WO2024053082A1 - Élément d'échange de chaleur et dispositif de ventilation à échange de chaleur - Google Patents

Élément d'échange de chaleur et dispositif de ventilation à échange de chaleur Download PDF

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Publication number
WO2024053082A1
WO2024053082A1 PCT/JP2022/033848 JP2022033848W WO2024053082A1 WO 2024053082 A1 WO2024053082 A1 WO 2024053082A1 JP 2022033848 W JP2022033848 W JP 2022033848W WO 2024053082 A1 WO2024053082 A1 WO 2024053082A1
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Prior art keywords
partition plate
heat exchange
flow path
counterflow
section
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PCT/JP2022/033848
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English (en)
Japanese (ja)
Inventor
史恭 三宅
一 外川
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三菱電機株式会社
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Priority to PCT/JP2022/033848 priority Critical patent/WO2024053082A1/fr
Publication of WO2024053082A1 publication Critical patent/WO2024053082A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F7/00—Ventilation
    • F24F7/04—Ventilation with ducting systems, e.g. by double walls; with natural circulation
    • F24F7/06—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit
    • F24F7/08—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit with separate ducts for supplied and exhausted air with provisions for reversal of the input and output systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements

Definitions

  • the present disclosure relates to a heat exchange element that allows two fluids, an intake air flow and an exhaust flow, to pass between laminated plate materials and exchanges heat between the respective fluids, and a heat exchange ventilation device equipped with the same.
  • Two fluid flow formats used in conventional heat exchange elements include cross flow, in which two fluids flow orthogonally to each other, and counterflow, in which two fluids flow opposite to each other.
  • cross flow in which two fluids flow orthogonally to each other
  • counterflow in which two fluids flow opposite to each other.
  • the amount of heat exchange per unit volume is theoretically greater in the counterflow type. For this reason, many conventional heat exchange ventilators employ counterflow type heat exchange elements.
  • Patent Document 1 discloses a counterflow type heat exchange element having a plurality of flow channels formed of plate materials, each flow channel having a rectangular cross section.
  • the conventional heat exchange element disclosed in Patent Document 1 allows two fluids to pass alternately and oppositely in the vertical and horizontal directions of each channel, thereby allowing the fluid to flow between the upper and lower channels through the partition plate that constitutes the channel.
  • heat exchange can also be performed between the left and right channels.
  • the conventional heat exchange element has a larger heat exchange area than a heat exchange element having a simple configuration in which two fluids are alternately opposed only in the vertical direction via partition plates.
  • each flow path by making each flow path into a rectangular shape that is elongated in the vertical direction, it is possible to increase the cross-sectional area of each flow path and to increase the heat exchange area. As a result, the conventional heat exchange element was able to obtain high sensible heat exchange efficiency while suppressing pressure loss.
  • heat exchange elements are required to have high total heat exchange efficiency, and in order to obtain high total heat exchange efficiency, it is necessary to simultaneously improve not only the sensible heat exchange efficiency but also the humidity exchange efficiency.
  • humidity exchange efficiency it is necessary to use partition plates with high moisture permeability, but due to the material characteristics of materials with high moisture permeability such as poor elasticity, it is necessary to use partition plates that are long in the vertical direction. It was difficult to mold. Therefore, it is not possible to use materials with high moisture permeability in conventional heat exchange elements that have rectangular channels that are long in the vertical direction, and although the sensible heat exchange efficiency is high, the humidity exchange efficiency is poor, and the total heat There was a problem that there was a limit to the improvement of exchange efficiency.
  • the present disclosure has been made to solve the above problems, and aims to provide a heat exchange element and a heat exchange ventilation device that can achieve both high total heat exchange efficiency and low pressure loss.
  • first partition plates and second partition plates are alternately stacked, and one surface of the first partition plate in the stacking direction and the other surface of the second partition plate in the stacking direction A plurality of first channels are formed between the two, and a plurality of second channels are formed between the other surface of the first partition plate in the stacking direction and one surface of the second partition plate in the stacking direction. ing.
  • the first partition plate and the second partition plate each have an opposing flow section that performs heat exchange between the fluid flowing through the plurality of first flow paths and the fluid flowing through the plurality of second flow paths
  • the counterflow section of the partition plate has a wavy shape in which a plurality of first channel ribs protruding from one side in the stacking direction are arranged in parallel
  • the counterflow section of the second partition plate has a waveform shape in which a plurality of first channel ribs protruding from one side in the stacking direction are arranged in parallel.
  • the counterflow section of the partition plate is formed of a sheet material having higher moisture permeability than the counterflow section of the first partition plate.
  • the heat exchange element according to the present disclosure has the effect of achieving both high total heat exchange efficiency and low pressure loss.
  • FIG. 1 is a perspective view showing a schematic configuration of a heat exchange element according to Embodiment 1.
  • FIG. 3 is a perspective view showing a first partition plate of the heat exchange element according to the first embodiment.
  • FIG. 3 is a perspective view showing a second partition plate of the heat exchange element according to the first embodiment.
  • FIG. 3 is a cross-sectional view showing a state in which counter-flow sections of the first partition plate and counter-flow sections of the second partition plate are alternately stacked.
  • FIG. 3 is a cross-sectional view showing a state in which counter-flow sections of the first partition plate and counter-flow sections of the second partition plate are alternately stacked.
  • FIG. 2 is a diagram showing a schematic configuration of a heat exchange ventilation device according to a second embodiment.
  • FIG. 1 is a perspective view showing a schematic configuration of a counterflow type heat exchange element 100 according to the first embodiment.
  • the heat exchange element 100 is formed into a hexagonal column shape.
  • the heat exchange element 100 is formed by alternately stacking first partition plates 1 and second partition plates 2.
  • the number of first partition plates 1 constituting heat exchange element 100 and the number of second partition plates 2 constituting heat exchange element 100 are both arbitrary.
  • the direction in which the first partition plate 1 and the second partition plate 2 are stacked is referred to as the "stacking direction.” Further, the stacking direction is sometimes referred to as the "up-down direction”. Furthermore, the upper surface of the first partition plate 1 and the second partition plate 2 is referred to as a "front surface”, and the surface opposite to the front surface is referred to as a "back surface”. Here, the front surfaces of the first partition plate 1 and the second partition plate 2 are also referred to as "one surface in the stacking direction.” Further, the back surfaces of the first partition plate 1 and the second partition plate 2 are also referred to as "the other surface in the stacking direction.”
  • FIG. 1 shows a first flow path 3 through which fluid flows in directions schematically indicated by solid arrows F1, F2, F3, F4, F5.
  • This first flow path 3 is formed between the front surface of the adjacent first partition plate 1 and the back surface of the second partition plate 2.
  • a second flow path 4 through which fluid flows in directions schematically indicated by dashed arrows G1, G2, G3, G4, and G5.
  • This second flow path 4 is formed between the back surface of the adjacent first partition plate 1 and the front surface of the second partition plate 2.
  • the fluid flowing in the first flow path 3 will be referred to as a "supply air flow”
  • the fluid flowing in the second flow path 4 will be referred to as an "exhaust flow”.
  • the direction perpendicular to the direction in which the first flow path 3 or the second flow path 4 extends and the stacking direction is referred to as the "flow path width direction.”
  • FIG. 2 is a perspective view showing the first partition plate 1 of the heat exchange element 100 according to the first embodiment.
  • FIG. 2 shows the first partition plate 1 viewed from the same direction as FIG.
  • a counterflow section 10 is formed in the center of the first partition plate 1 to perform heat exchange between the supply air flow and the exhaust air flow.
  • the counterflow section 10 mainly performs sensible heat exchange.
  • sensible heat exchange refers to exchanging "heat" between the supply air flow and the exhaust flow.
  • the counterflow section 10 has a rectangular shape when viewed along the stacking direction (when viewed from above or below).
  • a plurality of first flow passage ribs 11 are formed in parallel, extending from the upstream side to the downstream side of the air supply flow.
  • the first channel rib 11 projects upward from the front surface of the counterflow section 10 .
  • a part of the first flow path 3 is formed between two adjacent first flow path ribs 11.
  • a bottom side 12a of a triangular upstream header portion 12 is connected to an upstream end portion 10a, which is the upstream side of the four sides of the rectangular counterflow portion 10. Furthermore, a bottom side 13a of a triangular downstream header portion 13 is connected to a downstream end portion 10b, which is the downstream side of the four sides of the rectangular counterflow portion 10.
  • a plurality of first rib pieces 12b are formed on the upstream header portion 12 at intervals. These first rib pieces 12b are arranged parallel to the first oblique side 12c of the upstream header section 12. Note that the first oblique side 12c is also referred to as "one oblique side.” A part of the first flow path 3 is formed between two adjacent first rib pieces 12b. Therefore, the supply air flow passes between the two adjacent first rib pieces 12b, and the supply air flow enters the counterflow section 10 from the upstream end 10a of the counterflow section 10.
  • a plurality of first rib pieces 13b are formed on the downstream header portion 13 at intervals. These first rib pieces 13b are arranged parallel to the first oblique side 13c of the downstream header section 13. Note that the first oblique side 13c is also referred to as "one oblique side.” A part of the first flow path 3 is formed between two adjacent first rib pieces 13b. Therefore, the air supply flow emerging from the downstream end 10b of the counterflow section 10 travels between the two adjacent first rib pieces 13b.
  • FIG. 3 is a perspective view showing the second partition plate 2 of the heat exchange element 100 according to the first embodiment.
  • FIG. 3 shows the second partition plate 2 viewed from the same direction as FIG.
  • a counterflow section 20 is formed in the center of the second partition plate 2 to perform heat exchange between the supply air flow and the exhaust air flow.
  • the counterflow section 20 mainly performs humidity exchange.
  • the counterflow section 20 has a rectangular shape when viewed along the stacking direction (when viewed from above or below).
  • a plurality of second passage ribs 21 are formed in parallel on the front surface of the counterflow section 20, extending from the upstream side to the downstream side of the exhaust flow.
  • the second passage rib 21 projects upward from the front surface of the counterflow section 20 .
  • a part of the second flow path 4 is formed between two adjacent second flow path ribs 21 .
  • a bottom side 22a of a triangular upstream header section 22 is connected to an upstream end section 20a, which is the upstream side of the four sides of the rectangular counterflow section 20. Further, among the four sides of the rectangular counterflow section 20, the bottom side 23a of the triangular downstream header section 23 is connected to the downstream end section 20b, which is the downstream side.
  • a plurality of second rib pieces 22b are formed on the upstream header portion 22 at intervals. These second rib pieces 22b are arranged parallel to the second oblique side 22c of the upstream header section 22. Note that the second oblique side 22c is also referred to as "the other oblique side.” A part of the second flow path 4 is formed between two adjacent second rib pieces 22b. Therefore, the exhaust flow passes between the two adjacent second rib pieces 22b, and the exhaust flow enters the counterflow section 20 from the upstream end 20a of the counterflow section 20.
  • a plurality of second rib pieces 23b are formed on the downstream header portion 23 at intervals. These second rib pieces 23b are arranged parallel to the second oblique side 23c of the downstream header section 23. Note that the second oblique side 23c is also referred to as "the other oblique side.” A part of the second flow path 4 is formed between two adjacent second rib pieces 23b. Therefore, the exhaust flow emerging from the downstream end 20b of the counterflow section 20 travels between the two adjacent second rib pieces 23b.
  • FIG. 4 is a cross-sectional view showing a state in which counterflow sections 10 and counterflow sections 20 are alternately stacked.
  • FIG. 4 shows a cross-sectional view of the counterflow section 10 and the counterflow section 20 taken along a plane perpendicular to the extending direction of the first flow path 3 or the second flow path 4 in FIG.
  • the counterflow section 10 has a plurality of first flow path ribs 11 in an inverted U shape (convex toward the top of the page when referring to FIG. 4) in the width direction of the flow path. It is formed continuously along the
  • the first channel rib 11 is composed of a top portion 11a and a pair of side wall portions 11b and 11c. By arranging the plurality of first passage ribs 11 in parallel, the counterflow section 10 has a wave-like shape as a whole.
  • a plurality of second flow path ribs 21 having an inverted U shape are continuous along the flow path width direction. It is formed by The second flow path rib 21 includes a top portion 21a and a pair of side wall portions 21b and 21c. By arranging the plurality of second passage ribs 21 in parallel, the counterflow section 20 has a waveform shape as a whole. Note that the cross-sectional shapes of the first passage ribs 11 and the second passage ribs 21 are not limited to rectangles, and may be polygons such as trapezoids and hexagons, for example.
  • the counterflow section 10 is stacked on top of the counterflow section 20 such that the bottom of the first flowpath rib 11 covers the top 21a of the second flowpath rib 21. Further, the counterflow section 20 is stacked on top of the counterflow section 10 such that the top 11a of the first flowpath rib 11 is covered by the bottom of the second flowpath rib 21.
  • the first flow path 3 is located in a region 3a sandwiched between two adjacent first flow path ribs 11 and in a region 3b surrounded by the top 21a and side walls 21b and 21c of the second flow path rib 21. It is formed.
  • a second flow path 4 is formed in a region 4a sandwiched between two adjacent second flow path ribs 21 and a region 4b surrounded by the top 11a and side walls 11b and 11c of the first flow path rib 11. is formed.
  • the cross-sectional shapes of the first flow path 3 and the second flow path 4 are both rectangular.
  • the symbol “+” written in the first flow path 3 in FIG. 4 indicates the direction of the air supply flow that advances from the front to the back of the page.
  • the symbol “-” written in the second flow path 4 in FIG. 4 indicates the direction of the exhaust flow that advances from the back of the paper toward the front. Note that the symbol “+” and symbol “-” are the same in FIG. 5 as well.
  • the first flow path 3 and the second flow path 4 are adjacent in the stacking direction and also adjacent in the width direction of the flow path. Not only is the heat exchange between the supply air flow and the exhaust air flow performed with the flow path 4, but also between the first flow path 3 and the second flow path 4, which are adjacent in the width direction of the flow path. Heat exchange takes place.
  • a moisture-impermeable sheet material such as plastic or metal is used. Then, by bending this sheet material by a process such as press working, compression molding, or vacuum forming, a corrugated counterflow section 10 in which a plurality of first flow path ribs 11 are arranged in parallel is formed.
  • a highly moisture permeable sheet material such as a highly moisture permeable resin or paper to which a moisture permeable material is added is used. Then, by bending this sheet material by a process such as press working, compression molding, or vacuum forming, a wavy-shaped counterflow section 20 in which a plurality of second flow path ribs 21 are arranged in parallel is formed.
  • the sheet material used as the counterflow section 10 and the sheet material used as the counterflow section 20 are each a single flat plate sheet material. If a single planar sheet material is used, the counterflow section 10 and the counterflow section 20 can be formed by a simple processing method such as press processing, so that processing performance is improved.
  • the sheet material used for the counterflow section 10 has a higher elongation rate than the sheet material used for the counterflow section 20. Therefore, the counterflow section 10 is easier to shape than the counterflow section 20. Therefore, by extending the respective side wall portions 11b and 11c of the plurality of first channel ribs 11 in the stacking direction, the length A of each of the plurality of first channel ribs 11 in the stacking direction is By making each rib 21 longer than the length B in the stacking direction, the heat exchange area in the counterflow section 10 can be increased.
  • the aspect ratio of the second passage rib 21 is about 1, whereas the aspect ratio of the first passage rib 11 is 2 or more.
  • the aspect ratio is the ratio (A/C) of the length A in the stacking direction of the first channel rib 11 to the length C in the channel width direction, or the ratio of the length A in the stacking direction of the second channel rib 21. It is the ratio (B/C) of length B to length C in the channel width direction.
  • the counterflow section 10 which has a wider heat exchange area than the counterflow section 20, contributes to improving the sensible heat exchange efficiency.
  • the sensible heat exchange efficiency refers to the efficiency of exchanging "heat accompanied by temperature change" between the supply air flow and the exhaust flow.
  • the sheet material used for the counterflow section 20 is a material with higher moisture permeability than the sheet material used for the counterflow section 10. Therefore, the sheet material used for the counterflow section 20 has better humidity exchange performance than the sheet material used for the counterflow section 10. Therefore, the counterflow section 20, which is made of a material with higher moisture permeability than the counterflow section 10, contributes to improving the humidity exchange efficiency.
  • the aspect ratio of the first channel rib 11 is 2 or more, it is not limited to this aspect ratio, and the length A in the stacking direction is at least longer than the length C in the channel width direction. Thereby, the heat exchange area in the counterflow section 10 can be secured. Further, the aspect ratio of the second flow path rib 21 can also be adjusted within a processable range.
  • the heat exchange element 100 according to the present embodiment has the counterflow section 10 that contributes to improvement in sensible heat exchange efficiency and the counterflow section 20 that contributes to improvement in humidity exchange efficiency stacked, so that sensible heat exchange is possible. Both efficiency and humidity exchange efficiency can be increased. Since the total heat exchange efficiency also increases as the sensible heat exchange efficiency and humidity exchange efficiency increase, the heat exchange element 100 according to the present embodiment can achieve high total heat exchange efficiency.
  • the heat exchange element 100 according to the present embodiment can reduce the pressure loss inside the heat exchange element while increasing the total heat exchange efficiency. As described above, the heat exchange element 100 according to the present embodiment has the effect of achieving both high total heat exchange efficiency and low pressure loss.
  • FIG. 5 is a cross-sectional view showing a state in which counterflow sections 30 and counterflow sections 40 are alternately stacked. Similar to FIG. 4, FIG. 5 is a cross-sectional view of the counterflow section 30 and the counterflow section 40 cut along a plane perpendicular to the extending direction of the first flow path 3 or the second flow path 4 in FIG. It shows.
  • This modification is different from the heat exchange element 100 shown in FIG.
  • the point is that a counterflow section 40 is provided instead of the flow section 20.
  • the other configurations are the same or equivalent to those of the heat exchange element 100.
  • the sheet material used for the counterflow section 30 is a moisture-impermeable sheet material such as plastic or metal, for example.
  • the sheet material used for the counterflow section 40 is a highly moisture permeable sheet material such as a highly moisture permeable resin or paper to which a moisture permeable material is added, for example.
  • a plurality of inverted V-shaped third flow path ribs 31 are continuously formed in the counter flow section 30 along the flow path width direction.
  • the third passage rib 31 is composed of a pair of side wall parts 31a and 31b.
  • the counterflow section 30 has a waveform shape as a whole.
  • the counterflow section 40 has a planar shape without ribs. This is because the elongation rate of the sheet material used for the counterflow section 40 is low, and it is difficult to bend the sheet material to form a plurality of ribs.
  • the third flow path rib 31 has an inverted V shape
  • the first flow path 3 having a triangular cross-sectional shape is formed in the area sandwiched between two adjacent third flow path ribs 31. be done.
  • a second flow path 4 having a triangular cross-sectional shape is formed in a region of the third flow path rib 31 surrounded by a pair of side walls 31a and 31b. Sensible heat exchange and humidity exchange are performed between the supply air flow passing through the first flow path 3 and the exhaust flow passing through the second flow path 4.
  • the counterflow section 40 planar, it can be used with materials that have problems in shape forming, such as materials with low rigidity that make it difficult to maintain the formed shape, and materials whose moisture permeation performance decreases due to heating during forming. It becomes possible to do so.
  • the cross-sectional shape of the third flow path rib 31 is not limited to a triangle, and may be a polygon such as a trapezoid or a pentagon, for example.
  • the sheet material used as the counterflow section 30 be a single flat plate sheet material. If a single planar sheet material is used, the counterflow section 30 can be formed by a simple processing method such as press processing, so that processing performance is improved.
  • the heat exchange element according to the present embodiment includes the counterflow sections 10 and 30 that contribute to improving the sensible heat exchange efficiency and the counterflow sections 20 and 40 that contribute to the improvement of the humidity exchange efficiency. Laminated. Therefore, the heat exchange element according to this embodiment can increase both sensible heat exchange efficiency and humidity exchange efficiency, and can obtain high total heat exchange efficiency. Further, by increasing the length A of the first passage rib 11 and the first rib pieces 12b, 13b in the stacking direction, the pressure loss inside the heat exchange element can be reduced. Similarly, by increasing the length of the third passage rib 31 in the stacking direction, the pressure loss inside the heat exchange element can be reduced. As described above, the heat exchange element according to this embodiment has the effect of achieving both high total heat exchange efficiency and low pressure loss.
  • FIG. 6 is a diagram showing a schematic configuration of a heat exchange ventilation apparatus 200 in which the heat exchange element 100 is mounted.
  • the heat exchange ventilation device 200 includes a supply air blower 201, an exhaust air blower 202, a heat exchange element 100, and a casing 203.
  • the casing 203 is a box-shaped member that houses the supply air blower 201, the exhaust air blower 202, and the heat exchange element 100. Inside the casing 203, an air supply air passage 205 through which the air supply flow 204 passes and an exhaust air passage 207 through which the exhaust air flow 206 passes are provided.
  • the air supply flow 204 is an air supply flow from the outdoors to the room.
  • the exhaust flow 206 is an exhaust flow from indoors to outdoors.
  • An air supply outlet 208 and an exhaust suction port 209 are provided on the side surface of the casing 203 on the indoor side.
  • An air intake inlet 210 and an exhaust outlet 211 are provided on the side surface of the casing 203 on the outdoor side.
  • the air supply blower 201 is arranged within the air supply air path 205.
  • the air supply blower 201 takes in outdoor air from the air intake port 210 into the air supply air passage 205 to generate an air supply flow 204 .
  • the air supply flow 204 passes through the air supply air path 205 and is blown out from the air supply outlet 208 toward the room.
  • the supply air blower 201 generates a supply air flow 204 directed from the outdoors into the room.
  • the exhaust blower 202 is arranged within the exhaust air passage 207.
  • the exhaust blower 202 takes indoor air from the exhaust suction port 209 into the exhaust air passage 207 to generate an exhaust flow 206.
  • the exhaust flow 206 passes through the exhaust air path 207 and is blown out from the exhaust outlet 211 toward the outside.
  • the exhaust blower 202 generates an exhaust flow 206 from indoors to outdoors.
  • the heat exchange element 100 is provided at a position where the supply air passage 205 and the exhaust air passage 207 intersect.
  • the heat exchange element 100 performs total heat exchange between the supply air flow 204 passing through the supply air passage 205 and the exhaust air flow 206 passing through the exhaust air passage 207.
  • the heat exchange ventilation device 200 according to the second embodiment can obtain high total heat exchange efficiency by having the heat exchange element 100 according to the first embodiment.
  • a first partition plate and a second partition plate are alternately stacked, and a plurality of first A flow path is formed, and a plurality of second flow paths are formed between the other surface of the first partition plate in the lamination direction and the one surface of the second partition plate in the lamination direction.
  • the first partition plate and the second partition plate each have an opposing flow section that performs heat exchange between the fluid flowing through the plurality of first flow paths and the fluid flowing through the plurality of second flow paths
  • the counterflow portion of the first partition plate has a wavy shape in which a plurality of first channel ribs protruding from one surface in the stacking direction are arranged in parallel
  • the counterflow portion of the second partition plate has a wavy shape in which a plurality of second flow path ribs protruding from one surface in the stacking direction are arranged in parallel
  • the first channel rib has a longer length in the stacking direction than the second channel rib
  • the counterflow section of the second partition plate is a heat exchange element formed of a sheet material having higher moisture permeability than the counterflow section of the first partition plate.
  • the first channel rib and the second channel rib each include a top portion and both side wall portions,
  • the first flow path is formed in a region sandwiched between two adjacent first flow path ribs and a region surrounded by the top and both side wall portions of the second flow path rib, and
  • the second flow path is formed in a region sandwiched between the two second flow path ribs and a region surrounded by the top portion and the both side wall portions of the first flow path rib,
  • the heat exchange element according to supplementary note 1, wherein the first flow path and the second flow path have a rectangular cross section.
  • Each of the first channel ribs has a length in the stacking direction that is longer than a length in the channel width direction, which is a direction perpendicular to the stacking direction and the direction of movement of the fluid flowing through the first channel.
  • the heat exchange element according to appendix 1 or 2, wherein the heat exchange element is long.
  • a first partition plate and a second partition plate are alternately stacked, and a plurality of first A flow path is formed, and a plurality of second flow paths are formed between the other surface of the first partition plate in the lamination direction and the one surface of the second partition plate in the lamination direction.
  • the first partition plate and the second partition plate each have an opposing flow section that performs heat exchange between the fluid flowing through the plurality of first flow paths and the fluid flowing through the plurality of second flow paths
  • the counterflow portion of the first partition plate has a wavy shape in which a plurality of third flow path ribs protruding from one surface in the stacking direction are arranged in parallel
  • the counterflow part of the second partition plate has a planar shape
  • the counterflow section of the second partition plate is a heat exchange element formed of a sheet material having higher moisture permeability than the counterflow section of the first partition plate.
  • the third flow path rib consists of a pair of side walls, The first flow path is formed in an area sandwiched between two adjacent third flow path ribs, and the second flow path is formed in an area surrounded by the pair of side walls of the third flow path rib. is formed, The heat exchange element according to appendix 4, wherein the first flow path and the second flow path have a triangular cross section.
  • the counterflow part of the first partition plate and the counterflow part of the second partition plate have a rectangular shape when viewed along the stacking direction, The first partition plate and the second partition plate include an upstream header section provided at an upstream end of the counterflow section, and a downstream header section provided at a downstream end of the counterflow section.
  • the upstream header section and the downstream header section have a triangular shape when viewed along the stacking direction, The bottom of the upstream header portion is made to match the upstream end of the counterflow portion, and the bottom of the downstream header portion is made to match the downstream end of the counterflow portion;
  • the upstream header portion and the downstream header portion of the first partition plate each have a plurality of first rib pieces arranged parallel to one of the two oblique sides,
  • the upstream header part and the downstream header part of the second partition plate each have a plurality of second rib pieces arranged parallel to the other of the two oblique sides, according to any one of Supplementary Notes 1 to 5.
  • the heat exchange ventilation device includes, inside the casing, an air supply path that supplies outdoor air into the room, and an exhaust air path that exhausts indoor air to the outside.

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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Un élément d'échange de chaleur (100) comprend des premières plaques de séparation (1) et des secondes plaques de séparation (2) qui sont stratifiées de manière alternée. Les premières plaques de séparation (1) et les secondes plaques de séparation (2) ont respectivement des parties de contre-écoulement (10, 20) qui échangent de la chaleur entre un fluide s'écoulant à travers une pluralité de premiers trajets d'écoulement (3) et un fluide s'écoulant à travers une pluralité de seconds trajets d'écoulement (4). La partie de contre-écoulement (10) de chacune des premières plaques de séparation (1) a une forme d'onde dans laquelle une pluralité de premières nervures de trajet d'écoulement (11) faisant saillie depuis une surface dans la direction de stratification sont agencées en parallèle. La partie de contre-écoulement (20) de chacune des secondes plaques de séparation (2) a une forme d'onde dans laquelle une pluralité de secondes nervures de trajet d'écoulement (21) faisant saillie depuis une surface dans la direction de stratification sont agencées en parallèle. Les premières nervures de trajet d'écoulement (11) sont plus longues dans la direction de stratification par comparaison aux secondes nervures de trajet d'écoulement (21). La partie de contre-écoulement (20) de chacune des secondes plaques de séparation (2) est formée par un matériau en feuille ayant une perméabilité à l'humidité supérieure à celle de la partie de contre-écoulement (10) de chacune des premières plaques de séparation (1).
PCT/JP2022/033848 2022-09-09 2022-09-09 Élément d'échange de chaleur et dispositif de ventilation à échange de chaleur WO2024053082A1 (fr)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001027489A (ja) * 1999-05-10 2001-01-30 Mitsubishi Electric Corp 熱交換器及び熱交換器の製造方法
JP2003130571A (ja) * 2001-10-26 2003-05-08 Mitsubishi Electric Corp 積層型熱交換器
WO2004010055A1 (fr) * 2002-07-22 2004-01-29 Daikin Industries,Ltd. Element de deshumidification et element adsorbant destine a cet element de deshumidification
JP2015509178A (ja) * 2011-12-19 2015-03-26 ディーポイント テクノロジーズ インコーポレイテッドｄＰｏｉｎｔ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｉｎｃ． 向流式エネルギー回収換気装置（ｅｒｖ）コア
JP2019528419A (ja) * 2016-07-25 2019-10-10 ツェンダー グループ インターナショナル アーゲー 全熱交換器エレメント、そのようなエレメントを含む全熱交換器、およびその製造方法

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001027489A (ja) * 1999-05-10 2001-01-30 Mitsubishi Electric Corp 熱交換器及び熱交換器の製造方法
JP2003130571A (ja) * 2001-10-26 2003-05-08 Mitsubishi Electric Corp 積層型熱交換器
WO2004010055A1 (fr) * 2002-07-22 2004-01-29 Daikin Industries,Ltd. Element de deshumidification et element adsorbant destine a cet element de deshumidification
JP2015509178A (ja) * 2011-12-19 2015-03-26 ディーポイント テクノロジーズ インコーポレイテッドｄＰｏｉｎｔ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｉｎｃ． 向流式エネルギー回収換気装置（ｅｒｖ）コア
JP2019528419A (ja) * 2016-07-25 2019-10-10 ツェンダー グループ インターナショナル アーゲー 全熱交換器エレメント、そのようなエレメントを含む全熱交換器、およびその製造方法

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