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US20100232984A1 - Compressor Unit and Use of a Cooling Medium - Google Patents

Compressor Unit and Use of a Cooling Medium Download PDF

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Publication number
US20100232984A1
US20100232984A1 US12/225,325 US22532507A US2010232984A1 US 20100232984 A1 US20100232984 A1 US 20100232984A1 US 22532507 A US22532507 A US 22532507A US 2010232984 A1 US2010232984 A1 US 2010232984A1
Authority
US
United States
Prior art keywords
cooling
compressor unit
compressor
rotor
medium
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.)
Abandoned
Application number
US12/225,325
Other languages
English (en)
Inventor
Maria Bade
Axel Möhle
Günter Zwarg
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.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ZWARG, GUNTER, BADE, MARIA, MOHLE, AXEL
Publication of US20100232984A1 publication Critical patent/US20100232984A1/en
Abandoned 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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F04D13/10—Units comprising pumps and their driving means the pump being electrically driven for submerged use adapted for use in mining bore holes
    • 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
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/005—Cooling of bearings of magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0474—Active magnetic bearings for rotary movement
    • F16C32/0489—Active magnetic bearings for rotary movement with active support of five degrees of freedom, e.g. two radial magnetic bearings combined with an axial bearing

Definitions

  • the invention relates to a compressor unit for compression of a pumping medium, in particular for underwater operation, comprising a compressor and an electric motor which comprises a stator and a rotor, with the stator of the motor being connected to a separate cooling arrangement and being cooled by means of the separate cooling arrangement, which cooling arrangement has a cooling medium.
  • the subject matter of the invention covers the use of a special cooling medium for cooling a stator of a motor of a compressor unit for operation under water.
  • a compressor unit of the abovementioned type is already known from international patent application WO 02/099286 A1.
  • the compressor unit described there provides, for cooling purposes, that a portion is tapped off from the pumping medium, generally natural gas, in the area of an overflow from the radial stages of the compressor and is used to pass around the components to be cooled, in such a way that the heat losses, which are in the order of magnitude of 100-200 kW, are dissipated with the cold medium to be pumped.
  • This concept for cooling the compressor unit is particularly advantageous since the pumping medium which must be transported in any case is used to dissipate the heat losses and there is no need for any additional media exchange between the compressor unit and further components of the environment.
  • this procedure results in particular difficulties owing to the aggressive chemistry of the media to be pumped.
  • the pumping medium is frequently heavily contaminated and can adversely affect the operation of sensitive components because it flows around them.
  • the bearings, the axial bearings and the radial bearings are therefore encapsulated in such a way that no substances are exchanged between the surrounding area and these components.
  • magnetic bearings must be used.
  • This also applies to the rotor and to the stator, which are protected against the aggressive pumping media in a similar manner by means of encapsulation. While it is sufficient to cool the rotor by passing flow around it, further cooling measures are required to dissipate the heat losses for the stator.
  • One solution from the prior art provides for the stator to be provided with cooling channels, with the pumping medium flowing through these channels for cooling purposes.
  • the invention is therefore based on the object of providing a cooling arrangement for the stator of an electric motor of a motor-driven compressor unit, in particular for undersea operation, which on the one hand offers excellent operational reliability and on the other hand does not require any substances to be exchanged with the environment during operation.
  • a compressor unit as claimed in claim 1 and the use of a pentaerythritol tetracarboxylic acid ester as cooling medium according to claim 11 are proposed in order to solve this problem.
  • the dependent claims each contain advantageous developments of the invention.
  • One particularly advantageous variant for operation of the cooling arrangement is to use a pentaerythritol tetracarboxylic acid ester as a cooling medium for cooling the stator of the motor during operation under water.
  • the high flammability of the pentaerythritol tetracarboxylic acid ester and the reduced risk of fire associated with it are a major advantage of use according to the invention.
  • the low corrosion characteristic and the excellent compatibility with the insulating materials used in these areas, such as mica strips and epoxy resin and/or impregnation resins, are further factors.
  • ester liquids and the “Midel” or “Shell Fluid 4600” may be mentioned as examples of pentaerythritol tetracarboxylic acid esters. These liquids are respectively not only an excellent insulator and compatible with the surrounding materials but also comply with the stringent fire protection requirements and stringent requirements for environmental compatibility, since, in particular, they can be classified as not water-contaminating.
  • the sensitivity of the stator to contamination is taken into account if the cooling arrangement has a closed circuit in which the cooling medium (pentaerythrityl tetracarbonate) circulates. It is worthwhile in this case for the cooling arrangement to have a heat exchanger which is connected to the cooled stator by means of a feed line and a return line, with the cooling arrangement being designed such that the cooling medium (pentaerythritol tetracarboxylic acid ester) circulates between the heat exchanger, the return line, the stator and the feed line.
  • the cooling medium penentaerythritol tetracarboxylic acid ester
  • the circulation can be driven by means of natural convection, thus resulting in a natural circulation of the cooling medium between the abovementioned components.
  • the cooling medium circuit is operated in a forced-circulation mode by means of a pump. No phase exchange should take place in this case. This ensures a particularly wide thermal range of operation.
  • separate cooling for the stator of the electric motor of the compressor unit, on the one hand, and another cooling system for the further elements of the compressor unit, on the other hand, are particularly expedient.
  • the separation of the cooling from the cooling system is appropriate for the particular requirements for the heat dissipation from the stator of a compressor unit of this generic type.
  • the cooling system which, inter alia, cools the compressor and the rotor of the motor as well particularly advantageously provides the pumping medium as the cooling medium, as a result of which the heat losses are dissipated with the pumping medium to be compressed. This is particularly advantageous for undersea pumping of natural gas, since this is generally relatively cold.
  • FIG. 1 shows a schematic illustration of a longitudinal section through a compressor unit according to the invention.
  • FIG. 1 shows, schematically, a section along a compressor unit 1 according to the invention which has, as major components, a motor 2 and a compressor 3 in a gas-tight housing 4 .
  • the housing 4 accommodates the motor 2 and the compressor 3 .
  • the housing 4 is provided with an inlet 6 and an outlet 7 in the area of the junction between the motor 2 and the compressor 3 , with the fluid to be compressed being sucked in through the inlet 6 by means of a suction connecting stub 8 , and with the compressed fluid flowing out through the outlet 7 .
  • the compressor unit 1 is arranged vertically during operation, with a motor rotor 15 of the motor 2 above a compressor rotor 9 of the compressor 3 being combined to form a common shaft 19 which rotates about a common vertical rotation axis 60 .
  • the motor rotor 15 is borne in a first radial bearing 21 at the upper end of the motor rotor 15 .
  • the compressor rotor 9 is borne by means of a second radial bearing 22 in the lower position.
  • An axial bearing 25 is provided at the upper end of the common shaft 19 , that is to say at the upper end of the motor rotor 15 .
  • the radial bearings and the axial bearing operate electromagnetically and are each encapsulated.
  • the radial bearings extend around the respective bearing point of the shaft 19 in the circumferential direction and in this case are circumferential through 360° and are undivided.
  • the compressor 3 is in the form of a centrifugal compressor and has three compressor stages 11 which are each connected by means of an overflow 33 .
  • the pressure differences which result across the compressor stages 11 ensure that there is a thrust on the compressor rotor 9 which is transmitted on the motor rotor 15 and is directed against the force of gravity from the entire resultant rotor comprising the compressor rotor 9 and the motor rotor 15 , thus resulting in a very high degree of thrust matching during rated operation.
  • This allows the axial bearing 25 to be designed to be comparatively smaller than if the rotation axis 60 were to be arranged horizontally.
  • the electromagnetic bearings 21 , 22 , 25 are cooled to the operating temperature by means of a cooling system 31 , with the cooling system 31 providing a tap 32 in an overflow of the compressor 3 .
  • a portion of the pumping medium which is preferably natural gas, is passed from the tap 32 by means of pipelines through a filter 35 , and is then passed through two separate pipelines to the respective outer bearing points (first radial bearing 21 and fourth radial bearing 24 as well as the axial bearing 25 ).
  • This cooling by means of the cold pumping medium 80 saves additional supply lines.
  • the motor rotor 15 is surrounded by a stator 16 which has encapsulation 39 such that the aggressive pumping medium 80 does not damage the windings of the stator 16 .
  • the encapsulation is in this case preferably designed such that it can contribute to the full operating pressure. This is also because a separate cooling arrangement 40 is provided for the stator, in which cooling arrangement 40 a dedicated cooling medium (pentaerythritol tetracarboxylic acid ester) 56 circulates.
  • a pump 42 in this case ensures circulation via a heat exchanger 43 .
  • At least the encapsulation 39 is designed such that the section which extends between the stator 16 and the motor rotor 15 , while having a thin wall thickness, is nevertheless able to withstand the design pressure when the stator cooling arrangement 40 is completely filled by means of the cooling medium 56 . This makes it possible to avoid relatively high eddy current losses in this area, thus improving the efficiency of the overall arrangement.
  • the compressor rotor 9 expediently has a compressor shaft 10 on which the individual compressor stages 11 are mounted. This can preferably be done by means of a thermal shrink fit. An interlock, for example by means of polygons, is likewise possible. Another embodiment provides for different compressor stages 11 to be welded to one another, thus resulting in an integral compressor rotor 9 .
  • FIG. 2 shows the motor rotor 15 , the stator 16 and the cooling arrangement 40 .
  • the cooling arrangement 40 has a cooling circuit 50 which extends through cooling channels 51 , collecting areas 52 arranged on both sides of the cooling channels 51 , into lines which connect these collecting areas, specifically a feed line 53 and a return line 54 , as well as a condenser 55 arranged between the feed line 53 and the return line 54 .
  • the cooling medium 56 namely a pentaerythritol tetracarboxylic acid ester with the trade name “Midel”, starts to flow in cooling channels 51 of the stator 16 , flows through the feed line 53 into the heat exchanger 55 where the cooling medium 56 is cooled flows through the return line 54 into a collecting area 52 which is located at the return end of the cooling channels 51 .
  • the circuit is closed.
  • the temperature difference between the feed and the return is preferably 10 K.
  • the heat exchanger is located geodetically at the highest point (height difference ⁇ H), thus assisting natural convection.
  • a pump 42 is arranged in the return.
  • the stator is encapsulated, and cooling by means of the pumping medium 80 which flows around the rotor 15 takes place in a gap between the rotor 15 and the stator 16 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US12/225,325 2006-03-24 2007-02-13 Compressor Unit and Use of a Cooling Medium Abandoned US20100232984A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP06006069.6 2006-03-24
EP06006069 2006-03-24
PCT/EP2007/051393 WO2007110271A1 (fr) 2006-03-24 2007-02-13 Unité de compression et utilisation d'un fluide de refroidissement

Publications (1)

Publication Number Publication Date
US20100232984A1 true US20100232984A1 (en) 2010-09-16

Family

ID=38057555

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/225,325 Abandoned US20100232984A1 (en) 2006-03-24 2007-02-13 Compressor Unit and Use of a Cooling Medium

Country Status (7)

Country Link
US (1) US20100232984A1 (fr)
EP (1) EP1999378A1 (fr)
CN (1) CN101410626A (fr)
BR (1) BRPI0709178A2 (fr)
NO (1) NO20084447L (fr)
RU (1) RU2394172C1 (fr)
WO (1) WO2007110271A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090322095A1 (en) * 2008-06-26 2009-12-31 Ed Mazur Wind turbine
US20150064026A1 (en) * 2013-09-03 2015-03-05 Dresser-Rand Company Motor cooling system manifold
US20170298755A1 (en) * 2015-02-23 2017-10-19 Mitsubishi Heavy Industries, Ltd. Compressor system
US10400788B2 (en) * 2014-02-06 2019-09-03 Mitsubishi Heavy Industries Compressor Corporation Intermediate intake-type diaphragm and centrifugal rotating machine
WO2020106879A1 (fr) * 2018-11-19 2020-05-28 Smart E, Llc Compresseur centrifuge sans lubrification
CN111637341A (zh) * 2020-05-26 2020-09-08 南京林业大学 一种智能适老家居功能控制装置
US10989201B2 (en) * 2016-03-29 2021-04-27 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2103810A1 (fr) * 2008-03-19 2009-09-23 Siemens Aktiengesellschaft Unité de compresseur
DE102008031994B4 (de) * 2008-04-29 2011-07-07 Siemens Aktiengesellschaft, 80333 Fluidenergiemaschine
WO2011019334A1 (fr) * 2009-08-11 2011-02-17 General Electric Company Moteur à aimant permanent pour entraînement de pompe sous-marine
FR2966528B1 (fr) * 2010-10-25 2016-12-30 Thermodyn Groupe compresseur centrifuge
CN110118184B (zh) * 2019-06-19 2020-12-11 徐州精一泵业有限公司 一种具有协同密封系统的全干式潜水电泵

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5560850A (en) * 1994-10-15 1996-10-01 Roehm Gmbh Chemische Fabrik Biodegradable oligoesters suitable as lubricants
US20040170505A1 (en) * 2001-06-05 2004-09-02 Lenderink Gerardus Maria Compressor unit comprising a centrifugal compressor and an electric motor
US6994602B2 (en) * 2001-11-29 2006-02-07 Siemens Aktiengesellschaft Ship propulsion system

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2042710C1 (ru) * 1990-09-28 1995-08-27 Дзе Лабризол Корпорейшн Охлаждающая жидкость
RU2104448C1 (ru) * 1996-04-17 1998-02-10 Акционерное общество закрытого типа "ВИК" Холодильная установка и центробежный компрессорный агрегат холодильной установки

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5560850A (en) * 1994-10-15 1996-10-01 Roehm Gmbh Chemische Fabrik Biodegradable oligoesters suitable as lubricants
US20040170505A1 (en) * 2001-06-05 2004-09-02 Lenderink Gerardus Maria Compressor unit comprising a centrifugal compressor and an electric motor
US6994602B2 (en) * 2001-11-29 2006-02-07 Siemens Aktiengesellschaft Ship propulsion system

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090322095A1 (en) * 2008-06-26 2009-12-31 Ed Mazur Wind turbine
US8513826B2 (en) * 2008-06-26 2013-08-20 Ed Mazur Wind turbine
US20150064026A1 (en) * 2013-09-03 2015-03-05 Dresser-Rand Company Motor cooling system manifold
US9777746B2 (en) * 2013-09-03 2017-10-03 Dresser-Rand Company Motor cooling system manifold
US10400788B2 (en) * 2014-02-06 2019-09-03 Mitsubishi Heavy Industries Compressor Corporation Intermediate intake-type diaphragm and centrifugal rotating machine
US20170298755A1 (en) * 2015-02-23 2017-10-19 Mitsubishi Heavy Industries, Ltd. Compressor system
US10989201B2 (en) * 2016-03-29 2021-04-27 Mitsubishi Heavy Industries Compressor Corporation Centrifugal compressor
WO2020106879A1 (fr) * 2018-11-19 2020-05-28 Smart E, Llc Compresseur centrifuge sans lubrification
CN111637341A (zh) * 2020-05-26 2020-09-08 南京林业大学 一种智能适老家居功能控制装置

Also Published As

Publication number Publication date
NO20084447L (no) 2008-12-16
CN101410626A (zh) 2009-04-15
BRPI0709178A2 (pt) 2011-06-28
RU2008142100A (ru) 2010-04-27
RU2394172C1 (ru) 2010-07-10
EP1999378A1 (fr) 2008-12-10
WO2007110271A1 (fr) 2007-10-04

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Owner name: SIEMENS AKTIENGESELLSCHAFT, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BADE, MARIA;MOHLE, AXEL;ZWARG, GUNTER;SIGNING DATES FROM 20080910 TO 20080915;REEL/FRAME:021578/0996

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION