WO2024121984A1 - Échangeur thermique, unité extérieure comprenant un échangeur thermique et dispositif de climatisation comprenant une unité extérieure - Google Patents

Échangeur thermique, unité extérieure comprenant un échangeur thermique et dispositif de climatisation comprenant une unité extérieure Download PDF

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Publication number
WO2024121984A1
WO2024121984A1 PCT/JP2022/045137 JP2022045137W WO2024121984A1 WO 2024121984 A1 WO2024121984 A1 WO 2024121984A1 JP 2022045137 W JP2022045137 W JP 2022045137W WO 2024121984 A1 WO2024121984 A1 WO 2024121984A1
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Prior art keywords
heat exchanger
refrigerant
distribution space
header
lower header
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PCT/JP2022/045137
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English (en)
Japanese (ja)
Inventor
洋次 尾中
七海 岸田
理人 足立
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三菱電機株式会社
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Priority to PCT/JP2022/045137 priority Critical patent/WO2024121984A1/fr
Publication of WO2024121984A1 publication Critical patent/WO2024121984A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates

Definitions

  • This disclosure relates to a heat exchanger having a plurality of flat tubes, an outdoor unit equipped with the heat exchanger, and an air conditioner equipped with the outdoor unit.
  • the heat exchanger comprises a heat exchange body having a plurality of flat tubes arranged at intervals in the horizontal direction, an upper header provided at the upper end of the heat exchange body, a lower header provided at the lower end of the heat exchange body, an inlet portion provided at one end of the lower header into which a refrigerant flows when the lower header functions as an evaporator, and a partition plate that divides the interior of the lower header into a plurality of spaces in the horizontal direction, the lower header has at least one lower distribution space therein that distributes the refrigerant when the lower header functions as an evaporator, one of the lower distribution spaces is a first lower distribution space that is located most upstream in the refrigerant flow when the lower header functions as an evaporator, and the first lower distribution space is provided with at least one suppression plate that protrudes upward from the bottom of the lower header and suppresses the refrigerant flow, and one of the suppression plates is provided between the inlet portion and the flat tube closest to the inlet portion in the horizontal direction
  • the air conditioning device according to the present disclosure is equipped with the outdoor unit described above.
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner equipped with a heat exchanger according to a first embodiment.
  • 4 is a front view showing a schematic diagram of a refrigerant flow during heating operation of the heat exchanger according to the first embodiment;
  • FIG. FIG. 3 is an enlarged view of the portion indicated by the arrow A in FIG. 2 .
  • 4 is a cross-sectional view taken along the line BB in FIG. 3.
  • 4 is an enlarged front view showing a schematic view of an upper distribution space inside an upper header and a lower distribution space inside a lower header of the heat exchanger according to the first embodiment.
  • FIG. 1 is a diagram showing the relationship between the inner diameter of the upper header of a heat exchanger functioning as an evaporator and the liquid level of a gas-liquid two-phase refrigerant when taking into account refrigerant operating conditions typically used in an air conditioning apparatus according to embodiment 1.
  • 11 is a front view showing a schematic diagram of a refrigerant flow during heating operation of a heat exchanger according to a second embodiment.
  • FIG. 11 is an enlarged front view showing a schematic view of a lower distribution space inside a lower header of a heat exchanger according to a second embodiment.
  • FIG. 13 is a diagram showing the relationship between the distance between adjacent restraint plates inside the lower header of the heat exchanger according to the second embodiment and heat exchange performance.
  • the air conditioner 100 also includes a refrigerant circuit in which the compressor 11, flow path switching device 12, heat exchanger 30, throttling device 21, and indoor heat exchanger 22 are connected by refrigerant piping, and the refrigerant circulates.
  • the air conditioner 100 can perform both cooling and heating operations by switching the flow path switching device 12.
  • Compressor 11 draws in low-temperature, low-pressure refrigerant, compresses it, and discharges high-temperature, high-pressure refrigerant.
  • Compressor 11 is, for example, an inverter compressor whose capacity, which is the amount of refrigerant discharged per unit time, is controlled by changing the operating frequency.
  • the heat exchanger 30 exchanges heat between the outdoor air and the refrigerant.
  • the heat exchanger 30 functions as a condenser that releases heat from the refrigerant to the outdoor air and condenses the refrigerant.
  • the heat exchanger 30 functions as an evaporator that evaporates the refrigerant and cools the outdoor air with the heat of vaporization.
  • the fan 13 supplies outdoor air to the heat exchanger 30, and the amount of air sent to the heat exchanger 30 is adjusted by controlling the rotation speed.
  • the indoor heat exchanger 22 exchanges heat between the indoor air and the refrigerant.
  • the indoor heat exchanger 22 functions as an evaporator that evaporates the refrigerant and cools the outdoor air with the heat of vaporization.
  • the indoor heat exchanger 22 functions as a condenser that releases heat from the refrigerant to the outdoor air to condense the refrigerant.
  • the indoor fan 23 supplies indoor air to the indoor heat exchanger 22, and the amount of air sent to the indoor heat exchanger 22 is adjusted by controlling the rotation speed.
  • Fig. 2 is a front view showing a schematic refrigerant flow during heating operation of the heat exchanger 30 according to the first embodiment.
  • Fig. 3 is an enlarged view of the portion viewed from the arrow A in Fig. 2.
  • Fig. 4 is a cross-sectional view viewed from the arrow B-B in Fig. 3.
  • Fig. 5 is an enlarged front view showing a schematic upper distribution space 35b in the upper header 35 and a lower distribution space 34a in the lower header 34 of the heat exchanger 30 according to the first embodiment.
  • the black arrows in Figs. 2 and 3 indicate the refrigerant flow when the heat exchanger 30 functions as an evaporator.
  • the heat exchanger 30 includes a heat exchange body 31 having a plurality of flat tubes 38 and a plurality of fins 39.
  • the flat tubes 38 are arranged in parallel in the horizontal direction (left-right direction in FIG. 2) at intervals so that the wind generated by the fan 13 can flow, and the refrigerant flows vertically in the tubes extending in the vertical direction (up-down direction in FIG. 2).
  • the fins 39 are connected between adjacent flat tubes 38 and transfer heat to the flat tubes 38.
  • the fins 39 improve the efficiency of heat exchange between the air and the refrigerant, and for example, corrugated fins are used. However, this is not limited to this. Since heat exchange between the air and the refrigerant occurs on the surfaces of the flat tubes 38, the fins 39 may not be required.
  • a lower header 34 is provided at the lower end of the heat exchange body 31.
  • the lower ends of the flat tubes 38 of the heat exchange body 31 are directly inserted into the lower header 34.
  • An upper header 35 is provided at the upper end of the heat exchange body 31.
  • the upper ends of the flat tubes 38 of the heat exchange body 31 are directly inserted into the upper header 35.
  • the lower header 34 is provided with a first pipe 36 and a second pipe 37, and the heat exchanger 30 is connected to the refrigerant circuit of the air conditioning device 100 via the first pipe 36 and the second pipe 37.
  • the first pipe 36 allows the low-temperature, high-pressure liquid refrigerant after heat exchange in the heat exchanger 30 to flow out to the refrigerant circuit during cooling operation, and allows the low-temperature, low-pressure two-phase gas-liquid refrigerant after being decompressed by the throttling device 21 to flow into the heat exchanger 30 during heating operation.
  • the second pipe 37 allows the high-temperature, high-pressure gas refrigerant from the compressor 11 to flow into the heat exchanger 30 during cooling operation, and allows the low-temperature, low-pressure gas refrigerant after heat exchange in the heat exchanger 30 to flow out to the refrigerant circuit during heating operation.
  • the second pipe 37 is provided in the upper header 35 instead of the lower header 34.
  • the first pipe 36 is also referred to as the inlet section
  • the second pipe 37 is also referred to as the outlet section.
  • the flat tubes 38, the fins 39, the lower header 34, and the upper header 35 are all made of aluminum and are joined by brazing.
  • the low-temperature, high-pressure liquid refrigerant that flows out of the heat exchanger 30 is decompressed by the throttling device 21, becomes a low-temperature, low-pressure two-phase gas-liquid refrigerant, and flows into the indoor heat exchanger 22.
  • the low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the indoor heat exchanger 22 exchanges heat with the indoor air taken in by the indoor fan 23, evaporates while absorbing heat, cools the indoor air, and flows out of the indoor heat exchanger 22 as a low-temperature, low-pressure gas refrigerant.
  • the low-temperature, low-pressure gas refrigerant that flows out of the indoor heat exchanger 22 is sucked into the compressor 11 and becomes a high-temperature, high-pressure gas refrigerant again.
  • ⁇ Heating operation> During heating operation, the flow path switching device 12 is switched to the state shown by the broken line in Fig. 1. Then, the high-temperature, high-pressure gas refrigerant discharged from the compressor 11 flows into the indoor heat exchanger 22 through the flow path switching device 12. The high-temperature, high-pressure gas refrigerant that flows into the indoor heat exchanger 22 exchanges heat with the indoor air taken in by the indoor fan 23 and condenses while releasing heat, heating the indoor air and becoming a low-temperature, high-pressure liquid refrigerant, which flows out of the indoor heat exchanger 22.
  • the low-temperature, high-pressure liquid refrigerant that flows out of the indoor heat exchanger 22 is decompressed by the throttling device 21, becomes a low-temperature, low-pressure two-phase gas-liquid refrigerant, and flows into the heat exchanger 30.
  • the low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the heat exchanger 30 exchanges heat with the outdoor air taken in by the fan 13, evaporates while absorbing heat, and flows out of the heat exchanger 30 as a low-temperature, low-pressure gas refrigerant.
  • the low-temperature, low-pressure gas refrigerant that flows out of the heat exchanger 30 is sucked into the compressor 11 and becomes a high-temperature, high-pressure gas refrigerant again.
  • defrosting operation the fan 13 is stopped, the flow path switching device 12 is switched to the same state as in cooling operation (the state shown by the solid line in FIG. 1), and high-temperature, high-pressure gas refrigerant flows into the heat exchanger 30. This melts the frost that has adhered to the flat tubes 38 and the fins 39.
  • defrosting operation the high-temperature, high-pressure gas refrigerant flows into each of the flat tubes 38 via the lower header 34.
  • the high-temperature refrigerant that has flowed into the flat tubes 38 melts the frost that has adhered to the flat tubes 38 and the fins 39 and turns them into water.
  • the water that is produced by the melting of the frost is drained below the heat exchanger 30 along the flat tubes 38 or the fins 39.
  • a partition plate 40 is provided inside the lower header 34, which divides the interior horizontally into a number of spaces.
  • This partition plate 40 is provided to divide the interior of the heat exchanger 30 horizontally into a number of regions.
  • the partition plate 40 is also provided so that the refrigerant flows in opposite directions (turns) between adjacent regions, so that the refrigerant flows in opposite directions between adjacent regions.
  • the heat exchanger 30 is divided into two regions by the partition plate 40.
  • Two or more partition plates 40 may be provided in the lower header 34, or one or more may be provided in the upper header 35.
  • a lower distribution space 34a and a lower merging space 34b separated by the partition plate 40 are formed, and inside the upper header 35, an upper merging space 35a and an upper distribution space 35b are formed.
  • the lower distribution space 34a is also referred to as the first lower distribution space.
  • the lower distribution space 34a is a space that distributes the refrigerant that flows in from the first pipe 36 to the multiple flat tubes 38 when the heat exchanger 30 functions as an evaporator.
  • the upper merging space 35a is a space where the refrigerant distributed to the multiple flat tubes 38 in the lower distribution space 34a merges when the heat exchanger 30 functions as an evaporator.
  • the upper distribution space 35b is a space where the refrigerant that flows in from the upper merging space 35a is distributed to the multiple flat tubes 38 when the heat exchanger 30 functions as an evaporator.
  • the lower merging space 34b is a space where the refrigerant distributed to the multiple flat tubes 38 in the upper distribution space 35b merges when the heat exchanger 30 functions as an evaporator.
  • a suppression plate 41 is provided that protrudes upward from the bottom of the lower header 34 and suppresses the flow of refrigerant.
  • This suppression plate 41 is provided between the first pipe 36 and the flat tube 38 closest to the first pipe 36 in the horizontal direction of the lower distribution space 34a.
  • an opening 42 is formed above the suppression plate 41. In this way, in the horizontal direction of the lower distribution space 34a, the suppression plate 41 is provided between the first pipe 36 and the flat tube 38 closest to the first pipe 36.
  • the liquid phase of the gas-liquid two-phase refrigerant is prevented from being distributed toward the rear due to the inertial force of the refrigerant flowing into the lower distribution space 34a, and the refrigerant distribution performance can be improved when the gas-liquid two-phase refrigerant flows into the lower header 34 when the heat exchanger 30 functions as an evaporator.
  • the flat tubes 38 have upper protruding tips 38a that protrude upward from the bottom of the upper header 35.
  • the upper protruding tips 38a that protrude upward from the bottom of the upper header 35 are provided.
  • the flat tubes 38 have lower protruding tips 38b that protrude downward from the upper part of the lower header 34.
  • the length hu of the upper protruding tips 38a is greater than the length hl of the lower protruding tips 38b (hu>hl).
  • the greater the length of the upper protruding tips 38a the weaker the inertial force of the refrigerant flowing into the upper distribution space 35b, and the better the distribution performance.
  • the greater the length of the lower protruding tips 38b the greater the fluid resistance and the greater the pressure loss.
  • Figure 6 is a diagram showing the relationship between the inner diameter of the upper header 35 of the heat exchanger 30 functioning as an evaporator and the liquid level of the two-phase gas-liquid refrigerant when considering the refrigerant operating conditions typically used in the air conditioning device 100 according to embodiment 1. As shown in Figure 6, as the inner diameter of the upper header 35 increases, the liquid level of the two-phase gas-liquid refrigerant approaches a peak value.
  • the peak value is around 4.7 mm
  • the length hu of the upper protruding tip 38a is set to 5 mm or more, it can be made to protrude above the liquid level of the two-phase gas-liquid refrigerant, and the effect of reducing the influence of the inertial force of the refrigerant flowing into the upper distribution space 35b and improving distribution performance can be obtained sufficiently in practical terms.
  • the heat exchanger 30 includes a heat exchange body 31 having a plurality of flat tubes 38 arranged at intervals in the horizontal direction, an upper header 35 provided at the upper end of the heat exchange body 31, a lower header 34 provided at the lower end of the heat exchange body 31, an inlet portion provided at one end of the lower header 34 into which the refrigerant flows when functioning as an evaporator, and a partition plate 40 that divides the interior of the lower header 34 into a plurality of spaces in the horizontal direction.
  • the lower header 34 also has at least one lower distribution space 34a therein that distributes the refrigerant when functioning as an evaporator, and one of the lower distribution spaces 34a is a first lower distribution space located at the most upstream side in the refrigerant flow when functioning as an evaporator, and the first lower distribution space is provided with at least one suppression plate 41 that protrudes upward from the bottom of the lower header 34 and suppresses the refrigerant flow.
  • One of the suppression plates 41 is provided between the inlet portion and the flat tube 38 closest to the inlet portion in the horizontal direction of the first lower distribution space.
  • At least one suppression plate 41 is provided inside the first lower distribution space, protruding upward from the bottom of the lower header 34 and suppressing the flow of the refrigerant.
  • One of the suppression plates 41 is provided between the inlet and the flat tube 38 closest to the inlet in the horizontal direction of the first lower distribution space.
  • the upper header 35 has an upper distribution space 35b therein that distributes the refrigerant when functioning as an evaporator.
  • the flat tubes 38 connected to the upper distribution space 35b have upper protruding tips 38a that protrude upward from the bottom of the upper header 35 in the upper distribution space 35b.
  • the flat tubes 38 connected to the upper distribution space 35b have upper protruding tips 38a that protrude upward from the bottom of the upper header 35 in the upper distribution space 35b. Therefore, before the refrigerant flowing into the upper distribution space 35b is distributed to the flat tubes 38, the liquid phase of the gas-liquid two-phase refrigerant collides with the upper protruding tips 38a, weakening the inertial force. Then, after colliding with the upper protruding tips 38a, only the liquid phase of the gas-liquid two-phase refrigerant that has overcome the upper protruding tips 38a passes above it and flows to the rear side (opposite the inlet side).
  • the liquid phase of the gas-liquid two-phase refrigerant is prevented from flowing biased toward the rear side due to the inertial force of the refrigerant flowing into the upper distribution space 35b, and is not distributed more to the rear side, improving the distribution performance of the refrigerant.
  • the flat tubes 38 connected to the first lower distribution space have lower protruding tips 38b that protrude downward from the upper part of the interior of the lower header 34 in the first lower distribution space.
  • the length hu of the upper protruding tips 38a is greater than the length hl of the lower protruding tips 38b.
  • the heat exchanger 30 by making the length hu of the upper protruding tip 38a greater than the length hl of the lower protruding tip 38b, it is possible to reduce the effect of the inertial force of the refrigerant flowing into the upper distribution space 35b, improving distribution performance while reducing pressure loss.
  • the length hu of the upper protruding tip 38a is 5 mm or more.
  • the heat exchanger 30 by making the length hu of the upper protruding tip 38a 5 mm or more, it is possible to practically obtain the effect of reducing the influence of the inertial force of the refrigerant flowing into the upper distribution space 35b and improving the distribution performance.
  • Embodiment 2 Hereinafter, the second embodiment will be described, but explanations of parts that overlap with the first embodiment will be omitted, and parts that are the same as or equivalent to the first embodiment will be given the same reference numerals.
  • FIG. 7 is a front view showing a schematic of the refrigerant flow during heating operation of the heat exchanger 30 according to embodiment 2.
  • FIG. 8 is an enlarged front view showing a schematic of the lower distribution space 34a inside the lower header 34 of the heat exchanger 30 according to embodiment 2.
  • FIG. 9 is a diagram showing the relationship between the distance L between adjacent suppression plates 41 inside the lower header 34 of the heat exchanger 30 according to embodiment 2 and the heat exchange performance.
  • the black arrows in FIG. 7 indicate the refrigerant flow when the heat exchanger 30 functions as an evaporator.
  • multiple suppression plates 41 that protrude upward from the bottom of the lower header 34 and suppress the refrigerant flow are provided at a predetermined interval L. Also, one of the multiple suppression plates 41 is provided between the first pipe 36 and the flat tube 38 closest to the first pipe 36 in the horizontal direction of the lower distribution space 34a.
  • the liquid phase of the gas-liquid two-phase refrigerant is prevented from flowing biased toward the back side (the side opposite the inlet side) due to the inertial force of the refrigerant flowing into the lower distribution space 34a and being distributed more to the back side, so that when the heat exchanger 30 functions as an evaporator, the refrigerant distribution performance can be improved when the gas-liquid two-phase refrigerant flows into the lower header 34.
  • the liquid phase of the gas-liquid two-phase refrigerant whose inertial force gradually increases after colliding with the suppression plate 41, can collide with the suppression plate 41 again, weakening the inertial force again.
  • the effect of the inertial force of the inflowing refrigerant can be reduced more by providing multiple suppression plates 41 than by providing only one suppression plate 41.
  • two suppression plates 41 are provided inside the lower header 34, but three or more may be provided as long as the number is less than the number of flat tubes 38 connected to the lower distribution space 34a.
  • the reason for making the number of suppression plates 41 less than the number of flat tubes 38 connected to the lower distribution space 34a is to reduce waste of suppression plates 41, since the effect obtained by providing more than the number of flat tubes 38 connected to the lower distribution space 34a, that is, the effect of improving distribution performance, remains the same.
  • the distance L between adjacent suppression plates 41 is smaller than 10D (L ⁇ 10D).
  • L ⁇ 10D is set because, as shown in FIG. 9, when the distance L between adjacent suppression plates 41 becomes larger than 10D, the liquid-phase flow of the gas-liquid two-phase refrigerant develops, the area where the refrigerant distribution performance deteriorates relatively increases, and the heat exchange performance drops sharply from a certain value. Therefore, in order to prevent a sudden drop in heat exchange performance, the distance L between adjacent suppression plates 41 is set smaller than 10D.
  • a plurality of suppression plates 41 are provided in the first lower distribution space, and the number of suppression plates 41 is less than the number of flat tubes 38 connected to the first lower distribution space.
  • the influence of the inertial force of the inflowing refrigerant can be reduced more than when only one suppression plate 41 is provided.
  • the number of suppression plates 41 less than the number of flat tubes 38 connected to the first lower distribution space, waste of suppression plates 41 can be reduced.
  • the distance L between adjacent suppression plates 41 is smaller than 10D.
  • Embodiment 3 Hereinafter, the third embodiment will be described, but explanations of parts that overlap with the first and second embodiments will be omitted, and the same parts as or corresponding parts to the first and second embodiments will be given the same reference numerals.
  • FIG. 10 is a diagram showing a schematic longitudinal section of the lower header 34 of the heat exchanger 30 according to the third embodiment.
  • the lower distribution space 34a inside the lower header 34 is provided with a suppression plate 41 having a height h protruding upward from the bottom of the lower header 34.
  • R is the inner radius of the lower header 34
  • ⁇ ' is the angle of the upper end of the suppression plate 41 having the height h.
  • ⁇ ' satisfies the relationship ⁇ Do ⁇ ' ⁇ Ds .
  • ⁇ Do (-0.0408 ⁇ As+74.124) ⁇ 0.62
  • ⁇ Ds (-0.0408 ⁇ As+74.124) ⁇ 1.2
  • ⁇ Do is the liquid level angle when it is assumed that the slip ratio between the gas and liquid phases of the gas-liquid two-phase refrigerant is 1 and the gas-liquid interface is flat and horizontal
  • ⁇ Ds is the slip ratio between the gas and liquid phases of the gas-liquid two-phase refrigerant and the wetted boundary angle in the circumferential direction of the pipe used for predicting the evaporation transfer rate taking into account the inertial force
  • As is the flow path cross-sectional area of the portion inside the lower header 34 where the suppression plate 41 is not provided.
  • h Do R (1 - cos ⁇ Do )
  • h Ds R (1 - cos ⁇ Ds )
  • the flow path cross-sectional area inside the lower header 34 excluding the suppression plate 41 is As
  • h Do R(1 - cos ⁇ Do )
  • h Ds R(1 - cos ⁇ Ds )
  • ⁇ Do (-0.0408 x As + 74.124) x 0.62
  • ⁇ Ds (-0.0408 x As + 74.124) x 1.2
  • the height h of the suppression plate 41 is a value that satisfies h Do ⁇ h ⁇ h Ds .
  • the heat exchanger 30 by setting the height h of the suppression plate 41 to a value that satisfies hDo ⁇ h ⁇ hDs , it is possible to improve the refrigerant distribution performance while minimizing an increase in pressure loss.
  • Embodiment 4 Hereinafter, the fourth embodiment will be described, but explanations of parts that overlap with the first to third embodiments will be omitted, and the same parts as or corresponding parts to the first to third embodiments will be given the same reference numerals.
  • FIG. 11 is a diagram showing a schematic vertical section of the lower header 34 of the heat exchanger 30 according to the fourth embodiment.
  • FIG. 12 is a diagram showing a schematic vertical section of the lower header 34 of the heat exchanger 30 according to the fourth embodiment, excluding the suppression plate 41.
  • the cross section of the lower distribution space 34a has a noncircular cross section.
  • the height h of the suppression plate 41 is a value that satisfies hDo ⁇ h ⁇ hDs . In this way, even when the inside of the lower header 34 is a noncircular flow path, the suppression plate 41 is provided so that hDo ⁇ h ⁇ hDs , and the refrigerant distribution performance can be improved while minimizing the increase in pressure loss.
  • the height h of the suppression plate 41 is a value that satisfies hDo ⁇ h ⁇ hDs .
  • Embodiment 5 Hereinafter, the fifth embodiment will be described, but explanations of parts that overlap with the first to fourth embodiments will be omitted, and the same parts as or corresponding parts to the first to fourth embodiments will be given the same reference numerals.
  • FIG. 13 is a schematic diagram showing a vertical cross section of the lower header 34 of the heat exchanger 30 according to the fifth embodiment.
  • a gap 43 is formed between the side of the suppression plate 41 and the side inside the lower header 34.
  • the gap 43 is formed on both side sides of the suppression plate 41, but the gap 43 may be formed only on one side side of the suppression plate 41. In this way, by forming the gap 43 between the side of the suppression plate 41 and the side inside the lower header 34, the fluid resistance is reduced compared to when the gap 43 is not formed, and therefore the refrigerant distribution performance can be improved while suppressing an increase in pressure loss.
  • a gap 43 is formed between the side of the suppression plate 41 and the inside side of the lower header 34.
  • a gap 43 is formed between the side of the suppression plate 41 and the side of the inside of the lower header 34, so that the refrigerant distribution performance can be improved while suppressing an increase in pressure loss.
  • Embodiment 6 The sixth embodiment will be described below, but explanations of parts that overlap with those of the first to fifth embodiments will be omitted, and parts that are the same as or equivalent to those of the first to fifth embodiments will be given the same reference numerals.
  • FIG. 14 is a front view showing a schematic diagram of the refrigerant flow during heating operation of the heat exchanger 30 according to the sixth embodiment.
  • a plurality of partition plates 40 are provided inside the lower header 34.
  • two partition plates 40 are provided in the lower header 34, and one partition plate is provided in the upper header 35.
  • three or more partition plates 40 may be provided in the lower header 34, or two or more partition plates 40 may be provided in the upper header 35.
  • a lower distribution space 34a and a lower merging space 34b are formed inside the lower header 34, and an upper merging space 35a and an upper distribution space 35b are formed inside the upper header 35.
  • the lower header 34 has two lower distribution spaces 34a inside for distributing the refrigerant when the heat exchanger 30 functions as an evaporator.
  • the lower distribution space 34a located on the upstream side is the upstream lower distribution space 34a1
  • the lower distribution space 34a located on the downstream side is the downstream lower distribution space 34a2.
  • the lower header 34 has two lower distribution spaces 34a inside that distribute the refrigerant when the heat exchanger 30 functions as an evaporator, but it may have three or more.
  • the suppression plate 41 is provided in each of the lower distribution spaces 34a.
  • the height of the suppression plate 41 provided in the lower distribution space 34a located downstream is lower than the height of the suppression plate 41 provided in the lower distribution space 34a located upstream.
  • the height of the suppression plate 41 provided in the downstream lower distribution space 34a2 is lower than the height of the suppression plate 41 provided in the upstream lower distribution space 34a1.
  • the lower header 34 has three or more lower distribution spaces 34a that distribute the refrigerant when the heat exchanger 30 functions as an evaporator, and a suppression plate 41 is provided in each of the lower distribution spaces 34a
  • the height of the suppression plate 41 provided in the lower distribution space 34a located furthest downstream will be the lowest
  • the height of the suppression plate 41 provided in the lower distribution space 34a located furthest upstream will be the highest, in the refrigerant flow when the heat exchanger 30 functions as an evaporator.
  • the lower distribution space 34a located downstream has a smaller proportion of the liquid phase of the gas-liquid two-phase refrigerant, so the height of the suppression plate 41 is adjusted according to the proportion of the liquid phase of the gas-liquid two-phase refrigerant.
  • the height of the suppression plate 41 provided in the lower distribution space 34a where the proportion of the liquid phase of the gas-liquid two-phase refrigerant is smaller the flow resistance is reduced and an increase in pressure loss is suppressed.
  • the refrigerant distribution performance can be improved while suppressing an increase in pressure loss.
  • the relationship in height between the suppression plates 41 in the same lower distribution space 34a is not particularly limited.
  • a plurality of partition plates 40 are provided inside the lower header 34, and the lower header 34 has a plurality of lower distribution spaces 34a inside. Furthermore, a suppression plate 41 is provided in each of the lower distribution spaces 34a. And, the height of the suppression plate 41 provided in the lower distribution space 34a located downstream in the refrigerant flow when functioning as an evaporator is lower than the height of the suppression plate 41 provided in the lower distribution space 34a located upstream.
  • the height of the suppression plate 41 provided in the lower distribution space 34a located downstream in the refrigerant flow is lower than the height of the suppression plate 41 provided in the lower distribution space 34a located upstream, so that the refrigerant distribution performance can be improved while suppressing an increase in pressure loss.

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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne un échangeur thermique qui comprend : un corps d'échange thermique qui a une pluralité de tubes plats qui sont agencés dans la direction horizontale avec des intervalles entre eux ; un collecteur supérieur qui est disposé sur une partie d'extrémité supérieure du corps d'échange thermique ; un collecteur inférieur qui est disposé sur une partie d'extrémité inférieure du corps d'échange thermique ; une partie d'entrée qui est disposée sur une extrémité du collecteur inférieur et dans laquelle un fluide frigorigène s'écoule pendant la fonction en tant qu'évaporateur ; et une plaque de séparation qui sépare l'intérieur du collecteur inférieur en une pluralité d'espaces dans la direction horizontale. Le collecteur inférieur a au moins un espace de distribution inférieur pour distribuer le fluide frigorigène pendant la fonction en tant qu'évaporateur. Un espace de distribution inférieur est un premier espace de distribution inférieur qui est positionné le plus en amont dans l'écoulement du fluide frigorigène pendant la fonction en tant qu'évaporateur. Est disposée sur le premier espace de distribution inférieur au moins une plaque de suppression qui fait saillie vers le haut à partir d'une partie inférieure du collecteur inférieur et supprime l'écoulement du fluide frigorigène. Une plaque de suppression est disposée entre la partie d'entrée et le tube plat le plus éloigné du côté de la partie d'entrée dans la direction horizontale du premier espace de distribution inférieur.
PCT/JP2022/045137 2022-12-07 2022-12-07 Échangeur thermique, unité extérieure comprenant un échangeur thermique et dispositif de climatisation comprenant une unité extérieure WO2024121984A1 (fr)

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PCT/JP2022/045137 WO2024121984A1 (fr) 2022-12-07 2022-12-07 Échangeur thermique, unité extérieure comprenant un échangeur thermique et dispositif de climatisation comprenant une unité extérieure

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PCT/JP2022/045137 WO2024121984A1 (fr) 2022-12-07 2022-12-07 Échangeur thermique, unité extérieure comprenant un échangeur thermique et dispositif de climatisation comprenant une unité extérieure

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000346568A (ja) * 1999-05-31 2000-12-15 Mitsubishi Heavy Ind Ltd 熱交換器
JP2005140374A (ja) * 2003-11-05 2005-06-02 Denso Corp 熱交換器
JP2005241170A (ja) * 2004-02-27 2005-09-08 Mitsubishi Heavy Ind Ltd 熱交換器
JP2005300072A (ja) * 2004-04-14 2005-10-27 Calsonic Kansei Corp 蒸発器
WO2009048451A1 (fr) * 2007-10-12 2009-04-16 Carrier Corporation Echangeurs de chaleur comportant des collecteurs à chicanes
WO2012176336A1 (fr) * 2011-06-24 2012-12-27 三菱電機株式会社 Élément chauffant à plaques et dispositif de cycle de réfrigération
JP2013155966A (ja) * 2012-01-31 2013-08-15 Keihin Thermal Technology Corp エバポレータ
CN104764255A (zh) * 2015-03-26 2015-07-08 广东美的制冷设备有限公司 平行流换热器

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000346568A (ja) * 1999-05-31 2000-12-15 Mitsubishi Heavy Ind Ltd 熱交換器
JP2005140374A (ja) * 2003-11-05 2005-06-02 Denso Corp 熱交換器
JP2005241170A (ja) * 2004-02-27 2005-09-08 Mitsubishi Heavy Ind Ltd 熱交換器
JP2005300072A (ja) * 2004-04-14 2005-10-27 Calsonic Kansei Corp 蒸発器
WO2009048451A1 (fr) * 2007-10-12 2009-04-16 Carrier Corporation Echangeurs de chaleur comportant des collecteurs à chicanes
WO2012176336A1 (fr) * 2011-06-24 2012-12-27 三菱電機株式会社 Élément chauffant à plaques et dispositif de cycle de réfrigération
JP2013155966A (ja) * 2012-01-31 2013-08-15 Keihin Thermal Technology Corp エバポレータ
CN104764255A (zh) * 2015-03-26 2015-07-08 广东美的制冷设备有限公司 平行流换热器

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