EP2052158A1 - Refroidissement de rotor pour pompes à vide ou compresseurs à deux arbres fonctionnant à sec - Google Patents

Refroidissement de rotor pour pompes à vide ou compresseurs à deux arbres fonctionnant à sec

Info

Publication number
EP2052158A1
EP2052158A1 EP07786670A EP07786670A EP2052158A1 EP 2052158 A1 EP2052158 A1 EP 2052158A1 EP 07786670 A EP07786670 A EP 07786670A EP 07786670 A EP07786670 A EP 07786670A EP 2052158 A1 EP2052158 A1 EP 2052158A1
Authority
EP
European Patent Office
Prior art keywords
heat
vacuum pump
compressor according
shaft
coolant
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.)
Withdrawn
Application number
EP07786670A
Other languages
German (de)
English (en)
Inventor
Uwe Friedrichsen
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.)
Busch Produktions GmbH
Original Assignee
Busch Produktions 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
Application filed by Busch Produktions GmbH filed Critical Busch Produktions GmbH
Publication of EP2052158A1 publication Critical patent/EP2052158A1/fr
Withdrawn legal-status Critical Current

Links

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
    • 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
    • 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
    • F04C18/123—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 radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth
    • 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
    • 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
    • F04C2220/00—Application
    • F04C2220/10—Vacuum
    • F04C2220/12—Dry running

Definitions

  • the invention relates to a dry-running twin-shaft vacuum pump or - compressor according to the preamble of claim 1.
  • Such a machine may be provided in a standing or lying version, and it may be the Verdrängerrotoren klauenkolbenförmig, helical, helical-spindle or waltz-shaped.
  • the invention is therefore based on the object, the dry-running twin-shaft vacuum pump or compressor of the generic type to eliminate the disadvantages described in such a way that the dissipation of the heat of compression from the working space is significantly improved by a simple, robust and cost-effective technical solution ,
  • the invention relates here to both flying and both sides of the working space mounted dry-running claw, screw and Wälzkolben- vacuum pumps or compressors, in which the two positive displacement rotors in the ratio 1: 1, for example, mechanically synchronized by means of an oil-lubricated gear transmission ,
  • each shaft of the positive displacement rotors has an axially extending cavity extending at least over a partial length of the shaft, in which at least one heat pipe is arranged in each case such that the Condensation heat from the positive displacement rotors via the waves from the working space and possibly an adjacent sealing space and derived outside of the working space by heat dissipation means is derived from the machine.
  • heat pipes themselves, also called “heat pipes”.
  • a heat pipe is an externally closed one
  • Heat source evaporates, the heat with the steam centrally in the interior of the
  • Reflux of the condensed working fluid to the heat source takes place at the outer diameter of the cavity by capillary forces.
  • the technical design of the capillary structure on the inner wall depends on the design of the
  • Heat pipe off As a working medium can be used in the temperature range used here
  • Water can be used.
  • the required pressure in the heat pipe results from the desired operating points of the heat pipe.
  • the transportable amount of heat can be up to a factor of 10,000 higher than solid copper. It is within the scope of the invention that as the heat dissipation means outside the working space cooled coolant, preferably gear oil, is used, which is supplied continuously by a coolant circuit.
  • the heat-dissipating means can also consist of metallic ableitmaschinen particularly high thermal conductivity, which are attached to or near the respective heat sink at the end of the heat pipes at the shaft ends of the Verdrängerrotoren.
  • the metallic sauceableit analyses may consist of axial sleeves, which are arranged on the shaft ends of the Verdrängerrotoren; instead or additionally, it is also possible that the heat dissipation body consist of metal pins which radially pass through the shaft ends of the positive displacement rotors at or near the respective heat sink at the end of the heat pipes.
  • the positive displacement rotors are at least two-fold to increase the delivery volume and / or at least two stages to increase the total pressure difference and that the discharge of the compression heat from at least one heat source and at least one heat sink of a heat pipe per rotor.
  • the heat dissipation from the region of the heat sinks of the heat pipes or from the region of the heat dissipation body on the waves of the positive displacement rotors can take place with a precisely aligned, metered oil jet.
  • an oil-air heat exchanger or an oil-water heat exchanger in both cases, if necessary, an oil filter, be installed.
  • a coolant pump for conveying the coolant, in particular oil, a coolant pump from the group of viscosity, centrifugal, threaded, gear,
  • capillary structures used in the heat pipes are mechanically secured, in particular by positive engagement, soldering, welding, pressing, gluing or the like., against rotation between the heat pipe and capillary structure.
  • the built-in rotor shafts heat pipes mechanically, in particular by positive engagement, soldering, welding, pressing, gluing or the like., Are secured against rotation between the heat pipe and capillary structure.
  • a heat conducting means is arranged, which prevented by a static elastic seals, such as O-rings or the like., From flowing is.
  • Figure 1 shows schematically in section the rotor cooling according to the invention on a cantilevered claw vacuum pump.
  • FIG. 2 shows the rotor cooling according to the invention in a claw compressor mounted on both sides of the working space
  • FIG 3 shows the rotor cooling according to the invention in a screw vacuum pump mounted on both sides of the working space; and Fig. 4 at a both sides of the working space mounted Roots pump.
  • the pumped liquid is sucked in via a dashed line indicated suction nozzle 1 from above and compressed against a control opening, not shown in the drawing below.
  • the resulting heat of compression heats the housing around the claw pistons 2, 3 around and the claw pistons 2, 3 itself.
  • the shafts 4, 5 are synchronized by two gears 6, 7. These synchronization gears 6, 7 and the bearing of the shafts 4, 5 are located in a gear housing and are oil lubricated.
  • In the shafts 4, 5 respectively axially extending cavities are provided, in which heat pipes 8, 9 are arranged. These serve to drain the comparatively high proportion of heat energy to the gear compartment.
  • the heat flow is transported radially to the heat through sleeves 4, 5 passing through the metal pins 10, 11 particularly high thermal conductivity ( ⁇ > 100 W / (K * m)) to kannabithggsen 12, 13, extending axially the ends of the shafts 4, 5 are attached.
  • the heat-releasing sleeves 12, 13 themselves are kept at a low temperature with cooled transmission oil exiting from aligned nozzles 31.
  • an external cooler 32 is provided in order to keep the oil temperature in the transmission low and at the same time to achieve a high temperature difference across the heat pipes 8, 9.
  • the heat of compression is also with two heat pipes from the compression bodies, here claw pistons, on the rotor shafts in the side space against the gear compartment and from there by means of heat exchangers or directly on the wall of the transmission housing excepte dis outer Urgsgsb'jr.g tellgsbsn.
  • the pumped liquid is sucked in via the dashed lines indicated suction nozzle 1 from above and compressed against a not visible in the drawing below control port.
  • the resulting heat of compression heats the housing around the claw pistons 2, 3 around and the claw pistons 2, 3 itself.
  • the shafts 4, 5 are synchronized by two gears 6, 7.
  • Front side to the working space, opposite the synchronization gear 6, 7 is a second bearing 14, 15 of the shafts 4, 5.
  • the heat of compression is in this embodiment with lubricated oil storage on a heat sink, consisting of good thermal conductivity radially arranged metal pins 10, 11 and axially extending parchmentithggsen 12, 13, at the end of the heat pipes 8, 9 derived in the bearing side space. From here then the heat can be dissipated either by direct air cooling or more effectively by the cooling circuit with cooler 32 from the machine.
  • the heat of compression is also delivered with two heat pipes from the compression bodies, here screw rotors, through the shaft ends in the gear compartment and from there by means of heat exchangers or directly through the wall of the transmission housing to the outside environment.
  • the fluid is sucked in via the suction port 1 from the side and compressed in the threads of the screw rotors 17, 18.
  • An outlet nozzle 16 for the pumped medium is located at the other end of the helical spindle-shaped
  • the resulting VerdichU-P.gsv.'ärrrie heats the Housing 19 around the screw rotors 17, 18 and the screw rotors 17, 18 itself.
  • the screw rotors 17, 18 are synchronized by two gears 6, 7. Similar to the examples described here is the heat of compression at the free end of the shaft by an axially disposed sauceableitelement 22 and the shaft end of the driven screw rotor 17 with a heat dissipating sleeve 12 derived from the heat pipes 8, 9. From here, the heat is then dissipated either by direct air cooling or more effectively by the illustrated cooling circuit with cooler 32 from the machine.
  • the pumped liquid is sucked in via the suction nozzle 1 indicated by dashed lines from above and conveyed downwards, not visible in the drawing, to the outlet 16.
  • the resulting heat of compression heats the housing around the Wälzkolben 23, 24 and the Wälzkolben 23, 24 itself.
  • the shaft ends of the Wälzkolbens 23, 24 are synchronized by two gears 6, 7.
  • the total of four heat pipes 8, 9, 27, 28 are in turn arranged centrally in the rotor central axes.
  • the heat source of all four heat pipes 8, 9, 27, 28 is located centrally in the working space.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne une pompe à vide ou un compresseur à deux arbres fonctionnant à sec présentant deux arbres parallèles et des rotors volumétriques (2, 3 ; 17, 18 ; 23, 24) se trouvant dans un espace de travail et disposés sur ces derniers. Ces rotors sont synchronisés selon un rapport 1:1 par exemple de manière mécanique au moyen d'un engrenage ou de manière électronique au moyen d'un moteur d'entraînement pour chaque arbre de rotor, et ils présentent une ouverture d'aspiration (1) sur leur côté aspiration ainsi qu'au moins une ouverture de sortie (16) sur leur côté refoulement. L'agencement est tel que chaque arbre (4, 5) des rotors volumétriques présente un espace creux disposé axialement et s'étendant au moins sur une longueur partielle de l'arbre, au moins un tube échangeur de chaleur (8, 9) étant respectivement disposé dans cet espace creux de sorte que la chaleur de compression soit conduite par les rotors volumétriques par l'intermédiaire des arbres depuis l'espace de travail et le cas échéant un espace étanche adjacent et de sorte qu'elle soit évacuée de la machine à l'extérieur de l'espace de travail par un moyen de dissipation de la chaleur.
EP07786670A 2006-08-17 2007-08-13 Refroidissement de rotor pour pompes à vide ou compresseurs à deux arbres fonctionnant à sec Withdrawn EP2052158A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610038419 DE102006038419A1 (de) 2006-08-17 2006-08-17 Rotorkühlung für trocken laufende Zweiwellen-Vakuumpumpen bzw. -Verdichter
PCT/EP2007/007150 WO2008019815A1 (fr) 2006-08-17 2007-08-13 Refroidissement de rotor pour pompes à vide ou compresseurs à deux arbres fonctionnant à sec

Publications (1)

Publication Number Publication Date
EP2052158A1 true EP2052158A1 (fr) 2009-04-29

Family

ID=38692088

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07786670A Withdrawn EP2052158A1 (fr) 2006-08-17 2007-08-13 Refroidissement de rotor pour pompes à vide ou compresseurs à deux arbres fonctionnant à sec

Country Status (3)

Country Link
EP (1) EP2052158A1 (fr)
DE (1) DE102006038419A1 (fr)
WO (1) WO2008019815A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012023675A1 (de) 2012-12-03 2014-06-05 Hans-Erich Maul Gekühltes spielfreies Zahnradgetriebe
CN105298847A (zh) * 2015-11-20 2016-02-03 卜学飞 螺杆真空泵转子冷却装置
CN106704176B (zh) * 2016-12-02 2018-11-06 马德宝真空设备集团有限公司 一种罗茨泵的冷却系统
CN108302040B (zh) * 2018-03-14 2023-05-09 深圳市志橙半导体材料有限公司 一种干式真空泵的防卡死装置及防卡死方法

Family Cites Families (12)

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Publication number Priority date Publication date Assignee Title
DE972831C (de) * 1951-08-30 1959-10-08 Emil Siegwart Lager- und Wellenkuehlung fuer ein Heissgas-Radialgeblaese
US4073607A (en) * 1976-07-29 1978-02-14 Ingersoll-Rand Company Gas compressor system
JPS61226583A (ja) * 1985-03-29 1986-10-08 Toray Ind Inc ギヤポンプ
JPH01237388A (ja) * 1988-03-18 1989-09-21 Hitachi Ltd 無給油式回転圧縮機のロータ冷却装置
JPH0794826B2 (ja) * 1990-11-07 1995-10-11 株式会社日立製作所 スクリユー流体機械のロータ冷却装置
DE19745616A1 (de) * 1997-10-10 1999-04-15 Leybold Vakuum Gmbh Gekühlte Schraubenvakuumpumpe
DE19752003C2 (de) * 1997-11-24 1999-10-14 Fuerstlich Hohenzollernsche We Seilwinde mit flüssigkeitsgekühltem Elektromotor
CH692954A5 (de) * 1997-11-28 2002-12-31 Barmag Barmer Maschf Galette zum Fördern und Führen eines laufenden synthetischen Fadens.
GB9819261D0 (en) * 1998-09-03 1998-10-28 Concentric Pumps Ltd Improvements to rotary pumps
US6394777B2 (en) * 2000-01-07 2002-05-28 The Nash Engineering Company Cooling gas in a rotary screw type pump
DE10120409B4 (de) * 2001-04-26 2004-02-12 Sero Pumpenfabrik Gmbh & Co. Kg Kreiselpumpe zur Förderung heißer Medien
DE20302990U1 (de) * 2003-02-24 2004-07-08 Werner Rietschle Gmbh + Co. Kg Drehkolbenpumpe

Non-Patent Citations (1)

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Title
See references of WO2008019815A1 *

Also Published As

Publication number Publication date
WO2008019815A1 (fr) 2008-02-21
DE102006038419A1 (de) 2008-02-21

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