EP1876390A1 - Method of producing steam in a gas tube steam boiler and gas tube steam boiler for implementing said method - Google Patents
Method of producing steam in a gas tube steam boiler and gas tube steam boiler for implementing said method Download PDFInfo
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- EP1876390A1 EP1876390A1 EP06388049A EP06388049A EP1876390A1 EP 1876390 A1 EP1876390 A1 EP 1876390A1 EP 06388049 A EP06388049 A EP 06388049A EP 06388049 A EP06388049 A EP 06388049A EP 1876390 A1 EP1876390 A1 EP 1876390A1
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- Prior art keywords
- steam
- flow
- gas
- distance
- wall
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- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/0206—Heat exchangers immersed in a large body of liquid
- F28D1/0213—Heat exchangers immersed in a large body of liquid for heating or cooling a liquid in a tank
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
- F22B1/1884—Hot gas heating tube boilers with one or more heating tubes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B9/00—Steam boilers of fire-tube type, i.e. the flue gas from a combustion chamber outside the boiler body flowing through tubes built-in in the boiler body
- F22B9/02—Steam boilers of fire-tube type, i.e. the flue gas from a combustion chamber outside the boiler body flowing through tubes built-in in the boiler body the boiler body being disposed upright, e.g. above the combustion chamber
- F22B9/04—Steam boilers of fire-tube type, i.e. the flue gas from a combustion chamber outside the boiler body flowing through tubes built-in in the boiler body the boiler body being disposed upright, e.g. above the combustion chamber the fire tubes being in upright arrangement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22G—SUPERHEATING OF STEAM
- F22G3/00—Steam superheaters characterised by constructional features; Details of component parts thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22G—SUPERHEATING OF STEAM
- F22G3/00—Steam superheaters characterised by constructional features; Details of component parts thereof
- F22G3/006—Steam superheaters with heating tubes
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- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
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- 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
- F28D7/16—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 arranged in parallel spaced relation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
Abstract
A gas tube steam boiler comprising a heat exchange compartment (2) filled with water forming a water surface (2A), a steam head space (8) above the water surface and delimited by a cylindrical wall (1) with a substantially vertical axis (10) and a top plate (4), a steam outlet (6) communicating with the steam head space (8), gas tubes (3) extending through the heat exchange compartment (2) and the steam head space (8), means for supplying heated gas to the gas tubes (3) for generating a flow of steam from said water surface (2A) by heat exchange between the gas tubes (3) and the water, and a steam flow conduit (7',7") arranged in the steam head space (8) for conducting the flow of steam from the water surface (2A) to the steam outlet (6), at least one of the gas tubes (3) extending transversely through the conduit such that the flow of steam flows in a direction transverse, preferably generally orthogonal, to the gas tubes (3), the configuration of the conduit being such that more than half, preferably substantially all, of the steam in the flow is constrained to flow along a flow path which when projected on a horizontal surface has a length at least equal to the shortest distance between a first point of the wall (1) and a second point of the wall (1) horizontally opposite the first point, said distance, in the case the wall (1) is circular cylindrical, being the diameter D of the circular cylindrical wall.
Description
- The present invention relates to a method of producing steam in a gas tube steam boiler and a gas tube steam boiler for implementing said method.
- In connection with such a method and apparatus it is of importance to optimise the energy transfer from the gas tubes to the water and steam in order to reduce the overall size of the boiler for a given energy output. Typically, the primary design parameters are involving the input gas temperature, the exhaust gas temperature and the desired maximum energy output, i.e. feed water temperature, steam pressure, temperature and mass flow. Preferably, the steam should be dry or even more preferred superheated.
- From
US 1,546,665 it is known to provide a gas tube steam boiler with a baffle plate providing an annular opening along the boiler wall, whereby the steam flow from the water surface is restricted to flow from the water surface to the annular opening and from there to the centrally positioned steam outlet. In this construction a major part of the generated steam will only pass the gas tubes over a distance corresponding to approximately 1/2 of the diameter of the gas tube boiler leading to insufficient heat exchange between the gas tubes and the generated steam. - In particular, but not exclusively, for marine boilers, the size of the boiler is of great importance due to limited space available, and accordingly it is an object of the present invention to provide a method and an apparatus of the type in reference that allows reduction of the space requirements of a boiler.
- According to the invention this object is achieved by the method comprising the steps of
- providing a gas tube steam boiler comprising:
- a heat exchange compartment filled with water forming a water surface,
- a steam head space above said water surface and delimited by a cylindrical wall with a substantially vertical axis and a top plate,
- a steam outlet communicating with said steam head space,
- one or more gas tubes extending through said heat exchange compartment and said steam head space,
- supplying heated gas to said gas tubes for generating a flow of steam from said water surface by heat exchange between said gas tubes and said water in said heat exchange compartment,
- causing said flow of steam to flow through said steam head space from said water surface to said steam outlet in such a manner that more than half, preferably substantially all, of the steam in said flow in said head space is constrained to flow in a direction transverse, preferably generally orthogonal, to said gas tubes along a flow path which when projected on a horizontal surface has a length at least equal to the shortest distance between a first point of said wall and a second point of said wall horizontally opposite said first point, said distance, in the case said wall is circular cylindrical, being the diameter of said circular cylindrical wall,
such that residual heat in said gas tubes is transferred to said flow of steam. - Hereby, the heat transfer from the gas tubes to the steam in the steam head space is significantly improved, whereby the efficiency of the boiler is increased and at the same time the produced steam has a higher quality by being dried and possibly superheated.
- In a currently preferred embodiment of the method according to the invention said horizontal projection of said flow path is at least two times said distance. In this way the contact between the gas tubes and the flow of steam from the water surface to the steam outlet is increased, thus increasing the heat transfer in the steam head space.
- In a currently preferred embodiment of the method according to the invention the steam outlet is located at a distance from the axis of the wall, preferably proximate to the wall of the head space, thus restricting the steam flow to flow sideways along all of the gas tubes before leaving through the steam outlet.
- In a currently preferred embodiment of the method according to the invention the horizontal projection of the flow path extends from proximate or at a first point on said wall past said axis to proximate or at a second point on said wall opposite said first point and preferably extends back from the second point and at least partways back to said first point. In this way the steam flow is caused to move past all of the gas tubes, preferably at least two times before leaving through the steam outlet steam outlet.
- In a currently preferred embodiment of the method according to the invention the steam flow velocity is lower when flowing from the second point towards the first point than when flowing from proximate said first point towards said second point, providing a relative high velocity, preferably approximately 15-30 m/s, more preferably 15-25 m/s over a part of the distance between the water surface and the steam outlet and to pass the gas tubes at a reduced velocity, preferably approximately 10-15 m/s over a subsequent part of the path from the water surface to the steam outlet, whereby the high velocity provides a turbulent flow around the gas tubes securing a high heat transfer and securing that possible droplets of water in the steam will hit the tubes and evaporate.
- In a currently preferred embodiment of the method according to the invention the hot gasses for the gas tubes are provided from a combustion chamber, combusting a fuel such as oil, carbon dust, natural gas, etc., however, also hot exhaust gasses from a gas turbine or an internal combustion motor and the like may be used. When using hot gasses from a combustion chamber, said combustion chamber may be provided in contact with the water in the heat exchange compartment, in order to deliver further heating to the water directly from the combustion chamber.
- In a second aspect the present invention relates to a gas tube steam boiler comprising
- a heat exchange compartment filled with water forming a water surface,
- a steam head space above said water surface and delimited by a cylindrical wall with a substantially vertical axis and a top plate,
- a steam outlet communicating with said steam head space,
- one or more gas tubes extending through said heat exchange compartment and said steam head space,
- means for supplying heated gas to said gas tubes for generating a flow of steam from said water surface by heat exchange between said gas tubes and said water in said heat exchange compartment,
- a steam flow conduit arranged in said steam head space for conducting said flow of steam from said water surface to said steam outlet, at least one of said gas tubes extending transversely through said conduit such that said flow of steam flows in a direction transverse, preferably generally orthogonal, to said gas tubes, the configuration of said conduit being such that more than half, preferably substantially all, of the steam in said flow is constrained to flow along a flow path which when projected on a horizontal surface has a length at least equal to the shortest distance between a first point of said wall and a second point of said wall horizontally opposite said first point, said distance, in the case said wall is circular cylindrical, being the diameter of said circular cylindrical wall.
- This gas tube steam boiler is particularly suited for carrying out the above method.
- In a third aspect the present invention relates to a gas tube steam boiler comprising
- a heat exchange compartment filled with water forming a water surface,
- a steam head space above said water surface and delimited by a circular cylindrical wall with a substantially vertical axis and a top plate,
- a steam outlet communicating with said steam head space,
- one or more gas tubes extending through said heat exchange compartment and said steam head space,
- means for supplying heated gas to said gas tubes for generating a flow of steam from said water surface by heat exchange between said gas tubes and said water in said heat exchange compartment,
- a steam flow conduit arranged in said steam head space for conducting said flow of steam from said water surface to said steam outlet and comprising:
- a first generally horizontal plate arranged at a vertical distance h1 below said top plate and having a first gap forming edge arranged at a distance from said wall to provide a first steam flow gap between said first plate and said wall.
- Preferred embodiments of the gas tube steam boilers in accordance with the second and third aspect of the present invention, the advantages of which will be evident from the following detailed description, are revealed in the subordinate claims 11-21 and 23-31.
- In the following the invention will be explained in more detail with reference to the embodiments shown solely by way of example in the drawings, where
- Fig. 1 schematically shows a vertical cross sectional view along A-A in a boiler in accordance with a preferred embodiment of the present invention,
- Fig 1a schematically shows the boiler in Fig. 1 seen from the top and indicating the lines along which the cross sectional views in Figs. 1 and 2 are taken,
- Fig. 2 schematically shows a vertical cross sectional view along B-B perpendicular to the one in Fig. 1,
- Fig. 3 schematically shows a perspective view of the baffle plate configuration,
- Fig. 4-7 show four different possible configurations of the boiler steam head space in accordance with the present invention.
- The gas tube steam boiler shown in Fig. 1 comprises a
heat exchange compartment 2 filled with water, said water forming awater surface 2a, and asteam head space 8 above said water surface and delimited by acylindrical wall 1 with a substantiallyvertical axis 10, atop plate 4 and a diameter D. Asteam outlet 6 is connected to thesteam head space 8 andseveral gas tubes 3 extend through theheat exchange compartment 2 and thesteam head space 8. Heated gas flows through thegas tubes 3 in order to generate a flow of steam from the water surface by heat exchange between thegas tubes 3 and the water in theheat exchange compartment 2. - In the embodiment shown in Figs. 1-3 and Fig. 5 the steam flow from the water surface is caused to flow along a conduit delimited by the
baffle plates 7', 7", whereby said steam is made to flow in a direction transverse to thegas tubes 3 and all of the steam in the flow is constrained to flow between the twobaffle plates 7', 7" in a horizontal direction and back between theupper baffle plate 7" and thetop plate 4 in an opposite horizontal direction and out through thesteam outlet 6. - As shown in Figs. 2 and 3 the two
baffle plates 7', 7" each covers a smaller area than the cross sectional area of thesteam head space 5 and the edges of the twobaffle plates 7', 7" are connected tovertical plates 9 extending from thetop plate 4 down to the lower baffle plate 7' in the vertical direction and in the horizontal direction all the way across between individual positions on the cylindrical wall of thesteam head space 5. - The
gas tubes 3 extend from the bottom of the boiler, possibly from acombustion chamber 14 as shown in Fig. 2 up through the water filledheat exchange compartment 2 and thesteam head space 5, where thegas tubes 3 extend through theplates 7', 7" and through holes in thetop plate 4, from where the gas leaves through agas exhaust 11. - Heat exchange between the gas tubes and the water will produce steam entering the
steam head space 5 at the water surface and the plate 7' forces the steam to move to the left as seen in Fig. 1 around a gap forming edge 12 and in between the twoplates 7', 7" moving to the right as seen in Fig. 1 and around agap forming edge 13 and moving between the plate 7' and thetop plate 4 to thesteam outlet 6. In this way the steam is forced to move in a direction transverse to thegas tubes 3 over a distance corresponding to approximately two times the diameter of theboiler 1. Minor leakage of steam between the openings in theplates 7', 7" and thegas tubes 3 will be no problem as the steam in these small gaps will come very close to the tube walls and be heated up here. In order to provide a sufficient heat exchange between the gas tubes and the flow of steam, more than half of all the steam in the flow in the head space is constrained to flow in a direction transverse, preferably generally orthogonal, to said gas tubes along a flow path, which when projected on a horizontal surface has a length at least equal to the diameter of the circular cylindrical wall. By this feature the present invention is distinguished over the above-mentionedUS 1, 546,665 , in which less than half of the steam flows over a distance corresponding to less than 3/4 of the diameter of the circular cylindrical wall. - When the steam leaves the water surface it will typically contain small water droplets, which, by the forced flow across the
gas tubes 3 with a relatively high flow velocity, will hit thegas tubes 3 and evaporate, and furthermore the relatively high velocity of the steam will provide a heat exchange between the steam and the gas tubes in thesteam head space 5, said heat exchange is increased compared to the traditional boiler construction in which the steam simply moves from the water surface to the steam outlet in a slow flow mainly parallel to thegas tubes 3 in an open steam head space withoutplate 7', 7". Furthermore, the distance between the water level and the top plate can be reduced, said distance normally being relatively high in order to avoid a high concentration of water droplets in the steam leaving thesteam outlet 6. - When the water in the
boiler 1 is not boiling, the water level inside the boiler corresponds to the level measured with different traditional equipment, such as pressure difference between two known levels, water level glasses, etc. However, the actual water level seen inside the boiler will rise because of the presence of a large amount of steam bubbles inside the water area, and the water level will be fluctuating more or less, dependent on the heat load and the steam pressure. The highest water level will be around thegas tubes 3 and accordingly the gas tubes are wetted by water up to this water level, which typically is about 250 mm above the measured water level, in the following named water surface in cold condition. - The total height h of the
steam head space 5 is subdivided into the distance h1 between thetop plate 4 and thefirst plate 7", the distance h2 between thefirst plate 7" and the second plate 7', and finally the distance h3 between the second plate 7' and the water surface in cold condition. - In a preferred embodiment the distances h1 and h2 are dimensioned in such a way that the steam velocity between the
top plate 4 and thefirst plate 7" is approximately 10-15 m/s and the steam velocity between the twoplates 7' and 7" is approximately 20-30 m/s., i.e. the distance h1 is approximately two times the distance h2. Under all circumstances the distance h3 should be sufficient to secure that during boiling at full load, the actual water level should be approximately 200 mm below the second plate 7'. - In the steam head space, as described above, the flow of the steam perpendicular to the
gas tubes 3 is relatively high between the twoplates 7', 7", a bit lower between thetop plate 4 and theplate 7" and even between the water surface and the plate 7' a certain cross flow relative to thegas tubes 3 will be present. The steam velocity provides a higher heat transfer coefficient from thegas tubes 3 to the steam compared to a traditional situation in which thesteam head space 5 transmits steam at a low velocity, substantially parallel to the tubes. Actually, the heat transfer is close to the same heat transfer that exists in the water filledheat exchange compartment 2 in which water is in direct contact with thegas tubes 3. - The produced steam is not only free of water droplets when it leaves the boiler through the
steam outlet 6, but it is actually superheated. This superheating ensures that no salts leave the boiler, resulting in that there will be no deposits in the steam pipe from the boiler to the user. Furthermore, a possible steam outlet valve after the steam outlets can be dimensioned to a higher steam velocity, which means that the size of the valve can be reduced, thus saving both space, weight and costs for said steam outlet valve. Furthermore, the total heating surface can be reduced due to increased heat transfer, which means reduced tube length, number of tubes, boiler height and thus both weight and cost price for the boiler. - In the following table process data for at gas tube steam boiler in accordance with the present invention are indicated.
Boiler steam capacity kg/h 3700 Working pressure of steam barg 6.5 Saturation point °C 167 Fuel flow (HFO) kg/h 250 Flue gas flow kg/h 3900 Smoke tube dimension mm ∅18x2 Number of smoke tubes pcs 300 Total tube length, furnace top plate to boiler top plate mm 1440 Boiler shell, inside diameter mm 01276 h1, distance between boiler top plate and upper baffle plate mm 125 h2, distance between the two baffle plates mm 75 h3, distance below lower baffle plate and measured water level (Normal Water Level) mm 450 Boiling up (wet heating surface above measured water level) mm 250 Wet tube length mm 1040 Max. steam velocity, 2. pass (between the two baffle plates) m/s 16 Max. steam velocity, 3. pass (between upper baffle plate and boiler top plate) m/s 10 Steam space volume load (to measured NWL) h-1 1100 Inlet gas temperature (leaving furnace) °C 1360 Gas velocity, tube inlet m/s 107 Gas temperature inside smoke tubes at actual water level (upper part of wet heating surface) °C 550 Outlet gas temperature °C 400 Outlet steam temperature °C 220 - The following table compares a traditionally dimensioned gas tube steam boiler indicated as standard, and a gas tube steam boiler in accordance with the present invention indicated as new. The two boilers have been designed for having the same steam capacity, thermal efficiency (i.e. same flue gas outlet temperature) and same pressure drop.
Description Unit Standard New Tube dimension mm 18x2 18x2 Number of tubes Pcs 375 300 Wet tube length mm 1370 1040 Length to normal water level (measured) mm 1120 790 Steam space to measured water level mm 840 650 Total tube length mm 1960 1440 Total tube length in boiler m 735 432 - It can be seen that the direct result of using the present invention is that approximately 40% of the tubes (approximately 240 kg) in the standard boiler design can be saved. Furthermore, the tube length and accordingly the boiler height is shortened by 520 mm, which with a boiler diameter of 1300 and a plate thickness of 12 mm provides a difference in plate weight of approximately 200 kg.
- Above the invention has been described in connection with a preferred embodiment, however, many modifications may be envisaged without departing from the following claims. Among such modifications are the omission of the second plate 7' leading to a more simplified construction, but, however, still providing a flow of the steam through the
steam head space 5 from the water surface to thesteam outlet 6 in such a manner that the majority of the steam in the flow in saidhead space 5 is constrained to flow in a direction transverse to the gas tubes along a flow path having a length corresponding to the diameter of theboiler 1. This possibility is shown in Fig. 4, and the above described preferred embodiment is schematically shown in Fig. 5. Other possibilities as shown in Fig. 6 and Fig. 7 provide a steam flow from the water surface to the steam outlet restricted by a first plate having a central hole for passing the steam and a second plate above said first plate, said second plate providing an annular opening along the boiler wall, whereby the steam flow is restricted to flow across the gas tubes, first in a radially outward direction and following in a radially inward direction towards the centrally positionedsteam outlet 6. - In the Fig. 7 embodiment the steam flow is restricted to a helically flow path by means of a helically shaped plate positioned between a central tube and the outer wall of the
boiler 1, said steam flow path again having a length corresponding to at least the distance between two opposite point of the wall of theboiler 1.
Claims (31)
- A method of generating steam comprising the steps of:- providing a gas tube steam boiler comprising:- a heat exchange compartment filled with water forming a water surface,- a steam head space above said water surface and delimited by a cylindrical wall with a substantially vertical axis and a top plate,- a steam outlet communicating with said steam head space,- one or more gas tubes extending through said heat exchange compartment and said steam head space,- supplying heated gas to said gas tubes for generating a flow of steam from said water surface by heat exchange between said gas tubes and said water in said heat exchange compartment,- causing said flow of steam to flow through said steam head space from said water surface to said steam outlet in such a manner that more than half, preferably substantially all, of the steam in said flow in said head space is constrained to flow in a direction transverse, preferably generally orthogonal, to said gas tubes along a flow path which when projected on a horizontal surface has a length at least equal to the shortest distance between a first point of said wall and a second point of said wall horizontally opposite said first point, said distance, in the case said wall is circular cylindrical, being the diameter of said circular cylindrical wall,
such that residual heat in said gas tubes is transferred to said flow of steam. - A method according to claim 1, wherein said residual heat in said gas tubes is transferred to said flow of steam to an extent that all the steam exiting said steam space through said steam outlet is super-heated.
- A method according to claim 1 or 2, wherein the length of said horizontal projection of said flow path is at least two times said distance.
- A method according to any of the preceding claims, wherein said steam outlet is located at a distance from said axis of said wall, preferably proximate to or in said wall.
- A method according to any of the preceding claims, wherein said horizontal projection of said flow path extends from proximate or at a first point on said wall past said axis to proximate or at a second point on said wall opposite said first point.
- A method according to claim 5, wherein said horizontal projection of said flow path extends back from said second point and at least partways back to said first point.
- A method according to claim 6, wherein the flow velocity of said flow is lower when flowing from said second point towards said first point than when flowing from proximate said first point towards said second point.
- A method according to claim 7, wherein the flow velocity of said flow is approximately 10-15 m/s when flowing from said second point towards said first point and preferably approximately 15-30 m/s, more preferably 15-25 m/s when flowing from proximate said first point towards said second point.
- A method according to any of the preceding claims, wherein said heated gas is supplied from any of the following sources:a) a combustion chamber,b) a gas turbine,c) an internal combustion motor, andd) a gas or oilfired engine used e.g. for ships propulsion or electricity production, heating processes, industrial and power plants.
- A gas tube steam boiler comprising:- a heat exchange compartment filled with water forming a water surface,- a steam head space above said water surface and delimited by a cylindrical wall with a substantially vertical axis and a top plate,- a steam outlet communicating with said steam head space,- one or more gas tubes extending through said heat exchange compartment and said steam head space,- means for supplying heated gas to said gas tubes for generating a flow of steam from said water surface by heat exchange between said gas tubes and said water in said heat exchange compartment,- a steam flow conduit arranged in said steam head space for conducting said flow of steam from said water surface to said steam outlet, at least one of said gas tubes extending transversely through said conduit such that said flow of steam flows in a direction transverse, preferably generally orthogonal, to said gas tubes, the configuration of said conduit being such that more than half, preferably substantially all, of the steam in said flow is constrained to flow along a flow path which when projected on a horizontal surface has a length at least equal to the shortest distance between a first point of said wall and a second point of said wall horizontally opposite said first point, said distance, in the case said wall is circular cylindrical, being the diameter of said circular cylindrical wall.
- A gas tube steam boiler according to claim 10, wherein said steam outlet is located at a distance from said axis of said wall, preferably in said top plate proximate to said wall.
- A gas tube steam boiler according to claim 10 or 11, wherein said steam flow conduit comprises a first generally horizontal plate arranged at a vertical distance h1 below said top plate and having a first gap forming edge arranged at a distance from said wall to provide a first steam flow gap between said first plate and said wall.
- A gas tube boiler according to claim 12, wherein said steam flow conduit comprises a second generally horizontal plate arranged at a vertical distance h2 below said first plate and having a second gap forming edge arranged at a distance from said wall to provide a second steam flow gap between said second plate and said wall.
- A gas tube boiler according to claim 13, wherein said first gap and said second gap are located opposite one another relative to said axis.
- A gas tube boiler according to any of the claims 12-14, wherein said steam outlet is located proximate or in said wall opposite said first gap relative to said axis.
- A gas tube boiler according to any of the claims 13-15, wherein the distance h1 is larger than the distance h2 such that the flow velocity of said steam flow is lower in the portion of said conduit located between said top plate and said first plate than said flow velocity in the portion of said conduit located between said first and second plates.
- A gas tube boiler according to claim 16, wherein all said gas tubes extend through said first and second plates.
- A gas tube boiler according to any of the claims 13-17, wherein said water surface in cold condition of said water is located at a vertical distance h below said top plate and said distance h1 is approximately 15-25%, preferably 18-22% of said distance h and said distance h2 is approximately 7-13%, preferably 8-12% of said distance h.
- A gas tube boiler according to any of the claims 12-18, wherein said first and second plates have smaller areas than the cross sectional area of said steam head space and the edges of said first and second plates extending from said first and second gap forming edges, respectively, are interconnected by means of vertical plates to form a tube.
- A gas tube boiler according to any of the claims 12-19, wherein said first plate has a smaller area than the cross sectional area of said steam head space and the edges of said first plate extending from said first gap forming edges, respectively, are interconnected with the top plate by means of vertical plates to form a tube.
- A gas tube boiler according to any of the claims 12-20, wherein said first and second plates are generally rectangular.
- A gas tube steam boiler comprising:- a heat exchange compartment filled with water forming a water surface,- a steam head space above said water surface and delimited by a circular cylindrical wall with a substantially vertical axis and a top plate,- a steam outlet communicating with said steam head space,- one or more gas tubes extending through said heat exchange compartment and said steam head space,- means for supplying heated gas to said gas tubes for generating a flow of steam from said water surface by heat exchange between said gas tubes and said water in said heat exchange compartment,- a steam flow conduit arranged in said steam head space for conducting said flow of steam from said water surface to said steam outlet and comprising:- a first generally horizontal plate arranged at a vertical distance h1 below said top plate and having a first gap forming edge arranged at a distance from said wall to provide a first steam flow gap between said first plate and said wall.
- A gas tube boiler according to claim 22, wherein said steam flow conduit comprises a second generally horizontal plate arranged at a vertical distance h2 below said first plate and having a second gap forming edge arranged at a distance from said wall to provide a second steam flow gap between said second plate and said wall.
- A gas tube boiler according to claim 23, wherein said first gap and said second gap are located opposite one another relative to said axis.
- A gas tube boiler according to any of the claims 22-24, wherein said steam outlet is located proximate or in said wall opposite said first gap relative to said axis.
- A gas tube boiler according to any of the claims 23-25, wherein the distance h1 is larger than the distance h2 such that the flow velocity of said steam flow is lower in the portion of said conduit located between said top plate and said first plate than said flow velocity in the portion of said conduit located between said first and second plates.
- A gas tube boiler according to any of the claims 23-26, wherein all said gas tubes extend through said first and second plates.
- A gas tube boiler according to any of the claims 23-27, wherein said water surface in cold condition of said water is located at a vertical distance h below said top plate and said distance h1 is approximately 15-25%, preferably 18-22% of said distance h and said distance h2 is approximately 7-13%, preferably 8-12% of said distance h.
- A gas tube boiler according to any of the claims 22-28, wherein said first and second plates have smaller areas than the cross sectional area of said steam head space and the edges of said first and second plates extending from said first and second gap forming edges, respectively, are interconnected by means of vertical plates to form a tube.
- A gas tube boiler according to any of the claims 22-29, wherein said first plate has a smaller area than the cross sectional area of said steam head space and the edges of said first plate extending from said first gap forming edges, respectively, are interconnected with the top plate by means of vertical plates to form a tube.
- A gas tube boiler according to any of the claims 22-30, wherein said first and second plates are generally rectangular.
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06388049A EP1876390A1 (en) | 2006-07-05 | 2006-07-05 | Method of producing steam in a gas tube steam boiler and gas tube steam boiler for implementing said method |
DK07764471.4T DK2044365T3 (en) | 2006-07-05 | 2007-07-05 | PROCEDURE FOR PRODUCING STEAM IN A GAS PIPE BOAT AND GAS PIPE BOAT |
CN2007800326447A CN101512223B (en) | 2006-07-05 | 2007-07-05 | Method of producing steam in a gas tube steam boiler and gas tube steam boiler for implementing said method |
KR1020097002269A KR101009212B1 (en) | 2006-07-05 | 2007-07-05 | Method of producing steam in a gas tube steam boiler and gas tube steam boiler for implementing said method |
PCT/DK2007/000342 WO2008003322A1 (en) | 2006-07-05 | 2007-07-05 | Method of producing steam in a gas tube steam boiler and gas tube steam boiler for implementing said method |
JP2009516904A JP2009541705A (en) | 2006-07-05 | 2007-07-05 | Steam generation method for gas pipe steam boiler and gas pipe steam boiler for implementing the above method |
EP07764471.4A EP2044365B1 (en) | 2006-07-05 | 2007-07-05 | Method of producing steam in a gas tube steam boiler and gas tube steam boiler |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06388049A EP1876390A1 (en) | 2006-07-05 | 2006-07-05 | Method of producing steam in a gas tube steam boiler and gas tube steam boiler for implementing said method |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1876390A1 true EP1876390A1 (en) | 2008-01-09 |
Family
ID=38016951
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06388049A Withdrawn EP1876390A1 (en) | 2006-07-05 | 2006-07-05 | Method of producing steam in a gas tube steam boiler and gas tube steam boiler for implementing said method |
EP07764471.4A Not-in-force EP2044365B1 (en) | 2006-07-05 | 2007-07-05 | Method of producing steam in a gas tube steam boiler and gas tube steam boiler |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07764471.4A Not-in-force EP2044365B1 (en) | 2006-07-05 | 2007-07-05 | Method of producing steam in a gas tube steam boiler and gas tube steam boiler |
Country Status (6)
Country | Link |
---|---|
EP (2) | EP1876390A1 (en) |
JP (1) | JP2009541705A (en) |
KR (1) | KR101009212B1 (en) |
CN (1) | CN101512223B (en) |
DK (1) | DK2044365T3 (en) |
WO (1) | WO2008003322A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2789909A1 (en) * | 2013-04-12 | 2014-10-15 | RETECH Spólka z o.o. | Steam generator |
CN109000214A (en) * | 2018-08-28 | 2018-12-14 | 郭召海 | The dedicated superheated steam generator in oil field and its technique for applying |
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US1546665A (en) * | 1921-06-18 | 1925-07-21 | Frank F Landis | Steam boiler |
FR809123A (en) * | 1935-11-19 | 1937-02-24 | Steam boiler | |
GB1140222A (en) * | 1965-02-12 | 1969-01-15 | Schmidt Sche Heissdampf | Improvements relating to gas coolers |
US3437077A (en) * | 1966-01-21 | 1969-04-08 | Babcock & Wilcox Co | Once-through vapor generator |
US4991408A (en) * | 1989-09-29 | 1991-02-12 | John Liszka | Adiabatic separator |
DE10237681A1 (en) * | 2002-08-16 | 2004-03-04 | Ritter Energie- Und Umwelttechnik Gmbh & Co. Kg | Plate-type heat exchanger for transferring heat between two fluids has first fluid flowing vertically downward between plates vertical plates, while second fluid flows in zigzag pattern past baffles |
Family Cites Families (7)
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CN2044684U (en) * | 1989-02-17 | 1989-09-20 | 孙继忠 | Steam purifying tank |
JP3126487B2 (en) | 1992-04-28 | 2001-01-22 | 東京エレクトロン株式会社 | Oxidation treatment equipment |
US5653282A (en) * | 1995-07-19 | 1997-08-05 | The M. W. Kellogg Company | Shell and tube heat exchanger with impingement distributor |
JP2000088478A (en) * | 1998-09-14 | 2000-03-31 | Osaka Gas Co Ltd | Heat exchanger |
CN2385220Y (en) * | 1999-06-25 | 2000-06-28 | 刘强 | Constant pressure vertical steam boiler |
JP4313605B2 (en) * | 2003-05-06 | 2009-08-12 | 株式会社神戸製鋼所 | Fluid cooler |
KR100530265B1 (en) * | 2005-05-17 | 2005-11-22 | 김도연 | A steam generator |
-
2006
- 2006-07-05 EP EP06388049A patent/EP1876390A1/en not_active Withdrawn
-
2007
- 2007-07-05 KR KR1020097002269A patent/KR101009212B1/en active IP Right Grant
- 2007-07-05 CN CN2007800326447A patent/CN101512223B/en not_active Expired - Fee Related
- 2007-07-05 WO PCT/DK2007/000342 patent/WO2008003322A1/en active Application Filing
- 2007-07-05 JP JP2009516904A patent/JP2009541705A/en active Pending
- 2007-07-05 DK DK07764471.4T patent/DK2044365T3/en active
- 2007-07-05 EP EP07764471.4A patent/EP2044365B1/en not_active Not-in-force
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1546665A (en) * | 1921-06-18 | 1925-07-21 | Frank F Landis | Steam boiler |
FR809123A (en) * | 1935-11-19 | 1937-02-24 | Steam boiler | |
GB1140222A (en) * | 1965-02-12 | 1969-01-15 | Schmidt Sche Heissdampf | Improvements relating to gas coolers |
US3437077A (en) * | 1966-01-21 | 1969-04-08 | Babcock & Wilcox Co | Once-through vapor generator |
US4991408A (en) * | 1989-09-29 | 1991-02-12 | John Liszka | Adiabatic separator |
DE10237681A1 (en) * | 2002-08-16 | 2004-03-04 | Ritter Energie- Und Umwelttechnik Gmbh & Co. Kg | Plate-type heat exchanger for transferring heat between two fluids has first fluid flowing vertically downward between plates vertical plates, while second fluid flows in zigzag pattern past baffles |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2789909A1 (en) * | 2013-04-12 | 2014-10-15 | RETECH Spólka z o.o. | Steam generator |
CN109000214A (en) * | 2018-08-28 | 2018-12-14 | 郭召海 | The dedicated superheated steam generator in oil field and its technique for applying |
CN109000214B (en) * | 2018-08-28 | 2024-04-02 | 新疆桑顿能源科技有限公司 | Special superheated steam generator for oil field and application process thereof |
Also Published As
Publication number | Publication date |
---|---|
KR20090031606A (en) | 2009-03-26 |
CN101512223A (en) | 2009-08-19 |
JP2009541705A (en) | 2009-11-26 |
EP2044365B1 (en) | 2013-05-15 |
EP2044365A1 (en) | 2009-04-08 |
DK2044365T3 (en) | 2013-08-12 |
CN101512223B (en) | 2011-12-07 |
KR101009212B1 (en) | 2011-01-19 |
WO2008003322A1 (en) | 2008-01-10 |
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