US20050205244A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US20050205244A1
US20050205244A1 US10/519,984 US51998405A US2005205244A1 US 20050205244 A1 US20050205244 A1 US 20050205244A1 US 51998405 A US51998405 A US 51998405A US 2005205244 A1 US2005205244 A1 US 2005205244A1
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United States
Prior art keywords
heat exchanger
planes
deflection
flow
refrigerant
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Abandoned
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US10/519,984
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English (en)
Inventor
Martin Kaspar
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Mahle Behr GmbH and Co KG
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Behr GmbH and Co KG
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Assigned to BEHR GMBH & CO. KG reassignment BEHR GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WOLK, GERRIT, KASPAR, MARTIN
Publication of US20050205244A1 publication Critical patent/US20050205244A1/en
Abandoned legal-status Critical Current

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    • 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
    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F25B39/04—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
    • 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
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0084—Condensers

Definitions

  • the invention relates to a heat exchanger, in particular a condenser or gas cooler for air conditioning systems, in particular for motor vehicles, preferably according to the preamble of patent claim 1 .
  • Condensers have become known from EP-B 0 414 433, in which two condensers are arranged one behind the other on the air side and are connected mechanically to one another by means of additional fastening elements.
  • the flow passes through the two condensers either in series or in parallel.
  • heat exchange takes place in cross countercurrent, that is to say the flow passes first through the leeward-side condenser, and the refrigerant then passes via a connecting line over into the windward-side condenser and flows through the latter as far as the refrigerant outlet located on the windward side.
  • the two condensers have the flow passing through them in a multiflow manner with a decreasing flow cross section (degressive connection).
  • a deflection of the refrigerant therefore takes place only within the plane of each condenser, that is to say only in width.
  • This known duplex condenser has the disadvantage that two condensers have to be connected to one another both mechanically and on the refrigerant side, thus necessitating additional components and assembly time. This means increased production costs. Furthermore, the known condenser also has thermodynamic potentials, since the flow does not pass through it optimally.
  • the object of the present invention is to improve a heat exchanger, in particular gas cooler or condenser, of the type initially mentioned, to the effect that, while the end face remains the same, the power output is increased and/or the weight and/or production costs are reduced.
  • the heat exchanger according to the invention such as, in particular, condenser or gas cooler, is preferably produced as a materially integral block which is preferably soldered “in one shot”. Consequently, mechanical connection parts are dispensed with, and production costs are lowered. Furthermore, the condenser is divided in the plane or in the planes of the flow ducts, that is to say in width, into blocks and/or perpendicularly to the planes, that is to say in depth, into segments through which the flow passes in succession, both a deflection in depth or in width and a deflection in depth and in width taking place. Owing to this division of the two-row condenser network, optimum throughflow possibilities arise on the refrigerant side, thus resulting in an increase in the power output of the condenser.
  • each block consists of two segments with an equal number of flow ducts.
  • the throughflow possibilities of the condenser are thereby further extended, thus allowing additional increases in power output. It is advantageous, furthermore, if the refrigerant inlet is arranged on a leeward-side or windward-side segment and the refrigerant outlet is arranged on a windward-side or leeward-side segment.
  • the flow passes through the individual segments in succession, in such a way that a deflection of the refrigerant in depth and in width takes place alternately. This gives rise to a cross counter/cocurrent for heat exchange between air and refrigerant.
  • the flow ducts are designed as flat tubes, specifically either in two, three or more rows or in one row, the “continuous” flat tube having the flow passing through it in a two-flow, three-flow or multiflow manner.
  • the flat tubes in this case have, if appropriate, inner ducts which are arranged in parallel and through which the flow passes in parallel. These ducts may also have connecting orifices with respect to one another. These flat tubes may also have turbulence inserts which are introduced into the flat tube.
  • the flat tube ends are fastened in a manifold which is common to more than one flat tube and in which the deflection in depth takes place. Furthermore, in an advantageous solution, the flat tube ends issue on the other side into two manifolds in which the deflection in width takes place. In this case, it is advantageous if the two manifolds either are produced in one piece and consequently hold the block together or are produced as separate manifolds which are held together via the “continuous” flat tubes.
  • the flat tubes have arranged between them continuous corrugated ribs which, by being soldered to the flat tubes, ensure a compact and inherently stable condenser block.
  • additional deflection members between the manifolds are provided, by means of which a simultaneous deflection of the refrigerant both in depth and in width becomes possible.
  • deflection members for example tube bends, segments through which the flow is capable of passing in series are connected to one another on the refrigerant side.
  • deflection members may be soldered into the manifolds, so that this variant of the condenser according to the invention can also be soldered in one operation in the soldering furnace.
  • FIG. 1 shows a two-row heat exchanger with deflection in depth and in width
  • FIG. 2 shows a two-row heat exchanger with deflection in depth and deflection both in width and in depth
  • FIG. 3 shows two manifolds formed in one piece for two flat tube rows
  • FIG. 4 shows two separate manifolds for a row of two-flow flat tubes
  • FIG. 5 shows a first flow variant
  • FIG. 6 shows a second flow variant
  • FIG. 7 shows a third flow variant
  • FIG. 8 shows a fourth flow variant
  • FIG. 9 shows a power output graph for a heat exchanger according to the invention, such as a condenser, as compared with the prior art.
  • FIG. 1 shows a two-row heat exchanger 1 , such as a condenser or gas cooler, with a first row 2 and a second row 3 of flat tubes 4 , known corrugated ribs, not illustrated, being arranged between the flat tubes 4 .
  • a two-row heat exchanger 1 such as a condenser or gas cooler
  • the rib height of the corrugated ribs is advantageously 4 mm to 12 mm.
  • the rib density that is to say the number of ribs per decimeter, is advantageously in the range of 45 to 95 ribs/dm, which corresponds to a rib spacing or a rib division of 1.05 to 2.33 mm.
  • the rib or corrugated rib may advantageously be inserted from a strip, in which the strip is inserted in corrugations or in zigzag form between the flat tubes. Expediently, the rib thus configured will have thermal separation between different regions, so that the regions which are arranged between different flat tubes or flat tube regions are at least partially insulated thermally.
  • the rib may also consist of a plurality of individual strips which are inserted between the adjacent flat tubes. It is advantageous, in this case, that the individual ribs of different rows have no thermal connection.
  • the flat tubes are advantageously configured in such a way that the tube width, that is to say the extent of the tubes in the direction of an adjacent tube of the same planes, is in the range of 1 mm to 5 mm, in particular advantageously of 1.2 mm to 3 mm.
  • the extent of the tubes between the direction perpendicular to the planes, the tube depth is expediently in the range of 3 mm to 20 mm, advantageously in the range of 5 mm to 10 mm.
  • the tube depth may be essentially identical in the blocks of the heat exchanger. In another exemplary embodiment of the invention, however, the selected tube depth may also be different from block to block. It is particularly expedient if the tube depth in the windward-side plane is smaller than the tube depth in the leeward-side plane.
  • the tubes of different planes are arranged in alignment in series, as seen in the airflow direction, that is to say they are arranged in series of the same height.
  • the tubes of one plane may be arranged so as to be offset with respect to the tubes of a further plane.
  • This offset arrangement may preferably take place up to the height of half the rib height plus half the tube width. Intermediate values may also be assumed.
  • different or identical ribs which are advantageously produced as independent strips, may be used between the tubes of various planes.
  • the flat tubes 4 of the two rows 2 , 3 have flat tube ends 4 a which issue into a common manifold 5 .
  • the flat tubes 4 of the two rows 2 , 3 have flat tube ends 4 b which issue into two separate manifolds 6 , 7 .
  • the manifold 7 is a refrigerant inlet 8 .
  • the two manifolds 6 , 7 are subdivided into manifold sections by means of partitions, of which a partition 9 is illustrated only in the manifold 6 which is illustrated as being open. The air flows through the condenser in the direction of the arrow L, the airflow direction.
  • the flow profile of the refrigerant in the condenser 1 is illustrated by a multiply angled line beginning with the refrigerant inlet KME and ending with the refrigerant outlet KMA.
  • the two rows 2 , 3 of the flat tubes 4 are subdivided into three blocks I, II, III, each block being subdivided in each case into two segments Ia, Ib; IIa, IIb and IIIa, IIIb.
  • the refrigerant therefore flows first through the leeward-side segment Ia of the rear tube row 3 , then passes into the manifold 5 , where it is deflected in depth, illustrated by the arrow UT 1 , and then passes into the windward-side segment Ib and into the windward-side manifold 6 , where it is deflected in width, illustrated by the arrow UB 1 .
  • the refrigerant then flows through the next segment IIa back again into the manifold 5 , where it is deflected once more in depth, but in the opposite direction to previously, according to the arrow UT 2 .
  • FIG. 2 shows a further exemplary embodiment of a condenser 10 which is constructed essentially identically to the condenser 1 according to FIG. 1 , the same reference numerals being used for identical parts.
  • the condenser 10 has an additional partition 11 in the windward-side manifold 6 and two tubular deflection members 12 , 13 which in each case connect sections of the windward-side manifold 6 to sections of the leeward-side manifold 7 .
  • the refrigerant flow path is again illustrated by a continuous multiply angled line beginning at the refrigerant inlet KME and ending at the refrigerant outlet KMA.
  • the refrigerant thus flows first through the leeward-side segment Ia, is deflected in the manifold 5 in depth in the direction of the windward-side segment Ib according to the arrow UT 1 and flows through the latter until it reaches the windward-side manifold 6 . Due to the position of the partition 11 , there are therefore six flat tubes 4 for the segments Ia and Ib of the block I.
  • the refrigerant is then deflected via the deflection member 12 into a section of the leeward-side manifold 7 , that is to say a simultaneous deflection both in width and in depth takes place, as illustrated by the arrow UBT 1 .
  • the refrigerant flows through the leeward-side segment IIb in the direction of the manifold 5 , is deflected there opposite to the airflow direction according to the arrow UT 2 and enters the windward-side segment IIa.
  • the windward-side manifold 6 that is to say the section between the two partitions 9 , 11 , is reached, a renewed deflection in width and in depth takes place by means of the deflection member 13 , this being illustrated by the arrow UBT 2 .
  • FIG. 3 shows the design of the two manifolds 6 , 7 , referred to here by 6 ′, 7 ′, in the form of a double tube 14 of spectacle shape.
  • the two manifolds 6 ′, 7 ′ are formed from a continuous sheet metal strip 15 with end edges 16 , 17 which are inserted into a web 18 connecting the two manifolds 6 ′, 7 ′ and are soldered to said web. This results in a firm connection between the two manifolds 6 ′, 7 ′ which receive the flat tubes 4 with their flat tube ends 4 b . This makes it possible to produce the two-row condenser in a soldered block.
  • FIG. 4 shows a further version for the design of the manifolds 6 , 7 , referred to here by 6 ′′, 7 ′′, which are designed as separate manifolds.
  • the flat tubes here are not arranged in two separate rows, as in the previous exemplary embodiments, but are formed by one “continuous” flat tube 19 through which the flow passes in a two-flow manner, that is to say in a front (windward-side) region 19 a and a rear (leeward-side) region 19 b .
  • the two regions 19 a , 19 b are separated from one another in flow terms by means of a middle separation region 19 c .
  • the continuous flat tube 19 has separate flat tube ends 19 a′ , and 19 b′ which are inserted into rim holes 20 for the two manifolds 6 ′′, 7 ′′ and are soldered to these.
  • An interconnected compact soldered condenser block is likewise obtained in this way.
  • FIG. 5 shows a diagrammatic illustration of the flow pattern of the exemplary embodiment according to FIG. 1 , that is to say a cross counter/cocurrent.
  • the entire network of the condenser 1 according to FIG. 1 is subdivided into three blocks I, II, III, each block consisting of two segments Ia and Ib, IIa and IIb and IIIa and IIIb.
  • the segments of a block have in each case the same number of tubes and lie in series, as seen in the airflow direction L.
  • the segments Ia, Ib have in each case nine flat tubes 4
  • the segments Ia, Ib have in each case seven flat tubes
  • the segments IIIa, IIIb have in each case five flat tubes 4 .
  • the refrigerant-side outlet cross section is smaller than the refrigerant inlet cross section and amounts to 5/9 or to 56 percent of the inlet cross section.
  • This is a favorable value for the gradation of the refrigerant-side flow ducts in the case of three blocks and six segments.
  • Remaining alphanumeric designations correspond to those of the exemplary embodiment according to FIG. 1 , that is to say the flow profile has three deflections in depth UT 1 , UT 2 and UT 3 and two deflections in width UB 1 and UB 2 .
  • FIG. 6 shows the flow pattern on which the exemplary embodiment according to FIG. 2 is based, once again the same alphanumeric designations being adopted.
  • the network of the condenser 10 ( FIG. 2 ) is again subdivided in width into three blocks I, II and III, and each block is subdivided in depth into two identical segments Ia, Ib; IIa, IIb and IIIa, IIIb.
  • the number of tubes for the block I is 2 ⁇ nine
  • for the block II is 2 ⁇ seven
  • for the block III is 2 ⁇ five, that is to say as in the previous exemplary embodiment.
  • the deflection in depth takes place in the same direction, that is to say opposite to the airflow direction L, in the direction of the arrows UT 1 , UT 2 and UT 3 .
  • a deflection both in width and in depth takes place, as illustrated by the arrow UBT 1
  • a deflection both in width and in depth likewise takes place, as illustrated by the arrow UBT 2 .
  • This flow type is to that extent a cross countercurrent which affords advantages in power output terms, as compared with the cross counter/cocurrent.
  • FIG. 7 shows a further flow pattern in which the network of the condenser is divided in width into two blocks I, II.
  • the block I is subdivided in depth into two identical segments Ia and Ib which in each case have nine flat tubes 4 .
  • the block II is subdivided into a segment IIb with nine flat tubes 4 and two subsegments IIaa with five flat tubes 4 and one subsegment IIab with four flat tubes.
  • the refrigerant first flows through the leeward-side segment Ia, a deflection in depth then takes place according to the arrow UT 1 , the refrigerant subsequently flows through the windward-side segment Ib, a deflection in width, according to the arrow UB 1 , thereafter takes place into the adjacent subsegment IIaa, there is then a deflection in depth UT 2 to the leeward-side segment IIb, and there is again a deflection in depth, according to the arrow UT 3 , from there to the windward-side subsegment IIab.
  • five flow paths are obtained here, that is to say an odd number.
  • Such a variant with subsegments may be advantageous, in particular, for the subcooling of the refrigerant in the last subsegment IIab.
  • a partition is advantageously used in the manifold.
  • This partition may expediently be designed as a separating plate.
  • FIG. 8 shows a further variant of the division of the condenser network into seven flow paths.
  • the network is subdivided in width into three blocks I, II, III; the block I is subdivided into two identical segments Ia, Ib, each with nine flat tubes 4 .
  • the block II is subdivided into two identical segments IIa, IIb, each with seven flat tubes, and the block III is subdivided into one segment IIIa with seven flat tubes and two subsegments IIIba with four flat tubes and one further subsegment IIIbb with three flat tubes.
  • the refrigerant routing between said segments takes place in the order of the arrows designated below: UT 1 , UB 1 , UT 2 , UB 2 , UT 3 and UB 3 .
  • FIG. 9 shows a power output comparison of the condensers according to the invention with the prior art, with a variable air onflow velocity in m/s on the abscissa.
  • the power output of the condenser in kW is plotted on the ordinate.
  • the unbroken line S represents the power output of a conventional serpentine condenser with multiflow throughflow and with degressive connection.
  • the first variant of the invention according to FIG. 1 is illustrated as a closely dotted line and is identified by KGG, which stands for cross counter/cocurrent.
  • the second variant of the invention according to FIG. 2 is illustrated as a widely dotted line and is designated by KG, which stands for cross countercurrent.
  • the flow can pass through the heat exchanger from the top downward or from the bottom upward.
  • Bottom and top are defined by the installation position of the heat exchanger.
  • a flow can pass through one plane of the heat exchanger from the bottom upward and through another plane from the top downward.
  • the flow ducts are preferably arranged horizontally.
  • the flow ducts are expediently oriented vertically and the manifolds are oriented horizontally.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
US10/519,984 2002-12-10 2003-11-03 Heat exchanger Abandoned US20050205244A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10257767.6 2002-12-10
DE10257767A DE10257767A1 (de) 2002-12-10 2002-12-10 Wärmeübertrager
PCT/EP2003/012224 WO2004053411A1 (de) 2002-12-10 2003-11-03 Wärmeübertrager

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US20050205244A1 true US20050205244A1 (en) 2005-09-22

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US10/519,984 Abandoned US20050205244A1 (en) 2002-12-10 2003-11-03 Heat exchanger

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US (1) US20050205244A1 (zh)
EP (1) EP1573259A1 (zh)
JP (1) JP2006509182A (zh)
KR (1) KR20050084778A (zh)
CN (1) CN1723378A (zh)
AU (1) AU2003287988A1 (zh)
BR (1) BR0309404A (zh)
DE (1) DE10257767A1 (zh)
MX (1) MXPA04010517A (zh)
WO (1) WO2004053411A1 (zh)

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US20050230093A1 (en) * 2002-11-27 2005-10-20 Uwe Forster Heat exchanger
US20060215365A1 (en) * 2005-03-24 2006-09-28 Cooler Master Co., Ltd. Monitor heat dissipator
US20070295490A1 (en) * 2004-10-12 2007-12-27 Behr Gmbh & Co. Kg Flat Tube for a Heat Exchanger
US20090151918A1 (en) * 2006-05-09 2009-06-18 Kon Hur Heat Exchanger for Automobile and Fabricating Method Thereof
US20110036546A1 (en) * 2007-12-10 2011-02-17 Michael Kohl Heat exchanger, in particular heater for motor vehicles
US20110139420A1 (en) * 2009-06-30 2011-06-16 Shanghai Oriental MHE Co., Ltd. Heat exchanger with microchannel, parallel flow, all-aluminium flat tube welding structure and its application
EP2565571A1 (en) * 2010-04-28 2013-03-06 Sanden Corporation Vehicle interior heat exchanger

Families Citing this family (11)

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DE102007009923A1 (de) * 2007-02-27 2008-08-28 Behr Gmbh & Co. Kg Kondensator für eine Klimaanlage, insbesondere eines Kraftfahrzeuges
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FR2986316B1 (fr) * 2012-01-30 2014-01-10 Valeo Systemes Thermiques Ensemble comprenant un echangeur de chaleur et un support sur lequel ledit echangeur est monte
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JP6106546B2 (ja) * 2013-07-10 2017-04-05 カルソニックカンセイ株式会社 熱交換装置
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CN105821632B (zh) * 2015-01-28 2018-12-11 东芝生活电器株式会社 衣物干燥机
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EP1573259A1 (de) 2005-09-14
MXPA04010517A (es) 2004-12-13
JP2006509182A (ja) 2006-03-16
CN1723378A (zh) 2006-01-18
KR20050084778A (ko) 2005-08-29
AU2003287988A1 (en) 2004-06-30

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