US20150330407A1 - Turbomachine having a temperature-controlled cover - Google Patents

Turbomachine having a temperature-controlled cover Download PDF

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Publication number
US20150330407A1
US20150330407A1 US14/380,966 US201314380966A US2015330407A1 US 20150330407 A1 US20150330407 A1 US 20150330407A1 US 201314380966 A US201314380966 A US 201314380966A US 2015330407 A1 US2015330407 A1 US 2015330407A1
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US
United States
Prior art keywords
temperature
control
shaft
turbomachine
cover
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.)
Abandoned
Application number
US14/380,966
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English (en)
Inventor
Ricarda Klett
Erich Muranyi
Dieter Nass
Gregor Senyk
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.)
Siemens AG
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Siemens 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
Application filed by Siemens AG filed Critical Siemens AG
Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KLETT, RICARDA, SENYK, GREGOR, MURANYI, ERICH, NAB, DIETER
Publication of US20150330407A1 publication Critical patent/US20150330407A1/en
Abandoned legal-status Critical Current

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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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • 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
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid 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
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • 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
    • F04D29/06—Lubrication
    • F04D29/063—Lubrication specially adapted for elastic fluid pumps
    • 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
    • F04D29/083—Sealings especially adapted for elastic fluid pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/403—Casings; Connections of working fluid especially adapted for elastic fluid pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps

Definitions

  • the following relates to a turbomachine having a lower housing part, an assemblage—which is placed in the lower housing part from above and comprises two mutually opposing housing covers and a rotor, guided between the two housing covers, having a shaft—and an upper housing part, which encloses the assemblage from above and is secured to the lower housing part.
  • Turbomachines are used to expand or compress gases.
  • inlet gases are introduced into the turbine at high pressure and expand there, giving off energy to the rotor.
  • Compressors are used to compress air or other gases to final pressures of up to 100 bar or more.
  • aggressive gases which are not intended to pass into the environment to be compressed. Accordingly, turbomachines should be sealed off such that the operating gases thereof cannot escape to the outside, or can escape to the outside only insignificantly, through the gaps between the shaft and the housing.
  • GB 219 016 A discloses a turbo-generator arrangement having a turbine arranged in a housing.
  • a shaft of the turbine is mounted on separate pillow blocks arranged outside the turbine housing and in their own housings.
  • the shaft mounts are oil lubricated, the bearing lubrication oil being located inside bearing housings of the pillow blocks. Leakage steam from the turbine housing and radiant heat from the turbine housing can lead to undesirable heating of the bearing lubrication oil in the bearing housings of the pillow blocks.
  • GB 219 016 A provides screwed-on protective covers on the bearing housings, which covers are in each case water-cooled.
  • An aspect relates to a turbomachine by means of which a reliable shaft seal can be achieved.
  • An aspect further relates to a turbomachine of the type mentioned in the introduction, in which at least one of the covers has a temperature-control means which is guided around the shaft and serves to control the temperature of the cover in the region around the shaft. A temperature-induced movement of the cover and the shaft with respect to one another can be countered.
  • Embodiments of the invention are based on the consideration that turbomachines are supplied with gases, the temperature of which can deviate sometimes considerably from the housing temperature of the turbomachine.
  • gases the temperature of which can deviate sometimes considerably from the housing temperature of the turbomachine.
  • a turbine is supplied with a hot gas which expands in the turbine. Accordingly, some elements of the turbine are heated more by the hot gas than others.
  • compressors it is possible for extremely cold gases to be introduced and compressed, and so these gases cool the housing greatly at the location of the influx.
  • different elements of the turbomachine cool at different rates. This also affects the two axial covers of the housing, which cool down or heat up relatively rapidly and greatly relative to the shaft and the housing.
  • a shaft seal is arranged between the shaft and the axial covers in which it is mounted, for example, a labyrinth seal or a fluid seal, having a gap between its rotating part on the shaft and its static part on the cover. If such a cooling or heating acts on the sealing region, this can lead to drawbacks with respect to the seal. In order to ensure an optimum seal, the gap should be as small as possible, but it has to be just large enough to avoid any abutment of the elements when the shaft is in operation. If the cover around the shaft cools down, it contracts such that the gap grows and the seal deteriorates.
  • the gap shrinks in the case of the cover heating up to a high temperature, for example, on the gas outlet side of a compressor.
  • the gap In order to avoid any abutment, the gap must in this case be chosen so as to be accordingly large enough in all permitted operational temperatures of the cover. Consequently, the seal gap must be dimensioned so as to be relatively large, which is not conducive to a good seal.
  • cover seal may be provided by two or more seal stages, wherein the inner stage has a larger diameter than the outer stage.
  • the cover may be pressed axially outward against the seals in order to provide a seal with respect to the housing.
  • this embodiment makes it necessary to place the rotor, together with both covers, into the lower part of the housing as one assembly unit or as one assemblage.
  • the cover of large machines it is possible for the cover of large machines to be temperature-controlled, during operation, in the region around the shaft such that the gap does not change much during operation, such that it remains close to a gap width which is optimum for the seal, in terms of its dimensions.
  • Elaborate thermal insulation of the cover may be dispensed with, or the cost of insulation may be kept low.
  • the temperature-control means may be a heating means and/or a cooling means. It can expediently be used both for cooling and for heating. This is of particular advantage in the case of a compressor since in this case the housing cover at the gas inlet is cooled by inflowing cold gases and the housing cover at the gas outlet is heated by outflowing hot gases. With the aid of the temperature-control means, which is expediently operated in the same manner in both covers, it is possible for the housing cover at the gas inlet to be heated and the housing cover at the gas outlet to be cooled.
  • the turbomachine may be an expansion machine, such as a turbine, or a compressor, for example, a turbocompressor, in particular a single-spool radial compressor.
  • the assemblage may contain further elements in addition to the cover and the rotor, for example, a flow guiding device, in particular an inflow guiding device.
  • the temperature-control means is guided about a shaft seal which is arranged between the cover and the shaft. In this manner the shaft seal can be protected, all around the ring, from the undesirable temperature, heat or cold, which acts from outside.
  • Temperature control of the cover in particular of the sealing region of the cover about the shaft, may be performed in a plurality of ways. Heating coils may be used, although the electricity of these must be well-shielded. It is also possible to use heating pads, although these must be well-sealed and pressure-resistant. It is particularly advantageous if the temperature-control means has a first temperature-control duct in the cover which is fluidically connected to a temperature-control fluid reservoir. In this manner, temperature-control fluid can be brought to a desired temperature and can be guided around the shaft or the shaft seal, where it gives off its heat or cold.
  • a temperature-control fluid which may be any appropriate fluid. If, however, the temperature-control fluid used is bearing oil which is provided for mounting the shaft, the bearing oil is then used for multiple purposes, such that a further fluid reservoir and an additional fluid temperature-control means may be dispensed with.
  • the temperature-control duct is advantageously machined directly into the cover, depending on the length, such that the temperature-control fluid flows directly through the cover.
  • the temperature-control duct is machined into the inner side of the cover. Since this inner side is in direct contact with the operating gas, it is particularly cold or hot, such that the cover is markedly cooled or heated from that point. If the temperature-control duct is machined into the inner side of the cover, this undesirable temperature effect can be counteracted particularly effectively.
  • a flow guiding device which may be an inflow guiding device or an outflow guiding device, may lie on the inner side of the cover.
  • the temperature-control means has a second temperature-control duct arranged radially outside the first temperature-control duct.
  • the second temperature-control duct may be directly connected to the first temperature-control duct, such that a flow passes through both ducts, one after the other, or they may be separate, such that for example a flow passes through them in parallel.
  • the temperature-control duct prefferably be guided about the shaft in the shape of an open ring.
  • the ring must be open in order to permit an inlet and an outlet.
  • this opening in the ring which in the following will be referred to as the gap free from temperature-control ducts, heat or cold can penetrate radially from outside into the inner region of the duct and thus to the shaft seal.
  • the second temperature-control duct is guided about the first temperature-control duct such that a tangential gap, free from temperature-control ducts, in the region of the first temperature-control duct is shielded in the radially outward direction by the second temperature-control duct.
  • the two temperature-control ducts are connected to one another such that temperature-control fluid from the temperature-control fluid reservoir flows first through the radially inner temperature-control duct and thence into the radially outer temperature-control duct, before returning to the temperature-control fluid reservoir.
  • temperature-control ducts having different functions, in particular a radial shielding function and an axial shielding function. Both functions may be achieved if both temperature-control ducts have a rectangular cross section and one of the temperature-control ducts has a longer extent in the axial direction and the other of the temperature-control ducts has a longer extent in the radial direction. A longer extent in the axial direction can achieve a radial shielding and a longer extent in the radial direction can achieve an axial shielding
  • the radially outer temperature-control duct has a longer extent in the axial direction and the radially inner temperature-control duct has a longer extent in the radial direction.
  • the radially innermost region can thus be most effectively shielded against heat or cold from an inflow guiding device.
  • a gas supply for a shaft seal is guided radially between two temperature-control ducts of the temperature-control means. It is thus possible for gas supplied to the shaft seal to be held at a desired temperature and thus a good seal to be maintained.
  • the shaft seal may be a gas- or oil-operated fluid seal. A labyrinth seal is also possible.
  • FIG. 1 shows a schematic section representation of a turbomachine
  • FIG. 2 shows an embodiment of a lower housing part of the turbomachine having an installed cover
  • FIG. 3 shows a view in section of a radially inner part of the cover about the shaft with multiple temperature-control ducts
  • FIG. 4 shows an axial plan view of the guiding of two temperature-control ducts.
  • the housing is divided into a lower housing part and an upper housing part.
  • a rotor assemblage is inserted from above into the lower housing part. This is schematically illustrated in FIG. 1 .
  • the lower housing part 4 of the turbomachine 2 stands on a solid underlying surface and the assemblage 6 is lowered from above into the lower housing part 4 .
  • the upper housing part 8 is placed onto the lower housing part 4 and screwed together therewith, resulting in the overall housing 10 .
  • the assemblage is surrounded by the housing 10 , wherein two covers 12 of the assemblage 6 remain visible from the outside and can also be designated part of the housing 10 .
  • the two covers 12 are in turn connected to the rotor 14 , the shaft 16 of which is guided through the two covers 12 and is sealed off in the two covers 12 by way of a shaft seal (not illustrated).
  • the rotor comprises, in addition to the shaft 16 , multiple rotor disks of the turbomachine.
  • FIG. 2 shows a rough perspective illustration of the lower housing part 4 with one of the two covers 12 .
  • the turbomachine 2 is a single-spool radial compressor having a gas inlet 18 and a gas outlet 20 .
  • the gas to be compressed flows into the turbomachine 2 through the gas inlet 18 , is compressed by the rotation of the rotor 14 and leaves the turbomachine 2 in a compressed and heated state through the gas outlet 20 .
  • the lower housing part 4 is secured to the solid underlying surface via supports 22 .
  • FIG. 2 does not show an assembled state of the turbomachine 2 since, for the sake of improved clarity, the cover 12 is illustrated on its own without the rotor 14 and the further opposite cover 12 .
  • FIG. 2 would be considered to be complete with the cover 12 shown being placed on the shaft 16 of the rotor 14 and the opposite cover 12 likewise being positioned on the shaft 16 .
  • this assemblage 6 is then deposited in the lower housing part 4 .
  • FIG. 3 shows a view in section of a radially inner part of the cover 12 about the shaft 16 .
  • Multiple seal elements 26 of a shaft seal which atmospherically shields an inner gas region of the compressor 2 from the outer region of the compressor 2 , are arranged in a sealing region 24 .
  • the cover 12 has, in the axial direction in the sealing region 24 , a temperature-control means 28 which comprises multiple temperature-control ducts 32 , 34 .
  • a fluid supply 36 for supplying gas or sealing oil to at least one of the seal elements 26 is arranged between the temperature-control ducts 32 , 34 .
  • a mount 38 for the shaft 16 in a pillow block 40 is shown axially further out.
  • a housing cover insert 42 of an inflow guiding device which steers the inflowing operating gas, which is to be compressed, to the blades of the rotor 14 is shown axially inside the cover 12 .
  • the two temperature-control ducts 32 , 34 are shown in a schematic axial section view in FIG. 4 .
  • Bearing oil as temperature-control fluid is stored in a temperature-control fluid reservoir 44 , is pumped thence to a heater 46 , which can also be used as a cooler for cooling the temperature-control fluid, where it is brought to a desired temperature, that is to say, it is cooled or heated with respect to the surroundings.
  • the temperature-control fluid reaches the radially inner temperature-control duct 34 via a supply line 48 and flows about the shaft 16 (not shown) in annular fashion in a not fully closed loop, in order to reach the outer temperature-control duct 32 via a connecting duct 50 .
  • the temperature-control fluid flows in the opposite tangential direction in the outer temperature-control duct 32 , again in annular fashion, about the shaft 16 in order to then be fed back to the temperature-control fluid reservoir 44 via an outlet 52 .
  • the opposite tangential flow direction in the two temperature-control ducts 32 , 34 produces an even tangential temperature control of the cover 12 about the shaft 16 .
  • the radially innermost temperature-control duct 34 is supplied, via the supply line 48 , with temperature-control fluid directly from the heater 46 , such that the temperature can be adjusted with precision there, which is particularly advantageous in the innermost region of the cover 12 .
  • the two temperature-control ducts 32 , 34 are guided with respect to one another in such a manner that the radially outer temperature-control duct 32 is guided radially about a tangential gap 54 , free from temperature-control ducts, of the inner temperature-control duct 34 such that, in the region of the gap 54 , the shaft 16 is shielded in the radial direction by the outer temperature-control duct 32 .
  • the outer temperature-control duct 32 is formed as a radial duct; its purpose is first of all thermal shielding in the radial direction. Accordingly, its rectangular, elongate cross section is longer in the axial direction than in the radial direction.
  • the radially inner temperature-control duct 34 is formed as an axial duct; its purpose is first of all thermal shielding in the axial direction. Accordingly, its rectangular, elongate cross section is longer in the radial direction than in the axial direction.
  • a further radial duct may also be present.
  • Both temperature-control ducts 32 , 34 are created in the inside of the cover 12 .
  • the axial duct 34 predominantly shields the cover 12 from cold from the flow guiding device or housing cover insert 42 .
  • the radial duct 32 shields the inner region of the cover 12 from cold from the gas inlet 18 which predominantly penetrates radially from outside inwards in the cover 12 .
  • the inner region of the cover 12 is shielded, by all the ducts 32 , 34 , from the cold emanating from inflowing gas, which is to be compressed, such that the inner region of the cover 12 and thus also the shaft seal is kept within a desired temperature range.
  • FIGS. 3 and 4 show only that axial cover 12 of the housing 10 which is positioned at the gas inlet 18 .
  • the cover 12 at the outlet 20 is also formed in the same manner. It also contains the temperature-control ducts in the same configuration, which are connected to the temperature-control fluid reservoir 44 in parallel with the temperature-control ducts 32 , 34 of the inlet-side cover 12 . They are therefore supplied with the same temperature-control fluid which is guided, via supply lines 48 , with the same temperature to both covers 12 . Since the inlet-side cover 12 is cooled by the operating gas and the outlet-side cover 12 is heated, the same fluid takes on different functions in the two covers 12 , namely heating in the inlet-side cover 12 and cooling in the outlet-side cover 12 .

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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)
  • Turbine Rotor Nozzle Sealing (AREA)
US14/380,966 2012-02-29 2013-02-27 Turbomachine having a temperature-controlled cover Abandoned US20150330407A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102012203144.8 2012-02-29
DE102012203144A DE102012203144A1 (de) 2012-02-29 2012-02-29 Strömungsmaschine
PCT/EP2013/053911 WO2013127837A1 (de) 2012-02-29 2013-02-27 Strömungsmaschine mit temperiertem deckel

Publications (1)

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US20150330407A1 true US20150330407A1 (en) 2015-11-19

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US14/380,966 Abandoned US20150330407A1 (en) 2012-02-29 2013-02-27 Turbomachine having a temperature-controlled cover

Country Status (5)

Country Link
US (1) US20150330407A1 (de)
EP (1) EP2820309A1 (de)
CN (1) CN104160157A (de)
DE (1) DE102012203144A1 (de)
WO (1) WO2013127837A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2017081810A1 (ja) * 2015-11-13 2018-07-19 三菱重工コンプレッサ株式会社 遠心圧縮機
US20180274388A1 (en) * 2017-03-23 2018-09-27 Hanwha Power Systems Co., Ltd. Oil seal structure and compressing apparatus including the same
US20180320597A1 (en) * 2015-11-10 2018-11-08 Siemens Aktiengesellschaft Method for assembling a turbomachine, and turbomachine
US20190101133A1 (en) * 2016-03-28 2019-04-04 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor
US11022125B2 (en) * 2017-02-28 2021-06-01 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor

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Publication number Priority date Publication date Assignee Title
DE102014207461A1 (de) * 2014-04-17 2015-10-22 Siemens Aktiengesellschaft Anordnung von Bauteilen einer Fluidenergiemaschine, Fügeverfahren
CN109469646B (zh) * 2018-10-22 2021-06-11 沈阳透平机械股份有限公司 空分机壳结构

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180320597A1 (en) * 2015-11-10 2018-11-08 Siemens Aktiengesellschaft Method for assembling a turbomachine, and turbomachine
JPWO2017081810A1 (ja) * 2015-11-13 2018-07-19 三菱重工コンプレッサ株式会社 遠心圧縮機
US20180347589A1 (en) * 2015-11-13 2018-12-06 Mitsubishi Heavy Industries, Ltd. Centrifugal compressor
US10527062B2 (en) * 2015-11-13 2020-01-07 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor
US20190101133A1 (en) * 2016-03-28 2019-04-04 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor
US10876546B2 (en) * 2016-03-28 2020-12-29 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor
US11022125B2 (en) * 2017-02-28 2021-06-01 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor
US20180274388A1 (en) * 2017-03-23 2018-09-27 Hanwha Power Systems Co., Ltd. Oil seal structure and compressing apparatus including the same
US10865795B2 (en) * 2017-03-23 2020-12-15 Hanwha Power Systems Co., Ltd. Oil seal structure and compressing apparatus including the same

Also Published As

Publication number Publication date
WO2013127837A1 (de) 2013-09-06
CN104160157A (zh) 2014-11-19
EP2820309A1 (de) 2015-01-07
DE102012203144A1 (de) 2013-08-29

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