WO2023281731A1 - Heat exchanger and air conditioner - Google Patents
Heat exchanger and air conditioner Download PDFInfo
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- WO2023281731A1 WO2023281731A1 PCT/JP2021/025912 JP2021025912W WO2023281731A1 WO 2023281731 A1 WO2023281731 A1 WO 2023281731A1 JP 2021025912 W JP2021025912 W JP 2021025912W WO 2023281731 A1 WO2023281731 A1 WO 2023281731A1
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- intermediate header
- heat exchanger
- heat transfer
- refrigerant
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- 239000003507 refrigerant Substances 0.000 claims abstract description 177
- 238000012546 transfer Methods 0.000 claims abstract description 121
- 238000005192 partition Methods 0.000 claims abstract description 35
- 230000005484 gravity Effects 0.000 claims abstract description 15
- 238000007664 blowing Methods 0.000 claims description 12
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 claims description 4
- 239000001294 propane Substances 0.000 claims description 2
- 238000007599 discharging Methods 0.000 claims 1
- 238000000638 solvent extraction Methods 0.000 abstract 2
- 239000007788 liquid Substances 0.000 description 65
- 238000009826 distribution Methods 0.000 description 17
- 239000012071 phase Substances 0.000 description 13
- 238000001816 cooling Methods 0.000 description 12
- 230000000694 effects Effects 0.000 description 12
- 238000012986 modification Methods 0.000 description 10
- 230000004048 modification Effects 0.000 description 10
- 238000010586 diagram Methods 0.000 description 8
- 230000014759 maintenance of location Effects 0.000 description 8
- LCGLNKUTAGEVQW-UHFFFAOYSA-N Dimethyl ether Chemical compound COC LCGLNKUTAGEVQW-UHFFFAOYSA-N 0.000 description 4
- 239000002826 coolant Substances 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- 238000011144 upstream manufacturing Methods 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
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- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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Classifications
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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
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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
- F28F9/02—Header boxes; End plates
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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
Definitions
- the present disclosure relates to a heat exchanger having a first heat exchanger and a second heat exchanger and an air conditioner having such a heat exchanger.
- An air conditioner is equipped with a heat exchanger that functions as a condenser as one of the components of the refrigeration cycle circuit.
- the condenser heat-exchanges the incoming gaseous refrigerant with the outside air.
- the refrigerant that has undergone heat exchange flows out of the condenser as a liquid refrigerant through a gas-liquid two-phase state.
- a heat transfer tube group is provided on the windward side and the leeward side as a condenser, and one end of the heat transfer tube group is folded back, and the refrigerant in the gas-liquid two-phase state on the leeward side is flowed to the windward side for heat exchange.
- the heat exchanger which is the condenser, generates a lot of liquid phase in the upper heat transfer tube when the wind speed distribution is formed while it is mounted in the top-blown housing.
- the heat transfer tube outlets are in communication with each other in the header, the liquid refrigerant that has fallen from the upper heat transfer tube in the header cannot be lifted by only the refrigerant in the lowermost heat transfer tube in the gravity direction, and the liquid refrigerant stays, especially in the middle. Performance degrades under load.
- the present disclosure has been made in view of the above circumstances, and aims to provide a heat exchanger and an air conditioner having a first heat exchanger and a second heat exchanger capable of improving heat exchange performance.
- a heat exchanger includes a first intermediate header extending in the direction of gravity, a first heat transfer tube connected to the first intermediate header and performing heat exchange between refrigerant and air, and the first intermediate header.
- a first heat exchanger having a first partition that divides the interior into a first space and a second space arranged below the first space; and arranged side by side on the windward side of the first heat exchanger.
- the intermediate header is provided with a first outlet through which the refrigerant flows out, the first intermediate header forming the second space is provided with a second outlet through which the refrigerant flows out, and the second intermediate header is provided with a second outlet through which the refrigerant flows out.
- the header is connected to the first intermediate header, and has a first inlet through which the refrigerant flows into the third space through the first outlet, and a second outlet through which the refrigerant flows into the third space. and a second inlet.
- the second intermediate header is connected to the first intermediate header, the first inlet through which the liquid-based refrigerant flows into the third space from the first outlet, and the gas-based refrigerant from the second outlet. and a second inlet through which the coolant flows into the third space.
- FIG. 1 is a configuration diagram of an air conditioner according to Embodiment 1.
- FIG. 1 is a perspective perspective view of an outdoor heat exchanger according to Embodiment 1.
- FIG. 3 is a vertical cross-sectional view showing the periphery of the first intermediate header and the second intermediate header of the outdoor heat exchanger according to Embodiment 1.
- FIG. 4 is a vertical cross-sectional view showing refrigerant flows around a first intermediate header and a second intermediate header of a conventional outdoor heat exchanger. 4 is a longitudinal sectional view showing refrigerant flows around the first intermediate header and the second intermediate header of the outdoor heat exchanger according to Embodiment 1.
- FIG. 1 is a perspective perspective view of an outdoor heat exchanger according to Embodiment 1.
- FIG. 3 is a vertical cross-sectional view showing the periphery of the first intermediate header and the second intermediate header of the outdoor heat exchanger according to Embodiment 1.
- FIG. 4 is a vertical cross-sectional view showing refrigerant flows around a
- FIG. 4 is a conceptual schematic diagram showing the flow rate of refrigerant flowing into the first intermediate header and the wind speed distribution of the outdoor heat exchanger according to Embodiment 1; 4 is a performance curve with respect to operating load in the outdoor heat exchanger according to Embodiment 1.
- FIG. FIG. 2 is a schematic diagram showing an example of a refrigerant channel configuration of the outdoor heat exchanger according to Embodiment 1;
- FIG. 8 is a vertical cross-sectional view showing a first intermediate header and a second intermediate header of an outdoor heat exchanger according to Embodiment 2;
- FIG. 11 is a vertical cross-sectional view showing a first intermediate header and a second intermediate header of an outdoor heat exchanger according to Embodiment 3;
- FIG. 11 is a cross-sectional top view of a first intermediate header and a second intermediate header according to Embodiment 4;
- 13 is an enlarged cross-sectional view taken along line AA of FIG. 12;
- FIG. 13 is an enlarged cross-sectional view taken along the line AA of FIG. 12, showing a first modified example of the first intermediate header and the second intermediate header according to Embodiment 4;
- 13 is an enlarged cross-sectional view taken along the line AA of FIG. 12, showing a second modification of the first intermediate header and the second intermediate header according to the fourth embodiment;
- FIG. 11 is a vertical cross-sectional view showing a first intermediate header and a second intermediate header of an outdoor heat exchanger according to Embodiment 3;
- FIG. 11 is a cross-sectional top view of a first intermediate header and a second intermediate header according to Em
- FIG. 1 is a configuration diagram of an air conditioner 200 according to Embodiment 1.
- FIG. 1 The white arrows and black arrows along the refrigerant pipe 18 in FIG. 1 indicate the flow direction of the refrigerant during the cooling operation.
- a white arrow indicates that the refrigerant is in a gaseous state
- a black arrow indicates that the refrigerant is in a liquid state.
- hatched arrows attached near the first intermediate header 1 and the second intermediate header 2 schematically indicate a gas-liquid two-phase state.
- the refrigerant flows when the outdoor heat exchanger 10 functions as a condenser.
- the AF direction indicates the direction of air flow
- the direction of the arrow 90 indicates the direction of gravity.
- the air conditioner 200 includes a compressor 14 that compresses the refrigerant, an outdoor heat exchanger 10 that functions as a condenser, an expansion device 17 that decompresses and expands the refrigerant, and an indoor heat exchanger 16 that functions as an evaporator. ing.
- a compressor 14, an outdoor heat exchanger 10, an expansion device 17, and an indoor heat exchanger 16 are sequentially connected by refrigerant pipes 18 to form a refrigeration cycle circuit.
- the compressor 14 and the outdoor heat exchanger 10 are housed in the outdoor unit 201.
- the housing of the outdoor unit 201 is a top-blowing housing provided with a blower 13 that supplies outdoor air to the outdoor heat exchanger 10 and blows the air upward.
- the indoor heat exchanger 16 and the expansion device 17 are housed in the indoor unit 202 .
- the indoor unit 202 also accommodates an indoor fan (not shown) that supplies the indoor heat exchanger 16 with indoor air, which is the air in the space to be air-conditioned.
- the outdoor heat exchanger 10 has a first heat exchanger 11 and a second heat exchanger 12.
- the first heat exchanger 11 includes a first intermediate header 1 extending in the direction of gravity 90, and a first heat transfer tube 3_1 (see FIG. 3) connected to the first intermediate header 1 and performing heat exchange between refrigerant and air.
- the second heat exchanger 12 is arranged in parallel on the windward side of the first heat exchanger 11 and is connected to the second intermediate header 2 extending in the direction of gravity 90 and the second intermediate header 2 to heat the refrigerant and the air. It has a second heat transfer tube 3_2 to be exchanged.
- FIG. 2 is a perspective perspective view of the outdoor heat exchanger 10 according to Embodiment 1.
- FIG. FIG. 3 is a longitudinal sectional view showing the periphery of the first intermediate header 1 and the second intermediate header 2 of the outdoor heat exchanger 10 according to Embodiment 1. As shown in FIG. This FIG. 3 is a longitudinal sectional view parallel to the extending direction of the first heat transfer tube 3_1 and the second heat transfer tube 3_2.
- the outdoor heat exchanger 10 is mounted in a top-blowing housing 203 of an outdoor unit 201 having a blower 13 that blows air upward.
- the top-blowing housing 203 has an air outlet at the top through which the air sent from the blower 13 is discharged.
- the outdoor heat exchanger 10 has a first heat exchanger 11 and a second heat exchanger 12 provided upstream of the first heat exchanger 11 in the air flow direction AF. .
- the outdoor heat exchanger 10 is composed of at least two rows of first heat exchangers 11 and second heat exchangers 12 .
- the first heat exchanger 11 has a plurality of first heat transfer tubes 3_1.
- the first heat transfer pipes 3_1 extend in the horizontal direction and are arranged at regular intervals in the vertical direction.
- the second heat exchanger 12 has a plurality of second heat transfer tubes 3_2.
- the second heat exchangers 12 extend horizontally and are arranged at regular intervals in the vertical direction.
- Embodiment 1 When the outdoor heat exchanger 10 functions as a condenser, the refrigerant flowing through the first heat transfer tube 3_1 and the second heat transfer tube 3_2 is cooled and condensed by the outdoor air.
- a plurality of fins 4 are connected to a plurality of first heat transfer tubes 3_1 and a plurality of fins 4 are connected to a plurality of second heat transfer tubes 3_2 in order to promote heat exchange between the refrigerant and the outdoor air.
- a plurality of fins (not shown) are connected.
- the first heat exchanger 11 provided downstream of the airflow and the second heat exchanger 12 provided upstream of the airflow are sequentially connected via the first intermediate header 1 and the second intermediate header 2 .
- the first intermediate header 1 has a structure in which the first heat transfer pipe 3_1 is inserted into a pipe having a constant volume.
- the second intermediate header 2 is configured such that a second heat transfer tube 3_2 is inserted into a pipe having a constant volume.
- the first intermediate header 1 is a header that connects at least two of the first heat transfer tubes 3_1 in the same row in the same space.
- the second intermediate header 2 is a header that connects at least two of the second heat transfer tubes 3_2 in the same row in the same space.
- the first intermediate header 1 is partitioned by a first partition 35 into a first space 21 provided on the upper side and a second space 22 provided on the lower side. At least one of the first heat transfer tubes 3_1 connected to the first intermediate header 1 is connected to the first space 21 . At least two first heat transfer tubes 3_1 among the first heat transfer tubes 3_1 connected to the first intermediate header 1 are connected to the second space 22 .
- a pipe wall of the first intermediate header 1 that defines the first space 21 is provided with a first outflow port 31_1 through which the refrigerant flows out.
- a pipe wall of the first intermediate header 1 that defines the second space 22 is provided with a second outlet 32_1 through which the refrigerant flows.
- the second intermediate header 2 is partitioned by a second partition 36 into a third space 23 provided on the upper side and a fourth space 24 provided on the lower side. At least one second heat transfer tube 3_2 is connected to the third space 23 .
- the tube wall of the second intermediate header 2 forming the third space 23 has a first inlet 33_1 and a second inlet 34_1 into which the refrigerant flows.
- the first connection pipe 31 connects the first outlet 31_1 to the first inlet 33_1 and communicates the first space 21 with the third space 23 .
- the second connection pipe 32 connects the second outlet 32_1 to the second inlet 34_1 and communicates the second space 22 with the third space 23 .
- the second outflow port 32_1 is provided above the second partition 36 .
- first outlet 31_1 and the first inlet 33_1 may be directly connected without using the first connection pipe 31.
- second outlet 32_1 and the second inlet 34_1 may be directly connected without using the second connecting pipe 32 .
- the sum of the number of first heat transfer tubes 3_1 connected to the first space 21 and the number of the first heat transfer tubes 3_1 connected to the second space is greater than the number of second heat transfer tubes 3_2. .
- the high-temperature, high-pressure gas refrigerant that has flowed into the indoor heat exchanger 16 is cooled while supplying heat to the indoor air, and flows out of the indoor heat exchanger 16 as a low-temperature liquid refrigerant.
- the liquid refrigerant flowing out of the indoor heat exchanger 16 is decompressed by the expansion device 17 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant, and flows into a distributor (not shown) of the outdoor heat exchanger 10 functioning as an evaporator.
- the low-temperature, low-pressure gas-liquid two-phase refrigerant that has flowed into the distributor of the outdoor heat exchanger 10 is distributed to the second heat transfer tubes 3_2.
- the refrigerant flowing through the second heat transfer pipe 3_2 is heated by the outdoor air to evaporate, and flows through the first connection pipe 31 and the second connection pipe 32 through the first heat transfer pipe 3_1.
- the refrigerant flowing through the first heat transfer tube 3_1 is heated by the outdoor air, evaporates, becomes a low-pressure gas refrigerant, and flows out from the first heat transfer tube 3_1.
- the low-pressure gas refrigerant that has flowed out of the first heat transfer pipe 3_1 flows out of the outdoor heat exchanger 10 after being merged in a union pipe (not shown).
- the low-pressure gas refrigerant that has flowed out of the outdoor heat exchanger 10 is sucked into the compressor 14 after passing through a four-way valve (not shown).
- the low-pressure gas refrigerant sucked into the compressor 14 is again compressed by the compressor 14 into high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant that has flowed into the junction pipe of the outdoor heat exchanger 10 is distributed to the first heat transfer pipes 3_1 of the outdoor heat exchanger 10. Then, the refrigerant flowing through the first heat transfer pipe 3_1 is cooled by the outdoor air, condensed, becomes a low-temperature liquid refrigerant, and flows through the second heat transfer pipe 3_2 via the first connection pipe 31 and the second connection pipe 32. , flows out from the second heat transfer tube 3_2.
- the low-temperature liquid refrigerant that has flowed out of the second heat transfer pipe 3_2 flows out of the outdoor heat exchanger 10 after joining at a distributor (not shown).
- the liquid refrigerant flowing out of the outdoor heat exchanger 10 is depressurized by the expansion device 17 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant, and flows into the indoor heat exchanger 16 functioning as an evaporator.
- the low-temperature, low-pressure gas-liquid two-phase refrigerant that has flowed into the indoor heat exchanger 16 evaporates while absorbing heat from the indoor air, and flows out of the indoor heat exchanger 16 as a low-pressure gas refrigerant.
- the low-pressure gas refrigerant flowing out of the indoor heat exchanger 16 is sucked into the compressor 14 after passing through a four-way valve (not shown), where it is again compressed into a high-temperature and high-pressure gas refrigerant.
- the gas refrigerant exchanges heat with the leeward airflow in the first heat exchanger 11, and changes from a gas state to a gas-liquid state. phase changes.
- the refrigerant changed to the gas-liquid two-phase state flows from the first heat transfer tubes 3_1 of the first heat exchanger 11 into the first space 21 and the second space 22 of the first intermediate header 1 .
- This gas-liquid two-phase refrigerant is mixed inside the first space 21 and the second space 22, respectively, and then flows from the first space 21 and the second space 22 through the first connecting pipe 31 and the second connecting pipe 32, respectively. It flows into the third space 23 of the second intermediate header 2 of the second heat exchanger 12 .
- the gas-liquid two-phase refrigerant flowing from the first connecting pipe 31 and the second connecting pipe 32 is mixed and divided into the heat transfer tubes 3 of the second heat exchanger 12 to exchange heat with the upwind airflow. .
- FIG. 4 is a longitudinal sectional view showing refrigerant flows around the first intermediate header 1 and the second intermediate header 2 of the conventional outdoor heat exchanger 10.
- the first heat transfer tubes 3_1 of the first heat exchanger 11 on the downstream side of the airflow are arranged with a specified interval in the vertical direction and connected to the first intermediate header 1.
- the second heat transfer tubes 3_2 of the second heat exchanger 12 on the upstream side of the airflow are arranged at regular intervals in the vertical direction and connected to the second intermediate header 2 .
- the first intermediate header 1 and the second intermediate header 2 are connected by a first connecting pipe 31 .
- the gaseous refrigerant that has flowed into the first heat exchanger 11 exchanges heat with the downstream air stream, enters a two-phase state, and flows into the first intermediate header 1 .
- the airflow passing through the first heat exchanger 11 is increased in velocity between the first heat transfer tube 3_1 and the fins 4 provided on the upper side by the blower 13 provided in the top-blowing housing that blows air upward.
- the velocity of the wind flowing between the first heat transfer tube 3_1 and the fins 4 provided on the lower side becomes smaller.
- the liquid-based refrigerant 102 having a larger mass flow rate ratio of the liquid refrigerant than the outlet on the lower side flows into the inside of the first intermediate header 1 .
- the gas-based refrigerant 103 having a larger mass flow rate ratio of the gas refrigerant than the outlet on the upper side flows into the inside of the first intermediate header 1 .
- the driving force for causing the refrigerant to flow upward is the inertial force of the refrigerant flowing out from the first heat transfer tube 3_1 downstream of the lower portion of the first space 21 and upstream of the refrigerant flow.
- the inertial force of the refrigerant is small, and the liquid refrigerant that has fallen is not lifted upward, causing a liquid stagnation 104 .
- the flow rate of the refrigerant is small, and the inertial force of the refrigerant in the horizontal direction in the first heat transfer tube 3_1 is small.
- a liquid backflow 105 occurs.
- FIG. 5 is a longitudinal sectional view showing refrigerant flows around the first intermediate header 1 and the second intermediate header of the outdoor heat exchanger 10 according to the first embodiment.
- the first intermediate header 1 is partitioned into the first space 21 and the second space 22 by the first partition 35 .
- the first heat transfer tubes 3_1 connected to the first intermediate header 1 at least one first heat transfer tube 3_1 is connected to the first space 21 from above.
- At least two or more first heat transfer tubes 3_1 provided on the lower side are connected to the second space 22 .
- the liquid-based refrigerant 102 flowing out from the upper first heat transfer tubes 3_1 does not enter the second space 22 inside the first intermediate header 1 .
- the liquid-based refrigerant 102 flows into the third space 23 of the second intermediate header 2 via the first connecting pipe 31 .
- the liquid stagnation 104 inside the second space 22 is reduced, a region for heat exchange is secured, and the heat exchange performance of the condenser is improved.
- the flow rate of refrigerant flowing through the second connection pipe 32 is the sum of the flow rates of refrigerant flowing from the plurality of first heat transfer tubes 3_1 connected to the second space 22 .
- the flow path diameter of the second connection pipe 32 can be designed without depending on the flow path diameter of the first heat transfer tube 3_1, backflow 105 of the liquid from the third space 23 to the second space 22 can be suppressed (see FIG. 4).
- FIG. 6 is a conceptual schematic diagram showing the flow rate of refrigerant flowing into the first intermediate header 1 of the conventional outdoor heat exchanger 10 and the wind velocity distribution.
- FIG. 6 is a white bar graph showing the flow rate of the refrigerant flowing through the first heat transfer tube 3_1 connected to the conventional first intermediate header 1 for each height of the heat transfer tube. It is a figure which shows distribution with a solid line.
- FIG. 7 is a conceptual schematic diagram showing the flow rate of refrigerant flowing into the first intermediate header 1 and the wind speed distribution of the outdoor heat exchanger 10 according to the first embodiment.
- FIG. 7 shows the flow rate of the refrigerant flowing through the first heat transfer tube 3_1 connected to the first intermediate header 1 according to Embodiment 1 by a black bar graph for each height of the heat transfer tube. It is a figure which shows the wind speed distribution of a direction with a solid line.
- the gas-liquid two-phase refrigerant has the characteristic that when the gas refrigerant is large, the volume flow rate of the refrigerant is large and the refrigerant pressure loss is large, and when the liquid refrigerant is large, the refrigerant volume flow rate is small and the refrigerant pressure loss is small.
- the refrigerants at the outlets of the first heat transfer tubes 3_1 are mixed at the outlet of the first intermediate header 1 and mixed through the first connecting pipe 31 to the second intermediate header 2 .
- the refrigerant flow rate difference between the first heat transfer tubes 3_1 is small as shown in FIG.
- the wind speed is high on the upper side where the air flow path length is short, and the wind speed is low on the lower side where the air flow path length is long. As a result, the difference between the wind velocity distribution and the refrigerant flow rate distribution becomes large, which is a factor in the deterioration of performance.
- the first space 21, which is the outlet of the upper first heat transfer tube 3_1, and the second space 22, which is the outlet of the lower first heat transfer tube 3_1, are not communicated with each other. partitioned. Therefore, as shown in FIG. 7, the flow rate of the refrigerant in the first heat transfer tube 3_1 connected to the first space 21 into which the liquid-based refrigerant 102 flows is the first It increases with respect to the refrigerant flow rate of the heat transfer tube 3_1. Therefore, the divergence between the wind speed distribution and the refrigerant flow rate distribution is reduced, and the heat exchange performance is improved.
- FIG. 8 is a performance curve for the operating load of the outdoor heat exchanger 10 according to Embodiment 1.
- FIG. The horizontal axis indicates the ratio of cooling capacity to the maximum cooling capacity, and the vertical axis indicates the ratio of each operating capacity to the theoretical maximum performance of the outdoor heat exchanger 10 .
- the solid line indicates the characteristic curve of the first embodiment, and the dashed line indicates the conventional characteristic curve.
- liquid stagnation 104 occurred in the first intermediate header 1, especially during low-load operation, resulting in performance degradation.
- the performance of the outdoor heat exchanger 10 is improved due to the effect of suppressing liquid retention, particularly during low-load operation.
- the performance of the outdoor heat exchanger 10 from low load to high load operation is improved, and the energy saving performance of the air conditioner 200 is improved. improves.
- the outdoor unit 201 is not a top-blowing housing, by mounting the outdoor heat exchanger 10, the liquid refrigerant falling to the lower part of the second space 22 of the first intermediate header 1 is reduced, so the performance is improved. It works. Furthermore, when the outdoor heat exchanger 10 is mounted in the top-blowing housing, a large amount of liquid refrigerant is formed on the upper side of gravity during cooling operation. For this reason, compared with the conventional configuration, the amount of liquid refrigerant falling into the lower portion of the second space 22 of the first intermediate header 1 is reduced for the same capacity, and the performance improvement effect is large.
- the air conditioner 200 described above is an example of the air conditioner 200 according to the first embodiment.
- the outdoor heat exchanger 10 may be installed in the indoor unit 202 of the air conditioner 200.
- the number of divided spaces in the first intermediate header 1 is three or more, there is no problem with the effect, and it is a design item selected from the improvement effect and the manufacturing cost.
- the first space 21 and the second space 22 are partitioned by the first partition 35, but the effect can be obtained even if the first space 21 and the second space 22 are formed by separate headers. Absent.
- the number of outdoor units 201 and indoor units 202 is not limited to one, and a plurality of them may be provided in the air conditioner 200 .
- the type of refrigerant circulating in the refrigeration cycle circuit of the air conditioner 200 is not particularly limited.
- the refrigerant includes R32, R410A, or at least refrigerants having a lower gas density relative to R32 refrigerants, including olefinic refrigerants, propane, or DME (dimethyl ether). With such a refrigerant, the deviation between the wind speed distribution and the refrigerant distribution due to the pressure loss of the gas refrigerant can be suppressed, so the performance improvement effect is greater.
- the first heat transfer tube 3_1 and the second heat transfer tube 3_2 of the outdoor heat exchanger 10 are not limited to circular heat transfer tubes, and the cross section orthogonal to the axial direction of the first heat transfer tube 3_1 and the second heat transfer tube 3_2 Various heat transfer tubes such as a flat heat transfer tube whose long axis is along the air flow direction can be used.
- a flat heat transfer tube whose long axis is along the air flow direction can be used.
- the flow path diameter in the vertical direction of the header is larger than the length of the long axis of the flat tubes, so the cross-sectional area of the flow path is increased.
- the flow velocity in the second space 22 is reduced, and the amount of liquid refrigerant stagnation 104 is increased.
- the sum of the number of first heat transfer tubes 3_1 connected to the first space 21 and the number of first heat transfer tubes 3_1 connected to the second space 22 is the third
- the number of heat transfer tubes connected to the space may be greater than or equal to that of the heat transfer tubes.
- FIG. 9 is a schematic diagram showing an example of the refrigerant channel configuration of the outdoor heat exchanger 10 according to Embodiment 1.
- the outdoor heat exchanger 10 is composed of a parallel flow condenser in which two or more rows of headers are provided at both ends of heat transfer tubes.
- the sum of the number of first heat transfer tubes 3_1 connected to the first space 21 and the number of first heat transfer tubes 3_1 connected to the second space 22 is greater than the number of second heat transfer tubes 3_2 connected to the third space 23. .
- the liquid refrigerant in the lower portion of the first intermediate header 1 needs to flow upward, so the application of this configuration has a large improvement effect.
- the first connecting pipe 31 connecting the first space 21 and the third space 23 has an average height of the first heat transfer pipe 3_1 connected to the first space 21. It is provided below the height.
- the average height is the average height of all the first heat transfer tubes 3_1 connected to the first space 21 in the vertical direction.
- the outdoor heat exchanger 10 of Embodiment 1 it is possible to suppress liquid retention under the gravity of the first heat exchanger 11 and the first intermediate header 1 .
- the first intermediate header 1 does not have the first partition 35, as in the conventional art, the liquid refrigerant that has fallen from the upper side of the first intermediate header 1 due to gravity cannot be lifted up only by the refrigerant in the lowermost heat transfer tube in the direction of gravity. Liquid stays, especially at intermediate loads.
- the first intermediate header 1 is provided with the first partition 35 .
- the liquid-based refrigerant in the first space 21 and the gas-based refrigerant in the second space 22 are joined in the third space 23 of the second intermediate header 2 by the first connection pipe 31 and the second connection pipe 32, respectively.
- Embodiment 2 items that are not particularly described are the same as those in Embodiment 1, and the same functions and configurations are described using the same reference numerals.
- FIG. 10 is a longitudinal sectional view showing the first intermediate header 1 and the second intermediate header 2 of the outdoor heat exchanger 10 according to Embodiment 2.
- FIG. 10 is a longitudinal sectional view showing the first intermediate header 1 and the second intermediate header 2 of the outdoor heat exchanger 10 according to Embodiment 2.
- the third space 23 is located below the third space 23 and connected to at least one second heat transfer tube 3_2 separated from the third space 23.
- 4 spaces 24 are provided in the second intermediate header 2 .
- a first partition 35 that partitions the first space 21 and the second space 22 is provided above a second partition 36 that partitions the third space 23 and the fourth space 24 .
- the first partition 35 and the second partition 36 are plate members.
- the outdoor heat exchanger 10 By configuring the outdoor heat exchanger 10 in this way, the head difference between the first partition 35 and the second partition 36 causes liquid refrigerant to flow from the first space 21 to the third space 23 via the first connection pipe 31 . of the liquid is promoted to suppress the retention of the liquid inside the first space 21 . Thereby, the cooling performance of the air conditioner 200 is improved.
- Embodiment 3 In Embodiment 3, items that are not particularly described are the same as those in Embodiments 1 and 2, and the same functions and configurations are described using the same reference numerals.
- FIG. 11 is a longitudinal sectional view showing the first intermediate header 1 and the second intermediate header 2 of the outdoor heat exchanger 10 according to Embodiment 3.
- FIG. Embodiment 3 is different from Embodiment 2 in that the second outlet 32_1 in the second space 22 of the first intermediate header 1 of the second connection pipe 32 is the third space separating the third space 23 and the fourth space 24. It is a configuration provided above the second partition 36 .
- the second connection pipe 32 connects the second space 22 of the first intermediate header 1 and the third space 23 of the second intermediate header 2 .
- the head difference between the second outlet 32_1 in the second space 22 and the second partition 36 causes the liquid refrigerant to flow back 105 (see FIG. 4) into the second space 22. ) is suppressed, and the cooling performance of the air conditioner 200 is improved.
- Embodiment 4 In Embodiment 4, items that are not particularly described are the same as those in Embodiment 3, and the same functions and configurations are described using the same reference numerals.
- FIG. 12 is a cross-sectional top view of the first intermediate header 1 and the second intermediate header 2 according to Embodiment 4.
- FIG. 13 is an enlarged cross-sectional view taken along the line AA of FIG. 12.
- 71 indicates the central axis of the first intermediate header 1 in the extending direction
- 72 indicates the central axis of the second intermediate header 2 in the extending direction
- 73 indicates the central axis of the connecting pipe.
- Two dashed lines extending from the central axis 72 of the second intermediate header 2 in the extending direction indicate the range in which the pipe wall 38 of the first intermediate header 1 can be seen.
- 111 indicates the refrigerant flow from the first space 21 to the third space 23
- 112 indicates the refrigerant flow from the second space 22 to the third space 23 .
- the first outflow port 31_1 is the first outlet in the range in which the first intermediate header 1 can be seen when viewed from the central axis 72 in the extending direction of the first intermediate header and the extending direction of the second intermediate header 2 . It is provided on the tube wall 38 of the intermediate header 1 . That is, the first outflow port 31_1 is provided in the pipe wall 38 of the first intermediate header 1 on the second intermediate header 2 side.
- the path length of the first connecting pipe 31 from the first space 21 to the third space 23 is shortened, and the flow of the refrigerant flow 111 is promoted. Retention of the liquid refrigerant in the first space 21 is suppressed. Further, the route length of the second connection pipe 32 from the second space 22 to the third space 23 is shortened, and the coolant is transported to the third space 23 without greatly reducing the inertia force of the coolant flow 112 . Therefore, a large amount of the gas-based refrigerant is supplied upward due to gravity in the third space 23, and the refrigerant can be distributed according to the wind speed distribution of the top-blowing housing.
- FIG. 14 is an enlarged sectional view taken along the line AA of FIG. 12, showing a first modification of the first intermediate header 1 and the second intermediate header 2 according to the fourth embodiment.
- the height of the first outlet 31_1 to the third space 23 in the first space 21 of the first intermediate header 1 is is the same as or higher than the height position of the first inlet 33_1 from the first space 21 in .
- the flow of the refrigerant flow 111 is promoted due to the head difference between the height position of the first outlet 31_1 and the first inlet 33_1, and the first space 21 Stagnation of the liquid refrigerant inside is suppressed. Thereby, the performance of the condenser is improved, and the cooling performance of the air conditioner 200 is improved.
- the height position of the second outflow port 32_1 to the third space 23 in the second space 22 of the first intermediate header 1 is the second It is a higher configuration than the height position of the partition 36 .
- FIG. 15 is an enlarged sectional view taken along line AA of FIG. 12, showing a second modification of the first intermediate header 1 and the second intermediate header 2 according to the fourth embodiment.
- the first outlet 31_1 and the second outlet 32_1 are partitioned by the first partition 35 . That is, the first partition 35 is provided within the height range of one opening provided in the tube wall of the first intermediate header 1, and the upper side of the first partition 35 of this opening is the first outlet 31_1. , the lower side is the second outflow port 32_1.
- the first connection pipe 31 and the second connection pipe 32 may be integrally configured with one pipe. good.
- the performance of the condenser is improved, and the cooling performance of the air conditioner 200 is improved.
- the improvement effect is large in low-load operation where the refrigerant flow velocity becomes small.
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Abstract
Description
<構成>
図1は、実施の形態1に係る空気調和装置200の構成図である。なお、図1の冷媒配管18に沿って付された白抜き矢印及び黒矢印は、冷房運転時の冷媒の流れ方向を示している。白抜き矢印は、冷媒がガス状態であること、黒矢印は冷媒が液状態であることを示している。また、第1中間ヘッダ1及び第2中間ヘッダ2近傍に付された網掛け矢印は気液二相状態であることを模式的に示している。室外熱交換器10が凝縮器として機能する際の冷媒の流れを示している。図1において、AFの方向は、空気の流れ方向を示し、90の矢印の方向は重力方向を示す。
<Configuration>
FIG. 1 is a configuration diagram of an
続いて、空気調和装置200の動作について説明する。
<暖房運転>
まず、空気調和装置200の暖房運転時の動作について説明する。圧縮機14で圧縮された高温高圧のガス冷媒は、図示せぬ四方弁を通って、凝縮器として機能する室内熱交換器16に流入する。 <Action>
Next, the operation of the
<Heating operation>
First, the operation of the
次に、空気調和装置200の冷房運転時の動作について説明する。
圧縮機14で圧縮された高温高圧のガス冷媒は、図示せぬ四方弁を通って、凝縮器として機能する室外熱交換器10の図示せぬ合流管に流入する。 <Cooling operation>
Next, the operation of the
The high-temperature, high-pressure gas refrigerant compressed by the
続いて、実施の形態1に係る室外熱交換器10の第1中間ヘッダ1及び第2中間ヘッダ2の効果について説明する。まず始めに、図4を用いて、実施の形態1に係る室外熱交換器10の比較対象である、従来の室外熱交換器10について説明する。 <effect>
Next, effects of the first
実施の形態2において、特に記述しない項目については実施の形態1と同様とし、同一の機能及び構成については同一の符号を用いて述べることとする。
In
実施の形態3において、特に記述しない項目については実施の形態1~実施の形態2のいずれかと同様とし、同一の機能及び構成については同一の符号を用いて述べることとする。
In
実施の形態4において、特に記述しない項目については実施の形態3と同様とし、同一の機能及び構成については同一の符号を用いて述べることとする。
In
Claims (12)
- 重力方向に延びた第1中間ヘッダと、
前記第1中間ヘッダに接続され、冷媒と空気との熱交換を行う第1伝熱管と、
前記第1中間ヘッダの内部を、第1空間と、前記第1空間より下側に配置された第2空間とに仕切る第1仕切りと
を有する第1熱交換器と、
前記第1熱交換器の風上に並設され、前記重力方向に延びた第2中間ヘッダと、
前記第2中間ヘッダに接続され、前記冷媒と前記空気との熱交換を行う第2伝熱管と、
前記第2中間ヘッダの内部を、第3空間と、前記第3空間より下側に配置された第4空間とに仕切る第2仕切りと
を有する第2熱交換器と
を具備し、
前記第1伝熱管は複数であり、前記複数の前記第1伝熱管は、前記第1空間に接続される前記第1伝熱管と、前記第2空間に接続される前記第1伝熱管とを有し、
前記第1空間を構成する前記第1中間ヘッダには、前記冷媒が流出する第1流出口が設けられ、
前記第2空間を構成する前記第1中間ヘッダには、前記冷媒が流出する第2流出口が設けられ、
前記第2中間ヘッダは、前記第1中間ヘッダと接続され、前記第1流出口から前記冷媒が前記第3空間に流入する第1流入口と、前記第2流出口から前記冷媒が前記第3空間に流入する第2流入口とを具備する
熱交換器。 a first intermediate header extending in the direction of gravity;
a first heat transfer tube connected to the first intermediate header and performing heat exchange between refrigerant and air;
a first heat exchanger having a first partition that divides the inside of the first intermediate header into a first space and a second space arranged below the first space;
a second intermediate header arranged in parallel on the windward side of the first heat exchanger and extending in the direction of gravity;
a second heat transfer tube connected to the second intermediate header and performing heat exchange between the refrigerant and the air;
a second heat exchanger having a second partition that divides the inside of the second intermediate header into a third space and a fourth space arranged below the third space;
There are a plurality of the first heat transfer tubes, and the plurality of the first heat transfer tubes includes the first heat transfer tube connected to the first space and the first heat transfer tube connected to the second space. have
The first intermediate header forming the first space is provided with a first outlet through which the refrigerant flows,
The first intermediate header forming the second space is provided with a second outlet through which the refrigerant flows,
The second intermediate header is connected to the first intermediate header, and has a first inlet through which the refrigerant flows into the third space from the first outlet, and a first outlet through which the refrigerant flows into the third space from the second outlet. and a second inlet that flows into the space. - 前記第1伝熱管及び前記第2伝熱管は、前記第1伝熱管及び前記第2伝熱管の軸方向に直交する断面の長軸が気流方向に沿う扁平伝熱管である
請求項1に記載の熱交換器。 2. The first heat transfer tube and the second heat transfer tube according to claim 1, wherein the flat heat transfer tube has a long axis of a cross section orthogonal to an axial direction of the first heat transfer tube and the second heat transfer tube along an airflow direction. Heat exchanger. - 前記第2伝熱管は、前記第3空間に接続され、
前記第1空間に接続される前記第1伝熱管の数と、前記第2空間に接続される前記第1伝熱管の数との和が、前記第2伝熱管の数よりも多い
請求項1又は2に記載の熱交換器。 The second heat transfer tube is connected to the third space,
2. The sum of the number of said first heat transfer tubes connected to said first space and the number of said first heat transfer tubes connected to said second space is greater than the number of said second heat transfer tubes. Or the heat exchanger according to 2. - 前記第1流出口と、前記第1流入口とを接続する第1接続配管を具備し、
前記第1接続配管は、前記第1空間に接続される前記第1伝熱管の平均高さよりも下方に設けられる
請求項1~3のいずれか1項に記載の熱交換器。 A first connection pipe that connects the first outlet and the first inlet,
The heat exchanger according to any one of claims 1 to 3, wherein the first connection pipe is provided below an average height of the first heat transfer pipes connected to the first space. - 前記第1仕切りは、前記第2仕切りよりも上側に設けられている
請求項1~4のいずれか1項に記載の熱交換器。 The heat exchanger according to any one of claims 1 to 4, wherein the first partition is provided above the second partition. - 前記第2流出口は、前記第2仕切りよりも上側に設けられている
請求項1~5のいずれか1項に記載の熱交換器。 The heat exchanger according to any one of claims 1 to 5, wherein the second outlet is provided above the second partition. - 前記第2流出口と、前記第2流入口とを接続する第2接続配管を具備する
請求項4に記載の熱交換器。 5. The heat exchanger according to claim 4, further comprising a second connecting pipe connecting said second outlet and said second inlet. - 前記第1流出口は、前記第1中間ヘッダの延伸方向に見て、前記第2中間ヘッダの中心軸から前記第1中間ヘッダが見える範囲の前記第1中間ヘッダの菅壁に設けられる
請求項1~7のいずれか1項に記載の熱交換器。 3. The first outflow port is provided in the tube wall of the first intermediate header within a range where the first intermediate header can be seen from the central axis of the second intermediate header when viewed in the extending direction of the first intermediate header. The heat exchanger according to any one of 1 to 7. - 前記第1流出口は、前記第1流入口よりも高い位置に設けられる
請求項1~8のいずれか1項に記載の熱交換器。 The heat exchanger according to any one of claims 1 to 8, wherein the first outlet is provided at a position higher than the first inlet. - 前記冷媒はR32、R410A又は少なくともオレフィン系冷媒、プロパン、DMEを含むR32冷媒に対してガス密度の小さい冷媒を含む、
請求項1~9のいずれか1項に記載の熱交換器。 The refrigerant comprises R32, R410A, or at least a refrigerant having a lower gas density than R32 refrigerants, including olefinic refrigerants, propane, and DME.
A heat exchanger according to any one of claims 1-9. - 請求項1~10のいずれか1項に記載の熱交換器を備えた空気調和装置。 An air conditioner comprising the heat exchanger according to any one of claims 1 to 10.
- 前記空気調和装置は、
空気を上側へ送風する送風機と、
前記送風機に送風された空気を流出するための吹出口を備える上吹き筐体と
を備え、
前記熱交換器は前記筐体に搭載される
請求項11に記載の空気調和装置。 The air conditioner is
a blower for blowing air upward;
a top-blowing housing including an outlet for discharging the air blown by the blower,
The air conditioner according to claim 11, wherein the heat exchanger is mounted on the housing.
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Citations (4)
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WO2017149950A1 (en) * | 2016-02-29 | 2017-09-08 | 三菱重工サーマルシステムズ株式会社 | Heat exchanger and air conditioner |
JP2018162934A (en) * | 2017-03-27 | 2018-10-18 | ダイキン工業株式会社 | Heat exchanger unit |
WO2019130394A1 (en) * | 2017-12-25 | 2019-07-04 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
JP2019132537A (en) * | 2018-01-31 | 2019-08-08 | ダイキン工業株式会社 | Heat exchanger, or refrigeration device having heat exchanger |
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WO2017149950A1 (en) * | 2016-02-29 | 2017-09-08 | 三菱重工サーマルシステムズ株式会社 | Heat exchanger and air conditioner |
JP2018162934A (en) * | 2017-03-27 | 2018-10-18 | ダイキン工業株式会社 | Heat exchanger unit |
WO2019130394A1 (en) * | 2017-12-25 | 2019-07-04 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
JP2019132537A (en) * | 2018-01-31 | 2019-08-08 | ダイキン工業株式会社 | Heat exchanger, or refrigeration device having heat exchanger |
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