtextures. Considering the smaller area at the front and rear ends and the lower internal flow than the external, circular and teardrop-shaped microtextures are incorporated on both sides, while maintaining a V-shaped flow path. Due to the symmetry and uniform geometry of the circular microtextures, heat is evenly distributed across the entire surface of the fins. This uniformity helps avoid localized overheating or insufficient cooling, improving the overall thermal efficiency of the heat exchanger. Furthermore, the circular microtexture profile facilitates directing the fluid into the separation zone on the leeward side of the fins, enhancing the heat transfer capacity on the leeward side of the fins. The streamlined design of the teardrop-shaped fins significantly reduces air resistance during fluid flow. Compared to fins of other shapes, the teardrop-shaped fins taper gradually after the front fluid separation point, reducing vortex and swirl formation at the tail, resulting in lower pressure loss and a higher PEC value.

[0082] like Figures 6A and 6B As shown, Figures 6A and 6B This is a temperature distribution cloud diagram of a heat exchange component provided in an embodiment of the present application; Figure 6A (a) is the temperature distribution cloud map of the outer fin after adding texture, (b) is the temperature distribution cloud map of the outer fin before adding texture (yz plane, from top to bottom, x = 0.005, 0.006, 0.007);

[0083] Figure 6B (a) is the temperature distribution cloud map of the inner fin after adding texture, and (b) is the temperature distribution cloud map of the outer fin before adding texture (yz plane, x=0.005, 0.006, 0.007 from top to bottom).

[0084] By observing the temperature cloud map comparison, it can be found that the temperature of the area with texture is significantly lower than that without fins, and the cooling effect on the space is more significant.

[0085] Due to the presence of different types of microtextures, the thermal boundary layer is interrupted and redeveloped. Compared with the untextured fins, the turbulence intensity is significantly enhanced, and the disturbance to the surrounding fluid is enhanced, so that the fins with added microtextures have a stronger cooling effect and better temperature uniformity in space; at the same time, the presence of microtextures changes the flow of the surrounding fluid by increasing the heat transfer area, significantly improves the chaotic advection, and makes the fluid mixing between the mainstream flow area and the recirculation flow area better, thereby enhancing heat transfer, improving heat transfer efficiency, achieving a reduction in spatial temperature, and a more uniform temperature distribution.

[0086] like Figures 7A and 7B As shown, Figures 7A and 7B This is a velocity distribution cloud diagram of a heat exchange component provided in an embodiment of the present application; Figure 7A(a) (b) are velocity distribution cloud maps of the outer fin with texture (x=0.004, 0.006 respectively), (c) is the streamline diagram of the outer fin with texture at x=0.006; (d) (e) are velocity distribution cloud maps of the outer fin without texture (x=0.004, 0.006 respectively), and (f) is the streamline diagram of the outer fin without texture at x=0.006.

[0087] Figure 7B (a) (b) are the velocity distribution cloud maps of the inner fin with texture (x=0.0008, 0.00014 respectively), (c) is the streamline diagram of the outer fin with texture on the plane of x=0.00014; (d) (e) are the velocity distribution cloud maps of the inner fin without texture (x=0.0008, 0.00014 respectively), (f) is the streamline diagram of the outer fin without texture on the plane of x=0.00014.

[0088] By observing the velocity cloud map comparison, it can be seen that the introduction of micro-textures of different shapes plays a guiding role. Due to the presence of micro-texture, the fluid velocity is redistributed; and compared with the inlet, the presence of micro-texture makes the space near the inlet and outlet have a higher fluid flow rate, which brings higher turbulence intensity and promotes the development of horseshoe vortexes near the micro-textured fins.

[0089] At the same time, by observing the streamline diagrams (c) and (f), it can be found that the micro-textured fins generate more vortices than ordinary fins, and the vortex intensity is further enhanced, which further promotes the mixing of the fluid and the disturbance of the flow boundary layer, making the flow boundary layer thinner. These behaviors are conducive to enhancing heat transfer and thus improving heat transfer efficiency.

[0090] like Figures 8A to 8C As shown, Figures 8A to 8C This is a temperature distribution cloud, velocity distribution cloud map, and streamline map of a heat exchange component at different opening angles provided in an embodiment of the present application.

[0091] Figure 8A Figures 2 and 3 show the temperature distribution contours along different sections at different opening angles. Figures (a), (b), and (c) show the temperature distribution contours at sections x=0.0046, x=0.0066, and x=0.0086 when the outer fin opening angle is 20° and the inner fin opening angle is 12°, respectively. Figures (d), (e), and (f) show the temperature distribution contours at sections x=0.0046, x=0.0066, and x=0.0086 when the outer fin opening angle is 50° and the inner fin opening angle is 30°, respectively. The section x=0.0046 is closer to the cooling source, while the section x=0.0086 is farther away.

[0092] As can be seen from Figures (a)-(c), the temperature drops significantly along the direction of fluid flow around the fins, achieving a better cooling effect on the external hot air. Furthermore, the closer to the cooling source, the greater the temperature gradient, and the better the cooling effect. This is because, under the small opening angle design, the structure focuses more on the longitudinal effect, resulting in significant temperature changes along the direction of fluid flow along the fins. Simultaneously, the spanwise motion causes the thermal boundary layer to be periodically interrupted and redeveloped, and the fin microtexture enhances the fin's disturbance of the mainstream, increasing heat transfer capacity and thus promoting heat transfer. In contrast, the large opening angle design in Figures (d)-(f) exhibits a significant temperature gradient perpendicular to the flow direction, indicating that the transverse expansion structure effectively reduces fluid retention between the two layers, enhances the disturbance of the fluid as it passes through the fins, and thus promotes the mixing of hot and cold fluids, improving overall heat transfer performance. The large opening angle design further enhances the overall reduction in spatial temperature through a wider range of microtexture disturbances.

[0093] Traditional vertically inserted fins usually rely on linear cooling along the flow direction during the heat exchange process. Although this method is simple, it easily leads to a gradual increase in the thickness of the boundary layer, thereby forming a stable temperature gradient. In addition, the fluid is not sufficiently disturbed when flowing through the fins, and heat transfer is limited. Especially in the latter part of the fluid flow, stagnation areas and high-temperature areas are easily formed, affecting the overall heat exchange performance and reducing the heat exchange efficiency. The fin design with expansion function, especially when combined with micro-texture, not only significantly improves the heat transfer effect in the flow direction, but also forms a multi-dimensional flow disturbance through lateral expansion and structural complexity. This disturbance effectively breaks the continuity of the boundary layer, allowing the cold source to act more deeply on the fluid, avoiding the high-temperature stagnation phenomenon common in traditional fin designs. At the same time, the periodic disturbance brought about by the micro-texture further enhances the turbulent effect, prompting more fluid to participate in heat exchange, greatly improving the heat transfer efficiency.

[0094] Figure 8B Velocity distribution contours along different sections along x for different opening angles. (a), (b), (c), and (d) are velocity distribution contours along sections x = 0.0046, x = 0.0066, x = 0.0086, and x = 0.0106 when the outer fin opening angle is 20° and the inner fin opening angle is 12°, respectively. (e), (f), (g), and (h) are velocity distribution contours along sections x = 0.0046, x = 0.0066, x = 0.0086, and x = 0.0106 when the outer fin opening angle is 50° and the inner fin opening angle is 30°, respectively.

[0095] Regardless of the size of the expansion angle, the overall flow field maintains a high degree of symmetry. From Figures ad, we can see that as the flow section moves from x = 0.0046 to x = 0.0106, the flow field exhibits a relatively stable velocity distribution, and there is a larger velocity variation area compared to sections abc and section d. In these sections, the central area (yellow and orange areas) shows a higher velocity, while the area close to the fin surface (blue area) has a significantly lower velocity. As the fluid moves downstream, the boundary layer gradually increases. This is because section d is closer to the air outlet, so there are stronger velocity disturbances on both sides. At the same time, due to the small expansion angle, the fluid exerts a viscous force on the fin surface, causing the fluid velocity in the boundary layer to gradually slow down.

[0096] Figures eh show more complex velocity distribution patterns, particularly at the tips and sides of the fins. Due to the more tortuous flow path created by the wide aperture angle design, the fluid forms multiple localized high-speed zones on the fin surface, interspersed with low-speed zones. These low-speed zones also represent the presence of a velocity boundary layer, but unlike the narrow aperture angle design, the boundary layer distribution in the wide aperture angle design is more uneven. Specifically, as the fluid passes through the fins, the wide-angle fin structure complicates the flow path and subjects the fluid to stronger shear forces, leading to localized thinning of the boundary layer and even possible flow separation in certain areas. This fluctuating and uneven boundary layer increases the disturbance on the heat transfer surface, contributing to improved local heat transfer efficiency. In the cross-section of Figure (h), the boundary layer appears even more complex, forming multiple branching regions. This indicates that significant eddies and secondary flows are generated as the flow passes through the fins. These complex flow structures exacerbate the variations in the boundary layer, causing it to become extremely thin in certain areas, which is beneficial for enhanced heat transfer.

[0097] Figure 8C Streamline diagrams for different opening angles of the x=0.046 section. (a) Streamline diagram for the x=0.0046 section when the outer fin opening angle is 20° and the inner fin opening angle is 12°. (b) Streamline diagram for the x=0.0046 section when the outer fin opening angle is 50° and the inner fin opening angle is 30°.

[0098] From Figure (a), it can be seen that after the streamlines flow near the fin surface, a relatively high speed flow appears in the center area, while the surface area close to the fin shows a lower speed, indicating that the boundary layer has been fully developed on the fin surface. At the same time, the fluid forms local small vortices at the tip and sides of the fin. This is because the small opening angle design results in a wider flow channel and a more straight flow direction. The shear force on the fluid when entering and leaving the fin is relatively small, so the vortex formation is weak.

[0099] Figure (b) shows a more complex streamline distribution on both sides of the fins, with significantly higher fluid velocities, indicating accelerated flow in these areas. This is due to the constriction of the flow path caused by the fin shape. Furthermore, the vortex structures in Figure (b) are more pronounced and larger in scale. The large aperture angle design creates a strong separation effect on the leading edge and sides of the fins, forming distinct recirculation zones and large-scale vortices. These large-scale vortices significantly enhance fluid mixing and localized heat transfer. By disrupting the flow path, these vortices destabilize the boundary layer, promoting heat transfer from the fluid to the fin surface. The boundary layer in Figure (b) exhibits greater volatility and localized thinning. Due to the flow complexity caused by the large aperture angle, the boundary layer distribution on the fin surface is uneven, and boundary layer separation may even occur in some areas. While this unevenness may enhance heat transfer locally, it can also lead to increased turbulence and increased drag.

[0100] The present invention adopts a linkage deformation mechanism, which starts the screw 4 to rotate forward by driving the motor 3. The screw 4 drives the socket concave block 7 to move downward under the action of the thread transmission force, and the push shaft 10 carries the push plate 11 to move downward, and the push plate 11 drives multiple push rods 12 to move left, and multiple slip rings 6 move left synchronously. Multiple fish-scale shaped internal heat exchange fins 18 can expand toward the outer shape, and multiple fish-scale shaped external heat exchange fins 24 can expand toward the outer shape. During heat exchange, large-area displacement heat exchange can be achieved, the heat exchange flow area is wider, and the heat exchange efficiency is greatly improved.

[0101] Based on the mutual influence of the above-mentioned multiple effects, the multiple slip rings 6 are first synchronously shifted to the left, and then the multiple fish-scale shaped internal heat exchange fins 18 are able to achieve outward flow displacement like fish scales, and finally the multiple fish-scale shaped external heat exchange fins 24 are able to displace and exchange heat. In summary, large-area displacement heat exchange can be achieved during heat exchange, the heat exchange flow area is wider, and the heat exchange efficiency is greatly improved.

[0102] The fish-scale inner and outer heat exchange fins 24 both contain textured flow channels. Cross-V-shaped micro-channels are added to the inner and outer sides of the fish-scale inner heat exchange fins 18, and diamond-shaped and triangular micro-channels are added to the inner and outer sides of the fish-scale outer heat exchange fins 24. The flow channels are symmetrically distributed along the center of the fins. By adding textured flow channels, fluid disturbance is enhanced and the fin space is maximized to enhance heat exchange.

[0103] The structures are staggered to avoid interference with each other.

[0104] Compared with the existing technology, the technical solution provided by this application brings the following beneficial technical effects:

[0105] The embodiment of the present application links the deformation module with the heat exchange module, so that the internal and external heat exchange components can be deformed from fixed to outward expansion, thereby extending the frosting time; the inner and outer surfaces of the internal and external heat exchange components contain textured microchannels, which enhances the disturbance and thus increases the heat exchange efficiency; a breakthrough application of the microchannel heat exchanger is achieved, realizing large-area displacement heat exchange, and significantly improving the reliability, heat dissipation and stability of the microchannel heat exchanger in the field of refrigeration and heating.

[0106] Those skilled in the art will understand that the various operations, methods, steps, measures, and schemes in the processes discussed in this application may be alternated, changed, rearranged, decomposed, combined, or deleted.

[0107] The specific implementation methods of the present application described above do not limit the scope of protection of the present application. Any other corresponding changes and modifications made based on the technical concept of the present application should be included in the scope of protection of the claims of the present application.

Claims

1. A heat exchanger based on textured flow channels and microchannels, characterized in that: include: Fixed pipe; a heat exchange tube, wherein a plurality of the heat exchange tubes are distributed in parallel and are all connected to the fixed tube; A drive module, comprising a drive motor and a screw, wherein the drive motor is in driving connection with the screw; A deformation module, wherein the deformation module is in driving connection with the screw, and the screw drives the deformation module to reciprocate along the screw; A heat exchange module, comprising a support ring, a slip ring, and a heat exchange component. The support ring is fixedly connected to the heat exchange tube, the slip ring is transmission-connected to the deformation module, the deformation module drives the slip ring to reciprocate along the heat exchange tube, the heat exchange component is rotationally connected to the support ring and transmission-connected to the slip ring, the slip ring drives one end of the heat exchange component to move away from or toward the heat exchange tube, and the other end of the heat exchange component rotates around the support ring; In which, the heat exchange module includes inner heat exchange fins and outer heat exchange fins, the opening angle of the inner heat exchange fins is smaller than the opening angle of the outer heat exchange fins, the inner and outer surfaces of the inner heat exchange fins are provided with textured flow channels, the textured flow channels include multiple mutually staggered sub-flow channels, the textured flow channels include circular micro-column textures, the inner and outer surfaces of the outer heat exchange fins are provided with textured flow channels, the textured flow channels include multiple mutually staggered sub-flow channels, the textured flow channels include rectangular, triangular and diamond-shaped micro-column textures.

2. A heat exchanger based on textured flow channels and microchannels according to claim 1, characterized in that: The deformation module includes a sleeve recessed block, a first sleeve rod, a push plate and a push rod. The sleeve recessed block is transmission-connected to the screw and its movement direction is parallel to the extension direction of the screw. The first sleeve rod is rotationally connected to the sleeve recessed block through a connecting shaft. The push plate is rotationally connected to the first sleeve rod through a push shaft. The movement direction of the push rod is parallel to the extension direction of the heat exchange tube.

3. A heat exchanger based on textured flow channels and microchannels according to claim 2, characterized in that: It also includes a frame plate, which is fixedly connected to one side of the fixed tube, and the inner wall of the frame plate is rotatably connected to the screw rod.

4. The heat exchanger based on textured flow channels and microchannels according to claim 1, characterized in that: The heat exchange modules are arranged in multiple groups, and the multiple heat exchange tubes are arranged in sequence and at equal intervals. Each group of heat exchange modules is evenly sleeved on one heat exchange tube.

5. A heat exchanger based on textured flow channels and microchannels according to claim 4, characterized in that: The multiple heat exchange modules on two adjacent heat exchange tubes are staggered.

6. The heat exchanger based on textured flow channels and microchannels according to claim 1, characterized in that: It also includes a diverter pipe, which is arranged opposite to the fixed pipe and is connected to the plurality of heat exchange pipes respectively.

7. The heat exchanger based on textured flow channels and microchannels according to claim 1, characterized in that: The heat exchange assembly includes a support rod, a second set of rods, a push rod, a hinged sleeve and a support rod, the support rod is fixedly connected to the slip ring, one end of the second set of rods is rotatably connected to the support rod, the push rod is rotatably connected to the other end of the second set of rods, the inner heat exchange fins are fixedly connected to the push rod, the support rod is fixedly connected to the support ring, and the hinged sleeve is rotatably connected to the support rod and fixedly connected to the inner heat exchange fins.

8. The heat exchanger based on textured flow channels and microchannels according to claim 1, characterized in that: The heat exchange assembly also includes a linkage push rod, a third set of rods, a driving shaft, a sleeve rotating block and a support shaft. The linkage push rod is fixedly connected to the slip ring, the third set of rods is rotatably connected to the linkage push rod, the outer heat exchange fins and the slip ring respectively, the driving shaft is rotatably connected to the third set of rods, the outer heat exchange fins are fixedly connected to the driving shaft, the sleeve rotating block is fixedly connected to the outer heat exchange fins, and the support shaft is rotatably connected to the sleeve rotating block and fixedly connected to the support ring.

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