EP3108145B1 - Rotative et procédé d'échange de chaleur dans une rotative - Google Patents

Rotative et procédé d'échange de chaleur dans une rotative Download PDF

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Publication number
EP3108145B1
EP3108145B1 EP15703933.0A EP15703933A EP3108145B1 EP 3108145 B1 EP3108145 B1 EP 3108145B1 EP 15703933 A EP15703933 A EP 15703933A EP 3108145 B1 EP3108145 B1 EP 3108145B1
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EP
European Patent Office
Prior art keywords
heat exchange
fluid
rotary machine
exchange system
heat carrier
Prior art date
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Application number
EP15703933.0A
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German (de)
English (en)
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EP3108145B2 (fr
EP3108145A1 (fr
Inventor
Simon Gassmann
Benedikt Trottmann
Marcelo Inforsati
Thomas Felix
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Sulzer Management AG
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Sulzer Management AG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
    • F04D29/128—Shaft sealings using sealing-rings especially adapted for liquid pumps with special means for adducting cooling or sealing fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/5866—Cooling at last part of the working fluid in a heat exchanger
    • F04D29/5873—Cooling at last part of the working fluid in a heat exchanger flow schemes and regulation thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals

Definitions

  • the invention relates to a rotary machine for conveying a fluid and a method for the heat exchange in such a according to the preamble of the independent claim of the respective category.
  • Rotary machines such as pumps, are used to convey fluid media in a variety of technological fields.
  • pumps throughout the processing chain which typically begins at the oil or gas field, play an important role and often need to operate under technically demanding conditions. So it is possible, for example, when pumping oil that the medium to be delivered is present under very high temperatures of up to 200 ° C. Such high temperatures place great demands on the pump and in particular on the mechanical seals in such a pump.
  • Mechanical seals are commonly used to seal the shaft which carries the impeller of the pump and which is driven by the drive unit, for example a motor. These seals should prevent leakage of the fluid to be delivered on or along the shaft.
  • mechanical seals are configured as sliding or mechanical seals comprising a stator and a rotor.
  • the rotor is rotatably connected to the shaft, while the stator is fixed relative to the pump housing so that it is secured against rotation.
  • the Rotor and the stator to each other, resulting in a high mechanical stress on these parts results.
  • it is necessary that these seals are not subject in the operating state to high thermal loads.
  • the mechanical seals must be cooled. Too high a temperature in the region of the mechanical seal can lead to material degradation on the sliding surfaces or other parts of the seal, damage to the secondary seals, undesirable phase transitions in the fluid to be pumped or thermally induced changes to the shaft, eg. B. bending.
  • a heat exchange jacket is provided in the vicinity of the mechanical seal, which is a cooling jacket for dissipating heat or a heating jacket for supplying heat depending on the application.
  • This jacket comprises a cavity, which surrounds, for example, the mechanical seal in the form of an annular space, and through which flows a fluid heat carrier, which supplies or dissipates the heat.
  • the cavity has no connection to the space in which the mechanical seal is arranged so that there is no direct contact between the heat transfer medium and the mechanical seal.
  • external auxiliary systems such.
  • an external pump used to promote the fluid heat carrier in the cavity of the heat exchanger shell and to circulate the heat carrier.
  • the second possibility for the heat exchange is based on a direct contact of the mechanical seal with a fluid heat carrier and is commonly referred to as "flushing".
  • the mechanical seal or at least parts thereof is applied directly to a fluid heat carrier to thereby deprive her of heat or supply heat.
  • the circulation of the heat carrier is driven by an external pump.
  • an impeller may be provided on the mechanical seal, which is driven by the rotation of the shaft and circulates the fluid heat carrier.
  • closed flushing systems it is also known to use open systems in which the heat carrier is not circulated in a closed circuit, but is taken from a source and discharged after passing through the pump, such as a sanitation.
  • open systems can usually be dispensed with an external heat exchanger.
  • a rotary machine for conveying a fluid with a drive unit for driving a shaft, with an impeller arranged on the shaft for conveying the fluid, with at least one mechanical seal for sealing the shaft, with a first and a second heat exchange system for cooling or for heating the mechanical seal, wherein the first heat exchange system is designed for direct loading of the mechanical seal with a fluid heat carrier, and the second heat exchange system comprises a heat exchange jacket, which is flowed through by a fluid heat carrier without direct contact with the mechanical seal.
  • the first and second heat exchange systems form a common heat exchange system in which a common fluid heat carrier is circulated, and an impeller for circulating the fluid heat carrier is provided in the heat exchange system.
  • the rotary machine according to the invention is particularly suitable for high-temperature applications in which the fluid to be delivered can have temperatures of up to 200 ° C. or more.
  • the rotary machine is configured as a pump, wherein the drive unit comprises a motor which is arranged in a motor housing.
  • impeller is arranged in a pump housing, which is connected to the motor housing to form an overall housing, so that the pump including the motor is enclosed in a single housing.
  • This compact and outwardly finished design allows the operation of the pump even under difficult environmental conditions.
  • the rotary machine operates in a vertical arrangement. Then it is preferred that the drive unit is arranged in the normal use position above the pump unit, because then the drive unit is not burdened by the weight of the impeller.
  • the barrier liquid is then particularly preferably provided as the fluid heat carrier.
  • the impeller for the circulation of the heat carrier is driven by the drive unit and is preferably provided on the side facing away from the impeller of the drive unit.
  • the rotary machine according to the invention is designed as a subsea pump.
  • a preferred use of the rotary machine is for conveying hot fluids whose temperature is at least 150 ° C.
  • a method for heat exchange in a rotary machine for conveying a fluid having a drive unit for driving a shaft, an impeller arranged on the shaft for conveying the fluid, and at least one mechanical seal for sealing the shaft in which method the mechanical seal is cooled or heated with a first and a second heat exchange system, wherein the mechanical seal is acted upon directly by a fluid heat carrier by means of the first heat exchange system, and in the second heat exchange system flows through a heat exchange jacket of a fluid heat carrier without direct contact with the mechanical seal becomes.
  • the first and second heat exchange systems are connected to a common heat exchange system in which a common fluid heat carrier is circulated, the fluid heat carrier being circulated through an impeller in the heat exchange system.
  • the common heat exchange system is a cooling system.
  • the method is particularly suitable when the rotary machine is a pump, wherein the drive unit comprises a motor which is arranged in a motor housing, wherein the fluid heat carrier is used as a barrier liquid, with which the motor housing is filled and the impeller preferably from the drive unit is driven.
  • the fluid heat carrier is a water-based liquid, because these liquids are generally inexpensive, have sufficient heat capacity and are not harmful to the environment.
  • mixtures of water and glycol are suitable as fluid heat carrier.
  • the inventive method is particularly suitable for high temperature applications in which the fluid to be delivered has a temperature of at least 150 ° C.
  • the method according to the invention is also suitable for applications in which the rotary machine is a subsea pump.
  • a rotary machine according to the invention and a method according to the invention for heat exchange, reference is made by way of example to the case of application, which is particularly important in practice, in that the rotary machine is a pump. It is understood, however, that the invention is not limited to such cases, but also includes all other rotary machines which is provided for shaft seal a mechanical seal.
  • the rotary machine may for example also be a compressor, a turbine or a generator.
  • the heat exchange is a cooling, in which heat is thus extracted from the system. It goes without saying that the invention also encompasses, in an analogous manner, applications in which the heat exchange is heating, ie applications in which heat is supplied to the system.
  • Fig. 1 shows in a very schematic representation of a rotary machine, which is designed as a pump and is generally designated by the reference numeral 1.
  • the pump 1 comprises a drive unit 2 with a motor 21, which is arranged in a motor housing 22 and is designed here as an electric motor.
  • the motor 21 has a motor shaft 25 which is the rotor of the electric motor.
  • the pump 1 further comprises a pump unit 3 with a pump housing 32, in which an impeller 31 is provided for conveying a fluid.
  • the impeller 31 is arranged on a shaft 5, which is connected by means of a coupling 9 with the motor shaft 25, and thus driven by the motor 21 and in rotation about its longitudinal axis A (FIG. Fig. 2 ).
  • the motor housing 22 and the pump housing 32 are firmly connected to each other, for example, screwed together with a plurality of screws, and thus form an overall housing 4 for the drive unit 2 and the pump unit.
  • the shaft 5 and the motor shaft 25 are mounted in a conventional manner in a plurality of thrust bearings 7 and radial bearings 8.
  • the pump unit 3 further comprises an inlet 33 through which the fluid to be delivered by the action of the impeller 31 in the pump housing 32 is sucked, and an outlet 34 through which the fluid to be delivered is ejected.
  • two mechanical seals 6 are provided in the pump, namely a first, which seals the shaft 5 at the boundary between the pump unit 3 and the drive unit 2, so that the fluid to be conveyed is not along the shaft 5 in the drive unit. 2 can reach, and a second, which is provided according to the representation below the impeller 31 and the penetration of the fluid to be conveyed along the shaft 5 in a representation according to the impeller 31 provided below the storage space 35 prevents, in which one of the radial bearing 8 is arranged.
  • the exemplary embodiment of the rotary machine according to the invention described here is a multi-stage process pump for high-temperature applications in which the fluid to be delivered has very high temperatures of, for example, 150 ° C., 180 ° C., 200 ° C. or even more. Such high temperatures can occur, for example, in the natural gas or petroleum production, because there are oil fields in which the oil is present at temperatures of 200 ° C.
  • the embodiment described here is designed as a subsea (subsea) pump, which is mounted on the seabed and works there, z. B. for oil or gas extraction. Especially in such applications an extremely compact design and highest possible reliability and reliability is essential.
  • the pump 1 is configured in a vertical arrangement with overhead drive unit 2, ie in Fig. 1 the pump 1 is shown in its usual position of use.
  • the motor housing 22 of the drive unit 2 is filled in a conventional manner with a barrier liquid 23, which serves to cool the mechanical and electrical components of the motor 21, and for lubrication.
  • Also arranged below the impeller 31 storage space 35 is filled with the sealing liquid 23.
  • Fig. 2 one of the mechanical seals 6 is shown in a highly simplified and schematic way. Mechanical seals are well known to those skilled in the art and therefore require no further explanation here. For that reason, and because it is sufficient for understanding, are in Fig. 2 many details such as the fixations of the parts of the seal 6 or secondary seals, z. B. O-rings, not shown.
  • mechanical seals are configured as sliding or mechanical seals that include a stator 61 and a rotor 62.
  • the rotor is rotatably connected to the shaft 5, while the stator 61 with respect to the overall housing 4 or with respect to the pump housing 32 is fixed so that it is secured against rotation.
  • the stator 61 with respect to the overall housing 4 or with respect to the pump housing 32 is fixed so that it is secured against rotation.
  • the rotor 62 and the stator 61 slide against each other.
  • first heat exchange system 41 and a second heat exchange system 42 - here cooling systems - which are connected to a common heat exchange system 40.
  • This integrated heat exchange system 40 serves to cool the mechanical seals 6.
  • the first heat exchange system 41 for cooling the mechanical seal 6 is a so-called flushing system, in which the mechanical seal 6 or at least parts thereof directly with a fluid heat transfer medium - is acted upon here - a coolant.
  • the mechanical seal 6 is arranged in a sealing chamber 63, which is designed for example as an annular space and the shaft 5 surrounds.
  • the heat transfer medium is introduced through an inlet opening 64.
  • an outlet opening, not shown on the Seal chamber 63 is provided, through which the heat carrier can leave the seal chamber 63 again.
  • the outlet opening is arranged, for example, at 45 ° or rotated by 90 ° with respect to the longitudinal axis A to the inlet opening 64.
  • the seal chamber 63 is substantially completely filled with the heat transfer medium, that is to say the same amount of coolant (heat transfer medium) flows through the inlet opening 64 into the seal chamber 63 as it leaves the seal chamber 63 through the outlet opening.
  • the heat exchange - in this case the cooling - thus takes place by the direct contact of the heat transfer medium with the mechanical seal 6, in which the heat transfer medium of the seal 6 extracts heat and thus cools it.
  • the second heat exchange system 42 for cooling the mechanical seal 6 comprises a heat exchange jacket 421, which in the present embodiment is a cooling jacket 421.
  • the cooling jacket 421 comprises a cavity 422, which is designed, for example, as an annular space and surrounds the entire shaft 5.
  • An inlet 423 is provided, through which the heat carrier is introduced into the cavity 422 and an outlet 424, through which the heat carrier leaves the cavity 422.
  • the cavity 422 is completely filled with the heat transfer medium which is circulated through the cavity 422.
  • this type of heat exchange or cooling there is no direct physical contact between the heat transfer medium and the mechanical seal 6.
  • the cooling jacket 421 is arranged in each case on the hotter side of the mechanical seal 6, ie on the side of the seal 6, in which the higher temperature prevails in the operating state.
  • the pump housing 32 is filled in the operating state with the exception of the storage space 35 with the fluid to be delivered - so for example with the hot oil.
  • the fluid to be delivered is also cooled in the vicinity of the seal 6 by the cooling jacket 421, that is, for example, in the gap 51 which leads to the seal 6.
  • the first heat exchange system 41 and the second heat exchange system 42 are now connected to the integrated common heat exchange system 40.
  • a common fluid heat carrier is necessary, which may be, for example, the same heat carrier as that of the first or the second heat exchange system.
  • the barrier liquid 23 is particularly preferably provided, which is also used for lubricating and cooling the motor 21 or the drive unit 2. This has the advantage that only a single liquid must be provided, which is used both as a barrier liquid 23 and as a fluid heat carrier for the heat exchange system 40. Especially for submarine applications, this measure has a very positive effect on the equipment required.
  • water-based liquids such as a mixture of water and glycol are suitable.
  • the common heat exchange system 40 is designed as a closed system, ie as a cooling system or a cooling circuit in which the fluid heat carrier is circulated.
  • an impeller 44 is provided, which is arranged on the motor shaft 25 and thus by the drive unit 2, especially by the rotation of the motor shaft 25 of the motor 21, is driven.
  • the impeller 44 conveys the heat transfer medium via a main line 45 to a heat exchanger 43, in which the heat carrier emits the heat absorbed at the mechanical seal 6 or in the drive unit 2 or in the storage space 35 and is thereby cooled. Downstream of the heat exchanger 43 now branch off a plurality of lines from the main line 45, first a first line 451, through which the heat transfer medium enters the motor housing 22, as indicated by the arrow on the line 451 symbolically.
  • the heat carrier fills the motor housing and serves as a sealing liquid 23.
  • a second conduit 452 branches off from the main conduit 45, through which the heat carrier passes to the cooling system for the mechanical seal 6.
  • the second conduit 452 branches again into a branch leading to the inlet 423 (FIG. Fig. 2 ) of the cooling jacket 421, and a branch leading to the inlet opening 64 of the sealing space 63. From the outlet opening (not shown) from the sealing space 63 and the outlet 424 of the cavity 422 of the cooling jacket 421, the fluid heat carrier reaches the return line 46 via respective lines which are brought together to line 461.
  • the main line 45 merges into a third line 453, through which the heat transfer medium reaches the cooling system for the lower mechanical seal 6 as shown.
  • the third conduit 453 branches again into a branch leading to the inlet 423 (FIG. Fig. 2 ) of the cooling jacket 421, and a branch leading to the inlet opening 64 of the sealing space 63.
  • this sealing space 63 is connected to the storage space 35, so that the heat transfer medium can also reach the storage space 35 via the same line leading to the inlet opening 64 of the sealing space 63.
  • the fluid heat carrier From the outlet opening of the sealing space 63 and the outlet 424 of the cavity 422 of the cooling jacket 421, the fluid heat carrier reaches the return line 46 via respective lines, which are brought together to line 462.
  • the heat carrier passes back into the region of the impeller 44, which is the circulation of the heat carrier in the closed cooling circuit drives. Also, the introduced via the first line 451 in the motor housing 22 heat transfer is recirculated by the action of the impeller 44, as indicated by the arrow with the reference numeral 463.
  • the impeller 44 for the circulation of the fluid heat carrier is preferably on the side facing away from the impeller 31 of the pump unit 3 side of the drive unit 2 and. the side facing away from the impeller 31 of the motor 21 is provided.
  • the first heat exchange system 41 for the mechanical seals 6 and the second heat exchange system 42 for the mechanical seals 6 are connected to a common heat exchange system 40, thus forming an integral heat exchange system for the mechanical seals 6.
  • the common heat exchange system 40 also serves to supply the motor housing with the barrier liquid 23, which is identical to the fluid heat carrier.
  • the sealing liquid 23 is kept in the motor housing 22 at a higher pressure than the fluid to be pumped in the pump housing 32.
  • the pressure of the sealing liquid 23 in the motor housing 22 is for example 20-25 bar higher as the pressure in the pump housing 32nd
  • the inventive method or the inventive rotary machine are suitable for a variety of applications. So they are particularly suitable for high temperature applications and especially for those in the submarine area.
  • the rotary machine according to the invention can be used for conveying oil, gas, seawater or so-called "produced water".
  • the pump can be configured as a single-phase, as a multi-phase or as a hybrid pump with the accordingly adapted thereto wheels. It is possible to design as well as single-stage as well as multi-stage pumps.
  • the proposed solution according to the invention by their integrated heat exchange system is an efficient, reliable, aperatively simple and compact way to cool or for heating mechanical seals.
  • a vertical arrangement is preferred in which the drive unit 2 is arranged above the pump unit 3.
  • horizontal arrangements are possible in which the drive unit 2 and the pump unit 3 are arranged side by side. Such an arrangement is often preferred when the pump is not used in subsea operation but, for example, on land, or on ships or on drilling platforms.
  • the rotary machine or the method according to the invention is also suitable for cryogenic applications, for example for the pumping of liquid gases in cryotechnology.
  • the mechanical seals are heated or heated by the heat transfer medium.
  • the heat exchanger 43 then serves to supply heat to the heat carrier, which then transports this in a similar manner to the mechanical seals.
  • the heat exchange jacket of the second heat exchange system is then arranged on the colder side of the mechanical seal 6, that is to say on the side of the mechanical seal 6 which, in the operating state, faces the region of lower temperature.
  • the invention is not limited to pumps, but is also suitable for all other rotary machines in which mechanical seals are provided, such as compressors, turbines or generators.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Manufacture Of Motors, Generators (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • General Induction Heating (AREA)

Claims (13)

  1. Une machine rotative pour convoyer un fluide avec une unité d'entraînement (2) pour entraîner un arbre (5), avec une roue (31) disposée sur l'arbre (5) pour convoyer le fluide, avec au moins un joint mécanique (6) pour étanchéifier l'arbre (5), avec un premier et un deuxième système d'échange de chaleur (41; 42) pour refroidir ou chauffer le joint mécanique (6), dans lequel le premier système d'échange de chaleur (41) est conçu avec un caloporteur fluide pour appliquer directement le joint mécanique (6), et le deuxième système d'échange de chaleur (42) comprend une chemise d'échange de chaleur (421), qui peut être traversé par un caloporteur fluide sans contact direct avec le joint mécanique (6), caractérisé en ce que la machine rotative est conçue comme une pompe sous-marine et le premier et le deuxième système d'échange de chaleur (41; 42) forment un système d'échange de chaleur commun (40) dans lequel un caloporteur fluide commun peut circuler, et en ce qu'une roue à aubes (44) est prévue dans le système d'échange de chaleur (40) pour faire circuler le caloporteur fluide.
  2. Une machine rotative selon la revendication 1, qui est conçue comme une pompe, dans lequel l'unité d'entraînement (2) comprend un moteur (21) qui est disposé dans un boîtier du moteur.
  3. Une machine rotative selon la revendication 2, dans laquelle la roue (31) est disposée dans un boîtier de pompe (32) qui est relié au boîtier du moteur (22) en un boîtier total (4).
  4. Une machine rotative selon l'une des revendications précédentes, dans laquelle l'unité d'entraînement (2) est disposée au-dessus de l'unité de pompe (3) dans la position normale d'utilisation.
  5. Une machine rotative selon l'une des revendications 2 à 4, dans laquelle le boîtier du moteur (22) est rempli d'un liquide de barrage (23) à l'état de fonctionnement.
  6. Une machine rotative selon la revendication 5, dans laquelle le liquide de barrage (23) est prévu comme caloporteur fluide.
  7. Une machine rotative selon l'une des revendications précédentes, dans laquelle la roue à aubes (44) est entraînée par l'unité d'entraînement (2) pour faire circuler le caloporteur fluide et est prévue de préférence sur le côté de l'unité d'entraînement (2) opposé à la roue (31).
  8. Une utilisation d'une machine rotative selon l'une des revendications précédentes pour convoyer des fluides chauds dont la température est d'au moins 150°C.
  9. Un procédé pour l'échange de chaleur dans une machine rotative pour convoyer un fluide, qui présente une unité d'entraînement (2) pour entraîner un arbre (5), une roue (31) disposée sur l'arbre (5) pour convoyer le fluide, et au moins un joint mécanique (6) pour étanchéifier l'arbre (5), dans lequel procédé le joint mécanique (6) est refroidi ou chauffé avec un premier et un deuxième système d'échange de chaleur (41; 42), dans lequel le joint mécanique (6) est appliqué directement avec un caloporteur fluide au moins du premier système d'échange de chaleur (41) et, dans le deuxième système d'échange de chaleur (42), une chemise d'échange de chaleur (421) est traversée par un caloporteur fluide sans contact direct avec le joint mécanique (6), caractérisé en ce que la machine rotative est une pompe sous-marine et le premier et le deuxième système d'échange de chaleur (41; 42) sont reliés à un système d'échange de chaleur commun (40) dans lequel un caloporteur fluide commun est circulé et en ce que le caloporteur fluide est circulé par une roue à aubes (44) dans le système d'échange de chaleur.
  10. Un procédé selon la revendication 9, dans lequel le système d'échange de chaleur commun est un système de refroidissement.
  11. Un procédé selon l'une des revendications 9 ou 10, dans lequel la machine rotative est une pompe, dans lequel l'unité d'entraînement (2) comprend un moteur, qui est disposé dans un boîtier du moteur (22), dans lequel le caloporteur fluide est utilisé comme fluide de barrage (23) avec lequel le boîtier du moteur (22) est rempli, et dans lequel la roue à aubes (44) est de préférence entraîné par l'unité d'entraînement (2).
  12. Un procédé selon l'une des revendications 9 à 11, dans lequel le caloporteur fluide est un liquide à base d'eau.
  13. Un procédé selon l'une des revendications 9 à 12, dans lequel le fluide à convoyer a une température d'au moins 150°C.
EP15703933.0A 2014-02-19 2015-02-02 Rotative et procédé d'échange de chaleur dans une rotative Active EP3108145B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14155716 2014-02-19
PCT/EP2015/052089 WO2015124414A1 (fr) 2014-02-19 2015-02-02 Machine rotative et procédé d'échange de chaleur dans une machine rotative

Publications (3)

Publication Number Publication Date
EP3108145A1 EP3108145A1 (fr) 2016-12-28
EP3108145B1 true EP3108145B1 (fr) 2019-10-02
EP3108145B2 EP3108145B2 (fr) 2022-07-27

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EP15703933.0A Active EP3108145B2 (fr) 2014-02-19 2015-02-02 Rotative et procédé d'échange de chaleur dans une rotative

Country Status (12)

Country Link
US (1) US10557474B2 (fr)
EP (1) EP3108145B2 (fr)
KR (1) KR20160124076A (fr)
CN (1) CN105940225B (fr)
AU (1) AU2015221121B2 (fr)
BR (1) BR112016009943B1 (fr)
CA (1) CA2926371A1 (fr)
ES (1) ES2750312T5 (fr)
MX (1) MX2016010065A (fr)
RU (1) RU2670994C2 (fr)
SG (1) SG11201602881XA (fr)
WO (1) WO2015124414A1 (fr)

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CN108488073B (zh) * 2018-05-18 2023-07-04 广州市昕恒泵业制造有限公司 一种环保型浆液循环泵组
SG10201912904SA (en) * 2019-02-18 2020-09-29 Sulzer Management Ag Process fluid lubricated pump and seawater injection system
RU191959U1 (ru) * 2019-04-16 2019-08-28 Федеральное государственное бюджетное образовательное учреждение высшего образования "Кубанский государственный технологический университет" (ФГБОУ ВО "КубГТУ") Управляемый каскадный электрический привод
EP3739215A1 (fr) * 2020-04-20 2020-11-18 Sulzer Management AG Pompe lubrifiée dans un fluide de traitement
DE102021129695A1 (de) * 2021-11-15 2023-05-17 KSB SE & Co. KGaA Kreiselpumpe mit Kühleinsatz

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CH536955A (de) 1971-11-24 1973-05-15 Feodor Burgmann Jr Asbest Und Gekühlte Gleitringdichtung
CH560341A5 (en) 1973-02-13 1975-03-27 Sulzer Ag Pump arrangement with slide ring seal - incorporates pressure increase element in front of blocking circuit
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US2687096A (en) 1950-01-26 1954-08-24 Combustion Eng Seal in centrifugal pump
US3467396A (en) 1967-05-10 1969-09-16 Durametallic Corp Internally cooled seal assembly
CH536955A (de) 1971-11-24 1973-05-15 Feodor Burgmann Jr Asbest Und Gekühlte Gleitringdichtung
CH560341A5 (en) 1973-02-13 1975-03-27 Sulzer Ag Pump arrangement with slide ring seal - incorporates pressure increase element in front of blocking circuit
DE3136721A1 (de) 1981-09-16 1983-03-31 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Verfahren zur vermeidung von wellenverkruemmungen bei horizontalen kreiselpumpen zur foerderung heisser medien und einrichtungen zur durchfuehrung des verfahrens
WO2013182528A1 (fr) * 2012-06-06 2013-12-12 Alstom Technology Ltd Dispositif d'étanchéité de pompe

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EP3108145B2 (fr) 2022-07-27
SG11201602881XA (en) 2016-05-30
RU2016125738A (ru) 2018-03-22
BR112016009943A2 (fr) 2017-08-01
AU2015221121A1 (en) 2016-07-21
ES2750312T5 (es) 2022-10-07
CN105940225B (zh) 2019-02-22
RU2670994C2 (ru) 2018-10-29
BR112016009943B1 (pt) 2022-08-02
CA2926371A1 (fr) 2015-08-27
MX2016010065A (es) 2016-10-07
KR20160124076A (ko) 2016-10-26
RU2016125738A3 (fr) 2018-09-18
CN105940225A (zh) 2016-09-14
ES2750312T3 (es) 2020-03-25
AU2015221121B2 (en) 2018-11-08
EP3108145A1 (fr) 2016-12-28
US10557474B2 (en) 2020-02-11
US20160348687A1 (en) 2016-12-01
WO2015124414A1 (fr) 2015-08-27

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