EP2711658A2 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP2711658A2
EP2711658A2 EP13182842.8A EP13182842A EP2711658A2 EP 2711658 A2 EP2711658 A2 EP 2711658A2 EP 13182842 A EP13182842 A EP 13182842A EP 2711658 A2 EP2711658 A2 EP 2711658A2
Authority
EP
European Patent Office
Prior art keywords
flat tubes
refrigerant
heat exchanger
inflow region
inflow
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP13182842.8A
Other languages
German (de)
English (en)
Other versions
EP2711658A3 (fr
Inventor
Dr. rer. nat. Günther Feuerecker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2711658A2 publication Critical patent/EP2711658A2/fr
Publication of EP2711658A3 publication Critical patent/EP2711658A3/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes

Definitions

  • the invention relates to a heat exchanger with a block of parallel arranged flat tubes and arranged between the flat tubes ribs, the flat tubes form flow channels, which are traversed by a refrigerant and the flat tubes are flowed around by a coolant, wherein the flat tubes at their end with collecting tanks in Fluid communication are, wherein the refrigerant is flowed into an inflow region of a collection box, which is in fluid communication with at least one of the flow channels.
  • Evaporators in air conditioning systems of motor vehicles are often flowed through with a refrigerant.
  • the refrigerant present in a two-phase state is completely converted into a gaseous phase in the evaporator.
  • the refrigerant has both a liquid and a gaseous phase.
  • the DE 10 2005 004 284 A1 discloses, for example, a flat-tube evaporator, which has on one of its laterally arranged collection box, a lateral surface oriented parallel to the plane of the flat tubes on the side, an inflow opening through which the refrigerant can flow into the evaporator.
  • the refrigerant is distributed freely in the inflow region and flows from there into the flat tubes.
  • the US 2006/0201198 A1 discloses a flat tube evaporator having a nozzle on the side wall of the header tank oriented parallel to the plane of the flat tubes. Through the nozzle is trying to ensure the most uniform inflow of the refrigerant over the entire length of the header tank.
  • the EP 1 548 380 A2 discloses an injection conduit led into the header having along its extension into the header a plurality of openings which are preferably aligned in a common direction. The refrigerant flows through this injection pipe and exits from the plurality of openings to be evenly distributed in the collecting box.
  • the openings point in a direction away from the inlets of the flat tubes.
  • a disadvantage of the devices according to the prior art is that a uniform distribution of the two-phase refrigerant is not achieved via the collecting box, both at low and at high mass flows.
  • An embodiment of the invention relates to a heat exchanger with a block of flat tubes arranged parallel to each other and between the flat tubes arranged ribs, wherein the flat tubes form flow channels, which are traversed by a refrigerant and the flat tubes are flowed around by a coolant, wherein the flat tubes are in fluid communication at their end with collecting tanks, wherein the refrigerant can be flowed into an inflow region of a collecting box, which with at least one of the flow channels is in fluid communication, wherein the inflow region has a line extending through the inflow region for flowing the refrigerant, wherein a refrigerant transfer from the conduit to the inflow region of the header box is provided, which is arranged in the central region of the inflow region of the header tank, wherein the middle Range is related to a direction which is oriented perpendicular to a plane of the flat tubes.
  • the refrigerant Via the line, which runs in the interior of the collecting tank, the refrigerant can be flowed into the inflow region of the collecting tank at a defined point. As a result, a more even distribution of the refrigerant in the inflow region of the collecting tank can be produced. By a more uniform distribution, the efficiency of the heat exchanger can be increased.
  • the arrangement of the refrigerant transfer in the central region of the inflow region is particularly conducive to a uniform distribution of the refrigerant in the inflow region, since the flow path to the respective most remote flat tubes is the same.
  • a flat tube consists of essentially two opposing large flat side surfaces, which are connected to each other via two narrow sides.
  • the plane of the flat tubes therefore refers to a plane that runs parallel to the large flat side surfaces of the flat tubes.
  • the line extends substantially perpendicular to a plane of the flat tubes.
  • the line extends substantially over half the length of the inflow region or extends over the substantially entire length of the inflow region.
  • An extension of the conduit over the entire length of the inflow region ensures that the blocking effect caused by the conduit is the same for the refrigerant that has flowed into the inflow region over the entire length of the inflow region. This promotes a uniform distribution of the refrigerant in the inflow area.
  • the blocking effect arises through the line, which is the free flow of the refrigerant within the inflow in the way.
  • an embodiment with a line which extends only over half the length of the inflow region can be advantageous, in particular, if the spatial conditions do not allow any extension of the line over the entire length.
  • the refrigerant By the flow from the refrigerant passage perpendicular to the extension of the conduit is achieved that the refrigerant preferably flows to one of the walls of the inflow region, before it continues to flow in one of the flat tubes. In this way, a more uniform distribution of the refrigerant is achieved in the inflow.
  • the refrigerant transfer is arranged at an angle to the main flow direction of the flat tubes and in the plane of the flat tubes, wherein the angle is in a range of 140 ° to 220 °, preferably in a range of 160 ° to 200 °, while preferably corresponds to about 180 °.
  • the refrigerant transfer in a predetermined angle to the main flow direction of the flat tubes in the plane of the flat tubes, it can be achieved that the refrigerant does not flow directly into the flat tubes, but previously distributed along the inflow region. In this way, a more uniform distribution of the refrigerant is achieved in the inflow.
  • the refrigerant transfer is formed by an opening.
  • the refrigerant transfer is formed by a plurality of openings, which are arranged in the extension direction of the line adjacent to each other and which are arranged in a plane of the flat tubes at the same angle to the main flow direction of the flat tubes or in individually different angles are arranged to the main flow direction.
  • a plurality of openings which are arranged directly adjacent to each other in a small area of the conduit, may be particularly advantageous for a uniform distribution of the refrigerant in the inflow area.
  • a small area is meant a range that occupies a maximum of about one quarter of the length of the line in relation to the total length of the line in the collecting box.
  • the outer dimension of the conduit is in a ratio of 0.25 to 0.5 to the inner dimension of the collecting tank.
  • the limitation of the outer dimension of the line in relation to the inner dimension of the collecting tank is advantageous because it ensures that always sufficiently large gaps remain between the line and the inner walls of the collecting tank. If the line, compared to the inner dimensions of the collecting tank, occupy too large a region, the line would have an excessive blocking effect for the refrigerant. The inflow of the refrigerant into the flat tubes would be hindered.
  • the outer dimension would be given, for example, by the outer diameter.
  • a width of the opening of the refrigerant passage or the refrigerant passage openings is in a ratio of 0.1 to 0.4 to the inner dimension of the header tank.
  • the opening or the openings of the refrigerant transfer extends over a range of about 1% to 25% of the length of the inflow region.
  • a spatial limitation of the refrigerant transfer in relation to the length of the inflow region is advantageous because it can be achieved that the refrigerant transfer can not extend to an arbitrarily long piece of the inflow, whereby disadvantages would arise in terms of uniform distribution.
  • the line is guided by a parallel to the plane of the flat tubes arranged end face of the collecting tank in the inflow region.
  • the guidance of the line through a parallel to the plane of the flat tubes arranged end face of the collecting tank is advantageous because the line also extends within the collecting tank in a direction perpendicular to the plane of the flat tubes direction of the collecting tank. It can be avoided by already taking place in this direction introduction of the line unnecessary deflection, which can bring undesirable pressure losses.
  • a particularly advantageous embodiment of the invention provides that the heat exchanger is an evaporator.
  • FIG. 1 shows a section through a heat exchanger 1.
  • the heat exchanger 1 has a collection box 2, 2 a on two mutually opposite selves.
  • the two header boxes 2, 2 a are connected to one another via the flat tubes 4.
  • Via the flat tubes 4, a refrigerant can flow between the two header tanks 2, 2 a.
  • FIG. 1 as well as the FIG. 2 only one of the two headers 2, 2a is shown in each case.
  • the collection box 2 shown in each case has the inflow region of the heat exchanger 1.
  • the collection box 2 of FIG. 1 is divided by partitions 8 into several chambers.
  • a refrigerant flowing into the collecting box 2 can in each case only spread along one of these chambers before it flows through the flat tubes 4 into the respective second collecting box 2 a.
  • the refrigerant continues to be distributed and flows via further flat tubes 4 into the next chamber of the collecting tank 2.
  • this deflection between the first collecting box 2 and the second collecting box 2a takes place more or less frequently.
  • the first chamber of the collecting tank 2 is the inflow region 3 of the heat exchanger 1.
  • the lateral end face 7 of the collecting tank 2 lying parallel to the plane of the flat tubes is in this case penetrated by a line 5.
  • This line 5 is in fluid communication with a refrigerant source. Via the line 5, the refrigerant flows into the inflow region 3 of the collecting tank 2.
  • line 5 extends over the entire length I of the inflow 3.
  • the line 5 a refrigerant transfer 6 on. Via this refrigerant transfer 6, the refrigerant, which flows via the line 5 into the collecting box 2, can pass from the line 5 into the inflow region 3.
  • the in FIG. 1 shown refrigerant transfer 6 is formed by a single opening. It allows a flow of the refrigerant from the line 5 into the inflow region 3, which runs parallel to a plane of the flat tubes.
  • the refrigerant transfer 6 is positioned on the line 5 such that the refrigerant flows out of the line 5 in the direction of the wall 9 of the collecting tank 2 opposite the flat tubes 4.
  • the refrigerant transfer 6 should be oriented in such a way that the refrigerant is primarily directed to the wall 9 of the collecting tank 2 opposite the flat tubes 4. This contributes to a better distribution of the refrigerant in the inflow region 3.
  • the refrigerant transfer is not formed by a single opening, but rather by a plurality of small openings. These may for example be arranged in an area in which they are arranged directly adjacent to each other. This area is viewed in the extension direction of the line, preferably in the middle region of the inflow area. By arranging the refrigerant transfer in the middle region of the inflow region, a uniform distribution of the refrigerant is favored.
  • the refrigerant transfer 6 is formed from a plurality of openings, these can be aligned either uniformly at an equal angle to the main flow direction 10 of the flat tubes in a plane of the flat tubes or in individual, different angles to the main flow direction 10. Also in the arrangement of multiple openings Preferably, each of the openings aligned so that the refrigerant flows primarily to the flat tubes 4 opposite wall 9.
  • FIG. 2 shows an arrangement of a heat exchanger according to the embodiment of FIG. 1 ,
  • the reference numerals between the two figures are largely identical. Deviating is only the line 5a, which in comparison to FIG. 1 does not extend over the entire length I of the inflow region 3, but only protrudes into the collecting box 2 until it is slightly more than half the length I of the inflow region 3.
  • the refrigerant transfer 6 is in FIG. 2 arranged at the end of the line 5a. For the design of the refrigerant transfer 6 apply the already in FIG. 1 described possible alternative embodiments.
  • a conduit as in FIG. 1 shown a routing, as in FIG. 2 shown to be preferred.
  • Conduction along the entire length I of the inflow region 3 ensures that the entire refrigerant, which flows into the inflow region 3 above the line 5, 5a, experiences the same flow resistance.

Landscapes

  • 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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP13182842.8A 2012-09-25 2013-09-03 Echangeur de chaleur Withdrawn EP2711658A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012217340.4A DE102012217340A1 (de) 2012-09-25 2012-09-25 Wärmeübertrager

Publications (2)

Publication Number Publication Date
EP2711658A2 true EP2711658A2 (fr) 2014-03-26
EP2711658A3 EP2711658A3 (fr) 2014-09-10

Family

ID=49083592

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13182842.8A Withdrawn EP2711658A3 (fr) 2012-09-25 2013-09-03 Echangeur de chaleur

Country Status (4)

Country Link
US (1) US9709338B2 (fr)
EP (1) EP2711658A3 (fr)
CN (1) CN203657589U (fr)
DE (1) DE102012217340A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014206612A1 (de) * 2014-04-04 2015-10-29 Mahle International Gmbh Wärmetauscher
TWI686580B (zh) * 2019-02-20 2020-03-01 龍大昌精密工業有限公司 冷凝器之散熱結構
JP6767606B1 (ja) * 2019-12-09 2020-10-14 日立ジョンソンコントロールズ空調株式会社 分配装置、分配装置を備えた熱交換器およびその熱交換器を備えた空気調和機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1548380A2 (fr) 2003-12-22 2005-06-29 Hussmann Corporation Evaporateur à tubes plats avec micro-distributeur
DE102005004284A1 (de) 2004-01-28 2005-08-11 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere Flachrohr-Verdampfer für eine Kraftfahrzeug-Klimaanlage
US20060201198A1 (en) 2005-03-09 2006-09-14 Denso Corporation Heat exchanger

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1548380A2 (fr) 2003-12-22 2005-06-29 Hussmann Corporation Evaporateur à tubes plats avec micro-distributeur
DE102005004284A1 (de) 2004-01-28 2005-08-11 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere Flachrohr-Verdampfer für eine Kraftfahrzeug-Klimaanlage
US20060201198A1 (en) 2005-03-09 2006-09-14 Denso Corporation Heat exchanger

Also Published As

Publication number Publication date
US9709338B2 (en) 2017-07-18
US20140083665A1 (en) 2014-03-27
CN203657589U (zh) 2014-06-18
DE102012217340A1 (de) 2014-03-27
EP2711658A3 (fr) 2014-09-10

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