WO2019039401A1 - Condenseur - Google Patents

Condenseur Download PDF

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Publication number
WO2019039401A1
WO2019039401A1 PCT/JP2018/030522 JP2018030522W WO2019039401A1 WO 2019039401 A1 WO2019039401 A1 WO 2019039401A1 JP 2018030522 W JP2018030522 W JP 2018030522W WO 2019039401 A1 WO2019039401 A1 WO 2019039401A1
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WO
WIPO (PCT)
Prior art keywords
flat tube
tube group
header
flat
refrigerant
Prior art date
Application number
PCT/JP2018/030522
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English (en)
Japanese (ja)
Inventor
紗代 深田
史郎 片平
貴彦 水田
Original Assignee
株式会社Uacj
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.)
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Publication date
Application filed by 株式会社Uacj filed Critical 株式会社Uacj
Priority to CN201880046519.XA priority Critical patent/CN110869690B/zh
Publication of WO2019039401A1 publication Critical patent/WO2019039401A1/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
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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 invention relates to a condenser.
  • a heat exchanger configured to function as a condenser during cooling operation and to function as an evaporator during heating operation is incorporated in the outdoor unit of this type of air conditioner.
  • Patent Document 1 describes a parallel flow type heat exchanger including two vertical header pipes and a plurality of horizontal flat tubes connecting the header pipes.
  • a partition plate is provided in the header pipe to divide the flat tube into a plurality of groups.
  • the heat exchanger incorporated in the outdoor unit of the air conditioning apparatus only needs to have only a function as a condenser for condensing the high temperature / high pressure refrigerant gas supplied from the compressor.
  • the heat exchanger of Patent Document 1 is configured to function as a condenser during cooling operation and to function as an evaporator during heating operation, it has low pressure loss both during cooling operation and during heating operation. It is required to be compatible with a high heat exchange amount. Therefore, there is still room for improvement in the heat exchange performance as a condenser.
  • the present invention has been made in view of the above background, and an object of the present invention is to provide a condenser that has excellent heat exchange performance and is suitable for an air conditioner dedicated to cooling operation.
  • One aspect of the present invention is a core in which a plurality of flat tubes for circulating a refrigerant are arranged in parallel via fins, and the flat tubes and the fins are alternately stacked in the vertical direction.
  • a first header disposed at one end of the core in the longitudinal direction of the flat tube;
  • a second header disposed at the other end of the core in the longitudinal direction;
  • the plurality of flat tubes are divided into a first flat tube group, a second flat tube group, a third flat tube group, and a fourth flat tube group in order from the top,
  • the first header is An inlet connected to the first flat tube group and the refrigerant supply pipe;
  • a first partition plate for partitioning between the inlet portion and the second turn portion, and between the second turn portion and the
  • Another aspect of the present invention is a condenser satisfying the following formulas (6) to (7) instead of the formulas (4) to (5) in the condenser of the above-mentioned aspect. 0.22 ⁇ a / A ⁇ (A-6.825) / A (6) ⁇ 0.47 ⁇ (B ⁇ 6.825-12.825) +12.825 ⁇ / B ⁇ b / B ⁇ (B ⁇ 6.825) / B (7)
  • the ratio A / L of the inlet portion occupied in the first header And the ratio B / L of the outlet part occupied in the first header satisfies the above formulas (2) to (3).
  • the heat transfer area in the first flat tube group can be made in an appropriate range.
  • the high-temperature, high-pressure gaseous refrigerant that has flowed from the compressor into the first flat tube group via the inlet can be efficiently cooled.
  • the refrigerant flow path in the refrigerant discharge pipe, the outlet, and the fourth flat pipe group can be easily secured in the manufacturing process of the condenser. can do.
  • the ratio a / A of the distance a from the upper end of the first header to the end length of the refrigerant supply pipe to the length A of the inlet portion, and the length a of the outlet portion The ratio b / B of the distance from the lower end of the first header to the end of the refrigerant discharge pipe satisfies the expressions (4) to (5). Thereby, the amount of heat exchange can be increased while suppressing an increase in pressure loss of the condenser.
  • the ratio a of the distance a from the upper end of the first header to the end of the refrigerant supply pipe with respect to the length A of the inlet instead of the expressions (4) to (5)
  • the ratio b / B of the distance from the lower end of the first header to the end of the refrigerant discharge pipe with respect to the length of the outlet portion satisfy the expressions (6) to (7).
  • the structure of the first header, the connection position of the refrigerant supply pipe and the connection position of the refrigerant discharge pipe are optimized. This can improve the performance as a condenser as compared to a condenser configured to also function as an evaporator. Both the condenser of the first aspect and the condenser of the second aspect are suitable for an air conditioner dedicated to cooling operation.
  • the condenser is configured as a so-called parallel flow type heat exchanger in which a refrigerant flows in a flat pipe extending in the horizontal direction. Further, the condenser is disposed in a direction in which the first flat tube group is upward and the fourth flat tube group is downward.
  • the high temperature and high pressure refrigerant supplied from the refrigerant supply pipe flows into the inlet of the first header and is distributed to the first flat pipe group.
  • the refrigerant that has passed through the first flat tube group flows into the first turn portion of the second header and is distributed to the second flat tube group.
  • the flow direction of the refrigerant in the second flat tube group is opposite to the flow direction of the refrigerant in the first flat tube group.
  • the refrigerant passes sequentially through the second turn portion of the first header, the third flat tube group, the third turn portion of the second header, and the fourth flat tube group.
  • the refrigerant that has flowed out of the fourth flat tube group to the outlet portion is discharged to the outside of the condenser via the refrigerant discharge pipe.
  • the number of flat tubes belonging to the first flat tube group is larger than that of the second flat tube group, and the number of flat tubes belonging to the second flat tube group is larger than that of the third flat tube group, the third flat tube group It is preferable that the number of flat tubes belonging to is larger than that of the fourth flat tube group.
  • the refrigerant that has flowed into the first flat tube group from the inlet is a high-temperature, high-pressure gas, and therefore has a low density. Therefore, in order to efficiently remove heat from the refrigerant flowing into the first flat tube group, it is necessary to widen the heat transfer area. By maximizing the number of flat tubes in the first flat tube group, the heat transfer area in the first flat tube group can be sufficiently secured, and heat can be efficiently removed from the high-temperature, high-pressure gaseous refrigerant.
  • the refrigerant moving in the condenser is cooled by heat exchange with the outside air and gradually condenses. Therefore, the flow of the refrigerant in the condenser becomes a single-phase gas phase flow at the inlet, and changes to a two-phase gas-liquid flow in which the gas phase and the liquid phase are mixed as it moves downstream. The proportion of the liquid phase in the gas-liquid two-phase flow increases toward the downstream side, and eventually becomes a single-phase flow of the liquid phase.
  • the liquid phase refrigerant has a higher density than the gas phase refrigerant, heat can be efficiently removed with a smaller heat transfer area than the gas phase refrigerant. Therefore, by reducing the number of flat tubes in the order of the second flat tube group, the third flat tube group, and the fourth flat tube group, a sufficient heat transfer area is secured according to the increase in the proportion of the liquid phase, Heat exchange between the refrigerant and the outside air can be performed efficiently.
  • the number of flat tubes belonging to the first flat tube group disposed on the upstream side is maximized, and the number of flat tubes in the order of the second flat tube group, the third flat tube group, and the fourth flat tube group By reducing the heat exchange amount of the condenser.
  • the number of flat tubes belonging to the first flat tube group is 35 to 45%
  • the second flat The number of flat tubes belonging to the tube group is 25 to 35%
  • the number of flat tubes belonging to the third flat tube group is 15 to 25%
  • the number of flat tubes belonging to the fourth flat tube group is 5 to 15% It is further preferable to do.
  • the first header has an inlet located at the upper side, an outlet located at the lower side, and a second turn located between the inlet and the outlet.
  • the inlet and the second turn and the second and the outlet are separated by the first partition plate.
  • the length L [mm] of the first header in the vertical direction that is, the stacking direction of the flat tube and the fin satisfies the following formula (1). 400 ⁇ L ⁇ 1500 (1)
  • the condenser satisfying the formula (1) conforms to the size of the outdoor unit in a home or business air conditioner, and can be easily incorporated into the outdoor unit.
  • the upper portion of the first header is configured as an inlet for distributing the refrigerant supplied from the refrigerant supply pipe to the first flat tube group.
  • the ratio A / L of the length A [mm] of the inlet to the length L [mm] of the first header in the vertical direction satisfies the following formula (2). 0.4 ⁇ A / L ⁇ 0.75 (2)
  • the length of the inlet portion can be appropriately increased.
  • the number of flat tubes connected to the inlet that is, the number of flat tubes belonging to the first flat tube group can be sufficiently increased.
  • the heat exchange amount of the condenser can be increased.
  • the value of A / L is less than 0.4, the number of flat tubes belonging to the first flat tube group is insufficient, which may lead to a decrease in the heat exchange amount of the condenser.
  • the value of A / L exceeds 0.7, the number of flat tubes belonging to the first flat tube group increases, so the flat members belonging to the second flat tube group to the fourth flat tube group relatively The total number of tubes is reduced. As a result, the pressure loss of the condenser may increase.
  • a refrigerant supply pipe for supplying a refrigerant into the condenser is connected to the inlet portion.
  • the distance in the vertical direction from the center of the end portion of the refrigerant supply pipe connected to the inlet portion to the upper end of the first header is a [mm]
  • the value of a / A satisfies the following formula (6) doing. 0.22 ⁇ a / A ⁇ (A-6.825) / A (6)
  • the refrigerant supply pipe is connected to a position appropriately separated from the upper end of the first header, and the deviation of the refrigerant between the flat tubes belonging to the first flat tube group is obtained. It can be reduced. As a result, the amount of heat exchange can be increased while suppressing an increase in pressure loss.
  • the value of a / A is less than 0.22, the bias of the refrigerant among the flat tubes belonging to the first flat tube group becomes large, and the heat exchange amount of the condenser may be reduced.
  • the value of a / A is set to (A ⁇ 6.825) / A or less, it is possible to avoid the deterioration of the dimensional accuracy of the first header.
  • the value of a / A exceeds (A ⁇ 6.825) / A, the distance in the vertical direction from the center of the end of the refrigerant supply pipe to the center of the first partition plate is less than 6.825 mm.
  • the first header is deformed when processing for attaching the refrigerant supply pipe and the first partition plate to the first header.
  • the dimensional accuracy of the header may deteriorate. Also, in some cases, it may be difficult to make a condenser.
  • a / A preferably satisfies the following formula (4). 0.22 ⁇ a / A ⁇ 0.64 (4)
  • the refrigerant supply pipe can be connected to a position appropriately separated from the upper end of the first header and also appropriately separated from the first partition plate.
  • the pressure of the refrigerant in the inlet portion is maximum at the end of the refrigerant supply pipe and decreases with distance from the refrigerant supply pipe. Therefore, the flow velocity of the refrigerant flowing in the flat tube belonging to the first flat tube group tends to be higher as it is closer to the refrigerant supply tube and to be slower as it is away from the refrigerant supply tube.
  • the refrigerant in the flat pipe disposed above among the flat pipes belonging to the first flat pipe group Flow velocity tends to be fast.
  • the refrigerant passing through the flat tube disposed above has a longer moving distance until reaching the second flat tube group than the refrigerant passing through the flat tube disposed below.
  • heat exchange with the outside of the condenser can be promoted by reducing the value of a / A and increasing the flow velocity of the refrigerant passing through the flat tube disposed above.
  • the heat exchange amount of the entire condenser can be increased.
  • the value of a / A is small, the average moving distance of the refrigerant becomes long, which may cause an increase in pressure loss.
  • the lower portion of the first header is configured as an outlet for leading the refrigerant flowing out of the fourth flat tube group to the refrigerant discharge pipe.
  • the length B [mm] of the outlet part with respect to the length L [mm] of the first header in the vertical direction satisfies the following formula (3). 30.275 / L ⁇ B / L ⁇ (L ⁇ A) / 3 L (3)
  • the length of the exit can be appropriately increased. Thereby, the amount of heat exchange can be increased while suppressing an increase in pressure loss of the condenser.
  • the length of the outlet becomes excessively short. Therefore, when brazing is performed in the manufacturing process of the condenser, unnecessary wax may flow into the refrigerant discharge pipe, the outlet portion, and the fourth flat pipe group, and the refrigerant flow path may be narrowed. As a result, the pressure loss of the condenser may increase and the heat exchange amount may decrease.
  • the value of B / L exceeds the specific range, the length of the outlet becomes excessively long, so the lengths of the inlet and the second turn become relatively short. As a result, the total of the flat tubes belonging to the first flat tube group to the third flat tube group runs short, and the heat exchange amount of the condenser may be reduced.
  • a refrigerant discharge pipe for discharging the refrigerant in the condenser to the outside is connected to the outlet portion.
  • the value of b / B satisfies the following formula (5) doing. ⁇ 0.09 ⁇ (B-6.825-12.825) +12.825 ⁇ / B ⁇ b / B ⁇ (B-6.825) / B (5)
  • the value of b / B By setting the value of b / B to (B ⁇ 6.825) / B or less, deterioration in the dimensional accuracy of the first header can be avoided.
  • the value of b / B exceeds (B ⁇ 6.825) / B, the distance in the vertical direction from the center of the end of the refrigerant discharge pipe to the center of the first partition plate is less than 6.825 mm.
  • the first header is deformed when processing for attaching the refrigerant discharge pipe and the first partition plate to the first header.
  • the dimensional accuracy of the header may deteriorate. Also, in some cases, it may be difficult to make a condenser.
  • the pressure of the refrigerant in the outlet is minimal at the end of the refrigerant outlet and increases with distance from the refrigerant outlet. Therefore, the flow velocity of the refrigerant flowing in the flat tube belonging to the fourth flat tube group tends to be higher as it is closer to the refrigerant discharge pipe, and tends to be slower as it is away from the refrigerant discharge pipe.
  • the flow velocity of the gas phase refrigerant is usually different from the flow velocity of the liquid phase refrigerant. Therefore, at the interface between the gas phase refrigerant and the liquid phase refrigerant, a shear force causing pressure loss is generated due to the difference in flow velocity between the two.
  • reducing the ratio of the gas-liquid two-phase flow it is possible to reduce the influence of the above-described shear force and to suppress an increase in pressure loss of the condenser.
  • the deformation of the first header is made in the same manner as in the case where the refrigerant discharge pipe is connected in the vicinity of the first partition plate. There is a risk of In order to avoid such a problem, it is necessary to connect the refrigerant discharge pipe at a position at least 12.825 mm away in the vertical direction from the lower end of the first header.
  • the distance between the refrigerant discharge pipe and the lower end of the first header is 12. Further, after securing 825 mm or more, the refrigerant discharge pipe can be appropriately separated from the lower end of the first header and connected. As a result, it is possible to avoid the deformation of the first header, to suppress the increase in the ratio of the gas-liquid two-phase flow described above, and to suppress the increase in pressure loss.
  • b / B preferably satisfies the following formula (7). ⁇ 0.47 ⁇ (B ⁇ 6.825-12.825) +12.825 ⁇ / B ⁇ b / B ⁇ (B ⁇ 6.825) / B (7)
  • the refrigerant discharge pipe can be connected further upward.
  • the ratio of the gas-liquid two-phase flow can be further reduced, and the pressure loss of the condenser can be further reduced.
  • a known refrigerant for an air conditioner can be used.
  • a refrigerant such as R410A, R32, R1234yf, R1123 or the like.
  • R32 it is particularly effective to use R32.
  • Example 1 An embodiment of the condenser will be described with reference to the drawings.
  • the specific aspect of the condenser which concerns on this invention is not limited to the aspect of an Example, It can change suitably in the range which does not impair the meaning of this invention.
  • a plurality of flat tubes 2 for circulating a refrigerant are arranged in parallel via the fins 3, and the flat tubes 2 and the fins 3 are alternately stacked in the vertical direction
  • the core 11 is connected to a first header 4 disposed at one end of the core 11 in the longitudinal direction of the flat tube 2, a second header 5 disposed at the other end of the core 11 in the longitudinal direction, and the first header 4
  • the refrigerant supply pipe 6 and the refrigerant discharge pipe 7 are provided.
  • the plurality of flat tubes 2 are divided into a first flat tube group 21, a second flat tube group 22, a third flat tube group 23, and a fourth flat tube group 24 in order from the top .
  • the first header 4 has an inlet 41 connected to the first flat tube group 21 and the refrigerant supply tube 6, and a second turn 42 connected to the second flat tube group 22 and the third flat tube group 23.
  • the second header 5 includes a first turn portion 51 connected to the first flat tube group 21 and the second flat tube group 22, and a second turn connected to the third flat tube group 23 and the fourth flat tube group 24.
  • a third turn portion 52 and a second partition plate 53 that divides the first turn portion 51 and the third turn portion 52 are provided.
  • the condenser 1 of this example satisfies the following formulas (1) to (3), and a combination of the following formula (4) and the following formula (5), or the following formula (6) and the following formula ( 7) and any combination of the combination is satisfied.
  • the core 11 has a plurality of flat tubes 2 spaced apart in the vertical direction, and fins 3 interposed between the flat tubes 2.
  • the flat tube 2 and the fins 3 are joined by brazing.
  • the number of flat tubes 2 can be appropriately set according to the required heat exchange amount and pressure loss, and can be, for example, 30 to 160.
  • the core 11 in this example further includes a side sheet 111 made of a plate material of aluminum or aluminum alloy.
  • the side sheet 111 is joined to the flat tube 2 a disposed at the upper end of the plurality of flat tubes 2 and the flat tube 2 b disposed at the lower end via the fins 3.
  • the plurality of flat tubes 2 includes four flat tubes of a first flat tube group 21, a second flat tube group 22, a third flat tube group 23 and a fourth flat tube group 24 in order from the top It is divided into tube groups.
  • the number of flat tubes 2 belonging to the first flat tube group 21 can be, for example, 35 to 45% of the total number of flat tubes 2.
  • the number of flat tubes 2 belonging to the second flat tube group 22 can be, for example, 25 to 35% of the total number of flat tubes 2.
  • the number of flat tubes 2 belonging to the third flat tube group 23 can be, for example, 15 to 25% of the total number of flat tubes 2.
  • the number of flat tubes 2 belonging to the fourth flat tube group 24 can be, for example, 5 to 15% of the total number of flat tubes 2.
  • the flat tube 2 is made of aluminum or an aluminum alloy. Although not shown in the drawings, the cross section of the flat tube 2 viewed from the longitudinal direction has an oval shape or a rectangular shape. Further, as shown in FIG. 1, the upper surface 211 and the lower surface 212 of the flat tube 2 are formed of flat surfaces, and the fins 3 are joined to the upper surface 211 and the lower surface 212.
  • the outer dimensions of the flat tube 2 can be set appropriately from, for example, a thickness of 1.1 to 3.0 mm and a width of 6 to 20 mm.
  • the flat tube 2 may be a single-hole tube having a single refrigerant flow passage inside, or may be a multi-hole tube having a plurality of refrigerant flow passages.
  • the number of refrigerant channels in the multi-hole pipe can be, for example, 4 to 20.
  • corrugated fins made of aluminum or an aluminum alloy can be used as the fins 3.
  • the thickness of the fins 3 can be, for example, 0.06 to 0.12 mm.
  • the height of the fins 3 in the vertical direction can be 6 to 8 mm.
  • louver protruding in the thickness direction of the fins 3 may be provided on the flat portions 31 (see FIG. 1) of the fins 3, that is, the portions between the bent portions 32 joined to the flat tube 2.
  • the number of louvers can be 6 to 16 per flat portion.
  • the louvers can be extended in a direction inclined 20 to 60 degrees with respect to the width direction of the fins 3.
  • ruber was abbreviate
  • the first header 4 is made of aluminum or an aluminum alloy. As shown in FIG. 2, the first header 4 has a cylindrical header body 46 extending in the vertical direction, ie, the stacking direction of the cores 11, and caps 47 and 48 for closing the upper end and the lower end of the header body 46. And.
  • a cylindrical tube having an outer diameter of 15 to 25 mm and a wall thickness of 1.0 to 2.5 mm can be used as the header body 46, but the present invention is not limited to this shape.
  • the caps 47 and 48 and the first partition plates 44 and 45 are joined to the header main body 46 by brazing.
  • description of the caps 47 and 48 was abbreviate
  • the internal space of the first header 4 surrounded by the header body 46 and the caps 47 and 48 is divided into three spaces by two first partition plates 44 and 45.
  • the portion from the upper end 411 of the first header 4 to the first partition plate 44 disposed above constitutes the inlet 41 of the first header 4.
  • the end of the flat tube 2 belonging to the first flat tube group 21 is inserted into the inlet portion 41.
  • a refrigerant supply pipe 6 for supplying a refrigerant into the condenser 1 is connected to the inlet 41.
  • the end 61 of the refrigerant supply pipe 6 is inserted into the inlet 41.
  • the refrigerant supply pipe 6 is extended outward from the end portion 61 in the longitudinal direction of the flat pipe 2. Thereby, the first flat tube group 21 and the refrigerant supply pipe 6 are connected via the inlet 41.
  • the portion of the first header 4 from the first partition plate 44 disposed above to the first partition plate 45 disposed below constitutes a second turn portion 42.
  • the end portion of the flat tube 2 belonging to the second flat tube group 22 and the third flat tube group 23 is inserted into the second turn portion 42.
  • the 2nd flat pipe group 22 and the 3rd flat pipe group 23 are connected via the 2nd turn part 42. As shown in FIG.
  • the portion from the lower end 412 of the first header 4 to the first partition plate 45 disposed below constitutes an outlet 43.
  • the end of the flat tube 2 belonging to the fourth flat tube group 24 is inserted into the outlet 43.
  • a refrigerant discharge pipe 7 for discharging the refrigerant in the condenser 1 to the outside is connected to the outlet portion 43.
  • the end 71 of the refrigerant discharge pipe 7 is inserted into the outlet 43.
  • the refrigerant discharge pipe 7 is extended outward from the end portion 71 in the longitudinal direction of the flat pipe 2.
  • the fourth flat tube group 24 and the refrigerant discharge pipe 7 are connected via the outlet 43.
  • the flat tube 2 inserted into the first header 4, the refrigerant supply pipe 6 and the refrigerant discharge pipe 7 are joined to the header main body 46 of the first header 4 by brazing.
  • the second header 5 is made of aluminum or an aluminum alloy, and has a tubular header body 56 extending in the vertical direction, that is, the stacking direction of the cores 11, and a cap closing the upper end and the lower end of the header body 56. 57 and 58 are included. Further, the internal space of the second header 5 surrounded by the header body 56 and the caps 57 and 58 is divided into two spaces by one second partition plate 53.
  • a cylindrical tube having an outer diameter of 15 to 25 mm and a wall thickness of 1.0 to 2.5 mm can be used as the header body 56, but the shape is limited to this It is not something to be done. Also, the caps 57 and 58 and the second partition plate 53 are joined to the header main body 56 by brazing.
  • the portion from the upper end 511 of the second header 5 to the second partition plate 53 constitutes a first turn portion 51.
  • the end portions of the flat tubes 2 belonging to the first flat tube group 21 and the second flat tube group 22 are inserted into the first turn portion 51. Thereby, the first flat tube group 21 and the second flat tube group 22 are connected via the first turn portion 51.
  • the portion from the lower end 512 of the second header 5 to the second partition plate 53 constitutes a third turn portion 52.
  • the end portion of the flat tube 2 belonging to the third flat tube group 23 and the fourth flat tube group 24 is inserted into the third turn portion 52. Thereby, the third flat tube group 23 and the fourth flat tube group 24 are connected via the third turn portion 52.
  • the flat tube 2 inserted into the second header 5 is joined to the header body 56 of the second header 5 by brazing.
  • the condenser 1 of this example is an inlet occupying the first header 4 on the premise that the total length L of the first header 4 in the vertical direction, that is, the stacking direction of the cores 11 is 400 to 1500 mm (the formula (1)).
  • the ratio A / L of the part 41 and the ratio B / L of the outlet 43 occupying the first header 4 satisfy the expressions (2) to (3).
  • the heat transfer area in the first flat tube group 21 can be made in an appropriate range.
  • the high-temperature, high-pressure gaseous refrigerant that has flowed from the compressor into the first flat tube group 21 via the inlet 41 can be efficiently cooled. Further, by setting the value of B / L in the range specified by the equation (3), in the manufacturing process of the condenser 1, the flow path of the refrigerant in the refrigerant discharge pipe 7, the outlet portion 43, and the fourth flat tube group 24 Can be easily secured.
  • the value of a / A and the value of b / B may be a combination of the formula (4) and the formula (5), or the formula (6) and the formula (7). Satisfy any combination of combinations.
  • the first partition plate 44 disposed at an appropriate distance from the upper end 411 of the first header 4 and above the refrigerant supply pipe 6 , 45 can also be connected at a suitable distance. Thereby, the bias of the refrigerant between the flat tubes 2 belonging to the first flat tube group 21 can be further reduced, and the heat exchange amount can be further increased.
  • the value of b / B satisfies the above equation (5)
  • the distance between the refrigerant discharge pipe 7 and the lower end 412 of the first header 4 is secured by 12.825 mm or more, and then the refrigerant is further added.
  • the discharge pipe 7 can be connected at a suitable distance from the lower end 412 of the first header 4. As a result, an increase in pressure loss can be suppressed.
  • the refrigerant supply pipe 6 can be connected to a position appropriately separated from the upper end 411 of the first header 4. Thereby, the bias of the refrigerant between the flat tubes 2 belonging to the first flat tube group 21 can be reduced, and the reduction of the heat exchange amount can be avoided. Further, when the value of b / B satisfies the equation (7), the refrigerant discharge pipe 7 can be connected relatively above the outlet 43. Thereby, the ratio of the gas-liquid two-phase flow which flows into the 4th flat tube group 24 can be reduced more, and the pressure loss of condenser 1 can be reduced more.
  • Example 2 This example is an example in which the connection position of the refrigerant supply pipe 6 and the connection position of the refrigerant discharge pipe 7 are variously changed.
  • the same reference numerals as those used in the previous embodiments indicate the same constituent elements as those in the first embodiment unless otherwise specified.
  • the manufacturability of the condenser 1 (specimen 1 to 36) in which the value of a / A and the value of b / B were set was evaluated. Further, the amount of heat exchange and the pressure loss were measured for the test pieces 1 to 25 for which the condenser 1 could be produced. Moreover, as a standard of the heat exchange amount and the pressure loss, the value of a / A is 0.15, and the value of b / B is 0.40.
  • the condenser 1 (test body R) was produced.
  • the test body R is a test body in which the refrigerant supply pipe 6 and the refrigerant discharge pipe 7 are connected to a general position in the heat exchanger of the on-vehicle air conditioner.
  • test body of this example is as follows.
  • Thickness of flat tube 2 1.3mm Flat tube 2 width 14 mm Number 15 of refrigerant channels in flat tube 2 Cross-sectional shape of refrigerant channels in flat tube 2 Rectangle
  • Second header 4 Outer diameter of header body 46 18 mm Header body 46 thickness 1.2 mm Total length L 464 mm of the first header 4 in the vertical direction Length A 192.5 mm of the inlet 41 in the vertical direction Length B 59.5 mm of the outlet 43 in the vertical direction
  • the method of evaluating the manufacturability, the method of measuring the amount of heat exchange, and the method of measuring the pressure loss are as follows.
  • the heat exchange amount and pressure loss of each test body were measured by a method according to the outdoor air enthalpy test method defined in JIS B 8615-1: 2013 Annex G. Specifically, the test body was installed in a wind tunnel apparatus provided in a constant temperature and humidity test room, and the air temperature in the test room was set to a dry bulb temperature of 35 ° C. and a wet bulb temperature of 24 ° C. While blowing air at a wind speed of 1.6 m / sec from the wind tunnel device to the test body, the refrigerant R32 is circulated into the test body so that the temperature in the refrigerant supply pipe 6 is 65 ° C.
  • the test bodies 1 to 4 and the test bodies 9 to 12 satisfying the above formulas (1) to (5) are compared with the test body R while suppressing an increase in pressure loss. Heat exchange amount could be increased. Further, in the test pieces 1 to 8 satisfying the above formulas (1) to (3) and the above formulas (6) to (7), the pressure loss compared with the test body R while avoiding the decrease in the heat exchange amount could be reduced.
  • test bodies 1 to 12 the test bodies 1 to 4 satisfying the above formulas (1) to (3), the above formula (4) and the above formula (7) are compared to the test body R.
  • the pressure loss can be reduced and the amount of heat exchange can be increased.
  • the value of a / A is small, and the refrigerant supply pipe 6 is disposed excessively upward, so the bias of the refrigerant among the flat tubes 2 belonging to the first flat tube group 21 is increased . As a result, the amount of heat exchange decreased.
  • the value of b / B was small and the refrigerant discharge pipe 7 was disposed excessively downward, the ratio of the gas-liquid two-phase flow flowing through the fourth flat tube group 24 increased. As a result, an increase in pressure loss was caused.
  • the value of b / B was increased to try to connect the refrigerant discharge pipe 7 in the immediate vicinity of the first partition plate 45.
  • the value of a / A was increased to try to connect the refrigerant supply pipe 6 in the immediate vicinity of the first partition plate 44.

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

Abstract

L'invention concerne un condenseur (1) qui présente des performances d'échange de chaleur supérieures et convient à un dispositif de climatisation dédié à l'opération de refroidissement. Le condenseur (1) comprend : un noyau (11) dans lequel des tubes plats (2) et des ailettes (3) sont empilés en alternance ; un premier collecteur (4) disposé à une extrémité du noyau (11) ; un deuxième collecteur (5) disposé à une autre extrémité du noyau (11) ; et un tuyau d'alimentation en fluide frigorigène (6) et un tuyau d'évacuation de fluide frigorigène (7) qui sont reliés au premier collecteur (4). Le premier collecteur (4) comprend une portion d'entrée (41) couplée au tuyau d'alimentation en fluide frigorigène (6), une deuxième portion courbée (42), et une portion de sortie (43) couplée au tuyau d'évacuation de fluide frigorigène (7). Le condenseur (1) satisfait les expressions (1) à (5). (1) : 400 ≤ L ≤ 1500 (2) : 0,4 ≤ A/L ≤ 0,75 (3) : 30,275/L ≤ B/L ≤ (L - A)/3L (4) : 0,22 ≤ a/A ≤ 0,64 (5) : {0,09 × (B - 6,825 - 12,825) + 12,825}/B ≤ b/B ≤ (B - 6,825)/B
PCT/JP2018/030522 2017-08-21 2018-08-17 Condenseur WO2019039401A1 (fr)

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JP2017158675A JP2019035559A (ja) 2017-08-21 2017-08-21 凝縮器

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Publication number Priority date Publication date Assignee Title
JP7383935B2 (ja) * 2019-08-29 2023-11-21 株式会社デンソー 熱交換器
JP7394722B2 (ja) * 2020-07-28 2023-12-08 三菱電機株式会社 除湿装置
WO2023144917A1 (fr) * 2022-01-26 2023-08-03 株式会社Uacj Échangeur de chaleur à flux parallèle et climatiseur

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JP2016053473A (ja) * 2016-01-22 2016-04-14 三菱電機株式会社 熱交換器及び冷凍サイクル装置

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US6003592A (en) * 1992-11-25 1999-12-21 Denso Corporation Refrigerant condenser
JPH1089883A (ja) * 1996-09-17 1998-04-10 Zexel Corp 熱交換器用ヘッダーパイプとその製造装置
KR100264815B1 (ko) * 1997-06-16 2000-09-01 신영주 다단기액분리형응축기
JP2001165532A (ja) * 1999-12-09 2001-06-22 Denso Corp 冷媒凝縮器
CN201476625U (zh) * 2009-06-15 2010-05-19 浙江康盛股份有限公司 微通道冷凝器
WO2013058953A1 (fr) * 2011-10-19 2013-04-25 Carrier Corporation Echangeur de chaleur à ailettes en tube aplati et procédé de fabrication

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JP2016053473A (ja) * 2016-01-22 2016-04-14 三菱電機株式会社 熱交換器及び冷凍サイクル装置

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