WO2007110272A1 - Unité de compresseur - Google Patents

Unité de compresseur Download PDF

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Publication number
WO2007110272A1
WO2007110272A1 PCT/EP2007/051415 EP2007051415W WO2007110272A1 WO 2007110272 A1 WO2007110272 A1 WO 2007110272A1 EP 2007051415 W EP2007051415 W EP 2007051415W WO 2007110272 A1 WO2007110272 A1 WO 2007110272A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor unit
rotor
compressor
motor
rotation
Prior art date
Application number
PCT/EP2007/051415
Other languages
German (de)
English (en)
Inventor
Gaston Mathijssen
Mark Van Aarsen
Original Assignee
Siemens Aktiengesellschaft
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 Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Priority to EP07726371A priority Critical patent/EP1999377A1/fr
Publication of WO2007110272A1 publication Critical patent/WO2007110272A1/fr
Priority to NO20084449A priority patent/NO20084449L/no

Links

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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/601—Mounting; Assembling; Disassembling 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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0686—Units comprising pumps and their driving means the pump being electrically driven specially adapted 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps

Definitions

  • the invention relates to a compressor unit with a motor and a compressor, the motor having a motor rotor and the compressor having a compressor rotor, which rotate as a common rotor about a common axis of rotation, wherein the compressor unit comprises a housing, on which support elements are provided by means of which the compressor unit is mounted in operating position in support points.
  • Preferred field of application of the invention is the undersea production of natural gas.
  • a compressor unit of the aforementioned type is already known from international patent application WO 02/099286 A1.
  • the compressor rotor With the aim of uncompromising simplification to reduce maintenance and at the same time high life there is proposed to make the compressor rotor with the motor rotor in one piece and to store each end by means of only two radial bearings.
  • a separate axial bearing is provided.
  • the axis of rotation of the rotor is vertically aligned, which allows a thrust balance by means of its own weight and exposes the rotor no bending AC voltage from the weight.
  • EP 1 074 746 B1 discloses equipping a turbocompressor with three radial bearings, wherein the motor rotor is connected to the compressor rotor by means of a coupling.
  • the dynamically very dominant motor rotor is mounted by means of two of the three radial bearings and the compressor rotor on the end side of the resulting overall rotor with only one radial bearing.
  • Speed spectra are not too high and on the other hand may not be exposed to the surrounding components due to their damping function to a large load or excitation become.
  • other conditions apply to underwater operation because the surrounding medium has different damping properties than air.
  • the invention has made it its mission to achieve with the least possible effort a good vibration behavior.
  • Vibration amplitudes in the region of the center of gravity or rotational center of gravity of the rotor are smaller in relation to the remaining regions of the machine and, on the other hand, the damping at this point of the moving system is particularly efficient. While a fixation outside the
  • Center of gravity of the rotor has the consequence that the center of gravity receives an excitation from the restoring force of the bearing and moves despite its moment of inertia, which leads to destabilization of the overall system, stabilizes a fixation of the center of rotation of the rotor on the one hand the center of gravity position and on the other hand, the adjacent systems. Due to the symmetry properties of the center of gravity, the support elements not only experience the slightest translatory excitation in the support points, but also a moment load from the oscillation is completely eliminated.
  • the common plane of the support points and the rotational center of gravity of the rotor is perpendicular to the preferably vertically oriented axis of rotation. So that no unfavorable moments arise due to the position of the support points.
  • An advantageous development provides that in three support points by means of preferably one support element in each case, the support of the compressor unit takes place in a plane of the center of gravity of the rotor. In this way, the unit is kept in a defined spatial position and avoided a mechanical over-determination.
  • Particularly useful is a combination of the described storage with a vertically oriented axis of rotation, because the compressor units are regularly formed along the axis of rotation elongated and in this way the support points are positioned relatively close to the rotor's center of gravity.
  • a symmetry of the support points around the center of rotation can be realized in a constructively problem-free manner and, in addition to a substantially equal distance between the support points and the center of gravity, an angular symmetry can be achieved. This means that in the preferred embodiment with three support points they are each arranged at a distance of 120 ° to each other.
  • the support points may be at least partially designed as sliding bearings, so that thermal relative movements between a frame on which the compressor unit is supported and the compressor unit itself do not lead to a mechanical load on the involved components.
  • a certain position of the compressor unit can be achieved by means of one or more fixed bearing in the three support points.
  • a preferred provided in the alignment of the axis of rotation of the rotor centering provide for a particular position of the compressor unit.
  • the arrangement of the centering in alignment with the axis of rotation has the additional advantage that at this point a damping particularly efficiently reduces the vibration amplitudes.
  • the compressor unit can be mounted in a frame in the manner described, wherein the frame is expediently to be mounted on a base member which receives further adjacent modules.
  • a preferred embodiment of the invention provides that the compressor unit is rotatably mounted in the frame about a horizontal axis, so that at a vertical axis of rotation of the rotor, the end located in the operating position can be turned upwards.
  • This has the advantage of a drainage provided at the axially lower end, that for a mounting under water to be closed inputs and outputs of the compressor unit does not have to endure the full water pressure of the operating site before a connection of the delivery lines is performed, but the compressor unit in the Overhead layer can be filled with an incompressible fluid, which prevents penetration of the surrounding medium during transport to the mounting location.
  • This mounting option is of particular interest if the surrounding medium is salt water, for example when producing natural gas at the bottom of the sea.
  • a drainage is preferably at the lowest point in the
  • Figure 1 shows a longitudinal section through a schematic representation of a compressor unit mounted on a frame in accordance with the invention
  • Figure 2 is a schematic representation of a conveyor system with a compressor unit in inventive storage on a frame.
  • FIG. 1 shows schematically a section along a compressor unit 1 according to the invention, which has as essential components a motor 2 and a compressor 3 in a gas-tight housing 4.
  • the housing 4 accommodates the engine 2 and the compressor 3.
  • the housing 4 In the area of the transition from the engine 2 to the compressor 3, the housing 4 is provided with an inlet 6 and an outlet 7, through the inlet 6 by means of an intake manifold 8 to be compacted Fluid is sucked and flows through the outlet 7, the compressed fluid.
  • the compressor unit 1 is arranged vertically in operation, wherein a motor rotor 15 of the motor 2 are united via a compressor rotor 9 of the compressor 3 to a common rotor 19 which rotates about a common vertical axis of rotation 60.
  • the motor rotor 15 is mounted in a first radial bearing 21 at the upper end of the motor rotor 15.
  • the compressor rotor 9 is mounted by means of a second radial bearing 22 in the lower position.
  • a thrust bearing 25 is provided.
  • the radial bearings and the thrust bearing work electromagnetically and are each encapsulated.
  • the radial bearings extend in the circumferential direction about the respective bearing point of the rotor 19 and are in this case 360 ° circumferentially and undivided.
  • the compressor 3 designed as a centrifugal compressor has three compressor stages 11 which are in each case connected by means of an overflow 33.
  • the resulting at the compressor stages 11 pressure differences provide for a thrust on the compressor rotor 9, which transmits to the motor rotor 15 and against the weight of the resulting entire rotor of compressor rotor 9 and motor rotor 15, is directed, so that in nominal operation as far as possible thrust balance he follows.
  • the thrust bearing 25 can be dimensioned comparatively smaller than in a horizontal arrangement of the rotation axis 60th
  • the electromagnetic bearings 21, 22, 25 are cooled by means of a cooling system not shown in detail to the operating temperature, wherein the cooling system provides a tap in an overflow 33 of the compressor 3. From the tap a part of the pumped medium, which is preferably natural gas, passed through a filter by means of piping and then through two separate pipes to the respective outer bearings (first radial bearing 21 and second radial bearing 22 and thrust bearing 25) out. This cooling by means of the cold pumped medium (80) saves additional supply lines.
  • the motor rotor 15 is surrounded by a stator 16, which has an encapsulation, so that the aggressive conveying medium 80 does not damage windings of the stator 16.
  • the encapsulation is preferably designed so that it can bear the full operating pressure. This is also because a separate cooling is provided for the stator, in which a separate cooling medium circulates.
  • the compressor rotor 9 expediently has a compressor shaft 10 on which the individual compressor stages 11 are mounted. This can preferably be done by means of a thermal shrinkage fit. Likewise, a positive connection, for example by means of polygons possible. Another embodiment provides for a fusion of different compressor stages 11 to each other, from which a one-piece compressor rotor 9 results.
  • FIG. 1 shows that supporting elements 69 are provided on the housing 4, by means of which the compressor unit 1 acts against the force of gravity
  • Support surfaces 83 of a frame 70 is supported in bearing points 84 on bearing surfaces 83 of a frame 70.
  • Figure 1 shows the support members 69 drawn for better illustration rotated about the axis of rotation 60.
  • the supporting elements 69 are arranged symmetrically about the axis of rotation 60 offset by 120 ° as well as the bearing points 84 and the bearing surfaces 83 of the frame 70.
  • the bearing points 84 are located together with the rotor centroid 68 essentially in a plane which is oriented perpendicular to the vertical axis of rotation 60.
  • the frame 70 is mounted on a common base member 87, on which further modules 90 of the conveyor unit 91 are arranged.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)

Abstract

La présente invention concerne une unité de compresseur (1) comprenant un moteur (2) et un compresseur (3). Le moteur (2) présente un rotor de moteur (15) et le compresseur (3) présente un rotor de compresseur (9), lesquels rotors tournent sous forme de rotor commun (19) autour d'un axe de rotation commun (60). L'unité de compresseur (1) comprend un carter (4) qui présente des éléments d'appui (69) conçus pour s'appuyer en des points d'appui (84) et permettant de monter l'unité de compresseur (1) en position de service. L'objectif de la présente invention est d'obtenir un bon comportement aux vibrations avec le minimum de moyens. A cette fin, au moins trois des points d'appui (84) se trouvent sensiblement dans le même plan que le centre de gravité (68) du rotor (19). L'avantage présenté par un tel montage de l'unité de compresseur (1) est que les amplitudes des vibrations dans la zone du centre de gravité (68) ou du centre de gravité de rotation du rotor sont relativement faibles par rapport aux autres zones de la machine et que l'amortissement du système en mouvement est particulièrement efficace à cet endroit.
PCT/EP2007/051415 2006-03-24 2007-02-14 Unité de compresseur WO2007110272A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP07726371A EP1999377A1 (fr) 2006-03-24 2007-02-14 Unité de compresseur
NO20084449A NO20084449L (no) 2006-03-24 2008-10-22 Kompressorenhet

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP06006070.4 2006-03-24
EP06006070 2006-03-24

Publications (1)

Publication Number Publication Date
WO2007110272A1 true WO2007110272A1 (fr) 2007-10-04

Family

ID=38093318

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/051415 WO2007110272A1 (fr) 2006-03-24 2007-02-14 Unité de compresseur

Country Status (3)

Country Link
EP (1) EP1999377A1 (fr)
NO (1) NO20084449L (fr)
WO (1) WO2007110272A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2542657C2 (ru) * 2009-07-10 2015-02-20 Нуово Пиньоне С.п.А. Интегрированная компрессионная установка высокого давления для рабочей текучей среды и способ сжатия рабочей текучей среды

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3441203A (en) * 1966-03-01 1969-04-29 Danfoss As Motor-compressor for an encapsulated refrigerating unit
GB1265151A (fr) * 1968-03-05 1972-03-01
DE2542336A1 (de) * 1975-09-23 1977-03-24 Kalnin Mehrstufenkreiselverdichter
US6255752B1 (en) * 1997-07-26 2001-07-03 Allweiler Ag Mounting for a turbo-machine rotor and its use
WO2002099286A1 (fr) * 2001-06-05 2002-12-12 Siemens Demag Delaval Turbomachinery B.V. Unite compresseur comprenant un compresseur centrifuge et un moteur electrique

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3441203A (en) * 1966-03-01 1969-04-29 Danfoss As Motor-compressor for an encapsulated refrigerating unit
GB1265151A (fr) * 1968-03-05 1972-03-01
DE2542336A1 (de) * 1975-09-23 1977-03-24 Kalnin Mehrstufenkreiselverdichter
US6255752B1 (en) * 1997-07-26 2001-07-03 Allweiler Ag Mounting for a turbo-machine rotor and its use
WO2002099286A1 (fr) * 2001-06-05 2002-12-12 Siemens Demag Delaval Turbomachinery B.V. Unite compresseur comprenant un compresseur centrifuge et un moteur electrique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2542657C2 (ru) * 2009-07-10 2015-02-20 Нуово Пиньоне С.п.А. Интегрированная компрессионная установка высокого давления для рабочей текучей среды и способ сжатия рабочей текучей среды

Also Published As

Publication number Publication date
NO20084449L (no) 2008-12-17
EP1999377A1 (fr) 2008-12-10

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