Defrosting device and defrosting method

Abstract

The invention provides a defrosting device and a defrosting method.The defrosting device comprises an air supply static pressure air pipe used for storing dry air, and the air supply static pressure air pipe is arranged on one side of a calandria assembly; the input end of the jet pipe assembly is connected with the output end of the air supply static pressure air pipe, and the output end of the jet pipe assembly faces the calandria assembly; the air guide assembly is arranged adjacent to the calandria assembly, the air guide assembly is used for guiding the dry airflow blown out by the jet pipe assembly so that the dry airflow can be restrained to the calandria assembly and an air curtain can be formed, and the air curtain prevents external air from flowing to the calandria assembly; through the air supply static pressure air pipe, the air uniformizing jet flow air opening and the air guide assembly, the frosting degree of the calandria refrigeration house is greatly reduced, and no frost can be achieved under the ideal condition.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of cold storage defrosting, in particular to a defrosting device and a defrosting method. BACKGROUND

[0002] In the field of refrigeration engineering, the frosting phenomenon on the surface of the evaporative discharge pipe fin of the cold storage is a core problem that has existed for a long time and seriously affects the system energy efficiency and stability. As the core of cold exchange of the system, the surface temperature of the discharge pipe must be lower than the dew point temperature of the air in the warehouse, and this temperature difference drives the continuous condensation and freezing of water vapor in the air on the fin surface, forming a porous frost layer.

[0003] The formation and development of the frost layer is a dynamic process, and its morphology and thickness are affected by the coupling of multiple physical field parameters such as relative humidity in the warehouse, air flow rate, discharge pipe surface temperature and running time. As a low thermal conductivity material (usually in the range of 0.1-0.4 W / (m·K)), the accumulation of the frost layer introduces a significant additional thermal resistance. Studies have shown that for every 1 mm increase in frost layer thickness, the heat transfer thermal resistance can increase by 20% to 30%, resulting in a decrease in evaporation temperature, an increase in compressor compression ratio, a significant deterioration of system performance coefficient (COP), and an increase in energy consumption by 10% to 30%. At the same time, the frost layer will physically block the air flow channel between the fins, causing a sharp decrease in air flow. For example, for fins with a standard spacing of 5 mm, when the frost thickness reaches 3 mm, the flow area decreases by more than 50%, the air flow resistance increases exponentially, further exacerbating the decline in heat exchange performance. In addition, the continuous accumulation of frost also brings mechanical load, which poses a risk of deformation of the fins or sagging of the discharge pipe structure, and causes fluctuations in the warehouse temperature due to periodic defrosting, which threatens the quality of stored goods.

[0004] To address this stubborn problem, the industry has developed a variety of defrosting technologies, but all have inherent defects:

[0005] Electric heating defrosting: heating the discharge pipe through direct Joule effect, the energy conversion path is "high-grade electric energy → heat energy", which is poor in energy economy, and the defrosting energy consumption accounts for one fourth of the total system energy consumption. Local overheating and unevenness during the heating process can cause thermal stress damage, and there are potential electrical safety hazards.

[0006] Hot gas defrosting: a kind of internal balancing technology of heat pump cycle, which directs the high-temperature refrigerant vapor at the outlet of the compressor to the evaporator to heat and defrost. This method requires the addition of complex valves and piping systems, increasing initial investment and maintenance complexity. The refrigeration cycle is interrupted during the defrosting period, and the warehouse temperature rises, which is difficult to avoid, and in a multi-loop system, defrosting is not complete due to uneven flow distribution.

[0007] Water defrosting: using the convection heat transfer of sensible heat water to realize rapid defrosting, but it needs a complete water treatment, pumping and spraying system, and there are water source, corrosion and anti-freezing requirements. The huge heat shock (ΔT>60℃) tests the fatigue life of the pipe material and the weld, and the humidity in the warehouse rises sharply after defrosting, which may accelerate the subsequent frosting process.

[0008] Natural defrosting and artificial defrosting: the former relies on environmental heat, and the defrosting time is long, and the warehouse temperature control is completely out of control; the latter purely relies on manpower, and the operation efficiency is low, and there is a risk of operation safety and equipment damage, and both cannot meet the strict requirements of modern cold chain logistics for continuous, stable and automatic operation.

[0009] In summary, the existing defrosting technology has not fundamentally solved the inherent contradiction between high energy consumption, warehouse temperature fluctuation, system complexity and equipment reliability. SUMMARY

[0010] Based on the above problems, the present application provides a defrosting device and a defrosting method, which greatly reduces the frosting degree of the pipe warehouse through the supply air static pressure air pipe, the air distribution jet flow port and the air guide assembly, and can realize frost-free under ideal conditions.

[0011] In a first aspect, the present application provides a defrosting device, comprising:

[0012] A supply air static pressure air pipe, the supply air static pressure air pipe contains dry air, and the supply air static pressure air pipe is arranged on one side of the pipe assembly; the dew point temperature of the dry air is lower than the evaporation temperature of the cold storage refrigerator;

[0013] A jet pipe assembly, the input end of the jet pipe assembly is connected to the output end of the supply air static pressure air pipe, the output end of the jet pipe assembly faces the pipe assembly, and the output end of the jet pipe assembly blows dry air flow towards the pipe assembly;

[0014] An air guide assembly is arranged adjacent to the pipe assembly, the air guide assembly is used to guide the dry air flow blown by the jet pipe assembly, so that the dry air flow can be constrained to the pipe assembly and form an air curtain, and the air curtain blocks the flow of external air to the pipe assembly.

[0015] Preferably, the air guide assembly comprises a first air guide structure and a second air guide structure, the first air guide structure and the second air guide structure are arranged on the first surface and the second surface of the pipe assembly respectively, so as to guide the dry air flow output by the jet pipe assembly to flow through the surface of the pipe assembly.

[0016] Preferably, the first air guide structure comprises a plurality of first air guide plates arranged at equal intervals, and the connecting ends of the first air guide plates are connected to the first surface of the pipe assembly; and the second air guide structure comprises a plurality of second air guide plates arranged at equal intervals, and the connecting ends of the second air guide plates are connected to the second surface of the pipe assembly.

[0017] Preferably, the first air guide plate and the second air guide plate have an airfoil profile, and the chord length of the airfoil profile gradually narrows in the direction of the airflow; and the chord line of the airfoil profile forms an angle of 12° to 17° with the horizontal direction, and the opening of the angle is towards the air supply static pressure air pipe.

[0018] Optionally, the first air guide plate and the second air guide plate are straight plates, and form an installation angle of 12° to 17° with the surface of the refrigeration pipe; and the opening of the installation angle is towards the air supply static pressure air pipe.

[0019] Preferably, the first air guide plate and the second air guide plate are arranged in mirror image along the pipe assembly.

[0020] Alternatively, the first projection and the second projection are arranged alternately, and the spacing between adjacent first projection and second projection is a preset value; wherein the first projection is the projection of the first air guide plate on the pipe assembly, and the second projection is the projection of the second air guide plate on the pipe assembly.

[0021] Preferably, the jet pipe assembly comprises a plurality of uniform air jet air outlets, the input end of each uniform air jet air outlet is connected to the output end of the air supply static pressure air pipe, and the output end of the uniform air jet air outlet is towards the pipe assembly; and the jet direction of the outlet center line of the uniform air jet air outlet forms an angle of 12° to 17° with the horizontal direction.

[0022] Preferably, the input end of the uniform air jet air outlet extends to form a flow guide structure, and the flow guide structure is inserted into the air supply static pressure air pipe.

[0023] Preferably, the flow guide structure is a left-cut flow guide port or a right-cut flow guide port; wherein the aperture of the flow guide port is larger than the aperture of the output port of the uniform air jet air outlet.

[0024] Preferably, the defrosting device further comprises: a return air static pressure air pipe, which is arranged on one side of the pipe assembly and is arranged opposite to the air supply static pressure air pipe, and the input end of the return air static pressure air pipe is towards the pipe assembly.

[0025] The defrosting device further comprises:

[0026] a dehumidification device for dehumidifying input air to obtain dry air;

[0027] An air supply pipeline, one end of which is connected to the air outlet of the dehumidifying device, and the other end of which is connected to the input end of the air supply static pressure air pipe;

[0028] An air return pipeline, one end of which is connected to the air return static pressure air pipe, and the other end of which is connected to the air inlet of the dehumidifying device.

[0029] In a second aspect, the present application provides a defrosting method, comprising:

[0030] Dry air in the air supply static pressure air pipe is uniformly ejected at a set angle towards the row pipe assembly through the jet pipe assembly;

[0031] The ejected dry air is guided by the air guide assembly to flow through the surface of the row pipe assembly, forming a dry air film, and the dry air film blocks external air from flowing to the row pipe assembly.

[0032] Compared with the prior art, the present application has at least the following beneficial effects: through the air supply static pressure air pipe, the air uniformization jet air outlet and the air guide assembly, the row pipe cold storage realizes a fundamental change from periodic defrosting to continuous defrosting, and the long-standing frosting problem of the row pipe cold storage is completely solved. The huge power consumption caused by electric heating defrosting (the defrosting power consumption accounts for 15%-25% of the total power consumption) and the additional power consumption of the compressor caused by hot gas defrosting are eliminated, the row pipe fins are always kept in a frost-free or thin frost state, the extremely high heat transfer coefficient (high thermal conductivity of aluminum) is maintained, the evaporation temperature can be correspondingly increased, the operation efficiency (COP value) of the compressor is greatly improved, and the energy consumption is significantly reduced; since periodic and high-power defrosting operations are not required, the temperature in the cold storage can be kept stable, and the large fluctuation (5-10℃) of the temperature in the cold storage caused by the traditional defrosting method is avoided; the safety hazards such as electric leakage and fire caused by electric heating defrosting are eliminated, the thermal stress fatigue and corrosion of the row pipe and the fins caused by the large temperature change due to hot gas defrosting and water defrosting are avoided, and the overall service life of the evaporation row pipe and the refrigeration system is effectively prolonged. BRIEF DESCRIPTION OF DRAWINGS

[0033] Figure 1 is a defrosting device structure schematic diagram of an embodiment of the present application;

[0034] Figure 2 is a partial enlarged view of A in the present application; Figure 1

[0035] Figure 3 is another defrosting device structure schematic diagram of an embodiment of the present application;

[0036] Figure 4 is a partial enlarged view of B in the present application; Figure 3

[0037] ​​Figure 5 is a guide flow simulation effect schematic diagram of the air guide assembly of the embodiment of the present application when it is mirror-symmetrical;

[0038] Figure 6 is another guide flow simulation effect schematic diagram of the air guide assembly of the embodiment of the present application when it is mirror-symmetrical;

[0039] Figure 7 is a guide flow simulation effect schematic diagram of the air guide assembly of the present application when the preset value = 0;

[0040] Figure 8 is a guide flow simulation effect schematic diagram of the air guide assembly of the present application when the preset value > 200;

[0041] Figure 9 is a structure schematic diagram of the air supply static pressure air pipe and the air uniformization jet flow air outlet of the embodiment of the present application;

[0042] Figure 10 is a structure schematic diagram of the air uniformization jet flow air outlet of the embodiment of the present application;

[0043] Figure 11 is a structure schematic diagram of the air uniformization jet flow air outlet of the embodiment of the present application;

[0044] Figure 12 is another structure schematic diagram of the air uniformization jet flow air outlet of the embodiment of the present application.

[0045] Figure 13 is an application scenario schematic diagram of the defrosting device of the embodiment of the present application.

[0046] In the figure: 1, dehumidification equipment; 2, air supply static pressure air pipe; 3, air uniformization jet flow air outlet; 4, exhaust pipe assembly; 41, exhaust pipe; 42, fin; 5, air guide assembly; 51, first air guide plate; 52, second air guide plate; 6, return air static pressure air pipe; 7, air supply pipeline; 8, return air pipeline; 9, air valve. DETAILED DESCRIPTION

[0047] Example implementations will now be described more fully with reference to the accompanying drawings. Example implementations may, however, be implemented in many different forms and should not be construed as limited to the implementations set forth herein; rather, these implementations are provided so that this disclosure will be thorough and complete, and will fully convey the inventive concept to those skilled in the art.

[0048] It should be noted that the embodiments described below are examples only, and are not intended to limit the present application, and the embodiments described are only a part of the embodiments of the present application, and are not all the embodiments. Based on the embodiments in the present application, any alternative, modification, equivalent method and scheme within the spirit, principle and scope of the present application defined by the claims, and all other embodiments obtained by those of ordinary skill in the art without creative labor, are within the scope of protection of the present application.

[0049] In the description of the present application, "first", "second", "third", and similar words do not represent any order, number or importance, but are only used to distinguish different components. Similarly, "one" or "a" and similar words do not represent a quantity limit, but represent the existence of at least one. "Include" or "contain" and similar words mean that the elements or objects appearing before "include" or "contain" cover the elements or objects listed after "include" or "contain" and their equivalents, and do not exclude other elements or objects. "Connected" or "connected" and similar words are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect.

[0050] In the description of the present application, the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like indicate the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application. In addition, when using two sides, outer sides, upper and lower position terms, it should be understood that they are only used for easy understanding and description, taking into account that the structure can be oriented to other positions.

[0051] In the description of the present application, unless otherwise explicitly specified and limited, the technical terms or scientific terms used should be understood as the usual meaning understood by those skilled in the art in the field to which the present application belongs, and the terms "mounting", "connecting", "connecting" and the like should be understood broadly, for example, it can be fixed connection, or detachable connection, or abutting connection or integral connection; for those of ordinary skill in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0052] The embodiments of the present application are intended to introduce and explain the structural composition of the AAAA and the cooperation relationship between each component structure. Unless otherwise specified, the size, material and manufacturing process of each component in the AAAA in the embodiments of the present application can be selected according to the specific circumstances, and no special limitation and explanation is made here.

[0053] Further, in order to make the public have a better understanding of the present application, in the following detailed description of the present application, some specific details are described in detail. The description of these details can also be completely understood by those skilled in the art without the description of these details.

[0054] Referring to the drawings Figures 1-4 The embodiments of the present application provide a defrosting device applied to defrosting of a pipe assembly 4 of a pipe freezer; comprising: a supply static pressure air pipe 2, a jet pipe assembly and the jet pipe assembly.

[0055] The supply static pressure air pipe 2 contains dry air, and is arranged on one side of the pipe assembly 4; the dew point temperature of the dry air is lower than the evaporating temperature of the freezer.

[0056] The jet pipe assembly is connected to the output end of the supply static pressure air pipe 2, and the output end of the jet pipe assembly faces the pipe assembly 4; and the output end of the jet pipe assembly blows dry air flow towards the pipe assembly 4;

[0057] The air guide assembly 5 is arranged adjacent to the pipe assembly 4, and is used to guide the dry air flow blown by the jet pipe assembly, so that the dry air flow can be constrained to the pipe assembly 4 and form an air curtain, and the air curtain blocks the outside air from flowing to the pipe assembly 4.

[0058] The air guide assembly 5 includes a first air guide structure and a second air guide structure, and the first air guide structure and the second air guide structure are arranged on the first surface and the second surface of the pipe assembly 4, respectively, to guide the dry air flow output by the jet pipe assembly to flow through the surface of the pipe assembly 4.

[0059] The pipe assembly 4 includes a pipe 41 and a fin 42, and the pipe assembly 4 is used as a refrigeration core component of the cold storage. The pipe assembly 4 is formed by the pipe 41 and the fin 42. The pipe 41 is a continuous metal pipe (usually made of aluminum, copper or galvanized steel), and the pipe 41 is arranged in a serpentine shape. The core function of the serpentine structure is to prolong the residence path of the refrigerant in the cold storage, to increase the contact time with the air, and to enhance the heat exchange efficiency. The pipe 41 is used to circulate the refrigerant (such as ammonia, freon or CO2), and the pipe wall exchanges heat with the outside air. The refrigerant absorbs heat and evaporates (or releases heat and condenses), so as to achieve the cooling of the air in the cold storage (or the heating in the defrosting stage). The fin 42 is a thin metal sheet (usually made of aluminum, light weight and good heat conductivity), which is arranged in a dense parallel manner on the surface of the pipe 41, and forms a large area of heat dissipation / absorption surface. The serpentine structure of the pipe 41 extends along the length direction of the cold storage, and the fin 42 is densely distributed perpendicular to the axis of the pipe.

[0060] The dry air stored in the supply static pressure air pipe 2 has a dew point temperature lower than the evaporation temperature of the cold storage refrigeration machine, and is sent out through the jet pipe assembly at a set angle. After the dry air sent out by the jet pipe assembly reaches the vicinity of the pipe assembly 4, the air is guided and constrained by the air guide assembly 5, and is guided to the end of the pipe assembly 4 or a set distance, so as to form a specific airflow around the pipe assembly 4. The specific airflow wraps the pipe assembly 4, accurately acts on the surface of the fin 42 and the pipe 41, and forms a dry air field in the vicinity of the pipe assembly 4, which isolates the wet air from the cold storage door infiltration and the product emission in the cold storage. In addition, the dry air field can be started at irregular intervals according to the actual situation, to resolve the frost layer on the pipe by high-speed jet flow, to avoid or control the frosting on the surface of the pipe, and to solve the problems of fast frosting, slow defrosting and difficult defrosting of the pipe. Good cold storage environment is created, and the operation cost of the pipe cold storage is reduced.

[0061] In a possible implementation, the first air guide structure includes a plurality of first air guide plates 51 arranged at equal intervals, and the connection end of the first air guide plate 51 is connected to the first surface of the pipe assembly 4.

[0062] The second air guide structure includes a plurality of second air guide plates 52 arranged at equal intervals, and the connection end of the second air guide plate 52 is connected to the second surface of the pipe assembly 4. The first air guide plate 51 and the second air guide plate 52 jointly form an air duct for guiding the airflow to flow through the surface of the pipe assembly 4.

[0063] In a preferred embodiment, the first air guide plate 51 and the second air guide plate 52 have a wing-shaped profile, and the chord length of the wing-shaped profile gradually narrows along the airflow direction. The chord line of the wing-shaped profile forms an angle of 12° to 17° with the horizontal direction, and the opening of the angle is towards the supply static pressure air pipe 2. The transverse coverage range of the widest part of the first air guide plate 51 and the second air guide plate 52 is consistent with the projection width of the pipe assembly 4 perpendicular to the airflow direction.

[0064] In another embodiment, the first air deflector 51 and the second air deflector 52 can also be straight air deflectors; the installation included angle between the air deflectors and the surface of the refrigeration pipe 4 is 12° to 17°; the openings of the installation included angle are all directed towards the air supply static pressure air pipe 2. The first included angle between the first air deflector 51 and the first surface of the pipe assembly 4 is 12° to 17°; the second included angle between the second air deflector 52 and the second surface of the pipe assembly 4 is 12° to 17°; the openings of the first included angle and the second included angle are all directed towards the air supply static pressure air pipe 2, and the outlet is directed towards the inside of the warehouse; the first air deflector 51 and the second air deflector 52 are installed on the pipe assembly 4 through the fixing frame, so that the air deflectors are suspended near the upper and lower surfaces of the pipe assembly 4; so that the airflow in the upstream flows along the pipe assembly 4 to the downstream.

[0065] The first air deflector 51 and the second air deflector 52 are arranged in pairs near the upper and lower surfaces of the pipe assembly 4, and jointly form a tapered flow channel; the chord length near the air supply static pressure air pipe 2 end is the largest, forming a flow channel entrance horn, which gradually narrows along the airflow path to the side of the cold storage warehouse, can maximize the capture of dry air from the air supply jet flow nozzle 3, and effectively reduce the airflow dispersion; the airfoil-shaped streamline design can efficiently guide the airflow, maximize the reduction of vortex and energy loss, and constrain and concentrate the airflow to the gap between the fins 42 of the pipe assembly 4, so that the airflow enters the tapered flow channel formed by the air deflectors and the surface of the pipe 41; according to the principle of fluid mechanics, the flow rate of the airflow will be significantly accelerated when flowing through the flow channel with gradually decreasing cross-sectional area, and this acceleration effect gives the airflow higher kinetic energy, so that it can strongly penetrate the dense fin 42 gap of the pipe assembly 4, and ensure that the deep back of the pipe 41 can also be effectively covered by the airflow, completely eliminating the defrosting dead angle. The accelerated airflow is shot out at high speed from the narrow opening of the flow channel, and flows along the surface of the pipe at the angle set by the air deflector, forming a concentrated, high-speed and directionally stable quasi-linear dry air curtain; this air curtain not only has high defrosting efficiency, but also can more effectively isolate the humid air in the warehouse and delay frosting.

[0066] The position setting of the first air deflector 51 and the second air deflector 52 of the present application includes at least two cases (1)-(2).

[0067] (1) The first air deflector 51 and the second air deflector 52 are mirror image arranged along the pipe assembly 4; the spacing between adjacent air deflectors is determined according to the wind speed, the size characteristics of the air deflector and the outlet diffusion angle of the airflow; the larger the spacing, the more dry air escapes, and the smaller the spacing, the higher the overall cost; the preferred range is between 300mm to 500mm.

[0068] (2) The first projection and the second projection are staggered, and the interval between adjacent first projection and second projection is a preset value; wherein the first projection is the projection of the first deflector 51 on the pipe assembly 4, the second projection is the projection of the second deflector 52 on the pipe assembly 4, and the preset value can be greater than 0 or less than 0, preferably 0. The smaller the threshold value, the more windshields required, the higher the cost, the larger the threshold value, the larger the gap, and the more dry air escapes.

[0069] Attached Figure 5 to the attached Figure 8 The simulation effect diagram of the air deflector assembly.

[0070] Attached Figure 5 and attached Figure 6 In the first air deflector 51 and the second air deflector 52 are mirror symmetrically arranged along the pipe assembly 4, attached Figure 5 The interval between adjacent first air deflectors 51 or second air deflectors 52 is the first interval; attached Figure 6 The interval between adjacent first air deflectors 51 or second air deflectors 52 is the second interval; wherein the second interval is greater than the first interval.

[0071] Attached Figure 5 In the first air deflector 51 and the second air deflector 52 are mirror symmetrically arranged along the pipe assembly 4, forming a plurality of completely symmetrical and independent tapered flow channels on the upper and lower sides of the pipe assembly 4. The airflow from the uniform jet nozzle 3 is efficiently captured, accelerated and guided by these symmetrical flow channels, thereby generating symmetrical and balanced high-speed airflow on the upper and lower surfaces of the pipe assembly 4. After flowing through the pipe surface, the two airflows converge in the middle area on the other side of the pipe, forming a uniform and balanced composite air curtain.

[0072] The mirror layout avoids the deflection torque caused by asymmetric airflow, ensuring that the airflow force on the pipe assembly 4 is balanced, which is beneficial to the stable operation of the system. The symmetrical flow channel design makes the flow field structure stable and predictable, reduces the generation of vortex, and reduces the energy loss of airflow organization. It can ensure that the airflow velocity and flow distribution on the upper and lower surfaces of the pipe assembly 4 are basically consistent, thereby achieving uniform defrosting effect.

[0073] Attached Figure 6In this design, multiple first air guide plates 51 are arranged at equal intervals with a second spacing, and multiple second air guide plates 52 are arranged at equal intervals with the same second spacing. This layout also forms a symmetrical, tapering flow channel, but because the spacing between the air guide plates is larger, the total number of air guide plates required is less. This reduces the system's material cost, processing complexity, and weight. Although the airflow constraint per unit area may be less than that of the first spacing scheme, it can still form an effective symmetrical airflow and a composite air curtain, making it a preferred solution for balancing performance and cost, especially suitable for cost-sensitive applications where the frosting load is not extremely severe.

[0074] However, if the horizontal distance between adjacent first air guide plates 51 or second air guide plates 52 is too large, exceeding the effective coverage area of ​​the airflow, the lack of effective physical constraints to guide the airflow in the gaps between the air guide plates causes a large amount of dry air to overflow directly from these gaps without impacting the surface of the pipe, resulting in a significant waste of energy and a significant decrease in defrosting effect.

[0075] Appendix Figure 7 and attached Figure 8 In the diagram, the first projection and the second projection are alternately arranged. The first projection is the projection of the first air guide plate 51 onto the pipe assembly 4, and the second projection is the projection of the second air guide plate 52 onto the pipe assembly 4. (See attached diagram) Figure 7 The spacing between adjacent first and second projections is 0; Figure 8 The distance between adjacent first and second projections is greater than 0. The first projection of the first air guide plate 51 on the pipe assembly 4 and the second projection of the second air guide plate 52 are staggered, causing the airflow coverage area guided by the first air guide plate 51 and the airflow coverage area guided by the second air guide plate 52 to overlap and connect in the horizontal direction. This fundamentally fills the weak flow area or gap that may exist between two airflows in a symmetrical layout, preventing airflow from escaping from this point. From a macroscopic perspective, the staggered air guide plate group no longer generates a series of independent airflows, but jointly constructs a continuous and uninterrupted composite air curtain. This air curtain seamlessly wraps the surface of the pipe, making the distribution of dry air more uniform, leaving nowhere for it to escape, and thus enabling its efficient utilization.

[0076] Appendix Figure 7 When the preset value is 0 (i.e., the first and second projections are exactly connected): this is a critical state of staggered layout, which achieves seamless connection between the upper and lower airflow coverage areas and also avoids the generation of blind spots in the middle. Through its innovative spatial topology design, it exhibits small but crucial performance advantages in filling airflow gaps and forming a continuous air curtain, and has been established as the globally optimal solution because it can significantly reduce the number of air guides required.

[0077] Appendix Figure 8, the preset value is greater than 200mm: there is a horizontal spacing between the guide vanes, which exceeds the effective coverage range of the airflow; at the gap between the guide vanes, there is a lack of effective physical constraints to guide the airflow, resulting in a large amount of dry air directly overflowing from such gaps, failing to impact the surface of the pipe, causing waste of energy, and the defrosting effect is significantly reduced.

[0078] The concept of preset value provides great design flexibility. The staggered spacing can be optimized and adjusted according to the pipe diameter of the pipe, the fin spacing, and the air supply speed and other parameters, to achieve the best coverage effect and energy efficiency ratio; in particular, experiments have proved that the staggered layout can reduce the total number of guide vanes under the premise of achieving the same or even better defrosting effect, effectively reducing the manufacturing cost and complexity of the system.

[0079] Referring to the accompanying drawings Figure 9 In one possible implementation, the input end of the uniform air jet nozzle 3 extends to form a guide structure, and the side wall of the air supply static pressure pipe 2 is provided with a plurality of installation openings with a set spacing, and the guide structure is inserted into the air supply static pressure pipe 2 through the installation openings; the air outlet angle of the uniform air jet nozzle 3 is fixed, and the connection interface of the uniform air jet nozzle 3 and the air supply static pressure pipe 2 has an anti-misassembly structure; referring to the accompanying drawings Figure 10 The emission direction of the outlet center line of the uniform air jet nozzle 3 forms an included angle of 12° to 17° with the horizontal direction; the emission direction of the outlet center line of the uniform air jet nozzle 3 matches the windward angle of the guide vane, that is, the emission direction of the outlet center line of the uniform air jet nozzle 3 is parallel or approximately parallel to the installation direction or the airfoil chord direction of the guide vane.

[0080] Referring to the accompanying drawings Figure 11 and the accompanying drawings Figure 12 The guide structure is a left-cut guide port or a right-cut guide port; wherein the hole diameter of the guide port is greater than the hole diameter of the output port of the uniform air jet nozzle 3.

[0081] The uniform air jet nozzle 3 is matched with the air supply amount of the main machine and the air supply static pressure pipe 2, and can have different opening sizes;

[0082] The air outlet 3 of the uniform air jet nozzle has a guide structure. By using a specific flow area contraction ratio and angle design, the air is ejected at a higher flow rate and an optimal angle, avoiding the problem of uneven air outlet along the static pressure air pipe. The guide structure (left or right cutting guide port) inserted into the inside of the air supply static pressure air pipe 2 plays a core role like a static pre-rotation blade. When the airflow in the air supply static pressure air pipe 2 encounters the entrance of the oblique cutting structure, it will be forced to change the flow path along the tangential direction, thereby generating a rotating and tangential velocity component, which can effectively destroy the large-scale vortex and uneven velocity distribution that may exist in the static pressure air pipe, making the airflow more uniform and stable before entering the nozzle. At the same time, the left and right cutting designs allow precise directional control of the airflow outlet angle. By regularly alternating or combining left and right cutting ports, the airflow can be guided to form the required flow field pattern, ensuring that the airflow directions of each nozzle are consistent and work together. The pre-rotated airflow then enters the main body of the nozzle. Since the aperture of the guide port is larger than that of the output port, the flow channel of the nozzle is actually a tapered pipe. According to Bernoulli's equation and the continuity theorem, when the airflow passes through this tapered flow channel, the flow rate will increase significantly, and the static pressure will decrease. Finally, the airflow is accelerated and ejected from the outlet in the form of a high-speed, directional, and concentrated jet. The tangential velocity component brought by pre-rotation allows the jet to better adhere to the surface of the subsequent air guide plate, extending the jet distance, reducing mixing with the surrounding air, and ensuring that the back of the exhaust pipe is also effectively covered by the airflow, eliminating defrosting dead angles.

[0083] The fixed air outlet angle of 12° to 17° is the optimized best value. This angle ensures that the jet can be most effectively captured and guided by the downstream airfoil-shaped air guide plate, forming a stable flow field adhering to the surface of the exhaust pipe, maximizing the use of airflow kinetic energy, and reducing escape; when the angle is less than 12°, the airflow will walk downward along the horizontal direction, and when the angle is greater than 17°, the airflow will walk upward, which will result in a decrease in the blocking effect of the airflow on the external humid air compared to 12° to 17°.

[0084] The jet direction of the nozzle is highly matched with the windward angle of the air guide plate, ensuring that the high-speed dry air ejected from the nozzle can be captured by the air guide plate with minimal impact loss and maximum efficiency, avoiding the impact of airflow on the non-working surface of the air guide plate due to angle deviation, which produces intense vortex and energy dissipation, so that the kinetic energy of the airflow can be maximized and used for subsequent defrosting.

[0085] Parallel angle guidance allows the airflow to flow smoothly and smoothly along the streamlined surface of the air guide plate. This adhesion effect can effectively constrain the airflow, making it less likely to escape and reach the deep part of the aluminum exhaust fin 42 along the predetermined path, improving the uniformity and reliability of defrosting.

[0086] The mistake-proofing structure physically ensures that each tuyere is installed at a unique correct angle (left cut or right cut) and orientation, eliminating flow field confusion caused by manual installation errors and ensuring the consistency and reliability of system performance.

[0087] The uniform flow scheme is achieved through the structure of the tuyere itself, without the need for additional complex structures such as perforated plates and guide vanes inside the supply static pressure air pipe, greatly simplifying the design and manufacturing process of the static pressure air pipe itself, reducing the processing difficulty and overall cost, and avoiding maintenance problems and increased wind resistance caused by built-in components.

[0088] Referring to the accompanying Figure 4 In a possible implementation, the defrosting device further includes: a return air static pressure air pipe 6, which is arranged on one side of the pipe bank assembly 4 and opposite to the supply air static pressure air pipe 2, and the input end of the return air static pressure air pipe 6 faces the pipe bank assembly 4.

[0089] In a possible implementation, the defrosting device further includes: a dehumidification device 1, a supply air duct 7, and a return air duct 8.

[0090] The dehumidification device 1 is placed inside or outside the pipe bank cold storage, and can be a frost-free dehumidification device. The dehumidification device 1 sucks in the humid air in the pipe bank cold storage, and in the dehumidification device 1, the humid air is dried by condensation, adsorption, and other dehumidification techniques, so that the dew point of the processed air is lower than the evaporation temperature of the pipe bank cold storage.

[0091] The supply air duct 7 has one end connected to the air outlet of the dehumidification device 1 and the other end connected to the input end of the supply air static pressure air pipe 2.

[0092] The return air duct 8 has one end connected to the return air static pressure air pipe 6 and the other end connected to the air inlet of the dehumidification device 1.

[0093] In a possible implementation, the defrosting device further includes an air valve 9 arranged at the connection between the supply air duct 7 and the supply air static pressure air pipe 2, for adjusting and controlling the supply air area and the supply air size.

[0094] In a possible implementation, the defrosting device further includes a static pressure fan, which is connected in series to the supply air duct 7, for providing supply air relay when the supply air duct 7 is too long, overcoming the air pipe resistance, and ensuring that the inlet static pressure of the supply air static pressure air pipe 2 meets the requirements.

[0095] The air after drying treatment is transported to the supply air static pressure pipe 2 at one end of the pipe group through the supply air pipe 7. When the supply air pipe 7 is long, the air is subjected to a large resistance during transportation, which causes the air to be unable to be smoothly transported to the end of the pipe group. In this case, the static pressure fan connected to the supply air pipe 7 is started to provide additional power for the air, so as to increase the pressure in the supply air static pressure pipe 2, thereby ensuring that the dry air can be smoothly transported to the end of the pipe group.

[0096] The single dehumidifying device 1 can be connected to multiple supply air static pressure pipes 2, and the size of the single supply air static pressure pipe 2 can be adjusted according to actual needs and arranged at one end of the pipe group 4, so as to realize air supply to multiple pipe group areas.

[0097] The high-pressure dry air is temporarily stored in the supply air static pressure pipe 2 and balanced in pressure, and then uniformly discharged at a specific angle and speed through the air uniformizing jet air outlet 3. The discharged dry air flow forms a stable high-speed air flow layer adhering to the surface of the pipe group 4 under the constraint and guidance of the air guide assembly 5. The dry high-speed air flow layer provides sensible heat to melt the existing frost layer, forms a dry air curtain, and isolates the pipe from the contact with the humid air in the warehouse, thereby fundamentally delaying the frosting;

[0098] The return air static pressure pipe 6 is fixed at the other end of the pipe group and arranged opposite to the supply air static pressure pipe 2. The end surface of the return air static pressure pipe 6 facing the pipe group 4 is designed with multiple return air outlets. The air that has absorbed moisture (increased humidity) through the surface of the pipe group 4 is uniformly captured by the return air static pressure pipe 6 arranged at the other end of the pipe group 4 under the action of the system pressure difference, and then sent into the dehumidifying device 1 through the return air pipe 8. The air is dried again in the dehumidifying device 1 and then sent out to start a new cycle, so as to continuously maintain the dry air field near the pipe group 4, thereby forming a complete dry air closed loop cycle. The return air static pressure pipe 6 ensures uniform return air through the porous design of the surface thereof, thereby avoiding local short circuit.

[0099] The application of the dehumidifying device in the cold storage is shown in the accompanying Figure 13 , the accompanying Figure 13 is a schematic diagram of an application scene of the defrosting device.

[0100] Embodiment 2:

[0101] On the basis of the embodiment 1, the embodiment provides a pipe group cold storage, which comprises:

[0102] The defrosting device, the supply air fan and the return air fan.

[0103] The supply air fan can be arranged on the supply air pipe 7, or the supply air fan in the dehumidifying device 1 can be multiplexed with the return air fan. The return air fan can be arranged on the return air pipe 8, or the return air fan in the dehumidifying device 1 can be multiplexed.

[0104] Embodiment 3:

[0105] The embodiment is based on the implementation 1 or the implementation 2, and provides a defrosting method, comprising:

[0106] The dry air in the supply static pressure air pipe 2 is ejected at a set angle and uniformly towards the row pipe assembly 4 through the jet pipe assembly;

[0107] The ejected dry air is guided by the air guide assembly 5 so that the dry air flows through the surface of the row pipe assembly 4; a dry air film is formed, which blocks the external air from flowing to the row pipe assembly 4.

[0108] The method further comprises:

[0109] The wet air in the row pipe cold storage is dried into dry air with a dew point lower than the evaporation temperature of the row pipe cold storage refrigeration machine by the dehumidification device 1, and the dry air is stored in the supply static pressure air pipe 2 arranged on one side of the row pipe assembly 4;

[0110] The air flowing through the surface of the row pipe assembly is recovered; the recovered air is dehumidified to form an air circulation.

[0111] Specifically, the air flowing through the surface of the row pipe assembly 4 is recovered through the return static pressure air pipe 6 arranged on the other side of the row pipe assembly 4;

[0112] The recovered air is sent back to the dehumidification device 1 for drying treatment to form a closed-loop air circulation.

[0113] The jet pipe assembly comprises a plurality of air uniformizing jet air outlets 3, and the step of ejecting the dry air at a set angle comprises:

[0114] The airflow from the supply static pressure air pipe 2 is balanced and guided through the bevel guide structure of the air uniformizing jet air outlet 3.

[0115] The airflow is guided along a predetermined path through the surface of the row pipe assembly by the air guide assembly 5, and the airflow is accelerated by the tapered flow channel formed by the air guide assembly 5 to improve the ability of the airflow to penetrate the gap between the row pipe fins.

[0116] The air supply area and the air supply amount are controlled by adjusting the air valve 9 arranged on the air supply pipe 7.

[0117] The method further comprises:

[0118] When the length of the air supply pipe 7 exceeds a preset value, the static pressure fan connected in series on the air supply pipe 7 is started to provide relay power for air delivery.

[0119] The method further comprises:

[0120] The delivery flow rate and delivery time of the dry air are controlled according to the humidity change in the library.

[0121] Although the embodiments of the present application have been shown and described above, it should be understood by those skilled in the art that the above-described embodiments are exemplary, and should not be construed as limiting the present application, and those skilled in the art can make changes, modifications, replacements and variations to the above-described embodiments without departing from the principles and spirit of the present application, all of which should be within the scope of the present application.

Claims

1. A defrosting device, characterized in that, The defrosting device comprises: an air supply static pressure air pipe (2) containing dry air, which is arranged on one side of the pipe group assembly (4); the dew point temperature of the dry air is lower than the evaporating temperature of the cold storage refrigeration machine; a jet pipe assembly, the input end of which is connected to the output end of the air supply static pressure air pipe (2), the output end of the jet pipe assembly is directed towards the pipe group assembly (4), and the dry air flow is blown out from the output end of the jet pipe assembly towards the pipe group assembly (4); a wind guide assembly (5) arranged adjacent to the pipe group assembly (4), which is used to guide the dry air flow blown out by the jet pipe assembly, so that the dry air flow is constrained to the pipe group assembly (4) and forms an air curtain, which blocks the outside air from flowing to the pipe group assembly (4).

2. The defrosting device according to claim 1, characterized in that The wind guide assembly (5) comprises a first wind guide structure and a second wind guide structure arranged on the first surface and the second surface of the pipe group assembly (4) respectively, so as to guide the dry air flow output by the jet pipe assembly to flow through the surface of the pipe group assembly (4); the first wind guide structure comprises a plurality of first wind guide plates (51) arranged at equal intervals, the connecting end of the first wind guide plate (51) being connected to the first surface of the pipe group assembly (4); the second wind guide structure comprises a plurality of second wind guide plates (52) arranged at equal intervals, the connecting end of the second wind guide plate (52) being connected to the second surface of the pipe group assembly (4).

3. The defrosting device according to claim 2, characterized in that The first wind guide plate (51) and the second wind guide plate (52) have an airfoil profile, and the chord length of the airfoil profile gradually narrows along the air flow direction; the chord line of the airfoil profile forms an angle of 12° to 17° with the horizontal direction, and the opening of the angle is directed towards the air supply static pressure air pipe (2).

4. The defrosting device according to claim 2, characterized in that The first wind guide plate (51) and the second wind guide plate (52) are straight plates, which form an installation angle of 12° to 17° with the surface of the refrigeration pipe group (4); the opening of the installation angle is directed towards the air supply static pressure air pipe (2).

5. The defrosting device according to claim 2, characterized in that The first wind guide plate (51) and the second wind guide plate (52) are arranged in mirror image along the pipe group assembly (4); or, the first projection and the second projection are arranged alternately, and the spacing between adjacent first projection and second projection is a preset value; wherein the first projection is the projection of the first wind guide plate (51) on the pipe group assembly (4), and the second projection is the projection of the second wind guide plate (52) on the pipe group assembly (4).

6. The defrosting device according to claim 1, wherein the jet pipe assembly comprises a plurality of uniform air jet air outlets (3), the input end of each uniform air jet air outlet (3) being connected to the output end of the air supply static pressure air pipe (2), and the output end of the uniform air jet air outlet (3) being directed towards the pipe group assembly (4); the outlet center line of the uniform air jet air outlet (3) forms an angle of 12° to 17° with the horizontal direction.

7. The defrosting device according to claim 5, wherein The input end of the uniform air jet nozzle (3) extends to form a flow guide structure, which is inserted into the air supply static pressure pipe (2); the flow guide structure is a left-cut flow guide port or a right-cut flow guide port; wherein the aperture of the flow guide port is larger than the aperture of the output port of the uniform air jet nozzle (3).

8. The defrosting device according to claim 1, characterized in that The defrosting device further comprises: a return air static pressure pipe (6) arranged on one side of the pipe group assembly (4) and opposite to the air supply static pressure pipe (2), wherein the input end of the return air static pressure pipe (6) faces the pipe group assembly (4).

9. The defrosting device according to claim 1, characterized in that The defrosting device further comprises: a dehumidification device (1) for dehumidifying input air to obtain dry air; an air supply pipe (7) having one end connected to the air outlet of the dehumidification device (1) and the other end connected to the input end of the air supply static pressure pipe (2); a return air pipe (8) having one end connected to the return air static pressure pipe (6) and the other end connected to the air inlet of the dehumidification device (1).

10. A defrosting method, characterized by, comprises: dry air in the air supply static pressure pipe (2) is uniformly ejected at a set angle towards the pipe group assembly (4) through the jet pipe assembly; the ejected dry air is guided by the air guide assembly to flow through the surface of the pipe group assembly (4); a dry air film is formed, which blocks the flow of external air to the pipe group assembly (4).

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