WO2017073096A1 - 空気調和機の室外機および室内機 - Google Patents
空気調和機の室外機および室内機 Download PDFInfo
- Publication number
- WO2017073096A1 WO2017073096A1 PCT/JP2016/061662 JP2016061662W WO2017073096A1 WO 2017073096 A1 WO2017073096 A1 WO 2017073096A1 JP 2016061662 W JP2016061662 W JP 2016061662W WO 2017073096 A1 WO2017073096 A1 WO 2017073096A1
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- WIPO (PCT)
- Prior art keywords
- heat exchanger
- exchanger body
- air conditioner
- outdoor unit
- refrigerant
- Prior art date
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Classifications
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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
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
- F24F1/16—Arrangement or mounting thereof
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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
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
- F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
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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
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/46—Component arrangements in separate outdoor units
- F24F1/48—Component arrangements in separate outdoor units characterised by air airflow, e.g. inlet or outlet airflow
- F24F1/50—Component arrangements in separate outdoor units characterised by air airflow, e.g. inlet or outlet airflow with outlet air in upward direction
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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
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
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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
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
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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
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
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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
Definitions
- the present invention relates to an outdoor unit and an indoor unit of an air conditioner with improved energy efficiency.
- liquid refrigerant condensed by a heat exchanger functioning as a condenser mounted in an indoor unit is decompressed by an expansion valve, and a gas-liquid two-phase state in which gas refrigerant and liquid refrigerant are mixed It flows into the heat exchanger that functions as an evaporator mounted on the outdoor unit.
- the refrigerant flows into the heat exchanger that functions as an evaporator in a gas-liquid two-phase state, the distribution performance of the refrigerant to the heat exchanger deteriorates.
- the header as a distributor of the heat exchanger mounted on the outdoor unit, the amount of branch pipe protruding into the header, the partition plate in the header, the installation of the ejection holes, etc. There is a way to adjust the structure in the header.
- the distribution of the gas-liquid two-phase refrigerant in the header is greatly affected by the mass velocity of the refrigerant. For example, when operating at high output, more refrigerant is distributed at the top of the header than at the bottom of the header, and when operating at low output, more refrigerant is distributed at the bottom of the header than at the top of the header. Will be. And since the heat exchange performance of the heat exchanger deteriorates due to the deterioration of the refrigerant distribution performance, there is a problem that the energy efficiency of the air conditioner is reduced. In addition, the outdoor unit of the air conditioner has more wind flowing closer to the fan.
- Patent Document 1 In order to improve the energy efficiency of the air conditioner, it is necessary to make the distribution of the gas-liquid two-phase refrigerant uniform. As a method for this, a method of providing a turbulent flow promoter for stirring the refrigerant in the header has been conventionally used. Yes (see Patent Document 1). In Patent Document 1, the gas-liquid two-phase refrigerant in the header is agitated by the turbulence promoting body, so that the gas-liquid two-phase refrigerant is uniformly distributed.
- the present invention has been made to solve the above-described problems, and an object thereof is to provide an outdoor unit and an indoor unit for an air conditioner that improve energy efficiency while suppressing an increase in cost.
- An outdoor unit of an air conditioner according to the present invention has a suction port and a blower outlet, and is provided in the casing and includes a casing constituting an outer shell, sucks outside air from the suction port, and discharges outside air from the blower outlet And a heat exchanger provided in the casing for exchanging heat between the outside air sucked by the fan and the refrigerant, and the heat exchanger includes a plurality of fins arranged in parallel at intervals.
- the first heat exchanger main body in which a flat tube having a high heat exchange performance is a heat transfer tube is disposed near a fan having a high contribution rate to the heat exchange performance.
- the second heat exchanger body, which is a heat transfer tube is arranged in the distance from the fan that has a low contribution rate to the heat exchange performance, but the heat exchange performance is low, but the refrigerant distribution performance is high and the manufacturing cost is low. . Therefore, energy efficiency can be improved while suppressing an increase in cost.
- FIG. 3 is a cross-sectional view taken along line AA in FIG. 2.
- FIG. 3 is a diagram showing another example of the AA cross-sectional view of FIG. 2.
- FIG. 3 is a sectional view taken along line BB in FIG.
- It is a schematic diagram of the distributor which concerns on Embodiment 1 of this invention.
- It is a schematic diagram which shows the distributor different from the distributor which concerns on Embodiment 1 of this invention.
- FIG. 4 It is a perspective view of the outdoor unit of the air conditioner which concerns on Embodiment 4 of this invention. It is a side surface schematic diagram of the heat exchanger which concerns on Embodiment 4 of this invention. It is a schematic diagram which shows a part of structure at the time of using an internal heat exchanger as a dryness adjustment apparatus of the outdoor unit of an air conditioner. It is a 1st figure which shows another example of FIG. It is a 2nd figure which shows another example of FIG. It is a 3rd figure which shows another example of FIG. It is a side surface schematic diagram of the heat exchanger which concerns on Embodiment 5 of this invention, and its periphery.
- FIG. FIG. 1 is a perspective view of an outdoor unit 100a for an air conditioner according to Embodiment 1 of the present invention
- FIG. 2 is a schematic side view of a heat exchanger 10a according to Embodiment 1 of the present invention and its surroundings.
- 3 is a cross-sectional view taken along the line AA in FIG. 2
- FIG. 4 is a view showing another example of the cross-sectional view taken along the line AA in FIG. 2
- the arrow in FIG. 1 has shown the flow of the wind
- the arrow in FIG. 2 has shown the flow of the refrigerant
- the outdoor unit 100a of the air conditioner according to Embodiment 1 is equipped with a heat exchanger 10a shown in FIG.
- the outdoor unit 100a of the air conditioner is a top flow type, and constitutes a refrigeration cycle by circulating a refrigerant with an indoor unit (not shown).
- the outdoor unit 100a is used, for example, in a building multi-unit outdoor unit, and is installed on the roof of a building.
- the outdoor unit 100 a is arranged in the casing 1 along the casing 1 formed in a box shape, the suction port 2 formed by the opening on the side surface of the casing 1, and the suction port 2.
- the heat exchanger 10a, the air outlet 3 formed by the opening on the upper surface of the casing 1, the fan guard 4 provided so as to be ventilated so as to cover the air outlet 3, and the fan guard 4 are disposed inside And a fan 5 that sucks outside air from the mouth 2 and discharges outside air from the air outlet 3.
- the heat exchanger 10a mounted on the outdoor unit 100a of the air conditioner exchanges heat between the outside air sucked from the suction port 2 by the fan 5 and the refrigerant.
- the heat exchanger 10 a is disposed below the fan 5, and includes an upper heat exchanger 11 and a lower heat exchanger 12.
- the upper heat exchanger 11 and the lower heat exchanger 12 are arranged in the vertical direction when viewed from the front or from the side. Specifically, the upper heat exchanger 11 is disposed on the upper side near the fan 5, and the lower heat exchanger 12 is disposed on the lower side far from the fan 5.
- the upper heat exchanger 11 includes a plurality of fins 21 that are arranged in parallel at intervals, and a plurality of heat transfer tubes that penetrate the fins 21 in the direction in which the fins 21 are arranged and in which the refrigerant flows.
- An upper heat exchanger body 20, an upper first header 23 connected to one end of the plurality of heat transfer tubes, and an upper second header 24 connected to the other end of the plurality of heat transfer tubes are provided.
- An upper first header 23 is connected to the upstream side of the upper heat exchanger body 20 during heating operation, and an upper second header 24 is connected to the downstream side of the upper heat exchanger body 20 during heating operation.
- the distributor connected to the upstream side of the upper heat exchanger body 20 or the lower heat exchanger body 30 during the heating operation is referred to as an upstream distributor.
- the lower heat exchanger 12 includes a plurality of fins 31 arranged in parallel at intervals, and a plurality of heat transfer tubes that penetrate the fins 31 in the juxtaposition direction of the fins 31 and through which the refrigerant flows.
- a distributor 34 is connected via a capillary tube 33 to the upstream side of the lower heat exchanger body 30 during heating operation, and a lower header 35 is connected to the downstream side of the lower heat exchanger body 30 during heating operation. ing.
- the upper first header 23 of the upper heat exchanger 11 is connected to a first branch pipe 41 branched from a first pipe 40 through which a gas-liquid two-phase refrigerant mixed with gas refrigerant and liquid refrigerant passes during heating operation. ing.
- the upper second header 24 of the upper heat exchanger 11 is connected to a first branch pipe 51 branched from the second pipe 50 through which the gas refrigerant passes during heating operation.
- the distributor 34 of the lower heat exchanger 12 is connected to a second branch pipe 42 branched from the first pipe 40.
- the lower header 35 of the lower heat exchanger 12 is connected to a second branch pipe 52 branched from the second pipe 50.
- the heat transfer tube of the upper heat exchanger 11 according to the first embodiment is a flat tube 22 having a flat cross section shown in FIG. 3, but the cross section shown in FIG. 4 is a flat shape and has a plurality of holes inside. It is good also as the flat porous tube 22a in which is formed. Moreover, although the flat tube 22 shown in FIG. 3 and the flat porous tube 22a shown in FIG. 4 are both smooth surfaces, it is good also as a grooved surface which expands a heat-transfer area by cutting a groove
- FIG. 16 is a first diagram showing another example of FIG. 2
- FIG. 17 is a second diagram showing another example of FIG.
- the first embodiment there is a gap between the upper heat exchanger 11 and the lower heat exchanger 12 as shown in FIG. 2, but in reality, water droplets on the fin surface of the upper heat exchanger 11 are removed.
- the upper heat exchanger 11 and the lower heat exchanger 12 may be brought into close contact with each other as shown in FIG.
- the fin has no cut
- the gas-liquid two-phase refrigerant passes through the first pipe 40 and is divided into the first branch pipe 41 and the second branch pipe 42.
- the gas-liquid two-phase refrigerant that has flowed to the second branch pipe 42 flows to the distributor 34, is homogenized therein, and then flows into the lower heat exchanger main body 30 through the capillary tube 33.
- the gas-liquid two-phase refrigerant flowing into the lower heat exchanger body 30 is gasified by exchanging heat with the outside air sucked from the suction port 2 there and flows out to the lower header 35.
- the gas-liquid two-phase refrigerant that has flowed to the first branch pipe 41 flows to the upper first header 23, where it is distributed to each flat pipe 22 and flows from each flat pipe 22 into the upper heat exchanger body 20.
- the gas-liquid two-phase refrigerant flowing into the upper heat exchanger body 20 is gasified by exchanging heat with the outside air sucked from the suction port 2 there and flows out to the upper second header 24.
- FIG. 6 is a schematic diagram of the distributor 34 according to the first embodiment of the present invention.
- the distributor 34 shown in FIG. 6 includes a distribution main pipe portion 61, a distribution expansion portion 62, and a distribution diverting member 63.
- the distribution main pipe portion 61 is provided with an area abrupt reduction portion 64.
- One end of a capillary tube 33 is connected to the distributor 34.
- the gas-liquid two-phase refrigerant flows into the distributor 34 and is squeezed by the area abrupt reduction section 64 of the distribution main pipe section 61, and the gas refrigerant and the liquid refrigerant are agitated and homogenized by the distribution expansion section 62.
- the homogenized gas refrigerant and liquid refrigerant are distributed to each capillary tube 33 by a distribution branching member 63.
- the other end of the capillary tube 33 is connected to the circular pipe 32 of the lower heat exchanger 12, and the flow rate of the refrigerant flowing through each circular pipe 32 can be controlled by adjusting the length of the capillary tube 33.
- FIG. 7 is a schematic diagram showing a distributor different from the distributor 34 according to Embodiment 1 of the present invention.
- the arrow in FIG. 7 has shown the gravity direction.
- the distributor connected to the upstream side of the lower heat exchanger main body 30 during the heating operation is the distributor 34 shown in FIG. 6, but may be the header 70 shown in FIG.
- the header 70 shown in FIG. 7 has a structure that distributes the gas-liquid two-phase refrigerant that has flowed into the header 70 to the circular tubes 32 that are a plurality of heat transfer tubes arranged in parallel in the direction of gravity.
- the gas-liquid two-phase refrigerant flows upward in the header 70 in the upward direction, and is divided into a plurality of circular pipes 32 at an angle perpendicular to the flow in the header 70.
- the distributor 34 generally has a higher refrigerant distribution performance than the header.
- the flat tube 22 is used in a heat exchanger that is a heat transfer tube, the number of paths increases, so that it is necessary to increase the number of branches of the distributor 34 or to use a plurality of distributors 34. There is a demerit that the handling of is complicated.
- the header is easy to handle the piping, can be easily applied to automation such as automatic brazing, and can be manufactured at low cost.
- gravity acts on the gas-liquid two-phase refrigerant, for example, when the refrigerant flow rate is small, there is a problem that the liquid refrigerant having a high density flows more biased to the lower part of the heat transfer tube. There is a demerit that the distribution performance is lower than that of the distributor 34.
- FIG. 8 is a diagram showing the air volume with respect to the height direction of the heat exchanger 10a according to Embodiment 1 of the present invention. Since the heat exchanger 10a according to the first embodiment is mounted on the top flow type outdoor unit 100a, the fan 5 is arranged above the heat exchanger 10a, and the fan 5 causes the wind to be heat exchanger. It passes through the gap 10a, thereby exchanging heat with air. And since the fan 5 is arrange
- the flow of wind increases in the upper heat exchanger 11 disposed on the upper side of the lower heat exchanger 12 disposed on the lower side. Therefore, when the front surface areas of the upper heat exchanger 11 and the lower heat exchanger 12 are the same, the upper heat exchanger 11 has a higher contribution ratio to the heat exchange performance of the outdoor unit 100a than the lower heat exchanger 12. Become.
- an upper heat exchanger 11 having a high heat exchange performance and having a flat tube 22 as a heat transfer tube is arranged on the upper side of the outdoor unit 100a where the flow of wind is large, that is, near the fan 5, and the flow of wind is
- a lower heat exchanger 12 in which the circular tube 32 is a heat transfer tube having a low heat exchange performance but a high refrigerant distribution performance is disposed below the few outdoor units 100a, that is, at a position far from the fan 5.
- an optimum distributor is used for each upstream distributor of the heat exchanger in which the flat tube 22 is a heat transfer tube and the heat exchanger in which the circular tube 32 is a heat transfer tube.
- a header is used as a distributor in the heat exchanger in which the flat tube 22 is a heat transfer tube, that is, the upper heat exchanger 11, and a heat exchanger in which the circular tube 32 is a heat transfer tube, that is, in the lower heat exchanger 12 is distributed.
- Distributor 34 is used as a device.
- the flow resistance of the distributor is larger in the distributor 34 than in the header, more refrigerant can flow through the upper heat exchanger 11 by using the distributor as described above. Therefore, the distribution characteristic of the refrigerant can be improved, and the heat exchange performance of the heat exchanger 10a can be improved. It is even better because the flow rate of the refrigerant flowing in the header can be adjusted by changing the length of the capillary tube 33 connected to the distributor 34.
- FIG. 18 is a third diagram showing another example of FIG.
- the distributor 34 is connected to the circular tube 32 and the header is connected to the flat tube 22 as shown in FIG. 2, but this is only an example.
- the same distributor may be attached to either the flat tube 22 or a distributor 34 may be connected to the flat tube 22 and a header may be connected to the circular tube 32.
- the flat tube 22 having a high heat exchange performance is a heat transfer tube near the fan 5 having a high contribution rate to the heat exchange performance of the outdoor unit 100a.
- a certain upper heat exchanger 11 it is possible to provide a heat exchanger 10a with good cost performance.
- the upper heat in which the flat tube 22 having a high heat exchange performance is a heat transfer tube near the fan 5 having a high contribution rate to the heat exchange performance.
- FIG. 9 is a schematic side view of the heat exchanger 10b and its surroundings according to Embodiment 2 of the present invention.
- the arrow in FIG. 9 has shown the flow of the refrigerant
- the outdoor unit 100b of the air conditioner according to Embodiment 2 includes a gas-liquid separator 80 on the upstream side of the heat exchanger 10b.
- the gas-liquid separator 80 is used to adjust the dryness of the refrigerant.
- the first pipe 40 through which the liquid refrigerant separated by the gas-liquid separator 80 flows is connected.
- the fourth pipe 83 is connected to the bypass flow valve 85, the bypass flow valve 85 is connected to the fifth pipe 84, and the fifth pipe 84 is connected to the second pipe 50.
- the second pipe 50 is connected to the compressor 81.
- FIG. 15 is a schematic diagram showing a part of the configuration when the internal heat exchanger 110 is used as a dryness adjusting device for an outdoor unit of an air conditioner.
- the gas-liquid separator 80 corresponds to the “dryness adjusting device” of the present invention, but is only an example of a device for adjusting the dryness, and is not limited thereto.
- an internal heat exchanger 110 as shown in FIG. 15 or a heat exchanger that exchanges heat with another low-temperature heat source or the like may be used.
- the refrigerant passes through the pipe 111 and flows into the internal heat exchanger 110.
- the refrigerant that has flowed into the internal heat exchanger 110 is self-cooled by the pipe 116 at the outlet of the heat exchanger 117 and a part of the bypassed refrigerant, and flows to the heat exchanger 117 through the pipe 112 in a state of reduced dryness.
- the bypassed refrigerant passes through the pipe 115, and the bypass flow rate is adjusted by a valve 114 installed on the pipe 113.
- the valve 114 installed on the pipe 113 is not limited to a valve, and may be a flow resistor such as a capillary tube, a thin tube, or a float valve.
- the gas-liquid two-phase refrigerant passes through the third pipe 82 and flows into the gas-liquid separator 80.
- the gas-liquid two-phase refrigerant that has flowed into the gas-liquid separator 80 is separated into gas refrigerant and liquid refrigerant there.
- the gas refrigerant separated by the gas-liquid separator 80 passes through the fourth pipe 83, the bypass flow valve 85, the fifth pipe 84, and the second pipe 50 and flows into the compressor 81.
- the liquid refrigerant separated by the gas-liquid separator 80 passes through the first pipe 40 and is divided into the first branch pipe 41 and the second branch pipe 42.
- the liquid refrigerant that has flowed to the second branch pipe 42 flows to the distributor 34, where it is homogenized, and then flows into the lower heat exchanger body 30 through the capillary tube 33.
- the liquid refrigerant flowing into the lower heat exchanger body 30 is gasified by exchanging heat with the outside air sucked from the suction port 2 there and flows out to the lower header 35.
- the liquid refrigerant that has flowed to the first branch pipe 41 flows to the upper first header 23, where it is distributed to each flat pipe 22 and flows from each flat pipe 22 into the upper heat exchanger body 20.
- the gas-liquid two-phase refrigerant flowing into the upper heat exchanger body 20 is gasified by exchanging heat with the outside air sucked from the suction port 2 there and flows out to the upper second header 24.
- the flow rate ratio of the refrigerant flowing through the first branch pipe 41 and the second branch pipe 42 is that of the first branch pipe 41, the upper first header 23, the flat pipe 22, the upper second header 24, and the first branch pipe 51.
- the total flow resistance and the total flow resistance of the second branch pipe 42, distributor 34, capillary tube 33, circular pipe 32, lower header 35, and second branch pipe 52 are determined.
- the length of the capillary tube 33 the flow rate ratio of the refrigerant flowing through the first branch pipe 41 and the second branch pipe 42 can be optimally adjusted.
- the gas refrigerant flow rate / total refrigerant flow rate (hereinafter referred to as dryness)
- dryness the gas refrigerant flow rate / total refrigerant flow rate
- the gas is in the upper first header 23.
- the liquid refrigerant easily flows to the flat tubes 22 unevenly. Therefore, by reducing the gas refrigerant flowing through the upper first header 23 using the gas-liquid separator 80, the distribution performance of the refrigerant flowing through the upper first header 23 is improved, and the heat exchange performance is improved.
- the gas-liquid two-phase refrigerant is separated into the gas refrigerant and the liquid refrigerant by the gas-liquid separator 80, but the gas flowing into the upper first header 23 even if it cannot be completely separated. What is necessary is just to be able to reduce a refrigerant
- the gas-liquid separator 80 the pressure loss when passing through the distributor and the heat transfer tube can be reduced as a whole, and the flow rate ratio adjustment by the capillary tube 33 becomes easy.
- FIG. 10 is a schematic side view showing another example of the heat exchanger 10b according to the second embodiment of the present invention and its periphery
- FIG. 11 shows the heat exchanger 10b according to the second embodiment of the present invention. It is a side surface schematic diagram which shows another example of the periphery.
- the arrow in FIG. 10 and FIG. 11 has shown the flow of the refrigerant
- the arrangement of the gas-liquid separator 80 is not limited to the position shown in FIG. 9, and the gas-liquid separator 80 may be arranged in the first branch pipe 41 as shown in FIG. As shown, a gas-liquid separator 80 may be disposed in the second branch pipe 42.
- the control range of the flow rate of the refrigerant flowing through the first branch pipe 41 and the second branch pipe 42 is further widened.
- FIG. 12 is a schematic side view of the heat exchanger 10c according to the third embodiment of the present invention and its periphery.
- the arrow in FIG. 12 has shown the flow of the refrigerant
- at least two types of heat transfer tubes, a flat tube 22 and a circular tube 32 are connected in series via an intermediate header 26.
- the heat exchanger 10c is disposed below the fan 5, and includes an upper heat exchanger body 20, a lower heat exchanger body 30, a header 25, an intermediate header 26, a distributor 34, a capillary tube 33, It has.
- the upper heat exchanger body 20 includes a plurality of fins 21 arranged in parallel at intervals, and a plurality of flat tubes 22 that pass through the fins 21 in the juxtaposition direction of the fins 21 and through which the refrigerant flows.
- the lower heat exchanger main body 30 includes a plurality of fins 31 arranged in parallel at intervals, a plurality of circular pipes 32 that pass through the fins 31 in the direction in which the fins 31 are arranged, and in which the refrigerant flows. It consists of The upper heat exchanger main body 20 and the lower heat exchanger main body 30 are arranged in a vertical direction when viewed from the front or from the side, and the upper heat exchanger main body 20 is located on the upper side near the fan 5. The lower heat exchanger body 30 is disposed on the lower side far from the fan 5.
- the plurality of flat tubes 22 of the upper heat exchanger body 20 and the plurality of circular tubes 32 of the lower heat exchanger body 30 are juxtaposed in the direction of gravity.
- One end of the plurality of flat tubes 22 of the upper heat exchanger body 20 is connected to the header 25, and one end of the plurality of circular tubes 32 of the lower heat exchanger body 30 is connected to the distributor 34 via the capillary tube 33.
- the other end of the plurality of flat tubes 22 of the upper heat exchanger body 20 and the other end of the plurality of circular tubes 32 of the lower heat exchanger body 30 are connected to the intermediate header 26.
- the distributor connected to the upstream side of the upper heat exchanger body 20 during the cooling operation is the header 25, and the distributor connected to the upstream side of the lower heat exchanger body 30 during the cooling operation is Distributor 34.
- the header 25 is connected to a first pipe 91 through which gas refrigerant passes during cooling operation, and the distributor 34 is connected to a second pipe 92 through which liquid refrigerant passes during cooling operation.
- the high-temperature and high-pressure gas refrigerant passes through the first pipe 91 and flows to the header 25, where it is distributed to each flat tube 22 and flows into the upper heat exchanger body 20 from each flat tube 22.
- the gas refrigerant that has flowed into the upper heat exchanger body 20 exchanges heat with the outside air sucked from the suction port 2 to dissipate heat, thereby becoming a gas-liquid two-phase state and flows to the intermediate header 26.
- the gas-liquid two-phase refrigerant flows into the circular pipe 32 of the lower heat exchanger main body 30, where it further exchanges heat with the surrounding air to become a liquid single phase.
- the flat tube 22 is used for a heat exchanger in which a gas-liquid two-phase refrigerant with a large proportion of liquid refrigerant flows, such as the lower heat exchanger 12 in which the circular tube 32 is a heat transfer tube, the heat exchanger height is increased.
- the flat tube 22 is more conspicuous in lowering the heat transfer coefficient in the liquid single phase than the circular tube 32.
- the flat tube 22 is used for the heat exchanger in which the refrigerant with a large proportion of the liquid refrigerant flows, and the flat tube 22 is used in the heat exchanger in which the gas single-phase to gas-liquid two-phase state flows.
- the disadvantage of the tube 22 can be compensated, and a heat exchanger with excellent cost performance can be provided.
- FIG. 13 is a perspective view of an air conditioner outdoor unit 100d according to Embodiment 4 of the present invention
- FIG. 14 is a schematic side view of a heat exchanger 10d according to Embodiment 4 of the present invention.
- the arrow in FIG. 14 has shown the flow of the wind.
- the outdoor unit 100d of the air conditioner according to the fourth embodiment is equipped with a heat exchanger 10d shown in FIG.
- the outdoor unit 100d of the air conditioner is a side flow type, and constitutes a refrigeration cycle by circulating a refrigerant with an indoor unit (not shown).
- the outdoor unit 100d is used, for example, for a building multi-unit outdoor unit, and is installed on the roof of a building.
- the outdoor unit 100 d is arranged on a casing 101 formed in a box shape, a suction port (not shown) formed by an opening on the back of the casing 101, and a back side in the casing 101.
- the heat exchanger 10 d mounted on the outdoor unit 100 d of the air conditioner exchanges heat between the outside air sucked from the suction port by the fan 105 and the refrigerant, and the heat exchanger 10 d is behind the fan 105. Arranged on the side.
- the heat exchanger 10 d includes a front heat exchanger main body 120 constituted by the fins 21 and the flat tubes 22, and a rear heat exchanger main body 130 constituted by the fins 31 and the circular pipes 32.
- the front heat exchanger main body 120 and the rear heat exchanger main body 130 are arranged in the front-rear direction when viewed from the front. Specifically, the front heat exchanger main body 120 is arranged on the front side of the outdoor unit 100 d close to the fan 105, and the rear heat exchanger main body 130 is arranged on the back side of the outdoor unit 100 d far from the fan 105.
- the front heat exchanger main body 120 in which the flat tube 22 having high heat exchange performance is a heat transfer tube is arranged in the front row close to the fan 105, and the rear heat in which the circular tube 32 is a heat transfer tube in the rear row.
- the exchanger main body 130 By arranging the exchanger main body 130, it is possible to improve the heat exchange performance with good cost performance in the front row where the temperature difference between the refrigerant and the outside air is large.
- the upper heat exchanger main body 20 and the front heat exchanger main body 120 correspond to the “first heat exchanger main body” of the present invention, and the lower heat exchanger main body 30 and the rear heat exchanger main body 130 of the present invention. Corresponds to "second heat exchanger body”.
- the front surface of the casing 101 corresponds to the “side surface of the casing” of the present invention.
- FIG. 19 is a schematic side view of a heat exchanger 10e according to Embodiment 5 of the present invention and its periphery.
- the arrow in FIG. 19 has shown the flow of the refrigerant
- the heat exchanger 10e includes an upper first header 23 on the upstream side of the refrigerant flow in the upper heat exchanger body 20 and a lower first header 140 on the upstream side of the refrigerant flow in the lower heat exchanger body 30. Is connected, and a flow rate adjusting valve 150 is provided on the upstream side of the lower first header 140, and the flow rate of refrigerant flowing through the upper heat exchanger body 20 and the lower heat exchanger body 30 is adjusted by the valve opening. .
- an expansion valve is mentioned here as an example of a mechanism for adjusting the refrigerant flow rate, it is only an example, and any device that adjusts the refrigerant flow rate by changing the flow resistance, such as a capillary tube or a float, may be used.
- the distributor connected to the upper heat exchanger main body 20 or the lower heat exchanger main body 30 is connected to the header as an example of the fifth embodiment, but is not limited to this. You may mix headers and distributors.
- the flow rate of the refrigerant flowing through the lower heat exchanger main body 30 constituted by the circular pipe 32 is controlled by the flow rate adjusting valve 150 to achieve distribution adjustment, and the lower heat exchanger main body.
- the heat exchange contribution ratio of 30 can be changed, for example, a large amount of refrigerant can be stably supplied to the upper heat exchanger body 20 having a high heat exchange contribution ratio even during low-load operation, and the cost performance is excellent.
- a heat exchanger can be provided.
- FIG. 20 is a schematic side view of the heat exchanger 10f according to Embodiment 6 of the present invention and its periphery.
- the arrow in FIG. 20 has shown the flow of the refrigerant
- the heat exchanger 10f is connected to the upstream side of the lower heat exchanger main body 30 formed of the circular pipe 32 and the upper heat exchanger main body 20 formed of the flat tube 22 during the heating operation.
- the headers connected to the downstream side and the headers connected to the downstream side are one upstream header 160 and one downstream header 170 without being divided vertically. That is, one upstream header 160 and one downstream header 170 are connected across the upper heat exchanger body 20 and the lower heat exchanger body 30.
- piping can be reduced, or it is not necessary to attach a plurality of headers, and cost performance can be improved.
- the header connected to the upstream side of the upper heat exchanger body 20 and the lower heat exchanger body 30 and the header connected to the downstream side are respectively Although it is comprised by one, it is not limited to it.
- the upstream side is connected to a single header, but the downstream side may be a plurality of headers divided up and down, and the upstream side is connected to a distributor other than the header, such as a single distributor.
- the downstream side may be a plurality of headers divided into upper and lower sides.
- the upstream side may be a plurality of headers or distributors separated vertically, and the downstream side may be connected to a single header.
- FIG. 21 is a schematic side view of the heat exchanger 10g according to the seventh embodiment of the present invention and its periphery.
- the arrow in FIG. 21 has shown the flow of the refrigerant
- an anticorrosion sheet 180 is inserted between the upper heat exchanger body 20 and the lower heat exchanger body 30. This is because, for example, when the flat tube 22 is made of aluminum, the circular tube 32 is made of a copper tube, etc., and different kinds of metals exist vertically, the corrosion rate of the lower heat exchanger body 30 is reduced by drainage or the like. is there. It is also effective to configure the upper heat exchanger body 20 and the lower heat exchanger body 30 with the same material instead of the anticorrosion sheet 180.
- FIG. 22 is a schematic side view of the heat exchanger 10h according to Embodiment 8 of the present invention and its periphery.
- the arrow in FIG. 22 has shown the flow of the refrigerant
- the lower heat exchanger body 30 configured by the circular pipe 32 is farther from the fan 5 than the upper heat exchanger body 20 configured by the flat tube 22.
- the heat transfer tubes of the heat exchanger are disposed substantially vertically, that is, vertically.
- a flat tube 22 having a relatively high heat transfer performance is used at a position close to the fan 5, and a circular tube 32 having a relatively low heat transfer performance but a good cost performance is disposed at a position far from the fan 5.
- a heat exchanger excellent in cost performance can be provided.
- the header position where the refrigerant flows is the lower part of the heat exchanger body, but this is only an example.
- the refrigerant flow position is the upper part of the heat exchanger body, or the upper heat exchanger body.
- the lower part of 20 and the upper part of the lower heat exchanger main body 30 may be used.
- FIG. Embodiment 9 of the present invention will be described below.
- FIG. 23 is a first schematic diagram showing an indoor unit 100e of an air conditioner equipped with a turbo fan 250 according to Embodiment 9 of the present invention
- FIG. 24 is a turbo according to Embodiment 9 of the present invention.
- It is a 2nd schematic diagram which shows the indoor unit 100e of the air conditioner which mounts the fan 250.
- the turbo fan 250 is rotated by the motor 230.
- the wind flows along the bell mouth 240 and is blown out in the centrifugal direction by the turbo fan 250.
- the blown wind passes through the first heat exchanger 200 and the second heat exchanger 210 arranged around the turbo fan 250 to exchange heat, and blows along the air path formed by the ceiling material 190. It will be.
- a drain pan 220 is disposed below the second heat exchanger 210 and has a structure for storing condensed water generated in the heat exchanger.
- the air volume distribution of the indoor unit 100e according to the ninth embodiment is as shown in FIG. 24, and the heat exchange performance is relative to the first heat exchanger 200, which is close to the tip of the turbo fan 250 and has a large wind flow velocity.
- a circular pipe 32 having a relatively low heat exchange performance but a high cost performance is used for the second heat exchanger 210 that uses a relatively high flat tube 22 and is far from the tip of the turbofan 250 and has a small wind flow velocity.
- the refrigerant circuit of the 1st heat exchanger 200 and the 2nd heat exchanger 210 may be connected in parallel, or may be connected in series, and the 2nd heat exchanger 210 is liquid single phase at the time of air_conditionaing
- the clearance gap is drawn between the 1st heat exchanger 200 and the 2nd heat exchanger 210 in FIG.23 and FIG.24, the 1st heat exchanger 200 and the 2nd heat exchanger 210 are connected. By making contact, the drainage path of the fins may be secured.
- the configuration of the indoor unit 100e according to the ninth embodiment can also be applied to an outdoor unit.
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Abstract
Description
図1は、本発明の実施の形態1に係る空気調和機の室外機100aの斜視図であり、図2は、本発明の実施の形態1に係る熱交換器10aおよびその周辺の側面模式図であり、図3は、図2のA-A断面図であり、図4は、図2のA-A断面図の別の一例を示す図であり、図5は、図2のB-B断面図である。なお、図1中の矢印は風の流れを示しており、図2中の矢印は暖房運転時における冷媒の流れ、または、風の流れを示している。
空気調和機の室外機100aはトップフロー型であり、室内機(図示せず)との間で冷媒を循環させることにより冷凍サイクルを構成する。なお、この室外機100aは、例えばビル用マルチの室外機などに用いられ、ビルの屋上などに設置される。
一方、下部熱交換器12のディストリビュータ34は、第一配管40から分岐した第二分岐管42と接続されている。また、下部熱交換器12の下部ヘッダー35は、第二配管50から分岐した第二分岐管52と接続されている。
なお、本実施の形態1では、図2に示すように上部熱交換器11と下部熱交換器12との間に隙間が存在するが、実際には上部熱交換器11のフィン表面の水滴を排水するために、図16に示すように上部熱交換器11と下部熱交換器12とを密着させてもよい。また、図17に示すようにフィンは上部熱交換器11と下部熱交換器12との間に切れ目が無く、一体のフィンを共有していてもよい。
暖房運転時、気液二相冷媒は、第一配管40を通過し、第一分岐管41と、第二分岐管42とに分流される。第二分岐管42に流れた気液二相冷媒は、ディストリビュータ34へ流れ、そこで均質化された後、キャピラリーチューブ33を通って下部熱交換器本体30に流入する。下部熱交換器本体30に流入した気液二相冷媒は、そこで吸込口2から吸い込まれた外気と熱交換することでガス化し、下部ヘッダー35へ流出する。
図6に示すディストリビュータ34は、ディストリ主管部61と、ディストリ膨張部62と、ディストリ分流部材63と、を備えており、ディストリ主管部61には面積急縮小部64が設けられている。また、ディストリビュータ34には、キャピラリーチューブ33の一端が接続されている。
暖房運転時における下部熱交換器本体30の上流側に接続されている分配器は、図6に示すディストリビュータ34であるが、図7に示すヘッダー70としてもよい。
図7に示すヘッダー70は、ヘッダー70内に流入した気液二相冷媒を、重力方向に並設された複数の伝熱管である円管32に分配する構造のものである。そして、気液二相冷媒は、ヘッダー70内を鉛直上向きに上昇流で流れ、複数の円管32にヘッダー70内の流れに対して垂直の角度で分流される。
本実施の形態1に係る熱交換器10aは、トップフロー型の室外機100aに搭載されているため、ファン5は熱交換器10aの上方に配置されており、ファン5によって風が熱交換器10aの隙間を通過し、それによって空気と熱交換する。そして、ファン5が上部熱交換器11の上方に配置されているため、室外機100aを流れる風量分布は、図8に示すようにファン5から近い熱交換器10aの上側の方が下側よりも多くなる。つまり、下側に配置された下部熱交換器12よりも上側に配置された上部熱交換器11の方が、風の流れが多くなる。そのため、上部熱交換器11および下部熱交換器12の前面面積を同じとした場合、上部熱交換器11の方が下部熱交換器12よりも、室外機100aの熱交換性能に対する寄与率が高くなる。
なお、本実施の形態1では、図2に示すように円管32にディストリビュータ34、扁平管22にヘッダーを接続しているが、あくまでも一例であり、例えば、図18に示すように円管32と扁平管22のいずれにも同じ分配器を取り付けてもよく、あるいは扁平管22にディストリビュータ34、円管32にヘッダーを接続してもよい。
以下、本発明の実施の形態2について説明するが、実施の形態1と重複するものについては(一部の)説明を省略し、実施の形態1と同じ部分または相当する部分には同じ符号を付す。
図9は、本発明の実施の形態2に係る熱交換器10bおよびその周辺の側面模式図である。なお、図9中の矢印は暖房運転時における冷媒の流れ、または、風の流れを示している。
本実施の形態2に係る空気調和機の室外機100bは、熱交換器10bの上流側に気液分離器80を備えている。気液分離器80は、冷媒の乾き度を調整するために用いられ、気液二相冷媒が流れる第三配管82、気液分離器80で分離されたガス冷媒が流れる第四配管83、および、気液分離器80で分離された液冷媒が流れる第一配管40と接続されている。第四配管83は、バイパス流量弁85と接続されており、バイパス流量弁85は、第五配管84と接続されており、第五配管84は、第二配管50と接続されている。また、第二配管50は、圧縮機81と接続されている。
なお、気液分離器80は、本発明の「乾き度調整装置」に相当するが、あくまで乾き度を調整する装置の一例であり、これに限定されるものではない。その他の乾き度調整装置としては、図15に示すような内部熱交換器110、または他の低温熱源などと熱交換する熱交換器を用いてもよい。
暖房運転時、気液二相冷媒は、第三配管82を通過し、気液分離器80に流入する。気液分離器80に流入した気液二相冷媒は、そこでガス冷媒と液冷媒とに分離される。気液分離器80で分離されたガス冷媒は、第四配管83、バイパス流量弁85、第五配管84、および、第二配管50を通過し、圧縮機81に流入する。一方、気液分離器80で分離された液冷媒は、第一配管40を通過し、第一分岐管41と、第二分岐管42とに分流される。
なお、気液分離器80の配置は、図9に示す位置に限定されず、図10に示すように第一分岐管41中に気液分離器80を配置してもよいし、図11に示すように、第二分岐管42中に気液分離器80を配置してもよい。また、気液分離器80を複数配置すると、第一分岐管41と第二分岐管42とに流れる冷媒流量の制御幅が広がるため、なおよい。
以下、本発明の実施の形態3について説明するが、実施の形態1と重複するものについては(一部の)説明を省略し、実施の形態1と同じ部分または相当する部分には同じ符号を付す。
図12は、本発明の実施の形態3に係る熱交換器10cおよびその周辺の側面模式図である。なお、図12中の矢印は冷房運転時における冷媒の流れ、または、風の流れを示している。
本実施の形態3に係る熱交換器10cは、扁平管22および円管32の少なくとも2種類の伝熱管が中間ヘッダー26を介して直列に接続されている。
熱交換器10cは、ファン5の下方に配置されており、上部熱交換器本体20と、下部熱交換器本体30と、ヘッダー25と、中間ヘッダー26と、ディストリビュータ34と、キャピラリーチューブ33と、を備えている。
上部熱交換器本体20の複数の扁平管22の一端は、ヘッダー25と接続されており、下部熱交換器本体30の複数の円管32の一端は、キャピラリーチューブ33を介してディストリビュータ34と接続されている。また、上部熱交換器本体20の複数の扁平管22の他端および下部熱交換器本体30の複数の円管32の他端は、中間ヘッダー26と接続されている。なお、冷房運転時における上部熱交換器本体20の上流側に接続されている分配器は、ヘッダー25であり、冷房運転時における下部熱交換器本体30の上流側に接続されている分配器は、ディストリビュータ34である。
冷房運転時、高温高圧のガス冷媒が第一配管91を通過し、ヘッダー25へ流れ、そこで各扁平管22に分配され、各扁平管22から上部熱交換器本体20に流入する。上部熱交換器本体20に流入したガス冷媒は、そこで吸込口2から吸い込まれた外気と熱交換して熱を放熱することで気液二相状態となり、中間ヘッダー26へ流れる。中間ヘッダー26で気液二相冷媒は下部熱交換器本体30の円管32へと流入し、そこでさらに周囲の空気と熱交換し、液単相となる。
以下、本発明の実施の形態4について説明するが、実施の形態1と重複するものについては(一部の)説明を省略し、実施の形態1と同じ部分または相当する部分には同じ符号を付す。
図13は、本発明の実施の形態4に係る空気調和機の室外機100dの斜視図であり、図14は、本発明の実施の形態4に係る熱交換器10dの側面模式図である。なお、図14中の矢印は風の流れを示している。
空気調和機の室外機100dはサイドフロー型であり、室内機(図示せず)との間で冷媒を循環させることにより冷凍サイクルを構成する。なお、この室外機100dは、例えばビル用マルチの室外機などに用いられ、ビルの屋上などに設置される。
以下、本発明の実施の形態5について説明するが、実施の形態1と重複するものについては(一部の)説明を省略し、実施の形態1と同じ部分または相当する部分には同じ符号を付す。
図19は、本発明の実施の形態5に係る熱交換器10eおよびその周辺の側面模式図である。なお、図19中の矢印は暖房運転時の冷媒の流れ、または風の流れを示している。
以下、本発明の実施の形態6について説明するが、実施の形態1と重複するものについては(一部の)説明を省略し、実施の形態1と同じ部分または相当する部分には同じ符号を付す。
図20は、本発明の実施の形態6に係る熱交換器10fおよびその周辺の側面模式図である。なお、図20中の矢印は暖房運転時の冷媒の流れ、または風の流れを示している。
このように、ヘッダーを上下に分割しないことで、配管を減らすことができ、または、複数のヘッダーを取り付ける必要が無く、コストパフォーマンスを向上させることができる。
以下、本発明の実施の形態7について説明するが、実施の形態1と重複するものについては(一部の)説明を省略し、実施の形態1と同じ部分または相当する部分には同じ符号を付す。
図21は、本発明の実施の形態7に係る熱交換器10gおよびその周辺の側面模式図である。なお、図21中の矢印は暖房運転時の冷媒の流れ、または風の流れを示している。
以下、本発明の実施の形態8について説明するが、実施の形態1と重複するものについては(一部の)説明を省略し、実施の形態1と同じ部分または相当する部分には同じ符号を付す。
図22は、本発明の実施の形態8に係る熱交換器10hおよびその周辺の側面模式図である。なお、図22中の矢印は暖房運転時の冷媒の流れ、または風の流れを示している。
以下、本発明の実施の形態9について説明する。
図23は、本発明の実施の形態9に係るターボファン250を搭載した空気調和機の室内機100eを示す第一の模式図であり、図24は、本発明の実施の形態9に係るターボファン250を搭載した空気調和機の室内機100eを示す第二の模式図である。なお、図23および図24中の矢印は風の流れを表している。
また、本実施の形態9に係る室内機100eの構成は、室外機にも適用できる。
Claims (18)
- 吸込口および吹出口を有し、外郭を構成するケーシングと、
前記ケーシング内に設けられ、前記吸込口から外気を吸い込み、前記吹出口から外気を排出するファンと、
前記ケーシング内に設けられ、前記ファンが吸い込んだ外気と冷媒とを熱交換する熱交換器と、を備え、
前記熱交換器は、
間隔を空けて並設された複数のフィンと、該フィンを並設方向に貫通し、内部を前記冷媒が流れる複数の扁平管と、で構成される第一熱交換器本体と、
間隔を空けて並設された複数のフィンと、該フィンを並設方向に貫通し、内部を前記冷媒が流れる複数の円管と、で構成される第二熱交換器本体と、を備え、
前記第一熱交換器本体は前記第二熱交換器本体よりも前記ファンの近くに配置されている
空気調和機の室外機。 - 暖房運転時における前記第一熱交換器本体の上流側に、ヘッダーが接続されており、
暖房運転時における前記第二熱交換器本体の上流側に、キャピラリーチューブを介してディストリビュータが接続されている
請求項1に記載の空気調和機の室外機。 - 暖房運転時における前記熱交換器の上流側に、前記冷媒の乾き度を調整する乾き度調整装置が設けられている
請求項1または2に記載の空気調和機の室外機。 - 前記第一熱交換器本体と前記第二熱交換器本体とは正面視して上下方向に配置されており、前記第一熱交換器本体は前記第二熱交換器本体よりも上方に配置されており、前記第一熱交換器本体と前記第二熱交換器本体とは中間ヘッダーで直列に接続されている
請求項1~3のいずれか一項に記載の空気調和機の室外機。 - 前記吹出口を前記ケーシングの上面に有する
トップフロー型である
請求項4に記載の空気調和機の室外機。 - 前記第一熱交換器本体と前記第二熱交換器本体とは正面視して前後方向に配置されている
請求項1~3のいずれか一項に記載の空気調和機の室外機。 - 前記吹出口を前記ケーシングの側面に有する
サイドフロー型である
請求項6に記載の空気調和機の室外機。 - 前記第一熱交換器本体および前記第二熱交換器本体の少なくともいずれか一方に、暖房運転時に前記第一熱交換器本体および前記第二熱交換器本体に流れる冷媒流量を調整する機構を有する
請求項1~6のいずれか一項に記載の空気調和機の室外機。 - 暖房運転時における前記第一熱交換器本体および前記第二熱交換器本体の上流側、および、下流側の少なくともいずれか一方に、前記第一熱交換器本体と前記第二熱交換器本体とにまたがって一つの分配器が接続されている
請求項1~8のいずれか一項に記載の空気調和機の室外機。 - 前記第一熱交換器本体と前記第二熱交換器本体との間に防食シートが挿入されている
請求項1~9のいずれか一項に記載の空気調和機の室外機。 - 前記第一熱交換器本体と前記第二熱交換器本体とは同じ材質で構成されている
請求項1~10のいずれか一項に記載の空気調和機の室外機。 - 前記第一熱交換器本体および前記第二熱交換器本体の少なくともいずれか一方の伝熱管が鉛直向きに配置されている
請求項1~6、8~11のいずれか一項に記載の空気調和機の室外機。 - 吸込口および吹出口を有し、外郭を構成するケーシングと、
前記ケーシング内に設けられ、前記吸込口から外気を吸い込み、前記吹出口から外気を排出するターボファンと、
前記ケーシング内に設けられ、前記ターボファンが吸い込んだ外気と冷媒とを熱交換する熱交換器と、を備え、
前記熱交換器は、
間隔を空けて並設された複数のフィンと、該フィンを並設方向に貫通し、内部を前記冷媒が流れる複数の扁平管と、で構成される第一熱交換器本体と、
間隔を空けて並設された複数のフィンと、該フィンを並設方向に貫通し、内部を前記冷媒が流れる複数の円管と、で構成される第二熱交換器本体と、を備え、
前記第一熱交換器本体は前記第二熱交換器本体よりも前記ターボファンの先端の近くに配置されている
空気調和機の室外機。 - 前記第一熱交換器本体と前記第二熱交換器本体とは直列に接続されている
請求項13に記載の空気調和機の室外機。 - 前記第一熱交換器本体と前記第二熱交換器本体とは並列に接続されている
請求項13に記載の空気調和機の室外機。 - 吸込口および吹出口を有し、外郭を構成するケーシングと、
前記ケーシング内に設けられ、前記吸込口から外気を吸い込み、前記吹出口から外気を排出するターボファンと、
前記ケーシング内に設けられ、前記ターボファンが吸い込んだ外気と冷媒とを熱交換する熱交換器と、を備え、
前記熱交換器は、
間隔を空けて並設された複数のフィンと、該フィンを並設方向に貫通し、内部を前記冷媒が流れる複数の扁平管と、で構成される第一熱交換器本体と、
間隔を空けて並設された複数のフィンと、該フィンを並設方向に貫通し、内部を前記冷媒が流れる複数の円管と、で構成される第二熱交換器本体と、を備え、
前記第一熱交換器本体は前記第二熱交換器本体よりも前記ターボファンの先端の近くに配置されている
空気調和機の室内機。 - 前記第一熱交換器本体と前記第二熱交換器本体とは直列に接続されている
請求項16に記載の空気調和機の室内機。 - 前記第一熱交換器本体と前記第二熱交換器本体とは並列に接続されている
請求項16に記載の空気調和機の室内機。
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EP16859333.3A EP3370000B1 (en) | 2015-10-28 | 2016-04-11 | Outdoor unit for air conditioner |
US15/766,243 US20180292096A1 (en) | 2015-10-28 | 2016-04-11 | Outdoor unit and indoor unit of air-conditioning apparatus |
CN201680061472.5A CN108139089B (zh) | 2015-10-28 | 2016-04-11 | 空气调节机的室外机及室内机 |
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CN108139089B (zh) | 2021-01-01 |
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US20180292096A1 (en) | 2018-10-11 |
JP6545277B2 (ja) | 2019-07-17 |
EP3370000B1 (en) | 2022-07-20 |
JPWO2017073096A1 (ja) | 2018-06-07 |
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