WO2004074689A1 - Pompe a pistons rotatifs - Google Patents

Pompe a pistons rotatifs Download PDF

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Publication number
WO2004074689A1
WO2004074689A1 PCT/EP2004/001770 EP2004001770W WO2004074689A1 WO 2004074689 A1 WO2004074689 A1 WO 2004074689A1 EP 2004001770 W EP2004001770 W EP 2004001770W WO 2004074689 A1 WO2004074689 A1 WO 2004074689A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotary lobe
pump according
lobe pump
common shaft
drive shafts
Prior art date
Application number
PCT/EP2004/001770
Other languages
German (de)
English (en)
Inventor
Fritz-Martin Scholz
Jürgen OSWALD
Herbert Vogt
Daniel Greiner
Wolf-Rüdiger WAGENER
Original Assignee
Rietschle Thomas Gmbh + Co. Kg
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 Gmbh + Co. Kg filed Critical Rietschle Thomas Gmbh + Co. Kg
Publication of WO2004074689A1 publication Critical patent/WO2004074689A1/fr

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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C18/126—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 from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots 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
    • 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
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • 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
    • 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

Definitions

  • the invention relates to a rotary lobe pump with at least two counter-rotating, intermeshing rotors with associated drive shafts, and a transmission coupling the drive shafts, the drive shafts being driven by a common shaft.
  • the invention particularly relates to a dry compacting
  • 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 invention particularly relates to a rotary lobe pump with such floating 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.
  • Through the bearing tube the associated drive shaft then projects through it and has an end on the drive side and an end coupled to the rotor.
  • the generic DE 100 04 373 AI describes a screw vacuum pump with a gear, in which the rotors are driven with a common crown gear.
  • the invention has for its object to provide a simple rotary pump, in particular screw vacuum pump, which is low-maintenance, is characterized by a low gear noise and in which a translation independent of the center distance of the drive shafts can be realized with a small height.
  • the common shaft can be guided laterally and not downwards out of the gear housing, where a drive motor that can be easily flanged can then be positioned.
  • the gears attached to the drive shafts can be made small, i.e. their diameter is significantly smaller than the center distance of the drive shafts.
  • the driving gears, which are set at an angle or perpendicular to it, can therefore have a significantly larger diameter in order to ensure a translation into the fast.
  • a bevel gear pair is preferably coupled to each drive shaft so that the bevel gear pairs are driven by the common shaft.
  • the central axes of the drive shafts are arranged parallel to one another and perpendicular to the central axis of the common shaft.
  • hyperboloid wheels or peg wheels would also be conceivable.
  • 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.
  • the part of the gearbox inside that is filled with coolant and lubricant is part of the coolant circuit.
  • the shaft can expand at both ends when heat is applied.
  • a particularly smooth-running gear can be achieved by using spiral bevel gears.
  • 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
  • FIG. 3 is a longitudinal sectional view through a bearing area of the rotors modified from the previous embodiments.
  • FIG. 4 shows an enlarged view of the framed region designated by X in FIG. 3.
  • FIG. 1 shows a dry-compressing rotary lobe pump in the form of a screw vacuum pump, which has a suction connection 10 on the vacuum side and a blow-out connection 12 on the pressure side, both of which are connected to one another by a working space 14.
  • a working 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 each other, are opposed to each other and form chambers 18 which, when the rotors 8 are rotated from the suction side to the pressure side, i.e. with a standing pump, are transported from top to bottom, so that the fluid enclosed in the chambers is compressed to the pressure side.
  • 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, which is fixedly attached to a transmission housing 30, projects into the section of the through-hole having a larger diameter defined by the inner side 24, namely with its so-called lower, fixedly fixed end 31.
  • the drive shaft 26 extends through this bearing tube 28 into the interior 34 of the transmission housing 30.
  • a gear pair in the present case a bevel gear pair, is coupled to the drive housing 32 in the gear housing.
  • each drive shaft 26 At the lower end of each drive shaft 26, a spiral bevel pinion 38 is connected to it, 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 central axis of the common shaft 42 is perpendicular to the parallel central axes of the drive shafts 26.
  • the speed of the drive shafts 26 can be increased (the pitch circle of the spiral bevel gears 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 central axis of the shaft 42 obliquely to that of the drive shafts 26.
  • 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 is designed as an open bearing, ie not permanently lubricated and not sealed, in the bearing tube 28 and at the free, upper end of the bearing tube 28 Floating bearing 42 positioned 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, by means of which the cooling and lubricating liquid 60 inside the gear housing 30, which is available for lubricating and cooling the gearwheels provided therein, is required.
  • the coolant circuit therefore starts from the interior of the gear housing 30 and runs through the open-mounted fixed bearing 50 and / or a bypass 32 provided there.
  • a cylindrical annular gap results between the drive shaft 26 and the bearing tube 28, which extends to the bearing 42.
  • This gap 62 is referred to below as the radially inner, second gap. It is in flow communication with a first, radially outer gap 64, 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 leads then to the coolant inlet (upper end) of the first gap 64.
  • the coolant outlet 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 arrives at the liquid inlet, the lower end of the gap 62, after it may have 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 rotors 8, which heat up during compression, give the heat largely 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.
  • 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 distinguishing features explained below can also be combined with one another as desired within the illustrated embodiments.
  • the shaft 42 is not supported at the left end in the transmission housing 30, 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 for each of the second Column 62 pumps. 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 bridged by a bypass 160 in the form of a longitudinal groove in the bearing tube 28 by part of the coolant.
  • 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) à rotation inverse s'engrenant l'un dans l'autre et auxquels sont associés des arbres d'entraînement (26), ainsi qu'un système d'engrenage couplant lesdits arbres d'entraînement (26), ces derniers étant entraînés par un arbre commun (42). L'invention se caractérise en ce qu'une paire de roues dentées, disposées l'une par rapport à l'autre selon une position allant de la diagonale à la perpendiculaire, est couplée à chaque arbre d'entraînement (26) de telle sorte que les paires de roues dentées soient entraînées par l'arbre commun (42) et que l'axe central de cet arbre commun (42) ne soit pas parallèle aux axes centraux des arbres d'entraînement (26).
PCT/EP2004/001770 2003-02-24 2004-02-23 Pompe a pistons rotatifs WO2004074689A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE20302990.9 2003-02-24
DE20302990U DE20302990U1 (de) 2003-02-24 2003-02-24 Drehkolbenpumpe

Publications (1)

Publication Number Publication Date
WO2004074689A1 true WO2004074689A1 (fr) 2004-09-02

Family

ID=32695288

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/001770 WO2004074689A1 (fr) 2003-02-24 2004-02-23 Pompe a pistons rotatifs

Country Status (2)

Country Link
DE (1) DE20302990U1 (fr)
WO (1) WO2004074689A1 (fr)

Families Citing this family (4)

* 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
DE102006038419A1 (de) * 2006-08-17 2008-02-21 Busch Produktions Gmbh Rotorkühlung für trocken laufende Zweiwellen-Vakuumpumpen bzw. -Verdichter
DE102009019220B4 (de) * 2009-04-30 2013-04-11 Leistritz Pumpen Gmbh Schraubenspindelpumpe
WO2011101064A2 (fr) * 2010-02-18 2011-08-25 Ralf Steffens Entraînement pour un compresseur à broches

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1943515A (en) * 1929-10-09 1934-01-16 Alemite Corp Grease dispensing apparatus
US3388854A (en) * 1966-06-23 1968-06-18 Atlas Copco Ab Thrust balancing in rotary machines
DE19820523A1 (de) * 1998-05-08 1999-11-11 Peter Frieden Schraubenspindel-Vakuumpumpe mit Rotorkühlung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1943515A (en) * 1929-10-09 1934-01-16 Alemite Corp Grease dispensing apparatus
US3388854A (en) * 1966-06-23 1968-06-18 Atlas Copco Ab Thrust balancing in rotary machines
DE19820523A1 (de) * 1998-05-08 1999-11-11 Peter Frieden Schraubenspindel-Vakuumpumpe mit Rotorkühlung

Also Published As

Publication number Publication date
DE20302990U1 (de) 2004-07-08

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