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WO2021245788A1 - Échangeur de chaleur et dispositif de pompe à chaleur - Google Patents

Échangeur de chaleur et dispositif de pompe à chaleur Download PDF

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Publication number
WO2021245788A1
WO2021245788A1 PCT/JP2020/021767 JP2020021767W WO2021245788A1 WO 2021245788 A1 WO2021245788 A1 WO 2021245788A1 JP 2020021767 W JP2020021767 W JP 2020021767W WO 2021245788 A1 WO2021245788 A1 WO 2021245788A1
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WO
WIPO (PCT)
Prior art keywords
low
flow path
pressure refrigerant
pressure
heat exchanger
Prior art date
Application number
PCT/JP2020/021767
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English (en)
Japanese (ja)
Inventor
洋次 尾中
崇 松本
理人 足立
Original Assignee
三菱電機株式会社
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2022529175A priority Critical patent/JP7281059B2/ja
Priority to PCT/JP2020/021767 priority patent/WO2021245788A1/fr
Publication of WO2021245788A1 publication Critical patent/WO2021245788A1/fr

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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

Definitions

  • the present disclosure relates to a heat exchanger and a heat pump device using the heat exchanger as an evaporator.
  • the above-mentioned conventional heat exchanger does not have an internal heat exchange portion in the upper header provided with an outlet for the low-pressure refrigerant, when the distribution of the refrigerant to a plurality of heat transfer tubes becomes uneven. There is a concern that the low-pressure refrigerant in the liquid phase that has not been evaporated in some heat transfer tubes will flow into the upper header, and the low-pressure refrigerant will flow out to the outside of the heat exchanger while containing the liquid phase.
  • the present disclosure has been made to solve the above-mentioned problems, and even if the low-pressure refrigerant that has passed through the heat transfer tube flows into the header with the liquid phase contained, heat exchange between the refrigerants in the header is made.
  • the purpose is to obtain a heat exchanger in which the low-pressure refrigerant can be evaporated before it flows out to the outside of the heat exchanger and the heat exchange efficiency is improved.
  • the heat exchanger according to the present disclosure is provided at intervals in the first direction, and is formed in a tubular shape by a plurality of heat transfer tubes long in the second direction perpendicular to the first direction and an outer wall long in the first direction. , A first header to which one end of a plurality of heat transfer tubes is connected, a second header formed in a tubular shape long in the first direction and to which the other ends of the plurality of heat transfer tubes are connected, and to one end side of the first header.
  • the first header is a heat exchanger, and the first header communicates with the outside through a low-pressure refrigerant inflow pipe and the outside through a low-pressure refrigerant outflow pipe, and is inside the heat transfer pipe and the second header.
  • the liquid phase low pressure refrigerant is exchanged with the refrigerant passing through the heat transfer tube. Even if it is contained, it can be evaporated and has the effect of improving the heat exchange efficiency.
  • FIG. It is a circuit diagram which shows the heat pump apparatus of Embodiment 1.
  • FIG. It is sectional drawing which shows the heat exchanger of Embodiment 1.
  • FIG. It is sectional drawing of the main part which shows the heat exchanger of Embodiment 1.
  • FIG. It is 1st schematic diagram for demonstrating the flow of a low pressure refrigerant in a conventional heat exchanger.
  • It is a 2nd schematic diagram for demonstrating the flow of a low pressure refrigerant in a conventional heat exchanger.
  • It is a schematic diagram for demonstrating the flow of the low pressure refrigerant in the heat exchanger of Embodiment 1.
  • FIG. It is sectional drawing which shows the 1st modification of the heat exchanger of Embodiment 1.
  • FIG. 1 It is sectional drawing which shows the 2nd modification of the heat exchanger of Embodiment 1.
  • FIG. It is sectional drawing of the main part which shows the 2nd modification of the heat exchanger of Embodiment 1.
  • FIG. 2 is sectional drawing of the main part which shows the 3rd modification of the heat exchanger of Embodiment 1.
  • FIG. It is sectional drawing which shows the heat exchanger of Embodiment 2.
  • FIG. It is sectional drawing of the main part which shows the heat exchanger of Embodiment 2.
  • FIG. It is sectional drawing of the main part which shows the modification of the heat exchanger of Embodiment 3.
  • FIG. It is sectional drawing of the main part which shows the heat exchanger of Embodiment 4. It is sectional drawing which shows the heat exchanger of Embodiment 5. It is sectional drawing of the main part which shows the heat exchanger of Embodiment 5.
  • Embodiment 1 The heat exchanger of the first embodiment and the heat pump device using the heat exchanger as an evaporator will be described with reference to FIGS. 1 to 6.
  • FIG. 1 is a circuit diagram showing a heat pump device 1000 according to the present embodiment.
  • the high-pressure refrigerant circuit is shown by a single line
  • the low-pressure refrigerant circuit is shown by a double line
  • the bypass circuit 5 of the high-pressure refrigerant circuit is shown by a single line thinner than the main circuit 4.
  • the black arrow (denoted as H in FIG. 1) schematically indicates the direction in which the high-pressure refrigerant flows
  • the white-painted arrow (denoted as L in FIG. 1) schematically indicates the direction in which the low-pressure refrigerant flows. It shall be shown as a target.
  • the size of the arrow may differ regardless of the flow rate of the refrigerant or the like.
  • the heat pump device 1000 condenses in the main circuit 4 connected by a plurality of pipes so that the refrigerant circulates in the order of the compressor 1, the condenser 2, the expansion valve 3, and the heat exchanger 100 as the evaporator, and the main circuit 4. It is a refrigeration cycle device that has a bypass circuit 5 connected between the vessel 2 and the expansion valve 3 and branched from the main circuit 4, and transfers heat by utilizing the latent heat of evaporation and condensation of the refrigerant.
  • the condenser 2 is installed indoors and the heat exchanger 100 as an evaporator is installed outdoors to heat the room, or the condenser 2 heats water to make hot water. Used for hot water supply systems, etc.
  • the main circuit 4 dissipates heat from the compressor 1 that compresses the low-pressure refrigerant in the gas phase to make it a high-pressure refrigerant in the gas phase, and dissipates the high-pressure refrigerant in the gas phase compressed by the compressor 1 and condenses it into the high-pressure refrigerant in the liquid phase. It is included in the condenser 2, the expansion valve 3 that decompresses the high-pressure refrigerant of the liquid phase condensed by the condenser 2 into a low-pressure refrigerant of the liquid phase or the gas-liquid two-phase, and the low-pressure refrigerant decompressed by the expansion valve 3.
  • This is a circulation path formed by connecting a heat exchanger 100 as an evaporator that evaporates a low-pressure refrigerant in a liquid phase to a low-pressure refrigerant in a gas phase with a plurality of pipes so that the refrigerant circulates.
  • the compressor 1 compresses the low-pressure refrigerant in the gas phase that flows in through the heat exchanger 100 as an evaporator to make it a high-pressure refrigerant in the gas phase. Further, the compressor 1 can change the amount of the refrigerant flowing in the circulation path by adjusting the rotation speed, whereby the amount of heat carried by the heat pump in the entire heat pump device 1000 can be changed.
  • the condenser 2 is a heat exchanger in which heat exchange is performed between the refrigerant passing through the inside and the outside air, and the high pressure refrigerant in the gas phase is condensed into the high pressure refrigerant in the liquid phase.
  • the condenser 2 has two headers and a plurality of heat transfer tubes connected between the headers.
  • the expansion valve 3 decompresses the high-pressure refrigerant in the liquid phase to make it a low-pressure refrigerant in the liquid phase or the gas-liquid two-phase. Further, the expansion valve 3 can continuously change the opening degree through which the refrigerant passes, whereby the pressure of the refrigerant flowing in the circulation path can be adjusted.
  • the expansion valve 3 is provided as a means for reducing the pressure of the high-pressure refrigerant into the low-pressure refrigerant will be described, but the present invention is not limited to this, and any one that functions as a pressure reducing device may be used.
  • the heat exchanger 100 is used as an evaporator, and heat exchange is performed between the liquid phase or gas-liquid two-phase low-pressure refrigerant flowing through the expansion valve 3 and the outside air to evaporate the liquid-phase low-pressure refrigerant. Use a low-pressure refrigerant in the gas phase.
  • the heat exchanger 100 includes a first header 10, and the first header 10 is provided with a low pressure flow path 13 through which the low pressure refrigerant flows in the main circuit 4 and a high pressure flow path 14 through which the high pressure refrigerant flows in the bypass circuit 5. ..
  • the first header 10 of the heat exchanger 100 functions as an internal heat exchange unit in which the low-pressure refrigerant and the high-pressure refrigerant exchange heat in the circulation path of the heat pump device 1000.
  • the detailed configuration of the heat exchanger 100 will be described later.
  • the bypass circuit 5 branches from the piping of the main circuit 4 connecting between the condenser 2 and the expansion valve 3 at the branch point A, passes through the check valve 6 and the fixed fluid resistance 7, and passes through the heat exchanger 100. It is a branch path of the main circuit 4 that rejoins the main circuit 4 at the confluence B between the branch point A and the expansion valve 3 after passing through the header 10. That is, the circulation path of the refrigerant in the heat pump device 1000 is composed of the main circuit 4 and the bypass circuit 5, and among the refrigerants circulating in the main circuit 4, the high-pressure refrigerant flowing out of the condenser 2 is bypassed with the main circuit 4 at the branch point A. It will be divided into the circuit 5.
  • the resistance of the flow path is made larger than that of the main circuit 4 by the fixed fluid resistance 7.
  • the check valve 6 and the fixed fluid resistance 7 may be interchanged and arranged.
  • the fixed fluid resistance 7 can be composed of, for example, a thin tube, an orifice, a bent tube, or the like.
  • the bypass circuit 5 provided with the check valve 6 and the fixed fluid resistance 7 is described as an example, but as a substitute for the check valve 6 and the fixed fluid resistance 7, for example, a flow control valve is described.
  • a bypass circuit may be provided in which the fluid resistance can be adjusted arbitrarily.
  • the high-pressure refrigerant passing through the high-pressure flow path 14 formed in the first header 10 of the heat exchanger 100 exchanges heat with the low-pressure refrigerant passing through the low-pressure flow path 13 formed in the first header 10. By doing so, heat is dissipated, and the outflow occurs in a state where the enthalpy is reduced as compared with that before passing through the high-pressure flow path 14. After that, the dissipated high-pressure refrigerant joins the main circuit 4 at the confluence point B.
  • the combined high-pressure refrigerant is depressurized through the expansion valve 3, and the liquid-phase or gas-liquid two-phase low-pressure refrigerant flows into the low-pressure flow path 13 formed in the first header of the heat exchanger 100.
  • the low pressure flow is measured by measuring the temperature difference between the inlet and the outlet in the low pressure flow path 13 of the heat exchanger 100. Overheating of the refrigerant flowing out of the road 13 can be detected. Therefore, by controlling the frequency of the compressor 1, the expansion valve 3, the check valve 6, and the like to adjust the flow rate based on the detection result of overheating, the low-pressure refrigerant flowing into the heat exchanger 100 as the evaporator can be used. All of the low-pressure refrigerant in the liquid phase contained therein can be vaporized by the time it flows out of the heat exchanger 100.
  • the frequency of the compressor 1 is used in the bypass circuit 5.
  • the refrigerant flow rate can be estimated.
  • the fluid resistance of the bypass circuit is set to a constant value, and the frequency of the compressor, the expansion valve, etc. are controlled to exchange heat as an evaporator.
  • the low-pressure refrigerant in the liquid phase contained in the low-pressure refrigerant flowing into the vessel can be completely evaporated before flowing out of the heat exchanger. By doing so, it becomes possible to control the amount of the refrigerant more easily.
  • the flow control valve is adjusted.
  • the low-pressure refrigerant in the liquid phase contained in the low-pressure refrigerant flowing into the heat exchanger as an evaporator can be completely vaporized before flowing out of the heat exchanger. By doing so, it is possible to adjust the amount of the refrigerant under a wider range of operating conditions, and it is possible to improve the engine efficiency of the entire heat pump device.
  • FIG. 2 is a cross-sectional view of the heat exchanger 100 of the present embodiment as viewed from a third direction
  • FIG. 3 is a cross-sectional view of a main part of the heat exchanger 100 as viewed from the first direction.
  • the first direction, the second direction, and the third direction shown in each of the following figures shall indicate three directions orthogonal to each other.
  • the heat exchanger 100 is provided with a plurality of heat exchangers 101 spaced apart from each other in the first direction, and the corrugated fins 102 inserted between the plurality of heat transfer tubes 101 and the plurality of heat transfer tubes 101.
  • One end 101a of the plurality of heat transfer tubes 101 is connected to have a first header 10 long in the first direction, and the other end 101b of the plurality of heat transfer tubes 101 is connected to have a second header 103 long in the first direction.
  • a low-pressure refrigerant inflow pipe 104 and a high-pressure refrigerant outflow pipe 107 are provided at one end 10a of the first header 10, and a low-pressure refrigerant outflow pipe 105 and a high-pressure refrigerant inflow pipe 106 are provided at the other end 10b.
  • the low-pressure refrigerant inflow pipe 104 and the low-pressure refrigerant outflow pipe 105 are connected to the pipes constituting the main circuit 4 of the heat pump device 1000, and the high-pressure refrigerant inflow pipe 106 and the high-pressure refrigerant outflow pipe 107 form the bypass circuit 5. Connected to.
  • the low pressure flow path 13 and the high pressure flow path 14 formed in the first header 10 are countercurrent flows.
  • the high-pressure refrigerant flowing through the high-pressure flow path 14 has a higher temperature and higher pressure than the low-pressure refrigerant flowing through the low-pressure flow path 13, and the low-pressure refrigerant and the high-pressure refrigerant exchange heat in the first header 10 via the inner wall 12.
  • the heat transfer tube 101 has a flat shape that is longitudinal in the second direction and wider in the third direction than the first direction, and the internal flow path is porously divided. Further, a plurality of heat transfer tubes 101 are provided at intervals in the first direction, and one end 101a is connected to the first header 10 and the other end 101b is connected to the second header 103.
  • the heat exchanger 100 is used as an evaporator, and the heat transfer tube 101 exchanges heat with the outside air for a low-pressure refrigerant having a liquid phase or a gas-liquid two-phase passing through the inside, and the low-pressure refrigerant in the liquid phase evaporates.
  • the corrugated fin 102 is provided between adjacent heat transfer tubes 101.
  • the corrugated fin 102 is provided will be described, but the present invention is not limited to this, and for example, plate fins may be provided.
  • the first header 10 and the second header 103 are formed in a tubular shape long in the first direction, and both ends thereof are closed by caps. Further, the first header 10 and the second header 103 have an insertion hole for inserting the heat transfer tube 101, one end 101a of the heat transfer tube 101 is inserted in the first header 10, and the heat transfer tube 101 is transferred to the second header 103. The other end 101b of the heat tube 101 is connected to each other.
  • the first header 10 has an outer wall 11 which is long in the first direction and is exposed to the outside, and an inner wall 12 which is long in the first direction and is provided inside the outer wall 11.
  • a low-pressure flow path 13 formed in the outer wall 11 from one end 10a to the other end 10b of the first header 10, and a high-pressure flow separated from the low-pressure flow path 13 by the inner wall 12 from one end 10a to the other end 10b of the first header 10. It has a road 14.
  • the outer wall 11 is brazed with a flat plate member 11a long in the first direction and a U-shaped curved member 11b long in the first direction and viewed in cross section from the first direction. It is formed integrally by being brazed.
  • the flat plate member 11a can be easily formed with an insertion hole for inserting the heat transfer tube 101 at low cost by press molding. Further, it is desirable that the outer wall 11 is made of a heat-conducting material.
  • the outer wall 11 is not limited to the one composed of the flat plate member 11a and the curved member 11b, and may be integrally formed by brazing by combining parts having any shape, or may be integrally formed in a tubular shape. ..
  • the inner wall 12 is provided in the area surrounded by the outer wall 11, and the space formed in the outer wall 11 that is long in the first direction is divided into two spaces in the second direction.
  • the inner wall 12 is longitudinal in the first direction as shown in FIG. 2, and is formed in an arc shape in a cross-sectional view as seen from the first direction as shown in FIG. Further, the inner wall 12 is provided so as to be separated from the heat transfer tube 101 in the second direction, and both ends thereof are brazed so as to be in contact with the inner surface of the outer wall 11. Since the low-pressure refrigerant flowing through the low-pressure flow path 13 and the high-pressure refrigerant flowing through the high-pressure flow path 14 exchange heat through the inner wall 12, the inner wall 12 is formed of a heat-conducting material.
  • the outer wall 11 and the inner wall 12 are not limited to those formed separately and brazed, and the whole may be integrally molded.
  • the flow path leading to both ends of the first header can be easily formed by molding by extrusion molding.
  • the low-pressure flow path 13 is partitioned by the low-pressure flow path partition 13c, and the low-pressure refrigerant distribution path 13a communicating with the outside of the first header 10 via the low-pressure refrigerant inflow pipe 104, and the low-pressure refrigerant. It is composed of a low-pressure refrigerant junction channel 13b that communicates with the outside of the first header 10 via the outflow pipe 105 and joins the low-pressure refrigerant that has passed through the inside of the heat transfer tube 101 and the inside of the second header 103.
  • one end 10a side partitioned by the low-pressure flow path partition 13c is the low-pressure refrigerant distribution path 13a, and the other end 10b side is the low-pressure refrigerant combined flow path 13b. Further, one end 101a of the plurality of heat transfer tubes 101 is connected to the low pressure flow path 13.
  • the low-pressure refrigerant flowing from the low-pressure refrigerant inflow pipe 104 provided at one end 10a of the first header 10 flows, and the low-pressure refrigerant is distributed to the plurality of heat transfer tubes 101 connected to the low-pressure refrigerant distribution path 13a. It is a flow path to be used.
  • the low-pressure refrigerant junction 13b is distributed from the low-pressure refrigerant distribution passage 13a to a plurality of heat transfer tubes 101, and further, after passing through the second header 103, the low-pressure refrigerant that has passed through the heat transfer tube 101 on the low-pressure refrigerant junction 13b merges. It is a flow path to be used.
  • a low-pressure refrigerant outflow pipe 105 is provided outside the first direction and on the other end 10b side of the first header 10 with respect to the plurality of heat transfer tubes 101, and the low-pressure refrigerant outflow pipe 105 is provided on the downstream side of the low-pressure refrigerant communication flow path 13b. It communicates with the outside of the first header 10 via.
  • the heat transfer tube 101 is inserted halfway through the low pressure flow path 13 from the insertion hole formed in the first header 10. At this time, it is desirable that the distance A 2 between one end 101 a of the heat transfer tube 101 and the inner wall 12 is larger than the length A 1 in which the heat transfer tube 101 is inserted into the low pressure flow path 13. By doing so, it is possible to reduce the unevenness in the low pressure flow path 13 and reduce the pressure loss of the low pressure refrigerant.
  • the high-pressure flow path 14 is formed in a region surrounded by a part of the curved member 11b of the outer wall 11 on the side separated from the heat transfer tube 101 in the second direction and the inner wall 12. Further, the high pressure flow path 14 is formed in a circular shape in a cross-sectional view seen from the first direction.
  • the high-pressure flow path 14 is not limited to a circular shape in a cross-sectional view, but by forming the high-pressure flow path 14 so that the circular shape or the outer circumference is curved in a cross-sectional view, stress concentration is less likely to occur, so that the pressure resistance performance is improved. It can be improved and the wall thickness of the high pressure refrigerant flow path can be reduced.
  • the inner wall 12 is a high pressure flow path in a cross-sectional view seen from the first direction. It occupies more than half of the entire outer circumference of 14. This promotes heat exchange between the high-pressure refrigerant and the low-pressure refrigerant via the inner wall 12.
  • the wall thickness of the pipe wall including a part of the curved member 11b of the outer wall 11 forming the high-pressure flow path 14 and the inner wall 12 is such that the wall thickness of the curved member 11b of the outer wall 11 is ⁇ 1.
  • the wall thickness of the inner wall 12 is defined as ⁇ 2, ⁇ 1> ⁇ 2, and the wall thickness of the outer wall 11 is larger. This is because the pressure difference between the low pressure flow path 13 and the high pressure flow path 14 is smaller than the pressure difference between the high pressure flow path 14 and the outside air.
  • the cross-sectional area of the low-pressure flow path 13 is larger than the cross-sectional area of the high-pressure flow path 14. This is because the low-pressure refrigerant has a lower density than the high-pressure refrigerant and has a large pressure loss, so that the flow path needs to be widened, and the high-pressure refrigerant flowing into the high-pressure flow path 14 passes through the bypass circuit 5 shown in FIG. This is because the flow rate is smaller than that of the low-pressure refrigerant flowing into the low-pressure flow path 13 because it is a part of the refrigerant.
  • the liquid-phase or gas-liquid two-phase low-pressure refrigerant that has passed through the expansion valve 3 in the main circuit 4 of the heat pump device 1000 flows from the low-pressure refrigerant inflow pipe 104 into the low-pressure refrigerant distribution path 13a formed in the first header 10. It flows in the first direction, which is the longitudinal direction of the first header 10. Then, the low-pressure refrigerant flowing in the low-pressure refrigerant distribution path 13a is distributed into a part of the heat transfer tubes 101 connected in the low-pressure refrigerant distribution path 13a in the process.
  • the low-pressure refrigerant exchanges heat with the outside air via the heat transfer tube 101 and the corrugated fin 102 in the process of flowing through the heat transfer tube 101.
  • the low-pressure refrigerant in the liquid phase evaporates in the heat transfer tube 101, flows in a gas-liquid two-phase state while increasing the dryness, and then flows into the second header 103.
  • the low pressure refrigerant is one end 101a of the heat transfer tube 101. Flows from to the other end 101b.
  • the low-pressure refrigerant flowing out from a part of the heat transfer tubes 101 arranged on the one end 10a side of the first header 10 merges in the second header 103 in the longitudinal direction of the second header 103 as shown by the arrow shown in FIG. It flows in the first direction. Then, the low-pressure refrigerant flowing in the second header 103 is distributed into the remaining heat transfer tube 101 arranged on the other end 10b side of the low-pressure flow path partition 13c.
  • the low pressure refrigerant flows from the other end 101b of 101 to one end 101a. Then, the liquid-phase low-pressure refrigerant contained in the low-pressure refrigerant flowing in the heat transfer tube 101 exchanges heat with the outside air and evaporates, and flows into the low-pressure refrigerant combined flow path 13b while increasing the dryness in the gas-liquid two-phase state. do.
  • the high-pressure refrigerant flowing into the bypass circuit 5 of the heat pump device 1000 flows from the high-pressure refrigerant inflow pipe 106 into the high-pressure flow path 14 formed in the first header 10, and from the other end 10b side of the first header 10. One end flows to the 10a side.
  • the high-pressure refrigerant that has flowed to one end 10a of the first header 10 is discharged from the high-pressure refrigerant outflow pipe 107.
  • the low-pressure flow path 13 faces the high-pressure flow path 14 via the inner wall 12, the low-pressure refrigerant flowing through the low-pressure flow path 13 and the high-pressure refrigerant flowing through the high-pressure flow path 14 are inside the first header 10. Heat exchange with. Of these, the low-pressure refrigerant flowing through the low-pressure refrigerant combined flow path 13b absorbs heat by exchanging heat with the high-pressure refrigerant, and when the low-pressure refrigerant in the liquid phase is contained, it evaporates until the dryness becomes 1, and the low-pressure refrigerant outflow pipe 105 It flows out to.
  • the low-pressure refrigerant outflow pipe 105 what flows out from the low-pressure refrigerant outflow pipe 105 is the low-pressure refrigerant in the gas phase having a dryness of 1, and is overheated by heat exchange with the high-pressure refrigerant.
  • the high-pressure refrigerant flowing through the high-pressure flow path 14 dissipates heat, reduces the enthalpy, and flows out to the high-pressure refrigerant outflow pipe 107.
  • FIGS. 4 and 5 are schematic views for explaining the flow of the low pressure refrigerant in the conventional heat exchanger 900.
  • FIG. 6 is a schematic diagram for explaining the flow of the low-pressure refrigerant in the heat exchanger 100 of the present embodiment.
  • the colored portions schematically show the liquid phase refrigerant, and the other white portions schematically show the gas phase refrigerant.
  • the flow rate and dryness of the low-pressure refrigerant distributed to the plurality of heat transfer tubes 101 vary, so that the low-pressure refrigerant combined flow path from the heat transfer tube 101 to the first header 90 In the vicinity of the refrigerant flowing into 13b, there may be a refrigerant having a gas phase and a refrigerant having a gas-liquid two-phase.
  • a part of the low-pressure refrigerant that has passed through the plurality of heat transfer tubes 101 flows from one of the heat transfer tubes 101 into the low-pressure refrigerant combined flow path 13b in a wet state with a dryness of less than 1.
  • a state is likely to occur in a heat exchanger in which the flow rate of the circulating refrigerant changes.
  • the pressure of the low-pressure refrigerant is further lowered to increase the temperature difference between the outside air and the refrigerant, thereby promoting the evaporation of the low-pressure refrigerant, and the heat transfer tube 101 to the first header 90.
  • a single-phase low-pressure refrigerant can be used in the vicinity of the refrigerant flowing into the low-pressure refrigerant combined flow path 13b.
  • the refrigerant in the heat transfer tube 101 evaporates at a position away from the low pressure refrigerant junction flow path 13b to become a gas phase, and the length of the heat transfer tube 101 becomes long.
  • the region (hatched portion in FIG. 5) that cannot be effectively utilized becomes large, and the heat exchange efficiency in the heat exchanger 100 decreases.
  • the dryness is less than 1 and the gas liquid Two-phase low pressure refrigerant may be present.
  • the low-pressure refrigerant containing the liquid phase flows through the low-pressure refrigerant combined flow path 13b, but evaporates by absorbing heat from the high-pressure refrigerant flowing through the high-pressure flow path 14, and after the dryness becomes 1, superheat is applied to the low-pressure refrigerant. It can flow out to the outflow pipe 105.
  • the internal heat exchange section is provided in the first header 10 so that the low-pressure refrigerant junction channel 13b where the low-pressure refrigerants that have passed through the plurality of heat transfer tubes 101 and the second header 103 merge with the high-pressure refrigerant exchanges heat with the high-pressure refrigerant.
  • the low-pressure refrigerant can be brought into a damp state with a dryness of less than 1 in the vicinity of the flow of the refrigerant from the heat pipe 101 into the low-pressure refrigerant combined flow path 13b.
  • the heat exchanger 100 can heat and evaporate the low-pressure refrigerant flowing through the low-pressure refrigerant combined flow path 13b, which is the most downstream of the low-pressure refrigerant flowing inside, with the high-pressure refrigerant. Therefore, even when the refrigerant distribution is non-uniform and the low-pressure refrigerant in the liquid phase flows out from the heat transfer tube 101, the low-pressure refrigerant can be evaporated by the internal heat exchange unit. As a result, since the entire region in the plurality of heat transfer tubes 101 can be effectively utilized, it is possible to obtain a heat exchanger with improved heat exchange efficiency.
  • the heat exchanger 100 of the present embodiment since the first header 10 is provided with an internal heat exchange section for heat exchange between the low pressure refrigerant and the high pressure refrigerant, the heat exchanger as a whole can be miniaturized and the cost can be reduced. Has the effect of reducing.
  • the heat exchanger 100 when the heat exchanger 100 is installed so that the first header 10 is on the lower side and the second header 103 is on the upper side with the second direction as the vertical direction, gravity causes the low-pressure refrigerant junction 13b in the first header 10 to be installed.
  • the low-pressure refrigerant in the liquid phase tends to collect in the lower part. Therefore, the effect that the low-pressure refrigerant of the liquid phase accumulated in the lower part of the low-pressure refrigerant combined flow path 13b stays at a position lower than the low-pressure refrigerant outflow pipe 105 further promotes heat exchange with the high-pressure refrigerant flowing through the high-pressure flow path 14. Play.
  • the heat exchanger 100 of the present embodiment is not limited to the one installed with the second direction as the vertical direction.
  • the air flow passing through the outside of the heat transfer tubes 101 is also affected.
  • Condensation water is generated around the heat transfer tube 101 through which the two-phase gas-liquid two-phase low-pressure refrigerant flows and the corrugated fin 102 located in the vicinity thereof, and the ventilation resistance increases.
  • dew condensation water does not occur around at least a part of the heat transfer tube 101 in which the single-phase low-pressure refrigerant flows and the corrugated fins 102 located in the vicinity thereof, and the ventilation resistance becomes small. That is, the distribution of air is biased due to the difference in ventilation resistance, and more air passes around the heat transfer tube 101, which has a small amount of liquid phase refrigerant to be evaporated, so that the heat exchange efficiency is lowered.
  • the dryness of the low-pressure refrigerant can be set to less than 1 up to the most downstream of the heat transfer tube 101, so that the decrease in heat exchange efficiency due to the uneven distribution of air can be suppressed. Has the effect of being able to. According to the experiments of the inventors, it was found that this effect is particularly remarkable in the corrugated fin, which has poorer drainage property in the fin than the plate fin. Therefore, the heat exchanger using the corrugated fin is particularly effective.
  • the heat exchanger 100 when the heat exchanger 100 is installed so that the first header 10 is located on the lower side of the heat exchanger 100 and the second header 103 is located on the upper side with the second direction shown in FIG. 2 as the vertical direction, the heat exchanger 100 is installed downward. Condensation water tends to collect in the vicinity of the first header 10 located in.
  • the heat exchanger 100 of the present embodiment since the high pressure flow path 14 through which the high pressure refrigerant flows is provided below the first header 10, it is possible to heat the lower part of the first header 10 where dew condensation water tends to collect. It has the effect of reducing the amount of root ice generated in the lower part of the heat exchanger 100.
  • the high-pressure refrigerant is provided in the inner wall by providing the high-pressure flow path 14 with the proportion of the inner wall 12 being more than half of the part of the outer wall 11 and the inner wall 12 which are the pipe walls of the high-pressure flow path 14. Since the area in contact with the low-pressure refrigerant increases through 12, the effect of improving the internal heat exchange efficiency is achieved. Further, since the high pressure flow path 14 is provided with a part of the outer wall 11 as a pipe wall, heat exchange with the low pressure refrigerant can be promoted by transferring heat to the outer wall 11.
  • the low pressure flow path 13 is divided into a low pressure refrigerant distribution path 13a and a low pressure refrigerant combined flow path 13b by the low pressure flow path partition 13c. Therefore, it is conceivable that the temperature of the low-pressure refrigerant is higher in the low-pressure refrigerant combined flow path 13b than in the low-pressure refrigerant distribution path 13a due to overheating. Further, when a mixed refrigerant is used, the temperature may change due to the change in the composition of the gas and liquid due to the change of state. It is possible that it will be higher.
  • the low pressure flow path 13 has a temperature gradient as described above, the temperature difference between the high pressure refrigerant and the low pressure refrigerant can be obtained by making the low pressure flow path 13 and the high pressure flow path 14 countercurrent. Therefore, the effect of further improving the heat exchange efficiency in the internal heat exchange unit is obtained.
  • the wall thickness ⁇ 2 of the inner wall 12 is smaller than the wall thickness ⁇ 1 of the outer wall 11, it is possible to promote heat exchange between the low pressure refrigerant and the high pressure refrigerant while reducing the material cost. Play.
  • the low pressure flow path 13 and the high pressure flow path 14 are formed so as to reach both ends in the first direction except for the cap, so that extrusion molding is easy. Therefore, the moldability is improved and the molding cost can be reduced.
  • the heat pump device 1000 of the present embodiment is provided with a bypass circuit 5 in addition to the main circuit 4 constituting the refrigeration cycle. Therefore, since the bypass circuit 5 can be used as a liquid reservoir and the amount of refrigerant in the main circuit 4 can be adjusted, it is possible to reduce the size of the tank (not shown) for the liquid reservoir provided in the refrigeration cycle. It has the effect that can be achieved.
  • the header 10 can be miniaturized, and the heat exchanger 100 as a whole can be miniaturized.
  • the case where one low-voltage flow path partition 13c is provided in the low-voltage flow path 13 of the first header 10 has been described, but it is also possible to provide a plurality of flow path partitions. good. Even in this case, the low-pressure refrigerant distribution path and the low-pressure refrigerant combined flow path are provided in the first header.
  • the configuration in which the heat exchanger 100 of the present embodiment is used as an evaporator has been described as an example, but the present invention is not limited to this, and the heat exchanger 100 of the present embodiment is not limited to this, but as an evaporator in the same circuit configuration.
  • the heat exchangers of the modifications and other embodiments described below may be used.
  • FIG. 7 is a cross-sectional view of the heat exchanger 110 according to the first modification of the heat exchanger 100 of the present embodiment as viewed from a third direction.
  • the heat exchanger 110 according to the first modification is the first embodiment in that the low pressure flow path 13 and the high pressure flow path 14 provided in the first header 10 are parallel flows. It is different from the heat exchanger 100 of. Hereinafter, the points different from the heat exchanger 100 will be mainly described.
  • the low-pressure flow path 13 and the high-pressure flow path 14 provided in the first header 10 of the heat exchanger 110 are both parallel flows flowing from one end 10a side to the other end 10b side of the first header 10.
  • the positions where the high-pressure refrigerant inflow pipe 106 and the high-pressure refrigerant outflow pipe 107 are provided are different from those of the heat exchanger 100 of the first embodiment.
  • the high-pressure refrigerant inflow pipe 106 is provided at one end 10a of the first header 10.
  • a high-pressure refrigerant outflow pipe 107 is provided on the other end 10b side, respectively.
  • the heat exchanger 110 configured in this way has the effect of improving the heat exchange efficiency, as in the heat exchanger 100 of the present embodiment.
  • FIG. 8 is a cross-sectional view of the heat exchanger 120 according to the second modification of the heat exchanger 100 of the present embodiment as viewed from a third direction.
  • FIG. 9 is a cross-sectional view of a main part of the heat exchanger 120 as viewed from a third direction. In FIG. 9, the corrugated fin 102 is not shown.
  • the heat exchanger 120 according to the second modification is the heat of the first embodiment in that the low pressure refrigerant inflow pipe 104 and the low pressure refrigerant outflow pipe 105 are connected so as to face the third direction. It is different from the exchanger 100.
  • the points different from the heat exchanger 100 will be mainly described.
  • the low-pressure refrigerant inflow pipe 104 is provided outside the first direction of the plurality of heat transfer tubes 101 and on the one end 10a side of the first header 10 facing the third direction, and is connected to the low-pressure refrigerant distribution path 13a. That is, the low-pressure refrigerant inflow pipe 104 is provided so that the low-pressure refrigerant flows in the third direction.
  • the low-pressure refrigerant outflow pipe 105 is provided outside the first direction and on the other end 10b side of the first header 10 with respect to the plurality of heat transfer pipes 101 so as to face the third direction, and is connected to the low-pressure refrigerant combined flow path 13b. That is, the low-pressure refrigerant outflow pipe 105 is provided so that the low-pressure refrigerant flows out in the third direction.
  • the diameter d1 of the low-pressure refrigerant inflow pipe 104 can be made larger than the distance t1 between one end 101a of the heat transfer tube 101 and the inner wall 12.
  • the diameter of the low-pressure refrigerant outflow pipe 105 can be larger than the distance between one end 101a of the heat transfer pipe 101 and the inner wall 12.
  • the low pressure refrigerant inflow pipe 104 is provided in the first direction, it interferes with the high pressure refrigerant outflow pipe 107. Therefore, a routing circuit is provided or the low pressure refrigerant inflow pipe 104 is provided. It is necessary to reduce the diameter.
  • the low pressure refrigerant inflow pipe 104 is provided in the third direction as in the heat exchanger 120 according to the second modification shown in FIG. 9, it does not interfere with the high pressure refrigerant outflow pipe 107 provided in the first direction.
  • the diameters of the low-pressure refrigerant inflow pipe 104 and the high-pressure refrigerant outflow pipe 107 can be increased, and the pressure loss can be reduced.
  • the low-pressure refrigerant outflow pipe 105 is provided in the third direction, the low-pressure refrigerant outflow pipe 105 and the high-pressure refrigerant inflow pipe 106 are increased in diameter because they do not interfere with the high-pressure refrigerant inflow pipe 106 provided in the first direction. can do.
  • FIG. 10 is a cross-sectional view of a main part of the heat exchanger 130 according to the third modification of the heat exchanger 100 of the present embodiment as viewed from the first direction.
  • the heat exchanger 130 according to the third modification is different from the heat exchanger 100 of the first embodiment in that the protrusion 15 is provided on the pipe wall forming the high pressure flow path.
  • the points different from the heat exchanger 100 will be mainly described.
  • the heat exchanger 130 is provided with protrusions 15 for promoting heat transfer so as to face the high pressure flow path 14 on the pipe wall composed of a part of the outer wall 11 forming the high pressure flow path 14 and the inner wall 12.
  • protrusions 15 for promoting heat transfer so as to face the high pressure flow path 14 on the pipe wall composed of a part of the outer wall 11 forming the high pressure flow path 14 and the inner wall 12.
  • groove processing may be performed. That is, at least one of the protrusion 15 and the groove is formed on the surface of the pipe wall forming the high pressure flow path 14 on the surface on the high pressure flow path 14 side.
  • the low-pressure refrigerant flowing from the low-pressure refrigerant inflow pipe 104 into the low-pressure flow path 13 is a liquid single phase or a liquid-rich gas-liquid two-phase, and heat is absorbed by heat exchange with the high-pressure refrigerant with heat transfer. ..
  • the high-pressure refrigerant flowing from the high-pressure refrigerant inflow pipe 106 into the high-pressure flow path 14 is a liquid single phase or a liquid-rich gas-liquid two-phase, and heat is dissipated by condensation heat transfer by heat exchange with the low-pressure refrigerant.
  • the heat exchange efficiency between the high-pressure refrigerant and the low-pressure refrigerant is improved while reducing the pressure loss of the low-pressure refrigerant in the low-pressure flow path 13. It has an effect that can be further improved.
  • FIG. 11 is a cross-sectional view of the heat exchanger 200 of the present embodiment as viewed from a third direction
  • FIG. 12 is a cross-sectional view of a main part of the heat exchanger 200 as viewed from the first direction.
  • FIG. 13 is a schematic diagram for explaining the flow of the low-pressure refrigerant in the heat exchanger 200.
  • the heat exchanger 200 of the present embodiment is further provided with a long dividing wall 21 in the first direction for dividing the low pressure refrigerant distribution path 23a into two in the second direction. It is different from the heat exchanger 100 of 1.
  • the points different from the heat exchanger 100 of the first embodiment will be mainly described.
  • the heat exchanger 200 is provided with a low pressure flow path 23 including a low pressure refrigerant distribution path 23a and a low pressure refrigerant combined flow path 23b in the first header 20. Further, in the heat exchanger 200, the low-pressure refrigerant inflow pipe 104 and the low-pressure refrigerant outflow pipe 105 have a third direction similar to the heat exchanger 120 according to the second modification of the heat exchanger 100 of the first embodiment. It is provided facing.
  • the dividing wall 21 is provided in the low-pressure refrigerant distribution path 23a of the low-pressure flow path 23, and a plurality of orifice holes 21a are formed at positions between adjacent heat transfer tubes 101.
  • the low-pressure refrigerant distribution path 23a is separated from the first low-pressure refrigerant distribution path 231 to which the heat transfer tube 101 is connected by the split wall 21 in the second direction. It is divided into a low-pressure refrigerant distribution path 232.
  • the first low-pressure refrigerant distribution path 231 and the second low-pressure refrigerant distribution path 232 communicate with each other through the orifice hole 21a.
  • the low-pressure refrigerant inflow pipe 104 is connected to the second low-pressure refrigerant distribution path 232 of the low-pressure refrigerant distribution paths 23a. Therefore, as shown in FIG. 13, the low-pressure refrigerant flows from the outside of the heat exchanger 200 into the second low-pressure refrigerant distribution path 232 through the low-pressure refrigerant inflow pipe 104, passes through the orifice hole 21a, and is the first low-pressure refrigerant. It is distributed from the refrigerant distribution path 231 to the heat transfer tube 101.
  • the heat transfer tube 101 projects and is connected to the low pressure refrigerant distribution path. Therefore, when the low-pressure refrigerant distribution path 13a does not have a dividing wall as in the heat exchanger 100 of the first embodiment, the flow path is uneven at the portion where the heat transfer tube 101 protrudes and the portion where the heat transfer tube 101 is not provided. Is formed, and the fluid loss due to the expansion and contraction of the refrigerant due to this is increased. According to the experiments and analysis of the inventors, when the flow path area is designed assuming the frictional resistance of the fluid, the pressure loss is actually larger than the predicted value, and the breakdown is the total fluid loss of expansion and contraction. In some cases, it accounted for more than 50% of the pressure loss.
  • the pressure loss of the refrigerant when flowing in the first direction can be reduced, the distribution of the low-pressure refrigerant to the heat transfer tube 101 can be made uniform, and the heat exchange efficiency with the outside air in the heat exchanger 200 can be improved. Has the effect of being able to.
  • FIG. 14 is a cross-sectional view of a main part of the heat exchanger 300 of the present embodiment as viewed from the first direction.
  • the low pressure flow path 33 has a cross section separated from the first low pressure flow path 331 to which the heat transfer tube 101 is connected in the second direction from the heat transfer tube 101.
  • the heat exchanger of the first embodiment is provided with a second low-voltage flow path 332 formed in a circular shape with a part cut out visually, and a point in which the outer wall 31 and the inner wall 32 are integrally formed. Different from 100.
  • the points different from the heat exchanger 100 of the first embodiment will be mainly described.
  • the low pressure flow path 33 includes a low pressure refrigerant distribution path and a low pressure refrigerant combined flow path, similarly to the heat exchanger 100 of the first embodiment.
  • the low-voltage flow path 33 is formed by integrally forming a first low-pressure flow path 331 on the side where the heat transfer tube 101 is inserted in the second direction and a second low-pressure flow path 332 on the side separated from the heat transfer tube 101.
  • the second low-voltage flow path 332 is formed in a circular shape with a part of the side facing the heat transfer tube 101 cut out in a cross-sectional view seen from the first direction.
  • two second low-voltage flow paths 332 are provided side by side in the third direction.
  • the high pressure flow path 34 is formed in a circular shape in a cross-sectional view seen from the first direction. Further, the high-pressure flow path 14 is formed at a position between the two second low-pressure flow paths 332 in the third direction, and the high-pressure refrigerant exchanges heat with the low-pressure refrigerant flowing through the two second low-pressure flow paths 332. be able to.
  • the first header 30 of the heat exchanger 300 is integrally formed by extrusion molding so that the low pressure flow path 33 and the high pressure flow path 34 reach both ends. Therefore, the inner wall 32 and the outer wall 31 are integrally formed without a boundary.
  • the heat exchanger 300 of the present embodiment the low pressure refrigerant flowing in the first direction flows through the second low pressure flow path 332, which has the effect of reducing the pressure loss.
  • the heat exchanger 300 is installed so that the first header 30 is on the lower side with the second direction as the vertical direction, so that the low pressure refrigerant easily flows into the second low pressure flow path 332.
  • the second low-pressure flow path 332 is formed in a circular shape with a part cut out in a cross-sectional view, among the low-pressure refrigerants flowing inside the second low-pressure flow path 332, the low-pressure refrigerant in the liquid phase is the pipe wall.
  • the low-pressure refrigerant in the gas phase tends to form a circular flow flowing in the center. Therefore, heat transfer is promoted between the high-pressure refrigerant flowing through the high-pressure flow path 34 and the liquid refrigerant flowing through the second low-pressure flow path 332, which has the effect of improving the efficiency of internal heat exchange.
  • FIG. 14 is a cross-sectional view of a main part of the heat exchanger 310 according to a modification of the heat exchanger 300 of the present embodiment as viewed from the first direction.
  • the heat exchanger 310 is the heat exchanger 300 of the third embodiment in that a long dividing wall 35 is further provided in the first direction for dividing the low pressure refrigerant distribution path 33a in the second direction. Is different. Hereinafter, the differences from the heat exchanger 300 will be mainly described.
  • the dividing wall 35 is provided at least in the low pressure refrigerant distribution path 33a of the low pressure flow path 33, and a plurality of orifice holes are provided at positions between adjacent heat transfer tubes 101. 35a is formed.
  • the low pressure refrigerant distribution path 33a has a second low pressure flow path 331 to which the heat transfer tube 101 is connected and a second low pressure flow path 331 separated from the heat transfer tube 101 in the second direction. It is divided into a flow path 332 and a flow path 332.
  • the first low pressure flow path 331 and the two second low pressure flow paths 332 communicate with each other via the orifice hole 35a.
  • FIG. 16 is a cross-sectional view of a main part of the heat exchanger 400 of the present embodiment as viewed from the first direction.
  • the inner wall 42 is composed of the first inner wall 421 and the second inner wall 422, and the shape of the flow path is different from that of the heat exchanger 100 of the first embodiment.
  • the points different from the heat exchanger 100 of the first embodiment will be mainly described.
  • the inner wall 42 has a first inner wall 421 that divides the internal space surrounded by the outer wall 41 into a first flow path 45 and a second flow path 46 in the second direction, and a second flow path 46 that is divided into two in the third direction. It is composed of a second inner wall 422 to be divided.
  • the first inner wall 421 and the second inner wall 422 are flat plate-shaped members elongated in the first direction, respectively, and are joined by brazing. Further, both the first inner wall 421 and the second inner wall 422 are formed of a heat-conducting material.
  • the first inner wall 421 has an internal space surrounded by the outer wall 41, a first flow path 45 to which the heat transfer tube 101 is connected, and a second flow path 46 separated from the heat transfer tube 101 in the second direction. Divide into two in the direction.
  • An orifice hole 421a is formed on the upstream side of the outside air flow in the first inner wall 421.
  • the second inner wall 422 divides the second flow path 46 into two in the third direction.
  • one of the flow paths on the upstream side of the outside air flow, which is divided by the second inner wall 422, is the second low pressure flow path 432.
  • the other flow path on the downstream side of the outside air flow, which is divided by the second inner wall 422, is the high pressure flow path 44.
  • the first flow path 45 is the first low pressure flow path 431 through which the low pressure refrigerant flows. Then, the first low pressure flow path 431 (first flow path 45) communicates with the second low pressure flow path 432 of the second flow path 46 by the orifice hole 421a formed in the first inner wall 421. That is, in the first header 40 of the heat exchanger 400 of the present embodiment, the low pressure flow path is configured by the first low pressure flow path 431 and the second low pressure flow path 432.
  • the low-pressure refrigerant inflow pipe 104 is connected to the first low-pressure flow path 431 , but the present invention is not limited to this, and the low-pressure refrigerant inflow pipe 104 is connected to the second low-pressure flow path 432. May be done.
  • the inner wall 42 is composed of the flat plate-shaped first inner wall 421 and the second inner wall 422, it can be formed at low cost by using a plate-shaped member and further pressing. It has the effect that can be achieved.
  • the second low-pressure flow path 432 is located on the upstream side of the outside air flow in the second flow path 46, more low-pressure refrigerant is allowed to flow on the upstream side of the outside air flow in the heat transfer tube 101 as well. This has the effect of improving heat exchange efficiency.
  • the second low pressure flow path 432 is not limited to the one located on the upstream side of the outside air flow, and the high pressure flow path 44 may be located on the upstream side.
  • FIG. 17 is a cross-sectional view of the heat exchanger 500 of the present embodiment as viewed from a third direction
  • FIG. 18 is a cross-sectional view of a main part of the heat exchanger 500 as viewed from the first direction.
  • the high pressure flow path 54 includes a first high pressure flow path 541 and a second high pressure flow path 542, and the high pressure refrigerant inflow pipe 106 and high pressure.
  • the refrigerant outflow pipe 107 is different from the heat exchanger 100 of the first embodiment in that each of the refrigerant outflow pipes 107 is provided on one end 50a side of the first header 50.
  • the points different from the heat exchanger 100 of the first embodiment will be mainly described.
  • the high-pressure flow path 54 includes a first high-pressure flow path 541 and a second high-pressure flow path 542 that are countercurrent with each other. As shown in FIG. 18, the first high-pressure flow path 541 and the second high-pressure flow path 542 are formed so as to be separated from each other in the third direction.
  • the first high-pressure flow path 541 and the second high-pressure flow path 542 are folded back and connected by a U-shaped tube 501 provided on the other end 50b side of the first header 50.
  • a U-shaped tube 501 is provided outside the first header 50 to fold back the first high-voltage flow path 541 and the second high-voltage flow path 542 will be described.
  • the present invention is not limited to this, and for example, a folded portion may be provided in the cap of the first header.
  • the high-pressure refrigerant inflow pipe 106 and the high-pressure refrigerant outflow pipe 107 are both provided on one end 50a side of the first header 50, as shown in FIG.
  • the high-pressure refrigerant inflow pipe 106 and the high-pressure refrigerant outflow pipe 107 show the same location for convenience, but in reality, they are separated from each other in the third direction in the first high-pressure flow path 541 and the second high-pressure flow path 542, respectively. Be connected.
  • first header 50 in the heat exchanger 500 of the present embodiment the outer wall 51 and the inner wall 52 are integrally formed without a boundary as shown in FIG.
  • Such a first header 50 can be easily formed by extrusion molding.
  • the high-pressure flow path 54 is formed by extrusion molding, and the outer wall 51 and the inner wall 52 are integrally formed, so that the pressure resistance can be improved.
  • the heat exchanger 500 is provided with a plurality of high-pressure flow paths 54, the heat transfer area between the low-pressure flow path 13 and the high-pressure flow path 54 can be increased, which has the effect of promoting internal heat exchange.
  • the high-pressure flow path 54 is composed of two high-pressure flow paths 541 and a second high-pressure flow path 542. Therefore, both the high-pressure refrigerant inflow pipe 106 and the high-pressure refrigerant outflow pipe 107 can be formed on one end 50a side of the same first header 50, which has the effect of reducing the number of handling refrigerant pipes.
  • the high-pressure flow path may be composed of a plurality of three or more flow paths, and in this case as well, if the number of high-pressure flow paths is an even number, it is possible to reduce the number of refrigerant pipes to be handled.
  • the wall thickness of the pipe wall including the outer wall 51 and the inner wall 52 forming the high-pressure flow path 54 is ⁇ 1 for the wall thickness of the portion related to the outer wall 51 and the wall thickness of the portion related to the inner wall 52. Is defined as ⁇ 2, ⁇ 1> ⁇ 2, and the wall thickness of the outer wall 51 is larger.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur dans lequel l'échange de chaleur entre les fluides frigorigènes dans un collecteur permet de provoquer l'évaporation d'un fluide frigorigène à basse pression avant que celui-ci ne s'écoule vers l'extérieur, et dans lequel l'efficacité de l'échange de chaleur est améliorée.　L'échangeur de chaleur (100) est pourvu d'une pluralité de tubes de transfert de chaleur (101), d'un premier collecteur (10) auquel une extrémité (101a) des tubes de transfert de chaleur est raccordée, d'un second collecteur (103) auquel l'autre extrémité (101b) des tubes de transfert de chaleur est raccordée, un tube d'entrée de fluide frigorigène basse pression (104) disposé sur le côté d'une extrémité (10a) du premier collecteur, et un tube de sortie de fluide frigorigène basse pression (105) disposé à une position qui est sur le côté de l'autre extrémité (10b) du premier collecteur et plus loin que la pluralité de tubes de transfert de chaleur sur le côté externe. Le premier collecteur (10) comporte : un trajet d'écoulement à basse pression s'étendant d'une extrémité à l'autre extrémité du premier collecteur et comprenant un trajet de distribution de réfrigération à basse pression (13a) pour distribuer un fluide réfrigérant à basse pression aux tubes de transfert de chaleur et un trajet de convergence de fluide réfrigérant à basse pression (13b) dans lequel le fluide réfrigérant à basse pression converge ; et un trajet d'écoulement à haute pression qui est séparé du trajet d'écoulement à basse pression et qui s'étend d'une extrémité à l'autre extrémité du premier collecteur.
PCT/JP2020/021767 2020-06-02 2020-06-02 Échangeur de chaleur et dispositif de pompe à chaleur WO2021245788A1 (fr)

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PCT/JP2020/021767 WO2021245788A1 (fr) 2020-06-02 2020-06-02 Échangeur de chaleur et dispositif de pompe à chaleur

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JP2004353936A (ja) * 2003-05-28 2004-12-16 Denso Corp 熱交換器および受液器一体型凝縮器
JP2007093097A (ja) * 2005-09-28 2007-04-12 Mitsubishi Electric Corp ヒートポンプ給湯機及びヒートポンプ給湯機の制御方法
US20130312441A1 (en) * 2012-05-25 2013-11-28 Hussmann Corporation Heat exchanger with integrated subcooler
JP2017187256A (ja) * 2016-04-08 2017-10-12 ダイキン工業株式会社 熱交換器

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US20040089439A1 (en) 2002-11-07 2004-05-13 Treverton Andrew Clare Tube-to-tube heat exchanger assembly
JP2006097911A (ja) 2004-09-28 2006-04-13 Calsonic Kansei Corp 熱交換器
JP2017044428A (ja) 2015-08-27 2017-03-02 株式会社東芝 熱交換器、分流部品、および熱交換装置
JP7108177B2 (ja) 2018-03-30 2022-07-28 ダイキン工業株式会社 熱交換器および空気調和装置
CN113330268B (zh) 2019-02-04 2023-05-16 三菱电机株式会社 热交换器以及具备热交换器的空气调节装置

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Publication number Priority date Publication date Assignee Title
JP2002098486A (ja) * 2000-09-25 2002-04-05 Zexel Valeo Climate Control Corp 熱交換器及びその製造方法
JP2004353936A (ja) * 2003-05-28 2004-12-16 Denso Corp 熱交換器および受液器一体型凝縮器
JP2007093097A (ja) * 2005-09-28 2007-04-12 Mitsubishi Electric Corp ヒートポンプ給湯機及びヒートポンプ給湯機の制御方法
US20130312441A1 (en) * 2012-05-25 2013-11-28 Hussmann Corporation Heat exchanger with integrated subcooler
JP2017187256A (ja) * 2016-04-08 2017-10-12 ダイキン工業株式会社 熱交換器

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