EP3406998B1 - Heat exchanger for molten salt steam generator in concentrated solar power plant - Google Patents
Heat exchanger for molten salt steam generator in concentrated solar power plant Download PDFInfo
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- EP3406998B1 EP3406998B1 EP17172695.3A EP17172695A EP3406998B1 EP 3406998 B1 EP3406998 B1 EP 3406998B1 EP 17172695 A EP17172695 A EP 17172695A EP 3406998 B1 EP3406998 B1 EP 3406998B1
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- fluid
- heat exchanger
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- straight
- shell
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- 150000003839 salts Chemical class 0.000 title claims description 30
- 239000012530 fluid Substances 0.000 claims description 86
- 238000009826 distribution Methods 0.000 claims description 11
- 239000007788 liquid Substances 0.000 claims description 7
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 6
- 239000000203 mixture Substances 0.000 claims description 5
- DGAQECJNVWCQMB-PUAWFVPOSA-M Ilexoside XXIX Chemical compound C[C@@H]1CC[C@@]2(CC[C@@]3(C(=CC[C@H]4[C@]3(CC[C@@H]5[C@@]4(CC[C@@H](C5(C)C)OS(=O)(=O)[O-])C)C)[C@@H]2[C@]1(C)O)C)C(=O)O[C@H]6[C@@H]([C@H]([C@@H]([C@H](O6)CO)O)O)O.[Na+] DGAQECJNVWCQMB-PUAWFVPOSA-M 0.000 claims description 4
- 229910052708 sodium Inorganic materials 0.000 claims description 4
- 239000011734 sodium Substances 0.000 claims description 4
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 3
- 239000001569 carbon dioxide Substances 0.000 claims description 3
- 238000007789 sealing Methods 0.000 claims description 3
- 238000001816 cooling Methods 0.000 claims description 2
- 238000012546 transfer Methods 0.000 description 11
- 238000013461 design Methods 0.000 description 9
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 8
- 210000003660 reticulum Anatomy 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 230000015556 catabolic process Effects 0.000 description 2
- 238000006731 degradation reaction Methods 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- AAQFSZFQCXLMNT-ACMTZBLWSA-N (3s)-3-amino-4-[[(2s)-1-methoxy-1-oxo-3-phenylpropan-2-yl]amino]-4-oxobutanoic acid;hydrochloride Chemical compound Cl.OC(=O)C[C@H](N)C(=O)N[C@H](C(=O)OC)CC1=CC=CC=C1 AAQFSZFQCXLMNT-ACMTZBLWSA-N 0.000 description 1
- 241000321453 Paranthias colonus Species 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000002860 competitive effect Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000013529 heat transfer fluid Substances 0.000 description 1
- 238000011835 investigation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910000510 noble metal Inorganic materials 0.000 description 1
- 230000003071 parasitic effect Effects 0.000 description 1
- 238000007711 solidification Methods 0.000 description 1
- 230000008023 solidification Effects 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 238000013517 stratification Methods 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
- 238000009827 uniform distribution Methods 0.000 description 1
- 238000013022 venting Methods 0.000 description 1
Images
Classifications
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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
- F28D7/06—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 having a single U-bend
-
- 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
- F22B1/006—Methods of steam generation characterised by form of heating method using solar heat
-
- 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
- F22B1/06—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being molten; Use of molten metal, e.g. zinc, as heat transfer medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B17/00—Water-tube boilers of horizontally-inclined type, e.g. the water-tube sets being inclined slightly with respect to the horizontal plane
- F22B17/02—Water-tube boilers of horizontally-inclined type, e.g. the water-tube sets being inclined slightly with respect to the horizontal plane built-up from water-tube sets in abutting connection with two header boxes in common for all sets, e.g. with flat header boxes
- F22B17/025—Water-tube boilers of horizontally-inclined type, e.g. the water-tube sets being inclined slightly with respect to the horizontal plane built-up from water-tube sets in abutting connection with two header boxes in common for all sets, e.g. with flat header boxes with combined inlet and outlet header boxes, e.g. connected by U-tubes or Field tubes
-
- 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
-
- 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
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
- F28D2021/0064—Vaporizers, e.g. evaporators
-
- 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
- F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
-
- 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
- F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
- F28F2009/226—Transversal partitions
-
- 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
- F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
- F28F2009/228—Oblique partitions
Definitions
- the present invention is related to the field of heat exchangers, in particular heat exchangers such as evaporators, superheaters, reheaters, and economizers intended to be used in thermal fluid steam generators such as Molten Salt Steam Generators (MSSG) of Concentrated Solar Power plants (CSP).
- heat exchangers such as evaporators, superheaters, reheaters, and economizers intended to be used in thermal fluid steam generators such as Molten Salt Steam Generators (MSSG) of Concentrated Solar Power plants (CSP).
- the CSP tower plants generally comprise one or more solar receivers which are situated at the apex of a central tower. These solar receivers are heated by concentrated incident solar rays and they generate a hot fluid that will be further used to produce high-pressure steam capable of driving a turbine and of producing electricity.
- the CSP tower plant has as main components, namely, at least a heliostat solar field, a solar receiver installed on the top of the tower, a steam generator, a steam turbine and a storage system.
- the molten salt is heated typically to 565 °C in the solar receiver and stored in the hot storage tank.
- the hot salt flows from the hot tank to the Molten Salt Steam Generator (MSSG) to generate steam which will be injected into the steam turbine.
- MSSG Molten Salt Steam Generator
- FIG. 1 diagrammatically shows the components of a typical so-called heat exchanger train for MSSG.
- the hot molten salt flows, from an inlet 100, through a reheater 101 and a superheater 104 to enter in an evaporator 102. Thereafter, the hot salt flows from the outlet of the evaporator 102 to the economizer 103 and further to the outlet 105.
- So-called "shell and tube” heat exchangers refer in prior art to a class of heat exchanger designs suitable for higher pressure applications.
- This type of heat exchanger is consisting of a large pressure vessel called a "shell” having a set of tubes, called “bundle”, inside it.
- a first fluid runs through the tubes while a second fluid flows inside the shell over the tubes, the first and the second fluid having different temperatures, with the aim of transferring heat from the second fluid to the first fluid or vice versa.
- FIG. 2 diagrammatically shows a straight-tube heat exchanger (two pass tube-side).
- the ends of each tube 21 are connected to water boxes or plenums 29 through holes provided in separating plates called 'tube sheets" 27.
- the tubes 21 may be straight, as depicted in FIG. 2 , or bent in "U" (U-tubes).
- the flow path of the second fluid is often determined by intermediate baffles 28 forming respective passages so that the second fluid flow changes its direction in passing from one passage to the next one.
- the baffles are usually under the form of partial circular segments or annular rings and disks, installed perpendicular to the longitudinal axis of the shell 22 to provide a zigzag flow of the second fluid.
- hair pin heat exchanger 1 has two shells 22 containing the straight part of U-tubes.
- the head of the hairpin contains the 180° U-bent part of the tubes.
- a hair pin heat exchanger according to the preamble of claim 1 is known from JP S60 4790A .
- the advantages of this hairpin design are :
- baffles mounted in the shell can have a specific shape intended to guide the fluid in a helical path.
- the heat transfer rate increases of about 10% compared with that of conventional segmental baffles for the same shell-side pressure drop ( J. Heat Transfer (2007), Vol. 129(10), 1425-1431 ).
- This pattern allows to reduce leakage streams occurring in segmental baffles and further to increase the heat transfer coefficient greatly ( J. Heat Transfer (2010), Vol. 132(10), 101801 ).
- the flow stratification and stagnant zone are avoided (according to calculations), which allows a complete draining and decreases fouling susceptibility (lower fouling resistance and lower heat transfer area).
- Document WO 2009/148822 discloses baffles mounted in the shell to guide the fluid into a helical flow pattern, with different helix angles when the baffle is proximate the inlet and the outlet respectively.
- Documents US 2,384,714 , US 2,693,942 , US 3,400,758 , US 4,493,368 and WO 2005/019758 each disclose each different kinds of baffles, but with the same aim of providing a helical flow pattern of the fluid.
- Document US 1,782,409 discloses a continuous helical baffle.
- forced-recirculation evaporator material and manufacturing costs are higher than those for natural-circulation evaporators due to the recirculation pump capital cost.
- the present invention aims to overcome the drawbacks of the heat exchangers of prior art intended for steam generators.
- the invention aims to obtain a reduced-size evaporator presenting high flexibility in terms of thermal gradient as well as improved efficiency thanks to optimized hydrodynamic salt flow leading to lower pressure drop, lower internal leakage (by-pass), improved heat transfer coefficient, lower tendency to foul, easily drainable molten salt, natural circulation (i.e. without circulation pump), long lifetime, and competitive cost.
- Another purpose of the present invention is to avoid the utilization of thick components such as current tube sheets necessary in the shell-and-tube classical heat exchangers leading to the drawback that a high pressure zone is adjacent a low pressure zone.
- a first aspect of the present invention relates to a hairpin heat exchanger having a first straight section, a second straight section and a bent section linking the first straight section and the second straight section, each straight section comprising a part of a first cylindrical shell or internal cylindrical shell and of a second cylindrical shell or external cylindrical shell, said first cylindrical shell being located inside said second cylindrical shell, both forming an intershell space enclosing a bundle of parallel U-bent tubes having each a first and a second straight part respectively located in said first and second straight section of the exchanger and a 180°-bent part located in said bent section of the exchanger, wherein, in use, a first fluid to be heated and vaporized is flowing, said external cylindrical shell being provided respectively at one end with an inlet and at another end with an outlet for a second fluid which is a hot thermal fluid, so that, in use, said second fluid is flowing in the intershell space and cooling down by exchanging heat with the first fluid flowing in the straight tubes, said intershell space enclosing also baffles to guide
- the hairpin heat exchanger also comprises one of the following characteristics or a suitable combination thereof:
- a second aspect of the invention relates to the use of the hairpin heat exchanger as described above, as an evaporator.
- a third aspect of the invention relates to the use of the hairpin heat exchanger as described above, as a superheater.
- a fourth aspect of the invention relates to the use of the hairpin heat exchanger as described above, as a reheater or an economizer.
- a fifth aspect of the invention relates to the use of the evaporator, the superheater, the reheater and economizer as described above, making at least one heat exchanger train in a molten salt steam generator (MSSG).
- MSSG molten salt steam generator
- the superheater, the reheater and/or the economizer are running counter-current, while the evaporator is running co-current.
- the molten salt steam generator is a once-through or a forced circulation steam generator.
- the present invention relates to a new design for a horizontal hairpin heat exchanger 1, as depicted in FIG. 4 to 8 .
- the heat exchanger has a reciprocating flow between two fluids.
- a first fluid generally a mixture of water and water steam, circulates through a first bundle of parallel horizontal straight tubes sections 2 located in the first straight part of the hairpin and further through a second bundle of parallel horizontal straight tubes sections 2 located in the second straight part of the hairpin.
- the tubes 2 of the first bundle are connected to the tubes 2 of the second bundle by 180° bent tube sections located in the head of the hairpin, forming thereby U-bent tube sections.
- Supercritical carbon dioxide is another example of usable first fluid in the present invention.
- the straight tubes sections of the first bundle can discharge fluid into a bonnet through a thick(er) tube shell into which also end the straight tubes sections of the second bundle.
- the tubes have no U-bent tube sections.
- the bundle of tubes 2 in each straight part is located between an internal cylindrical shell 3 and an external cylindrical shell 4, as represented in FIG. 5 .
- the internal space 5 delimited by the two shells 3, 4 permits to hold a heat source, preferably a second fluid, within an annular flow path.
- This second fluid is a thermal fluid, for example molten salt(s) having been heated by the solar receivers at the apex of a CSP tower plant.
- the thermal fluid by having its flow in contact with the bundle(s) of tubes 2, will transfer heat to the parallel-flowing first fluid running through the tubes 2.
- the first fluid and the second fluid can be co-current or counter-current, without departing from the scope of the present invention.
- the heat source or the second fluid can be any thermal fluid such as water, thermal oil, liquid sodium, fluidized bed, etc.
- the external cylindrical shell 4, or a distribution jacket coupled therewith is provided at one end with an inlet nozzle 6, respectively an outlet nozzle 6, through which the thermal fluid enters into, respectively leaves the heat exchanger 1.
- an outlet nozzle 7, respectively inlet nozzle 7, is provided at another end of the external cylindrical shell 4 in order to discharge the cooled thermal fluid, respectively admit the hot fluid.
- the thermal fluid is uniformly distributed on the shell at 360° (inlet, circulation, fluid temperature) thanks to a distribution jacket located at the inlet nozzle of the heat exchanger (see below).
- space 5 is provided in the straight parts of the hairpin exchanger with an enclosed continuous helical baffle 8 allowing to guide the flow of the thermal fluid.
- the thermal fluid then helically flows in the heat exchanger, which is for example an evaporator running under natural circulation, between the internal and the external shell, according to an annular flow path.
- the continuous helical baffle configuration ensures a gentle flowing of the second fluid, without any sharp direction change or dead zones as in the exchangers having flow-perpendicular baffles. In this manner, the heat transfer rate is greatly increased and the pressure drop is greatly lowered compared with that of exchangers with conventional segment baffles (see above).
- the internal cylindrical shell 3 and the baffles 8 can be welded or bolted. Further a sealing means can be provided between the external shell 4 and the baffles 8 to avoid parasitic streams.
- the annular bundle of parallel straight tubes 2 is connected, via suitably bent tubes 11, located outside the internal and the external shells 3, 4 to at least one cylindrical linear header 9, 10.
- the header axis is orthogonal to the hairpin exchanger axis.
- the bundle of straight tubes 2 is connected to at least a first cylindrical linear header 9, or entry header 9, which feeds the straight tubes 2 with the first fluid, while, at a second end of the exchanger, the first fluid which is running inside the bundle of tubes 2 is collected by at least a second cylindrical linear header 10, or exit header 10, from the bundle of tubes 2.
- the need of more than one entry header 9 or exit header 10 may appear when there is a large number of tubes 2 in the bundle.
- the bundle of straight tubes 2 is connected, either to the entry header 9 or to the exit header 10 by suitably bent tubes 11, in an area which is outside the internal and external shells 3, 4 of the hairpin exchanger.
- the use of tube sheets and/or high pressure spherical collectors, bonnets and headers, as in the so-called "shell-and-tube” heat exchangers of prior art, is avoided in the present invention because it is simply replaced by the use of cylindrical headers moved outside of the hairpin heat exchanger.
- the first fluid usually water
- the first fluid is generally under high pressure in quasi-spherical vessels or plenums.
- the salt flowing around the tube bundles is maintained under much lower pressure, requiring very thick tube sheets to withstand the pressure difference.
- the invention configuration provides prolongated tubes connected to standard headers (cylindrical, spherical, etc.) at the ends of the exchanger, in which the high pressure fluid is circulating. This allows to reduce the thickness of the tube sheets, if any, the pressure being limited. More specifically, in the rectangular section on FIG.7 , one sees that the pressure drop supported by the tube sheet 16 is governed by the difference of the external (air) pressure 12 and the internal thermal fluid pressure 13.
- a tube sheet is preferably used under the form of a elliptical tube sheet 16 or the like, having orifices or passages 17 for the parallel tubes 2.
- the tubes 2 are welded to the elliptical tube sheet 16 only with the sole purpose to ensure fluid tightness.
- These elliptical tube sheets 16 advantageously have lower thickness than prior art flat tube sheets for the reasons explained above.
- Thick vessel walls or headers are not suited for accepting higher temperature gradients and are more subject to fatigue leading to shorter lifetime of the heat exchanger.
- the present invention provides extended lifetime of the heat exchanger components.
- FIG. 7 also shows a detailed view for an embodiment of the entry/exit distribution jacket 30 from the fluid inlet/outlet 6, 7 into the hairpin heat exchanger.
- a uniform distribution of the second fluid at its entry/exit in the heat exchanger is ensured by a series of distribution openings 31 located at 360° over the internal side of the distribution jacket 30, preferably in a first turn 32 of the helical baffle 8.
- the present invention is flexible and intended to be applied to a series of heat exchanger design used in MSSG technology, such as reheater, superheater, preheater and evaporator devices, wherein all the common components are made according to the generic heat exchanger design of the invention.
- a hot molten salt with decreasing temperature flows for example firstly in parallel through a reheater and a superheater to recombine and enter into the evaporator and further in the preheater/economizer in series.
- hot molten salt is entering the system at high temperature, for example 563°C and certainly below 565°C which is the degradation temperature for the usal molten salts.
- the thermal fluid can withstand a temperature up to 700°C. All metal parts are advantageously made of stainless steel or noble metals which can withstand temperatures up to 600°C and above.
- Cold salt leaves the preheater at a temperature typically in the range of 290-300°C, or above a minimum temperature which is either the solidification temperature of the heat transfer fluid (as low as 240°C for the molten salts such as sodium derivatives).
- a thermal fluid e.g. thermal oil
- molten salt with an operating temperature range in this case going for example from 80°C (condensation and/or cristallization temperature) to 380°C (example of degradation temperature).
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Description
- The present invention is related to the field of heat exchangers, in particular heat exchangers such as evaporators, superheaters, reheaters, and economizers intended to be used in thermal fluid steam generators such as Molten Salt Steam Generators (MSSG) of Concentrated Solar Power plants (CSP).
- It is known that the CSP tower plants generally comprise one or more solar receivers which are situated at the apex of a central tower. These solar receivers are heated by concentrated incident solar rays and they generate a hot fluid that will be further used to produce high-pressure steam capable of driving a turbine and of producing electricity.
- More specifically the CSP tower plant has as main components, namely, at least a heliostat solar field, a solar receiver installed on the top of the tower, a steam generator, a steam turbine and a storage system. In molten salt technology, the molten salt is heated typically to 565 °C in the solar receiver and stored in the hot storage tank. When a production of electricity is required, the hot salt flows from the hot tank to the Molten Salt Steam Generator (MSSG) to generate steam which will be injected into the steam turbine.
-
FIG. 1 diagrammatically shows the components of a typical so-called heat exchanger train for MSSG. The hot molten salt flows, from aninlet 100, through areheater 101 and asuperheater 104 to enter in anevaporator 102. Thereafter, the hot salt flows from the outlet of theevaporator 102 to theeconomizer 103 and further to theoutlet 105. - So-called "shell and tube" heat exchangers refer in prior art to a class of heat exchanger designs suitable for higher pressure applications. This type of heat exchanger is consisting of a large pressure vessel called a "shell" having a set of tubes, called "bundle", inside it. A first fluid runs through the tubes while a second fluid flows inside the shell over the tubes, the first and the second fluid having different temperatures, with the aim of transferring heat from the second fluid to the first fluid or vice versa.
- There are many variations on the shell and tube design. As an example,
FIG. 2 diagrammatically shows a straight-tube heat exchanger (two pass tube-side). The ends of eachtube 21 are connected to water boxes or plenums 29 through holes provided in separating plates called 'tube sheets" 27. Thetubes 21 may be straight, as depicted inFIG. 2 , or bent in "U" (U-tubes). - To provide an improved heat exchange between the two fluids, the flow path of the second fluid is often determined by
intermediate baffles 28 forming respective passages so that the second fluid flow changes its direction in passing from one passage to the next one. The baffles are usually under the form of partial circular segments or annular rings and disks, installed perpendicular to the longitudinal axis of theshell 22 to provide a zigzag flow of the second fluid. - A prior art alternative of the above design, depicted in
FIG. 3 , is the horizontal hairpin heat exchanger. Hairpin heat exchanger 1 has twoshells 22 containing the straight part of U-tubes. The head of the hairpin contains the 180° U-bent part of the tubes. A hair pin heat exchanger according to the preamble ofclaim 1 is known fromJP S60 4790A - no need for a joint expansion system, as thermal expansion is naturally managed by the hairpin design ;
- easier draining and venting of the exchanger owing to the straight tubes and to the horizontal position of the exchanger.
- Different concepts of steam generator are already known. A synthesis of these different concepts is reported in the Sandia report 93-7084 "Investigation of thermal storage and steam generator issues, Bechtel Corporation", in which are listed advantages and drawbacks of the existing steam generators.
- In order to improve efficiency of the heat transfer in the heat exchangers, it is known since the 1920s that baffles mounted in the shell can have a specific shape intended to guide the fluid in a helical path. Moreover, with a continuous helical baffle, the heat transfer rate increases of about 10% compared with that of conventional segmental baffles for the same shell-side pressure drop (J. Heat Transfer (2007), Vol. 129(10), 1425-1431). This pattern allows to reduce leakage streams occurring in segmental baffles and further to increase the heat transfer coefficient greatly (J. Heat Transfer (2010), Vol. 132(10), 101801). Also, the flow stratification and stagnant zone are avoided (according to calculations), which allows a complete draining and decreases fouling susceptibility (lower fouling resistance and lower heat transfer area).
- Document
WO 2009/148822 discloses baffles mounted in the shell to guide the fluid into a helical flow pattern, with different helix angles when the baffle is proximate the inlet and the outlet respectively. DocumentsUS 2,384,714 ,US 2,693,942 ,US 3,400,758 ,US 4,493,368 andWO 2005/019758 each disclose each different kinds of baffles, but with the same aim of providing a helical flow pattern of the fluid. DocumentUS 1,782,409 discloses a continuous helical baffle. - The current solutions are not satisfactory for example in terms of thermal gradient flexibility, efficiency (pressure drop, heat transfer coefficient), drainability, natural circulation, etc. and newly designed steam generator and/or individual heat exchangers thereof should meet technical requirements such as :
- improved thermal efficiency by reducing internal leakages and bypass streams ;
- improved pressure drop by reducing local stream obstacles ;
- improved ramp-up capability ;
- improved reliability ;
- improved fouling behavior, etc.
- Moreover forced-recirculation evaporator material and manufacturing costs are higher than those for natural-circulation evaporators due to the recirculation pump capital cost.
- The present invention aims to overcome the drawbacks of the heat exchangers of prior art intended for steam generators.
- In particular, the invention aims to obtain a reduced-size evaporator presenting high flexibility in terms of thermal gradient as well as improved efficiency thanks to optimized hydrodynamic salt flow leading to lower pressure drop, lower internal leakage (by-pass), improved heat transfer coefficient, lower tendency to foul, easily drainable molten salt, natural circulation (i.e. without circulation pump), long lifetime, and competitive cost.
- Another purpose of the present invention is to avoid the utilization of thick components such as current tube sheets necessary in the shell-and-tube classical heat exchangers leading to the drawback that a high pressure zone is adjacent a low pressure zone.
- A first aspect of the present invention relates to a hairpin heat exchanger having a first straight section, a second straight section and a bent section linking the first straight section and the second straight section, each straight section comprising a part of a first cylindrical shell or internal cylindrical shell and of a second cylindrical shell or external cylindrical shell, said first cylindrical shell being located inside said second cylindrical shell, both forming an intershell space enclosing a bundle of parallel U-bent tubes having each a first and a second straight part respectively located in said first and second straight section of the exchanger and a 180°-bent part located in said bent section of the exchanger, wherein, in use, a first fluid to be heated and vaporized is flowing, said external cylindrical shell being provided respectively at one end with an inlet and at another end with an outlet for a second fluid which is a hot thermal fluid, so that, in use, said second fluid is flowing in the intershell space and cooling down by exchanging heat with the first fluid flowing in the straight tubes, said intershell space enclosing also baffles to guide the second fluid, wherein the bundle of parallel U-bent tubes is extended out of the exchanger and connected, via bent tubes, respectively beyond an end of the internal shell and of the external shell at the first straight section to a first header distributing the first fluid to the bundle of straight tubes and beyond an end of the internal shell and of the external shell at the second straight section to a second header collecting the first fluid under the form of liquid, vapor or a mixture liquid /vapor from the bundle of straight tubes.
- According to preferred embodiments of the invention, the hairpin heat exchanger also comprises one of the following characteristics or a suitable combination thereof:
- the hairpin heat exchanger is horizontal and the flow of the second fluid with respect to the flow of the first fluid therein is either co-current or counter-current;
- the first header and the second header are straight and cylindrical, or spherical ;
- said first fluid is a fluid comprising feedwater or supercritical carbon dioxide;
- said second fluid is a molten salt or a mixture of molten salts, a thermal oil or liquid sodium ;
- the baffles are under the form of a continuous helical baffle ;
- the baffles are assembled, preferably welded or bolted, to the internal cylindrical shell ;
- a tube sheet is provided between the first header, the second header respectively, and the hairpin section of the exchanger containing the internal and external cylindrical shells ;
- the tube sheet is of elliptical shape and is provided with passageways for allowing sealed passage of the U-bent tubes through the tube sheet;
- a sealing means is provided between the external shell and the baffles ;
- the hairpin exchanger is equipped with a distribution jacket for uniformly feeding the second fluid from the thermal fluid inlet to the heat exchanger;
- the distribution jacket has a plurality of openings distributed at 360° over an internal face thereof, said openings preferably feeding the second fluid into a first turn of the helical baffle.
- A second aspect of the invention relates to the use of the hairpin heat exchanger as described above, as an evaporator.
- A third aspect of the invention relates to the use of the hairpin heat exchanger as described above, as a superheater.
- A fourth aspect of the invention relates to the use of the hairpin heat exchanger as described above, as a reheater or an economizer.
- A fifth aspect of the invention relates to the use of the evaporator, the superheater, the reheater and economizer as described above, making at least one heat exchanger train in a molten salt steam generator (MSSG). Advantageously, the superheater, the reheater and/or the economizer are running counter-current, while the evaporator is running co-current.
- Still under the scope of the present invention, the molten salt steam generator is a once-through or a forced circulation steam generator.
-
-
FIG.1 diagrammatically represents the components of a typical heat exchanger train for a Molten Salt Steam Generator. -
FIG. 2 schematically represents an embodiment for a "shell-and-tube" straight tube heat exchanger according to prior art. -
FIG. 3 represents a perspective view of a horizontal haipin generator of prior art. -
FIG. 4A and 4B respectively show a plane view and an elevation view for a preferred embodiment of a heat exchanger according to the present invention. -
FIG. 5 is a longitudinal cross-sectional view of the heat exchanger according to the embodiment ofFIG. 4 . -
FIG. 6A and 6B respectively show views corresponding toFIG. 4 but with a supporting system of the heat exchanger. -
FIG. 7 is a longitudinal cross-sectional detailed view of the exchanger according to the invention, focusing on the elliptical tube sheet. -
FIG. 8A and 8B respectively show a perspective view and a cross sectional view of the above-mentioned elliptical tube sheet. - The present invention relates to a new design for a horizontal
hairpin heat exchanger 1, as depicted inFIG. 4 to 8 . - The heat exchanger has a reciprocating flow between two fluids. A first fluid, generally a mixture of water and water steam, circulates through a first bundle of parallel horizontal
straight tubes sections 2 located in the first straight part of the hairpin and further through a second bundle of parallel horizontalstraight tubes sections 2 located in the second straight part of the hairpin. Thetubes 2 of the first bundle are connected to thetubes 2 of the second bundle by 180° bent tube sections located in the head of the hairpin, forming thereby U-bent tube sections. - Supercritical carbon dioxide is another example of usable first fluid in the present invention.
- According to one alternate embodiment, the straight tubes sections of the first bundle can discharge fluid into a bonnet through a thick(er) tube shell into which also end the straight tubes sections of the second bundle. Thus, according to this particular embodiment the tubes have no U-bent tube sections.
- According to the invention, the bundle of
tubes 2 in each straight part is located between an internalcylindrical shell 3 and an externalcylindrical shell 4, as represented inFIG. 5 . - The
internal space 5 delimited by the twoshells tubes 2, will transfer heat to the parallel-flowing first fluid running through thetubes 2. The first fluid and the second fluid can be co-current or counter-current, without departing from the scope of the present invention. Similarly the heat source or the second fluid can be any thermal fluid such as water, thermal oil, liquid sodium, fluidized bed, etc. - As illustrated by
FIG. 6 , the externalcylindrical shell 4, or a distribution jacket coupled therewith is provided at one end with aninlet nozzle 6, respectively anoutlet nozzle 6, through which the thermal fluid enters into, respectively leaves theheat exchanger 1. Similarly, anoutlet nozzle 7, respectivelyinlet nozzle 7, is provided at another end of the externalcylindrical shell 4 in order to discharge the cooled thermal fluid, respectively admit the hot fluid. - Advantageously, as mentioned above, the thermal fluid is uniformly distributed on the shell at 360° (inlet, circulation, fluid temperature) thanks to a distribution jacket located at the inlet nozzle of the heat exchanger (see below).
- In order to improve the efficiency of heat transfer, as shown in
FIG. 6 ,space 5 is provided in the straight parts of the hairpin exchanger with an enclosed continuoushelical baffle 8 allowing to guide the flow of the thermal fluid. The thermal fluid then helically flows in the heat exchanger, which is for example an evaporator running under natural circulation, between the internal and the external shell, according to an annular flow path. The continuous helical baffle configuration ensures a gentle flowing of the second fluid, without any sharp direction change or dead zones as in the exchangers having flow-perpendicular baffles. In this manner, the heat transfer rate is greatly increased and the pressure drop is greatly lowered compared with that of exchangers with conventional segment baffles (see above). - According to one embodiment, the internal
cylindrical shell 3 and thebaffles 8 can be welded or bolted. Further a sealing means can be provided between theexternal shell 4 and thebaffles 8 to avoid parasitic streams. - As shown on
FIG. 7 , on each external end of the hairpin exchanger straight part, the annular bundle of parallelstraight tubes 2 is connected, via suitablybent tubes 11, located outside the internal and theexternal shells linear header - More specifically, as shown on
FIG. 4 to FIG. 6 , at a first end of the exchanger, the bundle ofstraight tubes 2 is connected to at least a first cylindricallinear header 9, orentry header 9, which feeds thestraight tubes 2 with the first fluid, while, at a second end of the exchanger, the first fluid which is running inside the bundle oftubes 2 is collected by at least a second cylindricallinear header 10, orexit header 10, from the bundle oftubes 2. The need of more than oneentry header 9 orexit header 10 may appear when there is a large number oftubes 2 in the bundle. - Furthermore as shown on
FIG. 7 , the bundle ofstraight tubes 2 is connected, either to theentry header 9 or to theexit header 10 by suitablybent tubes 11, in an area which is outside the internal andexternal shells - In the shell-and-tube configuration, the first fluid, usually water, is generally under high pressure in quasi-spherical vessels or plenums. On the other side of the tube sheet, the salt flowing around the tube bundles is maintained under much lower pressure, requiring very thick tube sheets to withstand the pressure difference. The invention configuration provides prolongated tubes connected to standard headers (cylindrical, spherical, etc.) at the ends of the exchanger, in which the high pressure fluid is circulating. This allows to reduce the thickness of the tube sheets, if any, the pressure being limited. More specifically, in the rectangular section on
FIG.7 , one sees that the pressure drop supported by thetube sheet 16 is governed by the difference of the external (air)pressure 12 and the internalthermal fluid pressure 13. - According to one embodiment of the present invention shown on
FIG. 7 andFIG. 8 , a tube sheet is preferably used under the form of aelliptical tube sheet 16 or the like, having orifices orpassages 17 for theparallel tubes 2. Thetubes 2 are welded to theelliptical tube sheet 16 only with the sole purpose to ensure fluid tightness. Theseelliptical tube sheets 16 advantageously have lower thickness than prior art flat tube sheets for the reasons explained above. - Today, increased speed for ramp-up and stop are often required by the client. Thick vessel walls or headers are not suited for accepting higher temperature gradients and are more subject to fatigue leading to shorter lifetime of the heat exchanger. In this context the present invention provides extended lifetime of the heat exchanger components.
-
FIG. 7 also shows a detailed view for an embodiment of the entry/exit distribution jacket 30 from the fluid inlet/outlet distribution openings 31 located at 360° over the internal side of thedistribution jacket 30, preferably in afirst turn 32 of thehelical baffle 8. - The present invention is flexible and intended to be applied to a series of heat exchanger design used in MSSG technology, such as reheater, superheater, preheater and evaporator devices, wherein all the common components are made according to the generic heat exchanger design of the invention.
- As mentioned above, a hot molten salt with decreasing temperature flows for example firstly in parallel through a reheater and a superheater to recombine and enter into the evaporator and further in the preheater/economizer in series.
- In current embodiments, hot molten salt is entering the system at high temperature, for example 563°C and certainly below 565°C which is the degradation temperature for the usal molten salts. However it is under the scope of the present invention that the thermal fluid can withstand a temperature up to 700°C. All metal parts are advantageously made of stainless steel or noble metals which can withstand temperatures up to 600°C and above.
- Cold salt leaves the preheater at a temperature typically in the range of 290-300°C, or above a minimum temperature which is either the solidification temperature of the heat transfer fluid (as low as 240°C for the molten salts such as sodium derivatives). Alternately any thermal fluid, e.g. thermal oil, can be used instead of molten salt with an operating temperature range in this case going for example from 80°C (condensation and/or cristallization temperature) to 380°C (example of degradation temperature).
- Water at high pressure flows in tubes or pipes not in the shell side which allows lower thickness for the tube sheets and headers/shells and consequently a higher thermal gradient capability.
- Although the design of the exchanger according to the present invention is optimized for natural circulation running, it could also be used in once-through or forced circulation steam generators.
-
- 1
- Hairpin heat exchanger
- 2
- Straight tube (section)
- 3
- Internal cylindrical shell
- 4
- External cylindrical shell
- 5
- Intershell space
- 6
- Thermal fluid inlet
- 7
- Thermal fluid outlet
- 8
- Helical baffle
- 9
- Inlet straight header
- 10
- Outlet straight header
- 11
- Bent tube (section)
- 12
- First low pressure fluid (air)
- 13
- Second low pressure fluid (molten salt)
- 14
- U-benttube
- 15
- High pressure fluid (water/steam)
- 16
- Elliptical tube sheet
- 17
- Tube passageway
- 18
- Front closure
- 19
- Rear closure
- 20
- Support
- 21
- Straight tube
- 22
- Shell
- 23
- Shell-side fluid in
- 24
- Tube-side fluid in
- 25
- Tube-side fluid out
- 26
- Shell-side fluid out
- 27
- Tube sheet
- 28
- Baffle
- 29
- Water box or plenum or bonnet
- 30
- Distribution jacket
- 31
- Distribution openings to the first helical turn (or pitch) of the baffle
- 32
- First helical turn of the baffle
- 100
- Molten salt inlet of the MSSG
- 101
- Reheater of the MSSG
- 102
- Evaporator of the MSSG
- 103
- Economizer of the MSSG
- 104
- Superheater of the MSSG
- 105
- Molten salt outlet of the MSSG
Claims (18)
- A hairpin heat exchanger (1) having a first straight section, a second straight section and a bent section linking the first straight section and the second straight section, characterized in that each straight section comprises a part of a first cylindrical shell or internal cylindrical shell (3) and of a second cylindrical shell or external cylindrical shell (4), said first cylindrical shell (3) being located inside said second cylindrical shell (4), both forming an intershell space (5) enclosing a bundle of parallel U-bent tubes (2) having each a first and a second straight part respectively located in said first and second straight section of the exchanger and a 180°-bent part located in said bent section of the exchanger, wherein, in use, a first fluid to be heated and vaporized is flowing, said external cylindrical shell (4) being provided respectively at one end with an inlet (6) and at another end with an outlet (7) for a second fluid which is a hot thermal fluid, so that, in use, said second fluid is flowing in the intershell space (5) and cooling down by exchanging heat with the first fluid flowing in the straight tubes (2), said intershell space (5) enclosing also baffles (8) to guide the second fluid, wherein the bundle of parallel U-bent tubes (2) is extended out of the exchanger and connected, via bent tubes (11), respectively beyond an end of the internal shell (3) and of the external shell (4) at the first straight section to a first header (9) distributing the first fluid to the bundle of straight tubes (2) and beyond an end of the internal shell (3) and of the external shell (4) at the second straight section to a second header (10) collecting the first fluid under the form of liquid, vapor or a mixture liquid /vapor from the bundle of straight tubes (2).
- The hairpin heat exchanger (1) according to claim 1, wherein it is horizontal and in which the flow of the second fluid with respect to the flow of the first fluid is either co-current or counter-current.
- The hairpin heat exchanger (1) according to claim 1, wherein the first header (9) and the second header (10) are straight and cylindrical, or spherical.
- Use of the hairpin heat exchanger (1) according to claim 1, wherein said first fluid is a fluid comprising feedwater or supercritical carbon dioxide.
- Use of the hairpin heat exchanger (1) according to claim 1, wherein said second fluid is a molten salt or a mixture of molten salts, a thermal oil or liquid sodium.
- The hairpin heat exchanger (1) according to claim 1, wherein the baffles (8) are under the form of a continuous helical baffle.
- The hairpin heat exchanger (1) according to claim 1, wherein the baffles (8) are assembled, preferably welded or bolted, to the internal cylindrical shell (3).
- The hairpin heat exchanger according to claim 1, wherein a tube sheet (16) is provided between the first header (9), the second header (10) respectively, and the hairpin section of the exchanger containing the internal and external cylindrical shells (3, 4).
- The hairpin heat exchanger according to claim 8, wherein the tube sheet (16) is of elliptical shape and is provided with passageways (17) for allowing sealed passage of the U-bent tubes (2) through the tube sheet (16).
- The hairpin heat exchanger according to claim 1, wherein a sealing means is provided between the external shell (4) and the baffles (8).
- The hairpin heat exchanger according to claim 1, wherein it is equipped with a distribution jacket (30) for uniformly feeding the second fluid from the thermal fluid inlet (6, 7) to the heat exchanger.
- The hairpin heat exchanger according to claim 11, wherein the distribution jacket (30) has a plurality of openings (31) distributed at 360° over an internal face thereof, said openings (31) preferably feeding the second fluid into a first turn (32) of the helical baffle (8).
- Use of the heat exchanger according to claim 1, as an evaporator.
- Use of the heat exchanger according to claim 1, as a superheater.
- Use of the heat exchanger according to claim 1, as a reheater or an economizer.
- Use of an evaporator according to claim 13, of a superheater according to claim 14, and of a reheater and/or economizer according to claim 15, making at least one heat exchanger train in a molten salt steam generator (MSSG).
- Use according to claim 16, wherein the superheater, the reheater and/or the economizer are running counter-current, while the evaporator is running co-current.
- Use according to claim 16, wherein the molten salt steam generator is a once-through or a forced circulation steam generator.
Priority Applications (12)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP17172695.3A EP3406998B1 (en) | 2017-05-24 | 2017-05-24 | Heat exchanger for molten salt steam generator in concentrated solar power plant |
ES17172695T ES2844382T3 (en) | 2017-05-24 | 2017-05-24 | Heat exchanger for molten salt steam generator in a concentrated solar power plant |
US16/615,845 US20200141568A1 (en) | 2017-05-24 | 2018-05-15 | Heat exchanger for molten salt steam generator in concentrated solar power plant |
PCT/EP2018/062490 WO2018215239A1 (en) | 2017-05-24 | 2018-05-15 | Heat exchanger for molten salt steam generator in concentrated solar power plant |
MX2019013991A MX2019013991A (en) | 2017-05-24 | 2018-05-15 | Heat exchanger for molten salt steam generator in concentrated solar power plant. |
AU2018274073A AU2018274073A1 (en) | 2017-05-24 | 2018-05-15 | Heat exchanger for molten salt steam generator in concentrated solar power plant |
PE2019002300A PE20200088A1 (en) | 2017-05-24 | 2018-05-15 | HEAT EXCHANGER FOR MELTED SALT VAPOR GENERATOR IN CONCENTRATED SOLAR POWER PLANT (II) |
CN201880034199.6A CN110691953B (en) | 2017-05-24 | 2018-05-15 | Heat exchanger for a molten salt steam generator in a concentrated solar power plant |
KR1020197036756A KR20200010318A (en) | 2017-05-24 | 2018-05-15 | Heat Exchanger for Molten Salt Steam Generator in Concentrated Solar Power Plant |
ZA201907258A ZA201907258B (en) | 2017-05-24 | 2019-10-31 | Heat exchanger for molten salt steam generator in concentrated solar power plant |
IL270461A IL270461B (en) | 2017-05-24 | 2019-11-05 | Heat exchanger for molten salt steam generator in concentrated solar power plant |
CL2019003253A CL2019003253A1 (en) | 2017-05-24 | 2019-11-13 | Heat exchanger for a molten salt steam generator in a concentrated solar power plant (ii). |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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EP17172695.3A EP3406998B1 (en) | 2017-05-24 | 2017-05-24 | Heat exchanger for molten salt steam generator in concentrated solar power plant |
Publications (2)
Publication Number | Publication Date |
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EP3406998A1 EP3406998A1 (en) | 2018-11-28 |
EP3406998B1 true EP3406998B1 (en) | 2020-11-04 |
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EP17172695.3A Active EP3406998B1 (en) | 2017-05-24 | 2017-05-24 | Heat exchanger for molten salt steam generator in concentrated solar power plant |
Country Status (12)
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US (1) | US20200141568A1 (en) |
EP (1) | EP3406998B1 (en) |
KR (1) | KR20200010318A (en) |
CN (1) | CN110691953B (en) |
AU (1) | AU2018274073A1 (en) |
CL (1) | CL2019003253A1 (en) |
ES (1) | ES2844382T3 (en) |
IL (1) | IL270461B (en) |
MX (1) | MX2019013991A (en) |
PE (1) | PE20200088A1 (en) |
WO (1) | WO2018215239A1 (en) |
ZA (1) | ZA201907258B (en) |
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EP3804100A1 (en) * | 2018-07-09 | 2021-04-14 | Siemens Energy, Inc. | Supercritical co2 cooled electrical machine |
CN116062825B (en) * | 2023-04-06 | 2023-06-23 | 山西清凯环保工程有限公司 | High-salt wastewater salt extraction device |
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US1782409A (en) | 1927-12-19 | 1930-11-25 | Griscom Russell Co | Heat exchanger |
US2384714A (en) | 1943-04-12 | 1945-09-11 | Tech Studien Ag | Tubular heat exchanger |
DE839945C (en) * | 1948-12-13 | 1952-05-26 | Escher Wyss Ag | Tube heat exchanger |
US2693942A (en) | 1952-06-09 | 1954-11-09 | Gulf Oil Corp | Heat transfer apparatus |
US3168136A (en) * | 1955-03-17 | 1965-02-02 | Babcock & Wilcox Co | Shell and tube-type heat exchanger |
US3400758A (en) | 1966-05-16 | 1968-09-10 | United Aircraft Prod | Helical baffle means in a tubular heat exchanger |
NO148573C (en) | 1981-06-22 | 1983-11-02 | Norsk Hydro As | HEAT EXCHANGE |
JPS604790A (en) * | 1983-06-24 | 1985-01-11 | Babcock Hitachi Kk | Heat exchanger |
DD276521A1 (en) * | 1988-10-25 | 1990-02-28 | Brennstoffinstitut Freiberg,Dd | RINGWAERMETAUSCHER |
US6827138B1 (en) * | 2003-08-20 | 2004-12-07 | Abb Lummus Global Inc. | Heat exchanger |
CN101029787A (en) * | 2006-12-08 | 2007-09-05 | 于奎明 | Heat exchanger |
CN100453951C (en) * | 2007-02-09 | 2009-01-21 | 西安交通大学 | Combined helix baffle plate shell-and-tube heat exchanger |
US7740057B2 (en) * | 2007-02-09 | 2010-06-22 | Xi'an Jiaotong University | Single shell-pass or multiple shell-pass shell-and-tube heat exchanger with helical baffles |
US20090301699A1 (en) | 2008-06-05 | 2009-12-10 | Lummus Novolent Gmbh/Lummus Technology Inc. | Vertical combined feed/effluent heat exchanger with variable baffle angle |
CN101382277B (en) * | 2008-09-10 | 2010-09-15 | 东莞理工学院 | Solar molten salt sleeve pipe type steam generation method and device thereof |
DE102011075930A1 (en) * | 2011-05-16 | 2012-11-22 | Siemens Aktiengesellschaft | Steam generator, in particular for a solar thermal power plant |
CN103105075B (en) * | 2013-01-24 | 2014-09-10 | 东南大学 | U-shaped tubular condenser of vertical type spiral baffle plate |
EP3159649B1 (en) * | 2015-10-23 | 2020-03-04 | Hamilton Sundstrand Corporation | Heat exchangers |
CN205919715U (en) * | 2016-08-27 | 2017-02-01 | 哈尔滨锅炉厂有限责任公司 | A novel heat exchanger for solar thermal power generation system |
-
2017
- 2017-05-24 EP EP17172695.3A patent/EP3406998B1/en active Active
- 2017-05-24 ES ES17172695T patent/ES2844382T3/en active Active
-
2018
- 2018-05-15 KR KR1020197036756A patent/KR20200010318A/en not_active Application Discontinuation
- 2018-05-15 AU AU2018274073A patent/AU2018274073A1/en not_active Abandoned
- 2018-05-15 CN CN201880034199.6A patent/CN110691953B/en not_active Expired - Fee Related
- 2018-05-15 WO PCT/EP2018/062490 patent/WO2018215239A1/en active Application Filing
- 2018-05-15 MX MX2019013991A patent/MX2019013991A/en unknown
- 2018-05-15 US US16/615,845 patent/US20200141568A1/en not_active Abandoned
- 2018-05-15 PE PE2019002300A patent/PE20200088A1/en unknown
-
2019
- 2019-10-31 ZA ZA201907258A patent/ZA201907258B/en unknown
- 2019-11-05 IL IL270461A patent/IL270461B/en active IP Right Grant
- 2019-11-13 CL CL2019003253A patent/CL2019003253A1/en unknown
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Also Published As
Publication number | Publication date |
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EP3406998A1 (en) | 2018-11-28 |
CN110691953B (en) | 2021-05-18 |
US20200141568A1 (en) | 2020-05-07 |
ES2844382T3 (en) | 2021-07-22 |
CN110691953A (en) | 2020-01-14 |
CL2019003253A1 (en) | 2020-02-14 |
KR20200010318A (en) | 2020-01-30 |
WO2018215239A1 (en) | 2018-11-29 |
ZA201907258B (en) | 2020-11-25 |
MX2019013991A (en) | 2020-02-05 |
PE20200088A1 (en) | 2020-01-15 |
IL270461B (en) | 2021-05-31 |
AU2018274073A1 (en) | 2019-11-21 |
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