EP0666422B1 - Paliers et système d'entraînement pour les rotors d'un compresseur à vis - Google Patents

Paliers et système d'entraînement pour les rotors d'un compresseur à vis Download PDF

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Publication number
EP0666422B1
EP0666422B1 EP95101024A EP95101024A EP0666422B1 EP 0666422 B1 EP0666422 B1 EP 0666422B1 EP 95101024 A EP95101024 A EP 95101024A EP 95101024 A EP95101024 A EP 95101024A EP 0666422 B1 EP0666422 B1 EP 0666422B1
Authority
EP
European Patent Office
Prior art keywords
rotor
rotors
bearing
bearings
compressor
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
EP95101024A
Other languages
German (de)
English (en)
Other versions
EP0666422A1 (fr
Inventor
Hans-Hermann Dipl.-Ing. Reinersmann
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.)
GHH Rand Schraubenkompressoren GmbH
Original Assignee
MAN Gutehoffnungshutte 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
Priority claimed from DE19944403648 external-priority patent/DE4403648A1/de
Priority claimed from DE19944403647 external-priority patent/DE4403647A1/de
Priority claimed from DE19944403649 external-priority patent/DE4403649C2/de
Application filed by MAN Gutehoffnungshutte GmbH filed Critical MAN Gutehoffnungshutte GmbH
Publication of EP0666422A1 publication Critical patent/EP0666422A1/fr
Application granted granted Critical
Publication of EP0666422B1 publication Critical patent/EP0666422B1/fr
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

Definitions

  • the invention relates to a rotor compressor with meshing engagement between a screw-toothed rib rotor and a screw-toothed slot rotor.
  • the screw rotor compressor as a positive displacement machine not only transports the pumped medium from the suction to the pressure side, but also compresses it in this way by reducing the tooth space. If the rotors or rotors rotate in the housing, they disengage at the control edge on the suction side, so that a cross section and a volume open for suction. With further rotation, the rotors come back into engagement on their control edges. The cross section of the work space moving in the axial direction is reduced to the control edge on the pressure side of the housing, at which the compressed medium is pushed out.
  • Screw rotor compressors can be driven directly at the engine speed or via a built-in gear.
  • Compressors with high compression ratios (final pressure / suction pressure) above about 4.0 are oil-injected into the working area on the suction side in order to increase the compression temperature limit a maximum of 100 ° C. In these machines, there is an oil film between the rotors. In contrast to compressors without oil injection, there is no need for a differential gear that protects the rotors from contact.
  • the gap to the housing should be kept as small as possible in order to reduce leakages of the compressed medium.
  • the narrow sealing gaps required for this are achieved by precisely adjusting the rotor position to the housing, taking into account the expected operating conditions. For safety reasons, a slightly larger gap is chosen than is theoretically necessary. This safety gap difference inevitably increases the degree of leakage and reduces the compressor efficiency.
  • the rotors of the known screw rotor compressors have pins arranged on both sides, which are mounted in axial and radial bearings in the housing.
  • a disadvantage of this design is the high deflection of the rotors and the simultaneous occurrence of high torsional and bending stresses on the driven rotor journal.
  • the bearing pins are made as large as possible. The consequence of this is that the bearing diameter and the bearing spacing must also be chosen to be correspondingly large.
  • the invention is therefore based on the object of reducing the load on the driven journals in a screw rotor compressor and giving the rotors a higher overall rigidity, reducing the sealing gaps between the end faces of the rotors and the housing parts to a minimum, thereby increasing the efficiency of the compressor increase and design a drive so that the tightness of the compressor is improved.
  • the screw rotor compressor has internal rotor bearings.
  • the bearing journals, hereinafter referred to as journals, for the main and secondary rotors are parts of the suction-side and pressure-side bearing housings, respectively, and therefore consist of the same material, e.g. B. Cast steel.
  • the one-piece journals protrude into the bores of the rotors, which are equipped with plain or roller bearings to support the journals.
  • Either axial and radial bearings on the suction side and radial bearings on the pressure side or radial bearings on the suction side and axial and radial bearings on the pressure side can be used for the bearing.
  • the drive of the screw rotor compressor can be arranged on one of the rotors on the suction or pressure side.
  • a torsion shaft is provided for the drive, which is guided through a bore in the suction or pressure-side bearing housing and one of the four pins.
  • the compressor is driven by a coupling at the outer end of the torsion shaft.
  • the torsion shaft is not loaded by bending forces, but only by torsional forces.
  • sealing washers according to the invention can be used both in screw rotor compressors with the rotor mounted on the outside and in the machines according to the invention, the rotors of which are mounted on housing journals arranged inside the rotors.
  • a PTFE (polytetrafluoroethylene) mica mixture is proposed as the material for the sealing washers. Sealing washers made from this extremely durable plastic-mineral mixture, known under the name Fluorsint, have already proven themselves. Of course, the proposed invention extends to any other materials or material mixtures with the same or similar properties.
  • the sealing washers are screwed or glued to the suction and pressure side housing parts. They can also be inserted with a positive fit.
  • the bearing housing (3) of the drive side shown in FIG. 1 is equipped on its inside with a pin (14) for engaging in the bore in the rotor (12) and with a further pin (14) for engaging in the rotor (12a).
  • the pressure-side bearing housing (15) also has pins (14) on its inside. One of these pins engages in the bore in the rotor (12) and the other in the bore in the rotor (12a).
  • the rotors (12, 12a) according to the invention within the compressor housing (11) only consist of the screw-toothed rib rotor and the screw-toothed slot rotor, in the ends of which central bores for receiving the pins (14) are made.
  • the drive of the compressor is located on the suction side on the rotor (12), the screw-toothed rib rotor.
  • the rotors (12, 12a) are supported on the pressure-side pins by radial bearings (16, 17). On the suction side, the rotors (12, 12a) are mounted on the pins (14) in radial bearings (6, 22) and axial bearings (9, 21).
  • the rotor (12) is driven on the suction side by means of a torsion shaft (4).
  • This torsion shaft is guided through a bore in the drive-side bearing housing (3) and the pin (14) and points on the inside End a thickening (4a), which is located in a recess in the bore.
  • the thickened end (4a) of the torsion shaft (4) can be inserted into the recess in the bore when mounting the compressor.
  • the drive-side bearing housing (3) is then pushed over the torsion shaft (4) and the pin (14) with the bearings (6, 9) is pushed into the rotor (12).
  • a positive connection is thereby established between the torsion shaft (4) and the rotor (12).
  • a shaft seal (2) for the torsion shaft (4) is arranged inside the drive-side bearing housing (3).
  • the coupling flange (1) belonging to the compressor is placed on the outer end of the torsion shaft (4) and is held by a nut (23).
  • FIG. 2 shows that the rotor (12) is driven on the suction side via a gear transmission.
  • a gear output gear (25) can be seen on the side of the rotor (12), which engages in a gear input gear (27) with a drive shaft (26).
  • the drive shaft is mounted in radial bearings (13, 18) on the inside of the gearbox of the compressor housing (11) and on the outside of the gearbox of the bearing housing (3) on the drive side.
  • the inside of the drive-side bearing housing (3) is equipped with a pin (14) for engaging in the bore in the rotor (12) and with a further pin (14) for engaging in the rotor (12a).
  • the pressure-side bearing housing (15) also has pins (14) on its inside. One of these pins (14) engages in the bore in the rotor (12) and the other in the bore in the rotor (12a).
  • the drive-side mounting of the rotor (12) is denoted by (6,7,8,9,10), that of the rotor (12a) is denoted by (19,20,21,22).
  • the bearing on the pressure side on the pins (14) of the bearing housing (15) is carried out by radial bearings (16, 17).
  • the compressor drive is on the suction side of the rotor (12). This rotor is driven by a torsion shaft (4).
  • the compressor-side coupling flange (1) can be seen at one end of the torsion shaft (4).
  • sealing disks (5) Between the end faces of the rotors (12, 12a) arranged in the compressor housing (11) and the suction and pressure-side housing parts (3, 15) are the sealing disks (5), which are screwed to these housing parts (3, 15) in recesses, glued or inserted positively.
  • These sealing washers consist of a reduced PTFE-mica mixture or of a material with similar properties.
  • FIG. 4 shows in a further variant a rib rotor (12) on the drive side arranged in the compressor housing (11), which has a magnetic coupling.
  • Radial (6) and axial bearings (9) are also used for the rotor bearings.
  • a torsion shaft (4) is guided through a bore in the bearing housing (3) and in the pin (14) and is supported in the bearing housing (3) by means of a support bearing (28).
  • the inner end of the torsion shaft (4a) is positively connected to the rotor (12).
  • the compressor-side magnetic coupling half (29) On the torsion shaft (4) is the compressor-side magnetic coupling half (29), which is equipped with internal magnets (30).
  • the motor-side magnetic coupling half (31) engages around the first-mentioned coupling half. It contains the external magnets (32).
  • a bellows (29) is arranged between the compressor-side magnetic coupling half (29) and the motor-side magnetic coupling half (31). This can be made of a metallic material.

Claims (3)

  1. Compresseur à rotors, formé d'un rotor à nervures hélicoïdales (12) et d'un rotor à rainures hélicoïdales (12a), en prise d'engrènement,
    caractérisé en ce que
    - le carter de palier du côté aspiration (3) et celui du côté pression (15) comportent un tourillon (14) en une seule pièce faisant partie de la paroi des carters de palier (13, 15) et pénétrant dans des perçages des rotors (12, 12a) munis de paliers radiaux et axiaux (6, 9, 16, 17, 21, 22)
    - un axe de torsion (4) traverse un perçage dans le carter de palier (3, 15) du côté aspiration ou du côté pression et l'un des quatre tourillons (14), cet axe, non sollicité par des forces de flexion mais uniquement par des forces de traction, comportant une bride de couplage (1) pour l'entraînement du compresseur,
    - un joint d'arbre (2) du côté du carter de palier et une cavité à l'extrémité du perçage de l'arbre de torsion (4) réalisent une liaison par la forme entre le renforcement (4a) de l'arbre de torsion (4) et le rotor (12).
  2. Compresseur à rotors selon la revendication 1,
    caractérisé en ce que
    les perçages des rotors (12, 12a) pour le tourillon (14) comportent sélectivement des paliers axiaux (9) et radiaux (6) du côté aspiration, des paliers radiaux (16, 17) du côté pression ou des paliers radiaux (16, 17) du côté aspiration, et des paliers axiaux (9) et radiaux (6) du côté pression.
  3. Compresseur à rotors selon les revendications 1 et 2,
    caractérisé en ce que
    - les parties de carter (15) du côté entraînement (3) et du côté pression, entre les faces frontales des rotors (12, 12a), comportent des rondelles d'étanchéité (5) reliées aux parties de carter (3, 15) par vissage, par collage ou par une liaison par la forme et
    - les rondelles d'étanchéité (5) sont formées d'un mélange PTFE-mica ou d'une matière ayant des propriétés analogues.
EP95101024A 1994-02-05 1995-01-26 Paliers et système d'entraînement pour les rotors d'un compresseur à vis Expired - Lifetime EP0666422B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE19944403648 DE4403648A1 (de) 1994-02-05 1994-02-05 Abdichtung der Stirnflächen der Rotoren eines Schraubenrotorverdichters gegenüber dem Gehäuse
DE4403647 1994-02-05
DE4403648 1994-02-05
DE4403649 1994-02-05
DE19944403647 DE4403647A1 (de) 1994-02-05 1994-02-05 Magnetantrieb für einen Schraubenrotorverdichter
DE19944403649 DE4403649C2 (de) 1994-02-05 1994-02-05 Lagerung und Antrieb der Rotoren eines Schraubenverdichters

Publications (2)

Publication Number Publication Date
EP0666422A1 EP0666422A1 (fr) 1995-08-09
EP0666422B1 true EP0666422B1 (fr) 1997-10-22

Family

ID=27206052

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95101024A Expired - Lifetime EP0666422B1 (fr) 1994-02-05 1995-01-26 Paliers et système d'entraînement pour les rotors d'un compresseur à vis

Country Status (6)

Country Link
US (1) US5599176A (fr)
EP (1) EP0666422B1 (fr)
JP (1) JPH07279868A (fr)
AU (1) AU689829B2 (fr)
DE (1) DE59500818D1 (fr)
FI (1) FI950482A (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2376505B (en) * 2001-06-11 2003-12-17 Compair Uk Ltd Improvements in screw compressors
JP4784484B2 (ja) * 2006-11-02 2011-10-05 株式会社豊田自動織機 電動ポンプ
EP2602428B1 (fr) * 2011-12-08 2018-04-25 Alfa Laval Corporate AB Pompe rotative à déplacement positif dotée d'arbres fixes et de manchons rotatifs
CN103277309A (zh) * 2013-06-17 2013-09-04 上海大隆机器厂有限公司 一种双螺杆压缩机的同步齿轮装置
US20170226857A1 (en) * 2014-08-08 2017-08-10 Eaton Corporation Energy recovery device with heat dissipation mechanisms
US10704549B2 (en) * 2015-03-31 2020-07-07 Hitachi Industrial Equipment Systems Co., Ltd. Screw compressor having a discharging passage with enlarged cross section area
BE1022922B1 (nl) * 2015-04-17 2016-10-19 Atlas Copco Airpower Naamloze Vennootschap Compressorelement voor een schroefcompressor en schroefcompressor waarin zulk compressorelement is toegepast
JP6747572B2 (ja) 2017-02-20 2020-08-26 ダイキン工業株式会社 スクリュー圧縮機
GB2560375A (en) * 2017-03-10 2018-09-12 Edwards Ltd Rotating machine and rotors for use therein
CN108757450B (zh) * 2018-05-14 2020-04-28 西安交通大学 一种采用滑动轴承的螺杆压缩机
DE202018107141U1 (de) * 2018-12-13 2020-03-18 Vogelsang Gmbh & Co. Kg Drehkolbenpumpe mit innenliegender Lagerung
GB2610547A (en) * 2020-06-10 2023-03-08 Bora Kuzucan Mehmet Compressor
WO2021253060A1 (fr) * 2020-06-10 2021-12-16 CILLIE, Willem, Isaac Ensemble rotor

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1834976A (en) * 1928-03-09 1931-12-08 Patiag Patentverwertungs Und I Rotary compressor, pump or the like
US3417915A (en) * 1966-10-10 1968-12-24 Albert J. Granberg Rotary blower and timing adjustment mechanism
DE2115058A1 (de) * 1970-05-13 1971-12-16 VEB Kühlautomat, χ 1197 Berlin Lagerung der Rotoren von Schraubenverdichtern
DE2520667C2 (de) * 1975-05-09 1984-11-29 Allweiler Ag, 7760 Radolfzell Schraubenspindelpumpe
US4293290A (en) * 1979-05-04 1981-10-06 Crepaco, Inc. Positive displacement rotary pump with bearings in countersunk portions of the rotors
FR2530742B1 (fr) * 1982-07-22 1987-06-26 Dba Compresseur volumetrique a vis
US4674960A (en) * 1985-06-25 1987-06-23 Spectra-Physics, Inc. Sealed rotary compressor
US4797078A (en) * 1986-06-11 1989-01-10 Wankel Gmbh Bearing arrangement of an external-axial rotary piston blower
JP3074829B2 (ja) * 1991-09-05 2000-08-07 松下電器産業株式会社 流体回転装置
US5374173A (en) * 1992-09-04 1994-12-20 Matsushita Electric Industrial Co., Ltd. Fluid rotating apparatus with sealing arrangement
US5449278A (en) * 1994-11-14 1995-09-12 Lin; Chi-So Double action piston having plural annular check valves

Also Published As

Publication number Publication date
JPH07279868A (ja) 1995-10-27
FI950482A (fi) 1995-08-06
AU689829B2 (en) 1998-04-09
US5599176A (en) 1997-02-04
FI950482A0 (fi) 1995-02-03
AU1147295A (en) 1995-08-17
EP0666422A1 (fr) 1995-08-09
DE59500818D1 (de) 1997-11-27

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