WO2013183508A1 - パラレルフロー型熱交換器及びそれを搭載した空気調和機 - Google Patents
パラレルフロー型熱交換器及びそれを搭載した空気調和機 Download PDFInfo
- Publication number
- WO2013183508A1 WO2013183508A1 PCT/JP2013/064847 JP2013064847W WO2013183508A1 WO 2013183508 A1 WO2013183508 A1 WO 2013183508A1 JP 2013064847 W JP2013064847 W JP 2013064847W WO 2013183508 A1 WO2013183508 A1 WO 2013183508A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat exchanger
- water
- receiving tank
- water receiving
- refrigerant
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D3/00—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 flows in a continuous film, or trickles freely, over the conduits
- F28D3/02—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 flows in a continuous film, or trickles freely, over the conduits with tubular conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F25/00—Component parts of trickle coolers
- F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid
- F28F25/04—Distributing or accumulator troughs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/22—Means for preventing condensation or evacuating condensate
- F24F13/222—Means for preventing condensation or evacuating condensate for evacuating condensate
- F24F2013/225—Means for preventing condensation or evacuating condensate for evacuating condensate by evaporating the condensate in the cooling medium, e.g. in air flow from the condenser
-
- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0084—Condensers
Definitions
- the present invention relates to a parallel flow heat exchanger and an air conditioner equipped with the heat exchanger.
- a parallel flow type heat in which a plurality of flat tubes are arranged between a plurality of header pipes so that a plurality of refrigerant passages in the flat tubes communicate with the inside of the header pipe, and fins such as corrugated fins are arranged between the flat tubes.
- Exchangers are widely used in outdoor units of car air conditioners and building air conditioners.
- Patent Document 1 describes a side flow parallel flow heat exchanger including two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes.
- corrugated fins are arranged between the flat tubes.
- drain water generated in the indoor unit is stored in the bucket of the outdoor unit.
- the bucket is changed from the storage posture to the discharge posture, and once the drain water is received by the housing, it is allowed to flow downward, and the outdoor unit-side heat exchanger takes air into the atmosphere. By dripping drain water along the surface, the operation energy is saved during cooling.
- JP 2010-249388 A Japanese Patent No. 3861219
- the present invention provides a side flow parallel flow heat exchanger having a structure in which water can be easily applied to the surface, and by taking advantage of the structure, drain water generated in the indoor unit is removed from the outdoor unit side. It is intended to improve the condensation performance of the heat exchanger.
- a parallel flow heat exchanger has the following configuration: a parallel flow heat exchange of a side flow system including two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes.
- a water receiving tank parallel to the flat tube is formed in the upper part, and water dripped from a water introduction hole formed in the water receiving tank flows down along the surface of the heat exchanger.
- a plurality of the water introduction holes are arranged at predetermined intervals along the length direction of the water receiving tank.
- the water receiving tank has a length that covers the entire length of the flat tube.
- a side sheet attached to the corrugated fin located at the top of the corrugated fins attached to the flat tube is formed as a water receiving tank.
- An air conditioner according to the present invention has the following configuration: an outdoor unit and an indoor unit, the parallel flow type heat exchanger having the above structure is mounted on the outdoor unit, and the water receiving tank of the parallel flow type heat exchanger has the above structure. Drain water generated in the indoor unit is guided.
- water can be poured evenly on the surface of the parallel flow heat exchanger by pouring water into the upper water receiving tank.
- the parallel flow heat exchanger is mounted on an outdoor unit of an air conditioner, and drain water generated in the indoor unit is guided to the water receiving tank so that the parallel flow heat is used as a condenser during cooling operation.
- the condensation performance of the exchanger can be improved.
- FIG. 5 is a sectional view taken along line VV in FIG. 4. It is an expanded sectional view of a part of FIG. It is a top view which shows 1st Embodiment of the water conveyance hole formed in a water receiving tank.
- FIG. 5 It is a top view which shows 14th Embodiment of the water conveyance hole formed in a water receiving tank. It is an expanded sectional view similar to FIG. 5, and shows the deformation
- Fig. 4 shows the basic structure of a side flow parallel flow heat exchanger 50.
- the upper side of the paper is the upper side of the heat exchanger
- the lower side of the paper is the lower side of the heat exchanger.
- the parallel flow heat exchanger 50 includes two vertical header pipes 51 and 52 and a plurality of horizontal flat tubes 53 disposed therebetween.
- the header pipes 51 and 52 are arranged in parallel at intervals in the horizontal direction, and the flat tubes 53 are arranged at a predetermined pitch in the vertical direction. Since the heat exchanger 50 is installed at various angles according to design requirements at the stage of actually mounting on equipment, the “vertical direction” and “horizontal direction” in this specification should not be interpreted strictly. It should be understood as a mere measure of direction.
- the flat tube 53 is an elongated molded product obtained by extruding a metal, and as shown in FIG. 5, a refrigerant passage 54 through which a refrigerant flows is formed. Since the flat tube 53 is arranged so that the extrusion molding direction, which is the longitudinal direction, is horizontal, the refrigerant flow direction of the refrigerant passage 54 is also horizontal. A plurality of refrigerant passages 44 having the same cross-sectional shape and cross-sectional area are arranged in the left-right direction in FIG. 5, and therefore the vertical cross-section of the flat tube 53 has a harmonica shape. Each refrigerant passage 54 communicates with the header pipes 51 and 52.
- Corrugated fins 55 are attached to the flat surface of the flat tube 53. Of the corrugated fins 55 arranged vertically, side plates 56 are arranged outside the uppermost and lowermost ones. In addition, the code
- the header pipes 51 and 52, the flat tubes 53, the corrugated fins 55, and the side plates 56 and 56a are all made of a metal having good heat conductivity such as aluminum.
- the flat tubes 53 are flat with respect to the header pipes 51 and 52.
- the side plates 56 and 56a are fixed to the corrugated fin 55 by brazing or welding to the tube 53, respectively.
- the inside of the header pipe 51 is partitioned into two sections S1 and S2 by a single partition P1.
- the partition part P1 divides the plurality of flat tubes 53 into a plurality of flat tube groups.
- a flat tube group consisting of 12 out of a total of 24 flat tubes 53 is connected to the section S1, and a flat tube group consisting of 12 flat tubes 53 is connected to the section S2.
- the interior of the header pipe 52 is partitioned into three sections S3, S4, and S5 by two partition portions P2 and P3.
- the partition parts P2 and P3 divide the plurality of flat tubes 53 into a plurality of flat tube groups.
- a flat tube group consisting of 4 of the 24 flat tubes 53 in total is connected to the section S3, a flat tube group consisting of 15 flat tubes 53 is connected to the section S4, and 5 pieces are connected to the section S5.
- a flat tube group consisting of the flat tubes 53 is connected.
- the total number of the flat tubes 53 described above, the number of partition portions inside each header pipe and the number of partitions partitioned thereby, and the number of flat tubes 53 for each flat tube group divided by the partition portions are merely examples. Yes, it does not limit the invention.
- a refrigerant access pipe 57 is connected to the compartment S3.
- a refrigerant inlet / outlet pipe 58 is connected to the section S5.
- the function of the heat exchanger 50 is as follows.
- the refrigerant is supplied to the compartment S3 through the refrigerant inlet / outlet pipe 57.
- the refrigerant that has entered the compartment S3 travels through the four flat tubes 53 connecting the compartment S3 and the compartment S1 to the compartment S1.
- the flat tube group formed by the four flat tubes 53 constitutes the refrigerant path A.
- the refrigerant path A is symbolized by a block arrow. Other refrigerant paths are also symbolized by block arrows.
- the refrigerant that has entered the compartment S1 turns back and passes through the eight flat tubes 53 that connect the compartment S1 and the compartment S4 to the compartment S4.
- the flat tube group formed by the eight flat tubes 53 constitutes the refrigerant path B.
- the refrigerant that has entered the compartment S4 is turned back and passes through the seven flat tubes 53 connecting the compartment S4 and the compartment S2 toward the compartment S2.
- the flat tube group formed by the seven flat tubes 53 constitutes the refrigerant path C.
- the refrigerant that has entered the compartment S2 is turned back there, and travels to the compartment S3 through the five flat tubes 53 that connect the compartment S2 and the compartment S5.
- the flat tube group formed by the five flat tubes 53 constitutes the refrigerant path D.
- the refrigerant entering the compartment S5 flows out from the refrigerant inlet / outlet pipe 58.
- the refrigerant is supplied to the section S5 through the refrigerant inlet / outlet pipe 58. Subsequent refrigerant flows follow the refrigerant path when the heat exchanger 50 is used as a condenser. That is, the refrigerant enters the section S ⁇ b> 1 through the route of the refrigerant path D ⁇ refrigerant path C ⁇ refrigerant path B ⁇ refrigerant path A and flows out from the refrigerant inlet / outlet pipe 57.
- FIG. 1 shows a schematic configuration of a separate air conditioner 1 using the heat exchanger 50 as a component of a heat pump cycle.
- the air conditioner 1 includes an outdoor unit 10 and an indoor unit 30.
- the outdoor unit 10 houses a compressor 12, a switching valve 13, an outdoor heat exchanger 14, an expansion valve 15, an outdoor blower 16, and the like in a housing 11 made of sheet metal parts and synthetic resin parts. is doing.
- the switching valve 13 is a four-way valve.
- a heat exchanger 50 is used as the outdoor heat exchanger 14.
- the outdoor blower is a combination of a motor and a propeller fan.
- the outdoor unit 10 is connected to the indoor unit 30 through two refrigerant pipes 17 and 18.
- Liquid refrigerant flows through the refrigerant pipe 17 during the cooling operation, and a pipe that is thinner than the refrigerant pipe 18 is used. Therefore, the refrigerant pipe 17 may be referred to as “liquid pipe”, “narrow pipe”, or the like.
- a gas refrigerant flows through the refrigerant pipe 18 during the cooling operation, and a pipe that is thicker than the refrigerant pipe 17 is used. Therefore, the refrigerant pipe 18 may be referred to as “gas pipe”, “thick pipe”, or the like.
- HFC R410A or R32 is used as the refrigerant.
- a two-way valve 19 is provided in the refrigerant pipe connected to the refrigerant pipe 17, and a three-way valve 20 is provided in the refrigerant pipe connected to the refrigerant pipe 18.
- the two-way valve 19 and the three-way valve 20 are closed when the refrigerant pipes 17 and 18 are removed from the outdoor unit 10 to prevent the refrigerant from leaking from the outdoor unit 10 to the outside.
- the recovery is performed through the three-way valve 20.
- the indoor unit 30 houses an indoor heat exchanger 32, an indoor blower 33, and the like inside a casing 31 made of synthetic resin parts.
- the indoor heat exchanger 32 is a combination of three heat exchangers 32 ⁇ / b> A, 32 ⁇ / b> B, and 32 ⁇ / b> C like a roof that covers the indoor blower 33. Any or all of the heat exchangers 32 ⁇ / b> A, 32 ⁇ / b> B, and 32 ⁇ / b> C can be configured by the heat exchanger 50.
- the indoor blower 33 is a combination of a motor and a cross flow fan.
- temperature detectors are arranged in the outdoor unit 10 and the indoor unit 30.
- a temperature detector 21 is disposed in the outdoor heat exchanger 14, and a temperature detector 22 is disposed in the discharge pipe 12 a serving as the discharge unit of the compressor 12, and the suction serving as the suction unit of the compressor 12.
- a temperature detector 23 is disposed in the pipe 12 b, a temperature detector 24 is disposed in the refrigerant pipe between the expansion valve 15 and the two-way valve 19, and a temperature detector for measuring the outside air temperature at a predetermined location inside the housing 11. 25 is arranged.
- a temperature detector 34 is disposed in the indoor heat exchanger 32.
- Each of the temperature detectors 21, 22, 23, 24, 25, and 34 is formed of a thermistor.
- the control unit 40 shown in FIG. 3 controls the overall control of the air conditioner 1.
- the control unit 40 performs control so that the room temperature reaches a target value set by the user.
- the control unit 40 issues operation commands to the compressor 12, the switching valve 13, the expansion valve 15, the outdoor blower 16, and the indoor blower 33.
- the control unit 40 receives output signals of the detected temperatures from the temperature detectors 21 to 25 and the temperature detector 34, respectively. While referring to the output signals from the temperature detectors 21 to 25 and the temperature detector 34, the control unit 40 issues an operation command to the compressor 12, the outdoor fan 16, and the indoor fan 33, and the switching valve 13 and the expansion valve are expanded. A command for switching the state is issued to the valve 15.
- FIG. 1 shows a state where the air conditioner 1 is performing a cooling operation or a defrosting operation.
- the compressor 12 circulates the refrigerant in a cooling mode, that is, a circulation mode in which the refrigerant discharged from the compressor 12 first enters the outdoor heat exchanger 14.
- the high-temperature and high-pressure refrigerant discharged from the compressor 12 enters the outdoor heat exchanger 14 where heat exchange with outdoor air is performed.
- the refrigerant dissipates heat to the outdoor air and condenses.
- the refrigerant that is condensed to become liquid enters the expansion valve 15 from the outdoor heat exchanger 14 and is decompressed there.
- the decompressed refrigerant is sent to the indoor heat exchanger 32, expands to a low temperature and low pressure, and lowers the surface temperature of the indoor heat exchanger 32.
- the indoor side heat exchanger 32 whose surface temperature has been lowered absorbs heat from the room air, thereby cooling the room air. After the heat absorption, the low-temperature gaseous refrigerant returns to the compressor 12.
- the air flow generated by the outdoor blower 16 promotes heat radiation from the outdoor heat exchanger 14, and the air flow generated by the indoor blower 33 promotes heat absorption of the indoor heat exchanger 32.
- FIG. 2 shows a state where the air conditioner 1 is performing a heating operation.
- the switching valve 13 is switched to reverse the refrigerant flow during the cooling operation.
- the compressor 12 circulates the refrigerant in a circulation mode during heating, that is, in a circulation mode in which the refrigerant discharged from the compressor 12 first enters the indoor heat exchanger 32.
- the high-temperature and high-pressure refrigerant discharged from the compressor 12 enters the indoor heat exchanger 32 where heat exchange with the indoor air is performed.
- the refrigerant dissipates heat to the room air, and the room air is warmed.
- the refrigerant that has dissipated heat and has become liquid by condensing enters the expansion valve 15 from the indoor heat exchanger 32 and is decompressed there.
- the decompressed refrigerant is sent to the outdoor heat exchanger 14 and expands to a low temperature and low pressure, thereby lowering the surface temperature of the outdoor heat exchanger 14.
- the outdoor heat exchanger 14 whose surface temperature has dropped absorbs heat from outdoor air. After the heat absorption, the low-temperature gaseous refrigerant returns to the compressor 12.
- the air flow generated by the indoor fan 33 promotes heat dissipation from the indoor heat exchanger 32, and the air flow generated by the outdoor fan 16 promotes heat absorption by the outdoor heat exchanger 14.
- a water receiving tank 60 for receiving water supplied from the outside is provided on the upper part of the parallel flow heat exchanger 50 constituting the outdoor heat exchanger 14.
- the water receiving tank 60 extends in parallel with the flat tube 53 and has a length that covers the entire length of the flat tube 53.
- the water receiving tank 60 may be approximately the same length as the flat tube 53, and there is no particular problem even if it is a length that slightly protrudes from the flat tube 53 or a length that does not reach the flat tube 53 a little.
- a water introduction hole 61 is formed at the bottom of the water receiving tank 60.
- a plurality of water introduction holes 61 are arranged at predetermined intervals along the length direction of the water receiving tank 60.
- the upper side plate 41 a has a square-shaped cross section, and the side plate 56 a constitutes the water receiving tank 60. Since the side plate is a member necessary for the parallel flow type heat exchanger for the reason of productivity, it is possible to save resources by integrating the side plate and the water receiving tank. Moreover, the strength is increased by making the side plate into a cross-sectional shape such as a bowl, and the reliability improvement effect of the heat exchanger itself can be expected.
- drain water generated in the indoor heat exchanger 32 is poured into the water receiving tank 60 via the drain hose 35.
- water is poured into a plurality of locations of the corrugated fins 55 directly below the water guiding holes 61.
- the end of the corrugated fin 55 protrudes from the edge of the flat tube 53 on both the upstream side and the downstream side in the blowing direction, and the drain water falling from the edge of the uppermost corrugated fin 55 is blown in the blowing direction.
- Both the end of the corrugated fin 55 on the upstream side and the end of the corrugated fin 55 on the downstream side in the air blowing direction are wetted.
- the drain water sequentially flows down the corrugated fins 55 stacked vertically from the upper side to the lower side.
- the drain water evaporates in the middle of the flow and cools the heat exchanger 50 with the heat of vaporization.
- the condensation pressure of the heat exchanger 50 functioning as a condenser during the cooling operation is greatly reduced, and the condensation performance is greatly improved.
- the water receiving tank 60 constituted by the side plate 56a has a length equal to the interval between the header pipes 51 and 52, water can be poured evenly on the surface of the heat exchanger 50.
- a drain pan for receiving such drain water is disposed inside the housing 11 of the outdoor unit 10 so that the drain water received can be appropriately discarded to the outside.
- an inclination may be provided on the inner bottom surface of the water receiving tank 60 so that drain water poured into the water receiving tank 60 via the drain hose 35 reaches the entire water receiving tank 60.
- the bottom of the water receiving tank 60 may be changed to incline the inner bottom surface, and the header pipe 52 on the drain hose 35 side of the entire heat exchanger 50 may be higher than the other header pipe 51.
- the entire outdoor unit 10 may be similarly inclined.
- the inclination in any case is sufficient if drain water flows, and it is not necessary to incline so as to be visible.
- the water guide hole 61 is in an elliptical shape in which the direction of the long axis coincides with the length direction of the water receiving tank 60, and the length of the water receiving tank 60 is plural. They are arranged at regular intervals along the direction.
- the ellipse may be an oval (land track shape).
- the oval shape may be an oval shape as well in the following embodiments.
- the water guide hole 61 has an elliptical shape whose major axis is perpendicular to the length direction of the water receiving tank 60, and the length of the water receiving tank 60 is plural. They are arranged at regular intervals along the direction.
- the water guide holes 61 are circular, and a plurality of the water guide holes 61 are arranged at regular intervals along the length direction of the water receiving tank 60.
- the water guide holes 61 are triangular, and a plurality of the water guide holes 61 are arranged at regular intervals along the length direction of the water receiving tank 60.
- the water guide holes 61 are square, and a plurality of the water guide holes 61 are arranged at regular intervals along the length direction of the water receiving tank 60.
- the water guide holes 61 have an elliptical shape similar to that of the first embodiment, and a plurality of the water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. Has been. The interval between the water guide holes 61 in each row is constant.
- the water guide holes 61 are formed in the same elliptical shape as in the second embodiment, and a plurality of the water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. Has been. The interval between the water guide holes 61 in each row is constant.
- the water guide holes 61 have a circular shape similar to that of the third embodiment, and a plurality of the water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. ing. The interval between the water guide holes 61 in each row is constant.
- the water guide holes 61 are formed in the same triangle as in the fourth embodiment, and a plurality of water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. ing. The interval between the water guide holes 61 in each row is constant.
- the water guide holes 61 have the same square shape as the fifth embodiment, and a plurality of the water guide holes 61 are arranged in two rows along the length direction of the water receiving tank 60. ing. The interval between the water guide holes 61 in each row is constant.
- the water guide hole 61 has an elliptical shape and a circular shape alternately in the length direction of the water receiving tank 60, the major axis of which coincides with the length direction of the water receiving tank 60. It is arranged at regular intervals along. The distance between the elliptical water guide hole 61 and the circular water guide hole 61 is constant.
- the size of the water guiding hole 61 is the same at any position (in the eleventh embodiment, the elliptical water guiding holes 61 are compared in size, and the circular water guiding hole 61 is compared with each other. The sizes of the holes 61 are compared with each other). The intervals between the water guide holes 61 in the row are equal. However, an equal amount of water may be dripped regardless of the distance from the drain hose 35, for example, by enlarging the water guide holes 61 as the distance from the drain hose 35 or by narrowing the interval between the water guide holes 61.
- circular water guide holes 61 are arranged in two rows on the side close to the drain hose 35, that is, on the right side of the figure, and on the side far from the drain hose 35, that is, on the left side of the figure. Are arranged in two rows. Since the elliptical water guide hole 61 has a larger area than the circular water guide hole 61, even this configuration alone compensates for the distance difference from the drain hose 35 and equalizes the amount of dripped water. In addition to this, the circular water conveyance holes 61 are between them, and the elliptical water conveyance holes 61 are between them. As the distance from the drain hose 35 is increased, the water conveyance holes 61 are increased, or the distance between the water conveyance holes 61 is decreased. For example, the amount of dripping water may be further equalized.
- triangular water guide holes 61 are arranged in a row on the side close to the drain hose 35, that is, on the right side of the figure, and on the side far from the drain hose 35, that is, on the left side of the figure.
- the water guide holes 61 are arranged in two rows. Even with this configuration alone, the distance difference from the drain hose 35 is compensated, and the amount of dripping water is equalized.
- the water flow holes 61 may be enlarged as the distance from the drain hose 35 is increased, or the distance between the water flow holes 61 may be narrowed to further equalize the amount of dripped water.
- a slit is provided as the water guide hole 61 along the length direction of the water receiving tank 60.
- a capillary phenomenon occurs in the slit. That is, even if the amount of drain water flowing into the water receiving tank 60 is small, the drain water can reach a wide range by a thin tube phenomenon generated in the slit.
- the number of slits is one in FIG. 20, a plurality of slits may be provided in parallel.
- bridge-shaped portions may be provided in the slits.
- the cross-sectional shape of the water receiving tank 60 is not limited to a square.
- the semicircle shown in FIG. 21 may be sufficient. Even if it is the same square, as shown in FIG. 22, the height of the edge of one side may be low. It may be L-shaped as shown in FIG.
- the water receiving tank 60 of FIG. 24 is a modification of the water receiving tank 60 of FIG. 23, and has a horizontal base that is slanted and a tip that is slightly lifted.
- the water receiving tank 60 of FIG. 25 is a further modification of the water receiving tank 60 of FIG. 24, and the bottom that has been horizontal up to the middle is lifted obliquely from the middle.
- the water receiving tank 60 in FIG. 26 is a modification of the water receiving tank 60 in FIG. 21 and has a shallow arc cross section.
- the present invention is widely applicable to a side flow type parallel flow type heat exchanger and an air conditioner equipped with the same.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
Description
10 室外機
11 筐体
12 圧縮機
13 切替弁
14 室外側熱交換器
15 膨張弁
16 室外側送風機
30 室内機
31 筐体
32 室内側熱交換器
33 室内側送風機
35 ドレンホース
40 制御部
50 熱交換器
51、52 ヘッダパイプ
53 偏平チューブ
55 コルゲートフィン
56、56a サイドプレート
60 受水槽
61 導水孔
Claims (5)
- パラレルフロー型熱交換器であって、以下の構成を備えるもの:
当該パラレルフロー型熱交換器は、2本の垂直方向ヘッダパイプと、前記両ヘッダパイプを連結する複数の水平方向偏平チューブを備えるサイドフロー方式のものであり、
上部に前記偏平チューブと平行な受水槽が形成され、前記受水槽に形成された導水孔から滴下した水が当該熱交換器の表面伝いに流下する。 - 請求項1のパラレルフロー型熱交換器であって、以下の構成を備えるもの:
前記導水孔は前記受水槽の長さ方向に沿って所定間隔で複数個配置されている。 - 請求項1のパラレルフロー型熱交換器であって、以下の構成を備えるもの:
前記受水槽は前記偏平チューブの全長をカバーする長さである。 - 請求項1のパラレルフロー型熱交換器であって、以下の構成を備えるもの:
前記偏平チューブに取り付けられるコルゲートフィンのうち、最上位に位置するコルゲートフィンに取り付けられるサイドシートが受水槽として形成される。 - 空気調和機であって、以下の構成を備えるもの:
室外機と室内機を備え、
前記室外機に請求項1から4のいずれかのパラレルフロー型熱交換器を搭載し、当該パラレルフロー型熱交換器の前記受水槽に前記室内機で発生したドレン水を導く。
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201380011298.XA CN104136876B (zh) | 2012-06-04 | 2013-05-29 | 并流式热交换器和安装有该并流式热交换器的空气调节机 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012-126740 | 2012-06-04 | ||
JP2012126740A JP5940895B2 (ja) | 2012-06-04 | 2012-06-04 | パラレルフロー型熱交換器及びそれを搭載した空気調和機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013183508A1 true WO2013183508A1 (ja) | 2013-12-12 |
Family
ID=49711900
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/064847 WO2013183508A1 (ja) | 2012-06-04 | 2013-05-29 | パラレルフロー型熱交換器及びそれを搭載した空気調和機 |
Country Status (4)
Country | Link |
---|---|
JP (1) | JP5940895B2 (ja) |
CN (1) | CN104136876B (ja) |
MY (1) | MY168586A (ja) |
WO (1) | WO2013183508A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015224844A (ja) * | 2014-05-29 | 2015-12-14 | パナソニックIpマネジメント株式会社 | 熱交換器 |
US11415371B2 (en) | 2017-03-27 | 2022-08-16 | Daikin Industries, Ltd. | Heat exchanger and refrigeration apparatus |
US11428446B2 (en) | 2017-03-27 | 2022-08-30 | Daikin Industries, Ltd. | Heat exchanger unit |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60147076A (ja) * | 1984-01-12 | 1985-08-02 | サンデン株式会社 | 建物用空調システム |
JPH04119206U (ja) * | 1991-04-04 | 1992-10-26 | 三菱自動車工業株式会社 | 車両の空調装置 |
JPH0611210A (ja) * | 1992-06-29 | 1994-01-21 | Nippondenso Co Ltd | 熱交換器及びそれを用いた空気調和機 |
JPH09310994A (ja) * | 1996-05-24 | 1997-12-02 | Calsonic Corp | アルミニウム合金製熱交換器の取付ブラケット装着部 |
JP3056201U (ja) * | 1998-05-01 | 1999-02-12 | 詮旭電機股▲ふん▼有限公司 | 高効率の蒸発式熱交換器 |
JP3057989U (ja) * | 1998-09-25 | 1999-06-08 | 劉 富欽 | 蒸発式冷却機 |
JPH11347666A (ja) * | 1998-06-09 | 1999-12-21 | Nippon Light Metal Co Ltd | 熱交換器及びその製造方法 |
JP3084460U (ja) * | 2001-09-03 | 2002-03-22 | 和信 呉 | 冷凍或いは空調設備用の熱交換器 |
JP2002250543A (ja) * | 2001-02-22 | 2002-09-06 | Hitachi Ltd | 空気調和機 |
JP2004197984A (ja) * | 2002-12-17 | 2004-07-15 | Toyo Radiator Co Ltd | 一体型多板式熱交換器 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3556730B2 (ja) * | 1995-04-28 | 2004-08-25 | 三菱電機株式会社 | エレベータ空気調和機 |
JP3674129B2 (ja) * | 1996-02-07 | 2005-07-20 | 株式会社デンソー | 異種コア一体型熱交換器 |
JP3861219B2 (ja) * | 2003-03-19 | 2006-12-20 | 勝 北野 | 冷房装置の運転エネルギー省力化装置 |
JP2008304168A (ja) * | 2007-06-11 | 2008-12-18 | Denso Corp | 熱交換器 |
JP2010175171A (ja) * | 2009-01-30 | 2010-08-12 | Nippon Spindle Mfg Co Ltd | 温度調整装置 |
JP5336914B2 (ja) * | 2009-04-15 | 2013-11-06 | シャープ株式会社 | 熱交換器及びそれを搭載した空気調和機 |
JP2011085368A (ja) * | 2009-10-19 | 2011-04-28 | Sharp Corp | 熱交換器及びそれを搭載した空気調和機 |
-
2012
- 2012-06-04 JP JP2012126740A patent/JP5940895B2/ja active Active
-
2013
- 2013-05-29 WO PCT/JP2013/064847 patent/WO2013183508A1/ja active Application Filing
- 2013-05-29 MY MYPI2014002486A patent/MY168586A/en unknown
- 2013-05-29 CN CN201380011298.XA patent/CN104136876B/zh active Active
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60147076A (ja) * | 1984-01-12 | 1985-08-02 | サンデン株式会社 | 建物用空調システム |
JPH04119206U (ja) * | 1991-04-04 | 1992-10-26 | 三菱自動車工業株式会社 | 車両の空調装置 |
JPH0611210A (ja) * | 1992-06-29 | 1994-01-21 | Nippondenso Co Ltd | 熱交換器及びそれを用いた空気調和機 |
JPH09310994A (ja) * | 1996-05-24 | 1997-12-02 | Calsonic Corp | アルミニウム合金製熱交換器の取付ブラケット装着部 |
JP3056201U (ja) * | 1998-05-01 | 1999-02-12 | 詮旭電機股▲ふん▼有限公司 | 高効率の蒸発式熱交換器 |
JPH11347666A (ja) * | 1998-06-09 | 1999-12-21 | Nippon Light Metal Co Ltd | 熱交換器及びその製造方法 |
JP3057989U (ja) * | 1998-09-25 | 1999-06-08 | 劉 富欽 | 蒸発式冷却機 |
JP2002250543A (ja) * | 2001-02-22 | 2002-09-06 | Hitachi Ltd | 空気調和機 |
JP3084460U (ja) * | 2001-09-03 | 2002-03-22 | 和信 呉 | 冷凍或いは空調設備用の熱交換器 |
JP2004197984A (ja) * | 2002-12-17 | 2004-07-15 | Toyo Radiator Co Ltd | 一体型多板式熱交換器 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2015224844A (ja) * | 2014-05-29 | 2015-12-14 | パナソニックIpマネジメント株式会社 | 熱交換器 |
US11415371B2 (en) | 2017-03-27 | 2022-08-16 | Daikin Industries, Ltd. | Heat exchanger and refrigeration apparatus |
US11428446B2 (en) | 2017-03-27 | 2022-08-30 | Daikin Industries, Ltd. | Heat exchanger unit |
Also Published As
Publication number | Publication date |
---|---|
MY168586A (en) | 2018-11-14 |
CN104136876B (zh) | 2016-04-20 |
JP5940895B2 (ja) | 2016-06-29 |
CN104136876A (zh) | 2014-11-05 |
JP2013250033A (ja) | 2013-12-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US9651317B2 (en) | Heat exchanger and air conditioner | |
CN108139089B (zh) | 空气调节机的室外机及室内机 | |
JP5385589B2 (ja) | 空気調和機の室外機 | |
US20130220584A1 (en) | Heat exchanger, and all-in-one air conditioner equipped therewith | |
JP5858478B2 (ja) | パラレルフロー型熱交換器及びそれを搭載した空気調和機 | |
JP6625229B2 (ja) | 熱交換器および空気調和装置 | |
JP6120978B2 (ja) | 熱交換器及びそれを用いた空気調和機 | |
JP5940895B2 (ja) | パラレルフロー型熱交換器及びそれを搭載した空気調和機 | |
JP2014137177A (ja) | 熱交換器および冷凍装置 | |
JP2014043985A (ja) | パラレルフロー型熱交換器及びそれを搭載した空気調和機 | |
JP2010127510A (ja) | 熱交換器 | |
JP2018138826A (ja) | 空気調和装置 | |
AU2017444848B2 (en) | Heat exchanger and refrigeration cycle device | |
JP3177302U (ja) | 冷暖房空調装置 | |
JP4995308B2 (ja) | 空気調和機の室内機 | |
JP2014137172A (ja) | 熱交換器及び冷凍装置 | |
WO2018040036A1 (zh) | 微通道换热器及风冷冰箱 | |
WO2018040037A1 (zh) | 微通道换热器及风冷冰箱 | |
JP6906101B2 (ja) | 熱交換器および冷凍サイクル装置 | |
JP2013234815A (ja) | 空気調和機 | |
JP2012067971A (ja) | 熱交換器及び機器 | |
JP2021076363A (ja) | 熱交換器及び該熱交換器を用いた空気調和機 | |
JP2015227754A (ja) | 熱交換器 | |
JP2015169358A (ja) | 熱交換器 | |
JP2012042128A (ja) | 熱交換器及びそれを搭載した空気調和機 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201380011298.X Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 13801040 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: IDP00201405249 Country of ref document: ID |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 13801040 Country of ref document: EP Kind code of ref document: A1 |