Refrigerant line with ice-melting defrosting

Abstract

This invention relates to a defrosting and de-icing refrigeration pipeline, belonging to the field of refrigeration pipe technology. It includes a pipe body assembly and a controller, which are electrically connected. The pipe body assembly includes a refrigeration pipe body with a defrosting heat-conducting layer on its inner wall. The refrigeration pipe body has a hollow structure with an internal cavity serving as a refrigerant flow channel. A hot-fluorine defrosting assembly is inserted into the refrigerant flow channel. The hot-fluorine defrosting assembly includes a defrosting assembly mounting bracket at the inlet end of the refrigeration pipe body, on which a hot-fluorine delivery pipe is fixedly mounted. The inlet end of the hot-fluorine delivery pipe is connected to the compressor exhaust pipe of the refrigeration system, and the outlet end is connected to a spiral guide pipe via an electronic expansion valve. The end of the spiral guide pipe is connected to the condenser of the refrigeration system via a hot-fluorine return pipe. An ice / frost thickness sensor is also provided on the outer surface of the refrigeration pipe body.

Description

Technical Field

[0001] This invention relates to a refrigeration pipeline for defrosting and de-icing, belonging to the field of refrigeration pipe technology. Background Technology

[0002] Currently, refrigerant pipes are the core heat exchange components of refrigeration systems. They achieve heat exchange through the circulation of refrigerant within the pipe, thereby achieving the purpose of cooling. During long-term operation, because the surface temperature of the refrigerant pipe is lower than the ambient dew point temperature, water vapor in the environment will condense and freeze on the surface of the pipe, forming a frost or ice layer. As the operating time increases, the frost layer will continue to thicken. On the one hand, this will significantly reduce the heat exchange efficiency of the refrigerant pipe, increase the energy consumption of the refrigeration system, and lead to a decrease in cooling effect. On the other hand, the thick frost layer will exert compressive stress on the refrigerant pipe, which can easily cause pipe damage and leakage under long-term effects, shorten the service life of the refrigerant pipe, and even cause refrigeration system failure.

[0003] Currently, the main defrosting methods for refrigeration pipes include manual defrosting, electric defrosting, water defrosting, and reverse circulation defrosting. Among them, manual defrosting is inefficient, labor-intensive, poses safety hazards such as working at heights, and is prone to damaging the pipe surface, resulting in incomplete defrosting; electric defrosting consumes a lot of electricity, has high operating costs, and the heating element is prone to damage and failure, and the defrosting process can cause a significant increase in the ambient temperature, affecting the refrigeration effect; water defrosting consumes a lot of water, requires a complex drainage system, and water can easily splash, causing goods to get damp or the floor to freeze, and in cold regions, the issue of water pipe antifreeze must also be considered; reverse circulation defrosting has the drawbacks of incomplete defrosting, long defrosting time, and low efficiency.

[0004] In view of the above-mentioned shortcomings, the present invention aims to create a refrigeration pipeline for defrosting and de-icing, making it more industrially valuable. Summary of the Invention

[0005] To solve the above-mentioned technical problems, the purpose of this invention is to provide a refrigeration pipeline for defrosting and de-icing.

[0006] This invention discloses a defrosting refrigeration pipeline, comprising a pipe body assembly and a controller, wherein the pipe body assembly and the controller are electrically connected. The pipe body assembly includes a refrigeration pipe body, on which a defrosting heat-conducting layer is provided. The refrigeration pipe body has a hollow structure, with an internal cavity serving as a refrigerant flow channel. A hot refrigerant defrosting assembly is also inserted into the refrigerant flow channel. The hot refrigerant defrosting assembly includes a defrosting assembly fixing bracket located at the inlet end of the refrigeration pipe body, on which a hot refrigerant delivery pipe is fixedly mounted. The inlet end of the hot refrigerant delivery pipe is connected to the compressor exhaust pipe of the refrigeration system, and the outlet end is connected to a spiral guide pipe via an electronic expansion valve. The end of the spiral guide pipe is connected to the condenser of the refrigeration system via a hot refrigerant return pipe. An ice and frost thickness sensor is also provided on the outer surface of the refrigeration pipe body.

[0007] Furthermore, the body of the refrigeration pipe is made of brass, and its surface is treated with an anti-frost treatment. The specific steps of the anti-frost treatment are as follows:

[0008] (1) Take 1 to 2 parts by weight of fumed nano silica and disperse it in 30 to 40 parts of anhydrous ethanol to obtain a fumed nano silica suspension. Add 0.6 to 0.8 parts of trimethylethoxysilane slowly to the fumed nano silica suspension and stir to obtain a hydrophobic nano silica solution. (2) By weight, 0.4 to 0.5 parts of hydrochloric acid solution with a concentration of 0.01 mol / L, 0.4 to 0.6 parts of deionized water, 2 to 4 parts of anhydrous ethanol and 1 to 1.5 parts of methyltriethoxysilane are mixed sequentially and stirred to obtain a mixed modified solution; (3) Slowly add the mixed modified liquid to the hydrophobic nano silica solution, and stir magnetically at room temperature until the reaction is complete, and finally obtain hydrophobic gas phase nano silica sol. (4) The refrigeration tube body is sequentially immersed in hydrofluoric acid solution with a concentration of 5 mol / L and hydrochloric acid solution with a concentration of 2 mol / L for 10 min and 30 min respectively. After being removed, it is ultrasonically cleaned with deionized water to obtain a pre-roughened refrigeration tube body. Hydrophobic fumed silica sol is sprayed onto the surface of the pre-roughened refrigeration tube body with a pressure of 0.15-0.25 MPa using a spray gun. The spray thickness is controlled to be 0.5-1.5 mm. After drying and curing, the surface of the pre-cooled tube body is treated to prevent frost formation.

[0009] Furthermore, the spiral guide tube is arranged in an axial spiral configuration.

[0010] Furthermore, the defrosting heat-conducting layer is a thermally conductive silicone pad, and the thickness of the defrosting heat-conducting layer is 0.05-0.1mm.

[0011] Furthermore, the electronic expansion valve and the controller are connected by an electrical signal, and the controller and the frost thickness sensor are connected by an electrical signal.

[0012] Furthermore, the controller is a PLC controller, which has a defrost threshold internally, the defrost threshold being 0.5 to 2.0 mm of frost thickness.

[0013] By means of the above-described solution, the present invention has at least the following advantages: (1) The present invention employs acid etching roughening and hydrophobic vapor-phase nano-silica sol spraying to prevent frost formation on the refrigeration tube body, forming a micro-nano scale ladder structure. First, acid etching roughens the tube surface to form micron-scale rectangular pits. Then, spraying forms a grafting base of raised hydrophobic nano-silica particles, so that the micron-scale rough structure surface is modified by hydrophobic nano-silica particles to reduce surface energy. Since the hydrophobic nano-silica particles are grafted onto the micron-scale rough structure surface, through nano-scale silica and micron-scale pre- The roughened surfaces work together to form a micro-nano scale ladder structure. When the outer wall of the tube comes into contact with the droplet, the actual solid-liquid contact area of ​​the droplet on the surface of the micro-nano scale ladder structure will be reduced. Furthermore, because a large amount of air is retained in the micro-nano scale ladder structure, the droplet is not easy to spread on the surface of the micro-nano scale ladder structure, which leads to a significant reduction in the spreading radius of the droplet on the surface of the micro-nano scale ladder structure. This can prevent the droplet from adhering to the tube surface, thereby avoiding the possibility of liquid frost from the source and improving the defrosting and anti-frost effect of the refrigeration pipeline.

[0014] Furthermore, in the frost melting process on the surface of the micro / nano-scale ladder structure, the frost layer first breaks into liquid fragments containing a mixture of ice and water. These fragments then merge through liquid bridges to form larger liquid blocks. Due to the superhydrophobicity and low water adhesion work of the micro / nano-scale ladder structure surface, when used in conjunction with the thermal defrosting component, the liquid fragments shrink and easily merge into independently dispersed spherical droplets. These droplets can quickly melt into independently distributed spherical droplets, achieving excellent defrosting efficiency. Moreover, the synergistic effect between the micron-scale rough structure and the hydrophobic nano-silica particles traps a large amount of air within the micro / nano-scale ladder structure, forming an air cushion. This reduces the actual contact area between the spherical droplets formed during defrosting and the surface of the micro / nano-scale ladder structure. Simultaneously, the air cushion acts as a lubricant, allowing the defrosting droplets to roll off quickly and complete the defrosting process.

[0015] (2) The spiral guide tube with axial spiral arrangement can guide the refrigerant in a spiral manner during the refrigeration process. The spiral guide surface will have a forced guiding effect on the flowing refrigerant, forcing the refrigerant to flow along the spiral trajectory. The original laminar flow state is destroyed and transformed into turbulent or transitional flow state. In the turbulent state, the irregular movement of refrigerant molecules is intensified, the heat transfer speed between molecules is accelerated, and at the same time, the turbulence will wash away the thermal boundary layer on the surface of the tube wall, making the thermal boundary layer thinner, significantly reducing the thermal resistance and enhancing the convective heat transfer effect inside the tube. In addition, the spiral structure extends the actual flow path of the refrigerant in the refrigeration tube. Compared with a straight tube, under the same tube length, the spiral guide can extend the residence time of the refrigerant by more than 30%. This design allows the refrigerant more time to exchange heat with the pipe wall, fully releasing or absorbing heat, reducing the loss of refrigerant that has not been adequately heat-exchanged, and improving the adequacy of heat exchange. Furthermore, the spiral guide tube effectively suppresses refrigerant flow deviation and short-circuiting, ensuring the refrigerant is evenly distributed throughout the entire pipe cross-section, avoiding dead zones in localized heat exchange, maximizing the utilization of the refrigerant pipe's heat exchange area, and ensuring uniform heat exchange intensity throughout the pipe wall. In addition, during the spiral flow process, the refrigerant flows tightly against the pipe wall under centrifugal force, further increasing the contact tightness between the refrigerant and the pipe wall, reducing contact thermal resistance. Simultaneously, the spiral structure promotes internal mixing of the refrigerant, preventing excessively large local temperature gradients, and further optimizing heat exchange and refrigeration efficiency. During the hot fluorine de-icing process, the spiral structure enhances convective heat transfer within the pipe, improving the fundamental heat transfer mechanism. For pipes of the same length, the spiral structure allows for a tighter, more tightly wound arrangement, increasing the contact area with the ice layer by over 50% compared to straight pipes. Furthermore, the spiral winding allows the pipe to cover a wider de-icing area, ensuring that the heat transferred by the hot fluorine is more effectively applied to the ice surface, reducing heat loss, improving heat utilization, and thus accelerating the overall de-icing rate. When the hot fluorine flows along the spiral trajectory, the actual flow path is much longer than that of a straight pipe of the same length, significantly extending the residence time of the hot fluorine within the pipe. This allows the hot fluorine to fully release its sensible and latent heat, providing a continuous and stable heat supply for ice melting. When spiral pipes are wound in a spiral pattern, the spacing between different parts of the pipe is uniform, and the heat transferred from the hot fluorine to the pipe wall can be evenly distributed throughout the de-icing area, avoiding local overheating or undercooling that occurs in straight pipes. At the same time, the spiral structure can guide heat to radiate evenly to the periphery of the pipe, so that the ice layer can absorb heat and melt evenly from the surface to the inside and from the periphery of the pipe to a distance, effectively solving the problems of local ice residue and uneven de-icing, and ensuring thorough de-icing.

[0016] (3) The present invention monitors the frost thickness of the pipe in real time through the frost thickness sensor. The PLC controller has a built-in defrost threshold and is linked with the electronic expansion valve electrical signal. The defrosting program is started only when the frost thickness reaches the preset threshold. The opening of the electronic expansion valve is precisely adjusted according to the actual frost thickness, and the hot fluorine flow rate is controlled to achieve on-demand energy supply and precise defrosting. This avoids the problems of blind defrosting and excessive energy supply in the traditional defrosting method. At the same time, the hot fluorine defrosting component uses the compressor of the refrigeration system itself to complete the defrosting, without the need for additional heating and water supply equipment, further reducing the energy consumption and operating cost of the defrosting stage.

[0017] (4) This invention reduces the frosting rate from the source, reduces the compressive stress of the frost layer on the tube body, and avoids damage and leakage problems caused by long-term frost compression. At the same time, it adopts an active and gentle hot fluorine defrosting method to replace the mechanical scraping of manual defrosting and the local high temperature of electric defrosting, which are easy to damage the tube body, and effectively protects the tube body structure and surface performance. In addition, the coordinated work of each component makes the refrigeration system not need to be frequently started and stopped due to frequent defrosting or sudden drop in heat exchange efficiency, reducing the probability of system failure, which not only extends the service life of the refrigeration tube, but also improves the long-term operational stability and reliability of the entire refrigeration system.

[0018] (5) The hot fluorine defrosting assembly of the present invention is directly inserted into the refrigerant flow channel of the refrigeration pipe body. Each component is modularly designed and can be directly connected to the compressor and condenser of the existing refrigeration system without large-scale modification of the existing refrigeration system. It has strong installation adaptability. At the same time, the core anti-frost treatment process can be adapted and completed in the existing refrigeration pipe production process. The process is controllable, the operation is simple, the transformation cost for industrial application is low, and it has good industrial promotion value.

[0019] (6) The anti-frost treatment, defrosting heat-conducting layer, spiral guide tube, and intelligent monitoring defrosting system of the present invention do not function individually, but form a synergistic whole: the anti-frost treatment reduces the amount of frost and lowers the defrosting frequency; the spiral guide tube simultaneously enhances refrigeration heat exchange and improves defrosting efficiency; the defrosting heat-conducting layer facilitates efficient heat transfer of hot fluorine and, together with the spiral guide tube, improves the defrosting effect; the intelligent control system precisely regulates the defrosting process, matching the actual needs of anti-frost and defrosting, and the various components work together to achieve integrated optimization of anti-frost, defrosting, and refrigeration, thereby achieving a qualitative improvement in the overall performance of the refrigeration pipeline, which is far superior to existing single-improvement refrigeration pipeline products.

[0020] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, the preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings. Attached Figure Description

[0021] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show a certain embodiment of the present invention and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0022] Figure 1 This is a schematic diagram of the refrigeration pipeline for defrosting and de-icing according to the present invention.

[0023] In the figure: 10. Pipe body assembly; 20. Controller; 1. Refrigeration pipe body; 2. Defrosting heat-conducting layer; 3. Hot refrigerant defrosting assembly; 11. Refrigerant flow channel; 31. Defrosting assembly mounting bracket; 32. Hot refrigerant delivery pipe; 33. Electronic expansion valve; 34. Spiral guide pipe; 35. Hot refrigerant return pipe; 4. Frost thickness sensor. Detailed Implementation

[0024] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and are not intended to limit the scope of the invention.

[0025] See Figure 1 A preferred embodiment of the present invention describes a defrosting refrigeration pipeline, comprising a pipe body assembly 10 and a controller 20, which are electrically connected. The pipe body assembly 10 includes a refrigeration pipe body 1, with a defrosting heat-conducting layer 2 on the inner wall of the refrigeration pipe body 1. The refrigeration pipe body 1 has a hollow structure, with an internal cavity serving as a refrigerant flow channel 11. A hot refrigerant defrosting assembly 3 is also inserted into the refrigerant flow channel 11. The hot refrigerant defrosting assembly 3 includes a defrosting assembly fixing bracket 31 located at the inlet end of the refrigeration pipe body 1. A hot refrigerant delivery pipe 32 is fixedly mounted on the defrosting assembly fixing bracket 31. The inlet end of the hot refrigerant delivery pipe 32 is connected to the compressor exhaust pipe of the refrigeration system, and the outlet end is connected to a spiral guide pipe 34 via an electronic expansion valve 33. The end of the spiral guide pipe 34 is connected to the condenser of the refrigeration system via a hot refrigerant return pipe 35. An ice and frost thickness sensor 4 is also provided on the outer wall surface of the refrigeration pipe body 1.

[0026] The body of the refrigeration pipe 1 is made of brass, and its surface is treated with an anti-frost treatment. The specific steps of the anti-frost treatment are as follows: (1) Take 1 to 2 parts by weight of fumed nano silica and disperse it in 30 to 40 parts of anhydrous ethanol to obtain a fumed nano silica suspension. Add 0.6 to 0.8 parts of trimethylethoxysilane slowly to the fumed nano silica suspension and stir to obtain a hydrophobic nano silica solution. (2) By weight, 0.4 to 0.5 parts of hydrochloric acid solution with a concentration of 0.01 mol / L, 0.4 to 0.6 parts of deionized water, 2 to 4 parts of anhydrous ethanol and 1 to 1.5 parts of methyltriethoxysilane are mixed sequentially and stirred to obtain a mixed modified solution; (3) Slowly add the mixed modified liquid to the hydrophobic nano silica solution, and stir magnetically at room temperature until the reaction is complete, and finally obtain hydrophobic gas phase nano silica sol. (4) The refrigeration tube body is sequentially immersed in hydrofluoric acid solution with a concentration of 5 mol / L and hydrochloric acid solution with a concentration of 2 mol / L for 10 min and 30 min respectively. After being removed, it is ultrasonically cleaned with deionized water to obtain a pre-roughened refrigeration tube body. Hydrophobic fumed silica sol is sprayed onto the surface of the pre-roughened refrigeration tube body with a pressure of 0.15-0.25 MPa using a spray gun. The spray thickness is controlled to be 0.5-1.5 mm. After drying and curing, the surface of the pre-cooled tube body is treated to prevent frost formation.

[0027] First, acid etching roughens the tube surface, creating micron-scale rectangular pits. Then, spraying forms a grafting base of raised hydrophobic nano-silica particles. This modifies the micron-scale rough surface with hydrophobic nano-silica particles, reducing surface energy. Because the hydrophobic nano-silica particles are grafted onto the micron-scale rough surface, a micro-nano-scale ladder structure is formed through the synergistic interaction between nano-scale silica and the micron-scale pre-roughened surface. When a droplet comes into contact with the outer wall of the tube, the actual solid-liquid contact area of ​​the droplet on the micro-nano-scale ladder structure surface is reduced. Furthermore, the large amount of air retained in the micro-nano-scale ladder structure makes it difficult for the droplet to spread on the surface, resulting in a significant reduction in the spread radius of the droplet on the micro-nano-scale ladder structure surface. This prevents the droplet from adhering to the tube surface, thus avoiding the possibility of liquid frost at the source and improving the defrosting and anti-frost effect of the refrigeration pipeline.

[0028] Furthermore, in the frost melting process on the surface of the micro / nano-scale ladder structure, the frost layer first breaks into liquid fragments containing a mixture of ice and water. These fragments then merge through liquid bridges to form larger liquid blocks. Due to the superhydrophobicity and low water adhesion work of the micro / nano-scale ladder structure surface, when combined with the thermal defrosting component, the liquid fragments shrink and easily merge into independently dispersed spherical droplets. These droplets can quickly melt into independently distributed spherical droplets, achieving excellent defrosting efficiency. Moreover, the synergistic effect between the micron-scale rough structure and the hydrophobic nano-silica particles traps a large amount of air within the micro / nano-scale ladder structure, forming an air cushion. This reduces the actual contact area between the spherical droplets formed during defrosting and the surface of the micro / nano-scale ladder structure. Simultaneously, the air cushion acts as a lubricant, allowing the defrosting droplets to roll off quickly and complete the defrosting process.

[0029] The defrosting heat-conducting layer 2 is a heat-conducting silicone pad with a thickness of 0.05-0.1mm. It is used to fill the gap between the spiral guide tube 34 and the refrigeration tube body, enhance the heat conduction efficiency, and make the defrosting process more efficient. The electronic expansion valve 33 and the controller 20 are connected by an electrical signal, and the controller 20 and the frost thickness sensor 4 are also connected by an electrical signal. The controller 20 is a PLC controller, which has an internal defrosting threshold of 0.5 to 2.0 mm for frost thickness. The controller 20 controls the opening of the electronic expansion valve 33 and the flow rate of hot refrigerant based on the frost thickness value transmitted by the frost thickness sensor 4, thereby achieving precise defrosting and reducing energy consumption.

[0030] The spiral guide tube 34 is arranged in an axial spiral configuration. During the refrigeration process, it can guide the refrigerant in a spiral manner. The spiral guide surface generates a forced flow effect on the flowing refrigerant, compelling it to flow along a spiral trajectory. The original laminar flow state is disrupted, transforming into a turbulent or transitional flow state. In the turbulent state, the irregular motion of refrigerant molecules intensifies, and the heat transfer rate between molecules accelerates. At the same time, the turbulence erodes the thermal boundary layer on the tube wall surface, thinning the thermal boundary layer and significantly reducing thermal resistance, thereby enhancing the convective heat transfer effect inside the tube. In addition, the spiral structure extends the actual flow path of the refrigerant inside the refrigeration tube. Compared with a straight tube, for the same tube length, the spiral guide can extend the refrigerant residence time by more than 30%. This design allows the refrigerant more time to exchange heat with the pipe wall, fully releasing or absorbing heat, reducing the loss of refrigerant that has not been adequately heat-exchanged, and improving the adequacy of heat exchange. Furthermore, the spiral guide tube effectively suppresses refrigerant flow deviation and short-circuiting, ensuring the refrigerant is evenly distributed throughout the entire pipe cross-section, avoiding dead zones in localized heat exchange, maximizing the utilization of the refrigerant pipe's heat exchange area, and ensuring uniform heat exchange intensity throughout the pipe wall. In addition, during the spiral flow process, the refrigerant flows tightly against the pipe wall under centrifugal force, further increasing the contact tightness between the refrigerant and the pipe wall, reducing contact thermal resistance. Simultaneously, the spiral structure promotes internal mixing of the refrigerant, preventing excessively large local temperature gradients, and further optimizing heat exchange and refrigeration efficiency. During the hot fluorine de-icing process, the spiral structure enhances convective heat transfer within the pipe, improving the fundamental heat transfer mechanism. For pipes of the same length, the spiral structure allows for a tighter, more tightly wound arrangement, increasing the contact area with the ice layer by over 50% compared to straight pipes. Furthermore, the spiral winding allows the pipe to cover a wider de-icing area, ensuring that the heat transferred by the hot fluorine is more effectively applied to the ice surface, reducing heat loss, improving heat utilization, and thus accelerating the overall de-icing rate. When the hot fluorine flows along the spiral trajectory, the actual flow path is much longer than that of a straight pipe of the same length, significantly extending the residence time of the hot fluorine within the pipe. This allows the hot fluorine to fully release its sensible and latent heat, providing a continuous and stable heat supply for ice melting. When spiral pipes are wound in a spiral pattern, the spacing between different parts of the pipe is uniform, and the heat transferred from the hot fluorine to the pipe wall can be evenly distributed throughout the de-icing area, avoiding local overheating or undercooling that occurs in straight pipes. At the same time, the spiral structure can guide heat to radiate evenly to the periphery of the pipe, so that the ice layer can absorb heat and melt evenly from the surface to the inside and from the periphery of the pipe to a distance, effectively solving the problems of local ice residue and uneven de-icing, and ensuring thorough de-icing.

[0031] The working principle of this invention is as follows: During normal refrigeration operation, the defrosting refrigeration pipe of the present invention circulates refrigerant inside the refrigeration pipe body 1 to achieve heat exchange and complete the refrigeration operation; the surface of the refrigeration pipe body 1 is treated with special anti-frost treatment to reduce the probability of frost formation and ice formation; the frost thickness sensor 4 detects the frost thickness on the surface of the refrigeration pipe body 1 in real time and feeds the detection data back to the controller 20.

[0032] When the controller 20 determines that the frost thickness reaches the preset threshold of 0.5-2mm, it starts the defrosting operation: First, it controls the operation of the hot fluorine defrosting component 3, adjusts the opening of the electronic expansion valve, and transports the high-temperature and high-pressure hot fluorine discharged from the compressor through the spiral guide pipe 34 through the refrigeration pipe body. The sensible heat of the hot fluorine melts the frost layer on the surface of the pipe body. After heat exchange, the hot fluorine flows into the condenser through the hot fluorine return pipe 35 to complete the hot fluorine cycle, thereby completing the entire defrosting process.

[0033] Example 1 A defrosting refrigeration pipeline includes a pipe body assembly 10 and a controller 20, which are electrically connected. The pipe body assembly 10 includes a refrigeration pipe body 1, with a defrosting heat-conducting layer 2 on the inner wall of the refrigeration pipe body 1. The refrigeration pipe body 1 has a hollow structure, with an internal cavity serving as a refrigerant flow channel 11. A hot refrigerant defrosting assembly 3 is also inserted into the refrigerant flow channel 11. The hot refrigerant defrosting assembly 3 includes a defrosting assembly fixing bracket 31 located at the inlet end of the refrigeration pipe body 1. A hot refrigerant delivery pipe 32 is fixedly mounted on the defrosting assembly fixing bracket 31. The inlet end of the hot refrigerant delivery pipe 32 is connected to the compressor exhaust pipe of the refrigeration system, and the outlet end is connected to a spiral guide pipe 34 via an electronic expansion valve 33. The end of the spiral guide pipe 34 is connected to the condenser of the refrigeration system via a hot refrigerant return pipe 35. An ice and frost thickness sensor 4 is also provided on the outer wall surface of the refrigeration pipe body 1.

[0034] The body of the refrigeration pipe 1 is made of brass, and its surface is treated with an anti-frost treatment. The specific steps of the anti-frost treatment are as follows: (1) Take 1.5 parts by weight of fumed nano silica and disperse it in 35 parts of anhydrous ethanol to obtain a fumed nano silica suspension. Add 0.7 parts of trimethylethoxysilane slowly to the fumed nano silica suspension and stir to obtain a hydrophobic nano silica solution. (2) By weight, 0.45 parts of hydrochloric acid solution with a concentration of 0.01 mol / L, 0.45 parts of deionized water, 3 parts of anhydrous ethanol and 1.3 parts of methyltriethoxysilane are mixed sequentially and stirred to obtain a mixed modified solution; (3) Slowly add the mixed modified liquid to the hydrophobic nano silica solution, and stir magnetically at room temperature until the reaction is complete, and finally obtain hydrophobic gas phase nano silica sol. (4) The refrigeration tube body is sequentially immersed in hydrofluoric acid solution with a concentration of 5 mol / L and hydrochloric acid solution with a concentration of 2 mol / L for 10 min and 30 min respectively. After being removed, it is ultrasonically cleaned with deionized water to obtain a pre-roughened refrigeration tube body. Hydrophobic gas phase nano silica sol is sprayed onto the surface of the pre-roughened refrigeration tube body with a pressure of 0.2 MPa using a spray gun. The spray thickness is controlled to be 1.0 mm. After drying and curing, the surface anti-frost treatment of the pre-cooled tube body is completed.

[0035] The defrosting heat-conducting layer 2 is a heat-conducting silicone pad with a thickness of 0.08 mm. It is used to fill the gap between the spiral guide tube 34 and the refrigeration tube body, enhance the heat conduction efficiency, and make the defrosting process more efficient. The electronic expansion valve 33 and the controller 20 are connected by an electrical signal, and the controller 20 and the frost thickness sensor 4 are also connected by an electrical signal. The controller 20 is a PLC controller, which has an internal defrosting threshold of 1.5mm frost thickness. The controller 20 controls the opening of the electronic expansion valve 33 and the flow rate of hot refrigerant based on the frost thickness value transmitted by the frost thickness sensor 4, thereby achieving precise defrosting and reducing energy consumption.

[0036] The spiral guide tube 34 is arranged in an axial spiral.

[0037] Comparison Example Compare with Example 1 This comparative example uses a conventional refrigeration pipe body 1 as the refrigeration pipe, without adding the hot fluorine defrosting assembly 3, controller 20, frost thickness sensor 4 and other hardware facilities of the present invention. Compare with Example 2 This comparative example is basically the same as Embodiment 1 of the present invention, except that the surface of the cooling pipe body 1 is not treated with anti-frost, and the other parts are the same. Compare with Example 3 This comparative example is basically the same as Embodiment 1 of the present invention, except that the defrosting heat-conducting layer 2 is not provided on the inner wall of the refrigeration pipe body 1, and the other parts are the same. Compare with Example 4 This comparative example is basically the same as Embodiment 1 of the present invention, except that a regular straight pipe is used instead of the spiral guide tube 34 of the present invention, and the other parts are the same; Performance tests were performed on Example 1 and Comparative Examples 1-4 of the present invention, and the test results are shown in the table below: I. Performance Testing Methods To accurately verify the performance of the refrigeration piping system of this invention in terms of anti-frost formation, defrosting efficiency, heat exchange performance, and energy consumption, uniform performance tests were conducted on Example 1 and Comparative Examples 1-4. The tests were carried out under ambient temperature of 25°C, relative humidity of 85%, and rated operating conditions of the refrigeration system. The specific test methods for each test index are as follows: 1. Frosting rate detection The refrigeration system was started and ran continuously and stably for 4 hours. The frost thickness at different locations on the outer wall of the refrigeration pipe was measured every 30 minutes using a high-precision laser thickness gauge (10 measurement points were selected evenly). The average frost thickness at each measurement point was calculated, and the average frost thickness per hour (mm / h) was used as the evaluation index for the frost rate.

[0038] 2. Defrosting efficiency test When the frost thickness on the surface of the refrigerant pipe reaches the preset defrosting threshold of 1.5mm, the defrosting program is started. The defrosting process is monitored in real time using a high-speed camera and a laser thickness gauge. The total time (s) for the frost to completely melt is recorded as the defrosting time index. At the same time, the thickness of frost melted per unit time (mm / s) is calculated, which is the core index of defrosting efficiency. Defrosting efficiency = 1.5mm / total defrosting time.

[0039] 3. Heat exchange efficiency testing When the refrigeration system is operating stably (without frost), the refrigerant temperature and flow rate at the inlet and outlet of the refrigeration pipe are detected using temperature and flow sensors, respectively. Combined with the refrigerant's specific heat capacity, the heat transfer of the refrigeration pipe is calculated using the formula Q=cmΔTq (where c is the refrigerant's specific heat capacity, m is the refrigerant's mass flow rate, ΔT is the inlet and outlet temperature difference, and q is a correction factor). Simultaneously, the heat transfer coefficient (W / (m²)) of each sample under the same operating conditions is measured. K) is used as an indicator for evaluating heat exchange efficiency; the higher the value, the better the heat exchange performance.

[0040] 4. Defrosting energy consumption test Throughout the defrosting process, a power meter is used to monitor the total power consumption of the refrigeration system during the defrosting phase in real time. Combined with the defrosting time, the energy consumption per unit defrosting thickness (kW) is calculated. (h / mm), that is, defrosting energy consumption = total defrosting power consumption / 1.5mm. The lower the value, the better the defrosting energy consumption control effect.

[0041] 5. Defrosting uniformity test After the defrosting process is completed, a visual inspection device is used to scan the entire surface of the outer wall of the refrigerant pipe and count the percentage (%) of the unmelted frost residue area to the total surface area. The defrosting residue rate is 0, which means that the defrosting is complete and the uniformity is optimal.

[0042] Table 1 Performance Test Results

[0043] Detection data verification and analysis 1. The frosting rate of 0.12 mm / h in Example 1 of the present invention is much lower than that of 0.68 mm / h in Control Example 2. The defrosting time is shorter, the energy consumption is lower, and the residual rate is 0, which fully verifies the core role of the anti-frosting treatment of the micro-nano scale ladder structure.

[0044] In contrast to Example 2, no anti-frost treatment was performed. The pipe surface lacked hydrophobic micro-nano structures, allowing water vapor to spread, adhere, and frost quickly, significantly increasing the frost rate. During the defrosting process, the frost layer adhered strongly to the pipe surface, increasing defrosting time and making it prone to local residues. Furthermore, more energy was required to melt the thick frost layer.

[0045] In Example 1, a micro-nano ladder structure is formed by acid etching and hydrophobic nanosol spraying, which reduces the solid-liquid contact area and the remaining air layer prevents water vapor from adhering, thus reducing the frosting rate from the source. During defrosting, the frost layer easily breaks into droplets, and the superhydrophobic surface makes the droplets roll off quickly, achieving defrosting without residue and reducing defrosting energy consumption.

[0046] 2. The frost rate of Example 1 and Comparative Example 3 is basically the same, indicating that the defrosting heat-conducting layer does not affect the anti-frost effect. However, the defrosting efficiency of Example 1 is significantly higher than that of Comparative Example 3, and the defrosting energy consumption and residual rate are also lower, which verifies the heat conduction enhancement effect of the defrosting heat-conducting layer.

[0047] In contrast to Example 3, no defrosting heat-conducting layer was installed. There was a gap between the spiral guide tube and the refrigerant tube body. The heat transferred by the refrigerant would be lost in the gap, reducing the heat transfer efficiency. It would take longer to transfer the heat to the frost layer on the outer wall of the tube body. Not only did the defrosting time increase, but the energy consumption also increased due to insufficient heat utilization. At the same time, uneven heat transfer could easily cause slow melting of local ice layers, resulting in defrosting residue.

[0048] In Example 1, the defrosting heat-conducting layer fills the gaps, eliminating contact thermal resistance and allowing the heat from the hot refrigerant to be transferred quickly and evenly to the refrigeration pipe body, greatly improving defrosting efficiency while reducing heat loss, lowering energy consumption, and achieving uniform defrosting without residue.

[0049] 3. The defrosting efficiency of Example 1 of the present invention, 0.033 mm / s, is much higher than that of Control Example 4, 0.016 mm / s, and the defrosting residue rate is 0, while that of Control Example 4 is 5.8%, verifying the structural advantages of the spiral guide tube during defrosting. Compared with Example 4, which uses a regular straight pipe, the contact area with the ice layer is small, the heat radiation range is limited, and the hot fluorine stays in the straight pipe for a short time, resulting in insufficient heat release and a slow defrosting rate. At the same time, the heat distribution of the straight pipe is uneven, which can easily lead to local overheating and local undercooling, resulting in a large amount of defrosting residue.

[0050] The spiral guide tube in Example 1 increases the hot fluorine contact area by more than 50%, prolongs the hot fluorine residence time, fully releases heat and radiates it evenly, and melts the ice layer evenly from the surface to the inside and from the periphery to the distance, greatly improving the defrosting efficiency and leaving no residue.

[0051] The heat transfer coefficient of Example 1 is 890 W / (m²) K) is much higher than 650 W / (m²) in Control Example 4. K), verifying the enhancing effect of the spiral guide tube on refrigeration heat transfer: The spiral guide tube disrupts the laminar flow of the refrigerant, transforming it into turbulent flow. This scours the thermal boundary layer on the tube wall, thinning it and reducing thermal resistance. Simultaneously, it extends the refrigerant flow path, increasing the residence time by more than 30%, and suppresses flow deviation and short-circuiting, resulting in uniform refrigerant distribution, maximizing the utilization of the heat exchange area, and significantly improving the heat transfer coefficient. In contrast, the refrigerant in ordinary straight tubes is in a laminar flow state, with a thick thermal boundary layer, low heat transfer efficiency, and dead zones.

[0052] 4. Comparative Example 1 of this invention uses conventional refrigerant pipes, without a hot-air refrigerant defrosting assembly, controller, frost thickness sensor, or anti-frost treatment. The frost rate is as high as 0.85 mm / h, and the frost thickness reaches 3.4 mm after 4 hours of operation. The heat transfer coefficient is only 520 W / (m²). K) decreased by 41.6% compared to Example 1, which fully verifies the synergistic superiority of the overall system of the present invention.

[0053] Example 1, through the synergistic effect of various structures and processes, reduces frost formation at the source, monitors frost thickness in real time, accurately initiates the defrosting process, and completes defrosting efficiently with low energy consumption, while ensuring high heat exchange efficiency during the refrigeration stage. This solves the core problems of traditional refrigeration pipes, such as rapid frost formation, poor defrosting effect, low heat exchange efficiency, and high energy consumption. In contrast, Example 1 has no active defrosting capability, and frost formation continuously affects heat exchange efficiency, ultimately leading to a sharp increase in energy consumption and a significant decrease in refrigeration effect of the refrigeration system.

[0054] 5. Verification of the accuracy of intelligent control Example 1 uses a PLC controller combined with a frost thickness sensor to set a defrost threshold of 1.5mm, achieving precise defrosting with a defrosting energy consumption of only 0.012kW. The h / mm is significantly lower than that of the control examples. The principle is that the controller precisely controls the opening of the electronic expansion valve based on sensor data, adjusts the hot refrigerant flow rate, and initiates defrosting only when the frost thickness reaches the threshold. Furthermore, it supplies hot refrigerant on demand, avoiding the problems of blind defrosting and excessive energy supply in traditional defrosting methods, thus achieving precise control of energy consumption.

[0055] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A defrosting and de-icing refrigeration pipeline, comprising a pipe body assembly and a controller, characterized in that: The pipe assembly and the controller are electrically connected. The pipe assembly includes a refrigeration pipe body with a defrosting heat-conducting layer on its inner wall. The refrigeration pipe body has a hollow structure with an internal cavity serving as a refrigerant flow channel. A hot refrigerant defrosting assembly is also inserted into the refrigerant flow channel. The hot refrigerant defrosting assembly includes a defrosting assembly mounting bracket located at the inlet end of the refrigeration pipe body. A hot refrigerant delivery pipe is fixedly mounted on the defrosting assembly mounting bracket. The inlet end of the hot refrigerant delivery pipe is connected to the compressor exhaust pipe of the refrigeration system, and the outlet end is connected to a spiral guide pipe via an electronic expansion valve. The end of the spiral guide pipe is connected to the condenser of the refrigeration system via a hot refrigerant return pipe. An ice and frost thickness sensor is also provided on the outer wall surface of the refrigeration pipe body.

2. The refrigeration pipeline for defrosting and de-icing according to claim 1, characterized in that: The body of the refrigeration pipe is made of brass, and its surface is treated with an anti-frost coating. The specific steps of the anti-frost coating treatment are as follows: (1) Take 1 to 2 parts by weight of fumed nano silica and disperse it in 30 to 40 parts of anhydrous ethanol to obtain a fumed nano silica suspension. Add 0.6 to 0.8 parts of trimethylethoxysilane slowly to the fumed nano silica suspension and stir to obtain a hydrophobic nano silica solution. (2) By weight, 0.4 to 0.5 parts of hydrochloric acid solution with a concentration of 0.01 mol / L, 0.4 to 0.6 parts of deionized water, 2 to 4 parts of anhydrous ethanol and 1 to 1.5 parts of methyltriethoxysilane are mixed sequentially and stirred to obtain a mixed modified solution; (3) Slowly add the mixed modified liquid to the hydrophobic nano silica solution, and stir magnetically at room temperature until the reaction is complete, and finally obtain hydrophobic gas phase nano silica sol. (4) The refrigeration tube body is sequentially immersed in hydrofluoric acid solution with a concentration of 5 mol / L and hydrochloric acid solution with a concentration of 2 mol / L for 10 min and 30 min respectively. After being removed, it is ultrasonically cleaned with deionized water to obtain a pre-roughened refrigeration tube body. Hydrophobic fumed silica sol is sprayed onto the surface of the pre-roughened refrigeration tube body with a pressure of 0.15-0.25 MPa using a spray gun. The spray thickness is controlled to be 0.5-1.5 mm. After drying and curing, the surface of the pre-cooled tube body is treated to prevent frost formation.

3. A defrosting and de-icing refrigeration pipeline according to claim 1, characterized in that: The spiral guide tube is arranged in an axial spiral configuration.

4. A defrosting and de-icing refrigeration pipeline according to claim 1, characterized in that: The defrosting heat-conducting layer is a thermally conductive silicone pad, and the thickness of the defrosting heat-conducting layer is 0.05-0.1mm.

5. A defrosting and de-icing refrigeration pipeline according to claim 1, characterized in that: The electronic expansion valve and the controller are connected by an electrical signal, and the controller and the frost thickness sensor are connected by an electrical signal.

6. A defrosting and de-icing refrigeration pipeline according to claim 5, characterized in that: The controller is a PLC controller, which has a defrost threshold inside, the defrost threshold being 0.5 to 2.0 mm of frost thickness.

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