EP1256772A2 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP1256772A2
EP1256772A2 EP02010387A EP02010387A EP1256772A2 EP 1256772 A2 EP1256772 A2 EP 1256772A2 EP 02010387 A EP02010387 A EP 02010387A EP 02010387 A EP02010387 A EP 02010387A EP 1256772 A2 EP1256772 A2 EP 1256772A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
beads
exchanger according
sheets
sheet
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Withdrawn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
EP02010387A
Other languages
German (de)
English (en)
Other versions
EP1256772A3 (fr
Inventor
Gottfried Dipl.-Ing. Dürr
Peter Dr. Geskes
Michael Kohl
Andreas Dipl.-Ing. Leister
Kurt Dr.-Ing. Molt
Emil Neumann
Franz Ott
Christian Dipl.-Ing. Rebinger
Wolfgang Seewald
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
Priority claimed from DE20114850U external-priority patent/DE20114850U1/de
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1256772A2 publication Critical patent/EP1256772A2/fr
Publication of EP1256772A3 publication Critical patent/EP1256772A3/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Withdrawn legal-status Critical Current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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element

Definitions

  • the invention relates to a heat exchanger in the preamble of claim 1 specified genus.
  • a heat exchanger is known from EP 0 935 115 A2 consists of heat-conducting plates, which are put together in pairs are, and a variety of outward-looking Have ribs. More heat conductive within a pair Plates are passages for a coolant. Outside the plates flow perpendicular to the direction of flow of the Coolant air. The ribs prevent the air from Plates passed straight and create a turbulent Flow.
  • a disk heat exchanger is described in DE 43 08 858 A1, whose discs consist of two identical sheets. These sheets have a sheet level on both sides frustoconical shapes, the top of which a corresponding surface of the next sheet is applied. In this way, one between the sheets Disc and between adjacent discs flow channels formed for the fluids involved in the heat exchange.
  • the invention has for its object a heat exchanger of the generic type to create the simple Construction and cost-effective manufacture an improved Offers heat transfer.
  • the beads have different lengths in one sheet.
  • the beads can for example a width of 1 mm to 4 mm and a Have a length of 3 mm to 50 mm.
  • Adjacent slices are in particular at points of intersection between themselves elongated ridges soldered together, whereby the stability of the evaporator is increased.
  • the beads have different heights over their length, crossing beads especially in Areas of high height are soldered. Appropriately point the beads two heights, the ratio of the low Height to great height is from 0.2 to 0.8.
  • a course of the beads at an angle becomes favorable of approx. 30 ° in relation to the flow direction of the outer one Viewed fluids.
  • the knobs are useful an oval base with a width of 1.5 mm to 4 mm and a length of about 2.5 mm to 25 mm. Through this configuration the knobs result in a favorable flow guidance for the inner fluid.
  • the oval design of the knobs causes a high stiffness of the sheets and thus the entire heat exchanger.
  • a disc forming sheets on contact surfaces between those touching Knobs are formed, soldered together. This results in a fluidically favorable fixed connection.
  • the enlarged free flow cross section leads to a Reduction of pressure loss in the internal fluid. It can be expedient that the directed towards the inside of the pane Elevations of the sheets are formed as beads. In particular, sheets forming a disc are at contact points soldered between crossed beads.
  • the sheets have a wall thickness of 0.25 mm in particular up to 0.40 mm, a width of 35 mm to 70 mm and a length from 200 mm to 270 mm.
  • Two parallel channels are expediently formed in one disk, the one arranged on the sheets on the long sides Edge bars and one lengthways in the middle arranged central web are limited, the webs on the inside of the pane protrude and webs inside and on Edge of the disks are soldered together.
  • the canals have in particular a width of 7.5 mm to 40 mm. Especially when inclined to the longitudinal direction of the disc A good condensate drainage is achieved by arranging the beads.
  • the increases are expedient in an area on the Sheet in one after a longitudinal section of the sheet repeating patterns arranged on the sheet. hereby a uniform flow profile is achieved. expedient the length of the longitudinal section is 10 mm to 35 mm. In particular are in the longitudinal direction in each longitudinal section Sheet metal two elevations directed towards the inside of the pane trained, which ensures high stability of the heat exchanger is achieved.
  • each longitudinal section in each channel two elevations directed towards the outside of the pane are formed, in particular in the longitudinal direction of the Disc are offset from each other, the amount being around the increases are offset against each other, expedient corresponds to the longitudinal division.
  • the length of the Beads should be larger than the longitudinal division.
  • the ratio of the transverse division which is the total height of a Disk referred to the entrance gap width that the Width of the gap through which the external fluid passes between two can flow into adjacent panes on the outside, designated, 4: 3 to 4: 1. Due to the relatively small Entry gap width is a high heat transfer to the external fluid reached.
  • Passages are expedient at at least one end of the channels formed a longitudinal collection channel form the heat exchanger.
  • the passages are formed so that with two channels four collecting channels are formed.
  • the inflow knobs expediently have the inside of the pane.
  • For inlet and outlet of the interior Fluids are intended to be on the same side of the heat exchanger are arranged. This results in cheap Conditions when installing the heat exchanger. expedient the increases are made by deep drawing. It However, it can be advantageous that the increases by Embossing are made.
  • a heat exchanger 1 is shown, which is preferably trained as a disc evaporator and part of a Air conditioning system of a motor vehicle, not described in more detail here is.
  • the disk evaporator 1 has a variety of Disks 4, which are stacked together to form a block 10 are and each made of two sheet metal elements joined together 2 exist.
  • the discs 4 form under influence a cavity pipe elements for the passage of a refrigerant out.
  • the disks 4 are elongated and fluidly connected to one another such that the Refrigerant in the direction of arrow 21 the disk evaporator 1 flows through. Around the flow path represented by arrows 21 can be reached between certain panes 4 Partitions 19 arranged.
  • the disks 4 are in each case on the the plates 4 forming sheet metal elements 2 a connecting piece 6 formed, which with the connecting piece 6 ' adjacent disc 4 is connected.
  • the Disks 4 are each in overlap in the Disc block 10, in addition to the ribs 33 a variety of spaces for the passage of air to be cooled in Direction of depth of the evaporator block are formed.
  • the The depth direction is the direction perpendicular to Leaf level of the drawing is, that is, the extension of the evaporator block in the direction perpendicular to it Front side.
  • the sheet metal elements 2 are shaped such that they face the outside projecting cooling webs 33 in the form of ribs. These cooling webs 33 are in contact with the mirror image arranged cooling bars of the neighboring Washer 4 and are soldered to them. By soldering there is not only an increase in the surface of the Discs, but also a higher strength of the disc evaporator 1. In addition to those facing outwards Expressions of the sheet metal elements 2 are also directed inwards Knobs 26 provided.
  • Fig. 2 shows a sheet metal element 2, which consists of a variety of basic elements 34, which are connected by webs 14, 15.
  • 34 creates a depression 25, which after joining the sheet metal elements the flow channel for the refrigerant forms. From the level of the depression 25 rise in one Towards cooling webs 33 and in the other direction Knobs 26.
  • the cooling webs 33 are in the embodiment of the 2 as inclined to the longitudinal direction of the base element 34 extending ribs formed.
  • the sheet metal elements 2 When assembling the disc evaporator, the sheet metal elements 2, from one of the desired depth of the evaporator block corresponding number of basic elements 34 exist, in the area of their edges 53 closely joined together including the cavity to direct the Refrigerant.
  • the discs can be used as disc modules variable depth, each running several Include basic elements 34.
  • the sheet metal element 2 becomes corresponding their length of the semi-finished product with a variety of Basic elements 34 are produced, for example, by stamping.
  • the basic elements 34 hang in one piece by means of the webs 14, 15 together, the webs 14, 15 preferably adjacent Ends 8, 9 of the elongated base elements 34 are provided are.
  • Fig. 3 shows a heat exchanger 1, which is a disk pack 16 comprises, which is constructed from sheets 22. Two each identical sheets 22 are against each other by 180 ° Longitudinal axis rotated together to form a disc 4, as can be seen from FIG. 5.
  • One disc 4 Forming sheets 22 can also be different Have structure, in particular two can be mirror images trained sheets assembled into a disc his.
  • the sheets 22 have arranged in the longitudinal direction Each ends two swaths 18 in the Width of the sheets 22 are arranged side by side, and the form a total of four collecting channels 17. Each collecting channel 17 extends in the width B of the heat exchanger 1.
  • Each Disk 4 comprises a cavity containing two channels, through a central web 13 and two edge webs 12 and are limited by the inner sides of the sheets 22.
  • the channels extend in the longitudinal direction of the disks 4, d. H. towards the height H of the heat exchanger 1. Inside the disks 4 the inner fluid flows in the channels, for example a refrigerant.
  • the external fluid flows perpendicular to the direction of flow of the internal fluid in the direction indicated by arrow 3.
  • On the sheets 22 are on the inside of the pane directed knobs 26 and directed towards the outside of the disc beads 33 'arranged as cooling webs.
  • the Disk package 16 is constructed from stacked disks 4. On the sides facing the inside of the pane the sheets 22, which form a disc 4, on the touching Knobs 26, the central web 13 and the edge webs 12 soldered together.
  • the individual disks 4 are on the points of contact of the beads 33 'and the passages 18 with one another soldered.
  • the passages 18 touch one another Annular surface 49 (Fig. 4), which is a good contact surface for represents the soldering.
  • the knobs 26 and the beads 33 ' are advantageously produced by deep drawing or embossing.
  • the webs 12, 13, which are formed by the beads 33 ', are advantageous. and knobs 26 formed bumps and the passages 18 in a tool.
  • the disk package 16 is on one side in the direction of Width B of the heat exchanger 1 delimited by an end plate 56, which is made of sheet metal, and the one Has inlet 11 and an outlet 5 for the internal fluid.
  • the inlet 11 and the outlet 5 are designed as pipe connections, the outlet 5 having a larger diameter has as the inlet 11.
  • the disk pack 16 is removed from the end disk 57 limited, which is also formed from a sheet is, and the via a connecting plate 48 to the disk package 16 is connected.
  • the connecting disk 48 has two openings that match the openings of the bottom two Collection channels 17 correspond and congruent with these are arranged.
  • the end plate 57 has a deflection channel 20 on which is a fluidic connection between the two connected to him collecting channels 17.
  • the diversion channel 20 can also be designed as a tube, for example his.
  • the beads 33 ' are transverse arranged to the longitudinal direction of the sheets 22.
  • the beads 33 ' are inclined to the longitudinal axis by an angle, which is advantageous can be between about 20 ° and 30 °. However, there are deviating angles of inclination are also possible.
  • the length of the longitudinal section L is, for example, 17.5 mm.
  • knobs 26 are arranged on the side of the Sheets 22 on which the inner fluid in the arrow 21 flows in the direction indicated.
  • the knobs 26 are essentially in the embodiment oval in shape and conveniently have a length of 3 mm to 7 mm, in particular of 4.6 mm, and a width of 2 mm to 4 mm, in particular 2.7 mm.
  • In the longitudinal direction of the Sheets 22 are in a longitudinal section L on each sheet 22 on each channel two knobs 26 and at a distance in the longitudinal direction, which is about half the length of the longitudinal section L corresponds to a knob 26 arranged.
  • two inflow knobs 54 arranged on the inside of the pane, which has a larger base area than the knobs 26 to have.
  • the bead 33 'adjacent to the inflow knobs 54' is shortened due to lack of space.
  • the edge webs 12 follow the contour of the passages in the area of the passages 18 18 and merge into this in the area of the central web 13, so that when joining the inside of adjacent sheets 22, which form a disc 4, each channel upwards and is closed down and the inner fluid only through the passages 18 forming the collecting channel 17 from the or can flow into or out of the channel.
  • Fig. 5 illustrates the position of the beads 33 ', 33' ' and knobs 26, 54 formed increases in the direction of Width B of the heat exchanger 1.
  • the beads 33 'adjacent Discs 4 intersect at the three contact points 27 each bead 33 '.
  • the beads are at the contact points 27 33 'soldered together.
  • the knobs 26 are between the Beads 33 'arranged on the opposite side of a sheet 22, with knobs 26 of adjacent sheets 22, one Form disc 4, touch surface at contact surfaces 28 and are soldered together.
  • knobs 26 are only touch point.
  • the beads 33 'it can make sense be that they touch each other.
  • the edge webs 12 and the middle webs 13 of two sheets forming a disk 4 22 touch and are soldered together, the Width of the contact surface is designed so that a good Soldering is achieved.
  • a disc 4 has a height which corresponds to the transverse division S Q.
  • the inlet gap width S, through which the external fluid can flow between two disks 4, is a quarter to three quarters, in particular approximately a third, of the transverse division S Q.
  • the arrow 3, which indicates the direction of flow of the external fluid through the disk pack 16, illustrates the deflection of the external fluid through the beads 33 ′ in the direction of the width B of the heat exchanger 1.
  • the 7 is the flow direction 21 of the inner fluid represented by the heat exchanger 1 shown in FIG. 3.
  • the internal fluid flows through inlet 11 into one Section of the collecting duct 17 in the downstream of the flow direction of the outer fluid arranged channel row 23.
  • the inlet 11 and the outlet 5 open into upper collecting channels 17a, and the one on the opposite Collection channels arranged on the side of the channels are lower collection channels 17b.
  • the four collecting channels 17a, 17b are through one partition 19 each divided into two sections.
  • the internal fluid flows from the first section of the upper collecting channel 17a in channels of the channel row 23 in a section of the lower collecting duct 17b, from there in one fluidically separated from the inlet 11 by a partition 19 Section of the upper collecting duct 17a and through further channels of the channel row 23 in a further section of the lower collecting duct 17b of the duct row 23.
  • the fluid from the channel row 23 into the channel row 24, which is upstream of the direction of flow of the outer fluid is arranged, deflected and flows in this in the opposite flow direction to the channel row 23 to the outlet 5, where it exits the heat exchanger 1.
  • There can be more than one partition in a collecting duct 17 19 may be provided.
  • the partition 19 can be a separate one Component be executed. However, it can also be used in one Sheet 22 can be integrated, for example, instead of the passage 18 arranged only an increase as a solder joint is.
  • FIG. 8 and 9 show a further arrangement of the beads 33 'and the knob 26 on a disc 4.
  • two knobs 26 are arranged between two Beads 33 'which are inclined to the longitudinal axis of the sheet 22, two knobs 26 are arranged.
  • disk 4 shown touch the beads 33 ' four contact points 29 on each bead 33 '.
  • the beads 33 ' have approximately the longitudinal direction of the disks 4 one and a half times the length of the longitudinal section L.
  • the pimples 26 are each in one through the beads 33 'two Adjacent panes 4 formed space arranged.
  • the Nubs 26 touch surface at contact points 30 and are soldered together.
  • the central web 13 has widenings 31 on and the edge webs 12 widenings 32.
  • the widenings 31 and 32 correspond approximately in the longitudinal direction disc 4 halved knobs 26.
  • the widenings 31, 32 lead to increased stability of the Disc 4.
  • 10 and 11 is a further arrangement of the ridges shown on a sheet 51.
  • the beads 33 'point in the longitudinal direction of the sheet 51 to a length of about three quarters corresponds to the length of the longitudinal section L.
  • the Knobs 26 correspond to knobs 26 in FIGS. 8 and 9 arranged.
  • sheet 51 becomes a bead 33 'of row 35' by a Bead 33 'of row 35 of an adjacent one on the outside of the pane Blechs 51 continued.
  • the beads 33 'of the rows 35 'and 35 each have two contact points 36 to beads 33 'adjacent discs 4.
  • the knobs 26 have contact surfaces 37 within a disc 4. Training the beads 33 'in two rows 35 and 3' leads to one greater deflection of the external fluid in the direction of the Width B of the heat exchanger 1.
  • FIGS of a sheet 41 shown Another embodiment variant is shown in FIGS of a sheet 41 shown.
  • the one on the inside Raised protrusions formed from two sheets 41 are formed as beads 44.
  • the on the outside of the Disk-projecting beads 45 are partially small Height a and a large height b in a central area (Fig. 14).
  • the ratio of the low height a to the large one Height b is in particular 0.2 to 0.8.
  • the beads 44 and 45 are on each channel in two rows 42, 43 arranged, the beads 44, 45 in a row 42 in opposite direction, but by the same angular amount are inclined to the longitudinal direction, like the beads in a row 43.
  • Fig. 13 is a sheet 41 with the outward Beading 45 of an adjacent plate 41 is shown. This arrangement results from the assembly two identical to each other by 180 ° around the longitudinal axis twisted sheets.
  • the beads 45 of adjacent sheets 41 are soldered at contact points 46 and the beads 44 at touch points 47.
  • a sheet 50 is shown, which is also for find the heat exchanger 1 shown in Fig. 3 use could.
  • This sheet 50 has at the longitudinal ends Passages 18 on the collection channels in the assembled stack 17 form.
  • the edge webs 12 Along the edge of the sheet 50 extend the edge webs 12 and along the longitudinal median plane extends the middle web 13.
  • the beads 52, 52 'in one direction are formed out of the sheet level and into the opposite The knobs 55 extend in the direction. How 15 can be seen, the beads 52 have a Length that is such that this is about half the distance between the central web 13 and the edge web 12 corresponds.
  • FIG. 16 An embodiment variant of the sheet 50 is shown in FIG. 16, the base of the sheet metal element 50 with that 15 matches. But it is different Arrangement of beads 58 and 58 ', each with respect to their Longitudinal direction at an angle ⁇ to the flow direction run according to arrow 3, whereby as shown in FIG. 17 the beads 58 obliquely upwards and the beads 58 'obliquely are downward.
  • Adjacent to the edge webs 12 and the Center web 13 are arranged in a V-shape, relatively short Beads 60 provided. Between the different beads 58, 58 ', 59 and 60 are from the sheet metal level to the other Knobs 55 on the side.
  • FIGS. 18 and 19 show further embodiment variants of a Sheet 50, only in FIGS. 18 and 19 a middle section of the extending in length Sheet 50 is shown.
  • beads 61, 62 and 63 are provided, which are different Have length, with relatively longer beads 61, medium beads 62 and relatively short beads 63 with different Angle to the direction of flow according to arrow 3 are arranged.
  • the density of the Beads 61, 62, 63 in Fig. 19 is significantly larger than in Fig. 18, whereby not only the heat transfer surface enlarged, but also, but only to a limited extent Dimensions that the air-side pressure drop is affected. How 19 also becomes clear from there are certain Place adjacent to the edge webs 12 and the central web 13 crossed beads 64 arranged.
  • Get lost the beads preferably at an angle of about 30 ° to Flow direction of that passing between the disks Fluids, which is particularly favorable in terms of flow technology. It has been shown that by choosing the bead height and said angle does not deflect the air in Longitudinal direction of the discs takes place, so that no noticeable Extension of the flow path between the disks occurs. If the external pressure drop is reduced and the Flow distribution over the disc height even should be, it is appropriate to count the number on the To minimize outside crossing ribs, being of course, sufficient strength and solderability to watch out for. By minimizing the soldering menisci unfavorable speed peaks of the Current in the area of the solder menisci and dead areas in the Avoided flow distribution.
  • the beads have also proven to be particularly useful rather shorter in length and opposite to move successive beads in each case.
  • beads of different lengths to arrange in a given pattern such as this 18 and 19 is shown.
  • the height of the beads should be a maximum of half one Entry gap width between two adjacent panes be.
  • the knobs 26 on the inside have one oval shape with a width of approx. 1.5 mm and a length 2.5 mm.
  • FIGS. 15 and 16 are suitable especially for panes of a disk evaporator, at which the disc has a minimum width of 20 mm and a Has a minimum length of 100 mm.
  • the length of a longitudinal section, within which are the inner and outer Repeated structure of surveys is at least 10 mm.
  • FIG. 20 shows a diagram in which the air-side pressure drop ⁇ p and the heat transfer capacity Q related to various embodiments of the above-mentioned embodiments is registered. It can be seen that with almost constant heat transfer performance Q the air-side pressure drop ⁇ p depending on the embodiment can be significantly different.
  • there the information in level I stands for the exemplary embodiments 8 to 11 compared to the significantly lower Pressure drop in level II for FIGS. 12 to 14 and the even further reduced pressure drop in level III 15 to 19.
  • the air-side pressure drop .DELTA.p and the heat transfer capacity Q are again given in percent and indicated over the transverse division S Q or air gap width S. It can be seen from this that the air-side pressure drop depends essentially on the air gap width and a satisfactory heat transfer performance and an acceptable pressure drop can only be recorded in the range between 1/3 and 2/3 of the transverse division S Q or the gap width S.

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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)
EP02010387A 2001-05-11 2002-05-08 Echangeur de chaleur Withdrawn EP1256772A3 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10122925 2001-05-11
DE10122925 2001-05-11
DE20114850U DE20114850U1 (de) 2001-09-07 2001-09-07 Wärmetauscher
DE20114850U 2001-09-07

Publications (2)

Publication Number Publication Date
EP1256772A2 true EP1256772A2 (fr) 2002-11-13
EP1256772A3 EP1256772A3 (fr) 2005-02-09

Family

ID=26009271

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02010387A Withdrawn EP1256772A3 (fr) 2001-05-11 2002-05-08 Echangeur de chaleur

Country Status (3)

Country Link
US (1) US6938685B2 (fr)
EP (1) EP1256772A3 (fr)
DE (1) DE10220532A1 (fr)

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DE102012217333A1 (de) * 2012-09-25 2014-03-27 Behr Gmbh & Co. Kg Flachrohr
EP1682842B1 (fr) * 2003-10-28 2014-06-04 Behr GmbH & Co. KG Canal d'ecoulement pour dispositif de transfert de chaleur et dispositif de transfert de chaleur comprenant de tels canaux d'ecoulement

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ATE450768T1 (de) * 2004-11-30 2009-12-15 Valeo Systemes Thermiques Sas Wärmetauscher mit wärmespeicherung
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US9127895B2 (en) * 2006-01-23 2015-09-08 MAHLE Behr GmbH & Co. KG Heat exchanger
CN101375048B (zh) 2006-01-23 2011-06-15 贝洱两合公司 热交换器
ITVR20060154A1 (it) * 2006-10-06 2008-04-07 Gianfranco Natali Procedimento per la realizzazione di tubi di scambiatori di calore e tubi di scambiatori di calore
KR20100106434A (ko) * 2008-01-10 2010-10-01 베헤르 게엠베하 운트 콤파니 카게 열교환기용 압출 튜브
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ATE554361T1 (de) * 2009-04-28 2012-05-15 Abb Research Ltd Wärmerohr mit gewundenem rohr
EP2246654B1 (fr) * 2009-04-29 2013-12-11 ABB Research Ltd. Échangeur thermique à thermosiphon à rangs multiples
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US20110277974A1 (en) * 2009-09-30 2011-11-17 Carrier Corporation Condensing Heat Exchanger for Gas Furnaces
DE102012202515A1 (de) * 2012-02-17 2013-08-22 Behr Gmbh & Co. Kg Fahrzeug-Klimatisierungssystem mit Fluidkreislauf
DE102012013755B8 (de) 2012-07-12 2022-01-13 Al-Ko Therm Gmbh Wärmetauscherplatteneinheit, Wärmetauscher und Verfahren zur Herstellung eines Wärmetauschers
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DE10220532A1 (de) 2002-11-14
US6938685B2 (en) 2005-09-06
US20020195239A1 (en) 2002-12-26
EP1256772A3 (fr) 2005-02-09

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