EP1601877A1 - Pompe a pistons rotatifs - Google Patents

Pompe a pistons rotatifs

Info

Publication number
EP1601877A1
EP1601877A1 EP04713529A EP04713529A EP1601877A1 EP 1601877 A1 EP1601877 A1 EP 1601877A1 EP 04713529 A EP04713529 A EP 04713529A EP 04713529 A EP04713529 A EP 04713529A EP 1601877 A1 EP1601877 A1 EP 1601877A1
Authority
EP
European Patent Office
Prior art keywords
pump according
rotary lobe
bearing tube
coolant
lobe pump
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Withdrawn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
EP04713529A
Other languages
German (de)
English (en)
Inventor
Fritz-Martin Scholz
Jürgen OSWALD
Herbert Vogt
Daniel Greiner
Wolf-Rüdiger WAGENER
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.)
Gardner Denver Schopfheim GmbH
Original Assignee
Rietschle Thomas Schopfheim 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 Rietschle Thomas Schopfheim GmbH filed Critical Rietschle Thomas Schopfheim GmbH
Publication of EP1601877A1 publication Critical patent/EP1601877A1/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Withdrawn legal-status Critical Current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
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C2220/00—Application
    • F04C2220/10—Vacuum
    • F04C2220/12—Dry running
    • 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

Definitions

  • the invention relates to a rotary lobe pump with at least two rotors with associated drive shafts, with an associated bearing tube being provided for each rotor, which extends into the associated rotor and through which the associated drive shaft runs, between the inside of the rotor and the outside of the Bearing tube a first gap is provided.
  • the invention relates in particular to a dry-compressing screw vacuum pump or such a Roots pump.
  • the parallel drive shafts are usually synchronized with one another by a gearbox 1: 1.
  • the speed of the shafts either corresponds to that of the motor, or the motor speed is increased via an additional spur gear pair.
  • the contactlessly intermeshing, counter-rotating rotors form chambers which are transported from the suction side to the pressure side and thereby take up a smaller volume, which is achieved by changing the rotor increase of the rotors.
  • the heat of compression that occurs can be dissipated, for example, via the outer wall of the housing, the rotors also being able to be cooled from the inside, which, however, leads to considerable additional design effort.
  • the thermal expansion of the parts should be minimized, which can only be achieved by cooling, so that smaller gaps between the rotors can be achieved and which in turn leads to a reduction in the gap losses.
  • cooling can not only increase the efficiency, but the media, for example gases, which would be brought to temperatures above 200 ° C. without cooling due to compression, can be conveyed far below this temperature.
  • lower temperatures have an effect also beneficial to the design and life of the parts of the rotary lobe pump.
  • the invention relates to a rotary lobe pump with such flying bearings of the rotors.
  • the bearing tube of each rotor protrudes into an axial opening therein.
  • the bearing tube is usually stationary at one end, preferably by coupling to the pump housing.
  • the associated drive shaft then projects through the bearing tube and has an end on the drive side and an end coupled to the rotor.
  • the generic WO 97/01038 describes a complex cooling of the rotors, in which cooling channels are formed in the bearing tubes, through which coolant flows.
  • radiant heat is to be transferred from the rotor to the bearing tube through a gap between the rotor and the bearing tube.
  • sealing gas can also be introduced, which is provided for cooling and for protecting the bearing and drive area from the access of the conveying medium or of substances contained in the conveying medium.
  • the invention has for its object to provide a simple rotary pump, in particular screw vacuum pump, which is also low maintenance.
  • the first gap contains coolant during operation, ie is transported through it, and is part of a coolant circuit.
  • the first gap has a coolant inlet and a coolant outlet spatially separated therefrom, ie physically separated therefrom.
  • cooling via the first gap is considerably more effective since cooling liquid is introduced into the gap, which allows good heat dissipation directly on the rotor.
  • This coolant is part of a coolant circuit, so that cooler liquid is constantly being fed to the rotor becomes. Because of the separate inlets and outlets, there is only one direction of flow through the cooled gap section, ie no blind-hole-like dead spaces into which the cooling liquid has to flow in and out again.
  • the cooling channels provided in the wall of the bearing tube or in the drive shaft in the prior art can therefore be omitted, which simplifies the manufacture and maintenance of the pump according to the invention. Additional tubes, pockets, cavities and the like can also be omitted in the rotor.
  • a second gap which is part of the coolant circuit, is preferably provided between the respective inner side of the bearing tube and the associated outer side of the drive shaft. This means that both gaps, which are very easy to produce, are in flow connection with one another.
  • the coolant circuit is preferably designed such that coolant first flows into the second, radially inner gap and then flows from the latter into the first gap.
  • the bearing tube has a stationary fixed end and an opposite free end that projects into the rotor.
  • the invention provides that the second gap has an associated coolant inlet at the stationary fixed end and a coolant outlet at the axially opposite end, which is in flow connection with a coolant inlet of the first gap at the free end of the bearing tube.
  • a connecting channel between the two gaps is provided between the end face of the free end of the respective bearing tube and the adjacent wall of the rotor.
  • the invention provides further advantages. While in the prior art all bearings should be expensive, sealed, permanently lubricated bearings and complex additional seals were sought, the invention goes the opposite way. It provides, for example, that at least one bearing is provided between the respective bearing tube and the associated drive shaft, through which the coolant flow passes completely or partially, so that the bearing is cooled and lubricated.
  • One or more bypasses for coolant can be provided between the bearing (s) and the adjacent parts. These bypasses increase the flow rate or, if the bearing should be sealed against the above statements, it allows coolant to pass through in the area of the corresponding bearing point.
  • the coolant circuit is preferably open to the coolant and lubricant of the transmission.
  • Lubricant of the gearbox for driving the rotors simultaneously represents the cooling liquid of the rotors.
  • the hermetic seal provided in the prior art can thus be dispensed with, the entire pump is constructed much more simply. Conversely, the part of the interior of the gearbox that is filled with coolant and lubricant is part of the coolant circuit.
  • the drive shaft is designed as at least in the area of its drive-side end (gear end), but in particular over the entire length without a cooling channel, which makes production cheaper and increases stability.
  • a reservoir for coolant e.g. the gear housing with the cooling and lubricating fluid therein is in flow connection with the first or second gap via a channel located outside the drive shaft.
  • the rotary lobe pump according to the invention is according to the preferred one
  • Embodiment designed barrier gas-free.
  • FIG. 1 shows a longitudinal sectional view through a first embodiment of the rotary lobe pump according to the invention, designed as a screw vacuum pump,
  • FIG. 2 shows a longitudinal sectional view through a second embodiment of the rotary lobe pump according to the invention, designed as a screw vacuum pump,
  • Embodiments changed the storage area of the rotors
  • FIG. 4 shows an enlarged view of the framed region designated by X in FIG. 3.
  • a dry-compressing rotary lobe pump is shown in the form of a screw vacuum pump, one on the vacuum side
  • Suction port 10 and has a blow-out port 12 on the pressure side both are connected to each other by a work space 14.
  • two parallel rotors 8 are accommodated, which have a helix 16 that is increasingly provided with a lower pitch.
  • the rotors 8 mesh with one another, are in opposite directions and form chambers 18 which, when the rotors 8 are rotated, are transported from the suction side to the pressure side, ie from top to bottom when the pump is at a standstill, so that the medium enclosed in the chambers compresses to the pressure side becomes.
  • the two rotors 8 are hollow on the inside, are overhung, have the same geometry and the same structure in terms of their mounting, so that for simplification only the right rotor 8 including the mounting must be explained.
  • the rotor 8 has an axial through bore with an upper section 20 with a smaller diameter and an adjoining section with a larger diameter, which is defined below by an inner side 24.
  • a drive shaft 26 is pressed into section 20 so that the rotor and drive shaft 26 are coupled to one another in a rotationally fixed manner.
  • a bearing tube 28 projects, which is fixedly attached to a transmission housing 30, with its so-called lower, stationary end 31. Through this bearing tube 28, the drive shaft 26 extends through to into the interior 34 of the transmission housing 30.
  • a spiral bevel pinion 38 is connected at the lower end to the drive shaft 26, which meshes with a spiral bevel gear 40, which in turn is fixed in position on a shaft 42 which is rotated by a motor, not shown.
  • the two drive shafts 26 each have their own pair of spiral bevel gears or gears 38, 40, but the spiral bevel gears 40 are mounted on a common shaft 42.
  • the shaft 42 is in turn rotatably mounted in the gear housing 30.
  • the gear arrangement is a so-called vertical shaft arrangement, in which the shaft 42 is perpendicular to the parallel drive shafts 46. With this arrangement, the speed of the drive shafts 26 can be increased (the pitch circle of the spiral cone wheels 40 is larger than that of the spiral bevel pinion 38), but at the same time the direction of rotation of the drive shafts 26 is synchronized.
  • the peripheral speed of the gearwheels coupled to the drive shafts 26 is decisive for the transmission noise.
  • the peripheral speed was dependent on the center distance.
  • the peripheral speed of the spiral bevel gears 40 and the spiral bevel pinion 38 is independent of the center distance, the diameter of the spiral bevel pinion 38 is even significantly smaller than the center distance between the drive shafts 26.
  • Another advantage of the construction according to the invention is that different center distances can be realized with the same gears when different rotors 8 are used.
  • the drive shaft 26 is in the region of the lower end via a fixed bearing 50, which as an open bearing, i.e. is not permanently lubricated and is not sealed, positioned in the bearing tube 28 and at the free, upper end of the bearing tube 28 via a floating bearing 42 in the axial and radial directions.
  • the rotor 8 is thus also supported in the axial and circumferential directions.
  • the bearing 42 is otherwise not sealed, but designed as an open bearing.
  • each rotor has its own cooling liquid circuit, through which the cooling and lubricating liquid 60 inside the
  • Gear housing 30 which is provided for lubrication and cooling of the
  • Gear housing represents a reservoir for the cooling liquid of the rotors 8.
  • the coolant circuit therefore starts from the interior of the transmission housing 30 and runs through the openly configured fixed bearing 50 and / or a bypass 32 provided there, that is, a channel provided outside the drive shaft 26. Between the drive shaft 26 and the bearing tube 28 there is a cylindrical annular gap which extends to the bearing 42. This gap 62 is referred to below as the radially inner, second gap. He stands with a first radially outer gap 64 in flow connection, which is formed between the inside 24 of the rotor 8 and the outside of the bearing tube 28.
  • the flow connection between gap 62 and gap 64 takes place via the open floating bearing 42, an optionally provided bypass 70 and groove-shaped connecting channels or an annular gap 80 between the end face of the free end of the bearing tube 28 and the adjoining end wall of the rotor 8.
  • This connecting channel 80 then leads to the coolant inlet 81 (upper end) of the first gap 64.
  • the coolant outlet 83 of the first gap 64 is provided at its lower end, where a channel 90 leads into a collecting ring and from there into an oil pan (not shown) or into the transmission interior 34 ,
  • the coolant thus gets into the liquid inlet, the lower end of the gap 62, after it has possibly cooled and lubricated the bearing 50, flows up to its liquid outlet to the bearing 42 and / or the bypass 70, and then via the connecting channel 80 to get into the gap 64, where it is pressed against the inside 24 of the rotor 8 by the existing centrifugal forces and where there are shear flows.
  • the rotor 8 which heats up during compression, largely emits the heat to the coolant, which then reaches the coolant source and mixes there with the cold coolant 60.
  • the pump shown is also characterized by a very simple seal. No seal is required on the vacuum side at all. Seals 92 are only required on the pressure side of the vacuum pump between the lower end of the rotors 8 and the gear. However, since there is a connection to the blow-out connection 12 of the pump and thus to the atmosphere, the seals 92 are never pressurized, which increases their service life and their sealing performance. Seal gas is also superfluous.
  • FIGS. 2 to 4 essentially correspond to those according to FIG. 1, so that only the differences will be discussed in the following. It should be emphasized that these differences explained in the following tion features can also be combined with one another as desired within the illustrated embodiments.
  • the shaft 42 is not supported in the transmission housing 30 at the left end, because here a shaft extension 100 is provided as a drive for an integrated coolant pump 110, which is accommodated in the transmission interior 34 and the coolant 60 to each of the second gaps 62 inflated. Corresponding lines are designated 120. Between the spiral bevel gears 40, a rib 130 of the gear housing 30 extends, in which the shaft 42 is additionally mounted. A corresponding fixed bearing is designated 132.
  • the fixed bearing 132 between the spiral bevel gears 40 is advantageous because the shaft 42 can expand freely toward both axial ends when heat is applied.
  • an open floating bearing 150 is again provided at the lower end of each rotor 8 between the inside 24 and the bearing tube 28, by means of which the corresponding rotor 8 is additionally stabilized at the lower end.
  • the bearing 150 is preferably a relatively simple slide bearing, which is bypassed by a bypass 160 in the form of a longitudinal groove in the bearing tube 28 by part of the cooling liquid.
  • the coolant is preferably oil.
  • the construction with the cooling circuit in the gaps 62, 64 can also be provided for a Roots pump.
  • the pump according to the invention is characterized by a very simple construction, by the lack of complex channels in the interior of the rotor, the bearing tube and the drive shaft and by very large surfaces which serve for rapid heat transfer to dissipate the heat.
  • an additional cooling channel 180 with cooling liquid can of course also be provided in the housing 170, which surrounds the rotors 8.

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 pistons rotatifs comprenant au moins deux rotors (8) auxquels sont associés des arbres d'entraînement (26). A chaque rotor (8) est également associé un tube palier (28) qui s'étend dans le rotor (8) respectif et à travers lequel s'étend l'arbre d'entraînement (26) correspondant. Un premier interstice (64) est ménagé entre la face intérieure (24) de chaque rotor (8) et la face extérieure du tube palier (28). En fonctionnement, ce premier interstice (64) contient un liquide de refroidissement et fait partie d'un circuit de liquide de refroidissement.
EP04713529A 2003-02-24 2004-02-23 Pompe a pistons rotatifs Withdrawn EP1601877A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE20302989U 2003-02-24
DE20302989U DE20302989U1 (de) 2003-02-24 2003-02-24 Drehkolbenpumpe
PCT/EP2004/001769 WO2004074690A1 (fr) 2003-02-24 2004-02-23 Pompe a pistons rotatifs

Publications (1)

Publication Number Publication Date
EP1601877A1 true EP1601877A1 (fr) 2005-12-07

Family

ID=32695287

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04713529A Withdrawn EP1601877A1 (fr) 2003-02-24 2004-02-23 Pompe a pistons rotatifs

Country Status (8)

Country Link
US (1) US20060222553A1 (fr)
EP (1) EP1601877A1 (fr)
JP (1) JP2006518827A (fr)
KR (1) KR20050103954A (fr)
CN (1) CN1768206A (fr)
AU (1) AU2004213587A1 (fr)
DE (1) DE20302989U1 (fr)
WO (1) WO2004074690A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005012040A1 (de) * 2005-03-16 2006-09-21 Gebr. Becker Gmbh & Co Kg Rotor und Schraubenvakuumpumpe
GB0510892D0 (en) * 2005-05-27 2005-07-06 Boc Group Plc Vacuum pump
CN101321955A (zh) * 2005-12-08 2008-12-10 Ghh-兰德旋转式压缩机有限责任公司 螺旋压缩机
JP2007170341A (ja) * 2005-12-26 2007-07-05 Toyota Industries Corp スクリュー式流体機械
CN102192151A (zh) * 2011-05-19 2011-09-21 台州市星光真空设备制造有限公司 内冷式真空泵
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
US10006340B2 (en) * 2013-10-16 2018-06-26 John Malcolm Gray Supercharger
JP6377839B2 (ja) * 2015-03-31 2018-08-22 株式会社日立産機システム ガス圧縮機
DE102017210771B4 (de) * 2017-06-27 2019-05-29 Continental Automotive Gmbh Schraubenspindelpumpe, Kraftstoffförderaggregat und Kraftstofffördereinheit
DE102018109866A1 (de) * 2018-04-24 2019-10-24 Nidec Gpm Gmbh Regelbares Schmierölfördersystem für Verbrennungsmaschinen
CN112012931B (zh) * 2020-09-04 2022-05-24 浙江思科瑞真空技术有限公司 一种泵转子的冷却方法

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US2938664A (en) * 1955-01-17 1960-05-31 Leybold S Nachfolger Fa E Pump
FR2637655B1 (fr) * 1988-10-07 1994-01-28 Alcatel Cit Machine rotative du type pompe a vis
DE59603870D1 (de) * 1995-06-21 2000-01-13 Sterling Ind Consult Gmbh Mehrstufiger schraubenspindelverdichter
DE19839501A1 (de) * 1998-08-29 2000-03-02 Leybold Vakuum Gmbh Trockenverdichtende Schraubenspindelpumpe
GB9913969D0 (en) * 1999-06-16 1999-08-18 Boc Group Plc Improvements in screw pumps
DE19963172A1 (de) * 1999-12-27 2001-06-28 Leybold Vakuum Gmbh Schraubenpumpe mit einem Kühlmittelkreislauf

Non-Patent Citations (1)

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Title
See references of WO2004074690A1 *

Also Published As

Publication number Publication date
JP2006518827A (ja) 2006-08-17
US20060222553A1 (en) 2006-10-05
WO2004074690A1 (fr) 2004-09-02
CN1768206A (zh) 2006-05-03
AU2004213587A1 (en) 2004-09-02
KR20050103954A (ko) 2005-11-01
DE20302989U1 (de) 2004-07-08

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