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WO2018173356A1 - Échangeur de chaleur et climatiseur faisant appel audit échangeur - Google Patents

Échangeur de chaleur et climatiseur faisant appel audit échangeur Download PDF

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Publication number
WO2018173356A1
WO2018173356A1 PCT/JP2017/040420 JP2017040420W WO2018173356A1 WO 2018173356 A1 WO2018173356 A1 WO 2018173356A1 JP 2017040420 W JP2017040420 W JP 2017040420W WO 2018173356 A1 WO2018173356 A1 WO 2018173356A1
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WIPO (PCT)
Prior art keywords
heat exchanger
gas
header
refrigerant
liquid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/040420
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English (en)
Japanese (ja)
Inventor
佐々木　重幸
禎夫 関谷
広 米田
佐藤　大和
遠藤　剛
福治 塚田
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Hitachi Johnson Controls Air Conditioning Inc
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Hitachi Johnson Controls Air Conditioning Inc
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Publication of WO2018173356A1 publication Critical patent/WO2018173356A1/fr
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  • the present invention relates to an air conditioner equipped with a heat exchanger, and in particular, effectively uses the heat exchanger by optimizing the distribution amount of the gas-liquid two-phase refrigerant that flows to each of the plurality of heat transfer tubes connecting the headers.
  • the present invention relates to an air conditioner that uses and reduces power consumption.
  • a cross fin tube heat exchanger composed of circular copper heat transfer tubes and aluminum strip fins is currently used. This heat exchanger performs heat exchange between the refrigerant and air by flowing a fluorocarbon refrigerant in the copper heat transfer tube.
  • parallel flow type heat exchangers are widely used in automobile radiators and air conditioners for cooling to reduce size, weight, performance, and cost.
  • This heat exchanger is provided with two header pipes at the openings of both ends of a plurality of flat heat transfer tubes brazed with aluminum fins on the outer surface, and from the inflow side header pipes to the outflow side via the respective flat heat transfer tubes. It is a heat exchanger of the form which makes a refrigerant flow toward a header pipe.
  • the refrigerant flows as a refrigerant in a gas-liquid two-phase state while changing the phase of evaporation and condensation, so that it stands in the vertical direction under the condition that the flow rate of the refrigerant is small and the momentum is low. Since the liquid refrigerant in the header pipe on the inflow side stays downward due to the influence of gravity, there is a tendency that it is difficult to supply sufficient liquid refrigerant to the flat heat transfer pipe connected to the upper part of the header pipe on the inflow side.
  • the parallel flow heat exchanger when used as an evaporator, the amount of liquid refrigerant to be supplied is reduced in the upper one of the stacked flat heat transfer tubes, and all of the liquid refrigerant is upstream of the flat heat transfer tubes. Since it evaporates, heat absorption due to the evaporation of the liquid refrigerant does not occur downstream from the middle stream. That is, in the upper flat heat transfer tube, there is a problem that the liquid component of the refrigerant is small and the degree of superheat increases from the middle flow to the downstream, and the heat transfer area in that portion is not effectively used.
  • the amount of liquid refrigerant supplied is excessive, so that the liquid refrigerant remains even at the outlet of the flat heat transfer tubes. That is, from the flat heat transfer tube below, the liquid refrigerant that has left the heat absorption capacity flows out, which causes a problem that the efficiency of the entire heat exchanger is deteriorated.
  • the liquid refrigerant in each flat heat transfer tube is completely eliminated at a substantially aligned position near the header tube on the outflow side. Desirable to maximize heat exchanger performance.
  • a heat exchanger such as an outdoor unit of an air conditioner, it is required that the refrigerant can be equally distributed to each flat heat transfer tube without drift.
  • the air conditioner includes a compressor 8, a four-way valve 9, an indoor heat exchanger 101, an expansion valve 103, an outdoor heat exchanger 106, and the like.
  • the compressor 8 compresses the gas refrigerant, and the refrigerant 60 that has been brought to a high temperature / high pressure state by the compressor 8 is led to the indoor heat exchanger 101 (condenser) in the indoor unit 100 via the four-way valve 9. It is burned. And the room
  • the liquid refrigerant that has flowed out of the indoor unit 100 becomes a gas-liquid two-phase refrigerant in a low-temperature and low-pressure state by an expansion action when passing through the expansion valve 103.
  • This low-temperature, low-pressure gas-liquid two-phase refrigerant is guided to the outdoor heat exchanger 106 (evaporator) in the outdoor unit 105.
  • the refrigerant is gasified and returns to the compressor 8 with a degree of superheat of several degrees C.
  • the refrigerant 60 circulates counterclockwise as described above.
  • the heating operation of the air conditioner is realized by a series of refrigeration cycles.
  • the four-way valve 9 is switched to form a refrigeration cycle in which the refrigerant 61 circulates clockwise.
  • the indoor heat exchanger 101 acts as an evaporator
  • the outdoor heat exchanger 106 acts as a condenser.
  • FIG. 21 is a plan view schematically showing the evaporator, and a part of the evaporator is simplified, such as omitting the individual display of the flat heat transfer tube.
  • FIG. 21A is an explanatory diagram when there is a drift of liquid refrigerant
  • FIG. 21B is an explanatory diagram when there is no drift of liquid refrigerant.
  • the heat exchanger is provided with headers 3a and 3b that are substantially perpendicular to the left and right, and connected by a number of flat heat transfer tubes 1 that are stacked in the vertical direction therebetween.
  • Each flat heat transfer tube 1 is brazed with a fin for enlarging the heat transfer area, but is not shown here.
  • the hatched portion is a two-phase region 90 through which the gas-liquid two-phase refrigerant flows
  • the white portion is an overheat region 91 through which the gas refrigerant flows.
  • low-temperature and low-pressure gas-liquid two-phase refrigerant flows from the lower part of the header 3b.
  • the refrigerant flowing in flows in the flat heat transfer tubes 1 in the order of the regions (A) ⁇ (B) ⁇ (C) ⁇ (D) while changing the flow direction, and exchanges heat with the air passing between the flat heat transfer tubes 1 ( After the heat absorption), the refrigerant is discharged from the upper portion of the header 3b as a medium temperature / low pressure refrigerant.
  • the two-phase region 90 is short and the superheat region 91 is long in the flat heat transfer tube 1 above the region (D), so that the two-phase region 90 greatly contributes to the heat absorption from the air.
  • the heat transfer area decreases and the compression work increases.
  • this refrigerant flow divider has a single refrigerant inflow pipe and a plurality of refrigerant outflow pipes.
  • the gas-liquid two-phase refrigerant that has entered the refrigerant distributor from the refrigerant inflow pipe is separated into the gas refrigerant and the liquid refrigerant when moving over the partition plate at the lower part of the refrigerant distributor, and the gas refrigerant that has accumulated in the upper part of the refrigerant distributor.
  • the liquid refrigerant accumulated in the lower side of the refrigerant flow divider from the gas refrigerant outlet opening on the side of the refrigerant outlet pipe flows into the refrigerant outlet pipe from the refrigerant outlet at the lower end of the refrigerant outlet pipe, and the gas refrigerant and liquid refrigerant have a desired ratio. It becomes a gas-liquid two-phase refrigerant merged at, and flows out of the refrigerant distributor.
  • the diameter of the refrigerant outlet pipe, the installation position, size, and number of the refrigerant outlet and the gas refrigerant outlet opening are designed according to the rated load conditions of the air conditioner. Under the conditions, an appropriate amount of liquid refrigerant can be led to the refrigerant outlet pipe.
  • the air conditioner is operated under an intermediate load condition or a minimum load condition, the flow rate of the gas refrigerant is small, so that the static pressure necessary for sucking up the liquid refrigerant cannot be obtained, and a sufficient amount of liquid refrigerant is not supplied. There was a problem that it could not be lifted.
  • Patent Document 1 is effective for performance improvement under rated load conditions, but for performance improvement under intermediate load conditions or minimum load conditions frequently used in recent air conditioners. There was a problem that the same level of effect could not be obtained and the impact on the reduction of annual power consumption during actual operation was limited.
  • the liquid refrigerant supply amount bias to each flat heat transfer tube in the parallel flow type evaporator is suppressed with a simple structure, It aims at providing the air conditioner provided with the heat exchanger which can improve the performance as an evaporator.
  • a heat exchanger includes an inflow header, an outflow header, a plurality of heat transfer tubes connecting the two headers, and a fin that expands the heat transfer area of the heat transfer tubes.
  • the inflow-side header includes a gas-liquid mixing unit into which the gas-liquid two-phase refrigerant flows in via an inlet pipe, and a plurality of gas-liquid mixing units arranged above the gas-liquid mixing unit and partitioned in a vertical direction by a partition plate. And a plurality of communication passages that directly communicate with the gas-liquid mixing portion and each header inner space, and at least one heat transfer tube is connected to each header inner space.
  • the flow path was a heat exchanger having at least one opening in the gas-liquid mixing part.
  • the energy distribution of an air conditioner can be improved by equalizing the refrigerant
  • the longitudinal cross-sectional view of the header of the heat exchanger of Example 1 Cross-sectional view of header of heat exchanger of embodiment 1
  • the front view of the communicating tube of the heat exchanger of Example 1 The longitudinal cross-sectional view of the header of the heat exchanger of Example 2 Cross-sectional view of header of heat exchanger of embodiment 2 Front view of the heat exchanger of Example 4 Top view of heat exchanger of Example 4 Top view of heat exchanger of Example 4 Front view of the heat exchanger of Example 5
  • the longitudinal cross-sectional view of the header of the heat exchanger of Example 3 Cross-sectional view of header of heat exchanger of embodiment 3
  • Cross-sectional view of header of heat exchanger of embodiment 6 Cross-sectional view of header of heat exchanger of embodiment 6
  • Cross-sectional view of header of heat exchanger of embodiment 6 Cross-sectional view of header of heat exchanger of embodiment 6
  • the longitudinal cross-sectional view of the header of the heat exchanger of Example 7 The exploded perspective view of the header of the heat exchanger of Example 8 Cross-sectional view
  • the heat exchanger of the present embodiment includes two substantially cylindrical headers 3 arranged substantially vertically on the upstream side and the downstream side, a plurality of flat heat transfer tubes 1 connecting between them, and the flat heat transfer tubes 1. It consists of a plurality of fins 2 that expand the heat transfer area.
  • FIG. 1 is a partial cross-sectional view of the vicinity of the upstream header 3, and as shown here, a plurality of substantially horizontal flat heat transfer tubes 1 are stacked in a vertical direction with a predetermined gap (step pitch Pd).
  • a plurality of plate-like fins 2 are arranged with a predetermined gap (fin pitch Pf) in the left-right direction, and the flat heat transfer tubes 1 and the fins 2 are brazed so that heat can be transferred.
  • Each flat heat transfer tube 1 is inserted into the header 3, and the refrigerant supplied via the header 3 flows into each flat heat transfer tube 1.
  • the header 3, the flat heat transfer tube 1, and the fin 2 will be described more specifically.
  • a plurality of holes for inserting the flat heat transfer tubes 1 are formed in advance at a step pitch.
  • the flat heat transfer tube 1 is made of aluminum, and has a plurality of multi-hole flow paths formed by extrusion processing in a flat cross section.
  • the fins 2 are made of aluminum, and cuts are made at equal intervals in the upper and lower longitudinal ends, and the flat heat transfer tubes 1 are inserted into the cuts, or through holes are formed in the fins themselves and the flat heat transfer tubes 1 are inserted. Thus, it is formed integrally with the flat heat transfer tube 1.
  • each flat heat transfer tube 1 is inserted into the hole of the header 3, and further, the fins 2 are attached to the flat heat transfer tube 1.
  • a heat exchanger may be manufactured by brazing, or a heat exchanger may be manufactured by partially brazing with a torch.
  • the flat heat transfer tube 1 and the fins 2 are joined to the flat heat transfer tube 1 by plastic deformation by pressurizing the inside of the multi-hole flow path with a hydraulic pressure or a gas pressure instead of the brazing described above.
  • a method may be adopted.
  • a corrugated (corrugated) fin that is currently mainstream in a condenser of an automotive air conditioner may be inserted between the flat heat transfer tubes 1. good.
  • FIG. 1 is a diagram schematically showing that the plurality of communication pipes 5 communicate with different spaces, and the arrangement of the communication pipes 5 is not accurately shown.
  • FIG. 2 is a cross-sectional view of the mixing chamber 41 in the AA section of FIG. 1, and shows the arrangement of the communication pipes 5 in the mixing chamber 41 more accurately.
  • 51 is a lower hole provided at the lower end of the communication pipe 5. That is, FIG. 2 shows that the outlet of the inlet pipe 36 and the inlet of the communication pipe 5 are installed at substantially the same height, and that the four communication pipes 5 are arranged in a straight line substantially perpendicular to the inlet pipe 36. It shows that.
  • FIG. 3 is a side view illustrating the detailed structure of the communication pipe 5.
  • the side surface of the communication pipe 5 has a plurality or a single opening at a height corresponding to the height of the mixing chamber 41.
  • side round holes 52a are provided with a predetermined gap in the vertical direction
  • FIG. 3B narrow side long holes 52b are provided.
  • FIG.3 (c) in addition to the side long hole 52b of FIG.3 (b), the plug 53 which plugs up the lower hole 51 of the communicating pipe 5 is attached.
  • Which communication pipe 5 shown in FIG. 3 is used is determined according to the flow rate of the refrigerant and the dryness condition, and a plurality of communication pipes 5 having the same shape may be connected to the gas-liquid mixing unit 4. It is good also as a structure which connects the gas-liquid mixing part 4 combining the communication pipe 5 of a different shape. For example, by changing the dimensions of the side round hole 52a and the side long hole 52b for each communication pipe 5, the refrigerant amount of the communication pipe 5 having different heights can be finely adjusted.
  • the amount of liquid refrigerant sucked from the lower end of the communication pipe 5 and the amount of gas refrigerant sucked from the side hole can be changed depending on the presence or absence of the plug 53, and fine adjustment of the ratio of gas refrigerant to liquid refrigerant in the gas-liquid two-phase refrigerant Is possible.
  • the communication pipe 5 in the mixing chamber 41 has a substantially upper half located above the gas-liquid interface 42 and a substantially lower half located below the gas-liquid interface 42.
  • the gas refrigerant can be sucked from the upper one, and the gas-liquid two-phase refrigerant can be sucked from the lower one.
  • the height of the gas-liquid interface 42 varies depending on the environmental conditions of the air conditioner and the operating condition of the load, but the side round hole 52a and the side long hole 52b are provided over the entire height of the mixing chamber 41. Therefore, even when the height of the gas-liquid interface 42 changes, the communication pipe 5 can appropriately suck up the gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant flows into the gas-liquid mixing unit 4 from the inlet pipe 36.
  • the gas-liquid two-phase refrigerant releases part of the gas refrigerant in a relatively wide space called the mixing chamber 41.
  • the gas-liquid two-phase refrigerant in which the ratio of the liquid refrigerant is increased by the release of the gas refrigerant accumulates in the lower part of the mixing chamber 41 due to the action of gravity, while the gas refrigerant separated from the gas-liquid two-phase refrigerant is above the mixing chamber 41. Moving. As a result, a gas-liquid interface 42 is formed between the gas refrigerant and the gas-liquid two-phase refrigerant.
  • the gas refrigerant in the upper part of the mixing chamber 41 flows into the communication pipe 5 at high speed from the opening (side round hole 52a, side long hole 52b) above the gas-liquid interface 42. At this time, negative pressure is generated by the high-speed gas refrigerant flowing in the communication pipe 5, and from the openings (lower hole 51, side round hole 52 a, side long hole 52 b) below the gas-liquid interface 42, Since the gas-liquid two-phase refrigerant accumulated in the lower part is sucked up, the gas refrigerant and the gas-liquid two-phase refrigerant are mixed in the communication pipe 5 at a predetermined ratio. This is a phenomenon that occurs in the same way in any of the four communication pipes 5 having different heights. Therefore, the ratio of the gas refrigerant to the liquid refrigerant in the gas-liquid two-phase refrigerant sucked up by the communication pipe 5 is four. In any of the communication pipes 5 of FIG.
  • the gas-liquid two-phase refrigerant sucked up by the communication pipe 5 is directly supplied to each of the header inner spaces 32 a to 32 d stacked in the header 3.
  • the refrigerant that has entered the header inner spaces 32a to 32d flows into each of the four flat heat transfer tubes 1 connected to the header inner spaces.
  • the substantially homogeneous gas-liquid two-phase refrigerant supplied to the header inner spaces 32a to 32d contains a large amount of gas refrigerant, and since the apparent density is small, the interior of each header inner space can be filled substantially evenly. As a result, the influence of the liquid head difference due to the difference in the height position of the flat heat transfer tubes 1 connected to the space in each header is reduced, and the substantially uniform gas-liquid two-phase is applied to each of the flat heat transfer tubes 1 having different heights.
  • a refrigerant can be supplied.
  • the substantially homogeneous gas-liquid two-phase refrigerant is supplied to the plurality of header inner spaces having different heights in the header, and further, the plurality of headers connected to the header inner spaces. Since the substantially homogeneous gas-liquid two-phase refrigerant can be supplied to the flat heat transfer tube, the influence of the drift due to the height can be suppressed even in a heat exchanger having a height.
  • the refrigerant flows in the direction opposite to the arrow shown in FIG. That is, the refrigerant first flows from each flat heat transfer tube 1 into the header inner spaces 32 a to 32 d in the header 3, and then flows into the mixing chamber 41 from each header inner space through the communication tube 5. Finally, it flows out of the heat exchanger through the inlet pipe 36 connected to the lower part of the mixing chamber 41.
  • the refrigerant in the condenser sequentially moves in the header 3 from the high place to the low place, the liquid refrigerant does not move against the gravity, and the flow of the stable refrigerant without increasing the pressure loss. Can be maintained.
  • FIG. 4 and 5 are diagrams for explaining the heat exchanger used in the second embodiment.
  • duplication description is abbreviate
  • FIG. 4 is a partial cross-sectional view of the vicinity of the upstream header 3 in the present embodiment
  • FIG. 5 is a cross-sectional view of the mixing chamber 41 in the AA portion of FIG. 4 to show the connection direction of the inlet pipe 36. Inlet pipes 36 at different heights are also shown.
  • a perforated plate 43 is provided in the mixing chamber 41 in place of the side round hole 52a and the side long hole 52b of the communication pipe 5 in FIG.
  • the perforated plate 43 is not provided with a hole above the inlet pipe 36, and has a plurality of holes from the center to the bottom.
  • the gas-liquid two-phase refrigerant flowing from the inlet pipe 36 collides with the flat portion of the perforated plate 43 and flows downward while releasing a part of the contained gas refrigerant. Thereby, since the direction of the main flow of the refrigerant is largely changed, the influence of the main flow on the subsequent flow of the refrigerant is suppressed.
  • the bubbles of the gas refrigerant contained when passing through the holes below the perforated plate 43 are further subdivided and separated from the gas-liquid two-phase refrigerant.
  • the gas refrigerant passes through the central hole and moves above the gas-liquid interface 42.
  • FIGS. 10 and 11 are diagrams for explaining the heat exchanger used in the third embodiment.
  • duplication description is abbreviate
  • the header 3 of this embodiment has an inlet pipe 36 connected to the lower surface of the mixing chamber 41 so that the refrigerant flows from below the gas-liquid mixing unit 4.
  • FIG. 11 is a plan view showing the arrangement of the inlet pipe 36 and each communication pipe 5 in the mixing chamber 41.
  • FIG. 6 to 8 are diagrams for explaining the heat exchanger used in the fourth embodiment.
  • duplication description is abbreviate
  • the heat exchanger of the present embodiment is divided into two in the vertical direction, and a header 3a using the refrigerant distribution structure of the above-described embodiment is provided between the lower heat exchanger 201 and the upper heat exchanger 202. Structure.
  • a lower heat exchanger 201 and an upper heat exchanger 202 are stacked one above the other in order to improve the drainage of the condensed water generated in the fins 2 of the heat exchanger.
  • the gas-liquid mixing unit 4 is provided below the header 3a of the upper heat exchanger 202, which is disposed downstream of the header 3b of the lower heat exchanger 201. Since the header 3a protrudes downward by the amount of the gas-liquid mixing unit 4, the upper header 3a is arranged to be shifted outward by a predetermined distance D from the lower header 3b.
  • FIG. 7 is a top view when FIG. 6 is observed from above, and shows a configuration in which the gas-liquid mixing unit 4 is mounted by shifting the header 3a to the outside of the header 3b.
  • FIG. 8 is a modification of FIG. Although FIG. 7 shows the positional relationship between the headers 3a and 3b in the planar heat exchanger, FIG. 8 shows the positional relationship between the headers 3a and 3b in the heat exchanger bent in an L shape with the curvature R.
  • a heat exchanger that is required to be downsized such as a heat exchanger used in an outdoor unit of an air conditioner
  • the front surface area can be secured within the same unit size by the configuration as shown in FIG.
  • a distribution structure can be realized.
  • FIG. 9 is a diagram for explaining a heat exchanger used in the fifth embodiment.
  • duplication description is abbreviate
  • FIG. 9 shows a case where the heat exchanger is divided into three heat exchangers.
  • a plurality of the refrigerant distribution structures of the above-described embodiments can be mounted.
  • a gas-liquid mixing unit 4a is provided at the lower part of the header 3 upstream of the middle heat exchanger
  • a gas-liquid mixing unit 4b is provided at the lower part of the header 3 upstream of the upper heat exchanger.
  • the liquid component in the gas-liquid two-phase refrigerant gradually decreases toward the downstream due to heat exchange. Therefore, the downstream gas is less than the gas-liquid mixing unit 4a on the upstream side.
  • the liquid refrigerant that accumulates in the liquid mixing unit 4b decreases.
  • the volume of the downstream gas-liquid mixing unit 4b is smaller than the volume of the upstream gas-liquid mixing unit 4a (or the volume of the upstream gas-liquid mixing unit 4a is set downstream. By making it larger than the volume of the mixing portion 4b, the downstream header 3 is relatively miniaturized.
  • FIG. 12 to 14 are modifications of the first embodiment and the second embodiment in which the inlet pipe 36 is connected to the side surface of the gas-liquid mixing section 4.
  • FIG. 15 shows a modification of the third embodiment in which an inlet pipe is connected below.
  • the 12 has a side opening 52d of the communication pipe 5 provided in the direction opposite to the inlet pipe.
  • the influence of the main flow of the inlet pipe can be prevented, and a substantially equal amount of refrigerant can be supplied to each communication pipe 5.
  • the side opening 52d the side round hole 52a described above may be adopted, or the side long hole 52b may be adopted.
  • a partition plate 37 is provided between the inlet pipe 36 and the communication pipe 5. That is, the perforated portion is omitted from the perforated plate 43 of the second embodiment. Even with such a configuration, similarly to the second embodiment, the influence of the refrigerant main flow from the inlet pipe can be suppressed.
  • the inlet pipe 36 is provided in the tangential direction of the inner surface of the header 3, and the four communication pipes 5 are collected and arranged at the center.
  • the fast flow from the inlet pipe 36 becomes a swirling flow in the header 3, and the communication pipe 5 sucks the refrigerant from the central region where the flow velocity is slow. Even with this configuration, the influence of the mainstream from the inlet pipe 36 can be suppressed.
  • FIG. 15 is a modification of FIG. 11 in which a connecting pipe is provided below, and a horizontal partition plate 38 is provided between the inlet pipe 36 and the communication pipe 5 to reduce the main flow speed of the refrigerant flowing from the inlet pipe 36. To do.
  • the configuration shown in FIGS. 12 to 15 also suppresses the influence of the high-speed refrigerant flowing from the inlet pipe 36 on the communication pipe 5, and each communication pipe 5 sucks up the substantially homogeneous gas-liquid two-phase refrigerant. Since it can distribute to each header inner space, a substantially homogeneous gas-liquid two-phase refrigerant can be supplied also to the flat heat exchanger tube 1 connected to each header inner space.
  • FIG. 16 is a diagram illustrating a heat exchanger used in Example 7.
  • duplication description is abbreviate
  • FIG. 1 to FIG. 15 four flat heat transfer tubes 1 are connected to the spaces in each header, that is, the refrigerant supplied from one communication tube 5 is branched into four flat heat transfer tubes 1.
  • one flat heat transfer tube 1 is connected to each header space, that is, the refrigerant flows from one communication tube 5 to one flat heat transfer tube 1.
  • FIGS. 17 and 18 are diagrams for explaining a heat exchanger used in Example 8.
  • FIG. 17 and 18 are diagrams for explaining a heat exchanger used in Example 8.
  • FIG. 17 and 18 are diagrams for explaining a heat exchanger used in Example 8.
  • duplication description is abbreviate
  • the communication pipe 5 is constituted by a pipe-shaped hollow pipe, but in this embodiment, a plurality of communication pipes 5 are formed by a substantially cylindrical core 5 a inserted into the circular groove-shaped header 3. It takes the form to do.
  • the core 5a is provided with partitioned header inner spaces 32a to 32d on the outer peripheral flat heat transfer tube 1 side, and on the opposite side is provided with a groove 5b for sucking the refrigerant. It has been.
  • Each of the grooves 5b is provided with an opening indicated by hatching in the drawing, which communicates with the header inner spaces 32a to 32d.
  • FIG. 19 is a diagram illustrating the heat exchanger used in Example 9.
  • duplication description is abbreviate
  • FIG. 1 to 18 show a configuration in which the gas-liquid mixing unit 4 is built in the lower part of the header 3, but in this embodiment, the two are separated and are connected using a plurality of communication pipes 5. . If such a separation configuration is used, only the gas-liquid mixing unit 4 can be installed perpendicular to the direction of gravity, and the header 3 can be inclined from the direction of gravity, which greatly increases the degree of freedom in designing the heat exchanger. Therefore, the effect equivalent to that of the above-described embodiment can be provided to a heat exchanger that requires space saving, such as a heat exchanger used in an indoor unit of an air conditioner.
  • FIG. 20 is a diagram illustrating the heat exchanger used in Example 10.
  • duplication description is abbreviate
  • the partition plate 31 is provided in the header 3.
  • the partition 31 is removed and the upper openings of the communication pipes 5 are arranged at different heights.
  • the substantially homogeneous gas-liquid two-phase refrigerant can be guided to various heights of the header 3, so that the flat heat transfer tube 1 of any height connected to the header 3 can be used.
  • a substantially homogeneous gas-liquid two-phase refrigerant can be supplied.
  • the present invention is not limited to the above-described embodiments, and includes various modifications.
  • the above-described embodiments have been described in detail for easy understanding by the present invention, and are not necessarily limited to those having all the configurations described.
  • a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.

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Abstract

L'invention concerne un échangeur de chaleur comprenant un tube de transfert de chaleur introduit à partir de la direction horizontale par rapport à une ailette verticale, ledit échangeur pouvant présenter des problèmes compliqués de réduction de la consommation d'énergie du fait que la surface de transfert de chaleur de l'échangeur de chaleur entier n'est pas utilisée en raison de l'apparition d'un écoulement déséquilibré de fluide frigorigène coulant d'un collecteur vers une pluralité de tubes de transfert de chaleur. Afin de résoudre ce genre de problème, l'invention décrit un échangeur de chaleur comprenant un collecteur côté entrée, un collecteur côté sortie, un pluralité de tubes de transfert de chaleur reliés entre les collecteurs, et une ailette destinée à élargir la surface de transfert de chaleur des tubes de transfert de chaleur. Le collecteur côté entrée comprend une unité de mélange gaz-liquide vers laquelle coule un fluide frigorigène diphasique gaz-liquide par l'intermédiaire d'un tuyau d'entrée, une pluralité d'espaces de collecteur agencés dans la partie supérieure de l'unité de mélange gaz-liquide et divisés verticalement par une plaque de séparation, et une pluralité de canaux de communication permettant la communication directe de l'unité de mélange gaz-liquide avec les espaces de collecteur ; chaque espace de collecteur est relié à au moins un tube de transfert de chaleur ; et chaque canal de communication comporte au moins une ouverture à l'intérieur de l'unité de mélange gaz-liquide.
PCT/JP2017/040420 2017-03-24 2017-11-09 Échangeur de chaleur et climatiseur faisant appel audit échangeur Ceased WO2018173356A1 (fr)

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JP2017-059083 2017-03-24
JP2017059083A JP2018162901A (ja) 2017-03-24 2017-03-24 熱交換器、および、それを用いた空気調和機

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WO2020178930A1 (fr) * 2019-03-04 2020-09-10 日立ジョンソンコントロールズ空調株式会社 Appareil de climatisation, machine frigorifique et distributeur
TWI712771B (zh) * 2019-05-29 2020-12-11 國立中央大學 用於板式熱交換器之入口分佈器
CN112378123A (zh) * 2020-11-04 2021-02-19 上海交通大学 一种高效均流低阻的变径太阳能光伏/光热集热/蒸发器
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WO2022071368A1 (fr) * 2020-09-30 2022-04-07 三菱重工サーマルシステムズ株式会社 Échangeur de chaleur et climatiseur pour véhicule
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WO2025203542A1 (fr) * 2024-03-29 2025-10-02 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération
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EP4513122A4 (fr) * 2022-04-20 2025-06-04 Mitsubishi Electric Corporation Échangeur de chaleur et dispositif de climatisation

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