WO2017154336A1 - Échangeur de chaleur et pompe à chaleur utilisant celui-ci - Google Patents

Échangeur de chaleur et pompe à chaleur utilisant celui-ci Download PDF

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Publication number
WO2017154336A1
WO2017154336A1 PCT/JP2017/000696 JP2017000696W WO2017154336A1 WO 2017154336 A1 WO2017154336 A1 WO 2017154336A1 JP 2017000696 W JP2017000696 W JP 2017000696W WO 2017154336 A1 WO2017154336 A1 WO 2017154336A1
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WO
WIPO (PCT)
Prior art keywords
header
heat exchanger
branch pipe
branch
protrusion
Prior art date
Application number
PCT/JP2017/000696
Other languages
English (en)
Japanese (ja)
Inventor
遠藤　和広
Original Assignee
株式会社日立製作所
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 株式会社日立製作所 filed Critical 株式会社日立製作所
Publication of WO2017154336A1 publication Critical patent/WO2017154336A1/fr

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Classifications

    • 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
    • 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
    • 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
    • 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

  • the present invention relates to a heat exchanger and a heat pump apparatus using the same.
  • Patent Document 1 discloses a configuration in which a mesh and a stationary blade are arranged in a flow divider main body upstream of a narrow tube as a flow divider that evenly distributes a gas-liquid two-phase refrigerant to an evaporator constituting a refrigeration cycle. Is described.
  • a mesh and a stationary blade are disposed downstream of a mesh and a stationary blade by arranging a mesh and a stationary blade at an inflow portion of a cylindrical header (a shunt) in which a plurality of heat transfer tubes (narrow tubes) are connected in a vertical direction at predetermined intervals.
  • a shunt a cylindrical header
  • heat transfer tubes narrow tubes
  • gas-liquid mixing of the refrigerant can be achieved.
  • the gas-liquid is returned to a non-homogeneous original flow state, the gas-liquid mixing state at the branch portion of the heat transfer tube cannot be maintained, and the effect of improving the non-uniform flow distribution to each heat transfer tube is small.
  • an object of the present invention is to provide a heat exchanger provided with a header that suppresses non-uniform flow distribution.
  • a heat exchanger includes a cylindrical header arranged in a vertical direction, a branch pipe connected to a vertical side wall of the header, and an inlet of the branch pipe.
  • a plate-like member disposed on the upstream surface of the header, which is a wall surface of the opposing header and is upstream of the inlet of the branch pipe.
  • a heat exchanger including a header that suppresses non-uniform flow distribution.
  • FIG. 1 is a cycle configuration diagram of an air conditioner according to Embodiment 1.
  • FIG. It is a figure of the heat exchanger which concerns on Example 1.
  • FIG. It is sectional drawing of the header of the heat exchanger which concerns on Example 1.
  • FIG. It is AA sectional drawing of FIG.
  • FIG. It is BB sectional drawing of FIG.
  • It is a figure showing the distribution characteristic of the header of 4 branches without a protrusion part.
  • It is a figure showing the internal flow state of a 4-branch header without a protrusion part.
  • It which compared the distribution characteristic of the 4-branch header with a protrusion part with the case where there is no protrusion part.
  • It is a figure showing the internal flow state of the 4 branch header with a protrusion part.
  • FIG. 10 is a view of a sheet that forms protrusions according to Example 5;
  • the present invention relates to a cylindrical header arranged in a vertical direction, a branch pipe connected to a vertical side wall of the header, and a wall surface of the header facing the inlet of the branch pipe, And a protrusion disposed below the inlet.
  • a cylindrical header arranged in the vertical direction having a refrigerant inflow portion at the bottom, a branch pipe connected to the vertical side wall of the header, and a wall surface of the header facing the inlet of the branch pipe. And a protruding portion disposed upstream of the inlet of the branch pipe in the header.
  • a cylindrical header arranged in the vertical direction, a branch pipe connected to the vertical side wall of the header, and protruding portions alternately in the vertical direction on the side surface in the header are provided.
  • the gas-liquid is mixed in the entire header by changing the flow of the gas phase against the buoyancy in relation to the inlet position of the branch pipe, so that the unevenness of the flow distribution can be improved.
  • FIG. 1 is a cycle configuration diagram of an air conditioner as a heat pump device according to the present embodiment.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 3 flows into the outdoor heat exchanger 2 that functions as a condenser via the four-way valve 4.
  • the refrigerant that has flowed into the outdoor heat exchanger 2 is condensed and becomes liquid refrigerant by exchanging heat with the outdoor air sent by the outdoor fan 2f.
  • the liquid refrigerant passes through the expansion valve 5 to become a low-temperature and low-pressure two-phase refrigerant and flows into the indoor heat exchanger 1 that functions as an evaporator.
  • the low-temperature and low-pressure two-phase refrigerant that has flowed into the indoor heat exchanger 1 exchanges heat with indoor air sent by the indoor fan 1f and evaporates.
  • the indoor air sent to the indoor heat exchanger 1 is cooled by the low-temperature and low-pressure two-phase refrigerant flowing into the indoor heat exchanger 1 and discharged into the room from the outlet. Since the air discharged into the room from the outlet is lower than the temperature of the air at the inlet, the room temperature can be lowered.
  • the refrigerant heat-exchanged in the indoor heat exchanger 1 returns to the compressor 3 through the four-way valve 4 again.
  • the compressor 3, the outdoor heat exchanger 2, the outdoor blower fan 2f, and the expansion valve 5 are arranged in the outdoor unit, and the indoor heat exchanger 1 and the indoor blower fan 1f are arranged in the indoor unit.
  • FIG. 2 is a diagram of the indoor heat exchanger 1 according to the present embodiment.
  • the indoor heat exchanger 1 is arranged at a predetermined interval in the horizontal direction with cylindrical headers 10 and 20 arranged in the vertical direction in the longitudinal direction, and connected to the vertical side walls of the headers 10 and 20.
  • a plurality of heat transfer tubes 30 and a plurality of fins 40 arranged at predetermined intervals in the vertical direction and joined to the heat transfer tubes 30 are configured.
  • a gas-liquid two-phase refrigerant flows from the lower side of the header 20, the refrigerant is distributed to the heat transfer tubes 30 by the header 20, evaporates, merges at the header 30, and the refrigerant flows out from the upper side.
  • FIG. 3 is a cross-sectional view of the header 10 according to the present embodiment.
  • the lower part of the cylindrical header 10 has an opening 16 through which a refrigerant flows, and the upper part has a closing part 17 that does not flow in and out.
  • An end 31 of a branch pipe (heat transfer pipe) 30 is formed inside the header 10 on the side wall 15. It is connected so that it does not protrude or protrudes very little.
  • the branch pipe 30 of this embodiment is a circular pipe, and the number thereof is ten.
  • the protruding portion 11 is horizontally disposed at the same height position as the branch pipe 30 on the inner wall surface 15 a facing the end (inlet) 31 of the branch pipe 30.
  • the protruding portion 13 is at a height position that is horizontally shifted by the distance between the branch pipes 30 and by one half the distance upstream (vertically downward). Has been placed. That is, the protruding portions 11 and 13 are alternately arranged on the wall surface inside the header 10 at positions facing the vertical direction. Further, the protruding portions 11 and 13 are arranged upstream of the inlets of the branch pipes 30.
  • the protruding portion 13 has a plate shape or a flat plate shape in this embodiment, and extends into the header 10 substantially vertically from the wall surface in the longitudinal direction of the header 10.
  • FIGS. 4 and 5 are a sectional view taken on line AA and a line BB in FIG. 3, respectively.
  • the projecting portions 11 and 13 are semicircular and are inserted into the notched portions 12 and 14 of the side wall 15 and then joined by brazing.
  • FIG. 6 is a diagram showing distribution characteristics (liquid phase ratio of each branch and inlet dryness) of a header having a four-branch rectangular section without a protrusion.
  • the liquid phase refrigerant having latent heat of evaporation contributes to cooling, and the distribution ratio of the liquid phase ratio is important.
  • the liquid phase ratio of each branch and the dryness of the inlet were estimated from the heating amount and flow rate measurement of the heater of each branch pipe downstream of the header.
  • the dryness condition at the header inlet is 0.2.
  • Branch No. Are in the order of 1 to 4 from the top.
  • the liquid phase ratio of equal distribution is 0.25.
  • the branch hole has a flat shape.
  • the liquid phase ratio is distributed to the lower three branches (No. 2 to 4) by about 30%, and the top branch No. Only 0.06 flows in 1. Further, the dryness of the branch inlet at this time indicates that the lower three branches are almost zero and the gas phase hardly flows.
  • FIG. 7 is a photograph showing the internal flow state of the header at this time.
  • the flow pattern in the header is considered to be a churn flow in which large and small bubbles flow in the liquid phase flow.
  • the liquid level is branch No. 1 and No. Exists between 2 and fluctuates up and down.
  • FIG. 8 is a diagram comparing the distribution characteristics of a four-branch header with protrusions with no protrusions.
  • the top branch No. The liquid phase ratio of 1 is improved from about 0.06 to 0.19.
  • the inlet dryness of the lower three branches is improved from almost zero to 0.1 to 0.18.
  • FIG. 9 is a photograph showing the internal flow state of the header at this time. It is considered that gas-liquid was mixed by installing alternating protrusions as obstacles in the vertically upward flow of the gas phase due to buoyancy, and the ratio of gas-liquid was equalized throughout the header.
  • FIG. 10 is a cross-sectional view of the header of the heat exchanger according to the second embodiment.
  • An end portion 51 of the branch pipe 50 is connected to the side wall 15 of the header 10A so as to protrude by a radius toward the inside of the header 10A.
  • the protrusion part 11 is arrange
  • the branch pipe 50 is a flat pipe as shown in FIGS. 11 and 12, the width thereof is slightly smaller than the inner diameter of the header 10A, and the area where the branch pipe 50 projects into the header 10A occupies nearly half of the inner cross section of the header 10A. .
  • the branch pipe 50 protrudes approximately half of the inner cross-section of the header 10A, so that the gas phase is vertically upward due to buoyancy. On the other hand, it becomes an obstacle and gas-liquid is mixed, and the same effect as in Example 1 can be obtained. Moreover, since the separate protrusion part 13 can be decreased compared with Example 1, manufacturing cost can be held down.
  • FIG. 13 is a cross-sectional view of the header of the heat exchanger according to the third embodiment.
  • the arrangement of the protruding portions 11 and 13 of the header 10B is rough in the lower half of the header on the upstream side and dense in the upper half of the header on the downstream side. That is, the distance between the protrusions 11 and 13 is made closer toward the top. Since the refrigerant flows in from the opening 16 and flows in order from the lower branch pipe 30, the refrigerant in the header 10B is decelerated as it goes up. The slower the coolant speed, the smaller the effect of gas-liquid mixing by the protrusions 11 and 13. Therefore, the effect of gas-liquid mixing can be obtained by increasing the set density of the protrusions 11 and 13 as the header upper part has a lower refrigerant speed.
  • FIG. 14 is a cross-sectional view of the header of the heat exchanger according to the fourth embodiment.
  • the header 10 ⁇ / b> C is provided with protruding portions 60 and 61 having large plate thicknesses instead of densely arranging the protruding portions 11 and 13 in the upper half of the header B of the third embodiment. That is, the protrusions 11 and 13 are plate-like, and the upper protrusions 11 and 13 in the header 10C are thicker than the lower protrusions 11 and 13 in the header 10C.
  • the internal volume of the upper half of the header 10C becomes small, the refrigerant speed increases, and the effect of gas-liquid mixing due to the collision with the protruding portion can be obtained.
  • FIG. 15 is a cross-sectional view of the header of the heat exchanger according to the fifth embodiment.
  • the header 10 ⁇ / b> D forms a protrusion by inserting a sheet 70 (plate) that forms the protrusion 71 instead of the protrusion 11 of the second embodiment. That is, the projecting portion 71 has a plate-like member formed on the sheet 70 (plate), and the sheet 70 is inserted into the header 10D.
  • the sheet 70 is a rectangular plate, and a semicircle that becomes protrusions 71 installed at a predetermined interval in the longitudinal direction is cut leaving a part 72 of the arc, and a part 72 of the arc Bend vertically.
  • the sheet 70 is rolled in a direction perpendicular to the longitudinal direction and inserted from below the header 10D.
  • the notch portion is provided on the side wall of the header, and the projecting portion is inserted into the notch and brazing work can be eliminated, so that the manufacturing cost can be reduced.

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

Abstract

La présente invention concerne un échangeur de chaleur pourvu d'un collecteur pour supprimer l'irrégularité de distribution de débit, et une pompe à chaleur pourvue de l'échangeur de chaleur. Afin de résoudre ce problème, cet échangeur de chaleur et une pompe à chaleur pourvue de celui-ci sont caractérisés en ce qu'ils sont pourvus d'un collecteur cylindrique 10 disposé dans la direction verticale, de tuyaux de branchement 30 raccordés à la paroi latérale du collecteur 10 dans la direction verticale, et de sections saillantes 11, 13 disposées dans la paroi latérale du collecteur 10 faisant face aux entrées des tuyaux de branchement 30 et disposées au-dessous des entrées des tuyaux de branchement 30.
PCT/JP2017/000696 2016-03-10 2017-01-12 Échangeur de chaleur et pompe à chaleur utilisant celui-ci WO2017154336A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-046450 2016-03-10
JP2016046450A JP2019095073A (ja) 2016-03-10 2016-03-10 熱交換器及びこれを用いたヒートポンプ装置

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020118385A (ja) * 2019-01-25 2020-08-06 東芝キヤリア株式会社 熱交換器及び冷凍サイクル装置
WO2020237960A1 (fr) * 2019-05-31 2020-12-03 浙江三花智能控制股份有限公司 Tuyau de distribution et échangeur de chaleur
CN114623702A (zh) * 2020-12-11 2022-06-14 杭州三花微通道换热器有限公司 换热器

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02219966A (ja) * 1989-02-21 1990-09-03 Matsushita Refrig Co Ltd 冷媒分流器
JPH0355490A (ja) * 1989-07-21 1991-03-11 Nippondenso Co Ltd 熱交換器
JPH03260566A (ja) * 1990-03-08 1991-11-20 Mitsubishi Electric Corp 気液二相流体の分配器
JP2005300072A (ja) * 2004-04-14 2005-10-27 Calsonic Kansei Corp 蒸発器
CN101691979A (zh) * 2009-09-03 2010-04-07 三花丹佛斯（杭州）微通道换热器有限公司 集流管以及具有该集流管的热交换器
US20100300647A1 (en) * 2009-05-28 2010-12-02 Hans-Ulrich Steurer Heat exchanger
JP2011242119A (ja) * 2010-04-23 2011-12-01 Calsonic Kansei Corp 熱交換器のヘッダタンク
JP2013002688A (ja) * 2011-06-14 2013-01-07 Sharp Corp パラレルフロー型熱交換器及びそれを搭載した空気調和機
WO2014068687A1 (fr) * 2012-10-31 2014-05-08 株式会社 日立製作所 Échangeur de chaleur à courants parallèles et climatiseur l'utilisant

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02219966A (ja) * 1989-02-21 1990-09-03 Matsushita Refrig Co Ltd 冷媒分流器
JPH0355490A (ja) * 1989-07-21 1991-03-11 Nippondenso Co Ltd 熱交換器
JPH03260566A (ja) * 1990-03-08 1991-11-20 Mitsubishi Electric Corp 気液二相流体の分配器
JP2005300072A (ja) * 2004-04-14 2005-10-27 Calsonic Kansei Corp 蒸発器
US20100300647A1 (en) * 2009-05-28 2010-12-02 Hans-Ulrich Steurer Heat exchanger
CN101691979A (zh) * 2009-09-03 2010-04-07 三花丹佛斯（杭州）微通道换热器有限公司 集流管以及具有该集流管的热交换器
JP2011242119A (ja) * 2010-04-23 2011-12-01 Calsonic Kansei Corp 熱交換器のヘッダタンク
JP2013002688A (ja) * 2011-06-14 2013-01-07 Sharp Corp パラレルフロー型熱交換器及びそれを搭載した空気調和機
WO2014068687A1 (fr) * 2012-10-31 2014-05-08 株式会社 日立製作所 Échangeur de chaleur à courants parallèles et climatiseur l'utilisant

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020118385A (ja) * 2019-01-25 2020-08-06 東芝キヤリア株式会社 熱交換器及び冷凍サイクル装置
JP7132138B2 (ja) 2019-01-25 2022-09-06 東芝キヤリア株式会社 熱交換器及び冷凍サイクル装置
WO2020237960A1 (fr) * 2019-05-31 2020-12-03 浙江三花智能控制股份有限公司 Tuyau de distribution et échangeur de chaleur
CN114623702A (zh) * 2020-12-11 2022-06-14 杭州三花微通道换热器有限公司 换热器
CN114623702B (zh) * 2020-12-11 2023-08-29 杭州三花微通道换热器有限公司 换热器

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