WO2011101064A2 - Entraînement pour un compresseur à broches - Google Patents

Entraînement pour un compresseur à broches Download PDF

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Publication number
WO2011101064A2
WO2011101064A2 PCT/EP2010/070875 EP2010070875W WO2011101064A2 WO 2011101064 A2 WO2011101064 A2 WO 2011101064A2 EP 2010070875 W EP2010070875 W EP 2010070875W WO 2011101064 A2 WO2011101064 A2 WO 2011101064A2
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
spur gear
pair
pump according
screw
Prior art date
Application number
PCT/EP2010/070875
Other languages
German (de)
English (en)
Other versions
WO2011101064A3 (fr
Inventor
Ralf Steffens
Original Assignee
Ralf Steffens
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 Ralf Steffens filed Critical Ralf Steffens
Publication of WO2011101064A2 publication Critical patent/WO2011101064A2/fr
Publication of WO2011101064A3 publication Critical patent/WO2011101064A3/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
    • 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
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing 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
    • F04C29/0042—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
    • 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
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C29/0078—Fixing rotors on shafts, e.g. by clamping together hub and shaft

Definitions

  • Drying compressors are gaining in importance in industrial compressor technology, because increasing obligations in environmental regulations and rising operating and disposal costs and increased demands on the purity of the pumped medium, the known wet-running compressors, such as liquid ring machines, rotary vane pumps and oil or water-injected screw compressors, increasingly replaced by dry compacting machines. These machines include dry screw compressors, claw pumps, diaphragm pumps, piston pumps, scroll machines and Roots pumps. However, these machines have in common that they still do not meet today's demands in terms of reliability and robustness and size and weight while maintaining low price level and satisfactory compressor efficiency.
  • PCT patent WO 01/57401 describes an embodiment for the drive for such a screw-type screw compressor.
  • the object of the present invention is for dry-compressing
  • 2-shaft rotary displacement machines for conveying and compressing gaseous media to make the drive for the displacement rotors such that the rotor synchronization and the rotor speed increase occur simultaneously, that the space required for the drive is minimized that different positions be made possible for the drive motor that auxiliary equipment, such as coolant (oil) feed pump and cooling fan, etc., are advantageously driven at a suitable speed that the displacement rotors form fully balancing separate units that the coolant / oil supply for each rotor end face At each end of the rotor shaft on the oil-lubricated side of the transmission, it becomes easy to realize that different rotor speeds can be conveniently achieved with the same rotor axis distance in the modular positive displacement machine modular system and that the gear noise is effectively minimized.
  • auxiliary equipment such as coolant (oil) feed pump and cooling fan, etc.
  • this object is achieved in that in a dry-compressing screw machine with a rotor internal cooling for the spindle rotor pair, the sum of the outer teeth radii of the two rotor-driven to-be-driven spur gears is smaller than the axial distance from the pair of spindle rotors and the rotor-fixed gears are thus no longer in direct engagement with each other , And that an additional pair of larger spur gear wheels, which are directly in engagement with each other, engages in each rotor fixed spur gear individually, that rotate the rotor fixed spur gears both synchronized in the opposite direction to each other and driven at a higher speed than this additional Stirn beaun beauts, that the direct transmission-side access frontally at each spindle rotor shaft end for the coolant for internal rotor cooling is easily achieved, and that auxiliary equipment such as the coolant pump on a r the waves of the additional spur gear pair is arranged, that in at least one (preferably of course in each) meshing the cooled via an external heat exchanger
  • Fig. 1 shows an example of the embodiment of the present invention with a plan view of the drive in a simplified form of representation.
  • the two rotor-fixed spur gears (1) to be driven have the illustrated axial distance a R from each other and belong to the respective displacement rotor, which is shown here via the pitch circle (2) of the outer spindle rotor conveyor thread whose diameter value is preferably as large as the mirror image identical spindle rotor pair Center distance a R of the screw machine.
  • the tooth diameter entered as 0d for the both driven rotor-fixed spur gears (1) are inventively chosen so low that they are not engaged with each other. With this feature, each spindle rotor can be preassembled separately as a complete rotation unit and can finally be fully balanced final and final.
  • the two additional spur gears (3) have a larger by a factor i gear diameter, as shown in the dimension as a product 0ixd and are at the axial distance a M preferably the same size.
  • Each additional spur gear (3) is according to the invention with exactly one to be driven rotor fixed spur gear (1) and in addition to each other in meshing engagement, so that overall the illustrated 3 gearing interventions, as shown in FIG. 3 also shown.
  • the (coolant) feed pump (4) is preferably driven via the gear shaft at a speed which is desired by the factor i less than the spindle rotor speed.
  • a more technically detailed embodiment of the coolant (oil) feed pump (4) is shown in Fig. 4 yet.
  • the coolant can be conveniently supplied for the spindle rotor internal cooling, which is shown in greater detail in FIG. 4 as an exemplary embodiment.
  • the pulley (12) to be driven fixedly connected to the additional spur gear (3) is driven by the drive motor (10) via the belt drive (9) by the driving pulley (13).
  • the drive motor (10) can also be positioned differently to the spindle compressor machine, so both parallel, and above or below or even in alignment with the extension of the spindle compressor machine.
  • the drive motor (10) is preferably to be positioned so that the belt forces and the toothing forces compensate each other in their orientation instead of reinforcing each other.
  • the additional spur gear (3) can also be placed directly on the motor shaft of the drive motor (10) with direct drive.
  • Fig. 3 shows how Fig. 1 by way of example the embodiment of the present invention with a plan view of the drive in a simplified form of representation.
  • the injection (1 1) of cooled lubricant (oil) is targeted specifically in each individual tooth engagement by the coolant injection direction is compliant with the illustrated direction of rotation of the meshing gears.
  • the technically accurate embodiment can be seen in Fig. 4.
  • significantly lower tooth meshing speeds are realized for the further reduction of toothed noise due to the smaller diameter values of the toothed wheels compared to the prior art. This is solved significantly less favorable in current screw compressors because their gears are significantly larger and therefore cause more noise.
  • Fig. 4 shows for the present invention by way of example a more detailed sectional drawing as a practically complete construction design.
  • the coolant (oil) feed pump (4) is connected via the intermediate shaft (25) fixed to an additional spur gear (3) and conveys the coolant (oil) in a circuit through the heat exchanger (21) as a "cooler” over both the two Rotorstimseitjgen accesses (6) in each spindle rotor (16) for internal rotor cooling (18) as well as the illustrated 3 injections (1 1) in each tooth engagement as shown in Fig. 3.
  • FIG. 5 and FIG. 6 different orientations of the axial distances from one another are shown for the present invention for the rotor-proof spur gear pair (1) to be driven and for the additional spur gear pair (3) in addition to the embodiment in FIG Requirements in terms of volume and / or different drive positions are to be met.
  • the engagement contacts between the spur gears are indicated in Fig. 5 and Fig. 6 with the letter C and a circular ring.
  • the Spindelverdrängerrotore can rotate in opposite directions to each other in the compressor working space without touching, the gear described from the two rotor fixed spur gears (1) and two additional spur gears (3) to ensure synchronization for the spindle rotor pair (16) constantly. Due to the total of three gearing interventions, however, add the inevitable meshing Vercardflanken admir and give a correspondingly poorer synchronization accuracy for the spindle rotor pair (16). To compensate for these increased VerF admir the slope on the spindle rotor pair (16) is kept as low as possible, the Verdückflankenemployed each meshing are also minimized. It should be noted that:
  • Coolant (oil) delivery pump (as auxiliary unit)
  • working space housing (can be made in several parts)
  • Coolants and lubricants (here in a distributor after the heat exchanger)
  • Cooler for the coolant and lubricant (preferably oil)
  • Cooling fan for the heat exchanger (cooler)

Landscapes

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

Abstract

L'invention concerne des machines de déplacement rotatives à deux arbres à compression à sec, de préférence réalisées sous forme de compresseurs à broches hélicoïdales pour refouler et comprimer des gaz. Selon l'invention, synchronisation el l'augmentation souhaitable de la vitesse de rotation de la paire de rotors à broches sont obtenues tout en conservant un espace de construction aussi compact que possible et une construction d'ensemble simple par les mesures suivantes : la somme des rayons extérieurs de denture des deux pignons droits (1) à entraîner et fixés au rotor est inférieure à la distance entre les axes aR de la paire de rotors (16) à broches hélicoïdales et donc les pignons droits (1) fixés au rotor ne sont plus en prise d'engagement avec les dentures; simultanément une paire de plus grands pignons droits supplémentaires (3), qui sont en prise directe d'engagement avec les dentures l'un avec l'autre, viennent en prise à chaque fois individuellement dans chaque pignon droit (1) fixé au rotor de telle sorte que les pignons droits (1) fixés au rotor soient entraînés à la fois de manière synchronisée l'un avec l'autre dans une direction opposée et avec une vitesse de rotation supérieure à celle de cette paire de pignons droits supplémentaire (3); l'entrée directe (6) du côté de la transmission est aisément accessible du côté frontal au niveau de chaque bout d'arbre de rotor à broche pour le fluide de refroidissement servant à refroidir l'intérieur du rotor; et des groupes auxiliaires tels que la pompe de refoulement (4) de réfrigérant sont disposés sur l'un des arbres de la paire de pignons droits supplémentaires; dans au moins un engagement des dents (de préférence naturellement dans chaque engagement des dents), du lubrifiant refroidi par un échangeur de chaleur externe est injecté de manière ciblée; le moteur d'entraînement pour l'entraînement de l'un des deux arbres de la paire de pignons droits supplémentaires (3) est disposé parallèlement ou en affleurement avec la machine à broche; et en option un entraînement à courroie est disposé entre le pignon droit supplémentaire (3) à entraîner et l'arbre de moteur.
PCT/EP2010/070875 2010-02-18 2010-12-29 Entraînement pour un compresseur à broches WO2011101064A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010002135.0 2010-02-18
DE102010002135 2010-02-18

Publications (2)

Publication Number Publication Date
WO2011101064A2 true WO2011101064A2 (fr) 2011-08-25
WO2011101064A3 WO2011101064A3 (fr) 2012-06-07

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/070875 WO2011101064A2 (fr) 2010-02-18 2010-12-29 Entraînement pour un compresseur à broches

Country Status (2)

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DE (1) DE102011003177A1 (fr)
WO (1) WO2011101064A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105134592A (zh) * 2015-09-08 2015-12-09 无锡压缩机股份有限公司 一种双螺杆端面型线的设计方法
DE202018000178U1 (de) 2018-01-12 2019-04-15 Leybold Gmbh Kompressor
CN112032026A (zh) * 2020-09-10 2020-12-04 河北通嘉宏盛科技有限公司 一种真空泵的降温防护装置

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000012899A1 (fr) 1998-08-29 2000-03-09 Ralf Steffens Pompe a broche helicoidale a compression a sec
WO2001057401A1 (fr) 2000-02-02 2001-08-09 Ralf Steffens Systeme d'entrainement de pompe a vis

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0290662B1 (fr) * 1987-05-15 1993-03-31 Leybold Aktiengesellschaft Pompe à vide à déplacement positif avec deux arbres
JPH0577592U (ja) * 1991-02-14 1993-10-22 株式会社アンレット 高速用まゆ型二軸容積ポンプ
DE20302990U1 (de) * 2003-02-24 2004-07-08 Werner Rietschle Gmbh + Co. Kg Drehkolbenpumpe
DE10334481A1 (de) * 2003-07-29 2005-03-17 Steffens, Ralf, Dr. Antrieb einer Spindelvakuumpumpe
DE102007030199A1 (de) * 2006-07-03 2008-01-10 Steffens, Ralf, Dr. Ing. Getriebe für eine Schraubenspindelpumpe
WO2010006663A1 (fr) 2008-07-18 2010-01-21 Ralf Steffens Refroidissement d'une pompe à vis

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000012899A1 (fr) 1998-08-29 2000-03-09 Ralf Steffens Pompe a broche helicoidale a compression a sec
WO2001057401A1 (fr) 2000-02-02 2001-08-09 Ralf Steffens Systeme d'entrainement de pompe a vis

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105134592A (zh) * 2015-09-08 2015-12-09 无锡压缩机股份有限公司 一种双螺杆端面型线的设计方法
DE202018000178U1 (de) 2018-01-12 2019-04-15 Leybold Gmbh Kompressor
WO2019137852A1 (fr) 2018-01-12 2019-07-18 Leybold Gmbh Compresseur
CN112032026A (zh) * 2020-09-10 2020-12-04 河北通嘉宏盛科技有限公司 一种真空泵的降温防护装置

Also Published As

Publication number Publication date
DE102011003177A1 (de) 2011-08-18
WO2011101064A3 (fr) 2012-06-07

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