CN111630336B - Indoor heat exchanger and air conditioner - Google Patents

Indoor heat exchanger and air conditioner Download PDF

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Publication number
CN111630336B
CN111630336B CN201880087296.1A CN201880087296A CN111630336B CN 111630336 B CN111630336 B CN 111630336B CN 201880087296 A CN201880087296 A CN 201880087296A CN 111630336 B CN111630336 B CN 111630336B
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China
Prior art keywords
indoor
heat exchanger
flat tubes
indoor heat
outdoor
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CN201880087296.1A
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Chinese (zh)
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CN111630336A (en
Inventor
吉冈俊
松本祥志
藤井智步
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Daikin Industries Ltd
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Daikin Industries Ltd
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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
    • 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
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • F28D1/024—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels with an air driving element
    • 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
    • F24F1/0068—Indoor units, e.g. fan coil units characterised by the arrangement of refrigerant piping outside the heat exchanger within the unit casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0471—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a non-circular cross-section
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • 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
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D2001/0253—Particular components
    • F28D2001/026—Cores
    • F28D2001/0273—Cores having special shape, e.g. curved, annular
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Abstract

Provided are an indoor heat exchanger and an air conditioner having a plurality of flat tubes, which can suppress dew condensation water from scattering. An indoor heat exchanger (51) is used for an indoor unit (3) of an air conditioning device (1), and comprises: a plurality of indoor flat tubes (55) arranged vertically in parallel and having refrigerant flow paths (55 c); and a plurality of indoor fins (60) joined to the plurality of indoor flat tubes (55), wherein the indoor fins (60) have vertically extending communication sections (64) connected to respective sections of the indoor flat tubes (55) that are positioned in parallel vertically, and satisfy a relationship of 4.0 DP/HT 10.0 (HT is the height of the indoor flat tubes (55), DP is the pitch of the indoor flat tubes (55) that are in parallel vertically).

Description

Indoor heat exchanger and air conditioner
Technical Field
The present invention relates to an indoor heat exchanger and an air conditioner.
Background
Conventionally, as an outdoor heat exchanger provided in an outdoor unit of an air conditioner, there is an outdoor heat exchanger in which heat transfer fins are joined to a plurality of flat tubes as described in patent document 1 (japanese patent application laid-open No. 2016-.
Disclosure of Invention
Problems to be solved by the invention
When such a heat exchanger configured by joining heat transfer fins to a plurality of flat tubes is used in an indoor unit of an air conditioning apparatus, dew condensation water generated when the heat exchanger functions as an evaporator of a refrigerant is scattered into an indoor space, which is a problem.
The present invention has been made in view of the above circumstances, and an object of the present invention is to provide an indoor heat exchanger and an air conditioner having a plurality of flat tubes, which can suppress dew condensation water from scattering.
Means for solving the problems
The indoor heat exchanger according to claim 1 is an indoor heat exchanger for an indoor unit of an air conditioner. The indoor heat exchanger has a plurality of flat tubes and a plurality of heat transfer fins. The flat tube has a flow path inside for the refrigerant to pass through. The plurality of flat tubes are arranged in parallel in the vertical direction. A plurality of heat transfer fins are joined to the plurality of flat tubes. The heat transfer fin has a communicating portion. The communication part extends up and down. The communicating portion of the heat transfer fin is connected to a portion of the heat transfer fin, that is, each portion between the flat tubes arranged in parallel in the vertical direction. The indoor heat exchanger satisfies a relation of DP/HT of 4.0 ≦ DP/HT of 10.0. Here, HT is the height of the flat tube. DP is the distance between the flat tubes arranged side by side.
In this indoor heat exchanger, even when the flow rate of the air flow supplied to the indoor heat exchanger is increased, scattering of dew condensation water generated when the indoor heat exchanger is used as an evaporator of the refrigerant can be suppressed.
The indoor heat exchanger according to claim 2 is an indoor heat exchanger for an indoor unit. The indoor unit and the outdoor unit having an outdoor heat exchanger constitute an air conditioning apparatus. The outdoor heat exchanger has a plurality of flat tubes and a plurality of heat transfer fins. The indoor heat exchanger also has a plurality of flat tubes and a plurality of heat transfer fins. These flat tubes have flow paths for the refrigerant to pass through inside the tubes. The plurality of flat tubes are arranged in parallel in the vertical direction. The plurality of fins are joined to the plurality of flat tubes. The heat transfer fin has a communicating portion extending vertically. The communicating portion of the heat transfer fin is connected to a portion of the heat transfer fin, that is, each portion between the flat tubes arranged in parallel in the vertical direction. The value of DP/HT of the indoor heat exchanger is less than the value of DP/HT of the outdoor heat exchanger. Here, HT is the height of the flat tube. DP is the distance between the flat tubes arranged side by side.
In the indoor heat exchanger, frost formation can be suppressed when the outdoor heat exchanger is used as an evaporator of the refrigerant, and scattering of dew condensation water generated when the indoor heat exchanger is used as an evaporator of the refrigerant can be suppressed.
An indoor heat exchanger according to aspect 3 is the indoor heat exchanger according to aspect 1 or 2, wherein the flat tubes include: a plurality of upstream flat tubes disposed on an upstream side in an air flow direction; and a plurality of downstream side flat tubes disposed on a downstream side in the air flow direction from the upstream side flat tubes.
In this indoor heat exchanger, dew condensation water can be prevented from scattering from the downstream-side end portions of the downstream-side flat tubes in the air flow direction.
In the indoor heat exchanger according to claim 4, the communication portion is located on the leeward side of the flat tube in the air flow direction in the indoor heat exchanger according to any one of claims 1 to 3.
In this indoor heat exchanger, dew condensation water generated in the flat tubes is guided downward while being transferred to the communication portions of the heat transfer fins located on the downstream side in the air flow direction, and therefore, it is possible to suppress the dew condensation water from scattering from the downstream side end portions of the heat transfer fins in the air flow direction.
The indoor heat exchanger according to claim 5 satisfies the relationship WL/WF of 0.2 ≦ WL/WF ≦ 0.5 in the indoor heat exchanger according to any one of claims 1 to 4. Here, WF is the length of the heat transfer fin in the air flow direction. WL is the length of the communicating portion in the air flow direction.
In this indoor heat exchanger, the material cost of the heat transfer fins is suppressed, and the communication portion is sufficiently secured, whereby the scattering of dew condensation water can be suppressed.
The indoor heat exchanger according to claim 6 is the indoor heat exchanger according to any one of claims 1 to 5, wherein the heat transfer fin has a cut-and-raised portion. The longitudinal direction of the cut-and-raised part is the vertical direction.
In the indoor heat exchanger, the heat transfer fin has the cut-and-raised portion, and therefore, the heat transfer performance can be improved.
The indoor heat exchanger according to claim 7 satisfies the relationship DP/HT of 4.6 ≦ DP/HT ≦ 8.0 in the indoor heat exchanger according to any one of claims 1 to 6.
In this indoor heat exchanger, scattering of dew condensation water generated when the indoor heat exchanger is used as an evaporator of a refrigerant is more easily suppressed.
The air conditioner according to aspect 8 includes: an indoor unit having the indoor heat exchanger according to any one of aspects 1 to 7; and an outdoor unit having an outdoor heat exchanger.
In this air conditioner, it is easy to suppress the scattering of dew condensation water that occurs when the indoor heat exchanger is used as an evaporator of the refrigerant.
Drawings
Fig. 1 is a schematic configuration diagram of an air conditioner.
Fig. 2 is a schematic external perspective view of the outdoor unit.
Fig. 3 is a schematic plan view of the outdoor unit.
Fig. 4 is a schematic external perspective view of the outdoor heat exchanger.
Fig. 5 is an explanatory diagram showing a positional relationship between the outdoor fins and the outdoor flat tubes.
Fig. 6 is a schematic external perspective view of the indoor unit.
Fig. 7 is a schematic plan view of the indoor unit.
Fig. 8 is a side view schematically showing the indoor unit along a section a-a of fig. 7.
Fig. 9 is a schematic external perspective view of the indoor heat exchanger.
Fig. 10 is a partially enlarged schematic external perspective view of the indoor heat exchanger.
Fig. 11 is an explanatory diagram showing a positional relationship between the indoor fin and the indoor flat tube.
Fig. 12 is an explanatory view showing a joined state of the indoor fin and the indoor flat tube.
Fig. 13 is an explanatory diagram illustrating a positional relationship between the indoor fins and the indoor flat tubes in modification a.
Fig. 14 is an explanatory view of a portion near the downstream side of the water guide rib included in the indoor fin of modification a in the air flow direction along the section B-B in fig. 13.
Detailed Description
(1) Structure of air conditioner
Fig. 1 shows a schematic configuration diagram of an air conditioner 1.
The air conditioner 1 is a device capable of cooling or heating rooms of a building or the like by performing a vapor compression refrigeration cycle.
The air conditioner 1 mainly includes an outdoor unit 2, an indoor unit 3, a liquid refrigerant communication pipe 4 and a gas refrigerant communication pipe 5, which are refrigerant paths connecting the outdoor unit 2 and the indoor unit 3. The outdoor unit 2 and the indoor unit 3 are connected to each other via refrigerant communication pipes 4 and 5, thereby constituting a vapor compression type refrigerant circuit 6 of the air conditioner 1. The refrigerant communication pipes 4 and 5 are refrigerant pipes that are constructed on site when the air conditioner 1 is installed in an installation place such as a building. Although not particularly limited, in the present embodiment, R32 is filled as the working refrigerant in the refrigerant circuit 6.
(2) Outdoor unit
(2-1) schematic Structure of outdoor Unit
The outdoor unit 2 is installed outdoors (e.g., on the roof of a building or near the wall surface of a building), and constitutes a part of the refrigerant circuit 6. The outdoor unit 2 mainly includes a gas-liquid separator 7, a compressor 8, a four-way switching valve 10, an outdoor heat exchanger 11, an outdoor expansion valve 12 as an expansion mechanism, a liquid-side shutoff valve 13, a gas-side shutoff valve 14, an outdoor fan 15, and a casing 40.
The gas-liquid separator 7 is a container for supplying the gas refrigerant to the compressor, and is provided on the suction side of the compressor 8.
The compressor 8 sucks and compresses a low-pressure gas refrigerant, and discharges a high-pressure gas refrigerant.
The outdoor heat exchanger 11 is a heat exchanger as follows: during the cooling operation, the refrigerant discharged from the compressor 8 functions as a radiator, and during the heating operation, the refrigerant sent from the indoor heat exchanger 51 functions as an evaporator. The liquid side of the outdoor heat exchanger 11 is connected to the outdoor expansion valve 12, and the gas side is connected to the four-way switching valve 10.
The outdoor expansion valve 12 is an electric expansion valve as follows: during the cooling operation, the refrigerant from which heat has been radiated in the outdoor heat exchanger 11 is decompressed before being sent to the indoor heat exchanger 51, and during the heating operation, the refrigerant from which heat has been radiated in the indoor heat exchanger 51 is decompressed before being sent to the outdoor heat exchanger 11.
One end of the liquid refrigerant communication pipe 4 is connected to the liquid side shutoff valve 13 of the outdoor unit 2. One end of the gas refrigerant communication pipe 5 is connected to the gas-side shutoff valve 14 of the outdoor unit 2.
The respective devices and valves of the outdoor unit 2 are connected by refrigerant pipes 16 to 22.
The four-way switching valve 10 switches between a connection state of a cooling operation and a connection state of a heating operation, which will be described later, by switching between a state in which the discharge side of the compressor 8 is connected to the outdoor heat exchanger 11 side and the suction side of the compressor 8 is connected to the gas-side shutoff valve 14 side (see the solid line of the four-way switching valve 10 in fig. 1) and a state in which the discharge side of the compressor 8 is connected to the gas-side shutoff valve 14 side and the suction side of the compressor 8 is connected to the outdoor heat exchanger 11 side (see the broken line of the four-way switching valve 10 in fig. 1).
The outdoor fan 15 is disposed inside the outdoor unit 2, and generates the following air flows (indicated by arrows in fig. 3): outdoor air is sucked in, supplied to the outdoor heat exchanger 11, and then discharged to the outside of the unit. In this way, the outdoor air supplied by the outdoor fan 15 is used as a cooling source or a heating source in heat exchange with the refrigerant of the outdoor heat exchanger 11.
As shown in the schematic external perspective view of the outdoor unit 2 of fig. 2 and the schematic plan configuration view of the outdoor unit 2 of fig. 3, the casing 40 mainly includes a bottom frame 40a, a top plate 40b, a left front plate 40c, a right front plate 40d, and a right side plate 40 e. The bottom frame 40a is a horizontally long substantially rectangular plate-like member constituting a bottom surface portion of the housing 40, and is provided on an on-site installation surface by fixing legs 41 fixed to a lower surface. The top plate 40b is a horizontally long substantially rectangular plate-like member constituting a top surface portion of the housing 40. The left front plate 40c is a plate-like member mainly constituting the left front portion and the left side portion of the casing 40, and 2 air outlets for blowing air taken in from the back surface side and the left side surface side into the casing 40 by the outdoor fan 15 toward the front surface side are formed in parallel in the upper and lower directions. Each of the outlets is provided with a fan grill 42. The right front plate 40d is mainly a plate-like member constituting the front of the right front portion and the right side surface of the housing 40. The right side plate 40e is mainly a plate-like member constituting a rear part of the right side face and a right back part of the housing 40.
Further, a partition plate 43 is provided in the casing 40, and the partition plate 43 partitions a blower chamber in which the outdoor fan 15 and the like are disposed and a machine chamber in which the compressor 8 and the like are disposed.
(2-2) schematic Structure of outdoor Heat exchanger
Fig. 4 is a schematic external perspective view of the outdoor heat exchanger 11.
The outdoor heat exchanger 11 mainly includes a gas-side flow diverter 23, a liquid-side flow diverter 24, a plurality of inflow-side turn-back members 25, a plurality of inflow-side opposite-side turn-back members 26, a plurality of outdoor flat tubes 90, and a plurality of outdoor fins 91. Here, all of the components constituting the outdoor heat exchanger 11 are formed of aluminum or an aluminum alloy, and are joined to each other by welding or the like.
The plurality of outdoor flat tubes 90 are arranged in parallel in the vertical direction.
The outdoor fins 91 are arranged in parallel in the plate thickness direction along the outdoor flat tubes 90 and fixed to the outdoor flat tubes 90.
The gas-side flow divider 23 is connected to the refrigerant pipe 19 and the outdoor flat tube 90 disposed above among the plurality of outdoor flat tubes 90. When the outdoor heat exchanger 11 functions as a radiator of the refrigerant, the refrigerant flowing into the outdoor heat exchanger 11 from the refrigerant pipe 19 is branched into a plurality of height positions and sent to the outdoor flat tube 90 disposed above among the plurality of outdoor flat tubes 90.
The liquid-side flow diverter 24 is connected to the refrigerant pipe 20 and the outdoor flat tube 90 disposed below of the plurality of outdoor flat tubes 90. When the outdoor heat exchanger 11 functions as a radiator of the refrigerant, the refrigerant flowing in from the lower outdoor flat tube 90 among the plurality of outdoor flat tubes 90 is joined and flows out to the outside of the outdoor heat exchanger 11 through the refrigerant tube 20.
The plurality of inflow-side turn-back members 25 are disposed between the gas-side flow diverter 23 and the liquid-side flow diverter 24, and connect the ends of the outdoor flat tubes 90 disposed at different height positions to each other.
The opposite-inflow-side turn-back member 26 is provided at an end portion of the outdoor heat exchanger 11 opposite to an end portion of the side where the gas-side flow diverter 23, the liquid-side flow diverter 24, and the plurality of inflow-side turn-back members 25 are provided, and connects end portions of the outdoor flat tubes 90 provided at different height positions to each other.
In this way, in the outdoor heat exchanger 11, by providing the plurality of inflow-side turn-back members 25 and the inflow-side opposite-side turn-back member 26, the refrigerant can be made to flow while being turned back at both ends of the outdoor heat exchanger 11.
(2-3) outdoor Flat tube
Fig. 5 shows a positional relationship between the outdoor fin 91 and the outdoor flat tube 90 as viewed from a direction in which the flow paths 90c extend, in a state in which the outdoor flat tube 90 is cut along a cross section perpendicular to the direction in which the flow paths 90c extend inside the outdoor flat tube 90.
The outdoor flat tube 90 has an upper flat surface 90a facing vertically upward to form an upper surface, a lower flat surface 90b facing vertically downward to form a lower surface, and a plurality of small flow paths 90c through which the refrigerant flows. The outdoor flat tube 90 has a plurality of flow paths 90c arranged in parallel in the air flow direction (indicated by arrows in fig. 5, the longitudinal direction of the outdoor flat tube 90 when viewed from the cross section of the flow paths 90 c). The plurality of outdoor flat tubes 90 are all flat tubes having the same vertical height HT. Here, the height HT is a width in the height direction of the upper flat surface 90a and the lower flat surface 90b of the outdoor flat tube 90. The plurality of outdoor flat tubes 90 are arranged at a predetermined pitch (inter-layer pitch DP) in the vertical direction. Here, the inter-layer distance DP is the interval between the upper flat surfaces 90a of the outdoor flat tubes 90.
In the outdoor heat exchanger 11 of the present embodiment, the downstream end portions of the plurality of outdoor flat tubes 90 in the air flow direction are located on the downstream side of the downstream end portions of the outdoor fins 91 in the air flow direction. This suppresses damage and breakage of the leeward end of the outdoor fin 91 during manufacture or transportation of the outdoor heat exchanger 11.
(2-4) outdoor Fin
The outdoor fins 91 are plate-like members extending in the air flow direction and the vertical direction, and are arranged at predetermined intervals in the plate thickness direction and fixed to the outdoor flat tubes 90.
The outdoor fin 91 has a plurality of insertion portions 92, an outdoor communicating portion 97a, a plurality of leeward portions 97b, a corrugated portion 93, a windward fin wing 94a, a leeward fin wing 94b, an outdoor slit 95, a windward rib 96a, a leeward rib 96b, and the like. The thickness of the flat portion of the outdoor fin 91 in the plate thickness direction is, for example, 0.05mm to 0.15 mm.
The insertion portion 92 is formed by cutting in the horizontal direction from the leeward edge of the outdoor fin 91 to the front of the windward edge. The plurality of insertion portions 92 are provided side by side in the vertical direction. The insertion portion 92 constitutes a fin collar (fin collar) formed by burring or the like. The shape of the insertion portion 92 substantially matches the outer shape of the cross section of the outdoor flat tube 90, and the insertion portions 92 are welded and fixed to each other with the outdoor flat tube 90 inserted.
The outdoor communicating portion 97a is a portion of the outdoor fin 91 that is continuous in the vertical direction on the windward side of the windward side end portion of the outdoor flat tube 90. In addition, from the viewpoint of ensuring frost resistance, the distance in the air flow direction from the upstream end of the outdoor flat tube 90 to the upstream end of the outdoor communicating portion 97a of the outdoor fin 91 is preferably 4mm or more.
The plurality of leeward portions 97b project from different height positions of the outdoor communicating portion 97a toward the downstream side in the air flow direction. Each leeward portion 97b is surrounded by the adjacent insertion portions 92 in the vertical direction.
The bellows 93 is formed near the center of the outdoor fin 91 in the air flow direction, and includes a raised portion and a non-raised portion in the plate thickness direction.
The windward fin 94a and the leeward fin 94b are provided in the vicinity of the windward side end portion and the vicinity of the leeward side end portion, respectively, to restrict the interval between the outdoor fins 91.
The outdoor slits 95 are formed by cutting flat portions in the plate thickness direction in order to improve the heat transfer performance of the outdoor fins 91, and are formed on the downstream side of the bellows 93 in the air flow direction. The outdoor slits 95 are formed such that the longitudinal direction thereof is in the vertical direction (the arrangement direction of the outdoor flat tubes 90), and a plurality of (2 in the present embodiment) outdoor slits are arranged in the air flow direction. These outdoor slits 95 are cut from a flat portion to the same side in the plate thickness direction, and thereby have openings on the upstream side and the downstream side in the air flow direction, respectively.
The windward rib 96a is formed so as to extend in the air flow direction between the outdoor flat tubes 90 adjacent to each other vertically above and below the windward fin 94 a. The leeward rib 96b is provided so as to extend continuously from the leeward end of the windward rib 96a to the leeward side.
(3) Indoor unit
(3-1) schematic Structure of indoor Unit
Fig. 6 is an external perspective view of the indoor unit 3. Fig. 7 is a schematic plan view showing the indoor unit 3 with the ceiling removed. Fig. 8 is a schematic side sectional view of the indoor unit 3 taken along a section a-a shown in fig. 7.
In the present embodiment, the indoor unit 3 is an indoor unit of a type that is installed in a ceiling of an indoor space or the like as a space to be air-conditioned by being fitted into an opening of the ceiling, and constitutes a part of the refrigerant circuit 6. The indoor unit 3 mainly has an indoor heat exchanger 51, an indoor fan 52, a casing 30, a baffle 39, a bell mouth 33, and a drain pan 32.
The indoor heat exchanger 51 is a heat exchanger as follows: during the cooling operation, the refrigerant is sent from the indoor heat exchanger 51 to function as an evaporator, and during the heating operation, the refrigerant is discharged from the compressor 8 to function as a radiator. The liquid side of the indoor heat exchanger 51 is connected to the indoor side end of the liquid refrigerant communication pipe 4, and the gas side is connected to the indoor side end of the gas refrigerant communication pipe 5.
The indoor fan 52 is a centrifugal blower disposed inside the casing main body 31 of the indoor unit 3. The indoor fan 52 creates an air flow (shown by arrows in fig. 8) as follows: the indoor air is sucked into the casing 30 through the suction port 36 of the decorative panel 35, passes through the indoor heat exchanger 51, and is blown out of the casing 30 through the blow-out port 37 of the decorative panel 35. In this way, the indoor air supplied by the indoor fan 52 exchanges heat with the refrigerant in the indoor heat exchanger 51, thereby adjusting the temperature.
The housing 30 mainly has a housing main body 31 and a decorative panel 35.
The casing body 31 is disposed so as to be inserted into an opening formed in a ceiling U of an air-conditioning room, is a substantially octagonal box-like body in which long sides and short sides are alternately formed in a plan view, and has an opening on a lower surface. The case main body 31 has a top plate and a plurality of side plates extending downward from the peripheral edge of the top plate.
The decorative panel 35 is disposed so as to fit into the opening of the ceiling U, extends outward in plan view from the top plate and the side plates of the enclosure main body 31, and is attached to the lower side of the enclosure main body 31 from the indoor side. The decorative panel 35 has an inner frame 35a and an outer frame 35 b. A substantially rectangular suction port 36 that opens downward is formed inside the inner frame 35 a. Above the suction port 36, a filter 34 for removing dust from the air sucked from the suction port 36 is provided. An air outlet 37 and a corner air outlet 38 that open obliquely downward from below are formed inside the outer frame 35b and outside the inner frame 35 a. The air outlet 37 has a 1 st air outlet 37a, a 2 nd air outlet 37b, a 3 rd air outlet 37c, and a 4 th air outlet 37d at positions corresponding to the respective sides of the substantially rectangular shape in the plan view of the decorative panel 35. The corner air outlet 38 has a 1 st corner air outlet 38a, a 2 nd corner air outlet 38b, a 3 rd corner air outlet 38c, and a 4 th corner air outlet 38d at positions corresponding to four corners of a substantially rectangular shape in a plan view of the decorative panel 35.
The baffle 39 is a member that can change the direction of the airflow passing through the outlet 37. The baffle 39 has a 1 st baffle 39a disposed at the 1 st outlet 37a, a 2 nd baffle 39b disposed at the 2 nd outlet 37b, a 3 rd baffle 39c disposed at the 3 rd outlet 37c, and a 4 th baffle 39d disposed at the 4 th outlet 37 d. The shutters 39a to 39d are pivotally supported at predetermined positions of the housing 30 so as to be rotatable.
The drain pan 32 is disposed below the indoor heat exchanger 51, and receives drain water generated by condensation of moisture in the air in the indoor heat exchanger 51. The drain pan 32 is fitted to a lower portion of the housing main body 31. In a plan view, a cylindrical space extending in the vertical direction inside the indoor heat exchanger 51 is formed in the drain pan 32, and the bell mouth 33 is disposed inside and below the space. The bell mouth 33 guides the air sucked from the suction port 36 to the indoor fan 52. In addition, in a plan view, the drain pan 32 is formed with a plurality of outlet flow paths 47a to 47d and corner outlet flow paths 48a to 48c extending in the vertical direction outside the indoor heat exchanger 51. The outlet flow paths 47a to 47d include a 1 st outlet flow path 47a communicating with the 1 st outlet 37a at the lower end, a 2 nd outlet flow path 47b communicating with the 2 nd outlet 37b at the lower end, a 3 rd outlet flow path 47c communicating with the 3 rd outlet 37c at the lower end, and a 4 th outlet flow path 47d communicating with the 4 th outlet 37d at the lower end. The corner portion outlet flow paths 48a to 48c include a 1 st corner portion outlet flow path 48a communicating with the 1 st corner portion outlet 38a at the lower end, a 2 nd corner portion outlet flow path 48b communicating with the 2 nd corner portion outlet 38b at the lower end, and a 3 rd corner portion outlet flow path 48c communicating with the 3 rd corner portion outlet 38c at the lower end.
(3-2) schematic Structure of indoor Heat exchanger
Fig. 9 is a schematic external perspective view of the indoor heat exchanger 51. Fig. 10 is a partially enlarged external perspective view showing the upwind side of the plurality of indoor fins 60 of the indoor heat exchanger 51.
The indoor heat exchanger 51 is disposed inside the casing main body 31 in a state of being bent so as to surround the periphery thereof at the same height position as the indoor fan 52. The indoor heat exchanger 51 mainly includes a liquid-side header 81, a gas-side header 71, a return header 59, a plurality of indoor flat tubes 55, and a plurality of indoor fins 60. Here, all of the components constituting the indoor heat exchanger 51 are formed of aluminum or an aluminum alloy, and are joined to each other by welding or the like.
The indoor heat exchanger 51 includes an upwind heat exchange portion 70 (an inner portion in a plan view) constituting an upwind side in the air flow direction, and a downwind heat exchange portion 80 (an outer portion in a plan view) constituting a downwind side in the air flow direction.
The liquid-side header 81 constitutes one end of the leeward heat exchange portion 80 of the indoor heat exchanger 51 in a plan view, and is a cylindrical member extending in the vertical direction. The liquid-side header 81 is connected to the indoor-side end of the liquid refrigerant communication tube 4. Further, the liquid-side header 81 is connected to a plurality of indoor flat tubes 55 that constitute the leeward heat exchange portion 80 of the indoor heat exchanger 51 in a vertically aligned manner.
The gas-side header 71 constitutes one end of the upwind heat exchange portion 70 of the indoor heat exchanger 51 in a plan view, and is a cylindrical member extending in the vertical direction. The gas-side header 71 is connected to the indoor-side end of the gas refrigerant communication tube 5. Further, the plurality of indoor flat tubes 55 constituting the windward heat exchange portion 70 of the indoor heat exchanger 51 are connected to the gas-side header 71 so as to be arranged vertically.
The folded header 59 constitutes an end portion of the indoor heat exchanger 51 opposite to the liquid-side header 81 and the gas-side header 71 in plan view, and has a plurality of folded spaces arranged vertically inside. The indoor flat tubes 55 constituting the windward heat exchange portion 70 and the indoor flat tubes 55 constituting the leeward heat exchange portion 80, which are provided at the same height position with each other, are connected to the respective turn-back spaces. Thus, in the turn-back header 59, the refrigerant flowing through the indoor flat tubes 55 at different height positions can be prevented from mixing with each other, and the refrigerant flowing through the indoor flat tubes 55 at each height position can be sent while being turned back to the indoor flat tubes 55 on the upwind side (in the case where the indoor heat exchanger 51 functions as an evaporator of the refrigerant) or the downwind side (in the case where the indoor heat exchanger 51 functions as a radiator of the refrigerant) at the same height position.
The indoor flat tubes 55 are provided with a portion constituting the windward heat exchange portion 70 and a portion constituting the leeward heat exchange portion 80. That is, the plurality of indoor flat tubes 55 include a portion arranged in parallel in the vertical direction in the windward heat exchange portion 70 of the indoor heat exchanger 51 and a portion arranged in parallel in the vertical direction in the leeward heat exchange portion 80 of the indoor heat exchanger 51. Each of the plurality of indoor flat tubes 55 constituting the windward heat exchange portion 70 has one end connected to the gas-side header 71 and the other end connected to the windward side portion of the turn-back header 59. One end of each of the plurality of indoor flat tubes 55 constituting the leeward heat exchange portion 80 is connected to the liquid-side header 81, and the other end is connected to a leeward-side portion of the turn-back header 59.
The plurality of indoor fins 60 are also provided with a portion constituting the windward heat exchange portion 70 and a portion constituting the leeward heat exchange portion 80. That is, the plurality of indoor fins 60 include portions fixed to the indoor flat tubes 55 constituting the windward heat exchange portion 70 in the indoor heat exchanger 51 and portions fixed to the indoor flat tubes 55 constituting the leeward heat exchange portion 80 in the indoor heat exchanger 51. The indoor fins 60 are arranged in parallel along the indoor flat tubes 55 in the plate thickness direction of the indoor fins 60.
(3-3) indoor Flat tube
Fig. 11 shows a positional relationship between the indoor fin 60 and the indoor flat tube 55 as viewed from a direction in which the flow paths 55c extend, in a state in which the indoor flat tube 55 is cut along a cross section perpendicular to the direction in which the flow paths 55c extend.
The indoor flat tube 55 has an upper flat surface 55a facing vertically upward to form an upper surface, a lower flat surface 55b facing vertically downward to form a lower surface, and a plurality of small flow paths 55c through which a refrigerant flows. The plurality of flow paths 55c of the indoor flat tubes 55 are arranged in parallel in the air flow direction (indicated by arrows in fig. 11, the longitudinal direction of the indoor flat tubes 55 when viewed from the cross section of the flow paths 55 c). The plurality of indoor flat tubes 55 are all flat tubes having the same vertical height HT. Here, the height HT is a width in the height direction of the upper flat surface 55a and the lower flat surface 55b of the indoor flat tube 55, and is preferably 1.2mm or more and 2.5mm or less. The plurality of indoor flat tubes 55 are arranged at a predetermined pitch (inter-floor pitch DP) in the vertical direction in the windward heat exchange portion 70 and the leeward heat exchange portion 80, similarly. Here, the inter-layer distance DP is a distance between the upper flat surfaces 55a of the indoor flat tubes 55, and is preferably 8.0mm or more and 15.0mm or less. Here, the indoor heat exchanger 51 satisfies the relationship of 4.0. ltoreq. DP/HT. ltoreq.10.0. The lower limit of DP/HT of the indoor heat exchanger 51 is preferably 4.6 or more, the upper limit of DP/HT of the indoor heat exchanger 51 is preferably 8.0 or less, and the indoor heat exchanger 51 preferably satisfies the relationship of DP/HT of 4.6. ltoreq.8.0.
In the air conditioner 1 of the present embodiment, the DP/HT value of the indoor heat exchanger 51 is smaller than the DP/HT value of the outdoor heat exchanger 11.
In the present embodiment, the indoor flat tubes 55 constituting the upwind heat exchange portion 70 and the indoor flat tubes 55 constituting the downwind heat exchange portion 80 are arranged so as to overlap each other at each height position as viewed in the air flow direction.
In the indoor heat exchanger 51 of the present embodiment, the upstream end portions of the plurality of indoor flat tubes 55 in the air flow direction and the upstream end portions of the indoor fins 60 in the air flow direction are provided at substantially the same positions in the air flow direction.
(3-4) indoor Fin
The indoor fins 60 are plate-like members extending in the air flow direction and the vertical direction, are arranged at predetermined intervals in the plate thickness direction, and are fixed to the indoor flat tubes 55. In the present embodiment, the indoor fins 60 constituting the windward heat exchange portion 70 and the indoor fins 60 constituting the leeward heat exchange portion 80 are arranged so as to substantially overlap each other when viewed in the air flow direction. Further, the leeward side end portions of the indoor fins 60 constituting the windward heat exchange portion 70 and the windward side end portions of the indoor fins 60 constituting the leeward heat exchange portion 80 are arranged so that at least a part thereof is in contact with each other.
Each of the indoor fins 60 constituting the windward heat exchange portion 70 and the leeward heat exchange portion 80 similarly has a main surface 61, a plurality of fin hoop portions 65a, an indoor communicating portion 64, a plurality of windward portions 65, a main slit 62, a communicating position slit 63, and the like. The thickness of the flat main surface 61 of the indoor fin 60 in the plate thickness direction is, for example, 0.05mm to 0.15 mm. Further, it is preferable that the pitch in the plate thickness direction of the plurality of indoor fins 60 (the interval between the surfaces on the same side of the indoor fins 60 adjacent to each other) is 1.0mm or more and 1.6mm or less.
The main surface 61 constitutes a flat portion of the indoor fin 60 where the fin collar 65a, the main slit 62, and the communication position slit 63 are not provided.
The fin collar 65a is formed to extend horizontally from the upstream edge of the indoor fin 60 toward the downstream edge to the front of the downstream edge. The fin collar portions 65a are arranged side by side in the vertical direction. The fin collar 65a is formed by burring or the like. The fin collar portion 65a has a contour shape substantially matching the outer shape of the cross section of the indoor flat tube 55, and is welded and fixed to each other in a state where the fin collar portion 65a is inserted into the indoor flat tube 55. Here, fig. 12 shows a joined state of the indoor fins 60 and the indoor flat tubes 55 in a cross section of the flow paths 55c of the indoor flat tubes 55 along the refrigerant passage direction, the cross section including the vertical direction. As shown in fig. 12, the fin cuff 65a is configured to rise from the main surface 61 toward the opposite side of the cut-and-raised side of the main slit 62 in the plate thickness direction of the main surface 61. Further, a positioning portion 65x is provided on the opposite side of the fin collar portion 65a from the main surface 61 side, and the positioning portion 65x is curved so as to extend in a direction away from the upper flat surface 55a (or the lower flat surface 55b) of the corresponding indoor flat tube 55. The positioning portions 65x are in surface contact with the main surfaces 61 of the adjacent indoor fins 60, thereby defining the intervals in the plate thickness direction of the indoor fins 60. As shown in fig. 12, the fin band 65a is joined by welding with the welding member 58 interposed between the upper flat surface 55a (or the lower flat surface 55b) of the indoor flat tube 55. Further, although not particularly limited, as shown in fig. 12, it is preferable that the distance DS between the portion where the finpass 65a starts to rise with respect to the main surface 61 and the portion where the main slit 62 starts to be cut is 1mm or less on the lower flat surface 55b side of the indoor flat tube 55. Since the dew condensation water on the lower flat surface 55b of the indoor flat tube 55 is guided downward through the portion where the main slit 62 starts to be cut and discharged, by setting the distance DS to a short distance of 1mm or less, it is possible to suppress the dew condensation water from being continuously held on the lower flat surface 55b of the indoor flat tube 55.
The indoor communicating portion 64 is a portion of the indoor fin 60 that is continuous in the vertical direction on the leeward side of the leeward side end portion of the indoor flat tube 55. In addition, it is preferable that the relationship between the width WL of the indoor communication portion 64 in the air flow direction in the indoor fins 60 and the width WF of the indoor fins 60 in the air flow direction satisfy the relationship of WL/WF 0.5 or less.
The plurality of windward portions 65 project from different height positions of the indoor communication portion 64 toward the upstream side in the air flow direction. Each windward portion 65 is surrounded by the adjacent fin hoop portions 65a in the vertical direction. The length of each windward portion 65 in the vertical direction is defined by DP-HT.
The main slits 62 are formed by cutting the flat main surface 61 in the plate thickness direction in order to improve the heat transfer performance of the indoor fin 60, and are formed in the leeward portions 65 of the indoor fin 60. The main slits 62 are formed in plural (4 in the present embodiment) in parallel in the air flow direction.
The communication position slits 63 are also portions formed by cutting from the flat main surface 61 in the plate thickness direction in order to improve the heat transfer performance of the indoor fins 60, and are formed at a plurality of height positions in the indoor communication portions 64 of the indoor fins 60. The communication position slits 63 are provided correspondingly on the downstream side in the air flow direction of the main slits 62 provided at the respective height positions, respectively. The communication position slit 63 is formed to have a longitudinal direction in the vertical direction, and is formed to have an upper end higher than the upper end of the corresponding main slit 62 and a lower end lower than the lower end of the corresponding main slit 62.
These main slit 62 and the communication position slit 63 are cut from the flat main surface 61 to the same side in the plate thickness direction, and thereby have openings on the upstream side and the downstream side in the air flow direction, respectively.
(4) Operation of air conditioner
Next, the operation of the air conditioner 1 will be described with reference to fig. 1. In the air conditioning apparatus 1, a cooling operation in which the refrigerant flows in the order of the compressor 8, the outdoor heat exchanger 11, the outdoor expansion valve 12, and the indoor heat exchanger 51, and a heating operation in which the refrigerant flows in the order of the compressor 8, the indoor heat exchanger 51, the outdoor expansion valve 12, and the outdoor heat exchanger 11 are performed.
(4-1) Cooling operation
During the cooling operation, the connection state of the four-way switching valve 10 is switched to: the outdoor heat exchanger 11 serves as a radiator of the refrigerant, and the indoor heat exchanger 51 serves as an evaporator of the refrigerant (see a solid line in fig. 1). In the refrigerant circuit 6, a low-pressure gas refrigerant of the refrigeration cycle is sucked into the compressor 8, compressed to a high pressure of the refrigeration cycle, and then discharged. The high-pressure gas refrigerant discharged from the compressor 8 is sent to the outdoor heat exchanger 11 through the four-way switching valve 10. The high-pressure gas refrigerant sent to the outdoor heat exchanger 11 exchanges heat with outdoor air supplied as a cooling source by the outdoor fan 15 in the outdoor heat exchanger 11 functioning as a radiator of the refrigerant, dissipates heat, and becomes a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is depressurized to a low pressure in the refrigeration cycle when passing through the outdoor expansion valve 12, becomes a gas-liquid two-phase refrigerant, and is sent to the indoor unit 3 through the liquid-side shutoff valve 13 and the liquid refrigerant communication pipe 4.
The low-pressure gas-liquid two-phase refrigerant is evaporated in the indoor heat exchanger 51 by heat exchange with the indoor air supplied as a heat source by the indoor fan 52 during the cooling operation. Thereby, the air passing through the indoor heat exchanger 51 is cooled, and the indoor air is cooled. At this time, moisture contained in the air passing through the indoor heat exchanger 51 condenses, and dew condensation water is generated on the surface of the indoor heat exchanger 51. The low-pressure gas refrigerant evaporated in the indoor heat exchanger 51 is sent to the outdoor unit 2 through the gas refrigerant communication pipe 5.
The low-pressure gas refrigerant sent to the outdoor unit 2 is again sucked into the compressor 8 through the gas-side shutoff valve 14, the four-way switching valve 10, and the gas-liquid separator 7. In the cooling operation, as described above, the refrigerant circulates in the refrigerant circuit 6.
(4-2) heating operation
During the heating operation, the connection state of the four-way switching valve 10 is switched to: the outdoor heat exchanger 11 serves as an evaporator of the refrigerant, and the indoor heat exchanger 51 serves as a radiator of the refrigerant (see a broken line in fig. 1). In the refrigerant circuit 6, a low-pressure gas refrigerant of the refrigeration cycle is sucked into the compressor 8, compressed to a high pressure of the refrigeration cycle, and then discharged. The high-pressure gas refrigerant discharged from the compressor 8 is sent to the indoor unit 3 through the four-way switching valve 10, the gas-side shutoff valve 14, and the gas refrigerant communication pipe 5.
The high-pressure gas refrigerant exchanges heat with indoor air supplied as a cooling source by the indoor fan 52 in the indoor heat exchanger 51 to dissipate heat, and becomes a high-pressure liquid refrigerant. Thereby, the air passing through the indoor heat exchanger 51 is heated, and the indoor heat is generated. The high-pressure liquid refrigerant having radiated heat in the indoor heat exchanger 51 is sent to the outdoor unit 2 through the liquid refrigerant communication pipe 4.
The high-pressure liquid refrigerant sent to the outdoor unit 2 passes through the liquid-side shutoff valve 13, is depressurized to a low pressure in the refrigeration cycle by the outdoor expansion valve 12, and becomes a low-pressure refrigerant in a gas-liquid two-phase state. The low-pressure refrigerant in the gas-liquid two-phase state decompressed by the outdoor expansion valve 12 is evaporated by heat exchange with outdoor air supplied as a heat source by the outdoor fan 15 in the outdoor heat exchanger 11 functioning as an evaporator of the refrigerant, and becomes a low-pressure gas refrigerant. The low-pressure gas refrigerant is again sucked into the compressor 8 through the four-way switching valve 10 and the gas-liquid separator 7. In the heating operation, as described above, the refrigerant circulates through the refrigerant circuit 6.
(5) Feature(s)
(5-1)
In general, the narrower the interval between the indoor flat tubes, the higher the heat transfer rate of the indoor fins of the indoor heat exchanger can be. However, if the space between the indoor flat tubes is narrowed, the flow velocity of the air flow passing between the indoor flat tubes increases, and the dew condensation water is easily scattered. In addition, when the height of the indoor flat tubes in the vertical direction is large, the flow velocity of the air flow passing between the indoor flat tubes is also increased, and the dew condensation water is easily scattered. On the other hand, when the space between the indoor flat tubes is widened, the heat transfer rate of the indoor fins is lowered, and therefore, the evaporation temperature of the refrigerant in the indoor heat exchanger has to be lowered, and an environment in which dew condensation water is likely to occur is created.
In contrast, in the indoor heat exchanger 51 of the present embodiment and the air conditioner 1 including the indoor heat exchanger 51, the following configuration is adopted: when HT is the height of the indoor flat tubes 55 in the vertical direction and DP is the pitch of the plurality of indoor flat tubes 55 in the vertical direction, a relationship DP/HT of 4.0. ltoreq.DP/HT. ltoreq.10.0 is satisfied. As described above, it is found from the analysis data in which the respective values of DP and HT are changed, that it is preferable to set the value of DP/HT of the indoor heat exchanger 51 to be in the numerical range in terms of dew condensation water suppression.
That is, by setting the value DP/HT of the indoor heat exchanger 51 to 4.0 or more in this way, the flow velocity of the air flow flowing so as to cross the indoor fins 60 is suppressed from becoming excessively large, and even when the indoor fan 52 is used with a large air volume, dew condensation water generated by a large air flow can be suppressed from scattering from the leeward side end portion.
Furthermore, by setting the value DP/HT of the indoor heat exchanger 51 to 10.0 or less, the region of the indoor fins 60 that is distant from the indoor flat tubes 55 is kept small, and the heat transfer rate of the indoor fins 60 can be increased, so the necessity of reducing the evaporation temperature of the refrigerant of the indoor heat exchanger 51 to ensure the capacity is kept low, dew condensation water is not easily generated, and thus, when used with the air volume of the indoor fan 52 increased, dew condensation water can be kept from scattering from the indoor fins 60.
In addition, when the indoor heat exchanger 51 is configured so as to satisfy the relationship of 4.6. ltoreq. DP/HT. ltoreq.8.0, the effect of suppressing dew condensation water from scattering can be more significant.
(5-2)
In general, in an outdoor heat exchanger used in an outdoor unit of an air conditioner, frost is formed on outdoor fins when the outdoor heat exchanger is caused to function as an evaporator of refrigerant, and ventilation resistance tends to increase. When a heat exchanger having the same structure as an outdoor heat exchanger having such a structure with a wide pitch between the flat tubes is used as an indoor heat exchanger, the heat transfer rate of the indoor fins is lowered due to the wide pitch between the flat tubes, and therefore, the evaporation temperature of the refrigerant in the indoor heat exchanger has to be lowered, and dew condensation water is likely to occur.
In contrast, in the indoor heat exchanger 51 of the present embodiment and the air conditioning apparatus 1 including the indoor heat exchanger 51, when HT is the height of the flat tubes 90 and 55 in the vertical direction and DP is the pitch of the plurality of flat tubes 90 and 55 in the vertical direction, the relationship that the value of DP/HT of the indoor heat exchanger 51 is smaller than the value of DP/HT of the outdoor heat exchanger 11 is satisfied.
Therefore, in the outdoor heat exchanger 11 in which the scattering of dew condensation water does not become a problem, the frost formation in the case of being used as an evaporator is suppressed, in the indoor heat exchanger 51 in which the scattering of dew condensation water is likely to become a problem, the heat transfer rate of the indoor fins 60 is increased, and in the case of being used as an evaporator, the necessity of lowering the evaporation temperature of the refrigerant in the indoor heat exchanger 51 is suppressed, and the dew condensation water is less likely to be generated, whereby the scattering of dew condensation water can be suppressed.
(5-3)
In the indoor heat exchanger 51 of the present embodiment, the following structure is adopted: the indoor flat tubes 55 are arranged in at least 2 rows, and have an upwind heat exchange portion 70 and a downwind heat exchange portion 80.
Therefore, among the dew condensation water generated in the indoor heat exchanger 51, the dew condensation water generated in the windward heat exchange portion 70 is easily guided downward to be drained at a portion between the windward heat exchange portion 70 and the leeward heat exchange portion 80 or the leeward heat exchange portion 80. Further, since the air having increased dryness due to the dew-water generated in the windward heat exchange portion 70 when passing through the windward heat exchange portion 70 is supplied to the leeward heat exchange portion 80, the dew-water generated in the leeward heat exchange portion 80 can be suppressed to a small amount, and the dew-water can be suppressed from scattering from the leeward side end portion of the leeward heat exchange portion 80.
(5-4)
In the indoor heat exchanger 51 of the present embodiment, the indoor fins 60 are provided with indoor communicating portions 64 on the leeward side of the indoor flat tubes 55. Therefore, the dew condensation water generated in the indoor flat tubes 55 is easily transferred to the indoor communication portion 64 of the indoor fin 60 located on the downstream side in the air flow direction, and is easily guided downward to be discharged. Therefore, the dew condensation water can be suppressed from scattering from the downstream end of the indoor fin 60 in the air flow direction.
In particular, in the indoor heat exchanger 51 of the present embodiment, in the structure in which 2 or more rows of indoor flat tubes 55 are arranged, the indoor communicating portions 64 are provided on the downstream sides of the indoor fins 60 of the leeward heat exchange portion 80, and therefore, it is possible to suppress the occurrence of dew condensation water at the downstream side end portions of the indoor fins 60 and improve the drainage of the dew condensation water that occurs.
(5-5)
In the indoor heat exchanger 51 of the present embodiment, when WF is the length of the indoor fins 60 in the air flow direction and WL is the length of the indoor communication portion 64 in the air flow direction, the relationship of 0.2 ≦ WL/WF ≦ 0.5 is satisfied. By setting the WL/WF value to 0.2 or more in the indoor fins 60 in this way, the width of the indoor communication portion 64 in the air flow direction is sufficiently ensured, and the dew condensation water generated in the indoor heat exchanger 51 is easily discharged downward through the indoor communication portion 64. Further, by setting the WL/WF value to 0.5 or less in the indoor fins 60, the area that is far from the indoor flat tubes 55 and is difficult to contribute to the improvement of the heat transfer performance in the area of the indoor fins 60 is suppressed to be small, whereby the performance of the indoor fins 60 can be maintained and the material cost can be suppressed.
In particular, by positioning the indoor communication portions 64 on the downstream side of the indoor flat tubes 55 in the air flow direction in the indoor fins 60 and setting the value of WL/WF of the indoor fins 60 to 0.2 or more, the drainage of the dew condensation water generated in the indoor flat tubes 55 through the indoor communication portions 64 can be improved.
(5-6)
In the indoor heat exchanger 51 of the present embodiment, the indoor fins 60 are provided with main slits 62 and communication position slits 63 that are formed by cutting so as to open in the air flow direction. Therefore, the air supplied to the indoor heat exchanger 51 can be sufficiently brought into contact with the indoor fins 60, and the air heat source can be sufficiently utilized.
Further, since the upper ends of the main slit 62 and the communication position slit 63 are provided so as to be located in the vicinity of the lower portion of the indoor flat tubes 55 located immediately above, the dew condensation water generated in the indoor flat tubes 55 immediately above is easily caught and guided downward, and the drainage performance can be improved. In particular, as shown in fig. 12, the distance DS between the portion where the finpass part 65a starts to rise with respect to the main surface 61 of the indoor fin 60 and the portion where the main slit 62 of the indoor fin 60 starts to cut is designed to be 1mm or less on the lower flat surface 55b side of the indoor flat tube 55, whereby the stagnation of the dew condensation water on the lower flat surface 55b side of the indoor flat tube 55 can be suppressed, and the drainage performance can be improved.
(6) Modification example
(6-1) modification A
In the above embodiment, the case where the downstream-side end portion of the indoor fin 60 has a flat shape has been described as an example.
However, the shape of the downstream end portion of the indoor fin 60 is not limited to this, and for example, as described below, an indoor fin 60a having a water guide rib 99 extending along the downstream end portion in the air flow direction may be used.
Fig. 13 shows the positional relationship between the indoor fins 60a and the indoor flat tubes 55, and fig. 14 shows the vicinity of the downstream side of the water guide rib 99 in the air flow direction of the section B-B in fig. 13.
In the indoor heat exchanger 51 of modification a, as in the above-described embodiment, the upwind heat exchanger 70 and the downwind heat exchanger 80 are provided, and the water guide ribs 99 are provided on the indoor fins 60a of the upwind heat exchanger 70 and the downwind heat exchanger 80, respectively, and the water guide ribs 99 extend vertically along the downstream end portion in the air flow direction of the indoor communicating portion 64 provided on the downstream side in the air flow direction. As shown in fig. 14, the water guide ribs 99 are recessed from the surrounding main surface 61 in the plate thickness direction of the indoor fins 60 a. The water guide rib 99 is not particularly limited, but is preferably configured to have a plate thickness of the recessed indoor fin 60a or more.
By providing the water guide ribs 99 in the indoor fins 60a in this manner, dew condensation water generated in the indoor heat exchanger 51 is easily caught by the water guide ribs 99, and the dew condensation water is guided downward along the water guide ribs 99. Therefore, dew condensation water is suppressed from reaching the leeward end of the indoor fin 60a, and scattering of dew condensation water can be sufficiently suppressed.
The water guide rib 99 is preferably provided on the downstream side of the half width in the air flow direction of the indoor communicating portion 64 of the indoor fin 60a, and more preferably provided within 20% of the width in the air flow direction of the indoor communicating portion 64 from the downstream side end in the air flow direction.
In the indoor fins 60a provided with the water guide ribs 99, in particular, the relationship between the width WL in the air flow direction of the indoor communicating portion 64 in the indoor fin 60 and the width WF in the air flow direction of the indoor fin 60 preferably satisfies the relationship of 0.2 ≦ WL/WF.
(6-2) modification B
In the above embodiment, the following case is exemplified: the indoor heat exchanger 51 has an upwind heat exchange portion 70 and a downwind heat exchange portion 80, and 2 rows of indoor flat tubes 55 are arranged in parallel.
However, the number of rows of the indoor flat tubes 55 of the indoor heat exchanger 51 arranged in the air flow direction is not limited to 2, and may be a plurality of rows of 3 or more. By increasing the number of rows of the indoor flat tubes 55 in this way, the dew condensation water can be more effectively suppressed from scattering from the downstream end in the air flow direction of the indoor heat exchanger 51.
(6-3) modification C
In the above embodiment, the following case is exemplified: in the indoor heat exchanger 51, the plurality of indoor flat tubes 55 belonging to the upwind heat exchange portion 70 and the plurality of indoor flat tubes 55 belonging to the downwind heat exchange portion 80 are arranged so as to overlap each other when viewed in the air flow direction.
However, the indoor heat exchanger 51 is not limited to this, and the plurality of indoor flat tubes 55 belonging to the heat exchange portion on the windward side and the plurality of indoor flat tubes 55 belonging to the heat exchange portion on the leeward side may be arranged so as not to overlap each other when viewed in the air flow direction. This allows the air flow to sufficiently contact the indoor flat tubes 55 on the upwind side and the indoor flat tubes 55 on the downwind side.
(6-4) modification D
In the above embodiment, the following case is exemplified: the indoor fin 60 of the indoor heat exchanger 51 is provided with a main slit 62 and a communication position slit 63, which are formed by cutting the entire slit sheet so as to be positioned on one side in the plate thickness direction with respect to the main surface 61 of the indoor fin 60.
However, the cut-off formed in the indoor fin 60 is not limited to this, and instead of the main slit 62 and the communication position slit 63, the following structure called a louver may be adopted: for example, in the slit pieces cut out, the upstream end in the air flow direction of the slit pieces is located on one side in the plate thickness direction of the main surface 61 of the indoor fin 60, and the downstream end in the air flow direction of the slit pieces is located on the other side in the plate thickness direction of the main surface 61 of the indoor fin 60.
While the embodiments and modifications of the present invention have been described above, it is to be understood that various changes in the form and details may be made therein without departing from the spirit and scope of the present invention as set forth in the appended claims.
Description of the reference symbols
1 air-conditioning apparatus
2 outdoor unit (outdoor machine)
3 indoor unit (indoor machine)
11 outdoor heat exchanger
51 indoor heat exchanger
55 indoor flat tube (Flat tube)
55c flow path
60 indoor fin (Heat transfer fin)
62 Main slit (cut-and-raised part)
63 communication position gap (cut-and-raised part)
64 indoor communication part (communication part)
65 upwind part (each part between the flat tubes arranged side by side up and down)
90 outdoor flat tube (Flat tube)
90c flow path
91 outdoor fin (Heat transfer fin)
97a communication part
97b downwind part
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2016 & 041986

Claims (11)

1. An indoor heat exchanger (51), the indoor heat exchanger (51) being for an indoor unit (3) of an air conditioning device (1), wherein the indoor heat exchanger has:
a plurality of flat tubes (55) arranged vertically, the plurality of flat tubes (55) having flow paths (55c) for passing a refrigerant therein; and
a plurality of heat transfer fins (60), the plurality of heat transfer fins (60) being joined to the plurality of flat tubes,
the heat transfer fin has a communication portion (64) extending vertically, the communication portion (64) is connected to each portion (65) between the flat tubes arranged vertically, the communication portion (64) has a first cut-and-raised portion (63) having a longitudinal direction in a vertical direction,
when the height of the flat tubes is HT and the pitch between the flat tubes arranged in parallel up and down is DP, the relation DP/HT is more than or equal to 4.0 and less than or equal to 10.0 is satisfied,
when the length of the heat transfer fin of the indoor heat exchanger in the air flow direction is WF and the length of the communication portion of the indoor heat exchanger in the air flow direction is WL, a relationship of WL/WF of 0.2 to 0.5 is satisfied.
2. An indoor heat exchanger according to claim 1,
the flat tube of the indoor heat exchanger includes: a plurality of upstream flat tubes disposed on an upstream side in an air flow direction; and a plurality of downstream side flat tubes disposed on a downstream side in an air flow direction from the upstream side flat tubes.
3. The indoor heat exchanger according to claim 1 or 2, wherein,
the communication portion (64) of the indoor heat exchanger is located on a leeward side of the flat tube in an air flow direction.
4. The indoor heat exchanger according to claim 1 or 2, wherein,
the heat transfer fin of the indoor heat exchanger has a second cut-and-raised portion (62) whose longitudinal direction is the vertical direction on the main surface.
5. The indoor heat exchanger according to claim 1 or 2, wherein,
satisfies the relation of DP/HT being more than or equal to 4.6 and less than or equal to 8.0.
6. An indoor heat exchanger (51) for an indoor unit (3), the indoor unit (3) constituting an air conditioning device (1) together with an outdoor unit (2) having an outdoor heat exchanger (11),
the outdoor heat exchanger and the indoor heat exchanger each have:
a plurality of flat tubes (90, 55) arranged vertically, the plurality of flat tubes (90, 55) having flow paths (90c, 55c) for passing a refrigerant therein; and
a plurality of heat transfer fins (91, 60), the plurality of heat transfer fins (91, 60) being engaged with the plurality of flat tubes,
the heat transfer fin has communication portions (97a, 64) extending in the vertical direction, the communication portions (97a, 64) are connected to portions (97b, 65) between the flat tubes arranged in the vertical direction, the communication portions (97a, 64) have first cut-and-raised portions (63) whose longitudinal directions are in the vertical direction,
when the height of the flat tubes is HT and the distance between the flat tubes arranged in parallel is DP, the value of DP/HT of the indoor heat exchanger is smaller than that of the outdoor heat exchanger,
when the length of the heat transfer fin of the indoor heat exchanger in the air flow direction is WF and the length of the communication portion of the indoor heat exchanger in the air flow direction is WL, a relationship of WL/WF of 0.2 to 0.5 is satisfied.
7. An indoor heat exchanger according to claim 6,
the flat tube of the indoor heat exchanger includes: a plurality of upstream flat tubes disposed on an upstream side in an air flow direction; and a plurality of downstream side flat tubes disposed on a downstream side in an air flow direction from the upstream side flat tubes.
8. The indoor heat exchanger according to claim 6 or 7, wherein,
the communication portion (64) of the indoor heat exchanger is located on a leeward side of the flat tube in an air flow direction.
9. The indoor heat exchanger according to claim 6 or 7,
the heat transfer fin of the indoor heat exchanger has a second cut-and-raised portion (62) whose longitudinal direction is the vertical direction on the main surface.
10. The indoor heat exchanger according to claim 6 or 7,
satisfies the relation that DP/HT of the indoor heat exchanger is not less than 4.6 and not more than 8.0.
11. An air conditioning device (1), the air conditioning device (1) comprising:
an indoor unit (3) having the indoor heat exchanger (51) according to any one of claims 1 to 10; and
and an outdoor unit (2) having an outdoor heat exchanger (11).
CN201880087296.1A 2018-01-22 2018-12-27 Indoor heat exchanger and air conditioner Active CN111630336B (en)

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JP2018008352A JP7092987B2 (en) 2018-01-22 2018-01-22 Indoor heat exchanger and air conditioner
JP2018-008352 2018-01-22
PCT/JP2018/048147 WO2019142642A1 (en) 2018-01-22 2018-12-27 Indoor heat exchanger and air conditioning device

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JP7092987B2 (en) 2022-06-29
US20210041115A1 (en) 2021-02-11
ES2941545T3 (en) 2023-05-23
EP3745075B1 (en) 2023-03-08
EP3745075A4 (en) 2021-01-06
WO2019142642A1 (en) 2019-07-25
JP2019128060A (en) 2019-08-01
EP3745075A1 (en) 2020-12-02

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