EP0451085B1 - Pompe à rotors à vis - Google Patents

Pompe à rotors à vis Download PDF

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Publication number
EP0451085B1
EP0451085B1 EP91710004A EP91710004A EP0451085B1 EP 0451085 B1 EP0451085 B1 EP 0451085B1 EP 91710004 A EP91710004 A EP 91710004A EP 91710004 A EP91710004 A EP 91710004A EP 0451085 B1 EP0451085 B1 EP 0451085B1
Authority
EP
European Patent Office
Prior art keywords
spindle
pressure
screw rotor
rotor pump
angle
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
EP91710004A
Other languages
German (de)
English (en)
Other versions
EP0451085A2 (fr
EP0451085A3 (en
Inventor
Rolf Dipl.-Ing. Quast
Klaus Dipl.-Ing. Willibald
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.)
Allweiler GmbH
Original Assignee
Allweiler AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6401666&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0451085(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Allweiler AG filed Critical Allweiler AG
Priority to EP96105318A priority Critical patent/EP0727581B1/fr
Publication of EP0451085A2 publication Critical patent/EP0451085A2/fr
Publication of EP0451085A3 publication Critical patent/EP0451085A3/de
Application granted granted Critical
Publication of EP0451085B1 publication Critical patent/EP0451085B1/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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels

Definitions

  • the invention relates to a screw pump with a Drive spindle and at least one spindle according to the preamble of claim 1.
  • EP-A-209 984 can be one Screw pump can be removed, the drive spindle with their cantilevered thread in thread formations of some Spindles engages and form several tight chambers should.
  • at least one is circumferential Channel provided around the periphery of the spindles so that the last of the tight chambers at an outlet with this - short its release by the chamber - partly via the canal communicates.
  • US-A-29 22 377 indicates as an error Screw pumps have a high pressure, temperature and Noise development as a result of the discharge closed pockets. Then one is described Drive spindle with itself at an angle of, for example 30 ° tapering cross-section at the end of the print in the area of a adapted desk surface of the housing. This arrangement is said to those closed pockets by making one Prevent sealing edge over the entire length of the spindle.
  • FR-A-799903 describes a liquid pump with a Drive spindle and a spindle, which in one Recess of a surrounding housing between one Pressure chamber and two suction rooms flanking these are.
  • the spindle gears are as sliding partitions disclosed, between each of which a pump chamber is formed. These partitions move away Pressure chamber gradually from the surrounding housing wall, so that the tightness of a pump chamber in relation to Pressure space is reduced.
  • That outer wall and that inner partitions move away towards the pressure side the pump from each other at individual points or on the entire length, and the tightness of the pump chamber / s decreases towards the pressure chamber gradually in the direction of the latter is the eight-shaped wall at the outer end of one or each individual turn of the spindle gear completely or partly cut out in a funnel shape, or - differently said - the cylindrical interface of one or both Coils have a conical shape.
  • a screw pump leads to the solution of this task according to the teaching of patent claim 1;
  • the conical surface of the Outer diameter of the pressure side, conically turned Profile outlet of the spindle has one and the Inclination angle below 10 °.
  • Of particular importance for the reduction in pulsation is extremely flat Conical surface with an inclination angle of less than 5 °, preferred even below 3 °.
  • This bevel on the pressure side causes the appropriate Point in time a gradual and defined opening of the pressure-side chamber takes place; so that through the Closing the suction side resulting volume flow or Pressure increase can be largely compensated.
  • the Initial pulsation is significantly reduced.
  • this can also be done suction-side profile end with such a flat Be conical surface provided, however, the axial Length of the last-mentioned conical surface should be less than the axial length of the pressure-side cone surface.
  • the housing 12 is both on the pressure side and on the suction side Formation of a pressure chamber 20 and a suction chamber 22 each with a pump cover 25 or 24 closed.
  • the through the pressure-side pump cover 25 guided drive spindle 14 is in Area of a through hole 26 with an axial thrust compensation piston 28 provided and with a bearing 30 in one Lid attachment 32 additionally supported. In the latter there is also a shaft seal 34.
  • the interior 36 of the lid attachment 32 is from the delivery pressure relieved; the liquid entering from the pressure chamber 20 is over discharged a relief channel 38, which via a Connection bore 40 of the housing 12 in the suction chamber 22 flows into.
  • Fig. 2 shows that the drive spindle 14 - the profile length - is turned conically at their ends, wherein the length of the pressure-side taper 42 e, the length of the with that end face 44 by an amount i protruding suction cone 42 s with e l , the remaining cylinder length of the drive spindle 14 between the conical surfaces 43, 43 s with q, the pitch angle of the thread 15 of the drive spindle 14 - or the spindle 16 - only partially indicated in FIG. 2 - with t and the pitch with s are.
  • the pressure-side cone angle w or the suction-side cone angle w l is preferably 2 °.
  • the length adjustment of the entire system is chosen so that during part of the funding period in FIG. 3 reproduced more of sealing lines is generated; this means, an increase from Qvmax to Qvmin.
  • the pulsation pattern is thus changed by attaching the described conical surface 43 to the pressure-side spindle end, which leads to a decrease in Qv and -Q kom .
  • the extension of the cross-sectionally inclined conical surface 43 has the effect that, on the one hand, the pressure side opens earlier, and on the other hand, the cross-sections become continuously larger during opening. It may be sufficient to provide the pressure side with the cone 42 and to leave the spindle end on the suction side cylindrical.
  • the operating system for the three-spindle screw pump 10 shown can be described as follows: On the basis of a certain number of chambers n, which is a measure of the internal pressure build-up in the pump, the ratio of length to slope - ie a / s - represents an analogue quantity for the geometric implementation; the greater this ratio, the smaller the pressure increase per unit length.
  • a 1 + (2. N -1).
  • the pre-factor x is a measure of the pre-compression, which in the other only depending on the profile for values above 0.1 - 0.15 occurs.
  • the pressure-side cone must 42 to that dimension x - that is, to the pre-compression achieved - be coordinated.
  • the length e chosen such that for the normal case
  • the cone 42 s on the suction side generally allows the closing characteristic to be adapted, as is shown at A 'in FIG. 2.
  • This cone 42 s must be precisely matched to the pressure-side cone 42 on the basis of a defined length ratio a / s.
  • the length e l of the cone 42 s is expediently chosen to be smaller than the length e of the other cone 42.
  • the length e of the pressure-side cone 42 is to be made smaller overall.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Supercharger (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (5)

  1. Pompe à rotors à vis comprenant une broche d'entraínement et au moins une broche à rotation libre, qui sont montées à rotation dans une cavité d'un boítier les entourant entre un espace d'aspiration et un espace de pression, la fin du profilé du côté sous pression présentant une forme conique de tournage sur le diamètre extérieur, caractérisée en ce que l'angle d'inclinaison (w) de la surface conique (43) de la broche (14, 16) est inférieur à 10°.
  2. Pompe à rotors à vis selon la revendication 1, caractérisée en ce que la broche (14, 16) comporte à son extrémité du côté aspiration une surface conique (43s) présentant un angle d'inclinaison (wl).
  3. Pompe à rotors à vis selon la revendication 1 ou 2, caractérisée en ce que l'angle d'inclinaison (w, wl) est inférieur à 5°.
  4. Pompe à rotors à vis selon la revendication 1 ou 2, caractérisée en ce que l'angle d'inclinaison (w, wl) est inférieur à 3°.
  5. Pompe à rotors à vis selon la revendication 1 et 2, caractérisée en ce que la longueur axiale (e) de la surface conique (43) du côté en pression est supérieure à la longueur axiale (el) de la surface conique (43s) du côté aspiration.
EP91710004A 1990-03-08 1991-03-07 Pompe à rotors à vis Expired - Lifetime EP0451085B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP96105318A EP0727581B1 (fr) 1990-03-08 1991-03-07 Pompe à rotors à vis

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4007273 1990-03-08
DE4007273 1990-03-08

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP96105318A Division EP0727581B1 (fr) 1990-03-08 1991-03-07 Pompe à rotors à vis

Publications (3)

Publication Number Publication Date
EP0451085A2 EP0451085A2 (fr) 1991-10-09
EP0451085A3 EP0451085A3 (en) 1992-07-08
EP0451085B1 true EP0451085B1 (fr) 1998-08-12

Family

ID=6401666

Family Applications (2)

Application Number Title Priority Date Filing Date
EP96105318A Expired - Lifetime EP0727581B1 (fr) 1990-03-08 1991-03-07 Pompe à rotors à vis
EP91710004A Expired - Lifetime EP0451085B1 (fr) 1990-03-08 1991-03-07 Pompe à rotors à vis

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP96105318A Expired - Lifetime EP0727581B1 (fr) 1990-03-08 1991-03-07 Pompe à rotors à vis

Country Status (6)

Country Link
US (1) US5123821A (fr)
EP (2) EP0727581B1 (fr)
JP (1) JP3036874B2 (fr)
KR (1) KR0177815B1 (fr)
AT (2) ATE169721T1 (fr)
BR (1) BR9100993A (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI104440B (fi) * 1995-06-22 2000-01-31 Kone Corp Ruuvipumppu ja ruuvipumpun ruuvi
US6623262B1 (en) 2001-02-09 2003-09-23 Imd Industries, Inc. Method of reducing system pressure pulsation for positive displacement pumps
GB0226529D0 (en) * 2002-11-14 2002-12-18 Dana Automotive Ltd Pump
US8096288B2 (en) * 2008-10-07 2012-01-17 Eaton Corporation High efficiency supercharger outlet
DE102017210767B4 (de) 2017-06-27 2019-10-17 Continental Automotive Gmbh Schraubenspindelpumpe, Kraftstoffförderaggregat und Kraftstofffördereinheit

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2652192A (en) * 1947-06-13 1953-09-15 Curtiss Wright Corp Compound-lead screw compressor or fluid motor
US2952216A (en) * 1956-03-13 1960-09-13 Wildhaber Ernest Rotary screw unit for displacing fluid
US2922377A (en) * 1957-09-26 1960-01-26 Joseph E Whitfield Multiple arc generated rotors having diagonally directed fluid discharge flow
CH390690A (de) * 1959-02-23 1965-04-15 Imo Industri Ab Schraubenpumpe
FR1243471A (fr) * 1959-08-31 1960-10-14 Perfectionnements aux rotors pour pompes, moteurs, compresseurs, ventilateurs, compteurs et autres dispositifs similaires
US3103894A (en) * 1960-02-18 1963-09-17 Laval Turbine Screw pump
DE2033201C3 (de) * 1970-07-04 1979-02-01 Allweiler Ag Schraubenspindelmotor oder -pumpe
SE383774B (sv) * 1975-04-02 1976-03-29 Imo Industri Ab Skruvpump
JPS5238615A (en) * 1975-09-22 1977-03-25 Mayekawa Mfg Co Ltd Screw compressor
JPS5936116B2 (ja) * 1976-08-07 1984-09-01 株式会社荏原製作所 流体機械
FR2538463B1 (fr) * 1982-12-23 1985-06-21 Dba Machine volumetrique a vis coniques
JPS61294178A (ja) * 1985-06-24 1986-12-24 Kawasaki Heavy Ind Ltd ねじポンプ
DE3815158A1 (de) * 1988-05-04 1989-11-16 Allweiler Ag Verfahren zur verringerung der druckpulsation einer verdraengerpumpe, insbesondere einer schraubenspindelpumpe und eine danach ausgefuehrte schraubenspindelpumpe

Also Published As

Publication number Publication date
EP0451085A2 (fr) 1991-10-09
US5123821A (en) 1992-06-23
EP0451085A3 (en) 1992-07-08
KR910017081A (ko) 1991-11-05
EP0727581B1 (fr) 1999-02-10
BR9100993A (pt) 1991-11-05
ATE169721T1 (de) 1998-08-15
ATE176717T1 (de) 1999-02-15
EP0727581A1 (fr) 1996-08-21
JPH05231341A (ja) 1993-09-07
JP3036874B2 (ja) 2000-04-24
KR0177815B1 (ko) 1999-04-15

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