CN113498471A - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
CN113498471A
CN113498471A CN202080017287.2A CN202080017287A CN113498471A CN 113498471 A CN113498471 A CN 113498471A CN 202080017287 A CN202080017287 A CN 202080017287A CN 113498471 A CN113498471 A CN 113498471A
Authority
CN
China
Prior art keywords
heat exchanger
raised portion
fan
indoor
refrigerant
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
CN202080017287.2A
Other languages
Chinese (zh)
Inventor
岛野太贵
渡边政利
前间庆成
高冈亮
仲田升平
冈孝多郎
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujitsu General Ltd
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Fujitsu General Ltd
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Filing date
Publication date
Application filed by Fujitsu General Ltd filed Critical Fujitsu General Ltd
Publication of CN113498471A publication Critical patent/CN113498471A/en
Pending legal-status Critical Current

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    • 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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28D1/04—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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • 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
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/04—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by preventing the formation of continuous films of condensate on heat-exchange surfaces, e.g. by promoting droplet formation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • 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
    • 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

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

Abstract

In an air conditioner (1), a heat exchanger (31) is provided with: a plurality of flat tubes (40); a fin (50) in which a plurality of cutout sections (51) into which the flat tubes (40) are inserted are arranged in a line in the direction of gravity, and which has a plurality of intermediate sections (52) formed between cutout sections (51) at vertically adjacent positions, and a communication section (53) that connects the intermediate sections (52) to each other; a first raised portion (54) at least a portion of which is located in the intermediate portion (52); and a second raised part (55) which is provided in the communication part (53) in a manner of blocking a gap (S) between the flat tube (40) and the first raised part (54). The first raised portion (54) and the second raised portion (55) are configured to allow an air flow to flow through at least one of them in the ventilation direction.

Description

Air conditioner
Technical Field
The present invention relates to an air conditioner.
Background
In the field of air conditioners, heat exchangers using flat tubes have been known. Some of these heat exchangers have a ridge portion that protrudes so as to intersect the flow direction of the air flow, between the upper and lower flat tubes (intermediate portions) of the fin, in order to increase the thermal conductivity. However, there is a phenomenon (drift) in which the flow velocity of the air flowing through the ridge portion and the flow velocity of the air flowing through the gap between the flat tube and the ridge portion are greatly different, and in this case, heat exchange cannot be performed smoothly, and a desired improvement in heat exchanger performance cannot be obtained.
In contrast, there is disclosed a technique in which, in order to suppress a drift in the surface of the fin, in addition to a first raised portion provided in the intermediate portion, a second raised portion is provided in a communication portion of the fin for connecting the intermediate portion, the second raised portion being arranged so as to overlap with a gap generated between the first raised portion and the flat tube as viewed in the ventilation direction (see, for example, patent document 1). This can suppress the occurrence of a drift, i.e., a phenomenon in which the flow velocity of the air flow flowing through the heat exchanger when passing through the gap is extremely large relative to the flow velocity of the air flow flowing around the protrusion. As a result, heat exchange between the air flow and the refrigerant in the flat tubes can be performed smoothly, and performance improvement due to the provision of the ridge portion can be obtained.
However, the technique of patent document 1 can suppress the uneven flow on the fin surface, but on the other hand, there is a problem that the structure cannot suppress the splash of the condensed water staying around the flat tubes, that is, the splash of the condensed water.
Patent document 1: japanese patent laid-open publication No. 2017-194264
Disclosure of Invention
In order to solve the above problems, an object of the present invention is to suppress the splash of condensation water that remains on the surface of a fin or flat tube.
In order to achieve the above objects, the present invention can be understood as follows.
(1) A first aspect of the present invention is an air conditioner including a ventilation path in which a heat exchanger and a fan are disposed in a casing, wherein the heat exchanger includes: a plurality of flat tubes, a fin in which a plurality of notches into which the flat tubes are inserted are arranged in a vertical direction, a first bulge, and a second bulge, and has an intermediate portion formed between the cutout portions at vertically adjacent positions and a communication portion connecting the intermediate portions to each other, the heat exchanger is configured such that the intermediate portion is located on the windward side of the communication portion in the ventilation direction of the air flowing through the ventilation path, the first raised portion is provided, at least a part of which is located in the intermediate portion, and a virtual line having a point where the condensate water stays on the upwind side fins as a starting point and a point where the static pressure is lowest in the ventilation path on the downwind side as an end point is defined as a resistance line, and when the heat exchanger is viewed from the upwind side in the direction of the resistance line, the second bump is arranged to coincide with a gap generated between the first bump and the flat tube.
(2) According to the above (1), in the ventilation path, the fan is provided on the ventilation direction downstream side of the heat exchanger, and the end point is the center of the fan.
(3) According to the above (1), in the ventilation path, the fan is provided on the upstream side in the ventilation direction of the heat exchanger, and the end point is the center of a position in the ventilation path where the flow path sectional area is smallest.
(4) And (3) according to any one of the above items (1) to (3), wherein the first raised portion is formed such that an upper end edge thereof is located within a range of 4mm or less from a lower edge of the first cutout portion on the upper side.
(5) The first raised portion and the second raised portion are formed such that the distance between the notch portion and the second raised portion is equal to or greater than the distance between the first raised portion and the second raised portion according to any one of the above items (1) to (4).
According to the present invention, it is possible to suppress the condensate of the condensate accumulated on the surface of the fin or flat tube from splashing.
Drawings
Fig. 1A is a diagram illustrating an example of an air conditioner according to an embodiment of the present invention, and is a refrigerant circuit diagram showing a refrigerant circuit of the air conditioner.
Fig. 1B is a block diagram showing a control unit.
Fig. 2A is a diagram illustrating a heat exchanger according to an embodiment of the present invention, and is a plan view showing the heat exchanger.
Fig. 2B is a front view showing the heat exchanger.
Fig. 3 is a diagram illustrating the relationship between flat tubes and fins.
Fig. 4 is a diagram illustrating the first raised portion and the second raised portion.
Fig. 5 is an enlarged view illustrating a relationship between the heat exchanger and the fan in the case of the suction type.
Fig. 6 is an enlarged view illustrating a relationship between the fan and the heat exchanger in the case of the blow-out type.
Fig. 7 is a diagram illustrating a positional relationship of the first raised part as viewed from the front.
Fig. 8A is a view illustrating a distance between the upper end edge of the first raised part and the lower edge of the first cut part, and is a front view illustrating a form of the upper end edge of the first raised part and the lower edge of the first cut part as viewed from the front.
Fig. 8B is a side view of the upper end edge of the first raised part and the lower edge of the first cut part as viewed from the side.
Fig. 9 is a diagram illustrating a distance between the second raised portion and the middle portion side end of the cutout portion, and a distance between the first raised portion and the second raised portion.
Fig. 10 is a diagram illustrating a relationship between a heat exchanger and a fan in the case of the suction type, taking an air duct type as an example.
Fig. 11 is a diagram illustrating a relationship between a heat exchanger and a fan in the case of the suction type, using a wall-mounted type as an example.
Fig. 12 is a diagram illustrating a relationship between a heat exchanger and a fan in the case of the suction type, taking a vertical type as an example.
Fig. 13 is a diagram illustrating a relationship between a heat exchanger and a fan in the case of the suction type, taking a vertical blowing pipe type as an example.
Fig. 14 is a view showing a relationship between a heat exchanger and a fan in the case of the suction type, taking a window type as an example.
Fig. 15 is a diagram illustrating a relationship between a fan and a heat exchanger in the case of the blow-out type, taking a duct type as an example.
Fig. 16 is a diagram illustrating a relationship between a fan and a heat exchanger in the case of the air-out type, using a ceiling type as an example.
Fig. 17 is a view showing a relationship between a fan and a heat exchanger in the case of the blow-out type, taking the ceiling type as an example.
Fig. 18 is a diagram showing a relationship between a fan and a heat exchanger in the case of the blow-out type, using a wall-mounted type as an example.
Fig. 19A is a table showing the size d2 of the droplet when the contact angle θ is 10 °.
Fig. 19B is a table showing the size d2 of the droplet when the contact angle θ is 60 °.
Detailed Description
Detailed description of the preferred embodiments
Embodiments of the present invention will be described in detail below with reference to the drawings. The present invention is not limited to the following embodiments, and various modifications may be made without departing from the spirit of the present invention.
Structure of refrigerant circuit
First, a refrigerant circuit of an air conditioner 1 including an outdoor unit 2 will be described with reference to fig. 1A. As shown in fig. 1A, an air conditioner 1 of the present embodiment includes: an outdoor unit 2 installed outdoors, and an indoor unit 3 installed indoors and connected to the outdoor unit 2 through a liquid pipe 4 and a gas pipe 5. More specifically, the liquid-side closing valve 25 of the outdoor unit 2 and the liquid pipe connection portion 33 of the indoor unit 3 are connected to each other through the liquid pipe 4. The gas side shutoff valve 26 of the outdoor unit 2 and the gas pipe connection 34 of the indoor unit 3 are connected by the gas pipe 5. Thereby forming the refrigerant circuit 10 of the air conditioner 1.
Refrigerant circuit of outdoor unit
First, the outdoor unit 2 will be explained. The outdoor unit 2 includes: a compressor 21, a four-way valve 22, an outdoor heat exchanger 23, an expansion valve 24, a liquid-side shutoff valve 25 to which the liquid pipe 4 is connected, a gas-side shutoff valve 26 to which the gas pipe 5 is connected, and an outdoor fan 27. The devices other than the outdoor fan 27 are connected to each other by refrigerant pipes described later to form the outdoor unit refrigerant circuit 10a, and constitute a part of the refrigerant circuit 10. An accumulator (not shown) may be provided at the refrigerant suction side of the compressor 21.
The compressor 21 is a variable displacement compressor, and the operating capacity can be changed by controlling the rotation speed thereof by an inverter, not shown. The refrigerant discharge side of the compressor 21 is connected to a port a of the four-way valve 22 via a discharge pipe 61. The refrigerant suction side of the compressor 21 and the port c of the four-way valve 22 are connected by a suction pipe 66.
The four-way valve 22 is a valve for switching the flow direction of the refrigerant, and includes four ports a, b, c, and d. As described above, the port a is connected to the refrigerant discharge side of the compressor 21 via the discharge pipe 61. The port b is connected to one refrigerant inlet and outlet of the outdoor heat exchanger 23 by a refrigerant pipe 62. As described above, the port c is connected to the refrigerant suction side of the compressor 21 via the suction pipe 66. The port d and the gas side shutoff valve 26 are connected by an outdoor unit gas pipe 64. The four-way valve 22 is a flow path switching means of the present invention.
The outdoor heat exchanger 23 is for exchanging heat between the refrigerant and outside air sucked into the outdoor unit 2 by rotation of an outdoor fan 27, which will be described later. As described above, one refrigerant inlet and outlet of the outdoor heat exchanger 23 is connected to the port b of the four-way valve 22 via the refrigerant pipe 62, and the other refrigerant inlet and outlet is connected to the liquid-side closing valve 25 via the outdoor-unit liquid pipe 63. The outdoor heat exchanger 23 functions as a condenser during the cooling operation and as an evaporator during the heating operation by switching the four-way valve 22, which will be described later.
The expansion valve 24 is an electronic expansion valve driven by a pulse motor, not shown. Specifically, the opening degree thereof is adjusted according to the number of pulses supplied to the pulse motor. The opening degree of the expansion valve 24 is adjusted so that the discharge temperature, which is the temperature of the refrigerant discharged from the compressor 21, becomes a predetermined target temperature during the heating operation.
The outdoor fan 27 is formed of a resin material and is disposed in the vicinity of the outdoor heat exchanger 23. The center of the outdoor fan 27 is connected to a rotating shaft of a fan motor, not shown. The outdoor fan 27 is rotated by the rotation of the fan motor. By the rotation of the outdoor fan 27, outside air is sucked into the outdoor unit 2 from an unillustrated air inlet of the outdoor unit 2, and the outside air having exchanged heat with the refrigerant in the outdoor heat exchanger 23 is discharged to the outside of the outdoor unit 2 from an unillustrated air outlet of the outdoor unit 2.
In addition to the above-described configuration, the outdoor unit 2 is provided with various sensors. As shown in fig. 1A, the discharge pipe 61 is provided with: a discharge pressure sensor 71 that detects the pressure of the refrigerant discharged from the compressor 21; and a discharge temperature sensor 73 that detects the temperature of the refrigerant discharged from the compressor 21 (the discharge temperature described above). The suction pipe 66 is provided with: a suction pressure sensor 72 that detects the pressure of the refrigerant sucked by the compressor 21; and a suction temperature sensor 74 that detects the temperature of the refrigerant sucked by the compressor 21.
A heat exchange temperature sensor 75 is provided in a substantially middle portion of the refrigerant passage, not shown, of the outdoor heat exchanger 23, and detects the temperature of the outdoor heat exchanger 23, that is, the outdoor heat exchange temperature. An outdoor air temperature sensor 76 is provided near an unillustrated air inlet of the outdoor unit 2, and detects an outdoor air temperature, which is a temperature of the outdoor air flowing into the outdoor unit 2.
The outdoor unit 2 includes an outdoor unit control unit 200. The outdoor unit control unit 200 is mounted on a control circuit board, and the control circuit is housed in an unillustrated electronic control box of the outdoor unit 2. As shown in fig. 1B, the outdoor unit control unit 200 includes a CPU210, a storage unit 220, a communication unit 230, and a sensor input unit 240.
The storage unit 220 is composed of a flash memory, and stores a control program of the outdoor unit 2, detection values corresponding to detection signals from various sensors, control states of the compressor 21, the outdoor fan 27, and the like. In the storage unit 220, a rotation speed table (not shown) in which the rotation speed of the compressor 21 is defined in accordance with the required capacity received from the indoor unit 3 is stored in advance.
The communication unit 230 is an interface for communicating with the indoor unit 3. The sensor input unit 240 acquires detection results of various sensors of the outdoor unit 2 and outputs the detection results to the CPU 210.
The CPU210 acquires the detection results of the sensors of the outdoor unit 2 through the sensor input unit 240. Further, the CPU210 acquires the control signal transmitted from the indoor unit 3 through the communication unit 230. The CPU210 controls the driving of the compressor 21 or the outdoor fan 27 based on the acquired detection result, control signal, or the like. Further, the CPU210 performs switching control of the four-way valve 22 based on the acquired detection result or control signal. Further, the CPU210 adjusts the opening degree of the expansion valve 24 based on the acquired detection result or control signal.
Refrigerant circuit of indoor unit
Next, the indoor unit 3 will be described with reference to fig. 1A. The indoor unit 3 includes: an indoor heat exchanger 31, an indoor fan 32, a liquid pipe connection 33 to which the other end of the liquid pipe 4 is connected, and a gas pipe connection 34 to which the other end of the gas pipe 5 is connected. The devices other than the indoor fan 32 are connected to each other by refrigerant pipes described in detail below, thereby forming the indoor unit refrigerant circuit 10b and constituting a part of the refrigerant circuit 10.
The indoor heat exchanger 31 is for exchanging heat between the refrigerant and indoor air drawn into the indoor unit 3 from an air inlet, not shown, of the indoor unit 3 by rotation of an indoor fan 32, which will be described later. One refrigerant inlet and outlet of the indoor heat exchanger 31 is connected to the liquid pipe connection portion 33 via an indoor unit liquid pipe 67. The other refrigerant inlet and outlet of the indoor heat exchanger 31 is connected to the gas pipe connection 34 via an indoor unit gas pipe 68. The indoor heat exchanger 31 functions as an evaporator when the indoor unit 3 performs a cooling operation and as a condenser when the indoor unit 3 performs a heating operation.
The indoor fan 32 is formed of a resin material and is disposed in the vicinity of the indoor heat exchanger 31. The indoor fan 32 is rotated by a fan motor, not shown, to suck indoor air into the indoor unit 3 from an air inlet, not shown, of the indoor unit 3 and to blow out the indoor air, which has exchanged heat with the refrigerant in the indoor heat exchanger 31, into the room from an air outlet, not shown, of the indoor unit 3.
In addition to the above-described configuration, the indoor unit 3 is provided with various sensors. The indoor-unit liquid pipe 67 is provided with a liquid-side temperature sensor 77 that detects the temperature of the refrigerant flowing into the indoor heat exchanger 31 or flowing out from the indoor heat exchanger 31. The indoor unit gas pipe 68 is provided with a gas side temperature sensor 78 that detects the temperature of the refrigerant flowing out of the indoor heat exchanger 31 or flowing into the indoor heat exchanger 31. An indoor temperature sensor 79 is provided near an air inlet, not shown, of the indoor unit 3, and detects the temperature of the indoor air flowing into the indoor unit 3, that is, the indoor temperature.
The indoor unit 3 further includes an indoor unit control unit 300. As shown in fig. 1B, the indoor unit control unit 300 (in this specification, the indoor unit control unit 300 may be simply referred to as a control unit) includes a CPU310, a storage unit 320, a communication unit 330, and a sensor input unit 340.
The storage unit 320 is configured by a flash memory, and stores a control program of the indoor unit 3, detection values corresponding to detection signals from various sensors, control states of the indoor fan 32 and the like, and the like. Although not shown, the storage unit 320 stores in advance a tachometer or the like that defines the number of rotations of the indoor fan 32, including the number of rotations for monitoring the cooling/braking leakage during the operation stop period, which will be described later.
The communication unit 330 is an interface for communicating with the outdoor unit 2. The sensor input unit 340 acquires detection results of various sensors of the indoor unit 3 and outputs the detection results to the CPU 310.
The CPU310 acquires the detection results of the sensors of the indoor unit 3 through the sensor input unit 340. Further, the CPU310 acquires the control signal transmitted from the outdoor unit 2 through the communication unit 330. The CPU310 performs drive control of the indoor fan 32, including drive for monitoring refrigerant leakage during operation stop, which will be described later, based on the acquired detection result or control signal. The CPU310 calculates a temperature difference between a set temperature set by a user operating a remote controller, not shown, and the indoor temperature detected by the indoor temperature sensor 79, and transmits a required capacity based on the calculated temperature difference to the outdoor unit control unit 200 of the outdoor unit 2 through the communication unit 330.
Operation of refrigerant circuit
Next, the flow of the refrigerant in the refrigerant circuit 10 and the operation of each component during air conditioning operation of the air conditioner 1 according to the present embodiment will be described with reference to fig. 1A. Hereinafter, a case where the indoor unit 3 performs the heating operation based on the flow of the refrigerant shown by the solid line in the drawing will be described. In addition, the flow of the refrigerant shown by the dotted line indicates the cooling operation.
When the indoor unit 3 performs a heating operation, the CPU210 switches the four-way valve 22 to a state indicated by a solid line, that is, the port a and the port d of the four-way valve 22 communicate with each other and the port b and the port c communicate with each other, as shown in fig. 1A. As a result, the refrigerant circulates in the direction indicated by the solid arrows in the refrigerant circuit 10, thereby forming a heating cycle in which the outdoor heat exchanger 23 functions as an evaporator and the indoor heat exchanger 31 functions as a condenser.
The high-pressure refrigerant discharged from the compressor 21 flows through the discharge pipe 61 and into the four-way valve 22. The refrigerant flowing into the port a of the four-way valve 22 flows from the port d of the four-way valve 22 through the outdoor unit gas pipe 64, and flows into the gas pipe 5 through the gas side closing valve 26. The refrigerant flowing through the gas pipe 5 flows into the indoor unit 3 via the gas pipe connection 34.
After flowing into the indoor unit 3, the refrigerant flows through the indoor unit gas pipe 68, flows into the indoor heat exchanger 31, exchanges heat with indoor air sucked into the indoor unit 3 by the rotation of the indoor fan 32, and is condensed. As described above, the indoor heat exchanger 31 functions as a condenser, and the indoor air having exchanged heat with the refrigerant in the indoor heat exchanger 31 is blown out from the outlet port, not shown, into the room, thereby heating the room in which the indoor unit 3 is installed.
The refrigerant flowing out of the indoor heat exchanger 31 flows through the indoor unit liquid pipe 67, and flows into the liquid pipe 4 via the liquid pipe connection part 33. The refrigerant flowing through the liquid pipe 4 and flowing into the outdoor unit 2 via the liquid side closing valve 25 flows through the outdoor unit liquid pipe 63 and is decompressed while flowing through the expansion valve 24. As described above, the opening degree of the expansion valve 24 during the heating operation is adjusted so that the discharge temperature of the compressor 21 becomes a predetermined target temperature.
The refrigerant flowing through the expansion valve 24 and flowing into the outdoor heat exchanger 23 exchanges heat with the outside air sucked into the outdoor unit 2 by the rotation of the outdoor fan 27 and evaporates. The refrigerant flowing out of the outdoor heat exchanger 23 to the refrigerant pipe 62 flows through the ports b and c of the four-way valve 22 and the suction pipe 66, is sucked into the compressor 21, and is compressed again.
Heat exchanger
The heat exchanger of the present embodiment can be applied to the indoor heat exchanger 31 of the indoor unit 3 and the outdoor heat exchanger 23 of the outdoor unit 2, and in the following description, the heat exchanger is applied to the indoor heat exchanger (hereinafter, simply referred to as a heat exchanger) 31 of the indoor unit 3 that functions as a condenser during heating operation.
Fig. 2A and 2B are explanatory views of the heat exchanger 31 according to the present embodiment, fig. 2A is a plan view of the heat exchanger 31, and fig. 2B is a front view of the heat exchanger 31. As shown in fig. 2A and 2B, the heat exchanger 31 includes: a plurality of flat tubes 40 that are heat transfer tubes having an oblong or rounded rectangular cross-sectional shape, the flat tubes 40 being arranged in the vertical direction (direction perpendicular to the flow direction of the refrigerant) so that side surfaces (large-width surfaces) thereof face each other; a pair of left and right headers 12 connected to both ends of the flat tubes 40; and a plurality of fins 50 arranged in a direction crossing the flat tubes 40 and engaged therewith. In the following description, among the flat tubes 40 adjacent to each other in the vertical direction, the flat tube 40 positioned in the upper side in the drawing may be referred to as a first flat tube 40a, and the flat tube 40 positioned in the lower side in the drawing may be referred to as a second flat tube 40 b. In addition to these, the heat exchanger 31 is provided with a refrigerant pipe (not shown) through which the refrigerant flows, and the header 12 connects the heat exchanger 31 and other elements of the air conditioner 1.
More specifically, the flat tubes 40 are provided along a direction in which the refrigerant flows between the pair of headers 12 (also referred to as a longitudinal direction), and have a flat shape in a direction in which air flows (also referred to as a short-side direction). A plurality of refrigerant flow paths through which the refrigerant flows in the longitudinal direction are formed inside the refrigerant container. The flat tubes 40 are arranged side by side in the vertical direction with a gap S1 therebetween through which air flows, and both ends thereof are connected to the pair of headers 12. Specifically, the flat tubes 40 extending in the longitudinal direction are arranged in the vertical direction at a predetermined arrangement pitch Ph (the vertical distance of the gap S1), and both ends thereof are connected to the header 12.
The header 12 has a cylindrical shape, and has a refrigerant flow path (not shown) formed therein for branching the refrigerant supplied to the heat exchanger 31, flowing into the flat tubes 40, and converging the refrigerant flowing out of the flat tubes 40.
The fins 50 have a flat plate shape, and are stacked in a direction intersecting the flat tubes 40 when viewed from the front, and are arranged side by side with a gap S1 therebetween through which air flows. Specifically, the plurality of fins 50 extending in the vertical direction are arranged in the longitudinal direction of the flat tubes 40 with a predetermined fin pitch Pv (the longitudinal distance of the gap S1) therebetween. In the following description, of the plurality of fins 50, the fin 50 adjacent to each other on the left side in the drawing may be referred to as a first fin 50a, and the fin 50 on the right side in the drawing may be referred to as a second fin 50 b.
Flat tube, fin, bump, and fan
Next, the relationship among the flat tubes 40, the fins 50, the first raised portions 54 and the second raised portions 55, and the indoor fan (hereinafter simply referred to as a fan) 32 will be described with reference to fig. 3 and the following drawings. First, as shown in fig. 3, a plurality of notches 51 into which a plurality of flat tubes 40 are inserted are arranged in a vertical direction in a fin 50. The fin 50 has an intermediate portion 52 (windward side) and a communication portion 53 (leeward side), the intermediate portion 52 being formed between the cutout portions 51 (first cutout portion 51a and second cutout portion 51b) adjacent to each other in the upper and lower direction, the communication portion 53 connecting the plurality of intermediate portions 52 to each other. In the following description, of the plurality of cutouts 51, the upper cutout portion in the drawing is referred to as a first cutout portion 51a, and the lower cutout portion 51 is referred to as a second cutout portion 51b, of the two cutouts 51 adjacent to each other with the intermediate portion 52 interposed therebetween. The first notch portion 51a is inserted by the first flat tube 40a, and the second notch portion 51b is inserted by the second flat tube 40 b. The flat tube 40 is provided therein with a plurality of refrigerant passages 41 through which the refrigerant flows.
As shown in fig. 4, the intermediate portion 52 of the fin 50 is provided with a first raised portion 54 between the first notch portion 51a and the second notch portion 51 b. The first bump 54 has an upper end edge X1-X2 and a lower end edge Z1-Z2 disposed from the intermediate portion 52 to the communication portion 53. In more detail, the first bump 54 is provided such that at least a part thereof is located at the intermediate portion 52, and the communication-portion side edge X2-Z2 thereof is located at the communication portion 53. The first raised portion 54 promotes drainage of condensed water adhering to the surface of the flat tube 40 or the fin 50.
Since the first raised portion 54 is provided so that at least a part thereof is located in the intermediate portion 52, with respect to the upper end edge X1-X2 of the first raised portion 54, the condensed water adhering around the first flat tube 40a (not shown in fig. 4, see fig. 3) inserted into the first notched portion 51a above the first raised portion 54 flows along the leeward end portion (right end portion in the drawing) of the first notched portion 51a (first flat tube 40a) to the upper end edge X1-X2 of the first raised portion 54.
Then, the condensed water flows down along the middle portion side edges X1 to Z1 connecting the first upper end portion X1 and the first lower end portion Z1, and the communication portion side edges X2 to Z2 connecting the second upper end portion X2 and the second lower end portion Z2. The condensed water reaching the lower end edge Z1-Z2 flows to the second flat tube 40b or the communication portion 53, and is sequentially discharged.
The second raised portion 55 is provided on the leeward side (right side in the figure) of the communication portion side edge X2-Z2 of the first raised portion 54. The second raised portions 55 are provided in the communication portion 53 so as to overlap the notch portion 51 or the gap S between the flat tube 40 and the first raised portion 54 as viewed in the ventilation direction. This increases the flow path resistance when the air flow passes through the gap S, and reduces the flow velocity. When the flow velocity is reduced, resistance acting in the ventilation direction of the condensed water (force in the ventilation direction received from the air flow) is reduced, and thus it is possible to suppress splashing of condensed water droplets adhering to the surfaces of the flat tubes 40 or the fins 50 from the gaps S to the leeward side, that is, splashing of the condensed water. Fig. 4 shows an example in which the gap Sa between the first notch 51a and the first flat tube 40a and the first ridge 54 and the gap Sb between the second notch 51b and the second flat tube 40b and the first ridge 54 are both blocked by one second ridge 55, but the gap Sa and the gap Sb may be blocked by dividing the second ridge 55.
In the above description, the case where the ventilation direction is the longitudinal direction along the cross section of the flat tube 40 (the direction from the left to the right in fig. 3) has been described, but the ventilation direction changes depending on the positional relationship between the heat exchanger 31 and the indoor fan 32, etc., that is, depending on the type of the indoor unit 3. In the present embodiment, the ventilation direction is set as follows according to the type of the indoor unit 3. That is, a virtual line AF, which is a point where the condensed water stays in the windward fins 50 of the ventilation path 35 as a starting point AU and a point where the air static pressure is lowest in the leeward ventilation path of the ventilation path 35 as an end point AD, is set as a resistance line. Specifically, as shown in fig. 5, when the air flow is generated by the "suction type" in which the heat exchanger 31 is located on the windward side and the indoor fan 32 is located on the leeward side in the ventilation path 35, the ventilation direction can be set by a virtual line AF having a position where the condensate water stays on the windward side as a starting point AU and a portion where the static pressure is lowest on the leeward side (the center of the indoor fan 32) as an end point AD. That is, the air having passed through the heat exchanger 31 flows toward the portion where the static pressure is lowest. Therefore, the direction of the resistance received by the condensate staying at the starting point AU is the direction of the virtual line AF.
As shown in fig. 6, when the indoor fan 32 is positioned on the windward side and the heat exchanger 31 is positioned on the leeward side in the ventilation path 35, that is, when the air flow is generated by the "blow-out type", the ventilation direction can be set by a virtual line AF having a position where the condensate water stays on the windward side as a starting point AU and a position where the static pressure is lowest on the leeward side (the center of the position where the cross-sectional area is smallest in the ventilation path 35 on the leeward side of the heat exchanger 31) as an end point AD.
In either case, the starting point AU, which is the position where the condensed water is retained, is set to the communication portion side end of the flat tube 40 or the second lower end portion Z2 of the first raised portion 54. The virtual line AF passes through at least one of the first raised portion 54 and the second raised portion 55 in accordance with the positional relationship such as the inclination of the heat exchanger 31.
The setting of the virtual line AF, which differs depending on the type of the indoor unit 3 (duct type, wall type, vertical duct type, window type, ceiling type, etc.), will be described later.
Here, in order to smoothly discharge the condensed water staying around the first flat tube 40a, as shown in fig. 7, it is preferable that the first raised part 54 is formed such that a distance d1 between the first upper end X1 of the first raised part 54 and the lower edge of the first notch part 51a (corresponding to the lower edge of the first flat tube 40a in fig. 7) is in a range of 4mm or less. The reason why the distance d1 is set to be in the range of 4mm or less is based on the verification result described below. In fig. 7, the second raised portion 55 is omitted.
Fig. 19 is a graph comparing the sizes d2 of the condensed water (droplets) staying around the first flat tube 40a at different contact angles θ. Fig. 19A shows an average value of measurement results of the droplet size d2 at each fin pitch (1.0mm, 1.5mm, 2.0mm) when the contact angle θ was 10 °. Fig. 19B shows an average value of the measurement results of the droplet size d2 at each fin pitch (1.0mm, 1.5mm, 2.0mm) when the contact angle θ was 60 °.
As test conditions, as shown in fig. 7, three types of fin pitches Pv of the fins 50 were set to 1.0mm, 1.5mm, and 2.0mm for the condensed water retained between the adjacent first fins 50a and second fins 50b, and the size d2 of the droplet was measured in both cases, (1) when the contact angle θ was 10 degrees, which is a state in which hydrophilic processing of the surface of the fin 50 sufficiently functions; and (2) the case where the contact angle θ is 60 degrees, which is a state where hydrophilic processing of the surface of the fin 50 does not work due to deterioration or contamination. Wherein the contact angle θ is adjusted by adding a surfactant to the water forming the droplets. That is, by increasing the amount of surfactant, the contact angle θ of the droplet is decreased. In this test, an acrylic resin material was used for the fins.
As shown in fig. 19A, the average value of the sizes d2 of the droplets was 3.0 as a result of measurement under the conditions that the contact angle θ was 10 ° and the fin pitch Pv was 1.0 mm. Further, as shown in fig. 19A, the average value of the sizes d2 of the droplets was 3.3 as a result of measurement under the conditions that the contact angle θ was 10 ° and the fin pitch Pv was 1.5 mm. Further, as shown in fig. 19A, the average value of the sizes d2 of the droplets was 3.1 when the contact angle θ was 10 ° and the fin pitch Pv was 2.0 mm.
Further, as shown in fig. 19B, the average value of the sizes d2 of the droplets was 11.0 when the contact angle θ was 60 ° and the fin pitch Pv was 1.0 mm. Further, as shown in fig. 19B, the average value of the sizes d2 of the droplets was 11.2 as a result of measurement under the conditions that the contact angle θ was 60 ° and the fin pitch Pv was 1.5 mm. Further, as shown in fig. 19B, the average value of the sizes d2 of the droplets was 11.3 as a result of measurement under the conditions that the contact angle θ was 60 ° and the fin pitch Pv was 2.0 mm.
From the above measurement results, it is found that the smaller the contact angle θ, the smaller the droplet size d2, and therefore the distance d1 between the first upper end portion X1 of the first swelling portion 54 and the lower edge of the first cut portion 51a needs to be set small. The surface of the fin 50 is usually subjected to hydrophilic treatment, and the contact angle θ of the liquid droplets retained on the surface of the fin after the hydrophilic treatment is set to 20 ° or less. Since the effect of the hydrophilic treatment of the fin 50 is gradually reduced by contamination or deterioration, the distance d1 between the first upper end X1 of the first raised portion 54 and the lower edge of the first cut portion 51a may be set so as to be able to cope with the size d2 of the liquid droplet in the new state, that is, when the contact angle θ is 20 °.
Then, from the measurement results, an approximate calculation formula of the droplet size d2 corresponding to the contact angle θ was established, and the droplet size d2 was obtained when the contact angle θ became 20 °. As a result, the inventors found that, if the distance d1 is 4mm or less, the lower end of the liquid droplet comes into contact with the first upper end X1 of the first raised part 54 even if the contact angle θ becomes 20 °.
Therefore, when the distance d1 between the first upper end X1 of the first raised part 54 and the lower edge of the first notch part 51a (corresponding to the lower edge of the first flat tube 40a in fig. 8B) shown in fig. 8B is set to 4mm or less, even when the droplet size d2 of the condensed water is small and the contact angle is 20 degrees (the hydrophilic processing of the surface of the fin 50 is sufficiently effective), the distance d1 can be reduced to 4.6mm (the fin pitch Pv is 1.0mm) which is the minimum droplet size d2, so that the droplet can reach the first upper end X1 of the first raised part 54. In fig. 8B, the second bump 55 is omitted.
Thus, the droplets of the condensed water reach the first upper end portion X1 of the first raised part 54, and then flow over the upper end edge X1-X2 due to the influence of the surface tension, and further flow to the intermediate portion side edges X1-Z1 and the communication portion side edges X2-Z2 via the first upper end portion X1 and the second upper end portion X2. Since the water droplets are influenced by gravity in addition to the influence of the surface tension on the intermediate portion side edges X1 to Z1 and the communication portion side edges X2 to Z2, the water droplets can be easily discharged by providing the first raised portions 54.
Further, as shown in fig. 9, the first raised portion 54 and the second raised portion 55 are preferably formed such that a distance d3 between the communication portion side end of the cutout portion 51 and the second raised portion 55 is equal to or greater than a distance d4 between the first raised portion 54 and the second raised portion 55. Further, the first bump portion 54 is not formed integrally with the second bump portion 55 (i.e., d4 ≠ 0). The reason that the distance d3 may be longer than the distance d4 is as follows: since the wind speed is low in the dead water region behind the flat tube 40, the influence of the air flow is less significant than the wind speed on the leeward side of the first raised portion 54, and the water droplets of the condensed water are less likely to flow away.
The first raised portion 54 is disposed across the boundary between the intermediate portion 52 and the communication portion 53 of the fin 50 (see fig. 9), and therefore also contributes to suppressing the fin 50 from being bent or bent in an assembly process or the like.
Direction of ventilation
The above-described ventilation direction, which differs depending on the type of the indoor unit 3, will be described with reference to fig. 10 to 18. Fig. 10 to 14 show a type in which the heat exchanger 31 is located on the windward side and the indoor fan 32 is located on the leeward side in the ventilation path 35, that is, a case where the air flow is generated in a "suction type". Fig. 15 to 18 show a type in which the indoor fan 32 is located on the upwind side and the heat exchanger 31 is located on the downwind side in the ventilation path 35, that is, a case where the air flow is generated in "blow-out type". In fig. 10 to 18, the first raised part 54 and the second raised part 55 are not shown.
Suction type
Fig. 10 shows a duct-type indoor unit 3, fig. 11 shows a wall-mounted indoor unit 3, fig. 12 shows a vertical-type indoor unit 3, fig. 13 shows a vertical-blowing-duct-type indoor unit 3, and fig. 14 shows a window-type indoor unit 3 (which is integrated with the outdoor unit 2). In the case of these suction type indoor units 3, as shown in fig. 10 to 14, the ventilation direction can be set by a virtual line AF that takes the communicating portion side end of the flat tube 40, which is the position where the condensed water stays, as a starting point AU and the center of the indoor fan 32, which is the position where the static pressure is lowest, as an end point AD. The virtual line AF is set to cross the second raised portion 55 provided in the communication portion 53.
Here, as the indoor fan 32, an example is shown in which a centrifugal fan is used in a duct type (fig. 10), a vertical blower type (fig. 13), and a window type (fig. 14), and a cross flow fan is used in a wall type (fig. 11) and a vertical type (fig. 12).
Of these types, in the indoor unit 3 in which the heat exchanger 31 is formed by a plurality of heat exchange units, such as a wall-mounted type (fig. 11) and a vertical air blowing pipe type (fig. 13), the ventilation direction of the ventilation path 35 can be set by a virtual line AF that has a communication portion side end of each heat exchange unit as a starting point AU and a center of one indoor fan 32 as an end point AD. In the indoor unit 3 having a plurality of indoor fans 32 as in the vertical type (fig. 12), the ventilation direction can be set by a virtual line AF that has the end on the side of the communicating portion of one heat exchanger 31 as a starting point AU and the centers of the two indoor fans 32 as end points AD.
Blow-out type
Fig. 15 shows an air duct type indoor unit 3, fig. 16 shows a ceiling type indoor unit 3, fig. 17 shows a ceiling type indoor unit 3, and fig. 18 shows a wall type indoor unit 3. In the case of these indoor units 3 of the blow-out type, as shown in fig. 15 to 18, the ventilation direction of the ventilation path 35 is: a direction (virtual line AF) in which the position where the condensed water stays, that is, the end of the flat tube 40 on the communicating portion side is taken as a starting point AU and the portion where the static pressure is lowest is taken as an end point AD on the leeward side of the heat exchanger 31. The air flowing through the heat exchanger 31 flows toward the lowest static pressure point (end point AD). Therefore, the direction of the resistance received by the condensed water staying at the starting point AU is the direction of the virtual line AF. The virtual line AF is set to cross the second raised portion 55 provided in the communication portion 53.
Here, as the indoor fan 32, an example is shown in which a centrifugal fan is used for a duct type (fig. 15), a ceiling type (fig. 16), and a ceiling type (fig. 17), and a propeller fan is used for a wall type (fig. 12).
Of these types, in the indoor unit 3 in which the position where the cross-sectional area on the leeward side of the heat exchanger 31 is the smallest is the outlet port of the heat exchanger 31, such as the air duct type (fig. 15) and the ceiling type (fig. 16), the ventilation direction of the ventilation path 35 can be set by a virtual line AF that has the end on the communication portion side of the heat exchanger 31 as the starting point AU and the center of the outlet port as the end point AD. In the indoor unit 3 in which the position where the cross-sectional area of the ventilation path 35 is the smallest is not the outlet port of the heat exchanger 31, such as the ceiling type (fig. 17) and the wall type (fig. 18), the ventilation direction can be set by a virtual line AF having the end of the communication portion of the heat exchanger 31 as the starting point AU and the end point AD at the center of the position where the cross-sectional area is the smallest, which differs depending on the configuration of each ventilation path 35. In the indoor unit 3 illustrated in fig. 17 and 18, the heat exchanger 31 is formed by a plurality of heat exchange units, and a plurality of end points AD are set in correspondence with the air flows flowing through the respective heat exchange units.
Effects of the embodiments
The heat exchanger 31 according to the present embodiment can suppress the condensation of the condensed water accumulated on the surfaces of the fins 50 or the flat tubes 40 from splashing. Specifically, by providing the first raised portion 54 in the intermediate portion 52 of the fin 50 located below the flat tube 40, the condensed water around the flat tube 40 is discharged. As a result, the adhered water droplets are reduced, and the second raised portion 55 is provided in the communication portion 53 of the fin 50, so that the airflow velocity is reduced, and therefore the resistance acting on the condensed water in the ventilation direction (the force in the ventilation direction received from the airflow) is reduced. As a result, the condensed water can be prevented from splashing toward the leeward side from the heat exchanger 31, that is, from splashing of the condensed water. Further, the ventilation direction of the ventilation path 35 can be set by using a virtual line AF having a starting point AU at the end of the communicating portion of the flat tube 40 where the condensed water stays, and an end point AD at the center of the position where the cross-sectional area on the leeward side of the heat exchanger 31 where the static pressure is the lowest, whereby the positions of the first raised portion 54 and the second raised portion 55 can be set in the ventilation path 35 in accordance with the direction of the resistance force acting on the condensed water.
Description of the symbols
1 air conditioner
2 outdoor machine
3 indoor machine
4 liquid pipe
5 gas pipe
10 refrigerant circuit
10a outdoor machine refrigerant circuit
10b indoor unit refrigerant circuit
12 header
21 compressor
22 four-way valve
23 outdoor heat exchanger
24 expansion valve
25 liquid side shut-off valve
26 gas side closing valve
27 outdoor fan
31 indoor heat exchanger
32 indoor fan
33 liquid pipe connection part
34 gas pipe connection
35 ventilation path
40 flat tube
50 fin
51 notch part
52 intermediate section
53 connecting part
54 first raised portion
55 second bump
61 discharge pipe
62 refrigerant piping
63 outdoor unit liquid pipe
64 outdoor unit gas pipe
66 suction pipe
67 liquid pipe of indoor unit
68 indoor unit gas pipe
71 discharge pressure sensor
72 suction pressure sensor
73 discharge temperature sensor
74 suction temperature sensor
75 heat exchange temperature sensor
76 outside air temperature sensor
77 liquid side temperature sensor
78 gas side temperature sensor
79 indoor temperature sensor
200 outdoor unit control unit
210 CPU
220 storage part
230 communication unit
240 sensor input unit
300 indoor unit control unit
310 CPU
320 storage part
330 communication unit
340 a sensor input.

Claims (5)

1. An air conditioner having a ventilation path in which a heat exchanger and a fan are disposed in a casing,
the heat exchanger is provided with a plurality of flat tubes, fins, a first bulge part and a second bulge part,
the fin has a plurality of notches arranged in a vertical direction for inserting the flat tubes, and has an intermediate portion formed between the notches at vertically adjacent positions and a communication portion connecting the intermediate portions to each other,
the heat exchanger is arranged such that the intermediate portion is located on the windward side of the communication portion in the ventilation direction of the air flowing through the ventilation path,
the first raised portion is configured such that at least a portion thereof is located in the intermediate portion,
and a resistance line defined by a virtual line starting at a point where the condensate water stays on the upstream side fins and ending at a point where the static pressure is lowest in the ventilation path on the downstream side, wherein the second raised portion is provided so as to overlap a gap formed between the first raised portion and the flat tube when the heat exchanger is viewed from the upstream side in the direction of the resistance line.
2. The air conditioner according to claim 1,
in the ventilation path, the fan is provided on the ventilation direction downstream side of the heat exchanger,
the end point is the center of the fan.
3. The air conditioner according to claim 1,
in the ventilation path, the fan is provided on the ventilation direction upstream side of the heat exchanger,
the end point is a center of a position in the ventilation path where the flow path sectional area is smallest.
4. The air conditioner according to claim 1,
the first raised portion is formed such that an upper end edge thereof is located within a range of 4mm or less from a lower edge of the first cutout portion on the upper side.
5. The air conditioner according to claim 1,
the first raised portion and the second raised portion are formed such that a distance between the notch portion and the second raised portion is equal to or greater than a distance between the first raised portion and the second raised portion.
CN202080017287.2A 2019-03-26 2020-01-31 Air conditioner Pending CN113498471A (en)

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JP2019058395A JP2020159616A (en) 2019-03-26 2019-03-26 Air conditioner
JP2019-058395 2019-03-26
PCT/JP2020/003638 WO2020195153A1 (en) 2019-03-26 2020-01-31 Air conditioner

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CN (1) CN113498471A (en)
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WO (1) WO2020195153A1 (en)

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