Heat exchanger based on texture flow channels and micro-channels

Abstract

The invention discloses a heat exchanger based on texture flow channels and micro-channels. The heat exchanger based on the texture flow channels and the micro-channels comprises a fixed pipe, heat exchange pipes, a driving module, a deformation module and a heat exchange module. The multiple heat exchange pipes are distributed in parallel and communicate with the fixed pipe. The driving module comprises a driving motor and a screw rod, and the screw rod is in transmission connection with the driving motor; the deformation module is in transmission connection with the screw, and the movement direction is parallel to the extension direction of the screw; the heat exchange module comprises a supporting ring, a sliding ring and a heat exchange assembly, the supporting ring is fixedly connected with the heat exchange pipe, the sliding ring is in transmission connection with the deformation module, the moving direction is parallel to the extending direction of the heat exchange pipe, and the heat exchange assembly is rotationally connected with the supporting ring and is in transmission connection with the sliding ring. According to the embodiment of the invention, through linkage of the deformation module and the heat exchange module, the heat exchange assembly realizes deformation from fixation to outward expansion, so that the frosting time is prolonged; disturbance is enhanced, and heat exchange efficiency is improved; and the reliability, the heat dissipation performance and the stability of the heat exchanger are improved.

Description

Technical Field

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

[0002] Heat exchangers are devices that produce and output cold in refrigeration systems. Their heat exchange effect directly affects the performance of refrigeration devices and the economic efficiency of operation. The most commonly used heat exchanger for unit air conditioning units is the finned tube heat exchanger. Microchannel heat exchangers in refrigeration and heating have the function of improving heat exchange efficiency. Microchannel heat exchangers use tiny channel design to make the flow of refrigerant in the heat exchanger more uniform, thereby improving heat exchange efficiency. This design enables the heat exchanger to absorb and release heat more effectively, improving the effect of refrigeration and heating.

[0003] In the prior art, although heat exchange can be achieved through heat exchange microchannels, the fins are fixed in the heat exchange process, so 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 appear with the increase of use time. The above problems seriously limit the development of microchannel heat exchangers in the field of refrigeration and heating, so a heat exchanger structure combining textured flow channels and fish-scale microchannels is invented. At the same time, most of the heat exchangers containing fins today are single vertical plug-in fixed fins, the fins and tubes are an integral whole, 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 weak disturbance to the external gas, which makes the boundary layer thicker, so that the mixing of cold and hot fluids is weak, resulting in a decrease in the 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 microchannel, 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 being difficult to achieve large-area displacement heat exchange, a small heat exchange flow area, a significant decrease in heat exchange efficiency, and frosting 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 prior art that it is difficult to achieve large-area displacement 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: The present application provides a heat exchanger based on textured flow channels and microchannels, including a fixed tube, a heat exchange tube, a driving module, a deformation module and a heat exchange module: Fixed pipe; Heat exchange tubes, a plurality of which are distributed in parallel and are all connected to the fixed tube; A driving module, the driving module comprising a driving motor and a screw, the driving motor being drivingly connected to the screw; A deformation module, wherein the deformation module is drivingly connected to the screw rod, and the screw rod drives the deformation module to reciprocate along the screw rod; A heat exchange module, 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 close to the heat exchange tube, and the other end of the heat exchange component rotates around the support ring as the axis.

[0007] 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 transmission-connected to the screw and the movement direction is parallel to the extension direction of the screw. The first sleeve rod is rotationally connected to the sleeve recess via a connecting shaft, the push plate is rotationally connected to the first sleeve rod via a push shaft, and the movement direction of the push rod is parallel to the extension direction of the heat exchange tube.

[0008] 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.

[0009] 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.

[0010] In some embodiments of the present application, the plurality of heat exchange modules on two adjacent heat exchange tubes are arranged in a staggered manner.

[0011] In some embodiments of the present application, a shunt pipe is further included, wherein the shunt pipe is arranged opposite to the fixed pipe, and the shunt pipe is respectively connected to the plurality of heat exchange pipes.

[0012] 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 block 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 block is rotatably connected to the support rod and fixedly connected to the inner heat exchange fin.

[0013] In some embodiments of the present application, the inner and outer surfaces of the inner heat exchange fins are provided with textured flow channels, the textured flow channels include a plurality of mutually staggered sub-flow channels, and the textured flow channels include a circular micro-column texture.

[0014] In some embodiments of the present application, the heat exchange assembly also includes a linkage push rod, a third set of rods, a driving 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 driving shaft is rotatably connected to the third set of rods, the external heat exchange fin is fixedly connected to the driving 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.

[0015] In some embodiments of the present application, the inner and outer surfaces of the external heat exchange fins are provided with textured channels, the textured channels include a plurality of mutually staggered sub-channels, and the textured channels include rectangular, triangular, and diamond-shaped micro-column textures.

[0016] Compared with the prior art, the technical solution provided by this application has the following beneficial technical effects: 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

[0017] In order to more clearly illustrate the technical solution in this application, the following is a brief introduction to the drawings required for use in the embodiments: Figure 1 It is a structural schematic diagram of a heat exchanger based on textured flow channels and microchannels provided in an embodiment of the present application; Figure 2A-2B is a structural schematic diagram of a deformation module provided in an embodiment of the present application; Figure 3A~3B is a structural schematic diagram of a heat exchange module provided in an embodiment of the present application; Figure 4A~4B It is a schematic diagram of the structure of a heat exchange component provided in an embodiment of the present application; Figure 5A~5B is a structural schematic diagram of a textured flow channel provided in an embodiment of the present application; Figure 6A-6B It is a temperature distribution cloud diagram of a heat exchange component provided in an embodiment of the present application; Figure 7A-7BIt is a velocity distribution cloud diagram of a heat exchange component provided in an embodiment of the present application; Figures 8A to 8C It 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.

[0018] Reference numerals: 1-fixed tube, 2-heat exchange tube, 3-drive motor, 4-screw, 5-support ring, 6-slip ring, 7-sleeve concave block, 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 set block, 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

[0019] In order to make the purpose, technical solution and advantages of the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0020] Those skilled in the art will appreciate 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.

[0021] 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 prior art that it is difficult to achieve large-area displacement heat exchange, the heat exchange flow area is small, the heat exchange efficiency is greatly reduced, and frosting will occur with increasing use time.

[0022] In order to achieve the above technical objectives, this application adopts the following technical solutions: The present application provides a heat exchanger based on textured flow channels and microchannels, such as Figure 1 As shown, Figure 1 It is a structural schematic diagram of a heat exchanger based on textured flow channels and microchannels provided in an embodiment of the present application.

[0023] A heat exchanger based on textured flow channels and microchannels includes a fixed tube 1, a heat exchange tube 2, a driving module, a deformation module and a heat exchange module: Fixed tube 1; Heat exchange tubes 2, a plurality of heat exchange tubes 2 are distributed in parallel and are all connected to the fixed tube 1; A driving module, the driving module comprising a driving motor 3 and a screw 4, the driving motor 3 being drivingly connected to the screw 4; A deformation module, wherein the deformation module is in transmission connection with the screw rod 4, and the screw rod drives the deformation module to reciprocate along the screw rod 4; 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, 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 an axis 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 microchannel heat exchange has been achieved, large-area displacement heat exchange has been realized, and the reliability, heat dissipation and stability of the microchannel heat exchanger in the field of refrigeration and heating have been significantly improved.

[0024] Since the first end of the heat exchange component in the present 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 direction of the shunt 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 the Venturi tube, due to the continuity equation, the velocity reaches the maximum value and the static pressure reaches the minimum value at the narrowest part of the pipeline. 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.

[0025] like Figure 2A-2B As shown, Figure 2A-2B is a structural schematic diagram of a deformation module provided in an embodiment of the present application; Figure 2B yes Figure 2A A partial diagram of .

[0026] 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.

[0027] 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 an inner wall of the frame plate 13 is rotatably connected to the screw rod 4 .

[0028] 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, and a driving 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 and 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, and a heat exchange tube 2 welded and connected to the fixed tube 1 is provided on one side of each of the push rods 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 of the slip rings 6, and the support ring 5 is fixedly connected to the heat exchange tube 2, and an internal shape changing heat exchange component is provided on the outer wall of the support rod 15; and an external shape changing heat exchange component is provided on one side of the support rod 15.

[0029] 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 to be disassembled and replaced.

[0030] In some embodiments of the present application, the number of the heat exchange modules is multiple groups, and the multiple heat exchange tubes 2 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 2.

[0031] 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; the frame plate 13 and the sleeve recess 7 are both made of stainless steel, and the heat exchange tubes 2 are arranged equidistantly from top to bottom, and the heat exchange tubes 2 are made of copper.

[0032] In some embodiments of the present application, the multiple heat exchange modules on two adjacent heat exchange tubes 2 are arranged in a staggered manner.

[0033] In some embodiments of the present application, a shunt pipe 14 is further included. The shunt pipe 14 is arranged opposite to the fixed pipe 1 , and the shunt pipe 14 is respectively connected to the plurality of heat exchange pipes 2 .

[0034] In this embodiment, the heat exchange modules are arranged in a staggered manner to avoid mutual interference when deployed.

[0035] A shunt 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 shunt pipe 14 .

[0036] like Figure 3A~3B As shown, Figure 3A~3B is a structural schematic 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.

[0037] 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.

[0038] 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; a push rod 17 is rotatably connected to the inner wall of the second set of rods 16 and near its top end, and a fish-scale shaped internal heat exchange fin 18 is welded to one end of the push rod 17, and a hinged sleeve block 19 is fixedly installed on one side of the fish-scale shaped internal heat exchange fin 18; a support rod 20 is rotatably connected to the inner wall of the hinged sleeve block 19, and the support rod 20 is fixedly connected to the support ring 5.

[0039] like Figure 4A~4B As shown, Figure 4A~4B It is a structural schematic diagram of a heat exchange component provided in an embodiment of the present application; Figure 4A For the internal heat exchange fin 18, Figure 4B It is an external heat exchange fin 24.

[0040] In some embodiments of the present application, the inner and outer surfaces of the inner heat exchange fins 18 are provided with textured channels, the textured channels include a plurality of mutually staggered sub-channels, and the textured channels include a circular micro-column texture.

[0041] 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, the third set of rods 22 are 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 is fixedly connected to the support ring 5.

[0042] The external shape-changing heat-transforming assembly includes a linkage push rod 2112 disposed 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; 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, and 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.

[0043] The fish-scale shaped external heat exchange fins 24 and the slip ring 6 are both rotatably connected to the third set of rods 22 .

[0044] When the internal shape changes heat, the sliding 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 rods 17 to move leftward. The push rods 17 drive the fish scale-shaped internal heat exchange fins 18 to rotate, and the fish scale-shaped internal heat exchange fins 18 drive the hinged sleeves 19 to rotate, and the hinged sleeves 19 rotate along the outer wall of the support rods 20, and the support ring 5 supports the support rods 20, and the multiple fish scale-shaped internal heat exchange fins 18 can achieve outward expansion flow displacement like fish scales.

[0045] The external shape changes heat. When the slip ring 6 moves to the left, the slip ring 6 drives the multiple linkage push rods 2112 to move to the left at the same time, and the linkage push rods 2112 drive the third set of rods 22 to move to the left. The third set of rods 22 drives the driving shaft 23 to rotate, the driving shaft 23 drives the fish scale-shaped external heat exchange fins 24 to rotate, and the fish scale-shaped external heat exchange fins 24 drive the sleeve rotating block 25 to rotate. The sleeve rotating block 25 rotates on the outer wall of the support shaft 26, and the multiple fish scale-shaped external heat exchange fins 24 can expand and deform outward, so that the multiple fish scale-shaped external heat exchange fins 24 can change position and exchange heat, and the heat exchange area is wider.

[0046] The specific steps are: 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 to perform heat exchange operation.

[0047] Step 2: During linkage deformation, the screw 4 is started to rotate forward by driving the motor 3, and the screw 43 drives the sleeve concave block 7 to move downward under the action of the thread transmission force. The sleeve concave block 7 slides down along the inner wall of the frame plate 13, and at the same time, the sleeve concave block 7 drives the connecting shaft 8 to move downward, and the connecting shaft 8 drives the first sleeve rod 9 to move the push shaft 10 downward. 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 the push rods 12 drive multiple slip rings 6 to move left synchronously, and the slip rings 6 slide leftward along the outer wall of the heat exchange tube 2, and multiple slip rings 6 move left synchronously.

[0048] Step 3: When the internal shape changes heat, the sliding 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-shaped internal heat exchange fins 18 to rotate, and the fish scale-shaped internal heat exchange fins 18 drive the hinged sleeve 19 to rotate, and the hinged sleeve 19 rotates along the outer wall of the support rod 20, and the support ring 5 supports the support rod 20, and the multiple fish scale-shaped internal heat exchange fins 18 can achieve outward expansion flow displacement like fish scales.

[0049] Step 4: External deformation heat transfer, when the slip ring 6 moves to the left, the slip ring 6 simultaneously drives the multiple linkage push rods 2112 to move to the left, and the linkage push rods 2112 drive the third set of rods 22 to move to the left. The third set of rods 22 drives the driving shaft 23 to rotate, the driving shaft 23 drives the fish scale-shaped external heat exchange fins 24 to rotate, and the fish scale-shaped external heat exchange fins 24 drive the sleeve rotating block 25 to rotate. The sleeve rotating block 25 rotates on the outer wall of the support shaft 26, and the multiple fish scale-shaped external heat exchange fins 24 can expand and deform outward, so that the multiple fish scale-shaped external heat exchange fins 24 can be displaced for heat exchange, and the heat exchange area is wider.

[0050] The plurality of support rods 15 are evenly spaced and arranged in a circular ring, 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 evenly spaced and arranged in a circular ring, and the fish-scale shaped internal and external heat exchange fins 24 are both made of copper.

[0051] like Figure 5A~5B As shown, Figure 5A~5B It 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.

[0052] In some embodiments of the present application, the inner and outer surfaces of the external heat exchange fins 24 are provided with textured channels, the textured channels include a plurality of mutually staggered sub-channels, and the textured channels include rectangular, triangular, and diamond-shaped micro-column textures.

[0053] 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 utilized to the maximum extent to enhance heat exchange.

[0054] Regarding the selection of micro-texture shape: the microchannel is V-shaped as a whole. ① Through its unique geometric shape, the fluid is guided to make multiple deflections, so that secondary flow and double vortex are generated around the micro-texture in the channel. This fluid disturbance can significantly break the boundary layer, enhance the convective heat transfer between the fluid and the wall, and thus improve the heat transfer coefficient; ② At the same time, compared with the linear or parallel channel design, the V-shaped channel increases the contact area between the fluid and the wall of the heat exchanger by changing the geometric structure, effectively increasing the heat transfer area per unit volume, thereby maximizing the use of the fin space to enhance heat transfer; ③ Through the V-shaped structure, the fluid can be more evenly distributed in the heat exchanger, reducing the temperature gradient caused by local flow deviation. This uniformity optimizes the overall thermal performance of the heat exchanger and avoids the reduction in efficiency caused by local overheating or insufficient cooling. ④ The high disturbance characteristics of the V-shaped channel make it difficult for particles and impurities in the fluid to adhere to the channel, reducing the formation of dirt and sediment. This not only extends the maintenance cycle of the heat exchanger, but also maintains long-term high-efficiency heat transfer performance.

[0055] The outer layer is an arc-shaped fin, so the designed micro-texture contains a rectangular texture with an inclination angle of β=70° and a triangular and diamond-shaped micro-column texture. The inclination angle improves the heat transfer factor and the friction factor compared to the vertical structure. At the same time, the rectangular, triangular and diamond-shaped micro-columns can form a strong disturbance effect when the fluid flows due to their sharper appearance. Along the entire microchannel, traces of horseshoe vortices and wake vortices will be generated around each rectangular, diamond and triangular micro-column. The emergence of these longitudinal structures is induced by the interaction between the primary flow and the micro-columns, which helps to break the thermal boundary layer of the fluid and enhance convective heat transfer. Efficient heat transfer enables the cold fluid to exert the heat exchange effect as quickly as possible.

[0056] The design of the inner fin is still based on the micro-rectangular column micro-texture. Considering the small area of ​​the front and rear sides and the lower internal flow than the external, the front and rear sides are designed to include circular and teardrop-shaped micro-textures on the basis of ensuring the V-shaped flow channel. Due to the symmetry and uniform geometry of the circular micro-texture, the heat can be evenly distributed over the entire surface of the fin. This uniformity helps to avoid local overheating or insufficient cooling, and improves the overall thermal effect of the heat exchanger; at the same time, the circular micro-texture profile is conducive to guiding the fluid into the separation area on the leeward side of the fin, enhancing the heat transfer capacity of the leeward side of the fin. The streamlined design of the teardrop-shaped fin enables it to significantly reduce the air resistance during fluid flow. Compared with fins of other shapes, the shape of the teardrop-shaped fin gradually tapers after the front fluid separation point, which can reduce the vortex and vortex formation at the tail, so it has lower pressure loss and higher PEC value.

[0057] like Figure 6A-6B As shown, Figure 6A-6B It is a temperature distribution cloud diagram of a heat exchange component provided in an embodiment of the present application; Fig. 6A (a) is the temperature distribution cloud diagram of the external fin after adding texture, (b) is the temperature distribution cloud diagram of the external fin before adding texture (yz plane, from top to bottom, x=0.005, 0.006, 0.007); Figure 6B (a) is the temperature distribution cloud diagram of the inner fin after adding texture, and (b) is the temperature distribution cloud diagram of the outer fin before adding texture (yz plane, x=0.005, 0.006, 0.007 from top to bottom).

[0058] 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.

[0059] Due to the presence of different types of micro-textures, the thermal boundary layer is interrupted and redeveloped. Compared with the fins without textures, the turbulence intensity is significantly enhanced, and the disturbance to the surrounding fluid is enhanced, so that the fins with added micro-textures have a stronger cooling effect and better temperature uniformity in space; at the same time, the presence of micro-textures changes the flow of the surrounding fluid by increasing the heat exchange 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 exchange, improving heat exchange efficiency, achieving a reduction in spatial temperature, and making the temperature distribution more uniform.

[0060] like Figure 7A-7B As shown, Figure 7A-7B It is a velocity distribution cloud diagram of a heat exchange component provided in an embodiment of the present application; Fig. 7A(a) (b) are the velocity distribution cloud maps of the outer fin with texture (x=0.004, 0.006 respectively), (c) is the streamline diagram of the plane x=0.006 after the outer fin with texture; (d) (e) are the velocity distribution cloud maps of the outer fin without texture (x=0.004, 0.006 respectively), and (f) is the streamline diagram of the plane x=0.006 of the outer fin without texture.

[0061] 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 map 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), and (f) is the streamline map of the outer fin without texture on the plane of x=0.00014.

[0062] 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 existence of micro-textures, the fluid velocity is redistributed; and compared with the inlet, the existence of micro-textures 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 vortices near the micro-textured fins.

[0063] At the same time, by observing the streamline diagrams (c) and (f), it can be found that the micro-textured fins produce 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 the heat transfer efficiency.

[0064] like Figures 8A to 8C As shown, Figures 8A to 8C It 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.

[0065] Fig. 8A The temperature distribution cloud diagrams of different sections along x at different opening angles. Figures (a), (b), and (c) are the temperature distribution cloud diagrams of the three 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) are the temperature distribution cloud diagrams of the three 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. Among them, the x=0.0046 section is closer to the cold source, and the x=0.0086 section is farther away from the cold source.

[0066] As can be seen from Figures (a)-(c), the temperature drops significantly along the flow direction of the fin fluid, and the cooling effect on the external hot air is better. The closer to the cold source, the greater the temperature gradient change, and the better the cooling effect. This is because under the small opening angle design, the structure focuses more on the longitudinal effect, which makes the temperature of the fluid along the flow direction of the fin change significantly; at the same time, the spanwise movement causes the thermal boundary layer to be periodically interrupted and redeveloped, and the fin microtexture increases the disturbance effect of the fin on the mainstream, increases the heat exchange capacity, and thus promotes heat transfer; in contrast, the large opening angle design in Figures (d)-(f) shows a significant temperature gradient perpendicular to the flow direction, indicating that the lateral expansion structure effectively reduces the fluid retention between the two layers of the structure, strengthens the disturbance of the fluid when passing through the fin, and then promotes the mixing of cold and hot fluids, improving the overall heat transfer performance. The large opening angle design further enhances the overall reduction effect of the space temperature through a larger range of microtexture disturbances.

[0067] Traditional vertical fins usually rely on linear cooling along the flow direction during the heat exchange process. Although this method is simple, it is easy to cause the thickness of the boundary layer to gradually increase, thereby forming a stable temperature gradient. In addition, the fluid is not disturbed enough when flowing through the fins, and the heat transfer is limited. Especially in the latter part of the fluid flow, it is easy to form a stagnation zone and a high-temperature zone, which affects the overall heat exchange performance and reduces 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 design. At the same time, the periodic disturbance brought by the micro-texture further enhances the turbulent effect, prompting more fluids to participate in heat exchange, greatly improving the heat transfer efficiency.

[0068] Figure 8B The velocity distribution cloud diagrams along different sections of x at different opening angles. (a)(b)(c)(d) are the velocity distribution cloud diagrams of the four sections x=0.0046, x=0.0066, x=0.0086, x=0.0106 when the outer fin opening angle is 20° and the inner fin opening angle is 12°, respectively. (e)(f)(g)(h) are the velocity distribution cloud diagrams of the four sections x=0.0046, x=0.0066, x=0.0086, x=0.0106 when the outer fin opening angle is 50° and the inner fin opening angle is 30°, respectively.

[0069] Regardless of the size of the expansion angle, the flow field maintains a high degree of symmetry as a whole. From Figure ad, we can see that as the flow section moves from x=0.0046 to x=0.0106, the flow field shows a relatively stable velocity distribution, and there is a larger velocity change area compared to sections abc and 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; and 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.

[0070] From Figure eh, we can see that the velocity distribution cloud map shows more complex velocity changes, especially at the tip and both sides of the fin. Because the large opening angle design makes the flow channel more tortuous, the fluid forms multiple local high-speed areas on the fin surface, and these high-speed areas are interspersed with low-speed areas. These low-speed areas also represent the existence of the velocity boundary layer, but unlike the small opening angle design, the boundary layer distribution of the large opening angle design is more uneven. Specifically, when the fluid passes through the fin, the large-angle fin structure makes the flow path more complicated, and the fluid is subjected to stronger shear force, resulting in local thinning of the boundary layer, and even flow separation may occur in some areas. The volatility and unevenness of this boundary layer increase the disturbance on the heat exchange surface, which helps to improve the local heat transfer efficiency. On the cross-section of Figure (h), the boundary layer is more complex, forming multiple branching areas. This situation shows that when the flow passes through the fin, obvious vortices and secondary flows are generated. These complex flow structures aggravate the changes in the boundary layer, making the boundary layer extremely thin in some parts, which is conducive to enhancing heat transfer.

[0071] Figure 8C Streamline diagrams of the x=0.046 section at different opening angles. (a) is the streamline diagram of the x=0.0046 section when the outer fin opening angle is 20° and the inner fin opening angle is 12°, and (b) is the streamline diagram of the x=0.0046 section when the outer fin opening angle is 50° and the inner fin opening angle is 30°.

[0072] From Figure (a), it can be seen that after the streamline flows near the fin surface, a relatively high-speed flow appears in the central area, while a lower speed appears in the surface area close to the fin, indicating that the boundary layer is fully developed on the fin surface. At the same time, the fluid forms local small vortices at the tip and both 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. It can be seen from Figure (b) that the streamline distribution on both sides of the fin is more complex and the fluid velocity is significantly increased, indicating that the fluid is accelerating in these areas. This is due to the contraction of the flow channel caused by the shape of the fin; at the same time, the vortex structure in Figure (b) is more obvious and larger in scale. The large opening angle design causes the fluid to produce a strong separation effect at the leading edge and both sides of the fin, forming an obvious recirculation zone and large-scale vortices. These large-scale vortices significantly increase the mixing effect of the fluid and enhance the local heat transfer performance. By disturbing the flow path, these vortices can destroy the stability of the boundary layer and promote the transfer of heat from the fluid to the fin surface; and the boundary layer in Figure (b) shows a stronger volatility and a tendency to thin locally. Due to the complexity of the flow caused by the large opening angle, the boundary layer is unevenly distributed on the fin surface, and boundary layer separation may even occur in some areas. Although this unevenness will enhance heat transfer locally, it may also cause problems such as increased turbulence and increased resistance.

[0073] 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 sleeve recess 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 inner heat exchange fins 18 can expand toward the outer shape, and multiple fish-scale shaped outer 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.

[0074] 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 heat exchange. 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.

[0075] 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 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.

[0076] The structures are staggered to avoid interference with each other.

[0077] Compared with the prior art, the technical solution provided by this application has the following beneficial technical effects: 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 microchannel heat exchange has been achieved, large-area displacement heat exchange has been realized, and the reliability, heat dissipation and stability of the microchannel heat exchanger in the field of refrigeration and heating have been significantly improved.

[0078] Those skilled in the art will appreciate that the various operations, methods, steps, measures, and schemes in the processes discussed in this application may be alternated, modified, rearranged, decomposed, combined, or deleted.

[0079] The specific implementation methods of the present application described above do not constitute a limitation on the protection scope of the present application. Any other corresponding changes and modifications made according to the technical concept of the present application should be included in the protection scope 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; Heat exchange tubes, a plurality of which are distributed in parallel and are all connected to the fixed tube; A driving module, the driving module comprising a driving motor and a screw, the driving motor being drivingly connected to the screw; A deformation module, wherein the deformation module is drivingly connected to the screw rod, and the screw rod drives the deformation module to reciprocate along the screw rod; A heat exchange module, 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 close to the heat exchange tube, and the other end of the heat exchange component rotates around the support ring as the axis.

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

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 arranged in a staggered manner.

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

7. A 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, an inner heat exchange fin, a hinged sleeve block 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 block is rotatably connected to the support rod and fixedly connected to the inner heat exchange fin.

8. A heat exchanger based on textured flow channels and microchannels according to claim 7, characterized in that: The inner and outer surfaces of the inner heat exchange fins are provided with textured flow channels, the textured flow channels include a plurality of mutually staggered sub-flow channels, and the textured flow channels include circular micro-column textures.

9. A 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, 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 driving shaft is rotatably connected to the third set of rods, the external heat exchange fin is fixedly connected to the driving 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.

10. A heat exchanger based on textured flow channels and microchannels according to claim 9, characterized in that: The inner and outer surfaces of the external heat exchange fins are provided with textured flow channels, the textured flow channels include a plurality of mutually staggered sub-flow channels, and the textured flow channels include rectangular, triangular, and diamond-shaped micro-column textures.

Images