EP1642076A1 - Dispositif d'echange thermique polyetage et procede de fabrication d'un tel dispositif - Google Patents

Dispositif d'echange thermique polyetage et procede de fabrication d'un tel dispositif

Info

Publication number
EP1642076A1
EP1642076A1 EP04739733A EP04739733A EP1642076A1 EP 1642076 A1 EP1642076 A1 EP 1642076A1 EP 04739733 A EP04739733 A EP 04739733A EP 04739733 A EP04739733 A EP 04739733A EP 1642076 A1 EP1642076 A1 EP 1642076A1
Authority
EP
European Patent Office
Prior art keywords
flow
fluid
elements
particular according
fluids
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP04739733A
Other languages
German (de)
English (en)
Inventor
Markus Flik
Jochen Eitel
Peter Geskes
Michael LÖHLE
Ulrich Maucher
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1642076A1 publication Critical patent/EP1642076A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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 a device for multi-stage heat exchange and a method for producing such a device.
  • BESTATIGUNGSKOPIE two other fluids are available, which are at two different temperature levels.
  • the disadvantage of the two-stage temperature control of fluids is that the use of two conventionally connected heat exchangers is associated with significantly higher costs and a larger space requirement.
  • the invention is therefore based on the object of creating a device in which the at least two-stage cooling or heating of a fluid can be implemented in a compact and cost-effective manner.
  • the object is achieved according to the invention by a device according to claim 1.
  • the method according to the invention for producing such a device is the subject of claim 20.
  • Preferred embodiments and further developments are the subject of the subclaims.
  • the heat exchange device has at least three flow devices through which at least one flowable medium (fluid) flows. After flowing through the individual flow devices, at least two of the at least three fluids can also be mixed in the heat exchanger and discharged together.
  • the greater part of the heat output is preferably transferred in the first flow assembly of the cooling or heating, preferably over 60%, in particular up to 70%.
  • flowable media or fluids are understood to mean liquid and / or gaseous media of any viscosity, such as, in particular, but not exclusively, oils, liquids, in particular high heat of vaporization, water, air or gases, and refrigerants which can evaporate or condense.
  • the flowable media can also contain additives, for example to inhibit corrosion.
  • the device 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 essentially liquid fluids flow.
  • At least two flow modules are provided, each with at least two flow elements, which are arranged in such a way that different fluids flow through them alternately. Furthermore, the flow elements belonging to a flow device through which essentially liquid fluids flow are connected in a positive and / or material and / or non-positive, essentially gas and liquid tight manner to at least one fluid collection and / or distribution device.
  • the main flow directions of all fluids in the flow elements lie in mutually parallel planes. Furthermore, two flow assemblies of the device according to the invention are directly connected in series in a form-fitting and / or material and / or non-positive manner and / or in a flow-connected manner via a fluid distribution device, at least with respect to one flow device.
  • a device is understood to mean, by which a “liquid or gaseous medium flow can flow and or which, in the case of substantially liquid fluids flowing through flow means, gas substantially and liquid-tightly against the surrounding space delimited is ,
  • the flow devices are formed by flow elements connected in series and / or in parallel.
  • these flow elements are formed, at least in sections, by in particular, but not exclusively, hollow disks, flat tubes, plates and / or layers.
  • Hollow disks, plates or layers are understood to be essentially gas- and liquid-tight hollow bodies with inlet and outlet openings, their length and width extension is significantly larger than their height.
  • flat tubes are understood to be tubes which have a long side in cross section and a side which is considerably shorter than this long side.
  • the flow elements can have one or more flow channels for the medium flowing or flowing through. They can run in a straight line, but can also have several curved sections. In addition, the flow elements can also have twisted sections, that is to say those sections in which the flow element is twisted or twisted in itself.
  • a fluid distribution and / or collection device in the context of the invention in the case of the flow devices through which essentially liquid fluids are understood are essentially gas- and liquid-tight hollow bodies, in which fluids can flow or flow and in which these are collected. At the same time, however, these fluid distribution and / or collection devices can also serve to distribute the respective fluids over several flow elements or to collect them again from different flow elements.
  • flow-connected is understood to mean that a fluid can flow or flow between the flow elements, fluid distribution and / or collection devices.
  • substantially gas-tight and liquid-tight means in particular, but not exclusively, a division by separation devices, so that no fluid can flow or flow past the respective separation device along certain directions of the flow devices, flow elements, and fluid distribution and / or collection devices.
  • the flow or main flow direction of a fluid is understood to mean the direction which the fluid preferably takes within a flow device, a flow element and / or a fluid distribution and / or collection device, with changes in direction of the fluid which are locally limited being disregarded.
  • the fluid distribution and / or collection devices are collectors and / or distribution pipes in the broader sense.
  • At least one fluid collection and / or distribution device is formed, at least in part, from openings arranged in the longitudinal direction in the flow elements, a first number of simple openings forming fluid inlets and outlets to adjacent flow elements, and sealing devices around a second number of openings are arranged to form passages in the corresponding flow element, through which adjacent flow elements are fluidly connected.
  • the first number of openings arranged in the longitudinal direction in flow elements is understood to mean, in particular, but not exclusively, round punched holes or boreholes which are provided in the substantially longer and wider sides of the flow elements.
  • Openings in flow elements are understood in the context of the invention, in particular, but not exclusively, to be material and / or form-fitting and / or non-positively adjoining features in the corresponding flow element or sealing rings.
  • Partition walls are preferably provided in a gas-tight and liquid-tight manner in individual openings, as a result of which preferred control of the
  • Fluid distribution is made possible by, in particular, but not exclusively, stacking of the same plate-shaped flow elements.
  • turbulence-generating and / or increasing shaped elements are preferably provided within the flow device, which are used in particular to increase the heat transfer coefficient between the fluids contribute different flow devices.
  • These shaped elements which generate or increase turbulence are preferably taken from a group which contains, in particular, but not exclusively, ribs, webs, knobs, furrows, embossings or cutouts.
  • the turbulence-generating and / or increasing shaped elements are arranged in at least one and / or between at least two flow elements.
  • the profile of at least one flow element preferably has turbulence-generating and / or -increasing properties.
  • turbulence inserts are provided, preferably for insertion in at least one flow element, in particular, but not exclusively, in hollow disks, plates and / or layers.
  • turbulence inserts are understood, in particular, but not exclusively, to be sheets which form and / or increase turbulence-shaped elements such as Have ribs, webs, knobs, furrows, impressions and / or millings and are inserted into the flow elements to simplify production, preferably with external dimensions corresponding to the internal dimensions of the flow elements and to the distribution devices with sealing device, in particular corresponding to the characteristics in the flow elements. , the punched holes for the passages through which adjacent flow elements are fluidly connected.
  • At least two flow elements through which different fluids flow are connected to one another in a positive and / or material and / or non-positive manner along the longitudinal side.
  • At least two flow elements flowed through by the same fluid are arranged on the longitudinal side, in particular, but not exclusively, the intermediate or wise profile-specific turbulence-generating and / or increasing shaped elements connected in such a way that at least one cavity thereby created between these flow elements forms a flow element for another fluid.
  • connections of the flow elements are taken from a group which contains soldered connections, welded connections or adhesive connections.
  • At least one sealing element is provided at least between two flow elements through which different fluids flow, which is formed in particular, but not exclusively, by fluid-empty hollow elements and / or separating elements.
  • At least one sealing element is preferably arranged between flow assemblies designed in series.
  • At least one of the sealing elements in particular, but not exclusively, a fluid-empty hollow element, has a tightness control opening. This proves to be particularly advantageous during the manufacture of the device according to the invention. If the individual flow devices are then individually filled with their respective fluids and if the respective flow device should prove to be leaky due to, for example, an error in the manufacturing process, there is the possibility that the escaping fluid collects in the initially fluid-empty hollow or blind element and proves the leakage through its outlet at the leakage control opening.
  • each individual flow device with its corresponding fluid also makes it possible to check the gas and liquid tightness according to the invention of the various flow devices against one another by transferring the respectively filled fluid into a second flow device.
  • at least one of the sealing elements has at least one tightness sensor which, in the event of fluid leakage from one of the flow devices, causes a physically perceptible signal to be output.
  • At least two flow assemblies are separated from one another in a substantially thermally insulating manner, for example by means of an arrangement which is only spatially spaced apart, and / or also by means of fluid-hollow elements arranged in particular between them.
  • shaped elements are provided within at least one flow element, which change the main flow direction of the fluid flowing in the flow element at least in sections.
  • At least one flow device is mixed with a fluid, in particular, but not exclusively, via at least one further inflow device, which fluid corresponds to the fluid in this flow device.
  • the inventive series connection of at least two flow assemblies with respect to at least one flow device takes place in such a way that the temperature gradients 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 each with respect to the other, the flow assemblies of the Flow assembly series connection flowing fluids are essentially always smaller in amount.
  • fluids are mixed in the heat exchanger, different proportions of the total fluid being able to flow through different flow elements.
  • a further preferred embodiment allows a fluid to be separated in the heat exchanger, with different portions of the divided fluid being able to flow through different flow elements.
  • the heat exchange in individual flow assemblies takes place via condensation or evaporation of a fluid.
  • the individual flow modules can be operated as cross, countercurrent or cocurrent heat exchange units.
  • the heat exchanger is part of a cooling circuit and the supply of the individual flow assemblies with the fluid takes place via a further low and / or high temperature cooling circuit.
  • the heat exchanger is used as an at least two-stage heat exchanger for use in land, air or water vehicles, in particular for exhaust gas cooling for an internal combustion engine.
  • Figure 1 is a schematic section through a heat exchange device according to the invention with stacked disks as flow assemblies.
  • FIG. 2 shows a perspective partial exploded view of the two-stage heat exchanger according to FIG. 1; 3 shows an upper longitudinal sectional view of two types of disks for a further embodiment of the heat exchange device according to the invention;
  • FIG. 4 shows an upper longitudinal sectional view of two types of disks for a further exemplary embodiment of the heat exchange device according to the invention
  • FIG. 5 shows an upper longitudinal sectional view of two types of disks for a further exemplary embodiment of the heat exchange device according to the invention
  • FIG. 6 is a perspective view of a further exemplary embodiment of the heat exchange device according to the invention with flow assemblies arranged one above the other;
  • FIG. 7 is a perspective view of a further exemplary embodiment of the heat exchange device according to the invention with flow assemblies arranged next to one another;
  • FIG. 8 shows a perspective view of a further exemplary embodiment of the heat exchange device according to the invention with flow assemblies for a gaseous fluid 2 arranged one above the other;
  • FIG. 9 is a perspective view of a further exemplary embodiment of the heat exchange device according to the invention with flow assemblies arranged one above the other and an alternative arrangement of a discharge device.
  • FIG. 10 shows a perspective view of a further exemplary embodiment of the heat exchange device according to the invention with flow assemblies arranged next to one another and a common fluid drainage device;
  • FIG. 11 shows two plan views of further exemplary embodiments of the heat exchange device according to the invention.
  • FIG. 12 shows a cooling circuit in which the heat exchanger according to FIG. 10 has been integrated.
  • FIGS. 1 and 2 show a schematic 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 stacked disks with a hollow disk arranged therebetween, or a partial exploded perspective view of the same heat exchanger.
  • the fluid 1 flows in the top left via the inflow device 10 through the cover 5 into the flow assembly 120 and first passes through a second opening 100 with a shape through the uppermost disk 22 into the uppermost disk 12 as a flow element for fluid 1 there are two possible flow directions for the fluid 1, namely on the one hand essentially diagonally over the uppermost disk 12 to the first opening 102 shown in FIG. 2, a heat exchange taking place along this path with the fluid 2 flowing through the disks 22 above and below.
  • Fluid 1 then passes through the first opening 102 through a corresponding configuration in the underlying disk 22, through which fluid 2 again flows, into the subsequent disks 12.
  • the first opening 101 shown in FIG. 2 also allows passage through the underlying disk 22 to the subsequent disks 12.
  • a direct flow path for fluid 1 is directly through the partition wall 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 over the disks 12 of the lower flow assembly 130 71 blocked.
  • fluid 1 flows from the bottom disk 12 of the upper flow assembly 120 through a corresponding configuration in the blind disk 7 into the flow assembly 130 which is thereby connected in series with the flow assembly 120 with respect to fluid 1 and which forms a second heat exchange stage, through the disks 12 of which analogue flows flow paths between the discs 32 through which fluid 3 flows, which now permits heat exchange between the fluids 1 and 3.
  • partition walls 72 and 73 as well as 74 and 75 separate the disks 22 as an essential part of the flow device of fluid 2 from the disks 32 as an essential part of the flow device of fluid 3. Finally, fluid 1 passes through the bottom 6 and the drain device 11 from the two-stage heat exchanger 9 out.
  • fluid 2 flows through the disks 22 of the upper flow assembly 120 or fluid 3 through the disks 32 of the lower flow assembly 130, the outflow devices 21 and 31 corresponding to the inflow devices 20 and 30 for fluid 2 and 3 respectively being arranged on the same side, i.e. for fluid 2 above and for fluid 3 below.
  • the fluid-empty blind disk 7 allows thermal insulation of the flow assemblies 120 and 130, which are preferably at different temperature levels, and on the other hand serves to check the tightness and to avoid that fluids 3 and 2 go unnoticed during operation in the event of a leak in both flow devices or fluid circuits mix.
  • the blind disk 7 is closed from all sides and has a small opening 8 to the outside on one 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 another flow device.
  • Turbulence-generating ribs or elements can be inserted between the disks 12, 22 and 32 and / or the disks themselves have embossed ribs, webs and / or knobs (not shown here).
  • a predetermined compressive strength is achieved by soldering the elevations in the form of the inserts or impressions from pane to pane.
  • FIG. 3 shows an upper longitudinal sectional view of the two types of plates for a two-stage heat exchanger formed from plates, in which the separation of two fluids within the first disk type 15 takes place by means of two parallel webs 77, two smaller first openings 121, 122 and 131, 132 being provided for the inlet and outlet for fluid 2 and 3, respectively. Furthermore, the first disk type 15 has two larger second openings 113 and 114 with a circumferential configuration as a passage opening for fluid 1.
  • the second disc type 25 has two smaller second openings 123 and 124 and 133 and 134 with circumferential characteristics for the passage of fluid 2 and 3 through the second disc type 25 and two larger first openings 111 and 112 for the inlet and outlet for fluid 1 in or out of the second disc type 25.
  • Fluid 2 and 3 are supplied via separate fluid inflow devices.
  • Fluid 2 and 3 respectively, enter and pass through the first disk type 17 via two smaller third openings 126 and 136 with an interrupted circumferential configuration.
  • the passage of fluid 2 or 3 through the second disc type 27 allows two smaller second openings 125 and 135 with a circumferential configuration.
  • Fluid 2 and 3 are mixed within the first disk type 17 and discharged via an additional larger first opening 1231.
  • FIG. 5 shows an upper longitudinal sectional view of the two disk types for a two-stage heat exchanger formed from disks according to FIG.
  • Fluid 4 is preferably at a different temperature level than fluid 1 and / or it can also contain, for example, corrosion-inhibiting additives.
  • FIG. 6 shows a perspective view of a two-stage heat exchanger, the flow elements of which are formed from flat tubes 40 and from cavities 50 between them, the flow assemblies for fluid 1 and 2 or fluid 1 and 3 being arranged one above the other and the inlet and outlet of the tempering fluid 1 on the same side.
  • surface-enlarging cooling fins 99 are indicated, which contribute to an increase in the heat transfer coefficient between fluid 1 and 2.
  • the pressure resistance is increased by soldering the cooling fins 99 from flat tube to flat tube.
  • FIG. 7 shows a perspective view of a two-stage heat exchanger, the flow elements of which are formed from flat tubes 41 and from cavities 51 located therebetween, the flow assemblies for fluid 1 and 2 or fluid 1 and 3 being arranged next to one another and the inlet and outlet of the tempering fluid 1 on opposite sides.
  • FIG. 8 shows a perspective view of a two-stage heat exchanger, the flow elements of which are formed from flat tubes and from cavities in between, the flow assemblies according to the invention for fluid 1 and 2 or fluid 1 and 3 being arranged one above the other according to FIG. 5, but due to a Gaseous fluids 2, preferably ambient air, can be dispensed with a supply and discharge as well as a housing of the fluid flow assembly fluid 1 and 2.
  • the direction of flow of the fluid 2 is indicated by the arrow shown next to the corresponding reference number.
  • FIG. 9 shows a perspective view of a two-stage heat exchanger according to FIG.
  • FIG. 10 shows a perspective view of a two-stage heat exchanger according to FIG. 7, with more flat tubes being used than in FIG. 7. It is characteristic of this exemplary embodiment that fluid 2 and 3 are fluid, analogous to FIG Fig. 4. In this embodiment, fluids 2 and 3 flow into the heat exchanger with different mass flows and temperatures. Essentially in the common fluid collection device of fluid 2 and 3, both fluids mix and flow in a mixed manner via the common fluid drainage device.
  • FIG. 10 shows a top view of this exemplary embodiment, which clarifies that the flow assembly with the fluids 1 and 3 is predominantly operated in cocurrent, the flow assembly with the fluids 1 and 2 predominantly in countercurrent and not in predominantly cross flow according to FIG. 7 ,
  • This variant has advantages in the cooling of exhaust gases.
  • HT flow assembly high-temperature flow assembly
  • NT flow assembly low-temperature flow assembly
  • Boiling of the coolant is largely avoided by the direct current; in the low-temperature flow assembly (NT flow assembly) with fluids 1 and 2, a significantly lower coolant coolant mass flow flows in countercurrent to the already cooled exhaust gas.
  • a counterflow circuit can be permitted here, since the risk of boiling no longer exists due to the exhaust gas cooling that has already taken place.
  • the counterflow circuit has the advantage that the heat exchange between exhaust gas and coolant is very high and the exhaust gas can be cooled down considerably.
  • the position of the fluid inflow and outflow device can also be determined such that the entire cooler is flowed through in countercurrent (A) or cocurrent (B). This is possible if there is no risk of boiling for the coolant or coolants.
  • FIG. 12 schematically shows the integration of a cooler 300 according to FIG. 10 for the case of exhaust gas cooling for an internal combustion engine 400.
  • Many circuits are conceivable here, which is advantageous if a small mass flow flows through the NT flow assembly 311 of the cooler 300 which is brought to a very low temperature by air in a separate low-temperature cooler 310. This small mass flow is branched off from the main flow after the main air cooler 320 and cooled in the low-temperature cooler 310.
  • the HT flow assembly 321 of the two-stage cooler 300 is flowed through by a larger mass flow at a higher temperature level, which is branched off directly from the coolant mass flow flowing to the main air cooler 320.
  • the two-stage heat exchanger has its own coolant circuit, i.e. no integration into the actual engine cooling circuit is provided.
  • the NT circuit can also have its own pump.

Abstract

L'invention concerne un dispositif d'échange thermique polyétagé et un procédé de fabrication d'un tel dispositif, faisant intervenir au moins trois substances à écoulement libre (fluides) dans trois dispositifs d'écoulement divisés en au moins deux modules d'échange thermique ou d'écoulement. Lesdits modules d'écoulement sont composés d'au moins deux éléments d'écoulement disposés de telle manière qu'ils sont parcourus alternativement par des fluides différents. Pour des fluides essentiellement liquides, la répartition des fluides sur les éléments d'écoulement est effectuée par l'intermédiaire de dispositifs collecteurs et/ou répartiteurs de fluides reliés de façon étanche aux gaz et aux liquides. Les directions d'écoulement principales de tous les fluides dans les éléments d'écoulement sont situées dans des plans essentiellement parallèles. Au moins deux modules d'écoulement sont montés directement et/ou par l'intermédiaire de dispositifs répartiteurs de fluides, en communication fluidique, en série par rapport à au moins un dispositif d'écoulement.
EP04739733A 2003-06-25 2004-06-09 Dispositif d'echange thermique polyetage et procede de fabrication d'un tel dispositif Withdrawn EP1642076A1 (fr)

Applications Claiming Priority (2)

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DE10328746A DE10328746A1 (de) 2003-06-25 2003-06-25 Vorrichtung zum mehrstufigen Wärmeaustausch und Verfahren zur Herstellung einer derartigen Vorrichtung
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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EP1642076A1 true EP1642076A1 (fr) 2006-04-05

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US (1) US20070125527A1 (fr)
EP (1) EP1642076A1 (fr)
JP (1) JP2007506928A (fr)
CN (1) CN1813164A (fr)
BR (1) BRPI0411930A (fr)
DE (1) DE10328746A1 (fr)
MX (1) MXPA05014018A (fr)
WO (1) WO2004113815A1 (fr)

Families Citing this family (77)

* 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
WO2006128701A1 (fr) * 2005-06-03 2006-12-07 Behr Gmbh & Co. Kg Refroidisseur d'air de suralimentation
FR2887970B1 (fr) * 2005-06-29 2007-09-07 Alfa Laval Vicarb Soc Par Acti Echangeur thermique a plaques soudees, du type condenseur
US20080202735A1 (en) * 2005-07-19 2008-08-28 Peter Geskes Heat Exchanger
DE102005042396A1 (de) 2005-09-06 2007-03-15 Behr Gmbh & Co. Kg Kühlsystem für ein Kraftfahrzeug
US20080251242A1 (en) * 2005-10-20 2008-10-16 Behr Gmbh & Co. Kg Heat Exchanger
DE102006014188A1 (de) * 2006-03-24 2007-09-27 Behr Gmbh & Co. Kg Vorrichtung zur Kühlung eines Abgasstroms
EP2115375A1 (fr) 2007-01-31 2009-11-11 Behr GmbH & Co. KG Échangeur de chaleur
EP2137478A2 (fr) * 2007-04-11 2009-12-30 Behr GmbH & Co. KG Échangeur de chaleur
DE102008014169A1 (de) * 2007-04-26 2009-01-08 Behr Gmbh & Co. Kg Wärmetauscher, insbesondere zur Abgaskühlung, System mit einem Wärmetauscher zur Abgaskühlung, Verfahren zum Betreiben eines Wärmetauschers
WO2009003244A1 (fr) * 2007-07-04 2009-01-08 Astral Pool Australia Pty Ltd Appareil de chauffage d'eau, notamment pour les piscines
US7703282B1 (en) * 2007-12-10 2010-04-27 Iea, Inc. Heat exchanger with horizontal flowing charge air cooler
DE102008004529A1 (de) * 2008-01-15 2009-07-16 Kioto Clear Energy Ag Wärmetauscher
US8225852B2 (en) * 2008-04-30 2012-07-24 Dana Canada Corporation Heat exchanger using air and liquid as coolants
CN102112837B (zh) * 2008-07-31 2013-05-08 佐治亚科技研究公司 微型热传递系统或热与质量传递系统
JP2010048536A (ja) * 2008-08-25 2010-03-04 Denso Corp 熱交換器
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
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
DE202009015586U1 (de) * 2009-11-12 2011-03-24 Autokühler GmbH & Co. KG Wärmeaustauschernetz
DE102010048015B4 (de) * 2010-10-09 2015-11-05 Modine Manufacturing Co. Anlage mit einem Wärmeübertrager
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
KR20140005216A (ko) * 2010-12-24 2014-01-14 다나 캐나다 코포레이션 유체 흐름 제어장치를 갖는 유체 흐름 혼합박스
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
KR101776718B1 (ko) * 2011-11-22 2017-09-11 현대자동차 주식회사 차량용 열교환기
KR101765582B1 (ko) * 2011-12-06 2017-08-08 현대자동차 주식회사 차량용 열교환기
KR101316859B1 (ko) * 2011-12-08 2013-10-10 현대자동차주식회사 차량용 컨덴서
JP5943619B2 (ja) * 2012-01-31 2016-07-05 株式会社神戸製鋼所 積層型熱交換器及び熱交換システム
WO2013127009A1 (fr) * 2012-02-27 2013-09-06 Dana Canada Corporation Procédé et système de refroidissement d'air de suralimentation pour pile à combustible, et refroidisseur d'air de suralimentation à trois fluides
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
ES2522869T3 (es) * 2012-04-20 2014-11-18 Alfa Laval Corporate Ab Una placa de intercambiador de calor y un intercambiador de calor de placas
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
DE102012221925A1 (de) 2012-11-29 2014-06-05 Behr Gmbh & Co. Kg Wärmeübertrager
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
FR3000183B1 (fr) * 2012-12-21 2018-09-14 Valeo Systemes Thermiques Condenseur avec reserve de fluide frigorigene pour circuit de climatisation
FR3001795B1 (fr) * 2013-02-07 2016-06-10 Delphi Automotive Systems Lux Agencement d’echangeurs thermiques a plaques
CN105190202B (zh) * 2013-05-08 2017-11-17 三菱电机株式会社 热交换器和制冷循环装置
JP6346426B2 (ja) * 2013-08-12 2018-06-20 現代自動車株式会社Ｈｙｕｎｄａｉ Ｍｏｔｏｒ Ｃｏｍｐａｎｙ Ｅｇｒガス及びエンジンオイル冷却装置とその制御方法
ITBO20130632A1 (it) * 2013-11-20 2015-05-21 Gas Point S R L Scambiatore di calore a piastre, in particolare per caldaie a condensazione
US10589647B2 (en) 2013-12-05 2020-03-17 Gentherm Incorporated Systems and methods for climate controlled seats
US20170022884A1 (en) * 2014-01-30 2017-01-26 Yanmar Co., Ltd. Engine
DE102014201956A1 (de) 2014-02-04 2015-08-06 MAHLE Behr GmbH & Co. KG Rohranordnung für einen Ladeluftkühler
CN106028874B (zh) 2014-02-14 2020-01-31 金瑟姆股份公司 传导对流气候控制座椅
DE102014004322B4 (de) * 2014-03-25 2020-08-27 Modine Manufacturing Company Wärmerückgewinnungssystem und Plattenwärmetauscher
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
US11033058B2 (en) 2014-11-14 2021-06-15 Gentherm Incorporated Heating and cooling technologies
DE102016006127B4 (de) * 2015-06-08 2022-12-29 Modine Manufacturing Company Ladeluftkühler und Verfahren
CN105240110B (zh) * 2015-08-27 2017-09-26 沪东重机有限公司 一种船用柴油机用多段式空冷换热器
CN105090467A (zh) * 2015-09-02 2015-11-25 陕西法士特齿轮有限责任公司 一种变速器和缓速器的板翅式冷却装置及其控制方法
EP3387672A4 (fr) * 2015-12-10 2018-12-05 Laird Technologies, Inc. Échangeurs de chaleur
CN105571380A (zh) * 2016-01-19 2016-05-11 四川派尼尔环境科技有限公司 一种高效局部冷却系统用热交换方法
DE102016203951A1 (de) * 2016-03-10 2017-09-14 Mahle International Gmbh Wärmeübertrager
FR3053452B1 (fr) * 2016-07-01 2018-07-13 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Echangeur de chaleur comprenant un dispositif de distribution d'un melange liquide/gaz
JP2018054264A (ja) 2016-09-30 2018-04-05 株式会社マーレ フィルターシステムズ 熱交換器
JP6791704B2 (ja) * 2016-09-30 2020-11-25 株式会社マーレ フィルターシステムズ 熱交換器
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
IT201700122805A1 (it) * 2017-10-27 2019-04-27 Zilmet S P A Centralina termica di regolazione compatta del tipo "hiu"
US10670346B2 (en) * 2018-01-04 2020-06-02 Hamilton Sundstrand Corporation Curved heat exchanger
RS61922B1 (sr) * 2018-10-12 2021-06-30 Vahterus Oy Postavka pločastog izmenjivača topline
DE102018217757A1 (de) * 2018-10-17 2020-04-23 Volkswagen Aktiengesellschaft Abgasrückführungskühler und Verfahren zur Kühlungvon Abgas einer Brennkraftmaschine mit einer Kühlflüssigkeit
JP2020104827A (ja) * 2018-12-28 2020-07-09 株式会社マーレ フィルターシステムズ 熱交換器、及び、車両用の熱交換システム
KR102140781B1 (ko) * 2019-06-04 2020-08-03 두산중공업 주식회사 열교환장치 및 이를 포함하는 가스 터빈
CN110425603A (zh) * 2019-07-31 2019-11-08 安徽冠东科技有限公司 一种具有余热利用功能的商用燃气炉灶
CN111156850B (zh) * 2020-01-17 2021-07-20 陕西秦科世博航空科技有限公司 一种换热器及其换热方法
FR3111971B1 (fr) * 2020-06-29 2022-08-05 Valeo Systemes Thermiques Echangeur thermique pour véhicule automobile
CN111829370A (zh) * 2020-07-28 2020-10-27 贵州永红航空机械有限责任公司 一种热交换器及换热方法

Family Cites Families (22)

* 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
GB2062833B (en) * 1979-08-08 1983-02-02 Apv Co Ltd Plate heat exchangers
GB2076304B (en) * 1980-05-26 1984-02-22 Univ Sydney Heat exchange (evaporator) device
DE69125819T2 (de) * 1990-09-28 1997-12-11 Matsushita Refrigeration Laminatwärmetauscher
FR2733823B1 (fr) * 1995-05-04 1997-08-01 Packinox Sa Echangeur thermique a plaques
FR2751402B1 (fr) * 1996-07-19 1998-10-09 Packinox Sa Installation d'echange thermique entre au moins trois fluides
FR2757257B1 (fr) * 1996-12-13 1999-03-05 Packinox Sa Echangeur thermique a plaques
DE19654362B4 (de) * 1996-12-24 2007-12-06 Behr Gmbh & Co. Kg Wärmeübertrageranordnung
US6044902A (en) * 1997-08-20 2000-04-04 Praxair Technology, Inc. Heat exchange unit for a cryogenic air separation system
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
FR2789165B1 (fr) * 1999-02-01 2001-03-09 Air Liquide Echangeur de chaleur, notamment echangeur de chaleur a plaques d'un appareil de separation d'air
WO2000052411A1 (fr) * 1999-03-04 2000-09-08 Ebara Corporation Echangeur de chaleur a plaques
JP2000274968A (ja) * 1999-03-24 2000-10-06 Ebara Corp プレート式熱交換器
DE19948903C2 (de) * 1999-10-11 2002-07-18 Infineon Technologies Ag Getaktete Stromversorgung
EP1243886A4 (fr) * 1999-12-27 2006-05-03 Sumitomo Prec Products Company Echangeur thermique haute temperature a ailette plate
US6893619B1 (en) * 2000-09-13 2005-05-17 Ford Global Technologies, Llc Plate-frame heat exchange reactor with serial cross-flow geometry
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004113815A1 *

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CN1813164A (zh) 2006-08-02
DE10328746A1 (de) 2005-01-13
MXPA05014018A (es) 2006-03-17
BRPI0411930A (pt) 2006-08-15
US20070125527A1 (en) 2007-06-07
WO2004113815A1 (fr) 2004-12-29
JP2007506928A (ja) 2007-03-22

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