EP0988453A1 - Pompe a vide a vis et son procede de fonctionnement - Google Patents

Pompe a vide a vis et son procede de fonctionnement

Info

Publication number
EP0988453A1
EP0988453A1 EP98934953A EP98934953A EP0988453A1 EP 0988453 A1 EP0988453 A1 EP 0988453A1 EP 98934953 A EP98934953 A EP 98934953A EP 98934953 A EP98934953 A EP 98934953A EP 0988453 A1 EP0988453 A1 EP 0988453A1
Authority
EP
European Patent Office
Prior art keywords
screw
vacuum pump
chamber
inlet
inlet opening
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
EP98934953A
Other languages
German (de)
English (en)
Other versions
EP0988453B1 (fr
Inventor
Heiner KÖSTERS
Christian Dahmlos
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.)
Sterling Fluid Systems Germany GmbH
Original Assignee
Sterling Fluid Systems Germany 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 Sterling Fluid Systems Germany GmbH filed Critical Sterling Fluid Systems Germany GmbH
Publication of EP0988453A1 publication Critical patent/EP0988453A1/fr
Application granted granted Critical
Publication of EP0988453B1 publication Critical patent/EP0988453B1/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
    • 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
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors

Definitions

  • the temperature of the gas delivered by a compressor increases according to the compression pressure ratio.
  • screw compressors that rely on the least possible play both between the two rotors and between the rotors and the housing, the thermal expansion caused on the parts of the compressor can lead to problems.
  • the pre-inlet quantity supplied to the chambers is small in view of the efficiency of the machine. For example, when operating a screw machine as a compressor (US Pat. No. 4,812,110; US Pat. No.
  • the solution according to the invention consists in the features of claims 1 to 3. Accordingly, a screw pump vacuum pump is assumed which has at least three delivery chambers located one behind the other along each rotor. These are completed if you do not play the game that is unavoidable with dry extraction.
  • the last chamber on the pressure side shortly before it opens to the pressure side, is brought almost or completely to the final compression pressure through the pre-inlet by introducing a pre-inlet flow of cool gas which is at least five times larger than that Intake mass flow.
  • An operating point is assumed in which the ratio of the outer to the inner compression is at least five. On the one hand, this achieves effective cooling in the most critical area of the rotors with regard to temperature control.
  • this cooling also affects the penultimate chamber, because part of the cooler gas, which is under much higher pressure, flows back to the penultimate chamber in the last chamber.
  • this arrangement has the advantage that the development of noise is considerably reduced, because when the last chamber opens towards the pressure side, the pressure equalization is essentially complete. This means that at least 75% of the final pressure is reached by the pre-inlet before the last chamber is opened on the pressure side, preferably 90%.
  • Internal compression is the ratio of the volumes of the chamber closest to the suction side when this chamber is closed and the chamber closest to the pressure side when this chamber is opened. If the cross-sectional shape of the screw spindles is constant over the length, the internal compression is equal to 1.
  • a further possibility for defining the pre-entry according to the invention is contained in claim 2. Then the last chamber on the pressure side, before opening to the pressure side, should be supplied with a pre-inlet volume flow that is greater than 75% of the theoretical suction capacity of this chamber at the time of pre-inlet divided by the internal compression ratio. If the pre-admission extends over a period of considerable length, the point in time at which the pre-admission ends must be taken as a basis. Instead, the mean time between opening and closing the pre-admission can also be used. The volume flow is related to the outlet pressure and the temperature of the gas to be admitted. The theoretical pumping speed is the volume of the chamber at the decisive time multiplied by the speed.
  • the cross section of the pre-inlet opening in mm 2 should be at least as large as the theoretical suction capacity of the assigned chamber in m 3 / h, but preferably twice, more preferably three times as large.
  • the pre-inlet opening that is to say the wall opening which the gas enters the chamber introduces, no narrower cross-sections are upstream that affect the effect of the opening width again.
  • the theoretical pumping speed of the chamber is the product of the volume of this delivery chamber, the number of screw turns and the speed, based on the maximum speed that can be expected in continuous operation.
  • the powerful pre-inlet according to the invention is particularly effective in the last stage when the helical pitch of the rotors is constant, that is to say the compression is theoretically isochoric. But the invention also proves itself with a decreasing gradient, because the gradient is generally never reduced so much that the final pressure is reached in the normal operating point of the pump even without pre-admission in the last stage. Moreover, the invention does not rule out that, in addition to the strong pre-inlet in the last stage, a small pre-inlet is also provided in earlier stages, although in most applications this is unnecessary or even undesirable.
  • the deterioration in the suction capacity of the vacuum pump is negligible if the speed is not too low.
  • the pre-inlet opening is designed as a slot, in which at least the pressure-side boundary edge is formed parallel to the associated displacement screw thread.
  • the slot length should expediently be greater than 1/10 of the rotor diameter, preferably also greater than 1/5. It is expediently on the order of a third of the rotor diameter.
  • the width of the pre-inlet opening in the axial direction is expediently between half and the entire head width (measured in the same direction) of the displacement screw thread. It can even exceed the head width a little, as long as the pre-inlet filling of the last chamber on the pressure side is not endangered by the connection of the pre-inlet opening with the following chamber which is already occurring.
  • the suction edge of the pre-inlet opening can also run parallel to the associated displacement screw. However, it may be more expedient to at least partially incline the boundary on the suction side to the associated one
  • Form displacement screw thread in order to avoid a sudden opening of the pre-inlet opening, which could be associated with undesirable sound generation, in favor of a gradual opening.
  • the aim is for the pre-inlet opening to be closed before the chamber opens on the pressure side.
  • the pre-inlet opening at that rotor position in which the chamber is just opening on the pressure side is just covered by the associated screw thread. This avoids, for example, that a pressure surge entering the chamber from the pressure side penetrates to the pre-inlet opening and drives back heated gas which would reduce the cooling effect during the next pre-inlet process. This also avoids acoustic inconveniences.
  • the pre-inlet opening is already closed when the chamber is opened on the pressure side, provided that it is ensured that the pre-inlet opening is closed in the period of time that the pressure pulse coming from the pressure-side opening of the chamber at the speed of sound would need to reach the pre-inlet opening.
  • the free, axial projection of the pre-inlet opening over the cover edge of the associated screw thread should be smaller than its distance from the end of the screw thread forming the pressure-side opening of the chamber, multiplied by the number of revolutions and divided by the speed of sound.
  • Avoidance of undesirable interaction are provided between pre-admission and pressure side chamber opening (for example, min "1 above 6,000) are present at a high operating speed because at lower velocity these disadvantages speeds less consequence.
  • the pre-inlet is controlled by the interaction of the pre-inlet opening with the top surface of a screw thread. Although this is the preferred embodiment, it should not be ruled out that the pre-inlet opening is preceded by valves which are responsible for the timing of the pre-inlet or, in addition to the screw thread head surface, are jointly responsible.
  • pre-inlet opening or slot does not require the opening to be undivided.
  • an opening can be composed, for example, of a large number of individual bores which are separated from one another by webs.
  • the pre-inlet can take place by appropriately stretching the pre-inlet opening over a larger part of the chamber length.
  • An embodiment is preferred in which the pre-inlet opening, which is composed of a plurality of separate partial openings, extends over at least half the chamber length. It can be up to 270 °.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Coating With Molten Metal (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)
  • Manufacturing Of Printed Circuit Boards (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Non-Positive Displacement Air Blowers (AREA)
  • Glass Compositions (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Press Drives And Press Lines (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

L'invention concerne une pompe à vide à vis comportant au moins trois chambres de refoulement isolées, placées l'une à la suite de l'autre le long de chaque rotor, et un procédé de fonctionnement de ce compresseur. La dernière chambre côté pression est mise pratiquement à la pression finale de compression par préadmission, peu de temps avant son ouverture vers le côté pression. A cet effet est acheminé un flux de préadmission au moins cinq fois supérieur au flux massique d'aspiration, le rapport minimal entre la compression intérieure et extérieure devant être égal à cinq.
EP98934953A 1997-06-11 1998-06-09 Pompe a vide a vis et son procede de fonctionnement Expired - Lifetime EP0988453B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19724643A DE19724643A1 (de) 1997-06-11 1997-06-11 Schraubenverdichter und Verfahren zum Betrieb desselben
DE19724643 1997-06-11
PCT/EP1998/003544 WO1998057067A1 (fr) 1997-06-11 1998-06-09 Pompe a vide a vis et son procede de fonctionnement

Publications (2)

Publication Number Publication Date
EP0988453A1 true EP0988453A1 (fr) 2000-03-29
EP0988453B1 EP0988453B1 (fr) 2003-08-20

Family

ID=7832160

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98934953A Expired - Lifetime EP0988453B1 (fr) 1997-06-11 1998-06-09 Pompe a vide a vis et son procede de fonctionnement

Country Status (13)

Country Link
US (1) US6273696B1 (fr)
EP (1) EP0988453B1 (fr)
JP (1) JP4002304B2 (fr)
KR (2) KR100340166B1 (fr)
AT (1) ATE247780T1 (fr)
CA (1) CA2293618C (fr)
DE (2) DE19724643A1 (fr)
DK (1) DK0988453T3 (fr)
ES (1) ES2206958T3 (fr)
NO (1) NO327604B1 (fr)
PT (1) PT988453E (fr)
WO (1) WO1998057067A1 (fr)
ZA (1) ZA984959B (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100253005A1 (en) * 2009-04-03 2010-10-07 Liarakos Nicholas P Seal for oil-free rotary displacement compressor
JP5478362B2 (ja) * 2010-05-25 2014-04-23 株式会社日立製作所 スクリュー圧縮機
DE102011050018A1 (de) * 2011-04-29 2012-10-31 Allweiler Gmbh Pumpen-System
GB2498816A (en) 2012-01-27 2013-07-31 Edwards Ltd Vacuum pump
DE102015208784B3 (de) * 2015-05-12 2016-09-15 MTU Aero Engines AG Herstellen von Schaufelkanälen von Turbomaschinenrotoren

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3129877A (en) * 1956-05-17 1964-04-21 Svenska Rotor Maskiner Ab Rotary piston, positive displacement compressor
US3138320A (en) * 1959-01-15 1964-06-23 Svenska Roytor Maskiner Aktieb Fluid seal for compressor
DE2544082A1 (de) * 1975-10-02 1977-04-14 Comprotek Sa Drehkolbenmaschine
GB1570512A (en) * 1976-09-04 1980-07-02 Howden Compressors Ltd Meshing-screw gas-compressing apparatus
JPS5468510A (en) * 1977-11-11 1979-06-01 Kobe Steel Ltd Gas leak preventive method for self-lubricating screw compressor
JPS5951190A (ja) * 1982-09-17 1984-03-24 Hitachi Ltd オイルフリ−スクリユ−圧縮機の油切り装置
JPS61265381A (ja) * 1985-05-20 1986-11-25 Hitachi Ltd スクリユ−圧縮機のガス噴射装置
US4768934A (en) * 1985-11-18 1988-09-06 Eaton Corporation Port arrangement for rotary positive displacement blower
JPS6336085A (ja) * 1986-07-30 1988-02-16 Taiko Kikai Kogyo Kk スクリユウ型真空ポンプ
US4812110A (en) * 1986-08-11 1989-03-14 Kabushiki Kaisha Kobe Seiko Sho Oil-free screw compressor with bypass of cooled discharged gas
JPS63106389A (ja) * 1986-10-24 1988-05-11 Hitachi Ltd スクリユ−形真空ポンプの注入装置
DE3775553D1 (de) * 1987-05-15 1992-02-06 Leybold Ag Zweiwellenpumpe.
JPS6412092A (en) * 1987-07-01 1989-01-17 Kobe Steel Ltd Vacuum pump of screw type
US4781553A (en) * 1987-07-24 1988-11-01 Kabushiki Kaisha Kobe Seiko Sho Screw vacuum pump with lubricated bearings and a plurality of shaft sealing means
JP2515831B2 (ja) * 1987-12-18 1996-07-10 株式会社日立製作所 スクリユ―真空ポンプ
KR940000217B1 (ko) * 1989-06-05 1994-01-12 가부시기가이샤 히다찌 세이사꾸쇼 스크류 압축장치 및 그 제어장치
JPH0518381A (ja) * 1991-07-10 1993-01-26 Ebara Corp スクリユー形真空ポンプ
US5269667A (en) * 1993-02-24 1993-12-14 Ingersoll-Rand Company Removabe discharge port plate for a compressor
ATE187528T1 (de) * 1995-06-21 1999-12-15 Sterling Ind Consult Gmbh Mehrstufiger schraubenspindelverdichter

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9857067A1 *

Also Published As

Publication number Publication date
JP4002304B2 (ja) 2007-10-31
DK0988453T3 (da) 2003-12-15
JP2002504205A (ja) 2002-02-05
NO327604B1 (no) 2009-08-31
PT988453E (pt) 2004-01-30
KR20010013692A (ko) 2001-02-26
CA2293618C (fr) 2007-09-18
DE19724643A1 (de) 1998-12-17
ES2206958T3 (es) 2004-05-16
NO996129D0 (no) 1999-12-10
DE59809350D1 (de) 2003-09-25
ZA984959B (en) 1999-04-12
ATE247780T1 (de) 2003-09-15
CA2293618A1 (fr) 1998-12-17
KR100340166B1 (ko) 2002-06-10
WO1998057067A1 (fr) 1998-12-17
KR20010013629A (ko) 2001-02-26
US6273696B1 (en) 2001-08-14
EP0988453B1 (fr) 2003-08-20
NO996129L (no) 1999-12-10

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