EP1118831A2 - Mit Rippenzug versehene Wärmetauscherwand - Google Patents
Mit Rippenzug versehene Wärmetauscherwand Download PDFInfo
- Publication number
- EP1118831A2 EP1118831A2 EP00810953A EP00810953A EP1118831A2 EP 1118831 A2 EP1118831 A2 EP 1118831A2 EP 00810953 A EP00810953 A EP 00810953A EP 00810953 A EP00810953 A EP 00810953A EP 1118831 A2 EP1118831 A2 EP 1118831A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- rib
- flow channel
- flow
- train
- ribs
- 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.)
- Granted
Links
Images
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
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
-
- 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
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
Definitions
- the invention relates to a device for cooling a flow channel surrounding flow channel wall with at least one, in a through the Flow medium passing through flow channel inducing flow eddies Rib train on the side of the flow channel wall facing the flow channel is attached and has a main longitudinal extension, which in an angle ⁇ ⁇ 0 to the direction of flow of that passing through the flow channel Flow medium is oriented.
- inside turbine blades or cooling channels are provided along the combustion chamber walls, through which relatively cold air is fed in compared to the temperature of the hot gases.
- relatively cold air is fed in compared to the temperature of the hot gases.
- some of the compressed air is discharged from the air compressor and into the Cooling channels fed.
- the cooling duct 1 shown in the exemplary embodiment according to FIG. 2 has a square cross section and is therefore surrounded by four cooling duct walls of equal length.
- Two opposite cooling channel walls 2, 3 are provided with rib trains 4 arranged one behind the other in the longitudinal direction of the cooling channel.
- the cooling air flow now passes axially through the cooling channel 1, then a flow profile is formed by the ribs 4 in the flow cross section of the coolant flow, which provides two secondary vortices 5, 6.
- the secondary vortices 5, 6 in turn lead to a turbulent mixing of the boundary layer directly above the inner wall of the cooling duct, which results in an improved exchange of cooling air on the inner wall of the cooling duct and a greater heat flow from the inner wall of the cooling duct to the cooling air flow.
- the invention has for its object a device for cooling a Flow channel wall surrounding the flow channel with at least one, in one fluid flowing through the flow channel inducing rib train, on the side facing the flow channel of the Flow channel wall is attached and has a main longitudinal extension, which in an angle ⁇ ⁇ 0 ° to the direction of flow of that passing through the flow channel Flow media is oriented to develop such that the cooling effect the device should be increased significantly without sacrificing manufacturing technology Expenditure compared to conventional measures significantly increase.
- the improvements should make it possible to increase the cooling capacity by to improve cooling air flow passing through a flow channel, so that a further increase in performance due to increased process temperatures within the gas turbine plant becomes possible.
- the invention is a device according to the preamble of claim 1 further developed in such a way that the rib train at least along the main longitudinal extent partially has rib pull sections, the rib pull section axes of which the main longitudinal extension includes an angle ⁇ ⁇ 0 °.
- the invention is based on the known finding that preferably at an angle to The main flow within a cooling channel ribs that run schematically Generate secondary vortex shown in Figure 2, through the cool air from the Center of the cooling channel is transported to the hot cooling channel inner walls to cool them effectively.
- the invention provides for the rib elements to be curved around them Form the longitudinal axis of the ribs so that they have, for example, a serpentine shape assume that can be carried out in many ways.
- a particularly preferred one Embodiment consists in the sinusoidal design of the rib elements, wherein the main orientation of the rib element relative to the main flow as in the known rectilinear rib elements, preferably 45 ° relative to the main flow direction, is retained.
- the ribs according to the invention there are in particular two Advantages connected, namely a largely unchanged formation of secondary vertebrae, for an active mixing of the boundary layer near the cooling channel inner wall surface leads. It is also provided by the along the ribs curved sections created a larger surface of the ribs, which increases the heat transfer surface. Provided, that due to the geometric modification of the fins, the heat transfer coefficient compared to the conventional, straight rib elements remains largely unchanged, what can be assumed, increases with the increased heat transfer surface noticeably the heat exchange between the hot cooling channel inner walls and those flowing through the cooling channel Cooling air on.
- FIG. 1 shows the top view of a cooling channel inner wall in a highly schematic manner 3 shown, on the sides facing the cooling duct curved Ribs 4 are provided.
- the rib trains 4 are curved in the illustrated case formed, for example in the manner of a sinusoidal wave train.
- FIG. 3 a - d different ribbed courses are now shown in their heat transfer properties are compared.
- Figure 3a the conventional ribbed course shown, which is often in a known manner in Cooling channels is used.
- 3b shows sinusoidal ribs
- Figure 3c shows ribs which are composed of semicircular segments
- FIG. 3d shows ribbed lines that run over semicircle segments and these over straight lines connecting rib pull sections are composed. All in the figures 3a-d shown ribs have otherwise the same rib heights and are each provided on two opposing cooling channel walls the cooling air flows.
- Figures 4a and 4b are perspective cross-sectional views through a shown square-shaped cooling channel, as it were according to the representation Figure 2, but in Figures 4a, b, the ribs 4 are according to the invention executed curved. Ribs 4 run in the exemplary embodiment according to FIG Figure 4a sinusoidal, whereas the ribs according to 4b from a series consists of semicircular sections, each over rectilinear Rib tension sections are interconnected.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
- Air-Flow Control Members (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Die Sekundärwirbel 5, 6 führen ihrerseits zu einer turbulenten Durchmischung der Grenzschicht unmittelbar über der Kühlkanalinnenwand, wodurch ein verbesserter Kühlluftaustausch an der Kühlkanalinnenwand stattfindet und sich ein größerer Wärmefluss von der heißen Kühlkanalinnenwand auf den Kühlluftstrom ergibt. Basierend auf dieser Erkenntnis wurden viele Studien angestellt, die sich mit dem Einfluss der Änderung von, die Rippenzüge bestimmende Parameter auf die Wärmeübergangseffizienz beziehen, wie Änderungen von Rippenzughöhe, Rippenzugabstand, Rippenausrichtung relativ zur Kühlkanallängsachse, Reynolds- und Prandlzahl, Kühlkanalaspektverhältnis, etc.. Diesbezügliche Untersuchungen beschränkten sich jedoch lediglich auf geradlinig verlaufende Rippenzüge.
- Fig. 1
- schematisierte Draufsicht auf eine Kühlkanalinnenwand mit erfindungsgemäß ausgebildeten Rippenzügen,
- Fig. 2
- perspektivische Querschnittsdarstellung durch einen Kühlkanal mit Strömungsprofil (Stand der Technik),
- Fig. 3a -d
- unterschiedliche Ausführungsformen zu Rippenzügen,
- Fig. 4a, b
- perspektivische Querschnittsdarstellungen durch Kühlkanäle mit erfindungsgemäß ausgebildeten Rippenzügen sowie
- Fig. 5a -e
- schematisierte Darstellungen zum Verlauf weiterer Rippenzüge.
- 1
- Kühlkanal
- 2, 3
- Kühlkanalwand
- 4
- Rippenzug
- 5, 6
- Sekundärwirbel
- 7
- Strömungsrichtung
- 8
- Rippenzuglängsachse
Claims (10)
- Vorrichtung zur Kühlung einer, einen Strömungskanal (1) umgebenden Strömungskanalwand (2, 3) mit wenigstens einem, in ein durch den Strömungskanal (1) hindurchtretendes Strömungsmedium Strömungswirbel induzierenden Rippenzug (4), der an der, dem Strömungskanal (1) zugewandten Seite der Strömungskanalwand (2, 3) angebracht ist und eine Hauptlängserstreckung (8) aufweist, die in einem Winkel α≠0° zur Strömungsrichtung des durch den Strömungskanal (1) hindurchtretenden Strömungsmediums orientiert ist,
dadurch gekennzeichnet, dass der Rippenzug (4) entlang der Hauptlängserstrekkung (8) wenigstens teilweise Rippenzugabschnitte aufweist, deren Rippenzugabschnittsachsen mit der Hauptlängserstreckung (8) einen Winkel β#0° aufweist. - Vorrichtung nach Anspruch 1,
dadurch gekennzeichnet, dass die Rippenzugabschnitte sinusförmig ausgebildet sind. - Vorrichtung nach Anspruch 1,
dadurch gekennzeichnet, dass die Rippenzugabschnitte aus aneinandergereihten Halbkreissegmenten zusammengesetzt sind. - Vorrichtung nach Anspruch 1,
dadurch gekennzeichnet, dass die Rippenzugabschnitte aus Halbkreissegmenten zusammengesetzt sind, die jeweils über geradlinig verlaufende Rippenverbindungsstücke miteinander verbunden sind. - Vorrichtung nach einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet, dass der Strömungskanal (1) einen rechteckförmigen oder quadratischen Strömungsquerschnitt aufweist und von vier Strömungskanalwandseiten begrenzt ist. - Vorrichtung nach Anspruch 5,
dadurch gekennzeichnet, dass an zwei gegenüberliegenden Strömungskanalwandseiten (2, 3) Rippenzüge (4) vorgesehen sind, die in Strömungsrichtung jeweils einer Vielzahl hintereinander, jeweils voneinander beabstandet angeordnet sind. - Vorrichtung nach Anspruch 5 oder 6,
dadurch gekennzeichnet, dass der Rippenzug (4) über eine gesamte Strömungskanalwandseite (2, 3), die beidseitig von zwei Strömungskanalwandseiten begrenzt ist, verläuft. - Vorrichtung nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet, dass der gesamte Rippenzug (4) aus Rippenzugabschnitten besteht, die Rippenzugabschnittsachsen aufweisen , die mit der Hauptlängserstreckung einen Winkel β≠0 einschließen. - Vorrichtung nach einem der Ansprüche 1 bis 8,
dadurch gekennzeichnet, dass α etwa 45° beträgt. - Vorrichtung nach einem der Ansprüche 5 bis 9,
dadurch gekennzeichnet, dass der Rippenzug (4) eine Rippenhöhe aufweist, die in etwa 10 % der Länge einer Strömungskanalwandseite entspricht.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19963373A DE19963373A1 (de) | 1999-12-28 | 1999-12-28 | Vorrichtung zur Kühlung einer, einen Strömungskanal umgebenden Strömungskanalwand mit wenigstens einem Rippenzug |
DE19963373 | 1999-12-28 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1118831A2 true EP1118831A2 (de) | 2001-07-25 |
EP1118831A3 EP1118831A3 (de) | 2001-12-12 |
EP1118831B1 EP1118831B1 (de) | 2003-09-24 |
Family
ID=7934744
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00810953A Expired - Lifetime EP1118831B1 (de) | 1999-12-28 | 2000-10-16 | Mit Rippenzug versehene Wärmetauscherwand |
Country Status (3)
Country | Link |
---|---|
US (1) | US6666262B1 (de) |
EP (1) | EP1118831B1 (de) |
DE (2) | DE19963373A1 (de) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3774843B2 (ja) * | 2001-05-25 | 2006-05-17 | マルヤス工業株式会社 | 多管式熱交換器 |
DE10218912A1 (de) | 2002-04-27 | 2003-11-06 | Modine Mfg Co | Gewellter Wärmetauschkörper |
KR20080060933A (ko) * | 2006-12-27 | 2008-07-02 | 엘지전자 주식회사 | 환기 장치의 열교환기 |
TWI400421B (zh) * | 2010-01-14 | 2013-07-01 | Asia Vital Components Co Ltd | Heat exchanger structure |
US8353329B2 (en) * | 2010-05-24 | 2013-01-15 | United Technologies Corporation | Ceramic core tapered trip strips |
US20150219405A1 (en) * | 2014-02-05 | 2015-08-06 | Lennox Industries Inc. | Cladded brazed alloy tube for system components |
US10156157B2 (en) * | 2015-02-13 | 2018-12-18 | United Technologies Corporation | S-shaped trip strips in internally cooled components |
JP6735605B2 (ja) * | 2016-06-01 | 2020-08-05 | 川崎重工業株式会社 | ガスタービンエンジンの冷却構造 |
US20180066539A1 (en) * | 2016-09-06 | 2018-03-08 | United Technologies Corporation | Impingement cooling with increased cross-flow area |
US10815793B2 (en) * | 2018-06-19 | 2020-10-27 | Raytheon Technologies Corporation | Trip strips for augmented boundary layer mixing |
Citations (6)
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---|---|---|---|---|
FR1300121A (fr) * | 1961-02-13 | 1962-08-03 | Sepi | Perfectionnements aux échangeurs de chaleur |
US4314587A (en) * | 1979-09-10 | 1982-02-09 | Combustion Engineering, Inc. | Rib design for boiler tubes |
DE19526917A1 (de) * | 1995-07-22 | 1997-01-23 | Fiebig Martin Prof Dr Ing | Längswirbelerzeugende Rauhigkeitselemente |
JPH0972683A (ja) * | 1995-09-04 | 1997-03-18 | Hitachi Cable Ltd | 伝熱管 |
JPH10211537A (ja) * | 1997-01-24 | 1998-08-11 | Furukawa Electric Co Ltd:The | 伝熱管及びその製造方法 |
US5979548A (en) * | 1996-12-23 | 1999-11-09 | Fafco, Inc. | Heat exchanger having heat exchange tubes with angled heat-exchange performance-improving indentations |
Family Cites Families (23)
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DE851958C (de) * | 1948-07-16 | 1952-10-09 | Separator Ab | Platte fuer Waermeaustauscher |
DE848508C (de) * | 1949-05-21 | 1952-09-04 | Svenska Rotor Maskiner Ab | Elementsatz fuer Waermeaustauscher |
FR1078877A (fr) * | 1952-06-25 | 1954-11-24 | Ku Hlerfabrik Langerer & Reich | Refroidisseur, en particulier pour huile |
FR1325843A (fr) * | 1962-03-23 | 1963-05-03 | échangeur de chaleur à lames rainurées | |
US3741285A (en) * | 1968-07-09 | 1973-06-26 | A Kuethe | Boundary layer control of flow separation and heat exchange |
DE2111026B1 (de) * | 1971-03-08 | 1972-08-03 | Linde Ag | Kondensator-Plattenwaermetauscher |
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DE3521914A1 (de) | 1984-06-20 | 1986-01-02 | Showa Aluminum Corp., Sakai, Osaka | Waermetauscher in fluegelplattenbauweise |
DE3622316C1 (de) * | 1986-07-03 | 1988-01-28 | Schmidt W Gmbh Co Kg | Plattenwaermeaustauscher |
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FR2714456B1 (fr) * | 1993-12-29 | 1996-01-12 | Commissariat Energie Atomique | Echangeur de chaleur à plaques améliorées. |
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-
1999
- 1999-12-28 DE DE19963373A patent/DE19963373A1/de not_active Withdrawn
-
2000
- 2000-10-16 DE DE50003825T patent/DE50003825D1/de not_active Expired - Lifetime
- 2000-10-16 EP EP00810953A patent/EP1118831B1/de not_active Expired - Lifetime
- 2000-11-30 US US09/726,052 patent/US6666262B1/en not_active Expired - Lifetime
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1300121A (fr) * | 1961-02-13 | 1962-08-03 | Sepi | Perfectionnements aux échangeurs de chaleur |
US4314587A (en) * | 1979-09-10 | 1982-02-09 | Combustion Engineering, Inc. | Rib design for boiler tubes |
DE19526917A1 (de) * | 1995-07-22 | 1997-01-23 | Fiebig Martin Prof Dr Ing | Längswirbelerzeugende Rauhigkeitselemente |
JPH0972683A (ja) * | 1995-09-04 | 1997-03-18 | Hitachi Cable Ltd | 伝熱管 |
US5979548A (en) * | 1996-12-23 | 1999-11-09 | Fafco, Inc. | Heat exchanger having heat exchange tubes with angled heat-exchange performance-improving indentations |
JPH10211537A (ja) * | 1997-01-24 | 1998-08-11 | Furukawa Electric Co Ltd:The | 伝熱管及びその製造方法 |
Non-Patent Citations (2)
Title |
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PATENT ABSTRACTS OF JAPAN vol. 1997, no. 07, 31. Juli 1997 (1997-07-31) -& JP 09 072683 A (HITACHI CABLE LTD), 18. März 1997 (1997-03-18) * |
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 13, 30. November 1998 (1998-11-30) -& JP 10 211537 A (FURUKAWA ELECTRIC CO LTD:THE), 11. August 1998 (1998-08-11) * |
Also Published As
Publication number | Publication date |
---|---|
EP1118831A3 (de) | 2001-12-12 |
DE50003825D1 (de) | 2003-10-30 |
US6666262B1 (en) | 2003-12-23 |
EP1118831B1 (de) | 2003-09-24 |
DE19963373A1 (de) | 2001-07-12 |
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