EP0666422A1 - 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
EP0666422A1
EP0666422A1 EP95101024A EP95101024A EP0666422A1 EP 0666422 A1 EP0666422 A1 EP 0666422A1 EP 95101024 A EP95101024 A EP 95101024A EP 95101024 A EP95101024 A EP 95101024A EP 0666422 A1 EP0666422 A1 EP 0666422A1
Authority
EP
European Patent Office
Prior art keywords
rotor
rotors
drive
compressor
gear
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.)
Granted
Application number
EP95101024A
Other languages
German (de)
English (en)
Other versions
EP0666422B1 (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 DE19944403647 external-priority patent/DE4403647A1/de
Priority claimed from DE19944403648 external-priority patent/DE4403648A1/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 provided with oil injection into the work 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 the pressure-side bearing housing, respectively, and therefore consist of the same material, eg. B. Cast steel.
  • the pins protrude into the bores of the rotors, which are equipped with slide or roller bearings for mounting the pins.
  • 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.
  • 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 pins 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 compressor drive can also be carried out via a gear transmission.
  • a gear driven gear is screwed or shrunk onto one of the four rotor ends, which engages in a gear driven gear with a drive shaft.
  • a clutch is used for the rotor compressor drive according to a known magnetic principle, the outer magnets of the second (motor-side) coupling half being the inner magnets of the first (compressor-side) coupling half take.
  • the first, compressor-side magnetic coupling half is arranged at the end of the drive shaft of the rotor compressor.
  • a bellows is arranged between the first coupling half and the second coupling half and hermetically seals the compressor.
  • the second magnetic coupling half is on the motor side.
  • This magnetic clutch is not an electromagnetic clutch, but a permanent magnet clutch.
  • Such couplings for transmission of torques are generally known. So there are permanent magnet couplings, the torques of z. B. 312 N. m transmitted. This torque is sufficient in almost all cases for use as a drive coupling for screw rotor compressors.
  • 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 another 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 has a thickened portion (4a) at the inner end, 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 shaft seal (2) for the torsion shaft (4) is arranged inside the drive-side bearing housing (3).
  • the coupling half (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 half (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 coupling half (29) of the magnetic coupling which is equipped with internal magnets (30), is mounted on the torsion shaft (4).
  • the engine side Coupling half (31) of the magnetic coupling engages around the first-mentioned coupling half. It contains the external magnets (32).
  • a bellows (29) is arranged between the compressor-side coupling half (29) and the motor-side coupling half (31). This can be made of a metallic material.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
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
DE19944403647 DE4403647A1 (de) 1994-02-05 1994-02-05 Magnetantrieb für einen Schraubenrotorverdichter
DE4403647 1994-02-05
DE19944403648 DE4403648A1 (de) 1994-02-05 1994-02-05 Abdichtung der Stirnflächen der Rotoren eines Schraubenrotorverdichters gegenüber dem Gehäuse
DE4403648 1994-02-05
DE4403649 1994-02-05
DE19944403649 DE4403649C2 (de) 1994-02-05 1994-02-05 Lagerung und Antrieb der Rotoren eines Schraubenverdichters

Publications (2)

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

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2602428A1 (fr) * 2011-12-08 2013-06-12 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
BE1022922B1 (nl) * 2015-04-17 2016-10-19 Atlas Copco Airpower Naamloze Vennootschap Compressorelement voor een schroefcompressor en schroefcompressor waarin zulk compressorelement is toegepast
GB2560375A (en) * 2017-03-10 2018-09-12 Edwards Ltd Rotating machine and rotors for use therein
EP3540228A4 (fr) * 2017-02-20 2020-06-24 Daikin Industries, Ltd. Compresseur à vis
US20210348609A1 (en) * 2018-05-14 2021-11-11 Xi'an Jiaotong University Screw compressor with sliding bearings

Families Citing this family (7)

* 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
WO2016022392A1 (fr) * 2014-08-08 2016-02-11 Eaton Corporation Dispositif de récupération d'énergie avec des mécanismes de dissipation de chaleur
CN107429694B (zh) * 2015-03-31 2019-10-22 株式会社日立产机*** 螺杆压缩机
DE202018107141U1 (de) 2018-12-13 2020-03-18 Vogelsang Gmbh & Co. Kg Drehkolbenpumpe mit innenliegender Lagerung
GB2610547B (en) * 2020-06-10 2024-06-05 Bora Kuzucan Mehmet Compressor
WO2021253060A1 (fr) * 2020-06-10 2021-12-16 CILLIE, Willem, Isaac Ensemble rotor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2091537A5 (fr) * 1970-05-13 1972-01-14 Kuehlautomat Veb
DE2520667A1 (de) * 1975-05-09 1976-11-18 Allweiler Ag Schraubenspindelpumpe
EP0101345A1 (fr) * 1982-07-22 1984-02-22 BENDIX France Compresseur volumétrique à vis

Family Cites Families (8)

* 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
US4293290A (en) * 1979-05-04 1981-10-06 Crepaco, Inc. Positive displacement rotary pump with bearings in countersunk portions of the rotors
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

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2091537A5 (fr) * 1970-05-13 1972-01-14 Kuehlautomat Veb
DE2520667A1 (de) * 1975-05-09 1976-11-18 Allweiler Ag Schraubenspindelpumpe
EP0101345A1 (fr) * 1982-07-22 1984-02-22 BENDIX France Compresseur volumétrique à vis

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2602428A1 (fr) * 2011-12-08 2013-06-12 Alfa Laval Corporate AB Pompe rotative à déplacement positif dotée d'arbres fixes et de manchons rotatifs
WO2013083740A3 (fr) * 2011-12-08 2013-11-21 Alfa Laval Corporate Ab Pompe à lobe rotatif dotée de supports 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
BE1022922B1 (nl) * 2015-04-17 2016-10-19 Atlas Copco Airpower Naamloze Vennootschap Compressorelement voor een schroefcompressor en schroefcompressor waarin zulk compressorelement is toegepast
WO2016164988A3 (fr) * 2015-04-17 2016-11-24 Atlas Copco Airpower, Naamloze Vennootschap Élément compresseur pour compresseur à vis, et compresseur à vis dans lequel un élément compresseur est utilisé
RU2697017C2 (ru) * 2015-04-17 2019-08-08 Атлас Копко Эрпауэр, Намлозе Веннотсхап Компрессорный элемент для винтового компрессора (варианты) и винтовой компрессор
US10760574B2 (en) 2015-04-17 2020-09-01 Atlas Copco Airpower, Naamloze Vennootschap Compressor element for a screw compressor and screw compressor in which such a compressor element is applied
EP3540228A4 (fr) * 2017-02-20 2020-06-24 Daikin Industries, Ltd. Compresseur à vis
GB2560375A (en) * 2017-03-10 2018-09-12 Edwards Ltd Rotating machine and rotors for use therein
US20210348609A1 (en) * 2018-05-14 2021-11-11 Xi'an Jiaotong University Screw compressor with sliding bearings

Also Published As

Publication number Publication date
DE59500818D1 (de) 1997-11-27
US5599176A (en) 1997-02-04
FI950482A (fi) 1995-08-06
AU1147295A (en) 1995-08-17
AU689829B2 (en) 1998-04-09
FI950482A0 (fi) 1995-02-03
JPH07279868A (ja) 1995-10-27
EP0666422B1 (fr) 1997-10-22

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