EP1136780A2 - Doppelrohr-Wärmetauscher - Google Patents

Doppelrohr-Wärmetauscher Download PDF

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Publication number
EP1136780A2
EP1136780A2 EP01302664A EP01302664A EP1136780A2 EP 1136780 A2 EP1136780 A2 EP 1136780A2 EP 01302664 A EP01302664 A EP 01302664A EP 01302664 A EP01302664 A EP 01302664A EP 1136780 A2 EP1136780 A2 EP 1136780A2
Authority
EP
European Patent Office
Prior art keywords
tube
heat exchanger
liner
fluid
shell
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Withdrawn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
EP01302664A
Other languages
English (en)
French (fr)
Other versions
EP1136780A3 (de
Inventor
Jay J. Walron
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.)
Senior Investments GmbH
Original Assignee
Senior Investments GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Senior Investments GmbH filed Critical Senior Investments GmbH
Publication of EP1136780A2 publication Critical patent/EP1136780A2/de
Publication of EP1136780A3 publication Critical patent/EP1136780A3/de
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/14—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 one within the other, e.g. concentrically both tubes being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/105—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being corrugated elements extending around the tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0236—Header boxes; End plates floating elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the present invention relates to heat transfer apparatus, such as may be employed in fuel cell systems, internal combustion engine exhaust gas transfer systems, and other power generation systems.
  • the present invention relates to heat transfer systems that employ two or more fluid conduits that are in heat-exchanging contact with one another.
  • Heat transfer apparatus for accomplishing transfer of heat from one contained flowing fluid to another contained flowing fluid, are known.
  • heat transfer apparatus employ two or more fluid conduits that are placed into heat transfer contact with one another.
  • One method that is known for constructing such a heat transfer apparatus is to provide a larger fluid conduit, through which one or more smaller fluid conduits are placed. In such a configuration, one fluid is propelled through the smaller, inner conduits, while another different fluid is propelled in the spaced between the outer surfaces of the smaller, inner conduits, and the inner surface of the surrounding conduit.
  • Such heat exchangers are typically known as "shell and tube” heat exchangers. These heat exchangers are differentiated from finned heat exchangers, that pass a contained fluid flow through a fin array, that is cooled (or heated) by air flow, for example. Examples of finned heat exchangers are automotive radiators and refrigerator heat exchanger coils.
  • Prior art shell and tube heat exchangers which may be employed, for example, in fuel cell power plants, and other power generation schemes, may have relatively large diameters, such as 8 - 9 inches.
  • such heat exchangers may require bellows even in straight runs, to accommodate thermally induced expansion and contraction.
  • Such heat exchangers are also typically very robustly built, and are thus relatively heavy, in addition to taking up space.
  • the present invention comprises a heat exchanger apparatus, for facilitating heat transfer between at least two fluids having a temperature gradient between them.
  • the heat exchanger apparatus comprises at least one liner tube, for transporting a first fluid.
  • a shell tube surrounds the at least one liner tube, for transporting a second fluid having a different temperature than the first fluid, in the region between an outer surface of the at least one liner tube and an inner surface of the shell tube.
  • the shell tube and the at least one liner tube are mechanically connected to one another in at least two longitudinally spaced locations. At least one region of reduced resistance to bending is arranged at a desired location along the length of at least one of the shell tube and the at least one liner tube, for facilitating coordinated simultaneous bending of the shell tube and the at least one liner tube at substantially longitudinal locations, along each of the shell tube and the at least one liner tube.
  • At least one heat transfer structure is positioned in thermally conductive contact with at least portions of the outer surface of the at least one liner tube, for facilitating transfer of heat between the first and second fluids, when first fluid is being transported by the at least one liner tube and second fluid is being transported between the at least one liner tube and the shell tube.
  • the heat exchanger apparatus further comprises fittings disposed at opposite ends of the heat exchanger apparatus, operably connected to the at least one liner tube and the shell liner tube, for connecting the at least one liner shell tube to a source of first fluid and a destination for first fluid, and for connecting the shell tube to a source of second fluid and a destination for second fluid.
  • the at least one region of reduced resistance to bending preferably comprises a plurality of radially extending corrugations.
  • At least one of the shell tube and the at least one liner tube is formed from substantially smooth tubular material.
  • the at least one heat transfer structure comprises at least one heat conducting fin, operably connected to the outside surface of the at least one liner tube for projecting into the second fluid, when second fluid is being transported in the region between the at least one liner tube and the shell tube.
  • the at least one heat transfer structure may be formed as an accordion folded metal sheet that is wrapped circumferentially around and affixed to the at least one liner tube.
  • the at least one liner tube has a radial thickness of from 0.1 mm up to and including 0.5mm.
  • the shell tube has a radial thickness of from 0.1 mm up to and including 0.7mm.
  • the heat exchanger apparatus may further comprise at least one bulkhead, disposed at one end of the apparatus, for mechanically connecting the shell tube and the at least one liner tube.
  • the heat exchanger apparatus may further comprise at least one bracing member, operably disposed at a position longitudinally spaced from the ends of the apparatus, for mechanically connecting the shell tube and the at least one liner tube.
  • the heat exchanger apparatus may further include a non-linear flow path heat exchanger unit connected, in fluid transporting communication with the shell tube and the at least one liner tube.
  • Fig. 1 is a side elevation, in section, of a length of a heat exchanger, constructed in accordance with the principles of the present invention.
  • Fig. 2 is a sectional view, taken along line 2-2 of Fig. 1.
  • Fig. 3 is a schematic view of an end region of a heat exchanger according to the principles of the present invention.
  • Fig. 4 is a side elevation of a heat exchanger according to an alternative embodiment of the present invention, in which multiple liner tubes are employed.
  • Fig. 5 is a perspective view of the heat exchanger of Fig. 4, with the shell tube not shown, to illustrate the liner tubes, the areas of reduced resistance to bending and the bracing members.
  • Fig. 6 is a side elevation of a heat exchanger according to another alternative embodiment of the invention, in which an enhanced efficiency dedicated auxiliary heat exchanger unit is positioned in line.
  • Fig. 7 is a perspective view of the heat exchanger of Fig. 6, with the shell tube not illustrated.
  • Fig. 8 is a side elevation of a heat exchanger according to another alternative embodiment of the invention.
  • Fig. 9 is a cross-section of a terminating region of the heat exchanger of Fig. 8.
  • Fig. 10 is a side section of the terminating region of the heat exchanger of Fig. 8.
  • Heat exchanger apparatus 10 includes shell tube 12 and liner tube 14.
  • shell tube 12 For a typical heat exchanger application, in order to maximize the efficiency of the heat transfer, the two concentric flows will be in opposite directions, as indicated by the respective arrows. Only a section of apparatus 10 is shown in Fig. 1. It is understood that at each end of apparatus 10 (one end of which is illustrated schematically in Fig. 3), suitable termination structures will be provided, so that the two counterflows can be directed to their respective destinations.
  • heat exchanger apparatus 10 will be fabricated from temperature resistant material that are resistant to chemical attack by the fluids that will be conducted through them. It is additionally preferable that the materials used be resistant to chemical breakdown, when exposed to the fluids being transported, which would result in the creation of electrically conductive ions being released into the fluids. This is a crucial requirement for heat exchanger apparatus that are employed in fuel cell applications, inasmuch as the presence of such ionic materials could result in electrical short-circuiting of the fuel cell. Suitable materials include stainless steels, Inconels, high-nickel steels generally and nickel-chromium steels. The specific formulations of such materials may readily be determined by one of ordinary skill in the art having the present disclosure before them, according to the specific requirements of any given application.
  • the shell tube 12 will typically have a wall thickness from 0.1mm up to 0.7mm, and that the liner tube 14 will typically have a wall thickness from 0.1mm up to 0.5mm, for optimum heat transfer while retaining sufficient strength and flexibility.
  • other thicknesses may be employed, as desired or required by any specific application.
  • heat exchanger apparatus 10 may be manufactured in a number of standardized, initially straight lengths (e.g., 1 foot, 2 feet, 4 feet, etc.). Each such embodiment will be flexible, to enable the lengths to be bent, in situ , to accommodate installations where straight runs are not practical or even possible. Accordingly, In order to make heat exchanger apparatus 10 flexible, at least a portion of liner tube 14 will be provided with circumferential or spiral corrugations 16 as shown in Fig. 1. While shell tube 12 may be smooth, in alternative embodiments of the invention, shell tube 12 may also be provided with corrugations 18 (shown in broken lines in Fig. 1), preferably in regions that substantially surround, axially and circumferentially, corrugations 16 of liner tube 12.
  • corrugations are provided in the liner tube, to provide regions that are programmed to bend, upon application of force.
  • the liner tube may be entirely smooth, apart from the heat transfer structures described hereinbelow.
  • accomplishing coordinated bending of an outer tube (preferably also noncorrugated) and a smooth liner tube is physically more difficult, though techniques are known for accomplishing such coordinated bending, such as packing a substantially incompressible, but flowable material in the liner tube, and in the space between the liner tube and the shell tube.
  • the diameters of the corrugations 16 are such that their crests do not contact the inner surface of shell tube 12.
  • the crests of corrugations 16 may make contact with portions of the inner surface of shell tube 12, in order to facilitate bending.
  • Apparatus 10, as shown in the figures may be provided with predominantly straight lengths, combined with localized corrugated regions.
  • apparatus 10 may be provided with greater length corrugated regions, and little or no purely straight lengths.
  • the corrugations may be varied, from region to region, to make certain regions of the apparatus more likely to bend under application of bending forces than other regions. Corrugated regions having a smaller crest-to-crest pitch, and having higher corrugation amplitude, as compared to other, adjacent corrugated regions, will be more likely to bend under bending forces. Accordingly, bending locations can be predesigned into specific places along the length of apparatus 10.
  • bracing member 20 will be provided (Fig. 3), to concentrically locate and affix liner tube 14, relative to shell tube 12.
  • a spacer may be a simple bulkhead in the form of a disk having the diameter of the inner diameter of the shell tube 12 with an aperture in it, having a diameter that is the outer diameter of liner tube 14.
  • bracing member 20 is shown in Fig. 3 as forming the end of shell tube 12, in alternative embodiments of the invention, other bracing member configurations may be employed, that do not provide the end bulkhead for a length of apparatus.
  • additional bracing members 20 may be provided along the length of apparatus 10, as shown in broken lines in Fig. 1.
  • any such bracing members 20 that are used between the ends of the apparatus must be provided with suitable apertures in order to permit flow through the bracing member.
  • the ends of apparatus 10 may be provided with quick-connect structures, that will enable them to be snapped into corresponding fittings in the destination structures, in which the two flows will be separated from one another, inside the destination structure.
  • quick-connect structures that will enable them to be snapped into corresponding fittings in the destination structures, in which the two flows will be separated from one another, inside the destination structure.
  • One example would be the use of heat exchanger apparatus 10, to carry coolant and/or fuel and/or oxidant to a combination inlet/outlet for a fuel cell stack, or a reformer for a fuel cell stack.
  • such connections may employ O-rings as part of the connection structure, presuming that the operating temperature regime permits the use of such sealing materials.
  • heat transfer structures may be provided. These heat transfer structures will create additional thermally conductive paths between liner tube 14 and the fluid between liner tube 14 and shell tube 12.
  • heat transfer structure 22 may be provided (Fig. 2, not shown in Figs. 1 and 3), that circumferentially surrounds and is in physical contact with liner tube 12.
  • Heat transfer structure 22 comprises, in one embodiment of the invention, a thin (e.g., 0.2mm - 0.5mm) accordion folded structure that when wrapped around, and affixed to liner tube 12 (such as by welding/brazing), forms a plurality of fins 24 over and through which the "outer" fluid flows.
  • heat will pass from the "outer” fluid, into the fins, and into the liner tube; alternatively heat will transfer out of the surface of the liner tube, and some directly into the fluid and some into the fins and then into the "outer” fluid.
  • the individual fins may be straight or wavy, solid, or with cross-apertures to promote turbulent flow (and thus more heat transfer).
  • the heat transfer structure 22 has been illustrated as surrounding the "straight, smooth" portions of the liner tube 14, suitably configured structures may be used to surround corrugated or other non-smooth sections, to facilitate heat transfer.
  • the fins 24 of heat transfer structure 22 have been shown, as not making contact with the inner surface of shell tube 12. In alternative embodiments, fins 24 may in fact make contact. However, it is believed that heat being conducted along fins 24 will be transferred to or from the outer fluid, and will not be conducted all the way to the shell tube 12.
  • a fin structure may be helically wrapped around the liner tube(s).
  • the liner tubes may be constructed so that their cross-sectional configuration may vary along their length (e.g., from circular cross-section to rectangular, triangular, polygonal, ellipsoidal, etc.), for example, to provide circular cross-sections in areas where bending is to occur first, and to have one of the other configurations in regions that will have straight runs.
  • the heat transfer structure will be fabricated from the same type of metal material as the shell tube and liner tube.
  • the heat transfer structures instead of being applied and affixed to the liner tube(s), may be integrally, monolithically formed into the outer surface of the liner tube(s) if desired.
  • the liner tube(s), or at least portions of their length(s) may be formed with a star-shaped cross-sectional configuration, to create a greater amount of surface area, in proportion to the volume of the flow in the liner tube(s), that is exposed to the fluid in the shell tube.
  • liner tube(s) may be used for the liner tube(s), such as rectangles, ovals or other polygonal shapes.
  • a helical liner tube may be employed.
  • heat exchanger apparatus 10 will vary in accordance with the requirements of any given installation application and accordingly, the number of corrugated or finned sections will vary.
  • heat exchanger apparatus 10 may be usefully employed in many applications, such as heat exchange between the working fluids of a fuel cell, or in cooling recirculated exhaust gases, cooling internal combustion engine lubricating oil, etc.
  • the present invention has been disclosed in the embodiment of a single liner tube concentrically arranged within a shell tube, it is contemplated that the liner tube, held by suitable bracing members, may be non-concentrically arranged in the shell tube.
  • suitable bracing members instead of one liner tube, two or more liner tubes, carrying similar or different fluids, may be provided in the shell tube.
  • Heat exchanger 100 includes shell tube 112 and three liner tubes 114.
  • Shell tube 112 is provided with one or more regions of reduced resistance to bending, exemplified by bellows corrugations 118.
  • liner tubes 114 are provided with one or more regions of reduced resistance to bending exemplified by bellows corrugations 116.
  • Heat exchanger 100 is provided with terminal bulkheads 122, which close the ends of the flow region for the fluid that flows in the shell tube 112, outside of the liner tubes 114. Entry 124 and exit 126 are provided for the entry and exit of the "outer" fluid. Bulkheads 122 have apertures 128 at which liner tubes 114 align and terminate, creating collection regions 130. Bracing members 120 are provided to stabilize the three liner tubes.
  • Figs. 4 and 5 has only one region of reduced resistance to bending, depending upon the length of a given embodiment, several such areas of reduced bending resistance may be provided at longitudinally spaced locations along the length of the heat exchanger apparatus.
  • Figs. 6 and 7 illustrate another alternative embodiment of the invention.
  • the fin-like heat transfer structures on the liner tubes have been omitted from the drawings for simplicity of illustration, but are understood to be present, and may be as shown and described with respect to Figs. 1 - 3, or may be varied in configuration and placement as described hereinabove.
  • a dedicated, high-efficiency heat exchanger structure This means a heat exchanger in which the two fluid paths are non-linear, broken up, spread out and/or intertwined, to maximize the amount of effective heat exchanger surface area.
  • Heat exchanger 200 includes shell tube 212a and 212b, and two sets of three liner tubes 214a and 214b.
  • Shell tube 212a is provided with one or more regions of reduced resistance to bending, exemplified by bellows corrugations 218.
  • liner tubes 214a are provided with one or more regions of reduced resistance to bending exemplified by bellows corrugations 216.
  • Heat exchanger 200 is provided with terminal bulkheads 222, which close the ends of the flow region for the fluid that flows in the shell tubes 212a and 212b, outside of the liner tubes 214a, 214b. Entry 224 and exit 226 are provided for the entry and exit of the "outer" fluid. Bulkheads 222 have apertures 228 at which liner tubes 214a, 214b align and terminate, creating collection regions 230. Bracing members 220 are provided to stabilize the three liner tubes.
  • high efficiency non-linear flow path heat exchanger 232 is positioned.
  • Heat exchanger 232 will be provided with suitable inlet and outlet structures that will align with shell tube 212a and liner tubes 214b, and shell tube 212b and 214b.
  • the interior of high efficiency heat exchanger 232 will be provided with numerous labyrinthine non-linear flow paths that create large heat exchange surface areas between the two fluid flows, to provide the additional heat exchange capacity that may be required, when the available running length is insufficient to use the previously described embodiments.
  • Another method may be to simply provide a cube within a cube, with six sets (for each side of the cube) of adjacent planar surfaces, between which one of the fluids flow.
  • the other fluid may pass into the interior of the inner box.
  • This structure creates increased areas of active heat exchange surface, and is also a non-linear exchanger, as one fluid must go up, down and around the other, to pass through the exchanger.
  • Such high efficiency heat exchanger apparatus are known and commercially available, from such sources as Laminova US Inc., of Old Saybrook, Kentucky, which produces a heat exchanger unit known the "Laminova core design".
  • Figs. 6 and 7 has only one region of reduced resistance to bending, depending upon the length of a given embodiment, several such areas of reduced bending resistance may be provided at longitudinally spaced locations along the length of the heat exchanger apparatus.
  • Figs. 8 - 10 illustrate another embodiment of the invention, featuring multiple liner tubes, and the regions of reduced bending resistance (such as bellows corrugations 318) in which the arrangement of the end connection structures is reversed, relative to the arrangement of the embodiments of Figs. 1 - 7.
  • the fluid from the liner tubes enters or exits the respective heat exchangers either by having the liner tube(s) extend longitudinally out of the ends of the exchanger, passing through apertures in end bulkheads, or by having the liner tube(s) terminate in collection regions 130, 230.
  • the entry and exit openings for the fluid from the shell tube extend radially from the ends of the shell tube.
  • Each of the entry and exit openings may be connected to suitable fittings on the source and destination components, by known connection techniques, such as threaded connections, bolted flange connections, bayonet connections, etc., to provide quick-connections without the need for welding, etc.
  • Figs. 8 - 10 the fin-like heat transfer structures on the liner tubes have been omitted from the drawings for simplicity of illustration, but are understood to be present, and may be as shown and described with respect to Figs. 1 - 3, or may be varied in configuration and placement as described hereinabove.
  • liner tubes 314 terminate in enclosed, cylindrical (though other shapes may be used) collection regions 330, that are provided with radially extending entry and exit ports 334, 336, that project through shell tube 312.
  • the fluid flow in the shell tube 312 enters and exits longitudinally, through the annular space between shell tube 312 and collection regions 330.
  • Figs. 9 and 10 are cross- and side-sectional views of the terminating regions of heat exchanger 300 of Fig. 8, showing the relationship between shell tube 312, collection regions 330, and liner tube entry or exit ports 334/336.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP01302664A 2000-03-23 2001-03-22 Doppelrohr-Wärmetauscher Withdrawn EP1136780A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US53354000A 2000-03-23 2000-03-23
US533540 2000-03-23

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EP1136780A2 true EP1136780A2 (de) 2001-09-26
EP1136780A3 EP1136780A3 (de) 2002-11-06

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1460367A2 (de) * 2003-02-25 2004-09-22 Delphi Technologies, Inc. Wärmetauscher zur Verwärmung von Brennluft für eine Brennstoffzelle
US6857467B2 (en) 2003-02-07 2005-02-22 Gestion Lach Inc. Heat exchange system and method
US7174797B2 (en) * 2002-10-15 2007-02-13 Florida Turbine Technologies, Inc. High temperature and pressure testing facility
EP1770250A2 (de) 2005-09-28 2007-04-04 Witzenmann GmbH Wärmetauscher für Abgasleitungen
WO2009010839A2 (en) * 2007-07-16 2009-01-22 Industrie Ilpea S.P.A. Refrigeration circuit
US7866378B2 (en) 2004-11-09 2011-01-11 Denso Corporation Double-wall pipe, method of manufacturing the same and refrigerant cycle device provided with the same
DE102010021334A1 (de) 2010-05-22 2011-11-24 Boa Balg- Und Kompensatoren-Technologie Gmbh Verfahren zur Herstellung eines Wärmetauschers und Wärmetauscher
EP2396504A2 (de) * 2009-02-12 2011-12-21 Red Leaf Resources, Inc. Gewelltes heizrohr und verfahren zu seiner verwendung für wärmeexpansion und absenkungsminderung
ITCO20110033A1 (it) * 2011-08-25 2013-02-26 Nuovo Pignone Spa Scambiatore di calore integrato con compensazione della pressione e metodo
EP3239638A1 (de) * 2016-04-27 2017-11-01 Valeo Japan Co., Ltd. Doppelrohr
CN108518257A (zh) * 2018-04-16 2018-09-11 浙江创格科技有限公司 一种高效冷却的机油回油组件

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CN109282675B (zh) * 2018-08-23 2020-02-14 常州市盛士达汽车空调有限公司 套管式热交换器及其制造方法和模具

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US4033381A (en) 1975-06-27 1977-07-05 General Connectors Corporation Hot air duct
US4250927A (en) 1979-08-24 1981-02-17 Piper Aircraft Corporation Duct spacer clip and duct assembly
US4451966A (en) 1980-01-15 1984-06-05 H & H Tube & Mfg. Co. Heat transfer tube assembly
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Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7506555B2 (en) 2002-10-15 2009-03-24 Florida Turbine Technologies, Inc. Process and apparatus for testing a material under a high temperature and pressure environment
US7174797B2 (en) * 2002-10-15 2007-02-13 Florida Turbine Technologies, Inc. High temperature and pressure testing facility
US6857467B2 (en) 2003-02-07 2005-02-22 Gestion Lach Inc. Heat exchange system and method
EP1460367A3 (de) * 2003-02-25 2012-01-11 Delphi Technologies, Inc. Wärmetauscher zur Verwärmung von Brennluft für eine Brennstoffzelle
EP1460367A2 (de) * 2003-02-25 2004-09-22 Delphi Technologies, Inc. Wärmetauscher zur Verwärmung von Brennluft für eine Brennstoffzelle
US9669499B2 (en) 2004-11-09 2017-06-06 Denso Corporation Double-wall pipe, method of manufacturing the same and refrigerant cycle device provided with the same
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ITCO20110033A1 (it) * 2011-08-25 2013-02-26 Nuovo Pignone Spa Scambiatore di calore integrato con compensazione della pressione e metodo
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US9863723B2 (en) 2011-08-25 2018-01-09 Silvio Giachetti Integrated pressure compensating heat exchanger and method
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CN107421164A (zh) * 2016-04-27 2017-12-01 法雷奥日本株式会社 双层管
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