A defrosting device

Abstract

This utility model provides a defrosting device, comprising: a static pressure air duct for storing dry air, the static pressure air duct being disposed on one side of a pipe assembly; a jet pipe assembly, the input end of the jet pipe assembly being connected to the output end of the static pressure air duct, the output end of the jet pipe assembly facing the pipe assembly; and an air guide assembly disposed adjacent to the pipe assembly, the air guide assembly being used to guide the dry airflow blown out by the jet pipe assembly, so as to constrain the dry airflow to the pipe assembly and form an air curtain, the air curtain blocking outside air from flowing to the pipe assembly; through the static pressure air duct, the uniform air jet outlet, and the air guide assembly, the degree of frost formation in the pipe cold storage is significantly reduced, and under ideal conditions, frost-free operation can be achieved.

Description

Technical Field

[0001] This utility model relates to the field of cold storage defrosting technology, and in particular to a defrosting device. Background Technology

[0002] In the field of refrigeration engineering, frost formation on the surface of evaporator coil fins in cold storage is a long-standing and critical issue that significantly impacts system energy efficiency and stability. As the core of the system's cold energy exchange, the surface temperature of the coil is inevitably lower than the dew point temperature of the air inside the cold storage. 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 frost is a dynamic process, its morphology and thickness influenced by a combination of physical parameters, including relative humidity, air velocity, pipe surface temperature, and operating time. As a material with low thermal conductivity (typically in the range of 0.1-0.4 W / (m·K)), frost accumulation introduces significant additional thermal resistance. Studies show that for every 1 mm increase in frost thickness, heat transfer resistance can rise by 20% to 30%, leading to a decrease in evaporation temperature, an increase in compressor compression ratio, a significant deterioration in the system coefficient of performance (COP), and a 10% to 30% increase in energy consumption. Simultaneously, frost physically blocks the airflow channels between the fins, causing a sharp decrease in airflow. For example, for fins with a standard 5 mm spacing, when the frost thickness reaches 3 mm, the flow area decreases by more than 50%, and airflow resistance increases exponentially, further exacerbating the decline in heat transfer performance. Furthermore, continuous frost accumulation also introduces mechanical loads, posing a risk of fin deformation or pipe structure sagging, and periodic defrosting causes temperature fluctuations in the storage area, threatening the quality of stored goods.

[0004] To address this persistent problem, various defrosting technologies have been developed in the industry, but all of them have inherent flaws:

[0005] Electric defrosting: This method heats the coils directly using the Joule effect, with an energy conversion path of "high-grade electrical energy → heat energy." It has poor energy economy, with defrosting energy consumption accounting for up to a quarter of the total system energy consumption. Localized overheating and uneven heating during the process can lead to thermal stress damage and pose electrical safety hazards.

[0006] Hot gas defrosting: This is an internal balance technology within the heat pump cycle, where high-temperature refrigerant vapor from the compressor outlet is introduced into the evaporator to release heat and defrost. This method requires a complex valve and piping system, increasing initial investment and maintenance complexity. The refrigeration cycle is interrupted during the defrosting cycle, making a temperature rebound unavoidable. Furthermore, in multi-loop systems, uneven flow distribution can lead to incomplete defrosting.

[0007] Water defrosting: This method utilizes convective heat transfer of sensible water to achieve rapid defrosting, but it requires a complete water treatment, pumping, and spraying system, and has requirements for water source, corrosion prevention, and freeze protection. The huge thermal shock (ΔT>60℃) poses a severe test to the fatigue life of the pipe materials and welds, and the sudden increase in humidity inside the storage room after defrosting may accelerate the subsequent frosting process.

[0008] Natural defrosting versus manual defrosting: the former relies on ambient heat, has a long defrosting time, and results in complete loss of control over the storage temperature; the latter relies purely on manpower, has low operational efficiency, and poses risks to operational safety and equipment damage. Neither can meet the stringent requirements of modern cold chain logistics for continuous, stable, and automated operation.

[0009] In summary, existing defrosting technologies have failed to fundamentally resolve the inherent contradictions between high energy consumption, temperature fluctuations in storage facilities, system complexity, and equipment reliability. Utility Model Content

[0010] Based on the above problems, this utility model provides a defrosting device and defrosting method, which significantly reduces the degree of frost formation in pipe-type cold storage through air supply static pressure duct, air distribution jet outlet, and air guide component, and can achieve frost-free operation under ideal conditions.

[0011] In a first aspect, this utility model provides a defrosting device, comprising:

[0012] A static pressure air supply duct contains dry air and is located on one side of the duct assembly; the dew point temperature of the dry air is lower than the evaporation temperature of the cold storage chiller.

[0013] A jet tube assembly, wherein the input end of the jet tube assembly is connected to the output end of the air supply static pressure duct, and the output end of the jet tube assembly faces the pipe assembly; and the output end of the jet tube assembly blows out a dry airflow towards the pipe assembly;

[0014] An air guide assembly is disposed adjacent to the pipe assembly. The air guide assembly is used to guide the dry airflow blown out by the jet pipe assembly so that the dry airflow is constrained to the pipe assembly and forms an air curtain. The air curtain blocks outside air from flowing to the pipe assembly.

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

[0016] Preferably, the first air guiding structure includes a plurality of first air guiding plates arranged at equal intervals, and the connecting end of the first air guiding plate is connected to the first surface of the pipe assembly; the second air guiding structure includes a plurality of second air guiding plates arranged at equal intervals, and the connecting end of the second air guiding plate is connected to the second surface of the pipe assembly.

[0017] Preferably, the first and second air guide plates have airfoil profiles, and the chord length of their airfoils gradually narrows along the airflow direction; their airfoil chords form an angle of 12° to 17° with the horizontal direction, and the openings of the angles all face the air supply static pressure duct.

[0018] Optionally, the first and second air guide plates are straight plates, forming an installation angle of 12° to 17° with the surface of the refrigeration pipe; the openings of the installation angles all face the air supply static pressure duct.

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

[0020] Alternatively, the first projection and the second projection are staggered, and the distance between adjacent first projections and second projections 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 includes multiple uniform air jet outlets, the input end of each uniform air jet outlet is connected to the output end of the air supply static pressure duct, and the output end of the uniform air jet outlet faces the duct assembly; the jetting direction of the outlet centerline of the uniform air jet outlet forms an angle of 12° to 17° with the horizontal direction.

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

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

[0024] Preferably, the defrosting device further includes: a return air static pressure duct, which is disposed on one side of the duct assembly and opposite to the supply air static pressure duct, with the input end of the return air static pressure duct facing the duct assembly.

[0025] The defrosting device also includes:

[0026] Dehumidification equipment; used to dehumidify incoming air to obtain dry air;

[0027] An air supply duct, one end of which is connected to the air outlet of the dehumidification equipment, and the other end of which is connected to the input end of the air supply static pressure duct;

[0028] A return air duct, one end of which is connected to the return air static pressure duct, and the other end of which is connected to the air inlet of the dehumidification equipment.

[0029] Compared with the prior art, the beneficial effects of this utility model include at least the following: by using the air supply static pressure duct, the air distribution jet outlet, and the air guide assembly, the cold storage with pipes has achieved a fundamental transformation from periodic defrosting to continuous frost-free operation, completely solving the long-standing problem of frost formation in cold storage with pipes. It eliminates the huge power consumption of electric defrosting (saving 15%-25% of total energy consumption in defrosting) and the extra power consumption of the compressor in hot gas defrosting, ensuring that the pipe fins are always in a frost-free or thin-frost state, maintaining their extremely high heat transfer coefficient (high thermal conductivity of aluminum), which allows the evaporation temperature to be increased accordingly, significantly improving the compressor operating efficiency (COP value) and significantly reducing energy consumption; since there is no need for periodic, high-power defrosting operations, the temperature inside the refrigeration unit can remain stable, avoiding the large temperature fluctuations (5-10℃ rise) caused by traditional defrosting methods; it eliminates the safety hazards such as electric leakage and fire that may be caused by electric defrosting, and avoids the thermal stress fatigue and corrosion of the pipes and fins caused by drastic temperature changes due to hot gas defrosting and water defrosting, effectively extending the overall service life of the evaporator pipes and refrigeration system. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of a defrosting device according to an embodiment of the present utility model;

[0031] Figure 2 This is a utility model Figure 1 A magnified view of part A in the image;

[0032] Figure 3 This is a schematic diagram of another defrosting device according to an embodiment of the present invention;

[0033] Figure 4 This is a utility model Figure 3 A magnified view of part B in the image;

[0034] Figure 5 This is a schematic diagram of the airflow simulation effect when the air guide component of this utility model is mirror-symmetrical;

[0035] Figure 6 This is a schematic diagram of another airflow simulation effect when the air guide component of this utility model is mirror-symmetrical;

[0036] Figure 7 This is a schematic diagram of the airflow simulation effect of the air guide component with a preset value of 0.

[0037] Figure 8 This is a schematic diagram of the airflow guiding effect of the air guide component when the preset value is >200.

[0038] Figure 9 This is a schematic diagram of the air supply static pressure duct and the air distribution jet outlet structure according to an embodiment of this utility model;

[0039] Figure 10 This is a schematic diagram of the included angle setting of the uniform air jet nozzle in an embodiment of this utility model;

[0040] Figure 11 This is a schematic diagram of a uniform air jet outlet according to an embodiment of the present utility model;

[0041] Figure 12 This is another structural schematic diagram of the uniform air jet outlet according to an embodiment of this utility model.

[0042] Figure 13 This is a schematic diagram of an application scenario of a defrosting device according to an embodiment of this utility model.

[0043] In the diagram: 1. Dehumidification equipment; 2. Supply air static pressure duct; 3. Air distribution jet outlet; 4. Pipe assembly; 41. Pipe; 42. Fin; 5. Air guide assembly; 51. First air guide plate; 52. Second air guide plate; 6. Return air static pressure duct; 7. Supply air duct; 8. Return air duct; 9. Air valve. Detailed Implementation

[0044] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided to make the present invention more comprehensive and complete, and to fully convey the concept of the exemplary embodiments to those skilled in the art.

[0045] It should be noted that the embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application. The described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments in this application, this application covers any substitutions, modifications, equivalent methods and solutions made within the spirit, principles and scope of this application as defined by the claims. All other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0046] In the description of this application, the terms "first," "second," "third," and similar words do not indicate any order, quantity, or importance, but are merely used to distinguish different components. Similarly, the terms "a" or "one," and similar words, do not indicate a quantity limitation, but rather indicate the presence of at least one. The terms "comprising" or "including," and similar words, mean that the elements or objects preceding "comprising" or "including" encompass the elements or objects listed following "comprising" or "including," and their equivalents, but do not exclude other elements or objects. The terms "connected" or "linked," and similar words, are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect.

[0047] In the description of this application, the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used solely for the convenience of describing this application and for simplification, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application. Furthermore, when using positional terms such as "both sides," "outer side," and "upper and lower," it should be understood that they are used only for ease of understanding and description, taking into account that the structure may be oriented to other positions.

[0048] In the description of this application, unless otherwise expressly specified and limited, the technical or scientific terms used shall have the ordinary meaning understood by a person with ordinary skills in the art to which this application pertains. Terms such as “installation,” “connection,” and “joining” shall be interpreted broadly, for example, as fixed connection, detachable connection, mating connection, or integral connection. For a person skilled in the art, the specific meaning of the above terms in this application can be understood according to the specific circumstances.

[0049] The embodiments of this application are intended to introduce and explain the structural composition of an AAAA and the matching relationship between the various components. Unless otherwise specified, the dimensions, materials and manufacturing processes of the various components of the AAAA in the embodiments of this application can be selected according to specific circumstances, and no special limitations or explanations are made here.

[0050] Furthermore, to provide the public with a better understanding of this application, certain specific details are described in detail in the following description of the application. However, those skilled in the art can fully understand this application even without these detailed descriptions.

[0051] See attached document Figure 1-4This application provides a defrosting device, which is used for defrosting the pipe assembly 4 of a pipe cold storage; it includes: a static pressure air duct 2, a jet pipe assembly and a jet pipe assembly.

[0052] The air supply static pressure duct 2 contains dry air and is located on one side of the pipe assembly 4; the dew point temperature of the dry air is lower than the evaporation temperature of the cold storage chiller.

[0053] The jet tube assembly has its input end connected to the output end of the air supply static pressure duct 2, and its output end faces the pipe assembly 4; and the output end of the jet tube assembly blows out a dry airflow towards the pipe assembly 4.

[0054] An air guide assembly 5 is disposed adjacent to the pipe assembly 4. The air guide assembly 5 is used to guide the dry airflow blown out by the jet pipe assembly so that the dry airflow is constrained to the pipe assembly 4 and forms an air curtain. The air curtain blocks outside air from flowing to the pipe assembly 4.

[0055] The air guide assembly 5 includes a first air guide structure and a second air guide structure. The first air guide structure and the second air guide structure are respectively disposed on the first surface and the second surface of the pipe assembly 4 to guide the dry air output by the jet pipe assembly to flow through the surface of the pipe assembly 4.

[0056] The pipe assembly 4 includes pipes 41 and fins 42. As the core component of the cold storage refrigeration system, the pipe assembly 4 is composed of pipes 41 and fins 42 working together. Pipes 41 are continuous metal pipes (usually made of aluminum, copper, or galvanized steel) with a serpentine / winding layout. The core function of the winding structure is to extend the residence path of the refrigerant in the cold storage, thereby increasing the contact time with air and enhancing heat exchange efficiency. Refrigerant (such as ammonia, Freon, or CO2) flows inside pipes 41, exchanging heat with the outside air through the pipe walls. The refrigerant absorbs heat and evaporates (or releases heat and condenses), achieving cooling of the air inside the cold storage (or heating during the defrosting stage). Fins 42 are thin metal sheets (mostly made of aluminum, lightweight and with excellent thermal conductivity), densely arranged in parallel and fitted / welded to the surface of pipes 41, forming a large area for heat dissipation / absorption. The winding structure of pipes 41 extends along the length of the cold storage, and the fins 42 are densely distributed perpendicular to the axis of the pipes.

[0057] Dry air stored in the static pressure air duct 2, with a dew point temperature lower than the evaporation temperature of the cold storage unit, is delivered at a set angle through the jet pipe assembly. Upon reaching the vicinity of the pipe assembly 4, the dry air is guided and constrained by the air guide assembly 5, directing it to the end of the pipe assembly 4 or a predetermined distance, forming a specific airflow around the pipe assembly 4. This airflow wraps around the pipe assembly 4, precisely acting on the surfaces of the fins 42 and pipes 41, creating a dry air field near the pipe assembly 4. This isolates humid air from seepage from cold storage doors and evaporation from items inside. It can also be activated periodically as needed to dissolve frost on the pipes with a high-speed jet, preventing or controlling frost formation on the pipe surface and solving the long-standing problems of rapid frost formation, slow defrosting, and difficulty in defrosting in pipe-type cold storage. This creates a better cold storage environment and reduces the operating costs of pipe-type cold storage.

[0058] In one possible implementation, the first air guide structure includes a plurality of first air guide plates 51 arranged at equal intervals, and the connecting ends of the first air guide plates 51 are connected to the first surface of the pipe assembly 4.

[0059] The second air guiding structure includes multiple equally spaced second air guiding plates 52, the connecting ends of which are connected to the second surface of the pipe assembly 4; the first air guiding plate 51 and the second air guiding plate 52 together form an air duct that guides the airflow through the surface of the pipe assembly 4;

[0060] In a preferred embodiment, the first air guide plate 51 and the second air guide plate 52 have an airfoil profile, and the chord length of the airfoil gradually narrows along the airflow direction; the chord of the airfoil forms an angle of 12° to 17° with the horizontal direction, and the opening of the angle is facing the air supply static pressure duct 2. The lateral coverage 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.

[0061] In another embodiment, the first air guide plate 51 and the second air guide plate 52 can also be straight air guide plates; they form an installation angle of 12° to 17° with the surface of the refrigeration pipe 4; the openings of the installation angles both face the air supply static pressure duct 2. The first angle formed by the first air guide plate 51 and the first surface of the pipe assembly 4 is 12° to 17°; the second angle formed by the second air guide plate 52 and the second surface of the pipe assembly 4 is 12° to 17°; the openings of the first and second angles both face the air supply static pressure duct 2, and the outlet faces the inside of the warehouse; the first air guide plate 51 and the second air guide plate 52 are installed on the pipe assembly 4 by a fixing bracket, so that the air guide plates are suspended near the upper and lower surfaces of the pipe assembly 4; thereby so that the upstream airflow flows downstream along the pipe assembly 4.

[0062] The first air guide plate 51 and the second air guide plate 52 are arranged in pairs near the upper and lower surfaces of the pipe assembly 4, forming a gradually narrowing flow channel. The chord length is largest near the end of the air supply static pressure duct 2, forming a funnel-shaped inlet of the flow channel. It gradually narrows along the airflow path towards the cold storage side, which can capture the dry air delivered from the uniform air jet vent 3 to the maximum extent and effectively reduce airflow loss. The streamlined shape of the airfoil can efficiently guide the airflow, minimize eddies and energy loss, and constrain and concentrate the airflow to the gap between the fins 42 of the pipe assembly 4. The airflow enters the gradually narrowing flow channel formed by the air guide plate and the surface of the pipe 41. According to the principle of fluid mechanics, the airflow velocity is significantly accelerated when the airflow passes through this flow channel with a gradually decreasing cross-sectional area. This acceleration effect gives the airflow higher kinetic energy, which enables it to penetrate the dense gap between the fins 42 of the pipe assembly 4, ensuring that the back of the deep pipe 41 can also be effectively covered by airflow, and completely eliminating the defrosting dead corner. The accelerated airflow is ejected at high speed from the narrow opening of the flow channel and flows along the surface of the pipe along the angle set by the air guide plate, 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 frost formation.

[0063] The positions of the first air guide plate 51 and the second air guide plate 52 of this utility model include at least two scenarios: (1) and (2).

[0064] (1) The first air guide plate 51 and the second air guide plate 52 are arranged in a mirror image along the pipe assembly 4; and the distance between adjacent air guide plates is determined according to the wind speed, the size characteristics of the air guide plate and the outlet diffusion angle of the airflow. The larger the distance, the more dry air escapes, and the smaller the distance, the higher the overall cost; the preferred range is between 300mm and 500mm.

[0065] (2) The first projection and the second projection are staggered, and the distance between adjacent first projections and second projections is a preset value; wherein, the first projection is the projection of the first air guide plate 51 on the pipe assembly 4, and the second projection is the projection of the second air guide plate 52 on the pipe assembly 4. The preset value can be greater than 0 or less than 0, preferably 0. The smaller the threshold, the more baffles are required, and the higher the cost; the larger the threshold, the larger the gap, and the more dry air escapes.

[0066] Appendix Figure 5 To the attached Figure 8 This is a simulation diagram of the airflow guiding component.

[0067] Appendix Figure 5 and attached Figure 6 In the middle, the first air guide plate 51 and the second air guide plate 52 are arranged in a mirror-symmetrical manner along the pipe assembly 4, with attached... Figure 5 The spacing between adjacent first air guide plates 51 or second air guide plates 52 is the first spacing; (See attached text) Figure 6The distance between adjacent first air guide plates 51 or second air guide plates 52 is the second distance; wherein the second distance is greater than the first distance.

[0068] Appendix Figure 5 In this configuration, when the first guide vane 51 and the second guide vane 52 are arranged in a mirror-symmetrical manner along the pipe assembly 4, multiple completely symmetrical and independent tapering flow channels are formed 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 over the surface of the pipe, these two airflows converge in the middle region on the other side of the pipe, forming a uniformly covered and dynamically balanced composite air curtain.

[0069] The mirrored layout avoids deflection torque caused by airflow asymmetry, ensuring balanced force exerted by the airflow on the pipe assembly 4, 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 eddies, and lowers the energy loss of airflow organization. It can ensure that the airflow velocity and flow rate distribution on the upper and lower surfaces of the pipe assembly 4 are basically consistent, thereby achieving a uniform defrosting effect.

[0070] Appendix Figure 6 In 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.

[0071] 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.

[0072] 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 8The 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.

[0073] 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.

[0074] Appendix Figure 8 If the preset value is greater than 200mm: the horizontal spacing between the air guide plates is too large, exceeding the effective coverage range of the airflow; in the gaps between the air guide plates, there is a lack of effective physical constraints to guide the airflow, causing a large amount of dry air to overflow directly from these gaps without impacting the surface of the pipe, resulting in energy waste and a significant decrease in defrosting effect.

[0075] The concept of preset values ​​provides tremendous design flexibility. The staggered spacing can be optimized and adjusted based on parameters such as duct diameter, fin spacing, and airflow velocity to achieve the best coverage and energy efficiency ratio. In particular, experiments have shown that using a staggered layout can reduce the total number of air guides while achieving the same or even better defrosting effect, effectively reducing the system's manufacturing cost and complexity.

[0076] See attached document Figure 9 In one possible implementation, the input end of the uniform air jet outlet 3 extends to form a guide structure, and multiple installation ports with predetermined spacing are opened on the side wall of the supply air static pressure duct 2. The guide structure is inserted into the supply air static pressure duct 2 through the installation ports; the outlet angle of the uniform air jet outlet 3 is fixed, and its connection interface with the supply air static pressure duct 2 has an anti-misinstallation structure; see attached figure. Figure 10The ejection direction of the outlet centerline of the uniform air jet vent 3 forms an angle of 12° to 17° with the horizontal direction; the ejection direction of the outlet centerline of the uniform air jet vent 3 matches the windward angle of the air guide plate, that is, the ejection direction of the outlet centerline of the uniform air jet vent 3 is parallel or approximately parallel to the installation direction of the air guide plate or the airfoil chord direction.

[0077] See attached document Figure 11 and attached Figure 12 The flow guiding structure is either a left-cut or right-cut flow guiding port; wherein, the diameter of the flow guiding port is larger than the diameter of the output port of the uniform air jet outlet 3.

[0078] The uniform air jet outlet 3 is matched with the air volume of the main unit and the static pressure of the air supply duct 2, and can have different opening sizes;

[0079] The uniform air jet outlet 3 features a built-in guide structure. Utilizing a specific flow area contraction ratio and angle design, it allows air to be ejected at a higher velocity and a preferred angle, avoiding uneven airflow along the static pressure duct direction. The guide structure (left- or right-cut guide) extending and inserted into the supply static pressure duct 2 acts like a static pre-rotating blade. When the airflow in the supply static pressure duct 2 encounters the inlet of this obliquely cut structure, it is forced to change its flow path tangentially, generating a rotating, tangential velocity component. This effectively disrupts any large-scale vortices and uneven velocity distribution that may exist within the static pressure duct, making the airflow more uniform and stable before entering the outlet. Simultaneously, the left- or right-cut design allows for precise directional control of the airflow outlet angle. By regularly alternating or combining left and right-cut outlets, the airflow can be guided to form the desired flow field pattern, ensuring consistent airflow direction and coordinated operation across all outlets. The pre-rotated airflow then enters the main body of the outlet. Because the orifice diameter of the guide port is larger than that of the output port, the airflow channel of the vent is actually a tapered tube. According to Bernoulli's equation and the continuity theorem, when the airflow passes through this tapered channel, the velocity increases significantly while the static pressure decreases. Ultimately, the airflow is accelerated and ejected from the outlet as a high-speed, directional, and concentrated jet. The tangential velocity component introduced by the pre-swirl allows the jet to adhere better to the surface of the subsequent guide vane, extending the jet distance, reducing mixing with the surrounding air, ensuring effective airflow coverage even on the back of the duct, and eliminating defrosting dead zones.

[0080] A fixed outlet angle of 12° to 17° is the optimized optimal value. This angle ensures that the jet can be captured and guided most effectively by the downstream airfoil guide vane, forming a stable flow field attached to the surface of the pipe, maximizing the utilization of air kinetic energy and reducing dissipation. Specifically, when the angle is less than 12°, the airflow tends to flow downwards in the horizontal direction, while when it is greater than 17°, the airflow tends to flow upwards. Compared to 12° to 17°, this will result in a decrease in the airflow's ability to block outside humid air.

[0081] The jet direction of the air vent is highly matched with the windward angle of the air guide plate, ensuring that the high-speed dry air ejected from the air vent can be captured by the air guide plate with minimal impact loss and maximum efficiency. This avoids the airflow from hitting the non-working surface of the air guide plate due to angular deviation, generating violent eddies and energy dissipation, so that the kinetic energy of the airflow can be preserved to the maximum extent and used for the subsequent defrosting process.

[0082] The parallel angle guidance allows the airflow to flow smoothly and seamlessly against the streamlined surface of the air guide plate. This adhesion effect effectively confines the airflow, preventing it from escaping and guiding it along a predetermined path deep into the aluminum fins 42, thus improving the uniformity and reliability of defrosting.

[0083] The anti-misinstallation structure physically ensures that each air outlet can be installed at the only correct angle (left or right cut) and orientation, eliminating flow field chaos caused by human installation errors and ensuring the consistency and reliability of system performance.

[0084] The flow equalization scheme is achieved by the structure of the air outlet itself, eliminating the need to install additional perforated plates, guide vanes or other complex structures inside the static pressure air duct. This greatly simplifies the design and manufacturing process of the static pressure air duct itself, reduces processing difficulty and overall cost, and avoids maintenance problems and increased air resistance that may be caused by built-in components.

[0085] See attached document Figure 4 In one possible implementation, the defrosting device further includes: a return air static pressure duct 6, which is disposed on one side of the pipe assembly 4 and opposite to the supply air static pressure duct 2, with the input end of the return air static pressure duct 6 facing the pipe assembly 4.

[0086] In one possible implementation, the defrosting device further includes: a dehumidifier 1, an air supply duct 7, and a return air duct 8.

[0087] Dehumidification device 1; Dehumidification device 1 is placed inside or outside the pipe cold storage. Dehumidification device 1 can be a frost-free dehumidification device. It draws humid air from the pipe cold storage into the device. Inside the dehumidification device 1, the humid air is dried through dehumidification technologies such as condensation and adsorption, so that the dew point of the treated air is lower than the evaporation temperature of the cold storage unit.

[0088] Air supply duct 7, one end of which is connected to the air outlet of dehumidifier 1, and the other end of which is connected to the input end of air supply static pressure duct 2.

[0089] Return air duct 8, one end of which is connected to return air static pressure duct 6, and the other end of which is connected to the air inlet of dehumidification equipment 1.

[0090] In one possible implementation, the defrosting device also includes an air valve 9, which is located at the connection between the air supply duct 7 and the air supply static pressure duct 2, and is used to adjust and control the air supply area and the air supply volume.

[0091] In one possible implementation, the defrosting device also includes a static pressure fan, which is connected in series on the air supply duct 7 to provide air supply relay when the air supply duct 7 is too long, overcome the air duct resistance, and ensure that the inlet static pressure of the air supply static pressure duct 2 meets the requirements.

[0092] After drying, the air is transported through the air supply duct 7 to the air supply static pressure duct 2 at one end of the pipe. When the air supply duct 7 is long and the air encounters greater resistance during transport, making it difficult to be transported to the end of the pipe, the static pressure fan connected in series with the air supply duct 7 starts to provide additional power to the air and increase the pressure in the air supply static pressure duct 2, so as to ensure that the dried air can be smoothly transported to the end of the pipe.

[0093] A single dehumidifier 1 can be connected to multiple air supply static pressure ducts 2. The size of a single air supply static pressure duct 2 can also be adjusted according to actual needs and arranged at one end of multiple duct assembly 4, thereby realizing air supply to multiple duct areas.

[0094] High-pressure dry air is temporarily stored and its pressure equalized in the supply static pressure duct 2, and then uniformly ejected at a specific angle and speed through the uniform air jet nozzle 3. Under the constraint and guidance of the air guide assembly 5, the ejected dry airflow forms a stable high-speed airflow layer attached to the surface of the duct assembly 4. The dry high-speed airflow layer provides sensible heat, melts the existing frost layer, forms a dry air curtain, isolates the duct from the humid air inside the storage, and fundamentally delays frost formation.

[0095] The return air static pressure duct 6 is fixed at the other end of the ductwork assembly and is arranged opposite to the supply air static pressure duct 2. Its end face facing the ductwork assembly 4 is designed with a multi-hole return air port. The air that has absorbed moisture (increased humidity) after passing through the surface of the ductwork assembly 4 is evenly captured by the return air static pressure duct 6 located at the other end of the ductwork assembly 4 under the action of system pressure difference. Then it is sent into the dehumidification equipment 1 through the return air duct 8. In the dehumidification equipment 1, the air is dried again and then sent out again to start a new cycle, continuously maintaining the dry air field near the ductwork assembly 4, thus forming a complete dry air closed loop circulation. The multi-hole design on the surface of the return air static pressure duct 6 ensures uniform return air and avoids local short circuits.

[0096] Refer to the appendix for the application of dehumidification equipment in cold storage. Figure 13 , attached Figure 13 This is a schematic diagram of an application scenario for a defrosting device.

[0097] Example 2:

[0098] Based on implementation 1, this embodiment provides a pipe-lined cold storage unit, including:

[0099] The aforementioned defrosting device, as well as the supply air fan and return air fan.

[0100] The supply fan can be installed on the supply air duct 7; or it can be reused from the supply air fan in the dehumidification equipment 1. The return air fan can be installed on the return air duct 8; or it can be reused from the return air fan in the dehumidification equipment 1.

[0101] Example 3:

[0102] Based on implementation 1 or implementation 2, this embodiment provides a defrosting method, including:

[0103] The dry air in the static pressure air duct 2 is uniformly ejected towards the pipe assembly 4 at a set angle through the jet pipe assembly;

[0104] The air guide assembly 5 guides the ejected dry air to flow over the surface of the pipe assembly 4, forming a dry air film that blocks outside air from flowing to the pipe assembly 4.

[0105] The method further includes:

[0106] The dehumidifying equipment 1 dries the humid air in the pipe cold storage to dry air with a dew point lower than the evaporation temperature of the cold storage refrigeration unit, and then delivers the dry air to the air supply static pressure duct 2 located on one side of the pipe assembly 4 for storage.

[0107] The air flowing through the surface of the pipe assembly is recovered; the recovered air is dehumidified to form an air circulation.

[0108] Specifically, the air flowing through the surface of the pipe assembly 4 is recovered by the return air static pressure duct 6 located on the other side of the pipe assembly 4;

[0109] The recovered air is sent back to the dehumidification equipment 1 for drying, forming a closed-loop air circulation.

[0110] The jet tube assembly includes multiple uniform air jet nozzles 3, and the step of ejecting dry air at a set angle includes:

[0111] The airflow from the static pressure air duct 2 is balanced and guided by the oblique-cut guide structure at the inlet section of the uniform air jet vent 3.

[0112] The airflow is guided by the air guide component 5, so that the airflow flows along a predetermined path across the surface of the pipe assembly; and the airflow is accelerated by the gradually narrowing flow channel formed by the air guide component 5, thereby improving the airflow's ability to penetrate the gap between the pipe fins.

[0113] The air supply area and air volume are controlled by adjusting the air valve 9 installed on the air supply duct 7.

[0114] The method further includes:

[0115] When the length of the air supply duct 7 exceeds the preset value, the static pressure fan connected in series with the air supply duct 7 is started to provide relay power for air delivery.

[0116] The method further includes:

[0117] The flow rate and delivery time of the dry air are controlled according to the humidity changes inside the warehouse.

[0118] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and alterations to the above embodiments within the scope of the present invention without departing from the principles and spirit of the present invention, and all such changes should fall within the protection scope of the claims of the present invention.

Claims

1. A defrosting device, characterized in that, include: A static pressure air supply duct (2) contains dry air and is located on one side of the pipe assembly (4); the dew point temperature of the dry air is lower than the evaporation temperature of the cold storage chiller. The jet tube assembly has its input end connected to the output end of the air supply static pressure duct (2), and its output end faces the pipe assembly (4), and the output end of the jet tube assembly blows out dry airflow towards the pipe assembly (4). An air guide assembly (5) is disposed adjacent to the pipe assembly (4). The air guide assembly (5) is used to guide the dry airflow blown out by the jet pipe assembly so that the dry airflow is constrained to the pipe assembly (4) and forms an air curtain. The air curtain blocks the flow of outside air to the pipe assembly (4).

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

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

4. The defrosting device according to claim 2, characterized in that, The first air guide plate (51) and the second air guide plate (52) are straight plates, forming an installation angle of 12° to 17° with the surface of the pipe assembly (4); the openings of the installation angles are all facing the air supply static pressure duct (2).

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

6. The defrosting device according to claim 1, characterized in that, The jet tube assembly includes multiple air-equalizing jet nozzles (3), the input end of each air-equalizing jet nozzle (3) is connected to the output end of the air supply static pressure duct (2), and the output end of the air-equalizing jet nozzle (3) faces the duct assembly (4); the jetting direction of the outlet centerline of the air-equalizing jet nozzle (3) forms an angle of 12° to 17° with the horizontal direction.

7. The defrosting device according to claim 6, characterized in that, The input end of the uniform air jet outlet (3) extends to form a guide structure, which is inserted into the air supply static pressure duct (2); the guide structure is a left-cut guide or a right-cut guide; wherein the aperture of the guide is larger than the aperture of the output port of the uniform air jet outlet (3).

8. The defrosting device according to claim 1, characterized in that, The defrosting device further includes: a return air static pressure duct (6), which is located on one side of the pipe assembly (4) and is opposite to the supply air static pressure duct (2), with the input end of the return air static pressure duct (6) facing the pipe assembly (4).

9. The defrosting device according to claim 8, characterized in that, The defrosting device also includes: Dehumidification equipment (1); used to dehumidify the input air to obtain dry air; Air supply duct (7), one end of which is connected to the air outlet of the dehumidification device (1), and the other end of which is connected to the input end of the air supply static pressure duct (2); Return air duct (8), one end of which is connected to the return air static pressure duct (6), and the other end of which is connected to the air inlet of the dehumidification equipment (1).

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