EP2607830A1 - Hocheffektiver Gas-zu-Gas-Wärmetauscher - Google Patents

Hocheffektiver Gas-zu-Gas-Wärmetauscher Download PDF

Info

Publication number
EP2607830A1
EP2607830A1 EP20110194253 EP11194253A EP2607830A1 EP 2607830 A1 EP2607830 A1 EP 2607830A1 EP 20110194253 EP20110194253 EP 20110194253 EP 11194253 A EP11194253 A EP 11194253A EP 2607830 A1 EP2607830 A1 EP 2607830A1
Authority
EP
European Patent Office
Prior art keywords
fluid
heat exchange
recuperator
channels
cell
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
Application number
EP20110194253
Other languages
English (en)
French (fr)
Other versions
EP2607830B1 (de
Inventor
Charlie Penny
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.)
Senior UK Ltd
Original Assignee
Senior UK Ltd
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 Senior UK Ltd filed Critical Senior UK Ltd
Priority to EP11194253.8A priority Critical patent/EP2607830B1/de
Priority to DE11194253T priority patent/DE11194253T1/de
Publication of EP2607830A1 publication Critical patent/EP2607830A1/de
Application granted granted Critical
Publication of EP2607830B1 publication Critical patent/EP2607830B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits

Definitions

  • the present invention relates to heat exchangers.
  • Machines such as gas turbines and solid oxide fuel cells have exhaust gas containing a high level of thermal energy; they also require the inlet air to be pre-heated prior to entry into combustor or fuel cell.
  • a long used method of addressing both these problems is to have a gas to gas heat exchanger, also known as a recuperator, to transfer heat energy from the exhaust gas to the incoming air.
  • a gas to gas heat exchanger also known as a recuperator
  • the pressure drop through the recuperator must be low. High pressure loss requires mechanical energy to push the gases through the recuperator and thus reduces over all plant efficiency.
  • the material for the heat exchange surfaces needs to be high temperature special alloy. This is expensive material and thus the less weight of material required the better.
  • a recuperator comprising:
  • the recuperator is designed to be highly effective, greater than 80%, with a low pressure drop across both fluid paths of less than 4% of inlet pressures. It also is designed to be light weight when compared to known recuperators.
  • the recuperator uses thin gauge strip less than 0.5mm thickness, with each heat exchange surface being formed from a single sheet of material to maximize heat transfer and reduce weight.
  • the first gas flows from one end of the heat exchange surface to the other end.
  • the second gas is introduced to the heat exchange surface at the outlet end of the first gas flow, through a hole in the heat exchange surface at or near the centre line of the heat exchange surface, and exits at the opposite end of the surface through a hole at or near the centre line of the heat exchange surface.
  • the centre portion of the heat exchange surface has a ribbed profile, with the ribs running in the direction of flow of the gases from end to end.
  • the recuperator is substantially contra flow, with the first gas flow being in an opposite direction to the second gas flow.
  • the two gases must also be distributed relatively evenly across the width of the heat exchange surface.
  • the profile around the inlet and/or outlet holes for the second fluid are designed to direct and guide flow of the second fluid across the whole width of the heat exchange surface.
  • the profile, on the first fluid side, around the second fluid holes and the form of the centre portion ribbed profile is as such to distribute the first fluid relatively evenly across the width of the heat exchange surface.
  • the outer casing that contains the surfaces may also be made from thin gauge material.
  • the outermost air cell plates may form two sides of the outer skin of the recuperator. The edges of the air cell may be joined together to form two sides of the outer skin of the recuperator and the first (fluid 1) channels
  • the three of the four inlets and outlets for the recuperator are connected to the recuperator by expansion joints.
  • the whole of the recuperator can expand, reducing thermal stresses and delivering a durable product.
  • channel is used to denote a fluid pathway between an inlet and an outlet, and it may be either fully enclosed in the form of a tube having a solid fluid impervious wall, or it may be partially enclosed allowing for some amount of leakage either into or out of the passage between the inlet and outlet. In some embodiments leakage between adjacent fluid channels may occur.
  • the channel is guided by channel walls to guide the fluid along a pathway between an inlet and an outlet.
  • FIG. 1 herein illustrates schematically a specific embodiment recuperator assembly.
  • the recuperator is mounted vertically.
  • the recuperator 100 comprises a first fluid inlet 101; a first fluid outlet 102; a second fluid inlet 103; a second fluid outlet 104; a plurality of heat exchange cells 105, arranged in parallel with each other; and an outer casing 106 surround the plurality of heat exchange cells.
  • a first fluid enters the recuperator at the top of the assembly (second end of the recuperator) through a first expansion bellows (not shown) which connects to the first fluid inlet 101, flows around and between the cells and exits at the bottom of the assembly (first end of the recuperator) via the first fluid outlet 102.
  • the first fluid inlet, first fluid outlet, second fluid inlet, and second fluid outlet are all located on a centre line of the recuperator along a main central axis of the recuperator.
  • a second fluid enters the recuperator at the lower end of the assembly via second inlet 103, and a second expansion bellows 107 (this bellows is not always required) flows along the orifice formed by the inlet holes in each cell such that it supplies each individual cell, flows through the plurality of cells and exits through the outlet holes in the cells via a third expansion bellows 108 at the upper side of the assembly and through second outlet 104.
  • the overall direction of flow of the first fluid is substantially opposite to the overall direction of flow of the second fluid, so that the two fluids pass over the heat exchange cells in a contra-flow arrangement. This maximises the heat exchange between the first fluid and the second fluid, via the thin gauge metal walls of the heat exchange cells.
  • the paths of the first fluid channels are arranged side by side with and closely follow the paths of the second fluid channels, such that the first fluid in the plurality of first fluid channels flows parallel to and in an opposite direction to the second fluid flowing in a plurality of second fluid channels.
  • Figure 2 illustrates schematically a single heat exchange cell 105 viewed externally from the top (or bottom). This particular design is for relatively low pressure, for example pressures less than 1.5Bar A.
  • Each cell 105 comprises a pair of stamped or pressed metal plates 200, which are welded together around their external perimeter edges, the plates forming a fluid inlet 201 for the second fluid; a fluid outlet 202 for the second fluid; a central region 203, comprising a plurality of parallel substantially straight ribs or ridges 204, forming a plurality of channels which direct the first fluid flow in a direction right to left as shown in Figure 2 , and the second fluid flow in a direction left to right, so that the two fluids flow in 180° opposite directions to each other across the central section of the cell; a first flat unchannelled region 205 at the first end of the cell; a first raised formation 206 surrounding the fluid inlet 201, for dispersing and directing the second fluid across the whole width of the cell, in the unchannelled region 205 at the first end of the cell; a second unchannelled region 207 at a second end of the cell; a second raised formation 208 which serves to allow entry of the second fluid at any position around the fluid outlet
  • the cell 105 consists of two heat exchange plates each having the same form, which form two halves of the heat exchange cell. Each plate has two heat exchange surfaces which are between the second fluid in the centre of the cell, and the first fluid flowing around the outside of the cell.
  • the plates are welded together around the outer perimeter 200 of the cell and also at intervals 209 to 211 across the ribbed central channel section 203. The joint around the perimeter gives a leak tight cell that allows the second fluid (fluid 2) to enter and exit only through the inlet and outlet orifices 201, 202 respectively.
  • the centre section of the plate comprises a series of channels formed by ribs in the plates.
  • the profile of the ribs may vary across the width to improve relative flow of each fluid through the channels.
  • three of the channel roots 209 to 211 are welded together. This is to give mechanical strength to the plate.
  • the number of welds will depend on the fluid pressure of the application for which the recuperator is designed.
  • the two fluids are controlled to flow in opposite directions.
  • the forms disperse and direct the second fluid (fluid 2) at the inlet such that the second fluid flows into all the ribbed channels across the plate.
  • the forms enable smooth flow from the ribbed section into the outlet.
  • the inlet and outlet are also designed to reduce fluid pressure drop to a minimum whilst still controlling the flow of the second fluid.
  • the inlet for the second fluid has a peripheral lip portion 212 between the orifice and the plurality of second fluid channels, to prevent the second fluid from short circuiting across the smallest gap from the inlet to the channel, and to spread the second fluid in a direction across a width of the cell to fill the outermost second fluid channels.
  • Figure 3 herein illustrates schematically one end of a second embodiment of a single heat exchange cell 300 viewed externally from one side.
  • the cell 300 comprises a pair of stamped or pressed metal plates, which are welded together around their external perimeter edges, the plates forming a fluid inlet 301 for the second fluid; a fluid outlet for the second fluid; a central region 302, comprising a plurality of parallel substantially straight channels 303 which direct the first fluid flow in a direction bottom to top as shown in Figure 3 , and the second fluid flow in an downward direction as shown in Figure 3 , so that the two fluids flow in 180° opposite directions across the central section of the cell; a raised formation 304 around the fluid inlet 301; a substantially flat planar region 305; and a further set of formations 306 extending in an arched formation towards the outer edges of the cell, for dispersing and directing the second fluid across the whole width of the interior of the cell, in the otherwise unchannelled flat region 305 at the first end of the cell; and a second raised formations
  • This particular design in Figure 3 is for higher pressure applications.
  • the difference between the lower pressure application heat exchange cell of Figure 2 and the higher pressure cell of Figure 3 is that all of the channel roots are welded in the higher pressure cell.
  • the cell in figure 3 is capable of resisting fluid pressures up to 10 bar.
  • Figure 4 herein illustrates schematically an isometric view of two cells.
  • the cells are joined to each other at the second fluid (fluid 2) inlet and outlet.
  • the joints are leak tight such that the second fluid (fluid 2) can pass from one cell to the next.
  • First fluid (fluid 1) flows between the adjacent cells, whereas the second fluid (fluid 2) flows through the cells.
  • a plurality of cells when joined together to form a heat exchange assembly, locate with each other such that the plurality of inlets form an inlet manifold for the second fluid, and a plurality of second fluid outlets perform an outlet manifold for the second fluid.
  • Shown in Figure 4 is the second fluid (fluid 2) 400 flowing into the plurality of cells in a first direction 400, and a out of the cells in a second direction 401.
  • First fluid 402 flows between the two cells.
  • Figure 5 herein illustrates schematically an isometric view of a single cell illustrating how each fluid is introduced to the heat exchange surfaces.
  • the fluid contra-flows are arranged such that the hot first fluid enters the recuperator at the same end as the heated second fluid exits the recuperator.
  • the first fluid which is relatively cooler than when it entered the recuperator at the first end flows in an opposite direction to the second fluid which is inlet at the second end. Therefore, the hottest part of the first fluid enters the recuperator at the same end as the hottest part of the second fluid exits the recuperator, and the coolest part of the first fluid exits the recuperator at the same end as the coolest part of the second fluid enters the recuperator.
  • the centre line of the cell is shown at 506.
  • the recuperator is more efficient.
  • Figure 6 herein illustrates schematically an end on view of the recuperator from the fluid 1 inlet end.
  • the plurality of heat exchange cells 105 are arranged side by side, so that the first fluid entering the recuperator via the first fluid inlet 101 can pass through the assembly of heat exchange cells.
  • the second fluid outlet manifold which comprises the plurality of raised formations 208, as shown in Figures 2, 3 , 4 and 5 herein, which abut each other to form a gas tight substantially cylindrical manifold for the second fluid.
  • the first fluid must pass around this substantially cylindrical obstruction, either side, in order to enter the channelled regions of the cells and pass between adjacent touching cells towards the other end of the recuperator.
  • the first fluid flows in a plurality of channels 600 formed between the individual cells in the heat exchange assembly whereas the second fluid flows inside each sealed cell.
  • Figures 7A and 7B herein illustrate schematically an edge view of two cells, 7A from the side and 7B from the end.
  • FIG. 7A there is illustrated schematically in view from one side, a pair of heat exchange cells in contact with each other, as they would appear in use inside the recuperator.
  • a first end 700 the raised formations 206 around the second fluid inlet abut each other in order to form an inlet manifold.
  • the raised formations 208 at the second end of the heat exchange cells abut each other, to form a tubular substantially cylindrical outlet manifold for the second fluid.
  • the plurality of channels 600 through which the first fluid can flow from one end of the recuperator to the other.
  • each cell has a plurality of elongate ribs or ridges 702 which protrude on the outside of the cell, such that when two cells are in contact with each other, the ridges contact each other, forming a fluid channel 600 for passage of the first fluid along a length of the cells.
  • the protruding formations 206, 208 of adjacent cells meet each other, such that the first fluid cannot ingress between two adjacent cells an into the interior of a cell, and therefore cannot mix with the second fluid flow inside each cell. Rather, the first fluid flow is directed around the formations 206, which in combination form the second fluid inlet manifold (or formations 208 which form the second fluid outlet manifold at the other end of the cells).
  • Figure 8 herein illustrates schematically a computerized flow diagram of velocity vectors illustrating how first fluid (fluid 1) flows over a heat exchange surface of a cell between adjacent cells.
  • Shown in Figure 8 is a vector flow diagram in the plane between two adjoining cells. Since the cell is symmetric about a central axis along its length, the other side of the cell will have an equivalent mirror image vector flow.
  • the first fluid entering at the second end 800 of the heat exchange assembly flows around the outlet 208 for the second fluid flow, and into the plurality of channels 600. Once in the channels, the gas flows linearly along the length of the channels, and exits the channels into the cavity 205 at the first end 801 of the heat exchanger assembly.
  • Figure 9 herein illustrates schematically a computerized flow diagram plot of velocity vectors illustrating how the second fluid (fluid 2) flows through the interior of a cell.
  • the second fluid enters the cell at the first fluid inlet 201, and flows around the circular portions 900 around a perimeter of the second fluid inlet, and around the welded lip portion 901, filling the substantially flat cavity 902, and entering into the plurality of channels 204.
  • the computerized flow diagram is for the first embodiment heat exchange cell optimized for relatively low pressure fluids where an amount of fluid flow between the individual adjacent channels 204 is permitted, since the troughs 904 between adjacent channels are not all welded to each other along their entire length.
  • the second fluid flows out of the second fluid outlet 202, passing between the pillars 905 which extend internally across the depth of the cell.
  • Figure 10 herein illustrates schematically a diagram of the centre ribbed section of the cell.
  • Half of a single cell is shown in part cut away view, in contact with an adjacent half cell.
  • Each cell occupies a rectangular volume 1000 having a length I, a depth d, and a width w.
  • first fluid channels in total (19 cells across half of the cell) in which the first fluid flows between the adjacent cells, and 36 second fluid channels (18 channels in half a cell) through with the second fluid flows through the individual cell.
  • the plurality of channels for the first fluid, which are formed between adjacent cells are surrounded by the plurality of second fluid channels in the cells adjacent and either side of the plurality of first fluid channels.
  • the plurality of second fluid channels within each cell are surrounded by separate sets of first fluid channels either side of the cell, the first fluid channels and second fluid channels being separated by the thin metal walls of the cell typically having thickness of the order of less than 0.5mm, so that heat transfer occurs through the metal wall of the cell between the first fluid channels and the second fluid channels and vice versa.
  • FIG. 10 Also shown in Figure 10 , is the internal structure of the cell in the area around the second fluid inlet and second fluid outlet. Since the two sides of each cell must be separated and spaced apart from each other to form an end cavity through which the second fluid flows, and since the region around the second fluid inlet and second fluid outlet need to be rigid under compressive force, there are provided a plurality of cylindrical pillars 1001 around the circumference of the substantially circular inlet and outlet apertures. At the second fluid inlet aperture 201, there is also provided a substantially arcuate baffle region 1002, which prevents the second fluid flowing directly from second fluid inlet, directly into the centermost plurality of second fluid channels along the length of the cell. The baffle region 1002 forces the second fluid flow to travel across the width of the cell towards the outermost second fluid channels, as shown in Figure 9 herein.
  • FIG 11A there is illustrated schematically a plot of fluid flow measured as mass flow/cross sectional area in kg/m 2 s, across 19 of the first fluid channels, across half the width of the individual cells of the heat exchange assembly as shown in Figure 10 herein.
  • the first fluid channels are formed between adjacent individual cells.
  • the ideal with the first fluid flow is to achieve an uninterrupted fluid flow which is substantially uniform across the width of the cell. This needs to be balanced with the practicalities of size and complexity.
  • the cell has a relatively larger fluid channel (channel 10) a quarter way across the distance w of the cell, as well as relatively larger first fluid channels at the edge of the cell (channel 1) and along a central axis of the cell channel 19.
  • the fluid flow in the other half of the cell is a mirror image to that shown in Figure 11A .
  • An ideal fluid flow for the first fluid may be to have an equal fluid flow through each first fluid channel, across the heat exchanger assembly, or in other words, to have all of the individual heights of the channel flows shown in Figure 11A to be the same height.
  • the first fluid flow along and across the heat exchange unit is relatively uniform as shown in Figure 11A herein, but with a slightly lower rate of fluid flow along the innermost first fluid channels between the second fluid inlet and outlet, where the flow of first fluid through the heat exchange unit is disrupted by the inlet and outlet.
  • FIG. 11 B there is illustrated schematically a plot of fluid flow mass flow/divided by cross sectional area (kg/m 2 s) for 18 of the second fluid channels across one half of the width of an individual cell.
  • the object would be to distribute the second fluid across the width of the cell, such that the fluid flow across each second fluid channel is approximately the same, giving substantially uniform fluid flow along the device.
  • the rate of fluid flow along the second fluid channels at the outer edges of the cell are relatively lower (less than 50%) of the rate of fluid flow of second fluid along the inner most second fluid channels in the cell.
  • FIG. 12 there is illustrated schematically in end on view, one side of a heat exchange assembly 1200 comprising a plurality of heat exchange cells 1201 - 1210, each comprising a pair of heat exchange plates 1211.
  • the outermost heat exchange plates 1212, 1213 form two sides of the outer skin of the recuperator.
  • the casing is formed from two separate sheets, one of which 1214 is shown in Figure 12 .
  • Another similar plate is provided at an opposite side of the heat exchange assembly, so that the pair of externally presented heat exchange plates 1212, 1213 and the side plates 1214 form the outer casing of the recuparator.
  • the plurality of first fluid channels 1215 are enclosed by the outermost cells 1201, 1210, and the metal side plates 1214.
  • the heat exchange plates of individual cells are shown touching each other in the assembly.
  • each of the individual first fluid channels 1215 are fully separated from each other, and in other embodiments, there may be cross flow and leakage of first fluid between adjacent first fluid channels 1215.
  • the individual cells may be slightly spaced apart from each other, so that there may be a small amount of fluid transfer between adjacent first fluid channels 1215 along the length of the cell assembly 1200.
  • FIG. 13 there is illustrated schematically in view from on end, one side of a further embodiment heat exchange assembly 1300 comprising a plurality of heat exchange cells 1301 - 1310, each comprising a pair of heat exchange plates 1311.
  • the outermost heat exchange plates 1312, 1313 form two sides of the outer skin of the recuperator.
  • Another two sides 1314 of the heat exchange assembly are formed by connecting the sides of the adjacent plates.
  • the sides of the heat exchange plates are connected together in a fluid sealed manner so that first fluid cannot escape out of the sides of the heat exchanger.
  • Adjacent troughs in the heat exchange cells are welded, brazed or soldered together to form the sides of the heat exchange assembly.
  • the heat exchange plates of individual cells are shown touching each other in the assembly.
  • each of the individual first fluid channels 1315 are fully separated from each other, and in other embodiments, there may be leakage of first fluid between adjacent first fluid channels 1315.
  • the individual cells may be slightly spaced apart from each other, except at their connected sides, so that there may be a small amount of fluid transfer between adjacent first fluid channels 1315 along the length of the cell assembly 1300.
  • the heat exchange assembly 1400 comprises a plurality of heat exchange cells 1401 - 1410, each comprising a pair of heat exchange plates 1411.
  • the outermost heat exchange plates 1212 have connected to them a further substantially flat outer plate 1413, which acts as an outer casing to the heat exchange assembly and to the recuperator.
  • the other two sides of the heat exchange assembly may be formed by joining together adjacent cells as shown in Figure 13 herein, or by an additional side plate as shown in Figure 12 herein.
  • the heat exchange plates of individual cells are shown touching each other in the assembly.
  • each of the individual first fluid channels 1414 are fully separated from each other, and in other embodiments, there may be leakage of first fluid between adjacent first fluid channels 1414.
  • the individual cells may be slightly spaced apart from each other, so that there may be a small amount of fluid transfer between adjacent first fluid channels 1414 along the length of the cell assembly.
  • first fluid channels and second fluid channels are straight linear channels having substantially unobstructed straight flow paths.
  • first and second fluid channels may follow a curved or serpentine path, or may have a series of depressions or dimples to create turbulent fluid flow.
  • first and second fluid channels are each positioned adjacent to each other separate by a thin gauge material to allow efficient heat transfer between the first and second fluids.

Landscapes

  • 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)
EP11194253.8A 2011-12-19 2011-12-19 Hocheffektiver Gas-zu-Gas-Wärmetauscher Active EP2607830B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP11194253.8A EP2607830B1 (de) 2011-12-19 2011-12-19 Hocheffektiver Gas-zu-Gas-Wärmetauscher
DE11194253T DE11194253T1 (de) 2011-12-19 2011-12-19 Hocheffektiver Gas-zu-Gas-Wärmetauscher

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11194253.8A EP2607830B1 (de) 2011-12-19 2011-12-19 Hocheffektiver Gas-zu-Gas-Wärmetauscher

Publications (2)

Publication Number Publication Date
EP2607830A1 true EP2607830A1 (de) 2013-06-26
EP2607830B1 EP2607830B1 (de) 2018-09-12

Family

ID=45370447

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11194253.8A Active EP2607830B1 (de) 2011-12-19 2011-12-19 Hocheffektiver Gas-zu-Gas-Wärmetauscher

Country Status (1)

Country Link
EP (1) EP2607830B1 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104389683A (zh) * 2014-11-05 2015-03-04 中国船舶重工集团公司第七�三研究所 紧凑型回热器
CN107747881A (zh) * 2017-10-30 2018-03-02 佛山科学技术学院 方形管孔整圆形支撑板取代弓形折流板的管壳式换热器
CN110429358A (zh) * 2015-07-16 2019-11-08 浙江三花汽车零部件有限公司 热交换装置
CZ308367B6 (cs) * 2019-04-24 2020-06-24 Vysoká Škola Báňská - Technická Univerzita Ostrava Rekuperační deskový výměník tepla
CN114508956A (zh) * 2020-11-16 2022-05-17 丹佛斯有限公司 板壳式热交换器和用于板壳式热交换器的热传递板
JP2022173136A (ja) * 2021-05-06 2022-11-17 コミッサリア ア レネルジー アトミーク エ オ ゼネルジ ザルタナテイヴ スタッドにより形成された少なくとも１つの流体供給分配ゾーンを組み込んだチャネルを備えるプレートを有するタイプの熱交換器モジュール

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001098723A1 (en) * 2000-06-21 2001-12-27 Serck Heat Transfert Limited Exhaust gas cooler
US20020185265A1 (en) 1996-02-01 2002-12-12 Ingersoll-Rand Energy Systems Corporation Dual-density header fin for unit-cell plate-fin heat exchanger
US20040069475A1 (en) * 2002-06-28 2004-04-15 Modine Manufacturing Co. Heat exchanger
EP1936310A1 (de) * 2006-12-23 2008-06-25 Joachim Schult Kompaktplattenwärmeübertrager
EP2136175A1 (de) * 2008-06-21 2009-12-23 Joachim Schult Profilierte rechteckige Wärmeübertragungsplatte und ein damit hergestellter Kompaktplattenwärmeübertrager

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020185265A1 (en) 1996-02-01 2002-12-12 Ingersoll-Rand Energy Systems Corporation Dual-density header fin for unit-cell plate-fin heat exchanger
WO2001098723A1 (en) * 2000-06-21 2001-12-27 Serck Heat Transfert Limited Exhaust gas cooler
US20040069475A1 (en) * 2002-06-28 2004-04-15 Modine Manufacturing Co. Heat exchanger
EP1936310A1 (de) * 2006-12-23 2008-06-25 Joachim Schult Kompaktplattenwärmeübertrager
EP2136175A1 (de) * 2008-06-21 2009-12-23 Joachim Schult Profilierte rechteckige Wärmeübertragungsplatte und ein damit hergestellter Kompaktplattenwärmeübertrager

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104389683A (zh) * 2014-11-05 2015-03-04 中国船舶重工集团公司第七�三研究所 紧凑型回热器
CN110429358A (zh) * 2015-07-16 2019-11-08 浙江三花汽车零部件有限公司 热交换装置
CN110429358B (zh) * 2015-07-16 2023-05-09 浙江三花汽车零部件有限公司 热交换装置
CN107747881A (zh) * 2017-10-30 2018-03-02 佛山科学技术学院 方形管孔整圆形支撑板取代弓形折流板的管壳式换热器
CZ308367B6 (cs) * 2019-04-24 2020-06-24 Vysoká Škola Báňská - Technická Univerzita Ostrava Rekuperační deskový výměník tepla
CN114508956A (zh) * 2020-11-16 2022-05-17 丹佛斯有限公司 板壳式热交换器和用于板壳式热交换器的热传递板
JP2022173136A (ja) * 2021-05-06 2022-11-17 コミッサリア ア レネルジー アトミーク エ オ ゼネルジ ザルタナテイヴ スタッドにより形成された少なくとも１つの流体供給分配ゾーンを組み込んだチャネルを備えるプレートを有するタイプの熱交換器モジュール

Also Published As

Publication number Publication date
EP2607830B1 (de) 2018-09-12

Similar Documents

Publication Publication Date Title
EP2607830B1 (de) Hocheffektiver Gas-zu-Gas-Wärmetauscher
CA2839884C (en) Plate heat exchanger including separating elements
JP5093980B2 (ja) 燃料電池断熱熱交換器
US9631876B2 (en) Heat exchanger
US8033326B2 (en) Heat exchanger
CN103477042A (zh) 用于机动车辆的热电发生器的具有热交换器的装置
ES2504971T3 (es) Intercambiador de calor de placas y método para la fabricación de un intercambiador de calor de placas
US20210247103A1 (en) Heat exchanger unit and condensing boiler using the same
US10458679B2 (en) Plate heat exchanger, in particular for condensing boilers
US20070169924A1 (en) Heat exchanger installation
PH12015500532B1 (en) Hot air oven
US20210247102A1 (en) Heat-exchange pipe, heat-exchanger unit using same, and condensing boiler using same
KR20150051910A (ko) 연료 전지 유닛과 구성 요소를 포함하는 장치 및 그러한 장치에서 사용하기 위한 구성 요소 유닛과 스택 구성 요소
US20070235174A1 (en) Heat exchanger
RU2625324C2 (ru) Охлаждающий радиатор с жидкостным охлаждением
CS202599B2 (en) Lamellar heat exchanger
JP4891353B2 (ja) １次流体と２次流体の間の熱交換のための組立体
RU2395775C1 (ru) Коллекторный пластинчатый теплообменник
JP6449190B2 (ja) ガス給湯器
RU2619432C2 (ru) Радиально-пластинчатый тепломассообменный аппарат
US11598591B2 (en) Heat exchanger and method for manufacturing a heat exchanger core with manifold
CN108775828B (zh) 超导换热单元及其装置、***
CN216815133U (zh) 板式换热器
EP1563231B1 (de) Heisslufterzeuger
CA3054440A1 (en) Constant pressure heat exchanger

Legal Events

Date Code Title Description
17P Request for examination filed

Effective date: 20111219

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

REG Reference to a national code

Ref country code: DE

Ref legal event code: R210

Effective date: 20131219

Ref country code: DE

Ref legal event code: R210

Ref document number: 602011051947

Country of ref document: DE

Effective date: 20131219

17Q First examination report despatched

Effective date: 20150518

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20180525

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602011051947

Country of ref document: DE

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602011051947

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1041100

Country of ref document: AT

Kind code of ref document: T

Effective date: 20181015

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180912

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181212

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181212

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181213

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1041100

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180912

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190112

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190112

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602011051947

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed

Effective date: 20190613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181219

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20181231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181231

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181231

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20111219

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180912

Ref country code: MK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180912

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20231212

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20231213

Year of fee payment: 13