WO2023118402A1 - Échangeur de chaleur, en particulier échangeur de chaleur à calandre, pour agencement dans un rotor à axe de rotation - Google Patents

Échangeur de chaleur, en particulier échangeur de chaleur à calandre, pour agencement dans un rotor à axe de rotation Download PDF

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Publication number
WO2023118402A1
WO2023118402A1 PCT/EP2022/087405 EP2022087405W WO2023118402A1 WO 2023118402 A1 WO2023118402 A1 WO 2023118402A1 EP 2022087405 W EP2022087405 W EP 2022087405W WO 2023118402 A1 WO2023118402 A1 WO 2023118402A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchange
axis
rotation
heat
exchange medium
Prior art date
Application number
PCT/EP2022/087405
Other languages
German (de)
English (en)
Inventor
Bernhard Adler
Andreas LÄNGAUER
Christian RAKUSCH
Original Assignee
Ecop Technologies Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ecop Technologies Gmbh filed Critical Ecop Technologies Gmbh
Priority to KR1020247024128A priority Critical patent/KR20240126046A/ko
Priority to CN202280076843.2A priority patent/CN118265886A/zh
Priority to AU2022420806A priority patent/AU2022420806A1/en
Priority to CA3236896A priority patent/CA3236896A1/fr
Publication of WO2023118402A1 publication Critical patent/WO2023118402A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D7/1607—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 with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F25B3/00—Self-contained rotary compression machines, i.e. with compressor, condenser and evaporator rotating as a single unit
    • 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
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • F28D11/04—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller performed by a tube or a bundle of 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/08—Assemblies of conduits having different features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the invention relates to a heat exchanger, in particular a tube bundle heat exchanger, for use in a rotor with an axis of rotation, comprising: first heat exchange channels for conducting a first heat exchange medium, in particular a liquid, second heat exchange channels for Guidance of a second heat exchange medium, in particular a gas, preferably an inert gas, with the second heat exchange channels having, based on the mounted state of use of the heat exchanger, at least one inner heat exchange channel located closer to the axis of rotation and one outer heat exchange channel further away from the axis of rotation, a second heat exchange medium, widened, preferably conically widened, dividing element for feeding the second heat exchange medium from an inlet opening of the dividing element into inflow openings of the second heat exchange channels, and a narrowed, preferably substantially conically narrowed, merging element, seen in the direction of flow of the second heat exchange medium, for discharging the second heat exchange medium from outflow openings of the second heat exchange channels into an outlet opening of the
  • a rotary heat pump is known from WO2015/103656, in which the centrifugal acceleration of the rotor is used to generate different pressure or temperature levels. Heat at a high temperature is extracted from the compressed working medium and heat at a comparatively low temperature is supplied to the expanded working medium.
  • the rotary heat pump has internal heat exchangers and external heat exchangers, which are arranged essentially parallel to the axis of rotation of the rotor.
  • the inner heat exchangers are designed for lower temperature heat exchange and the outer heat exchangers for higher temperature heat exchange.
  • tube bundle heat exchangers are often used in stationary applications, in which the working medium flows through a bundle of tubes that is arranged inside a cylindrical housing jacket.
  • the location and direction references relate to the intended use of the heat exchanger as part of a rotor.
  • “Front” and “rear” refer to the flow direction of the second heat exchange medium.
  • “Radial” and “axial” refer to the axis of rotation of the rotor.
  • “Inside” means closer to the axis of rotation of the rotor.
  • “Outside” means further from the axis of rotation. The distances refer to the radial distances from the axis of rotation.
  • the invention is thus based on the surprising finding that the heat exchanger cannot be operated effectively under the effect of centrifugal acceleration by evenly dividing the second heat exchange medium.
  • the invention solves this problem in that the different pressure differences of the partial flows of the second heat exchange medium flowing at different distances from the axis of rotation between the inlet opening of the dividing element and the outlet opening of the Merging element at least partially, preferably substantially completely compensated.
  • it can be achieved in this way that the flow through the second heat exchange channels is essentially uniform.
  • the throttle element is set up to throttle the inner flow more than the outer flow. If heat is supplied from the first heat exchange medium to the second heat exchange medium in the second heat exchange channels, the throttle element is set up to throttle the outer flow more than the inner flow.
  • the throttling element is set up for asymmetrical throttling of the flow of the second heat exchange medium with respect to the central axis or axis of symmetry of the heat exchanger. With the aid of the throttle element, the second heat exchange medium is subjected to essentially the same pressure differences as it flows through the heat exchanger from the inlet to the outlet opening.
  • the throttle orifice can be arranged in front of the inflow openings, in particular immediately in front of the inflow openings, or after the outflow openings, in particular immediately after the outflow openings.
  • the throttle opening that is further away from the axis of rotation is larger than the throttle opening that is closer to the axis of rotation.
  • the throttle opening that is further away from the axis of rotation is smaller than the throttle opening that is closer to the axis of rotation.
  • the throttle orifice can have further throttle openings at greater distances from the axis of rotation of the rotor, with throttle openings further away from the axis of rotation being larger in each case than throttle openings located closer to the axis of rotation.
  • the heat exchanger has several Rows of second heat exchange channels, the second heat exchange channels of each row each having substantially the same distance from the axis of rotation of the rotor.
  • the throttle diaphragm preferably has a plurality of rows each with a plurality of throttle openings, with a row further away from the axis of rotation and a row closer to the axis of rotation having throttle openings of different sizes.
  • the start and/or end section of a distribution channel further away from the axis of rotation and the start and/or end section of a distribution channel closer to the axis of rotation have different flow cross sections.
  • the advantage of this design is that the flow grid is generally useful for good distribution and flow guidance in order to keep pressure losses as small as possible.
  • this flow grid can now also be designed as a throttle element, with which an asymmetrical widening of the cross section is achieved in order to compensate for the different pressure differences depending on the distance from the axis of rotation.
  • the initial section connects to the inlet of the heat exchanger.
  • the end section guides the second heat exchange medium to the inflow opening of the second heat exchange channel.
  • the flow grid preferably has at least one first distribution channel at a first distance from the axis of rotation and at least one second distribution channel at a second distance from the axis of rotation of the rotor, the second distance being greater than the first distance and the beginning and/or end section of the second Distribution channel has a larger flow cross section than the beginning and / or end portion of the first distribution channel.
  • the flow grid preferably has at least one third distribution channel at a third distance from the axis of rotation, the third distance being greater than the second distance and the start and/or end section of the third distribution channel having a larger flow cross section than the start and/or end section of the second split channel has.
  • the flow grid preferably has at least one fourth distribution channel at a fourth distance from the axis of rotation, the fourth distance being greater than the third distance and the beginning and/or end section of the fourth distribution channel having a larger flow cross section than the beginning and/or end section of the third distribution channel has.
  • the flow grid can have further distribution channels at greater distances from the axis of rotation, with the flow cross section of the beginning and/or end section increasing with the distance from the axis of rotation.
  • the flow grid preferably has at least a first row with a plurality of individual, i.e.
  • the end section of the distribution channel further away from the axis of rotation has a larger flow cross-section than the end section of the distribution channel located closer to the axis of rotation, with the initial section of the distribution channel further away from the axis of rotation having essentially the same flow cross-section as the initial section of the channel closer to the Having axis of rotation located distribution channel.
  • This design is structurally particularly simple.
  • the inflow into the flow grid can be symmetrical, but the outflow from the flow grid can be asymmetrical.
  • the asymmetric distribution of the second heat exchange medium by means of the flow grid has the result that a flow of the second heat exchange medium close to the axis from the entry into the heat exchanger to the exit from the heat exchanger flows through a smaller flow cross section in sections than an off-axis flow of the second heat exchange medium, as a result of which the flow close to the axis has a higher flow Pressure drop is exposed than the off-axis flow.
  • the pressure difference between the second heat exchange channel near the axis and the second heat exchange channel remote from the axis is at least partially, preferably substantially completely, compensated.
  • the device for equalizing the flow through the second heat exchange channels has turbulators, in particular spiral turbulators, within the second heat exchange channels, with a turbulator further away from the axis of rotation and a turbulator closer to the axis of rotation causing different pressure losses.
  • the turbulator farther from the axis of rotation causes less pressure loss than the turbulator located closer to the axis of rotation.
  • the turbulator farther from the axis of rotation can The turbulator and the turbulator closer to the axis of rotation have different spiral lengths.
  • the outer heat exchanger and/or the inner heat exchanger can be designed according to one of the above embodiments of the heat exchanger.
  • a first heat exchange medium in particular a liquid
  • a second heat exchange medium in particular a gas, preferably an inert gas
  • FIG. 1 shows a rotor 1 which, in the embodiment shown, is designed as a device for converting mechanical energy into thermal energy (and vice versa). This device is operated in particular as a rotary heat pump.
  • the rotor 1 has an axis of rotation 2, which is horizontal during operation, for example, about which the rotor 1 is rotated with the aid of a motor (not shown).
  • the rotor 1 has a compressor unit 3 in which a working medium is conducted away from the axis of rotation 2 to increase the pressure due to the centrifugal force.
  • the rotor 1 has an expansion unit 4 in which the working medium is guided towards the axis of rotation 2 to reduce the pressure.
  • the working medium is preferably conducted within the rotor 1 in a closed circuit.
  • the rotor 1 has a plurality of internal heat exchangers 5 (low-pressure heat exchangers) and a plurality of external heat exchangers 6 (high-pressure heat exchangers). In the inner 5 and outer 6 heat exchangers, heat exchange is carried out between a first heat exchange medium and a second heat exchange medium, namely the working medium.
  • FIG. 2A shows a heat exchanger 7, also referred to as a heat exchanger, in an embodiment which can be implemented in the inner 5 and/or the outer heat exchanger 6.
  • the heat exchanger 7 is described below as an example for use as an external heat exchanger 6, ie as a high-pressure heat exchanger.
  • the heat exchanger 7 has an inlet element 8, via which the second heat exchange medium, ie the working medium, is fed to the heat exchanger 7, and an outlet element 9 which the second heat exchange medium leaves the heat exchanger 7.
  • the heat exchanger 7 is designed as a tube bundle heat exchanger.
  • the tube bundle heat exchanger has a cylindrical housing 10 in which a tube bundle is arranged.
  • the tube bundle comprises elongate tubes 11 arranged parallel and spaced apart in the radial and circumferential directions. Inside, the tubes 11 enclose second heat exchange channels 12 for the second heat exchange medium.
  • the tubes 11 are each held at opposite ends in a tube plate in the form of a bottom plate 11A (see FIG. 2B).
  • the first heat exchange medium is guided into the interior of the housing 10 via a feed 13 and, after the heat exchange with the second heat exchange medium, is discharged from the housing 10 via a discharge line 14 .
  • Radial extent of the heat exchanger 7 (from the innermost of the second heat exchange channels 12 to the outermost of the heat exchange channels 12): 100 mm Average pressure in the heat exchanger: 120 bar Average temperature: 400K Gas: krypton
  • the flow of the gas which is assumed to be ideal, i.e. without considering real gas properties, takes place only under the acceleration of gravity, and the heat exchanger is aligned in such a way that the acceleration of gravity has the same direction as the centrifugal acceleration, then the pressure difference between the outermost flow channel and the innermost flow channel is 0.14 mbar and is not taken into account due to the minimal effect.
  • Fig. 5 shows a roughly calculated pressure difference between the flow channels ("outside” - arrow 23 in Fig. 4; "inside” - arrow 24 in Fig. 4) in revolutions per minute (rpm), the effect of the rotation on the heat exchanger 7 is illustrated.
  • the radial distance of the outermost channel from the axis of rotation 2 is indicated by arrow 25
  • the radial distance of the innermost channel from the axis of rotation 2 is indicated by arrow 26.
  • Arrow 27 shows the main flow direction of the gas.
  • this difference is 0.46 bar and is therefore greater by a factor of about 3300 (corresponding to the ratio of the accelerations) than under gravitational acceleration.
  • Fig. 6 and Fig. 7 show a first according to the invention Embodiment of the heat exchanger 7 for the case of the outer heat exchanger 6, with only the differences from the previous versions being described below.
  • a device 30 for equalizing the flow through the second heat exchange channels 12 is provided, with which different pressure differences of the second heat exchange medium are compensated, which are caused by the different radial distances of the second heat exchange channels 12 to the axis of rotation 2 of the rotor 2.
  • a throttling device for different throttling of the discrete second heat exchange ducts 12 is provided as a device 30 for equalizing the flow through the second heat exchange ducts 12 .
  • the throttle device has a disk-shaped throttle orifice plate 31, which is circular when viewed in the direction of flow of the second heat exchange medium, and has a large number of circular throttle openings 32, which are arranged directly in front of the inflow openings 29 of the second heat exchange channels 12.
  • the throttle openings 32 are arranged in rows, with the diameter of the throttle openings 32 increasing from row to row outwards, ie away from the axis of rotation 2 .
  • the throttle openings 32 have the same diameter.
  • a flow grid 21 of asymmetrical design (relative to the central axis 36 of the heat exchanger 7) is provided as the device 30 for equalizing the flow through the second heat exchange channels.
  • the dividing channels 22 of the flow grid 21 each have a beginning section 22A and an end section 22B.
  • the flow cross-section of the initial sections 22A increases with distance from the axis of rotation 2 .
  • the end sections 22B on the other hand, have the same flow cross sections. Extending between the beginning sections 22A and the end sections 22B are middle sections 22C, which bring about a continuous transition from the beginning sections 22A to the end sections 22B.
  • middle sections 22C Extending between the beginning sections 22A and the end sections 22B are middle sections 22C, which bring about a continuous transition from the beginning sections 22A to the end sections 22B.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur (7), en particulier un échangeur de chaleur à calandre, destiné à être disposé dans un rotor (1) ayant un axe de rotation (2), comprenant : des premiers canaux d'échange de chaleur (15) permettant de guider un premier milieu d'échange de chaleur, en particulier un liquide ; des seconds canaux d'échange de chaleur (12) permettant de guider un second milieu d'échange de chaleur, en particulier un gaz, de préférence un gaz noble, les seconds canaux d'échange de chaleur (12) comprenant, dans l'état d'utilisation assemblé, au moins un canal d'échange de chaleur interne qui est plus proche de l'axe de rotation (2), et un canal d'échange de chaleur externe qui est plus éloigné de l'axe de rotation (2) ; un élément de distribution (17) qui se dilate, de préférence de manière conique, dans la direction d'écoulement du second milieu d'échange de chaleur de sorte à amener le second milieu d'échange de chaleur à partir d'une ouverture d'entrée (17A) dans l'élément de distribution (17) dans des ouvertures d'entrée (29) dans les seconds canaux d'échange de chaleur (12) ; un élément de fusion (18) qui s'effile, s'effilant de préférence de manière sensiblement conique, dans la direction d'écoulement du second milieu d'échange de chaleur de sorte à évacuer le second milieu d'échange de chaleur des ouvertures de sortie (28) dans les seconds canaux d'échange de chaleur (12) dans une ouverture de sortie (18A) dans l'élément de fusion (18) ; et un dispositif (30) permettant d'homogénéiser l'écoulement à travers les seconds canaux d'échange de chaleur (12), lequel dispositif comprend un élément d'étranglement servant à étrangler, dans différentes mesures, un écoulement interne du second milieu d'échange de chaleur qui passe à travers le canal d'échange de chaleur interne, et un écoulement externe du second milieu d'échange de chaleur qui passe à travers le canal d'échange de chaleur externe entre l'ouverture d'entrée (17A) dans l'élément de distribution (17) et l'ouverture de sortie (18A) dans l'élément de fusion (18).
PCT/EP2022/087405 2021-12-22 2022-12-22 Échangeur de chaleur, en particulier échangeur de chaleur à calandre, pour agencement dans un rotor à axe de rotation WO2023118402A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
KR1020247024128A KR20240126046A (ko) 2021-12-22 2022-12-22 회전축을 갖는 로터에 배치하기 위한 열교환기, 특히 쉘-앤드-튜브 열교환기
CN202280076843.2A CN118265886A (zh) 2021-12-22 2022-12-22 用于布置在具有旋转轴线的转子中的热交换器、特别是壳管式热交换器
AU2022420806A AU2022420806A1 (en) 2021-12-22 2022-12-22 Heat exchanger, in particular shell-and-tube heat exchanger, for arrangement in a rotor having an axis of rotation
CA3236896A CA3236896A1 (fr) 2021-12-22 2022-12-22 Echangeur de chaleur, en particulier echangeur de chaleur a calandre, pour agencement dans un rotor a axe de rotation

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP21216865.2 2021-12-22
EP21216865.2A EP4202342A1 (fr) 2021-12-22 2021-12-22 Échangeur de chaleur, en particulier échangeur de chaleur à faisceau tubulaire, destiné à être agencé dans un rotor doté d'un axe de rotation

Publications (1)

Publication Number Publication Date
WO2023118402A1 true WO2023118402A1 (fr) 2023-06-29

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PCT/EP2022/087405 WO2023118402A1 (fr) 2021-12-22 2022-12-22 Échangeur de chaleur, en particulier échangeur de chaleur à calandre, pour agencement dans un rotor à axe de rotation

Country Status (6)

Country Link
EP (1) EP4202342A1 (fr)
KR (1) KR20240126046A (fr)
CN (1) CN118265886A (fr)
AU (1) AU2022420806A1 (fr)
CA (1) CA3236896A1 (fr)
WO (1) WO2023118402A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1383690A (en) 1971-12-15 1974-02-12 Stord Bartz Industri As Heat exchangers
CH576615A5 (en) 1973-07-05 1976-06-15 Fmc Corp Revolving linear tube heat exchanger - with cross-sections avoiding burn-inducing film build-up
WO2015103656A1 (fr) 2014-01-09 2015-07-16 Ecop Technologies Gmbh Dispositif de conversion d'une énergie thermique

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1383690A (en) 1971-12-15 1974-02-12 Stord Bartz Industri As Heat exchangers
CH576615A5 (en) 1973-07-05 1976-06-15 Fmc Corp Revolving linear tube heat exchanger - with cross-sections avoiding burn-inducing film build-up
WO2015103656A1 (fr) 2014-01-09 2015-07-16 Ecop Technologies Gmbh Dispositif de conversion d'une énergie thermique

Also Published As

Publication number Publication date
EP4202342A1 (fr) 2023-06-28
CA3236896A1 (fr) 2023-06-29
KR20240126046A (ko) 2024-08-20
CN118265886A (zh) 2024-06-28
AU2022420806A1 (en) 2024-05-16

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