EP1074746B1 - Turbo-compresseur - Google Patents

Turbo-compresseur Download PDF

Info

Publication number
EP1074746B1
EP1074746B1 EP00810274A EP00810274A EP1074746B1 EP 1074746 B1 EP1074746 B1 EP 1074746B1 EP 00810274 A EP00810274 A EP 00810274A EP 00810274 A EP00810274 A EP 00810274A EP 1074746 B1 EP1074746 B1 EP 1074746B1
Authority
EP
European Patent Office
Prior art keywords
compressor
electric motor
shaft
turbo
radial
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.)
Revoked
Application number
EP00810274A
Other languages
German (de)
English (en)
Other versions
EP1074746A3 (fr
EP1074746A2 (fr
Inventor
Denis Grob
Jean-Claude Pradetto
Dominique Dessibourg
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.)
MAN Energy Solutions SE
Original Assignee
MAN Turbo 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=26073836&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1074746(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority claimed from EP99810640A external-priority patent/EP0990798A1/fr
Application filed by MAN Turbo AG filed Critical MAN Turbo AG
Priority to EP00810274A priority Critical patent/EP1074746B1/fr
Priority to CA002312081A priority patent/CA2312081C/fr
Priority to US09/597,938 priority patent/US6464469B1/en
Priority to DE20011219U priority patent/DE20011219U1/de
Priority to JP2000192339A priority patent/JP4460116B2/ja
Priority to KR1020000039922A priority patent/KR100779959B1/ko
Priority to CNB001201131A priority patent/CN1153907C/zh
Publication of EP1074746A2 publication Critical patent/EP1074746A2/fr
Publication of EP1074746A3 publication Critical patent/EP1074746A3/fr
Publication of EP1074746B1 publication Critical patent/EP1074746B1/fr
Application granted granted Critical
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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
    • 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
    • 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
    • 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
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • F04D29/054—Arrangements for joining or assembling 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • 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
    • F04D29/5806—Cooling the drive system
    • 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

Definitions

  • the invention relates to a turbocompressor according to the preamble of Claim 1.
  • turbo compressor which is a radial turbo compressor and an electric motor, each of these units in one is arranged separate housing, and the shaft of the electric motor via a flexible shaft part is coupled to the shaft of the radial turbocompressor.
  • a disadvantage of this known turbocompressor is the fact that this relatively large is designed that a plurality of seals and Bearings are required, and that the manufacturing cost of Turbo compressor therefore relatively high.
  • a turbocompressor comprising an electric motor, a multi-stage radial turbocompressor and a common shaft, wherein a portion of the shaft as the rotor Electric motor is formed, and wherein a further portion of the shaft is designed as a rotor of Radialturboverêtrs, the runner a Compressor shaft and associated compressor wheels includes, and wherein for storing the shaft several electromagnetic radial bearings in Expended direction of the shaft are arranged spaced, and wherein between the rotor of the electric motor and the compressor wheel a single Electromagnetic radial bearing is arranged, and wherein the electric motor, the radial turbo compressor, the shaft and the radial bearings in one common, outwardly gastight housing are arranged, and wherein the housing consists of several sub-housings, which firmly can be connected to each other, the electric motor in a sub-housing and the Radial turbocompressor is arranged in a sub-housing, and the
  • turbocompressor comprising an electric motor, a multi-stage radial turbocompressor and a common shaft, wherein a portion of the shaft as a rotor of the electric motor is formed, and wherein a further portion of the Shaft is designed as a rotor of the radial turbocompressor, wherein the rotor a compressor shaft and associated compressor wheels, and wherein for supporting the shaft a plurality of electromagnetic radial bearings in Course of the wave are arranged spaced, wherein the Radial bearings are supported on a common base element.
  • turbocompressor comprising an outwardly gas-tight housing within which a common shaft an electric motor and a multi-stage Radial turbo compressor are arranged, wherein for storing the shaft in the Course arranged electromagnetic radial bearings spaced are, and being between the electric motor and the radial turbo compressor a shaft surrounding the dry gas seal is arranged to the Seal electric motor with respect to the radial turbo compressor, wherein the Electric motor has an interior, which fluid-conducting with a the Housing penetrating outlet is connected.
  • Fig. 1 shows a known turbocompressor, which has a double-sided mounted electric motor and a bilaterally mounted Radial turbocharger includes, wherein the shaft of the electric motor via a flexible shaft part is coupled to the shaft of the radial turbocompressor.
  • turbocompressor for complete storage of the entire shaft, opposite to the Embodiment according to FIG. 1, three radial bearings, in particular designed as electromagnetic radial bearings, suffice by between the Electric motor and the compressor a single radial bearing is arranged.
  • the turbo compressor is cheaper to produce.
  • the entire shaft can be designed in one piece.
  • a very stiff coupling allowed to form a total wave, which in the direction of the wave a has largely homogeneous stiffness profile.
  • the overall wave or the entire rotatable components of the Turbo compressors behave like a compact shaft, resulting in positively affects a stable running behavior of the turbo compressor. moreover this allows the entire shaft with the help of a single thrust bearing in store axial direction.
  • Fig. 1 is for the electric motor and the radial turbo compressor each a separate Thrust bearing required.
  • a radial turbo compressor is arranged so suffice three spaced in the direction of the wave arranged electromagnetic radial bearings for complete storage of entire wave. Is on both sides of the electric motor ever one Arranged radial turbocharger, so suffice four in the direction of the Shaft spaced arranged electromagnetic radial bearings for complete storage of the entire shaft.
  • the waiver of a radial bearing between the electric motor and the Radial turbo compressor also has the advantage that the length of the shorter shaft, which is advantageous in terms of rotor dynamics, a lighter one Wave allows to form, and also a more compact design of the Turbo compressor results. It should be noted that electromagnetic Radial bearings compared to hydrodynamic radial bearings a substantial lower bearing force, so that by the shorter shaft gained, more advantageous rotordynamic behavior and the lower Weight is crucial to keep the turbo compressor safe and trouble-free operation by means of electromagnetic bearings.
  • the engine and the Radial turbo compressor in a common, hermetically sealed Housing, in particular arranged a pressure housing, wherein a fluid-conducting inlet and outlet penetrate the housing or on the housing flanged to the radial turbo compressor to be compressed Add and remove fluid.
  • This arrangement has the decisive advantage on that on the shaft no seals against the outside, especially against Atmosphere more are needed, which in addition to the cost advantage of the others Advantages are that downtime caused by sealing problems no longer occur, and that the total length of the shaft in addition can be reduced, which in turn reduces the overall weight of the shaft as well the stability of the shaft held by electromagnetic radial bearings elevated.
  • the radial turbo compressor with a hermetically sealed to the outside Pressure housing allows the motor-compressor system according to the invention also to operate at locations, which so far for the enterprise of a Radial turbocompressors were unsuitable, for example, under water or in an environment with high pollutant content, high degree of contamination or high risk of explosion.
  • turbocompressor Another advantage of the inventive turbocompressor is in it too see that this is remote controlled very safe operable.
  • Turbo compressor for example, does not require a complex oil system Storage of the rotor.
  • the turbocompressor therefore has no components, too whose operation requires a specialist on site, or components which require regular control in relatively short time intervals.
  • a start and stop operation of the turbocompressor can be controlled remotely expire, by means of sensors, the states of the turbo compressor of Remotely monitorable, and detecting an irregularity suitable measures, for example stopping, are automatically initiated can be.
  • a turbocompressor has in the embodiment with hermetically sealed pressure housing on the further advantage that the Danger to external influences is very low.
  • a part of the compressed Fluids or process gas for longitudinal gas cooling of the engine and the Radial bearing used is especially true when using a common, hermetically sealed pressure housing advantageous.
  • Electric motor is preferably one for suction or standstill pressure designed engine used.
  • the electric motor has a separate, from the radial turbocompressor separate cooling circuit on.
  • a common base element which for example, is plate-shaped, and on which some, preferably all radial bearings are supported.
  • the arrangement of Radial bearing on a common base element has the advantage that they are aligned in a defined position against each other, and that due to tensile, compressive or shear stresses or caused by temperature influences mutual Shifts of the radial bearings can be minimized.
  • a mutually precisely arranged alignment of the radial bearings at guaranteed a wide range of operating conditions.
  • the radial bearings are arranged on the base element special also the other elements like the electric motor, the radial turbo compressor etc.
  • turbo compressor As a whole Assemble module ready in the factory.
  • This module can be at the Application can be put into operation very quickly, as it is no longer required is the radial turbocharger and the electric motor separately anchoring a document and their mutual position exactly adjust.
  • turbocompressor arranged within a housing, wherein a part of the housing, for example, the bottom disposed inner wall of the housing, at the same time forms the common base element.
  • the turbocompressor are the Radial turbo compressor and the engine in a common housing arranged, wherein the housing of a plurality of interconnected Part housings, or consists of a substantially single housing.
  • the entire drive device and in a further sub-housing of the entire radial turbocompressor arranged, wherein these sub-housing preferably so mutually Adapted are designed so that they are directly centered and mutually firmly connectable.
  • this is common housing designed so stiff that the entire Turbo compressor comprising the radial turbo compressor, the engine, etc.
  • turbo compressor consists of a separate motor with its own housing, as well as from a radial turbo compressor with another, own housing.
  • this known arrangement represents the mutual movement of the housing or the displacement of the individual waves is a significant problem that causes thereby is that each housing is anchored individually to the ground. By different thermal expansions or other forces acting on The individual housing changes their position.
  • the inventive Arrangement of engine and radial turbocompressor on a common Base element, in particular in a common housing has the Advantage on that the base element or the housing the Reference for storage, and therefore a mutual change the position of engine and radial turbocompressor largely excluded is.
  • Fig. 1 shows schematically a known turbocompressor 1, which a Radial turbocompressor 3 with a shaft 3a and a driving Electric motor 2 comprises a shaft 2a.
  • the shaft 3a of Radial turbocompressor 3 is supported by two radial bearings 5 on both sides.
  • the shaft 2a of the electric motor 2 by two radial bearings. 5 stored on both sides.
  • the two shafts 2a, 3a are connected via a coupling 4 comprising two coupling parts 4a and 4b a flexible intermediate piece connected, so that the electric motor 2 via the shaft 2a and the coupling 4th the shaft 3a of the radial turbocompressor 3 drives.
  • Fig. 2 shows a turbocompressor 1, which in a hermetic sealed pressure housing 6 is arranged, wherein each one the Pressure housing 6 penetrating supply line 6c and 6d discharge provided is to the radial turbocompressor 3 fluid-conducting with an outside of the Pressure housing 6 arranged device to connect.
  • the electric motor 2 comprises the rotor 2b and the stator 2c, wherein the rotor 2b part of the Motor shaft 2a, and the motor shaft 2a on both sides in the electromagnetic Radial bearing 5, each comprising a support device 5a and a electromagnetic coil 5b, is mounted in the radial direction.
  • the Motor shaft 2a has a thrust bearing 7 against the radial turbocompressor 3 on, which is a part of the motor shaft 2a forming disc 2d as well comprises electromagnetic coils 7a.
  • the motor shaft 2a is at the End section via a coupling 4 with the rotor 3a of the Radial turbocompressor 3 connected, with the opposite End portion of the rotor 3a is mounted in a radial bearing 5.
  • the Motor shaft 2a and the rotor 3a form a common shaft 13.
  • In Running direction of the rotor 3a are arranged two compressor wheels 3b, which a first compression stage 3c and a second compression stage Training. Not shown are the guide vanes 3f of Radial turbo-compressor 3.
  • the main mass flow 8 of the compressed Fluids pass via the inlet opening 6a and the lead 6c enters and becomes the first compression stage 3c subsequently to the second compression stage 3d and subsequently via the Discharge 6d passed to the outlet opening 6b.
  • a small fraction of the Main mass flow 8 is at the exit point of the first Compression level 3c derived via a connecting line 11 and as Cooling gas mass flow 9 a filter device 10 fed, which the Cooling gas mass flow 9 cleans of impurities, and the purified Cooling gas mass flow 9 as a coolant the electromagnetic Radallagagem 5 and the electric motor 2 supplies.
  • the cooling gas mass flow 9 is flowing in the longitudinal direction of the housing, the radial bearing 5 and subsequently the electric motor 2 and the other Radial bearing 5 fed, the cooling gas preferably between the Wave 2a and the respective magnet 5b, 2c is performed.
  • the Coolant gas mass flow 9 opens to the suction side of the first Compression level 3c, we compress this in turn, and is called Main mass flow 8 and / or further promoted as cooling gas mass flow 9.
  • the connecting line 11 and the filter device 10 can within or be arranged outside of the pressure housing 6 extending.
  • the Turbo compressor 1 according to the embodiment shown in Fig. 2 has the advantage that no seal the motor shaft 2a and the Runner 3a opposite atmosphere is required. In addition, there is no seal between the engine 2 and the first compression stage 3c required.
  • the electric motor 2 is designed in such a way that this with Suction pressure or with standstill pressure is operable.
  • the turbo-compressor 1 could, of course, a plurality of in the direction of travel of the rotor 3a have arranged spaced compressor wheels 3b, so for example, a total of four, six, eight or ten compressor wheels 3 b.
  • the compression pressure to be achieved is largely open to the top, wherein by a corresponding number connected in series Compressor wheels 3b, for example, a compression pressure of 600 bar is reachable.
  • the turbocompressor 1 could also have one or more others Radial turbo compressor 3 and / or electric motors 2 include, which in Running direction of the rotor 3a, 2a are arranged, with all runs 3a, 2a to train a common wave.
  • This common wave could be through Radial bearing, in particular magnetic radial bearings 5 be stored, wherein between each one Radialturbover Noticer 3 preferably a single Radial bearing 5 is arranged.
  • all radial turbocompressors 3 together with the electric motor 2 or the electric motors 2 in one common, single pressure housing 6 is arranged.
  • the electromagnetic radial bearing 5 and the radial bearings. 5 associated portions of the shafts 2a and 3a have further, for a Professional self-evident and therefore not shown components on to form an electromagnetic radial bearing 5, such as electrical Coils, ferromagnetic parts, etc.
  • Fig. 3 shows a longitudinal section of another embodiment of a Turbo compressor 1 comprising two radial turbocompressors 3, wherein at each Side of the electric motor 2 per a Radialturbover Noticer 3 arranged and whose rotor 3a is connected via a coupling 4 with the motor shaft 2a. Only the upper half of the turbocompressor 1 is shown. It will only the opposite to the embodiment according to FIG. 2 essential Differences in detail described.
  • the entire wave includes the Motor shaft 2a and the two rotor 3a is by four, in the longitudinal direction of the distributed throughout the wave electromagnetic radial bearings 5 stored.
  • the left-hand radial turbocompressor 3 is as Low pressure part connected and has six compressor wheels 3b.
  • the main mass flow 8 passes through the supply line 6c in the low pressure part, and after compression over a Connecting line 12 is supplied to the high pressure part, wherein the Main mass flow 8 the high pressure part after compression over the Derivative 6d leaves.
  • a small part of the main mass flow 8 is after the first compression stage 3c as the cooling gas mass flow 9 in the Conduction line 11 passed, said cooling gas mass flow 9 after the flow through the filter 10 that on the right side of the electric motor 2 arranged interior 9 c is supplied, and thereafter in the longitudinal direction the motor shaft 2 a flowing over the inner space 9 b of the suction port of the first compression stage 3c zuflust.
  • the Radial turbo compressor 3 located process gas for cooling the Derived and used electric motor 2.
  • a non-contact seal 19th arranged to the internal pressure on the right side of the electric motor. 2 keep it low.
  • the electric motor 2 is again designed to be operable at a suction pressure or a standstill pressure.
  • the Connecting line 12 and / or the connecting line 11 and the Filter device 10 could also be completely inside the housing 6 be arranged running.
  • the radial turbocompressor 3 for example, in a back to back "arrangement, in other words such that the by the two Radialturbover Noticer 3 on the shaft caused forces in act in the opposite direction to such in the direction of the Motor shaft 2a acting shear forces to compensate and reduce.
  • the housing 6 is set in the embodiments according to FIGS. 3 and 4 from the three sub-housings 6e, 6f, 6g together, the sub-housings 6e, 6g form part of the radial turbocompressor 3 and the part housing 6f part of Engine 2 forms.
  • the sub-housings 6e, 6f, 6g are adapted to one another in this way designed so that they, as shown in Figures 3 and 4, fixed can be connected to each other, for example by means of screws.
  • At this Junctions can also be arranged seals to the To hermetically seal the interior of the housing 6 so that only over the intended lines 6c, 6d, 11, 12 or corresponding flanges a fluid-conducting connection between the interior of the housing.
  • Figs. 3 and 4 show arrangement of the lines 11 and 12 only through the lines 6c, 6d and optionally through the discharge line 6i a fluid-conducting connection to the outside space exists.
  • the joints can also do so be adapted to each other that arranged adjacent Part housing when pushed together and connect with respect to Longitudinal axis of the turbocompressor 1 automatically center each other.
  • the two partial housings 6e, 6g each have an opening 23a in the outer wall which can be closed gas-tight with a cover 23b.
  • Fig. 3 is the in the sub-housing 6g arranged opening 23a with lid 23b shown.
  • the Turbo compressor 1 is preferably prefabricated such that the Radial turbo compressor 3 is installed in the respective sub-housing 6e, 6g and the electric motor 2 is installed in the sub housing 6f.
  • the like preconfigured sub-housing 6e, 6f, 6g are in the assembled State transported to the place of application.
  • the assembly of the Turbo compressor 1 is as follows: After the sub-housing 6e, 6f, 6g on the Flanges 6k, 6l are firmly connected to each other, the shaft 3a and the rotor 2b at the outside accessible through the opening 23a Clutch 4 firmly connected. Thereafter, the opening 23 a with the lid 23b firmly and sealed gas-tight.
  • the at the clutch 4 used fasteners, such as screws, are in themselves known and therefore not shown in detail.
  • the turbocompressor 1 shown in Fig. 4 in otherwise substantially the same configuration as the turbocompressor according to FIG. 3, in the housing part 6e a fluidically connected to the interior 9b outlet opening 6h and a subsequently arranged derivative 6i, through which the Cooling gas mass flow 9 and a minor proportion of Main mass flow 9a exits and example of a foreign investment Process source is supplied.
  • This arrangement is opposite to the Embodiment according to FIG. 3 has the advantage that the pressure in the Derivative 6i subsequent device independent of the pressure in Radial turbo compressor 3 is, this pressure is preferably selected is that the engine cooling is done at a lower pressure level than in the Embodiment according to FIG.
  • the Discharge 6i may be supplied to, for example, a compressor 24, which compresses the mass flow 9, 9a again the inlet opening 6a supplies.
  • the suction pressure generated by the compressor in the discharge line 6i can for example, be lower than 50 bar.
  • a control device 17 which at least for driving the electromagnetic radial bearing 5 and the motor 2 serves.
  • sensors 16a, 16b, 16c, 16d arranged, which the position of the entire shaft 13 and the sub-waves 2a, 3a with respect to the radial bearings 5, the sensors 16a, 16b, 16c, 16d via electrical lines 16e, 16f, 16g, 16h with the control device 17 are connected.
  • electrical lines 15a, 15b, 15c, 15d which are connected to the control device 17.
  • electrical line 15 e is also one electrical line 15 e is provided, which the control device 17 via a power electronics, not shown, with the winding of the Electric motor 2 connects.
  • Fig. 5 shows a longitudinal section through a housing 6, wherein the Junction of two sub-housing 6e, 6f is shown.
  • the flange 6k of the first sub-housing 6e has a recess configured in this way, that the flange 6I of the second part housing 6f is received therein, wherein the mutual position of the two sub-housings 6e, 6f at Joining together by the flanges 6k, 6l are centered on each other.
  • the Flanges 6k, 6l are distributed by several in the circumferential direction arranged screws 6m held together with nut 6n, wherein at the Face of the flanges 6k, 6l extending in the circumferential direction groove is provided, in which a sealing element 6o is arranged to the by the two sub-housing 6e, 6f limited interior to the outside seal.
  • FIG. 6 shows a longitudinal section of a schematically illustrated housing 6 consisting of three sub-housings 6e, 6f, 6g with flanges 6k, 6l and a Supply line 6c and a derivative 6d.
  • the housing 6 is about two Supporting elements 18a, 18b supported on a substrate 14.
  • a base member 6p which is a rigid, in Longitudinal direction of the housing 6 extending support, in particular a Supporting surface forms on which the electromagnetic radial bearings. 5 are arranged.
  • the function of the basic elements 6p is one as possible stable and preferably temperature-insensitive reference plane too form, on which at least some radial bearings 5 are arranged.
  • the Base member 6p may be configured in a variety of embodiments be, for example, as a solid, solid plate, as a carrier or as Grating. On the base element 6p further components such as Electric motor 2 or 3 Radialturbover Noticer be anchored.
  • the Using a base element 6p allows the electromagnetic Radial bearing 5 mutually very precise and in particular precisely aligned to arrange.
  • the common arrangement of the radial bearing 5 on the Base element 6p has the advantage that due to attacking Tensile, compressive or shear forces or due to temperature influences mutual shifts of the radial bearings turn out very low. moreover This arrangement can be set up very quickly ready for use. In the From Fig.
  • the bearing force generated by electromagnetic radial bearings is much lower than that of known hydrodynamic bearings producible bearing force. That is why the exact mutual Alignment of electromagnetic radial bearings and preventing a mutual displacement of the radial bearings of central importance.
  • the Electromagnetic radial bearing is usually operated such that the Shaft is held in the geometric center of the radial bearing.
  • One mutual displacement of the radial bearing has the consequence that the Radial bearing has to expend considerable forces to the shaft anyway in the to hold geometric center. Since the electromagnetic radial bearing relative it soon gets into the state of magnetic saturation Radial bearing in this situation over lower, to carry the shaft to Available forces.
  • Fig. 7 shows a turbocompressor 1 with a compared to Embodiment according to FIG. 4 separately cooled electric motor 2. It is between the pressure part of the radial turbocompressor 3 and the electric motor 2 each a system with a double seal, comprising a Dry gas seal 19 and subsequently a seal 20, arranged wherein between the two seals 19, 20 an outlet 21, as a vent (Exit to the atmosphere without gas combustion) or flare (exit to the Atmosphere with gas combustion) configured, which is arranged by the housing wall 6 runs.
  • the electric motor 2 has a separate, separated by the seals 19, 20 from the radial turbo compressor 3 Cooling circuit on which a connecting line 11 and a radiator 22nd includes.
  • a Coolant gas driving device not shown are other components of this cycle, such as a Coolant gas driving device.
  • a supply line 9d carries additional Cooling gas to, for example, the effluent via the discharge line 21 Compensate cooling gas components.
  • the cooling gas is not in particular aggressive gas such as nitrogen.
  • the cooling circuit of the Electric motor 2 may be designed such that this pressure in the Range of atmospheric pressure or slightly above it. As in 7, the cooling circuit can be designed such that a small proportion of the cooling gas mass flow 9 via the seal 20 for Outlet 21 arrives. This ensures that the Coolant gas mass flow 9 is not contaminated by foreign gases. in the Embodiment according to FIG. 7 also flows a small proportion of Process gas 8 via the seal 19 to the outlet 21.
  • the outlet 21 can a so-called flare or vent be subordinate to that from the Outlet 21 discharged gases unburned vent (vent) or via a subsequent combustion (flare) dissipate, especially to the environment leave.
  • cooling gas 9 has a low pressure and / or that as a cooling gas favorable or easily manageable gas is used, in particular a gas without aggressive properties.
  • turbocompressor 1 An advantage of the turbocompressor 1 according to the invention can be seen therein that the electric motor 2 and the radial turbocompressor 3 together with the corresponding housing parts 6e, 6f are preassembled, so that the Turbo compressor 1 as a housing 6 or as a unit for Site is transportable and can be set up there.

Claims (15)

  1. Turbocompresseur (1) comprenant un moteur électrique (2), un compresseur centrifuge radial multiétagé (3) ainsi qu'un arbre commun (13), une section partielle de l'arbre (13) étant configurée sous forme de rotor (2b) du moteur électrique (2), et une autre section partielle de l'arbre (13) étant configurée sous forme de roue motrice (3e) du compresseur centrifuge radial (3), la roue motrice (3e) comprenant un arbre de compresseur (3a) ainsi que des roues à aubes de compresseur (3b) assemblées avec ce dernier, et plusieurs paliers lisses radiaux électromagnétiques (5) étant disposés à distance mutuelle pour le logement de l'arbre (13) dans la direction d'extension de l'arbre (13), et un palier lisse radial électromagnétique unique (5) étant disposé entre le rotor (2b) du moteur électrique (2) et la roue à aubes de compresseur (3b), et le moteur électrique (2), le compresseur centrifuge radial (3), l'arbre (13) ainsi que les paliers lisses radiaux (5) étant disposés dans un carter commun (6) étanche aux gaz en direction de l'extérieur, caractérisé en ce que le carter (6) est constitué de plusieurs carters partiels (6e, 6f, 6g) qui peuvent être assemblés fixement entre eux, que le moteur électrique (2) est disposé dans un carter partiel (6f) et le compresseur centrifuge radial (3) dans un carter partiel (6e, 6g), et que le rotor (2b) du moteur électrique (2) ainsi que la roue motrice (3e) du compresseur centrifuge radial (3) peuvent être assemblés entre eux en un arbre commun par l'intermédiaire d'un accouplement (4) disposé entre le rotor (2b) du moteur électrique (2) et la roue à aubes de compresseur (3b).
  2. Turbocompresseur (1) suivant la revendication 1, caractérisé en ce qu'au moins un carter partiel (6e, 6f, 6g) présente une ouverture obturable (23a), disposée dans la zone de l'accouplement (4).
  3. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce que l'accouplement (4) est disposé axialement dans la zone des points d'assemblage (6k, 61) de deux carters partiels (6e, 6f, 6g).
  4. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce que les paliers lisses radiaux (5) sont supportés sur un élément de base commun (6p).
  5. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce que le carter commun (6), dans lequel sont disposés le moteur électrique (2), le compresseur radial centrifuge (3), l'arbre (13) ainsi que les paliers lisses radiaux (5), comprend un élément de base (6p) sur lequel s'appuient les paliers lisses radiaux (5).
  6. Turbocompresseur (1) suivant l'une des revendications 4 et 5, caractérisé en ce qu'une partie du côté intérieur du carter (6) forme l'élément de base (6p).
  7. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce que l'accouplement (4) présente une rigidité très élevée pour conférer à l'arbre (13) une rigidité élevée et en particulier homogène dans la direction longitudinale.
  8. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce qu'un compresseur centrifuge radial multiétagé (3), avec respectivement une roue motrice (3e), est disposé de part et d'autre du rotor (2b) du moteur électrique (2).
  9. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce que le carter commun (6) présente une conduite d'alimentation (6c) débouchant de l'extérieur dans le compresseur centrifuge radial (3) et une conduite d'évacuation (6d), pour relier en conduction fluidique des dispositifs, disposés à l'extérieur du carter (6), au compresseur centrifuge radial (3).
  10. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce que le moteur électrique (2) est configuré sous forme de moteur résistant à la pression d'aspiration, que le moteur électrique (2) est relié en conduction fluidique, sur l'une de ses extrémités côté aspiration, à l'admission d'un étage défini (3c, 3d) du compresseur centrifuge radial (3), et que l'autre extrémité du moteur électrique (2) est reliée en conduction fluidique à l'échappement de l'étage défini (3c, 3d) ou d'un étage aval du compresseur centrifuge radial (3), le premier étage (3c) étant choisi de préférence en tant qu'étage défini (3c, 3d).
  11. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce qu'aucun système d'étanchéité n'est disposé entre le moteur électrique (2) et le compresseur centrifuge radial (3) disposé sur l'extrémité côté aspiration du moteur électrique (2).
  12. Turbocompresseur (1) suivant l'une des revendications 1 à 10, caractérisé en ce qu'un système d'étanchéité (19, 20) est disposé entre le compresseur centrifuge radial (3) et le moteur électrique (2), et que le moteur électrique (2) présente un circuit de refroidissement séparé (22, 11).
  13. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce qu'un palier lisse de butée (7), agissant sur l'arbre (13), est disposé dans la direction longitudinale de l'arbre (13), en particulier entre le moteur électrique (2) et le compresseur centrifuge radial (3).
  14. Turbocompresseur (1) suivant l'une des revendications précédentes, caractérisé en ce que des capteurs (16a, 16b, 16c) sont disposés le long de l'arbre (13) pour détecter la position de l'arbre (13), qu'il est prévu un dispositif de commande et de régulation (17) relié en transmission de signaux aux capteurs (16a, 16b, 16c), et que les paliers lisses radiaux électromagnétiques (5) présentent des bobines électromagnétiques (5b), reliées en transmission de signaux au dispositif de commande et de régulation (17).
  15. Installation comprenant un turbocompresseur suivant l'une des revendications précédentes.
EP00810274A 1999-07-16 2000-03-31 Turbo-compresseur Revoked EP1074746B1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP00810274A EP1074746B1 (fr) 1999-07-16 2000-03-31 Turbo-compresseur
US09/597,938 US6464469B1 (en) 1999-07-16 2000-06-20 Cooling system for electromagnetic bearings of a turbocompressor
CA002312081A CA2312081C (fr) 1999-07-16 2000-06-20 Systeme de refroidissement pour paliers electromagnetique d'un turbocompresseur
DE20011219U DE20011219U1 (de) 1999-07-16 2000-06-26 Turboverdichter
JP2000192339A JP4460116B2 (ja) 1999-07-16 2000-06-27 ターボ圧縮機
KR1020000039922A KR100779959B1 (ko) 1999-07-16 2000-07-12 터보압축기
CNB001201131A CN1153907C (zh) 1999-07-16 2000-07-17 涡轮压缩机装置

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP99810640 1999-07-16
EP99810640A EP0990798A1 (fr) 1999-07-16 1999-07-16 Turbo-compresseur
EP00810274A EP1074746B1 (fr) 1999-07-16 2000-03-31 Turbo-compresseur

Publications (3)

Publication Number Publication Date
EP1074746A2 EP1074746A2 (fr) 2001-02-07
EP1074746A3 EP1074746A3 (fr) 2002-05-15
EP1074746B1 true EP1074746B1 (fr) 2005-05-18

Family

ID=26073836

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00810274A Revoked EP1074746B1 (fr) 1999-07-16 2000-03-31 Turbo-compresseur

Country Status (7)

Country Link
US (1) US6464469B1 (fr)
EP (1) EP1074746B1 (fr)
JP (1) JP4460116B2 (fr)
KR (1) KR100779959B1 (fr)
CN (1) CN1153907C (fr)
CA (1) CA2312081C (fr)
DE (1) DE20011219U1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1830070A2 (fr) 2006-02-17 2007-09-05 Nuovo Pignone S.P.A. Compresseur à moteur
EP2113671A1 (fr) 2008-04-28 2009-11-04 Siemens Aktiengesellschaft Agencement équipé d'un moteur électrique et d'une pompe
EP2252797A1 (fr) 2008-03-19 2010-11-24 Siemens Aktiengesellschaft Unité de compresseur
EP2290241A1 (fr) 2009-07-13 2011-03-02 Siemens Aktiengesellschaft Ensemble de turbocompresseur avec un système de refroidissement
EP2295811A1 (fr) 2009-07-10 2011-03-16 Nuovo Pignone S.p.A. Unité de compression à haute pression pour un fluide de process dans une installation industrielle et méthode de fonctionnement de cette installation
EP2315946A1 (fr) 2008-08-13 2011-05-04 Siemens Aktiengesellschaft Machine à énergie hydraulique ou pneumatique
EP2462350A1 (fr) 2009-08-03 2012-06-13 Atlas Copco Airpower, Naamloze Vennootschap Systeme de turbocompresseur
EP2469100A1 (fr) 2010-12-22 2012-06-27 Thermodyn Groupe motocompresseur à accouplement torsible placé dans un arbre creux du compresseur
EP2761187A1 (fr) 2011-09-27 2014-08-06 Termodinamica SAS Unité de motocompresseur comprenant une cartouche amovible
DE102007032933B4 (de) * 2007-07-14 2015-02-19 Atlas Copco Energas Gmbh Turbomaschine
EP4119798A1 (fr) 2021-07-14 2023-01-18 MAN Energy Solutions SE Ensemble turbomachine

Families Citing this family (82)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1018212C2 (nl) 2001-06-05 2002-12-10 Siemens Demag Delaval Turbomac Compressoreenheid omvattende een centrifugaalcompressor en een elektromotor.
NL1021656C2 (nl) 2002-10-15 2004-04-16 Siemens Demag Delaval Turbomac Compressoreenheid met gemeenschappelijke behuizing voor elektromotor en compressor, werkwijze voor het vervaardigen van een scheidingswand voor een compressoreenheid en gebruik van een compressoreenheid.
AU2003233369A1 (en) * 2003-03-10 2004-10-11 Thermodyn Integrated centrifugal compressor unit
WO2004094833A1 (fr) * 2003-04-11 2004-11-04 Thermodyn Groupe moto-compresseur centrifuge
NO323324B1 (no) * 2003-07-02 2007-03-19 Kvaerner Oilfield Prod As Fremgangsmate for regulering at trykket i en undervannskompressormodul
ATE348267T1 (de) * 2003-07-05 2007-01-15 Man Turbo Ag Schweiz Kompressorvorrichtung und verfahren zum betrieb derselben
EP1482179B1 (fr) * 2003-07-05 2006-12-13 MAN TURBO AG Schweiz Dispositif de compression et méthode de son opération
DE102004023148A1 (de) * 2004-05-07 2005-11-24 Atlas Copco Energas Gmbh Turbomaschine für Tieftemperaturanwendungen
DE102004027594B4 (de) * 2004-06-05 2006-06-29 Man B & W Diesel Ag Strömungsmaschine mit radial durchströmtem Verdichterrad
US8075668B2 (en) 2005-03-29 2011-12-13 Dresser-Rand Company Drainage system for compressor separators
DE102005039033B3 (de) * 2005-08-18 2006-11-02 Atlas Copco Energas Gmbh Turbomaschine für Tieftemperaturanwendungen
FR2896101B1 (fr) * 2006-01-10 2008-04-18 Mecanique Magnetique Sa Soc D Dispositif de filtrage de particules dans une machine tournante a paliers magnetiques actifs
JP2009530537A (ja) * 2006-03-24 2009-08-27 シーメンス アクチエンゲゼルシヤフト 圧縮機装置
NO326735B1 (no) * 2006-06-30 2009-02-09 Aker Subsea As Fremgangsmåte og anordning for beskyttelse av kompressormoduler mot uønsket innstrømming av forurenset gass.
CA2664121C (fr) 2006-09-19 2014-05-27 William C. Maier Joint rotatif pour separateur a tambour
WO2008036394A2 (fr) 2006-09-21 2008-03-27 Dresser-Rand Company Ensemble séparateur à tambour et rotor de compresseur
EP2066983B1 (fr) 2006-09-25 2013-12-11 Dresser-Rand Company Système de montage pour compresseur
US8231336B2 (en) 2006-09-25 2012-07-31 Dresser-Rand Company Fluid deflector for fluid separator devices
CA2663883C (fr) 2006-09-25 2015-02-03 Kevin M. Majot Systeme de protection de couplage
BRPI0717087B1 (pt) 2006-09-25 2018-10-16 Dresser Rand Co sistema de carretel conector para conectar um primeiro componente e um segundo componente de um sistema de compressão industrial
US8267437B2 (en) 2006-09-25 2012-09-18 Dresser-Rand Company Access cover for pressurized connector spool
WO2008039491A2 (fr) 2006-09-26 2008-04-03 Dresser-Rand Company Dispositif de séparation de fluides statique amélioré
US8156757B2 (en) * 2006-10-06 2012-04-17 Aff-Mcquay Inc. High capacity chiller compressor
US7700207B2 (en) * 2006-11-09 2010-04-20 Gm Global Technology Operations, Inc. Turbocompressor shutdown mechanism
US20080199326A1 (en) * 2007-02-21 2008-08-21 Honeywell International Inc. Two-stage vapor cycle compressor
US7901177B2 (en) * 2007-03-01 2011-03-08 Siemens Energy, Inc. Fluid pump having multiple outlets for exhausting fluids having different fluid flow characteristics
US8047809B2 (en) * 2007-04-30 2011-11-01 General Electric Company Modular air compression apparatus with separate platform arrangement
WO2009111616A2 (fr) 2008-03-05 2009-09-11 Dresser-Rand Company Ensemble compresseur comprenant séparateur et pompe à éjecteur
JP5632297B2 (ja) * 2008-03-13 2014-11-26 エーエーエフ−マックウェイ インク． チラーシステム及びチラーシステムの作動方法
DE102008031994B4 (de) * 2008-04-29 2011-07-07 Siemens Aktiengesellschaft, 80333 Fluidenergiemaschine
US8062400B2 (en) 2008-06-25 2011-11-22 Dresser-Rand Company Dual body drum for rotary separators
US7922218B2 (en) 2008-06-25 2011-04-12 Dresser-Rand Company Shear ring casing coupler device
US8079805B2 (en) 2008-06-25 2011-12-20 Dresser-Rand Company Rotary separator and shaft coupler for compressors
DE102009004376B4 (de) * 2009-01-12 2016-06-16 Man Diesel & Turbo Se Verfahren und System zur Steuerung eines Turbokompressorverbundes
US8210804B2 (en) 2009-03-20 2012-07-03 Dresser-Rand Company Slidable cover for casing access port
US8087901B2 (en) 2009-03-20 2012-01-03 Dresser-Rand Company Fluid channeling device for back-to-back compressors
US8061972B2 (en) 2009-03-24 2011-11-22 Dresser-Rand Company High pressure casing access cover
WO2011034764A2 (fr) 2009-09-15 2011-03-24 Dresser-Rand Company Séparateur compact basé sur une densité améliorée
IT1395822B1 (it) 2009-10-12 2012-10-26 Nuovo Pignone Spa Metodo e macchinario con combinazione di dispositivi di separazione particelle e di regolazione flusso
BR112012020085B1 (pt) 2010-02-10 2020-12-01 Dresser-Rand Company aparelho de coleta para um separador e método de separação
IT1399881B1 (it) * 2010-05-11 2013-05-09 Nuova Pignone S R L Configurazione di tamburo di bilanciamento per rotori di compressore
WO2012009158A2 (fr) 2010-07-15 2012-01-19 Dresser-Rand Company Séparateur rotatif en ligne amélioré
US8663483B2 (en) 2010-07-15 2014-03-04 Dresser-Rand Company Radial vane pack for rotary separators
US8657935B2 (en) 2010-07-20 2014-02-25 Dresser-Rand Company Combination of expansion and cooling to enhance separation
WO2012012143A2 (fr) 2010-07-21 2012-01-26 Dresser-Rand Company Faisceau de séparateurs rotatifs modulaires multiples en ligne
WO2012033632A1 (fr) 2010-09-09 2012-03-15 Dresser-Rand Company Drain à écoulement contrôlé permettant le rinçage
EP2633198A4 (fr) * 2010-10-27 2017-01-11 Dresser-Rand Company Système et procédé permettant la mise sous pression rapide d'un moteur/circuit de refroidissement pour un système de moteur/compresseur étanche
RU2448277C1 (ru) * 2010-12-28 2012-04-20 Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" Способ разгрузки и защиты упорного подшипника двухсекционного центробежного компрессора
US8994237B2 (en) 2010-12-30 2015-03-31 Dresser-Rand Company Method for on-line detection of liquid and potential for the occurrence of resistance to ground faults in active magnetic bearing systems
US9024493B2 (en) 2010-12-30 2015-05-05 Dresser-Rand Company Method for on-line detection of resistance-to-ground faults in active magnetic bearing systems
JP5697243B2 (ja) * 2011-02-25 2015-04-08 三菱重工コンプレッサ株式会社 回転軸組立体およびこれを備えた遠心圧縮機
RU2458253C1 (ru) * 2011-03-18 2012-08-10 Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" Центробежный компрессорный агрегат
WO2012138545A2 (fr) 2011-04-08 2012-10-11 Dresser-Rand Company Système de refroidissement à circulation d'huile diélectrique pour paliers enfermés et dispositifs électroniques enfermés
CN102200136B (zh) * 2011-05-25 2012-09-05 北京虎渡能源科技有限公司 一种空气悬浮供气可调高速电机直驱鼓风机
EP2715167B1 (fr) 2011-05-27 2017-08-30 Dresser-Rand Company Roulement segmenté à décélération en roue libre pour des systèmes de roulement magnétique
US8851756B2 (en) 2011-06-29 2014-10-07 Dresser-Rand Company Whirl inhibiting coast-down bearing for magnetic bearing systems
DE102012016844A1 (de) * 2011-08-30 2013-02-28 Ksb Aktiengesellschaft Turbokompressor und Verwendung
DE102012204403A1 (de) * 2012-03-20 2013-09-26 Man Diesel & Turbo Se Radialverdichtereinheit
DE102012207019B4 (de) * 2012-04-27 2015-12-24 Siemens Aktiengesellschaft Strömungsmaschine sowie Verfahren zur Kühlen einer solchen
US9371835B2 (en) 2013-07-19 2016-06-21 Praxair Technology, Inc. Coupling for directly driven compressor
FR2997739B1 (fr) * 2012-11-07 2015-01-09 Thermodyn Compresseur comprenant un equilibrage de poussee
EP2853749A1 (fr) * 2013-09-25 2015-04-01 Siemens Aktiengesellschaft Machine à énergie fluide, procédé pour fonctionner
ITCO20130069A1 (it) * 2013-12-18 2015-06-19 Nuovo Pignone Srl Compressore centrifugo multistadio
DE102014009146A1 (de) * 2014-06-20 2015-12-24 Ziehl-Abegg Se Elektromotor mit einem Rotor, einem Stator und einem Elektronikgehäuse sowie Lüfterrad für einen Elektromotor
WO2016079793A1 (fr) * 2014-11-17 2016-05-26 株式会社日立製作所 Dispositif de compression
US11421696B2 (en) 2014-12-31 2022-08-23 Ingersoll-Rand Industrial U.S., Inc. Multi-stage compressor with single electric direct drive motor
EP3121449B1 (fr) * 2015-07-22 2022-10-05 Thermodyn Compresseur centrifuge sous-marin avec arbre horizontal et avec un seul palier de poussée axiale
DE102015214788A1 (de) 2015-08-03 2017-02-09 Magna Powertrain Bad Homburg GmbH Elektrischer Verdichter und Verfahren zur Herstellung eines elektrischen Verdichters
IT201600120314A1 (it) * 2016-11-28 2018-05-28 Nuovo Pignone Tecnologie Srl Turbo-compressore e metodo di funzionamento di un turbo-compressore
US11274679B2 (en) 2017-02-14 2022-03-15 Danfoss A/S Oil free centrifugal compressor for use in low capacity applications
EP3372835B1 (fr) * 2017-03-07 2020-02-26 ATLAS COPCO AIRPOWER, naamloze vennootschap Module de compresseur pour comprimer le gaz et compresseur équipé avec ce module
GB201708289D0 (en) * 2017-05-24 2017-07-05 Rolls Royce Plc Preventing electrical breakdown
RU2670993C1 (ru) * 2017-08-02 2018-10-29 Василий Сигизмундович Марцинковский Компрессорный агрегат компримирования азото-водородной смеси в производстве аммиака (варианты)
IT201700097796A1 (it) * 2017-08-31 2019-03-03 Nuovo Pignone Tecnologie Srl Sistemi di turbomacchine con refrigerazione di cuscini magnetici attivi e metodo
FR3072429B1 (fr) * 2017-10-16 2020-06-19 L'air Liquide Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Dispositif et procede de compression
FR3072428B1 (fr) 2017-10-16 2019-10-11 L'air Liquide Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Dispositif et procede de compression et machine de refrigeration
FR3088386B1 (fr) * 2018-11-13 2021-01-08 Thermodyn Dispositif de filtration pour un groupe moto-compresseur
IT201900003077A1 (it) * 2019-03-04 2020-09-04 Nuovo Pignone Tecnologie Srl Configurazione di turbomacchina compressore-espantore multistadio
EP3726081B1 (fr) 2019-04-16 2023-10-25 GE Energy Power Conversion Technology Ltd Système mécanique et motocompresseur associé
JP7429541B2 (ja) 2020-01-06 2024-02-08 三菱重工コンプレッサ株式会社 圧縮機システム
CN115803507A (zh) 2020-07-02 2023-03-14 西门子能源全球有限两合公司 具有通过连接螺栓的流动回路的压缩机转子
CN115388017B (zh) * 2022-09-26 2023-09-19 烟台东德实业有限公司 一种高速离心空压机的膨胀端总成

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH663644A5 (de) * 1982-02-22 1987-12-31 Bbc Brown Boveri & Cie Turboverdichter.
FR2528127A1 (fr) * 1982-06-04 1983-12-09 Creusot Loire Moto-compresseur centrifuge electrique integre a grande vitesse
EP0297691A1 (fr) * 1987-06-11 1989-01-04 Acec Energie S.A. Ensemble moteur-compresseur
DE3729486C1 (de) 1987-09-03 1988-12-15 Gutehoffnungshuette Man Kompressoreinheit
GB9404436D0 (en) * 1994-03-08 1994-04-20 Welsh Innovations Ltd Compressor
IL109967A (en) * 1993-06-15 1997-07-13 Multistack Int Ltd Compressor
US5698917A (en) * 1995-09-25 1997-12-16 Glacier Rpb Inc. Electromagnetic bearing with a stationary armature canning arrangement
JPH09132924A (ja) * 1995-11-08 1997-05-20 Shin Caterpillar Mitsubishi Ltd 建設機械の点検用カバーおよびこれを備えた建設機械
JP3425308B2 (ja) * 1996-09-17 2003-07-14 株式会社 日立インダストリイズ 多段圧縮機
JP3399800B2 (ja) * 1997-09-24 2003-04-21 イビデン株式会社 モータ及びターボ分子ポンプ
KR100273380B1 (ko) * 1997-12-26 2001-01-15 구자홍 터보 압축기
JP3425351B2 (ja) * 1998-01-13 2003-07-14 株式会社 日立インダストリイズ ２段遠心圧縮機

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1830070A2 (fr) 2006-02-17 2007-09-05 Nuovo Pignone S.P.A. Compresseur à moteur
DE102007032933B4 (de) * 2007-07-14 2015-02-19 Atlas Copco Energas Gmbh Turbomaschine
EP2252797A1 (fr) 2008-03-19 2010-11-24 Siemens Aktiengesellschaft Unité de compresseur
EP2113671A1 (fr) 2008-04-28 2009-11-04 Siemens Aktiengesellschaft Agencement équipé d'un moteur électrique et d'une pompe
EP2315946A1 (fr) 2008-08-13 2011-05-04 Siemens Aktiengesellschaft Machine à énergie hydraulique ou pneumatique
US8632320B2 (en) 2009-07-10 2014-01-21 Nuovo Pignone S.P.A. High-pressure compression unit for process fluids for industrial plant and a related method of operation
EP2295811A1 (fr) 2009-07-10 2011-03-16 Nuovo Pignone S.p.A. Unité de compression à haute pression pour un fluide de process dans une installation industrielle et méthode de fonctionnement de cette installation
US8801398B2 (en) 2009-07-13 2014-08-12 Siemens Aktiengesellschaft Turbocompressor assembly with a cooling system
EP2290241A1 (fr) 2009-07-13 2011-03-02 Siemens Aktiengesellschaft Ensemble de turbocompresseur avec un système de refroidissement
EP2462350A1 (fr) 2009-08-03 2012-06-13 Atlas Copco Airpower, Naamloze Vennootschap Systeme de turbocompresseur
US9470238B2 (en) 2009-08-03 2016-10-18 Atlas Copco Airpower, Naamloze Vennootschap Electric motor having segmented stator windings
EP2469100A1 (fr) 2010-12-22 2012-06-27 Thermodyn Groupe motocompresseur à accouplement torsible placé dans un arbre creux du compresseur
EP2761187A1 (fr) 2011-09-27 2014-08-06 Termodinamica SAS Unité de motocompresseur comprenant une cartouche amovible
EP4119798A1 (fr) 2021-07-14 2023-01-18 MAN Energy Solutions SE Ensemble turbomachine
DE102021118253A1 (de) 2021-07-14 2023-01-19 Man Energy Solutions Se Strömungsmaschinenanordnung
DE102021118253B4 (de) 2021-07-14 2023-02-02 Man Energy Solutions Se Strömungsmaschinenanordnung

Also Published As

Publication number Publication date
KR20010015305A (ko) 2001-02-26
CA2312081C (fr) 2004-03-02
KR100779959B1 (ko) 2007-11-28
EP1074746A3 (fr) 2002-05-15
EP1074746A2 (fr) 2001-02-07
CN1281101A (zh) 2001-01-24
CA2312081A1 (fr) 2001-01-16
US6464469B1 (en) 2002-10-15
JP4460116B2 (ja) 2010-05-12
DE20011219U1 (de) 2000-10-05
JP2001041191A (ja) 2001-02-13
CN1153907C (zh) 2004-06-16

Similar Documents

Publication Publication Date Title
EP1074746B1 (fr) Turbo-compresseur
EP1069313B1 (fr) Turbo-compresseur
DE4334662C2 (de) Maschine mit einer Welle
DE3729486C1 (de) Kompressoreinheit
DE69727835T2 (de) Lagersystem für motorunterstützte turbolader für verbrennungsmotoren
DE102007032933A1 (de) Turbomaschine
EP1999375A1 (fr) Unité de compression
DE3600124A1 (de) Geblaese zum umwaelzen grosser gasmengen, insbesondere fuer hochleistungs-laser
EP3480929B1 (fr) Carter refroidi pour le stator d'entraînement direct
EP1391586A1 (fr) Turbocompresseur
WO2007110271A1 (fr) Unité de compression et utilisation d'un fluide de refroidissement
EP0408791A1 (fr) Pompe à effet visqueux à rotor en forme de cloche
DE4015732A1 (de) Antriebsmaschinenanlage und verfahren zum umwandeln eines flugzeugtriebwerks in ein triebwerk fuer andere zwecke
EP0569455B1 (fr) Pompe a vide du type a marche a sec avec deux arbres
EP0990798A1 (fr) Turbo-compresseur
EP0653566B1 (fr) Compresseur et transmission pour le compression d'oxygène
DE602004001156T2 (de) Verdichtereinheit mit unterstützter Kühlung
DE2100690A1 (de) Einbaublock zum Einbau in einen mehrstufigen Radialverdichter
EP0789815B1 (fr) Pompe a vide a friction pourvue d'un systeme de refroidissement
DE2324880C3 (de) Gehäuse eines Gaserzeugers für Gasturbinenanlagen
DE102014218936A1 (de) Radialturbofluidenergiemaschine, Verfahren zur Montage
DE4005923A1 (de) Kreiselpumpe mit laufraedern unterschiedlicher drehzahl
EP0713001B1 (fr) Turbine de détente à gaz
DE102021120100A1 (de) Stirnradgetriebe
DE3600125A1 (de) Geblaese zum umwaelzen grosser gasmengen, insbesondere fuer hochleistungs-laser

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

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAN TURBOMASCHINEN AG GHH BORSIG

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

RIC1 Information provided on ipc code assigned before grant

Free format text: 7F 04D 25/06 A, 7F 04D 17/12 B, 7F 04D 29/04 B, 7F 04D 29/10 B, 7F 04D 29/58 B

17P Request for examination filed

Effective date: 20020419

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAN TURBOMASCHINEN AG

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAN TURBOMASCHINEN AG

AKX Designation fees paid

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAN TURBO AG

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

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

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: 20050518

Ref country code: GB

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: 20050518

Ref country code: IE

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: 20050518

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

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 50010337

Country of ref document: DE

Date of ref document: 20050623

Kind code of ref document: P

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: 20050818

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: 20050818

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: 20050818

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

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: 20051024

GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]

Effective date: 20050518

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

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: 20060331

Ref country code: AT

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

Effective date: 20060331

Ref country code: LI

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

Effective date: 20060331

Ref country code: MC

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

Effective date: 20060331

Ref country code: CH

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

Effective date: 20060331

Ref country code: LU

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

Effective date: 20060331

ET Fr: translation filed
26 Opposition filed

Opponent name: SIEMENS AKTIENGESELLSCHAFT ABT. CT IP PG

Effective date: 20060217

NLR1 Nl: opposition has been filed with the epo

Opponent name: SIEMENS AKTIENGESELLSCHAFT ABT. CT IP PG

PLAF Information modified related to communication of a notice of opposition and request to file observations + time limit

Free format text: ORIGINAL CODE: EPIDOSCOBS2

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

Free format text: ORIGINAL CODE: EPIDOSNOBS3

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

BERE Be: lapsed

Owner name: MAN TURBO A.G.

Effective date: 20060331

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

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

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: 20050518

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

Ref country code: ES

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

Effective date: 20060331

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: MAN DIESEL & TURBO SE

APBM Appeal reference recorded

Free format text: ORIGINAL CODE: EPIDOSNREFNO

APBP Date of receipt of notice of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA2O

APAH Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNO

APBQ Date of receipt of statement of grounds of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA3O

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

Ref country code: FR

Payment date: 20130408

Year of fee payment: 14

Ref country code: DE

Payment date: 20130321

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R064

Ref document number: 50010337

Country of ref document: DE

Ref country code: DE

Ref legal event code: R103

Ref document number: 50010337

Country of ref document: DE

APBU Appeal procedure closed

Free format text: ORIGINAL CODE: EPIDOSNNOA9O

RDAF Communication despatched that patent is revoked

Free format text: ORIGINAL CODE: EPIDOSNREV1

RDAG Patent revoked

Free format text: ORIGINAL CODE: 0009271

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

Free format text: STATUS: PATENT REVOKED

27W Patent revoked

Effective date: 20131127

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

Ref country code: NL

Payment date: 20140319

Year of fee payment: 15

REG Reference to a national code

Ref country code: DE

Ref legal event code: R107

Ref document number: 50010337

Country of ref document: DE

Effective date: 20140522

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

Ref country code: IT

Payment date: 20140327

Year of fee payment: 15

REG Reference to a national code

Ref country code: AT

Ref legal event code: MA03

Ref document number: 295939

Country of ref document: AT

Kind code of ref document: T

Effective date: 20131127

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 50010337

Country of ref document: DE