US20020079085A1 - Turbine recuperator - Google Patents

Turbine recuperator Download PDF

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Publication number
US20020079085A1
US20020079085A1 US09/749,267 US74926700A US2002079085A1 US 20020079085 A1 US20020079085 A1 US 20020079085A1 US 74926700 A US74926700 A US 74926700A US 2002079085 A1 US2002079085 A1 US 2002079085A1
Authority
US
United States
Prior art keywords
support member
turbine
chamber
housing
recuperator
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
US09/749,267
Other languages
English (en)
Inventor
Lawrence Rentz
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.)
General Electric Co
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to US09/749,267 priority Critical patent/US20020079085A1/en
Assigned to GENERAL ELECTRIC COMPANY reassignment GENERAL ELECTRIC COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RENTZ, LAWRENCE EDWARD
Priority to PCT/US2001/048132 priority patent/WO2002052211A2/en
Priority to EP01985025A priority patent/EP1348098A2/en
Priority to KR1020027011148A priority patent/KR20020077921A/ko
Priority to JP2002553064A priority patent/JP2004516423A/ja
Publication of US20020079085A1 publication Critical patent/US20020079085A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • 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
    • F28D9/0012—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 apparatus having an annular form
    • F28D9/0018—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 apparatus having an annular form without any annular circulation of the heat exchange media

Definitions

  • the present invention relates to turbine recuperators, and, more particularly, to turbine recuperators having improved heat transfer and ease of fabrication.
  • recuperators take heated exhaust air and uses it to preheat cold air that is to be introduced into the turbine.
  • recuperators typically include cold cells, through which cold air to be preheated passes, and hot cells, through which the heated exhaust air passes.
  • a recuperator 2 includes a cylindrical housing 4 , within which a support member 6 is contained.
  • a plurality of cold cells 8 and hot cells 10 extend outwardly from support member 6 in alternating fashion about the circumference of support member 6 .
  • Cold cells 8 and hot cells 10 preferably are curved along their radial length, to accommodate expansion and contraction of the cells.
  • Cold air to be preheated passes through a header in support member 6 and then through cold cells 8 , as described below in connection with FIG. 2.
  • Heated exhaust air flows through annular channel 12 , formed between housing 4 and support member 6 , thereby passing over the surface of hot cells 10 . As seen in FIG.
  • cold cell 8 includes a heat transfer fin 14 , formed of a sheet of corrugated metal, encased in a shell 16 , typically welded about its edges ( shown in FIG. 2 with one end plate removed, and in a flat non-curved orientation for simplicity). Cold cell 8 is secured along side edge 21 to support member 6 .
  • Cold air 18 enters the interior of shell 16 through an inlet 20 that is in fluid communication via a header (not shown) with a cold air supply. Heated air 22 exits shell 16 through an outlet 24 into a header (not shown). As cold air 18 enters shell 16 , it passes over the surface of heat transfer fin 14 , gradually warming as it travels through shell 16 till it gets to outlet 24 . As seen in FIG.
  • hot cell 10 is formed of a heat transfer fin 14 , also formed of a sheet of corrugated metal (shown in a flat, non-curved orientation for simplicity).
  • Hot turbine exhaust air 26 passes over the surface of heat transfer fin 14 of hot cell 10 , cooling as it travels along fin 14 and exits hot cell 10 as cool exhaust air 28 .
  • recuperator 2 as seen in FIG. 1, heat is transferred from the hot turbine exhaust air, that travels through channel 12 over hot cells 10 , to cold cells 8 , thereby preheating the air to be used in the turbine.
  • recuperator design is limiting in that a significant amount of material must be used, and its assembly requires a significant amount of welding and handling of material. Further, the heat transfer between the hot and cold air primarily occurs between flat sheets, thereby failing to optimize the surface area used in the conduction of heat.
  • FIG. 4 Another example of a recuperator 29 with cold and hot cells is shown in FIG. 4.
  • a plurality of hot cells 30 are formed of tubes, or conduits.
  • Cold cells 32 are also formed of tubes or conduits that extend alongside hot cells 30 in parallel fashion. Only a few hot cells 30 and cold cells 32 are shown here for purposes of clarity.
  • Hot cells 30 are connected to one another through a set of headers 34 , only one of which is shown.
  • Cold cells 32 are similarly connected to one another via headers (not shown).
  • Heated exhaust 34 enters an endmost hot cell 30 through an inlet, not visible, and passes in serpentine fashion through each of the hot cells by way of headers 34 . Cooled exhaust 36 then exits at the opposite end through an outlet 38 in a hot cell 30 .
  • cold air 40 enters cold cells 32 through an inlet (not shown), and passes in serpentine fashion through each cold cell 32 and associated headers (not shown) and heated air 42 exits cold cells 32 through an outlet (not shown).
  • this design provides greater heat transfer than the prior art recuperator of FIGS. 1 - 3 due to the long path through which the air streams pass, this design consequently results in less than optimum pressure drops due to the serpentine path the air must follow. Excessive pressure drops reduce the overall turbine cycle efficiency.
  • Such a design is also limiting in that it requires the use of a complex set of headers, thereby requiring costly tooling for fabrication and a labor intensive and expensive assembly process.
  • recuperator that optimizes effectiveness of the turbine cycle and minimizes the pressure drop across the recuperator, while at the same time minimizes the amount of material used and the number of manufacturing operations required to assemble the recuperator.
  • a turbine recuperator in accordance with a first aspect, includes a housing.
  • a support member is positioned within the housing and defines a passage between the support member and the housing.
  • a plurality of heat transfer cells are secured to the support member.
  • Each heat transfer cell is formed of a sheet of corrugated material having two opposed ends and two opposed sides. The sheet is folded over upon itself such that the sides are proximate one another, and the sides are secured to the support member. The ends are sealed to define a chamber within the heat transfer cell.
  • the cell further has an inlet header and an outlet header.
  • a plurality of inlets are formed in the support member; with each inlet in fluid communication with the inlet header and a chamber.
  • a plurality of outlets are formed in the support member, with each outlet in fluid communication with the outlet header and a chamber.
  • FIG. 1 is an end view of a prior art recuperator design
  • FIG. 2 is a perspective view of a cold cell of the prior art recuperator of FIG. 1;
  • FIG. 3 is a perspective view of a hot cell of the prior art recuperator of FIG. 1;
  • FIG. 4 is a perspective view of another prior art recuperator design, shown partially assembled
  • FIG. 5 is a perspective view of a corrugated sheet of metal folded over upon itself to form a heat transfer cell of a recuperator of the present invention
  • FIG. 6 is an end view of a recuperator of the present invention.
  • FIG. 7 is a section view of the recuperator of FIG. 6, taken along line A-A of FIG. 6;
  • FIG. 8 is a perspective view in cross-section, shown partially broken away, of the recuperator of FIG. 6.
  • FIGS. 5 - 8 A preferred embodiment of a recuperator 50 of the present invention is shown in FIGS. 5 - 8 .
  • a sheet 52 of corrugated material having side edges 54 , 56 and end edges 58 , 60 is folded over upon itself such that side edges 54 , 56 are proximate one another.
  • Sheet 52 is preferably metal, and may be, for example, formed of iron, or a nickel-based alloy.
  • End edges 58 , 60 are then crimped and sealed, preferably by welding, and sides edges 54 , 56 are secured to support member 62 , preferably by welding as well, forming a heat transfer cell 63 .
  • a chamber 64 is defined within sheet 52 .
  • a plurality of heat transfer cells 63 are preferably secured around the circumference of support member 62 . Heat transfer cells 63 are preferably curved along their radial dimension with respect to support member 62 , as seen in FIGS. 6, 8, in order to accommodate thermal expansion and contraction.
  • Support member 62 is positioned within a housing 66 , defining a passage 67 between support member 62 and housing 66 .
  • support member 62 and housing 66 are circular in cross-section, and are also co-axial with one another, such that passage 67 has an annular shape.
  • An inlet header 68 is formed in one end of support member 62 and an outlet header 74 is provided in the other end of support member 62 .
  • Inlet header 68 is in fluid communication with a supply of cold air 70 to be preheated by recuperator 50 .
  • a plurality of inlets 72 are formed in support member 62 , with each inlet 72 forming a fluid communication pathway between inlet header 68 and a respective chamber 64 .
  • a plurality of outlets 76 are formed in support member 62 , with each outlet 76 forming a fluid communication pathway between a respective chamber 64 and outlet header 74 .
  • cold air 70 to be preheated flows into inlet header 68 and into chambers 64 through inlets 72 .
  • Hot turbine exhaust air 78 enters passage 67 and flows across the exterior surface of heat transfer cells 63 , exiting passage 67 as cooled exhaust 79 .
  • heat transferred from hot exhaust air 78 warms the air in chambers 64 , forming warm air 80 that exits chambers 64 via outlets 76 and exits recuperator 50 via outlet header 74 .
  • exhaust air 78 could pass through heat transfer cells 63 and cold air 70 to be preheated could pass over the exterior surface of heat transfer cells 63 .
  • hot exhaust air 78 flows counter to the flow of cold air 70 .
  • the recuperator of the present invention can be configured to work in a parallel flow arrangement, or in any other flow arrangement that is desired, as well.
  • the heat transfer cells 63 By forming the heat transfer cells 63 of a single piece of corrugated metal sealed along its edges, the amount of material used to form the cells is advantageously reduced, resulting in significant cost savings, as well as a reduction in the number of manufacturing steps required to build the heat transfer cells when assembling the recuperator.
  • the corrugated surface of heat transfer cells 63 provides greater surface area than the flat surfaces found in certain prior art recuperator designs, thereby optimizing heat transfer from the hot turbine exhaust to the cold air to be preheated.
  • the construction of the present invention also advantageously decreases the overall pressure drop across the recuperator as compared to some recuperators of the prior art. By providing such a simple construction with few parts, the recuperator of the present invention is well suited for high volume manufacturing and standardization of parts, reducing manufacturing and inventory costs.
  • the recuperator of the embodiment disclosed above is one in which the heat transfer cells extend radially outwardly from a central support member. It is to be appreciated that other configurations of the recuperator of the present invention are considered to be within the scope of the invention.
  • the support member and housing could have other shapes, e.g., rectangular.
  • the microturbine is surrounded by the recuperator to minimize heat loss and pressure drop.
  • the recuperator could be off-board, that is, detached from the microturbine and connected thereto only by necessary conduit or ductwork.

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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)
US09/749,267 2000-12-27 2000-12-27 Turbine recuperator Abandoned US20020079085A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US09/749,267 US20020079085A1 (en) 2000-12-27 2000-12-27 Turbine recuperator
PCT/US2001/048132 WO2002052211A2 (en) 2000-12-27 2001-12-12 Turbine recuperator
EP01985025A EP1348098A2 (en) 2000-12-27 2001-12-12 Turbine recuperator
KR1020027011148A KR20020077921A (ko) 2000-12-27 2001-12-12 터빈 전열식열교환기
JP2002553064A JP2004516423A (ja) 2000-12-27 2001-12-12 タービンの復熱装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US09/749,267 US20020079085A1 (en) 2000-12-27 2000-12-27 Turbine recuperator

Publications (1)

Publication Number Publication Date
US20020079085A1 true US20020079085A1 (en) 2002-06-27

Family

ID=25013017

Family Applications (1)

Application Number Title Priority Date Filing Date
US09/749,267 Abandoned US20020079085A1 (en) 2000-12-27 2000-12-27 Turbine recuperator

Country Status (5)

Country Link
US (1) US20020079085A1 (enExample)
EP (1) EP1348098A2 (enExample)
JP (1) JP2004516423A (enExample)
KR (1) KR20020077921A (enExample)
WO (1) WO2002052211A2 (enExample)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040040280A1 (en) * 2002-08-30 2004-03-04 General Electric Company Heat exchanger for power generation equipment
US20040083712A1 (en) * 2002-11-06 2004-05-06 Dewis David W. Heat transfer apparatus
US20140220878A1 (en) * 2013-02-05 2014-08-07 Adpv Technology Limited Gas release device for coating process
US20140260178A1 (en) * 2013-03-14 2014-09-18 Pratt & Whitney Canada Corp. Aerodynamically active stiffening feature for gas turbine recuperator
CN106091757A (zh) * 2016-07-22 2016-11-09 甘肃蓝科石化高新装备股份有限公司 一种全焊接波纹板束的组装结构及组装方法
US11168947B2 (en) * 2016-12-07 2021-11-09 Recair Holding B.V. Recuperator

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102097209B1 (ko) * 2018-07-31 2020-04-03 주식회사 이노윌 가스터빈 열교환기

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3507115A (en) * 1967-07-28 1970-04-21 Int Harvester Co Recuperative heat exchanger for gas turbines
DE2805912A1 (de) * 1978-02-13 1979-08-23 Linde Ag Plattenwaermetauscher
DE3029000C2 (de) * 1980-07-31 1982-07-22 Gartemann & Hollmann Gmbh, 4800 Bielefeld Ringwärmetauscher
GB9027994D0 (en) * 1990-12-22 1991-02-13 Atomic Energy Authority Uk Heat exchanger
JP3685890B2 (ja) * 1996-10-17 2005-08-24 本田技研工業株式会社 熱交換器
GB2343641A (en) * 1998-11-10 2000-05-17 Centrax Ltd Heat exchanger

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040040280A1 (en) * 2002-08-30 2004-03-04 General Electric Company Heat exchanger for power generation equipment
US6904747B2 (en) 2002-08-30 2005-06-14 General Electric Company Heat exchanger for power generation equipment
US20040083712A1 (en) * 2002-11-06 2004-05-06 Dewis David W. Heat transfer apparatus
US6966173B2 (en) * 2002-11-06 2005-11-22 Elliott Energy Systems, Inc. Heat transfer apparatus
US20140220878A1 (en) * 2013-02-05 2014-08-07 Adpv Technology Limited Gas release device for coating process
US20140260178A1 (en) * 2013-03-14 2014-09-18 Pratt & Whitney Canada Corp. Aerodynamically active stiffening feature for gas turbine recuperator
US9724746B2 (en) * 2013-03-14 2017-08-08 Pratt & Whitney Canada Corp. Aerodynamically active stiffening feature for gas turbine recuperator
CN106091757A (zh) * 2016-07-22 2016-11-09 甘肃蓝科石化高新装备股份有限公司 一种全焊接波纹板束的组装结构及组装方法
US11168947B2 (en) * 2016-12-07 2021-11-09 Recair Holding B.V. Recuperator

Also Published As

Publication number Publication date
EP1348098A2 (en) 2003-10-01
JP2004516423A (ja) 2004-06-03
KR20020077921A (ko) 2002-10-14
WO2002052211A2 (en) 2002-07-04
WO2002052211A3 (en) 2003-01-03

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Date Code Title Description
AS Assignment

Owner name: GENERAL ELECTRIC COMPANY, NEW YORK

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:RENTZ, LAWRENCE EDWARD;REEL/FRAME:011695/0047

Effective date: 20010404

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION