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WO2016031032A1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

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Publication number
WO2016031032A1
WO2016031032A1 PCT/JP2014/072668 JP2014072668W WO2016031032A1 WO 2016031032 A1 WO2016031032 A1 WO 2016031032A1 JP 2014072668 W JP2014072668 W JP 2014072668W WO 2016031032 A1 WO2016031032 A1 WO 2016031032A1
Authority
WO
WIPO (PCT)
Prior art keywords
fin
heat exchanger
heat
slit
fins
Prior art date
Application number
PCT/JP2014/072668
Other languages
English (en)
Japanese (ja)
Inventor
浩之 豊田
坪江　宏明
杉山　達也
敬大 石部
貴則 五十川
瑞樹 津田
Original Assignee
日立アプライアンス株式会社
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 日立アプライアンス株式会社 filed Critical 日立アプライアンス株式会社
Priority to PCT/JP2014/072668 priority Critical patent/WO2016031032A1/fr
Publication of WO2016031032A1 publication Critical patent/WO2016031032A1/fr

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Classifications

    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements

Definitions

  • the present invention relates to a heat exchanger and an air conditioner.
  • a finned tube heat exchanger that combines a heat transfer tube for flowing refrigerant and fins is used for heat exchange between the refrigerant and air.
  • a temperature distribution is generated in the heat transfer tube due to pressure loss due to refrigerant flow inside, supercooling in the liquid single-phase region, or overheating in the vapor single-phase region. For this reason, when a temperature difference arises in an adjacent heat exchanger tube, the heat
  • Patent Document 1 proposes a structure in which a slit is provided between the heat transfer tubes of the fins to suppress heat conduction between the heat transfer tubes. Moreover, in patent document 2, in order to improve the drainage property of a slit, the slit shape is changed.
  • the finned tube heat exchanger is assembled by inserting fins into the heat transfer tube.
  • slits are provided in the width direction of the fin, and if the slit width is increased, the fins are easily bent, causing a decrease in strength.
  • the slit width is reduced, the effect of suppressing heat conduction is reduced. For this reason, it is difficult to increase the width of the slit portion with respect to the fin width, and it is difficult to increase the effect of suppressing heat conduction.
  • An object of the present invention is to provide a highly efficient heat exchanger that suppresses a decrease in strength of fins.
  • the present invention provides a heat exchange comprising: a laminated fin; a heat transfer tube that passes through the fin in the lamination direction and through which a refrigerant flows; and a blower that blows air in the width direction of the fin.
  • the fin includes a plurality of through holes through which the heat transfer tube passes, and a slit between the adjacent through holes and having a width longer than the through holes in the width direction of the blower. Furthermore, the fin is provided with a convex portion at the outer edge in the width direction.
  • FIG. 2 shows the shape of a fin tube heat exchanger.
  • the fin tube type heat exchanger includes a large number of fins 1 stacked at a narrow interval and a plurality of heat transfer tubes 6 penetrating these fins 1 so as to be orthogonal to each other.
  • the heat transfer tubes 6 are arranged so as to be orthogonal to the air flow direction 8 that is the direction of the flow of air flowing over the fins 1. Further, the fins 1 are arranged so that air flows in parallel between the stacked layers with respect to the air flow direction 8.
  • the fin 1 is arranged so that the longitudinal direction thereof is parallel to the gravity direction 11, and water that is condensed or water that is formed by melting frost flows to the lower part of the heat exchanger. .
  • the number of heat transfer tubes in the direction in which the air flows is referred to as the number of columns
  • the number of heat transfer tubes in the direction perpendicular to this is referred to as the number of steps
  • the directions are referred to as the column direction and the step direction, respectively.
  • the row direction is the width direction of the fin 1
  • the step direction corresponds to the longitudinal direction of the fin 1.
  • FIG. 2 shows a heat exchanger with two rows and six stages.
  • the heat exchanger of the present invention has a configuration in which two rows of one row of heat exchangers are arranged, and the fins 1 are not connected between the rows, and there is no exchange of heat due to heat conduction.
  • Refrigerant flow 7 flowing through the heat exchanger is an example showing a case where the heat exchanger is used as a condenser.
  • the case where the heat exchanger is used as a condenser is, for example, a case where it is used as an outdoor unit during cooling of an air conditioner.
  • the refrigerant flow is composed of a refrigerant flow 7a in which the gas is in a superheated state and in a volume ratio with a large amount of gas, a state in which the volume ratio is rich in liquid, and a supercooled liquid refrigerant flow 7b.
  • the gas refrigerant flows from the two gas side refrigerant inlets / outlets 6a, merges through the U-shaped tube 9 through the three-way pipe 10 and the like, and reaches the liquid side refrigerant inlet / outlet 6b through the U-shaped tube 9.
  • the refrigerant is overheated at the inlet, the refrigerant is cooled from the overheated state to the saturated state as it passes through the heat exchanger. Exit the heat exchanger in the cold state.
  • the refrigerant temperature is almost constant as long as there is no pressure change, but the superheated and supercooled refrigerant is in a state higher and lower than the saturation temperature.
  • two gas side refrigerant inlets / outlets 6a are provided in order to reduce the flow velocity in the pipe of the gas side refrigerant having a large volume flow rate, and the gas side refrigerant flows through the two heat transfer pipes 6 in parallel.
  • the refrigerant is cooled to a certain degree and the volume flow rate is reduced to some extent, the refrigerant is merged in the middle of the path by the three-way pipe 10 to flow through one heat transfer tube 6 and finally the liquid side provided at one place A path for discharging the refrigerant from the refrigerant inlet / outlet 6b is formed.
  • coolant flow is made small.
  • the change in the refrigerant temperature in the saturated state region is also kept small.
  • the gas side refrigerant inlet / outlet 6a and the liquid side refrigerant inlet / outlet 6b are adjacent to each other in the row direction.
  • Refrigerants flowing through both are superheated gas refrigerant and supercooled refrigerant, and have a large temperature difference.
  • the fins 1 are not connected in the row direction, no heat conduction occurs between the two heat transfer tubes 6.
  • the heat transfer tube 6 in which the saturated refrigerant flows and the heat transfer tube 6 in which the supercooled refrigerant flows may be adjacent in the step direction. In this case, a larger temperature difference such as 0K to 10K occurs in the heat transfer tubes 6 adjacent in the step direction. Due to this temperature difference, heat conduction is generated via the fins 1 from the heat transfer tube 6 in which the high-temperature saturated refrigerant flows to the heat transfer tube 6 in which the low-temperature supercooled refrigerant flows.
  • the heat transfer tube 6 through which the low-temperature supercooled refrigerant flows is suppressed from radiating no matter how much the temperature is higher than the outside air. It may be heated by the heat of the heat transfer tube 6 through which the refrigerant in the state flows. Accordingly, the heat radiation amount of the heat transfer tube 6 through which the high-temperature saturated refrigerant flows increases, so that the heat radiation area on the side of the heat transfer tube 6 through which the low-temperature supercooling refrigerant flows is not completely wasted.
  • it is difficult to obtain the degree of supercooling of the refrigerant it is conceivable that the performance of the entire refrigeration cycle using this heat exchanger is reduced.
  • the refrigerant flow directions in FIG. 2 are all reversed.
  • the case where the heat exchanger is used as an evaporator is, for example, a case where it is used as an outdoor unit during heating of an air conditioner.
  • a liquid-rich state or a supercooled liquid refrigerant flow 7b flows in from the liquid-side refrigerant inlet / outlet 6b at one location.
  • the air temperature is higher than the refrigerant temperature, and the liquid refrigerant flows while being heated and gasified.
  • the gas ratio increases, the refrigerant flow is divided into two heat transfer tubes 6 through the three-way tube 10. From there, it is further heated and finally discharged from two gas-side refrigerant outlets 6a.
  • the three-way pipe 10 is used to increase the flow path of the refrigerant in which the amount of gas increases, and the pressure loss is reduced.
  • the case where the refrigerant is still used as an evaporator as compared with the case where the refrigerant is used as a condenser. Is subject to internal pressure loss.
  • the heat transfer tube 6 in which the refrigerant in the two-phase state flows a slight temperature difference occurs, and heat exchange occurs between the adjacent heat transfer tubes 6 by heat conduction.
  • the decrease in the degree of superheat leads to a decrease in the performance of the entire refrigeration cycle using this heat exchanger.
  • even if it is in a saturated state if heat transfer from the refrigerant to the refrigerant occurs due to heat conduction, this may suppress heat absorption from the outside air.
  • the conventional fin 1 includes a fin collar 2 (through hole) through which the heat transfer tube 6 penetrates and a slit 3 provided between the fin collar 2.
  • the slit 3 is provided in the center of the fin 1, the strength is insufficient.
  • the heat exchanger is often formed by a method in which the heat transfer tubes 6 are inserted into the fin collar 2 after the fins 1 are stacked. Therefore, if the strength of the fin is too low, it is conceivable that the fin 1 bends or breaks during the transportation of the fin 1 alone. This leads to a decrease in production yield, and it can be thought that this leads to an increase in costs including work costs.
  • the width of the slit 3 is reduced in order to ensure the strength, heat flows through the outer edge of the fin 1 where the slit 3 is not cut, so that the effect of suppressing heat conduction is reduced.
  • the heat transfer rate of the fin 1 surface is higher, the amount of heat transferred by heat conduction is smaller. This is because the higher the heat transfer rate, the more difficult it is to transmit the temperature of the fin collar 2 in contact with the heat transfer tube 6 to a long distance. That is, by making a portion having a high heat transfer coefficient on the entire fin 1 and the outer edge of the fin 1, heat passing through the outer edge of the fin 1 bypassing the slit 3 is suppressed, and heat conduction between adjacent heat transfer tubes 6 is performed. It is possible to suppress the movement of heat due to.
  • a step or a notch is provided on the surface of the fin 1 to promote convection, and the temperature boundary layer is thinned by a discontinuous surface.
  • FIG. 1 shows the fin 1 of the first embodiment.
  • a slit 3 is provided in the fin collar 2 on the fin 1 and in the center of the fin collar 2 in parallel with the air flow direction.
  • convex ribs 4 convex portions
  • the fins 1 are arranged in the intermediate part of the adjacent heat transfer tubes, on the outer edge side of the fin 1 relative to the slit 3 parallel to the air flow direction, so as to go straight to the slit 3 and border the outer edge of the fin 1.
  • the rib which becomes a convex part was provided so that it might become one step higher than the outer edge.
  • the structure of the present invention is provided with ribs that are convex portions on both outer edges of the fin 1 so as to have a step with respect to the outer edges, and adjacent heat transfer tubes so as to connect the two ribs. It is the fin 1 which provided the slit 3 in the intermediate part.
  • ribs bent so as to be convex are added to the fin 1.
  • the rib 4 has an upstream inclined surface and a downstream inclined surface in the air flow direction.
  • the upstream inclined surface and the downstream inclined surface are continuously formed, but a flat portion may be provided between both inclined portions.
  • a plurality of ribs 4 may be arranged.
  • the heat transfer coefficient is locally increased at the convex upper surface portion of the rib, and the rib is attached, the heat transfer coefficient is improved as a whole compared to the conventional flat plate shown in FIG. As a result, the heat conduction between the heat transfer tubes can be reduced. Furthermore, since the strength can be ensured by the ribs, the slit 3 can be widened, and the heat conduction can be further suppressed.
  • the shape of the slit 3 in Example 1 is different from the offset fin 1 in the direction parallel to the air flow direction, but uses a cut-and-raised, and deformation due to layering is conceivable.
  • the direction is parallel to the air flow direction and the cut surface is slightly inclined, the pressure loss is not greatly improved. Also, there is no influence on the suppression of heat conduction, which is the target effect.
  • the slit 3 in Example 1 is for suppressing the solid heat conduction by the fins, and is, for example, cut, cut out, or raised. As shown in the BB cross section of FIG. 1 and FIG. 8, a slit was provided as a slit in the center of the fin collar adjacent to the fin 1 in parallel with the air flow. In order to increase the effect of suppressing heat conduction, the slit 3 is preferably formed to have a width longer than the diameter of the heat transfer tube.
  • This cut-and-raised is an offset shape formed so that the cut-out slit portion is lifted up one step. Compared with the cut-out, this slit portion can also be used effectively as a heat radiating surface of the fin 1 so that it can be used as a heat exchanger. High efficiency. In addition, since the air flow is somewhat disturbed by the offset portion, there is an effect of improving the heat transfer coefficient on the surface of the fin 1.
  • FIG. 9 shows another example of the slit 3 shape.
  • an example in which the cut and raised is used as the slit 3 is shown. Even in this shape, the surface area of the fin 1 is not impaired, and the cut and raised portion causes turbulence of the airflow.
  • FIG. 10 shows the temperature distribution of the model fin calculated from the difference between the present invention and the conventional fin structure.
  • air at a temperature of 35 ° C. is flowed from the front at a wind speed of 1 m / s to one element of the fin, and the temperature of the heat transfer tube is simulated.
  • a constant temperature condition of 50 ° C. was given.
  • the slit 3 has a cut-out shape in both the conventional structure and the present invention, and a heat conduction boundary is given to the outer edge of the slit 3 so that the normal heat conduction condition and the complete heat insulation condition can be switched.
  • the conventional structure is a flat plate structure
  • the structure of the present invention is a structure with ribs.
  • the width of the fin 1 is assumed to be the same, and the rib portion is assumed to be somewhat thin during pressing, so that the cross-sectional area of the fin 1 itself is equal in the flat plate condition and the rib presence condition.
  • FIG. 11 is a graph comparing the heat radiation amount of the present invention with that of the conventional method under normal heat conduction conditions. From this result, it can be seen that the heat dissipation rate of the structure of the present invention is larger than that of the conventional structure, and the heat transfer coefficient of the fin 1 is improved.
  • FIG. 12 is a graph comparing the amount of heat conduction from the low temperature side to the high temperature side of the present invention and the conventional one.
  • the amount of heat released from the collar portion when calculated under the complete heat insulation condition is different from the amount of heat released from the collar portion when the heat conduction boundary at the center of the fin 1 is calculated under normal conditions.
  • the heat insulation condition when the heat insulation condition is completely used, the heat radiation from the high temperature side is lost in the collar on the low temperature side, and the amount of heat radiation increases.
  • the collar on the high temperature side heat conduction to the low temperature side is eliminated, so that the amount of heat radiation is reduced. That is, the difference between the fin collar portions when the heat conduction boundary is changed from normal to complete heat insulation is the amount of heat conduction.
  • the amount of heat conduction is smaller under the ribbed condition, indicating that the structure of the present invention has a greater effect of suppressing heat conduction.
  • the heat exchanger is assembled by inserting the fins 1 into the heat transfer tubes 6.
  • the fins 1 having low strength are easily broken during transportation or insertion, so that they must be handled with care. May cause deterioration. Because of this attention, the number of work steps increases or a dedicated jig is required, which may lead to an increase in cost. Therefore, since the fin 1 of the present invention has the rib 4 on the outer edge portion of the fin 1, the strength is increased as compared with the conventional structure, so that the assembling property is improved and the cost is reduced.
  • the fin 1 is required to drain the accumulated water more quickly.
  • water has been drained by the action of the wind flowing on the surface of the fin 1 and the gravity applied to the longitudinal direction (step direction) of the fin 1. Since the slit 3 obstructs the flow of water flowing in the step direction, the drainage performance may be lower than that of a flat plate.
  • FIG. 5 shows a perspective view and a partially enlarged view of the second embodiment.
  • the opening 5 is provided on the side surface 4 a on the heat transfer surface side of the rib 4 on the downstream side of the air flow direction 8 on the fin 1, at a position corresponding to the slit 3 in the one-step direction of the fin. Provided. Thereby, the effect which inhibits the heat conduction of the heat detoured from the side of a slit is acquired.
  • the opening part 5 is provided only in the side surface by the side of the slit of the rib 4, the rib 4 of the outer edge side can maintain intensity
  • the pressure on the leeward side of the rib is low, and if a through hole is provided on the leeward side surface of the rib, it is considered that the wind flows from the back to the front.
  • This wind flow also affects the flow of water, that is, the flow of water drainage on the surface of the fin 1.
  • the openings 5 are provided on the side surfaces of the rib 4 on the slit 3 side on both sides of the slit 3 as in this embodiment, one of the openings 5 becomes the windward side of the rib 4.
  • the water staying in the slit 3 is caused to flow to the leeward side of the fin 1 by the wind passing through the fin 1, the water can be flowed to the concave side of the rib, leading to improved drainage performance.
  • the strength is improved by the ribs 4 and the condensed water remaining in the slits 3 and the ribs 4 can be efficiently drained by providing the ribs 4 with the openings 5.
  • the opening 5 is provided at a position corresponding to the slit 3 in the longitudinal direction (step direction) of the fin 1, thereby producing an effect of reducing heat conduction. Furthermore, by setting the position where the opening 5 is provided on the side facing the air flow direction 8 of the rib 4, the opening 5 can be arranged while maintaining the strength.
  • FIG. 7 shows a perspective view and a partially enlarged view of the third embodiment.
  • the slit 3 was provided so as to be cut out from the side surface portion 4 a on the heat transfer surface side of the rib 4.
  • the width of the slit 3 can be further increased without impairing the strength of the fin 1, and the effect of improving the heat conduction suppressing effect can be obtained.
  • the slit 3 has a shape that penetrates the back surface side of the fin 1 of the rib 4.
  • the cut and raised slit portion is shaped like a beam connecting the ribs 4 on both sides of the fin 1, the strength against the twist of the fin 1 is increased.

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

Abstract

La présente invention concerne un échangeur de chaleur à haut rendement, dans lequel une baisse de la résistance d'ailette est atténuée. Dans la présente invention, un échangeur de chaleur est pourvu des éléments suivants : des ailettes empilées ; un tuyau de transfert de chaleur qui pénètre dans les ailettes dans le sens d'empilement des ailettes et à l'intérieur duquel s'écoule un fluide frigorigène ; et une soufflante qui souffle de l'air dans le sens de la largeur des ailettes. Les ailettes sont pourvues des éléments suivants : une pluralité de trous traversants par lesquels passe le tuyau de transfert de chaleur ; et des fentes qui sont formées entre les trous traversants adjacents et qui sont plus larges que les trous traversants dans le sens de la largeur des ailettes. Une saillie est formée au niveau du bord externe des ailettes, dans le sens de la largeur.
PCT/JP2014/072668 2014-08-29 2014-08-29 Échangeur de chaleur et climatiseur WO2016031032A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/072668 WO2016031032A1 (fr) 2014-08-29 2014-08-29 Échangeur de chaleur et climatiseur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/072668 WO2016031032A1 (fr) 2014-08-29 2014-08-29 Échangeur de chaleur et climatiseur

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WO2016031032A1 true WO2016031032A1 (fr) 2016-03-03

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020139677A (ja) * 2019-02-27 2020-09-03 株式会社Ｎｅｄインターナショナル 熱交換装置およびヒートポンプ装置
WO2022018877A1 (fr) * 2020-07-24 2022-01-27 株式会社Ｎｅｄインターナショナル Dispositif d'échange de chaleur et dispositif de pompe à chaleur

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4488593A (en) * 1982-09-10 1984-12-18 D. Mulock-Bentley And Associates (Proprietary) Limited Heat exchanger
JPH0828897A (ja) * 1994-07-15 1996-02-02 Shinko Kogyo Co Ltd 空気調和機用熱交換器
JPH109786A (ja) * 1996-06-21 1998-01-16 Matsushita Refrig Co Ltd フィン付熱交換器
JP2000171187A (ja) * 1998-12-04 2000-06-23 Daikin Ind Ltd 空調用熱交換器の伝熱フィン
JP2002228301A (ja) * 2001-01-26 2002-08-14 Matsushita Electric Ind Co Ltd 空気調和機のフィン付き熱交換器
US20090308585A1 (en) * 2008-06-13 2009-12-17 Goodman Global, Inc. Method for Manufacturing Tube and Fin Heat Exchanger with Reduced Tube Diameter and Optimized Fin Produced Thereby
WO2013157212A1 (fr) * 2012-04-16 2013-10-24 パナソニック株式会社 Échangeur de chaleur à tubes à ailettes

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4488593A (en) * 1982-09-10 1984-12-18 D. Mulock-Bentley And Associates (Proprietary) Limited Heat exchanger
JPH0828897A (ja) * 1994-07-15 1996-02-02 Shinko Kogyo Co Ltd 空気調和機用熱交換器
JPH109786A (ja) * 1996-06-21 1998-01-16 Matsushita Refrig Co Ltd フィン付熱交換器
JP2000171187A (ja) * 1998-12-04 2000-06-23 Daikin Ind Ltd 空調用熱交換器の伝熱フィン
JP2002228301A (ja) * 2001-01-26 2002-08-14 Matsushita Electric Ind Co Ltd 空気調和機のフィン付き熱交換器
US20090308585A1 (en) * 2008-06-13 2009-12-17 Goodman Global, Inc. Method for Manufacturing Tube and Fin Heat Exchanger with Reduced Tube Diameter and Optimized Fin Produced Thereby
WO2013157212A1 (fr) * 2012-04-16 2013-10-24 パナソニック株式会社 Échangeur de chaleur à tubes à ailettes

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020139677A (ja) * 2019-02-27 2020-09-03 株式会社Ｎｅｄインターナショナル 熱交換装置およびヒートポンプ装置
JP7061251B2 (ja) 2019-02-27 2022-04-28 株式会社Ｎｅｄインターナショナル 熱交換装置およびヒートポンプ装置
WO2022018877A1 (fr) * 2020-07-24 2022-01-27 株式会社Ｎｅｄインターナショナル Dispositif d'échange de chaleur et dispositif de pompe à chaleur

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