WO2018116929A1 - Heat exchanger and air conditioner - Google Patents
Heat exchanger and air conditioner Download PDFInfo
- Publication number
- WO2018116929A1 WO2018116929A1 PCT/JP2017/044694 JP2017044694W WO2018116929A1 WO 2018116929 A1 WO2018116929 A1 WO 2018116929A1 JP 2017044694 W JP2017044694 W JP 2017044694W WO 2018116929 A1 WO2018116929 A1 WO 2018116929A1
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- WIPO (PCT)
- Prior art keywords
- chamber
- heat transfer
- heat exchanger
- refrigerant
- header
- Prior art date
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Classifications
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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
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
- F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
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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
- 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
- F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
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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
- F28F9/0243—Header boxes having a circular cross-section
Definitions
- the present invention relates to a heat exchanger and an air conditioner. This application claims priority based on Japanese Patent Application No. 2016-247153 for which it applied on December 20, 2016, and uses the content here.
- a heat exchanger for an air conditioner in which a plurality of heat transfer tubes extending in the horizontal direction are arranged at intervals in the vertical direction and fins are provided on the outer surface of each heat transfer tube. Both ends of the plurality of heat transfer tubes are respectively connected to a pair of headers extending in the vertical direction.
- the refrigerant introduced into one header and circulated through the heat transfer tube to the other header is folded back at the other header and returned to the one header again through the heat transfer tube.
- a plurality of regions are defined by partition plates that divide the header in the vertical direction.
- the refrigerant introduced into the one area in the header via the heat transfer tube is introduced into the other area in the header via the connection pipe, and then the plurality of heat transfer pipes connected to the other area. Is returned to one header on the entrance / exit side.
- liquid phase refrigerant having a large specific gravity tends to flow downward
- gas phase refrigerant having a small specific gravity tends to flow upward. Therefore, a drift occurs in the refrigerant flowing into each heat transfer tube.
- Patent Document 1 describes that the header is divided into a heat transfer tube side space and a counter heat transfer tube side space by a partition plate, and these spaces are communicated with each other at an upper part and a lower part to suppress refrigerant drift. ing.
- the refrigerant flow rate flowing into the heat transfer tube is equalized in any heat transfer tube from the upper part to the lower part.
- This invention is made
- the heat exchanger according to the first aspect of the present invention includes a plurality of heat exchanger tubes that extend in the horizontal direction and in which a refrigerant flows therethrough and that are arranged in a plurality at intervals in the vertical direction, and that have a tubular shape that extends in the vertical direction.
- the heat transfer tube has one end connected to an internal space in a communicating state, and the header portion extends in a horizontal sectional view across each heat transfer tube and the inner peripheral surface of the header portion to pass through the header portion.
- Each of the heat transfer tubes is partitioned into a first chamber and a second chamber, and the first chamber and the second chamber are separated from each other at a position equal to or higher than the height of the uppermost heat transfer tube among the heat transfer tubes.
- a vertical partition plate that forms a first communicating portion that communicates, and a flow passage that is connected only to the first chamber among the first chamber and the second chamber, and through which the refrigerant flows.
- the refrigerant when the heat exchanger is used as an evaporator, the refrigerant is introduced into the first chamber in the header portion through the flow path. A part of the refrigerant introduced into the first chamber is introduced into each heat transfer tube.
- the refrigerant that has not been introduced into the heat transfer tubes is introduced into the second chamber via the first communication portion formed in the upper part of the vertical partition plate, and is introduced into each heat transfer tube while moving downward in the second chamber. It will be.
- the flow rate of the refrigerant moving in the first chamber can be suppressed, and the amount of refrigerant introduced into each heat transfer tube connected to the upper part or the central part in the header part is secured.
- the refrigerant may concentrate on the upper part of the first chamber, but the refrigerant is introduced into the upper part of the second chamber through the first series part formed at the upper part of the vertical partition plate. Since the refrigerant is introduced into each heat transfer tube while moving downward in the second chamber, the refrigerant is introduced into each heat transfer tube connected to the lower part and the central part in the header part without concentrating on the upper part of the header part. As a result, the amount of refrigerant to be ensured is ensured, so that the variation in the flow rate of the refrigerant flowing through each heat transfer tube can be suppressed.
- the first series passage may be a communication hole formed in the vertical partition plate.
- the first series part may be a gap between the vertical partition plate and an upper end of the header part.
- the vertical partition plate may form a second communication portion that allows the first chamber and the second chamber to communicate with each other between the vertically adjacent heat transfer tubes.
- the refrigerant is introduced from each heat transfer tube into the first chamber and the second chamber in the header portion, and the refrigerant introduced into the first chamber is introduced into the flow passage.
- the refrigerant introduced into the second chamber is introduced into the first chamber via the second communication portion formed in the vertical partition plate and then introduced into the flow passage.
- the vertical partition plate forms a third communication portion that communicates the first chamber and the second chamber with each other at a position below the lowest heat transfer tube among the heat transfer tubes. It may be.
- the refrigerant is introduced from each heat transfer tube into the first chamber and the second chamber in the header portion, and the refrigerant introduced into the first chamber is introduced into the flow passage.
- the refrigerant introduced into the second chamber moves downward in the second chamber, is introduced into the first chamber via the third communication portion formed in the vertical partition plate, and is then introduced into the flow passage.
- the refrigerant introduced into the second chamber from each heat transfer tube can be introduced into the first chamber via the second communication portion without being accumulated in the second chamber and introduced into the flow passage.
- a lower portion of the vertical partition plate is curved from the second chamber side to the first chamber side, and the third communication portion is between the vertical partition plate and a lower end of the header portion. It may be a gap.
- the refrigerant is introduced from each heat transfer tube into the first chamber and the second chamber in the header portion, and the refrigerant introduced into the first chamber is introduced into the flow passage.
- the refrigerant introduced into the second chamber moves downward in the second chamber, is introduced into the first chamber via the third communication portion formed in the vertical partition plate, and is then introduced into the flow passage.
- the refrigerant introduced into the second chamber from each heat transfer tube can be introduced into the first chamber via the second communication portion without being accumulated in the second chamber and introduced into the flow passage.
- the lower part of the vertical partition plate is curved toward the second chamber, the curved shape guides the flow of the refrigerant, and the refrigerant is easily introduced from the second chamber into the first chamber.
- the length Lp of the heat transfer tube in the header portion in the extending direction of the heat transfer tube may be less than or equal to half of the inner diameter Di of the header portion.
- the length in the header portion of the heat transfer tube is short, so that the gas-liquid two-phase state introduced from the flow passage to the first chamber and the first chamber to the second chamber is Disturbances in the flow of the refrigerant due to the refrigerant collecting between the upper and lower portions of the heat transfer tubes in the first chamber and the second chamber can be suppressed, and the liquid-phase refrigerant is easily introduced into the heat transfer tubes. This further suppresses the occurrence of variations in the flow rate of the refrigerant flowing through each heat transfer tube.
- the air conditioner according to the second aspect of the present invention includes any one of the above heat exchangers. As a result, it is possible to suppress the occurrence of variations in the flow rate of the refrigerant flowing through each heat transfer tube, and to avoid a decrease in cooling and heating performance.
- FIG. 1 is an overall configuration diagram of an air conditioner according to a first embodiment of the present invention. It is a longitudinal cross-sectional view of the heat exchanger which concerns on 1st embodiment of this invention. It is a perspective view of the heat exchanger which concerns on 1st embodiment of this invention. It is a horizontal sectional view of the 2nd header part of the heat exchanger concerning a first embodiment of the present invention. It is an A direction arrow directional view of FIG. It is a perspective view of the heat exchanger which concerns on the modification of 1st embodiment of this invention. It is a horizontal sectional view of the 2nd header part of the heat exchanger concerning the modification of a first embodiment of the present invention. It is a B direction arrow directional view of FIG.
- E arrow line view of FIG. It is a perspective view of the heat exchanger which concerns on the modification of 3rd embodiment of this invention. It is a longitudinal direction sectional view of the 2nd header part of the heat exchanger concerning the modification of a third embodiment of the present invention. It is a F arrow line view of FIG. It is a horizontal sectional view of the 2nd header part of the heat exchanger of the heat exchanger concerning a fourth embodiment of the present invention.
- the air conditioner 1 includes a compressor 2, an indoor heat exchanger 3 (heat exchanger 10), an expansion valve 4, an outdoor heat exchanger 5 (heat exchanger 10), a four-way valve 6, and The pipe 7 for connecting them is provided, and a refrigerant circuit composed of these is constituted.
- the compressor 2 compresses the refrigerant and supplies the compressed refrigerant to the refrigerant circuit.
- the indoor heat exchanger 3 performs heat exchange between the refrigerant and the indoor air.
- the indoor heat exchanger 3 is used as an evaporator during cooling operation and absorbs heat from the room, and is used as a condenser during heating operation and dissipates heat to the room.
- the outdoor heat exchanger 5 performs heat exchange between the refrigerant and the outdoor air.
- the expansion valve 4 reduces the pressure by expanding the high-pressure refrigerant liquefied by exchanging heat with the condenser.
- the outdoor heat exchanger 5 is used as a condenser during the cooling operation and dissipates heat to the outside, and is used as an evaporator during the heating operation and absorbs heat from the outside.
- the four-way valve 6 switches the direction in which the refrigerant flows between the heating operation and the cooling operation. Accordingly, during the cooling operation, the refrigerant circulates in the order of the compressor 2, the outdoor heat exchanger 5, the expansion valve 4, and the indoor heat exchanger 3. On the other hand, during the heating operation, the refrigerant circulates in the order of the compressor 2, the indoor heat exchanger 3, the expansion valve 4, and the outdoor heat exchanger 5.
- the heat exchanger 10 used as the indoor heat exchanger 3 and the outdoor heat exchanger 5 will be described with reference to FIGS.
- the heat exchanger 10 includes a plurality of heat transfer tubes 20, a plurality of fins 23, a pair of headers 30, and a connection tube 55.
- the heat transfer tube 20 is a tubular member extending linearly in the horizontal direction, and a flow path through which the refrigerant flows is formed.
- a plurality of such heat transfer tubes 20 are arranged at intervals in the vertical direction, and are arranged in parallel to each other.
- each heat transfer tube 20 has a flat tubular shape, and a plurality of flow paths arranged in parallel in the horizontal direction perpendicular to the extending direction of the heat transfer tube 20 are formed inside the heat transfer tube 20. ing.
- the plurality of flow paths are arranged in parallel to each other.
- the outer shape of the cross section orthogonal to the extending direction of the heat transfer tube 20 is a flat shape with the horizontal direction orthogonal to the extending direction of the heat transfer tube 20 as the longitudinal direction.
- the fins 23 are respectively disposed between the heat transfer tubes 20 arranged as described above.
- the fins 23 are alternately arranged in the heat transfer tubes 20 adjacent to each other in the vertical direction as they extend in the extending direction of the heat transfer tubes 20. It extends in a so-called corrugated shape extending so as to come into contact.
- the shape of the fin 23 is not limited to this, and may be any shape as long as it is provided so as to protrude from the outer peripheral surface of the heat transfer tube 20.
- the pair of headers 30 are provided so as to sandwich the heat transfer tubes 20 at both ends of the plurality of heat transfer tubes 20.
- One of the pair of headers 30 is an inlet / outlet header 40 serving as an inlet / outlet of the refrigerant into the heat exchanger 10 from the outside.
- the other of the pair of headers 30 is a folded-back header 50 for the refrigerant to be folded in the heat exchanger 10.
- the entrance / exit header 40 is a cylindrical member extending in the up-down direction, the upper end and the lower end are closed, and the inside is partitioned into two upper and lower regions by a partition plate.
- a lower area defined by the entry / exit partition plate 41 is a lower entry / exit area 42.
- An upper area partitioned by the entrance / exit partition plate 41 is an upper entrance / exit area 43.
- the lower entrance / exit area 42 and the upper entrance / exit area 43 are not in communication with each other in the entrance / exit header 40.
- the lower entry / exit area 42 and the upper entry / exit area 43 are connected to the pipes 7 constituting the refrigerant circuit.
- the heat transfer tube 20 connected in communication with the lower entrance / exit region 42 is the first heat transfer tube 21.
- the heat transfer tube 20 connected in communication with the upper entrance / exit region 43 is a second heat transfer tube 22 (heat transfer tube 20).
- the folded-back header 50 includes a header body 51, a folded-side partition plate 54, and a vertical partition plate 70.
- the header main body 51 is a cylindrical member extending in the vertical direction, and the upper end and the lower end are closed.
- the folding side partition plate 54 is provided in the header body 51, and divides the space in the header body 51 into two upper and lower areas.
- a lower portion of the folding side partition plate 54 of the header body 51 is a first header portion 52.
- the upper part of the folding side partition plate 54 of the header body 51 is a second header part 53 (header part).
- the header main body 51 is partitioned by the folding side partition plate 54, so that the first header portion 52 and the second header portion 53 each having a space therein are formed in the folding side header 50. ing.
- the first header portion 52 and the second header portion 53 constitute the folded-back header 50.
- the first heat transfer tube 21 is connected to the first header portion 52 from one side in the horizontal direction so as to communicate with the inside of the first header portion 52.
- the second heat transfer tubes 22 are connected to the second header portion 53 from one side in the horizontal direction so as to communicate with the inside of the second header portion 53, respectively.
- the heat transfer tube 20 connected to the first header portion 52 is the first heat transfer tube 21
- the heat transfer tube 20 connected to the second header portion 53 is the second heat transfer tube 22.
- the vertical partition plate 70 is a plate-like member extending in the vertical direction, and is provided in the second header portion 53.
- the vertical partition plate 70 divides the space in the second header portion 53 into two regions of a first chamber 76 and a second chamber 77 so that each space communicates with each second heat transfer tube 22 in a horizontal sectional view. ing.
- the vertical partition plate 70 is installed in a direction in which the second heat transfer tube 22 extends in a horizontal sectional view.
- the vertical partition plate 70 extends in the horizontal direction in the second header portion 53.
- each second heat transfer tube in which the first chamber 76 and the second chamber 77 are separated by the vertical partition plate 70 also between the second heat transfer tubes 22 adjacent in the vertical direction is the second header portion.
- the one end by the side of the 2nd heat exchanger tube among the both ends of the horizontal direction of the vertical partition plate 70 is contacting the 2nd heat exchanger tube.
- the opening of each second heat transfer tube 22 is divided in the horizontal direction perpendicular to the extending direction of the second heat transfer tube 22 by one end of the vertical partition plate.
- the connecting pipe 55 is a tubular member having a flow path formed therein, and one end of the connecting pipe 55 is connected to the first header portion 52 in communication with the inside of the first header portion 52, and the other end. Is connected to the second header portion 53 in communication with the inside of the second header portion 53. More specifically, one end of the connection pipe 55 is connected to the central portion of the first header portion 52 in the vertical direction. On the other hand, the other end of the connection pipe 55 is connected to the lower part of the first chamber 76 of the second header part 53.
- a flow path formed inside the connection pipe 55 serves as a flow passage 56 that allows the refrigerant to flow between the first header portion 52 and the second header portion 53.
- the flow passage 56 may be formed so as to directly connect the inside of the first header portion 52 and the first chamber 76 to the folded-back partition plate 54.
- the header 30 has a cylindrical shape extending in the vertical direction, and the internal space is also cylindrical.
- the vertical partition plate 70 is arrange
- the first chamber 76 and the second chamber 77 each have a semicircular shape in a horizontal sectional view.
- an upper communication hole 62 (first communication portion 61) that allows the first chamber 76 and the second chamber 77 to communicate with each other by penetrating the vertical partition plate 70 is formed.
- the upper communication hole 62 is equal to or higher than the height of the second header portion uppermost heat transfer tube 24, which is the heat transfer tube located at the uppermost position among the second heat transfer tubes 22. Formed in position.
- the upper communication hole 62 is formed at a position ahead of the tip of the second heat transfer tube 22, that is, on the side opposite to the connection portion between the second header portion 53 and the second heat transfer tube 22 in the horizontal sectional view. .
- the heat exchanger 10 When the heat exchanger 10 is the indoor heat exchanger 3, it is used as an evaporator during the cooling operation of the air conditioner 1, and when the outdoor heat exchanger 5 is used, it evaporates during the heating operation of the air conditioner 1. It will be used as a container.
- a gas-liquid two-phase refrigerant with a large liquid phase is supplied from the pipe 7 to the lower inlet / outlet region 42 of the inlet / outlet header 40 shown in FIG.
- This refrigerant is distributed and supplied into the plurality of first heat transfer tubes 21 in the lower entrance / exit region 42, and exchanges heat with the external atmosphere of the first heat transfer tubes 21 in the process of flowing through the first heat transfer tubes 21. Evaporation is encouraged.
- the refrigerant supplied from the first heat transfer tube 21 into the first header portion 52 of the folded-back header 50 is a gas-liquid two-phase in which the liquid phase ratio is reduced due to a partial change from the liquid phase to the gas phase. Becomes a refrigerant.
- the gas-liquid two-phase refrigerant supplied into the first header portion 52 is introduced into a connecting pipe 55 connected to the first header portion 52, and It is introduced into the first chamber 76 in the second header portion 53 through the connecting pipe 55.
- the refrigerant introduced into the first chamber 76 sequentially moves upward in the first chamber 76 as the refrigerant continues to be supplied, and is introduced into each second heat transfer tube 22.
- the refrigerant that has not been introduced into the second heat transfer tube 22 is introduced into the upper portion of the second chamber 77 through the upper communication hole 62 formed in the upper portion of the vertical partition plate 70.
- the refrigerant introduced into the upper portion of the second chamber 77 is introduced into each second heat transfer tube 22 while moving downward in the second chamber 77.
- the cross-sectional area of the refrigerant flow path in the first chamber 76 is the entire second header portion 53. It is smaller than the cross-sectional area. For this reason, even if it is a case where there is little refrigerant
- the amount of refrigerant introduced into the heat transfer tubes 22 is ensured, and the occurrence of variations in the flow rate of the refrigerant flowing through each second heat transfer tube 22 can be suppressed.
- the refrigerant may concentrate on the upper portion of the first chamber 76, but the upper portion of the second chamber 77 is formed via the upper communication hole 62 formed on the upper portion of the vertical partition plate 70. Since the refrigerant is introduced and introduced into each of the second heat transfer tubes 22 while moving downward in the second chamber 77, the refrigerant does not concentrate on the upper portion of the second header portion 53, and the second header portion.
- the amount of refrigerant introduced into each second heat transfer tube 22 connected to the lower part or the center part in 53 is secured, and also the occurrence of variation in the flow rate of refrigerant flowing through each second heat transfer tube 22 is suppressed. it can.
- the refrigerant is urged to evaporate again by exchanging heat with the external atmosphere of the second heat transfer tube 22 in the course of flowing through the second heat transfer tube 22.
- the liquid phase remaining in the refrigerant changes into a gas phase in the second heat transfer tube 22, and the gas phase refrigerant is supplied to the upper entrance / exit region 43 of the inlet / outlet header 40.
- the refrigerant is introduced into the pipe 7 from the upper entrance / exit area 43 and circulates in the refrigerant circuit.
- the refrigerant supplied to the second header portion 53 can be used for each second heat transfer tube 22 regardless of whether the refrigerant flow rate is small or large.
- the variation in the amount of refrigerant introduced into the heat exchanger can be suppressed, and the performance deterioration of the heat exchanger due to the deviation of the refrigerant flow rate flowing into the heat transfer tube can be suppressed.
- the cooling performance and the heating performance are not impaired.
- the height may be the same height as the two header portion uppermost heat transfer tubes 24 or the height between the second header portion uppermost heat transfer tube 24 and the upper end of the second header portion 53.
- a gap is formed between the vertical partition plate 70 and the second header portion 53, and the gap communicates the first chamber 76 and the second chamber 77 with the upper communication portion 63 (first communication portion 61).
- the refrigerant introduced into the first chamber 76 sequentially moves upward in the first chamber 76 as the refrigerant continues to be supplied, and is introduced into each second heat transfer tube 22.
- the refrigerant that has not been introduced into the second heat transfer tube 22 is introduced into the upper portion of the second chamber 77 via the upper communication portion 63 formed at the upper portion of the vertical partition plate 70, and moves downward in the second chamber. Since it will be introduced into each second heat transfer tube 22, the occurrence of variations in the amount of refrigerant introduced into each second heat transfer tube 22 can be suppressed as described above.
- the heat exchanger 80 which concerns on 2nd embodiment of this invention is demonstrated with reference to FIG.9, FIG10 and FIG.11.
- the same components as those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
- the vertical partition plate 71 of the heat exchanger 80 of the second embodiment is similar to the first embodiment in the internal space of the cylindrical second header portion 53. It arrange
- the vertical partition plate 71 is formed with an upper communication hole 62 similar to that of the first embodiment.
- the length of the vertical partition plate 71 in the horizontal direction is from the tip position of the heat transfer tube 22 to the inner peripheral surface of the second header portion 53.
- the upper and lower portions of each heat transfer tube 22 in the second header portion 53 are not provided with the vertical partition plate 71, and thereby the heat transfer tube side communication portion 65 (second communication portion) for communicating the first chamber 76 and the second chamber 77. 64) is formed.
- the heat exchanger 80 operates as a condenser during the cooling operation of the air conditioner 1, contrary to the case where the heat exchanger 80 is used as an evaporator, the first chamber 76 in the second header portion 53 from each second heat transfer tube 22 and A refrigerant is introduced into the second chamber 77.
- the refrigerant introduced into the first chamber 76 moves downward in the first chamber 76 and is introduced into the first header portion 52 via the connection pipe 55.
- the refrigerant introduced into the second chamber 77 is introduced into the first chamber 76 via the heat transfer tube side communication portion 65 formed in the vertical partition plate 71 and then into the first header portion 52 via the connection tube 55. be introduced.
- the heat exchanger 80 of the present embodiment when operating as an evaporator, it is the same as in the first embodiment, but when operating as a condenser, the second heat transfer tube 22
- the refrigerant introduced into the second chamber 77 does not accumulate in the second chamber 77 and is introduced into the first chamber 76 via the heat transfer tube side communication portion 65 formed in the vertical partition plate 71. It can introduce
- the cooling performance and the heating performance are not impaired.
- the length of the vertical partition plate 71 in the horizontal direction is the same as that of the first embodiment.
- the heat transfer tube side communication holes 66 may be formed in portions corresponding to the upper and lower portions of the second heat transfer tubes 22 in 71 so that the first chamber 76 and the second chamber 77 communicate with each other.
- the refrigerant introduced from each second heat transfer tube 22 into the second chamber 77 does not accumulate in the second chamber 77, and passes through the heat transfer tube side communication hole 66 formed in the vertical partition plate 71. It is introduced into the first chamber 76 and can be introduced into the first header portion via the connecting pipe 55 connected to the lower portion of the first chamber 76.
- the cooling performance and the heating performance are not impaired.
- the heat exchanger 90 which concerns on 3rd embodiment of this invention is demonstrated with reference to FIG.15, FIG16 and FIG.17.
- the same components as those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
- the vertical partition plate 72 of the heat exchanger 90 of the third embodiment is similar to the first embodiment in the internal space of the cylindrical second header portion 53.
- an upper communication hole 62 similar to the first embodiment is formed.
- the vertical partition plate 72 further includes the first chamber 76 and the first chamber 76 at a position lower than the second header portion lowermost heat transfer tube 25, which is a heat transfer tube located at the lowermost portion in each second heat transfer tube 22.
- a lower communication hole 68 (third communication portion 67) for communicating with the two chambers 77 is formed. Further, the lower communication hole 68 is formed at a position ahead of the tip of the second heat transfer tube 22, that is, on the side opposite to the connection portion between the second header portion 53 and the second heat transfer tube 22 in a horizontal sectional view. Is done.
- the heat exchanger 90 operates as a condenser during the cooling operation of the air conditioner 1, contrary to the case where it is used as an evaporator, the first chamber 76 in the second header section 53 from each second heat transfer tube 22 and A refrigerant is introduced into the second chamber 77.
- the refrigerant introduced into the first chamber 76 moves downward in the first chamber 76 and is introduced into the first header portion 52 via the connection pipe 55.
- the refrigerant introduced into the second chamber 77 moves downward in the second chamber 77, and then introduced into the first chamber 76 via the lower communication hole 68 formed in the vertical partition plate 72. It is introduced into the first header portion 52 through the connecting pipe 55.
- the heat exchanger 90 of the present embodiment when operating as an evaporator, it is the same as in the first embodiment, but when operating as a condenser, the second heat transfer tube 22
- the refrigerant introduced into the second chamber 77 does not accumulate in the second chamber 77 and is introduced into the first chamber 76 through the lower communication hole 68 formed in the vertical partition plate 72, and is placed in the lower portion of the first chamber 76. It can introduce into a 1st header part via the connected connecting pipe 55.
- FIG. As a result, in the air conditioner using the heat exchanger 90 of the present embodiment, the cooling performance and the heating performance are not impaired.
- the lower part of the vertical partition plate 72 is curved toward the first chamber 76, and the second header part lowermost heat transfer tube 25.
- a lower communication portion 69 (third communication portion 67) that allows the first chamber 76 and the second chamber 77 to communicate with each other may be formed further downward.
- the lower communication portion 69 is formed as a gap between the lower end of the vertical partition plate 72 and the lower end of the second header portion 53. Also by this, the refrigerant introduced from each second heat transfer tube 22 into the second chamber 77 does not accumulate in the second chamber 77, and the first through the lower communication portion 69 formed in the vertical partition plate 72.
- the second communication part 64 described in the second embodiment may be provided.
- the vertical partition plate has the same configuration as that of any one of the first to third embodiments.
- This embodiment demonstrates as a structure similar to the vertical partition plate 70 of 1st embodiment. Constituent elements similar to those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
- the length Lp in the second header portion 53 of the second heat transfer tube 22 in the extending direction of the second heat transfer tube 22 is the second header portion.
- the inner diameter Di of 53 is less than half.
- the tip position of the second heat transfer tube 22 is the same as the center position of the second header portion 53 or is closer to the connection portion side of the second header portion 53 and the second heat transfer tube 22 than the center of the second header portion 53. ing.
- a heat exchanger 100 when operating as an evaporator, since the length in the second header portion 53 of the second heat transfer tube 22 is short, the first chamber 76 and the first chamber 76 are connected from the connection tube 55.
- the refrigerant in the gas-liquid two-phase state introduced into the second chamber 77 through the upper communication hole 62 from the upper part of the first chamber 76 and the second heat transfer tubes 22 in the second chamber 77 is accumulated.
- the liquid phase refrigerant can be easily introduced into each second heat transfer tube.
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
This heat exchanger is provided with: a plurality of heat transfer pipes which extend horizontally, allow a refrigerant to flow therethrough, and are arranged at a distance from each other in the vertical direction; a header section which is pipe shaped, extends in the vertical direction, and has an internal space to which one end of each of the plurality of heat transfer pipes is connected in a communicating manner; a vertical partition plate which, in a horizontal cross-section, extends inside the header section between the inner peripheral surface of the header section and the heat transfer pipes, divides the inside of the header section into a first chamber and a second chamber, the first and second chambers being in communication with each of the heat transfer pipes, and has formed therein a first communication section for providing communication between the first chamber and the second chamber at a position higher than or equal to the height of the uppermost heat transfer pipe of the heat transfer pipes; and a flow path which is connected only to the first chamber of the first chamber and the second chamber and through which a refrigerant flows.
Description
本発明は、熱交換器及び空気調和機に関する。
本願は、2016年12月20日に出願された特願2016-247153号に基づき優先権を主張し、その内容をここに援用する。 The present invention relates to a heat exchanger and an air conditioner.
This application claims priority based on Japanese Patent Application No. 2016-247153 for which it applied on December 20, 2016, and uses the content here.
本願は、2016年12月20日に出願された特願2016-247153号に基づき優先権を主張し、その内容をここに援用する。 The present invention relates to a heat exchanger and an air conditioner.
This application claims priority based on Japanese Patent Application No. 2016-247153 for which it applied on December 20, 2016, and uses the content here.
空気調和機の熱交換器として、水平方向に延びる伝熱管を上下方向に間隔をあけて複数配置し、各伝熱管の外面にフィンを設けたものが知られている。複数の伝熱管の両端は上下方向に延びる一対のヘッダにそれぞれ接続されている。このような熱交換器では、一方のヘッダに導入されて伝熱管を経て他方のヘッダに流通した冷媒が、その他方のヘッダで折り返すようにして再度伝熱管を経て一方のヘッダに戻るように構成されている。
A heat exchanger for an air conditioner is known in which a plurality of heat transfer tubes extending in the horizontal direction are arranged at intervals in the vertical direction and fins are provided on the outer surface of each heat transfer tube. Both ends of the plurality of heat transfer tubes are respectively connected to a pair of headers extending in the vertical direction. In such a heat exchanger, the refrigerant introduced into one header and circulated through the heat transfer tube to the other header is folded back at the other header and returned to the one header again through the heat transfer tube. Has been.
折り返し側のヘッダ内には、該ヘッダ内を上下方向に区画する仕切板によって複数の領域が区画形成されている。これによって、ヘッダ内の一の領域内に伝熱管を経て導入された冷媒は、接続管を介してヘッダ内の他の領域に導入された後に、該他の領域に接続された複数の伝熱管を経由して出入口側の一方のヘッダに戻される。
冷媒が折り返しする際、比重の大きい液相冷媒は下方に流れやすく、また比重の小さい気相冷媒は上方に流れやすい。そのため、各伝熱管に流れ込む冷媒に偏流が生じる。
例えば特許文献1には、ヘッダ内を仕切板により伝熱管側空間と反伝熱管側空間とに区分けし、これら空間同士を上部及び下部で連通させることで冷媒の偏流を抑制させることが記載されている。 In the folded-back header, a plurality of regions are defined by partition plates that divide the header in the vertical direction. Thus, the refrigerant introduced into the one area in the header via the heat transfer tube is introduced into the other area in the header via the connection pipe, and then the plurality of heat transfer pipes connected to the other area. Is returned to one header on the entrance / exit side.
When the refrigerant turns, liquid phase refrigerant having a large specific gravity tends to flow downward, and gas phase refrigerant having a small specific gravity tends to flow upward. Therefore, a drift occurs in the refrigerant flowing into each heat transfer tube.
For example, Patent Document 1 describes that the header is divided into a heat transfer tube side space and a counter heat transfer tube side space by a partition plate, and these spaces are communicated with each other at an upper part and a lower part to suppress refrigerant drift. ing.
冷媒が折り返しする際、比重の大きい液相冷媒は下方に流れやすく、また比重の小さい気相冷媒は上方に流れやすい。そのため、各伝熱管に流れ込む冷媒に偏流が生じる。
例えば特許文献1には、ヘッダ内を仕切板により伝熱管側空間と反伝熱管側空間とに区分けし、これら空間同士を上部及び下部で連通させることで冷媒の偏流を抑制させることが記載されている。 In the folded-back header, a plurality of regions are defined by partition plates that divide the header in the vertical direction. Thus, the refrigerant introduced into the one area in the header via the heat transfer tube is introduced into the other area in the header via the connection pipe, and then the plurality of heat transfer pipes connected to the other area. Is returned to one header on the entrance / exit side.
When the refrigerant turns, liquid phase refrigerant having a large specific gravity tends to flow downward, and gas phase refrigerant having a small specific gravity tends to flow upward. Therefore, a drift occurs in the refrigerant flowing into each heat transfer tube.
For example, Patent Document 1 describes that the header is divided into a heat transfer tube side space and a counter heat transfer tube side space by a partition plate, and these spaces are communicated with each other at an upper part and a lower part to suppress refrigerant drift. ing.
液相冷媒と気相冷媒との気液分離による冷媒の偏流を抑制したとしても、冷媒がヘッダ内下部から流入しヘッダ内を上昇する際、各伝熱管に流れ込む冷媒流量の差が生じる。そのような状態では熱交換器の伝熱性能を十分に活用することができない。熱交換器の性能低下を抑制するためには、伝熱管に流れ込む冷媒流量は上部から下部のどの伝熱管でも均等化することが好ましい。
Even if the refrigerant drift due to gas-liquid separation between the liquid-phase refrigerant and the gas-phase refrigerant is suppressed, when the refrigerant flows in from the lower part in the header and rises in the header, a difference in the refrigerant flow rate flowing into each heat transfer tube occurs. In such a state, the heat transfer performance of the heat exchanger cannot be fully utilized. In order to suppress the performance deterioration of the heat exchanger, it is preferable that the refrigerant flow rate flowing into the heat transfer tube is equalized in any heat transfer tube from the upper part to the lower part.
本発明はこのような課題に鑑みてなされたものであって、性能低下を抑制することができる熱交換器、及び、該熱交換器を用いた空気調和機を提供することを目的とする。
This invention is made | formed in view of such a subject, Comprising: It aims at providing the heat exchanger which can suppress a performance fall, and the air conditioner using this heat exchanger.
本発明の第一態様の熱交換器は、水平方向に延びて内部に冷媒が流通するとともに、上下方向に間隔をあけて複数が配列された伝熱管と、上下方向に延びる管状をなして複数の前記伝熱管の一端が内部空間に連通状態で接続されたヘッダ部と、前記ヘッダ部内を水平断面視にて、各前記伝熱管と前記ヘッダ部内の内周面とにわたって延びて前記ヘッダ部内を各前記伝熱管とそれぞれ連通する第一室及び第二室とに区画するとともに、前記第一室及び前記第二室を前記伝熱管のうち最も上方の前記伝熱管の高さ以上の位置で互いに連通させる第一連通部を形成している縦仕切板と、前記第一室と前記第二室のうち前記第一室のみに接続されており、内部を冷媒が流通する流通路と、を備える。
The heat exchanger according to the first aspect of the present invention includes a plurality of heat exchanger tubes that extend in the horizontal direction and in which a refrigerant flows therethrough and that are arranged in a plurality at intervals in the vertical direction, and that have a tubular shape that extends in the vertical direction. The heat transfer tube has one end connected to an internal space in a communicating state, and the header portion extends in a horizontal sectional view across each heat transfer tube and the inner peripheral surface of the header portion to pass through the header portion. Each of the heat transfer tubes is partitioned into a first chamber and a second chamber, and the first chamber and the second chamber are separated from each other at a position equal to or higher than the height of the uppermost heat transfer tube among the heat transfer tubes. A vertical partition plate that forms a first communicating portion that communicates, and a flow passage that is connected only to the first chamber among the first chamber and the second chamber, and through which the refrigerant flows. Prepare.
このような熱交換器によれば、熱交換器が蒸発器として用いられる場合、流通路を介してヘッダ部内の第一室に冷媒が導入される。第一室に導入された冷媒の一部は各伝熱管に導入される。伝熱管に導入されなかった冷媒は、縦仕切板の上部に形成された第一連通部を介して第二室に導入され、第二室内を下方に移動しながら各伝熱管に導入されることになる。これによって、冷媒流量が少ない場合であっても第一室内を移動する冷媒の流速が下がることを抑制でき、ヘッダ部内の上部や中央部に接続される各伝熱管に導入される冷媒量が確保され、各伝熱管内を流通する冷媒流量のばらつきの発生を抑制できる。また、冷媒流量が多い場合、冷媒が第一室の上部に集中することがあるが、縦仕切板の上部に形成された第一連通部を介して第二室の上部に冷媒が導入され、第二室内を下方に移動しながら各伝熱管に導入されることになるので、冷媒はヘッダ部の上部に集中することなく、ヘッダ部内の下部や中央部に接続される各伝熱管に導入される冷媒量が確保されることになるので、各伝熱管内を流通する冷媒流量のばらつきの発生を抑制できる。
According to such a heat exchanger, when the heat exchanger is used as an evaporator, the refrigerant is introduced into the first chamber in the header portion through the flow path. A part of the refrigerant introduced into the first chamber is introduced into each heat transfer tube. The refrigerant that has not been introduced into the heat transfer tubes is introduced into the second chamber via the first communication portion formed in the upper part of the vertical partition plate, and is introduced into each heat transfer tube while moving downward in the second chamber. It will be. As a result, even when the refrigerant flow rate is small, the flow rate of the refrigerant moving in the first chamber can be suppressed, and the amount of refrigerant introduced into each heat transfer tube connected to the upper part or the central part in the header part is secured. Thus, it is possible to suppress the occurrence of variations in the flow rate of the refrigerant flowing through each heat transfer tube. In addition, when the flow rate of refrigerant is large, the refrigerant may concentrate on the upper part of the first chamber, but the refrigerant is introduced into the upper part of the second chamber through the first series part formed at the upper part of the vertical partition plate. Since the refrigerant is introduced into each heat transfer tube while moving downward in the second chamber, the refrigerant is introduced into each heat transfer tube connected to the lower part and the central part in the header part without concentrating on the upper part of the header part. As a result, the amount of refrigerant to be ensured is ensured, so that the variation in the flow rate of the refrigerant flowing through each heat transfer tube can be suppressed.
上記熱交換器では、前記第一連通部は、前記縦仕切板に形成された連通孔であってもよい。
In the above heat exchanger, the first series passage may be a communication hole formed in the vertical partition plate.
上記熱交換器では、前記第一連通部は、前記縦仕切板と前記ヘッダ部の上端との間の隙間であってもよい。
In the heat exchanger, the first series part may be a gap between the vertical partition plate and an upper end of the header part.
上記熱交換器では、前記縦仕切板は、上下に隣り合う前記伝熱管の間に、前記第一室及び前記第二室を互いに連通させる第二連通部を形成していてもよい。
In the heat exchanger, the vertical partition plate may form a second communication portion that allows the first chamber and the second chamber to communicate with each other between the vertically adjacent heat transfer tubes.
これによって、熱交換器が凝縮器として用いられる場合、各伝熱管からヘッダ部内の第一室および第二室へと冷媒が導入され、第一室に導入された冷媒は、流通路に導入される。第二室に導入された冷媒は、縦仕切板に形成された第二連通部を介して第一室に導入された後、流通路に導入される。これにより、各伝熱管から第二室へ導入された冷媒が第二室内で溜まり込むことなく、第二連通部を介して第一室へ導入され、流通路に導入することができる。
Thus, when the heat exchanger is used as a condenser, the refrigerant is introduced from each heat transfer tube into the first chamber and the second chamber in the header portion, and the refrigerant introduced into the first chamber is introduced into the flow passage. The The refrigerant introduced into the second chamber is introduced into the first chamber via the second communication portion formed in the vertical partition plate and then introduced into the flow passage. Thereby, the refrigerant introduced into the second chamber from each heat transfer tube can be introduced into the first chamber via the second communication portion without being accumulated in the second chamber and introduced into the flow passage.
上記熱交換器では、前記縦仕切板は、前記第一室と前記第二室とを前記伝熱管のうち最も下方の前記伝熱管よりも下方の位置で互いに連通させる第三連通部を形成していてもよい。
In the heat exchanger, the vertical partition plate forms a third communication portion that communicates the first chamber and the second chamber with each other at a position below the lowest heat transfer tube among the heat transfer tubes. It may be.
これによって、熱交換器が凝縮器として用いられる場合、各伝熱管からヘッダ部内の第一室および第二室へと冷媒が導入され、第一室に導入された冷媒は、流通路に導入される。第二室に導入された冷媒は、第二室内の下方に移動し、縦仕切板に形成された第三連通部を介して第一室に導入された後、流通路に導入される。これにより、各伝熱管から第二室へ導入された冷媒は第二室内で溜まり込むことなく、第二連通部を介して第一室へ導入され、流通路に導入することができる。
Thus, when the heat exchanger is used as a condenser, the refrigerant is introduced from each heat transfer tube into the first chamber and the second chamber in the header portion, and the refrigerant introduced into the first chamber is introduced into the flow passage. The The refrigerant introduced into the second chamber moves downward in the second chamber, is introduced into the first chamber via the third communication portion formed in the vertical partition plate, and is then introduced into the flow passage. Thereby, the refrigerant introduced into the second chamber from each heat transfer tube can be introduced into the first chamber via the second communication portion without being accumulated in the second chamber and introduced into the flow passage.
上記熱交換器では、前記縦仕切板の下部が前記第二室側から前記第一室側に湾曲しており、前記第三連通部は、前記縦仕切板と前記ヘッダ部の下端との間の隙間であってもよい。
In the heat exchanger, a lower portion of the vertical partition plate is curved from the second chamber side to the first chamber side, and the third communication portion is between the vertical partition plate and a lower end of the header portion. It may be a gap.
これによって、熱交換器が凝縮器として用いられる場合、各伝熱管からヘッダ部内の第一室および第二室へと冷媒が導入され、第一室に導入された冷媒は、流通路に導入される。第二室に導入された冷媒は、第二室内の下方に移動し、縦仕切板に形成された第三連通部を介して第一室に導入された後、流通路に導入される。これにより、各伝熱管から第二室へ導入された冷媒は第二室内で溜まり込むことなく、第二連通部を介して第一室へ導入され、流通路に導入することができる。さらに、縦仕切板の下部が第二室側へ湾曲されていることで、この湾曲形状が冷媒の流れをガイドすることになり、冷媒が第二室から第一室へ導入されやすくなる。
Thus, when the heat exchanger is used as a condenser, the refrigerant is introduced from each heat transfer tube into the first chamber and the second chamber in the header portion, and the refrigerant introduced into the first chamber is introduced into the flow passage. The The refrigerant introduced into the second chamber moves downward in the second chamber, is introduced into the first chamber via the third communication portion formed in the vertical partition plate, and is then introduced into the flow passage. Thereby, the refrigerant introduced into the second chamber from each heat transfer tube can be introduced into the first chamber via the second communication portion without being accumulated in the second chamber and introduced into the flow passage. Furthermore, since the lower part of the vertical partition plate is curved toward the second chamber, the curved shape guides the flow of the refrigerant, and the refrigerant is easily introduced from the second chamber into the first chamber.
上記熱交換器では、前記伝熱管の延在方向における該伝熱管の前記ヘッダ部内での長さLpは、前記ヘッダ部の内径Diの半分以下であってもよい。
In the heat exchanger, the length Lp of the heat transfer tube in the header portion in the extending direction of the heat transfer tube may be less than or equal to half of the inner diameter Di of the header portion.
これによって、熱交換器が蒸発器として用いられる場合、伝熱管におけるヘッダ部内の長さが短いため、流通路から第一室および第一室から第二室へ導入された気液二相状態の冷媒が第一室および第二室内の各伝熱管の上下間に溜まり込むことによる冷媒の流れの乱れを抑制することができ、液相冷媒が各伝熱管へ導入されやすくなる。これによりさらに各伝熱管内を流通する冷媒流量のばらつきの発生を抑制できる。
Thereby, when the heat exchanger is used as an evaporator, the length in the header portion of the heat transfer tube is short, so that the gas-liquid two-phase state introduced from the flow passage to the first chamber and the first chamber to the second chamber is Disturbances in the flow of the refrigerant due to the refrigerant collecting between the upper and lower portions of the heat transfer tubes in the first chamber and the second chamber can be suppressed, and the liquid-phase refrigerant is easily introduced into the heat transfer tubes. This further suppresses the occurrence of variations in the flow rate of the refrigerant flowing through each heat transfer tube.
本発明の第二態様に係る空気調和機は、上記いずれかの熱交換器を備える。
これによって、各伝熱管を流通する冷媒流量のばらつきの発生を抑制でき、冷房及び暖房性能の低下を回避することができる。 The air conditioner according to the second aspect of the present invention includes any one of the above heat exchangers.
As a result, it is possible to suppress the occurrence of variations in the flow rate of the refrigerant flowing through each heat transfer tube, and to avoid a decrease in cooling and heating performance.
これによって、各伝熱管を流通する冷媒流量のばらつきの発生を抑制でき、冷房及び暖房性能の低下を回避することができる。 The air conditioner according to the second aspect of the present invention includes any one of the above heat exchangers.
As a result, it is possible to suppress the occurrence of variations in the flow rate of the refrigerant flowing through each heat transfer tube, and to avoid a decrease in cooling and heating performance.
上述した熱交換器及び空気調和機によれば、複数の伝熱管を流通する冷媒流量の不均一化による性能低下を抑制することができる。
According to the heat exchanger and the air conditioner described above, it is possible to suppress performance degradation due to non-uniform refrigerant flow rates flowing through the plurality of heat transfer tubes.
以下、本発明の第一実施形態に係る熱交換器10を備えた空気調和機1について図1~4を参照して説明する。
図1に示すように、空気調和機1は、圧縮機2、室内熱交換器3(熱交換器10)、膨張弁4、室外熱交換器5(熱交換器10)、四方弁6、及び、これらを接続する配管7を備えており、これらからなる冷媒回路を構成している。 Hereinafter, an air conditioner 1 including aheat exchanger 10 according to a first embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 1, the air conditioner 1 includes acompressor 2, an indoor heat exchanger 3 (heat exchanger 10), an expansion valve 4, an outdoor heat exchanger 5 (heat exchanger 10), a four-way valve 6, and The pipe 7 for connecting them is provided, and a refrigerant circuit composed of these is constituted.
図1に示すように、空気調和機1は、圧縮機2、室内熱交換器3(熱交換器10)、膨張弁4、室外熱交換器5(熱交換器10)、四方弁6、及び、これらを接続する配管7を備えており、これらからなる冷媒回路を構成している。 Hereinafter, an air conditioner 1 including a
As shown in FIG. 1, the air conditioner 1 includes a
圧縮機2は、冷媒を圧縮し、圧縮した冷媒を冷媒回路に供給する。
室内熱交換器3は、冷媒と室内の空気との間で熱交換を行う。室内熱交換器3は、冷房運転時には蒸発器として用いられ室内から吸熱し、暖房運転時には凝縮器として用いられ室内へ放熱する。室外熱交換器5は、冷媒と室外の空気との間で熱交換を行う。
膨張弁4は、凝縮器で熱交換をすることで液化した高圧の冷媒を膨張させることで低圧化する。
室外熱交換器5は、冷房運転時には、凝縮器として用いられ室外へ放熱し、暖房運転時には、蒸発器として用いられ室外から吸熱する。
四方弁6は、暖房運転時と冷房運転時とで冷媒の流通する方向を切り替える。これにより、冷房運転時には、冷媒が、圧縮機2、室外熱交換器5、膨張弁4及び室内熱交換器3の順に循環する。一方、暖房運転時には、冷媒が、圧縮機2、室内熱交換器3、膨張弁4及び室外熱交換器5、の順に循環する。 Thecompressor 2 compresses the refrigerant and supplies the compressed refrigerant to the refrigerant circuit.
Theindoor heat exchanger 3 performs heat exchange between the refrigerant and the indoor air. The indoor heat exchanger 3 is used as an evaporator during cooling operation and absorbs heat from the room, and is used as a condenser during heating operation and dissipates heat to the room. The outdoor heat exchanger 5 performs heat exchange between the refrigerant and the outdoor air.
Theexpansion valve 4 reduces the pressure by expanding the high-pressure refrigerant liquefied by exchanging heat with the condenser.
Theoutdoor heat exchanger 5 is used as a condenser during the cooling operation and dissipates heat to the outside, and is used as an evaporator during the heating operation and absorbs heat from the outside.
The four-way valve 6 switches the direction in which the refrigerant flows between the heating operation and the cooling operation. Accordingly, during the cooling operation, the refrigerant circulates in the order of the compressor 2, the outdoor heat exchanger 5, the expansion valve 4, and the indoor heat exchanger 3. On the other hand, during the heating operation, the refrigerant circulates in the order of the compressor 2, the indoor heat exchanger 3, the expansion valve 4, and the outdoor heat exchanger 5.
室内熱交換器3は、冷媒と室内の空気との間で熱交換を行う。室内熱交換器3は、冷房運転時には蒸発器として用いられ室内から吸熱し、暖房運転時には凝縮器として用いられ室内へ放熱する。室外熱交換器5は、冷媒と室外の空気との間で熱交換を行う。
膨張弁4は、凝縮器で熱交換をすることで液化した高圧の冷媒を膨張させることで低圧化する。
室外熱交換器5は、冷房運転時には、凝縮器として用いられ室外へ放熱し、暖房運転時には、蒸発器として用いられ室外から吸熱する。
四方弁6は、暖房運転時と冷房運転時とで冷媒の流通する方向を切り替える。これにより、冷房運転時には、冷媒が、圧縮機2、室外熱交換器5、膨張弁4及び室内熱交換器3の順に循環する。一方、暖房運転時には、冷媒が、圧縮機2、室内熱交換器3、膨張弁4及び室外熱交換器5、の順に循環する。 The
The
The
The
The four-
次に、上記室内熱交換器3及び室外熱交換器5として用いられる熱交換器10について、図2~図4について説明する。
図2に示すように、熱交換器10は、複数の伝熱管20、複数のフィン23、一対のヘッダ30及び接続管55を備える。 Next, theheat exchanger 10 used as the indoor heat exchanger 3 and the outdoor heat exchanger 5 will be described with reference to FIGS.
As shown in FIG. 2, theheat exchanger 10 includes a plurality of heat transfer tubes 20, a plurality of fins 23, a pair of headers 30, and a connection tube 55.
図2に示すように、熱交換器10は、複数の伝熱管20、複数のフィン23、一対のヘッダ30及び接続管55を備える。 Next, the
As shown in FIG. 2, the
伝熱管20は、水平方向に直線状に延びる管状の部材であって、内部に冷媒が流通する流路が形成されている。このような伝熱管20は、上下方向に間隔をあけて複数が配列されており、互いに平行に配置されている。
本実施形態では、各伝熱管20は扁平管状をなしており、伝熱管20の内部には、該伝熱管20の延在方向に直交する水平方向に並設された複数の流路が形成されている。これら複数の流路は互いに平行に配列されている。これにより、伝熱管20の延在方向に直交する断面の外形は、伝熱管20の延在方向に直交する水平方向を長手方向とした扁平状とされている。 Theheat transfer tube 20 is a tubular member extending linearly in the horizontal direction, and a flow path through which the refrigerant flows is formed. A plurality of such heat transfer tubes 20 are arranged at intervals in the vertical direction, and are arranged in parallel to each other.
In this embodiment, eachheat transfer tube 20 has a flat tubular shape, and a plurality of flow paths arranged in parallel in the horizontal direction perpendicular to the extending direction of the heat transfer tube 20 are formed inside the heat transfer tube 20. ing. The plurality of flow paths are arranged in parallel to each other. Thereby, the outer shape of the cross section orthogonal to the extending direction of the heat transfer tube 20 is a flat shape with the horizontal direction orthogonal to the extending direction of the heat transfer tube 20 as the longitudinal direction.
本実施形態では、各伝熱管20は扁平管状をなしており、伝熱管20の内部には、該伝熱管20の延在方向に直交する水平方向に並設された複数の流路が形成されている。これら複数の流路は互いに平行に配列されている。これにより、伝熱管20の延在方向に直交する断面の外形は、伝熱管20の延在方向に直交する水平方向を長手方向とした扁平状とされている。 The
In this embodiment, each
フィン23は、上記のように配列された伝熱管20の間にそれぞれ配置されており、本実施形態では、各伝熱管20の延在方向に向かうにしたがって上下に隣り合う伝熱管20に交互に接触するように延びるいわゆるコルゲート状に延びている。なお、フィン23の形状はこれに限定されることはなく、伝熱管20の外周面から張り出すように設けられていれば、いかなる形状であってもよい。
The fins 23 are respectively disposed between the heat transfer tubes 20 arranged as described above. In this embodiment, the fins 23 are alternately arranged in the heat transfer tubes 20 adjacent to each other in the vertical direction as they extend in the extending direction of the heat transfer tubes 20. It extends in a so-called corrugated shape extending so as to come into contact. In addition, the shape of the fin 23 is not limited to this, and may be any shape as long as it is provided so as to protrude from the outer peripheral surface of the heat transfer tube 20.
一対のヘッダ30は、上記複数の伝熱管20の両端にこれら伝熱管20を挟み込むように設けられている。これら一対のヘッダ30の一方は、外部から熱交換器10内への冷媒の出入り口となる出入口側ヘッダ40とされている。これら一対のヘッダ30の他方は、熱交換器10内で冷媒が折り返すための折り返し側ヘッダ50とされている。
The pair of headers 30 are provided so as to sandwich the heat transfer tubes 20 at both ends of the plurality of heat transfer tubes 20. One of the pair of headers 30 is an inlet / outlet header 40 serving as an inlet / outlet of the refrigerant into the heat exchanger 10 from the outside. The other of the pair of headers 30 is a folded-back header 50 for the refrigerant to be folded in the heat exchanger 10.
出入口側ヘッダ40は、上下方向に延びる筒状の部材であって、上端及び下端が閉塞されるとともに内部が仕切板によって上下二つの領域に区画されている。出入側仕切板41によって区画された下方の領域は下部出入領域42とされている。出入側仕切板41によって区画された上方の領域は上部出入領域43とされている。これら下部出入領域42と上部出入領域43とは出入口側ヘッダ40内で互いに非連通状態とされている。これら下部出入領域42及び上部出入領域43は、冷媒回路を構成する配管7がそれぞれ接続されている。
ここで、複数の伝熱管20のうち、下部出入領域42と連通状態で接続されている伝熱管20は、第一伝熱管21とされている。複数の伝熱管20のうち、上部出入領域43と連通状態で接続されている伝熱管20は、第二伝熱管22(伝熱管20)とされている。 The entrance /exit header 40 is a cylindrical member extending in the up-down direction, the upper end and the lower end are closed, and the inside is partitioned into two upper and lower regions by a partition plate. A lower area defined by the entry / exit partition plate 41 is a lower entry / exit area 42. An upper area partitioned by the entrance / exit partition plate 41 is an upper entrance / exit area 43. The lower entrance / exit area 42 and the upper entrance / exit area 43 are not in communication with each other in the entrance / exit header 40. The lower entry / exit area 42 and the upper entry / exit area 43 are connected to the pipes 7 constituting the refrigerant circuit.
Here, among the plurality ofheat transfer tubes 20, the heat transfer tube 20 connected in communication with the lower entrance / exit region 42 is the first heat transfer tube 21. Among the plurality of heat transfer tubes 20, the heat transfer tube 20 connected in communication with the upper entrance / exit region 43 is a second heat transfer tube 22 (heat transfer tube 20).
ここで、複数の伝熱管20のうち、下部出入領域42と連通状態で接続されている伝熱管20は、第一伝熱管21とされている。複数の伝熱管20のうち、上部出入領域43と連通状態で接続されている伝熱管20は、第二伝熱管22(伝熱管20)とされている。 The entrance /
Here, among the plurality of
折り返し側ヘッダ50は、ヘッダ本体51、折り返し側仕切板54及び縦仕切板70を備えている。
ヘッダ本体51は、上下方向に延びる筒状をなす部材であって、上端及び下端が閉塞されている。折り返し側仕切板54は、ヘッダ本体51内に設けられ、該ヘッダ本体51内の空間を上下二つの領域に区画している。ヘッダ本体51の折り返し側仕切板54の下方の部分は第一ヘッダ部52とされている。ヘッダ本体51の折り返し側仕切板54の上方の部分は第二ヘッダ部53(ヘッダ部)とされている。即ち、本実施形態では、ヘッダ本体51内が折り返し側仕切板54によって区画されることで、折り返し側ヘッダ50に、それぞれ内部に空間を有する第一ヘッダ部52及び第二ヘッダ部53が形成されている。換言すれば、第一ヘッダ部52及び第二ヘッダ部53によって折り返し側ヘッダ50が構成されている。 The folded-back header 50 includes a header body 51, a folded-side partition plate 54, and a vertical partition plate 70.
The headermain body 51 is a cylindrical member extending in the vertical direction, and the upper end and the lower end are closed. The folding side partition plate 54 is provided in the header body 51, and divides the space in the header body 51 into two upper and lower areas. A lower portion of the folding side partition plate 54 of the header body 51 is a first header portion 52. The upper part of the folding side partition plate 54 of the header body 51 is a second header part 53 (header part). That is, in the present embodiment, the header main body 51 is partitioned by the folding side partition plate 54, so that the first header portion 52 and the second header portion 53 each having a space therein are formed in the folding side header 50. ing. In other words, the first header portion 52 and the second header portion 53 constitute the folded-back header 50.
ヘッダ本体51は、上下方向に延びる筒状をなす部材であって、上端及び下端が閉塞されている。折り返し側仕切板54は、ヘッダ本体51内に設けられ、該ヘッダ本体51内の空間を上下二つの領域に区画している。ヘッダ本体51の折り返し側仕切板54の下方の部分は第一ヘッダ部52とされている。ヘッダ本体51の折り返し側仕切板54の上方の部分は第二ヘッダ部53(ヘッダ部)とされている。即ち、本実施形態では、ヘッダ本体51内が折り返し側仕切板54によって区画されることで、折り返し側ヘッダ50に、それぞれ内部に空間を有する第一ヘッダ部52及び第二ヘッダ部53が形成されている。換言すれば、第一ヘッダ部52及び第二ヘッダ部53によって折り返し側ヘッダ50が構成されている。 The folded-
The header
上記第一伝熱管21は、それぞれ第一ヘッダ部52内と連通状態となるように該第一ヘッダ部52に水平方向一方側から接続されている。また、上記第二伝熱管22は、それぞれ第二ヘッダ部53内と連通状態となるように水平方向一方側から該第二ヘッダ部53に接続されている。換言すれば、第一ヘッダ部52に接続されている伝熱管20が第一伝熱管21とされ、第二ヘッダ部53に接続されている伝熱管20が第二伝熱管22とされている。
The first heat transfer tube 21 is connected to the first header portion 52 from one side in the horizontal direction so as to communicate with the inside of the first header portion 52. The second heat transfer tubes 22 are connected to the second header portion 53 from one side in the horizontal direction so as to communicate with the inside of the second header portion 53, respectively. In other words, the heat transfer tube 20 connected to the first header portion 52 is the first heat transfer tube 21, and the heat transfer tube 20 connected to the second header portion 53 is the second heat transfer tube 22.
図3に示すように、縦仕切板70は、上下方向に延びる板状の部材であって、第二ヘッダ部53内に設けられている。縦仕切板70は、第二ヘッダ部53内の空間を水平断面視にて、それぞれが各第二伝熱管22と連通するよう第一室76と第二室77との二つの領域に区画している。具体的には、縦仕切板70は、水平断面視にて第二伝熱管22が延びる方向に設置される。縦仕切板70は、第二ヘッダ部53内で水平方向にわたって延びている。これによって本実施形態では、上下に隣り合う第二伝熱管22の間でも縦仕切板70によって第一室76及び第二室77とが隔てられている各第二伝熱管が前記第二ヘッダ部53内に突出した部分では、縦仕切板70の水平方向の両端のうちの第二伝熱管側の一端は、第二伝熱管に接触している。各第二伝熱管22の開口部は、縦仕切板の一端によって第二伝熱管22の延在方向に直交する水平方向に分割されている。
As shown in FIG. 3, the vertical partition plate 70 is a plate-like member extending in the vertical direction, and is provided in the second header portion 53. The vertical partition plate 70 divides the space in the second header portion 53 into two regions of a first chamber 76 and a second chamber 77 so that each space communicates with each second heat transfer tube 22 in a horizontal sectional view. ing. Specifically, the vertical partition plate 70 is installed in a direction in which the second heat transfer tube 22 extends in a horizontal sectional view. The vertical partition plate 70 extends in the horizontal direction in the second header portion 53. Accordingly, in the present embodiment, each second heat transfer tube in which the first chamber 76 and the second chamber 77 are separated by the vertical partition plate 70 also between the second heat transfer tubes 22 adjacent in the vertical direction is the second header portion. In the part protruded in 53, the one end by the side of the 2nd heat exchanger tube among the both ends of the horizontal direction of the vertical partition plate 70 is contacting the 2nd heat exchanger tube. The opening of each second heat transfer tube 22 is divided in the horizontal direction perpendicular to the extending direction of the second heat transfer tube 22 by one end of the vertical partition plate.
接続管55は、内部に流路が形成された管状の部材であって、その一端が第一ヘッダ部52に対して該第一ヘッダ部52の内部と連通状態で接続されており、他端が第二ヘッダ部53に対して該第二ヘッダ部53の内部と連通状態で接続されている。より詳細には、接続管55の一端は、第一ヘッダ部52における上下方向の中央部に接続されている。一方で、接続管55の他端は、第二ヘッダ部53の第一室76における下部に接続されている。
この接続管55の内側に形成された流路が、第一ヘッダ部52内と第二ヘッダ部53内との間で冷媒の流通を可能とする流通路56とされている。
なお、接続管55を用いず、折り返し側仕切板54に第一ヘッダ部52内と第一室76とを直接連通するよう流通路56を形成してもよい。 The connectingpipe 55 is a tubular member having a flow path formed therein, and one end of the connecting pipe 55 is connected to the first header portion 52 in communication with the inside of the first header portion 52, and the other end. Is connected to the second header portion 53 in communication with the inside of the second header portion 53. More specifically, one end of the connection pipe 55 is connected to the central portion of the first header portion 52 in the vertical direction. On the other hand, the other end of the connection pipe 55 is connected to the lower part of the first chamber 76 of the second header part 53.
A flow path formed inside theconnection pipe 55 serves as a flow passage 56 that allows the refrigerant to flow between the first header portion 52 and the second header portion 53.
Instead of using the connectingpipe 55, the flow passage 56 may be formed so as to directly connect the inside of the first header portion 52 and the first chamber 76 to the folded-back partition plate 54.
この接続管55の内側に形成された流路が、第一ヘッダ部52内と第二ヘッダ部53内との間で冷媒の流通を可能とする流通路56とされている。
なお、接続管55を用いず、折り返し側仕切板54に第一ヘッダ部52内と第一室76とを直接連通するよう流通路56を形成してもよい。 The connecting
A flow path formed inside the
Instead of using the connecting
本実施形態では、ヘッダ30は上下方向に延びる円筒形状をなしており、これにともなって内部空間も円筒状をなしている。そして、縦仕切板70は、円筒状をなす第二ヘッダ部53の内部空間の水平断面視における直径方向に沿うようにして配置されている。これによって、第一室76及び第二室77はそれぞれ水平断面視が半円形状をなしている。
In the present embodiment, the header 30 has a cylindrical shape extending in the vertical direction, and the internal space is also cylindrical. And the vertical partition plate 70 is arrange | positioned so that the diametrical direction in the horizontal cross sectional view of the internal space of the cylindrical 2nd header part 53 may be followed. As a result, the first chamber 76 and the second chamber 77 each have a semicircular shape in a horizontal sectional view.
縦仕切板70には、該縦仕切板70を貫通することで第一室76と第二室77とを連通させる上部連通孔62(第一連通部61)が形成されている。上部連通孔62は、詳しくは図5に示すように、各第二伝熱管22のうち最も上方に位置する伝熱管である第二ヘッダ部最上部伝熱管24の高さと同一又はこれよりも高い位置に形成されている。上部連通孔62は、水平断面視にて、第二伝熱管22の先端よりも先の位置、すなわち第二ヘッダ部53と第二伝熱管22との接続部とは反対側に形成されている。
In the vertical partition plate 70, an upper communication hole 62 (first communication portion 61) that allows the first chamber 76 and the second chamber 77 to communicate with each other by penetrating the vertical partition plate 70 is formed. Specifically, as shown in FIG. 5, the upper communication hole 62 is equal to or higher than the height of the second header portion uppermost heat transfer tube 24, which is the heat transfer tube located at the uppermost position among the second heat transfer tubes 22. Formed in position. The upper communication hole 62 is formed at a position ahead of the tip of the second heat transfer tube 22, that is, on the side opposite to the connection portion between the second header portion 53 and the second heat transfer tube 22 in the horizontal sectional view. .
次に上記熱交換器10が蒸発器として用いられる場合の作用・効果について説明する。
なお、熱交換器10が室内熱交換器3の場合は空気調和機1の冷房運転時に蒸発器として用いられることになり、室外熱交換器5の場合には空気調和機1の暖房運転時に蒸発器として用いられることになる。 Next, operations and effects when theheat exchanger 10 is used as an evaporator will be described.
When theheat exchanger 10 is the indoor heat exchanger 3, it is used as an evaporator during the cooling operation of the air conditioner 1, and when the outdoor heat exchanger 5 is used, it evaporates during the heating operation of the air conditioner 1. It will be used as a container.
なお、熱交換器10が室内熱交換器3の場合は空気調和機1の冷房運転時に蒸発器として用いられることになり、室外熱交換器5の場合には空気調和機1の暖房運転時に蒸発器として用いられることになる。 Next, operations and effects when the
When the
熱交換器10が蒸発器として用いられる際には、図2に示す出入口側ヘッダ40の下部出入領域42に配管7から液相分の多い気液二相冷媒が供給される。この冷媒は、下部出入領域42で複数の第一伝熱管21内に分配供給され、第一伝熱管21を流通する過程で該第一伝熱管21の外部雰囲気との間で熱交換することで蒸発が促される。これにより、第一伝熱管21から折り返し側ヘッダ50の第一ヘッダ部52内に供給される冷媒は、一部が液相から気相に変化したことで液相割合が減少した気液二相冷媒となる。
When the heat exchanger 10 is used as an evaporator, a gas-liquid two-phase refrigerant with a large liquid phase is supplied from the pipe 7 to the lower inlet / outlet region 42 of the inlet / outlet header 40 shown in FIG. This refrigerant is distributed and supplied into the plurality of first heat transfer tubes 21 in the lower entrance / exit region 42, and exchanges heat with the external atmosphere of the first heat transfer tubes 21 in the process of flowing through the first heat transfer tubes 21. Evaporation is encouraged. Accordingly, the refrigerant supplied from the first heat transfer tube 21 into the first header portion 52 of the folded-back header 50 is a gas-liquid two-phase in which the liquid phase ratio is reduced due to a partial change from the liquid phase to the gas phase. Becomes a refrigerant.
そして、図2及び図3に示すように、第一ヘッダ部52内に供給される気液二相状態の冷媒は、該第一ヘッダ部52に接続された接続管55内に導入され、該接続管55を介して該第二ヘッダ部53内の第一室76に導入される。
第一室76に導入された冷媒は、冷媒が供給され続けるにしたがって順次第一室76内を上方に移動し各第二伝熱管22に導入される。第二伝熱管22に導入されなかった冷媒は、縦仕切板70の上部に形成された上部連通孔62を介して第二室77の上部に導入される。第二室77の上部に導入された冷媒は、第二室77内を下方に移動しながら各第二伝熱管22に導入される。 As shown in FIGS. 2 and 3, the gas-liquid two-phase refrigerant supplied into thefirst header portion 52 is introduced into a connecting pipe 55 connected to the first header portion 52, and It is introduced into the first chamber 76 in the second header portion 53 through the connecting pipe 55.
The refrigerant introduced into thefirst chamber 76 sequentially moves upward in the first chamber 76 as the refrigerant continues to be supplied, and is introduced into each second heat transfer tube 22. The refrigerant that has not been introduced into the second heat transfer tube 22 is introduced into the upper portion of the second chamber 77 through the upper communication hole 62 formed in the upper portion of the vertical partition plate 70. The refrigerant introduced into the upper portion of the second chamber 77 is introduced into each second heat transfer tube 22 while moving downward in the second chamber 77.
第一室76に導入された冷媒は、冷媒が供給され続けるにしたがって順次第一室76内を上方に移動し各第二伝熱管22に導入される。第二伝熱管22に導入されなかった冷媒は、縦仕切板70の上部に形成された上部連通孔62を介して第二室77の上部に導入される。第二室77の上部に導入された冷媒は、第二室77内を下方に移動しながら各第二伝熱管22に導入される。 As shown in FIGS. 2 and 3, the gas-liquid two-phase refrigerant supplied into the
The refrigerant introduced into the
ここで、第二ヘッダ部53を縦仕切板70により第一室76と第二室77とに区分けしているため、第一室76の冷媒流路の断面積は第二ヘッダ部53全体としての断面積よりも小さくなっている。このため、冷媒流量が少ない場合であっても第一室76内を上方に移動する冷媒の流速が下がることを抑制でき、第二ヘッダ部53内の上部や中央部に接続される各第二伝熱管22に導入される冷媒量が確保され、各第二伝熱管22内を流通する冷媒流量のばらつきの発生を抑制できる。また、冷媒流量が著しく多い場合は、冷媒が第一室76の上部に集中することがあるが、縦仕切板70の上部に形成された上部連通孔62を介して第二室77の上部に冷媒が導入され、第二室77内を下方に移動しながら各第二伝熱管22に導入されることになるので、冷媒は第二ヘッダ部53の上部に集中することなく、第二ヘッダ部53内の下部や中央部に接続される各第二伝熱管22に導入される冷媒量が確保されることになり、やはり各第二伝熱管22内を流通する冷媒流量のばらつきの発生を抑制できる。
Here, since the second header portion 53 is divided into the first chamber 76 and the second chamber 77 by the vertical partition plate 70, the cross-sectional area of the refrigerant flow path in the first chamber 76 is the entire second header portion 53. It is smaller than the cross-sectional area. For this reason, even if it is a case where there is little refrigerant | coolant flow volume, it can suppress that the flow velocity of the refrigerant | coolant moving upwards in the 1st chamber 76 falls, and each 2nd connected to the upper part in the 2nd header part 53 or a center part. The amount of refrigerant introduced into the heat transfer tubes 22 is ensured, and the occurrence of variations in the flow rate of the refrigerant flowing through each second heat transfer tube 22 can be suppressed. In addition, when the flow rate of the refrigerant is extremely high, the refrigerant may concentrate on the upper portion of the first chamber 76, but the upper portion of the second chamber 77 is formed via the upper communication hole 62 formed on the upper portion of the vertical partition plate 70. Since the refrigerant is introduced and introduced into each of the second heat transfer tubes 22 while moving downward in the second chamber 77, the refrigerant does not concentrate on the upper portion of the second header portion 53, and the second header portion. Thus, the amount of refrigerant introduced into each second heat transfer tube 22 connected to the lower part or the center part in 53 is secured, and also the occurrence of variation in the flow rate of refrigerant flowing through each second heat transfer tube 22 is suppressed. it can.
その後、冷媒は、第二伝熱管22を流通する過程で該第二伝熱管22の外部雰囲気との間で熱交換することで、再度蒸発が促される。
これにより、第二伝熱管22内にて、冷媒における残存していた液相が気相に変化し、出入口側ヘッダ40の上部出入領域43には気相状態の冷媒が供給される。そして、この冷媒は上部出入領域43から配管7に導入され、冷媒回路を循環することになる。 Thereafter, the refrigerant is urged to evaporate again by exchanging heat with the external atmosphere of the secondheat transfer tube 22 in the course of flowing through the second heat transfer tube 22.
As a result, the liquid phase remaining in the refrigerant changes into a gas phase in the secondheat transfer tube 22, and the gas phase refrigerant is supplied to the upper entrance / exit region 43 of the inlet / outlet header 40. Then, the refrigerant is introduced into the pipe 7 from the upper entrance / exit area 43 and circulates in the refrigerant circuit.
これにより、第二伝熱管22内にて、冷媒における残存していた液相が気相に変化し、出入口側ヘッダ40の上部出入領域43には気相状態の冷媒が供給される。そして、この冷媒は上部出入領域43から配管7に導入され、冷媒回路を循環することになる。 Thereafter, the refrigerant is urged to evaporate again by exchanging heat with the external atmosphere of the second
As a result, the liquid phase remaining in the refrigerant changes into a gas phase in the second
以上のように、本実施形態の熱交換器10によれば、第二ヘッダ部53に供給された冷媒は、冷媒流量が少ない場合であっても多い場合であっても各第二伝熱管22に導入される冷媒量のばらつきの発生を抑制でき、伝熱管に流れ込む冷媒流量の偏りによる熱交換器の性能低下を抑制することができる。その結果、本実施形態の熱交換器10を用いた空気調和機では、冷房性能や暖房性能が損なわれることはない。
As described above, according to the heat exchanger 10 of the present embodiment, the refrigerant supplied to the second header portion 53 can be used for each second heat transfer tube 22 regardless of whether the refrigerant flow rate is small or large. The variation in the amount of refrigerant introduced into the heat exchanger can be suppressed, and the performance deterioration of the heat exchanger due to the deviation of the refrigerant flow rate flowing into the heat transfer tube can be suppressed. As a result, in the air conditioner using the heat exchanger 10 of the present embodiment, the cooling performance and the heating performance are not impaired.
なお、第一実施形態の変形例として、縦仕切板70に上部連通孔62を形成するのではなく、例えば図6、図7及び図8に示すように、縦仕切板70の高さを第二ヘッダ部最上部伝熱管24と同じ高さ又は第二ヘッダ部最上部伝熱管24から第二ヘッダ部53の上端までの間の高さとしてもよい。この場合、縦仕切板70と第二ヘッダ部53との間には隙間が形成され、当該隙間が第一室76と第二室77とを連通させる上部連通部63(第一連通部61)となる。
これによっても、第一室76に導入された冷媒は、冷媒が供給され続けるにしたがって順次第一室76内を上方に移動し各第二伝熱管22に導入され、第一室76から各第二伝熱管22に導入されなかった冷媒は、縦仕切板70の上部に形成された上部連通部63を介して第二室77の上部に冷媒が導入され、第二室内を下方に移動しながら各第二伝熱管22に導入されることになるので、上記同様に各第二伝熱管22に導入される冷媒量のばらつきの発生を抑制できる。 As a modification of the first embodiment, instead of forming theupper communication hole 62 in the vertical partition plate 70, for example, as shown in FIGS. The height may be the same height as the two header portion uppermost heat transfer tubes 24 or the height between the second header portion uppermost heat transfer tube 24 and the upper end of the second header portion 53. In this case, a gap is formed between the vertical partition plate 70 and the second header portion 53, and the gap communicates the first chamber 76 and the second chamber 77 with the upper communication portion 63 (first communication portion 61). )
Also in this way, the refrigerant introduced into thefirst chamber 76 sequentially moves upward in the first chamber 76 as the refrigerant continues to be supplied, and is introduced into each second heat transfer tube 22. The refrigerant that has not been introduced into the second heat transfer tube 22 is introduced into the upper portion of the second chamber 77 via the upper communication portion 63 formed at the upper portion of the vertical partition plate 70, and moves downward in the second chamber. Since it will be introduced into each second heat transfer tube 22, the occurrence of variations in the amount of refrigerant introduced into each second heat transfer tube 22 can be suppressed as described above.
これによっても、第一室76に導入された冷媒は、冷媒が供給され続けるにしたがって順次第一室76内を上方に移動し各第二伝熱管22に導入され、第一室76から各第二伝熱管22に導入されなかった冷媒は、縦仕切板70の上部に形成された上部連通部63を介して第二室77の上部に冷媒が導入され、第二室内を下方に移動しながら各第二伝熱管22に導入されることになるので、上記同様に各第二伝熱管22に導入される冷媒量のばらつきの発生を抑制できる。 As a modification of the first embodiment, instead of forming the
Also in this way, the refrigerant introduced into the
次に本発明の第二実施形態に係る熱交換器80について、図9、図10及び図11を参照して説明する。なお、第二実施形態では、第一実施形態と同様の構成要素については、該第一実施形態同一の符号を付して詳細な説明を省略する。
図9、図10及び図11に示すように、第二実施形態の熱交換器80の縦仕切板71は、第一実施形態と同様に、円筒状をなす第二ヘッダ部53の内部空間の水平断面視における直径方向に沿うようにして配置されている。縦仕切板71は、第一実施形態と同様の上部連通孔62が形成されている。一方、本実施形態では、さらに縦仕切板71の水平方向の長さは、伝熱管22の先端位置から第二ヘッダ部53の内周面までとされている。第二ヘッダ部53内における各伝熱管22の上下の部分には縦仕切板71がなく、これによって第一室76と第二室77とを連通させる伝熱管側連通部65(第二連通部64)が形成されている。 Next, theheat exchanger 80 which concerns on 2nd embodiment of this invention is demonstrated with reference to FIG.9, FIG10 and FIG.11. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
As shown in FIGS. 9, 10, and 11, thevertical partition plate 71 of the heat exchanger 80 of the second embodiment is similar to the first embodiment in the internal space of the cylindrical second header portion 53. It arrange | positions so that the diametrical direction in a horizontal sectional view may be met. The vertical partition plate 71 is formed with an upper communication hole 62 similar to that of the first embodiment. On the other hand, in the present embodiment, the length of the vertical partition plate 71 in the horizontal direction is from the tip position of the heat transfer tube 22 to the inner peripheral surface of the second header portion 53. The upper and lower portions of each heat transfer tube 22 in the second header portion 53 are not provided with the vertical partition plate 71, and thereby the heat transfer tube side communication portion 65 (second communication portion) for communicating the first chamber 76 and the second chamber 77. 64) is formed.
図9、図10及び図11に示すように、第二実施形態の熱交換器80の縦仕切板71は、第一実施形態と同様に、円筒状をなす第二ヘッダ部53の内部空間の水平断面視における直径方向に沿うようにして配置されている。縦仕切板71は、第一実施形態と同様の上部連通孔62が形成されている。一方、本実施形態では、さらに縦仕切板71の水平方向の長さは、伝熱管22の先端位置から第二ヘッダ部53の内周面までとされている。第二ヘッダ部53内における各伝熱管22の上下の部分には縦仕切板71がなく、これによって第一室76と第二室77とを連通させる伝熱管側連通部65(第二連通部64)が形成されている。 Next, the
As shown in FIGS. 9, 10, and 11, the
次に上記熱交換器80が凝縮器として用いられる場合の作用・効果について説明する。
空気調和機1の冷房運転時に熱交換器80が凝縮器として作動する際、蒸発器として用いられる場合とは逆に、各第二伝熱管22から第二ヘッダ部53内の第一室76および第二室77へと冷媒が導入される。第一室76に導入された冷媒は、第一室76内の下方へ移動し、接続管55を介して第一ヘッダ部52に導入される。第二室77に導入された冷媒は、縦仕切板71に形成された伝熱管側連通部65を介して第一室76に導入された後、接続管55を介して第一ヘッダ部52に導入される。 Next, operations and effects when theheat exchanger 80 is used as a condenser will be described.
When theheat exchanger 80 operates as a condenser during the cooling operation of the air conditioner 1, contrary to the case where the heat exchanger 80 is used as an evaporator, the first chamber 76 in the second header portion 53 from each second heat transfer tube 22 and A refrigerant is introduced into the second chamber 77. The refrigerant introduced into the first chamber 76 moves downward in the first chamber 76 and is introduced into the first header portion 52 via the connection pipe 55. The refrigerant introduced into the second chamber 77 is introduced into the first chamber 76 via the heat transfer tube side communication portion 65 formed in the vertical partition plate 71 and then into the first header portion 52 via the connection tube 55. be introduced.
空気調和機1の冷房運転時に熱交換器80が凝縮器として作動する際、蒸発器として用いられる場合とは逆に、各第二伝熱管22から第二ヘッダ部53内の第一室76および第二室77へと冷媒が導入される。第一室76に導入された冷媒は、第一室76内の下方へ移動し、接続管55を介して第一ヘッダ部52に導入される。第二室77に導入された冷媒は、縦仕切板71に形成された伝熱管側連通部65を介して第一室76に導入された後、接続管55を介して第一ヘッダ部52に導入される。 Next, operations and effects when the
When the
以上のように、本実施形態の熱交換器80によれば、蒸発器として作動する場合は第一実施形態と同様であるが、さらに凝縮器として作動する場合、各第二伝熱管22から第二室77へ導入された冷媒が第二室77内で溜まり込むことなく、縦仕切板71に形成された伝熱管側連通部65を介して第一室76へ導入され、第一室76の下部に接続された接続管55を介して第一ヘッダ部に導入することができる。その結果、本実施形態の熱交換器80を用いた空気調和機では、冷房性能や暖房性能が損なわれることはない。
As described above, according to the heat exchanger 80 of the present embodiment, when operating as an evaporator, it is the same as in the first embodiment, but when operating as a condenser, the second heat transfer tube 22 The refrigerant introduced into the second chamber 77 does not accumulate in the second chamber 77 and is introduced into the first chamber 76 via the heat transfer tube side communication portion 65 formed in the vertical partition plate 71. It can introduce | transduce into a 1st header part via the connecting pipe 55 connected to the lower part. As a result, in the air conditioner using the heat exchanger 80 of the present embodiment, the cooling performance and the heating performance are not impaired.
なお、第二実施形態の変形例として、縦仕切板71の水平方向の長さは、第一実施形態と同様であるが、例えば図12、図13及び図14に示すように、縦仕切板71における各第二伝熱管22の上下に相当する部分に伝熱管側連通孔66(第二連通部64)を形成し、第一室76と第二室77とを連通させてもよい。これによっても、各第二伝熱管22から第二室77へと導入された冷媒が第二室77内で溜まり込むことなく、縦仕切板71に形成された伝熱管側連通孔66を介して第一室76へ導入され、第一室76の下部に接続された接続管55を介して第一ヘッダ部に導入することができる。その結果、本実施形態の熱交換器80を用いた空気調和機では、冷房性能や暖房性能が損なわれることはない。
As a modification of the second embodiment, the length of the vertical partition plate 71 in the horizontal direction is the same as that of the first embodiment. For example, as shown in FIG. 12, FIG. 13 and FIG. The heat transfer tube side communication holes 66 (second communication portions 64) may be formed in portions corresponding to the upper and lower portions of the second heat transfer tubes 22 in 71 so that the first chamber 76 and the second chamber 77 communicate with each other. Also by this, the refrigerant introduced from each second heat transfer tube 22 into the second chamber 77 does not accumulate in the second chamber 77, and passes through the heat transfer tube side communication hole 66 formed in the vertical partition plate 71. It is introduced into the first chamber 76 and can be introduced into the first header portion via the connecting pipe 55 connected to the lower portion of the first chamber 76. As a result, in the air conditioner using the heat exchanger 80 of the present embodiment, the cooling performance and the heating performance are not impaired.
次に本発明の第三実施形態に係る熱交換器90について、図15、図16及び図17を参照して説明する。なお、第三実施形態では、第一実施形態と同様の構成要素については、該第一実施形態同一の符号を付して詳細な説明を省略する。
図15、図16及び図17に示すように、第三実施形態の熱交換器90の縦仕切板72は、第一実施形態と同様に、円筒状をなす第二ヘッダ部53の内部空間の水平断面視における直径方向に沿うようにして配置され、第一実施形態同様の上部連通孔62が形成されている。本実施形態では、さらに縦仕切板72は、各第二伝熱管22中の最下部に位置する伝熱管である第二ヘッダ部最下部伝熱管25よりも下方の位置で第一室76と第二室77とを連通させる下部連通孔68(第三連通部67)が形成されている。また、下部連通孔68は、水平断面視にて、第二伝熱管22の先端よりも先の位置、即ち、第二ヘッダ部53と第二伝熱管22との接続部とは反対側に形成される。 Next, theheat exchanger 90 which concerns on 3rd embodiment of this invention is demonstrated with reference to FIG.15, FIG16 and FIG.17. In the third embodiment, the same components as those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
As shown in FIGS. 15, 16, and 17, thevertical partition plate 72 of the heat exchanger 90 of the third embodiment is similar to the first embodiment in the internal space of the cylindrical second header portion 53. Arranged along the diameter direction in the horizontal sectional view, an upper communication hole 62 similar to the first embodiment is formed. In the present embodiment, the vertical partition plate 72 further includes the first chamber 76 and the first chamber 76 at a position lower than the second header portion lowermost heat transfer tube 25, which is a heat transfer tube located at the lowermost portion in each second heat transfer tube 22. A lower communication hole 68 (third communication portion 67) for communicating with the two chambers 77 is formed. Further, the lower communication hole 68 is formed at a position ahead of the tip of the second heat transfer tube 22, that is, on the side opposite to the connection portion between the second header portion 53 and the second heat transfer tube 22 in a horizontal sectional view. Is done.
図15、図16及び図17に示すように、第三実施形態の熱交換器90の縦仕切板72は、第一実施形態と同様に、円筒状をなす第二ヘッダ部53の内部空間の水平断面視における直径方向に沿うようにして配置され、第一実施形態同様の上部連通孔62が形成されている。本実施形態では、さらに縦仕切板72は、各第二伝熱管22中の最下部に位置する伝熱管である第二ヘッダ部最下部伝熱管25よりも下方の位置で第一室76と第二室77とを連通させる下部連通孔68(第三連通部67)が形成されている。また、下部連通孔68は、水平断面視にて、第二伝熱管22の先端よりも先の位置、即ち、第二ヘッダ部53と第二伝熱管22との接続部とは反対側に形成される。 Next, the
As shown in FIGS. 15, 16, and 17, the
次に上記熱交換器90が凝縮器として用いられる場合の作用・効果について説明する。
空気調和機1の冷房運転時に熱交換器90が凝縮器として作動する際、蒸発器として用いられる場合とは逆に、各第二伝熱管22から第二ヘッダ部53内の第一室76および第二室77へと冷媒が導入される。第一室76に導入された冷媒は、第一室76内の下方へ移動し、接続管55を介して第一ヘッダ部52に導入される。第二室77内に導入された冷媒は、第二室77内の下方に移動し、その後、縦仕切板72に形成された下部連通孔68を介して第一室76に導入された後、接続管55を介して該第一ヘッダ部52に導入される。 Next, operations and effects when theheat exchanger 90 is used as a condenser will be described.
When theheat exchanger 90 operates as a condenser during the cooling operation of the air conditioner 1, contrary to the case where it is used as an evaporator, the first chamber 76 in the second header section 53 from each second heat transfer tube 22 and A refrigerant is introduced into the second chamber 77. The refrigerant introduced into the first chamber 76 moves downward in the first chamber 76 and is introduced into the first header portion 52 via the connection pipe 55. The refrigerant introduced into the second chamber 77 moves downward in the second chamber 77, and then introduced into the first chamber 76 via the lower communication hole 68 formed in the vertical partition plate 72. It is introduced into the first header portion 52 through the connecting pipe 55.
空気調和機1の冷房運転時に熱交換器90が凝縮器として作動する際、蒸発器として用いられる場合とは逆に、各第二伝熱管22から第二ヘッダ部53内の第一室76および第二室77へと冷媒が導入される。第一室76に導入された冷媒は、第一室76内の下方へ移動し、接続管55を介して第一ヘッダ部52に導入される。第二室77内に導入された冷媒は、第二室77内の下方に移動し、その後、縦仕切板72に形成された下部連通孔68を介して第一室76に導入された後、接続管55を介して該第一ヘッダ部52に導入される。 Next, operations and effects when the
When the
以上のように、本実施形態の熱交換器90によれば、蒸発器として作動する場合は第一実施形態と同様であるが、さらに凝縮器として作動する場合、各第二伝熱管22から第二室77へ導入された冷媒が第二室77内で溜まり込むことなく、縦仕切板72に形成された下部連通孔68を介して第一室76へ導入され、第一室76の下部に接続された接続管55を介して第一ヘッダ部に導入することができる。その結果、本実施形態の熱交換器90を用いた空気調和機では、冷房性能や暖房性能が損なわれることはない。
As described above, according to the heat exchanger 90 of the present embodiment, when operating as an evaporator, it is the same as in the first embodiment, but when operating as a condenser, the second heat transfer tube 22 The refrigerant introduced into the second chamber 77 does not accumulate in the second chamber 77 and is introduced into the first chamber 76 through the lower communication hole 68 formed in the vertical partition plate 72, and is placed in the lower portion of the first chamber 76. It can introduce into a 1st header part via the connected connecting pipe 55. FIG. As a result, in the air conditioner using the heat exchanger 90 of the present embodiment, the cooling performance and the heating performance are not impaired.
なお、第三実施形態の変形例として、例えば図18、図19及び図20に示すように、縦仕切板72の下部を第一室76側へ湾曲させ、第二ヘッダ部最下部伝熱管25よりも下方に第一室76と第二室77とを連通させる下部連通部69(第三連通部67)を形成させてもよい。この場合、下部連通部69は縦仕切板72の下端と第二ヘッダ部53の下端との間の隙間として形成されている。これによっても、各第二伝熱管22から第二室77へと導入された冷媒が第二室77内で溜まり込むことなく、縦仕切板72に形成された下部連通部69を介して第一室76へ導入され、第一室76の下部に接続された接続管55を介して第一ヘッダ部に導入することができる。また、縦仕切板72の下部を第二室77側へ湾曲させていることで、湾曲形状が冷媒の流れをガイドすることになり、冷媒が第二室77から第一室76へ導入されやすくなる。その結果、本実施形態の熱交換器90を用いた空気調和機では、冷房性能や暖房性能が損なわれることはない。
なお、第三実施形態では第二実施形態で説明した第二連通部64を設けてもよい。 As a modification of the third embodiment, for example, as shown in FIGS. 18, 19, and 20, the lower part of thevertical partition plate 72 is curved toward the first chamber 76, and the second header part lowermost heat transfer tube 25. A lower communication portion 69 (third communication portion 67) that allows the first chamber 76 and the second chamber 77 to communicate with each other may be formed further downward. In this case, the lower communication portion 69 is formed as a gap between the lower end of the vertical partition plate 72 and the lower end of the second header portion 53. Also by this, the refrigerant introduced from each second heat transfer tube 22 into the second chamber 77 does not accumulate in the second chamber 77, and the first through the lower communication portion 69 formed in the vertical partition plate 72. It can be introduced into the first header portion via the connecting pipe 55 introduced into the chamber 76 and connected to the lower portion of the first chamber 76. Further, since the lower part of the vertical partition plate 72 is curved toward the second chamber 77, the curved shape guides the flow of the refrigerant, and the refrigerant is easily introduced from the second chamber 77 into the first chamber 76. Become. As a result, in the air conditioner using the heat exchanger 90 of the present embodiment, the cooling performance and the heating performance are not impaired.
In the third embodiment, thesecond communication part 64 described in the second embodiment may be provided.
なお、第三実施形態では第二実施形態で説明した第二連通部64を設けてもよい。 As a modification of the third embodiment, for example, as shown in FIGS. 18, 19, and 20, the lower part of the
In the third embodiment, the
次に本発明の第四実施形態に係る熱交換器100について、図21を参照して説明する。第四実施形態では、縦仕切板は第一実施形態から第三実施形態のいずれかと同様の構成である。本実施形態では第一実施形態の縦仕切板70と同様の構成として説明する。第一実施形態と同様の構成要素については、該第一実施形態同一の符号を付して詳細な説明を省略する。
第四実施形態の熱交換器100は、図21に示すように、第二伝熱管22の延在方向における第二伝熱管22の第二ヘッダ部53内の長さLpが、第二ヘッダ部53の内径Diの半分以下とされている。すなわち、第二伝熱管22の先端位置は、第二ヘッダ部53の中心位置と同じ又は第二ヘッダ部53の中心よりも第二ヘッダ部53と第二伝熱管22との接続部側とされている。
このような熱交換器100によれば、蒸発器として作動する場合、第二伝熱管22における第二ヘッダ部53内の長さが短いため、接続管55から第一室76および第一室76から上部連通孔62を介して第二室77へ導入された気液二相状態の冷媒が第一室76および第二室77内の各第二伝熱管22の上下間に溜まり込むことによる冷媒の流れの乱れを抑制することができ、液相冷媒が各第二伝熱管へ導入されやすくなる。これによりさらに各第二伝熱管22内を流通する冷媒流量のばらつきの発生を抑制できる。
これにより、各第二伝熱管22内にて、冷媒における残存していた液相が気相に変化し、出入口側ヘッダ40の上部出入領域43には気相状態の冷媒が供給される。そして、この冷媒は上部出入領域43から配管7に導入され、冷媒回路を循環することになる。 Next, the heat exchanger 100 which concerns on 4th embodiment of this invention is demonstrated with reference to FIG. In the fourth embodiment, the vertical partition plate has the same configuration as that of any one of the first to third embodiments. This embodiment demonstrates as a structure similar to thevertical partition plate 70 of 1st embodiment. Constituent elements similar to those in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
In the heat exchanger 100 of the fourth embodiment, as shown in FIG. 21, the length Lp in thesecond header portion 53 of the second heat transfer tube 22 in the extending direction of the second heat transfer tube 22 is the second header portion. The inner diameter Di of 53 is less than half. That is, the tip position of the second heat transfer tube 22 is the same as the center position of the second header portion 53 or is closer to the connection portion side of the second header portion 53 and the second heat transfer tube 22 than the center of the second header portion 53. ing.
According to such a heat exchanger 100, when operating as an evaporator, since the length in thesecond header portion 53 of the second heat transfer tube 22 is short, the first chamber 76 and the first chamber 76 are connected from the connection tube 55. The refrigerant in the gas-liquid two-phase state introduced into the second chamber 77 through the upper communication hole 62 from the upper part of the first chamber 76 and the second heat transfer tubes 22 in the second chamber 77 is accumulated. The liquid phase refrigerant can be easily introduced into each second heat transfer tube. Thereby, it is possible to further suppress the variation in the flow rate of the refrigerant flowing through each second heat transfer tube 22.
As a result, the liquid phase remaining in the refrigerant changes into a gas phase in each secondheat transfer tube 22, and the gas phase refrigerant is supplied to the upper entrance / exit region 43 of the inlet / outlet header 40. Then, the refrigerant is introduced into the pipe 7 from the upper entrance / exit area 43 and circulates in the refrigerant circuit.
第四実施形態の熱交換器100は、図21に示すように、第二伝熱管22の延在方向における第二伝熱管22の第二ヘッダ部53内の長さLpが、第二ヘッダ部53の内径Diの半分以下とされている。すなわち、第二伝熱管22の先端位置は、第二ヘッダ部53の中心位置と同じ又は第二ヘッダ部53の中心よりも第二ヘッダ部53と第二伝熱管22との接続部側とされている。
このような熱交換器100によれば、蒸発器として作動する場合、第二伝熱管22における第二ヘッダ部53内の長さが短いため、接続管55から第一室76および第一室76から上部連通孔62を介して第二室77へ導入された気液二相状態の冷媒が第一室76および第二室77内の各第二伝熱管22の上下間に溜まり込むことによる冷媒の流れの乱れを抑制することができ、液相冷媒が各第二伝熱管へ導入されやすくなる。これによりさらに各第二伝熱管22内を流通する冷媒流量のばらつきの発生を抑制できる。
これにより、各第二伝熱管22内にて、冷媒における残存していた液相が気相に変化し、出入口側ヘッダ40の上部出入領域43には気相状態の冷媒が供給される。そして、この冷媒は上部出入領域43から配管7に導入され、冷媒回路を循環することになる。 Next, the heat exchanger 100 which concerns on 4th embodiment of this invention is demonstrated with reference to FIG. In the fourth embodiment, the vertical partition plate has the same configuration as that of any one of the first to third embodiments. This embodiment demonstrates as a structure similar to the
In the heat exchanger 100 of the fourth embodiment, as shown in FIG. 21, the length Lp in the
According to such a heat exchanger 100, when operating as an evaporator, since the length in the
As a result, the liquid phase remaining in the refrigerant changes into a gas phase in each second
以上、本発明の実施の形態について説明したが、本発明はこれに限定されることなく、その発明の技術的思想を逸脱しない範囲で適宜変更可能である。
The embodiment of the present invention has been described above, but the present invention is not limited to this, and can be appropriately changed without departing from the technical idea of the present invention.
上述した熱交換器及び空気調和機によれば、複数の伝熱管を流通する冷媒流量の不均一化による性能低下を抑制することができる。
According to the heat exchanger and the air conditioner described above, it is possible to suppress performance degradation due to non-uniform refrigerant flow rates flowing through the plurality of heat transfer tubes.
1 空気調和機
2 圧縮機
3 室内熱交換器
4 膨張弁
5 室外熱交換器
6 四方弁
7 配管
10 熱交換器
20 伝熱管
21 第一伝熱管
22 第二伝熱管
23 フィン
24 第二ヘッダ部最上部伝熱管
25 第二ヘッダ部最下部伝熱管
30 ヘッダ
40 出入口側ヘッダ
41 出入側仕切板
42 下部出入領域
43 上部出入領域
50 折り返し側ヘッダ
51 ヘッダ本体
52 第一ヘッダ部
53 第二ヘッダ部
54 折り返し側仕切板
55 接続管
56 流通路
61 第一連通部
62 上部連通孔
63 上部連通部
64 第二連通部
65 伝熱管側連通部
66 伝熱管側連通孔 1 Air conditioner
2 Compressor
3 Indoor heat exchanger
4 Expansion valve
5 Outdoor heat exchanger
6 Four-way valve
7 Piping
10 Heat exchanger
20 Heat transfer tube
21 1st heat transfer tube
22 Second heat transfer tube
23 Fin
24 Second header section uppermostheat transfer tube 25 Second header section lowermost heat transfer tube 30 Header
40 Entrance / exit header
41 Entrance / exit partition plate
42 Lower access area
43 Upper access area
50 Return header
51 Header body
52 First header
53 Second header section
54 Folding side divider
55 Connection pipe
56 Passage
61 Series 1
62 Upper communication hole
63 Upper communication part
64 Second communication part
65 Heat transfer tube side communication part
66 Heat transfer tube side communication hole
2 圧縮機
3 室内熱交換器
4 膨張弁
5 室外熱交換器
6 四方弁
7 配管
10 熱交換器
20 伝熱管
21 第一伝熱管
22 第二伝熱管
23 フィン
24 第二ヘッダ部最上部伝熱管
25 第二ヘッダ部最下部伝熱管
30 ヘッダ
40 出入口側ヘッダ
41 出入側仕切板
42 下部出入領域
43 上部出入領域
50 折り返し側ヘッダ
51 ヘッダ本体
52 第一ヘッダ部
53 第二ヘッダ部
54 折り返し側仕切板
55 接続管
56 流通路
61 第一連通部
62 上部連通孔
63 上部連通部
64 第二連通部
65 伝熱管側連通部
66 伝熱管側連通孔 1 Air conditioner
2 Compressor
3 Indoor heat exchanger
4 Expansion valve
5 Outdoor heat exchanger
6 Four-way valve
7 Piping
10 Heat exchanger
20 Heat transfer tube
21 1st heat transfer tube
22 Second heat transfer tube
23 Fin
24 Second header section uppermost
40 Entrance / exit header
41 Entrance / exit partition plate
42 Lower access area
43 Upper access area
50 Return header
51 Header body
52 First header
53 Second header section
54 Folding side divider
55 Connection pipe
56 Passage
61 Series 1
62 Upper communication hole
63 Upper communication part
64 Second communication part
65 Heat transfer tube side communication part
66 Heat transfer tube side communication hole
Claims (8)
- 水平方向に延びて内部に冷媒が流通するとともに、上下方向に間隔をあけて複数が配列された伝熱管と、
上下方向に延びる管状をなして複数の前記伝熱管の一端が内部空間に連通状態で接続されたヘッダ部と、
前記ヘッダ部内を水平断面視にて、各前記伝熱管と前記ヘッダ部内の内周面とにわたって延びて前記ヘッダ部内を各前記伝熱管とそれぞれ連通する第一室及び第二室とに区画するとともに、前記第一室及び前記第二室を前記伝熱管のうち最も上方の前記伝熱管の高さ以上の位置で互いに連通させる第一連通部を形成している縦仕切板と、
前記第一室と前記第二室のうち前記第一室のみに接続されており、内部を冷媒が流通する流通路と、
を備える熱交換器。 A refrigerant pipe that extends in the horizontal direction and circulates inside, and a plurality of heat transfer tubes that are arranged at intervals in the vertical direction;
A header portion which is formed in a tubular shape extending in the vertical direction, and one end of the plurality of heat transfer tubes is connected in communication with the internal space;
The header section is divided into a first chamber and a second chamber extending in a horizontal sectional view across the heat transfer tubes and an inner peripheral surface of the header portion and communicating with the heat transfer tubes. A vertical partition plate that forms a first communicating portion that allows the first chamber and the second chamber to communicate with each other at a position equal to or higher than the height of the uppermost heat transfer tube among the heat transfer tubes;
Of the first chamber and the second chamber, connected to only the first chamber, a flow passage through which the refrigerant flows,
A heat exchanger. - 前記第一連通部は、前記縦仕切板に形成された連通孔である請求項1に記載の熱交換器。 The heat exchanger according to claim 1, wherein the first communication part is a communication hole formed in the vertical partition plate.
- 前記第一連通部は、前記縦仕切板と前記ヘッダ部の上端との間の隙間である請求項1に記載の熱交換器。 The heat exchanger according to claim 1, wherein the first communication part is a gap between the vertical partition plate and an upper end of the header part.
- 前記縦仕切板は、上下に隣り合う前記伝熱管の間に、前記第一室及び前記第二室を互いに連通させる第二連通部を形成している請求項1から3のいずれか一項に記載の熱交換器。 4. The vertical partition plate according to claim 1, wherein a second communication portion that connects the first chamber and the second chamber to each other is formed between the heat transfer tubes that are vertically adjacent to each other. 5. The described heat exchanger.
- 前記縦仕切板は、前記第一室と前記第二室とを前記伝熱管のうち最も下方の前記伝熱管よりも下方の位置で互いに連通させる第三連通部を形成している請求項1から4のいずれか一項に記載の熱交換器。 The said vertical partition forms the 3rd communicating part which mutually connects the said 1st chamber and the said 2nd chamber in the position below the said lowermost heat exchanger tube among the said heat exchanger tubes. The heat exchanger according to any one of 4.
- 前記縦仕切板の下部が前記第二室側から前記第一室側に湾曲しており、
前記第三連通部は、前記縦仕切板と前記ヘッダ部の下端との間の隙間である請求項5に記載の熱交換器。 The lower part of the vertical partition plate is curved from the second chamber side to the first chamber side,
The heat exchanger according to claim 5, wherein the third communication part is a gap between the vertical partition plate and a lower end of the header part. - 前記伝熱管の延在方向における該伝熱管の前記ヘッダ部内での長さLpは、前記ヘッダ部の内径Diの半分以下である請求項1から6のいずれか一項に記載の熱交換器。 The heat exchanger according to any one of claims 1 to 6, wherein a length Lp of the heat transfer tube in the extending direction of the heat transfer tube in the header portion is not more than half of an inner diameter Di of the header portion.
- 請求項1から7のいずれか一項に記載の熱交換器を備える空気調和機。 An air conditioner comprising the heat exchanger according to any one of claims 1 to 7.
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EP3473963A4 (en) | 2019-07-03 |
EP3473963A1 (en) | 2019-04-24 |
JP2018100800A (en) | 2018-06-28 |
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