EP0834018B2 - Verfahren zum Kühlen eines mehrstufigen Schraubenspindelverdichters - Google Patents

Verfahren zum Kühlen eines mehrstufigen Schraubenspindelverdichters Download PDF

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Publication number
EP0834018B2
EP0834018B2 EP96922831A EP96922831A EP0834018B2 EP 0834018 B2 EP0834018 B2 EP 0834018B2 EP 96922831 A EP96922831 A EP 96922831A EP 96922831 A EP96922831 A EP 96922831A EP 0834018 B2 EP0834018 B2 EP 0834018B2
Authority
EP
European Patent Office
Prior art keywords
rotor
compressor according
rotors
cooling
opposite
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP96922831A
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German (de)
English (en)
French (fr)
Other versions
EP0834018A1 (de
EP0834018B1 (de
Inventor
Christian Dahmlos
Dietmar Rook
Ralf Steffens
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.)
Sterling Industry Consult GmbH
Original Assignee
Sterling Industry Consult GmbH
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
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Priority claimed from DE1995122557 external-priority patent/DE19522557A1/de
Priority claimed from DE1995122559 external-priority patent/DE19522559A1/de
Application filed by Sterling Industry Consult GmbH filed Critical Sterling Industry Consult GmbH
Publication of EP0834018A1 publication Critical patent/EP0834018A1/de
Publication of EP0834018B1 publication Critical patent/EP0834018B1/de
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Publication of EP0834018B2 publication Critical patent/EP0834018B2/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/51—Bearings for cantilever assemblies

Definitions

  • liquid coolant is injected (US-A4,515,540) or a portion of the pumped medium is returned after cooling (DE-A 25 44 082).
  • cooling may also be provided in combination with the invention; However, this aims at a cooling of the rotor, so that it can assume a temperature, in particular in the field of sensitive bearings, which is below the pressure-side temperature of the pumped medium.
  • the invention is therefore an object of the invention to provide a screw compressor mentioned in the preamble of claim 1, in which the rotors are cooled independently of the conveyed medium such that good conditions for a low clearance between the rotors among themselves and between the rotors and be created the pump chamber, without the need for trouble-prone waterproofing.
  • the solution according to claim 1 is composed of two components, namely, firstly, the feature that the positive displacement rotors are more strongly cooled on the suction side than the suction side, and secondly, a special type of rotor bearing cooling technology used.
  • Multi-stage rotors are to be understood as those whose compression channels forming screw flights rotate around the rotor several times, so that over the rotor length several each suction and pressure side separate compression chambers are formed.
  • the screw flights rotate around the associated rotor three times each.
  • the number of stages can be determined according to the respective pressure application area. Preferably, at least five stages are used.
  • each positive displacement rotor is mounted in a floating manner on a stationary bearing tube surrounding the rotor shaft and at least one rotor-side bearing, projecting into the rotor. Only this is cooled directly, while the cooling of the rotor takes place indirectly, that the opposing peripheral surfaces of the rotor and the bearing body are arranged heat exchangeable to each other.
  • the bearings and the rotor shaft are particularly well cooled because they are located inside the bearing tube.
  • the facing surfaces of the rotor and the bearing body can be equipped with the heat exchange improving properties.
  • the intermediate space should not be connected to the suction side but to the pressure side.
  • the surfaces may be provided with ridges and depressions that enhance the heat transfer coefficient to the medium therebetween. The mutual distance between the two surfaces should be as low as possible.
  • such a treatment of the surfaces may be provided that they have a high absorption coefficient in the region of thermal radiation.
  • the heat transfer to the opposing surfaces of the rotor and the bearing body can also be improved by the fact that the gas in between is placed in flow motion.
  • the gap can be connected to a gas source.
  • the gas flow can also be used for heat dissipation if the gas temperature (cooling if necessary) is selected accordingly be used.
  • he may optionally exercise a blocking function to protect the storage and drive area before the access of the pumped liquid or substances contained in the pumped medium.
  • the spent gas is expediently fed to the pressure side of the machine.
  • the cooperating surfaces of rotor and bearing body may be equipped with conveying members. This may make it unnecessary to provide an external compressed gas source. This is true even if the gas supplied is primarily not cooling but blocking purposes.
  • the conveying effect of the surfaces can be caused in particular by the fact that they are equipped on one side or on both sides with conveying thread. Instead, or in addition, they may also be conical, so that the centrifugal effect is exploited to promote. Such means promoting the movement of the gas in the intermediate space are also useful for improving the heat transfer, if no additional gas supply is provided.
  • the projecting into the rotor cavity part of the bearing body is suitably equipped with channels through which coolant flows, which are preferably arranged near the peripheral surface of the bearing body opposite the rotor.
  • the housing may be intensively cooled or at least maintained at a predetermined temperature without the risk of thermal run-up of the rotor on the housing arises.
  • the efficiency of the pump can be increased.
  • pre-admission it is known, in particular in the case of vacuum pumps, to allow gas to flow under higher pressure to cool the pumped medium and / or to reduce noise in the compression cells of the machine.
  • cooled gas may be used from a suitable source.
  • An external heat exchanger can be avoided by passing the Voreinlenfingas through a located in the housing-side cooling chamber heat exchanger.
  • liquid can also be added in the pump chamber, which evaporates there and thereby extracts heat from the fluid.
  • the cooling of the bearing body at least in that region in which it is in the heat influence of the rotor has the great advantage that rolling bearings can be used, which are lubricated with grease and therefore are particularly low maintenance and pose no risk of contamination for the suction chamber.
  • the above-mentioned possibility of equipping the cooperating surfaces of the rotor and the bearing body with conveying members can be used to protect the bearing area from foreign substances which could come from the suction chamber.
  • the cooperating conveying members are formed with conveying direction leading out of the rotor cavity.
  • the execution of the cooperating surfaces as conveyors is effected in that at least one of them is provided with a delivery thread. Both can also be provided with conveyor threads.
  • the direction of the thread or the thread is chosen so that the desired conveying direction results.
  • the opposing peripheral surfaces of the rotor and the bearing body are conical with a diameter which increases in the conveying direction so that the centrifugal force drives back any penetrating substances in the direction of the increasing diameter, that is to the pumping chamber. It is also possible to combine a plurality of such conveying means (for example conveying threads and conicity).
  • This effect is enhanced by the connection of the rotor cavity with a purge gas source. Thanks to the conveying effect, this source does not need to be under pressure; however, this is not excluded.
  • the gas can also serve cooling purposes.
  • a particularly important consequence of the invention is the security against the penetration of liquid into the storage and drive area.
  • the pump is not only insensitive to liquid surge with regard to the sealing effect, but it can also be flushed in a targeted manner, in particular for cleaning.
  • special means for the inlet of a washing liquid may be provided, for example, serves to solve on the rotor or housing surfaces deposited impurities and flush out. If the operating speed can not be maintained during this time, the rotors should be driven at a reasonably reduced speed.
  • appropriate control or regulating devices can be provided. It is particularly simple and advantageous to regulate the speed depending on the torque, because then the speed reduction results automatically. The speed reduction can be low, if only small amounts of liquid are sprayed into the gas flow.
  • the motor housing 2 On the foot part 1 rests the motor housing 2, which is optionally integrally connected at the top with the flange-like base plate 3, on which the pump chamber 4 is constructed. This is closed at the top by a cover 5 which contains a suction opening 6.
  • the flange plates 50 of the bearing body 7 are fastened, each serving to support a rotor 8, the circumference of which preferably carries helically two-displaceable Verdrängervorsprünge 9, which in the manner of a meshing in the delivery cavities 10 between the Verdrängervorsgen 9 of the adjacent rotor engage.
  • the Verdrängervorsge 9 cooperate on the circumference with the inner surface of the pump chamber housing part 4.
  • the rotors 8 are at the top with the suction chamber 11 and below with the pressure chamber 12 in conjunction.
  • the pressure chamber 12 is in communication with a pressure outlet, not shown. These parts are provided at the lower end of the vertically mounted pump chamber housing.
  • Each rotor 8 is rotatably connected to a shaft 20 which is mounted below in the bearing body 7 by a permanently lubricated roller bearing 21.
  • a second, likewise permanently lubricated roller bearing 22 is located at the upper end of a tubular part 23 of the bearing body 7, which projects into a downward, ie pressure side, open, concentric bore 24 of the rotor 8.
  • This bearing 22 is preferably located above the center of the rotor 8.
  • the tubular part 23 of the bearing body preferably extends through the greater part of the length of the rotor 8.
  • the end of the tubular part 23 is substantially higher than the pressure outlet 17 in a vertical arrangement of the pump This is useful for protecting the bearing and drive region from ingress of liquid or other heavy contaminants from the pump chamber.
  • cooling channels 25 are provided, which are connected via channels 26 with a cooling water source and via corresponding channels, which do not appear in the drawing, with a cooling water drain.
  • the cooling channels 25 are preferably formed by helical grooves, which are sealed by a sleeve.
  • the cooling of the rotor bearings extends the service life or the maintenance intervals of these bearings, if they are lubricated with grease. Further, the cooling also keeps the peripheral surface of the tubular part 23 of the bearing body at a low temperature. This peripheral surface is opposite the inner peripheral surface of the cavity 24 of the rotor with a small distance.
  • These surfaces are designed so that they are capable of good heat exchange and thus heat from the rotor indirectly via the tubular part 23 of the bearing body and the cooling means 25 can be removed.
  • To improve the heat exchange between the opposing surfaces of the tubular part 23 of the bearing body and the rotor cavity 24 may be formed in a suitable manner. For example, they can be treated or browned so that the radiation exchange is promoted by high absorption coefficients.
  • the convective heat exchange by means of the intervening gas layer can be improved by a small surface interval and suitable surface structure, which leads to an increase in the heat transfer coefficient.
  • One surface or both may be rough or formed with heat exchange fins or threads or the like for this purpose.
  • Suitable sealing and / or locking devices are provided. Particularly advantageous is the equipment of the opposing surfaces of the bearing body 23 and the inner surfaces of the rotor cavity 24 on one side or on both sides with a conveying thread, not shown, which exerts a delivery effect from the rotor cavity 24 to the pressure chamber 12 out. Due to its higher density, this conveying effect primarily affects solid or liquid particles, thereby preventing their penetration into the bearing and drive areas.
  • the conveyor thread is suitably designed so that this effect is still effective even at significantly reduced speed.
  • the conveying effect can also be brought about by the fact that the gap between the rotor and the bearing body widens conically towards the pressure chamber.
  • the Gap width (distance of the surface of the bearing body from the surface of the rotor) remains substantially constant.
  • the opposing surfaces may be provided on one side or on both sides with conveying thread; but this is not necessary.
  • the pump according to the invention is insensitive to the presence of liquid in the pump chamber, as long as the rotors are in rotation. This insensitivity also exists in the stationary state, thanks to the high bearing arrangement in the rotor, as long as the liquid in the pump chamber does not reach the storage level. It is not only important when the fluid is carrying a surge of fluid, but can also be used for the cleaning and / or cooling of the pump by liquid injection. For example, cleaning or cooling liquid can be sprayed through nozzles, one of which is indicated at 27. The same or separate nozzles 27 may be used for spraying the cleaning liquid and the cooling liquid.
  • the cleaning fluid should have a vapor pressure below the suction pressure. If the pump is multi-stage and the pollution is reflected (for example, pressure-dependent) mainly in the second and / or subsequent stages, it is possible to limit the injection of the cleaning liquid to the second or subsequent stage and thereby separate from the suction side.
  • the cleaning operation is not performed constantly, but periodically when cleaning demand is detected (for example, due to increase in drive torque). Thanks to the insensitivity of the pump to liquids then relatively large amounts of liquid can be used. If, due to the amount or type of cleaning liquid used, the operating speed can not be maintained, the speed can be reduced accordingly.
  • suitable control devices are provided. For example, the speed can be controlled depending on the drive torque, which automatically leads to a corresponding reduction in speed compared to the operating speed with increased power requirements.
  • the continued rotation of the rotors during the cleaning phase not only serves to seal the rotor bearing, but also promotes the action of the cleaning liquid on the soiled surfaces.
  • the conveying effect in the gap between the rotor and the bearing body can also be used to convey sealing gas independently of an external compressed gas source. In general, however, one will prefer to promote the sealing gas, the effect of such a compressed gas source to be independent of the rotor speed in the barrier gas supply.
  • the scoop chamber housing 4 may include a chamber 30 that circulates entirely or over a large portion of the circumference and circulates through the cooling water to maintain the housing at a predetermined temperature. Cooling the housing shell is not necessary in all cases. However, it is advantageously possible in the context of the invention, because the rotors 8 are cooled and their thermal expansion is therefore limited. There is no need to fear that the rotors only start up on the housing because they expand while the housing is kept at a lower temperature.
  • the pump according to the invention can be equipped with a pre-inlet. This means that in the areas high, possibly even medium compression in the housing channels 31 are provided through which in the suction chamber gas of higher pressure than it corresponds to the compression stage in this region of the pump chamber is admitted to a well-known principles To effect cooling and / or noise reduction.
  • the pre-inlet gas can be taken directly from the pressure side of the pump by being cooled in the cooling pockets 30 of the scoop jacket 4. For this purpose, it can be passed through heat exchanger tubes 32.
  • each shaft 20 preferably carries directly below the bearing 21. i.e. without intermediate coupling, the rotor 35 of the drive motor, whose stator 36 is arranged in the motor housing 2.
  • the motor housing may be equipped with cooling channels 38.
  • the flange plates 50 which consist in the example shown with the bearing bodies 7 in one piece, are placed with their outer edges 51, which follow substantially the circumference of the pump chamber housing 4, and their adjacent inner edges 52 on top of the base plate 3.
  • the flange plates 50 are sealed relative to the base plate 3.
  • a recess is provided, which includes with the top of the base plate 3, a space 39 which serves to receive synchronization gears 40, which rotates by known means on the shafts 20 between the bearings 21 and the motor rotors are arranged. So that they can mesh with one another in the region of the inner edges 52 of the flange plates 50, the inner edges have at a corresponding point a cutout, through which the toothed wheels pass.
  • the reference line of the inner edge generally indicative reference numeral 52 points. This web is advantageous not only for reasons of stability, but also because it allows a circumferential seal on the one hand with respect to the base plate 3 and on the other hand between the flattened secant surfaces of the flange plates 50.
  • the recesses 39 in the flange plates 50 have a diameter greater than the diameter of the timing gears 40. They are slightly eccentric with respect to the inner edges 52, so that the timing gears 40 are still in place during assembly of the rotor assemblies the presence of the sealing web at 52 can be used.
  • the space 39 containing the synchronization gears 40 is completely separated from the pumping space, there is no danger of contamination for the synchronization gears. They serve only the emergency synchronization of the rotors. Your teeth do not normally come into contact with each other. Lubrication is therefore usually not required. Although it may be applicable if desired, the dry running of the synchronizing gears simplifies the construction because a seal between the space 39 and the drive motors is not required.
  • the timing gears 40 may also serve as pulser disks or be supplemented by additional pulser disks scanned by sensors 42, one of which is shown in FIG. These sensors 42 are connected to a control device which monitors the respective rotational position of the rotors relative to a desired value and corrects them via the drive. It is a synchronization of the rotors by electronic means, which is known as such and therefore requires no further explanation here.
  • the clearance between the teeth of the synchronization gears 40 is slightly less than the backlash between the positive displacement projections 9 of the rotors 8. However, it is greater than the synchronization tolerance of the electronic synchronization device.
  • the performance data of the pump are in addition to the drive power and speed through the rotors formed on the rotors or. Delivery volume and thus determined by the length of the rotors. One can therefore change the delivery data by changing the length of the pump part containing the rotors.
  • a series of pumps with different performance data is therefore preferably characterized by the fact that the individual pumps of this series differ by grading the length of these parts, which include the pump chamber, the rotors and possibly the tubular projecting into the rotors parts of the bearing body ,
  • each rotor with the associated bearing and drive means forms an independently mountable assembly which, in addition to the rotor from the bearings 21, 22, the bearing body 7, the cooling means provided therein, the shaft 20, the synchronization gear 40, the associated sensor 42 and the motor rotor 35 consists.
  • These units are completely pre-assembled in the pump. You can easily be removed or used by the base plate 3 after the removal of the pump chamber housing. Their replacement can therefore be left to the user while the manufacturer takes care of the maintenance of the sensitive units as such.
  • the pump is preferably of an isochoric design in order to be able to convey even larger quantities of liquid harmlessly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
EP96922831A 1995-06-21 1996-06-18 Verfahren zum Kühlen eines mehrstufigen Schraubenspindelverdichters Expired - Lifetime EP0834018B2 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19522557 1995-06-21
DE19522559 1995-06-21
DE1995122557 DE19522557A1 (de) 1995-06-21 1995-06-21 Drehkolbenverdichter, insbesondere Vakuumpumpe
DE1995122559 DE19522559A1 (de) 1995-06-21 1995-06-21 Verdichter mit axialer Förderrichtung, insbesondere in Schraubenspindel-Bauweise
PCT/EP1996/002631 WO1997001038A1 (de) 1995-06-21 1996-06-18 Mehrstufiger schraubenspindelverdichter

Publications (3)

Publication Number Publication Date
EP0834018A1 EP0834018A1 (de) 1998-04-08
EP0834018B1 EP0834018B1 (de) 1999-12-08
EP0834018B2 true EP0834018B2 (de) 2006-10-25

Family

ID=26016151

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96922831A Expired - Lifetime EP0834018B2 (de) 1995-06-21 1996-06-18 Verfahren zum Kühlen eines mehrstufigen Schraubenspindelverdichters

Country Status (12)

Country Link
US (1) US5924855A (zh)
EP (1) EP0834018B2 (zh)
JP (1) JP3965507B2 (zh)
KR (1) KR100424386B1 (zh)
AT (1) ATE187528T1 (zh)
DE (1) DE59603870D1 (zh)
DK (1) DK0834018T4 (zh)
ES (1) ES2141515T5 (zh)
GR (1) GR3032683T3 (zh)
PT (1) PT834018E (zh)
TW (1) TW377384B (zh)
WO (1) WO1997001038A1 (zh)

Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19724643A1 (de) * 1997-06-11 1998-12-17 Sihi Gmbh & Co Kg Schraubenverdichter und Verfahren zum Betrieb desselben
DE19745616A1 (de) 1997-10-10 1999-04-15 Leybold Vakuum Gmbh Gekühlte Schraubenvakuumpumpe
DE19800825A1 (de) * 1998-01-02 1999-07-08 Schacht Friedrich Trockenverdichtende Schraubenspindelpumpe
US6045343A (en) * 1998-01-15 2000-04-04 Sunny King Machinery Co., Ltd. Internally cooling rotary compression equipment
DE19926891C2 (de) * 1999-06-12 2002-06-13 Diro Konstruktions Gmbh & Co K Verfahren zum Betreiben einer Turbomaschine und Turbomaschine
GB9913969D0 (en) * 1999-06-16 1999-08-18 Boc Group Plc Improvements in screw pumps
DE19963171A1 (de) * 1999-12-27 2001-06-28 Leybold Vakuum Gmbh Gekühlte Schraubenvakuumpumpe
DE19963172A1 (de) * 1999-12-27 2001-06-28 Leybold Vakuum Gmbh Schraubenpumpe mit einem Kühlmittelkreislauf
US6394777B2 (en) 2000-01-07 2002-05-28 The Nash Engineering Company Cooling gas in a rotary screw type pump
DE10039006A1 (de) * 2000-08-10 2002-02-21 Leybold Vakuum Gmbh Zweiwellenvakuumpumpe
GB2370320A (en) * 2000-12-21 2002-06-26 Ingersoll Rand Europ Sales Ltd Compressor and driving motor assembly
WO2002065366A1 (en) * 2001-02-13 2002-08-22 Yonet.Co., Ltd. Method and system for ticket purchasing and issuing using ic card
JP4403670B2 (ja) * 2001-05-16 2010-01-27 株式会社デンソー コンプレッサ
EP1552152B1 (en) 2002-10-14 2013-03-20 Edwards Limited Rotary piston vacuum pump with washing installation
DE20302989U1 (de) * 2003-02-24 2004-07-08 Werner Rietschle Gmbh + Co. Kg Drehkolbenpumpe
JP4558349B2 (ja) 2004-03-02 2010-10-06 財団法人国際科学振興財団 真空ポンプ
EP1784576B2 (en) * 2004-09-02 2016-01-13 Edwards Limited Cooling of pump rotors
JP2007170341A (ja) * 2005-12-26 2007-07-05 Toyota Industries Corp スクリュー式流体機械
US8007264B2 (en) * 2006-08-08 2011-08-30 Spx Corporation Positive displacement pump apparatus and method
US20080121497A1 (en) * 2006-11-27 2008-05-29 Christopher Esterson Heated/cool screw conveyor
EP2233748B1 (de) * 2009-03-10 2017-05-24 Grundfos Management A/S Mehrstufige Kreiselpumpe
CN102410219A (zh) * 2011-11-24 2012-04-11 威海智德真空科技有限公司 一种立式干式螺杆真空泵
WO2018132601A1 (en) * 2017-01-11 2018-07-19 Carrier Corporation Fluid machine with helically lobed rotors
US11146159B2 (en) * 2017-03-21 2021-10-12 Tti (Macao Commercial Offshore) Limited Brushless motor
AU2019433234A1 (en) * 2019-03-14 2021-09-16 Ateliers Busch Sa Dry pump for gas and set of a plurality of dry pumps for gas

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3289600A (en) * 1964-03-13 1966-12-06 Joseph E Whitfield Helically threaded rotors for screw type pumps, compressors and similar devices
US3795117A (en) * 1972-09-01 1974-03-05 Dunham Bush Inc Injection cooling of screw compressors
DE2544082A1 (de) * 1975-10-02 1977-04-14 Comprotek Sa Drehkolbenmaschine
US4515540A (en) * 1983-11-22 1985-05-07 Frick Company Variable liquid refrigerant injection port locator for screw compressor equipped with automatic variable volume ratio
EP0290664B1 (de) * 1987-05-15 1991-12-27 Leybold Aktiengesellschaft Zweiwellenpumpe
EP0290662B1 (de) * 1987-05-15 1993-03-31 Leybold Aktiengesellschaft Zweiwellenvakuumpumpe mit Schöpfraum
DE69132867T2 (de) * 1990-08-01 2002-09-12 Matsushita Electric Industrial Co., Ltd. Drehkolbenanlage für flüssige Medien
JP3074829B2 (ja) * 1991-09-05 2000-08-07 松下電器産業株式会社 流体回転装置
KR100190310B1 (ko) * 1992-09-03 1999-06-01 모리시따 요오이찌 진공배기장치
US5269667A (en) * 1993-02-24 1993-12-14 Ingersoll-Rand Company Removabe discharge port plate for a compressor

Also Published As

Publication number Publication date
TW377384B (en) 1999-12-21
ES2141515T3 (es) 2000-03-16
ATE187528T1 (de) 1999-12-15
KR100424386B1 (ko) 2004-07-15
PT834018E (pt) 2000-05-31
EP0834018A1 (de) 1998-04-08
ES2141515T5 (es) 2007-06-16
DK0834018T4 (da) 2007-02-26
JPH11508015A (ja) 1999-07-13
US5924855A (en) 1999-07-20
EP0834018B1 (de) 1999-12-08
WO1997001038A1 (de) 1997-01-09
DK0834018T3 (da) 2000-06-13
KR20000000512A (ko) 2000-01-15
JP3965507B2 (ja) 2007-08-29
DE59603870D1 (de) 2000-01-13
GR3032683T3 (en) 2000-06-30

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