US20130277026A1 - Evaporator, especially for a waste gas heat recovery device - Google Patents

Evaporator, especially for a waste gas heat recovery device Download PDF

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Publication number
US20130277026A1
US20130277026A1 US13/768,109 US201313768109A US2013277026A1 US 20130277026 A1 US20130277026 A1 US 20130277026A1 US 201313768109 A US201313768109 A US 201313768109A US 2013277026 A1 US2013277026 A1 US 2013277026A1
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US
United States
Prior art keywords
evaporator
evaporation
plates
accordance
gas
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.)
Abandoned
Application number
US13/768,109
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English (en)
Inventor
Stefan Geser
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.)
Eberspaecher Exhaust Technology GmbH and Co KG
Eberspaecher Climate Control Systems GmbH and Co KG
Original Assignee
J Eberspaecher GmbH and Co KG
Eberspaecher Exhaust Technology 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 J Eberspaecher GmbH and Co KG, Eberspaecher Exhaust Technology GmbH and Co KG filed Critical J Eberspaecher GmbH and Co KG
Assigned to EBERSPAECHER CLIMATE CONTROL SYSTEMS F/K/A J. EBERSPAECHER GMBH & CO. KG reassignment EBERSPAECHER CLIMATE CONTROL SYSTEMS F/K/A J. EBERSPAECHER GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GESER, STEFAN
Assigned to EBERSPAECHER EXHAUST TECHNOLOGY GMBH & CO. KG reassignment EBERSPAECHER EXHAUST TECHNOLOGY GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: EBERSPAECHER CLIMATE CONTROL SYSTEMS GMBH & CO. KG
Publication of US20130277026A1 publication Critical patent/US20130277026A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0064—Vaporizers, e.g. evaporators

Definitions

  • the present invention pertains to an evaporator, especially for a waste heat recovery device.
  • Evaporators by means of which the working medium of the closed cycle can be evaporated, while the heat needed for this is removed from the waste gas of an internal combustion engine, are used in waste heat recovery devices that are based on the principle of a Rankine cycle or a Rankine-Clausius cycle.
  • Such an evaporator correspondingly contains a gas path for the waste gas, on the one hand, and an evaporation path for the working medium to be evaporated, on the other hand.
  • Such an evaporator may be designed, for example, as a plate heat exchanger and correspondingly have a plurality of channel plate arrays, which are stacked in a stacking direction, wherein a gas path is formed between two adjacent channel plate arrays each, and a gas, by means of which the heat needed for the evaporation of the liquid can be fed, can be sent through said gas path.
  • the corresponding channel plate array may preferably contain a liquid inlet, a steam outlet and a channel connecting the liquid inlet with the steam outlet, said channel forming, for example, a multiply deflected evaporation path for the liquid to be evaporated.
  • An object of the present invention is to provide an improved embodiment for an evaporator of the type mentioned in the introduction or for a waste heat recovery device equipped therewith.
  • the evaporator according to the present invention comprises a plurality of evaporation devices for the flow of a fluid, which are arranged one on top of another in a stack-like manner in a stacking direction, and a plurality of rib structures, which are designed for the flow of a gas through them in a gas flow direction.
  • Each evaporation device has a pair of plates with a first evaporator plate and a second evaporator plate.
  • the first and second evaporator plates which have a mutually complementary design, have a meandering evaporation channel on a respective inner side.
  • the inner sides of the first and second evaporator plates are in flat contact with one another in an area outside of the area of the evaporation channel, in a mounted state. Adjacent pairs of plates being supported by their outer sides on such a rib structure.
  • a preferred dimension for the thickness of the first and second evaporator plates may be preferably between 0.2 mm and 0.5 mm and at most preferably approximately 0.4 mm.
  • the rib structure is arranged in a sandwich-like pattern between two adjacent pairs of plates. This makes it possible to manufacture a mechanically especially stable, but also highly compact evaporator.
  • the direction of gas flow is preferably at right angles to the stacking direction.
  • the provision of a large number of rib structures can nevertheless be combined with a highly compact design in this manner.
  • the evaporation channel has a plurality of main flow sections, which extend at right angles in respect to both the stacking direction and the gas flow direction, wherein adjacent main flow sections are fluidically connected with one another by means of connection sections extending in the gas flow direction.
  • a crossed counterflow principle which makes possible an especially good thermal interaction of the gas with the fluid, can be obtained in this manner for the evaporator concerning the flow of a fluid through the evaporation devices and the flow of gas through the rib structures.
  • the evaporation channel has an essentially flat flow cross section for the purpose of a very compact design.
  • “Flat” means here that an effective width of the evaporation channel in the flow cross section is substantially greater than a height of the evaporation channel, which is defined by a direction directed at right angles to a plane defined by the evaporator plates.
  • the width of the evaporation channel may be especially 4 times, 6 times, 8 times or 10 times the height.
  • Such a flat design of the evaporation channel also brings about a pronounced interaction of the gas flowing through the rib structures with the fluid flowing through the evaporation devices, which facilitates the evaporation thereof.
  • the rib structure comprises a plurality of rows of ribs arranged next to each other in relation to the gas flow direction and are corrugated and especially corrugated in a rectangular manner.
  • the efficiency of the thermal interaction can be further increased on the gas side by means of such rows of ribs.
  • each row of ribs consists of elevations and depressions alternating following each other, which are each connected with one another by means of webs, with rows of ribs that are adjacent to each other in relation to the gas flow direction being arranged offset in relation to one another in relation to the positions of elevations and depressions.
  • each evaporation device has an inlet area each with an inlet opening and an outlet area with an outlet opening for the inlet and outlet of the fluid, where adjacent inlet openings are in fluidic connection with one another and adjacent outlet openings are in fluidic connection with one another in a mounted state of the evaporator.
  • the inlet opening and the outlet opening are designed each as an inlet dome and outlet dome provided on the outer side of the first and second evaporator plates. Despite such a space-saving design, this ensures a large flow cross-section of the inlet and outlet openings for the fluid flowing through the evaporation devices.
  • the inlet dome and outlet dome preferably have each an essentially ring-shaped cover surface. Adjacent evaporator plates can be fastened to one another in a simple manner, especially by soldering, by means of such a cover surface.
  • the inlet dome and the outlet dome each taper conically in the direction of the adjacent evaporation devices.
  • the evaporator may have, in one embodiment variant, a fluid inlet opening and a fluid outlet opening, which are fluidically connected each with the inlet openings and outlet openings of the evaporation devices, respectively, said fluid inlet opening and said fluid outlet opening being arranged in the direction of gas flow.
  • the evaporator may, furthermore, preferably have a feeding line of a funnel-shaped design for feeding the gas into the rib structures and/or a drain line of a funnel-shaped design for removing the gas from the rib structures.
  • the evaporator comprises a housing for fluidically limiting a gas path of the gas flowing through the plurality of rib structures. It is thus unnecessary to provide an outer fluidic limitation of the rib structures, which reduces the total number of components needed for the evaporator.
  • the first and second evaporator plates may be soldered to one another in a mounted state, especially by means of Ni-based solders, in an embodiment that can be manufactured in an especially simple manner.
  • the rows of ribs may be made of steel, preferably stainless steel, for the purpose of providing an especially stable embodiment.
  • FIG. 1 is a schematic exploded isometric view of an evaporator according to the present invention
  • FIG. 2 is a schematic isometric view of an evaporation device of the evaporator in a non-mounted state
  • FIG. 3 is a schematic isometric view showing a plurality of evaporation devices of the evaporator in a mounted state
  • FIG. 4 is side view showing an inlet dome of an evaporation device
  • FIG. 5 is a schematic isometric view of a rib structure of the evaporator
  • FIG. 6 is a longitudinal sectional view showing the evaporator according to FIG. 1 ;
  • FIG. 7 is a schematic isometric view of the mounted evaporator according to the present invention.
  • the evaporator according to the present invention which may preferably be designed according to the cross counterflow principle, is designated by 1 in FIG. 1 .
  • the different components of the evaporator 1 are shown at spaced locations from one another (exploded) in the view in FIG. 1 in order to improve the possibility of representation.
  • Evaporator 1 comprises a plurality of evaporation devices 2 for the flow of a fluid, which are arranged one on top of another in a stack-like manner, and a plurality of rib structures 3 , which are intended for the flow of a gas through them in a gas flow direction G.
  • Gas flow direction G extends at right angles to the stacking direction S.
  • Each evaporation device 2 has a pair of plates 4 with first and second evaporator plates 5 , 6 .
  • Such a pair of plates 4 with first and second evaporator plates 5 , 6 is shown in FIG. 2 as an example in a non-mounted state.
  • the first and second evaporator plates 5 , 6 have mutually complementary designs and have a meandering evaporation channel 9 on a respective inner side 7 , 8 .
  • the inner sides 7 , 8 of the first and second evaporator plates are in flat contact with one another in an area outside of an area of the evaporation channel 9 .
  • Evaporation channel 9 may have a plurality of main flow sections 10 , which extend in a direction at right angles O in relation to both the stacking direction S and the gas flow direction G. Adjacent main flow sections 10 may be fluidically connected with one another by means of connection sections 11 each extending in the gas flow direction G.
  • Evaporation channel 9 may have an essentially flat design. “Flat” is defined here such that an effective width B of the evaporation channel is substantially greater in relation to a flow cross section than a height H of evaporation channel 9 , which is defined by a direction extending at right angles to a plane defined by the evaporator plates. This is shown schematically in a schematic diagram supplementing FIG. 2 by reference number 40 . This schematic diagram shows a flow cross section of evaporation channel 9 . Width B of evaporation channel 9 maybe, in respective alternative variants, especially 4 times, 6 times, 8 times or 10 times the height H. A large flow cross section can be combined in this manner with a large effective interaction surface (between fluid and gas) and with a compact design.
  • Each evaporation device 2 may have an inlet area 12 with an inlet opening 14 and an outlet area 13 with an outlet opening 15 for the inlet and outlet of a fluid.
  • Adjacent inlet openings 14 may be in fluidic connection with one another in a mounted state of the evaporation devices 2 , and adjacent outlet openings 15 may correspondingly also be in fluidic connection with one another. This becomes clear especially from the view in FIG. 3 , which shows a plurality of pairs of plates 4 with a plurality of inlet openings 14 in a mounted state.
  • Both inlet opening 14 and outlet opening 15 may be designed each as a respective inlet dome 18 and outlet dome 19 provided on an outer side 16 , 17 of the first and second evaporator plates 5 , 6 .
  • FIG. 4 shows as an example such an inlet dome 18 in a side view.
  • Both inlet dome 18 and the outlet dome may taper conically in the direction of the adjacent evaporation devices.
  • a taper angle may be between approximately 40° and 60° and preferably approximately 50°.
  • inlet dome 18 and outlet dome 19 may have an essentially ring-shaped cover surface 20 , 21 each. Especially good soldering of adjacent inlet and outlet domes 18 , 19 , for example, by means of an Ni-based solder, is possible in this manner.
  • FIG. 5 shows a rib structure 3 according to the present invention.
  • Rib structure 3 comprises here a plurality of rows of ribs 22 arranged next to each other and in a rectangularly corrugated manner in relation to the gas flow direction G. Rows of ribs 22 may be manufactured from steel, preferably from stainless steel. Each row of ribs 22 consists of elevations 23 and depressions 24 alternatingly following each other, which are connected with one another via webs 25 . Adjacent rows of ribs 22 are arranged offset in relation to one another in relation to the positions of elevations 23 and depressions 24 . Improved thermal interaction can be achieved in this manner between rib structures 3 and evaporation devices 2 .
  • each rib structure 3 is arranged in a sandwich-like pattern between two adjacent pairs of plates 4 , Adjacent pairs of plates 4 are supported according to the present invention with their respective outer sides 16 , 17 (cf. FIG. 2 ) on a rib structure 3 .
  • Evaporator 1 may comprise, furthermore, a housing 26 for fluidically limiting a gas path of the gas flowing through the plurality of rib structures 3 . It is thus unnecessary to provide an outer fluidic limitation of the rib structures 3 separately.
  • Evaporator 1 may have, furthermore, a feeding line 27 of a funnel-shaped design (cf. FIG. 1 ) for feeding the gas into the rib structures 3 and a drain line 28 of a funnel-shaped design for removing the gas from the rib structures 3 . It is clear that other geometries are also conceivable in variants concerning the design of feed line 27 and drain line 28 .
  • FIG. 6 shows an evaporator 1 according to the present invention in a longitudinal sectional view. It becomes clear from this view that evaporator 1 can have a fluid inlet opening 29 and a fluid outlet opening 30 , which are fluidically connected with the inlet openings 14 and outlet openings 15 of the evaporation devices 2 , respectively. Fluid inlet opening 29 and fluid outlet opening 30 are preferably arranged in the gas flow direction G. A gas stream, especially of a waste gas, is designated by arrows with the references number 31 in FIG. 1 .
  • FIG. 7 shows a perspective view of an evaporator 1 in a mounted state.
  • a hot gas especially a waste gas, for example, from an internal combustion engine of a motor vehicle, can enter in the direction of the gas flow direction G in the rib structures 3 of the evaporation devices 2 and thus reaches the rows of ribs 22 . Since adjacent pairs of plates 4 of the evaporation device 2 are supported at the rib structures 3 , strong thermal interaction of the rib structures 3 with the evaporation devices 2 is ensured. Consequently, strong thermal interaction of a gas flowing through the rib structures 3 can also take place with a fluid flowing through the evaporation channels 9 of the evaporation devices 2 . By means of such a thermal interaction, the hot gas can be cooled very effectively by means of such a thermal interaction before discharge from the rib structure 3 while the fluid flowing through the evaporation devices 2 evaporates.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
US13/768,109 2012-02-16 2013-02-15 Evaporator, especially for a waste gas heat recovery device Abandoned US20130277026A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012202361.5 2012-02-16
DE102012202361A DE102012202361A1 (de) 2012-02-16 2012-02-16 Verdampfer, insbesondere für eine Abgaswärmenutzungseinrichtung

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US20130277026A1 true US20130277026A1 (en) 2013-10-24

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US13/768,109 Abandoned US20130277026A1 (en) 2012-02-16 2013-02-15 Evaporator, especially for a waste gas heat recovery device

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DE (1) DE102012202361A1 (de)
WO (1) WO2013120996A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10876802B2 (en) 2018-04-27 2020-12-29 Mahle International Gmbh Stacked plate heat exchanger
US11319916B2 (en) 2016-03-30 2022-05-03 Marine Canada Acquisition Inc. Vehicle heater and controls therefor

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5114776A (en) * 1989-07-28 1992-05-19 Cesaroni Anthony Joseph Corrugated thermoplastic sheet having fluid flow passages
US5157944A (en) * 1991-03-01 1992-10-27 Modine Manufacturing Company Evaporator
US20030178189A1 (en) * 2002-02-19 2003-09-25 Calsonic Kansei Corporation Stacked heat exchanger
US20040244955A1 (en) * 2001-12-28 2004-12-09 Jean-Louis Laveran Circuit element for heat exchanger, in particular for motor vehicle, and resulting heat exchanger
US20060207753A1 (en) * 2005-03-18 2006-09-21 Homayoun Sanatgar Intank oil cooler
US20060278377A1 (en) * 2003-06-25 2006-12-14 Carlos Martins Module for cooling the charge air and recirculated exhaust gases from the internal combustion engine of a motor vehicle
US20070017661A1 (en) * 2003-10-20 2007-01-25 Behr Gmbh & Co, Kg Heat exchanger
US20070261815A1 (en) * 2006-05-09 2007-11-15 Melby Robert M Multi-passing liquid cooled charge air cooler with coolant bypass ports for improved flow distribution
US20080110595A1 (en) * 2006-11-13 2008-05-15 Dana Canada Corporation Heat exchanger with bypass
WO2009156365A1 (fr) * 2008-06-26 2009-12-30 Valeo Systemes Thermiques Echangeur de chaleur comportant un faisceau d'echange de chaleur et un boitier
US20100096101A1 (en) * 2006-08-18 2010-04-22 Braun Jason J Stacked/bar plate charge air cooler including inlet and outlet tanks

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3256930A (en) * 1959-11-24 1966-06-21 Norback Per Gunnar Heat exchanger
ES2127472T3 (es) * 1994-04-12 1999-04-16 Showa Aluminum Corp Intercambiador de calor duplex de tipo apilado.
DE10146368A1 (de) * 2000-09-22 2002-06-06 Denso Corp Wärmetauscher
JP3829928B2 (ja) * 2002-02-01 2006-10-04 株式会社デンソー 熱交換器
JP4079119B2 (ja) * 2004-05-27 2008-04-23 株式会社デンソー 熱交換器
JP2006207948A (ja) * 2005-01-28 2006-08-10 Calsonic Kansei Corp 空冷式オイルクーラ
DE102005012761A1 (de) * 2005-03-19 2006-09-21 Modine Manufacturing Co., Racine Wärmetauscher, bspw. Ladeluftkühler und Herstellungsverfahren
DE102009012493A1 (de) * 2009-03-12 2010-09-16 Behr Gmbh & Co. Kg Vorrichtung zum Austausch von Wärme und Kraftfahrzeug

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5114776A (en) * 1989-07-28 1992-05-19 Cesaroni Anthony Joseph Corrugated thermoplastic sheet having fluid flow passages
US5157944A (en) * 1991-03-01 1992-10-27 Modine Manufacturing Company Evaporator
US20040244955A1 (en) * 2001-12-28 2004-12-09 Jean-Louis Laveran Circuit element for heat exchanger, in particular for motor vehicle, and resulting heat exchanger
US20030178189A1 (en) * 2002-02-19 2003-09-25 Calsonic Kansei Corporation Stacked heat exchanger
US20060278377A1 (en) * 2003-06-25 2006-12-14 Carlos Martins Module for cooling the charge air and recirculated exhaust gases from the internal combustion engine of a motor vehicle
US20070017661A1 (en) * 2003-10-20 2007-01-25 Behr Gmbh & Co, Kg Heat exchanger
US20060207753A1 (en) * 2005-03-18 2006-09-21 Homayoun Sanatgar Intank oil cooler
US20070261815A1 (en) * 2006-05-09 2007-11-15 Melby Robert M Multi-passing liquid cooled charge air cooler with coolant bypass ports for improved flow distribution
US20100096101A1 (en) * 2006-08-18 2010-04-22 Braun Jason J Stacked/bar plate charge air cooler including inlet and outlet tanks
US20080110595A1 (en) * 2006-11-13 2008-05-15 Dana Canada Corporation Heat exchanger with bypass
WO2009156365A1 (fr) * 2008-06-26 2009-12-30 Valeo Systemes Thermiques Echangeur de chaleur comportant un faisceau d'echange de chaleur et un boitier

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11319916B2 (en) 2016-03-30 2022-05-03 Marine Canada Acquisition Inc. Vehicle heater and controls therefor
US10876802B2 (en) 2018-04-27 2020-12-29 Mahle International Gmbh Stacked plate heat exchanger

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DE102012202361A1 (de) 2013-08-22
WO2013120996A1 (de) 2013-08-22

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Owner name: EBERSPAECHER CLIMATE CONTROL SYSTEMS F/K/A J. EBER

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Effective date: 20130207

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Owner name: EBERSPAECHER EXHAUST TECHNOLOGY GMBH & CO. KG, GER

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Effective date: 20130416

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