WO2020121615A1 - Unité intérieure, et conditionneur d'air - Google Patents

Unité intérieure, et conditionneur d'air Download PDF

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Publication number
WO2020121615A1
WO2020121615A1 PCT/JP2019/035999 JP2019035999W WO2020121615A1 WO 2020121615 A1 WO2020121615 A1 WO 2020121615A1 JP 2019035999 W JP2019035999 W JP 2019035999W WO 2020121615 A1 WO2020121615 A1 WO 2020121615A1
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WO
WIPO (PCT)
Prior art keywords
fin
heat exchanger
cut
fins
indoor unit
Prior art date
Application number
PCT/JP2019/035999
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English (en)
Japanese (ja)
Inventor
祐介 安達
裕樹 宇賀神
中川　直紀
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Publication of WO2020121615A1 publication Critical patent/WO2020121615A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements

Definitions

  • the present invention relates to an indoor unit and an air conditioner in a refrigeration cycle device.
  • the present invention relates to an indoor unit or the like equipped with a heat exchanger that is arranged at an inclination.
  • a heat exchanger that performs heat exchange of air is indoors in a state of being inclined with respect to a vertical direction due to a positional relationship between an air inlet, an indoor blower, and an outlet. May be placed on board.
  • drain water due to dew condensation is generated and adheres to the fins of the heat exchanger due to the heat exchange action. If the drain water generated in the inclined heat exchanger cannot be smoothly discharged, the drain water may be dropped or scattered outside the heat exchanger and eventually discharged to the outside of the indoor unit.
  • the shorter of the minimum distance between the collar portion of the fin and the fin edge and the minimum distance between the cut and raised fin and the fin edge is 10 in the width dimension along the heat exchange air flow direction of the fin.
  • a heat exchanger set to be longer than one-half is proposed (for example, refer to Patent Document 1).
  • the fins have cut-and-raised parts for efficient heat exchange with air. Since the cut-and-raised part is formed by cutting and raising a part of the fin, a space is created in the cut-and-raised part. As the cut-and-raised part becomes larger, the amount of drain water accumulated in the space created by the cut-and-raised part increases. When the cut-and-raised part has a certain size or more, when the drain water cannot be retained in the space inside the cut-and-raised part, the drain water flows out to the downstream at once. Therefore, even if the setting according to Patent Document 1 is made, the heat exchanger may not be able to smoothly drain the drain water, and the drain water may be dropped or scattered outside the heat exchanger.
  • the fins set according to Patent Document 1 have a smaller number of cut and raised parts and a smaller area than the fins not set. If the number and area of cut and raised pieces are reduced, the temperature efficiency of the heat exchanger is lowered, and the heat exchange performance of the heat exchanger may be deteriorated. Therefore, in the heat exchanger, in order to realize smooth drainage, it is necessary to arrange the fins in a more appropriate cut-and-raised manner.
  • the present invention provides an indoor unit and an air conditioner equipped with a heat exchanger that can more smoothly discharge drain water generated and attached to the fins.
  • the indoor unit includes a heat exchanger having a heat transfer tube through which a refrigerant passes and a plurality of cut and raised portions, and a heat exchanger having a rectangular fin that contacts the heat transfer tube and promotes heat exchange with air,
  • An indoor unit including a blower that allows air to pass through the air conditioner, wherein the heat exchanger has an inclination angle with respect to the vertical direction and in which one or more rows of fins are arranged along the direction in which air passes. , The part of the fin that is surrounded by the upper short side along the air passage direction and the parallel line parallel to the upper short side that is a certain distance away from the upper short side is projected in the direction of the fin plate surface.
  • the fin projected area A is L
  • the distance between a heat transfer tube and an adjacent heat transfer tube is L
  • the fin projected area A when the distance between the upper short side and the parallel line is L
  • the fin projected area A L is
  • Wf is the length of the upper short side of the entire fins in one row or a plurality of rows
  • the total of the projected and projected areas B projected in the direction of the fin plate surface is the cut and raised in the cut and raised by the parallel lines.
  • An air conditioner according to the present invention includes the indoor unit described above and an outdoor unit that is connected to the indoor unit to form a refrigerant circuit that circulates a refrigerant.
  • an indoor unit having a heat exchanger having a high temperature efficiency that can smoothly drain drain water generated by the fins is obtained. be able to.
  • FIG. 6 is a diagram illustrating a fin 30 according to the first embodiment. It is a figure explaining the fin projected area A and the cut and raised projected area total B in the fin 30 which concerns on embodiment.
  • FIG. 3 is a diagram showing a relationship between a fin projected area A and a cut and raised projected area total B according to the first embodiment.
  • FIG. 9 is a diagram illustrating a fin 30 according to the second embodiment.
  • FIG. 1 is a diagram illustrating the configuration of the air conditioner 1 according to the first embodiment.
  • the air conditioner 1 will be described as an example of the refrigeration cycle apparatus.
  • the air conditioner 1 includes an indoor unit 2 and an outdoor unit 3.
  • the indoor unit 2 includes an indoor heat exchanger 4 and an indoor blower 5.
  • the outdoor unit 3 includes an outdoor heat exchanger 6, an outdoor blower 7, a compressor 8, a four-way switching valve 9, and an expansion valve 10.
  • the indoor heat exchanger 4 of the indoor unit 2 and the compressor 8, the four-way switching valve 9, and the expansion valve 10 of the outdoor unit 3 are connected to each other by a gas side communication pipe 11 and a liquid side communication pipe 12 to circulate a refrigerant.
  • the circuit 13 is configured.
  • the compressor 8 mounted on the outdoor unit 3 compresses the discharged refrigerant and discharges it.
  • the compressor 8 may change the capacity of the compressor 8 by arbitrarily changing the operating frequency by, for example, an inverter circuit or the like.
  • the four-way switching valve 9 is a valve that switches the flow of the refrigerant between the cooling operation and the heating operation, for example. In the case of the path of the four-way switching valve 9 shown by the solid line in FIG. 1, the air conditioner 1 performs the cooling operation. On the other hand, in the case of the path of the four-way switching valve 9 shown by the broken line in FIG. 1, the air conditioner 1 performs the heating operation.
  • the outdoor heat exchanger 6 exchanges heat between the refrigerant and the outdoor air.
  • the outdoor heat exchanger 6 functions as an evaporator during heating operation to evaporate and vaporize the refrigerant.
  • the outdoor heat exchanger 6 functions as a condenser during the cooling operation, condensing and liquefying the refrigerant.
  • the outdoor blower 7 drives a motor (not shown) to allow the air outside the air-conditioned space to pass through the outdoor heat exchanger 6 to promote heat exchange with the refrigerant.
  • the indoor heat exchanger 4 mounted on the indoor unit 2 exchanges heat between the air to be air-conditioned and the refrigerant, for example.
  • the indoor heat exchanger 4 functions as a condenser during heating operation and condenses and liquefies the refrigerant. Further, the indoor heat exchanger 4 functions as an evaporator during the cooling operation to evaporate and vaporize the refrigerant.
  • the indoor blower 5 drives a motor (not shown) to cause air to flow into the indoor unit 2, pass through the indoor heat exchanger 4, and form a flow to be blown out into the room that is the air-conditioned space.
  • the indoor unit 2 will be further described later.
  • each device of the refrigerant circuit 13 in the air conditioner 1 of the first embodiment will be described based on the flow of the refrigerant.
  • the cooling operation will be described.
  • the flow in the cooling operation is shown by a solid arrow in FIG.
  • the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 8 passes through the four-way switching valve 9 and flows into the outdoor heat exchanger 6.
  • the refrigerant that has passed through the outdoor heat exchanger 6 and condensed by exchanging heat with the outdoor air passes through the expansion valve 10.
  • the refrigerant is depressurized as it passes through the expansion valve 10.
  • the refrigerant decompressed by the expansion valve 10 and in the gas-liquid two-phase state passes through the liquid side communication pipe 12 and the indoor heat exchanger 4. Then, in the indoor heat exchanger 4, for example, the refrigerant that has been vaporized and gasified by exchanging heat with the air in the air-conditioned space passes through the gas-side communication pipe 11 and the four-way switching valve 9 and returns to the compressor 8. Inhaled. As described above, the refrigerant of the air conditioner 1 circulates to perform air conditioning related to cooling.
  • the flow in the heating operation is shown by the one-dot chain line arrow in FIG.
  • the high-temperature and high-pressure refrigerant compressed and discharged by the compressor 8 passes through the four-way switching valve 9 and the gas side communication pipe 11 and flows into the indoor heat exchanger 4. While passing through the indoor heat exchanger 4, the gas refrigerant condenses and liquefies by exchanging heat with the air in the air-conditioned space, for example.
  • the condensed and liquefied refrigerant passes through the liquid side communication pipe 12 and the expansion valve 10.
  • the refrigerant is depressurized as it passes through the expansion valve 10.
  • the refrigerant that has been decompressed by the expansion valve 10 and has become a gas-liquid two-phase state passes through the outdoor heat exchanger 6.
  • the refrigerant that has been vaporized and gasified by exchanging heat with the outdoor air passes through the four-way switching valve 9 and is sucked into the compressor 8 again.
  • the refrigerant of the air conditioner 1 circulates to perform air conditioning related to heating.
  • FIG. 2 is a diagram illustrating the configuration of the indoor unit 2 according to the first embodiment.
  • the main body of the indoor unit 2 has a front surface covered with a front panel 20 and a back surface covered with a rear panel 21.
  • the lower surface of the indoor unit 2 is covered with a lower surface panel 22, a vertical airflow direction plate 23, and an auxiliary airflow direction plate 24.
  • the top surface of the indoor unit 2 is covered with the top panel 25.
  • the top panel 25 has grid-shaped openings. The opening serves as a suction port 26 through which air flows into the indoor unit 2.
  • the above-mentioned indoor blower 5 is housed inside the indoor unit 2.
  • the indoor heat exchanger 4 is arranged around the indoor blower 5. Therefore, the indoor heat exchanger 4 is located upstream of the indoor blower 5 in the flow of air.
  • the indoor heat exchanger 4 is composed of a plurality of heat exchangers, and the front heat exchanger 4A is arranged on the front side of the indoor blower 5 so as to be bent or curved, and the rear heat exchanger arranged on the back side of the indoor blower 5. And a exchanger 4B. Both the front heat exchanger 4A and the rear heat exchanger 4B are arranged such that a part or all of them are inclined with respect to the vertical direction at a predetermined inclination angle ⁇ .
  • the indoor heat exchanger 4 will be described in detail later.
  • a drain pan 27 for receiving the dropped drain water is provided at the position of the lower end of the indoor heat exchanger 4.
  • the drain water generated from the indoor heat exchanger 4 during the cooling operation is discharged to the outside of the indoor unit 2 and the outside through the drain pan 27 and the discharge port.
  • arrow F in FIG. 2 indicates the flow of air.
  • the air sucked from the suction port 26 is heat-exchanged with the refrigerant flowing inside the indoor heat exchanger 4 when passing through the indoor heat exchanger 4.
  • the air is cooled, and in the heating operation, the air is warmed and reaches the indoor blower 5.
  • the air that has passed through the inside of the indoor blower 5 or the gap between the indoor blower 5 and the rear panel 21 is blown out forward or downward from the outlet 28.
  • a left and right wind direction plate 29 is provided near the outlet 28 to adjust the left and right wind directions.
  • a vertical wind direction plate 23 and an auxiliary wind direction plate 24 for adjusting the vertical wind direction are provided, respectively.
  • FIG. 3 is a diagram illustrating the configuration of the indoor heat exchanger 4 according to the first embodiment.
  • the indoor heat exchanger 4 of the first embodiment is a cross fin type fin-and-tube heat exchanger having fins 30 and heat transfer tubes 32.
  • the indoor heat exchanger 4 a plurality of plate-shaped fins 30 are arranged in parallel at predetermined intervals.
  • the heat transfer tube 32 vertically penetrates the through hole formed in the collar portion 31 provided on the fin 30.
  • the collar portion 31 is a contact portion between the fin 30 and the heat transfer tube 32.
  • the pipe ends of the plurality of heat transfer pipes 32 are sequentially connected by connecting pipes (not shown) to form a refrigerant flow path. Then, the refrigerant circulating in the refrigerant circuit 13 passes through the inside of the heat transfer tube 32.
  • FIG. 4 is a diagram illustrating the fin 30 according to the first embodiment.
  • the direction parallel to the air flow direction of the air flow F is the short side direction of the fin 30, and the side in the short side is the short side.
  • the direction perpendicular to the air flow direction of the air flow F is the longitudinal direction of the fin 30, and the side in the longitudinal direction is the long side.
  • inter-row slits 33 are provided at predetermined intervals along the longitudinal direction of the fins 30 in the center portion of the fins 30 in the lateral direction, and in accordance with the rows by the heat transfer tubes 32, The fins 30 are divided into a plurality of rows along the direction in which air passes.
  • the above-described collar portions 31 are provided side by side along the longitudinal direction and at predetermined intervals from each other in each of the rows partitioned by the inter-row slit 33.
  • the collar portions 31 in each row are designed so that their positions are not opposed to each other, and are arranged in a so-called zigzag pattern.
  • the heat exchanger is described as having a two-row configuration, but the heat exchanger is not limited to this and may have a configuration of three or more rows.
  • a plurality of cut-and-raised parts 34 are provided at predetermined intervals in the lateral direction of the fin 30 between the collar part 31 and the adjacent collar part 31 arranged in the same row.
  • the cut and raised portion 34 is a slit formed by cutting and raising a part of the fin 30. All the cut-and-raised parts 34 are cut-and-raised on the same surface side. Further, the cut-and-raised portion 34 is cut-and-raised so as to form a tunnel-shaped hole portion when viewed from the air circulation direction.
  • the velocity of the main flow of air in contact with the windward end portion 34a of the cut-and-raised portion 34 is increased by the so-called leading edge effect. Therefore, the temperature boundary layer becomes thin in the vertical direction with respect to the fin 30. Therefore, the main air flow and the cut-and-raised parts 34 can efficiently exchange heat.
  • the indoor heat exchanger 4 acts as an evaporator. At this time, heat exchange between the fins 30 to which the heat of the heat transfer tubes 32 is transferred and the air causes water vapor in the air to condense on the surfaces of the fins 30 to generate water droplets. The generated water droplets initially remain on the fin surface due to surface tension. When the cooling operation is continuously performed, the surrounding water droplets are combined with each other and gradually grow into large water droplets. Eventually, when the combined force of gravity and the force pushed by the wind exceeds the surface tension of the water droplet, the water droplet becomes drain water and flows downward.
  • drain water collects at the end of the fin 30 on the vertically lower side through the smooth surface of the fin 30 without the cut-and-raised parts 34 due to the influence of gravity. , Flows down.
  • the cut-and-raised parts 34 make the fins 30 uneven, but water drops are more likely to be retained in the internal space created by the unevenness. If the area of the inside of the cut-and-raised portion 34 projected toward the longitudinal direction of the fin 30 is large, the amount of water retained inside also increases. Then, in the cut-and-raised portion 34, when the amount of water that can be held is exceeded, a large amount of drain water temporarily flows through the ends of the fins 30. For this reason, the drain water may overflow from the fins 30 and drop on the indoor blower 5 or the rear panel 21 forming the air passage, and finally may be scattered from the blowout port 28 to pollute the room.
  • FIG. 5 is a diagram illustrating the fin projected area A and the cut and raised projected area total B in the fin 30 according to the embodiment.
  • the upper short side 35 which is parallel to the air flow F in the air flowing direction in the fin 30, is set as a starting point, and is separated from the upper short side 35 by a certain distance.
  • a parallel line 36 of the upper short side 35 is defined.
  • the total length of the upper short sides 35 in the plurality of rows of fins 30 is Wf.
  • the area formed when the portion surrounded by the upper short side 35 and the parallel line 36 in the region on the most leeward row is projected in the direction of the plate surface of the fin 30 is the fin projection. Let area A. In FIG.
  • the portion that is the fin projection area A is shown by hatching. Further, the total of areas formed by projecting the cut-and-raised portion 34 in the lowermost row traversed by the parallel lines 36 in the direction of the fin 30 with respect to the plate surface is defined as the cut-and-raised projected area total B. In FIG. 5, the part that is the cut-up raised total area B is shown in black.
  • the distance between a certain heat transfer tube 32 and the adjacent heat transfer tube 32 is L.
  • the fin projection area A L when the distance between the upper short side 35 and the parallel line 36 is L.
  • the maximum value Bmax of the total cut-and-raised projected area B is the product of the distance L and the minimum distance Wf/10 between the collar portion 31 of the fin 30 and the end of the fin 30 from the fin projected area A L. It becomes the subtracted area. Therefore, Bmax ⁇ A L ⁇ Wf ⁇ L/10.
  • the minimum distance between the collar portion 31 of the fin 30 and the end of the fin 30 exceeds 10% of the length of the short side of the fin 30, the amount of drain water scattered to the outside of the heat exchanger is significantly large. It is known to decrease to. Therefore, the minimum distance between the collar portion 31 of the fin 30 and the end of the fin 30 is set to Wf/10, and the area in this portion is excluded from the fin projected area A L.
  • the minimum distance between the collar portion 31 of the fin 30 and the end of the fin 30 can ensure 10% of the length Wf of the upper short side 35, which is the length of the short side of the fin 30.
  • the drain water does not drip from the fins 30 even if Bmax is not made smaller than A L /3, because the amount of drain water accumulated in the cut and raised portions is sufficiently small. Therefore, the Bmax ⁇ A L / 3.
  • FIG. 6 is a diagram showing the relationship between the fin projected area A and the cut and raised projected area total B according to the first embodiment.
  • FIG. 6 is an experimentally investigated example of the relationship in the case where the inclination angle ⁇ of the indoor heat exchanger 4 when the vertical direction is 0° is 35° ⁇ 45°.
  • the distance L 20.4 mm.
  • the length Wf 12.7 mm, and the collar diameter in the collar portion 31 is ⁇ 7.2.
  • the shaded portion in FIG. 6 is a combination of the fin projected area A and the cut and raised projected area total B in which drain water is smoothly drained without overflowing from the fin 30.
  • the temperature conversion efficiency decreases if the total projected area B of the cut and raised areas is small. Therefore, the cut-raised projected area total B is brought as close as possible to Bmax, and the number and area of the cut-raised parts 34 are formed in the fins 30 so that B becomes large. It is possible to maintain and suppress deterioration of heat exchange performance.
  • the inclination angle ⁇ of the indoor heat exchanger 4 is 35° ⁇ 45. This is especially effective when the angle is °.
  • the drain water does not drip from the fin 30 regardless of the total projected area B of the cut and raised projections.
  • the fin 30 to which the above relationship is applied may be used.
  • the indoor unit 2 becomes large, and drain water collected in the groove portion of the fin 30 on the vertically lower side is affected by gravity. 45° ⁇ is not set because the fins 30 may overflow.
  • the above-described relationship between the fin projected area A and the cut-raised projected area total B is particularly effective when the drain pan 27 does not exist below the inclined heat exchanger in the vertical direction. It can also be applied to the case where the drain water dropped from can be collected.
  • the indoor unit 2 of the first embodiment in the fins 30 of the plurality of rows of the indoor heat exchangers 4 that are arranged in an inclined manner, the upper short side 35 and the parallel line 36 in the most leeward row are formed.
  • the fin projection area A which is the area surrounded by
  • the total projected area of the cut-and-raised parts 34 that the parallel line 36 traverses in the most leeward row of the plurality of columns is defined as the cut-and-raised projected area total B.
  • the fin 30 has the cut-and-raised portion 34 that satisfies the relationship of L/10.
  • the drain water generated and attached to the fin 30 can be discharged more smoothly.
  • the total cut-and-raised projected area B to the number and area of the cut-and-raised parts 34 that approach Bmax, it is possible to suppress a decrease in the heat exchange performance of the indoor heat exchanger 4.
  • FIG. 7 is a diagram illustrating the fin 30 according to the second embodiment.
  • the fins 30 have a single row configuration. Even when the fins 30 have a single-row configuration, the above-described relationship between the fin projected area A and the cut-raised projected area total B is established. Therefore, the same effect as the indoor heat exchanger 4 in the indoor unit 2 of Embodiment 1 is exhibited.
  • the air conditioner has been described as an example of the refrigeration cycle device, but the present invention is not limited to this.
  • it can be applied to other refrigeration cycle devices such as a refrigerating device and a refrigerating device.
  • 1 air conditioner 2 indoor unit, 3 outdoor unit, 4 indoor heat exchanger, 4A front heat exchanger, 4B rear heat exchanger, 5 indoor blower, 6 outdoor heat exchanger, 7 outdoor blower, 8 compressor, 9
  • 10 expansion valve 11 gas side connecting pipe, 12 liquid side connecting pipe, 13 refrigerant circuit, 20 front panel, 21 rear panel, 22 lower panel, 23 up/down wind direction plate, 24 auxiliary wind direction plate, 25 top panel , 26 suction port, 27 drain pan, 28 outlet, 29 left and right wind direction plate, 30 fins, 31 collar part, 32 heat transfer tube, 33 row-row slit, 34 cut and raised, 34a wind side end part, 35 upper side short side, 36 parallel lines.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

L'unité intérieur de l'invention est équipée : d'un échangeur de chaleur qui possède des conduits de transfert de chaleur, et des ailettes de forme rectangulaire sur lesquelles sont agencées des parties découpées et relevées ; et d'un ventilateur. L'échangeur de chaleur qui présente un angle d'inclinaison par rapport à la direction perpendiculaire, et sur lequel est disposée une ou plusieurs ailettes suivant la direction de passage de l'air, présente une ailette qui satisfait les relations Ｂ≦Ｂｍａｘ, Ｂｍａｘ＝－Ａ／６＋（９／４）, et ＡＬ／３≦Ｂｍａｘ≦ＡＬ－Ｗｆ×Ｌ／１０ lorsque une portion entourée par un côté court supérieur suivant la direction de passage de l'air et par une droite parallèle à ce côté court supérieur et éloignée d'une distance constante de ce côté court supérieur, consiste en une surface projetée (A) des ailettes projetée dans une direction opposée à la face plate des ailettes, et la distance entre un conduit de transfert de chaleur et un conduit de transfert de chaleur adjacent est représentée par L, et lorsque la longueur du côté court supérieur de l'ensemble des ailettes d'une ou plusieurs rangées est représentée par Wf quand la surface projetée (A) des ailettes quand la distance entre le côté court supérieur et la droite parallèle est représentée par L, est représentée par la surface projetée (ＡＬ), et le total de la surface projetée (B) des parties découpées et relevées projetée dans une direction opposée à la face plate de des ailettes, est représenté par Ｂｍａｘ, dans les parties découpées et relevées que la droite parallèle croise.
PCT/JP2019/035999 2018-12-14 2019-09-13 Unité intérieure, et conditionneur d'air WO2020121615A1 (fr)

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JPPCT/JP2018/046099 2018-12-14

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CN113251493B (zh) * 2021-04-30 2022-09-02 青岛海尔空调器有限总公司 空调内机及空调器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02166392A (ja) * 1988-12-16 1990-06-27 Matsushita Refrig Co Ltd 熱交換器
JPH09105594A (ja) * 1995-01-23 1997-04-22 Lg Electronics Inc フィンチューブ型熱交換器
JPH1123179A (ja) * 1997-06-30 1999-01-26 Matsushita Electric Ind Co Ltd フィン付熱交換器
JP2002071289A (ja) * 2000-08-30 2002-03-08 Toshiba Kyaria Kk 空気調和機用熱交換器

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02166392A (ja) * 1988-12-16 1990-06-27 Matsushita Refrig Co Ltd 熱交換器
JPH09105594A (ja) * 1995-01-23 1997-04-22 Lg Electronics Inc フィンチューブ型熱交換器
JPH1123179A (ja) * 1997-06-30 1999-01-26 Matsushita Electric Ind Co Ltd フィン付熱交換器
JP2002071289A (ja) * 2000-08-30 2002-03-08 Toshiba Kyaria Kk 空気調和機用熱交換器

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