evaporator

Abstract

The present application provides a kind of evaporator.It is used for storage library and is equipped with the cold air temperature and humidity changing part comprising ice heat exchanger and air supply device.Can realize the stability of temperature in the library and reduce the consumption power and the consumption water quantity for ice making.The constant temperature high humidity storage library evaporator is characterized in that, it is equipped with the cold air temperature and humidity changing part comprising multiple ice heat exchanger and air supply device for supplying cold air to the cold air temperature and humidity changing part, when observing the section of multiple ice heat exchanger perpendicular to the axial direction, in the direction perpendicular to the airflow direction of cold air, form the wing shape with the head width is large and the width gradually becomes smaller towards the tail direction, in the direction perpendicular to the airflow direction of the cold air, the ice heat exchanger adjacent is configured to its wing head and wing tail are adjacent between the two.The ice is accumulated in the wing type in the evaporator, therefore, the surface area and volume of ice increase, the temperature stability in the library and the evaporation capacity increase.

Description

Technical Field

[0001] This invention relates to an evaporator for ice and water used in a constant temperature and high humidity storage facility. Background Technology

[0002] Previously, temperature-controlled storage facilities (sometimes referred to as "storage facilities") were used to preserve the freshness of food items requiring temperature management, such as meat, fish, and vegetables. Generally, because there is a positive correlation between enzyme activity and food temperature, the lower the storage temperature, the easier it is to maintain freshness. Therefore, by controlling the temperature in a temperature-controlled storage facility at a low temperature, the freshness of food can be ensured. In addition, the growth rate of molds and bacteria is extremely slow near 0°C.

[0003] However, if the storage facility is kept at a low temperature, for example, in edible meat and seafood where water accounts for 70% to 80%, and in fruits and vegetables where water accounts for 80% to 90% or more, prolonged cooling of food at temperatures below -3°C will result in freezing. When water freezes, it expands in volume, and the extracellular fluid of the food freezes first, forming large ice crystals. Therefore, the cell membranes are damaged from the outside, and the food is frozen in this state. Furthermore, if the relative humidity is not above the food's moisture content during food storage, water vapor will escape from the food into the surrounding air, causing the food to dry out. That is, when storing food in the open, the relative humidity inside the storage facility needs to be controlled at least 80%, and preferably at least 90%. Additionally, since the anteroom in conventional storage facilities is designed to maintain the low temperature, it is not used to maintain the humidity of the storage facility.

[0004] Then, when food is removed from the storage facility and thawed, intracellular and intercellular fluids leak out from damaged cells, losing flavor components and nutrients along with water, and the food's texture deteriorates. The temperature at which water crystallizes into ice is called the freezing point (hereinafter referred to as "freezing point"). In the case of pure water, the freezing point is 0°C when slowly cooled at 1 atmosphere. However, to prevent ice from forming inside food and other temperature-controlled items, raising the storage facility temperature increases the activity of enzymes that break down food, making it impossible to reach a temperature sufficient to maintain the freshness of meat and other foods. Therefore, when using conventional storage facilities with the temperature set near 0°C, ice can form inside the food when the storage temperature changes and falls below the freezing point.

[0005] Therefore, Patent Document 1 discloses an evaporator for a storage facility, wherein a cold air temperature and humidity changing section including a crushed ice heat exchanger is disposed adjacent to and between a first air supply device and a second air supply device. This cold air temperature and humidity changing section has ice supplied from the crushed ice section, so that the basic cold air comes into contact with the ice and becomes cold air containing water vapor at around 0°C.

[0006] Furthermore, as the ice melts and the melted water vaporizes, water vapor fills the storage room, creating a high-humidity environment with an internal temperature of around 0°C and a relative humidity of around 100%. Therefore, by controlling the management of food and other items stored in this storage room at around 0°C and around 100% relative humidity, their quality can be maintained.

[0007] Existing technical documents

[0008] Patent documents

[0009] Patent Document 1: Japanese Patent No. 6559305 Summary of the Invention

[0010] The problem that the invention aims to solve

[0011] However, according to this evaporator, ice crushed below the freezing point, produced by an ice maker, is heated to 0°C, resulting in melted water accumulating on the ice surface. By blowing air onto the falling ice crushed or accumulated ice blocks (hereinafter referred to as "ice crushed"), the surface melted water evaporates, generating water vapor near 0°C, which is then blown into the storage chamber. Under normal operating conditions, the ice crushed forms from bottom to top along the internal shape of the evaporator, thus forming ice columns roughly the same shape as the evaporator. The temperature of melting or frozen ice, and mixtures of ice and water, is approximately 0°C or near the freezing point. When a large amount of a substance with a high specific heat at the same temperature as the freezing point is present, the product of specific heat and mass near the freezing point, i.e., the heat capacity, increases, and the temperature inside the storage chamber stabilizes near the freezing point. However, in Patent Document 1, because the total internal volume of the evaporator is small, the total amount of ice crushed is small. Furthermore, the surface area of ​​the airflow in contact with the ice crushed is small. Therefore, the humidification and cooling efficiency is poor, and the temperature stability is low.

[0012] Furthermore, when observing a cross-section perpendicular to the vertical direction, in the wing-shaped ice-crushing heat exchanger, with the wingtips of the ice-crushing heat exchanger section adjacent to each other along the airflow direction within the cold air temperature and humidity changing section, and the tail sections adjacent to each other in this direction, the airflow introduced from the air supply device decreases internally due to the smaller gaps within the ice-crushing heat exchanger near the tail section, while the larger gaps within the ice-crushing heat exchanger near the wingtips result in a larger internal airflow volume. Consequently, within the cold air temperature and humidity changing section containing the ice-crushing heat exchanger, the static pressure increases downstream in the airflow direction, thus reducing the airflow rate.

[0013] Therefore, the purpose of this invention is to provide a technical solution that can increase the total volume of crushed ice in the internal space of the evaporator and the surface area of ​​the crushed ice in contact with the air supply, thereby improving the stability of temperature and humidity.

[0014] Methods for solving problems

[0015] The evaporator of the first aspect of the present invention is an evaporator for use in a constant temperature and high humidity storage warehouse, characterized in that it comprises:

[0016] One or more cold air temperature and humidity changing units, each comprising a plurality of crushed ice heat exchangers, wherein the plurality of crushed ice heat exchangers are arranged within a first internal space defined by a wall provided in the internal space of the constant temperature and high humidity storage facility, and have an internal space from which crushed ice is supplied from a crushed ice supply device; and,

[0017] An air supply device is used to circulate cool air between the first interior space and the second interior space.

[0018] Each of the multiple ice-crushing heat exchangers has multiple holes on its sidewall.

[0019] The plurality of ice-crushing heat exchangers are arranged side-by-side in the first internal space, with at least a portion of the sidewalls provided with the plurality of holes facing each other at equal intervals along the airflow direction of the air supply device.

[0020] According to the evaporator of the first aspect of the invention, the plurality of ice-crushing heat exchangers are arranged side-by-side in a first internal space, with at least a portion of the sidewalls of each ice-crushing heat exchanger having a plurality of holes spaced at equal intervals along the airflow direction of the air supply device. Thus, airflow can pass stably and at approximately equal speed through the gap formed by the at least a portion of the opposing sidewalls of the adjacent ice-crushing heat exchangers in the side-by-side direction. That is, equalization of the airflow through this gap between the adjacent ice-crushing heat exchangers in the side-by-side direction can be achieved.

[0021] Therefore, compared to existing technologies, it is possible to improve the contact efficiency between the crushed ice supplied to each internal space of the crushed ice heat exchanger and the air through multiple holes provided on the sidewalls of each crushed ice heat exchanger. As a result, even when the internal space of the crushed ice heat exchanger is not filled with crushed ice, the airflow in the internal space can be ensured. Therefore, the amount of air in contact with the melted water on the surface of the crushed ice is increased, and the target relative humidity can be achieved with less crushed ice. This reduces the amount of ice produced, thereby saving electricity and water consumption.

[0022] A constant temperature and high humidity storage warehouse refers to a storage warehouse that maintains a certain internal temperature and the air inside the warehouse contains saturated water vapor at or close to the internal temperature, with a relative humidity of 80% to 100% for storing food and other items.

[0023] In the evaporator of the first type, preferably, three or more of the ice-crushing heat exchangers are arranged side by side in the first internal space, such that the spacing of the sidewalls on which the plurality of holes are respectively provided is equal for all the ice-crushing heat exchangers, with the distance between each pair of adjacent ice-crushing heat exchangers.

[0024] In the first type of evaporator, preferably, the crushed ice heat exchanger is disposed within the first internal space defined by the wall portion, such that the wall portion and the sidewall are evenly spaced opposite each other along the airflow direction of the air supply device, and the sidewall is the sidewall of the crushed ice heat exchanger opposite the wall portion that is provided with the plurality of holes.

[0025] In the evaporator of the first type, it is preferable that the plurality of crushed ice heat exchangers are designed to have the same shape.

[0026] In the evaporator of the first embodiment, it is preferred that the side surface of the crushed ice heat exchanger is shaped as follows: at least a portion of the sidewall of each of the adjacent crushed ice heat exchangers, which is opposite to each other and provided with the plurality of holes, is respectively formed as a planar shape, or as a convex curved surface and a concave curved surface.

[0027] In the evaporator of the first embodiment, it is preferred that the plurality of ice-crushing heat exchangers are configured such that the cross-section of each ice-crushing heat exchanger is formed as a wing-shaped cylinder, and in the parallel direction of the plurality of ice-crushing heat exchangers, the wing head and wing tail of one ice-crushing heat exchanger are respectively adjacent to the wing tail and wing head of another ice-crushing heat exchanger adjacent to that one ice-crushing heat exchanger.

[0028] The second embodiment of the evaporator of the present invention is an evaporator for use in a constant temperature and high humidity storage facility, comprising: one or more cold air temperature and humidity changing units, the one or more cold air temperature and humidity changing units being composed of a plurality of crushed ice heat exchangers, the plurality of crushed ice heat exchangers being disposed within a first internal space defined by a wall provided in the internal space of the constant temperature and high humidity storage facility and having an internal space extending along an axial direction from which crushed ice is supplied from a crushed ice supply device; and an air supply device for circulating cold air between the first internal space and the second internal space, wherein each of the plurality of crushed ice heat exchangers has a plurality of holes provided on its sidewall, the plurality of crushed ice heat exchangers being designed with the same shape having rotational symmetry about an axis, and the plurality of crushed ice heat exchangers being arranged in a grid-like arrangement with translational symmetry in a direction perpendicular to the axial direction.

[0029] According to a second aspect of the evaporator of the invention, a plurality of ice-crushing heat exchangers, designed to have rotational symmetry about an axis, are arranged in a grid pattern within a first internal space in a manner having translational symmetry in a direction perpendicular to the axis. This allows airflow to pass stably and at approximately equal speed through the gaps between the plurality of ice-crushing heat exchangers. In other words, equalization of airflow through these gaps in the grid-like arrangement of the ice-crushing heat exchangers can be achieved.

[0030] Therefore, compared to existing technologies, it is possible to improve the contact efficiency between the crushed ice supplied to each internal space of the crushed ice heat exchanger and the air through multiple holes provided on the sidewalls of each crushed ice heat exchanger. As a result, even when the internal space of the crushed ice heat exchanger is not filled with crushed ice, the airflow in the internal space can be ensured. Therefore, the amount of air in contact with the melted water on the surface of the crushed ice is increased, and the target relative humidity can be achieved with less crushed ice. This reduces the amount of ice produced, thereby saving electricity and water consumption.

[0031] In the evaporator of the first or second type, it is preferable to have a supply stop mechanism that stops the supply of crushed ice when the height of the crushed ice accumulated in all the crushed ice heat exchangers reaches near the supply port of the crushed ice supply device.

[0032] The storage vault of the present invention has an evaporator of a first or second type, and a humidification device is provided in an anteroom that is continuous with the storage vault via the inlet and outlet of the storage vault.

[0033] According to the storage vault of the present invention, by providing a humidification device in the anteroom, which has a higher temperature than the storage vault itself, the amount of saturated water vapor is reduced due to the low temperature when the vault door is opened or closed, even if the air with a higher temperature in the anteroom enters the interior of the storage vault. Therefore, the impact on the relative humidity inside the storage vault can be reduced.

[0034] Brief description of the attached diagram

[0035] Figure 1 This is a schematic structural diagram illustrating a vault as one embodiment of the present invention.

[0036] Figure 2 This is a schematic structural diagram illustrating an evaporator according to one embodiment of the present invention.

[0037] Figure 3 This is a block diagram of an evaporator as one embodiment of the present invention.

[0038] Figure 4 This is a schematic structural illustration of an evaporator as another embodiment of the present invention.

[0039] Figure 5 This is a schematic structural diagram illustrating an evaporator as another embodiment of the present invention.

[0040] Figure 6 This is a schematic structural diagram illustrating an evaporator as another embodiment of the present invention. Detailed Implementation

[0041] Figure 1 This shows a schematic structure of the constant temperature and high humidity storage warehouse according to the first embodiment of the present invention. Figure 2 yes Figure 1 The diagram shows a schematic horizontal or cross-sectional view of the evaporator.

[0042] like Figure 1 As shown, in this embodiment, the internal space (second internal space) of the constant temperature and high humidity storage room (hereinafter sometimes referred to as the "storage room") 10 is equipped with an internal temperature and humidity sensor 11 and an evaporator 20. The internal temperature and humidity sensor 11 is a sensor used to measure the temperature and humidity inside the storage room 10.

[0043] It should be noted that the temperature and humidity data received by the sensor are sent to the control device (controller) 27, which, based on the measured temperature and humidity, controls the operation of the first air supply device and the second air supply device, which will be described below. Figure 3 A block diagram including the aforementioned control device is shown.

[0044] The second interior space of the storage room 10 contains food items such as meat, fish, and vegetables, which are stored as items S.

[0045] like Figure 1 and Figure 2 As shown, the evaporator 20 includes a first air supply device 21, a second air supply device 22, and a cold air temperature and humidity changing section 23 disposed between the first air supply device 21 and the second air supply device 22. The first air supply device 21 and the second air supply device 22 are each composed, for example, of a rotary drive device such as an electric motor, a rotary shaft, and blades. The rotary shaft is connected to the output shaft of the rotary drive device and is driven to rotate. The blades are mounted in a direction perpendicular to the rotary shaft relative to the rotary shaft. The cold air temperature and humidity changing section 23 is composed of a plurality of crushed ice heat exchangers (hereinafter, sometimes referred to as "heat exchangers") 231 to 235 arranged side by side in a certain direction in the first internal space.

[0046] Air drawn from the second internal space into the first internal space via the first air supply device 21 passes through the chiller temperature change unit 23, which includes ice crusher heat exchangers 231-235, and is then delivered from the first internal space to the second internal space via the second air supply device. A temperature regulator 24 is provided on the side of the second air supply device 22 of the first air supply device 21, and the temperature regulator 24 controls the temperature of the first airflow CL1 from the first air supply device 21 as it is delivered to the chiller temperature and humidity change unit 23.

[0047] like Figure 2 As shown, each heat exchanger 231-235, when viewed in a cross-section perpendicular to its axis, has the following wing-like shape: a combination of a generally arcuate shape and a generally isosceles triangle with the chord of the arcuate shape as its base. The arcuate ... Figure 2 Between adjacent heat exchangers in the vertical direction, the wing head of one heat exchanger is adjacent to the wing tail of another heat exchanger.

[0048] pass Figure 1 and Figure 2It is evident that heat exchangers 231 to 235 are cylindrical bodies having an internal space for introducing crushed ice, extending with their axial direction approximately parallel to the vertical direction (including cases where they are inclined at an angle of less than 30°). Above each of the heat exchangers 231 to 235 are a crushed ice feeding guide 25 and an ice maker 26, which are equipped with a screw conveyor (not shown) for introducing crushed ice into the internal space. In this embodiment, the generally blade-shaped heat exchangers 231 to 235 are arranged with their axial direction approximately parallel to the vertical direction, but the generally blade-shaped heat exchangers 231 to 235 can also be arranged with their axial direction approximately parallel to the horizontal direction.

[0049] In addition, multiple holes are provided on the side walls of heat exchangers 231-235. The first airflow from the first air supply device 21 enters and exits the interior of the heat exchanger, and is cooled and humidified by these heat exchangers 231-235 to form a second airflow.

[0050] It should be noted that in this embodiment, the number of heat exchangers arranged side by side in a certain direction is "5", but it can also be more than 2 and less than 5, or more than 6.

[0051] Each heat exchanger 231-235 is made of, for example, stainless steel, copper, etc., and can be formed by punching multiple holes in a metal plate made of these materials and then bending it. It should be noted that the first air supply device 21 and the second air supply device 22 can also be made of a metal that is not easy to rust, such as stainless steel.

[0052] In this embodiment, firstly, the first cold air CL1 is introduced into the temperature regulator 24 via the first air supply device 21. When the temperature inside the storage chamber is +1°C or higher, the temperature of the first airflow CL1 is controlled to -5 to -10°C via the temperature regulator 24, and then introduced into the cold air temperature and humidity changing unit 23, which consists of multiple heat exchangers 231 to 235. In the cold air temperature and humidity changing unit 23, crushed ice from the ice maker 26 is introduced into the interior of each heat exchanger 231 to 235 via the crushed ice feeding guide 25.

[0053] Thus, the first airflow CL1 introduced into the cold air temperature and humidity changing unit 23, during its passage through the ventilation path SP between the heat exchangers 231-235 constituting the cold air temperature and humidity changing unit 23, comes into contact with the crushed ice supplied to the internal space of the heat exchangers 231-235 via the walls of the heat exchangers 231-235 in a falling manner. The airflow enters the internal space of the heat exchangers through holes formed in the side walls of the heat exchangers 231-235, directly contacting the crushed ice. As a result, the water vapor temperature in the first airflow CL1 is raised to 0°C by the cold air from the temperature regulator, causing the surface melted water to freeze and release the latent heat of solidification. It should be noted that the cold air or airflow CL2 containing water vapor at 0°C is, for example, in the range of -1°C to +0.5°C through mixing with the air inside the storage chamber.

[0054] Furthermore, the control device 27 controls the operation of the screw conveyor and ice maker for feeding crushed ice based on the output signal of an infrared sensor (not shown) that senses the position of crushed ice near the crushed ice inlet (e.g., the upper opening) of the heat exchanger 235. Specifically, the screw conveyor and ice maker operate continuously until the infrared sensor senses the position of the topmost ice block accumulated in the internal space of each of the heat exchangers 231-235 reaches a predetermined position, at which point crushed ice is fed into the internal space of each of the heat exchangers 231-235. For example, crushed ice is sequentially fed from the first heat exchanger 231 to the first heat exchangers 232, 233, and 234, and feeding is stopped when the first heat exchanger 235 is full. One hour after the feeding stops, the screw conveyor and ice maker are restarted to feed crushed ice again. The shape of the crushed ice is the same as that of the heat exchangers, forming an airfoil shape. As crushed ice is continuously supplied and filled, the ice blocks reach near the ice supply inlet. Comparing a full and partially filled state, a full state ensures sufficient ice volume and surface area. Due to the airflow within the storage chamber at temperatures above 0°C, some ice blocks melt, vaporize, or sublimate, causing them to shrink.

[0055] Furthermore, the ice melts, and the melted water vaporizes to produce water vapor at 0°C. This water vapor mixes with the first airflow CL1 to form the second airflow CL2. It should be noted that, as described above, the first airflow CL1 enters the internal space of the heat exchanger through holes formed in the sidewalls of heat exchangers 231-235. Therefore, the mixing efficiency of the first airflow CL1 and the water vapor increases.

[0056] The second airflow CL2 is cold air with a temperature of approximately 0°C and a relative humidity of approximately 80% to 100%. This second airflow CL2 is introduced into the storage room 10 via the second air supply device 22. Therefore, the stored items S, such as food, contained in the storage room 10 can be managed under conditions of approximately 0°C and approximately 100% relative humidity, thereby maintaining their quality.

[0057] It should be noted that, as described above, the temperature and humidity of the second internal space of the storage vault 10 are measured by the storage vault temperature and humidity sensor 11. The control device 27 can adjust the air volume of the first airflow CL1 through the first air supply device 21, the temperature adjustment of the first airflow CL1 in the temperature regulator 24, and the amount of crushed ice introduced at the cold air temperature and humidity change unit 23, so that the temperature of the second internal space of the storage vault 10 is stably maintained at around 0°C and the relative humidity is stably maintained at around 100%.

[0058] When the temperature measured by the temperature and humidity sensor 11 inside the warehouse is higher than +1°C, for example, Figure 3 As shown, the temperature regulator 24 is controlled by the control device 27 to deliver, for example, -10°C cold air to the cold air temperature and humidity control unit 23. When the temperature measured by the temperature and humidity sensor 11 inside the warehouse is lower than 0°C, the operation of the temperature regulator 24 is stopped.

[0059] It should be noted that, preferably, when the temperature measured by the temperature and humidity sensor 11 inside the storage room is less than +1°C and the measured humidity is less than 95%, the temperature regulator is stopped, and the first air supply device 21 and the second air supply device 22 are operated to deliver air with a temperature higher than 0°C inside the storage room to contact the evaporator, so that the humidity inside the storage room 10 is saturated. When the measured humidity reaches 100%, the operation of the ice maker 26 and the screw conveyor is stopped. However, in the hot and humid regions south of Honshu in Japan, extreme drops in humidity inside the storage room are less common, so the control of relative humidity can be omitted.

[0060] According to the evaporator of the first embodiment and the storage unit equipped with the evaporator, the wing heads 231A-235A and wing tails 231B-235B of the heat exchangers 231-235 are arranged adjacent to each other. The gap between the inlet side of the first airflow CL1 and the gap between the outlet side of the second airflow CL2, i.e., the spacing of the ventilation path SP sandwiched by the adjacent heat exchangers, is approximately equal along the airflow direction. Therefore, the wind speed on the inlet side of the first airflow CL1 and the wind speed on the outlet side of the second airflow CL2 are approximately constant. Therefore, cold air can stably pass through the ventilation path SP between the heat exchangers, i.e., the cold air temperature and humidity changing section 23. Therefore, compared with conventional evaporators, the static pressure in the cold air temperature and humidity changing section, i.e., the evaporator, is lower, and the airflow volume increases. As a result, the increased airflow volume increases the airflow that comes into contact with the melted water on the surface of the crushed ice, thereby enabling the target relative humidity to be achieved with a small amount of crushed ice. Therefore, the ice production volume is reduced, and power and water consumption can be saved.

[0061] It should be noted that, due to the presence of the temperature regulator 24, the temperature of the first airflow CL1 delivered from the first air supply device 21 can be appropriately adjusted, and its temperature (approximately 0°C) can be easily controlled when passing through the cold air temperature and humidity changing unit 23.

[0062] In this embodiment, the ice crushes piled in the evaporator have an airfoil-shaped cross-section, with the airfoil head and airfoil tail adjacent to each other. This increases the volume and surface area of ​​the ice crushes in the evaporator, and improves efficiency by increasing the airflow in contact with the surface of the ice crushes.

[0063] 33m manufactured according to patent document 1 2 A prefabricated, assembled, constant-temperature and high-humidity storage room (hereinafter referred to as "Storage Room ΛΛ") with a temperature of 0℃±1℃ and a relative humidity of 90%±5% was provided. The Storage Room ΛΛ of the comparative example has an evaporator comprising a cold air and humidity changing section composed of multiple airfoil-shaped heat exchangers. The wing head and tail of one of the airfoil-shaped heat exchangers are arranged opposite the wing head and tail of another airfoil-shaped heat exchanger in a parallel direction, wherein the other airfoil-shaped heat exchanger is arranged side-by-side with the first airfoil-shaped heat exchanger. After establishing a temperature of approximately 0℃ and a relative humidity of approximately 90% inside the storage room, the average daily water consumption of an ice maker operating at 60Hz AC, 100V single-phase, and consuming 493W of power was measured.

[0064] A storage tank (hereinafter referred to as "Storage Tank ΛV") was prepared according to one embodiment of the present invention. The Storage Tank ΛV of the embodiment includes an evaporator comprising a cold air and humidity changing section composed of a plurality of airfoil-shaped heat exchangers. The wing head and wing tail of one of the airfoil-shaped heat exchangers are arranged opposite the wing tail and wing head of another airfoil-shaped heat exchanger in a parallel direction, wherein the other airfoil-shaped heat exchanger is arranged side-by-side with the first airfoil-shaped heat exchanger. The average water consumption of the ice maker was measured under the same measurement conditions as in the comparative example.

[0065] [result]

[0066] Table 1 shows the above measurement results for the embodiments and comparative examples.

[0067] (Table 1)

[0068]

[0069] As shown in Table 1, the vault according to the embodiment can reduce electricity consumption and water consumption compared to the vault of the comparative example.

[0070] The foregoing has described several embodiments of the present invention, but these embodiments are merely illustrative and are not intended to limit the scope of the invention. These new embodiments can be implemented in various other ways, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their variations are included within the scope or spirit of the invention, and are included within the scope of the invention as described in the claims and its equivalents.

[0071] Even in high humidity conditions where the storage environment is set at +10°C and 80% or higher relative humidity, this embodiment can still be effective. In such cases, it is preferable to start supplying crushed ice only after the ice has melted to near the bottom of the evaporator. To increase the amount of ice melting in the evaporator, the average operating speed of the screw conveyor is slowed down. Therefore, the melting of the ice surface can be promoted at the guide in the crushed ice supply unit, thereby increasing the evaporation rate during air supply. When the evaporation rate increases, cooling can be performed using the heat of vaporization, thus reducing the burden on the temperature regulator and saving electricity. At +10°C, the rate of ATP decomposition in fish is slowest, thus it can be used to maintain the freshness of fish while maintaining its liveness. Furthermore, although the reason is unclear, it is known from experience that the appropriate storage temperature for wine or sake is also +10°C.

[0072] In the above embodiment, a first air supply device 21 and a second air supply device 22 are arranged within a first internal space defined by the wall. However, some or all of the components of the first air supply device 21 and / or the second air supply device 22 may be arranged in the second internal space. To allow air to circulate between the first and second internal spaces, a single air supply device or three or more air supply devices may be provided instead of two air supply devices. Alternatively, multiple additional first internal spaces, each containing a cold air temperature and humidity changing unit, may be defined by the wall along the airflow path formed by the air supply devices.

[0073] When viewed from above, each ice crusher heat exchanger appears wing-shaped. However, its shape does not have to be wing-shaped as long as the ventilation path SP is ensured, the airflow is ensured, and the airflow in contact with the melted water on the surface of the ice crusher is increased, so that the target relative humidity can be achieved with less ice crusher, and the amount of ice produced can be reduced to save electricity and water consumption.

[0074] For example, such as Figure 4 As shown, multiple ice-crushing heat exchangers 2311-2315, which are roughly rectangular cylindrical in shape, are arranged along the first internal space. Figure 4 The first interior space is arranged side by side in the vertical direction. Figure 4 The ice crusher heat exchangers 2311-2315 are defined by a pair of walls 30 and 31 extending in the left and right directions. The long side walls of the ice crusher heat exchangers 2311-2315 are respectively configured as a pair of long side walls along... Figure 4 Extending in the left and right directions (and the pair of short sidewalls along) Figure 4 (Extending vertically), multiple holes are provided on the long side wall. Crushed ice is supplied from the ice maker to the internal spaces of the roughly rectangular cylindrical crushed ice heat exchangers 2311 to 2315.

[0075] Figure 4 The multiple ice crusher heat exchangers 2311-2315 shown are all designed with the same shape, but the adjacent ice crusher heat exchangers may have different shapes, with the spacing between the opposing sidewalls of the parallel ice crusher heat exchangers being approximately equal in the ventilation direction. For example, the adjacent ice crusher heat exchangers may all be rectangular cylinders, and the rectangles may be rectangles with similar relationships.

[0076] Ice crusher 2311 and ice crusher 2315 are arranged in the first interior space with equal intervals D1 and D2. Interval D1 is the distance between one wall portion 30 and the ice crusher 2311 closest to that wall portion 30; interval D2 is the distance between the other wall portion 31 and the ice crusher 2315 closest to that other wall portion 31. However, intervals D1 and D2 can also be different.

[0077] In Figure 4 The parallel directions shown ( Figure 4 The heat exchangers 2311-2315, which are adjacent to each other in the vertical direction, are arranged in the first internal space with equal intervals d1, d2, d3, and d4. The intervals that constitute one pair of heat exchangers can also be different from the intervals that constitute another pair of heat exchangers.

[0078] The interval was designed with the equations D1 = D2 = d1 = d2 = d2 = d3 = d4 holding true. However, the interval can also be designed with the relation D1 = D2 ≠ d1 = d2 = d2 = d3 = d4 holding true.

[0079] like Figure 4 As shown, the long sidewalls of adjacent crushed ice heat exchangers in the parallel direction are all opposite each other, but the crushed ice heat exchangers can also be arranged such that only a portion of the long sidewalls of adjacent crushed ice heat exchangers in the parallel direction are opposite each other. For example, crushed ice heat exchanger 2311 can be arranged in the X-axis direction ( Figure 4 The configuration is staggered in the left and right directions.

[0080] The sidewalls of the opposing crushed ice heat exchangers are generally planar. Alternatively, the following shapes may be used: at least a portion of the sidewall of one crushed ice heat exchanger is designed as a convex curved surface (at least a portion of the sidewall in the profile of one crushed ice heat exchanger in cross-section is a convex curve), and at least a portion of the sidewall of the other crushed ice heat exchanger is designed as a concave curved surface (at least a portion of the sidewall in the profile of the other crushed ice heat exchanger in cross-section is a concave curve), and the gap formed by the at least portion of the sidewall is formed by a curved plate with approximately constant curvature or a curved plate with no change in the polarity of curvature.

[0081] Figure 5 The evaporator shown as a second embodiment of the present invention includes a cold air temperature and humidity changing unit 23, which is composed of a plurality of ice crushing heat exchangers 2321 to 2331. Each of the plurality of ice crushing heat exchangers 2321 to 2331 is formed into a generally regular hexagonal cylindrical shape and its central axis is arranged in an equilateral triangular lattice.

[0082] Multiple ice-crushing heat exchangers 2321 to 2331 are arranged in a translationally symmetrical configuration in the first internal space in a direction perpendicular to their axial direction. For example, as... Figure 5As shown, multiple ice crushing heat exchangers 2321-2331 are arranged such that a pair of opposing sidewalls are substantially parallel to a pair of walls defining a first internal space. At least one pair of sidewalls has multiple holes. Crushed ice is supplied from an ice maker to the internal space of the generally hexagonal cylindrical ice crushing heat exchangers 2321-2331.

[0083] Figure 6 The evaporator shown as a second embodiment of the present invention includes a cold air temperature and humidity changing section 23, which is composed of a plurality of ice crushing heat exchangers 2341 to 2352. Each of the plurality of ice crushing heat exchangers 2341 to 2352 is formed in a generally cylindrical shape and its center is arranged in a regular quadrilateral grid shape.

[0084] Crushed ice heat exchangers 2341 and 2352 are arranged in the first internal space with equal intervals D12 and D22. Interval D12 is the interval between one wall portion 30 and the nearest crushed ice heat exchanger 2341; interval D22 is the interval between the other wall portion 31 and the nearest crushed ice heat exchanger 2352. Intervals D12 and D22 can also be different intervals.

[0085] In Figure 6 The parallel directions shown ( Figure 6 The heat exchangers 2341-2352, which are adjacent to each other in the vertical direction, are arranged in the first internal space with equal intervals d12, d22, and d32. The intervals of the heat exchangers forming one pair can also be different from the intervals of the heat exchangers forming another pair.

[0086] The interval was designed with the equations D12 = D22 = d11 = d21 = d31 holding true. Alternatively, the interval could be designed with the relation D12 = D21 ≠ d12 = d22 = d32 holding true.

[0087] about Figure 5 , Figure 6 The spacing of the grid in the medium-sized crushed ice heat exchanger is appropriately designed based on the ease of airflow.

[0088] Multiple heat exchangers designed with rotational symmetry of the same shape may not be configured in an equilateral triangular lattice, but may be configured in other lattice shapes such as rhomboid lattice, square lattice, rectangular lattice, or parallel lattice.

[0089] Besides being roughly hexagonal cylindrical, heat exchangers can also be roughly cylindrical, roughly elliptical, or roughly polygonal, exhibiting rotational symmetry around a central axis. Furthermore, as with roughly cylindrical heat exchangers, the space or ventilation path between the sidewalls of adjacent heat exchangers may not extend along the airflow direction of the air supply device.

[0090] Symbol Explanation

[0091] 10 Low-temperature and high-humidity storage warehouse

[0092] 11. Warehouse temperature and humidity sensor

[0093] 20 Evaporator

[0094] 21 First air supply device

[0095] 22 Second air supply device

[0096] 23 Cold Air Temperature and Humidity Change Department

[0097] 231, 232, 233, 234, 235, 2311~2315, 2321~2331, 2341~2352 Crushed Ice Heat Exchangers

[0098] 231A~235A Crushed Ice Heat Exchanger Wing Head

[0099] 231B~235B Crushed Ice Heat Exchanger Tail Section

[0100] 24 Temperature Regulator

[0101] 25 Ice Crushing Guide

[0102] 26 Ice maker

[0103] 27 Control device

[0104] CL1 and CL2 airflow

[0105] The gaps in the crushed ice heat exchangers: d1~d4, d12, d22, d32

[0106] The gap between the D1 and D2 ice crusher heat exchangers and the casing

[0107] SP ventilation path

[0108] X (horizontal direction)

[0109] Y Depth Direction

[0110] Z represents the height direction.

Claims

1. An evaporator for use in a constant temperature and high humidity storage warehouse, characterized in that the evaporator comprises: One or more cold air temperature and humidity changing units, each comprising a plurality of crushed ice heat exchangers, wherein the plurality of crushed ice heat exchangers are arranged within a first internal space defined by a wall provided in the internal space of the constant temperature and high humidity storage facility, and have an internal space from which crushed ice is supplied from a crushed ice supply device; and, An air supply device is used to circulate cool air between the first interior space and the second interior space. Each of the multiple ice-crushing heat exchangers has multiple holes on its sidewall. The plurality of crushed ice heat exchangers are arranged side by side in the first internal space, with at least a portion of the sidewalls provided with the plurality of holes facing each other at equal intervals along the airflow direction of the air supply device. The plurality of ice-crushing heat exchangers are configured such that the cross-section of each ice-crushing heat exchanger is wing-shaped and cylindrical. In the parallel direction of the plurality of ice crushing heat exchangers, the wing head and wing tail of one ice crushing heat exchanger are respectively adjacent to the wing tail and wing head of another ice crushing heat exchanger adjacent to that one ice crushing heat exchanger.

2. The evaporator according to claim 1, characterized in that, Three or more of the aforementioned crushed ice heat exchangers are arranged side by side in the first internal space, such that the spacing of the sidewalls on which the plurality of holes are respectively provided is equal for all the aforementioned crushed ice heat exchangers, with the distance between each pair of adjacent crushed ice heat exchangers.

3. The evaporator according to claim 1, characterized in that, The ice crusher heat exchanger is disposed within the first internal space defined by the wall portion, such that the wall portion and the sidewall are evenly spaced apart and face each other along the airflow direction of the air supply device, and the sidewall is the sidewall of the ice crusher heat exchanger opposite the wall portion that is provided with the plurality of holes.

4. The evaporator according to claim 1, characterized in that, The multiple ice-crushing heat exchangers are designed to have the same shape.

5. The evaporator according to claim 1, characterized in that, The side surface of the ice crusher is shaped as follows: at least a portion of the sidewall of each of the adjacent ice crushers, which is opposite to each other and has the plurality of holes, is respectively formed as a planar shape, or as a convex curved surface and a concave curved surface.

6. The evaporator according to any one of claims 1 to 5, characterized in that, The device is equipped with a supply stop mechanism that stops supplying ice when the height of the ice blocks accumulated in all ice crushing heat exchangers reaches near the supply port of the ice crushing supply device.

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