EP1069313A2 - Turbo-compresseur - Google Patents

Turbo-compresseur Download PDF

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Publication number
EP1069313A2
EP1069313A2 EP00810275A EP00810275A EP1069313A2 EP 1069313 A2 EP1069313 A2 EP 1069313A2 EP 00810275 A EP00810275 A EP 00810275A EP 00810275 A EP00810275 A EP 00810275A EP 1069313 A2 EP1069313 A2 EP 1069313A2
Authority
EP
European Patent Office
Prior art keywords
turbocompressor
radial
electric motor
shaft
housing
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.)
Granted
Application number
EP00810275A
Other languages
German (de)
English (en)
Other versions
EP1069313B1 (fr
EP1069313A3 (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
Sulzer Turbo AG
MAN Turbomaschinen 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=26073837&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1069313(A2) "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
Priority to EP00810275A priority Critical patent/EP1069313B1/fr
Application filed by Sulzer Turbo AG, MAN Turbomaschinen AG filed Critical Sulzer Turbo AG
Priority to US09/599,098 priority patent/US6390789B1/en
Priority to CA002312085A priority patent/CA2312085C/fr
Priority to DE20011217U priority patent/DE20011217U1/de
Priority to JP2000192340A priority patent/JP4395242B2/ja
Priority to KR1020000039923A priority patent/KR100761917B1/ko
Priority to CNB001201123A priority patent/CN1153906C/zh
Publication of EP1069313A2 publication Critical patent/EP1069313A2/fr
Publication of EP1069313A3 publication Critical patent/EP1069313A3/fr
Publication of EP1069313B1 publication Critical patent/EP1069313B1/fr
Application granted granted Critical
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
    • F04D29/05—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
    • 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
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system

Definitions

  • the invention relates to a turbocompressor according to the preamble of Claim 1.
  • a turbocompressor which is a radial turbocompressor and an electric motor, each of these units in one separate housing is arranged, 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 is relatively large that a plurality of seals and Bearings are required and that the manufacturing cost of the Turbocompressors are therefore relatively high.
  • the publication DE 37 29 486 C1 discloses one in FIG Turbo compressor, which two two-stage radial turbo compressor and one Includes electric motor, which are coupled to a rigid shaft, which is supported in three places with magnetic radial bearings.
  • This Embodiment has the disadvantage that the assembly is very is complex and difficult that this arrangement for one at most two-stage radial turbocompressor is suitable, and that the Turbo compressor has relatively high dissipation losses.
  • the object of the present invention is an economically more advantageous one To propose turbocompressors.
  • the object is achieved in particular with a turbocompressor an electric motor, a multi-stage radial turbocompressor and one common shaft, with a portion of the shaft as the rotor of Electric motor is formed, and wherein a further section of the shaft is designed as a rotor of the radial turbocompressor, the rotor being a Compressor shaft and associated compressor wheels, and wherein to support the shaft several electromagnetic radial bearings in Direction of the shaft are arranged spaced, and wherein a single between the rotor of the electric motor and the compressor wheel electromagnetic radial bearing is arranged, and wherein the electric motor, the radial turbocompressor, the shaft and the radial bearings in one common, gas-tight housing are arranged to the outside, and wherein the housing consists of several sub-housings, which are fixed are interconnectable, the electric motor in a partial housing and Radial turbocompressor is arranged in a partial housing, and the rotor of the electric motor and the rotor of the
  • turbocompressor comprising an electric motor, a multi-stage radial turbocompressor and a common shaft, with a portion of the shaft as a rotor of the electric motor is formed, and wherein a further section of the Shaft is designed as a rotor of the radial turbocompressor, the rotor a compressor shaft and compressor wheels connected thereto, and with several electromagnetic radial bearings in to support the shaft Direction of the shaft are spaced, the Radial bearings are supported on a common base element.
  • turbocompressor comprising an externally gas-tight housing inside which a common shaft, an electric motor and a multi-stage Radial turbocompressors are arranged, being used to support the shaft in its Direction of electromagnetic radial bearings spaced apart are, and being between the electric motor and the radial turbocompressor a dry gas seal enclosing the shaft is arranged around the Seal electric motor with respect to the radial turbocompressor, the Electric motor has an interior, which fluidly with the Housing penetrating outlet opening is connected.
  • Fig. 1 shows a known turbocompressor, which one on both sides mounted electric motor and a bilateral Includes radial turbocompressor, wherein the shaft of the electric motor via a flexible shaft part is coupled to the shaft of the radial turbocompressor.
  • turbocompressor for the complete storage of the entire shaft, opposite the 1, three radial bearings, in particular configured as an electromagnetic radial bearing, suffice by between the Electric motor and the compressor a single radial bearing is arranged. This makes the turbocompressor cheaper to manufacture.
  • the entire shaft can be designed in one piece.
  • a very rigid coupling is allowed to form an overall shaft, which one in the direction of the wave largely homogeneous stiffness curve.
  • the total wave or the entire rotatable components of the As a result, turbo compressors behave like a compact shaft has a positive effect on the stable running behavior of the turbocompressor. In addition this enables the entire shaft in with the help of a single thrust bearing to store in the axial direction.
  • a radial turbocompressor If only on one side of the electric motor a radial turbocompressor is arranged, three are sufficient spaced in the direction of the shaft arranged electromagnetic radial bearings for complete storage of the entire wave. Is on each side of the electric motor Arranged radial turbocompressors, four are sufficient in the direction of the Shaft spaced electromagnetic radial bearings for complete storage of the entire shaft.
  • Dispensing with a radial bearing between the electric motor and the Radial turbo compressor also has the advantage that the length of the entire wave is shorter, which is advantageous in terms of rotor dynamics, an easier one Allows to form wave, and also a more compact design of the Turbo compressor results.
  • electromagnetic Radial bearings in comparison to hydrodynamic radial bearings an essential have less bearing force, so that is due to the shorter shaft gained, more advantageous rotor dynamic behavior and the lower Weight is critical to keep the turbocompressor safe and operate trouble-free by means of electromagnetic bearings.
  • the motor and the Radial turbocompressors in a common, hermetically sealed Housing, in particular a pressure housing, wherein a fluid-conducting inlet and outlet penetrate the housing or on the housing are flanged to compress the radial turbocompressor Supply and discharge fluid.
  • the radial turbocompressor with a hermetically sealed to the outside
  • the motor-compressor system according to the invention allows pressure housings also operate at locations that were previously used to operate a Radial turbo compressor were unsuitable, for example under water or in an environment with high levels of pollutants and high levels of pollution or high risk of explosion.
  • turbocompressor Another advantage of the turbocompressor according to the invention is therein see that this can also be operated very securely by remote control.
  • the Turbocompressors for example, do not have a complex oil system Storage of the rotor. In addition, there are no seals or only a few required. The turbocompressor therefore has no components whose operation requires a specialist on site, or components which require regular checks at relatively short intervals.
  • the turbocompressor can be started and stopped remotely run, whereby the states of the turbocompressor from Can be monitored remotely and when an irregularity is detected appropriate measures, such as stopping, are automatically initiated can be.
  • a turbocompressor is included in the design hermetically sealed pressure housing has the further advantage that the The risk of external interference is very low.
  • part of the compressed Fluids or process gases for longitudinal gas cooling of the engine and the Radial bearing used is an advantage.
  • Electric motor is preferably one for suction pressure or standstill pressure designed motor used.
  • the electric motor has a separate one from the radial turbocompressor separate cooling circuit.
  • the inventive Turbo compressor has a common base element, which for example, is plate-shaped, and on which some, preferably all radial bearings are supported.
  • the arrangement of the Radial bearings on a common base element have the advantage that they are aligned with each other in a defined position, and that due to tensile, compressive or shear stresses or mutual due to temperature influences Displacements in the radial bearings can be kept to a minimum. So is a mutually precisely arranged alignment of the radial bearings different operating conditions guaranteed.
  • the radial bearings are arranged on the base element but also the other elements such as the electric motor, the radial turbocompressor etc.
  • the turbocompressor as a whole Ready to assemble the module in the manufacturing plant.
  • This module can be Application site can be put into operation very quickly since it is no longer the radial turbocompressor and the electric motor are required separately anchoring a document and exactly the mutual position adjust.
  • the turbocompressor is arranged within a housing, part of the housing, for example, the inner wall of the housing arranged below, at the same time forms the common basic element.
  • the turbocompressor Radial turbo compressor and the motor in a common housing arranged, the housing consisting of several interconnectable Part housing, or consists of a substantially single housing.
  • the entire drive device is advantageously in one partial housing and in a further partial housing the entire radial turbocompressor arranged, these partial housings preferably mutually are adapted to be directly centerable and mutually are firmly connectable.
  • this is common housing designed so stiff that the entire Turbocompressor comprising the radial turbocompressor, the engine, etc. the common housing mutually essentially free of displacement is mounted so that the common housing, for example, designed as a pipe, without external support, or with only one or two Supports can be supported on a surface.
  • the turbocompressor known from FIG. 1 consists of a separate motor with its own housing, as well as with a radial turbocompressor another, own housing.
  • the mutual movement of the housing or the displacement of the individual waves is a significant problem, which is caused by this is that each housing is individually anchored to the floor. By different thermal expansions or other acting forces the individual housings change their position.
  • the inventive Arrangement of engine and radial turbocompressor on a common Base element, in particular in a common housing has the Advantage that the base element or the housing Reference for storage forms, and therefore a mutual change the position of the engine and radial turbocompressor largely excluded is.
  • Fig. 1 shows schematically a known turbocompressor 1, which one Radial turbocompressor 3 with a shaft 3a and a driving one Includes electric motor 2 with a shaft 2a.
  • the wave 3a of the Radial turbocompressor 3 is supported on both sides by two radial bearings 5.
  • the shaft 2a of the electric motor 2 is likewise formed by two radial bearings 5 each stored on both sides.
  • the two shafts 2a, 3a are via a coupling 4 comprising two coupling parts 4a and a flexible intermediate piece 4b connected so that the electric motor 2 via the shaft 2a and the clutch 4th drives the shaft 3a of the radial turbocompressor 3.
  • Fig. 2 shows a turbocompressor 1, which is in a hermetic sealed pressure housing 6 is arranged, each one Pressure housing 6 penetrating supply line 6c and discharge line 6d provided is fluid-conducting to the radial turbocompressor 3 with an outside of the To connect pressure housing 6 arranged device.
  • the electric motor 2 comprises the rotor 2b and the stator 2c, the rotor 2b being part of the Motor shaft 2a is, and the motor shaft 2a on both sides in the electromagnetic Radial bearing 5, each comprising a support device 5a and one electromagnetic coil 5b, is mounted in the radial direction.
  • the Motor shaft 2a has an axial bearing 7 against radial centrifugal compressor 3 on, which forms part of the motor shaft 2a disc 2d and includes electromagnetic coils 7a.
  • the motor shaft 2a is on the other End section via a clutch 4 with the rotor 3a of the Radial turbocompressor 3 connected, the opposite End portion of the rotor 3a is mounted in a radial bearing 5.
  • the Motor shaft 2a and rotor 3a form a common shaft 13.
  • two compressor wheels 3b are arranged, which has a first compression stage 3c and a second compression stage Train 3d.
  • the guide vanes 3f of the are not shown Radial turbo compressor 3.
  • the main mass flow 8 of the to be compressed Fluid passes through the inlet opening 6a and the feed line 6c into the first compression stage 3c subsequently to the second compression stage 3d and subsequently via the Discharge 6d directed to the outlet opening 6b.
  • a small fraction of the The main mass flow 8 is at the exit point of the first Compression stage 3c derived via a connecting line 11 and as Cooling gas mass flow 9 fed to a filter device 10, which the Cooling gas mass flow 9 cleans of impurities, and the cleaned Cooling gas mass flow 9 as a coolant to the electromagnetic radial bearings 5 and the electric motor 2 feeds.
  • the cooling gas mass flow 9 flows in the longitudinal direction of the housing, the radial bearing 5 and subsequently the electric motor 2 and the other Radial bearing 5 supplied, the cooling gas preferably between the Wave 2a and the respective magnet 5b, 2c is performed.
  • the Cooling gas mass flow 9 opens to the suction side of the first Compression level 3c, which is in turn compressed by this, and is called Main mass flow 8 and / or further promoted as a cooling gas mass flow 9.
  • the connecting line 11 and the filter device 10 can be inside or be arranged outside the pressure housing 6 extending.
  • the Turbo compressor 1 according to the embodiment shown in FIG. 2 has the advantage that no seal of the motor shaft 2a or Runner 3a versus atmosphere is required. In addition, there is no seal between between the engine 2 and the first compression stage 3c required.
  • the electric motor 2 is to be designed in such a way that it also has Suction pressure or can be operated with standstill pressure.
  • the turbocompressor 1 could of course have a plurality in the direction of travel of the rotor 3a have spaced-apart compressor wheels 3b, so for example, a total of four, six, eight or ten compressor wheels 3b.
  • the compression pressure to be achieved is largely open upwards, with a corresponding number connected in series Compressor wheels 3b, for example, a compression pressure of 600 bar is achievable.
  • the turbocompressor 1 could also have one or more others Radial turbocompressors 3 and / or electric motors 2, which in Direction of the runner 3a; 2a are arranged, with all runs 3a; 2a form a common wave.
  • This common wave could go through Radial bearings, in particular magnetic radial bearings 5, can be mounted preferably a single one between each radial turbocompressor 3 Radial bearing 5 is arranged. All radial turbocompressors 3 are preferably third together with the electric motor 2 or the electric motors 2 in one common, single pressure housing 6 arranged.
  • the electromagnetic radial bearings 5 and the radial bearings 5 assigned sections of the shafts 2a and 3a have further, for one Components which are obvious to a person skilled in the art and therefore not shown to form an electromagnetic radial bearing 5, such as electrical Coils, ferromagnetic parts etc.
  • Fig. 3 shows a longitudinal section of a further embodiment of a Turbocompressor 1 comprising two radial turbocompressors 3, each on Side of the electric motor 2 each arranged a radial turbocompressor 3 and whose rotor 3a is connected to the motor shaft 2a via a coupling 4. Only the upper half of the turbocompressor 1 is shown. It will only be the essential compared to the embodiment of FIG. 2 Differences described in detail.
  • the entire wave encompassing the Motor shaft 2a and the two rotor 3a is by four, in the longitudinal direction electromagnetic radial bearings 5 distributed over the entire shaft stored.
  • the radial turbocompressor 3 arranged on the left is as Low pressure part connected and has six compressor wheels 3b.
  • the radial turbocompressor 3 arranged on the right is a high-pressure part connected and has five compressor wheels 3b. Also shown are the guide vanes 3f.
  • the main mass flow 8 occurs via the feed line 6c into the low-pressure part, and after compressing it via a Connection line 12 fed to the high pressure part, the Main mass flow 8 the high pressure part after compression via the Lead 6d leaves.
  • a small part of the main mass flow 8 is after the first compression stage 3c as cooling gas mass flow 9 in the Connection line 11 passed, this cooling gas mass flow 9 after the flow through the filter 10 on the right side of the electric motor 2 arranged interior 9c is fed, and then in the longitudinal direction of the motor shaft 2a flowing over the interior 9b of the suction opening flows to the first compression stage 3c.
  • part of the Radial turbocompressor 3 located process gas for cooling the Electric motor 2 derived and used.
  • the electric motor 2 is in turn designed to to be operable at a suction pressure or a standstill pressure.
  • the Connecting line 12 and / or the connecting line 11 as well Filter device 10 could also be entirely within the housing 6 be arranged progressively.
  • the radial turbocompressors 3 can for example also in a “back to back “arrangement, in other words such that the forces caused by the two radial turbocompressors 3 on the shaft in act in the opposite direction, so that in the direction of the Motor shaft 2a to compensate and reduce acting thrust forces.
  • the housing 6 settles in the embodiments according to FIGS. 3 and 4 from the three sub-housings 6e, 6f, 6g together, the sub-housings 6e, Form 6g part of the radial turbocompressor 3 and the partial housing 6f part of the Motors 2 forms.
  • the sub-housings 6e, 6f, 6g are mutually adapted in this way configured that they, as shown in Figures 3 and 4, fixed can be connected to one another, for example by means of screws.
  • connection points can also be such mutually adapted to be arranged that are arranged adjacent Part housing when pushing together and connecting with respect to Center the longitudinal axis of the turbocompressor 1 automatically.
  • the two partial housings 6e, 6g each have an opening 23a in the outer wall on, which can be closed gas-tight with a cover 23b.
  • 3 is the in the partial housing 6g arranged opening 23a shown with cover 23b.
  • the Turbocompressor 1 is preferably prefabricated such that the Radial turbocompressor 3 is installed in the respective partial housing 6e, 6g and the electric motor 2 is installed in the sub-housing 6f.
  • the so Pre-configured sub-housings 6e, 6f, 6g are assembled Condition transported to the application site.
  • the assembly of the Turbocompressor 1 is as follows: After the partial housing 6e, 6f, 6g over the Flanges 6k, 61 are firmly connected, the shaft 3a and the rotor 2b on the one accessible from the outside through the opening 23a Coupling 4 firmly connected. Then the opening 23a with the lid 23b closed tightly and gas-tight.
  • the on the clutch 4 Fasteners used, such as screws, are in themselves known and therefore not shown in detail.
  • the turbocompressor 1 shown in FIG. 4 essentially has otherwise configured in the housing part 6e the same as the turbocompressor according to FIG. 3 an outlet opening 6h connected to the interior 9b in a fluid-conducting manner, and an adjoining lead 6i through which the Cooling gas mass flow 9 and a small proportion of the Main mass flow 9a emerges and, for example, a plant foreign Process source is fed.
  • This arrangement points towards the 3 has the advantage that the pressure in the Derivation 6i subsequent device regardless of the pressure in Radial turbocompressor 3, which pressure is preferably chosen in this way is that the engine cooling takes place at a lower pressure level than in the Embodiment according to FIG.
  • the Derivation 6i can be fed to a compressor 24, for example, which compresses the mass flow 9, 9a again the inlet opening 6a feeds.
  • the suction pressure generated by the compressor in the discharge line 6i can for example lower than 50 bar.
  • a control device 17 which at least to control the electromagnetic radial bearings 5 and the motor 2 serves.
  • the sensors 16a, 16b, 16c, 16d arranged, which the position of the entire shaft 13 or the partial shafts 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.
  • one electrical line 15e is provided, which the control device 17 a power electronics, not shown, with the winding of the Electric motor 2 connects.
  • Fig. 5 shows a longitudinal section through a housing 6, the Junction of two sub-housings 6e, 6f is shown.
  • the flange 6k of the first partial housing 6e has a recess designed in this way, that the flange 61 of the second partial housing 6f is accommodated therein, the mutual position of the two sub-housings 6e, 6f at Joining by the flanges 6k, 61 are mutually centered.
  • the Flanges 6k, 61 are distributed by several in the circumferential direction arranged screws 6m held together with nut 6n, on the Front of the flanges 6k, 61 a groove running in the circumferential direction is provided, in which a sealing element 6o is arranged, around which the two sub-housings 6e, 6f limited interior to the outside to seal.
  • FIG. 6 shows a longitudinal section of a schematically represented housing 6 consisting of three sub-housings 6e, 6f, 6g with flanges 6k, 61 and one Lead 6c and a lead 6d.
  • the housing 6 is over two Support elements 18a, 18b are supported on a base 14.
  • Within the A base element 6p is arranged in the housing, which has a rigid, in Support extending in the longitudinal direction of the housing 6, in particular a support Forms support surface on which the electromagnetic radial bearing 5th are arranged.
  • the function of the basic element 6p is one if possible stable and preferably temperature-insensitive reference plane form on which at least some radial bearings 5 are arranged.
  • the Base element 6p can be designed in a variety of embodiments be, for example as a solid, solid plate, as a support or as Grating. On the base element 6p, other components such as the Electric motor 2 or the radial turbocompressor 3 can be anchored.
  • the Using a base element 6p enables the electromagnetic Radial bearings 5 mutually very precise and in particular exactly aligned to arrange.
  • the common arrangement of the radial bearing 5 on the Base element 6p has the advantage that the attacking Tensile, compressive or shear forces or due to temperature influences mutual displacements of the radial bearings are very small. In addition this arrangement can be set up ready for operation very quickly.
  • the bearing force that can be generated by electromagnetic radial bearings is much lower than that of known hydrodynamic bearings Generatable bearing force. That is why the exact mutual Alignment of the electromagnetic radial bearings as well as preventing one mutual displacement of the radial bearings of central importance.
  • the Electromagnetic radial bearings are usually operated in such a way that the Shaft is held in the geometric center of the radial bearing. On mutual displacement of the radial bearings has the consequence that the Radial bearing has to exert considerable forces to keep the shaft in the keep geometric center. Because the electromagnetic radial bearing is relative soon reaches a state of magnetic saturation, that has Radial bearings in this situation have less, to support the shaft Available forces.
  • the two central radial bearings 5 have a relatively low one mutual distance, so that when there is a mutual offset this two central radial bearings 5 the problem may arise that this in radial forces produce opposing forces, which causes that the residual force of the electromagnetic radial bearing is less or not at all Available.
  • Fig. 7 shows a turbocompressor 1 with a compared to 4 separately cooled electric motor 2 between the pressure part of the radial turbocompressor 3 and the electric motor 2 each a system with a double seal, including one Dry gas seal 19 and subsequently a seal 20, arranged, an outlet 21 between the two seals 19, 20, as a vent (Leak to the atmosphere without gas combustion) or flare (leak to the Atmosphere with gas combustion) designed, 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 turbocompressor 3 Cooling circuit on which a connecting line 11 and a cooler 22nd includes.
  • a feed line 9d leads additional Cooling gas to, for example, those flowing off via the discharge line 21 To compensate for cooling gas.
  • a cooling gas in particular is not aggressive gas such as nitrogen.
  • the cooling circuit of the Electric motor 2 can be designed such that it has a pressure in the Range of atmospheric pressure or slightly above. 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 Cooling gas mass flow 9 is not contaminated by foreign gases. in the 7 also flows a small proportion of the Process gas 8 via the seal 19 to the outlet 21.
  • the outlet 21 can a so-called flare or vent can be subordinated to the from the Discharge exhaust gases 21 unburned (Vent) or via a to discharge subsequent combustion (flare), especially to the environment to deliver.
  • cooling gas 9 has a low pressure and / or that as a cooling gas inexpensive or easily manageable gas can be used, in particular a gas with no aggressive properties.
  • turbocompressor 1 An advantage of the turbocompressor 1 according to the invention can be seen in the fact that that the electric motor 2 and the radial turbocompressor 3 together with the corresponding housing parts 6e, 6f can be preassembled so that the Turbo compressor 1 as a housing 6 or as a unit for Installation site can be transported and set up there.
  • Lines 11, 12 and the associated components 22 can in a further embodiment also within the housing 6 be arranged progressively.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP00810275A 1999-07-16 2000-03-31 Turbo-compresseur Expired - Lifetime EP1069313B1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP00810275A EP1069313B1 (fr) 1999-07-16 2000-03-31 Turbo-compresseur
US09/599,098 US6390789B1 (en) 1999-07-16 2000-06-20 Cooling means for the motor of a turbocompressor
CA002312085A CA2312085C (fr) 1999-07-16 2000-06-21 Moyens de refroidissement pour le moteur d'un turbocompresseur
DE20011217U DE20011217U1 (de) 1999-07-16 2000-06-26 Turboverdichter
JP2000192340A JP4395242B2 (ja) 1999-07-16 2000-06-27 ターボ圧縮機
KR1020000039923A KR100761917B1 (ko) 1999-07-16 2000-07-12 터보압축기
CNB001201123A CN1153906C (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
EP00810275A EP1069313B1 (fr) 1999-07-16 2000-03-31 Turbo-compresseur

Publications (3)

Publication Number Publication Date
EP1069313A2 true EP1069313A2 (fr) 2001-01-17
EP1069313A3 EP1069313A3 (fr) 2002-05-15
EP1069313B1 EP1069313B1 (fr) 2005-09-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP00810275A Expired - Lifetime EP1069313B1 (fr) 1999-07-16 2000-03-31 Turbo-compresseur

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US (1) US6390789B1 (fr)
EP (1) EP1069313B1 (fr)
JP (1) JP4395242B2 (fr)
KR (1) KR100761917B1 (fr)
CN (1) CN1153906C (fr)
CA (1) CA2312085C (fr)
DE (1) DE20011217U1 (fr)

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WO2003071139A1 (fr) * 2002-02-21 2003-08-28 Alpha Thames Ltd Systeme d'etancheite aux gaz pour l'arbre d'un moteur de compresseur electrique
EP1467104A1 (fr) * 2003-04-11 2004-10-13 Thermodyn Groupe moto-compresseur centrifuge à réfrigération assistée
WO2007110281A1 (fr) * 2006-03-24 2007-10-04 Siemens Aktiengesellschaft Unité de compression
DE102010041210A1 (de) * 2010-09-22 2012-03-22 Siemens Aktiengesellschaft Gehäuse
US8221095B2 (en) 2006-06-30 2012-07-17 Aker Subsea As Method and apparatus for protection of compressor modules against influx of contaminated gas
RU2670993C1 (ru) * 2017-08-02 2018-10-29 Василий Сигизмундович Марцинковский Компрессорный агрегат компримирования азото-водородной смеси в производстве аммиака (варианты)

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EP2466144B1 (fr) 2010-12-16 2013-02-20 FIMA Maschinenbau GmbH Dispositif pour comprimer un gaz de procédé
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EP2715167B1 (fr) 2011-05-27 2017-08-30 Dresser-Rand Company Roulement segmenté à décélération en roue libre pour des systèmes de roulement magnétique
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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
FR2980538B1 (fr) 2011-09-27 2013-10-25 Thermodyn Groupe moto-compresseur a cartouche amovible
DE102012204403A1 (de) * 2012-03-20 2013-09-26 Man Diesel & Turbo Se Radialverdichtereinheit
RU2485354C1 (ru) * 2012-04-26 2013-06-20 федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Южно-Российский государственный технический университет (Новочеркасский политехнический институт)" Компрессорная установка
DE102012012540A1 (de) * 2012-06-26 2014-01-02 Robert Bosch Gmbh Turboverdichter
ITCO20130069A1 (it) * 2013-12-18 2015-06-19 Nuovo Pignone Srl Compressore centrifugo multistadio
KR20150074625A (ko) * 2013-12-24 2015-07-02 삼성테크윈 주식회사 압축 장치 코어용 지지대 및 이를 구비한 압축 장치 모듈
WO2015197467A1 (fr) * 2014-06-24 2015-12-30 Sterling Industry Consult Gmbh Pompe à canal latéral
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JP6460773B2 (ja) * 2014-12-19 2019-01-30 株式会社マーレ フィルターシステムズ ターボチャージャ
DE102015207341B4 (de) * 2015-04-22 2019-02-14 Ford Global Technologies, Llc Verdichter und Kraftfahrzeug
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CN108930655B (zh) * 2018-09-06 2023-11-03 东营市深蓝新材料有限公司 一种具有防堵塞功能的油田用离心泵
CN110953250B (zh) * 2019-12-03 2020-12-18 珠海格力电器股份有限公司 一种磁悬浮轴承转子结构、电机和空调器
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Cited By (10)

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Publication number Priority date Publication date Assignee Title
WO2003071139A1 (fr) * 2002-02-21 2003-08-28 Alpha Thames Ltd Systeme d'etancheite aux gaz pour l'arbre d'un moteur de compresseur electrique
EP1467104A1 (fr) * 2003-04-11 2004-10-13 Thermodyn Groupe moto-compresseur centrifuge à réfrigération assistée
FR2853700A1 (fr) * 2003-04-11 2004-10-15 Thermodyn Groupe moto-compresseur centrifuge a refrigeration assistee.
NO342391B1 (no) * 2003-04-11 2018-05-14 Thermodyn Kombinert motor og sentrifugalkompressor med kjøling
WO2007110281A1 (fr) * 2006-03-24 2007-10-04 Siemens Aktiengesellschaft Unité de compression
CN101410624B (zh) * 2006-03-24 2011-03-02 西门子公司 压缩机单元
US8221095B2 (en) 2006-06-30 2012-07-17 Aker Subsea As Method and apparatus for protection of compressor modules against influx of contaminated gas
DE102010041210A1 (de) * 2010-09-22 2012-03-22 Siemens Aktiengesellschaft Gehäuse
US9291073B2 (en) 2010-09-22 2016-03-22 Siemens Aktiengesellschaft Centering attachment of a compressor housing cover
RU2670993C1 (ru) * 2017-08-02 2018-10-29 Василий Сигизмундович Марцинковский Компрессорный агрегат компримирования азото-водородной смеси в производстве аммиака (варианты)

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JP2001041199A (ja) 2001-02-13
CN1281100A (zh) 2001-01-24
KR20010015306A (ko) 2001-02-26
US6390789B1 (en) 2002-05-21
EP1069313B1 (fr) 2005-09-14
JP4395242B2 (ja) 2010-01-06
CA2312085A1 (fr) 2001-01-16
EP1069313A3 (fr) 2002-05-15
CA2312085C (fr) 2003-10-21
DE20011217U1 (de) 2000-09-07
CN1153906C (zh) 2004-06-16
KR100761917B1 (ko) 2007-09-28

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