EP1811260A2 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP1811260A2
EP1811260A2 EP20070001137 EP07001137A EP1811260A2 EP 1811260 A2 EP1811260 A2 EP 1811260A2 EP 20070001137 EP20070001137 EP 20070001137 EP 07001137 A EP07001137 A EP 07001137A EP 1811260 A2 EP1811260 A2 EP 1811260A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
tubes
medium
flow
exchanger according
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Withdrawn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
EP20070001137
Other languages
German (de)
English (en)
Inventor
Martin Dipl.-Ing. Derleth
Martin Dipl.-Ing. Fieger
Andreas Dipl.-Ing. Grieb
Michael Dipl.-Ing. Kohl
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 EP1811260A2 publication Critical patent/EP1811260A2/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • 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
    • F28F9/0207—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions the longitudinal or transversal partitions being separate elements attached to header boxes
    • 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
    • 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
    • F28D2021/0091—Radiators
    • F28D2021/0096—Radiators for space heating

Definitions

  • the invention relates to a heat exchanger, in particular a radiator, for an air conditioning system of a motor vehicle, which comprises a plurality of tubes, which flows through a first medium, in particular of a coolant, and by a second medium, in particular of air, flows around.
  • the object of the invention is to provide a heat exchanger according to the preamble of claim 1, which has a low pressure drop in the tubes and a uniform outlet temperature profile of the second medium.
  • the object is in a heat exchanger, in particular a radiator, for an air conditioning system of a motor vehicle comprising a plurality of tubes, which flows through a first medium, in particular of a coolant, and flows through a second medium, in particular of air are achieved in that in the direction of flow of the second medium in each case at least two rows of flow channels for the first medium behind one another or, in particular offset, are arranged, which flows in opposite directions each simple and substantially perpendicular to the flow direction of the second medium from the first medium become.
  • By connecting the flow channels in the direction of flow of the second medium in series it is achieved that first of all the one and then the other of the at least two rows of flow channels for the first medium are flowed around by the second medium.
  • Simple flow in connection with the present invention means that the first medium flows through the flow channels only once in each case, simultaneously in opposite directions. To distinguish this is a so-called multiple flow.
  • the medium first flows through at least one flow channel in one direction. Subsequently, the same medium flows through at least one further flow channel in the opposite direction.
  • a preferred embodiment of the heat exchanger is characterized in that the heat exchanger in addition to the plurality of tubes has at least two connecting tubes, the two manifolds together or the manifolds connect to a deflection box for the first medium, between which the tubes for the first medium.
  • one of the collecting tanks is equipped with at least one inlet nozzle and at least one outlet nozzle.
  • the side with the connection piece is called the connection side.
  • the one connecting tube serves to transport the first medium from the connection side to the opposite side of the connection side.
  • the other connecting tube is used for the return transport of the first medium from the opposite side to the connection side.
  • a further preferred embodiment of the heat exchanger is characterized in that the tubes for the first medium are arranged between the connecting tubes. This results in a simple structure with a uniform outlet temperature profile of the second medium.
  • a further preferred embodiment of the heat exchanger is characterized in that at least one further connecting tube is arranged between the tubes. This allows the use of, for example, two inlets and one return or two returns and one inlet.
  • a further preferred embodiment of the heat exchanger is characterized in that in each case at least one separating element is arranged in the collecting tanks, which divides the associated collecting tank into an inlet volume and an outlet volume.
  • the inlet volume connects an inlet port to a series of flow channels.
  • the outlet volume connects one outlet nozzle to another series of flow channels.
  • the two flow channel rows are arranged offset in the direction of flow of the second medium.
  • Another preferred embodiment of the heat exchanger is characterized in that the separating element is formed by a double-L-shaped partition. As a result, a separation between the inlet volume and the outlet volume is achieved in a simple manner.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the depth of the connecting pipes, that is to say the extent of the connecting pipes in the direction of flow of the second medium is 10 mm to 100 mm, in particular 10 mm to 70 mm, in particular 20 mm to 60 mm. These values have proven to be particularly advantageous in the context of the present invention.
  • Another preferred exemplary embodiment of the heat exchanger is characterized in that the connecting tubes have the same depth, that is to say the extent of the connecting tubes in the direction of flow of the second medium, like the tubes. This creates a compact heat exchanger with a good efficiency.
  • Another preferred embodiment of the heat exchanger is characterized in that the pipes are interrupted by a deflection box are in which the first medium is deflected.
  • the deflection is preferably opposite to the direction of flow of the second medium.
  • Another preferred embodiment of the heat exchanger is characterized in that the transverse distribution of the tubes, that is the distance between the tubes 3mm to 14mm, in particular 4mm to 14 mm, in particular 5mm to 12mm. These values have proven to be particularly advantageous in the context of the present invention.
  • a further preferred exemplary embodiment of the heat exchanger is characterized in that the width, that is to say the extent of the tubes transversely to the direction of flow of the second medium, is 0.8 mm to 4 mm, in particular 1 mm to 4 mm, in particular 1 mm to 3 mm, in particular 0, 8mm to 3mm. These values have proven to be particularly advantageous in the context of the present invention.
  • a further preferred embodiment of the heat exchanger is characterized in that the heat exchanger has a mesh height of 100 to 800 mm, in particular from 200 to 500 mm. Net height refers to the extent of the pipes between two headers.
  • the heat exchanger has a mesh width of 50 mm to 500 mm, in particular 50 mm to 300 mm, in particular from 70 mm to 300 mm, in particular from 70 mm to 200 mm.
  • the mesh width is the extension of the tubes parallel to the length of the header boxes.
  • FIGS. 1 to 13 show a heat exchanger 1 according to a first exemplary embodiment in different views.
  • the heat exchanger 1 comprises a total of 12 flat tubes, which are flowed through by coolant.
  • the flat tubes as indicated by an arrow 11, flowed through by air.
  • Each flat tube is in Vietnameseumströmungscardi 11 in each case in two flow channels 3, 7; 4, 8 and 5, 9 divided.
  • the twelve flow channels, of which only the flow channels 7 to 9 are provided with reference numerals, are arranged in a first flow channel row 12.
  • the other twelve flow channels, of which only the flow channels 3 to 5 are provided with reference numerals, are arranged in a second flow channel row 13.
  • the two flow channel rows 12 and 13 are in the air flow direction 11 in succession or, in particular offset, arranged.
  • flow channels 7, 3; 8, 4; 9, 5 may be formed of separate tubes or of a tube having separate flow channels.
  • it is flat tubes, each with two separate flow channels 7.3; 8, 4; 9, 5 are equipped.
  • the ends of the flat tubes extend through floors 14, 15 of coolant collection boxes, which are referred to briefly as header boxes.
  • the flat tubes are arranged between two connecting tubes 17, 18, each comprising a flow channel.
  • the connecting tubes 17, 18 have substantially the same depth as the flat tubes.
  • the floor 15 belongs to a collection box 21.
  • the floor 14 belongs to a collection box 22, which is equipped with an inlet connection piece 24 and an outlet connection piece 25.
  • a partition wall 27 is arranged inside the collecting tank 22, which a partition wall 27 is arranged.
  • the partition wall 27 comprises a partition wall portion 30, which the Has the shape of a rectangular plate.
  • At the ends of the wall portion 30 are each a wall portion 31, 32 angled, the two wall portions 31 and 32 are each angled at right angles in opposite directions. As a result, the partition 27 gets a double-L-shaped shape.
  • the partition wall 28 has the same shape as the partition wall 27.
  • the incoming coolant is indicated by an arrow 34.
  • the escaping coolant is indicated.
  • the partition wall 27 serves to divide the interior of the collecting tank 22 into an inlet volume 36 and an outlet volume 37.
  • the entry volume 36 communicates with the inlet connection 24.
  • the outlet volume 37 communicates with the outlet nozzle 25 in connection.
  • the collection box 21 is also divided by the partition wall 28 into an inlet volume 38 and an outlet volume 39.
  • the inlet volume 38 communicates with the inlet volume 36 via the connecting tube 18.
  • the outlet volume 39 communicates via the connecting tube 17 with the outlet volume 37 in connection.
  • FIG. 3 shows that a gap 41 is provided between the connecting tube 17 and the flat tube containing the flow channel 7. In the same way is between two flat tubes each one. Gap 42 is provided.
  • the gaps 41 and 42 allow the passage of air between the flat tubes or the flat tubes and the connecting tubes.
  • In the intermediate spaces 41, 42 are preferably heat transfer devices, in particular louvers, arranged.
  • arrows 44 and 45 indicate that the coolant contained in the inlet volume 36 enters the flow channel row 13.
  • arrow 34 is indicated that a portion of the coolant from the inlet volume 36 enters the connecting pipe 18.
  • This coolant is passed through the connecting tube 18, as indicated by a dashed arrow 46.
  • An arrow 47 indicates that the coolant passes from the connecting tube 18 into the inlet volume 38.
  • From the Inlet volume 38 enters the coolant from below into the flow channel row 12, as indicated by arrows 48 and 49.
  • the coolant is then passed through the flow channel row 12 and enters the outlet volume 37, as indicated by arrows 43 and 55.
  • FIG 7 is indicated by arrows 52 and 53, that the emerging from the flow channel row 12 refrigerant is supplied to the exiting coolant stream 35.
  • the net height of the heat exchanger 1 is denoted by L.
  • the net height L of the heat exchanger is between 100 and 800 mm, in particular between 200 and 500 mm.
  • the mesh width of the heat exchanger 1 is designated B and is between 250 and 300 mm, in particular between 70 and 200 mm.
  • An arrow 51 indicates that the coolant exiting from the flow channel row 13 reaches the connecting tube 17 via the outlet volume 39. Then it is passed through the connecting pipe 17, as indicated by a dashed arrow 50.
  • the flow channels 3, 7; 3, 8 and 5, 9 are each integrally connected by a connecting web 56.
  • the width of the connecting tube 17 is designated in FIG. 8 by V1.
  • the width of the connecting tube 18 is denoted by V2.
  • the depth of the connecting pipes 17 and 18 is designated VT.
  • the transverse distribution of the flat tubes is denoted by q and is between 4 and 14 mm, in particular between 5 and 12 mm.
  • the width of the flat tubes is denoted by b and is between 1 and 4 mm, in particular between 1 and 3 mm.
  • the connection tube depth VT is between 10 and 70 mm, in particular between 20 and 60 mm.
  • the connecting tube depth VT is preferably exactly the same as the depth of the flat tubes.
  • the connection tube depth VT can also be smaller or larger.
  • the air flow is indicated by an arrow 60, which flows around first the flow channel row 12 and then the flow channel row 13.
  • the emerging from the flow channel row 13 coolant is indicated in Figure 12 by arrows 65 and 66. This coolant is, as indicated by an arrow 67, supplied to the connecting pipe 17.
  • the emerging from the connecting pipe 17 coolant is indicated by the arrow 51 in Figure 13.
  • the coolant is no longer deflected in the conventional sense.
  • at least two fluidically separated flow channels in the depth that is, in Luftumströmungscardi, arranged one behind the other.
  • the flow channels may consist of separate tubes or of a single tube having separate channels.
  • a single flat tube is used which has two separate flow channels. While a flow channel row is flowed through in one direction over the entire width of the heat exchanger, the coolant flows in the opposite direction in the other flow channel row. However, the coolant is not deflected in the conventional sense in the depth.
  • the entry states of the coolant into the respective flow channel row are approximately the same in the heat exchanger according to the invention.
  • This is realized by the outside in the previous embodiment connecting pipes.
  • the one connecting pipe is used to transport the coolant to the opposite side of the connection side with the connecting piece.
  • the other connecting pipe is used for the return transport of the medium after the exit from the first flow channel row back to the coolant connection collecting box.
  • the volume flow is divided in the collection boxes by the two double-L-shaped partitions.
  • the Solution according to the invention provides the advantage that the internal pressure drop of the heat exchanger is very low.
  • the inlet temperatures of the coolant, which are similar on both sides of the channel rows, result in a very homogenous air outlet temperature profile.
  • the heat exchanger according to the invention is also referred to as a pure Kreuzströmer.
  • the one collecting box is provided with two connecting pieces and is therefore also referred to as a terminal collecting box.
  • the other collection box contains no connecting pieces.
  • FIGS. 14 and 15 show a further exemplary embodiment of a heat exchanger 71 in various views.
  • the heat exchanger 71 comprises a connection box with two inlet connecting pieces 72 and 73 and an outlet connecting piece 74.
  • the heat exchanger 71 is equipped with three connecting pipes 75 to 77.
  • the two connecting pipes 75 and 77 are arranged outside.
  • the connecting tube 76 is located in the middle. Between the two connecting tubes 75 and 76 two flow channel rows 81 and 82 are arranged. Between the two connecting pipes 76 and 77 two further flow channel rows 83 and 84 are arranged.
  • the connecting region of the two flow channel rows 81 and 82 is, as in the previous embodiment, divided by a double-L-shaped partition 85.
  • the mouth region of the flow channel rows 83 and 84 is divided by a likewise double-L-shaped partition wall 88.
  • the associated collection boxes are not shown in Figures 16 and 17 for reasons of clarity.
  • the mouth regions of the flow channel rows 81, 82 and 83, 84 shown in FIG. 17 are subdivided in the same way by double L-shaped partitions 89 and 90.
  • FIGS. 16 and 17 the flow characteristics of the air and of the coolant in the heat exchanger 71 from FIGS. 14 and 15 are indicated by arrows.
  • an arrow 91 the entering through the inlet connection piece 74 coolant is indicated.
  • This coolant is distributed to the two flow channel rows 82 and 84, as indicated by arrows 92 and 93.
  • the coolant emerging from the two flow channel rows 82 and 84, as indicated by arrows 95 and 96 in FIG. 16, is returned via the connecting pipes 75 and 77.
  • FIG. 17 it can be seen that a part of the coolant flow 91 entering through the inlet of the connecting piece 74 is also guided through the connecting tube 76 arranged in the middle, as indicated by an arrow 94.
  • FIG. 17 it can be seen that a part of the coolant flow 91 entering through the inlet of the connecting piece 74 is also guided through the connecting tube 76 arranged in the middle, as indicated by an arrow 94.
  • the coolant emerging from the connecting tube 76 is supplied to the two flow channel rows 81 and 83, as indicated by arrows 97 and 98.
  • FIG. 17 it can be seen that the coolant 97 emerging from the flow channel row 81 exits through the outlet connecting piece 72, as indicated by an arrow 99.
  • the coolant 98 emerging from the flow channel row 83 exits through the outlet connecting piece 73, as indicated by an arrow 100.
  • the heat exchanger 71 is equipped with a left / right separation. In this case, thermodynamically considered, two funnelströmer arranged one behind the other. The two funnelströmer are connected in parallel, whereby the inlet temperatures are approximately equal.
  • FIG. 18 shows the same view as in FIG.
  • FIG. 19 shows the view of a section along the line IXX-IXX in FIG.
  • the air flow is indicated in Figure 19 by an arrow 103.
  • FIG. 20 shows a representation similar to that shown in FIG. 19, the air flow being indicated by two arrows 104 and 105.
  • the flat tubes of the heat exchanger are divided in the middle and open into a deflection box 110.
  • the coolant is deflected halfway, and against the Beer josströmungscardi 104, 105.
  • arrows 111 and 112 it is indicated that the coolant initially through a row of flow channels flows and is then deflected in the deflection box 110, as indicated by an arrow 113.
  • the diverted coolant is returned through another row of flow channels in the opposite direction, as indicated by an arrow 114.
  • the coolant supplied through a connecting pipe to the collecting tank 21 is supplied to a further flow channel row, as indicated by an arrow 115.
  • This coolant flow is also deflected into the deflection box 110, as indicated by an arrow 116.
  • the deflected coolant flows back into the collecting box 21, from where it is fed back to the collecting box 22 via a connecting pipe.
  • a arranged in the collection box 21 partition 108 is just like the partition 27 in the collection box 22 double-L-shaped, however, mirrored. This ensures that even in the lower region of the heat exchanger a cross countercurrent is realized.
  • the connecting pipes are interconnected and connected in the same way as in the previous embodiments. However, one connecting tube serves as an inlet for the second, lower cross countercurrent. The other connecting pipe serves as a return.
  • FIGS. 21 to 24 show a similar heat exchanger 121 as in FIG. 20 in different views.
  • the heat exchanger 121 is equipped with three terminals.
  • the heat exchanger 121 comprises an upper header 122 and a lower header 123.
  • the air flow around the heat exchanger 121 is indicated by arrows 124 and 125.
  • By arrows 126 to 129 it is indicated that the coolant in the upper half of the heat exchanger 121 is deflected in a deflection box 133.
  • arrows 130 to 132 it is indicated that the coolant in the lower half of the heat exchanger 121 is also deflected in the deflection box 131.
  • FIGS. 22 to 24 show that the heat exchanger 121 comprises two flow channel rows 138, 139 in the upper half and two further flow channel rows 148, 149 in the lower half.
  • the upper collection box 122 is connected via connecting pipes 141 and 142 with the deflection box 133 in connection.
  • the lower collecting tank 123 is also connected to the deflection box 133 via further connecting pipes 161 and 162.
  • FIG. 24 it can be seen that the heat exchanger 121 has an inlet connecting piece 144, which is also referred to as an inlet.
  • the heat exchanger 121 has two outlet connection pieces 145 and 146, which are also referred to as return lines.
  • the upper collecting box 122 is connected to the deflecting box 133 via the flow channel rows 138 and 139.
  • the lower collection box 123 communicates with the deflection box 133 via the flow channel rows 148 and 149.
  • the lower header 123 is provided with a double L-shaped partition 151.
  • the partition wall 151 comprises a rectangular wall section 152, from which two further wall sections 153 and 154 are angled in opposite directions.
  • the upper header 122 is provided with a partition 155 which is T-shaped at one end and L-shaped at the other end.
  • a partition 155 which is T-shaped at one end and L-shaped at the other end.
  • two also rectangular wall sections 157 and 158 are angled at right angles.
  • a wall portion 159 is angled.
  • the air flow and the coolant flow of the heat exchanger 121 are indicated in FIGS. 23 and 24 by arrows.
  • FIGS. 25 to 27 show a further exemplary embodiment of a heat exchanger 181 in various views.
  • the heat exchanger 181 comprises, in contrast to the previous embodiment, two inlets 184 and 185 and a return 186.
  • the lower header is, as in the previous embodiment, equipped with a double-L-shaped partition 151.
  • the upper header box is provided with a partition wall 196 having a rectangular wall portion 197.
  • two partition wall portions 199 and 200 are angled in opposite directions. From the other end of the partition wall portion 197, only a wall portion 198 is angled.
  • the air flow and the coolant flow of the heat exchanger 181 are indicated by arrows in FIGS. 26 and 27.
  • the heat exchanger according to the invention provides inter alia the advantage of a lower internal pressure drop, since there is no diversion from one channel to another channel.
  • the mass flow of the coolant is divided into two channel halves. This allows a very homogeneous air outlet temperature profile can be achieved. This is partly due to the fact that the inlet temperature of the coolant in the two sewer pipe halves is approximately equal. A small temperature drop can occur in the connecting pipe.
  • the principle of the invention works regardless of the number, the width and the length of the tubes. Thus, both long and narrow heat exchanger with compact external dimensions can be displayed.
  • the production of the heat exchanger is only slightly influenced.
  • the outer connecting pipes can be easily used.
  • the heat exchanger according to the invention can also be flowed around by a coolant or refrigerant instead of air, for example. Both double crossflow and cross counterflow can be realized.
  • the flow channels 12, 13, 81, 82 to 84, 138, 139, 148, 149, in particular the tubes can be arranged one behind the other in such a way that the rows, in particular the rows of tubes, lie in series one behind the other or are arranged.
  • the flow channels 12, 13, 81, 82 to 84, 138, 139, 148, 149, in particular the tubes can be arranged one behind the other in such a way that the rows, in particular rows of tubes, are arranged or arranged behind one another are.

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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)
EP20070001137 2006-01-19 2007-01-19 Echangeur de chaleur Withdrawn EP1811260A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006002855 2006-01-19

Publications (1)

Publication Number Publication Date
EP1811260A2 true EP1811260A2 (fr) 2007-07-25

Family

ID=37944121

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070001137 Withdrawn EP1811260A2 (fr) 2006-01-19 2007-01-19 Echangeur de chaleur

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Country Link
EP (1) EP1811260A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2219003A2 (fr) 2009-02-13 2010-08-18 Honda Motor Co., Ltd. Échangeur thermique pour système de climatisation de véhicule
EP2317271A1 (fr) * 2009-10-30 2011-05-04 Delphi Technologies, Inc. Radiateur à débit en U doté d'un réservoir terminal avec un séparateur en forme de Z
WO2015010853A1 (fr) * 2013-07-25 2015-01-29 Jaeggi Hybridtechnologie Ag Tube collecteur pour dispositif échangeur de chaleur, dispositif échangeur de chaleur et procédé de purge d'un dispositif échangeur de chaleur

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2219003A2 (fr) 2009-02-13 2010-08-18 Honda Motor Co., Ltd. Échangeur thermique pour système de climatisation de véhicule
EP2219003A3 (fr) * 2009-02-13 2013-02-27 Honda Motor Co., Ltd. Échangeur thermique pour système de climatisation de véhicule
EP2317271A1 (fr) * 2009-10-30 2011-05-04 Delphi Technologies, Inc. Radiateur à débit en U doté d'un réservoir terminal avec un séparateur en forme de Z
WO2015010853A1 (fr) * 2013-07-25 2015-01-29 Jaeggi Hybridtechnologie Ag Tube collecteur pour dispositif échangeur de chaleur, dispositif échangeur de chaleur et procédé de purge d'un dispositif échangeur de chaleur

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