EP0404921B1 - Paire de rotors pour compresseur a vis haute pression - Google Patents

Paire de rotors pour compresseur a vis haute pression Download PDF

Info

Publication number
EP0404921B1
EP0404921B1 EP90901801A EP90901801A EP0404921B1 EP 0404921 B1 EP0404921 B1 EP 0404921B1 EP 90901801 A EP90901801 A EP 90901801A EP 90901801 A EP90901801 A EP 90901801A EP 0404921 B1 EP0404921 B1 EP 0404921B1
Authority
EP
European Patent Office
Prior art keywords
rotor
teeth
main rotor
main
auxiliary
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
EP90901801A
Other languages
German (de)
English (en)
Other versions
EP0404921A1 (fr
Inventor
Dieter Mosemann
Hans-Ulrich Pews
Andreas c/o Kühlautomat Berlin GmbH RIETZKE
Horst Maier
Ottmar Neuwirth
Peter Kolberg
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.)
Bauer Kompressoren GmbH
Original Assignee
Bauer Kompressoren 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 Bauer Kompressoren GmbH filed Critical Bauer Kompressoren GmbH
Publication of EP0404921A1 publication Critical patent/EP0404921A1/fr
Application granted granted Critical
Publication of EP0404921B1 publication Critical patent/EP0404921B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C18/12—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

Definitions

  • the invention relates to a pair of rotors for a high-pressure screw compressor of the type specified in the introductory part of patent claim 1.
  • the tooth gaps of the main and secondary rotors form communicating V-shaped working chambers in which the working cycles include suction, compression and ejection due to the rotation of the rotors takes place and there are pressure differences on the rotors, which lead to action forces on the bearings.
  • a screw compressor which comprises a total of at least three rotors, ie a central screw rotor, which is the driven main rotor, and a secondary rotor on both sides thereof.
  • the main rotor is provided with concave teeth, while the two secondary rotors are provided with convex teeth.
  • This type of construction differs fundamentally from the screw compressor of the type mentioned both in terms of the number of rotors and the design of the teeth on the rotors.
  • the number of teeth is determined in such a way that the secondary rotor is stiff enough to prevent bending.
  • Combinations of teeth with a difference in the number of secondary rotor teeth minus the number of main rotor teeth from -1 to +2 are used, which means that the load capacity of the support bearings, particularly the secondary rotor, is relatively limited due to the small center distance of the rotors.
  • the area of use of known screw compressors is limited to approximately 2.5 MPa with regard to its maximum permissible operating pressure, and high-pressure applications cannot be covered.
  • the invention has for its object to develop a screw compressor of the generic type in a structurally simple manner such that it allows economical work even at higher operating pressures at which high pressure screw compressors can work.
  • a pair of rotors for a high-pressure screw compressor has a secondary rotor which has at least 3 teeth more than the main rotor, the difference in the number of teeth depending on the maximum operating pressure and being so great that the increased action force on the pressure-side support bearing of the associated with the increase in the number of teeth of the secondary rotor
  • Auxiliary rotor is smaller than the load-bearing capacity of the largest possible support bearing, which is caused by the size of the number of secondary rotor teeth due to the increase in the center distance.
  • the secondary rotor of the rotor pair according to the invention has at least 3 teeth more than the main rotor, the difference in the number of teeth depends on the maximum operating pressure and is so large that the increased action force on the pressure-side support bearing of the secondary rotor associated with the increase in the number of teeth of the secondary rotor is less than the load capacity of the largest possible support bearing, which can be used due to the increase in the center distance due to the size of the secondary rotor teeth.
  • the screwing angle of the secondary rotor is reduced to 50% of the main rotor, while the center distance compared to a combination of 4 to 6 increases by 23%, so that a roller bearing as a support bearing at the secondary rotor shaft end a 40 to 50% higher load capacity (comparison basis: bearing outer diameter for the secondary rotor equals the center distance) can be used, while the action force at this point increases only by 8% at a maximum operating pressure of 3.5 MPa if the number of secondary rotor teeth is increased from 6 to 8.
  • the inner column is positively influenced by the increase in the number of secondary rotor teeth, since the bearing play and thermal expansion of the rotor are in opposite directions.
  • the size of the screwing angle of the main rotor is determined as a function of the peripheral speed.
  • the distance between the rotors of a screw compressor which determines the size of the possible bearings, is achieved by increasing the number of secondary rotor teeth.
  • the secondary rotor has at least 3 teeth more than the main rotor.
  • the screwing angle of the secondary rotor is reduced to 50 percent of the main rotor.

Landscapes

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

Abstract

Une paire de rotors pour compresseur à vis haute pression comporte un rotor principal et un rotor auxiliaire. Le rotor principal comprend des dents sensiblement convexes disposés à l'extérieur de son cercle primitif de référence et le rotor auxiliaire présente des dents sensiblement concaves disposées à l'intérieur de son cercle primitif. L'entraxe qui délimite la dimension des éventuels coussinets est accru uniquement par l'augmentation du nombre de dents sur le rotor auxiliaire.

Claims (3)

  1. Paire de rotors pour un compresseur à vis haute pression comportant un rotor principal muni de dents sensiblement convexes en dehors de son cercle partiel et un rotor auxiliaire muni de dents sensiblement concaves à l'intèrieur de son cercle partiel, qui sont vissés avec un angle de vissage établi sur les surfaces frontales opposées du rotor principal au rotor auxiliaire, les rotors étant supportés coaxialement dans des logements d'appui et des logements de crapaudine à distance axiale de leurs axes de rotation qui, dans le cycle de travail comprenant l'aspiration, la compression et l'évacuation, prennent dans les sens radiaux et axiaux caractérisêe en ce que, pour l'augmentation de l'entraxe entre les rotors, le rotor auxiliaire comporte au moins trois dents de plus que le rotor principal de sorte que la force d'appui du logement d'appui du côté soumis à la poussée du rotor auxiliaire soit augmentée plus que l'addition de la force d'action actionnant ainsi par le nombre de dents plus grand du rotor auxiliaire dans les cycles de travail.
  2. Paire de rotors pour un compresseur à vis haute pression suivant la revendication 1, caractérisée en ce que l'angle de vissage du rotor principal mesuré en grade est de 14 à le fois aussi grand que la valeur en dents de la vitesse circonférentielle du rotor principal en mètre par seconde.
  3. Paire de rotors pour un compresseur à vis haute pression suivant la revendication 1 ou 2, caractérisée en ce que, pour une pression de service maximale de 3,5 MPa, le rotor principal présente quatre dents et le rotor auxiliaire huit dents.
EP90901801A 1989-01-17 1990-01-17 Paire de rotors pour compresseur a vis haute pression Expired - Lifetime EP0404921B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DD325088A DD301062A7 (de) 1989-01-17 1989-01-17 Rotorpaar für Hochdruckschraubenverdichter
DD325008 1989-01-17

Publications (2)

Publication Number Publication Date
EP0404921A1 EP0404921A1 (fr) 1991-01-02
EP0404921B1 true EP0404921B1 (fr) 1993-11-10

Family

ID=5606651

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90901801A Expired - Lifetime EP0404921B1 (fr) 1989-01-17 1990-01-17 Paire de rotors pour compresseur a vis haute pression

Country Status (6)

Country Link
US (1) US5096399A (fr)
EP (1) EP0404921B1 (fr)
JP (1) JP2812797B2 (fr)
DD (1) DD301062A7 (fr)
DE (1) DE59003410D1 (fr)
WO (1) WO1990008261A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006021704B4 (de) * 2006-05-10 2018-01-04 Gea Refrigeration Germany Gmbh Schraubenverdichter für große Antriebsleistungen
DE102006035783A1 (de) * 2006-08-01 2008-02-07 Grasso Gmbh Refrigeration Technology Schraubenverdichter
DE102006035782B4 (de) * 2006-08-01 2018-10-25 Gea Refrigeration Germany Gmbh Schraubenverdichter für extrem große Betriebsdrücke
GB0921968D0 (en) * 2009-12-17 2010-02-03 Epicam Ltd A rotary deviceand method of designingand makinga rotary device

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH255202A (de) * 1944-06-29 1948-06-15 Ljungstroms Angturbin Ab Rotationsmaschine.
DE3111834A1 (de) * 1981-03-26 1982-10-21 Balcke-Dürr AG, 4030 Ratingen Schraubenverdichter
DE3140108A1 (de) * 1981-10-09 1983-04-28 Technika Beteiligungsgesellschaft mbH, 4800 Bielefeld Drehkolbenverichter
JPS60116920A (ja) * 1983-11-30 1985-06-24 Hitachi Ltd 回転流体機械におけるスラスト軸受の保持装置
GB8413619D0 (en) * 1984-05-29 1984-07-04 Compair Ind Ltd Screw rotor machines
SE453318B (sv) * 1987-02-18 1988-01-25 Svenska Rotor Maskiner Ab Rotormaskin med en axialkraftbalanseringsanordning

Also Published As

Publication number Publication date
JPH03503307A (ja) 1991-07-25
EP0404921A1 (fr) 1991-01-02
WO1990008261A1 (fr) 1990-07-26
DD301062A7 (de) 1992-10-01
JP2812797B2 (ja) 1998-10-22
US5096399A (en) 1992-03-17
DE59003410D1 (de) 1993-12-16

Similar Documents

Publication Publication Date Title
DE69025456T2 (de) Verbesserte Befestigung für die Schaufel einer Gasturbine auf einer Turbinenlaufradscheibe
DE1109704B (de) Schraubenradmaschine
DE1428277C3 (de) Zweistufiger Schraubenverdichter der Tandembauart
DE4136541A1 (de) Spiralverdichter mit optimierter kupplung
DE69000731T2 (de) Drehkolbenmaschine fuer fluide.
DE3400594A1 (de) Stroemungsmaschine
DE60014340T2 (de) Schraubenrotorbauweise für fluidverdrängungsanlage
DE2454079A1 (de) Kugellager
EP0404921B1 (fr) Paire de rotors pour compresseur a vis haute pression
DE19736333C1 (de) Befestigung eines Laufrades einer Strömungsmaschine an einer Welle
EP1252444A1 (fr) Systeme d'entrainement de pompe a vis
EP0666422B1 (fr) Paliers et système d'entraînement pour les rotors d'un compresseur à vis
DE4305289C2 (de) Schraubenverdichter
DE60035451T2 (de) Spiralverdichter
EP0567874B1 (fr) Machine à courant pour la compression d'un gaz
DE3301137C2 (fr)
DE3912279C2 (fr)
DE3526517A1 (de) Turbomolekularpumpe
DE69013793T2 (de) Fluidumdruck-Drehkolbenanlage und verbesserte ortsfeste Ventilplatte.
DE2134241C3 (de) Zweistufige außenachsige Rotationskolbenmaschine
DE1528717B2 (de) Vorrichtung zum ausgleich des axialschubes bei mehrstufigen kreiselpumpen
DE1428244B2 (de) Schraubenverdichter mit einem Schraubenrippenrotor und einem Schraubennutenrotor
DE2411247A1 (de) Hochvakuum-molekularpumpe mit zylindertrommel
DE2200547C3 (de) Verzahnung von Zahnradpumpen
WO2002103205A1 (fr) Contour profile des rotors helicoidaux d'une pompe a vis

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): BE DE GB SE

RIN1 Information on inventor provided before grant (corrected)

Inventor name: NEUWIRTH, OTTMAR

Inventor name: KOLBERG, PETER

Inventor name: PEWS, HANS-ULRICH

Inventor name: RIETZKE, ANDREAS C/O KUEHLAUTOMAT BERLIN GMBH

Inventor name: MOSEMANN, DIETER

Inventor name: MAIER, HORST

17P Request for examination filed

Effective date: 19901231

17Q First examination report despatched

Effective date: 19920624

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): BE DE GB SE

REF Corresponds to:

Ref document number: 59003410

Country of ref document: DE

Date of ref document: 19931216

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19931220

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
EAL Se: european patent in force in sweden

Ref document number: 90901801.2

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19990115

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19990121

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000117

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000131

BERE Be: lapsed

Owner name: BAUER KOMPRESSOREN G.M.B.H.

Effective date: 20000131

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20000117

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20050125

Year of fee payment: 16

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060118

EUG Se: european patent has lapsed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20090112

Year of fee payment: 20

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20100117