WO2018026312A1 - Кожухотрубный конденсатор и теплообменная трубка кожухотрубного конденсатора (варианты) - Google Patents
Кожухотрубный конденсатор и теплообменная трубка кожухотрубного конденсатора (варианты) Download PDFInfo
- Publication number
- WO2018026312A1 WO2018026312A1 PCT/RU2017/000560 RU2017000560W WO2018026312A1 WO 2018026312 A1 WO2018026312 A1 WO 2018026312A1 RU 2017000560 W RU2017000560 W RU 2017000560W WO 2018026312 A1 WO2018026312 A1 WO 2018026312A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- tube
- shell
- coolant
- grooves
- heat transfer
- Prior art date
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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
- F28D7/16—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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/08—Tubular elements crimped or corrugated in longitudinal section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
- F28F1/424—Means comprising outside portions integral with inside portions
- F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
- F28F13/182—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing especially adapted for evaporator or condenser surfaces
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
- F28F19/02—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/046—Condensers with refrigerant heat exchange tubes positioned inside or around a vessel containing water or pcm to cool the refrigerant gas
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- 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
- F28D2021/0063—Condensers
-
- 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
- F28F2245/00—Coatings; Surface treatments
- F28F2245/04—Coatings; Surface treatments hydrophobic
Definitions
- the group of inventions relates to shell and tube heat exchangers, in particular to the device of shell and tube condensers, and can be used in energy, oil refining, petrochemical, chemical, gas and other industries.
- a shell-and-tube condenser is known, characterized in that the heat exchange tubes are made of polytetrafluoroethylene (PTFE) or metal, but with a layer of PTFE applied to the surface [CN 1078802, priority date 03.19.1993, publication date 11.24.1993, IPC: F28D 7/10, F28D 7/10].
- PTFE polytetrafluoroethylene
- a shell-and-tube condenser is known, characterized in that it contains guiding partitions, and a tube with holes and a rod of the corresponding diameter located in it is located in the lower part of the housing along its entire length [SU409445, priority date 12/01/1971, publication date 11/30/1973, IPC: F28D 7/00, F28F 9/00,].
- a shell-and-tube condenser which contains a housing, inside of which there is a bundle of heat-exchange tubes fixed by means of tube boards located on the end surfaces of the housing, inlet and outlet pipes of the annulus coolant, and pipes for the inlet and outlet of the pipe coolant, characterized in that heat transfer tubes contain grooves on the outer surface.
- the disadvantage of the prototype is the high risk of lowering the heat transfer coefficient between the heat transfer medium of the pipe and annular space, due to the fact that the design of the tubes does not provide an effective reduction in the thickness of the formed condensate film on the outer surface, and also allows the formation of crystalline structures of sparingly soluble compounds on the inner surface, which, having a low thermal conductivity, significantly increase the coefficient of thermal resistance to heat transfer, and significantly reduce the efficiency shell and tube condenser.
- the technical problem to which the group of inventions is directed is to increase the overall heat transfer coefficient between the heat transfer mediums of the tube and annular space of the shell-and-tube condenser.
- the technical result, to which the group of inventions is directed, is to reduce the risk of an increase in thermal resistance between the coolants of the tube and annular space of the shell-and-tube condenser.
- the essence of the shell-and-tube condenser according to the first embodiment is as follows.
- the shell-and-tube condenser contains a housing in which a bundle of heat-exchange tubes is placed, having grooves on the outer surface and secured with tube plates, guide walls, inlet and outlet pipes of the annulus coolant, and pipes for the inlet and outlet of the pipe coolant.
- the heat transfer tubes are externally coated with a material with a low wettability coefficient, while the distance between the guide walls decreases from the inlet pipe to the pipe end of the heat transfer medium.
- the essence of the shell-and-tube condenser according to the second embodiment is as follows.
- the shell-and-tube condenser contains a housing in which a bundle of heat-exchange tubes is placed, having grooves on the outer surface and secured with tube plates, guide walls, inlet and outlet pipes of the annulus coolant, and pipes for the inlet and outlet of the pipe coolant.
- heat transfer tubes are externally coated with a material with a low wettability coefficient, have bulges on the inner surface and are internally coated with a material with a high coefficient of adhesion resistance, while the distance between guiding partitions decreases from the input pipe to the pipe outlet of the coolant of the annulus.
- the essence of the heat transfer tube of the shell-and-tube condenser according to the first embodiment is as follows.
- the shell and tube heat exchanger tube has grooves on the outer surface. Unlike the prototype, the heat transfer tube is coated externally with a low wettability coefficient, has a convexity on the inner surface and is coated internally with a high adhesion resistance coefficient.
- the essence of the heat transfer tube of the shell-and-tube condenser according to the second embodiment is as follows.
- the shell and tube heat exchanger tube has grooves on the outer surface. Unlike the prototype, the heat transfer tube is coated externally with a low wettability coefficient, has a convexity on the inner surface and is coated internally with a high adhesion resistance coefficient.
- a material with a low wettability coefficient provides the possibility of creating a hydrophobic coating that facilitates the rolling of condensate from the outer surface of the heat transfer tube.
- a material with a low wettability coefficient can be characterized by a wetting angle. Moreover, the value of the contact angle in the range from 90 ° to 150 ° provides the highest hydrophobic characteristics of the outer surface of the heat transfer tube.
- Material with a low wettability coefficient can be represented by synthetic polyamides or polymers, for example, nylon, fluoroplast or polytetrafluoroethylene.
- Reducing the distance between the guide walls provides a constant optimal flow rate of the coolant through the annulus, which can be in the range of 65-120 m / s.
- the basic principle of reducing the distance between the guide walls is to maintain a constant average speed of steam along each passage of the annular coolant.
- the heat transfer path of the annulus is called the space between the closest guide baffles, in which the steam moves rectilinearly normal to the tubes.
- a constant average steam velocity for each passage of the annulus coolant is provided by a constant ratio of the average volumetric flow rate of steam for each passage of the annulus coolant and the cross-sectional area of the corresponding passage of the annulus coolant.
- the ratio is determined by the following formula.
- D'i is the volumetric flow rate of steam at the beginning of the i-ro stroke of the annular space
- m 3 / h D "i is the volumetric flow rate of steam at the end of the i-ro stroke of the annular space
- m 3 / h Fi is the cross-sectional area of the flow path of the annular coolant
- m2 F - total cross-sectional area of all moves m2
- An additional means of maintaining a constant flow velocity of the coolant in the annulus, especially in the turning zones, may be a reduction in the window area of subsequent guide baffles compared to the previous ones.
- the heat exchanger tube of the shell-and-tube condenser has grooves on the outer surface, which make it possible to create sloping surface portions that contribute to reducing the thickness or rupture of the condensate film formed on the outer surface of the heat exchanger tube.
- the grooves may have a different shape and direction and may be circular, spiral or multifaceted recesses and can be obtained by knurling, cutting or punching.
- the optimal parameters of the groove can be as follows: the grooves can have roundings with a radius in the range from 0.04 to 0.1 of the outer diameter of the heat transfer tube, while the radius of rounding of the formed sloping sections of the outer surface can be in the range from 0.3 to 2 of the outer diameters of the heat exchange tube.
- the grooves can have a depth, the value of which can be in the range from OD to 3 mm, while the pitch of the grooves may depend on the outer diameter of the heat exchanger tube, may be less or more than the diameter of the heat exchanger tube, but it must not exceed the diameter of the heat exchanger tubes more than 10 times.
- a material with a high coefficient of adhesion resistance provides the possibility of creating a coating with a low coefficient of friction, which prevents adhesion and deposition of salts and other inclusions contained in the coolant of the tube space on the inner surface of the heat transfer tube.
- a material with a high adhesion resistance coefficient can be represented by synthetic polyamides, polymers or fluorine-containing materials, for example, fluoroplast, polytetrafluoroethylene, as well as various metal coatings. Also, these materials can be applied to the inner surface of the heat transfer tube together, with the metal coating being deposited with the lower layer and fluorine-containing material as the upper layer.
- the use of polytetrafluoroethylene or fluoroplastic allows you to apply the thinnest coating layer (from 0.1 microns), thereby providing an additional reduction in thermal resistance between the heat transfer medium of the pipe and annular space.
- the heat exchange tube has convexities on the inner surface, which makes it possible to create turbulent eddies that contribute to disruption of the laminar flow of the heat transfer medium of the tube space, which reduces the likelihood of salts and other inclusions settling on the inner surface of the heat exchange tube.
- the creation of turbulent eddies also provides the possibility of abrasive action by salts and other inclusions on crystalline structures of poorly soluble compounds that have already formed on the inner surface of the tube.
- the bulges can have various shapes, for example, annular, diamond-shaped, rectangular and other shapes. Bulges may repeat with at a given step and have a predetermined height, determined depending on the diameter and wall thickness of the heat transfer tube, the flow rate and the properties of the coolant used in the pipe space, as well as on the content of salts and other impurities in it. Moreover, to reduce the risk of salt buildup between the bulges and, as a consequence, to reduce the risk of an increase in thermal resistance between the coolants of the pipe and annular spaces, the bulges can be repeated in increments of 0.1 to 10 outer diameters of the heat exchange tube. The height of the bulges can be in the range from 0.1 to 10 mm. The width of the bulges can be in the range from 0.5 to 10 mm.
- Ring bulges can be obtained by knurling or cutting.
- Diamond-shaped bulges can be obtained by cutting or forcing intersecting spiral grooves on the inner surface of the heat exchanger tube, and rectangular bulges can be obtained by cutting or forcing intersecting straight longitudinal and transverse grooves on the inner surface of the heat exchanger tube.
- Bulges can also be formed by inserts installed inside the heat exchanger tube and / or fixed on its inner surface, which can be ribs, spiral ribbons, rings or corrugated elements. At the same time, to increase the degree of swirl of the coolant flow in the pipe space, the inserts can have through perforation, and to prevent the deposition of salts, a material with a high adhesion resistance coefficient can be applied to their surface.
- the bulges on the inner surface of the heat exchanger tube can be made mating grooves on the outer surface.
- the bulges on the inner surface of the heat exchanger tube can be obtained by rolling grooves on the outer surface of the heat exchanger tube, which additionally provides higher reliability and ease of manufacture of the heat exchanger tube.
- the distance between the guide walls of the shell-and-tube condenser decreases from the input pipe to the pipe output of the annular coolant, which allows you to maintain a constant speed of the coolant annulus, ensuring effective removal of condensate droplets from the outer surface of the heat exchanger tubes by the flow of non-condensed coolant throughout the annular space.
- the outer surface of the heat exchanger tubes is coated with a material having a low wettability coefficient, which reduces the adhesion of condensate droplets and the outer surface of the heat exchanger tubes.
- - heat transfer tubes are internally coated with a material with a high coefficient of adhesion resistance, which reduces the degree of molecular interaction between salt particles and the inner surface of the heat transfer tubes, which slows down the formation of crystalline structures of poorly soluble compounds on the inner surface of the heat transfer tubes.
- the set of essential distinguishing features of the group of inventions allows for the efficient removal of condensate droplets from the outer surface of the heat exchanger tubes, to reduce the adhesion of condensate droplets to the outer surface of the heat exchanger tubes, to slow down the formation of crystalline structures of poorly soluble compounds on the inner surface of the heat exchanger tubes, and if they are formed, it allows them destroy, due to which a technical result is achieved, consisting in reducing the risk increase the thermal resistance between the heat transfer fluids and the pipe annulus, and improves heat transfer coefficient between the heat transfer fluids and the pipe annulus.
- the creation of a design that includes coating the heat exchanger tubes with a material with a low coefficient of wettability, grooves and convexity on the surfaces of the heat exchanger tubes, as well as a successively decreasing distance between the guide walls, allows to achieve a synergistic effect consisting in a significant increase in the heat transfer coefficient between the heat transfer fluids of the tube and annular space of the shell-and-tube condenser in including by reducing the coefficient of thermal resistance between those lonositelyami pipe and the annulus.
- the indicated synergistic effect is achieved due to the fact that the annulus heat carrier condensed during heat transfer, due to the coating of the outer surface of the heat exchanger tubes with a material with a low wettability coefficient, forms a film with a minimum thickness on the surface of the heat exchanger tubes and collects into droplets, most of which are rolled from convex arcuate segments of the surface of the heat transfer tubes into the annular grooves, and the remaining on the arcuate convex segments of the heat transfer tubes to Condensate removed fire coolant flow annulus, the velocity of which is maintained by reducing the distance between the baffles from entering the nozzle to the nozzle annulus O coolant.
- the salt particles contained in the coolant of the tube space due to coating the inner surface of the heat exchanger tube with a material with a high adhesion resistance coefficient, are repelled from the inner surface of the heat exchanger tube and, when interacting with the bulges, swirl, abrasively affecting the already formed salt deposits, actively destroying them.
- the group of inventions can be made of known materials using known means, which indicates the compliance of the group of inventions with the patentability criterion of "industrial applicability".
- Figure 1 Shell-and-tube condenser with one-sided flow of coolant annulus with a condensate cooler, General view, a longitudinal section.
- Figure 2 Shell-and-tube condenser with one-sided flow of coolant annulus without condensate cooler, General view, a longitudinal section.
- Fig.Z Shell-and-tube condenser with two-sided flow of coolant annulus, General view, a longitudinal section.
- Fig. 8 shows a heat-exchange tube of a shell-and-tube condenser with a spiral groove on the outer surface and a reciprocal spiral-shaped bulge on the inner surface, longitudinal section.
- Fig.9 Heat transfer tube shell-and-tube condenser with annular grooves on the outer surface and inserts made in the form of perforated rings, a longitudinal section.
- the shell-and-tube condenser comprises a housing 1, a distribution chamber 2, a rotary chamber 3.
- the housing 1 there is a bundle of heat exchange tubes 4 fixed by means of tube plates 5, guide walls 6, an inlet pipe 7 and an annular heat carrier outlet pipe 8, an inlet pipe 9 and a pipe 10 of the heat transfer medium of the pipe space, while the distance Sn between the guide walls 6 decreases from the inlet pipe 7 to the heat transfer medium pipe outlet 8, so that Sn> Sn + l.
- the heat transfer tubes 4 are coated with a material with a low wettability coefficient and have grooves 11, due to which arcuate convex segments 12 are formed on the outer surface of the heat transfer tubes 4.
- Shell-and-tube condenser operates as follows.
- a refrigerant having a temperature lower than the steam saturation temperature in the annulus of the housing 1 is supplied to the pipe coolant inlet pipe 9, then the refrigerant circulates inside the shell-and-tube condenser system from the pipe space coolant inlet 9 to the distribution chamber 2, then through the heat exchange tubes 4 and the rotary chamber 3 back to the distribution chamber 2 and to the pipe outlet 10 of the coolant of the pipe space.
- the annular coolant that requires cooling is supplied through the annular coolant inlet pipe 7 to the annulus of the casing 1, while in contact with the surface of the heat exchange tubes 4 it begins to partially condense, moving towards the annular coolant outlet pipe 8.
- condensate droplets 13 are formed on the outer surface of the heat exchange tubes, most of which are rolled from the arcuate convex segments 12 into the grooves 11, while the condensate residues 14 are removed by the flow of non-condensed annular coolant, the speed of which is maintained due to the fact that the distance between the guide walls 6 is sequential from the pipe 7 of the input of the coolant of the annular space to the pipe 8 of the output of the coolant of the annular space is reduced.
- the shell-and-tube condenser according to the second embodiment contains heat exchange tubes 4, additionally having bulges 15 on the inner surface and coated with a material with a high adhesion resistance coefficient.
- the shell-and-tube condenser according to the second embodiment works similarly to the shell-and-tube condenser according to the first embodiment, while the particles of 16 salts contained in the refrigerant are slightly deposited on the inner surface of the heat exchange tube 4 by coating it from the inside with a material with a high adhesion resistance coefficient, forming a thin layer 17 salt deposits.
- the refrigerant interacts with the bulges 15 and swirls, also preventing the particles of 16 salts from settling on the inner surface of the heat transfer tube and contributing to the destruction of the formed layer 17 of salt deposits by abrasive exposure to them by the flow of the refrigerant and particles 16 of the salts contained therein.
- the thickness of the condensate film on the outer surface of the heat exchanger tube and the amount of salt deposits on the inner surface of the tube and the tube are simultaneously reduced, thereby achieving a technical result consisting in reducing the risk of increasing thermal resistance between the coolants of the pipe and annular spaces, and increasing the overall heat transfer coefficient between the coolants of the pipe and annulus.
- by reducing the required heat transfer surface it is possible to improve the overall dimensions of the heat transfer tube and, as a result, improve the overall dimensions of the entire shell-and-tube condenser.
Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
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DK17837320.5T DK3415852T3 (da) | 2016-08-05 | 2017-07-31 | Skal- og rørkondensator og varmevekslingsrør til en skal- og rørkondensator (varianter) |
US16/321,790 US11493282B2 (en) | 2016-08-05 | 2017-07-31 | Shell and tube condenser and the heat exchange tube of a shell and tube condenser (variants) |
CA3032592A CA3032592C (en) | 2016-08-05 | 2017-07-31 | Shell-and-tube condenser comprising grooved tubes with coatings |
EP17837320.5A EP3415852B1 (en) | 2016-08-05 | 2017-07-31 | Shell and tube condenser and heat exchange tube of a shell and tube condenser (variants) |
CN201780048004.9A CN109791023A (zh) | 2016-08-05 | 2017-07-31 | 壳管式冷凝器和壳管式冷凝器的换热管 |
JP2019528014A JP2019527812A (ja) | 2016-08-05 | 2017-07-31 | シェルアンドチューブ式凝縮器およびシェルアンドチューブ式凝縮器の熱交換チューブ(複数のバージョン) |
PL17837320.5T PL3415852T3 (pl) | 2016-08-05 | 2017-07-31 | Skraplacz płaszczowo-rurowy i rura wymiany ciepła skraplacza płaszczowo-rurowego (warianty) |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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RU2016132511 | 2016-08-05 | ||
RU2016132511 | 2016-08-05 | ||
RU2017126870 | 2017-07-26 | ||
RU2017126870 | 2017-07-26 |
Publications (1)
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WO2018026312A1 true WO2018026312A1 (ru) | 2018-02-08 |
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Family Applications (1)
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PCT/RU2017/000560 WO2018026312A1 (ru) | 2016-08-05 | 2017-07-31 | Кожухотрубный конденсатор и теплообменная трубка кожухотрубного конденсатора (варианты) |
Country Status (8)
Country | Link |
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US (1) | US11493282B2 (ru) |
EP (1) | EP3415852B1 (ru) |
JP (1) | JP2019527812A (ru) |
CN (1) | CN109791023A (ru) |
CA (1) | CA3032592C (ru) |
DK (1) | DK3415852T3 (ru) |
PL (1) | PL3415852T3 (ru) |
WO (1) | WO2018026312A1 (ru) |
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US11818831B2 (en) * | 2019-09-24 | 2023-11-14 | Borgwarner Inc. | Notched baffled heat exchanger for circuit boards |
US20210164619A1 (en) * | 2019-12-02 | 2021-06-03 | Chart Inc. | Ambient Air Vaporizer with Icephobic/Waterphobic Treatment |
US11524249B2 (en) * | 2021-03-08 | 2022-12-13 | Saudi Arabian Oil Company | Controlling degradation in a reboiler via a hydrophobic coating |
US20230294015A1 (en) * | 2022-03-16 | 2023-09-21 | Saudi Arabian Oil Company | Controlling degradation in a reboiler via higher surface roughness |
EP4328519A1 (de) * | 2022-08-25 | 2024-02-28 | ERK Eckrohrkessel GmbH | Verfahren und vorrichtung zur gewinnung von erdwärme sowie verfahren zur erzeugung elektrischer energie |
EP4328520A1 (de) * | 2022-08-25 | 2024-02-28 | ERK Eckrohrkessel GmbH | Verfahren und einrichtung zur nutzung von erdwärme |
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CN1078802A (zh) * | 1993-03-19 | 1993-11-24 | 张留刚 | 聚四氟乙烯金属复合换热器 |
RU8459U1 (ru) * | 1998-01-05 | 1998-11-16 | Открытое акционерное общество "Нижнекамскнефтехим" | Аппарат для высокотемпературных теплообменных процессов |
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- 2017-07-31 PL PL17837320.5T patent/PL3415852T3/pl unknown
- 2017-07-31 WO PCT/RU2017/000560 patent/WO2018026312A1/ru active Application Filing
- 2017-07-31 JP JP2019528014A patent/JP2019527812A/ja active Pending
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PL3415852T3 (pl) | 2024-03-18 |
CA3032592A1 (en) | 2018-02-08 |
US20210278144A1 (en) | 2021-09-09 |
JP2019527812A (ja) | 2019-10-03 |
CN109791023A (zh) | 2019-05-21 |
CA3032592C (en) | 2020-11-24 |
DK3415852T3 (da) | 2024-02-05 |
US11493282B2 (en) | 2022-11-08 |
EP3415852A1 (en) | 2018-12-19 |
EP3415852B1 (en) | 2023-11-08 |
EP3415852A4 (en) | 2019-10-16 |
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