US20050133202A1 - Heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger - Google Patents
Heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger Download PDFInfo
- Publication number
- US20050133202A1 US20050133202A1 US10/840,952 US84095204A US2005133202A1 US 20050133202 A1 US20050133202 A1 US 20050133202A1 US 84095204 A US84095204 A US 84095204A US 2005133202 A1 US2005133202 A1 US 2005133202A1
- Authority
- US
- United States
- Prior art keywords
- fluid
- flow
- heat exchanger
- apertures
- coils
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
-
- 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
- F28D21/0005—Recuperative heat exchangers the heat being recuperated from exhaust gases for domestic or space-heating systems
- F28D21/0007—Water heaters
-
- 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
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
- F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
- F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2200/00—Heat sources or energy sources
- F24D2200/16—Waste heat
- F24D2200/18—Flue gas recuperation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/06—Derivation channels, e.g. bypass
Definitions
- the present invention relates to a heat exchanger for heat exchange between a first fluid and a second fluid and comprising a generally cylindrical casing with a first inlet and a first outlet for allowing said first fluid to flow through said casing in a generally axial direction, and at least one helical coil of a finned or corrugated tube arranged inside said casing.
- Heat exchangers of this type are known where the first fluid is forced to flow from inside the coil or coils outwards or vice versa.
- the transfer of heat from the first fluid to the second fluid in the coils is not very well controlled and therefore not as efficient as possible.
- first fluid for instance exhaust gas from a natural gas fired turbine, an internal combustion engine, an incinerator, a furnace, a burner or the like
- this object is obtained by providing a generally cylindrical fluid conduit inside said casing generally coaxial therewith so that an axially extending first tubular space is defined between said conduit and said casing, said conduit having a second inlet and a second outlet for allowing said first fluid to flow through said conduit in a generally axial direction, and said first tubular space having a third inlet and a third outlet for allowing said first fluid to flow through said first tubular space in a generally axial direction, the at least one helical coil of a finned or corrugated tube being arranged inside said first tubular space generally coaxial therewith and having a fourth inlet and a fourth outlet for allowing said second fluid to flow through said finned tube.
- the first fluid is forced to flow around the finned tube coil windings in a very efficient manner for heat exchange. This also reduces the space requirements for the heat exchanger, the so-called “footprint”.
- the heat exchanger further comprises first adjustable throttle means for adjustably throttling said flow of said first fluid through said conduit and/or second adjustable throttle means for adjustably throttling said flow of said first fluid through said first tubular space.
- the flow of first fluid may by-pass the finned tube coils so that the heat transfer to the second fluid may be reduced according to the demand for heated second fluid.
- the pressure loss from the inlet of the casing to the outlet thereof may be reduced by by-passing the finned tube coils which is desirable during start up of for instance a gas fired turbine generating the first fluid in the form of exhaust gas from the gas combustion.
- said first throttle means comprise a first butterfly valve, preferably arranged adjacent said second inlet or said second outlet
- said second throttle means comprise a second butterfly valve, preferably arranged adjacent said third inlet or said third outlet.
- said first throttle means comprise a first butterfly valve, preferably arranged adjacent said second inlet or said second outlet
- said second throttle means comprise a ring having planar dimensions corresponding to the cross section of said first tubular space and being arranged for being displaced from a heating position wherein said flow of first fluid through said tubular space is substantially unhindered to a bypass position wherein said flow is substantially obstructed.
- the space requirements are reduced.
- said first and second throttle means comprise a fixedly arranged stationary plate with first and second apertures provided therein arranged such that said second and third inlets or outlets are obstructed by said plate such that the flow of first fluid through said conduit and said first tubular space takes place through said first and second apertures, respectively, in said stationary plate, and one or two movable plates with third and fourth apertures provided therein and arranged displaceable, preferably rotatably displaceable, from a bypass position overlying said stationary plate, wherein said third apertures coincide with said first apertures and said fourth apertures do not coincide with said second apertures, to a heating position overlying said stationary plate wherein said fourth apertures coincide with said second apertures and said third apertures do not coincide with said first apertures.
- This embodiment of the first and second throttle means requires a minimum of space and is particularly well suited for precise adjustment of the by-pass flow through the conduit relative to the heat transfer flow through the tubular space.
- the heat exchanger according to the invention further comprises preferably motorized actuating means for adjusting the throttling effect of said first and second throttle means, and said throttling means and said actuating means are preferably adapted such that substantially any rate of flow between a maximum and minimum rate of flow of said first fluid through said second inlet and said third inlet may be obtained. Said minimum rate is substantially equal to zero.
- any distribution of fluid flow between the by-pass conduit and the tubular space may obtained which allows simple and precise regulation of the output of the heat exchanger according to the requirements for heat transfer from the first fluid.
- substantially total by-pass no heat is transferred to the second fluid which is advantageous in case no heat transfer is needed to means exterior of the heat exchanger and therefore no temperature increase with consequent steam formation will take place in the finned coil or coils.
- the currently preferred embodiment of a heat exchanger comprises two or more of said helical coils arranged concentrically and such that mutually adjacent coils are radially spaced such that an axially extending second tubular space is provided between said mutually adjacent coils, and the outer surface of said conduit is spaced radially from the coil adjacent said surface such that an axially extending third tubular space is provided between said surface and said adjacent coil, the radial dimensions of said second and third tubular spaces being adapted so as to achieve a certain pressure loss for a given rate of flow of said first fluid through said first tubular space.
- the pressure loss from said first inlet to said first outlet for a given flow of first fluid may be kept at a minimum while not substantially reducing the efficiency of the heat exchanger. This is particularly of importance in connection with gas fired turbines being the origin of said first fluid because gas turbines are particularly sensitive to the back pressure at the exhaust outlet thereof.
- the mutually adjacent individual windings of a coil are mutually axially spaced such that a helically extending space is provided between said adjacent windings.
- any differential thermal expansion or contraction of the casing and/or conduit relative to the coils in the axial direction will be taken up by said helically extending space.
- third throttling means are provided in the tubes constituting the coils located radially inwards of the outermost coil for increasing the pressure loss through the tubes of said inner coils so as to compensate for the shorter length of said tubes relative to the length of the tubes of the outermost coil such that the rate of flow of said second fluid through the tubes of all the coils is substantially the same for a given uniform pressure in said second fluid at said fourth inlets.
- the heat transfer efficiency of each coil will be substantially the same without having to vary the diameter of the tubes of each coil to achieve this effect.
- said third throttling means are constituted by a reduction of the cross sectional area of the flow of said second fluid relative to the internal cross sectional area of said tubes, the heat exchanger preferably further comprising an inlet header tube and an outlet header tube in fluid communication with said fourth inlets and fourth outlets, respectively, of all said tubes through corresponding communication apertures in said header tubes, said reduction of flow cross sectional area being constituted by reduced size of said communication apertures in said inlet header tube and/or in said outlet header tube.
- each helical coil may advantageously comprise two or more helically wound finned tubes extending adjacent one another with the same pitch.
- the number of flow paths is increased which is advantageous in connection with the large volume expansion of the water in the coil tubes resulting from the steam generation.
- the present invention relates to a combination of a heat exchanger according to the invention and an exhaust gas generating combustion means such as a natural gas fired turbine, an internal combustion engine based on gasoline, diesel oil or natural gas, a furnace, a burner, an incinerator and the like, the combination comprising interconnection means for interconnecting an exhaust gas outlet of the combustion means with said second and third inlets of the heat exchanger such that said exhaust gas constitutes said first fluid.
- an exhaust gas generating combustion means such as a natural gas fired turbine, an internal combustion engine based on gasoline, diesel oil or natural gas, a furnace, a burner, an incinerator and the like
- the currently preferred embodiment of the combination according to the invention may further comprise heat exchanging means for heat exchange between said second fluid and a third fluid and/or the surroundings of said heat exchanging means, said heat exchanging means being in fluid communication with said fourth outlet, measuring means for measuring the rate of heat exchange of said heat exchanging means, signal output means for emitting a signal representing the result of a measurement carried out by said measuring means, and first control means for controlling the adjustment of said first and second throttle means and adapted for receiving said signal.
- the combination according to the invention further comprises second control means for controlling the adjustment of said first throttle means such that the throttling effect thereof is at a minimum during the start up phase of the combustion means.
- the present invention relates to a method of manufacturing a heat exchanger according to the invention and comprising the steps of providing a first length of finned or corrugated tube, providing a body having a substantially circular cylindrical surface, providing rotating means for causing relative rotation of said tube and said surface, arranging a lead portion of said tube abutting against said surface, and causing relative rotation of said surface and said lead portion such that said first length of tube is helically wound on said surface to form a first helical coil.
- a particularly simple, precise and inexpensive method of manufacturing a heat exchanger according to the invention is achieved.
- the method according to the invention preferably comprises the further steps of providing spacing means, attaching said spacing means to said first helical coil, providing a second length of finned or corrugated tube, arranging a lead portion of said second length of finned tube abutting against said spacing means, causing relative rotation of first helical coil and said lead portion of said second length of tube such that said second length of tube is helically wound on said spacing means to form a second helical coil radially spaced from said first helical coil.
- the method according to the invention preferably comprises the further steps of fixating said helical coil relative to said body, and subjecting said body and said coil to annealing heat treatment and/or fixating said second helical coil relative to said body and/or said first helical coil, and subjecting said body and said first and second coils to annealing heat treatment.
- fixating said helical coil relative to said body and subjecting said body and said coil to annealing heat treatment and/or fixating said second helical coil relative to said body and/or said first helical coil, and subjecting said body and said first and second coils to annealing heat treatment.
- FIG. 1 is an elevational partly sectional diagrammatic view of a first currently preferred embodiment of a heat exchanger according to the invention
- FIGS. 2-3 are schematic plan views illustrating a fin configuration of the finned tubes according to the invention.
- FIG. 4 is a schematic bottom view of the embodiment of FIG. 1 .
- FIG. 5 is an elevational partly sectional diagrammatic view of a second currently preferred embodiment of a heat exchanger according to the invention.
- FIG. 6 is a schematic view of an inlet header tube for an embodiment of the heat exchanger according to the invention provided with four concentrically arranged finned tube coils,
- FIG. 7 is a broken away elevational view of a third embodiment of a heat exchanger according to the invention.
- FIG. 8 is a diagrammatic enlarged scale view of a portion of the embodiment in FIG. 1 illustrating the spacing of the finned tubes of the coils,
- FIG. 9 is a schematic elevational, broken away, partly sectional view of the top of the embodiment shown if FIG. 5 illustrating a first embodiment of throttle means according to the invention
- FIG. 10 is a schematic elevational, broken away, partly sectional view of the top of a fourth embodiment of a heat exchanger according to the invention illustrating a second embodiment of throttle means according to the invention
- FIG. 11 is a schematic top view of the embodiment of FIG. 10 .
- FIG. 12 is a schematic elevational, cut away view illustrating a third embodiment of throttle means according to the invention.
- FIG. 13 is a schematic top view illustrating a fourth embodiment of throttle means according to the invention.
- FIG. 14 is a schematic, partly sectional, naval, acoustic pressure, and acoustic pressure, and acoustic pressure, and acoustic pressure.
- FIG. 15 is a schematic top view illustrating the method according to the invention of manufacturing the embodiment of FIG. 5 .
- FIG. 16 is a diagram illustrating one embodiment of control means according to the invention for adjusting the throttle means according to the invention.
- a heat exchanger 1 according to the invention comprises an outer cylindrical casing 2 provided with a flanged inlet 3 and a flanged outlet 4 .
- An interior cylindrical casing or conduit 5 having an inlet 6 and an outlet 7 is arranged coaxially with the outer casing 2 thereby defining a tubular space 8 wherein two coils 9 and 10 of finned tubing are arranged.
- the finned tubing consists of a tube 11 provided with fins 12 arranged generally transversely to the axis of the tube 11 .
- the finned tube coils 9 and 10 are arranged mutually concentric and coaxially with the outer and inner casings 2 and 5 .
- a flanged outlet header tube 13 and a flanged inlet header tube 14 communicate with the interior of the tubes 11 of the coils 9 and 10 through apertures 15 and 16 , respectively.
- a butterfly valve 17 (by-pass valve) is pivotably arranged on a shaft 18 at the outlet 7 of the conduit 5 , a position wherein the valve 17 is in an intermediate position between fully closing the outlet 7 and fully opening said outlet 7 being shown with dotted lines at 17 a .
- Semicircular rings 19 and 20 are arranged for abutting the rim of the butterfly valve 17 in the closed position thereof thereby ensuring a good closing function of the valve 17 .
- the heat exchanger 1 is primarily intended for use in combination with a natural gas fired turbine for recuperating and utilizing the heat of the exhaust gases thereof, but may in principle be used in combination with any means producing a heated gas such as internal combustion engines, furnaces, burners, incinerators and the like.
- the butterfly by-pass valve 17 is in the closed position shown in full lines in FIG. 1 whereby all the exhaust gas from the gas turbine introduced into the inlet 3 flows through the tubular space 8 past the finned tube coils 9 and 10 as indicated by the full line arrows. Water to be heated is introduced into the coils 9 and 10 through inlet header 14 and is discharged through apertures 15 and 16 and outlet header 4 after having been heated by heat transmission from the exhaust gas through fins 12 to the tubes 11 and thereby to the water in said tubes.
- the heated water is transported to not shown exterior heat exchange means for transmitting some of the heat of the water to some other fluid or to the surroundings, typically radiators in a building heating system or a district heating system.
- the butterfly valve 17 is pivoted on shaft 18 so as to allow some or all the exhaust gas from the gas turbine to flow through the internal conduit 5 as indicated with dotted arrows thereby by-passing the tubular space 8 and the coils 9 and 10 .
- the butterfly valve 7 can also be described as a throttling means and may be substituted by other throttling means as described in the following in connection with FIGS. 9-13 .
- a strip 12 a of carbon steel is laterally cut to form tabs or fingers 12 b that are bent transverse to the plane of the strip in alternating directions and thereafter welded onto the surface of the tube 11 in a spiral configuration by means of welding seam 12 c .
- a very effective heat transfers from the hot exhaust gas to the fingers 12 b and thereby to the tube 11 may be achieved.
- Other configurations with circular plate shaped fins or corrugations may also be employed instead of the serrated spirally wound fins shown in FIGS. 2 and 3 .
- the tubes 11 are welded to the upper header tube 14 around the apertures 15 and 16 thereof whereby the interior of the tubes 11 communicates with the interior of the header tube 14 ,
- the coils 9 and 10 are attached to and suspended from the outer casing 2 and the inner conduit 5 by means of a beam 22 welded to said casing and conduit.
- the beam 22 is welded to two rings 23 and 24 fitting tightly around the fins 12 b of the coils 9 and 10 .
- a similar attachment is carried out at the bottom of the heat exchanger adjacent the inlet header tube 13 .
- FIG. 8 the position of the coils 9 and 10 relative to one another and relative to the outer casing 2 and the inner conduit 5 as well as the spacing between the windings of each coil is illustrated.
- the innermost coil 10 is spaced from the outermost coil 9 by a tubular space having a thickness or radial dimension t 1 , while the innermost coil 10 is spaced from the outer surface of the conduit 5 by a tubular space having a thickness or radial dimension t 3 .
- the outermost coil 9 is not spaced from the inner surface of the outer casing 2 , i.e. the coil 9 abuts the casing 2 .
- the spacings t 1 and t 3 are chosen such that the loss of pressure through the tubular space 8 is maintained at a level acceptable for the optimal operation of the gas turbine (or other hot exhaust gas generating means) delivering exhaust gas to the heat exchanger 1 .
- the heat exchange efficiency of the heat exchanger 1 is not substantially affected by the spacings t 1 and t 3 .
- operational tests show that if a spacing were present between the outer casing 2 and the outermost coil 9 , then the efficiency of the heat exchanger 1 would be considerably reduced.
- the exhaust gas pressure drop or loss is very dependent on the exhaust gas velocity and the geometry of the heating surface of the coil windings.
- the velocity is dependent on the free gas flow cross sectional area (total area for the gas flow between the tubes and fins in a cross section).
- the allowable exhaust gas pressure drop in heat exchangers and boilers after gas turbines (and engines as well) is quite limited.
- gas turbines it is extremely important to minimize the exhaust gas pressure drop as the power production on the turbine (and thus the efficiency of the turbine) is very dependent on the back pressure.
- the allowable exhaust gas pressure drop is preferably limited to be below 500 Pa (50 mm water column), giving very low exhaust gas velocities and thus large distance between the coils (alternatively more coils giving larger gas cross section area and larger diameter of the unit).
- the heat transfer coefficient should be as high as possible to minimize the heating surface area.
- the heat transfer coefficient is increased with higher exhaust gas velocities and more turbulent flow.
- the turbulence of the flow is very good, in general giving high heat transfer coefficient even for low exhaust gas velocities.
- Designing the heat exchanger according to the invention with the spacings t 1 and t 3 is also advantageous from a production point of view because it allows the coils to be inserted in the casing individually as compared with coils designed to abut one another or to be nested in one another that must be handled and inserted as a unit comprising several coils.
- a helically extending space is provided between adjacent windings of each coil 9 and 10 , the thickness or axial dimension of said space being t 2 .
- This spacing t 2 of the windings allows the casing 2 and/or the conduit 5 to thermally expand and contract axially relative to the coils 9 and 10 without causing unacceptable stresses as any differences in such expansion or contraction is taken up by variations of the spacing t 2 between the windings of the coils.
- FIG. 5 an embodiment of a heat exchanger 31 according to the invention having three concentric coils 32 - 34 is shown with the same reference numbers being utilized for elements similar to elements in FIG. 1 .
- the inner coils 33 and 34 [where the second fluid (typically water) have shorter flow paths than in the outermost coil 32 ] can transport more water than the outer coil 32 .
- the water in the coils 33 , 34 and 35 will then not be heated to the same temperature and will result in a skewed and reduced recuperation of the heat contained in the first fluid (for instance exhaust gas from a gas fired turbine).
- the flow rate through the coils be regulated so that best possible heat recuperation is obtained with best possible temperature distribution both in the water and in the exhaust gas. This is achieved by creating an extra pressure loss in the inner coils 33 and 34 relative to the outer coil 35 and each other.
- the inner coil adjacent the inner conduit 5 comprises two parallel wound finned tubes 50 and 51 establishing two parallel flow paths for the second fluid (typically water) indicated by the arrows R 1 and R 2 .
- This embodiment is intended for use for steam generation where it is necessary to take into consideration the large volume expansion of the mass inside the tubes (at the transition from liquid to vapour, water to steam) with corresponding increase in flow rate and velocity as well as pressure loss at the inner surface of the tubes. So as to provide sufficient inner flow cross sectional area in the tubes it will therefore often be necessary to use a larger tube diameter, a larger number of coils or provide for a larger number of flow paths in other ways.
- more flow paths may be obtained by having several parallel extending windings in the same coil as shown in FIG. 7 , i.e. several coils with the same coil diameter and large pitch “screwed” into each other.
- a larger inner cross section area is achieved without having a large number of coils with a large diameter of the outermost coil and therefore the outer casing 2 (large footprint).
- This smaller footprint or outer diameter of the heat exchanger entails important advantages both for the end user and during manufacture, erection and transport.
- the axial length or height of the heat exchanger for a given output will of course be larger, but this does normally not represent a substantial problem during manufacture or for the end user.
- throttle means for throttling the flow of first fluid (typically exhaust gas) through the conduit 5 and the tubular space 8 , respectively, are shown.
- the butterfly valve 17 cooperates with a ring 52 that is suspended in three steel wires 53 attached at equidistant points along the ring 52 .
- the wires 53 extend over pulleys 54 to the shaft 18 .
- the butterfly valve 17 is closed and does not allow any exhaust gas to flow through conduit 5 while the ring 52 is in its highest position in which it does not throttle the flow of exhaust gas through the tubular space 8 .
- the butterfly valve 17 a functions as a by-pass valve and allows unthrottled flow of exhaust gas through the conduit 5 while the ring 52 a is in its full throttle position supported on tightening rings 55 thereby preventing flow of exhaust gas through the tubular space 8 .
- the shaft 18 may be actuated manually, by an electric motor or a pneumatic or hydraulic mechanism.
- the wires are wound onto and off not shown pulleys arranged on the shaft 18 such that rotation of the shaft 18 for opening of the butterfly valve 17 automatically entails lowering of the ring 52 and vice versa.
- the butterfly valve 17 When no heat is required by the external heat consumption means connected to the heat exchanger 31 , then the butterfly valve 17 is in its fully open position ( 17 a ) and the ring 52 is in its lowered fully closed position ( 52 a ) so that all the exhaust gas is by-passed through the conduit 5 .
- the water in the finned tube coils is not heated so that external cooling means to avoid overheating of this water are not necessary.
- a very simple means for regulating the heat output of the heat exchanger 31 is thus provided.
- a temperature sensor and transmitter may be provided in the outlet header 38 for transmitting a signal to the not shown actuator (electric motor) for the shaft 18 so that if the temperature measured at the outlet header does not conform to the required temperature, then the shaft rotates in the corresponding direction to either open or shut the by-pass valve 17 .
- Many different regulating circuits are conceivable depending on the requirements of the end user and the configuration of the external heat consumption devices connected to the heat exchanger 31 .
- FIGS. 10 and 11 showing an elevational and top view, respectively, of a second embodiment of the first and second throttling means for the flow of exhaust gas through the internal conduit and the tubular space, respectively
- the internal conduit 5 is connected to a further conduit 56 having an outlet 57 in which a butterfly valve 58 is rotatably mounted on a shaft 59 .
- the outlet 57 communicates with the outlet 4 of the casing 5 .
- the butterfly valve 58 may rotate with the shaft 59 from the shown closed position wherein the outlet 57 is totally obstructed and an open position wherein flow of exhaust gas through outlet 57 is unhindered.
- the tubular space 8 communicates with a space 60 defined by an extension of the outer casing 2 , said space communicating with the outlet 4 through an aperture 61 in a plate 62 .
- a butterfly valve 63 is mounted in said aperture 61 on the shaft 59 such that rotation of the shaft 59 rotates the butterfly valve 63 from the shown fully open position in which flow of exhaust gas from the tubular space 8 through the space 60 and through the aperture 61 is unhindered to a fully closed position in which flow of exhaust gas through the aperture 61 is totally obstructed.
- the shaft 59 is connected to an electric motor 64 for being rotated in opposite directions so as to rotate the valves 58 and 63 between the two positions described above and to any intermediate position.
- FIG. 12 in this embodiment the butterfly valves 58 and 63 of the embodiment in FIGS. 10 and 11 have been substituted by a butterfly valve 65 and two butterfly valves 66 , respectively, the operation of the valves 65 and 66 and the shaft 59 being the same as described in connection with the embodiment of FIGS. 10 and 11 .
- a stationary circular plate 70 is arranged horizontally in an embodiment of the heat exchanger similar to the one shown in FIG. 1 or FIG. 4 (without the butterfly valve 17 ) over the outlet of the conduit 5 and the annular outlet of the tubular space 8 .
- the plate 70 is provided with apertures 71 communicating with the interior of conduit 5 and apertures 72 communicating with the tubular space 8 .
- a rotatably arranged circular plate 73 is arranged on top of plate 70 on a pivot 74 .
- the plate 73 is provided with apertures 75 identical in shape and distribution to apertures 72 in plate 70 and with apertures 76 identical in shape and distribution to apertures 71 in plate 70 .
- An electrical motor 77 is arranged for rotating the rotatable plate 73 in both directions.
- the lower plate 70 may instead be the rotatable one whereby the pressure from the exhaust gas will press the plate 70 against the stationary plate 73 and enhance the sealing effect of abutment of the plates 70 and 73 against each other. Sealing between the plates may also be achieved in many other ways obvious to those skilled in the art.
- FIG. 15 a method according to the invention of manufacturing a heat exchanger (the embodiment of FIG. 5 ) according to the invention is illustrated.
- a cylindrical body 80 is constituted by a steel plate 81 with a thickness of 10 mm, a steel rod 82 inserted between the free axially extending edges of the plate 81 , and not shown circumferentially extending tightening straps or wires for holding the plate 81 and rod 82 in the shown cylindrical configuration.
- the inner coil 34 is wound helically around the body or core 80 , the leading end (not shown) and the trailing end 11 a of the pipe 11 of the coil 34 being attached to the body by means of brackets or rods 83 welded to said ends and to the body 80 .
- the tightening straps mentioned above are located outside the area of the body 80 to be covered by the coil 34 .
- Four cylindrical plates 84 having a quarter circle cross section and a thickness equal to the required radial dimension t 1 (see FIG. 8 ) are arranged on the outer surface of coil 33 with rods 85 arranged between mutually adjacent axially extending edges of the plates 84 .
- the plates 84 and rods 85 are held in place by not shown circumferentially extending tightening straps or wires.
- the rods 85 have an oval or elliptical cross section and are placed between the plates 84 such that the major cross sectional dimension of the oval or ellipse is tangential to the circular circumference of the plates 84 .
- the next coil 33 is wound helically around the plates 84 and rods 85 with the leading and trailing ends of the coil 33 being welded to one of the plates 84 by means of brackets or rods 83 in a manner very similar to the winding and attachment of the inner coil 34 .
- the process is repeated for the next coil 32 . If more coils than three are required, the process described above may be repeated for any such further coils.
- the unit comprising the body 80 , the coils 32 - 34 and the plates 84 with rods 85 is thereafter subjected to annealing heat treatment for avoiding elastic diameter expansion of the coils and to remove potentially damaging stresses.
- the attachments by means of brackets 83 are removed, the rods 85 are rotated such that the major dimension of the oval or elliptical cross section is oriented radially whereby the coils 32 - 34 are forced to expand slightly such that the cylindrical plates 84 may be removed. Finally rod 82 is removed such that the body 80 may be removed.
- the coils 32 - 34 are now ready for being inserted in a casing 2 with a conduit 5 placed inside the inner coil 34 .
- a heat exchanger according to the invention is particularly well suited for use in a combination or system comprising a gas fired turbine (or an internal combustion engine utilizing natural gas as fuel).
- a gas fired turbine or an internal combustion engine utilizing natural gas as fuel.
- Such a system is furthermore particularly well suited for (but not in any way limited to) for use in a system for small scale combined production of electricity and heat, for instance for large buildings, hospitals, small district heating systems and the like.
- FIG. 16 a system or combination according to the invention including a heat exchanger according to the invention, a gas fired turbine and external heat consuming devices is shown with the following characteristics: Item Component Description 101 Heat exchanger according to the invention. 102 Exhaust gas by-pass damper or Can be regulated manually or as shown valve (butterfly valve for instance) here: regulated by an actuator (electrical motor), item 11 103 Exhaust gas stack 104 Gas fired turbine could be another kind of component producing exhaust gas 105 Circulation pump A forced circulation system, to circulate the required water/fluid flow. The pressure drop on water side in the heat exchanger, valves and piping system to be taken into account when calculating the delivery head of the pump.
- Expansion tank To take the expansion/contraction of the fluid in the system, when the temperature varies.
- External end user Or other heat consumption device Can be Heat exchanger for heating use in buildings, in greenhouses, district heating systems etc.
- Safety valve To be opened if the pressure in the system becomes too high
- Stop valves Normally open. Possible to close in case of repair.
- Air venting valve 111
- Electrical motor Electrical motor, automatically controlled by signals from the temperature transmitter 113. Opens the by-pass valve 102 a little, if the water temperature becomes too high, closes the valve 102 a little if the water temperature becomes too low. Set points to be decided by the end user.
- 112 Drain valve To drain the water/fluid from the system 113 Temperature transmitter Sends signal to electrical motor if temperature measured is too high or too low
- the system can comprise other exhaust gas generating devices, and the regulation of the heat exchanger's by-pass valve (and the heat exchanger's throttle valve for throttling fluid flow through the tubular space containing the finned tube coils) can be provided for in many different manners depending on the configuration of the end user's heat consuming devices.
Abstract
A heat exchanger for heat exchange between a first and a second fluid and comprising a cylindrical casing 2, a cylindrical fluid conduit 5 arranged inside the casing such that an axially extending tubular space 8 is defined, at least one helical coil 9, 10 of a finned or corrugated tube being arranged inside the tubular space, and adjustable throttle means 17, 17 a , 18 adapted and arranged for adjustably throttling flow of the first fluid through the conduit 5 to adjust the flow of the first fluid through the conduit and the first tubular space for adjusting the heat exchange between the first fluid and the second fluid flowing through the helical coils 9, 10.
Description
- The present invention relates to a heat exchanger for heat exchange between a first fluid and a second fluid and comprising a generally cylindrical casing with a first inlet and a first outlet for allowing said first fluid to flow through said casing in a generally axial direction, and at least one helical coil of a finned or corrugated tube arranged inside said casing.
- Heat exchangers of this type are known where the first fluid is forced to flow from inside the coil or coils outwards or vice versa. The transfer of heat from the first fluid to the second fluid in the coils is not very well controlled and therefore not as efficient as possible.
- It is an object of the invention to provide a heat exchanger of the type in reference where the flow of first fluid, for instance exhaust gas from a natural gas fired turbine, an internal combustion engine, an incinerator, a furnace, a burner or the like, takes place around the finned tube in a well controlled and efficient manner affording a highly efficient heat transfer from the first fluid to the second fluid, for instance water.
- According to the invention this object is obtained by providing a generally cylindrical fluid conduit inside said casing generally coaxial therewith so that an axially extending first tubular space is defined between said conduit and said casing, said conduit having a second inlet and a second outlet for allowing said first fluid to flow through said conduit in a generally axial direction, and said first tubular space having a third inlet and a third outlet for allowing said first fluid to flow through said first tubular space in a generally axial direction, the at least one helical coil of a finned or corrugated tube being arranged inside said first tubular space generally coaxial therewith and having a fourth inlet and a fourth outlet for allowing said second fluid to flow through said finned tube.
- Hereby, the first fluid is forced to flow around the finned tube coil windings in a very efficient manner for heat exchange. This also reduces the space requirements for the heat exchanger, the so-called “footprint”.
- According to the invention, the heat exchanger further comprises first adjustable throttle means for adjustably throttling said flow of said first fluid through said conduit and/or second adjustable throttle means for adjustably throttling said flow of said first fluid through said first tubular space.
- Hereby, the flow of first fluid may by-pass the finned tube coils so that the heat transfer to the second fluid may be reduced according to the demand for heated second fluid. Furthermore, the pressure loss from the inlet of the casing to the outlet thereof may be reduced by by-passing the finned tube coils which is desirable during start up of for instance a gas fired turbine generating the first fluid in the form of exhaust gas from the gas combustion.
- In one of the currently preferred embodiments of the heat exchanger according to the invention, said first throttle means comprise a first butterfly valve, preferably arranged adjacent said second inlet or said second outlet, and said second throttle means comprise a second butterfly valve, preferably arranged adjacent said third inlet or said third outlet. Hereby, rather simple mechanisms that are simple to adjust and regulate are provided.
- In an alternative embodiment, said first throttle means comprise a first butterfly valve, preferably arranged adjacent said second inlet or said second outlet, and said second throttle means comprise a ring having planar dimensions corresponding to the cross section of said first tubular space and being arranged for being displaced from a heating position wherein said flow of first fluid through said tubular space is substantially unhindered to a bypass position wherein said flow is substantially obstructed. In this embodiment, the space requirements are reduced.
- In another currently preferred embodiment, said first and second throttle means comprise a fixedly arranged stationary plate with first and second apertures provided therein arranged such that said second and third inlets or outlets are obstructed by said plate such that the flow of first fluid through said conduit and said first tubular space takes place through said first and second apertures, respectively, in said stationary plate, and one or two movable plates with third and fourth apertures provided therein and arranged displaceable, preferably rotatably displaceable, from a bypass position overlying said stationary plate, wherein said third apertures coincide with said first apertures and said fourth apertures do not coincide with said second apertures, to a heating position overlying said stationary plate wherein said fourth apertures coincide with said second apertures and said third apertures do not coincide with said first apertures. This embodiment of the first and second throttle means requires a minimum of space and is particularly well suited for precise adjustment of the by-pass flow through the conduit relative to the heat transfer flow through the tubular space.
- In the currently preferred embodiment, the heat exchanger according to the invention further comprises preferably motorized actuating means for adjusting the throttling effect of said first and second throttle means, and said throttling means and said actuating means are preferably adapted such that substantially any rate of flow between a maximum and minimum rate of flow of said first fluid through said second inlet and said third inlet may be obtained. Said minimum rate is substantially equal to zero. Hereby, any distribution of fluid flow between the by-pass conduit and the tubular space may obtained which allows simple and precise regulation of the output of the heat exchanger according to the requirements for heat transfer from the first fluid. By allowing substantially total by-pass, no heat is transferred to the second fluid which is advantageous in case no heat transfer is needed to means exterior of the heat exchanger and therefore no temperature increase with consequent steam formation will take place in the finned coil or coils.
- The currently preferred embodiment of a heat exchanger according to the invention comprises two or more of said helical coils arranged concentrically and such that mutually adjacent coils are radially spaced such that an axially extending second tubular space is provided between said mutually adjacent coils, and the outer surface of said conduit is spaced radially from the coil adjacent said surface such that an axially extending third tubular space is provided between said surface and said adjacent coil, the radial dimensions of said second and third tubular spaces being adapted so as to achieve a certain pressure loss for a given rate of flow of said first fluid through said first tubular space.
- Hereby, the pressure loss from said first inlet to said first outlet for a given flow of first fluid may be kept at a minimum while not substantially reducing the efficiency of the heat exchanger. This is particularly of importance in connection with gas fired turbines being the origin of said first fluid because gas turbines are particularly sensitive to the back pressure at the exhaust outlet thereof.
- Preferably, the mutually adjacent individual windings of a coil are mutually axially spaced such that a helically extending space is provided between said adjacent windings. Hereby any differential thermal expansion or contraction of the casing and/or conduit relative to the coils in the axial direction will be taken up by said helically extending space.
- In a currently preferred embodiment of a heat exchanger according to the invention and comprising three or more of said helical coils arranged concentrically and the interior diameter of the finned tubes constituting the coils preferably being the same, third throttling means are provided in the tubes constituting the coils located radially inwards of the outermost coil for increasing the pressure loss through the tubes of said inner coils so as to compensate for the shorter length of said tubes relative to the length of the tubes of the outermost coil such that the rate of flow of said second fluid through the tubes of all the coils is substantially the same for a given uniform pressure in said second fluid at said fourth inlets. Hereby, the heat transfer efficiency of each coil will be substantially the same without having to vary the diameter of the tubes of each coil to achieve this effect.
- In the currently preferred embodiment of a heat exchanger according to the invention said third throttling means are constituted by a reduction of the cross sectional area of the flow of said second fluid relative to the internal cross sectional area of said tubes, the heat exchanger preferably further comprising an inlet header tube and an outlet header tube in fluid communication with said fourth inlets and fourth outlets, respectively, of all said tubes through corresponding communication apertures in said header tubes, said reduction of flow cross sectional area being constituted by reduced size of said communication apertures in said inlet header tube and/or in said outlet header tube. This is a particularly simple and inexpensive way of compensating for the different lengths of the different coils.
- In case the heat exchanger according to the invention is to be used for generating steam, then according to the invention each helical coil may advantageously comprise two or more helically wound finned tubes extending adjacent one another with the same pitch. Hereby the number of flow paths is increased which is advantageous in connection with the large volume expansion of the water in the coil tubes resulting from the steam generation.
- In another aspect, the present invention relates to a combination of a heat exchanger according to the invention and an exhaust gas generating combustion means such as a natural gas fired turbine, an internal combustion engine based on gasoline, diesel oil or natural gas, a furnace, a burner, an incinerator and the like, the combination comprising interconnection means for interconnecting an exhaust gas outlet of the combustion means with said second and third inlets of the heat exchanger such that said exhaust gas constitutes said first fluid.
- The currently preferred embodiment of the combination according to the invention may further comprise heat exchanging means for heat exchange between said second fluid and a third fluid and/or the surroundings of said heat exchanging means, said heat exchanging means being in fluid communication with said fourth outlet, measuring means for measuring the rate of heat exchange of said heat exchanging means, signal output means for emitting a signal representing the result of a measurement carried out by said measuring means, and first control means for controlling the adjustment of said first and second throttle means and adapted for receiving said signal.
- Preferably, the combination according to the invention further comprises second control means for controlling the adjustment of said first throttle means such that the throttling effect thereof is at a minimum during the start up phase of the combustion means.
- In yet another aspect, the present invention relates to a method of manufacturing a heat exchanger according to the invention and comprising the steps of providing a first length of finned or corrugated tube, providing a body having a substantially circular cylindrical surface, providing rotating means for causing relative rotation of said tube and said surface, arranging a lead portion of said tube abutting against said surface, and causing relative rotation of said surface and said lead portion such that said first length of tube is helically wound on said surface to form a first helical coil. Hereby, a particularly simple, precise and inexpensive method of manufacturing a heat exchanger according to the invention is achieved.
- In connection with heat exchangers according to the invention having two or more concentric coils, the method according to the invention preferably comprises the further steps of providing spacing means, attaching said spacing means to said first helical coil, providing a second length of finned or corrugated tube, arranging a lead portion of said second length of finned tube abutting against said spacing means, causing relative rotation of first helical coil and said lead portion of said second length of tube such that said second length of tube is helically wound on said spacing means to form a second helical coil radially spaced from said first helical coil.
- So as to avoid inaccuracies in the diameter of the coils and other disadvantages, the method according to the invention preferably comprises the further steps of fixating said helical coil relative to said body, and subjecting said body and said coil to annealing heat treatment and/or fixating said second helical coil relative to said body and/or said first helical coil, and subjecting said body and said first and second coils to annealing heat treatment. Hereby the diameter alteration of the coils because of elasticity and stresses in the steel of the coil tubes is avoided in a simple and cost efficient manner.
- In the following the invention will be explained more in detail with reference to different embodiments thereof shown, solely by way of example, in the accompanying drawings where:
-
FIG. 1 is an elevational partly sectional diagrammatic view of a first currently preferred embodiment of a heat exchanger according to the invention, -
FIGS. 2-3 are schematic plan views illustrating a fin configuration of the finned tubes according to the invention, -
FIG. 4 is a schematic bottom view of the embodiment ofFIG. 1 , -
FIG. 5 is an elevational partly sectional diagrammatic view of a second currently preferred embodiment of a heat exchanger according to the invention, -
FIG. 6 is a schematic view of an inlet header tube for an embodiment of the heat exchanger according to the invention provided with four concentrically arranged finned tube coils, -
FIG. 7 is a broken away elevational view of a third embodiment of a heat exchanger according to the invention, -
FIG. 8 is a diagrammatic enlarged scale view of a portion of the embodiment inFIG. 1 illustrating the spacing of the finned tubes of the coils, -
FIG. 9 is a schematic elevational, broken away, partly sectional view of the top of the embodiment shown ifFIG. 5 illustrating a first embodiment of throttle means according to the invention, -
FIG. 10 is a schematic elevational, broken away, partly sectional view of the top of a fourth embodiment of a heat exchanger according to the invention illustrating a second embodiment of throttle means according to the invention, -
FIG. 11 is a schematic top view of the embodiment ofFIG. 10 , -
FIG. 12 is a schematic elevational, cut away view illustrating a third embodiment of throttle means according to the invention, -
FIG. 13 is a schematic top view illustrating a fourth embodiment of throttle means according to the invention, -
FIG. 14 is a schematic, partly sectional, perspectival, enlarged scale view of the top header tube and fastening means for the coils of the embodiment ofFIG. 1 , -
FIG. 15 is a schematic top view illustrating the method according to the invention of manufacturing the embodiment ofFIG. 5 , and -
FIG. 16 is a diagram illustrating one embodiment of control means according to the invention for adjusting the throttle means according to the invention. - Referring first to
FIGS. 1 and 4 , aheat exchanger 1 according to the invention comprises an outercylindrical casing 2 provided with a flangedinlet 3 and a flangedoutlet 4. An interior cylindrical casing orconduit 5 having aninlet 6 and anoutlet 7 is arranged coaxially with theouter casing 2 thereby defining atubular space 8 wherein twocoils tube 11 provided withfins 12 arranged generally transversely to the axis of thetube 11. - The
finned tube coils inner casings outlet header tube 13 and a flangedinlet header tube 14 communicate with the interior of thetubes 11 of thecoils apertures - A butterfly valve 17 (by-pass valve) is pivotably arranged on a
shaft 18 at theoutlet 7 of theconduit 5, a position wherein thevalve 17 is in an intermediate position between fully closing theoutlet 7 and fully opening saidoutlet 7 being shown with dotted lines at 17 a.Semicircular rings butterfly valve 17 in the closed position thereof thereby ensuring a good closing function of thevalve 17. - The
heat exchanger 1 is primarily intended for use in combination with a natural gas fired turbine for recuperating and utilizing the heat of the exhaust gases thereof, but may in principle be used in combination with any means producing a heated gas such as internal combustion engines, furnaces, burners, incinerators and the like. - During maximum output operation of the
heat exchanger 1, the butterfly by-pass valve 17 is in the closed position shown in full lines inFIG. 1 whereby all the exhaust gas from the gas turbine introduced into theinlet 3 flows through thetubular space 8 past thefinned tube coils coils inlet header 14 and is discharged throughapertures outlet header 4 after having been heated by heat transmission from the exhaust gas throughfins 12 to thetubes 11 and thereby to the water in said tubes. - The heated water is transported to not shown exterior heat exchange means for transmitting some of the heat of the water to some other fluid or to the surroundings, typically radiators in a building heating system or a district heating system.
- Either during start up of the gas turbine (when the pressure loss through the
heat exchanger 1 should be at a minimum to facilitate the turbine start up) or when the exterior heat exchange means do not require the full heating capacity of theheat exchanger 1, then thebutterfly valve 17 is pivoted onshaft 18 so as to allow some or all the exhaust gas from the gas turbine to flow through theinternal conduit 5 as indicated with dotted arrows thereby by-passing thetubular space 8 and thecoils - Hereby, the pressure loss through the
heat exchanger 1 is decreased and the heat transmission to the water in thetubes butterfly valve 7 can also be described as a throttling means and may be substituted by other throttling means as described in the following in connection withFIGS. 9-13 . - Referring now to
FIGS. 2 and 3 , astrip 12 a of carbon steel is laterally cut to form tabs or fingers 12 b that are bent transverse to the plane of the strip in alternating directions and thereafter welded onto the surface of thetube 11 in a spiral configuration by means of welding seam 12 c. Hereby a very effective heat transfers from the hot exhaust gas to the fingers 12 b and thereby to thetube 11 may be achieved. Other configurations with circular plate shaped fins or corrugations may also be employed instead of the serrated spirally wound fins shown inFIGS. 2 and 3 . - Referring now to
FIG. 14 , thetubes 11 are welded to theupper header tube 14 around theapertures tubes 11 communicates with the interior of theheader tube 14, Thecoils outer casing 2 and theinner conduit 5 by means of abeam 22 welded to said casing and conduit. Thebeam 22 is welded to tworings coils inlet header tube 13. - Referring now to
FIG. 8 , the position of thecoils outer casing 2 and theinner conduit 5 as well as the spacing between the windings of each coil is illustrated. - The
innermost coil 10 is spaced from theoutermost coil 9 by a tubular space having a thickness or radial dimension t1, while theinnermost coil 10 is spaced from the outer surface of theconduit 5 by a tubular space having a thickness or radial dimension t3. Theoutermost coil 9 is not spaced from the inner surface of theouter casing 2, i.e. thecoil 9 abuts thecasing 2. - The spacings t1 and t3 are chosen such that the loss of pressure through the
tubular space 8 is maintained at a level acceptable for the optimal operation of the gas turbine (or other hot exhaust gas generating means) delivering exhaust gas to theheat exchanger 1. The heat exchange efficiency of theheat exchanger 1 is not substantially affected by the spacings t1 and t3. On the other hand, operational tests show that if a spacing were present between theouter casing 2 and theoutermost coil 9, then the efficiency of theheat exchanger 1 would be considerably reduced. These two phenomena are at least to a certain degree owing to, on one hand, turbulent flow between thecoils conduit 5 and thecoil 10 and, on the other hand, laminar flow in a tubular space between theouter coil 9 and thecasing 2. - There are several parameters determining the spacings ti and t3 between the coils and between the innermost coil and the
conduit 5. The two most important considerations or parameters are: - Exhaust Gas Pressure Drop
- The exhaust gas pressure drop or loss is very dependent on the exhaust gas velocity and the geometry of the heating surface of the coil windings. The velocity is dependent on the free gas flow cross sectional area (total area for the gas flow between the tubes and fins in a cross section).
-
- Δp=ξ·½·ρ·w2, where
- Δp: exhaust gas pressure drop [Pa]
- ξ: pressure drop coefficient, dependent on geometry (fin shapes, tube diameter, inline/staggered configuration, number of windings etc),
- ρ: Density of the gas at mean temperature between
inlet 3 and outlet 4 [kg/m3] - w: exhaust gas velocity [m/s]
- In most cases, the allowable exhaust gas pressure drop in heat exchangers and boilers after gas turbines (and engines as well) is quite limited. For gas turbines it is extremely important to minimize the exhaust gas pressure drop as the power production on the turbine (and thus the efficiency of the turbine) is very dependent on the back pressure. In connection with the heat exchanger according to the invention the allowable exhaust gas pressure drop is preferably limited to be below 500 Pa (50 mm water column), giving very low exhaust gas velocities and thus large distance between the coils (alternatively more coils giving larger gas cross section area and larger diameter of the unit).
- Heat Transfer Coefficient
- In general the heat transfer coefficient should be as high as possible to minimize the heating surface area. The heat transfer coefficient is increased with higher exhaust gas velocities and more turbulent flow. For the heating surface chosen (serrated spiral wound fin tubes) the turbulence of the flow is very good, in general giving high heat transfer coefficient even for low exhaust gas velocities.
- Designing the heat exchanger according to the invention with the spacings t1 and t3 is also advantageous from a production point of view because it allows the coils to be inserted in the casing individually as compared with coils designed to abut one another or to be nested in one another that must be handled and inserted as a unit comprising several coils.
- Still referring to
FIG. 8 , a helically extending space is provided between adjacent windings of eachcoil casing 2 and/or theconduit 5 to thermally expand and contract axially relative to thecoils - In the following, the basic technical specifications for a combination according to the invention of a two coil heat exchanger according to the invention and a gas fired turbine are listed as a non-limiting example:
- Dimensions of the Heat Exchanger
Height excl. inlet: 1550 mm Diameter excl. insulation: 633 mm Insulation: 100 mm covered with galvanized steel plate Flue gas outlet flange: DN 450, DIN 86044 Water inlet/outlet connections: Carbon steel pipe, OD 60.5 × 3.6 mm, 2 “RGW Thickness of casing (inner 5 and outer 2): 5 mm Weight of heat exchanger excl. water: 475 kg Weight of heat exchanger incl. water: 500 kg Outside diameter of tubes 11: 38 mm Tube material thickness: 3.6 mm Fin type: Serrated spiral wound fins Height of fins: 15 mm Fin density: 250 pcs/m Thickness of fins: 1 mm Material, tube and fins: Carbon steel Tube configuration: Inline Number of coaxial and concentric coils: 2 Number of windings: 10 Tube pitch in gas direction: 70 mm Free spacing t2 between fins on coil windings in gas direction: 2 mm Diameter of by-pass channel (inner casing 5): 323.9 mm Length of inner casing 5, incl. by-pass valve:860 mm Centre diameter of inner coil 10: 401 mm Centre diameter of outer coil 9: 555 mm Free space t3 between inner casing 5 and fins on inner coil 10:4.5 mm Free space t1 between fins on the two coils: 9 mm Free space between fins on outer coil and inside of outer casing 2: 0 mm Size of holes header 13 for coil connection (both coils)30.8 mm - Process Data
Micro Gas turbine type: HONEYWELL Parallon 75 Max. electric output power from gas turbine: 75 kW(e) Exhaust gas flow: 0.68 kg/s Exhaust gas inlet temperature to heat exchanger: 246° C. Exhaust gas outlet temperature from heat exchanger: 90° C. Exhaust gas pressure loss across heating surface: 300 Pa Heating capacity of heat exchanger: 120 kW Water inlet temperature: 50° C. Water outlet temperature: 70° C. Water flow, approx: 1.44 kg/s Pressure drop, water side: 0.2 bar - Referring now to
FIG. 5 , an embodiment of aheat exchanger 31 according to the invention having three concentric coils 32-34 is shown with the same reference numbers being utilized for elements similar to elements inFIG. 1 . The main difference between theFIG. 1 andFIG. 5 embodiments, apart from the number of coils, is thatinlet apertures outlet header tube 38 are different sizes so as to compensate for the difference in coil length between the coils 32-34 as explained below. - As the length of the
tubes 11 of the different coils 32-34 are different and all the coils are interconnected at theoutlet header 38 and at theinlet header 39, a flow distribution will be established in the coils giving the same pressure loss through each of the coils. - Thus, the
inner coils 33 and 34 [where the second fluid (typically water) have shorter flow paths than in the outermost coil 32] can transport more water than theouter coil 32. The water in thecoils - It is therefore desirable that the flow rate through the coils be regulated so that best possible heat recuperation is obtained with best possible temperature distribution both in the water and in the exhaust gas. This is achieved by creating an extra pressure loss in the
inner coils outer coil 35 and each other. - This can be achieved in two manners:
-
- By providing the tubes of the coils with different diameters. From a practical point of view this is not desirable except in case a large number of concentric coils are involved in which case 2-3 different tube diameters may be acceptable.
- By installing throttle or baffle means in the tubes or at the inlet or outlet thereof. As can be seen in
FIG. 5 andFIG. 6 , this can be achieved by providing theoutlet header tube 38 with apertures 35-37 and 40-43, respectively, having different diameters. The diameters of the individual apertures are determined based on the tube diameter and tube length in the individual coils of a heat exchanger. As an example of diameters for the four apertures shown inFIG. 6 for an inner diameter of 56 mm of all four coil tubes,aperture 40 is 56 mm,aperture 41 is 13 mm,aperture 42 is 11 mm andaperture 43 is 9 mm. Other throttle or baffle means well known in the art may also be used to achieve the different pressure loss coefficients for the individual coil tubes.
- Referring now to
FIG. 7 , the inner coil adjacent theinner conduit 5 comprises two parallel wound finnedtubes - This embodiment is intended for use for steam generation where it is necessary to take into consideration the large volume expansion of the mass inside the tubes (at the transition from liquid to vapour, water to steam) with corresponding increase in flow rate and velocity as well as pressure loss at the inner surface of the tubes. So as to provide sufficient inner flow cross sectional area in the tubes it will therefore often be necessary to use a larger tube diameter, a larger number of coils or provide for a larger number of flow paths in other ways.
- Apart from providing many coils, more flow paths may be obtained by having several parallel extending windings in the same coil as shown in
FIG. 7 , i.e. several coils with the same coil diameter and large pitch “screwed” into each other. Hereby it is obtained that a larger inner cross section area is achieved without having a large number of coils with a large diameter of the outermost coil and therefore the outer casing 2 (large footprint). This smaller footprint or outer diameter of the heat exchanger entails important advantages both for the end user and during manufacture, erection and transport. The axial length or height of the heat exchanger for a given output will of course be larger, but this does normally not represent a substantial problem during manufacture or for the end user. - Referring now to
FIGS. 9-13 , various embodiments of throttle means for throttling the flow of first fluid (typically exhaust gas) through theconduit 5 and thetubular space 8, respectively, are shown. - In the embodiment of
FIG. 9 , thebutterfly valve 17 cooperates with aring 52 that is suspended in threesteel wires 53 attached at equidistant points along thering 52. Thewires 53 extend overpulleys 54 to theshaft 18. - In the situation shown with full lines, the
butterfly valve 17 is closed and does not allow any exhaust gas to flow throughconduit 5 while thering 52 is in its highest position in which it does not throttle the flow of exhaust gas through thetubular space 8. - In the situation shown with dotted lines, the
butterfly valve 17 a functions as a by-pass valve and allows unthrottled flow of exhaust gas through theconduit 5 while thering 52 a is in its full throttle position supported on tighteningrings 55 thereby preventing flow of exhaust gas through thetubular space 8. - The
shaft 18 may be actuated manually, by an electric motor or a pneumatic or hydraulic mechanism. In the simplest version, the wires are wound onto and off not shown pulleys arranged on theshaft 18 such that rotation of theshaft 18 for opening of thebutterfly valve 17 automatically entails lowering of thering 52 and vice versa. - When no heat is required by the external heat consumption means connected to the
heat exchanger 31, then thebutterfly valve 17 is in its fully open position (17 a) and thering 52 is in its lowered fully closed position (52 a) so that all the exhaust gas is by-passed through theconduit 5. Hereby, the water in the finned tube coils is not heated so that external cooling means to avoid overheating of this water are not necessary. - A very simple means for regulating the heat output of the
heat exchanger 31 is thus provided. A temperature sensor and transmitter (not shown) may be provided in theoutlet header 38 for transmitting a signal to the not shown actuator (electric motor) for theshaft 18 so that if the temperature measured at the outlet header does not conform to the required temperature, then the shaft rotates in the corresponding direction to either open or shut the by-pass valve 17. Many different regulating circuits are conceivable depending on the requirements of the end user and the configuration of the external heat consumption devices connected to theheat exchanger 31. - Referring now to
FIGS. 10 and 11 showing an elevational and top view, respectively, of a second embodiment of the first and second throttling means for the flow of exhaust gas through the internal conduit and the tubular space, respectively, theinternal conduit 5 is connected to afurther conduit 56 having an outlet 57 in which abutterfly valve 58 is rotatably mounted on ashaft 59. The outlet 57 communicates with theoutlet 4 of thecasing 5. Thebutterfly valve 58 may rotate with theshaft 59 from the shown closed position wherein the outlet 57 is totally obstructed and an open position wherein flow of exhaust gas through outlet 57 is unhindered. - The
tubular space 8 communicates with aspace 60 defined by an extension of theouter casing 2, said space communicating with theoutlet 4 through an aperture 61 in aplate 62. Abutterfly valve 63 is mounted in said aperture 61 on theshaft 59 such that rotation of theshaft 59 rotates thebutterfly valve 63 from the shown fully open position in which flow of exhaust gas from thetubular space 8 through thespace 60 and through the aperture 61 is unhindered to a fully closed position in which flow of exhaust gas through the aperture 61 is totally obstructed. Theshaft 59 is connected to anelectric motor 64 for being rotated in opposite directions so as to rotate thevalves - Referring now to
FIG. 12 , in this embodiment thebutterfly valves FIGS. 10 and 11 have been substituted by abutterfly valve 65 and twobutterfly valves 66, respectively, the operation of thevalves shaft 59 being the same as described in connection with the embodiment ofFIGS. 10 and 11 . - Referring now to
FIG. 13 , a stationarycircular plate 70 is arranged horizontally in an embodiment of the heat exchanger similar to the one shown inFIG. 1 orFIG. 4 (without the butterfly valve 17) over the outlet of theconduit 5 and the annular outlet of thetubular space 8. Theplate 70 is provided with apertures 71 communicating with the interior ofconduit 5 andapertures 72 communicating with thetubular space 8. - A rotatably arranged
circular plate 73 is arranged on top ofplate 70 on apivot 74. Theplate 73 is provided withapertures 75 identical in shape and distribution toapertures 72 inplate 70 and with apertures 76 identical in shape and distribution to apertures 71 inplate 70. Anelectrical motor 77 is arranged for rotating therotatable plate 73 in both directions. - In the position of the rotatable plate shown in
FIG. 13 the apertures 71 and 76 coincide or overly each other so that exhaust gas can flow practically unhindered through theconduit 5 underlying these coinciding apertures while flow through thetubular space 8 is obstructed because theapertures plate 73 by means of themotor 77, a position thereof may be attained where flow through the tubular space is relatively unhindered because theapertures conduit 5 is totally obstructed because the apertures 71 and 76 do not communicate with each other at all. - The
lower plate 70 may instead be the rotatable one whereby the pressure from the exhaust gas will press theplate 70 against thestationary plate 73 and enhance the sealing effect of abutment of theplates - Referring now to
FIG. 15 , a method according to the invention of manufacturing a heat exchanger (the embodiment ofFIG. 5 ) according to the invention is illustrated. - A
cylindrical body 80 is constituted by asteel plate 81 with a thickness of 10 mm, asteel rod 82 inserted between the free axially extending edges of theplate 81, and not shown circumferentially extending tightening straps or wires for holding theplate 81 androd 82 in the shown cylindrical configuration. - The
inner coil 34 is wound helically around the body orcore 80, the leading end (not shown) and the trailingend 11 a of thepipe 11 of thecoil 34 being attached to the body by means of brackets orrods 83 welded to said ends and to thebody 80. The tightening straps mentioned above are located outside the area of thebody 80 to be covered by thecoil 34. - Four
cylindrical plates 84 having a quarter circle cross section and a thickness equal to the required radial dimension t1 (seeFIG. 8 ) are arranged on the outer surface ofcoil 33 withrods 85 arranged between mutually adjacent axially extending edges of theplates 84. Theplates 84 androds 85 are held in place by not shown circumferentially extending tightening straps or wires. Therods 85 have an oval or elliptical cross section and are placed between theplates 84 such that the major cross sectional dimension of the oval or ellipse is tangential to the circular circumference of theplates 84. - The
next coil 33 is wound helically around theplates 84 androds 85 with the leading and trailing ends of thecoil 33 being welded to one of theplates 84 by means of brackets orrods 83 in a manner very similar to the winding and attachment of theinner coil 34. - The process is repeated for the
next coil 32. If more coils than three are required, the process described above may be repeated for any such further coils. - The unit comprising the
body 80, the coils 32-34 and theplates 84 withrods 85 is thereafter subjected to annealing heat treatment for avoiding elastic diameter expansion of the coils and to remove potentially damaging stresses. - After annealing, the attachments by means of
brackets 83 are removed, therods 85 are rotated such that the major dimension of the oval or elliptical cross section is oriented radially whereby the coils 32-34 are forced to expand slightly such that thecylindrical plates 84 may be removed. Finallyrod 82 is removed such that thebody 80 may be removed. The coils 32-34 are now ready for being inserted in acasing 2 with aconduit 5 placed inside theinner coil 34. - A heat exchanger according to the invention is particularly well suited for use in a combination or system comprising a gas fired turbine (or an internal combustion engine utilizing natural gas as fuel). Such a system is furthermore particularly well suited for (but not in any way limited to) for use in a system for small scale combined production of electricity and heat, for instance for large buildings, hospitals, small district heating systems and the like.
- Referring now to
FIG. 16 , a system or combination according to the invention including a heat exchanger according to the invention, a gas fired turbine and external heat consuming devices is shown with the following characteristics:Item Component Description 101 Heat exchanger according to the invention. 102 Exhaust gas by-pass damper or Can be regulated manually or as shown valve (butterfly valve for instance) here: regulated by an actuator (electrical motor), item 11103 Exhaust gas stack 104 Gas fired turbine Could be another kind of component producing exhaust gas 105 Circulation pump A forced circulation system, to circulate the required water/fluid flow. The pressure drop on water side in the heat exchanger, valves and piping system to be taken into account when calculating the delivery head of the pump. 106 Expansion tank To take the expansion/contraction of the fluid in the system, when the temperature varies. 107 External end user Or other heat consumption device. Can be Heat exchanger for heating use in buildings, in greenhouses, district heating systems etc. 108 Safety valve To be opened if the pressure in the system becomes too high 109 Stop valves Normally open. Possible to close in case of repair. 110 Air venting valve 111 Electrical motor Electrical motor, automatically controlled by signals from the temperature transmitter 113. Opens the by-pass valve 102 a little, if the water temperature becomes too high, closes the valve 102 a little if the water temperature becomes too low. Set points to be decided by the end user. 112 Drain valve To drain the water/fluid from the system 113 Temperature transmitter Sends signal to electrical motor if temperature measured is too high or too low - The system can comprise other exhaust gas generating devices, and the regulation of the heat exchanger's by-pass valve (and the heat exchanger's throttle valve for throttling fluid flow through the tubular space containing the finned tube coils) can be provided for in many different manners depending on the configuration of the end user's heat consuming devices.
Claims (43)
1. A heat exchanger for heat exchange between a first fluid and a second fluid and comprising:
a generally cylindrical casing with a first inlet and a first outlet for allowing said first fluid to flow through said casing in a generally axial direction,
a generally cylindrical fluid conduit arranged inside said casing generally coaxial therewith so that an axially extending first tubular space is defined between said conduit and said casing, said conduit having a second inlet and a second outlet for allowing said first fluid to flow through said conduit in a generally axial direction, and said first tubular space having a third inlet and a third outlet for allowing said first fluid to flow through said tubular space in a generally axial direction,
at least one helical coil comprising a tube selected from the group consisting of a finned tube and a corrugated tube arranged inside said first tubular space generally coaxial therewith and having a fourth inlet and a fourth outlet for allowing said second fluid to flow through said tube.
2. A heat exchanger according to claim 1 further comprising first adjustable throttle means for adjustably throttling said flow of said first fluid through said conduit and second adjustable throttle means for adjustably throttling said flow of said first fluid through said first tubular space.
3. A heat exchanger according to claim 2 , wherein said first throttle means comprise a first butterfly valve, arranged adjacent one of said second inlet and said second outlet, and said second throttle means comprise a second butterfly valve, arranged adjacent one of said third inlet and said third outlet.
4. A heat exchanger according to claim 2 , wherein said first throttle means comprise a first butterfly valve, arranged adjacent one of said second inlet and said second outlet, and said second throttle means comprise a ring having planar dimensions corresponding to the cross section of said first tubular space and being arranged for being displaced from a heating position wherein said flow of first fluid through said tubular space is substantially unhindered to a bypass position wherein said flow is substantially obstructed.
5. A heat exchanger according to claim 2 , wherein said first and second throttle means comprise:
a fixedly arranged stationary plate with first and second apertures provided therein arranged such that said second and third inlets or outlets are obstructed by said plate such that the flow of first fluid through said conduit and said first tubular space takes place through said first and second apertures, respectively, in said stationary plate, and
at least one movable plate with third and fourth apertures provided therein and arranged so as to be displaceable from a bypass position overlying said stationary plate, wherein said third apertures coincide with said first apertures and said fourth apertures do not coincide with said second apertures, to a heating position overlying said stationary plate wherein said fourth apertures coincide with said second apertures and said third apertures do not coincide with said first apertures.
6. A heat exchanger according to any of the claims 2-5 and further comprising actuating means for adjusting the throttling effect of said first and second throttle means.
7. A heat exchanger according to claim 6 , wherein said throttling means and said actuating means are adapted such that substantially any rate of flow between a maximum and minimum rate of flow of said first fluid through said second inlet and said third inlet may be obtained.
8. A heat exchanger according to claim 7 , wherein said minimum rate is substantially equal to zero.
9. A heat exchanger according to claim 1 and comprising at least two coil arranged concentrically and such that mutually adjacent coils are radially spaced such that an axially extending second tubular space is provided between said mutually adjacent coils.
10. A heat exchanger according to claim 1 , wherein the outer surface of said conduit is spaced radially from the coil adjacent said surface such that an axially extending third tubular space is provided between said surface and said adjacent coil.
11. A heat exchanger according to claim 9 or 10, wherein the radial dimensions of said second and third tubular spaces are adapted so as to achieve a certain pressure loss for a given rate of flow of said first fluid through said first tubular space.
12. A heat exchanger according to claim 1 , wherein the coil has mutually adjacent individual windings that are mutually axially spaced such that a helically extending space is provided between said adjacent windings.
13. A heat exchanger according to claim 1 and comprising three or more helical coils arranged concentrically, each comprising a finned tube one of the coils being an innermost coil and another of the coils being an outermost coil, the interior diameter of the finned tubes constituting the coils being the same, wherein third throttling means are provided in the tubes constituting the coils located radially inwards of the outermost coil for increasing the pressure loss through the tubes of the remaining coils so as to compensate for the shorter length of said tubes relative to the length of the tubes of the outermost coil such that the rate of low of said second fluid through the tubes of all the coils is substantially the same for a given uniform pressure in said second fluid at said fourth inlets.
14. A heat exchanger according to claim 13 , wherein said third throttling means are constituted by a reduction of the cross sectional area of the flow of said second fluid relative to the internal cross sectional area of said tubes.
15. A heat exchanger according to claim 14 and further comprising an inlet header tube and an outlet header tube in fluid communication with said fourth inlets and fourth outlets, respectively, of all said tubes through corresponding communication apertures in said header tubes, said reduction of flow cross sectional area being constituted by reduced size of said communication apertures in one of said inlet header tube and said outlet header tube.
16. A heat exchanger according to claim 1 , wherein the helical coil comprises two or more helically wound finned tubes extending adjacent one another with the same pitch.
17. A combination of a heat exchanger according to claim 1 and an exhaust gas generating combustion means selected from the group consisting of at least one of a natural gas fired turbine, an internal combustion engine, a furnace, a burner, an incinerator, the combination comprising interconnection means for interconnecting an exhaust gas outlet of the combustion means with said second and third inlets of the heat exchanger such that said exhaust gas constitutes said first fluid.
18. A combination according to claim 17 and further comprising
heat exchanging means for heat exchange between said second fluid and at least one of a third fluid and the surroundings of said heat exchanging means, said heat exchanging means being in fluid communication with said fourth outlet,
measuring means for measuring the rate of heat exchange of said heat exchanging means,
signal output means for emitting a signal representing the result of a measurement carried out by said measuring means, and
first control means for controlling the adjustment of said first and second throttle means and adapted for receiving said signal.
19. A combination according to claim 17 or 18 and further comprising second control means for controlling the adjustment of said first throttle means such that the throttling effect thereof is at a minimum during the start up phase of the combustion means.
20. A combination of a heat exchanger for heat exchange between a first fluid and a second fluid and an exhaust gas generating combustion means, the heat exchanger comprising:
a generally cylindrical casing with a first inlet and a first outlet for allowing said first fluid to flow through said casing in a generally axial direction,
a generally cylindrical fluid conduit arranged inside said casing generally coaxial therewith so that a axially extending first tubular space is defined between said conduit and said casing, said conduit having a second inlet and a second outlet for allowing said first fluid to flow through said conduit in a generally axial direction, and said first tubular space having a third inlet and a third outlet for allowing said first fluid to flow through said tubular space in a generally axial direction, and
at least one helical coil comprising a tube selected from the group consisting of a finned tube and a corrugated tube arranged inside said first tubular space generally coaxial therewith and having a fourth inlet and a fourth outlet for allowing said second fluid to flow through said finned tube,
the combination comprising interconnection means for interconnecting an exhaust gas outlet of the combustion means with said second and third inlets of the heat exchanger such that said exhaust gas constitutes said first fluid.
21. A combination according to claim 20 further comprising first adjustable throttle means for adjustably throttling said flow of said first fluid through at least one of said conduit and second adjustable throttle means for adjustably throttling said flow of said first fluid through said first tubular space.
22. A combination according to claim 21 , wherein said first throttle means comprise a first butterfly valve, arranged adjacent one of said second inlet and said second outlet, and said second throttle means comprise a second butterfly valve, arranged adjacent one of said third inlet and said third outlet.
23. A combination according to claim 21 , wherein said first throttle means comprise a first butterfly valve, arranged adjacent said one of second inlet and said second outlet, and said second throttle means comprise a ring having planar dimensions corresponding to the cross section of said first tubular space and being arranged for being displaced from a heating position wherein said flow of first fluid through said tubular space is substantially unhindered to a bypass position wherein said flow is substantially obstructed.
24. A combination according to claim 21 , wherein said first and second throttle means comprise:
a fixedly arranged stationary plate with first and second apertures provided therein arranged such that either said second and third inlets or said second and third outlets are obstructed by said plate such that the flow of first fluid through said conduit and said first tubular space takes place through said first and second apertures, respectively, in said stationary plate, and
at least one movable plate with third and fourth apertures provided therein and arranged displaceable from a bypass position overlying said stationary plate, wherein said third apertures coincide with said first apertures and said fourth apertures do not coincide with said second apertures, to a heating position overlying said stationary plate wherein said fourth apertures coincide with said second apertures and said third apertures do not coincide with said first apertures.
25. A combination according to claim 21 and further comprising actuating means for adjusting the throttling effect of said first and second throttle means.
26. A combination according to claims 21, wherein said throttling means and said actuating means are adapted such that substantially any rate of flow between a maximum and minimum rate of flow of said first fluid through said second inlet and said third inlet may be obtained.
27. A combination according to claim 26 , wherein said minimum rate is substantially equal to zero.
28. A combination according to claim 21 and comprising two or more helical coils arranged concentrically and such that mutually adjacent coils are radially spaced such that an axially extending second tubular space is provided between said mutually adjacent coils.
29. A combination according to claim 21 , wherein the outer surface of said conduit is spaced radially from the coil adjacent said surface such that an axially extending third tubular space is provided between said surface and said adjacent coil.
30. A combination according to claim 28 , wherein the radial dimension of said second tubular space is adapted so as to achieve a certain pressure loss for a given rate of flow of said first fluid through said first tubular space.
31. A combination according to claim 29 , wherein the radial dimension of said third tubular space is adapted so as to achieve a certain pressure loss for a given rate of flow of said first fluid through said first tubular space.
32. A combination according to claim 21 , wherein the mutually adjacent individual windings of a coil are mutually axially spaced such that a helically extending space is provided between said adjacent windings.
33. A combination according to claim 21 and comprising three or more helical coils arranged concentrically, one of said coils being an outermost coil, each of the coils comprising a finned tube, the interior diameter of the finned tubes being the same, wherein third throttling means are provided in the tubes of the coils located radially inward of the outermost coil for increasing the pressure loss through the tubes of said radially inward located coils so as to compensate for the shorter length of said tubes of said radially inward located coils relative to the length of the tubes of the outermost coil such that the rate of low of said second fluid through the tubes of all the coils is substantially the same for a given uniform pressure in said second fluid at said fourth inlets.
34. A combination according to claim 33 , wherein said third throttling means are constituted by a reduction of the cross sectional area of the flow of said second fluid relative to the internal cross sectional area of said tubes.
35. A combination according to claim 34 and further comprising an inlet header tube and an outlet header tube in fluid communication with said fourth inlets and fourth outlets, respectively, of all said tubes through corresponding communication apertures in said header tubes, said reduction of flow cross sectional area being constituted by reduced size of said communication apertures in one of said inlet header tube and said outlet header tube.
36. A combination according to claim 21 , wherein a helical coil comprises two or more helically wound finned tubes extending adjacent one another with the same pitch.
37. A combination according to claim 21 and further comprising
heat exchanging means for heat exchange between said second fluid and at least one of a third fluid and the surroundings of said heat exchanging means, said heat exchanging means being in fluid communication with said fourth outlet,
measuring means for measuring the rate of heat exchange of said heat exchanging means,
signal output means for emitting a signal representing the result of a measurement carried out by said measuring means, and
first control means for controlling the adjustment of said first and second throttle means and adapted for receiving said signal.
38. A combination according to claim 21 and further comprising second control means for controlling the adjustment of said first throttle means such that the throttling effect thereof is at a minimum during the start up phase of said combustion means.
39. A combination according to claim 20 , wherein said exhaust gas generating combustion means is chosen from the group comprising a natural gas fired turbine, an internal combustion engine, a burner, a furnace and an incinerator.
40. A method of manufacturing a heat exchanger according to claim 1 and comprising the steps of:
providing a first length of tube selected from the group consisting of a finned tube and a corrugated tube,
providing a body having a substantially circular cylindrical surface,
providing rotating means for causing relative rotation of said tube and said surface,
arranging a lead portion of said tube abutting against said surface,
causing relative rotation of said surface and said lead portion such that said first length of tube is helically wound on said surface to form a first helical coil.
41. A method according to claim 40 and comprising the further steps of:
providing spacing means,
attaching said spacing means to said first helical coil,
providing a second length of tube selected from the group consisting of a finned tube and a corrugated tube,
arranging a lead portion of said second length of tube abutting against said spacing means,
causing relative rotation of first helical coil and said lead portion of said second length of tube such that said second length of tube is helically wound on said spacing means to form a second helical coil radially spaced from said first helical coil.
42. A method according to claim 40 and comprising the further steps of:
fixating said helical coil relative to said body, and
subjecting said body and said coil to annealing heat treatment.
43. A method according to claim 41 and comprising the further steps of:
fixating said second helical coil relative to at least one of said body and said first helical coil, and
subjecting said body and said first and second coils to annealing heat treatment.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/840,952 US20050133202A1 (en) | 2001-11-09 | 2004-05-07 | Heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DKPA200101661 | 2001-11-09 | ||
DKDKPA200101661 | 2001-11-09 | ||
PCT/DK2002/000748 WO2003040641A1 (en) | 2001-11-09 | 2002-11-07 | A heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger |
US10/840,952 US20050133202A1 (en) | 2001-11-09 | 2004-05-07 | Heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DK2002/000748 Continuation WO2003040641A1 (en) | 2001-11-09 | 2002-11-07 | A heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20050133202A1 true US20050133202A1 (en) | 2005-06-23 |
Family
ID=34680188
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/840,952 Abandoned US20050133202A1 (en) | 2001-11-09 | 2004-05-07 | Heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger |
Country Status (1)
Country | Link |
---|---|
US (1) | US20050133202A1 (en) |
Cited By (69)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050006060A1 (en) * | 2003-06-26 | 2005-01-13 | Viktor Brost | Exhaust heat exchanger |
US20050081523A1 (en) * | 2003-10-16 | 2005-04-21 | Thomas Breitling | Charged internal combustion engine |
US20070062377A1 (en) * | 2005-09-20 | 2007-03-22 | Nestec S.A. | Thermoblock-based beverage production device with brewing chambers |
WO2007084011A1 (en) * | 2006-01-23 | 2007-07-26 | Kanfa-Tec As | Heat recovery unit |
US20070295493A1 (en) * | 2004-12-18 | 2007-12-27 | Neue Energie-Verwertungsge-Sellschaft Mbh | Heat Exchanger |
EP1923545A2 (en) * | 2006-08-11 | 2008-05-21 | Janich GmbH & Co. KG | Heat recovery system |
US20080135029A1 (en) * | 2003-09-05 | 2008-06-12 | Gregg Speer | Method for controlling a valve for an exhaust system |
GB2447974A (en) * | 2007-03-30 | 2008-10-01 | Rbr Associates Ltd | Heat exchanger of a condensing boiler |
US20090038302A1 (en) * | 2006-03-16 | 2009-02-12 | Takeshi Yamada | Exhaust gas heat recovery device |
US7506680B1 (en) * | 2005-05-23 | 2009-03-24 | Gil Del Castillo | Helical heat exchange apparatus |
WO2010013053A3 (en) * | 2008-07-30 | 2010-04-08 | Heat Recovery Solutions Limited | Heat exchanger |
US20100089043A1 (en) * | 2008-10-10 | 2010-04-15 | Dittmann Joerg | Cooling system |
US20100146954A1 (en) * | 2008-12-12 | 2010-06-17 | Wescast Industries, Inc. | Liquid-Cooled Exhaust Valve Assembly |
US20100192623A1 (en) * | 2007-07-16 | 2010-08-05 | Industrie Ilpea S.P.A. | Refrigeration circuit |
US20100206542A1 (en) * | 2009-02-17 | 2010-08-19 | Andrew Francis Johnke | Combined multi-stream heat exchanger and conditioner/control unit |
US20110041781A1 (en) * | 2009-08-18 | 2011-02-24 | Sridhar Deivasigamani | Coil tube heat exchanger for a tankless hot water system |
KR20110042335A (en) * | 2008-07-29 | 2011-04-26 | 헨켈 아게 운트 코. 카게아아 | Reinforcement assembly |
US20110094492A1 (en) * | 2008-04-11 | 2011-04-28 | Eduard Alper Bolkan | Device for feeding water steam via a heat exchanger in a combustion chamber and a method |
US20110126583A1 (en) * | 2008-12-29 | 2011-06-02 | Mccormick Stephen A | Liquid co2 passive subcooler |
NL2003980C2 (en) * | 2009-12-18 | 2011-06-21 | Muelink & Grol Bv | SMOKE GAS DRAINAGE APPLIANCE WITH HEAT EXCHANGER. |
WO2011089140A1 (en) * | 2010-01-21 | 2011-07-28 | Shell Internationale Research Maatschappij B.V. | Heat exchanger and method of operating a heat exchanger |
GB2477316A (en) * | 2010-01-29 | 2011-08-03 | Tanjung Citech Uk Ltd | Seal for a heat exchanger bypass valve |
CN102140952A (en) * | 2010-09-25 | 2011-08-03 | 苏州派格力减排系统有限公司 | Tail gas heater |
US20110185985A1 (en) * | 2010-02-03 | 2011-08-04 | Farshid Ahmady | Fluid heating apparatus |
US20110240266A1 (en) * | 2010-04-05 | 2011-10-06 | Holland Bryan C | Helicoid turbulator for heat exchangers |
FR2958735A1 (en) * | 2010-04-13 | 2011-10-14 | Air Proc Components | Air/liquid exchanger for use in installation that is used for recuperation of energy contained in foul air at professional kitchen, has tank provided with deflector located partly at top with respect to radial exit |
WO2011153179A1 (en) | 2010-06-01 | 2011-12-08 | Delphi Technologies, Inc. | Exhaust gas heat recovery heat exchanger |
WO2011092318A3 (en) * | 2010-01-29 | 2011-12-22 | Tanjung Citech Uk Limited | A heat exchange unit |
US8141199B1 (en) * | 2007-02-12 | 2012-03-27 | Garland Peter C | Heat exchanger system |
WO2011148178A3 (en) * | 2010-05-26 | 2012-07-26 | Heat Recovery Solutions Ltd | Heat exchange unit |
WO2012121696A1 (en) * | 2011-03-07 | 2012-09-13 | Aavid Thermalloy, Llc | Thermal transfer device with spiral fluid pathways |
US20130112371A1 (en) * | 2011-11-04 | 2013-05-09 | Delphi Technologies, Inc. | Exhaust gas heat recovery heat exchanger having a lobed tube coil |
WO2013028083A3 (en) * | 2011-08-25 | 2013-07-25 | Invention Mind Sp. Zo. O. | Oil heating boiler |
US20130239571A1 (en) * | 2012-03-15 | 2013-09-19 | Eberspächer Exhaust Technology GmbH & Co. KG | Steam generator for a rankine cycle |
WO2013156139A1 (en) * | 2012-04-19 | 2013-10-24 | Thyssenkrupp Uhde Gmbh | Process gas cooler having lever-controlled process gas cooler flaps |
US20140033703A1 (en) * | 2011-04-13 | 2014-02-06 | Emitec Gesellschaft Fuer Emissionstechnologie Mbh | Device having a heat exchanger for a thermoelectric generator of a motor vehicle and motor vehicle having the device |
EP2708711A1 (en) * | 2012-09-14 | 2014-03-19 | Eberspächer Exhaust Technology GmbH & Co. KG | Exhaust gas heat exchanger |
EP2708708A1 (en) * | 2012-09-14 | 2014-03-19 | Eberspächer Exhaust Technology GmbH & Co. KG | Exhaust gas heat exchanger |
DE102012108944A1 (en) * | 2012-09-21 | 2014-05-28 | Bio-System Gesellschaft Für Anwendungen Biologischer Verfahren Mbh | Steam generator for producing steam used for combustion engine, has tube for conducting medium to be evaporated, that is arranged in inner space of boiler |
US20140202157A1 (en) * | 2011-05-02 | 2014-07-24 | Meir Shinnar | Thermal energy storage for combined cycle power plants |
US20140208725A1 (en) * | 2013-01-30 | 2014-07-31 | Eberspächer Exhaust Technology GmbH & Co. KG | Heat exchanger of an internal combustion engine |
WO2013120998A3 (en) * | 2012-02-16 | 2014-10-02 | Eberspächer Exhaust Technology GmbH & Co. KG | Steam generator for a rankine process |
WO2014202942A1 (en) * | 2013-06-20 | 2014-12-24 | Boustead International Heaters Limited | Improvements in waste heat recovery units |
CN104246201A (en) * | 2011-12-28 | 2014-12-24 | 杜齐克天梦有限责任公司 | Anti-pollution economiser device |
US20150004552A1 (en) * | 2013-06-28 | 2015-01-01 | American Air Liquide, Inc. | Method and Heat Exchange System Utilizing Variable Partial Bypass |
US20150322899A1 (en) * | 2014-05-07 | 2015-11-12 | Benteler Automobiltechnik Gmbh | Exhaust-gas heat exchanger with bypass pipe |
US9239001B2 (en) | 2012-09-14 | 2016-01-19 | Eberspächer Exhaust Technology GmbH & Co. KG | Heat exchanger |
US20160146455A1 (en) * | 2014-11-21 | 2016-05-26 | Honeywell International Inc. | Fuel-air-flue gas burner |
EP2896802A4 (en) * | 2012-08-10 | 2016-06-01 | Futaba Ind Co Ltd | Exhaust heat recovery device |
US20160298516A1 (en) * | 2013-12-19 | 2016-10-13 | Volvo Truck Corporation | An exhaust gas treatment system to be fitted on a chassis of an automotive vehicle |
US20170097194A1 (en) * | 2014-06-30 | 2017-04-06 | Modine Manufacturing Company | Heat Exchanger and Method of Making the Same |
US9664087B2 (en) | 2010-07-22 | 2017-05-30 | Wescast Industries, Inc. | Exhaust heat recovery system with bypass |
CN106996705A (en) * | 2017-05-05 | 2017-08-01 | 张家港格林沙洲锅炉有限公司 | The cigarette journey structure of marine heat recovery boiler |
US20170248050A1 (en) * | 2016-02-26 | 2017-08-31 | Hanon Systems | Rolled fin spiral egr cooler |
US9835356B1 (en) * | 2015-02-06 | 2017-12-05 | Sioux Corporation | Fluid heating apparatus utilizing at least two fluid paths |
US10151476B2 (en) | 2015-04-06 | 2018-12-11 | Central Boiler Inc. | Boiler with access to heat exchangers |
DE102017209727A1 (en) * | 2017-06-08 | 2018-12-13 | Volkswagen Aktiengesellschaft | Device for heat recovery |
WO2018224296A1 (en) | 2017-06-08 | 2018-12-13 | Volkswagen Aktiengesellschaft | Apparatus for heat recovery |
DE102017209725A1 (en) * | 2017-06-08 | 2018-12-13 | Volkswagen Aktiengesellschaft | Device for heat recovery from a heating fluid |
US10371413B2 (en) | 2015-04-06 | 2019-08-06 | Central Boiler, Inc. | Boiler with access to heat exchangers |
WO2019197907A3 (en) * | 2018-04-13 | 2019-11-14 | Flowserve Management Company | Fluid coolers, heat exchangers, seal assemblies and systems including fluid coolers or heat exchangers and related methods |
US10514206B2 (en) * | 2017-02-24 | 2019-12-24 | Intellihot, Inc. | Multi-coil heat exchanger |
CN111492132A (en) * | 2017-12-15 | 2020-08-04 | 通用电气公司 | Heat regenerator for gas turbine engine |
US20200248087A1 (en) * | 2019-02-05 | 2020-08-06 | Saudi Arabian Oil Company | Producing Synthetic Gas |
US10753644B2 (en) | 2017-08-04 | 2020-08-25 | A. O. Smith Corporation | Water heater |
EP3159646B2 (en) † | 2015-10-20 | 2021-12-29 | Borsig GmbH | Heat exchanger |
US11353270B1 (en) * | 2019-04-04 | 2022-06-07 | Advanced Cooling Technologies, Inc. | Heat pipes disposed in overlapping and nonoverlapping arrangements |
EP4047296A1 (en) * | 2021-02-17 | 2022-08-24 | Pratt & Whitney Canada Corp. | Fluid cooler for a gas turbine engine |
US11867428B2 (en) | 2020-04-28 | 2024-01-09 | A.O. Smith Corporation | Heat exchange pipe, heat exchanger and water heating apparatus |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1885267A (en) * | 1929-10-28 | 1932-11-01 | Kalfus Victor | Fluid heating device |
US3392777A (en) * | 1966-04-22 | 1968-07-16 | Vapor Corp | Heat exchanger |
US3639963A (en) * | 1969-10-08 | 1972-02-08 | Vapor Corp | Method of making a heat exchanger coil assembly |
US4321963A (en) * | 1979-07-05 | 1982-03-30 | Solar Unlimited, Inc. | Single layer volute heat exchanger |
US4371027A (en) * | 1975-09-10 | 1983-02-01 | Jacobsen Orval E | Economizer with an integral gas bypass |
US20020179292A1 (en) * | 2000-01-26 | 2002-12-05 | Yanwen Zhu | Assembling heat exchanger of spiral sleeve |
-
2004
- 2004-05-07 US US10/840,952 patent/US20050133202A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1885267A (en) * | 1929-10-28 | 1932-11-01 | Kalfus Victor | Fluid heating device |
US3392777A (en) * | 1966-04-22 | 1968-07-16 | Vapor Corp | Heat exchanger |
US3639963A (en) * | 1969-10-08 | 1972-02-08 | Vapor Corp | Method of making a heat exchanger coil assembly |
US4371027A (en) * | 1975-09-10 | 1983-02-01 | Jacobsen Orval E | Economizer with an integral gas bypass |
US4321963A (en) * | 1979-07-05 | 1982-03-30 | Solar Unlimited, Inc. | Single layer volute heat exchanger |
US20020179292A1 (en) * | 2000-01-26 | 2002-12-05 | Yanwen Zhu | Assembling heat exchanger of spiral sleeve |
Cited By (132)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7036565B2 (en) * | 2003-06-26 | 2006-05-02 | Modine Manufacturing Company | Exhaust heat exchanger |
US20050006060A1 (en) * | 2003-06-26 | 2005-01-13 | Viktor Brost | Exhaust heat exchanger |
US20080135029A1 (en) * | 2003-09-05 | 2008-06-12 | Gregg Speer | Method for controlling a valve for an exhaust system |
US7836945B2 (en) * | 2003-09-05 | 2010-11-23 | Emcon Technologies Llc | Method for controlling a valve for an exhaust system |
US20050081523A1 (en) * | 2003-10-16 | 2005-04-21 | Thomas Breitling | Charged internal combustion engine |
US20070295493A1 (en) * | 2004-12-18 | 2007-12-27 | Neue Energie-Verwertungsge-Sellschaft Mbh | Heat Exchanger |
US7506680B1 (en) * | 2005-05-23 | 2009-03-24 | Gil Del Castillo | Helical heat exchange apparatus |
US20070062377A1 (en) * | 2005-09-20 | 2007-03-22 | Nestec S.A. | Thermoblock-based beverage production device with brewing chambers |
US8646377B2 (en) * | 2005-09-20 | 2014-02-11 | Nestec S.A. | Thermoblock-based beverage production device with brewing chambers |
US20100263831A1 (en) * | 2006-01-23 | 2010-10-21 | Terje Kaspersen | Heat recovery unit |
GB2448462A (en) * | 2006-01-23 | 2008-10-15 | Kanfa Tec As | Heat recovery unit |
GB2448462B (en) * | 2006-01-23 | 2011-07-13 | Kanfa Tec As | Heat recovery unit |
WO2007084011A1 (en) * | 2006-01-23 | 2007-07-26 | Kanfa-Tec As | Heat recovery unit |
DK178491B1 (en) * | 2006-01-23 | 2016-04-18 | Kanfa Tec As | Heat recovery unit |
US8517084B2 (en) | 2006-01-23 | 2013-08-27 | Kanfa-Tec As | Heat recovery unit |
US8297049B2 (en) * | 2006-03-16 | 2012-10-30 | Toyota Jidosha Kabushiki Kaisha | Exhaust gas heat recovery device |
US20090038302A1 (en) * | 2006-03-16 | 2009-02-12 | Takeshi Yamada | Exhaust gas heat recovery device |
EP1923545A2 (en) * | 2006-08-11 | 2008-05-21 | Janich GmbH & Co. KG | Heat recovery system |
EP1923545A3 (en) * | 2006-08-11 | 2011-01-05 | Janich GmbH & Co. KG | Heat recovery system |
US8141199B1 (en) * | 2007-02-12 | 2012-03-27 | Garland Peter C | Heat exchanger system |
GB2447974A (en) * | 2007-03-30 | 2008-10-01 | Rbr Associates Ltd | Heat exchanger of a condensing boiler |
US20100192623A1 (en) * | 2007-07-16 | 2010-08-05 | Industrie Ilpea S.P.A. | Refrigeration circuit |
US20110094492A1 (en) * | 2008-04-11 | 2011-04-28 | Eduard Alper Bolkan | Device for feeding water steam via a heat exchanger in a combustion chamber and a method |
KR101597852B1 (en) | 2008-07-29 | 2016-02-26 | 헨켈 아게 운트 코. 카게아아 | Reinforcement assembly |
KR20110042335A (en) * | 2008-07-29 | 2011-04-26 | 헨켈 아게 운트 코. 카게아아 | Reinforcement assembly |
US20110180234A1 (en) * | 2008-07-29 | 2011-07-28 | Heat Recovery Solutions Limited | Heat exchanger |
EP2713136A1 (en) * | 2008-07-30 | 2014-04-02 | Heat Recovery Solutions Limited | Heat exchanger |
AU2009275670B2 (en) * | 2008-07-30 | 2015-06-18 | Heat Recovery Solutions Limited | Heat exchanger |
WO2010013053A3 (en) * | 2008-07-30 | 2010-04-08 | Heat Recovery Solutions Limited | Heat exchanger |
US9080816B2 (en) * | 2008-07-30 | 2015-07-14 | Heat Recovery Solutions Limited | Exhaust recovery heat exchanger with inlet damper |
US10526967B2 (en) * | 2008-07-30 | 2020-01-07 | Heat Recovery Solutions Limited | Exhaust recovery heat exchanger with inlet damper |
CN102165280A (en) * | 2008-07-30 | 2011-08-24 | 热回收方案有限公司 | Heat exchanger |
US20100089043A1 (en) * | 2008-10-10 | 2010-04-15 | Dittmann Joerg | Cooling system |
US20100146954A1 (en) * | 2008-12-12 | 2010-06-17 | Wescast Industries, Inc. | Liquid-Cooled Exhaust Valve Assembly |
EP2386038A2 (en) * | 2008-12-12 | 2011-11-16 | Wescast Industries, Inc. | Liquid-cooled exhaust valve assembly |
EP2386038A4 (en) * | 2008-12-12 | 2012-12-12 | Wescast Ind Inc | Liquid-cooled exhaust valve assembly |
US8443593B2 (en) * | 2008-12-12 | 2013-05-21 | Westcast Industries, Inc. | Liquid-cooled exhaust valve assembly |
US20110126583A1 (en) * | 2008-12-29 | 2011-06-02 | Mccormick Stephen A | Liquid co2 passive subcooler |
US20100206520A1 (en) * | 2009-02-17 | 2010-08-19 | Andrew Francis Johnke | Combined multi-stream heat exchanger and conditioner/control unit |
US20100206542A1 (en) * | 2009-02-17 | 2010-08-19 | Andrew Francis Johnke | Combined multi-stream heat exchanger and conditioner/control unit |
WO2010096305A1 (en) * | 2009-02-17 | 2010-08-26 | Sme Products, Lp | Combined multi-stream heat exchanger and conditioner/control unit |
US8656867B2 (en) | 2009-08-18 | 2014-02-25 | Intellihot Green Technologies, Inc. | Coil tube heat exchanger for a tankless hot water system |
US20110041781A1 (en) * | 2009-08-18 | 2011-02-24 | Sridhar Deivasigamani | Coil tube heat exchanger for a tankless hot water system |
WO2011022452A3 (en) * | 2009-08-18 | 2011-06-09 | Sridhar Deivasigamani | Coil tube heat exchanger for a tankless hot water system |
JP2013505415A (en) * | 2009-08-18 | 2013-02-14 | デイバシガマニ,シュリダール | Coil tube heat exchanger for tankless hot water system |
AU2010284267B2 (en) * | 2009-08-18 | 2013-05-30 | Sivaprasad Akasam | Coil tube heat exchanger for a tankless hot water system |
NL2003980C2 (en) * | 2009-12-18 | 2011-06-21 | Muelink & Grol Bv | SMOKE GAS DRAINAGE APPLIANCE WITH HEAT EXCHANGER. |
EP2366971A1 (en) | 2009-12-18 | 2011-09-21 | Muelink & Grol B.V. | Condensing heating appliance with flue gas vent fitting with heat exchanger |
AU2011208759B2 (en) * | 2010-01-21 | 2014-03-20 | Air Products And Chemicals, Inc. | Heat exchanger and method of operating a heat exchanger |
WO2011089140A1 (en) * | 2010-01-21 | 2011-07-28 | Shell Internationale Research Maatschappij B.V. | Heat exchanger and method of operating a heat exchanger |
WO2011092318A3 (en) * | 2010-01-29 | 2011-12-22 | Tanjung Citech Uk Limited | A heat exchange unit |
GB2477316A (en) * | 2010-01-29 | 2011-08-03 | Tanjung Citech Uk Ltd | Seal for a heat exchanger bypass valve |
US9353967B2 (en) * | 2010-02-03 | 2016-05-31 | Farshid Ahmady | Fluid heating apparatus |
US20110185985A1 (en) * | 2010-02-03 | 2011-08-04 | Farshid Ahmady | Fluid heating apparatus |
US20110240266A1 (en) * | 2010-04-05 | 2011-10-06 | Holland Bryan C | Helicoid turbulator for heat exchangers |
FR2958735A1 (en) * | 2010-04-13 | 2011-10-14 | Air Proc Components | Air/liquid exchanger for use in installation that is used for recuperation of energy contained in foul air at professional kitchen, has tank provided with deflector located partly at top with respect to radial exit |
US10247487B2 (en) * | 2010-05-26 | 2019-04-02 | Heat Recovery Solutions Limited | Heat exchange unit |
CN103080688A (en) * | 2010-05-26 | 2013-05-01 | 热回收方案有限公司 | Heat exchange unit |
US20150361856A1 (en) * | 2010-05-26 | 2015-12-17 | Heat Recovery Solutions Limited | Heat exchange unit |
US9551256B2 (en) * | 2010-05-26 | 2017-01-24 | Heat Recovery Solutions Limited | Heat exchange unit |
US20170122675A1 (en) * | 2010-05-26 | 2017-05-04 | Heat Recovery Solutions Limited | Heat exchange unit |
WO2011148178A3 (en) * | 2010-05-26 | 2012-07-26 | Heat Recovery Solutions Ltd | Heat exchange unit |
US9127580B2 (en) * | 2010-05-26 | 2015-09-08 | Heat Recovery Solutions Limited | Heat exchange unit |
EP3165862A1 (en) * | 2010-05-26 | 2017-05-10 | Heat Recovery Solutions Limited | Heat exchange unit |
US20130139492A1 (en) * | 2010-05-26 | 2013-06-06 | Heat Recovery Solutions Ltd. | Heat exchange unit |
WO2011153179A1 (en) | 2010-06-01 | 2011-12-08 | Delphi Technologies, Inc. | Exhaust gas heat recovery heat exchanger |
EP2577031A1 (en) * | 2010-06-01 | 2013-04-10 | Delphi Technologies, Inc. | Exhaust gas heat recovery heat exchanger |
EP2577031A4 (en) * | 2010-06-01 | 2014-12-31 | Delphi Tech Inc | Exhaust gas heat recovery heat exchanger |
US9664087B2 (en) | 2010-07-22 | 2017-05-30 | Wescast Industries, Inc. | Exhaust heat recovery system with bypass |
CN102140952A (en) * | 2010-09-25 | 2011-08-03 | 苏州派格力减排系统有限公司 | Tail gas heater |
WO2012121696A1 (en) * | 2011-03-07 | 2012-09-13 | Aavid Thermalloy, Llc | Thermal transfer device with spiral fluid pathways |
US9127894B2 (en) * | 2011-04-13 | 2015-09-08 | Emitec Gesellschaft Fuer Emissiontechnologie Mbh | Device having a heat exchanger for a thermoelectric generator of a motor vehicle and motor vehicle having the device |
US20140033703A1 (en) * | 2011-04-13 | 2014-02-06 | Emitec Gesellschaft Fuer Emissionstechnologie Mbh | Device having a heat exchanger for a thermoelectric generator of a motor vehicle and motor vehicle having the device |
US20140202157A1 (en) * | 2011-05-02 | 2014-07-24 | Meir Shinnar | Thermal energy storage for combined cycle power plants |
US9540957B2 (en) * | 2011-05-02 | 2017-01-10 | The Research Foundation Of The City University Of New York | Thermal energy storage for combined cycle power plants |
WO2013028083A3 (en) * | 2011-08-25 | 2013-07-25 | Invention Mind Sp. Zo. O. | Oil heating boiler |
US20130112371A1 (en) * | 2011-11-04 | 2013-05-09 | Delphi Technologies, Inc. | Exhaust gas heat recovery heat exchanger having a lobed tube coil |
US8978745B2 (en) * | 2011-11-04 | 2015-03-17 | Delphi Technologies, Inc. | Exhaust gas heat recovery heat exchanger having a lobed tube coil |
CN104246201A (en) * | 2011-12-28 | 2014-12-24 | 杜齐克天梦有限责任公司 | Anti-pollution economiser device |
JP2015511291A (en) * | 2012-02-16 | 2015-04-16 | エーバーシュペッヒャー・エグゾースト・テクノロジー・ゲーエムベーハー・ウント・コンパニー・カーゲー | Steam generator, steam generation system, waste heat recovery device, and internal combustion engine |
WO2013120998A3 (en) * | 2012-02-16 | 2014-10-02 | Eberspächer Exhaust Technology GmbH & Co. KG | Steam generator for a rankine process |
US9140146B2 (en) * | 2012-03-15 | 2015-09-22 | Eberspächer Exhaust Technology GmbH & Co. KG | Steam generator for a rankine cycle |
DE102012204126A1 (en) * | 2012-03-15 | 2013-09-19 | Eberspächer Exhaust Technology GmbH & Co. KG | Steam generator for a Rankine process |
US20130239571A1 (en) * | 2012-03-15 | 2013-09-19 | Eberspächer Exhaust Technology GmbH & Co. KG | Steam generator for a rankine cycle |
DE102012007721B4 (en) | 2012-04-19 | 2022-02-24 | Thyssenkrupp Industrial Solutions Ag | Process gas cooler with lever-controlled process gas cooler flaps |
DE102012007721A1 (en) * | 2012-04-19 | 2013-10-24 | Thyssenkrupp Uhde Gmbh | Lever-controlled process gas cooler flaps |
WO2013156139A1 (en) * | 2012-04-19 | 2013-10-24 | Thyssenkrupp Uhde Gmbh | Process gas cooler having lever-controlled process gas cooler flaps |
EP2896802A4 (en) * | 2012-08-10 | 2016-06-01 | Futaba Ind Co Ltd | Exhaust heat recovery device |
CN103673676A (en) * | 2012-09-14 | 2014-03-26 | 埃贝斯佩歇废气技术合资公司 | Heat exchanger |
US9239001B2 (en) | 2012-09-14 | 2016-01-19 | Eberspächer Exhaust Technology GmbH & Co. KG | Heat exchanger |
EP2708708A1 (en) * | 2012-09-14 | 2014-03-19 | Eberspächer Exhaust Technology GmbH & Co. KG | Exhaust gas heat exchanger |
CN103670810A (en) * | 2012-09-14 | 2014-03-26 | 埃贝斯佩歇废气技术合资公司 | Exhaust gas heat exchanger |
EP2708711A1 (en) * | 2012-09-14 | 2014-03-19 | Eberspächer Exhaust Technology GmbH & Co. KG | Exhaust gas heat exchanger |
DE102012108944A1 (en) * | 2012-09-21 | 2014-05-28 | Bio-System Gesellschaft Für Anwendungen Biologischer Verfahren Mbh | Steam generator for producing steam used for combustion engine, has tube for conducting medium to be evaporated, that is arranged in inner space of boiler |
US20140208725A1 (en) * | 2013-01-30 | 2014-07-31 | Eberspächer Exhaust Technology GmbH & Co. KG | Heat exchanger of an internal combustion engine |
WO2014202942A1 (en) * | 2013-06-20 | 2014-12-24 | Boustead International Heaters Limited | Improvements in waste heat recovery units |
US11215406B2 (en) | 2013-06-20 | 2022-01-04 | Boustead International Heaters Limited | Waste heat recovery units |
US20150004552A1 (en) * | 2013-06-28 | 2015-01-01 | American Air Liquide, Inc. | Method and Heat Exchange System Utilizing Variable Partial Bypass |
US9828275B2 (en) * | 2013-06-28 | 2017-11-28 | American Air Liquide, Inc. | Method and heat exchange system utilizing variable partial bypass |
US20160298516A1 (en) * | 2013-12-19 | 2016-10-13 | Volvo Truck Corporation | An exhaust gas treatment system to be fitted on a chassis of an automotive vehicle |
US11319851B2 (en) * | 2013-12-19 | 2022-05-03 | Volvo Truck Corporation | Exhaust gas treatment system to be fitted on a chassis of an automotive vehicle |
US9964075B2 (en) * | 2014-05-07 | 2018-05-08 | Benteler Automobiltechnik Gmbh | Exhaust-gas heat exchanger with bypass pipe |
US20150322899A1 (en) * | 2014-05-07 | 2015-11-12 | Benteler Automobiltechnik Gmbh | Exhaust-gas heat exchanger with bypass pipe |
US10317143B2 (en) * | 2014-06-30 | 2019-06-11 | Modine Manufacturing Company | Heat exchanger and method of making the same |
US20170097194A1 (en) * | 2014-06-30 | 2017-04-06 | Modine Manufacturing Company | Heat Exchanger and Method of Making the Same |
US10060680B2 (en) | 2014-06-30 | 2018-08-28 | Modine Manufacturing Company | Heat exchanger and method of making the same |
US20160146455A1 (en) * | 2014-11-21 | 2016-05-26 | Honeywell International Inc. | Fuel-air-flue gas burner |
US9631808B2 (en) * | 2014-11-21 | 2017-04-25 | Honeywell International Inc. | Fuel-air-flue gas burner |
US9835356B1 (en) * | 2015-02-06 | 2017-12-05 | Sioux Corporation | Fluid heating apparatus utilizing at least two fluid paths |
US10371413B2 (en) | 2015-04-06 | 2019-08-06 | Central Boiler, Inc. | Boiler with access to heat exchangers |
US10151476B2 (en) | 2015-04-06 | 2018-12-11 | Central Boiler Inc. | Boiler with access to heat exchangers |
EP3159646B2 (en) † | 2015-10-20 | 2021-12-29 | Borsig GmbH | Heat exchanger |
US20170248050A1 (en) * | 2016-02-26 | 2017-08-31 | Hanon Systems | Rolled fin spiral egr cooler |
US10590816B2 (en) * | 2016-02-26 | 2020-03-17 | Hanon Systems | Rolled fin spiral EGR cooler |
US11359866B2 (en) * | 2017-02-24 | 2022-06-14 | Intellihot, Inc. | Multi-coil heat exchanger |
US10514206B2 (en) * | 2017-02-24 | 2019-12-24 | Intellihot, Inc. | Multi-coil heat exchanger |
CN106996705A (en) * | 2017-05-05 | 2017-08-01 | 张家港格林沙洲锅炉有限公司 | The cigarette journey structure of marine heat recovery boiler |
DE102017209728A1 (en) | 2017-06-08 | 2018-12-13 | Volkswagen Aktiengesellschaft | Device for heat recovery |
DE102017209725A1 (en) * | 2017-06-08 | 2018-12-13 | Volkswagen Aktiengesellschaft | Device for heat recovery from a heating fluid |
DE102017209727A1 (en) * | 2017-06-08 | 2018-12-13 | Volkswagen Aktiengesellschaft | Device for heat recovery |
WO2018224296A1 (en) | 2017-06-08 | 2018-12-13 | Volkswagen Aktiengesellschaft | Apparatus for heat recovery |
US10753644B2 (en) | 2017-08-04 | 2020-08-25 | A. O. Smith Corporation | Water heater |
CN111492132A (en) * | 2017-12-15 | 2020-08-04 | 通用电气公司 | Heat regenerator for gas turbine engine |
WO2019197907A3 (en) * | 2018-04-13 | 2019-11-14 | Flowserve Management Company | Fluid coolers, heat exchangers, seal assemblies and systems including fluid coolers or heat exchangers and related methods |
CN112166292A (en) * | 2018-04-13 | 2021-01-01 | 芙罗服务管理公司 | Fluid cooler, heat exchanger, seal assembly, and system including fluid cooler or heat exchanger and related methods |
US11703286B2 (en) | 2018-04-13 | 2023-07-18 | Flowserve Pte. Ltd. | Fluid coolers, heat exchangers, seal assemblies and systems including fluid coolers or heat exchangers and related methods |
US20200248087A1 (en) * | 2019-02-05 | 2020-08-06 | Saudi Arabian Oil Company | Producing Synthetic Gas |
US11807822B2 (en) * | 2019-02-05 | 2023-11-07 | Saudi Arabian Oil Company | Producing synthetic gas |
US11353270B1 (en) * | 2019-04-04 | 2022-06-07 | Advanced Cooling Technologies, Inc. | Heat pipes disposed in overlapping and nonoverlapping arrangements |
US11867428B2 (en) | 2020-04-28 | 2024-01-09 | A.O. Smith Corporation | Heat exchange pipe, heat exchanger and water heating apparatus |
EP4047296A1 (en) * | 2021-02-17 | 2022-08-24 | Pratt & Whitney Canada Corp. | Fluid cooler for a gas turbine engine |
US11530645B2 (en) | 2021-02-17 | 2022-12-20 | Pratt & Whitney Canada Corp. | Fluid cooler for a gas turbine engine |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20050133202A1 (en) | Heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger | |
CA2466564A1 (en) | A heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger | |
US7216696B2 (en) | External flue heat exchangers | |
RU2438073C2 (en) | Condensate heat exchanger having two primary tube banks and one secondary tube bank | |
US9476610B2 (en) | Hot fluid production device including a condensing heat exchanger | |
CA2123356C (en) | Ultra-high efficiency on-demand water heater | |
CA2367726C (en) | External flue heat exchangers | |
WO2014116805A2 (en) | Heat exchanger having a compact design | |
CA2999185C (en) | Heat exchanger with dual concentric tube rings | |
US4621592A (en) | Boiler having improved heat absorption | |
AU2006203707C1 (en) | Looped system fuel-fired fluid heating/storage device | |
JPH0642812A (en) | Heat exchanger for gas boiler | |
EP2504632A2 (en) | Double tubing condensation exchanger for heating water and/or for producing sanitary hot water | |
RU2386905C1 (en) | Heat generator | |
US20030056944A1 (en) | External flue heat exchangers | |
CN212082096U (en) | Coil pipe type heat exchange device | |
US4120267A (en) | Tube and plate heat exchanger | |
KR100363719B1 (en) | Spiral Wound Heat Transferring Equipment on the Single Passage for the Super-heater | |
US20230194179A1 (en) | Heat exchanger with tube bundle comprising at least two sections | |
WO2019169397A1 (en) | Multisection tubeless heat exchanger, fluid heating system including the same, and methods of manufacture thereof | |
JP2988363B2 (en) | Boiler with smoke tube | |
JP2023517635A (en) | Boiler and how to operate the boiler | |
CN117109181A (en) | Phase change heating furnace fully utilizing flue gas waste heat | |
US20120073792A1 (en) | Apparatus for reclaiming waste heat from a heating device flue pipe | |
KR960029759A (en) | heat transmitter |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: AALBORG INDUSTRIES A/S, DENMARK Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:JORGENSEN, LARS SKYTTE;SPENDER-ANDERSEN, NIELS;BODIL NIELSEN, MOSEKAER IRENE;REEL/FRAME:015771/0546;SIGNING DATES FROM 20050222 TO 20050228 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |