US20070137843A1 - Heat exchanger core and heat exchanger equipped therewith - Google Patents

Heat exchanger core and heat exchanger equipped therewith Download PDF

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Publication number
US20070137843A1
US20070137843A1 US11/525,467 US52546706A US2007137843A1 US 20070137843 A1 US20070137843 A1 US 20070137843A1 US 52546706 A US52546706 A US 52546706A US 2007137843 A1 US2007137843 A1 US 2007137843A1
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United States
Prior art keywords
heat exchanger
exchanger core
plates
core according
separating walls
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Abandoned
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US11/525,467
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English (en)
Inventor
Josef Gievers
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.)
Autokuehler GmbH and Co KG
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Autokuehler GmbH and Co KG
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Assigned to AUTOKUEHLER GMBH & CO. KG reassignment AUTOKUEHLER GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GIEVERS, JOSEF
Publication of US20070137843A1 publication Critical patent/US20070137843A1/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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F28D9/0068—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
    • 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
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • 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
    • F28D2021/0038—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for drying or dehumidifying gases or vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/108—Particular pattern of flow of the heat exchange media with combined cross flow and parallel flow

Definitions

  • the invention relates to a heat exchanger core comprising at least two plates and a passage disposed between said plates for a coolant, said passage containing a plurality of flow channels which are disposed in parallel and delimited laterally by separating walls, which are disposed perpendicular to the plates, have respectively two ends and are connected to each other in an undulating shape by deflection zones which are provided alternately at the one or other ends of the separating walls.
  • the invention also relates to a heat exchanger comprising such a heat exchanger core.
  • Heat exchangers produced with heat exchanger cores of this type are required e.g. in compressed air plants in order to dehumidify the compressed air produced by means of a compressor and at a pressure of e.g. 25 bar in order consequently to make it suitable for critical application purposes, such as e.g. in the food and paper industry or in the medical field.
  • the air drying is effected in that the heated air coming from the compressor is conducted after passage through an aftercooler through a device which contains an air/air and a coolant/air heat exchanger.
  • the coolant/air heat exchanger Whilst the air/air heat exchanger is generally produced in the manner of a plate heat exchanger of a normal construction, the coolant/air heat exchanger comprises e.g. a combined pipe/plate heat exchanger with a core which has air passages which are formed from plates and strips holding the plates at a given spacing and coolant passages situated therebetween.
  • the coolant passages comprise for example pipes, which have round or square cross-sections and are disposed respectively between two plates, said pipes having straight portions and deflecting portions connecting these in an undulating or in a meandering shape (EP 0 521 298 A2).
  • a disadvantage of this construction is that unused spaces are produced between the individual pipe portions and that the curved deflecting portions are generally outwit the space taken up by the actual core and are not involved in the heat exchange.
  • the separating walls are configured by the webs and/or flanges of profiles with I and/or U-shaped cross-sections disposed between the plates (EP 1 304 536 A2).
  • the flow channels are produced, according to a first variant, with the help of a multiplicity of I-profiles which are connected to the plates by soldering, then these profiles must be connected to the plates before the soldering process at at least two points by laser welding or the like in order to preclude relative positional changes between the plates and the profiles during immersion and tilting processes which are required during the soldering process.
  • the flow channels are configured, according to a second variant, as U-shaped grooves in solid, plane-parallel plates, these and the deflection zones must be produced by milling, in particular track milling. Both variants incur, therefore, comparatively high production costs which are not always tolerable.
  • a further object of the present invention is to design the heat exchanger core mentioned above in such a manner that manufacture thereof is unproblematic with respect to the soldering technology.
  • Yet another object of the present invention is to so design the heat exchanger core mentioned above that comparatively large flow cross-sections for the coolant can be provided within given overall dimensions.
  • a further object of the present invention is to provide a heat exchanger having a heat exchanger core of the type mentioned above.
  • the coolant passage is formed by at least one lamella which is connected to the plates, has a meandering cross-section and contains the separating walls, and wherein the deflection zones comprise recesses which are provided at the ends of the separating walls.
  • a coolant/air heat exchanger is charaterized in that it contains a heat exchanger core with the features mentioned above.
  • lamellae which respectively form a plurality of flow channels each, the number of welding operations to be implemented before the soldering process can be significantly reduced.
  • the lamellae can be produced by extrusion or milling and consequently economically with any arbitrary strength.
  • any arbitrary cross-sectional form can be given to the separating walls and/or to the flow channels delimited by these, which is favourable with respect to the output and stability of the heat exchanger core which is desired in the individual case.
  • FIG. 1 a schematic front view of a combined coolant/air and air/air heat exchanger block for cooling dryers in compressed air plants;
  • FIG. 2 and 3 sections along the lines II-II and III-III of FIG. 1 ;
  • FIG. 4 an enlarged plan view on a lamella according to the invention for producing coolant passages in a core according to FIG. 1 destined for the coolant/air-heat exchange;
  • FIG. 5 to 7 sections along the lines V-V to VII-VII of FIG. 4 ;
  • FIG. 8 an enlarged front view of a detail of a coolant passage in a core according to FIG. 1 destined for the coolant/air-heat exchange and being made with lamellae according to FIGS. 4 to 7 ;
  • FIG. 9 a plan view on the coolant passage according to FIG. 8 , an upper plate being omitted;
  • FIG. 10 an enlarged front view of the core of the block according to FIG. 1 , intended for the coolant/air heat exchange and being made with lamellae according to FIGS. 4 to 7 ;
  • FIG. 11 a section along the line XI-XI of FIG. 10 ;
  • FIG. 12 and 13 in views corresponding to FIGS. 10 and 11 a second embodiment of the core
  • FIG. 14 to 17 in views corresponding to FIGS. 4 to 7 a second embodiment of the lamella according to the invention.
  • FIG. 18 to 21 in views corresponding to FIGS. 4 to 7 a third embodiment of the lamella according to the invention.
  • FIG. 22 a front view corresponding to FIG. 8 of a coolant passage if lamellae according to FIGS. 14 to 21 are used.
  • a heat exchanger device for cooling dryers in compressed air plants contains, according to FIG. 1 to 3 , a coolant/air heat exchanger in the right portion and an air/air heat exchanger in the left portion. Only one coolant/air heat exchanger core 1 and, situated adjacently, one air/air heat exchanger core 2 are thereby illustrated, both being located beside each other in an assumed longitudinal direction, being combined into an integral constructional unit and forming a single, connected block 3 . Of course, it would be possible also as an alternative to produce and to operate both cores 1 and 2 as separate constructional units.
  • the two cores 1 and 2 are mainly formed by plane-parallel, rectangular or square plates or separating metal sheets 4 , respectively, which extend over the entire width and length of the block 3 .
  • a part of the plates 4 are spaced on the one hand by strips 5 which extend perpendicular to the longitudinal direction and are disposed on ends of the block 3 at the left in FIG. 3 and, on the other hand, by strips 6 , 7 which extend in the longitudinal direction and are disposed on the lateral edges of the plates 4 .
  • passages 8 are produced between these plates 4 .
  • the upper strips 6 are somewhat shorter so that intermediate spaces 9 respectively are produced between their left ends and the strips 5 , such that air is able to enter laterally through said intermediate spaces 9 in the direction of an illustrated arrow 10 .
  • the air can exit laterally in contrast parallel to the longitudinal direction of the passages 8 and in the direction of an illustrated arrow 11 .
  • Normal lamellae or fins 12 are furthermore inserted expediently into the passages 8 and are illustrated only in part in FIG. 1 , and the passages thereof are deflected by 90° along lines 14 , corresponding to FIG. 3 .
  • the other part of the plates, according to FIG. 1 and 2 are spaced in the part forming the core 2 in pairs by strips 15 and 16 which extend parallel to the longitudinal direction and are disposed on the lateral edges of the plates 4 and also by end or closing strips 17 and 18 which extend transversely thereto and form the left and right end of the core 2 .
  • a further passage 19 is produced respectively between two plates 4 respectively.
  • the upper strips 15 in FIG. 2 are slightly shorter so that intermediate spaces 20 respectively are produced between them and the closing strips 18 through which air can be supplied laterally in the direction of an illustrated arrow 21 ( FIG. 2 ).
  • the same plates 4 which delimit the passages 19 serve to form passages 24 which are disposed in an undulating shape ( FIG. 1 ), said passages having portions which are straight as well as portions which serve for deflection, as explained in more detail further on.
  • the passages 24 extend respectively from the closing strips 18 to a closing strip or plate 25 which is disposed in FIG. 1 and 2 at the right end of the block 3 .
  • pairs of plates with the passages 8 alternate with pairs of plates with the passages 19 , 24 in superimposed planes, at least one passage 8 , 19 , 24 respectively being present in each plane.
  • a coolant is supplied to the passages 24 at an inlet indicated by an arrow 26 and can flow out again at an outlet indicated by an arrow 27 for flowing the through a coolant cycle, not shown.
  • the inlets or outlets marked by the arrows 10 , 11 , 21 , 23 , 26 and 27 are connected to collection tanks or the like at known inlet nipples, not shown.
  • the mode of operation of the described heat exchanger device is essentially as follows:
  • the compressed air which comes from a compressed air plant and is heated e.g. to approx. 35° to 55° C. is supplied in the direction of the arrow 10 so that it flows through the passages 8 .
  • the air is thereby cooled initially in the core 2 by the cold air, which is supplied in counter-flow in the direction of the arrow 21 and comes from a water separator, not shown, to a temperature of e.g. 20° C.
  • the compressed air On its further path through the passages 8 , the compressed air is then cooled gradually in the core 1 to its dew point since it interacts here with the coolant which flows into the passages 24 in the direction of the arrow 26 ( FIG. 2 ).
  • the compressed air is then removed at the outlet marked by the arrow 11 ( FIG.
  • Heat exchangers of the described type and their mode of operation are generally known to the person skilled in the art (EP 0 521 298 A1, EP 1 304 536 A2) and do not therefore require to be explained in more detail.
  • the passage 24 is formed by a plurality of lamellae 31 which are disposed parallel next to each other ( FIG. 6 and 7 ).
  • Each lamella 31 according to FIG. 6 and 7 , has a meandering cross-section and a plurality of separating walls 32 , five in the embodiment.
  • the separating walls 32 are disposed vertically, parallel to each other and at the same spacings from each other and also connected to each other alternately above and below by horizontal, upper or lower webs 33 , 34 , as is typical of meanders. Because of the presence of five separating walls 32 , two upper and lower webs 33 , 34 respectively are provided so that respectively two adjacent separating walls 32 and a web 33 or 34 connecting them delimit a flow channel 35 , and in total four flow channels 35 of this type per lamella 31 are present. The arrangement is preferably such that each flow channel 35 has the same flow cross-section. At its lateral ends the lamelIa 31 is limited by a respective separating wall 32 .
  • the lamellae 31 are preferably produced by extrusion from aluminium or an aluminium alloy and subsequent cutting to a length desired in the individual case.
  • the separating walls 32 thereof are therefore initially of the same length and provided with a front and rear end or a front end face 32 a and a rear end face 32 b ( FIG. 5 ). After cutting to length, the separating walls 32 are however provided with a recess 36 at the one or other end 32 a , 32 b . As is indicated in FIG.
  • the recesses 36 are fitted alternately on the one or other end 32 a , 32 b in the case of successive separating walls 32 so that, in the embodiment, three recesses 36 of this type are situated at the front end of the lamella 31 and two at the rear end of the lamella 31 .
  • FIG. 8 and 9 show a coolant passage 24 which substantially extends in a plane and is produced by application of the lamellae 31 (cf. also FIG. 2 ). Further, FIG. 10 and 11 each show a complete portion of the heat exchanger device including the complete core 1 .
  • a first lamella 31 a is disposed parallel to and at a spacing from the closing strip 18 corresponding to the width of a flow channel 35 .
  • the position of the lamella 31 a is chosen such that an outer separating wall 32 a situated furthest left is disposed parallel to the strip 18 and has its recess 36 at the rear end of the lamella 31 a , not shown in FIG. 9 .
  • the lamella 31 shown in FIGS. 8 and 9 is used, but after rotating it about an axis perpendicular to the drawing plane in FIG. 4 and by about 180°.
  • a second lamella 32 b Abutting on the lamella 31 a there is a second lamella 32 b in FIG. 8 and 9 .
  • the latter is identically configured to the lamella 31 a but, in contrast to the latter, in a position shown in FIG. 4 and 6 , so that three recesses 36 are situated at the front and two further recesses 36 at the rear, not visible in FIG. 9 .
  • a separating wall 32 f of the lamella 31 a situated furthest to the left is disposed at a spacing corresponding to the width of a flow channel 35 from the separating wall 32 e of the lamella 31 a and parallel to the latter. Also this can be best seen from FIG. 11 .
  • the flow channels 35 which are alternately open at the top and bottom ( FIG. 6 and 7 ) are closed according to FIG. 8 at the top or bottom by respectively one of the plates 4 which are connected to the outer sides of the webs 33 , 34 expediently by soldering.
  • the front and rear ends of the flow channels 35 are closed by individual profiles 37 which have a width corresponding substantially to twice the spacing of two separating walls 32 , are connected in a gas-impermeable manner to the front and rear ends of the lamellae 31 a and 32 b or of the separating walls 32 and also to the plates 4 preferably by welding (MIG or WIG) and, for weight and cost reduction, have for example the trapezoidal cross-sections evident in FIG. 9 .
  • the front and rear and also upper and lower regions of the flow channels 38 , 38 a and 38 b are sealed in a gas-impermeable manner and are formed between the lamella 31 a and the closing strip 18 , between the lamellae 31 a and 31 b and on the other side of the core 1 between the last lamella 31 and the closing strip 25 ( FIG. 10 and 11 ), the two flow channels 38 and 38 b remaining open e.g. on the front side corresponding to FIG. 11 in order to be able to supply and discharge the coolant there in the direction of the arrows 26 , 27 .
  • the described recesses 36 after production of the coolant passage 24 (FIG. 11 and 13 ) form respectively a deflection zone alternately situated at the front or rear, which is delimited by the relevant plates 4 , profiles 37 (or plates 39 ) and separating walls 32 . Consequently, the coolant can enter for example in the direction of the arrow 26 according to FIG.
  • passage 24 illustrated in FIG. 8 further corresponding passages 24 can be present and be separated from each other by air passages, as FIG. 1 to 3 and 10 , 12 in particular make clear.
  • the profiles 37 (or plates 39 ) extend expediently over the entire height of the heat exchanger core.
  • the number of flow channels 35 and 38 from which the coolant passages 24 are formed, can be chosen as a function of the requirements of the individual case. Instead of the four flow channels 35 according to FIG. 6 and 7 , also more or fewer flow channels 35 per lamella 31 can be present. In the case of an even number of separating walls 32 per lamella 31 , these can be laid out in particular with the same orientation since, in this case, the recesses 36 of the first separating wall 32 are always situated for example at the front and the recesses 36 of the last separating wall 32 are always for example at the rear.
  • Lamellae 31 with a smaller number of separating walls 32 offer the advantage that, during extrusion, they become only slightly curved because of the more uniform material flow and hence can be straightened during setting up of the heat exchanger core 1 which is effected before the soldering.
  • lamellae 31 provided with a substantially greater number of separating walls 32 would require to be straightened before setting up the core 1 with the help of additional devices, such as e.g. rollers or the like.
  • the assembly of the heat exchanger block 3 according to FIG. 1 is effected in a normal manner for heat exchangers in that for example firstly the plates 4 and the lamellae 31 are connected by soldering and thereafter the profiles 37 (or plates 39 ) are fixed to the plates 4 and lamellae 31 by welding.
  • An advantage resulting therefrom is that before soldering the lamellae 31 require to be connected only at two points respectively by welding to an associated plate 4 respectively to ensure the position whilst, when applying individual profiles as separating walls (in the embodiment five individual profiles per lamella) respectively 10 welding processes would be required.
  • FIGS. 14 to 17 show a second embodiment of the lamellae 31 according to the invention. Contrary to the lamellae 31 of FIG.
  • the lamellae 31 of FIG. 14 to 17 have, at one of its lateral ends, a foot or web 34 a instead of a separating wall 32 .
  • This web 34 a projects outwardly from a respective end separating wall 32 as clearly shown in FIGS. 16 and 17 . It is, therefore, possible to arrange two or more lamellae 31 one beside the other without rotation (as in FIG. 8 ) in such as manner, that an end separating wall 32 of one lamella 31 always abuts a web 34 a of a neighbored lamella 31 .
  • Web 34 a thus defines the distance between two neighbored lamellae 31 .
  • a further lamella 31 according to FIGS. 18 to 21 is provided, said lamella 31 having two feet or webs 33 b and 34 c , each projecting outwardly from a respective end separating wall 32 as clearly shown in FIG. 20 and 21 .
  • one web e.g. 33 b
  • another web e.g. 34 c
  • a lamella 31 d according to FIG. 16 is provided such that an end separating wall 31 g at the left end thereof abuts web 34 c of lamella 31 c .
  • further lamellae 31 according to FIG. 16 can follow at the right side of lamella 31 d up to the closing strip 25 ( FIG. 11 ) in such a manner that the web 34 a of the farthest right lamella 31 abuts closing strip 25 for making the flow channel 38 b .
  • the complete core 1 can be set up without taking care of the distances between the lamellae because all such distances are given by the webs 34 a , 33 b and 34 c . It is, therefore, no danger that the distances erraneously will become too great or too small.
  • the invention is not restricted to the described embodiments which could be modified in many ways.
  • the webs 33 and 34 and/or the widenings 40 could be curved slightly convexly in order to obtain a roundness desired for improving the soldering process.
  • the lamellae 31 and profiles 37 or plates 39 in fact comprise for example aluminium and the plates 4 plated aluminium but it is clear that, according to requirement, also different materials which are generally used to produce heat exchanger cores can be used.
  • the production of the lamellae 31 can be made, as described, by extrusion but also in another way, particularly in that a plate is provided with the flow channels 35 by milling or the like.
  • the cores 1 and 2 form an integral component with the help of the continuous plates 4 , are produced separately and then assembled to form an integral component or are used as separate components which are connected to each other by corresponding lines or which are used independant upon each other.
  • the cores 1 , 2 can also be disposed one above the other instead of next to each other.
  • the different features can be provided also in combinations other than those described and illustrated.

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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)
US11/525,467 2005-09-28 2006-09-22 Heat exchanger core and heat exchanger equipped therewith Abandoned US20070137843A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202005015627.2 2005-09-28
DE202005015627U DE202005015627U1 (de) 2005-09-28 2005-09-28 Wärmeaustauschernetz und damit ausgerüsteter Wärmeaustauscher

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EP (1) EP1770345B1 (de)
JP (1) JP2007093199A (de)
DE (1) DE202005015627U1 (de)

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US20100290947A1 (en) * 2008-01-23 2010-11-18 Jms Co., Ltd. Medical heat exchanger, manufacturing method thereof and artificial lung device
US20120031597A1 (en) * 2009-04-06 2012-02-09 Atlas Copco Airpower Improved heat exchanger
EP2879162A4 (de) * 2012-07-27 2016-03-23 Kyocera Corp Strömungswegelement sowie wärmetauscher und vorrichtung zur halbleiterherstellung damit
US10143962B2 (en) 2010-04-14 2018-12-04 Kaeser Kompressoren Se Refrigerant dryer, in particular compressed air refrigerant dryer, and heat exchanger for a refrigerant dryer, in particular a compressed air refrigerant dryer
US20180372416A1 (en) * 2017-06-26 2018-12-27 United Technologies Corporation Manufacturing a heat exchanger using a material buildup process
US10215496B2 (en) 2013-02-19 2019-02-26 Bosal Emission Control Systems Nv Multi-flow heat exchanger for exchanging heat between cool fluid and hot fluid
WO2024056772A1 (de) * 2022-09-16 2024-03-21 Robert Bosch Gmbh Wärmetauscher zur kühlung von komponenten

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DE102009050482B4 (de) * 2009-10-23 2011-09-01 Voith Patent Gmbh Wärmeübertragerplatte und Verdampfer mit einer solchen

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US20050115701A1 (en) * 2003-11-28 2005-06-02 Michael Martin Low profile heat exchanger with notched turbulizer

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US20100290947A1 (en) * 2008-01-23 2010-11-18 Jms Co., Ltd. Medical heat exchanger, manufacturing method thereof and artificial lung device
US8609022B2 (en) * 2008-01-23 2013-12-17 Jms Co., Ltd. Medical heat exchanger, manufacturing method thereof and artificial lung device
US20120031597A1 (en) * 2009-04-06 2012-02-09 Atlas Copco Airpower Improved heat exchanger
US9574828B2 (en) * 2009-04-06 2017-02-21 Atlas Copco Airpower Naamloze Vennootschap Heat exchanger
US10143962B2 (en) 2010-04-14 2018-12-04 Kaeser Kompressoren Se Refrigerant dryer, in particular compressed air refrigerant dryer, and heat exchanger for a refrigerant dryer, in particular a compressed air refrigerant dryer
EP2879162A4 (de) * 2012-07-27 2016-03-23 Kyocera Corp Strömungswegelement sowie wärmetauscher und vorrichtung zur halbleiterherstellung damit
US10215496B2 (en) 2013-02-19 2019-02-26 Bosal Emission Control Systems Nv Multi-flow heat exchanger for exchanging heat between cool fluid and hot fluid
US20180372416A1 (en) * 2017-06-26 2018-12-27 United Technologies Corporation Manufacturing a heat exchanger using a material buildup process
US10823511B2 (en) * 2017-06-26 2020-11-03 Raytheon Technologies Corporation Manufacturing a heat exchanger using a material buildup process
US11835304B2 (en) 2017-06-26 2023-12-05 Rtx Corporation Heat exchanger with stacked flow channel modules
WO2024056772A1 (de) * 2022-09-16 2024-03-21 Robert Bosch Gmbh Wärmetauscher zur kühlung von komponenten

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EP1770345A3 (de) 2008-12-17
EP1770345B1 (de) 2012-08-01
JP2007093199A (ja) 2007-04-12
EP1770345A2 (de) 2007-04-04

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