Heat exchanger and total heat exchange ventilation system

Abstract

A heat exchanger comprising: a reversible airflow axial fan; a heat exchange element arranged side by side with the axial fan in the airflow direction; a pair of flow adjusting sections on both sides of the heat exchange element in the airflow direction; and a pipe that is a cylindrical body extending in the airflow direction and accommodating the axial fan, the heat exchange element, and the pair of flow adjusting sections, wherein each of the pair of flow adjusting sections has a flow adjusting plate, which is displaceable so that the orientation thereof can be changed, and adjusts the airflow according to the orientation of the flow adjusting plate.

Description

[Technical Field]

[0001] This disclosure relates to a heat exchange device and a total heat exchange ventilation system. This application claims priority to Japanese Patent Application No. 2023-17213, filed on February 8, 2023, the contents of which are incorporated herein by reference. [Background technology]

[0002] A heat storage element that can store heat up to a predetermined temperature while absorbing heat and moisture from gas, and a ventilation unit using the same, are known (see, for example, Patent Document 1). In Patent Document 1, two ventilation units can each supply and exhaust air. In each ventilation unit, the rotation direction of the ventilation fan when supplying air and the rotation direction of the ventilation fan when exhausting air are switched to opposite directions.

[0003] In a ventilation unit that exhausts air, the rotation of the ventilation fan draws in indoor air and supplies it to the heat storage element, and the air that passes through the heat storage element is exhausted outdoors. In a ventilation unit that supplies air, the rotation of the ventilation fan draws in outdoor air through the heat storage element, and the air that passes through the heat storage element is supplied indoors. The heat storage element absorbs the heat and moisture contained in the air that passes through it and accumulates them up to a predetermined value. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Laid-Open No. 2013-113463 Summary of the Invention [Problem to be solved by the invention]

[0005] When the ventilation fan is an axial fan, the following non-uniformity in the air speed distribution (air speed unevenness) occurs in the heat storage element when the ventilation fan is supplying air and exhausting air. For example, when the ventilation fan is sucking air from the heat storage element during exhaust, measurement of the air speed of the indoor air flowing into the heat storage element shows that the air speed is relatively fast on the axial side of the ventilation fan (the center of the heat storage element) and relatively slow on the outer circumferential edge side of the ventilation fan (the outer part of the heat storage element). On the other hand, when the ventilation fan is supplying air to the heat storage element during intake, measurement of the air speed of the outdoor air flowing out of the heat storage element shows that the air speed is relatively slow on the axial side of the ventilation fan (the inner side of the heat storage element) and relatively fast on the outer circumferential edge side of the ventilation fan (the outer side of the heat storage element).

[0006] Therefore, during exhaust, the air flow rate is high at the outer part of the heat storage element where the air speed is relatively high, and low at the center part of the heat storage element where the air speed is relatively low. Conversely, during intake, the air flow rate is high at the center part of the heat storage element and low at the outer part of the heat storage element. Such uneven air speed may reduce the efficiency of latent heat (humidity) exchange in the heat storage element. Air speed unevenness is particularly likely to occur in ductless heat exchangers where the distance between the axial fan and the heat storage element is short.

[0007] For example, when high-temperature, high-humidity outdoor air is supplied, most of the outdoor air flows through the outer part of the heat storage element and has difficulty flowing through the center of the heat storage element, so a large amount of moisture is absorbed by the outer part of the heat storage element. Then, when low-temperature, low-humidity indoor air is exhausted, most of the indoor air flows through the center of the heat storage element and has difficulty flowing through the outer part of the heat storage element, so moisture is not easily released by the outer part of the heat storage element. In this case, moisture is only absorbed but not released by the outer part of the heat storage element, which may cause condensation.

[0008] An object of one aspect of the present disclosure is to provide a heat exchange device and a total heat exchange ventilation system that can suppress a decrease in the exchange efficiency of latent heat (humidity) in a heat exchange element. [Means for solving the problem]

[0009] A heat exchange device according to one aspect of the present disclosure comprises an axial fan capable of switching the direction of airflow to the opposite side, a heat exchange element aligned with the axial fan in the direction of the airflow, a pair of straightening units provided on both sides of the heat exchange element in the direction of the airflow, and a cylindrical body extending in the direction of the airflow and accommodating the axial fan, the heat exchange element, and the pair of straightening units, wherein each of the pair of straightening units has a straightening plate that can be displaced to change direction and straightens the airflow according to the orientation of the straightening plate.

[0010] In one aspect of the present disclosure, a total heat exchange ventilation system includes a heat exchange device provided in a space portion, the heat exchange device including a first heat exchange device and a second heat exchange device, and when the first heat exchange device supplies air to the space portion, the second heat exchange device exhausts air from the space portion, and the supply air and the exhaust air are switched in conjunction with each other. [Brief explanation of the drawings]

[0011] [Figure 1] FIG. 1 is an overall configuration diagram of a total heat exchange ventilation system. [Figure 2] 1 is a perspective view of a heat exchange device according to a first embodiment. [Figure 3] 2 is a longitudinal cross-sectional view of the heat exchange device according to the first embodiment, viewed in the X direction. FIG. [Figure 4A] FIG. 2 is a vertical cross-sectional view showing the heat exchange device in the air supply mode according to the first embodiment. [Figure 4B] FIG. 4 is a perspective view of the first airflow rectifying section in an air supply mode according to the first embodiment. [Figure 4C] FIG. 10 is a perspective view of the second airflow rectifying section in the air supply mode according to the first embodiment. [Figure 5] 5A and 5B are diagrams for explaining a drive mechanism for a current plate according to the first embodiment. [Figure 6A] FIG. 2 is a vertical cross-sectional view showing the heat exchange device in exhaust mode according to the first embodiment. [Figure 6B] FIG. 4 is a perspective view of a second airflow straightening portion in an exhaust mode according to the first embodiment. [Figure 6C]FIG. 4 is a perspective view of a first airflow straightening portion in an exhaust mode according to the first embodiment. [Figure 7A] FIG. 11 is a perspective view of a first airflow rectifying section in an air supply mode according to a second embodiment. [Figure 7B] FIG. 11 is a perspective view of a second airflow rectifying section in an air supply mode according to a second embodiment. [Figure 8A] FIG. 11 is a perspective view of a second airflow straightening portion in an exhaust mode according to a second embodiment. [Figure 8B] FIG. 11 is a perspective view of a first airflow straightening portion in an exhaust mode according to a second embodiment. [Figure 9] FIG. 10 is a perspective view of a first rectifying portion according to a first modified example. [Figure 10A] FIG. 11 is a perspective view of a first airflow rectifying section in an air supply mode according to a second modified example. [Figure 10B] FIG. 11 is a perspective view of a first airflow straightening portion in an exhaust mode according to a second modified example. [Figure 11A] FIG. 10 is a plan view of a horizontal flow straightening vane according to a third embodiment. [Figure 11B] FIG. 10 is a perspective view of a horizontal flow straightening plate according to a third embodiment. [Figure 12] FIG. 11 is a cross-sectional view showing a heat exchange device in an air supply mode according to a third embodiment. [Figure 13] FIG. 10 is a cross-sectional view showing a heat exchanger in an exhaust mode according to a third embodiment. [Figure 14A] FIG. 11 is a perspective view of a first airflow rectifying section in an air supply mode according to the fourth embodiment. [Figure 14B] FIG. 13 is a perspective view of a second airflow rectifying section in an air supply mode according to the fourth embodiment. [Figure 15A] FIG. 11 is a perspective view of a first airflow straightening unit in an exhaust mode according to the fourth embodiment. [Figure 15B] FIG. 11 is a perspective view of a first airflow straightening unit in an exhaust mode according to the fourth embodiment. [Figure 16] FIG. 11 is a perspective view of a current plate according to a third modified example. DETAILED DESCRIPTION OF THE INVENTION

[0012] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In the drawings, the same or equivalent elements are designated by the same reference numerals, and redundant description will be omitted.

[0013] [First embodiment] [Total heat exchange ventilation system 1] Fig. 1 is an overall configuration diagram of a total heat exchange ventilation system 1. As shown in Fig. 1, the total heat exchange ventilation system 1 includes a heat exchanger 100 and a control device 900. The heat exchanger 100 is installed in a hole that penetrates a wall W of a structure such as a building or a residence, and exchanges sensible heat (temperature) and latent heat (humidity) between intake air from outside and exhaust air from inside the room, thereby suppressing changes in temperature and humidity inside the room during ventilation.

[0014] The control device 900 is a computer that is connected to the heat exchange device 100 by wire or wirelessly and drives and controls the heat exchange device 100, and has a processor such as a CPU. The control device 900 may include an MCU (Micro Control Unit) or an MPU (Micro Processor Unit), or may include an FPGA (Field Programmable Gate Array), an ASIC (Application Specific Integrated Circuit), or other computing functions.

[0015] The total heat exchange ventilation system 1 of this example has a plurality of heat exchange devices 100 (two in the example of FIG. 1 ). The plurality of heat exchange devices 100 are provided indoors (space S) of a building. The plurality of heat exchange devices 100 include a first heat exchange device 100A and a second heat exchange device 100B. The first heat exchange device 100A may be one heat exchange device 100 or may be multiple heat exchange devices 100. The second heat exchange device 100B may be one heat exchange device 100 or may be multiple heat exchange devices 100.

[0016] The control device 900 drives and controls each heat exchange device 100 so that when the first heat exchange device 100A supplies air to the space S, the second heat exchange device 100B exhausts air from the space S. Furthermore, the control device 900 drives and controls each heat exchange device 100 so that the above-mentioned supply and exhaust operations are switched in conjunction with each other. Specifically, the control device 900 switches the operation mode of the first heat exchange device 100A between the supply mode and the exhaust mode, and switches the operation mode of the second heat exchange device 100B between the exhaust mode and the supply mode, at a predetermined timing.

[0017] As a result, one of the first heat exchange device 100A and the second heat exchange device 100B operates in air supply mode while the other operates in exhaust mode, thereby ventilating the space S. At this time, each of the first heat exchange device 100A and the second heat exchange device 100B absorbs heat and moisture through total heat exchange with air in one of the air supply mode and exhaust mode, and releases heat and moisture through total heat exchange with air in the other mode. Therefore, changes in temperature and humidity in the space S during ventilation are suppressed.

[0018] [Overall structure of heat exchange device 100] Fig. 2 is a perspective view of the heat exchanger 100 according to the first embodiment. Fig. 3 is a longitudinal cross-sectional view of the heat exchanger 100 according to the first embodiment, seen in the X direction. The heat exchanger 100 is a ductless heat exchanger including an axial fan 110, a heat exchange element 120, a pair of rectifiers 130, and a pipe 140.

[0019] When the axial flow fan 110 rotates, it generates an airflow along an axis O that passes through the center of rotation of the axial flow fan 110. The axial flow fan 110 is a reversible flow fan that can switch the direction of the airflow to the opposite side by reversing its rotation direction. The heat exchange element 120 is a heat medium that has the function of exchanging total heat (sensible heat and latent heat), and is aligned with the axial flow fan 110 in the airflow direction. The pair of rectifiers 130 are members for adjusting the direction of the airflow, and are provided on both sides of the heat exchange element 120 in the airflow direction.

[0020] The pipe 140 is a cylindrical body extending in the direction of the airflow, and houses the axial fan 110, the heat exchange element 120, and a pair of rectifiers 130. Hereinafter, the direction in which the hole penetrates the wall W is referred to as the Z direction. The pipe 140 is fitted tightly into the hole in the wall W so that its axial direction extends in the Z direction. When the pipe 140 is viewed from the Z direction, the opening of the pipe 140 extends in the horizontal direction (X direction) and the vertical direction (Y direction). The openings at both ends of the pipe 140 face the indoors and outdoors. In this example, the pipe 140 is a rectangular tube, but it may have another tube shape (for example, a cylindrical or triangular tube) that fits the hole in the wall W.

[0021] The pair of rectifiers 130 includes a first rectifier 131 and a second rectifier 132. Inside the pipe 140, the axial fan 110, the first rectifier 131, the heat exchange element 120, and the second rectifier 132 are arranged in this order from the outdoors toward the indoors. When the axial fan 110 rotates, an airflow in the Z direction is generated inside the pipe 140. The axis O of the axial fan 110 substantially coincides with the center line of the cross section of the pipe 140 and extends in the Z direction so as to pass through the centers of the cross sections of the pair of rectifiers 130 and the heat exchange element 120. Note that the axial fan 110, the first rectifier 131, the heat exchange element 120, and the second rectifier 132 may also be arranged in this order from the indoors toward the outdoors inside the pipe 140.

[0022] In the air supply mode of the heat exchanger 100, the control device 900 rotates the axial fan 110 in the normal direction to generate an airflow from the outdoors to the indoors (an airflow directed downstream in the Z direction). The outdoor air blown from the axial fan 110 is supplied to the heat exchanger element 120 via the first rectifier 131. At this time, the heat exchanger element 120 exchanges total heat with the outdoor air passing through it. The outdoor air that has passed through the heat exchanger element 120 flows into the indoors via the second rectifier 132.

[0023] In the exhaust mode of the heat exchanger 100, the control device 900 reverses the rotation of the axial fan 110 to generate an airflow from indoors to outdoors (an airflow directed upstream in the Z direction). The indoor air drawn into the axial fan 110 flows into the heat exchange element 120 via the second rectification section 132. At this time, the heat exchange element 120 exchanges total heat with the indoor air passing through it. The indoor air that has passed through the heat exchange element 120 passes through the first rectification section 131 and the axial fan 110 and is discharged outdoors.

[0024] [Heat exchange element 120] The heat exchange element 120 has a structure in which a humidity control material is supported on a heat storage substrate. The humidity control material has the property of absorbing moisture when the surrounding humidity is relatively high compared to its own equilibrium humidity, and releasing moisture when the surrounding humidity is relatively low. Unlike desiccants such as silica gel, the humidity control material can repeatedly absorb and release moisture, so in principle it can be effective semi-permanently.

[0025] The humidity conditioner of this example includes a water-absorbent resin and a humidity-conditioning component (humidity-conditioning liquid) impregnated into the water-absorbent resin. The water-absorbent resin may be an ionic resin or a non-ionic resin. Specific examples of ionic resins include alkali metal salts of polyacrylic acid and starch-acrylate graft polymers. Specific examples of alkali metal salts of polyacrylic acid include sodium polyacrylate. Specific examples of non-ionic resins include vinyl acetate copolymers, maleic anhydride copolymers, polyvinyl alcohol, and polyalkylene oxides.

[0026] The humidity-regulating component preferably contains at least one selected from the group consisting of deliquescent substances that absorb moisture in the air and deliquesce, and polyhydric alcohols, which can further enhance the humidity-regulating effect.

[0027] Specific examples of polyhydric alcohols include glycerin, propanediol, butanediol, pentanediol, trimethylolpropane, butanetriol, ethylene glycol, diethylene glycol, and triethylene glycol. Among these, polyhydric alcohols having three or more hydroxyl groups, such as glycerin, are more preferred. The polyhydric alcohol may form a dimer or polymer. The polyhydric alcohol may contain only one of the above materials, or two or more of them.

[0028] Deliquescent substances are classified into salts and water-soluble organic substances. Specific examples of salts include sodium formate, potassium formate, ammonium formate, sodium acetate, potassium acetate, lithium acetate, ammonium acetate, sodium lactate, potassium lactate, sodium benzoate, potassium benzoate, sodium propionate, potassium propionate, calcium chloride, lithium chloride, and magnesium chloride. ,salt Examples of suitable salts include potassium formate, sodium chloride, zinc chloride, aluminum chloride, lithium bromide, calcium bromide, potassium bromide, sodium hydroxide, sodium pyrrolidonecarboxylate, potassium carbonate, calcium citrate, sodium citrate, potassium citrate, and lithium citrate. Only one of these salts may be contained, or two or more may be contained. Among these, sodium formate, potassium formate, sodium acetate, potassium acetate, and potassium carbonate are preferred, as they absorb and release a large amount of moisture per weight. Furthermore, among these, salts selected from the group consisting of carboxylates (sodium formate, sodium acetate, and sodium propionate) are preferred, as they form hydrate crystals in a humidity range of 30 to 80% relative humidity in the environment in which they are used, thereby promoting rapid absorption and release of moisture at a specific humidity range.

[0029] Specific examples of water-soluble organic substances include sugars such as sucrose, pullulan, glucose, xylol, fructose, mannitol, and sorbitol, carboxylic acids such as citric acid, and amides such as urea.

[0030] Assuming that the humidity-regulating component contains a deliquescent substance, other components may be added as additives to adjust the threshold humidity. Specific examples of such components include other of Examples of the nucleating material include deliquescent substances, polyhydric alcohols, and materials that act as nucleating materials for hydrate crystals. Specific examples of the nucleating material include carboxylic acids having two or more carboxyl groups and amides having two or more amide groups.

[0031] In addition, when the heat storage substrate on which the humidity-conditioning material is supported is made of metal, metal salts may cause corrosion of the heat storage substrate. Therefore, when the heat storage substrate is made of metal, it is preferable to select a carboxylate or a polyhydric alcohol as the humidity-conditioning component. As for the shape of the humidity-conditioning material, the water-absorbent resin may be in the form of a powder, particle, or block, or the water-absorbent resin may be supported on a ventilation member to efficiently contact with air.

[0032] The heat storage substrate may be made of a material made of hydrophilic fibers such as a porous body, nonwoven fabric, woven fabric, etc., in order to retain the humidity-conditioning component in a moist state. Alternatively, the heat storage substrate may be made of a material made of, for example, metal (aluminum, etc.) or ceramics in order to increase the heat storage capacity in order to improve the efficiency of heat exchange with the air.

[0033] The heat storage substrate is made of a sheet material made of the above-mentioned materials. In the manufacturing process of the heat exchange element 120, this sheet material is formed into various shapes such as a flat plate, pleated, honeycomb, etc. For example, the sheet is first formed into a wave (fluted) shape using a corrugator. Next, the formed sheet material is fixed with an adhesive to a flat liner made of the same or a different material as the sheet material, to produce an integrated heat storage substrate.

[0034] As a result, a large number of cells having minute cavities surrounded by the sheet material and liner are formed in the heat storage substrate. In the heat exchange element 120, the large number of cells formed in the heat storage substrate extend so as to penetrate the heat storage substrate in the Z direction. The heat exchange element 120 has a layered structure (corrugated structure) of wavy semicircular cells. Air in the pipe 140 flows through the cells, allowing it to pass through the heat exchange element 120 in the Z direction. During the manufacturing process of the heat exchange element 120, a humidity control material is attached to the inner surface of these cells. Note that the cell shape of the heat exchange element 120 is not limited to the above, and various shapes such as hexagonal (honeycomb), circular, and triangular shapes can be used.

[0035] When ceramics are used as the heat storage substrate, a honeycomb structure with an arrangement of cells of a hexagonal or other uniform shape is preferred. A large number of cells separated by porous partitions extend through the heat storage substrate in the Z direction, creating a large number of flow paths. In a method for manufacturing a honeycomb structure for a ceramic heat exchange element, a clay is first prepared by kneading raw materials such as ceramic raw material powder, binder, and pore-forming material. This clay is then extruded using a screw extruder to produce a molded body with a honeycomb structure. The resulting molded body is then dried or fired to produce a single heat storage substrate.

[0036] In this example, a metal is used as the material for the heat storage substrate to increase the heat storage capacity. The heat storage substrate of the heat exchange element 120 is fabricated by stacking metal sheets made of this metal. This heat storage substrate has a large number of cells formed therein, each having minute cavities surrounded by metal sheets. This makes the heat exchange element 120 a ventilation member that allows the air to be treated to flow along the inner surfaces of the cells.

[0037] As mentioned above, a humidity-regulating material is applied to the inner surface of the cell. In this example, since the heat storage substrate of the heat exchange element 120 is metal, a carboxylate that forms hydrate crystals is used as the humidity-regulating component. More preferably, the humidity-regulating component contains a carboxylate that forms hydrate crystals and an additive that adjusts the crystallization threshold humidity. This allows the threshold humidity to be freely adjusted while suppressing corrosion of the heat storage substrate.

[0038] In the heat exchange element 120 described above, the metal heat storage substrate can exchange sensible heat (temperature) with the air in the cells, and the humidity conditioner can exchange latent heat (humidity) with the air in the cells. To improve the efficiency of this heat exchange, it is desirable to have a large contact area between the heat exchange element 120 and the air. From this perspective, in order to increase the surface area of ​​the heat storage substrate, a thinner metal sheet may be used to form a larger number of fine cells. In order to increase the surface area of ​​the humidity conditioner, the particle size of the water-absorbent resin of the humidity conditioner may be made smaller, so that a larger number of humidity conditioners are attached to the inner surfaces of the cells.

[0039] [Pair of rectifiers 130] Fig. 4A is a vertical cross-sectional view showing the heat exchanger 100 in the air supply mode according to the first embodiment. Fig. 4B is a perspective view of the first rectifier 131 in the air supply mode according to the first embodiment. Fig. 4C is a perspective view of the second rectifier 132 in the air supply mode according to the first embodiment. Fig. 5 is a diagram for explaining the drive mechanism of the rectifier vane 300 according to the first embodiment. For ease of understanding, Fig. 4A omits the pipe 140, and only the horizontal rectifier vane 311 of the first rectifier 131 is shown, and only the horizontal rectifier vane 321 of the second rectifier 132 is shown.

[0040] As described above, when a structure in which a humidity-regulating material is attached to the cells of a metal heat storage substrate is employed in the heat exchange element 120, sensible heat (temperature) moves easily between the metal cells, but latent heat (humidity) moves less easily between the metal cells. If airflow speed unevenness occurs in this heat exchange element 120, there is a high possibility of condensation occurring, particularly due to imbalances in the absorption and release of latent heat (humidity). Therefore, in this embodiment, a pair of rectifying units 130 is provided to suppress airflow speed unevenness in the heat exchange element 120. Each of the pair of rectifying units 130 has a rectifying plate 300 (see FIG. 3) that can be displaced to change direction, and rectifies the airflow according to the direction of the rectifying plate 300.

[0041] 4B , the first airflow rectifier 131 has a rectangular frame 411 fixed to the inner circumferential surface of the pipe 140. Two vertical frames 412 extending in the Y direction are provided at an opening penetrating the inside of the frame 411 in the Z direction, symmetrically on the left and right sides with the center of the frame 411 in the X direction sandwiched between them. Two horizontal frames 413 extending in the X direction are provided between the two vertical frames 412, symmetrically on the top and bottom sides with the center of the frame 411 in the Y direction sandwiched between them. The square-shaped opening surrounded by the vertical frames 412 and the horizontal frames 413 is referred to as a central opening 131A of the first airflow rectifier 131. The axis O of the axial fan 110 passes through the central opening 131A.

[0042] The first rectifying section 131 is provided with a plurality of rectifying plates 300. In this example, the plurality of rectifying plates 300 includes two horizontal rectifying plates 311 and two vertical rectifying plates 312. Each horizontal rectifying plate 311 is a plate for adjusting the direction of the airflow in the up-down direction (Y direction). Each vertical rectifying plate 312 is a plate for adjusting the direction of the airflow in the left-right direction (X direction).

[0043] The two horizontal flow straightening plates 311 are rectangular in shape and are long in the X direction, and extend from the two horizontal frames 413 toward the heat exchange element 120 (downstream in the Z direction). The two vertical flow straightening plates 312 are rectangular in shape and are long in the Y direction, and extend from the two vertical frames 412 toward the heat exchange element 120 (downstream in the Z direction). These four flow straightening plates 300 are arranged to surround the central opening 131A. In this example, each flow straightening plate 300 is closer to the inner circumferential surface of the pipe 140 than to the axis O.

[0044] The plurality of rectifying plates 300 are rotatable so that the end of each rectifying plate 300 on the heat exchange element 120 side approaches the axis O. For example, FIG. 5 shows the movable mechanism of the lower horizontal rectifying plate 311 of the two horizontal rectifying plates 311. A support shaft 501 extending in the X direction is provided inside the lower horizontal frame 413 of the two horizontal frames 413. The end of the lower horizontal rectifying plate 311 on the axial fan 110 side (upstream side in the Z direction) is fixed to the support shaft 501 so as to be rotatable integrally with it. A gear 502 is provided on the end of the support shaft 501 in the X direction. The gear 502 is arranged inside the vertical frame 412 and is connected to a gear 503 located below it by a belt 504.

[0045] The gear 503 is fixed to the shaft of a motor that is driven to rotate by the control device 900. When the control device 900 rotates this motor, the rotation of the gear 503 is transmitted to the gear 502 via the belt 504, and the horizontal straightening vane 311 rotates around the support shaft 501. As a result, the horizontal straightening vane 311 in this example is displaceable between a normal position (see FIG. 6C ) in which it extends substantially horizontally and an inclined position (see FIG. 4B ) in which it is inclined toward the axis O. When the horizontal straightening vane 311 is displaced from the normal position to the inclined position, the horizontal straightening vane 311 is inclined obliquely backward so that the end 3110 on the heat exchange element 120 side (downstream side in the Z direction) approaches the axis O.

[0046] The other rectifying vanes 300 (the upper horizontal rectifying vane 311 and the two vertical rectifying vanes 312) can also be rotated by a mechanism similar to that shown in Fig. 5. The vertical rectifying vane 312 in this example can be displaced between a normal position (see Fig. 6C) extending substantially vertically and an inclined position (see Fig. 4B) inclined toward the axis O. The drive mechanism for the rectifying vane 300 is not limited to the example shown in Fig. 5, and any mechanism can be used as long as it can displace the rectifying vane 300 between the normal position and the inclined position.

[0047] 4C , like the first rectifier 131, the second rectifier 132 has a rectangular frame 421, and two vertical frames 422 and two horizontal frames 423 are provided at the opening of the frame 421. The square opening surrounded by the vertical frames 422 and the horizontal frames 423 is referred to as the central opening 132A of the second rectifier 132. The axis O of the axial fan 110 passes through the central opening 132A.

[0048] Similar to the first rectifier 131, the second rectifier 132 has a plurality of rectifier plates 300 (two horizontal rectifier plates 321 and two vertical rectifier plates 322). The two horizontal rectifier plates 321 extend from two horizontal frames 423 toward the heat exchange element 120 (upstream side in the Z direction). The two vertical rectifier plates 322 extend from two vertical frames 422 toward the heat exchange element 120 (upstream side in the Z direction). These four rectifier plates 300 are arranged to surround a central opening 132A. In this example, each rectifier plate 300 is closer to the axis O than to the inner circumferential surface of the pipe 140. Therefore, the central opening 132A of the second rectifier 132 is smaller than the central opening 131A of the first rectifier 131, and the entire central opening 132A is arranged inside the central opening 131A when viewed from the Z direction.

[0049] The rectifying plates 300 of the second rectifying section 132 are also rotatable by a mechanism similar to that shown in Fig. 5. However, the rectifying plates 300 of the second rectifying section 132 are rotatable so that the end of each rectifying plate 300 on the heat exchange element 120 side approaches the inner circumferential surface of the pipe 140 (the outer portion of the pipe 140). In this example, the horizontal rectifying plate 321 is displaceable between a normal position (see Fig. 4C) in which it extends substantially horizontally and an inclined position (see Fig. 6B) in which it inclines toward the inner circumferential surface of the pipe 140. The vertical rectifying plate 322 is displaceable between a normal position (see Fig. 4C) in which it extends substantially vertically and an inclined position (see Fig. 6B) in which it inclines toward the inner circumferential surface of the pipe 140.

[0050] As described above, the airflow direction in the axial fan 110 is switched depending on the air intake mode and the exhaust mode. Each of the pair of rectifiers 130 (first rectifier 131 and second rectifier 132) changes the orientation of the rectifier plate 300 in response to the switching of the airflow direction in the axial fan 110. The pair of rectifiers 130 includes an upstream rectifier located upstream of the heat exchange element 120 in the airflow direction, and a downstream rectifier located downstream of the heat exchange element. As will be described later, in the air intake mode, the first rectifier 131 is the upstream rectifier, and the second rectifier 132 is the downstream rectifier. In the exhaust mode, the first rectifier 131 is the downstream rectifier, and the second rectifier 132 is the upstream rectifier.

[0051] When the airflow direction is changed in the axial fan 110, the upstream rectifier changes the orientation of the rectifier vane 300 so that the rectifier vane 300 diffuses part of the airflow radially inward or radially outward from the axis O of the axial fan 110. The downstream rectifier changes the orientation of the rectifier vane 300 so that the area of ​​the rectifier vane 300 facing the airflow becomes smaller. The driving modes in the air supply mode and the exhaust mode will be described below.

[0052] [Air supply mode operation] 4A, in the heat exchanger 100 in the air supply mode, the forward rotation of the axial fan 110 generates an airflow from the outdoors to the indoors (an airflow directed downstream in the Z direction). At this time, the wind speed of the airflow sent by the axial fan 110 toward the heat exchange element 120 increases from the axis O toward the inner circumferential surface of the pipe 140. Therefore, on the first surface 121 of the heat exchange element 120 facing the axial fan 110, a high-speed airflow ST1 is supplied to the inner circumferential surface of the pipe 140, while a low-speed airflow ST3 is supplied to the center side of the pipe 140 (the side of the axis O), which may cause uneven wind speed.

[0053] Therefore, when the airflow direction is switched from the axial fan 110 toward the heat exchange element 120, the upstream rectifier changes the orientation of the airflow rectifier vane 300 so that the airflow rectifier vane 300 approaches the axis O as it moves downstream in the airflow direction and so that the angle between the airflow rectifier vane 300 and the axis O is 45 degrees or less. The downstream rectifier changes the orientation of the airflow rectifier vane 300 so that the airflow rectifier vane 300 is parallel to the axis O. In this example, as shown in FIGS. 4A to 4C , when the air supply mode is executed, the control device 900 displaces each of the airflow rectifier vanes 300 of the first rectifier unit 131 to an inclined position and displaces each of the airflow rectifier vanes 300 of the second rectifier unit 132 to a normal position. The airflow rectifier vanes 300 in the inclined position are rotated, for example, by 30 degrees from the normal position.

[0054] 4A and 4B, in the first stabilizing section 131, all of the plurality of stabilizing plates 300 (horizontal stabilizing plates 311 and vertical stabilizing plates 312) are inclined radially inward about the axis O toward the heat exchange element 120 (downstream side in the Z direction). The airflow supplied from the axial flow fan 110 is diffused radially inward about the axis O along each stabilizing plate 300. In detail, the vertical direction (Y direction) of the airflow is adjusted to face the center of the pipe 140 along the horizontal stabilizing plate 311, and the vertical direction (Y direction) of the airflow is adjusted to face the center of the pipe 140 along the vertical stabilizing plate 312. This improves the flow rate and flow velocity of the airflow at the center of the pipe 140, through which the low-speed airflow ST3 flows.

[0055] Because the inclination angle of each straightening vane 300 with respect to the axis O is 45 degrees or less, each straightening vane 300 can smoothly guide the airflow flowing in the Z direction and suppress a decrease in the flow velocity of the airflow. In the first straightening section 131 of this example, each straightening vane 300 is closer to the inner circumferential surface of the pipe 140 than to the axis O. Therefore, each straightening vane 300 reliably comes into contact with the high-speed airflow ST1 flowing along the inner circumferential surface of the pipe 140, and can diffuse the airflow ST1 radially inward from the axis O.

[0056] As a result, the airflow passing through the first rectifying portion 131 and heading toward the heat exchange element 120 is supplied at a substantially uniform wind speed across the entire first surface 121. This medium-speed airflow ST2 undergoes total heat exchange as it passes through the heat exchange element 120 and is discharged from the second surface 122 of the heat exchange element 120. The airflow ST2 discharged from the second surface 122 passes through the second rectifying portion 132 and is supplied into the room. At this time, as shown in FIGS. 4A and 4C , in the second rectifying portion 132, each of the rectifying plates 300 displaced to its normal position extends substantially parallel to the Z direction. Therefore, the airflow ST2 passing through the second rectifying portion 132 is prevented from decreasing in flow speed due to contact with each of the rectifying plates 300, and can therefore flow smoothly toward the room.

[0057] [Exhaust mode operation] Fig. 6A is a vertical cross-sectional view showing the heat exchanger 100 in exhaust mode according to the first embodiment. Fig. 6B is a perspective view of the second rectifier 132 in exhaust mode according to the first embodiment. Fig. 6C is a perspective view of the first rectifier 131 in exhaust mode according to the first embodiment.

[0058] 6A, in the heat exchanger 100 in the exhaust mode, the axial fan 110 reverses its rotation to generate an airflow from the room to the outside (an airflow directed upstream in the Z direction). At this time, the wind speed of the airflow directed from the room to the heat exchange element 120 by the suction force of the axial fan 110 decreases from the axis O toward the inner circumferential surface of the pipe 140. Therefore, on the second surface 122 of the heat exchange element 120 facing the opposite side from the axial fan 110, a high-speed airflow ST1 is supplied to the center side of the pipe 140 (the axis O side), while a low-speed airflow ST3 is supplied to the inner circumferential surface side of the pipe 140, which may cause uneven wind speeds.

[0059] Therefore, when the airflow direction is switched from the heat exchange element 120 toward the axial fan 110, the upstream rectifier changes the orientation of the airflow rectifier vane 300 so that the airflow rectifier vane 300 moves farther away from the axis O toward the downstream side of the airflow direction and so that the angle between the airflow rectifier vane 300 and the axis O is 45 degrees or less. The downstream rectifier changes the orientation of the airflow rectifier vane 300 so that the airflow rectifier vane 300 is parallel to the axis O. In this example, as shown in FIGS. 6A to 6C , when the exhaust mode is executed, the control device 900 displaces each of the airflow rectifier vanes 300 of the first rectifier unit 131 to the normal position and displaces each of the airflow rectifier vanes 300 of the second rectifier unit 132 to the inclined position. The airflow rectifier vanes 300 in the inclined position are rotated, for example, by 30 degrees from the normal position.

[0060] As a result, as shown in FIGS. 6A and 6B , in the second stabilizing section 132, all of the plurality of stabilizing plates 300 (horizontal stabilizing plates 321 and vertical stabilizing plates 322) are inclined radially outward from the axis O toward the heat exchange element 120 (upstream side in the Z direction). The airflow sucked by the axial fan 110 is diffused radially outward from the axis O along each stabilizing plate 300. In detail, the vertical direction (Y direction) of the airflow is adjusted to face the inner circumferential surface of the pipe 140 along the horizontal stabilizing plate 321, and the vertical direction (Y direction) of the airflow is adjusted to face the inner circumferential surface of the pipe 140 along the vertical stabilizing plate 322. As a result, the flow rate and flow velocity of the airflow are improved on the inner circumferential surface side of the pipe 140, through which the low-speed airflow ST3 flows.

[0061] Because the inclination angle of each straightening vane 300 with respect to the axis O is 45 degrees or less, each straightening vane 300 can smoothly guide the airflow flowing in the Z direction and suppress a decrease in the flow velocity of the airflow. In the second straightening section 132 of this example, each straightening vane 300 is closer to the axis O than to the inner circumferential surface of the pipe 140. Therefore, each straightening vane 300 reliably comes into contact with the high-speed airflow ST1 flowing along the axis O and can diffuse the airflow ST1 radially outward from the axis O.

[0062] As a result, the airflow passing through the second rectifying portion 132 and heading toward the heat exchange element 120 is supplied to the entire second surface 122 at a substantially uniform wind speed. This medium-speed airflow ST2 is totally heat exchanged as it passes through the heat exchange element 120 and is discharged from the first surface 121 of the heat exchange element 120. The airflow ST2 discharged from the first surface 121 passes through the first rectifying portion 131 and the axial flow fan 110 and is exhausted to the outdoors. At this time, as shown in FIGS. 6A and 6C , in the first rectifying portion 131, each of the rectifying plates 300 displaced to its normal position extends substantially parallel to the Z direction. Therefore, the airflow ST2 passing through the first rectifying portion 131 is prevented from decreasing in flow speed due to contact with each of the rectifying plates 300, and can therefore smoothly flow out toward the outdoors.

[0063] [Second embodiment] The pair of rectification sections 130 is not limited to the structure shown in the first embodiment, and various structures can be employed. In the following second to fourth embodiments, the structure of the pair of rectification sections 130 differs from that of the first embodiment.

[0064] A pair of rectifiers 130 according to the second embodiment will be described. Fig. 7A is a perspective view of a first rectifier 131 in the air supply mode according to the second embodiment. Fig. 7B is a perspective view of a second rectifier 132 in the air supply mode according to the second embodiment. Fig. 8A is a perspective view of the second rectifier 132 in the exhaust mode according to the second embodiment. Fig. 8B is a perspective view of the first rectifier 131 in the exhaust mode according to the second embodiment.

[0065] As shown in FIG. 7A, the first rectifying unit 131 has a frame portion 411 and multiple rectifying plates 300, similar to the first embodiment. In the second embodiment, the multiple rectifying plates 300 include multiple horizontal rectifying plates 311A ​​and 311B, but do not include a vertical rectifying plate 312 (see FIG. 4B). Each of the horizontal rectifying plates 311A ​​and 311B has a rectangular shape extending in the X direction through the inner opening of the frame portion 411, and both ends thereof are supported by the vertical frame of the frame portion 411. The multiple (three in this example) horizontal rectifying plates 311A ​​are arranged at intervals from each other upward from the center of the opening of the frame portion 411. The multiple (three in this example) horizontal rectifying plates 311B are arranged at intervals from each other downward from the center of the opening of the frame portion 411.

[0066] Each of the horizontal flow straightening vanes 311A, 311B is displaceable between a normal position (see FIG. 8B) extending substantially horizontally and an inclined position (see FIG. 7A) inclined toward the axis O. Specifically, when the multiple horizontal flow straightening vanes 311A ​​are displaced from the normal position to the inclined position, they all incline obliquely downward. When the multiple horizontal flow straightening vanes 311B are displaced from the normal position to the inclined position, they all incline obliquely upward. At this time, the inclination angle of these flow straightening vanes 300 (horizontal flow straightening vanes 311A, 311B) with respect to the axis O is 45 degrees or less.

[0067] As shown in FIG. 7B, the second rectifying unit 132 has a frame 421 and a plurality of rectifying plates 300 (a plurality of horizontal rectifying plates 321A, 321B), similar to the first rectifying unit 131. Each of the horizontal rectifying plates 321A, 321B can be positioned in a normal position (FIG. 8) extending substantially horizontally.B ) and the tilt position inclined toward the axis O (see Figure 7 A (see reference) and can be displaced.

[0068] 7A and 7B, when the air supply mode is executed, the control device 900 displaces each of the rectifying plates 300 of the first rectifying unit 131 to an inclined position, and displaces each of the rectifying plates 300 of the second rectifying unit 132 to a normal position. As a result, in the first rectifying unit 131, the direction of the airflow in the vertical direction (Y direction) is adjusted along each of the rectifying plates 300, so that the airflow is directed radially inward from the axis O. To, The air is supplied at a substantially uniform speed over the entire first surface 121. In the second rectifying section 132, each rectifying plate 300 extends substantially parallel to the Z direction, so that a decrease in the flow speed of the airflow is suppressed, and the airflow can flow smoothly into the room.

[0069] 8A and 8B, when the exhaust mode is executed, the control device 900 displaces each of the rectifying plates 300 of the first rectifying unit 131 to the normal position, and displaces each of the rectifying plates 300 of the second rectifying unit 132 to the inclined position. As a result, in the second rectifying unit 132, the vertical direction of the airflow (Y direction) is adjusted along each of the rectifying plates 300, so that the airflow is diffused radially outward from the axis O and supplied at a substantially uniform wind speed over the entire second surface 122. In the first rectifying unit 131, each of the rectifying plates 300 extends substantially parallel to the Z direction, so that a decrease in the flow speed of the airflow is suppressed, and the airflow can be smoothly discharged outdoors.

[0070] The frame 411 of the rectifier 130 is not limited to a rectangular frame shape, and various shapes can be adopted that correspond to the holes to which the rectifier 130 is attached. The multiple rectifier plates 300 are not limited to being the same shape or size, and may be different shapes or sizes. FIG. 9 is a perspective view of the first rectifier 131 according to the first modified example. For example, in the first rectifier 131 of the first modified example, the frame 411 is a circular frame shape, and the left-right lengths of the multiple rectifier plates 300 become smaller the further away from the center of the opening of the frame 411.

[0071] The rectifying plate 300 of the rectifying unit 130 is not limited to a flat plate shape, and various shapes can be adopted. Fig. 10A is a perspective view of the first rectifying unit 131 in the air supply mode according to the second modified example. .figure 10B is a perspective view of the first rectifying section 131 in the exhaust mode according to the second modified example.

[0072] 10A, the first rectifying unit 131 of the second modified example has a frame portion 411 (not shown) and a plurality of rectifying plates 300. The plurality of rectifying plates 300 includes a set of an upper rectifying plate 1011 and a lower rectifying plate 1012. The upper rectifying plate 1011 is a semicircular curved plate that protrudes upward when viewed from the Z direction. Lower rectifier plate 1012 is a semicircular curved plate that protrudes downward when viewed from the Z direction. A cylinder 1001 that penetrates in the Z direction is supported at the center of the inner opening of the frame part 411. The upper flow plate 1011 and the lower flow plate 1012 are arranged vertically side by side on the outer periphery of the cylinder 1001 and are rotatably supported by the cylinder 1001.

[0073] 10A, when each rectifying plate 300 is displaced to the inclined position in the air supply mode, the upper rectifying plate 1011 and the lower rectifying plate 1012 rotate in directions away from each other, and their ends on the heat exchange element 120 side (downstream side in the Z direction) approach the axis O. As a result, in the first rectifying section 131, the direction of the airflow in the vertical direction (Y direction) is adjusted along the upper rectifying plate 1011 and the lower rectifying plate 1012, so that the airflow is supplied to the entire first surface 121 at a substantially uniform wind speed.

[0074] 10B, when each of the straightening plates 300 is displaced to its normal position in the exhaust mode, the upper straightening plate 1011 and the lower straightening plate 1012 are stacked one on top of the other in a horizontal position, forming a cylindrical shape extending in the Z direction as a whole. As a result, in the first straightening section 131, the upper straightening plate 1011 and the lower straightening plate 1012 extend substantially parallel to the Z direction, so that a decrease in the flow velocity of the airflow is suppressed, and the air can flow smoothly outdoors.

[0075] [Third embodiment] A pair of rectifying units 130 according to a third embodiment will be described. The third embodiment differs from the second embodiment in that fins 1102 and 1103 for adjusting the direction of the airflow in the left-right direction (X direction) are provided on a rectifying plate 300 for adjusting the direction of the airflow in the up-down direction (Y direction). third11B is a plan view of a horizontal flow regulating plate 311A ​​according to the embodiment. third Fig. 12 is a perspective view of a horizontal straightening plate 311A ​​according to the embodiment. Fig. 13 is a horizontal cross-sectional view of the heat exchanger 100 in the exhaust mode according to the third embodiment.

[0076] 11A and 11B, each of the multiple horizontal flow straightening vanes 311A ​​provided in the first flow straightening section 131 has a slat 1101 and multiple fins 1102, 1103. The slat 1101 is the plate body of the horizontal flow straightening vane 311A ​​and extends radially outward from a rotation center line C that is perpendicular to the direction of the airflow. The rotation center line C passes through an axis that supports the rotation of the slat 1101. The multiple fins 1102, 1103 extend upright from the surface of the slat 1101 in a direction that intersects with the rotation center line C.

[0077] In this example, three fins 1102 and three fins 1103 are provided symmetrically on both sides of the axis O in each horizontal straightening plate 311A. The rotation center line C extends in the X direction, which is perpendicular to the airflow direction (Z direction). The three fins 1102 are inclined toward the axis O (upper right side in FIG. 11A) toward the heat exchange element 120 (downstream side in the Z direction). The three fins 1103 are inclined toward the axis O (upper left side in FIG. 11A) toward the heat exchange element 120 (downstream side in the Z direction). The inclination angle of each fin 1102, 1103 with respect to the axis O is 45 degrees or less.

[0078] Similar to the horizontal flow straightening plate 311A, the multiple horizontal flow straightening plates 311B also have multiple fins 1102, 1103 provided on the slats 1101. That is, in the flow straightening plate 300 (horizontal flow straightening plates 311A, 311B) of the first flow straightening section 131, the fins 1102, 1103 extend closer to the rotation center line C the further downstream they are in the direction of the airflow in the air supply mode (downstream in the Z direction).

[0079] Similar to the above-described first rectifying section 131, the second rectifying section 132 has fins 1102, 1103 provided on a plurality of rectifying plates 300 (a plurality of horizontal rectifying plates 321A, 321B). However, in the rectifying plates 300 (horizontal rectifying plates 321A, 321B) of the second rectifying section 132, the fins 1102, 1103 of the rectifying plates 300 extend farther away from the rotation center line C as they move toward the downstream side in the airflow direction in the exhaust mode (the upstream side in the Z direction) (see FIGS. 12 and 13).

[0080] In each of the flow rectifying plates 300, a central gap 1104 is formed between the plurality of fins 1202 and the plurality of fins 1203, through which the axis O passes in a plan view. The formation width (length in the X direction) of the central gap 1104 is the sum of the shortest distance L1 from the axis O to the plurality of fins 1102 in a plan view and the shortest distance L2 from the axis O to the plurality of fins 1103 in a plan view. In this example, the formation width of the central gap 1104 is larger in the flow rectifying plate 300 of the first flow rectifying section 131 than in the flow rectifying plate 300 of the second flow rectifying section 132 (see FIGS. 12 and 13 ).

[0081] In the first rectifier 131 in the air supply mode, the direction of the airflow in the up-down direction (Y direction) is adjusted along the slats 1101 of each rectifier vane 300, and the airflow is diffused radially inward about the axis O. Furthermore, as shown in FIG. 12 , the direction of the airflow in the left-right direction (X direction) is adjusted along the fins 1102, 1103 of each rectifier vane 300, and the airflow is diffused radially inward about the axis O. In the second rectifier 132 in the exhaust mode, the direction of the airflow in the up-down direction (Y direction) is adjusted along the slats 1101 of each rectifier vane 300, and the airflow is diffused radially outward about the axis O. Furthermore, as shown in FIG. 13 , the direction of the airflow in the left-right direction (X direction) is adjusted along the fins 1102, 1103 of each rectifier vane 300, and the airflow is guided radially outward about the axis O.

[0082] As a result, even if the first and second rectifiers 131 and 132 do not include the vertical rectifier plates 312, they can adjust both the vertical (Y direction) and horizontal (X direction) directions of the airflow, thereby suppressing unevenness in the wind speed of the airflow in the heat exchange element 120. Since the inclination angle of each of the fins 1102, 1103 with respect to the axis O is 45 degrees or less, each rectifier plate 300 can smoothly guide the airflow flowing in the Z direction, and suppress a decrease in the flow speed of the airflow.

[0083] In this example, the first flow rectifying unit 131 has a large central gap 1104, and therefore the multiple fins 1102, 1103 are arranged biased toward the inner circumferential surface of the pipe 140. The fins 1102, 1103 of the first flow rectifying unit 131 are in reliable contact with the high-speed airflow ST1 flowing along the inner circumferential surface of the pipe 140, and can diffuse the airflow ST1 radially inward about the axis O. On the other hand, the second flow rectifying unit 132 has a small central gap 1104, and therefore the multiple fins 1102, 1103 are arranged biased toward the center of the pipe 140. The fins 1102, 1103 of the second flow rectifying unit 132 are in reliable contact with the high-speed airflow ST1 flowing along the center of the pipe 140, and can diffuse the airflow ST1 radially outward about the axis O.

[0084] As a modification of the above embodiment, fins 1102, 1103 for adjusting the direction of the airflow in the up-down direction (Y direction) may be provided on the airflow rectifier 300 (for example, vertical airflow rectifiers 312, 322) for adjusting the direction of the airflow in the left-right direction (X direction). In this case, in each airflow rectifier 300, the left-right direction (X direction) of the airflow is adjusted along the slats 1101, and further the up-down direction (Y direction) of the airflow is adjusted along the fins 1102, 1103, so that the airflow can be diffused radially inward or outward from the axis O.

[0085] [Fourth embodiment] A pair of rectifiers 130 according to a fourth embodiment will be described. The fourth embodiment differs from the first to third embodiments in that the airflow is adjusted by the opening area of ​​a plurality of openings 1400 provided in the rectifier plate 300. Fig. 14A is a perspective view of a first rectifier 131 in the air supply mode according to the fourth embodiment. Fig. 14B is a perspective view of a second rectifier 132 in the air supply mode according to the fourth embodiment. Fig. 15A is a perspective view of a second rectifier 132 in the air exhaust mode according to the fourth embodiment. one Rectifier section 13 1 15B is a perspective view of the first rectifying unit 131 in the exhaust mode according to the fourth embodiment. In FIGS. 14A and 14B, the drive mechanism for the rectifying plate 300 is omitted.

[0086] As shown in FIG. 14A, in the first rectifying unit 131 of the fourth embodiment, one rectifying plate 300 is rotatably supported at the inner opening of the frame portion 411. The rectifying plate 300 has a plurality of openings 1400 penetrating in the thickness direction. The opening areas of the plurality of openings 1400 become smaller as they are further away from the axis O. As shown in FIG. 14B, the second rectifying unit 132 of the fourth embodiment has the same configuration as the first rectifying unit 131, but differs in that the opening areas of the plurality of openings 1400 become larger as they are further away from the axis O. The larger the opening area of ​​the opening 1400, the smaller the airflow resistance, and the smaller the opening area, the greater the airflow resistance.

[0087] As shown in FIG. 15A, the rectifying vane 300 of the first rectifying unit 131 is fixed to a shaft 1501 extending vertically through the inner opening of the frame 411. A gear 1502 is fixed to one end of the shaft 1501, and the gear 1502 meshes with a gear 1503 of a motor. As the motor rotates, the rectifying vane 300 rotates and is displaced between an inclined position and a normal position. As shown in FIG. 14A, when the rectifying vane 300 is displaced to the inclined position, the rectifying vane 300 extends perpendicular to the direction of the airflow (Z direction) and closes the inner opening of the frame 411. As shown in FIG. 15A, when the rectifying vane 300 is displaced to the normal position, the rectifying vane 300 extends parallel to the direction of the airflow (Z direction) and opens the inner opening of the frame 411. The rectifying vane 300 of the second rectifying unit 132 is also displaced between an inclined position and a normal position by a similar mechanism.

[0088] The drive mechanism of the rectifying vane 300 is not limited to the above. For example, as shown in Fig. 15B, the rectifying vane 300 may have a structure in which two blades are connected by a hinge, and the two blades may open and close in response to the rotation of the motor. In this case, when the two blades are folded closed in response to the rotation of the motor, the rectifying vane 300 may have a drive mechanism as shown in Fig. 1. 5 As shown in FIG. 15B, the rectifying vane 300 extends parallel to the direction of the airflow (Z direction) and opens the inside of the frame portion 411. When the two blades open in response to the rotation of the motor, the rectifying vane 300 extends perpendicular to the direction of the airflow (Z direction) and closes the inner opening of the frame portion 411, as shown in FIG.

[0089] When the air supply mode is executed, the control device 900 displaces the rectifying vane 300 of the first rectifying unit 131 to the inclined position (see FIG. 14A), and displaces the rectifying vane 300 of the second rectifying unit 132 to the normal position (see FIGS. 15A and 15B). In the first rectifying unit 131, the high-speed airflow ST1 flowing along the inner circumferential surface side of the pipe 140 passes through the opening 1400 with a small opening area, and therefore the flow velocity is likely to decrease. The low-speed airflow ST3 flowing along the center side of the pipe 140 passes through the opening 1400 with a large opening area, and therefore the flow velocity is unlikely to decrease.

[0090] As a result, the airflow passing through the rectifying plate 300 of the first rectifying section 131 is diffused from the inner circumferential surface side to the center side of the pipe 140. The airflow that has passed through the first rectifying section 131 is supplied at a substantially uniform wind speed over the entire first surface 121 of the heat exchange element 120. In the second rectifying section 132, the rectifying plate 300 extends substantially parallel to the Z direction, so a decrease in the flow speed of the airflow is suppressed.

[0091] When the exhaust mode is executed, the control device 900 displaces the rectifying vane 300 of the first rectifying unit 131 to the normal position (see FIGS. 15A and 15B), and displaces the rectifying vane 300 of the second rectifying unit 132 to the inclined position (see FIG. 14B). In the second rectifying unit 132, the high-speed airflow ST1 flowing toward the center of the pipe 140 passes through the opening 1400 with a small opening area, and therefore the flow velocity is likely to decrease. The low-speed airflow ST3 flowing toward the inner peripheral surface of the pipe 140 passes through the opening 1400 with a large opening area, and therefore the flow velocity is unlikely to decrease.

[0092] As a result, the airflow passing through the rectifying plate 300 of the second rectifying section 132 is diffused from the center side to the inner peripheral surface side of the pipe 140. The airflow that has passed through the second rectifying section 132 is supplied at a substantially uniform wind speed over the entire second surface 122 of the heat exchange element 120. In the first rectifying section 131, the rectifying plate 300 extends substantially parallel to the Z direction, so a decrease in the flow speed of the airflow is suppressed.

[0093] Various embodiments can be employed for the number, shape, and formation method of the multiple openings 1400. For example, the multiple openings 1400 may be formed from punched metal, or may be formed in a mesh or slit shape. FIG. 16 is a perspective view of a flow rectifying plate 300 according to a third modified example. In the third modified example, each of the multiple openings 1400 extends in a semicircular arc shape centered on the axis O. Since the flow rectifying plate 300 in FIG. 16 is used in the first flow rectifying section 131, the opening width of the multiple openings 1400 decreases as they are further away from the axis O. When the flow rectifying plate 300 is used in the second flow rectifying section 132, the opening width of the multiple openings 1400 increases as they are further away from the axis O.

[0094] [Fifth embodiment] As mentioned above, a large number of fine cells may be formed in a heat storage substrate made of a thin metal sheet in the heat exchange element 120. In this case, the surface area of ​​the heat exchange element 120 (i.e., the area of ​​contact with air) can be increased to improve the heat exchange efficiency, but the thinness of the heat storage substrate may result in a decrease in the heat storage capacity.

[0095] Therefore, in the heat exchange device 100 of the fifth embodiment, the rectifying plates 300 of the pair of rectifying sections 130 are made of metal, and a latent heat storage material is attached to these rectifying plates 300. This allows heat exchange not only in the heat storage substrate of the heat exchange element 120 but also in the pair of rectifying sections 130, thereby increasing the overall heat storage capacity of the heat exchange device 100. Furthermore, because heat exchange is possible in one of the pair of rectifying sections 130 before the air flows into the heat exchange element 120, the exchange efficiency of sensible heat and latent heat is improved.

[0096] A latent heat storage material is a material that stores latent heat exchanged with the outside during a phase change or transition of a substance as thermal energy. Latent heat storage materials utilize the heat of fusion and heat of solidification at their melting points. Latent heat storage materials undergo a phase change between solid and liquid. Because latent heat storage materials store heat at the phase change temperature, they can store heat in a boundary region (i.e., at a constant temperature). This principle is based on the phenomenon that as long as two layers, solid and liquid, coexist during a phase change, heat is continuously absorbed from the outside, preventing the temperature from rising above the melting point. The melting point of a latent heat storage material is 10 to 35°C, preferably 20 to 35°C. A melting point in the range of 10 to 35°C allows the latent heat storage material to effectively store heat when the heat exchanger 100 functions as a total heat exchanger to exchange heat between indoor air and outdoor air.

[0097] Specific examples of latent heat storage materials include fatty acids such as palmitic acid and myristic acid, aromatic hydrocarbon compounds such as benzene and p-xylene, ester compounds such as isopropyl palmitate, butyl stearate, stearyl stearate, and myristyl myristate, alcohols such as stearyl alcohol and glycerol, d-lactic acid, acetic acid, capric acid, and ethylenediamine. Examples of aliphatic hydrocarbons include paraffins. Examples of paraffins include linear and branched paraffins, with linear n-paraffins being preferred. Examples of n-paraffins include n-pentadecane, n-hexadecane, n-heptadecane, n-octadecane, and n-nonadecane. Examples of hydrates include Zn(NO3)2·6H20, NaHPO4·12H20, Na2CO3·10H20, Na2SO4·10H20, Li2NO3·3H20, Ca2Cl2·6H20, Ca2CO3·10H20, and FeBr3·6H20. These latent heat storage components may be used alone or in combination of two or more. It is preferable to use a chemically and physically stable and inexpensive substance as the latent heat storage component.

[0098] For example, when n-paraffin is used as a latent heat storage material, because n-paraffin is hydrophobic, it is difficult to mix n-paraffin with a latent heat storage material that is a humidity-controlling material that exchanges moisture and support it on the substrate of the heat exchange element 120. According to this embodiment, an aqueous humidity-controlling material is supported on the heat exchange element 120, while a hydrophobic latent heat storage material is supported on the rectifying plate 300, which is the sensible heat exchanger. This makes it possible to independently control and support the aqueous humidity-controlling material and the hydrophobic latent heat storage material in the heat exchanger 100, improving the production efficiency of the heat exchanger 100. Depending on the differences in the surface water affinity of the heat storage substrate, the humidity-controlling material and the latent heat storage material can each be supported on an optimal substrate.

[0099] When a hydrate salt is used as a latent heat storage material, the latent heat storage material may be affected by the exchange of moisture with the humidity-controlling component. According to this embodiment, the hydrate salt and the humidity-controlling component are not mixed together, and total heat exchange is performed in a state in which the latent heat storage material is continuously present on the heat storage substrate in the straightening plate 300, making it possible to control each of them.

[0100] A temperature control agent in which a latent heat storage material is held in a gel-like resin may be supported on the rectifying plate 300, which is the sensible heat exchanger. In this case, the latent heat storage material undergoes a phase change in a gel state, improving the fluidity of the latent heat storage material and allowing a larger heat storage capacity to be held in the rectifying plate 300. A temperature control agent in which a latent heat storage material is encapsulated in microcapsules may be supported on the sensible heat exchanger. In this case, the latent heat storage material undergoes a phase change in the microcapsules, improving the fluidity of the latent heat storage material and allowing a larger heat storage capacity to be held in the rectifying plate 300.

[0101] [remarks] The present disclosure is not limited to the above-described embodiments, and various modifications are possible within the scope of the claims. Embodiments obtained by appropriately combining the technical means disclosed in different embodiments are also included in the technical scope of the present disclosure. Furthermore, new technical features can be formed by combining the technical means disclosed in each embodiment.

[0102] Various embodiments can be employed for the number and shape of the multiple rectifying plates 300 in each rectifying section 130. For example, in the rectifying section 130 of the first embodiment, multiple horizontal rectifying plates 321 may be arranged on both the top and bottom sides of the axis O, or multiple vertical rectifying plates 322 may be arranged on both the left and right sides of the axis O. In the rectifying section 130 of the second modified example, the multiple rectifying plates 300 may be composed of three or more curved plates (for example, four curved plates on the top, bottom, left and right sides).

[0103] When the control device 900 displaces the plurality of rectifying plates 300 provided in each rectifying unit 130 to the inclined position, the inclination angles of the rectifying plates 300 may be different from each other. For example, in the rectifying unit 130 in the exhaust mode, the inclination angles of the rectifying plates 300 on the center side of the pipe 140 may be made smaller, and the inclination angles of the rectifying plates 300 on the inner peripheral surface side of the pipe 140 may be made larger.

Claims

1. An axial fan that can switch the airflow direction to the opposite side, a heat exchange element aligned in the direction of the axial flow fan and the airflow; a pair of rectifying units provided on both sides of the heat exchange element in the direction of the airflow; a cylindrical body extending in the direction of the airflow, the cylindrical body including a pipe accommodating the axial flow fan, the heat exchange element, and the pair of flow straightening units; each of the pair of rectifying units has a rectifying vane that is displaceable so as to change direction, rectifies the airflow according to the direction of the rectifying vane, and changes the direction of the rectifying vane according to the change in the direction of the airflow in the axial flow fan; the pair of rectifying units includes an upstream rectifying unit located upstream of the heat exchange element in the direction of the airflow, and a downstream rectifying unit located downstream of the heat exchange element, When the direction of the airflow is changed in the axial flow fan, the upstream rectifying portion changes the orientation of the rectifying vane so that the rectifying vane diffuses a portion of the airflow radially inward or radially outward of an axis of the axial flow fan, The downstream rectifying unit changes the orientation of the rectifying plate so that an area of ​​the rectifying plate facing the airflow becomes smaller. heat exchange equipment.

2. When the direction of the airflow is switched from the axial fan to the heat exchange element, the upstream rectifying unit changes the orientation of the rectifying plate so that the rectifying plate approaches the axis as it moves downstream in the airflow direction, and so that the angle between the rectifying plate and the axis is 45 degrees or less, When the direction of the airflow is switched from the heat exchange element to the axial fan, the upstream rectifying unit changes the orientation of the rectifying plate so that the rectifying plate moves away from the axis toward the downstream side of the airflow direction and so that the angle between the rectifying plate and the axis is 45 degrees or less. The heat exchange device of claim 1 .

3. The heat exchange device according to claim 1 , wherein when the direction of the airflow is changed in the axial fan, the downstream straightening portion changes the orientation of the straightening plate so that the straightening plate and the axis are parallel to each other.

4. An axial flow fan that can switch the airflow direction to the opposite side; a heat exchange element aligned in the direction of the axial flow fan and the airflow; a pair of rectifying units provided on both sides of the heat exchange element in the direction of the airflow; a cylindrical body extending in the direction of the airflow, the cylindrical body including a pipe accommodating the axial flow fan, the heat exchange element, and the pair of flow straightening units; Each of the pair of rectifying units has a rectifying plate that is displaceable so as to change direction, and rectifies the airflow according to the direction of the rectifying plate; the straightening vane has slats extending radially outward from a rotation center line perpendicular to the direction of the airflow, and fins standing upright from surfaces of the slats and extending in a direction intersecting the rotation center line, The fins extend closer to the rotation center line or further away from the rotation center line as they move downstream in the airflow direction. heat exchange equipment.

5. An axial flow fan that can switch the airflow direction to the opposite side; a heat exchange element aligned in the direction of the axial flow fan and the airflow; a pair of rectifying units provided on both sides of the heat exchange element in the direction of the airflow; a cylindrical body extending in the direction of the airflow, the cylindrical body including a pipe accommodating the axial flow fan, the heat exchange element, and the pair of flow straightening units; Each of the pair of rectifying units has a rectifying plate that is displaceable so as to change direction, and rectifies the airflow according to the direction of the rectifying plate; The rectifying plate has a plurality of openings penetrating in a thickness direction, The opening areas of the plurality of openings become smaller or larger as they are spaced apart from the axis of the axial flow fan. heat exchange equipment.

6. An axial flow fan that can switch the airflow direction to the opposite side; a heat exchange element aligned in the direction of the axial flow fan and the airflow; a pair of rectifying units provided on both sides of the heat exchange element in the direction of the airflow; a cylindrical body extending in the direction of the airflow, the cylindrical body including a pipe accommodating the axial flow fan, the heat exchange element, and the pair of flow straightening units; Each of the pair of rectifying units has a rectifying plate that is displaceable so as to change direction, and rectifies the airflow according to the direction of the rectifying plate; the heat exchange element is a ventilation member formed by laminating metal sheets and allowing the air to be treated to flow along the inner surface of the cell; A humidity control material is attached to the inner surface of the cell. heat exchange equipment.

7. The heat exchange device according to claim 6 , wherein the humidity-conditioning material includes a water-absorbent resin and a humidity-conditioning component impregnated in the water-absorbent resin.

8. The heat exchange device according to claim 7 , wherein the humidity control component is a deliquescent substance.

9. The heat exchange device according to claim 7 , wherein the humidity-regulating component includes a carboxylate that forms a hydrate crystal and an additive that adjusts the crystallization threshold humidity.

10. An axial flow fan that can switch the airflow direction to the opposite side; a heat exchange element aligned in the direction of the axial flow fan and the airflow; a pair of rectifying units provided on both sides of the heat exchange element in the direction of the airflow; a cylindrical body extending in the direction of the airflow, the cylindrical body including a pipe accommodating the axial flow fan, the heat exchange element, and the pair of flow straightening units; Each of the pair of rectifying units has a rectifying plate that is displaceable so as to change direction, and rectifies the airflow according to the direction of the rectifying plate; The rectifying plate is made of metal and has a latent heat storage material attached thereto. heat exchange equipment.

11. A heat exchange device is provided in the space portion, The heat exchange device is An axial fan that can switch the airflow direction to the opposite side, a heat exchange element aligned in the direction of the axial flow fan and the airflow; a pair of rectifying units provided on both sides of the heat exchange element in the direction of the airflow; a cylindrical body extending in the direction of the airflow, the cylindrical body including a pipe accommodating the axial flow fan, the heat exchange element, and the pair of flow straightening units; Each of the pair of rectifying units has a rectifying plate that is displaceable so as to change direction, and rectifies the airflow according to the direction of the rectifying plate; the heat exchange device includes a first heat exchange device and a second heat exchange device; When the first heat exchange device supplies air to the space, the second heat exchange device exhausts air from the space, and the supply of air and the exhaust of air are switched in conjunction with each other. Total heat exchange ventilation system.