US3801217A - Fluid machines - Google Patents

Fluid machines Download PDF

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Publication number
US3801217A
US3801217A US00216960A US3801217DA US3801217A US 3801217 A US3801217 A US 3801217A US 00216960 A US00216960 A US 00216960A US 3801217D A US3801217D A US 3801217DA US 3801217 A US3801217 A US 3801217A
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United States
Prior art keywords
end member
pump
delivery
delivery end
inlet
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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.)
Expired - Lifetime
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US00216960A
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English (en)
Inventor
M Ryall
H Anderson
G Pezzani
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.)
Weir Pumps Ltd
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Weir Pumps Ltd
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Publication date
Application filed by Weir Pumps Ltd filed Critical Weir Pumps Ltd
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Publication of US3801217A publication Critical patent/US3801217A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/063—Multi-stage pumps of the vertically split casing type

Definitions

  • a multi-stage centrifugal pump which includes a plurality of stages the impellers of which are mounted on [3O] Fnreign Application Priority Data a shaft common to all stages. All the stages are Feb. 3, 1971 Great Britain 3851/71 ount d ithin a tie-frame carrying pump inlet and June 18,1971 Great Britain 28654/71 delivery connections and are arranged between an inlet end member and a delivery end member.
  • the U-S- Cl. A, C end members and the casings of each tage are ar- 1 1 F041! F04!
  • 29/44 ranged in abutting relationship so that they are urged 1 1 Wild 1 415/219 4 199 A, 198 in 11 direction towards the inlet member by the delivcry pressure acting on a combination of a delivery end 1 1 References Cited I cover and the delivery end member, the inlet end UNITED STATES PATENTS member being held against movement relative to the 1,837,873 12/1931 Macmeeken 415/199 A tie-frame while the delivery end member is capable of 2,108,786 2/1938 Bigeiow et a1...
  • the present invention concerns improvements in or relating to fluid machines.
  • a multi-stage centrifugal pump including a plurality of stages each of which includes a casing and an impeller rotatable therein, the pump including a shaft having an impeller of each stage mounted thereon, a tie frame carrying pump inlet and delivery connections and surrounding said casing to define an annular passage therearound, fluid communication means to connect said annular passage with said pump inlet connection, an inlet end member and a delivery end member, said end members and casings being arranged in abutting relationships so that they are urged in a direction towards the inlet end member by the delivery pressure acting on the delivery end member, holding means being provided to hold the inlet end member, against movement relative to the tie frame in said direction and seal means being provided between the delivery end member and the tie frame to permit relative movement therebetween.
  • FIG. 1 is a partial sectional elevation of a first pump
  • FIG. 2 is a similar view of a second pump
  • FIG. 3 is a similar view of a third pump.
  • FIG. 4 shows a modification which can be made to any one of the pumps shown in FIGS. 1 to 3, but is shown here as a modification at the delivery end cover 42 of FIG. 1.
  • a multi-stage centrifugal pump has a plurality of stages which are arranged in series fluid communication, each stage including a casing 12 and an impeller 14, the impeller being rotatable within the casing which defines a diffuser section 16 and a fluid return section 18 directing fluid from the diffuser to the eye 20 of the impeller of the next stage.
  • the impellers 14 of each stage are mounted on a common shaft 22 which is supported at either end of the pump in bearings 24, and the normal glands, thrust bearings, balance rings, etcetera associated with this type of pump are provided for the shaft.
  • a hon-pressurised barrel 26 including inlet and delivery connections 28 and 30 respectively, the barrel serving as a tie frame, as will be described in more detail hereinafter.
  • the casing 12 of each stage abuts the casings of the neighbouring stage or stages and resilient sealing means 32 are provided to ensure a fluid tight connection between the casings.
  • bolts 34 are provided to connect the stages.
  • An inlet end member 36 and delivery end member 38 are provided to co-operate between the tie frame 26 and the assembly of stages.
  • the inlet end member 36 is fixed to an inlet end cover 40 which closes the tie frame 26 and is rigidly bolted thereto.
  • the projections from cover 40 define passages providing fluid communication between the inlet connection and the eye of the impeller of the lowest pressure stage. Similarly fluid communication between the diffuser 44 of the last or highest pressure stage and the delivery connection 30 is provided also.
  • a delivery end cover 42 is provided also and closes the delivery end of the tie frame 26 at the same time having bearings, glands and balance means for the shaft 22 which passes therethrough.
  • the delivery end cover 42 is retained in position against the end of the tie frame by bolts 42a.
  • the inlet end cover 40 and inlet end member 36 are rigidly mounted against movement.
  • the delivery end member 38 is slidably mounted in the tie frame 26 (note the slight axial space between components 38 and 44) and when the pump is fully assembled the delivery end member abuts the casing 12 of the last stage while the casing of the first stage abuts the inlet end member.
  • delivery pressure acting upon a portion of the delivery end cover 42 and the delivery end plate 38 forces this plate into closer engagement with the casing of the last but one stage and this force is transmitted through the casings to the inlet end cover.
  • Seal means 48 are provided between the delivery end member and the tie frame or barrel 26 to allow relative movement between these components without leakage of fluid therebetween.
  • the seal means conveniently comprises a suitable sliding packing which abuts an annular surface 50 formed on the delivery end member, the outer and inner sides of the packing abutting the sides of an annular passage 52 defined by the tie frame 26 and a cylindrical surface 54 of the delivery end member.
  • a secondary seal 56 between the delivery end member and the tie frame is provided, this sea] taking the form of a piston ring mounted in a groove cut in the cylindrical surface 54 of the delivery end member.
  • the assembly of stages end members and end covers is entered into the tie frame 26 at the delivery end thereof and preferably the driving unit, for example, a motor a steam turbine or other machine, is located at the delivery end.
  • the driving unit for example, a motor a steam turbine or other machine
  • tie frame 26 has been described as a non-pressurised barrel.
  • the frame since it is not pressurised or subjected to great stresses may take other convenient forms, for example, a plurality of bars connecting suitable inlet and delivery branches.
  • the barrel of the embodiment is not pressurised and, in fact, is connected to atmosphere, it is possible by including a pressure gauge (not shown) between the sliding joint packing and the piston ring to detect and measure leakage past the packing.
  • a pressure gauge (not shown) between the sliding joint packing and the piston ring to detect and measure leakage past the packing.
  • a multi-stage centrifugal pump includes a plurality of stages arranged with the outlet from one stage in fluid communication with the inlet to the next adjacent stage, each stage including a substantially cylindrical casing 112 and an impeller 114 mounted for rotation within the casing,
  • each impeller being carried by a shaft 122, common to all the stages.
  • the assembly of stages is mounted within a tie frame comprising a tubular barrel portion 126 and a branch vessel 160 rigidly fixed in a fluid tight manner at one end thereof.
  • the branch vessel 160 is substantially tubular and includes fluid inlet and outlet connections 128 and 130 respectively, the inlet 128 connection communicating with an annular space 162 defined by the exterior of the stage casings and the interior of the vessel while the outlet branch 130 communicates with the outlet 144 from the last stage.
  • the end of the tubular barrel portion 126 of the tie frame remote from the branch vessel 160 is closed by an inlet end cover 140 rigidly fixed thereto by bolts 1400, said cover carrying bearings and glands 124 for the shaft, having an inlet end member 136 formed integrally therewith and being provided with fluid passages 164 which guide fluid from the annular space 162 surrounding the casings of the stages to the inlet to the first or lowest pressure stage.
  • the branch vessel 160 is effectively closed by a delivery end cover 142 which has components assembled thereon including a balancing disc or drum 166 for the pump and a gland device and journal and thrust bearings 124 for the pump shaft 122 which passes therethrough, the shaft terminating in a coupling 168 adapted for attachment to a suitable driving unit.
  • a delivery end member 138 is provided also, this member being formed as part of the casing 112 of the highest pressure stage. This member 138 is a sliding fit in the branch vessel 160.
  • a resilient and slidable sealing means 148 such as a sliding packing or O-rings is housed in an annular passage 152 defined between the end member 138 and the branch essel 160, the sealing means 148 being held against movement out of this housing by a ring fitted 150 in a radial recess in the member.
  • sealing means in the form of a piston ring 156 held in a radial groove formed in the end member downstream of the sealing means 148 is provided and a tapping 168 through the branch vessel is provided in communication with the space between the sealing means and piston ring so that leakage of fluid past the sealing means can be detected.
  • the stages of the pump of this second embodiment are held together by the delivery pressure acting upon a portion of the delivery end cover 142 and the delivery end member 138 and forcing the stages into closer engagement with each other and with the inlet end member 136, sealing means 132 being provided between each stage casing.
  • lugs are provided on the stages through which tie bolts 134 can be fitted to connect a stage with the next adjacent stage.
  • the flow of incoming hot or cold water passes in a symmetrical manner through the annulus 162 and the stages so that all pressure walls are treated uniformly in the circumferential and axial aspects thus minimising distortion and almost eliminating differential movement at the sliding joints.
  • the assembly of the pump of this second embodiment is similar to that of the first embodiment, that is the stages with the end members and end covers are assembled on the shaft but this assembly is fitted axially into the tie frame from the end thereof remote from the branch vessel 160.
  • increase in delivery pressure causes not only a closer inter-engagement between the stages and the inlet end member but also a closer engagement of the self sealing delivery end cover 142 with a branch vessel flange 146.
  • FIG. 3 a pump having similar features to that of the first and second embodiments is shown, this pump however being assembled and dismantled through the delivery end of the tie frame.
  • inlet end cover and member and branch vessel are quite similar to those of the pump of the second embodiment shown in FIG. 2, they will not be described in detail and have been given the same reference numerals on the drawing.
  • the casing of the highest pressure stage defines the delivery end member 138, which in operation is also subjected to delivery pressure and tends to slide towards the inlet end member 136, movement without leakage being permitted by seals 148 and 156.
  • the delivery end cover 142 in this embodiment, is bolted on to the end of the branch vessel by bolts 142a to enable the assembly of shaft, stages, end plates and inlet end cover to be introduced to the interior of the barrel and branch vessel from the delivery end, this requiring the use of an erection cradle.
  • the pumps described above offer the advantages previously obtainable only from expensive barrel type pumps, for example, it has a very rigid pump casing which can carry large pipework loads and moments, it has the ability to withstand thermal shock and it provides the facility of removing the assembly of stages on the shaft without disturbing delivery and inlet pipework. Furthermore the pump is relatively economic when compared with normal barrel type pumps. In the normal barrel type pump, for example, the barrel which contains the stages is designed to withstand pump pressure and consequently the construction thereof is expensive.
  • a further important advantage of the pumps described above is the elimination of thermal distortion and the very high thermal stresses which may be involved in previous pump designs, when hot liquids are pumped.
  • the pumps of all the embodiments achieve this by providing a non-pressurised tie frame or a tie frame which is subjected only to inlet pressure which withstands only modest loads, for example, mechanical end loads particularly hydraulic axial loading on the end covers caused by the delivery pressure acting over the area of each stage, and in the case of the tie frame of the second embodiment, in addition by the relatively low inlet pressure; and by permitting the assembly of stages to expand and contract axially independently of the barrel.
  • the complete pump is suspended at or near its centre line by a system of keys and bolts to maintain correct alignment with the driver under all pressure and thermal conditions.
  • the integral construction of the barrel and branch piece and its attachment by bolts and keys to a bed-plate or foundation provides a rigid structure capsule of resisting the loadings imposed on the pump by the piping due to thermal and pressure conditions.
  • this embodiment has the advantage that the thrust bearing which is preferably situated at the delivery end of the shaft, is closer to the balance disc or drum.
  • the assembly of shaft, casings etc. may include two half casings clamped together by a splitting flange in a plane containing the shaft axis.
  • a resilient member 180 in the shape of a conical washer is interposed between an extension from the highest pressure stage diffuser 44 (144) the delivery end cover 42 (142).
  • this member 180 On assembly this member 180 is compressed so that after assembly, on attempting to return to its original undeformed state it tends to force the delivery end cover 42 (142) and the assembly of stages and inlet end cover away from each other and out of the barrel 26 126).
  • interstage bolts 34 (134) may be dispensed with.
  • a multi-stage centrifugal pump including a plurality of stages each of which includes a casing and an impeller rotatable therein, the pump including a shaft having an impeller of each stage mounted thereon, a tie frame carrying pump inlet and delivery connections, and including means surrounding said casings to define an annular passage therearound whereby said casings are subjected to only suction pressure, fluid communication means to connect said annular passage with said pump inlet connection, an inlet end member and a delivery end member, said annular passage extending between said delivery end members and enclosed by said tie frame so that during operation the delivery end member and said plural stage casings as interposed between said inlet and delivery end members are urged together in a direction towards the inlet end member by the delivery pressure acting on the delivery end member, holding means being provided to hold the inlet end member against movement relative to the tie frame in said direction, and seal means being provided between the delivery end member and the tie frame to permit relative movement therebetween.
  • a pump as claimed in claim 1, wherein said seal means between the delivery end member and the tie frame comprises a sliding packing.
  • a pump as claimed in claim 1 further including additional seal means in the form of a piston ring being provided downstream of said seal means between the delivery end member and the tie frame.
  • a pump as claimed in claim 1 further including a resilient member interposed between the highest pressure stage and the delivery end member, said resilient member tending to force the highest pressure stage and delivery end member away from each other.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US00216960A 1971-02-03 1972-01-11 Fluid machines Expired - Lifetime US3801217A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB385171 1971-02-03
GB2865471 1971-06-18

Publications (1)

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US3801217A true US3801217A (en) 1974-04-02

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US00216960A Expired - Lifetime US3801217A (en) 1971-02-03 1972-01-11 Fluid machines

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US (1) US3801217A (en:Method)
AU (1) AU431687B2 (en:Method)
CA (1) CA961346A (en:Method)
DE (1) DE2204995A1 (en:Method)
FR (1) FR2125018A5 (en:Method)
IT (1) IT948934B (en:Method)
SE (1) SE378443B (en:Method)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3942908A (en) * 1974-05-03 1976-03-09 Norwalk-Turbo, Inc. Gas turbine driven high speed centrifugal compressor unit
DE2656826A1 (de) * 1976-08-23 1978-03-09 Worthington Pump Mehrstufige zylinderzentrifugalpumpe
US4190395A (en) * 1978-04-28 1980-02-26 Borg-Warner Corporation Multiple stage pump
US4244675A (en) * 1979-04-30 1981-01-13 Worthington Pump, Inc. Multi-stage barrel type centrifugal pump with resilient compensator means for maintaining the seals between interstage pumping assemblies
US4277223A (en) * 1979-11-29 1981-07-07 Guy F. Atkinson Company Case construction for multi-stage pump
US4299536A (en) * 1979-08-09 1981-11-10 Roy E. Roth Company Multi-stage pumps
DE3537587A1 (de) * 1985-10-31 1987-04-23 Proizv Ob Nevskij Z Im V I Radialverdichter
US5846052A (en) * 1995-09-26 1998-12-08 Ebara Corporation High-pressure multistage pump
US6196809B1 (en) * 1997-03-19 2001-03-06 Hitachi, Ltd. Two-stage centrifugal compressor
US20030021681A1 (en) * 2001-07-24 2003-01-30 Weir Pumps Limited Pump assembly
US6568904B1 (en) * 1994-09-20 2003-05-27 Hitachi, Ltd. Fluidal machine
US20070110569A1 (en) * 2003-11-07 2007-05-17 Franco Sarri Multistage centrifugal compressor having a tank which can be opened horizontally
US20100322765A1 (en) * 2008-03-10 2010-12-23 Man Diesel & Turbo Se Turbo engine with improved compensating piston gasket
US20110206499A1 (en) * 2010-02-24 2011-08-25 Moritsugu Takahiro Double casing type pump and head adjusting method thereof
CN112855549A (zh) * 2019-11-27 2021-05-28 苏尔寿管理有限公司 多级离心泵
US20220018362A1 (en) * 2020-07-14 2022-01-20 Flowserve Management Company Compensation assemblies for fluid handling devices and related devices, systems, and methods
WO2023059321A1 (en) * 2021-10-06 2023-04-13 Siemens Energy Global GmbH & Co. KG In a turbomachine, rotor structure with seal assembly and method in connection with same
WO2024076721A1 (en) * 2022-10-07 2024-04-11 Siemens Energy, Inc. Split casing including a compliant element

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10322382A1 (de) 2003-05-17 2004-12-02 Ksb Aktiengesellschaft Mehrstufige Kreiselpumpe

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR398640A (fr) * 1909-01-19 1909-06-10 Louis Galland Pompe centrifuge et turbo-compresseur multicellulaires
GB168058A (en) * 1920-08-20 1922-08-03 Acec Improvements in and relating to centrifugal pumps, compressors and ventilating fans
US1837873A (en) * 1928-01-25 1931-12-22 Worthington Pump & Mach Corp Centrifugal pump
US2108786A (en) * 1936-09-23 1938-02-22 Pacific Pump Works Duplex high pressure rotary pump
GB526732A (en) * 1939-03-27 1940-09-24 Mather & Platt Ltd Improvements in multi-stage centrifugal pumps
GB645921A (en) * 1948-08-18 1950-11-08 Harland Engineering Co Ltd Improvements in and relating to feed pumps
US2843048A (en) * 1956-03-23 1958-07-15 Gilbert & Barker Mfg Co Liquid pumping apparatus
GB838317A (en) * 1957-07-31 1960-06-22 G & J Weir Ltd Improvements in or relating to centrifugal pumps

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR398640A (fr) * 1909-01-19 1909-06-10 Louis Galland Pompe centrifuge et turbo-compresseur multicellulaires
GB168058A (en) * 1920-08-20 1922-08-03 Acec Improvements in and relating to centrifugal pumps, compressors and ventilating fans
US1837873A (en) * 1928-01-25 1931-12-22 Worthington Pump & Mach Corp Centrifugal pump
US2108786A (en) * 1936-09-23 1938-02-22 Pacific Pump Works Duplex high pressure rotary pump
GB526732A (en) * 1939-03-27 1940-09-24 Mather & Platt Ltd Improvements in multi-stage centrifugal pumps
GB645921A (en) * 1948-08-18 1950-11-08 Harland Engineering Co Ltd Improvements in and relating to feed pumps
US2843048A (en) * 1956-03-23 1958-07-15 Gilbert & Barker Mfg Co Liquid pumping apparatus
GB838317A (en) * 1957-07-31 1960-06-22 G & J Weir Ltd Improvements in or relating to centrifugal pumps

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3942908A (en) * 1974-05-03 1976-03-09 Norwalk-Turbo, Inc. Gas turbine driven high speed centrifugal compressor unit
DE2656826A1 (de) * 1976-08-23 1978-03-09 Worthington Pump Mehrstufige zylinderzentrifugalpumpe
US4098558A (en) * 1976-08-23 1978-07-04 Worthington Pump, Inc. Preassembled unit or cartridge for multi-stage barrel type centrifugal pumps
US4190395A (en) * 1978-04-28 1980-02-26 Borg-Warner Corporation Multiple stage pump
US4244675A (en) * 1979-04-30 1981-01-13 Worthington Pump, Inc. Multi-stage barrel type centrifugal pump with resilient compensator means for maintaining the seals between interstage pumping assemblies
US4299536A (en) * 1979-08-09 1981-11-10 Roy E. Roth Company Multi-stage pumps
US4277223A (en) * 1979-11-29 1981-07-07 Guy F. Atkinson Company Case construction for multi-stage pump
DE3537587A1 (de) * 1985-10-31 1987-04-23 Proizv Ob Nevskij Z Im V I Radialverdichter
US6568904B1 (en) * 1994-09-20 2003-05-27 Hitachi, Ltd. Fluidal machine
US6749397B2 (en) * 1994-09-20 2004-06-15 Hitachi, Ltd. Fluidal machine
US5846052A (en) * 1995-09-26 1998-12-08 Ebara Corporation High-pressure multistage pump
US6196809B1 (en) * 1997-03-19 2001-03-06 Hitachi, Ltd. Two-stage centrifugal compressor
US20030021681A1 (en) * 2001-07-24 2003-01-30 Weir Pumps Limited Pump assembly
GB2379718A (en) * 2001-07-24 2003-03-19 Weir Pumps Ltd Pump assembly
US6884031B2 (en) 2001-07-24 2005-04-26 Weir Pumps Limited Pump assembly
GB2379718B (en) * 2001-07-24 2005-07-13 Weir Pumps Ltd Pump assembly
US20070110569A1 (en) * 2003-11-07 2007-05-17 Franco Sarri Multistage centrifugal compressor having a tank which can be opened horizontally
US7513735B2 (en) * 2003-11-07 2009-04-07 Nuovo Pignone Holding S.P.A. Multistage centrifugal compressor having a tank which can be opened horizontally
US20100322765A1 (en) * 2008-03-10 2010-12-23 Man Diesel & Turbo Se Turbo engine with improved compensating piston gasket
US9494165B2 (en) * 2008-03-10 2016-11-15 Man Diesel & Turbo Se Turbo engine with improved compensating piston gasket
US20110206499A1 (en) * 2010-02-24 2011-08-25 Moritsugu Takahiro Double casing type pump and head adjusting method thereof
US8807915B2 (en) * 2010-02-24 2014-08-19 Mitsubishi Heavy Industries, Ltd. Double casing type pump and performance adjusting method thereof
CN112855549A (zh) * 2019-11-27 2021-05-28 苏尔寿管理有限公司 多级离心泵
EP3828419A1 (en) * 2019-11-27 2021-06-02 Sulzer Management AG Multistage centrifugal pump
US11788532B2 (en) * 2020-07-14 2023-10-17 Flowserve Pte. Ltd. Compensation assemblies for fluid handling devices and related devices, systems, and methods
CN115803529A (zh) * 2020-07-14 2023-03-14 芙罗服务管理公司 用于流体处理装置的补偿组件以及相关装置、系统和方法
US20220018362A1 (en) * 2020-07-14 2022-01-20 Flowserve Management Company Compensation assemblies for fluid handling devices and related devices, systems, and methods
US20240026885A1 (en) * 2020-07-14 2024-01-25 Flowserve Pte. Ltd. Compensation assemblies for fluid handling devices and related devices, systems, and methods
US12123416B2 (en) * 2020-07-14 2024-10-22 Flowserve Pte. Ltd. Compensation assemblies for fluid handling devices and related devices, systems, and methods
US12467460B1 (en) 2020-07-14 2025-11-11 Flowserve Pte. Ltd. Compensation assemblies for fluid handling devices and related devices, systems, and methods
WO2023059321A1 (en) * 2021-10-06 2023-04-13 Siemens Energy Global GmbH & Co. KG In a turbomachine, rotor structure with seal assembly and method in connection with same
CN118056076A (zh) * 2021-10-06 2024-05-17 西门子能源全球有限两合公司 涡轮机中具有密封组件的转子结构和与其相关的方法
US12055152B1 (en) 2021-10-06 2024-08-06 Siemens Energy Global GmbH & Co. KG In a turbomachine, rotor structure with seal assembly and method in connection with same
JP2024537144A (ja) * 2021-10-06 2024-10-10 シーメンス エナジー グローバル ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト ターボ機械において、シールアセンブリを備えたローター構造、およびこれに関連する方法
WO2024076721A1 (en) * 2022-10-07 2024-04-11 Siemens Energy, Inc. Split casing including a compliant element
GB2636311A (en) * 2022-10-07 2025-06-11 Siemens Energy Inc Split casing including a compliant element

Also Published As

Publication number Publication date
SE378443B (en:Method) 1975-09-01
AU431687B2 (en) 1973-02-01
DE2204995A1 (de) 1972-08-24
CA961346A (en) 1975-01-21
AU3788372A (en) 1973-02-01
FR2125018A5 (en:Method) 1972-09-22
IT948934B (it) 1973-06-11

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