WO2016146294A1 - Échangeur de chaleur, en particulier pour un véhicule à moteur - Google Patents

Échangeur de chaleur, en particulier pour un véhicule à moteur Download PDF

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Publication number
WO2016146294A1
WO2016146294A1 PCT/EP2016/051930 EP2016051930W WO2016146294A1 WO 2016146294 A1 WO2016146294 A1 WO 2016146294A1 EP 2016051930 W EP2016051930 W EP 2016051930W WO 2016146294 A1 WO2016146294 A1 WO 2016146294A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
heat exchanger
exchanger according
flow direction
separating elements
Prior art date
Application number
PCT/EP2016/051930
Other languages
German (de)
English (en)
Inventor
Tobias Fetzer
Wilhelm Grauer
Boris Kerler
Marco Renz
Volker Velte
Original Assignee
Mahle International Gmbh
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 Mahle International Gmbh filed Critical Mahle International Gmbh
Publication of WO2016146294A1 publication Critical patent/WO2016146294A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • Heat exchanger in particular for a motor vehicle
  • the present invention relates to a heat exchanger, in particular for a waste heat utilization device, and a waste heat utilization device with such a heat exchanger.
  • heat exchangers are used, for example, in motor vehicles to cool the fresh air charged by means of an exhaust-gas turbocharger in a fresh-air system interacting with the internal combustion engine of the motor vehicle.
  • the fresh air to be cooled ie a gas
  • the heat exchanger is introduced into the heat exchanger, where it thermally interacts with a fluid in the form of a likewise introduced into the heat exchanger coolant and emits heat in this way to the coolant.
  • charge air cooler heat exchangers
  • heat exchangers can also be used to cool a liquid coolant by means of a gas.
  • coolant coolers Such heat exchangers are referred to as coolant coolers.
  • Such a heat exchanger may for example be designed as a plate heat exchanger and having a plurality of tubular bodies, which are typically stacked in a stacking direction, wherein between the plates of a tubular body, a coolant path is formed through which the coolant is passed.
  • the medium to be cooled such as the fresh air charged in an exhaust gas turbocharger
  • rib structures can additionally be provided between adjacent tubular bodies which increase the interaction area of the tubular bodies available for the thermal interaction.
  • the basic idea of the invention is accordingly to realize the heat exchanger in countercurrent principle, such that a gas flow direction for the gas guided through the heat exchanger substantially opposite, that is, at a 180 ° angle, to a fluid flow direction of the guided through the heat exchanger fluid ,
  • gas flow direction is understood here to mean the direction along which the gas flows through the heat exchanger while it undergoes thermal interaction with the fluid.
  • part of the gas flowing through the heat exchanger also flows in one direction in sections This may be the case, for example, when flow vortices are formed in the gas flow, ie the gas flow direction is a main flow direction of the gas flowing through the heat exchanger, which can vary locally mutatis mutandis for the fluid flowing through the heat exchanger and its fluid flow direction a realized as a charge air cooler heat exchanger as well as in a realized as a coolant radiator heat exchanger.
  • a heat exchanger comprises a plurality of flow paths for flowing through with a fluid.
  • Each fluid path is at least partially bounded by a tubular body.
  • the tubular bodies each extend along a tubular body extension direction and are stacked along a stacking direction.
  • at least two separating elements are arranged, which subdivide the relevant fluid path into a corresponding number of fluid channels. If two separating elements are present, three fluid channels are formed, with three separating elements, four fluid channels are formed, etc.
  • the fluid channels extend along the fluid flow direction already explained.
  • a gap is formed in each case. Through each such space, a gas path for flowing with the gas along a gas flow direction is formed in each case.
  • the fluid flow direction must run opposite to the gas flow direction.
  • the separating elements which are arranged along the fluid flow direction, are arranged orthogonal to the tube body extension direction.
  • the gas flow direction is as desired opposite to the fluid flow direction of the fluid flowing through the fluid channels. This applies in particular to that region of the gas or fluid paths in which the thermal interaction between gas and fluid takes place.
  • the heat exchanger serves to cool the gas flowing through the gas paths by heat exchange with the fluid, or conversely to cool the fluid by means of the gas.
  • the countercurrent principle it is achieved that there is always a temperature gradient between gas and fluid. This ensures that heat exchange between the gas and the fluid takes place over the entire gas or fluid paths. As a result, this leads to an improved efficiency of the heat exchanger.
  • the spaces for introducing and discharging the gas are formed open at opposite ends of the heat exchanger along the fluid flow direction.
  • the gas flow direction thus extends between the two opposite openings opposite to the fluid flow direction.
  • each gap there is a fin structure in each gap forming a gas path.
  • this rib structure adjacent tubular body based in the stacking direction.
  • the individual separating elements are each formed longitudinally. That is, the respective separator has an element length measured along the fluid flow direction that is at least ten times a member width measured across the fluid flow direction. In this way, a multiplicity of fluid channels extending fluidically relative to one another can be realized in the fluid paths with a small space requirement.
  • the element length is less than at least twenty times the element width, more preferably at least fifty times.
  • no separating elements are provided in a first fluid path end section of at least one fluid path with respect to the fluid flow direction.
  • the first fluid path end section fluidly connects all the fluid channels separated by the separating elements.
  • no separating elements are present in a second fluid path end section opposite the first fluid path end section along the fluid throughflow direction. This means that the second fluid path end section fluidly connects all the fluid channels separated by the separating elements.
  • the heat exchanger has at least one fluid distributor which is fluidically connected to the first fluid path end section. This serves to distribute the introduced into the heat exchanger fluid to the plurality of fluid paths.
  • the heat exchanger has at least one fluid collector fluidly connected to the second fluid path end portion. The fluid collector is used to collect the fluid after flowing through the fluid paths before it is removed from the heat exchanger.
  • the tubular body extending parallel to a longitudinal side of the tubular body.
  • exactly one fluid distributor and exactly one fluid collector are present in the heat exchanger.
  • the fluid distributor and the fluid collector are arranged at longitudinal ends opposite one another in the tube body extension direction of the tube body.
  • the fluid is first distributed by the fluid distributor to the individual fluid paths.
  • the fluid is distributed from the first fluid path end section to the various fluid channels.
  • the fluid in each fluid path is collected in the second fluid path end portion and collected from the individual fluid paths in the common fluid collector.
  • the fluid enters the fluid paths in the region of the longitudinal end of the tubular body, on which the fluid distributor is arranged. Accordingly, the entire fluid in the region of the longitudinal end of the tubular body again emerges from the fluid paths on which the fluid collector is arranged.
  • heat exchanger is very simple, resulting in significant cost advantages in the production.
  • the tubular body also extend parallel to a longitudinal side of the tubular body.
  • the heat exchanger has two fluid distributor and two fluid collector.
  • a fluid distributor and a fluid collector separate from this are arranged at each of the two longitudinal ends of the tubular body.
  • the tube extension direction is perpendicular to both the stacking direction and the fluid flow direction.
  • Such a designed heat exchanger requires very little space.
  • a heat exchanger with the above-described features according to the invention - including the preceding optional features - can be produced in a particularly simple manner and with particularly low production costs in series production by using an additive manufacturing method.
  • additive manufacturing process encompasses all manufacturing processes which generate the component in layers directly from a computer model. Such production processes are also known by the name “rapid forming”.
  • the term “rapid forming” covers in particular production processes for fast and flexible production of components by means of tool-free production directly from CAD data. The use of an additive manufacturing process allows manufacturing in a simple and flexible manner.
  • the additive manufacturing process may include laser sintering.
  • a laser sintering process is used to manufacture the heat exchanger.
  • Such a laser sintering method is also known by the term "laser melting”.
  • laser melting By means of such a method, that of the directly from 3D CAD data can be produced.
  • the heat exchanger during laser sintering is manufactured without tools and in layers on the basis of the three-dimensional CAD model assigned to the heat exchanger.
  • the heat exchanger may be integrally formed.
  • Such a one-piece training is particularly evident when using the previous presented above, in particular the laser sintering.
  • a one-piece design of the heat exchanger eliminates the very costly and therefore costly attaching the individual components of the heat exchanger together. For example, eliminating the cohesive fastening of the individual tubular body to the rib structures as well as the cohesive fastening of fluid distributor and fluid collector to the tubular bodies.
  • the separating elements can be formed web-like and integrally formed on the respective, the first fluid channel limiting tubular body.
  • two adjacent partition members together with the tubular body for each fluid channel form a tubular body through which the fluid channel is confined.
  • the flow pattern of the fluid flowing through the fluid channels is to be selectively influenced, for example in order to increase the heat exchange with the gas with the aid of turbulent flows, then a non-linear design of the separating elements proves to be particularly advantageous.
  • Particularly expedient adjacent element sections in the cross section perpendicular to Stacking direction be arranged at an obtuse angle to each other.
  • the formation of separating elements with a straight-line or non-straight-line geometry can be realized particularly simply by means of the above-described additive manufacturing method.
  • the separating elements may be formed in the cross section perpendicular to the stacking direction at least partially curved. In this way, the flow of the fluid through the fluid channels can be optimized. It is understood that in the above-mentioned embodiments, the element portions for forming a respective separating element directly merge into each other and are integrally formed on each other. Also for the curved design of the separating elements, the additive manufacturing process is particularly suitable.
  • turbulence generating elements in the fluid channels. These serve to generate turbulence in the fluid flowing through the fluid channels.
  • a plurality of extensions projects from the separating elements for this purpose.
  • the extensions are in this case arranged on the respective separating element such that the extensions protrude into the fluid channel bounded by the respective separating element.
  • the additive manufacturing process is particularly suitable for the formation of the turbulence generating elements on the separating elements.
  • the extensions can each protrude substantially transversely from the separating element, on which they are formed.
  • the individual projections provided on a specific separating element substantially equidistant from each other.
  • the invention further relates to a waste heat utilization device with a previously presented heat exchanger.
  • each schematically 1 shows an example of a heat exchanger according to the invention in a perspective view
  • FIG. 4 shows a variant of the example of FIG. 3
  • Tubular bodies existing dividing elements.
  • FIG. 1 shows a perspective illustration of an example of a heat exchanger 1 according to the invention.
  • FIG. 2 shows an enlarged partial view of FIG. 1. Below it is assumed that this is used as intercooler. It is understood that the heat exchanger 1 can also be used as a coolant radiator.
  • the heat exchanger 1 comprises a plurality of fluid paths 2, through which a fluid (see arrows X in Figure 2) along a fluid flow direction F can flow.
  • Each fluid path 2 is bounded by a tubular body 3, wherein the tubular body 3 are stacked along a stacking direction S.
  • Each tube body 3 extends along a tube body extension direction E, which runs parallel to a longitudinal side 15 of the tube body 3 and orthogonal to the fluid flow direction.
  • the fluid flow direction F thus runs parallel to a transverse side 19 of the tubular body 3 (see Fig. 2).
  • the tube extension direction E also runs orthogonal to the stacking direction S.
  • the tube bodies 3 can be designed as flat tubes as shown in FIG. FIG. 3 shows by way of example a fluid path 2 in a cross section perpendicular to the stacking direction S and along the sectional plane III-III of FIG. 1. It can be seen that in the fluid path 2 forming the tubular body 3, a plurality of separating elements 4 is arranged, which divides the fluid path 2 into a plurality of fluidically separated fluid channels 5.
  • the fluid channels 5 extend along the already mentioned fluid flow direction F which is orthogonal to the stacking direction S.
  • FIG. 1 A gas path 7 is in each case formed through the intermediate spaces 6 for flowing through with a gas to be cooled by the fluid.
  • the gas paths 7 are realized in such a way that the gas (see arrows Y in FIG. 3) flows along the gas flow direction G through the gas paths 7.
  • a rib structure 14 may be provided.
  • the interspaces 6 for introducing and discharging the gas are designed to be open at opposite ends of the heat exchanger 1, along the direction of fluid flow F. Through these openings 20, the gas in the interstices 6 and 7 gas paths and be discharged again.
  • the gas flow direction G and the fluid flow direction F are opposite to each other for the realization of the invention countercurrent principle for the gas and the fluid.
  • the countercurrent principle it is achieved that there is always a temperature gradient between gas and fluid. This ensures that heat exchange takes place between the gas and the fluid over the entire gas or fluid paths 7, 2. This leads to a particularly high efficiency of the heat exchanger 1.
  • the individual separating elements 4 are each formed longitudinally. That is, the respective partition member 4 has an element length I measured along the fluid flow direction F, which is at least ten times a member width b measured transversely to the fluid flow direction F. In this way, a large number of fluid channels 5 running fluidically relative to one another can be arranged in each fluid path 2 with a small space requirement.
  • the element length I is at least twenty times the element width b, more preferably at least fifty times.
  • Each fluid path 2 has, in the fluid flow direction F, a first fluid path end section 8a and a second fluid path end section 8b opposite the first fluid path end section 8a.
  • the first fluid path end section 8a can fluidly connect all the fluid channels 5 separated by the separating elements 4.
  • the second fluid path end section 8b also fluidly connects all the fluid channels 5 separated by the separating elements 4.
  • Such a fluidic connection can be realized, for example, by designing a width b of the tubular body 3 running along the fluid flow direction F greater than the length I of the dividing elements 4. Then, the fluid entering the tubular body 3 can be applied to the individual fluid channels 5 as desired distributed and after flowing through the fluid channels 5 are again merged from these and collected.
  • the heat exchanger 1 may comprise a fluid distributor 9 that is fluidically connected to the first fluid path end section 8 a. This serves to distribute the fluid introduced into the fluid distributor 9 via a fluid inlet 1 1 onto the fluid channels 5 formed in the fluid paths 2.
  • the heat exchanger 1 has a fluid collector 10 that is fluidically connected to the second fluid path end section 8b. It serves to collect the fluid again after flowing through the fluid paths 2 or the fluid channels 5 and to discharge it from the heat exchanger 1 via a fluid outlet 12.
  • exactly one fluid distributor 9 and exactly one fluid collector 10 are provided in the heat exchanger 1.
  • the fluid distributor 9 and the fluid collector 10 are arranged on longitudinal ends 13 of the tubular bodies 3 opposite one another in the tubular body extension direction E of the tubular body 3.
  • the flow through the heat exchanger 1 with the fluid takes place as follows:
  • the fluid is introduced into the fluid distributor 9 via the fluid inlet 12 and distributed by the latter to the individual fluid paths 2 or tubular bodies 3.
  • the fluid is distributed from the first fluid path end section 8 a to the individual fluid channels 5 of the fluid path 3.
  • the fluid is collected in the respective second fluid path end section 8 b and collected from the individual fluid paths 2 in the common fluid collector 10.
  • the fluid thus enters in the region of one of the two longitudinal ends 13 of the tubular body 3 in the fluid paths 2, on which the fluid distributor 9 is arranged. Accordingly, the fluid exits in the region of the other longitudinal end 13 of the tubular body 3 again from the fluid paths 2, on which the fluid collector 10 is arranged.
  • FIG. 4 shows a variant of the heat exchanger of FIGS. 1 to 3.
  • FIG. 4 shows this variant in a representation analogous to FIG. 3, ie in a cross section perpendicular to the stacking direction S.
  • the heat exchanger 1 has two fluid distributors 9 and two fluid collector 10.
  • the tubular body 3 extend along the tubular body extension direction E, which is parallel to the longitudinal side 15 of the tubular body.
  • a fluid distributor 9 and a fluid collector 10 separate from the fluid are arranged at each of the two longitudinal ends 13 of the tubular body 3.
  • the fluid flows through the two fluid inlet 11 into the two fluid distributors 9 opposite one another in the tube body extension direction E and from there onto the respective first fluid path end sections 8a individual fluid paths 2 and tube body 3 distributed.
  • the fluid is distributed from the first fluid path end section 8 a to the individual fluid channels 5 of the respective fluid path 2.
  • the fluid After flowing through the fluid channels 5, the fluid is collected in the second fluid path end sections 8b of the fluid paths 2 or tube bodies 3 and flows from there into one of the two fluid collectors 10, which lie opposite each other in the tube body extension direction E. From the fluid collector 10, the fluid is discharged from the heat exchanger 1 via the respective fluid outlet 12.
  • a particularly uniform heat exchange can be achieved in the heat exchanger 1.
  • Separating elements 4 may be web-like.
  • the separating elements 4 are integrally formed on the respective, the fluid channel 5 limiting tubular body 3. If the formation of eddy currents etc. in the fluid flowing through the fluid channels 5 is to be avoided, a rectilinear design of the separating elements 4 along the fluid throughflow direction F is recommended.
  • FIG. 7 shows a further variant in which the separating elements 4 in the cross section of the heat exchanger 1 perpendicular to the stacking direction S have a wave-like geometry. That is, the respective partition member 4 is formed as shown in Figure 7 along the fluid flow direction F of the heat exchanger 1 and the tubular body 3 curved. In a simplified variant, such a curved formation of the separating elements 4 can also take place only in sections.
  • turbulence generating elements 17 in the fluid passages 5 proves to be advantageous.
  • These can, as shown in FIG. 8 for rectilinear dividing elements 4, be realized as extensions 18 which protrude laterally from the dividing elements 4.
  • the extensions 18 are formed integrally on the separating elements 4.
  • the extensions 18 are formed on the respective separating element 4, as shown in FIG. 8, in such a way that they protrude into the fluid channel 5 delimited by the respective separating element 4.
  • the separating elements 4 are formed in a straight line.
  • the extensions 18 are each orthogonal, from the separating elements 4 and protrude into the fluid channel 5 delimited by the separating element 4.
  • the extensions 18 can also protrude from the separating elements at a different angle.
  • FIGS. 9 and 10 show further variants of the examples of FIGS. 5 to 7.
  • FIG. 9 shows a combination of the examples of FIGS. 6 and 8.
  • the separating elements 4 of FIG. 9 each comprise a plurality of element sections 16.
  • the element sections 16 of FIG Separating elements according to FIG. 9 are integrally formed on one another and complement each other to form the separating element 4.
  • rigid element sections 16 are arranged perpendicular to the stacking direction S at an obtuse angle, ie at an angle to one another.
  • FIG. 10 shows a combination of the examples of FIGS. 7 and 8.
  • the separating elements 4 have a wave-like geometry. That is, the respective partition member 4 is curved as shown in Figure 7 along the fluid flow direction F of the heat exchanger 1 and the tubular body 3, in particular wave-shaped. In a simplified variant, such a curved or wavy formation of the separating elements 4 can also take place only in sections.
  • the extensions 18 each protrude transversely, preferably orthogonally, from the separating elements 4 and protrude into the fluid channel 5 delimited by the separating element 4.
  • Fluid flow direction F adjacent extensions 18 on opposite sides of the separating elements 4 from.
  • Two extensions 18 which are adjacent in the fluid flow direction F thus protrude into two adjacent fluid channels 5.
  • an equidistant arrangement of the individual extensions 18 along the fluid throughflow direction F shown in FIGS. 6 to 8 is recommended.
  • the heat exchanger 1 according to FIGS. 1 to 4 can be produced in a particularly simple manner and with low production costs by using an additive manufacturing method such as, for example, laser sintering.
  • additive production process encompasses all production processes which build up the component in layers directly from a computer model.
  • the use of an additive manufacturing method allows the individual components of the heat exchanger, such as tubular bodies including separators, fin structure, fluid manifolds and fluid collectors, etc., to be directly defined as a CAD model and made directly from such a CAD model.
  • the heat exchanger 1 may be formed in one piece. Such a one-piece design is formed, in particular, when using the above-described additive manufacturing process, in particular the said laser sintering. In a one-piece design of the heat exchanger 1 eliminates the very costly and therefore costly attaching the individual components of the heat exchanger together. For example, the cohesive fastening of the individual tubular bodies 3 to the rib structures 14, for example by means of a welded or soldered connection, and the cohesive fastening of fluid distributor 9 and fluid collector 10 to the tubular bodies 3 are eliminated. This leads to considerable cost advantages in the production of the heat exchanger 1.

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

Abstract

L'invention concerne un échangeur de chaleur (1), en particulier pour un dispositif de récupération de chaleur perdue, qui comporte une pluralité de chemins fluidiques (2) destinés à être parcourus par un fluide. chaque chemin fluidique (2) étant délimité au moins en partie par un corps tubulaire (3), les corps tubulaires (3) s'étendant le long d'une direction d'extension tubulaire (E) et étant disposés empilés les uns sur les autres dans une direction d'empilement, un chemin de gaz (7) destiné à être parcouru par un gaz dans une direction d'écoulement gazeux (G) étant formé dans chaque cas par un espace intermédiaire (6) situé entre deux corps tubulaires (3) adjacents dans la direction d'empilement (S), une pluralité d'éléments de séparation (4), tous adjacents les uns aux autres, étant disposés dans les chemins fluidiques (2), lesdits éléments de séparation divisant chaque chemin fluidique (2) en une pluralité de passages pour fluide (5) qui s'étendent chacun dans une direction de parcours du fluide (F), la direction de parcours du fluide (F) s'étendant orthogonalement à la direction dans laquelle les corps tubulaires s'étendent (E).
PCT/EP2016/051930 2015-03-19 2016-01-29 Échangeur de chaleur, en particulier pour un véhicule à moteur WO2016146294A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015204983.3 2015-03-19
DE102015204983.3A DE102015204983A1 (de) 2015-03-19 2015-03-19 Wärmetauscher, insbesondere für ein Kraftfahrzeug

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WO2016146294A1 true WO2016146294A1 (fr) 2016-09-22

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WO (1) WO2016146294A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
EP3239641A1 (fr) * 2016-04-27 2017-11-01 Mahle International GmbH Tube plat pour un caloporteur

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DE102019002466B4 (de) * 2019-04-04 2020-11-19 Bundesrepublik Deutschland, vertr. durch das Bundesministerium der Verteidigung, vertr. durch das Bundesamt für Ausrüstung, Informationstechnik und Nutzung der Bundeswehr Luft-Wasser-Ladeluftkühler
DE102020112004A1 (de) 2020-05-04 2021-11-04 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Abgaswärmetauscher und Verfahren zur Herstellung eines solchen Abgaswärmetauschers

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US5771964A (en) * 1996-04-19 1998-06-30 Heatcraft Inc. Heat exchanger with relatively flat fluid conduits
WO1999064805A1 (fr) * 1998-06-10 1999-12-16 Heatcraft Inc. Echangeur de chaleur pourvu de conduits a fluide relativement plats
US6286201B1 (en) * 1998-12-17 2001-09-11 Livernois Research & Development Co. Apparatus for fin replacement in a heat exchanger tube

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DE1501568B2 (de) * 1966-10-12 1971-05-13 Linde Ag, 6200 Wiesbaden Plattenwaermetauscher
IT939692B (it) * 1970-11-02 1973-02-10 Engelhard Min & Chem Procedimento per produrre articoli tridimensionali a base di compo sizioni termoplastiche
US6595273B2 (en) * 2001-08-08 2003-07-22 Denso Corporation Heat exchanger
DE102007010969A1 (de) * 2007-03-05 2008-09-11 Behr Gmbh & Co. Kg Klimaanlage mit Kältespeicher und Verfahren zum Betreiben einer derartigen Klimaanlage

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Publication number Priority date Publication date Assignee Title
US5771964A (en) * 1996-04-19 1998-06-30 Heatcraft Inc. Heat exchanger with relatively flat fluid conduits
WO1999064805A1 (fr) * 1998-06-10 1999-12-16 Heatcraft Inc. Echangeur de chaleur pourvu de conduits a fluide relativement plats
US6286201B1 (en) * 1998-12-17 2001-09-11 Livernois Research & Development Co. Apparatus for fin replacement in a heat exchanger tube

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3239641A1 (fr) * 2016-04-27 2017-11-01 Mahle International GmbH Tube plat pour un caloporteur
US10295275B2 (en) 2016-04-27 2019-05-21 Mahle International Gmbh Flat tube for a heat exchanger

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