EP0529379B1 - Zusammengesetzter Rotor für Strömungsmaschinen - Google Patents

Zusammengesetzter Rotor für Strömungsmaschinen Download PDF

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Publication number
EP0529379B1
EP0529379B1 EP92113544A EP92113544A EP0529379B1 EP 0529379 B1 EP0529379 B1 EP 0529379B1 EP 92113544 A EP92113544 A EP 92113544A EP 92113544 A EP92113544 A EP 92113544A EP 0529379 B1 EP0529379 B1 EP 0529379B1
Authority
EP
European Patent Office
Prior art keywords
joining means
fluid flow
threads
flow machine
rotor parts
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.)
Expired - Lifetime
Application number
EP92113544A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0529379A1 (de
Inventor
Jörg Urban
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.)
KSB AG
Original Assignee
KSB 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 KSB AG filed Critical KSB AG
Publication of EP0529379A1 publication Critical patent/EP0529379A1/de
Application granted granted Critical
Publication of EP0529379B1 publication Critical patent/EP0529379B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/06—Rotors for more than one axial stage, e.g. of drum or multiple disc type; Details thereof, e.g. shafts, shaft connections
    • F01D5/066—Connecting means for joining rotor-discs or rotor-elements together, e.g. by a central bolt, by clamps
    • 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
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

  • the invention relates to a turbomachine according to the preamble of the protection claim.
  • the connecting screw rings can be designed as a separate component or as an integral part of the rotor part. Of at least two existing thread sections, only one thread section takes over the power transmission, while the other thread section only performs a securing function due to its large play. If the rotor parts are deflected too much, their movement is limited by the flanks of the securing thread. The torque is transmitted through the frictional forces between the centering ring and the rotor parts as well as through the friction in the connecting thread. Despite the high manufacturing costs of this solution, the prestressing forces of the respective connection can only be set very imprecisely due to the frictional forces on the centering ring.
  • the resiliently designed screw rings are designed to compensate for temperature influences on the rotor. This The design principle of only transmitting the torque between the rotor parts to be connected by friction forces makes this solution seem unsuitable in the long term. Machine revisions with disassembly and subsequent assembly of the rotor parts negatively affect the quality of the connection.
  • the object of the invention is to develop a shaftless design of a rotor which can be easily adapted to different operating conditions for multi-stage and highly loaded turbomachines. This object is achieved in accordance with the characterizing part of the main claim. Further configurations of the solution can be found in the subclaims.
  • the advantages of this design are diverse.
  • the centering and form-fitting connection between the impeller parts lying against each other on the front side takes over the torque transmission and centering of the rotor.
  • one impeller part is centered on the adjacent impeller part in a force-transmitting manner.
  • This connection can be made precisely as a toothing or corresponding design with little effort.
  • the joining means that press the impeller parts against each other enable reliable pressing of the parts to be assembled together due to their different threaded sections.
  • the joining means can have a section of smaller diameter and / or wall thickness, which enables a better adjustability of the prestressing forces.
  • the desired bias can be set in the simplest manner for each connection.
  • the threaded sections are arranged so that the direction of rotation of the machine can not loosen the dressing. Additional anti-rotation devices of known design can be used if necessary.
  • the main advantage of this connection is the distribution of the forces to be transmitted.
  • the torque to be transmitted is absorbed exclusively by the positive connection between the hubs of the rotor parts to be connected.
  • the axial forces take over the joining means extending in the same direction.
  • the joining means have in their interior or on their end faces a positive design, which makes it possible to carry out the screwing with the aid of a correspondingly shaped and insertable tool.
  • the fittings are hollow. As a result, part of the conveying means can flow through the shaft assembly in the axial direction and the temperature differences in the area of the joints can thus be reduced.
  • Drive shaft journals or shaft bearing journals can be stored as assemblies with the respective bearing or sealing units so that, if necessary, they can be assembled with the corresponding impeller parts to form a uniform rotor. Any necessary relief water from an axle thrust relief device can also be returned to the side with less pressure by the rotor. External bypass lines are no longer required. At the same time, there is the advantage of rapid and uniform heating or cooling of the entire turbomachine unit.
  • a shaft stub (2) protrudes into the inlet area (1) thereof, which, with a centering and form-fitting design (3) designed as spur toothing, bears against a correspondingly designed spur toothing of a first impeller (4).
  • the first impeller (4) also has a positive-locking design (3) on its back on the pressure side, in which a correspondingly toothed hub of a second impeller (5) engages.
  • the separation point between the impellers (4, 5) lies in the area of the transition from the first to the second stage.
  • the impeller (6) of a fifth stage is shown here at the start of installation.
  • a joining means (7) which is equipped with a contour (8) designed as an internal hexagon, can be set in rotation by a suitably designed tool (9). Any other force-transmitting form of the tool (9) with a correspondingly designed configuration of the joining means is also conceivable.
  • the joining means (7) is inserted at the end of an already installed impeller or a shaft journal and its thread (10) is brought into contact with the thread (11) of the impeller (12) already assembled here.
  • the impeller to be assembled, here (6) is brought into contact with its inner thread (13) on the second thread (14) of the joining means (7).
  • the wheel parts to be connected are held and pulled against each other by a rotational movement of the joining means (7) and clamped together. For example, if the threads (10, 11) are left-hand threads, then the threads (13, 14) are right-hand threads.
  • the reverse arrangement can also be used. This depends on the direction of rotation of the shaft assembly and the load on it.
  • the respective direction of thread rotation is selected so that the most dangerous direction of load rotation has a contracting effect on the threaded connections.
  • the wall thickness of the joining agent and the thread formation are designed in accordance with the axial forces prevailing in the turbomachine.
  • the thread pitch can be the same or different. If, on the other hand, threads with coarse thread sections are to be used for the parts to be connected, then for example the threads (10, 11) must have a smaller diameter and the pitch of the threads (10, 11) must differ from the pitch of the threads (13, 14) his. As a result of the smaller diameters, the joining means can be pushed through the hubs and connected to the adjacent parts. The thread length must be adjusted accordingly.
  • the first three joining means (7) shown in the drawing connect the impeller (4) to the shaft journal (2) and the impellers of the first three stages to one another and have additional sealing elements (15) as examples. These are designed as O-rings and lie sealingly on the inside of the hub. They have the task of sealing the respective stage pressure. Their use may depend on the operating conditions and the requirements placed on the turbomachine.
  • FIG. 2 shows a completely assembled three-stage flow machine in the form of a centrifugal pump.
  • a total of four identical joining means (7) connect three impellers (4, 5, 12) to one another and to a shaft journal (2), which serves here as a drive shaft journal.
  • a smaller joining means (16) which has no throughflow opening, connects in the same way a bearing journal (17) with a relief piston (18) screwed onto the last impeller (12).
  • the bearing journal (17) is drilled through and closed with a stopper (19).
  • the relief water passing the relief piston (18) flows through bores (20, 21) and through the hollow-shaped joining means (7) back to the inlet area (1).
  • toothing as a centering and force-transmitting element and the arrangement of the different threads in the hub areas of the impellers results in a very vibration-resistant rotor that can be used for high loads.
  • a section (22) of lesser wall thickness is present between the threads of the joining means (7). In contrast to the graphical representation chosen here, this can also be arranged in the area of the outer diameter of the joining means (7). This facilitates a more precise setting of the preload forces.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP92113544A 1991-08-29 1992-08-08 Zusammengesetzter Rotor für Strömungsmaschinen Expired - Lifetime EP0529379B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4128673 1991-08-29
DE4128673A DE4128673C1 (zh) 1991-08-29 1991-08-29

Publications (2)

Publication Number Publication Date
EP0529379A1 EP0529379A1 (de) 1993-03-03
EP0529379B1 true EP0529379B1 (de) 1995-05-17

Family

ID=6439393

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92113544A Expired - Lifetime EP0529379B1 (de) 1991-08-29 1992-08-08 Zusammengesetzter Rotor für Strömungsmaschinen

Country Status (3)

Country Link
EP (1) EP0529379B1 (zh)
DE (2) DE4128673C1 (zh)
ES (1) ES2073825T3 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7828531B2 (en) 2004-02-13 2010-11-09 Ksb Aktiengesellschaft Vertical centrifugal pump assembly

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI940630A (fi) * 1994-02-11 1995-08-12 Ahlstroem Oy Keskipakopumppu
DE10248162A1 (de) * 2002-10-16 2004-04-29 Ksb Aktiengesellschaft Einen Spalt definierendes, auf einer Welle anzuordnendes Element
ITCO20130071A1 (it) * 2013-12-18 2015-06-19 Nuovo Pignone Srl Metodo per assemblare un insieme di giranti mediante tiranti, girante e turbomacchina
ITUB20160070A1 (it) 2016-01-18 2017-07-18 Nuovo Pignone Tecnologie Srl Macchina rotante con albero rotante migliorato avente estremità di albero leggere
CN109630206A (zh) * 2018-12-16 2019-04-16 中国航发沈阳发动机研究所 一种多级轮盘转子结构
DE202021101195U1 (de) 2021-03-10 2021-05-27 3W Turbo Gmbh Gasgelagerte Mikro-Turbomaschine
DE102021105732A1 (de) 2021-03-10 2022-09-15 3W Turbo Gmbh Gasgelagerte Mikro-Turbomaschine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1551402A (en) * 1925-08-25 Botob fob elastic-pi
US2422763A (en) * 1944-03-02 1947-06-24 Worthington Pump & Mach Corp Centrifugal compressor
FR937533A (fr) * 1946-11-26 1948-08-19 Cem Comp Electro Mec Rotor de compresseur axial
CH257836A (de) * 1947-08-07 1948-10-31 Sulzer Ag Läufer für Kreiselmaschinen, insbesondere für Gasturbinen.
US3269324A (en) * 1964-12-30 1966-08-30 Tait Mfg Co The Pumps
US3269323A (en) * 1964-12-30 1966-08-30 Tait Mfg Co The Pumps
DE1801398A1 (de) * 1968-10-02 1970-10-01 Aeg Kanis Turbinen Laeufer einer Axialstroemungsmaschine
DD95762A1 (zh) * 1972-03-16 1973-02-12

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7828531B2 (en) 2004-02-13 2010-11-09 Ksb Aktiengesellschaft Vertical centrifugal pump assembly

Also Published As

Publication number Publication date
DE59202214D1 (de) 1995-06-22
ES2073825T3 (es) 1995-08-16
DE4128673C1 (zh) 1992-08-06
EP0529379A1 (de) 1993-03-03

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