WO1998022768A1 - Air preheater heat transfer surface - Google Patents
Air preheater heat transfer surface Download PDFInfo
- Publication number
- WO1998022768A1 WO1998022768A1 PCT/US1997/019005 US9719005W WO9822768A1 WO 1998022768 A1 WO1998022768 A1 WO 1998022768A1 US 9719005 W US9719005 W US 9719005W WO 9822768 A1 WO9822768 A1 WO 9822768A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat transfer
- notches
- flat sections
- transfer plate
- adjacent
- Prior art date
Links
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
- F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
- F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
- F28D19/041—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier with axial flow through the intermediate heat-transfer medium
- F28D19/042—Rotors; Assemblies of heat absorbing masses
- F28D19/044—Rotors; Assemblies of heat absorbing masses shaped in sector form, e.g. with baskets
Definitions
- the present invention relates to rotary regenerative air preheaters for the transfer of heat from a flue gas stream to a combustion air stream. More particularly, the present invention relates to a heat transfer surface of an air preheater.
- Rotary regenerative air preheaters are commonly used to transfer heat from the flue gases exiting a furnace to the incoming combustion air.
- Conventional rotary regenerative air preheaters have a rotor rotatably mounted in a housing.
- the rotor supports heat transfer surfaces defined by heat transfer elements for the transfer of heat from the flue gases to the combustion air.
- the rotor has radial partitions or diaphragms defining compartments therebetween for supporting the heat transfer elements.
- Sector plates extend across the upper and lower faces of the rotor to divide the preheater into a gas sector and an air sector.
- a hot flue gas stream is directed through the gas sector of the preheater and transfers heat to the heat transfer elements on the continuously rotating rotor.
- the heat transfer elements are then rotated to the air sector of the preheater.
- the combustion air stream directed over the heat transfer elements is thereby heated.
- the heat transfer elements are stationary and the air and gas inlet and outlet hoods rotate.
- Heat transfer elements for regenerative air preheaters have several requirements. Most importantly, the heat transfer element must provide the required quantity of heat transfer or energy recovery for a given depth of the heat transfer element.
- Conventional heat transfer elements for preheaters use combinations of flat or ribbed form-pressed or rolled-pressed steel sheets or plates. When in combination, the plates form flow passages for the movement of the flue gas stream and air stream through the rotor of the preheater.
- the surface design and arrangement of the heat transfer plates provides contact between adjacent plates to define and maintain the flow passages through the heat transfer element. Further requirements for the heat transfer elements are that the elements produce minimal pressure drop for a given depth of the heat transfer elements, and furthermore, fit within a small volume.
- Heat transfer elements are subject to fouling from particulates and condensed contaminants, commonly referred to as soot, in the flue gas stream. Therefore, another important performance consideration is low susceptibility of the heat transfer elements to significant fouling, and furthermore easy cleaning of the heat transfer element when fouled. Fouling of the heat transfer elements is conventionally removed by soot blowing equipment emitting pressurized dry steam or air to remove by impact the particulates, scale and contaminants from the heat transfer elements. The heat transfer elements therefore must allow the soot blower energy to penetrate through the layers of heat transfer elements with sufficient energy to clean heat transfer elements positioned further from the soot blowing equipment. In addition, the heat transfer elements must also survive the wear and fatigue associated with soot blowing.
- heat transfer elements Another consideration for designing heat transfer elements is the ability to have a line of sight view through the depth of the heat transfer elements.
- the line of sight allows infrared or other hot spot detection systems to sense hot spots or early stages of fires on the heat transfer elements. Rapid and accurate detection of hot spots and early element fires minimizes damage to the preheater.
- Conventional preheaters typically employ multiple layers of different types of heat transfer elements on the rotor.
- the rotor has a cold end layer positioned at the flue gas outlet, an intermediate layer and a hot end layer positioned at the flue gas inlet.
- the hot end layer employs high heat transfer elements which are designed to provide the highest relative energy recovery for a given depth of heat transfer element.
- These high heat transfer elements conventionally have open flow channels which provide the high heat transfer but which allow the energy from the soot blowing stream to spread or diverge as it travels into the elements.
- the divergence of the soot blower stream greatly reduces cleaning efficiency of the heat transfer element closest to the soot blower, and also more remotely positioned heat transfer element layers.
- the most significant amounts of fouling typically occur in the cold end layer due at least in part to condensation.
- the obliquely oriented flow channels of conventional high heat transfer elements often preclude their use in the cold end layer due to the soot blowing energy being significantly dissipated during penetration of such high heat transfer elements. Therefore, in order to provide heat transfer surfaces that allow for effective and efficient cleaning by soot blowing, heat transfer and energy recovery have typically been compromised.
- closed channel elements are employed. Closed channels elements typically are only open at the ends of the channels. The channels are preferably straight and do not fluidly interconnect. However, generally twice the depth of closed channel heat transfer elements are required to provide the equivalent heat transfer capacity compared to conventional obliquely oriented flow channel, high heat transfer elements.
- soot blower energy was measured to be decreased only 4% by the presence of the heat transfer element.
- soot blower energy was measured to be decreased only 4% by the presence of the heat transfer element.
- the invention is an improved heat transfer element for the transfer of heat from a flue gas stream to an air stream in a rotary regenerative air preheater.
- the heat transfer element comprises a first heat transfer plate defining straight, equidistantly laterally spaced apart, mutually parallel notches.
- the notches preferably extend longitudinally the entire depth of the heat transfer element.
- Each notch is formed from parallel double ridges extending preferably symmetrically from opposite sides of the first heat transfer plate.
- undulations preferably oriented at an angle to the notches.
- the first plate is in contact with a second adjacent heat transfer plate.
- the second heat transfer plate has straight, equidistantly laterally spaced apart, mutually parallel flat sections.
- the flat sections also preferably extend longitudinally the depth of the heat transfer element.
- the flat sections on the second heat transfer plate are in corresponding opposite relationship with the notches on the first heat transfer plate.
- the ridges of the notches on the first heat transfer plate are in generally line contact with the flat sections on the second heat transfer plate.
- the second plate further has undulations positioned between and preferably oriented at an angle to the flat sections. Therefore, the notches and flat sections of both the first and second heat transfer plates are mutually parallel.
- the first and second heat transfer plates together define generally straight channels therebetween.
- a stack of generally identical heat transfer plates define a heat transfer element.
- Each heat transfer plate has straight, equidistantly laterally spaced apart, mutually parallel notches. Alternating between and parallel to the notches are straight equidistantly laterally spaced apart, mutually parallel flat sections. The notches and flat sections of the heat transfer plates are mutually parallel. The distance from each notch to the next adjacent notch, and from each flat to the next adjacent flat, is generally equivalent. Furthermore, the distance between each adjacent flat section and notch is preferably equivalent. Between the alternating notches and flat sections are undulations oriented at an angle to ⁇ he notches and flat sections.
- the heat transfer element is constructed as a stack of the generally identical heat transfer plates.
- the plates are arranged in generally mutually parallel relationship with every other plate offset one half the distance between a pair of notches. Therefore, when arranged in the stack, the notches of an initial heat transfer plate are in surface to surface contact with the flat sections of each adjacent heat transfer plate, and the notches of the adjacent heat transfer plates are in surface to surface contact with the flat sections of the initial heat transfer plate.
- the initial and adjacent heat transfer plates therefore define channels therebetween.
- the channels are open at the ends for the passage of a fluid medium such as flue gas and air therethrough, but effectively closed on the longitudinally extending sides to prevent dissipation of soot blower energy.
- the heat transfer element of the invention provides high heat transfer while also allowing for efficient and effective soot blowing.
- the heat transfer surface provides a high heat transfer efficiency by virtue of the turbulence and boundary layer interruptions introduced by the undulations on the heat transfer plates.
- the heat transfer element further provides a closed element profile such that soot blower energy is not dissipated.
- An object of the invention is to provide a heat transfer element having improved heat transfer capacity. Another object of the invention is to provide a heat transfer element allowing for improved soot blowing.
- a still another object of the invention is to provide a heat transfer element that permits soot blower energy to penetrate through the heat transfer surface with sufficient energy to clean heat transfer elements positioned further from the soot blowing equipment.
- Figure 1 is a partially broken away perspective view of a rotary regenerative preheater
- Figure 2 is a fragmentary, cross sectional view of the rotor of Figure 1 ;
- FIG 3 is a perspective view of a heat transfer element of Figure 2 in accordance with the invention.
- Figure 4 is a fragmentary end-on-view of the heat transfer element of Figure 3;
- Figure 5 is a fragmentary perspective view of the heat transfer plate of Figure 3;
- Figure 6 is a fragmentary end-on-view of an alternate embodiment of a heat transfer element in accordance with the invention.
- a conventional rotary regenerative preheater is generally designated by the numerical identifier 10.
- the air preheater 10 has a rotor 1 2 rotatably mounted in a housing 14.
- the rotor 1 2 is formed of diaphragms or partitions 1 6 extending radially from a rotor post 1 8 to the outer periphery of the rotor 1 2.
- the partitions 1 6 define compartments 1 7 therebetween for containing heat exchange elements 40.
- the housing 1 4 defines a flue gas inlet duct 20 and a flue gas outlet duct 22 for the flow of heated flue gases through the air preheater 10.
- the housing 14 further defines an air inlet duct 24 and an air outlet duct 26 for the flow of combustion air through the preheater 10.
- Sector plates 28 extend across the housing 14 adjacent the upper and lower faces of the rotor 1 2.
- the sector plates 28 divide the air preheater 10 into an air sector and a flue gas sector.
- the arrows of Figure 1 indicate the direction of a flue gas stream 36 and an air stream 38 through the rotor 1 2.
- the hot flue gas stream 36 entering through the flue gas inlet duct 20 transfers heat to the heat transfer elements 40 mounted in the compartments 1 7.
- the heated heat transfer elements 40 are then rotated to the air sector 32 of the air preheater 10.
- the stored heat of the heat transfer elements 40 is then transferred to the combustion air stream 38 entering through the air inlet duct 24.
- the cold flue gas stream 36 exits the preheater 10 through the flue gas outlet duct 22, and the heated air stream 38 exits the preheater 10 through the air outlet duct 26.
- the rotor 1 2 has generally three layers of heat transfer elements 40. (See Figures 2 and 3) A hot end layer 42 is positioned closest to the flue gas inlet duct 20 and the air outlet duct 26. An intermediate layer 44 is positioned next to the hot end layer, and finally a cold end layer 46 is positioned generally next to the flue gas outlet duct 22 and air inlet duct 24. Conventionally, the most significant fouling of the heat transfer elements 40 occurs in the cold end layer 46. Particulates, scales and deposits condensed out of the cooled flue gas, together generally referred to as soot, most typically collect on the cold end layer 46.
- soot blowing equipment for removing soot and other contaminants from the rotor 1 2 is typically positioned at the cold end of the rotor 1 2.
- the cleaning medium of the soot blower typically compressed air or dry steam, must penetrate through the cold end layer 46 to the intermediate layer 44 and the hot end layer 42 in order to obtain efficient and effective cleaning of the entire rotor 1 2.
- the heat transfer element 40 in accordance with the invention is preferably employed in the cold end layer 46 of the rotor 1 2. However, in circumstances where it is preferred that a line of sight exist through the entire rotor 1 2, or for other performance criteria, the heat transfer element 40 can be further employed in the intermediate and hot end layers 44, 42.
- the heat transfer element 40 in accordance with the invention is formed as a stack of heat transfer plates 50.
- the preferred heat transfer plates 50 are generally the same in profile, having a series of alternating, straight, mutually parallel notches 52 and flat sections 54.
- the notches 52 and flat sections 54 preferably extend longitudinally the entire depth of the heat transfer element 40.
- the notches 52 and flat sections 54 are oriented parallel to the main flow direction of the air stream 38 and flue gas stream 36 through the heat transfer element 40.
- the main flow direction is indicated by arrows in Figures 2, 3 and 5.
- Undulations 56 oriented at an angle to the notches 52 and flat sections 54 extend laterally between each notch 52 and flat section 54.
- the flat sections 54 are generally in a plane defined by the heat transfer plate 50.
- the undulations 56 extend transversely from the plane of the heat transfer plate 50 a relatively small distance.
- Each notch 52 is formed of parallel double ridges 53 extending transversely from the opposite faces of the heat transfer plate 50.
- the ridges 53 extend a greater transverse distance from the plane of the heat transfer plate than the undulations extend transversely from the plane of the heat transfer plate 50.
- the notches 52 have a generally S-shaped cross section. However, the notches 52 can also have a more triangular or Z-shaped cross section, or have other well- known shapes of notches to form oppositely transversely extending multiple ridges.
- Each flat section 54 is positioned equidistantly laterally from each adjacent flat section 54 the same lateral distance the notches 52 are positioned laterally from each adjacent notch 52. Therefore, the ridges
- each notch 52 can be positioned on one of the flat sections 54 of an adjacent heat transfer plate 50. Therefore, by production of heat transfer plates 50 of a single profile, heat transfer elements 40 can be readily constructed.
- the ridges 53 of the notches 52 of one heat transfer plate 50 will be generally in line contact with the opposite flat section 54 of an adjacent heat transfer plate 50. (See Figure 4)
- the flat sections 54 have a width sufficient to ensure that the notches contact the flats even with small manufacturing variations.
- the flat sections 54 are flat relative to the undulations 56 and notches 52. Therefore, the flat sections 54 can be slightly curved in the lateral direction and still generally maintain line contact with the notch 52 of an alternately positioned heat transfer plate 50.
- the pair of heat transfer plates 50 define channels 58 of generally constant cross section therebetween.
- the heat transfer plates 50 preferably extend longitudinally the entire depth of the heat transfer element 40.
- the channels 58 defined by adjacent contacting heat transfer plates 50 are effectively closed on the longitudinally extending sides, allowing for the efficient penetration of soot blowing cleaning medium into and through the heat transfer element 40.
- the cleaning medium of the soot blower enters the channels 58 through the open end of the channels 58 to efficiently clean the heat transfer elements 40 and the heat transfer elements of more remote subsequent layers in the rotor 1 2.
- the flat sections 54 are preferably equidistantly positioned laterally from each adjacent notch 52. Therefore, the distance between a particular flat section 54 and an adjacent notch 52 is approximately half the distance between one flat section 54 and an adjacent flat section 54.
- the preferably equivalent cross sectional areas of the channels 58 are for efficient heat transfer between the fluid medium and the heat transfer element 40.
- the undulations 56 between the notches and flat sections 54 generate turbulence in the fluid medium flowing through the heat transfer element 40. The turbulence disrupts the thermal boundary layer between the surface of the heat transfer plate and the fluid medium of air or flue gas. Therefore the undulations improve heat transfer between the heat transfer plate 50 and a fluid medium.
- the undulations are oriented 60° from the longitudinally extending notches 52 and flat sections 54.
- the straight channels 58 defined by the adjacent heat transfer plates 50 do not produce a significant pressure drop across the heat transfer element 40 for a given heat transfer capacity.
- the heat transfer plate 50 of the invention is preferably formed from a single sheet of any well known material for the production of heat transfer elements. The sheet is first rolled to define the angled undulations 56. Then at prescribed intervals, the undulations are rolled out of the sheet to form either a notch 52 or a flat section 54.
- the flat sections 54 preferably occur mid-way between any two notches 52, and the notches 52 are equidistantly positioned laterally on the sheet.
- the heat transfer plates 50 are trim cut to allow the heat transfer plates 50 to be shifted sideways to form the stack. The sideways shifting of every other heat transfer plate 50 positions the flat sections 52 of one heat transfer plate
- a heat transfer element 44 is constructed of heat exchange plates wherein notches 52 and flat sections 54 are positioned on alternating heat transfer plates.
- a first heat transfer plate 60 defines straight, equidistantly laterally spaced apart, longitudinally extending notches 52.
- the notches 52 are generally mutually parallel.
- Undulations 56 extend laterally between the notches 52 and are oriented at an angle to the notches 52.
- Second heat transfer plates 62 defining straight, equidistantly laterally spaced apart, longitudinally extending flat sections 52, are positioned on either side of the first heat transfer plate 60.
- the flat sections 54 of each second heat transfer plate 62 are oriented longitudinally mutually parallel to each other. Undulations 56 extend laterally at an angle between the flat sections.
- the distance between adjacent flat sections 54 on the second heat transfer plates 62 is generally equal to the distance between adjacent notches 52 on the first heat transfer plate 60.
- the notches 52 and flat sections 54 are generally parallel to the main flow direction of the fluid mediums through the preheater 10.
- a heat transfer element 44 is constructed as a stack of alternating first and second heat transfer plates 60, 62.
- the ridges 53 of the notches 52 on the first plate 60 are preferably in surface to surface line contact with the flat sections 54 of the adjacent second heat transfer plates 62.
- the arrangement of the heat transfer plates 60, 62 to form the heat transfer element 44 defines channels 64, 66 of generally constant cross section therebetween.
- the channels 64, 66 are generally longitudinally straight, providing a line of sight view through the heat transfer element 44 for the efficient detection of hot spots and element fires within the rotor 1 2.
- the channels 64, 66 are essentially closed on the longitudinally oriented sides to permit efficient soot blowing of the heat transfer element 44 and subsequent heat transfer elements located on the rotor 1 2.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Air Supply (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Glass Melting And Manufacturing (AREA)
- Braking Arrangements (AREA)
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA002272264A CA2272264C (en) | 1996-11-22 | 1997-10-14 | Air preheater heat transfer surface |
DE69704576T DE69704576T2 (en) | 1996-11-22 | 1997-10-14 | HEAT TRANSFER ELEMENT FOR REGENERATIVE PREHEATERS |
AT97911836T ATE200569T1 (en) | 1996-11-22 | 1997-10-14 | HEAT TRANSFER ELEMENT FOR REGENERATIVE PREHEATER |
BR9713399-0A BR9713399A (en) | 1996-11-22 | 1997-10-14 | Air preheat heat transfer surface. |
EP97911836A EP0960314B1 (en) | 1996-11-22 | 1997-10-14 | Heat transfer element for regenerative preheater |
DK97911836T DK0960314T3 (en) | 1996-11-22 | 1997-10-14 | Heat transfer element for regenerative preheater |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/755,484 | 1996-11-22 | ||
US08/755,484 US5836379A (en) | 1996-11-22 | 1996-11-22 | Air preheater heat transfer surface |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998022768A1 true WO1998022768A1 (en) | 1998-05-28 |
Family
ID=25039347
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1997/019005 WO1998022768A1 (en) | 1996-11-22 | 1997-10-14 | Air preheater heat transfer surface |
Country Status (11)
Country | Link |
---|---|
US (1) | US5836379A (en) |
EP (1) | EP0960314B1 (en) |
JP (1) | JP3168427B2 (en) |
CN (1) | CN1111716C (en) |
AT (1) | ATE200569T1 (en) |
BR (1) | BR9713399A (en) |
CA (1) | CA2272264C (en) |
DE (1) | DE69704576T2 (en) |
DK (1) | DK0960314T3 (en) |
ES (1) | ES2158521T3 (en) |
WO (1) | WO1998022768A1 (en) |
Cited By (5)
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EP2700893A1 (en) * | 2012-08-23 | 2014-02-26 | Alstom Technology Ltd | Heat transfer assembly for rotary regenerative preheater |
WO2017062929A3 (en) * | 2015-10-07 | 2017-06-22 | Arvos, Inc. | An alternating notch configuration for spacing heat transfer sheets |
WO2018125134A1 (en) * | 2016-12-29 | 2018-07-05 | Arvos, Ljungstrom Llc. | A heat transfer sheet assembly with an intermediate spacing feature |
US10175006B2 (en) | 2013-11-25 | 2019-01-08 | Arvos Ljungstrom Llc | Heat transfer elements for a closed channel rotary regenerative air preheater |
US10197337B2 (en) | 2009-05-08 | 2019-02-05 | Arvos Ljungstrom Llc | Heat transfer sheet for rotary regenerative heat exchanger |
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DE19652999C2 (en) * | 1996-12-19 | 1999-06-24 | Steag Ag | Heat storage block for regenerative heat exchangers |
US5979050A (en) * | 1997-06-13 | 1999-11-09 | Abb Air Preheater, Inc. | Air preheater heat transfer elements and method of manufacture |
US6019160A (en) * | 1998-12-16 | 2000-02-01 | Abb Air Preheater, Inc. | Heat transfer element assembly |
US6516871B1 (en) * | 1999-08-18 | 2003-02-11 | Alstom (Switzerland) Ltd. | Heat transfer element assembly |
US6450245B1 (en) * | 2001-10-24 | 2002-09-17 | Alstom (Switzerland) Ltd. | Air preheater heat transfer elements |
GB2429054A (en) * | 2005-07-29 | 2007-02-14 | Howden Power Ltd | A heating surface element |
DE102006003317B4 (en) | 2006-01-23 | 2008-10-02 | Alstom Technology Ltd. | Tube bundle heat exchanger |
CN101813430B (en) * | 2009-02-20 | 2012-05-30 | 武汉东海石化重型装备有限公司 | Steel ball heat exchanging system |
US9285172B2 (en) | 2009-04-29 | 2016-03-15 | Westinghouse Electric Company Llc | Modular plate and shell heat exchanger |
US20120103578A1 (en) | 2009-04-29 | 2012-05-03 | Westinghouse Electric Company Llc | Modular plate and shell heat exchanger |
US8622115B2 (en) | 2009-08-19 | 2014-01-07 | Alstom Technology Ltd | Heat transfer element for a rotary regenerative heat exchanger |
US9644899B2 (en) | 2011-06-01 | 2017-05-09 | Arvos, Inc. | Heating element undulation patterns |
ES2699809T3 (en) * | 2012-01-12 | 2019-02-12 | Westinghouse Electric Co Llc | Shell heat exchanger and modular plate |
CN102788423A (en) * | 2012-08-02 | 2012-11-21 | 樊荣 | Air pre-heater |
MX368708B (en) * | 2013-09-19 | 2019-10-11 | Howden Uk Ltd | Heat exchange element profile with enhanced cleanability features. |
US9587894B2 (en) | 2014-01-13 | 2017-03-07 | General Electric Technology Gmbh | Heat exchanger effluent collector |
CN104457381B (en) * | 2014-12-30 | 2017-03-15 | 上海锅炉厂有限公司 | A kind of oblique wave wave type corrugated plating |
JP2017048973A (en) * | 2015-09-02 | 2017-03-09 | アルヴォス インコーポレイテッド | Heat transfer element laminated body |
US10837714B2 (en) * | 2017-06-29 | 2020-11-17 | Howden Uk Limited | Heat transfer elements for rotary heat exchangers |
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US4930569A (en) * | 1989-10-25 | 1990-06-05 | The Air Preheater Company, Inc. | Heat transfer element assembly |
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1996
- 1996-11-22 US US08/755,484 patent/US5836379A/en not_active Expired - Lifetime
-
1997
- 1997-10-14 DK DK97911836T patent/DK0960314T3/en active
- 1997-10-14 DE DE69704576T patent/DE69704576T2/en not_active Expired - Lifetime
- 1997-10-14 ES ES97911836T patent/ES2158521T3/en not_active Expired - Lifetime
- 1997-10-14 WO PCT/US1997/019005 patent/WO1998022768A1/en active IP Right Grant
- 1997-10-14 CA CA002272264A patent/CA2272264C/en not_active Expired - Lifetime
- 1997-10-14 AT AT97911836T patent/ATE200569T1/en not_active IP Right Cessation
- 1997-10-14 CN CN97199972A patent/CN1111716C/en not_active Expired - Lifetime
- 1997-10-14 JP JP52365498A patent/JP3168427B2/en not_active Expired - Lifetime
- 1997-10-14 BR BR9713399-0A patent/BR9713399A/en not_active Application Discontinuation
- 1997-10-14 EP EP97911836A patent/EP0960314B1/en not_active Expired - Lifetime
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US2596642A (en) * | 1945-05-28 | 1952-05-13 | Jarvis C Marble | Heat exchanger |
DE966614C (en) * | 1950-01-25 | 1957-08-29 | Svenska Rotor Maskiner Ab | Regenerative heat exchangers, especially air preheaters |
US4744410A (en) * | 1987-02-24 | 1988-05-17 | The Air Preheater Company, Inc. | Heat transfer element assembly |
US4930569A (en) * | 1989-10-25 | 1990-06-05 | The Air Preheater Company, Inc. | Heat transfer element assembly |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10982908B2 (en) | 2009-05-08 | 2021-04-20 | Arvos Ljungstrom Llc | Heat transfer sheet for rotary regenerative heat exchanger |
US10197337B2 (en) | 2009-05-08 | 2019-02-05 | Arvos Ljungstrom Llc | Heat transfer sheet for rotary regenerative heat exchanger |
AU2016201784B2 (en) * | 2012-08-22 | 2017-11-30 | Arvos Ljungstrom Llc | Heat transfer assembly for rotary regenerative preheater |
RU2561561C2 (en) * | 2012-08-23 | 2015-08-27 | Альстом Текнолоджи Лтд | Heat exchange unit for rotary regenerative heater |
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WO2018125134A1 (en) * | 2016-12-29 | 2018-07-05 | Arvos, Ljungstrom Llc. | A heat transfer sheet assembly with an intermediate spacing feature |
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AU2017384971B2 (en) * | 2016-12-29 | 2023-02-02 | Arvos Ljungstrom Llc | A heat transfer sheet assembly with an intermediate spacing feature |
Also Published As
Publication number | Publication date |
---|---|
EP0960314A1 (en) | 1999-12-01 |
US5836379A (en) | 1998-11-17 |
CN1111716C (en) | 2003-06-18 |
DE69704576T2 (en) | 2001-11-08 |
DE69704576D1 (en) | 2001-05-17 |
CA2272264A1 (en) | 1998-05-28 |
BR9713399A (en) | 2000-01-25 |
CN1238833A (en) | 1999-12-15 |
ATE200569T1 (en) | 2001-04-15 |
DK0960314T3 (en) | 2001-08-13 |
CA2272264C (en) | 2004-01-06 |
JP3168427B2 (en) | 2001-05-21 |
JP2000505187A (en) | 2000-04-25 |
ES2158521T3 (en) | 2001-09-01 |
EP0960314B1 (en) | 2001-04-11 |
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