US20070125527A1 - Device for multi-stage heat exchange and method for producing one such device - Google Patents

Device for multi-stage heat exchange and method for producing one such device Download PDF

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Publication number
US20070125527A1
US20070125527A1 US10/561,975 US56197504A US2007125527A1 US 20070125527 A1 US20070125527 A1 US 20070125527A1 US 56197504 A US56197504 A US 56197504A US 2007125527 A1 US2007125527 A1 US 2007125527A1
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Prior art keywords
flow
fluid
elements
fluids
exclusively
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Abandoned
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US10/561,975
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English (en)
Inventor
Markus Flik
Jochen Eitel
Peter Geskes
Michael Lohle
Ulrich Maucher
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Mahle Behr GmbH and Co KG
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Behr GmbH and Co KG
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Assigned to BEHR GMBH & CO. KG reassignment BEHR GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MAUCHER, ULRICH, LOHLE, MICHAEL, GESKES, PETER, EITEL, JOCHEN, FLIK, MARKUS
Publication of US20070125527A1 publication Critical patent/US20070125527A1/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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0412—Multiple heat exchangers arranged in parallel or in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
    • F02B29/0462—Liquid cooled heat exchangers
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F28D7/0083—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with units having particular arrangement relative to a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium
    • 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
    • F28D9/0031—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 paired plates touching each other
    • F28D9/0043—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28D9/0031—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 paired plates touching each other
    • F28D9/0043—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/0056—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the plates
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • F01P2003/182—Arrangements or mounting of liquid-to-air heat-exchangers with multiple heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/16—Outlet manifold
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • 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
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/02—Fastening; Joining by using bonding materials; by embedding elements in particular materials
    • F28F2275/025—Fastening; Joining by using bonding materials; by embedding elements in particular materials by using adhesives
    • 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

  • the present invention relates to an apparatus for multi-stage heat exchange, and to a process for producing an apparatus of this type.
  • Cooling and heating concepts of the current state of the art generally provide for single-stage heat transfer in heat exchangers.
  • fluids such as for example coolant, refrigerant, oil, exhaust gas or charge air
  • the efficiency which can be achieved with single-stage temperature control is normally limited. Therefore, to improve the performance of cooling circuits, it is in some cases appropriate for a fluid to be cooled or heated over two stages. This is possible if, in addition to the fluid whose temperature is to be controlled, there are two further fluids which are at two different temperature levels.
  • one drawback of the two-stage control of the temperature of the fluids is that the use of two heat exchangers connected in series in the conventional way entails considerably increased costs as well as a greater installation space requirement.
  • the invention is therefore based on the object of providing an apparatus in which the at least two-stage cooling or heating of a fluid can be of compact and inexpensive configuration.
  • the object is achieved by an apparatus as claimed in claim 1 .
  • the process according to the invention for producing an apparatus of this type forms the subject matter of claim 20 .
  • Preferred embodiments and refinements form the subject matter of the subclaims.
  • the apparatus according to the invention for heat exchange has at least three flow devices, through which at least one flowable medium (fluid) flows. After they have flowed through the individual flow devices, it is also possible for at least two of the at least three fluids to be mixed in the heat exchanger and discharged together.
  • the term flowable media or fluids is to be understood as meaning liquid and/or gaseous media of any desired viscosity, such as in particular, although not exclusively, oils, liquids, in particular with a high heat of evaporation, water, air or gases as well as refrigerants which can evaporate or condense.
  • the flowable media may in this case also contain additives, for example for inhibiting corrosion.
  • the apparatus according to the invention has at least one fluid inflow device, at least one fluid collection and/or distribution device and at least one fluid outflow device for at least one flow device through which substantially liquid fluids flow.
  • At least two flow assemblies are provided, each having at least two flow elements, which are arranged in such a manner that different fluids flow through them alternately. Furthermore, the flow elements belonging to a flow device through which substantially liquid fluids flow are connected in a substantially gastight and liquid-tight, positively locking and/or nonpositively locking and/or cohesive manner to at least one fluid collection and/or distribution device.
  • the main directions of flow of all the fluids in the flow elements lie in planes that are substantially parallel to one another.
  • two flow assemblies of the apparatus according to the invention are directly connected in series in a positively locking and/or nonpositively locking and/or cohesive manner and/or flow-connected by means of a fluid distribution device, at least with respect to one flow device.
  • a flow device is to be understood as meaning a device through which a liquid or gaseous medium can flow and which, in the case of the flow devices through which substantially liquid fluids flow, is delimited in a substantially gastight and liquid-tight manner with respect to the space surrounding it.
  • the flow devices are in this case formed by flow elements which are flow-connected in series and/or in parallel.
  • these flow elements are formed by in particular, although not exclusively, hollow disks, flat tubes, plates and/or layers.
  • hollow disks, plates or layers are to be understood as meaning substantially gastight and liquid-tight hollow bodies with inlet and outlet openings, the length and width dimensions of which are considerably greater than their height.
  • flat tubes is to be understood as meaning tubes which when seen in cross section have a long side and a side which is significantly shorter than this long side.
  • the flow elements may have one or more flow passages for the medium flowing through them. They may run in a straight line but they may also have a plurality of curved sections. In addition, the flow elements may also have twisted sections, i.e. sections in which the flow element is turned and/or wound in on itself.
  • a fluid distribution and/or collection device in the case of the flow devices through which substantially liquid fluids flow, is to be understood as meaning substantially gastight and liquid-tight hollow bodies within which fluids can flow and within which these fluids are collected.
  • these fluid distribution and/or collection devices can also be used to distribute the respective fluids between a plurality of flow elements and/or to collect them again from various flow elements.
  • the term flow-connected is to be understood as meaning that a fluid can flow between the flow elements, fluid distribution and/or collection devices.
  • substantially gastight and liquid-tight is to be understood as meaning in particular, although not exclusively, a division by separating devices, so that it is impossible for any fluid to flow past the respective separating device along certain directions of the flow devices, flow elements, fluid distribution and/or collection devices.
  • direction of flow or main direction of flow of a fluid is to be understood as meaning the direction which the fluid preferably adopts within a flow device, a flow element and/or a fluid distribution and/or collection device, disregarding locally limited changes in direction of the fluid.
  • the fluid distribution and/or collection devices are, in the broader sense, collection and/or distribution tubes.
  • At least one fluid collection and/or distribution device is formed at least in part from longitudinal-side openings in the flow elements, a first number of simple openings forming fluid inlets and fluid outlets with respect to adjacent flow elements, and sealing devices being arranged around a second number of openings, in order to form passages in the corresponding flow element, through which passages flow elements adjacent to this flow element are flow-connected.
  • the first number of longitudinal-side openings in flow elements are to be understood as meaning in particular, although not exclusively, round punched-out apertures or drilled holes which are provided in the significantly longer and wider sides of the flow elements.
  • sealing devices around the second number of longitudinal-side openings in flow elements are to be understood as meaning in particular, although not exclusively, stamped projections, which adjoin the adjacent flow element in a cohesive and/or positively locking and/or nonpositively locking manner, in the corresponding flow element or sealing rings.
  • partition walls prefferably be provided in a substantially gastight and liquid-tight manner in individual openings, allowing preferred control of the fluid distribution by in particular, although not exclusively, stacking identical plate-like flow elements on top of one another.
  • turbulence-generating and/or turbulence-increasing shaped elements are preferably provided within the flow device, which shaped elements in particular contribute to increasing the heat transfer coefficient between the fluids of the various flow devices. It is preferable for these turbulence-generating or turbulence-increasing shaped elements to be taken from a group which includes in particular, although not exclusively, fins, webs, studs, grooves, stamped indentations or milled-out sections.
  • the turbulence-generating and/or turbulence-increasing shaped elements are arranged in at least one flow element and/or between at least two flow elements. Furthermore, the profile of at least one flow element preferably has turbulence-generating and/or turbulence-increasing properties.
  • turbulence inlays are provided, preferably to be laid in at least one flow element, in particular, although not exclusively, in hollow disks, plates and/or layers.
  • turbulence inlays are to be understood as meaning in particular, although not exclusively, metal sheets which have turbulence-generating and/or turbulence-increasing shaped elements, such as for example fins, webs, studs, grooves, stamped indentations and/or milled-out sections and are laid in the flow elements, in a manner which simplifies production, preferably with external dimensions corresponding to the internal dimensions of the flow elements, and preferably with punched-out apertures corresponding to the distribution devices with leaktightness device, in particular the stamped projections in the flow elements, for the passages through which adjacent flow elements are flow-connected.
  • metal sheets which have turbulence-generating and/or turbulence-increasing shaped elements, such as for example fins, webs, studs, grooves, stamped indentations and/or milled-out sections and are laid in the flow elements, in a manner which simplifies production, preferably with external dimensions corresponding to the internal dimensions of the flow elements, and preferably
  • At least two flow elements through which different fluids flow are connected on the longitudinal sides in a positively locking and/or nonpositively locking and/or cohesive manner.
  • At least two flow elements through which the same fluid flows are connected on the longitudinal sides by means of in particular, although not exclusively, the turbulence-generating and turbulence-increasing shaped elements which have their own profile and/or are arranged between them, in such a manner that at least one cavity which is thereby formed between these flow elements forms a flow element for a different fluid.
  • joins between the flow elements are taken from a group which includes soldered joins, welded joins or adhesively bonded joins.
  • At least one sealing element which is formed in particular, although not exclusively, by separating elements and/or hollow elements which are empty of fluid, is provided at least between two flow elements through which different fluids flow.
  • At least one sealing element is arranged between flow assemblies which are in series.
  • At least one of the sealing elements has in particular, although not exclusively, a hollow element which is empty of fluid, a leaktightness control opening.
  • the method of first of all filling each individual flow device with its corresponding fluid also makes it possible for the gastightness and liquid-tightness according to the invention of the various flow devices with respect to one another to be checked as a result of the fluid which has in each case been introduced passing into a second flow device.
  • At least one of the sealing elements has at least one leaktightness sensor, which causes a physically perceptible signal to be output in the event of a fluid escaping from one of the flow devices.
  • At least two flow assemblies are separated from one another in a substantially thermally insulating manner, for example simply by being arranged spatially spaced apart, and/or alternatively by means of hollow elements that are empty of fluid in particular arranged between them.
  • shaped elements are provided within at least one flow element, which shaped elements, at least in sections, alter the main direction of flow of the fluid flowing within the flow element.
  • At least one flow device has admixed with it, via at least one further inflow device, a fluid, in particular, although not exclusively, a fluid which corresponds to the fluid in this flow device.
  • the series connection according to the invention of at least two flow assemblies with respect to at least one flow device is effected in such a manner that the temperature gradient of the fluid of this flow device along the flow path of this fluid from the fluid inflow device to the fluid outflow device of this flow device has a substantially constantly decreasing magnitude with respect to each of the other fluids flowing through the flow assemblies of the flow assembly series connection.
  • fluids are mixed in the heat exchanger, it being possible for different proportions of the overall fluid to flow through different flow elements.
  • Another preferred embodiment allows a fluid to be divided in the heat exchanger, it being possible for different proportions of the divided fluid to flow through different flow elements.
  • the heat exchange in individual flow assemblies takes place by condensation or evaporation of a fluid.
  • the individual flow assemblies can be operated as crosscurrent, countercurrent or cocurrent heat exchange units.
  • the heat exchanger is part of a cooling circuit, and the individual flow assemblies are supplied with the fluid via a further low-temperature and/or high-temperature cooling circuit.
  • the heat exchanger is used as an at least two-stage heat exchanger for use in land-based vehicles, aircraft or water-borne vehicles, in particular for exhaust-gas cooling for an internal combustion engine.
  • FIG. 1 shows a diagrammatic section through a heat exchange apparatus according to the invention with disk stacks arranged on top of one another as flow assemblies;
  • FIG. 2 shows a perspective partially exploded view of the two-stage heat exchanger from FIG. 1 ;
  • FIG. 3 shows an upper longitudinal section view of two types of disk for another embodiment of the heat exchange apparatus according to the invention
  • FIG. 4 shows an upper longitudinal section view of two types of disk for another exemplary embodiment of the heat exchange apparatus according to the invention
  • FIG. 5 shows an upper longitudinal section view of two types of disk for another exemplary embodiment of the heat exchange apparatus according to the invention
  • FIG. 6 shows a perspective ghosted view of another exemplary embodiment of the heat exchange apparatus according to the invention with flow assemblies arranged on top of one another;
  • FIG. 7 shows a perspective ghosted view of another exemplary embodiment of the heat exchange apparatus according to the invention with flow assemblies arranged next to one another;
  • FIG. 8 shows a perspective ghosted view of another exemplary embodiment of the heat exchange apparatus according to the invention with flow assemblies for a gaseous fluid 2 arranged on top of one another;
  • FIG. 9 shows a perspective ghosted view of another exemplary embodiment of the heat exchange apparatus according to the invention with flow assemblies arranged on top of one another and an alternative arrangement of an outflow device.
  • FIG. 10 shows a perspective ghosted view of another exemplary embodiment of the heat exchange apparatus according to the invention with flow assemblies arranged next to one another and a common fluid outflow device;
  • FIG. 11 shows two plan views of further exemplary embodiments of the heat exchange apparatus according to the invention.
  • FIG. 12 shows a cooling circuit in which the heat exchanger shown in FIG. 10 has been integrated.
  • FIGS. 1 and 2 show a diagrammatic section through a two-stage heat exchanger, the flow elements of which are disks and the heat exchange or flow assemblies of which are formed by disk stacks arranged on top of one another with a hollow disk arranged between them, and a perspective partially exploded view of the same heat exchanger, respectively.
  • the fluid 1 flows in at the top left via the inflow device 10 through the cover 5 into the flow assembly 120 and passes first of all through a second opening 100 with stamped projection through the top disk 22 into the top disk 12 as flow element for fluid 1 .
  • the fluid 1 has two possible directions of flow, namely on the one hand substantially diagonally over the top disk 12 to the first opening 102 illustrated in FIG. 2 , in which case along this path heat is exchanged with the fluid 2 flowing through the disks 22 located above and/or below.
  • fluid 1 passes through the first opening 102 through a corresponding stamped projection in the disk 22 below, which in turn has fluid 2 flowing through it, into the following disks 12 .
  • the first opening 101 illustrated in FIG. 2 also allows passage through the disk 22 below to the following disks 12 .
  • a direct flow path for fluid 1 directly through the first and second openings of the disks of both flow assemblies from the inflow device 10 to the outflow device 11 without the fluid 1 having to flow across the disks 12 of the lower flow assembly 130 is blocked by means of the partition wall 71 .
  • fluid 1 flows through a corresponding stamped projection in the blind disk 7 into the flow assembly 130 which is thereby connected in series with flow assembly 120 with regard to fluid 1 and which forms a second heat exchange stage, the disks 12 of which produce similar flow paths between the disks 32 through which fluid 3 flows, which now allows heat exchange between fluids 1 and 3 .
  • fluid 1 emerges from the two-stage heat exchanger 9 through the base 6 and the outflow device 11 .
  • fluid 2 flows through the disks 22 of the upper flow assembly 120 and fluid 3 flows through the disks 32 of the lower flow assembly 130 , with the outflow devices 21 and 31 for fluids 2 and 3 , respectively, corresponding to the inflow devices 20 and 30 , in each case being arranged on the same side, i.e. at the top for fluid 2 and at the bottom for fluid 3 .
  • the blind disk 7 which is empty of fluid, on the one hand allows thermal insulation of the flow assemblies 120 and 130 , which are preferably at different temperature levels, and on the other hand is also used to check the leaktightness and to prevent fluids 3 and 2 , in operation, from becoming mixed unnoticed in the event of leaks occurring in the two flow devices and/or fluid circuits.
  • the blind disk 7 is closed on all sides and has a small opening 8 to the outside on the side of its edge web. In the event of a leak, the respective fluid can flow out through this opening and does not penetrate into a different flow device.
  • Turbulence-generating fins or elements may be laid between the disks 12 , 22 and 32 , and/or the disks themselves have stamped-in fins, webs, and/or studs (not shown here).
  • a predetermined compressive strength is achieved by soldering the elevations in the form of the inlays or stamped indentations from disk to disk.
  • FIG. 3 illustrates an upper longitudinal section view of the two types of disk for a two-stage heat exchanger which is formed from disks and in which two fluids within the first type of disk 15 are separated by means of two parallel webs 77 , with in each case two smaller first openings 121 , 122 and 131 , 132 being provided as inlet and outlet for fluids 2 and 3 .
  • the first type of disk 15 has two larger second openings 113 and 114 with an encircling stamped projection as a passage opening for fluid 1 .
  • the second type of disk 25 in each case has two smaller second openings 123 and 124 , and 133 and 134 , with an encircling stamped projection for the passage of fluid 2 or 3 , respectively, through the second type of disk 25 , as well as two larger first openings 111 and 112 as inlet and outlet for fluid 1 into and out of the second type of disk 25 .
  • FIG. 4 illustrates another variant of the two types of disk for a two-stage heat exchanger formed from disks, in which fluids 2 and 3 are supplied via separate fluid inflow devices.
  • the inlet and passage of fluid 2 and 3 into or through the first type of disk 17 is effected by means of two smaller third openings 126 and 136 with an interrupted encircling stamped projection.
  • Two smaller second openings 125 and 135 with an encircling stamped projection allow fluids 2 and 3 to pass through. Fluids 2 and 3 are mixed within the first type of disk 17 and discharged via an additional, larger first opening 1231 .
  • An additional, larger second opening 1232 with encircling stamped projection located in the second type of disk 27 allows the mixture of fluids 2 and 3 to pass through the second type of disk 27 .
  • fluids 2 and 3 it is preferable for fluids 2 and 3 to be one fluid which, however, is at different temperature levels at the fluid inflow devices.
  • the mixing of the fluids means that there is no need for the flow devices to be separated by means of the webs 77 shown in FIG. 3 .
  • a characteristic of this embodiment is that the fluid 2 exchanges heat in cocurrent with fluid 1 , and fluid 3 exchanges heat in countercurrent with fluid 1 .
  • FIG. 5 represents an upper longitudinal section view of the two types of disk for a two-stage heat exchanger formed from disks as shown in FIG. 3 , with an additional, larger first opening 141 acting as inlet for a fluid 4 , preferably corresponding to fluid 1 , into the second type of disk 26 being provided in the second type of disk 26 .
  • fluid 4 it is preferable for fluid 4 to be at a different temperature level than fluid 1 and/or it may also contain, for example, corrosion-inhibiting additives.
  • FIG. 6 shows a perspective ghosted view of a two-stage heat exchanger, the flow elements of which are formed from flat tubes 40 and cavities 50 between them, the flow assemblies according to the invention for fluids 1 and 2 or fluids 1 and 3 being arranged on top of one another, and the fluid 1 whose temperature is to be controlled having its inlet and outlet on the same side.
  • Cooling fins 99 which increase the surface area and contribute to increasing the heat transfer coefficient between fluids 1 and 2 are indicated between the flat tubes. The compressive strength is increased by soldering the cooling fins 99 from flat tube to flat tube.
  • FIG. 7 shows a perspective ghosted view of a two-stage heat exchanger, the flow elements of which are formed from flat tubes 41 and from cavities 51 between them, with the flow assemblies according to the invention for fluids 1 and 2 or fluids 1 and 3 being arranged next to one another and the fluid 1 whose temperature is to be controlled having its inlet and outlet on opposite sides.
  • FIG. 8 shows a perspective ghosted view of a two-stage heat exchanger, the flow elements of which are formed from flat tubes and from cavities between them, with the flow assemblies according to the invention for fluids 1 and 2 or fluids 1 and 3 being arranged on top of one another, in accordance with FIG. 5 , but with the possibility of dispensing with a feed and a discharge and a housing for the flow assembly for fluids 1 and 2 , on account of the use of a gaseous fluid 2 , preferably the ambient air.
  • the direction of flow of the fluid 2 is indicated by the arrow illustrated next to the corresponding reference numeral.
  • FIG. 9 illustrates a perspective ghosted view of a two-stage heat exchanger in accordance with FIG. 5 , with the second heat exchange stage in the form of the flow assembly for fluids 1 and 3 being used or dispensed with depending on the alternative arrangement, indicated by the dashed outflow direction of fluid 1 , of the outflow device for fluid 1 on the same side as or the opposite side to the inflow for fluid 1 .
  • FIG. 10 illustrates a perspective ghosted view of a two-stage heat exchanger as shown in FIG. 7 , in which it is possible to use more flat tubes than in FIG. 7 .
  • a characteristic feature of this exemplary embodiment is that fluids 2 and 3 are one fluid, similarly to in FIG. 4 .
  • fluids 2 and 3 flow into the heat exchanger at different mass flow rates and temperatures. The two fluids mix with one another substantially in the common fluid collection device for fluids 2 and 3 and then flow out in mixed form via the common fluid outflow device.
  • FIG. 10 illustrates a perspective ghosted view of a two-stage heat exchanger as shown in FIG. 7 , in which it is possible to use more flat tubes than in FIG. 7 .
  • a characteristic feature of this exemplary embodiment is that fluids 2 and 3 are one fluid, similarly to in FIG. 4 .
  • fluids 2 and 3 flow into the heat exchanger at different mass flow rates and temperatures. The two fluids mix with one another substantially in the common fluid collection device for fluids 2 and 3 and then flow
  • FIG. 10 additionally shows a plan view of this exemplary embodiment which illustrates that the flow assembly comprising the fluids 1 and 3 is operated predominantly in cocurrent, the flow assembly comprising the fluids 1 and 2 is operated predominantly in countercurrent and not predominantly in crosscurrent in accordance with FIG. 7 .
  • This variant has advantages with regard to the cooling of exhaust gases.
  • HT flow assembly high-temperature flow assembly
  • LT flow assembly low-temperature flow assembly
  • LT flow assembly low-temperature flow assembly
  • a considerably smaller cool mass flow of coolant flows in countercurrent to the exhaust gas, which has already been greatly cooled.
  • countercurrent connection can be permitted, since there is no longer a risk of boiling, on account of the exhaust-gas cooling which has already taken place.
  • the countercurrent connection has the advantage that the heat exchange between exhaust gas and coolant is very high and the exhaust gas can be intensively cooled.
  • FIG. 11 shows that the position of the fluid inflow and outflow device, depending on the particular application, may also be set in such a way that the flow through the entire cooler is in countercurrent (A) or cocurrent (B). This is possible if there is no risk of the coolant(s) boiling.
  • FIG. 12 diagrammatically depicts the incorporation of a cooler 300 as shown in FIG. 10 for the case of exhaust gas cooling for an internal combustion engine 400 .
  • the LT flow assembly 311 of the cooler 300 has a low mass flow, which is cooled to a very low temperature by air in a separate low-temperature cooler 310 , flowing through it. This low mass flow is branched off from the main flow downstream of the main air cooler 320 and cooled in the low-temperature cooler 310 .
  • the HT flow assembly 321 of the two-stage cooler 300 has a greater mass flow at a higher temperature level, which is branched off directly from the mass flow of coolant flowing to the main air cooler 320 , flowing through it.
  • the two-stage heat exchanger prefferably has a dedicated coolant circuit, i.e. not to be incorporated in the actual engine cooling circuit. It is also possible for the LT circuit to have a dedicated pump.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US10/561,975 2003-06-25 2004-06-09 Device for multi-stage heat exchange and method for producing one such device Abandoned US20070125527A1 (en)

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DE10328746A DE10328746A1 (de) 2003-06-25 2003-06-25 Vorrichtung zum mehrstufigen Wärmeaustausch und Verfahren zur Herstellung einer derartigen Vorrichtung
DE10328746.0 2003-06-25
PCT/EP2004/006224 WO2004113815A1 (fr) 2003-06-25 2004-06-09 Dispositif d'echange thermique polyetage et procede de fabrication d'un tel dispositif

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CN (1) CN1813164A (fr)
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Cited By (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070221181A1 (en) * 2006-03-24 2007-09-27 Behr Gmbh & Co. Kg Device and method for cooling exhaust gas
US20080196679A1 (en) * 2005-09-06 2008-08-21 Behr Gmbh & Co. Kg Cooling System For a Motor Vehicle
US20080196871A1 (en) * 2005-06-29 2008-08-21 Alfa Laval Vicarb Condenser-Type Welded-Plate Heat Exchanger
US20080202735A1 (en) * 2005-07-19 2008-08-28 Peter Geskes Heat Exchanger
US20080245514A1 (en) * 2005-06-03 2008-10-09 Behr Gmbh & Co. Kg Charge Air Intercooler
US20080264609A1 (en) * 2007-04-26 2008-10-30 Behr Gmbh & Co. Kg Heat exchanger for exhaust gas cooling; method for operating a heat exchanger; system with a heat exchanger for exhaust gas cooling
US20090272515A1 (en) * 2008-04-30 2009-11-05 Wu Alan K Heat exchanger using air and liquid as coolants
US20100025023A1 (en) * 2007-01-31 2010-02-04 Michael Schmidt Heat exchanger, exhaust gas recirculation system, and use of a heat exchanger
US20100044019A1 (en) * 2008-08-25 2010-02-25 Denso Corporation Heat exchanger
US20100089548A1 (en) * 2007-04-11 2010-04-15 Viorel Braic Heat exchanger
US7703282B1 (en) * 2007-12-10 2010-04-27 Iea, Inc. Heat exchanger with horizontal flowing charge air cooler
US20100170452A1 (en) * 2007-07-04 2010-07-08 Darren William Ford Water heating apparatus, especially for pools
US20110072836A1 (en) * 2009-09-30 2011-03-31 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US20110072837A1 (en) * 2009-09-30 2011-03-31 Thermo Fisher Scientific (Asheville) Llc Refrigeration system mounted within a deck
US20110120678A1 (en) * 2009-11-12 2011-05-26 Autokuhler Gmbh & Co. Kg Heat exchanger network
US20110180235A1 (en) * 2008-07-31 2011-07-28 Georgia Tech Research Corporation Microscale heat or heat and mass transfer system
US20120060550A1 (en) * 2010-09-10 2012-03-15 Martin Mann Heat exchanger for a refrigeration system
US20120160450A1 (en) * 2010-12-24 2012-06-28 Dana Canada Corporation Fluid Flow Mixing Box With Fluid Flow Control Device
US20130126149A1 (en) * 2011-11-22 2013-05-23 Hyundai Motor Company Heat exchanger for vehicle
US20130140017A1 (en) * 2011-12-06 2013-06-06 Hyundai Motor Company Heat Exchanger for Vehicle
US20130146265A1 (en) * 2011-12-08 2013-06-13 Hyundai Motor Company Condenser for vehicle
US20130192806A1 (en) * 2012-01-31 2013-08-01 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Multilayer heat exchanger and heat exchange system
US20130224613A1 (en) * 2012-02-27 2013-08-29 Dana Canada Corporation Method and System for Cooling Charge Air for a Fuel Cell, and Three-Fluid Charge Air Cooler
US20150040875A1 (en) * 2013-08-12 2015-02-12 Hyundai Motor Company Cooling apparatus and cooling control method for egr gas and engine oil
US8986430B2 (en) 2009-08-03 2015-03-24 Fluor Technologies Corporation Low-energy waste gas cooling using direct contact condenser
US20150114594A1 (en) * 2012-04-20 2015-04-30 Alfa Laval Corporate Ab A heat exchanger plate and a plate heat exchanger
US20150276320A1 (en) * 2014-03-25 2015-10-01 Modine Manufacturing Company Heat recovery system having a plate heat exchanger
US20150323231A1 (en) * 2012-12-21 2015-11-12 Valeo Systemes Thermiques Condenser with a refrigerant supply for an air-conditioning circuit
US20160054038A1 (en) * 2013-05-08 2016-02-25 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
US20160298874A1 (en) * 2013-11-20 2016-10-13 Gas Point S.R.L. Plate Heat Exchanger, in Particular for Condensing Boilers
US20160356205A1 (en) * 2015-06-08 2016-12-08 Modine Manufacturing Company Charge Air Cooler and Method
WO2017100521A1 (fr) * 2015-12-10 2017-06-15 Laird Technologies, Inc. Échangeurs de chaleur
EP3103985A4 (fr) * 2014-01-30 2017-09-06 Yanmar Co., Ltd. Moteur
US20180094870A1 (en) * 2016-09-30 2018-04-05 Mahle Filter Systems Japan Corporation Heat exchanger
US9945614B2 (en) 2012-11-29 2018-04-17 Mahle International Gmbh Heat exchanger with high pressure phase refrigerant channel, low pressure phase refrigerant channel and coolant channel
US10281222B2 (en) 2016-09-30 2019-05-07 Mahle Filter Systems Japan Corporation Heat exchanger
US20190204012A1 (en) * 2018-01-04 2019-07-04 Hamilton Sundstrand Corporation Curved heat exchanger
WO2020136092A3 (fr) * 2018-12-28 2020-08-13 Mahle Filter Systems Japan Corporation Échangeur de chaleur et système d'échange de chaleur de véhicule
US20210333051A1 (en) * 2018-10-12 2021-10-28 Vahterus Oy A plate heat exchanger arrangement
FR3111971A1 (fr) * 2020-06-29 2021-12-31 Valeo Systemes Thermiques Echangeur thermique pour véhicule automobile
US11326520B2 (en) * 2019-06-04 2022-05-10 Doosan Heavy Industries & Construction Co., Ltd. Heat exchange apparatus and gas turbine having the same

Families Citing this family (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2886340B1 (fr) * 2005-05-31 2010-11-12 Valeo Systemes Thermiques Refroidisseur d'air d'admission pour un moteur thermique turbocompresse a deux etages de suralimentation et circuit d'air correspondant
US20080251242A1 (en) * 2005-10-20 2008-10-16 Behr Gmbh & Co. Kg Heat Exchanger
DE202008017767U1 (de) * 2008-01-15 2010-06-17 Kioto Clear Energy Ag Wärmetauscher
FR2935475B1 (fr) * 2008-08-27 2012-12-07 Valeo Systemes Thermiques Echangeur de chaleur pour le refroidissement d'un fluide, en particulier des gaz d'echappement recircules d'un moteur thermique
PT2161525T (pt) * 2008-09-08 2016-07-26 Balcke-Dürr GmbH Permutador de calor de construção modular
FR2936304B1 (fr) * 2008-09-25 2015-08-07 Valeo Systemes Thermiques Element d'echange de chaleur d'un faisceau d'echange de chaleur d'un echangeur de chaleur
SE533056C2 (sv) * 2008-11-28 2010-06-15 Scania Cv Ab Laddluftkylare för kylning av luft som leds till en överladdad förbränningsmotor
DE102009034723A1 (de) * 2009-07-24 2011-01-27 Behr Gmbh & Co. Kg Wärmetauscher und Aufladesystem
DE102010063324A1 (de) * 2010-12-17 2012-06-21 Behr Gmbh & Co. Kg Vorrichtung zur Kühlung von Ladeluft, System zum Konditionieren von Ladeluft und Ansaugmodul für einen Verbrennungsmotor
JP5496369B2 (ja) * 2011-01-18 2014-05-21 三菱電機株式会社 積層型熱交換器及びそれを搭載したヒートポンプシステム
CN103090707B (zh) * 2011-10-31 2015-11-25 杭州三花研究院有限公司 板式换热器
CN103090716B (zh) * 2011-10-31 2015-11-25 杭州三花研究院有限公司 用于板式换热器的流体分配器
CN103185470A (zh) * 2012-03-05 2013-07-03 哈尔滨工大金涛科技股份有限公司 流道式免焊污水换热器
CN102853695A (zh) * 2012-09-28 2013-01-02 陈建平 一种多流程板式换热器提高换热效率的方法及产品
CN102980328B (zh) * 2012-12-10 2015-04-22 丹佛斯（杭州）板式换热器有限公司 板式换热器
CN103868394B (zh) * 2012-12-13 2017-06-27 浙江三花汽车零部件有限公司 换热器的流通板、换热器的换热单元及换热器
FR3001795B1 (fr) * 2013-02-07 2016-06-10 Delphi Automotive Systems Lux Agencement d’echangeurs thermiques a plaques
WO2015085150A1 (fr) 2013-12-05 2015-06-11 Gentherm Incorporated Systèmes et procédés pour sièges climatisés
DE102014201956A1 (de) 2014-02-04 2015-08-06 MAHLE Behr GmbH & Co. KG Rohranordnung für einen Ladeluftkühler
KR102051617B1 (ko) 2014-02-14 2019-12-03 젠썸 인코포레이티드 전도식 대류식 기온 제어 시트
DE102014212906A1 (de) 2014-07-03 2016-01-07 Volkswagen Aktiengesellschaft Ladeluftkühler mit einem Plattenwärmetauscher
US11857004B2 (en) 2014-11-14 2024-01-02 Gentherm Incorporated Heating and cooling technologies
US11639816B2 (en) 2014-11-14 2023-05-02 Gentherm Incorporated Heating and cooling technologies including temperature regulating pad wrap and technologies with liquid system
EP3218942B1 (fr) 2014-11-14 2020-02-26 Charles J. Cauchy Technologies de chauffage et de refroidissement
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DE102016203951A1 (de) * 2016-03-10 2017-09-14 Mahle International Gmbh Wärmeübertrager
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JP2018084393A (ja) * 2016-11-25 2018-05-31 株式会社ノーリツ 熱交換器及び貯湯給湯装置
IT201700113260A1 (it) * 2017-10-09 2019-04-09 Zilmet S P A Gruppo scambiatore compatto a circuiti multipli
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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3117624A (en) * 1959-06-22 1964-01-14 Separator Ab Plate heat exchanger
US4372375A (en) * 1979-08-08 1983-02-08 The A.P.V. Company Limited Heat exchanger
US4763488A (en) * 1980-05-26 1988-08-16 University Of Sydney Plate heat exchanger for separating vapor and liquid phases
US5755280A (en) * 1995-05-04 1998-05-26 Packinox Plate-type heat exchanger
US5896834A (en) * 1996-12-24 1999-04-27 Behr Gmbh & Co. Heat transfer arrangement and method of making same
US6044902A (en) * 1997-08-20 2000-04-04 Praxair Technology, Inc. Heat exchange unit for a cryogenic air separation system
US6089313A (en) * 1996-07-16 2000-07-18 Packinox Apparatus for exchanging heat between at least three fluids
US6347662B1 (en) * 1999-02-01 2002-02-19 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger, in particular plate heat exchanger for an air separation unit
US6515874B2 (en) * 1999-10-11 2003-02-04 Infineon Technologies Ag Clocked power supply
US6893619B1 (en) * 2000-09-13 2005-05-17 Ford Global Technologies, Llc Plate-frame heat exchange reactor with serial cross-flow geometry

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69125819T2 (de) * 1990-09-28 1997-12-11 Matsushita Refrigeration Laminatwärmetauscher
FR2757257B1 (fr) * 1996-12-13 1999-03-05 Packinox Sa Echangeur thermique a plaques
DE19824026A1 (de) * 1998-05-29 1999-12-02 Behr Gmbh & Co Kühler
JP3936088B2 (ja) * 1998-12-08 2007-06-27 大阪瓦斯株式会社 三流体用プレート式熱交換器、及び、その製造方法
US6817406B1 (en) * 1999-03-04 2004-11-16 Ebara Corporation Plate type heat exchanger
JP2000274968A (ja) * 1999-03-24 2000-10-06 Ebara Corp プレート式熱交換器
WO2001048432A1 (fr) * 1999-12-27 2001-07-05 Sumitomo Precision Products Co., Ltd. Echangeur thermique haute temperature a ailette plate
DE10049890B4 (de) * 2000-10-10 2007-02-22 Behr Gmbh & Co. Kg Stapelscheiben-Wärmeübertrager
DE10112710A1 (de) * 2001-03-16 2002-09-26 Modine Mfg Co Plattenwärmetauscher und Herstellungsverfahren
US6516874B2 (en) * 2001-06-29 2003-02-11 Delaware Capital Formation, Inc. All welded plate heat exchanger
DE10137103A1 (de) * 2001-07-30 2003-02-13 Linde Ag Mehrstöckiger Kondensator-Verdampfer
FR2843449B1 (fr) * 2002-08-09 2005-05-06 Valeo Thermique Moteur Sa Echangeur de chaleur pour le circuit d'air d'admission d'un moteur thermique

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3117624A (en) * 1959-06-22 1964-01-14 Separator Ab Plate heat exchanger
US4372375A (en) * 1979-08-08 1983-02-08 The A.P.V. Company Limited Heat exchanger
US4763488A (en) * 1980-05-26 1988-08-16 University Of Sydney Plate heat exchanger for separating vapor and liquid phases
US5755280A (en) * 1995-05-04 1998-05-26 Packinox Plate-type heat exchanger
US6089313A (en) * 1996-07-16 2000-07-18 Packinox Apparatus for exchanging heat between at least three fluids
US5896834A (en) * 1996-12-24 1999-04-27 Behr Gmbh & Co. Heat transfer arrangement and method of making same
US6044902A (en) * 1997-08-20 2000-04-04 Praxair Technology, Inc. Heat exchange unit for a cryogenic air separation system
US6347662B1 (en) * 1999-02-01 2002-02-19 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger, in particular plate heat exchanger for an air separation unit
US6515874B2 (en) * 1999-10-11 2003-02-04 Infineon Technologies Ag Clocked power supply
US6893619B1 (en) * 2000-09-13 2005-05-17 Ford Global Technologies, Llc Plate-frame heat exchange reactor with serial cross-flow geometry

Cited By (73)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080245514A1 (en) * 2005-06-03 2008-10-09 Behr Gmbh & Co. Kg Charge Air Intercooler
US20080196871A1 (en) * 2005-06-29 2008-08-21 Alfa Laval Vicarb Condenser-Type Welded-Plate Heat Exchanger
US8443869B2 (en) * 2005-06-29 2013-05-21 Alfa Laval Vicarb Condenser-type welded-plate heat exchanger
US20080202735A1 (en) * 2005-07-19 2008-08-28 Peter Geskes Heat Exchanger
US20080196679A1 (en) * 2005-09-06 2008-08-21 Behr Gmbh & Co. Kg Cooling System For a Motor Vehicle
US8028522B2 (en) 2005-09-06 2011-10-04 Behr Gmbh & Co. Kg Cooling system for a motor vehicle
US20070221181A1 (en) * 2006-03-24 2007-09-27 Behr Gmbh & Co. Kg Device and method for cooling exhaust gas
US7478630B2 (en) * 2006-03-24 2009-01-20 Behr Gmbh & Co. Kg Device and method for cooling exhaust gas
US20100025023A1 (en) * 2007-01-31 2010-02-04 Michael Schmidt Heat exchanger, exhaust gas recirculation system, and use of a heat exchanger
US8627882B2 (en) 2007-01-31 2014-01-14 Behr Gmbh & Co. Kg Heat exchanger, exhaust gas recirculation system, and use of a heat exchanger
US20100089548A1 (en) * 2007-04-11 2010-04-15 Viorel Braic Heat exchanger
US9097466B2 (en) * 2007-04-11 2015-08-04 MAHLE Behr GmbH & Co. KG Heat exchanger
US20080264609A1 (en) * 2007-04-26 2008-10-30 Behr Gmbh & Co. Kg Heat exchanger for exhaust gas cooling; method for operating a heat exchanger; system with a heat exchanger for exhaust gas cooling
US20100170452A1 (en) * 2007-07-04 2010-07-08 Darren William Ford Water heating apparatus, especially for pools
US7703282B1 (en) * 2007-12-10 2010-04-27 Iea, Inc. Heat exchanger with horizontal flowing charge air cooler
US20090272515A1 (en) * 2008-04-30 2009-11-05 Wu Alan K Heat exchanger using air and liquid as coolants
US8225852B2 (en) 2008-04-30 2012-07-24 Dana Canada Corporation Heat exchanger using air and liquid as coolants
US20110180235A1 (en) * 2008-07-31 2011-07-28 Georgia Tech Research Corporation Microscale heat or heat and mass transfer system
US8651170B2 (en) * 2008-08-25 2014-02-18 Denso Corporation Exhaust gas heat exchanger
US20100044019A1 (en) * 2008-08-25 2010-02-25 Denso Corporation Heat exchanger
US8986430B2 (en) 2009-08-03 2015-03-24 Fluor Technologies Corporation Low-energy waste gas cooling using direct contact condenser
US8011191B2 (en) 2009-09-30 2011-09-06 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US8011201B2 (en) * 2009-09-30 2011-09-06 Thermo Fisher Scientific (Asheville) Llc Refrigeration system mounted within a deck
US20110072836A1 (en) * 2009-09-30 2011-03-31 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US20110072837A1 (en) * 2009-09-30 2011-03-31 Thermo Fisher Scientific (Asheville) Llc Refrigeration system mounted within a deck
US9835360B2 (en) 2009-09-30 2017-12-05 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US10072876B2 (en) 2009-09-30 2018-09-11 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US10845097B2 (en) 2009-09-30 2020-11-24 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US10816243B2 (en) 2009-09-30 2020-10-27 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
US20110120678A1 (en) * 2009-11-12 2011-05-26 Autokuhler Gmbh & Co. Kg Heat exchanger network
US20120060550A1 (en) * 2010-09-10 2012-03-15 Martin Mann Heat exchanger for a refrigeration system
US9581367B2 (en) * 2010-10-09 2017-02-28 Modine Manufacturing Company Multi-fluid plate heat exchanger for a refrigeration system
US10126068B2 (en) * 2010-12-24 2018-11-13 Dana Canada Corporation Fluid flow heat transfer box for multiple fluids with fluid flow control device
US20120160450A1 (en) * 2010-12-24 2012-06-28 Dana Canada Corporation Fluid Flow Mixing Box With Fluid Flow Control Device
US9322319B2 (en) * 2011-11-22 2016-04-26 Hyundai Motor Company Heat exchanger for vehicle
CN103134358A (zh) * 2011-11-22 2013-06-05 现代自动车株式会社 汽车热交换器
US20130126149A1 (en) * 2011-11-22 2013-05-23 Hyundai Motor Company Heat exchanger for vehicle
US20130140017A1 (en) * 2011-12-06 2013-06-06 Hyundai Motor Company Heat Exchanger for Vehicle
US9234604B2 (en) * 2011-12-06 2016-01-12 Hyundai Motor Company Heat exchanger for vehicle
US9140473B2 (en) * 2011-12-08 2015-09-22 Hyundai Motor Company Condenser for vehicle
US20130146265A1 (en) * 2011-12-08 2013-06-13 Hyundai Motor Company Condenser for vehicle
EP2623910A3 (fr) * 2012-01-31 2018-04-11 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Échangeur thermique multicouche et système d'échange de chaleur
US20130192806A1 (en) * 2012-01-31 2013-08-01 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Multilayer heat exchanger and heat exchange system
US9343755B2 (en) * 2012-02-27 2016-05-17 Dana Canada Corporation Method and system for cooling charge air for a fuel cell, and three-fluid charge air cooler
US20130224613A1 (en) * 2012-02-27 2013-08-29 Dana Canada Corporation Method and System for Cooling Charge Air for a Fuel Cell, and Three-Fluid Charge Air Cooler
US20150114594A1 (en) * 2012-04-20 2015-04-30 Alfa Laval Corporate Ab A heat exchanger plate and a plate heat exchanger
US9829259B2 (en) * 2012-04-20 2017-11-28 Alfa Laval Corporate Ab Heat exchanger plate and a plate heat exchanger
US9945614B2 (en) 2012-11-29 2018-04-17 Mahle International Gmbh Heat exchanger with high pressure phase refrigerant channel, low pressure phase refrigerant channel and coolant channel
US10254022B2 (en) * 2012-12-21 2019-04-09 Valeo Systemes Thermiques Condenser with a refrigerant supply for an air-conditioning circuit
US20150323231A1 (en) * 2012-12-21 2015-11-12 Valeo Systemes Thermiques Condenser with a refrigerant supply for an air-conditioning circuit
US20160054038A1 (en) * 2013-05-08 2016-02-25 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
US9791189B2 (en) * 2013-05-08 2017-10-17 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
US20150040875A1 (en) * 2013-08-12 2015-02-12 Hyundai Motor Company Cooling apparatus and cooling control method for egr gas and engine oil
US9512753B2 (en) * 2013-08-12 2016-12-06 Hyundai Motor Company Cooling apparatus and cooling control method for EGR gas and engine oil
US10458679B2 (en) * 2013-11-20 2019-10-29 Gas Point S.R.L. Plate heat exchanger, in particular for condensing boilers
US20160298874A1 (en) * 2013-11-20 2016-10-13 Gas Point S.R.L. Plate Heat Exchanger, in Particular for Condensing Boilers
EP3103985A4 (fr) * 2014-01-30 2017-09-06 Yanmar Co., Ltd. Moteur
US9823025B2 (en) * 2014-03-25 2017-11-21 Modine Manufacturing Company Heat recovery system having a plate heat exchanger
US20150276320A1 (en) * 2014-03-25 2015-10-01 Modine Manufacturing Company Heat recovery system having a plate heat exchanger
US10196964B2 (en) * 2015-06-08 2019-02-05 Modine Manufacturing Company Charge air cooler and method
US20160356205A1 (en) * 2015-06-08 2016-12-08 Modine Manufacturing Company Charge Air Cooler and Method
WO2017100521A1 (fr) * 2015-12-10 2017-06-15 Laird Technologies, Inc. Échangeurs de chaleur
US10281222B2 (en) 2016-09-30 2019-05-07 Mahle Filter Systems Japan Corporation Heat exchanger
US10378827B2 (en) * 2016-09-30 2019-08-13 Mahle Filter Systems Japan Corporation Heat exchanger
US20180094870A1 (en) * 2016-09-30 2018-04-05 Mahle Filter Systems Japan Corporation Heat exchanger
US20190204012A1 (en) * 2018-01-04 2019-07-04 Hamilton Sundstrand Corporation Curved heat exchanger
US10670346B2 (en) * 2018-01-04 2020-06-02 Hamilton Sundstrand Corporation Curved heat exchanger
US11867468B2 (en) * 2018-10-12 2024-01-09 Vahterus Oy Plate heat exchanger arrangement
US20210333051A1 (en) * 2018-10-12 2021-10-28 Vahterus Oy A plate heat exchanger arrangement
WO2020136092A3 (fr) * 2018-12-28 2020-08-13 Mahle Filter Systems Japan Corporation Échangeur de chaleur et système d'échange de chaleur de véhicule
US11326520B2 (en) * 2019-06-04 2022-05-10 Doosan Heavy Industries & Construction Co., Ltd. Heat exchange apparatus and gas turbine having the same
WO2022002617A1 (fr) * 2020-06-29 2022-01-06 Valeo Systemes Thermiques Echangeur thermique pour véhicule automobile
FR3111971A1 (fr) * 2020-06-29 2021-12-31 Valeo Systemes Thermiques Echangeur thermique pour véhicule automobile

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JP2007506928A (ja) 2007-03-22
BRPI0411930A (pt) 2006-08-15
MXPA05014018A (es) 2006-03-17
CN1813164A (zh) 2006-08-02
DE10328746A1 (de) 2005-01-13
EP1642076A1 (fr) 2006-04-05
WO2004113815A1 (fr) 2004-12-29

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