EP3108145B2 - Rotationsmaschine sowie verfahren für den wärmeaustausch in einer rotationsmaschine - Google Patents

Rotationsmaschine sowie verfahren für den wärmeaustausch in einer rotationsmaschine Download PDF

Info

Publication number
EP3108145B2
EP3108145B2 EP15703933.0A EP15703933A EP3108145B2 EP 3108145 B2 EP3108145 B2 EP 3108145B2 EP 15703933 A EP15703933 A EP 15703933A EP 3108145 B2 EP3108145 B2 EP 3108145B2
Authority
EP
European Patent Office
Prior art keywords
heat exchange
fluid
rotary machine
heat
exchange system
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP15703933.0A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3108145B1 (de
EP3108145A1 (de
Inventor
Simon Gassmann
Benedikt Trottmann
Marcelo Inforsati
Thomas Felix
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sulzer Management AG
Original Assignee
Sulzer Management AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=50156575&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3108145(B2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Sulzer Management AG filed Critical Sulzer Management AG
Publication of EP3108145A1 publication Critical patent/EP3108145A1/de
Publication of EP3108145B1 publication Critical patent/EP3108145B1/de
Application granted granted Critical
Publication of EP3108145B2 publication Critical patent/EP3108145B2/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04D29/08—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
    • 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
    • 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
    • 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
    • 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 heat exchange in such a machine according to the preamble of the independent patent claim of the respective category.
  • Rotary machines such as pumps, are used to convey fluid media in a wide variety of technological fields.
  • pumps play an important role in the entire processing chain, which usually starts at the oil or gas field, and often have to work under technically very demanding conditions.
  • the medium When pumping crude oil, for example, it is possible for the medium to be pumped to be at 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 such as a motor. These seals are intended to prevent the fluid to be pumped from escaping on or along the shaft.
  • mechanical seals are designed as face or slide ring seals, which include a stator and a rotor. The rotor is connected to the shaft in a rotationally fixed manner, while the stator is fixed with respect to the pump housing in such a way that it is secured against rotation. During the rotation of the shaft, the rotor and the stator slide against each other, which results in a high mechanical load on these parts. For the proper operation of such mechanical seals, it is necessary for these seals not to be subject to excessive thermal loads in the operating state.
  • the mechanical seals must be cooled, especially in the case of such fluids that are pumped at high temperatures. Too high a temperature in the area of the mechanical seal can lead to material degradation on the sliding surfaces or other parts of the seal, damage to the secondary seals, unwanted phase transitions in the fluid to be pumped or thermally induced changes in the shaft, e.g. B. Bends.
  • 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 includes a cavity that surrounds the mechanical seal in the form of an annular space, for example, and through which a fluid heat carrier flows, 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 e.g. B. used an external pump to promote the fluid heat transfer medium in the cavity of the heat exchange jacket and to circulate the heat transfer medium.
  • the second option for heat exchange is based on direct contact of the mechanical seal with a fluid heat transfer medium and is usually referred to as "flushing".
  • the mechanical seal or at least parts thereof, is directly subjected to a fluid heat transfer medium in order to withdraw heat from it or to supply heat to it.
  • a fluid heat transfer medium for this type of heat exchange, it is known to circulate the fluid heat carrier in a closed circuit, which then comprises an external heat exchanger, to which the heat carrier releases the heat absorbed by the mechanical seal (cooling of the seal), or to which the heat carrier transfers the absorbs heat, which it supplies to the mechanical seal (heating of the seal).
  • the circulation of the heat carrier is driven by an external pump.
  • an impeller can also be provided, e.g. on the mechanical seal, which is driven by the rotation of the shaft and circulates the fluid heat carrier.
  • a rotary machine for conveying a fluid according to claim 1 is proposed.
  • the rotary machine according to the invention is also particularly suitable for high-temperature applications in which the fluid to be conveyed can have temperatures of up to 200° C. or more.
  • the rotating machine is designed as a pump, with the drive unit comprising 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 design which is closed off from the outside, allows the pump to be operated even under difficult environmental conditions.
  • the rotary machine works in a vertical arrangement. It is then preferred that the drive unit is arranged above the pump unit in the normal position of use, because then the drive unit is not loaded by the weight of the impeller.
  • a further advantageous measure with regard to cooling, lubricating and protecting the drive unit, e.g. against the fluid to be pumped, is if the motor housing is filled with a sealing liquid during operation.
  • the sealing liquid is then particularly preferably provided as the fluid heat carrier.
  • the impeller for circulating the heat carrier is driven by the drive unit and is preferably provided on the side of the drive unit facing away from the impeller.
  • a preferred use of the rotary machine is for conveying hot fluids, the temperature of which is at least 150°C.
  • a method according to claim 9 is also proposed for heat exchange in a rotary machine for conveying a fluid.
  • the common heat exchange system is a refrigeration system.
  • the method is particularly suitable when the rotary machine is a pump, the drive unit comprising a motor which is arranged in a motor housing, the fluid heat carrier being used as a sealing liquid with which the motor housing is filled and the impeller preferably being driven by 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 a fluid heat carrier.
  • the method according to the invention is particularly suitable for high-temperature applications in which the fluid to be pumped has a temperature of at least 150°C.
  • 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 application that is particularly important in practice, that the rotary machine is a pump.
  • the invention is not limited to such cases, but also includes all other rotary machines in which a mechanical seal is provided for shaft sealing.
  • the rotary machine can also be a compressor, a turbine or a generator, for example.
  • the heat exchange is cooling, in which heat is therefore withdrawn from the system. It goes without saying that the invention also includes applications in the same way in which the heat exchange is heating, ie applications in which heat is supplied to the system.
  • the pump 1 1 shows, in a very schematic representation, a rotary machine which is designed as a pump and is denoted overall by the reference numeral 1.
  • the pump 1 includes 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 also includes 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 to the motor shaft 25 by means of a coupling 9 and is thus driven by the motor 21 and rotated about its longitudinal axis A ( 2 ) is relocated.
  • the motor housing 22 and the pump housing 32 are firmly connected to one another, for example screwed together with several screws, and thus form an overall housing 4 for the drive unit 2 and the pump unit 3
  • the shaft 5 and the motor shaft 25 are mounted in a number of axial bearings 7 and radial bearings 8 in a manner known per se.
  • the pump unit 3 also includes an inlet 33, through which the fluid to be pumped is sucked into the pump housing 32 by the action of the impeller 31, and an outlet 34 through which the fluid to be pumped is pushed out.
  • two mechanical seals 6 are provided in the pump, namely a first one, which seals the shaft 5 at the boundary between the pump unit 3 and the drive unit 2, so that the fluid to be pumped cannot flow along the shaft 5 into the drive unit 2 and a second, which is provided below the impeller 31 according to the illustration and which prevents the fluid to be pumped from penetrating along the shaft 5 into a bearing space 35 which is provided below the impeller 31 according to the illustration and in which one of the radial bearings 8 is arranged.
  • the exemplary embodiment of the rotary machine according to the invention explained here is a multi-stage process pump for high-temperature applications in which the fluid to be pumped has very high temperatures of, for example, 150° C., 180° C., 200° C. or even more. Such high temperatures can occur, for example, in natural gas or oil production, because there are oil fields in which the oil is present at temperatures below 200°C.
  • the embodiment described here is designed as a subsea (subsea) pump that is mounted on the seabed and operates there, z. B. for oil or gas production. Especially with such applications, an extremely compact design and the highest possible operational safety and reliability are essential.
  • the Pump 1 designed in a vertical arrangement with the drive unit 2 on top, ie in 1 the pump 1 is shown in its usual position of use.
  • the motor housing 22 of the drive unit 2 is filled with a sealing liquid 23 in a manner known per se, which is used to cool the mechanical and electrical components of the motor 21 and for lubrication.
  • the storage space 35 arranged below the impeller 31 is also filled with the sealing liquid 23 .
  • mechanical seals are designed as face or slide ring seals, which include a stator 61 and a rotor 62 .
  • the rotor is connected to the shaft 5 in a rotationally fixed manner, while the stator 61 is fixed in relation to the overall housing 4 or in relation to the pump housing 32 in such a way that it is secured against rotation.
  • the stator 61 is fixed in relation to the overall housing 4 or in relation to the pump housing 32 in such a way that it is secured against rotation.
  • the rotor 62 and the stator 61 slide against each other.
  • a first heat exchange system 41 and a second heat exchange system 42 are provided—here cooling systems—which are connected to form a common heat exchange system 40 .
  • This integrated heat exchange system 40 is used 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 is or are acted upon directly by a fluid heat carrier—here a coolant.
  • a fluid heat carrier here a coolant.
  • the mechanical seal 6 is arranged in a sealing space 63, which is designed, for example, as an annular space and surrounds the shaft 5.
  • the heat transfer medium is introduced into this sealing space 63 through an inlet opening 64 .
  • an outlet opening (not shown) is provided on the sealing space 63 through which the heat carrier can leave the sealing space 63 again.
  • the outlet opening is arranged, for example, rotated by 45° or by 90° with respect to the longitudinal axis A in relation to the inlet opening 64 .
  • the sealing chamber 63 is essentially completely filled with the heat carrier, i.e. the same amount of coolant (heat carrier) flows through the inlet opening 64 into the sealing chamber 63 as flows out of the sealing chamber 63 through the outlet opening.
  • the heat exchange - here the cooling - thus takes place through the direct contact of the heat transfer medium with the mechanical seal 6, in which the heat transfer medium extracts heat from the seal 6 and thus cools it.
  • the second heat exchange system 42 for cooling the mechanical seal 6 includes a heat exchange jacket 421, which is a cooling jacket 421 in the present exemplary embodiment.
  • the cooling jacket 421 includes 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 transfer medium is introduced into the cavity 422, and an outlet 424, through which the heat transfer medium leaves the cavity 422.
  • the cavity 422 is completely filled with the heat carrier that 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 in each case arranged 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 in the operating state, with the exception of the storage space 35 with the fluid to be pumped - so for example with the hot oil - filled.
  • the fluid to be conveyed in the vicinity of the seal 6 is also cooled by the cooling jacket 421 , ie for example also in the gap 51 which leads to the seal 6 .
  • This cooling of the fluid to be conveyed in the immediate vicinity of the mechanical seal 6 also significantly reduces the heat input into the seal 6 by the fluid to be conveyed, which corresponds to a cooling of the seal 6 .
  • the first heat exchange system 41 and the second heat exchange system 42 are now connected to form the integrated common heat exchange system 40 .
  • the consequence of this is that there must be a common fluid heat transfer medium for the common heat exchange system 40 .
  • different fluid heat carriers could also be used for these two separate systems in the case of separate first and second heat exchange systems, the solution according to the invention requires a common fluid heat carrier which, for example, can be the same heat carrier as that of the first or second heat exchange system.
  • the sealing liquid 23 which is also used for lubricating and cooling the motor 21 or the drive unit 2 , is particularly preferably provided as the fluid heat carrier for the common heat exchange system 40 .
  • This has the advantage that only a single liquid has to be provided, which is used both as a sealing liquid 23 and as a fluid heat carrier for the heat exchange system 40 . Especially for subsea applications, this measure has a very positive effect in terms of the equipment required.
  • Water-based liquids such as a mixture of water and glycol are particularly suitable as a fluid heat transfer medium.
  • 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 transfer medium is circulated.
  • An impeller 44 is provided for the circulation of the heat transfer medium, which is arranged on the motor shaft 25 and is thus driven by the drive unit 2, specifically by the rotation of the motor shaft 25 of the motor 21.
  • the impeller 44 conveys the heat transfer medium via a main line 45 to a heat exchanger 43 in which the heat transfer medium releases the heat absorbed at the mechanical seal 6 or in the drive unit 2 or in the storage space 35 and is thereby cooled.
  • a plurality of lines now branch off from the main line 45 downstream of the heat exchanger 43, first a first line 451, through which the heat carrier enters the motor housing 22, as symbolically indicated by the arrow on the line 451.
  • the heat carrier fills the motor housing and serves as a sealing liquid 23.
  • a second line 452 branches off from the main line 45 further downstream, through which the heat transfer medium reaches the cooling system for the mechanical seal 6 .
  • the second line 452 in turn branches into a branch leading to the inlet 423 ( 2 ) of the cooling jacket 421, and into a branch leading to the inlet port 64 of the seal chamber 63. From the outlet opening (not shown) from the sealing chamber 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 combined to form line 461.
  • the main line 45 merges into a third line 453, through which the heat carrier reaches the cooling system for the lower mechanical seal 6 according to the illustration.
  • the third line 453 in turn branches into a branch leading to the inlet 423 ( 2 ) of the cooling jacket 421, and into a branch leading to the inlet port 64 of the seal chamber 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 that leads to the inlet opening 64 of the sealing space 63 .
  • the fluid heat carrier From the outlet opening from the sealing chamber 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 combined to form line 462.
  • the heat carrier returns through the return line 46 to the area of the impeller 44, which drives the circulation of the heat carrier in the closed cooling circuit.
  • the heat transfer medium introduced into the motor housing 22 via the first line 451 is also recirculated by the action of the impeller 44, as indicated by the arrow with reference number 463.
  • the impeller 44 for circulating the fluid heat carrier is preferably on the side of the drive unit 2 or provided on the side of the motor 21 facing away from the impeller 31 .
  • 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 form a common heat exchange system 40, which thus forms 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 sealing liquid 23, which is identical to the fluid heat transfer medium.
  • the sealing liquid 23 in the motor housing 22 is kept under 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 than the pressure in the pump housing 32.
  • the method according to the invention and the rotary machine according to the invention are suitable for a large number of applications. They are particularly suitable for high-temperature applications and especially for those in the subsea area.
  • the rotary machine according to the invention can be used to pump oil, gas, seawater or so-called "produced water".
  • the pump can be designed as a single-phase, multi-phase or hybrid pump with the impellers correspondingly adapted to it. Both configurations as single-stage as well as multi-stage pumps are possible.
  • the solution proposed according to the invention thanks to its integrated heat exchange system, represents an efficient, reliable, simple to use and compact option for cooling or heating mechanical seals.
  • a vertical arrangement is preferred in an embodiment of the pump as a submersible pump, in which the drive unit 2 above the Pump unit 3 is arranged.
  • horizontal arrangements are also possible, in which the drive unit 2 and the pump unit 3 are arranged next to one another.
  • Such an arrangement is often preferred when the pump is not used in submarine operation but, for example, on land, or on ships or on drilling platforms.
  • the rotary machine according to the invention and the method according to the invention are also suitable for low-temperature applications, for example for pumping liquid gases in cryogenics.
  • the mechanical seals are warmed or heated by the heat carrier.
  • the heat exchanger 43 then serves to supply heat to the heat transfer medium, which heat is then transported to the mechanical seals in the same way.
  • the heat exchange jacket of the second heat exchange system is then arranged on the colder side of the mechanical seal 6, ie on that side of the mechanical seal 6 which faces the lower temperature range in the operating state.

Landscapes

  • 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)
EP15703933.0A 2014-02-19 2015-02-02 Rotationsmaschine sowie verfahren für den wärmeaustausch in einer rotationsmaschine Active EP3108145B2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14155716 2014-02-19
PCT/EP2015/052089 WO2015124414A1 (de) 2014-02-19 2015-02-02 Rotationsmaschine sowie verfahren für den wärmeaustausch in einer rotationsmaschine

Publications (3)

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

Family

ID=50156575

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15703933.0A Active EP3108145B2 (de) 2014-02-19 2015-02-02 Rotationsmaschine sowie verfahren für den wärmeaustausch in einer rotationsmaschine

Country Status (12)

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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NO345311B1 (en) * 2018-04-26 2020-12-07 Fsubsea As Pressure booster with integrated speed drive
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 (en) * 2020-04-20 2020-11-18 Sulzer Management AG Process fluid lubricated pump
DE102021129695A1 (de) * 2021-11-15 2023-05-17 KSB SE & Co. KGaA Kreiselpumpe mit Kühleinsatz

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2687096A (en) † 1950-01-26 1954-08-24 Combustion Eng Seal in centrifugal pump
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

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1276451B (de) * 1962-03-23 1968-08-29 Friedrich Wilhelm Pleuger In eine Leitung eingebaute, mit einem Elektromotor gekuppelte Kreiselpumpe
US3467396A (en) 1967-05-10 1969-09-16 Durametallic Corp Internally cooled seal assembly
US3459430A (en) * 1967-07-06 1969-08-05 Borg Warner Mechanical seal assembly
US3478689A (en) * 1967-08-02 1969-11-18 Borg Warner Circulating pump
DE1800254B2 (de) * 1968-01-24 1971-09-30 Vorrichtung zur sicherstellung der kuehlung der wellen abdichtungen und mediumgeschmierten radiallager von unter hohen systemdruecken arbeitenden umwaelzpumpen
JPS5443722B2 (zh) * 1973-02-02 1979-12-21
US4558870A (en) * 1977-11-28 1985-12-17 Borg-Warner Corporation Mechanical seal assembly
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
JP3752348B2 (ja) * 1997-03-14 2006-03-08 株式会社 日立インダストリイズ 多段遠心圧縮機装置およびその運転方法
RU41097U1 (ru) * 2004-01-30 2004-10-10 Общество с ограниченной ответственностью Научно-производственный центр "Анод" Торцовое уплотнение вала агрегата
WO2007110281A1 (de) 2006-03-24 2007-10-04 Siemens Aktiengesellschaft Verdichtereinheit
US8777596B2 (en) 2008-05-06 2014-07-15 Fmc Technologies, Inc. Flushing system
RU2425256C2 (ru) * 2009-08-11 2011-07-27 Открытое акционерное общество "Центральное конструкторское бюро машиностроения" Энергоблок
JP5557752B2 (ja) 2009-09-24 2014-07-23 イーグル工業株式会社 メカニカルシール
RU2418197C1 (ru) * 2009-09-25 2011-05-10 Открытое акционерное общество "Центральное конструкторское бюро машиностроения" Главный циркуляционный насосный агрегат
JP5846967B2 (ja) * 2012-03-02 2016-01-20 株式会社日立製作所 遠心式水蒸気圧縮機およびそれに用いる軸封システム
US9664289B2 (en) 2012-06-06 2017-05-30 General Electric Technology Gmbh Pump sealing device
FR2991736A1 (fr) * 2012-06-06 2013-12-13 Alstom Technology Ltd Dispositif d'etancheite d'une pompe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2687096A (en) † 1950-01-26 1954-08-24 Combustion Eng Seal in centrifugal pump
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

Also Published As

Publication number Publication date
RU2670994C2 (ru) 2018-10-29
BR112016009943B1 (pt) 2022-08-02
ES2750312T5 (es) 2022-10-07
RU2016125738A3 (zh) 2018-09-18
EP3108145B1 (de) 2019-10-02
CN105940225A (zh) 2016-09-14
CA2926371A1 (en) 2015-08-27
RU2016125738A (ru) 2018-03-22
AU2015221121B2 (en) 2018-11-08
ES2750312T3 (es) 2020-03-25
SG11201602881XA (en) 2016-05-30
EP3108145A1 (de) 2016-12-28
BR112016009943A2 (zh) 2017-08-01
KR20160124076A (ko) 2016-10-26
AU2015221121A1 (en) 2016-07-21
US10557474B2 (en) 2020-02-11
US20160348687A1 (en) 2016-12-01
WO2015124414A1 (de) 2015-08-27
CN105940225B (zh) 2019-02-22
MX2016010065A (es) 2016-10-07

Similar Documents

Publication Publication Date Title
EP3108145B2 (de) Rotationsmaschine sowie verfahren für den wärmeaustausch in einer rotationsmaschine
EP1999375B1 (de) Verdichtereinheit
DE102007021720B4 (de) Verdichtersystem für den Unterwassereinsatz im Offshore-Bereich
EP3163086B1 (de) Pumpen-antrieb-einheit zum fördern eines prozessfluids
DE3639719C3 (de) Spaltrohrmagnetpumpe
CH706860A2 (de) Stützvorrichtung zur Stützung eines Turbinenrotors und eines Turbinengehäuses.
DE2349978A1 (de) Mechanische dichtanordnung
DE1058618B (de) Hermetisch abgeschlossene, zur Foerderung eines Mediums hoeherer Temperatur geeignete elektrische Motorpumpe
WO2020099239A1 (de) Elektromotor
DE112012002650T5 (de) Abwärmestromerzeuger
DE102004013053A1 (de) Pumpenaggregat
DE2033711A1 (de) Verfahren zur Verbesserung der Saug fähigkeit von Zentrifugalpumpen sowie Pumpe zur Ausfuhrung des Verfahrens
DE1901284A1 (de) Anlauf-Schmiervorrichtung fuer eine mechanische Dichtung
EP3635259B1 (de) Kreiselpumpe zur förderung heisser medien
DE102012217361A1 (de) Elektrische Maschine mit Wärmetauscher
DE102020003928A1 (de) Pumpenanordnung mit temperierbarem Gehäuseteil
DE102008046890A1 (de) Drehdurchführung mit axialer Gleitdichtungseinrichtung
WO1997048167A1 (de) Flüssigkeitsgefüllter unterwassermotor
DE102005003476B4 (de) Spaltrohrmotor mit geschlossenem Kühlsystem
DE102007036032A1 (de) Unterwassermotor mit Wärmetauscher
DE19809957A1 (de) Mehrwellenvakuumpumpe
EP2598724A1 (de) Dampfturbine sowie verfahren zum kühlen einer solchen
WO2018206157A1 (de) Lageranordnung zur lagerung eines turbinenrotors einer turbomaschine
EP1546563B1 (de) Traglager für eine vertikal angeordnete kreiselpumpe
DE19814485A1 (de) Mehrstufiges Turbogebläse

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20160919

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20171002

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

INTG Intention to grant announced

Effective date: 20190730

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1186482

Country of ref document: AT

Kind code of ref document: T

Effective date: 20191015

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502015010513

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: NO

Ref legal event code: T2

Effective date: 20191002

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20191002

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2750312

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20200325

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200103

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200203

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200102

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200224

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

REG Reference to a national code

Ref country code: DE

Ref legal event code: R026

Ref document number: 502015010513

Country of ref document: DE

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

PG2D Information on lapse in contracting state deleted

Ref country code: IS

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200202

26 Opposition filed

Opponent name: KSB SE & CO. KGAA

Effective date: 20200702

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20200229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200202

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200229

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200229

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1186482

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200202

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

PUAH Patent maintained in amended form

Free format text: ORIGINAL CODE: 0009272

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT MAINTAINED AS AMENDED

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191002

27A Patent maintained in amended form

Effective date: 20220727

AK Designated contracting states

Kind code of ref document: B2

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: DE

Ref legal event code: R102

Ref document number: 502015010513

Country of ref document: DE

REG Reference to a national code

Ref country code: NO

Ref legal event code: TB2

REG Reference to a national code

Ref country code: ES

Ref legal event code: DC2A

Ref document number: 2750312

Country of ref document: ES

Kind code of ref document: T5

Effective date: 20221007

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NO

Payment date: 20230220

Year of fee payment: 9

Ref country code: FR

Payment date: 20230221

Year of fee payment: 9

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230412

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20240326

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240219

Year of fee payment: 10

Ref country code: GB

Payment date: 20240219

Year of fee payment: 10