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EP2894427A1 - Kreuzstrom-Wärmetauscher - Google Patents

Kreuzstrom-Wärmetauscher Download PDF

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Publication number
EP2894427A1
EP2894427A1 EP14193031.3A EP14193031A EP2894427A1 EP 2894427 A1 EP2894427 A1 EP 2894427A1 EP 14193031 A EP14193031 A EP 14193031A EP 2894427 A1 EP2894427 A1 EP 2894427A1
Authority
EP
European Patent Office
Prior art keywords
layer
corrugations
fluid
fin
heat exchanger
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Withdrawn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
EP14193031.3A
Other languages
English (en)
French (fr)
Inventor
Todd E Van Hal
Paul I Craig
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP2894427A1 publication Critical patent/EP2894427A1/de
Withdrawn legal-status Critical Current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
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • 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
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/20—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being attachable to the element
    • 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
    • F28F2275/04—Fastening; Joining by brazing
    • 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
    • F28F2275/06—Fastening; Joining by welding

Definitions

  • the invention pertains to heat exchangers. More particularly it relates to fluid to fluid (e.g. liquid to air) coolers for engine coolant, lubricating oil, or hydraulic fluid used in internal combustion engines, transmissions, and hydraulic circuits of work vehicles.
  • fluid to fluid e.g. liquid to air
  • coolers for engine coolant, lubricating oil, or hydraulic fluid used in internal combustion engines, transmissions, and hydraulic circuits of work vehicles.
  • Air cooled heat exchangers are subject to being plugged.
  • agricultural harvesters generate contaminated air by the activity of crop cleaning fans, engine cooling fans, and the like.
  • the contaminated air contains particulate matter (primarily plant matter) in sizes ranging from several inches in length to fine dust particles. This contaminated air surrounds the agricultural harvester almost as a cloud. It is difficult if not impossible to clean this air before it is used and reused in the various heat exchangers employed on the agricultural harvester. Similar problems exist for other work vehicles, such as road graders, bulldozers, tractors, backhoes, and excavators.
  • a heat exchanger for a work vehicle comprising: a tube layer comprised of a plurality of elongate tubes, wherein the plurality of elongate tubes are spaced apart by gaps and are oriented parallel to each other in a first direction, wherein each of the plurality of elongate tubes defines a channel for passing a first fluid therethrough; a first fin layer in the form of a corrugated sheet having a plurality of corrugations, in which the plurality of corrugations of the first fin layer extend in a second direction transverse to the first direction, and wherein the first fin layer is disposed parallel to the tube layer and on a first side of the tube layer, and wherein each of the plurality of corrugations of the first fin layer facing the tube layer define an enclosed channel for passing therethrough a fluid different from the first fluid; and a first fluid guide layer formed of a continuous, generally planar sheet that extends across and encloses the plurality of corrugations of the first fin layer over substantially an entire length of the plurality of cor
  • the heat exchanger may further comprise a second fin layer in the form of a corrugated sheet having a plurality of corrugations, in which the plurality of corrugations of the second fin layer extend in the second direction, and wherein the second fin layer is disposed parallel to the tube layer and on a second side of the tube layer that is opposite to the first side of the tube layer, and wherein the plurality of corrugations of the second fin layer facing the tube layer define channels for passing therethrough a fluid different from the first fluid; and a second fluid guide layer formed of a continuous, generally planar sheet that extends across and encloses the plurality of corrugations of the second fin layer over substantially an entire length of the plurality of corrugations.
  • the first fluid guide layer may extend across and enclose the gaps over substantially the entire length of the gaps.
  • the first fin layer may comprise metal and the first fluid guide layer may comprise metal, and the first fin layer may be bonded to a first side of the first fluid guide layer by a process selected from a group comprising soldering, brazing, and welding.
  • the tube layer may comprise metal and the tube layer may be bonded to a second side of the first fluid guide layer by a process selected from a group comprising soldering, brazing, and welding.
  • none of the channels has an interior region that is in fluid communication with an interior region of any of the plurality of elongate tubes.
  • the channels may be rectangular or square in cross-section.
  • heat exchanger a prior art cross flow heat exchanger (hereinafter “heat exchanger”) is shown comprising a first fin layer 100, a tube layer 102, and a second fin layer 104.
  • the first fin layer 100 is formed as a corrugated sheet from a thin sheet of thermally conductive metal, such as copper, brass, aluminum or other light metal alloy.
  • the corrugations are in the form of a square wave in cross-section.
  • the first fin layer 100 is bonded to the tube layer 102 by soldering, brazing, welding, or other metal-to-metal attachment means that permit heat transfer from the tube layer 102 to the first fin layer 100.
  • a series of enclosed channels 106 are formed for channeling a flow of air along the surface of the tube layer 102. This intimate contact of the air in the enclosed channels 106 enhances the exchange of heat from the tube layer 102 to the first fin layer 100.
  • the tube layer 102 is formed of individual elongate tubes 108 that are arranged in side-by-side relation.
  • the elongate tubes 108 are formed of a thermally conductive metal, typically copper, brass, aluminum or other light metal alloy.
  • the elongate tubes 108 have flat walls disposed parallel to and bonded to the coplanar and flat bottom surfaces 110 of the first fin layer 100.
  • a gap 112 is provided between each pair of adjacent elongate tubes 108. This provides for some airflow between the curved end walls 114 of the elongate tubes 108 and thus provides additional heat transfer from the curved end walls 114 to the flow of air passing through the enclosed channels 106.
  • the elongate tubes 108 extend in a direction perpendicular to the longitudinal extent of the enclosed channels 106. In this manner, air flowing down the enclosed channels 106 can branch at each gap 112 and flow around the curved end walls 114 of the elongate tubes 108.
  • the second fin layer 104 is identical in construction and operation to the first fin layer 100, but it is disposed on the opposite side of the tube layer 102 then the first fin layer 100.
  • This type of prior art heat exchanger is very effective when dealing with clean, processed air.
  • vehicles that work in the field such as dump trucks, front loaders, excavators, tractors, and particularly agricultural harvesters
  • the large amount of contaminants in the air, and particularly longer and more elongate fibrous contaminants such as chaff, leaves, husks, and the like, can plug these heat exchangers.
  • the heat exchangers are plugged by contaminants traveling with the cooling airflow through the enclosed channels 106. When these contaminants reach a branch at each gap 112, they tend to fill the gaps 112 and plug them.
  • the new arrangement of Figure 2 overcomes these problems with heat flow and cleaning by closing the gaps 112.
  • the first fin layer 100, the tube layer 102, and the second fin layer 104 are arranged with respect to each other as provided in the prior art discussed above.
  • the first fin layer 100 and the tube layer 102 are separated by the addition of a fluid guide layer 200.
  • the tube layer 102 and the second fin layer 104 are separated by the addition of a fluid guide layer 202.
  • the function of the fluid guide layer 200 and the fluid guide layer 202 is to reduce or eliminate the airflow passing into the gaps 112.
  • the fluid guide layer 200 and the fluid guide layer 202 prevent the airflow from being deflected into the gaps 112 and thereby preventing contaminants to pass into the gaps 112. In this manner, contaminants cannot wrap around the curved end walls 114 of each of the elongate tubes 108, accumulate, and eventually create a plug that cannot easily be removed.
  • the fluid guide layer 200 and the fluid guide layer 202 are in the form of thin, planar sheets.
  • the fluid guide layer 200 and the fluid guide layer 202 are formed of a thermally conductive metal, such as copper, brass, aluminum or other light metal alloy.
  • the elongate tubes 108 have flat walls disposed parallel to and bonded to the coplanar and flat bottom surfaces 110 of the first fin layer 100 and the second fin layer 104.
  • the fluid guide layer 200 and the fluid guide layer 202 are bonded between the first fin layer 100 and the tube layer 102, and between the second fin layer 104 and the tube layer 102, respectively.
  • the heat exchanger is formed in the manner suggested by Figure 2 .
  • the tube layer 102 is assembled by arranging the elongate tubes 108 in a regular orientation with the gap 112 between each tube.
  • the first fin layer 100 and the second fin layer 104 are formed from sheets into the corrugated arrangement shown in Figure 2 . Once these layers are formed, the fluid guide layer 200 is disposed between the first fin layer 100 and the tube layer 102, and the fluid guide layer 202 is disposed between the tube layer 102 and the second fin layer 104.
  • the layers are then brought together and are mechanically bonded, preferably by soldering, brazing, or welding the now-abutting layers together.
  • the heat exchanger has the appearance shown in Figure 3A and Figure 3B .
  • the fluid guide layer 200 encloses the open bottom of each enclosed channel 106, extending substantially the entire length of each enclosed channel 106 and preventing air from passing out of the enclosed channel 106 and into the gaps 112 between the elongate tubes 108.
  • the fluid guide layer 200 and the fluid guide layer 202 enclose opposing sides of the gap 112, extending substantially the entire length of each elongate tube 108. In this manner, air with entrained contaminants is prevented from entering the gaps 112 and traveling laterally through the gaps 112 and into adjacent enclosed channels 106.
  • a further advantage to this arrangement is that the fluid guide layer 200 and the fluid guide layer 202 form a continuous smooth bottom to each of their respective enclosed channels 106. This reduces irregularities in the cross-section of each enclosed channel 106 and thus reduces the possibility of contaminants becoming entrapped in any of the enclosed channels 106.
  • a cross flow heat exchanger with a first fluid (e.g. liquid) flow in the elongate tubes 108 traveling transverse to a second fluid (e.g. gas or air) flow in the enclosed channels 106.
  • a first fluid e.g. liquid
  • a second fluid e.g. gas or air
  • manifolds are coupled to the open ends of the enclosed channels 106 and the elongate tubes 108 to distribute (at their inlet ends) and to gather (at their outlet ends) the fluid flow.
  • manifolds are of conventional arrangement and have not been illustrated herein for convenience since they do not form a part of the invention.
  • the corrugated pattern shown here as a square wave may have a different cross sectional pattern, such as a sine wave, saw tooth wave, trapezoidal wave, or other repeating pattern.
  • the particular pattern will depend upon the particular cooling requirements, sheet thickness, and cross-sectional area of the enclosed channels 106.
  • the elongate tubes 108 shown herein have opposing flat sides and rounded ends (the "ends” in this context meaning the portion of the elongate tubes 108 that face into and define the gap 112).
  • the elongate tubes 108 could have a variety of other cross-sectional shapes, such as a circle, a square, rectangle, or an oval, as just a few examples.
  • the gaps 112 themselves can form an additional fluid flow channel for the fluid passing through the elongate tubes 108 by keeping the fluid passing through the gaps 112 separate from the fluid passing through the enclosed channels 106.
  • the arrangements illustrated herein shows two fluid guide layers 200, 202 separating two fin layers 100, 104 from both sides of the tube layer 102.
  • only a single fluid guide layer 200 and a single fin layer need to be used.
  • the arrangements discussed herein refer to the fluid passing through the first fin layer 100 and the second fin layer 104 as air (a gas).
  • the fluid passing to the first fin layer 100 and the second fin layer 104 may be a liquid.

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP14193031.3A 2014-01-13 2014-11-13 Kreuzstrom-Wärmetauscher Withdrawn EP2894427A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US14/153,635 US20150198385A1 (en) 2014-01-13 2014-01-13 Cross Flow Heat Exchanger

Publications (1)

Publication Number Publication Date
EP2894427A1 true EP2894427A1 (de) 2015-07-15

Family

ID=51900238

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14193031.3A Withdrawn EP2894427A1 (de) 2014-01-13 2014-11-13 Kreuzstrom-Wärmetauscher

Country Status (3)

Country Link
US (1) US20150198385A1 (de)
EP (1) EP2894427A1 (de)
BR (1) BR102015000502A2 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3564611A1 (de) * 2018-05-04 2019-11-06 Hamilton Sundstrand Corporation Verfahren zur herstellung eines wärmetauschers mit mikrorohren und -rippen
US11656011B2 (en) * 2019-01-22 2023-05-23 Hitachi Energy Switzerland Ag Condenser

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104459853B (zh) * 2013-09-22 2017-08-04 清华大学 金属光栅
US10060680B2 (en) * 2014-06-30 2018-08-28 Modine Manufacturing Company Heat exchanger and method of making the same

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2114340A1 (de) * 1971-03-24 1972-10-05 Linde Ag Flossenrohrwaermeaustauscher
EP1203923A2 (de) * 2000-11-01 2002-05-08 AKG-Thermotechnik GmbH & Co.KG Wärmeaustauscher, insbesondere für Kondensations-Wäschetrockner
US20020088246A1 (en) * 2001-01-05 2002-07-11 Cathy Bureau Air-conditioner for a motor vehicle
US20120318485A1 (en) * 2010-02-25 2012-12-20 Mitsuo Yabe Corrugated fin and heat exchanger including the same

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2214057A (en) * 1934-12-24 1940-09-10 Gen Motors Corp Refrigerating apparatus
US4966230A (en) * 1989-01-13 1990-10-30 Modine Manufacturing Co. Serpentine fin, round tube heat exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2114340A1 (de) * 1971-03-24 1972-10-05 Linde Ag Flossenrohrwaermeaustauscher
EP1203923A2 (de) * 2000-11-01 2002-05-08 AKG-Thermotechnik GmbH & Co.KG Wärmeaustauscher, insbesondere für Kondensations-Wäschetrockner
US20020088246A1 (en) * 2001-01-05 2002-07-11 Cathy Bureau Air-conditioner for a motor vehicle
US20120318485A1 (en) * 2010-02-25 2012-12-20 Mitsuo Yabe Corrugated fin and heat exchanger including the same

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3564611A1 (de) * 2018-05-04 2019-11-06 Hamilton Sundstrand Corporation Verfahren zur herstellung eines wärmetauschers mit mikrorohren und -rippen
US11656011B2 (en) * 2019-01-22 2023-05-23 Hitachi Energy Switzerland Ag Condenser

Also Published As

Publication number Publication date
US20150198385A1 (en) 2015-07-16
BR102015000502A2 (pt) 2016-06-07

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