EP0405160A1 - Pompe à rotors hélicoidaux - Google Patents

Pompe à rotors hélicoidaux Download PDF

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Publication number
EP0405160A1
EP0405160A1 EP90110215A EP90110215A EP0405160A1 EP 0405160 A1 EP0405160 A1 EP 0405160A1 EP 90110215 A EP90110215 A EP 90110215A EP 90110215 A EP90110215 A EP 90110215A EP 0405160 A1 EP0405160 A1 EP 0405160A1
Authority
EP
European Patent Office
Prior art keywords
bearing
screw pump
spindles
spindle
interior
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
EP90110215A
Other languages
German (de)
English (en)
Other versions
EP0405160B1 (fr
Inventor
Wolfgang Dipl.-Ing. Leiber (Fh)
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
Application filed by Allweiler AG filed Critical Allweiler AG
Priority to AT90110215T priority Critical patent/ATE92594T1/de
Publication of EP0405160A1 publication Critical patent/EP0405160A1/fr
Application granted granted Critical
Publication of EP0405160B1 publication Critical patent/EP0405160B1/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
    • 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
    • F04C2/086—Carter
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps 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
    • F04C2/16—Rotary-piston machines or pumps 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
    • F04C2/165—Rotary-piston machines or pumps 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 having more than two rotary pistons with parallel axes

Definitions

  • the invention relates to a screw pump with a drive spindle arranged in the interior of a pump housing and at least one sealing spindle parallel to the axis, and with an inlet and an outlet for a flow medium to be conveyed by the spindles.
  • At least the sealing spindle is equipped with a peg-like bearing end and is preferably mounted in the pump cover.
  • Such a screw pump with two sealing or running spindles flanking the drive spindle can be found, for example, in DE-PS 716 161; the bearing recesses for all spindles are located in the pump cover and connected to the interior of the pump housing.
  • the temperature conditions, particularly in the spindle area, are of particular importance for the operation of such screw pumps, which is why the aim of this invention is to make the temperature uniform over the length of the pump rotor.
  • the temperature conditions, particularly in the spindle area, are of particular importance for the operation of such screw pumps, which is why the aim of this invention is to make the temperature uniform over the length of the pump rotor.
  • the spindles are surrounded by a tubular housing insert and this, with the pump housing surrounding it, delimits at least one annular space which is connected to the interior receiving the spindles by at least one opening.
  • the annular space on the suction side against the interior and to provide the radial openings at its pressure-side end.
  • the outlet should be provided at the suction-side end of the annular space.
  • an inlet on the suction side is preferably arranged outside the housing insert in the radial region of the bearing of the spindles.
  • the housing insert according to the invention is easy to manufacture and assemble. It can also be easily fitted with low-wear inserts on the inside.
  • the free end face of the bearing bush with the bottom of the recess of the pump cover delimits a tight gap space connected to the interior of the screw pump, which is preferably connected to an extension of the interior via a radial line.
  • the profile outlet of the sealing spindle is surrounded by a compensating bush, which strikes the shoulder of the sealing spindle with its pressure-side end.
  • This compensating sleeve - which forms a control edge with its suction-side end - is adjoined by a shell made of low-wear material which is fixed in the bearing sleeve and which advantageously projects beyond the end face of the bearing journal; an end gap connected to the pressure chamber is desired between the end face of the bearing journal and the bottom of the bearing recess.
  • the end gaps of the bearing journals should advantageously be connected to a transverse line by means of at least one line passing through the bearing bush. It has proven to be expedient to let a bore emanate from the bottom of the bearing bush, which bore connects to a sleeve penetrating that gap as part of the line.
  • the pressure supply in the bearing bushes is sealed, but the bearing bushes themselves can be moved radially.
  • the screw pump which is usually designed for lubricating fluids, at a function-critical point - in particular the hydrostatic axial thrust compensation, for example also when pumping water.
  • the specific arrangement of cylindrical bearing bodies or bearing bushes into which the spindles are immersed up to a radial stop serves this purpose.
  • the bearing body or bushing has an axial opening that connects the storage space - in which the spindle pin is immersed - with the pressure chamber of the pump.
  • the connection of the pressure-carrying connection of the bearing sleeve is designed so that the fluid pressure is effective only on the cross section of the spindle pin.
  • a minimal axial movement across the gap between the spindle and the axial collar can balance the axial thrust and hydraulic relief.
  • the introduction of the pump pressure to compensate for the axial thrust is designed so that the pressure can be concentrated on only for the purpose described above.
  • the bearing sleeve should move radially freely, ie be able to continuously adapt to the radial movement of the spindle.
  • a non-positive rotation inhibition for example in the form of an elastic ring element, ensures that the bearing bush does not rotate, since otherwise the necessary seal between the bearing body and the pressure-carrying connection or line would not be provided.
  • a screw pump 10 has, in the interior 12 of a pump housing 14 screwed onto a pump base 11, a drive spindle 18 flanked by two sealing or running spindles 16.
  • the sealing or running spindles 16 are mounted on the suction side in a pump cover 20, the drive spindle 18 is connected on the drive side to a coaxial drive shaft journal 22.
  • the drive shaft journal 22 passes through roller bearings 28 arranged in a bearing cover 24 - between a labyrinth ring 25 and a support disk 26 with a downstream lubrication chamber 27. That bearing cover 24 is connected to a drive-side pump cover 31 by means of cylinder screws 29 and with the interposition of a mechanical seal 30, 34, wherein the mechanical seal 30, 34 lies in a seal space 32.
  • a compensating piston 36 surrounded by low-wear shells 35 and provided with throttle grooves can be recognized on a flange 38. This rests partly in the pump cover 31 and partly in the pump housing 14, the length a of which is approximately 270 mm.
  • a compensating bushing 40 of length n which abuts a shoulder-like shoulder 42 of the spindle 16, is shrunk onto the suction-side bearing journal 17 of the two running spindles 16.
  • This compensating bushing 40 faces with its suction-side end a bearing recess 44 of a bearing body or a bearing bush 46 and forms a control edge there for regulating the hydrostatic pressure.
  • the control edge here lies opposite the edge of a shell 41 seated in the bearing recess 44 and made of particularly wear-resistant material.
  • the length t of the shell 41 is greater than the free length of the bearing pin 17 and thus determines the width of an end gap 48 remaining between the suction-side end face 17 s of the bearing pin 17 and the bottom 45 of the bearing recess 44.
  • An axial inlet bore 50 of the bearing bush opens into this 46; this inlet bore 50 is connected to a channel 54 of the suction-side pump cover 20 by means of a sleeve 53, which has an axial bore 52; the channels 54 of the spindle bearings are connected to one another by a blind bore 56 provided radially in the pump cover 20.
  • FIG. 1 shows that said sleeve 53 bridges a gap space 58 of the 46 one hand, between the suction-side end of the bearing bush and the bottom of a pump cover 20 is formed 60 of a blind recess 58 receiving the same.
  • This gap space 58 is connected via radial bores 59 to a cylindrical extension 13 of the interior 12 of the pump housing 14.
  • an O-ring 62 can be seen as a sealant in the periphery of the bearing bush 46 - other O-rings respectively provided in ring grooves are also designated by 62.
  • the pump housing 14 is designed such that a tubular housing insert 64 surrounding the spindles 16, 18 of length b of, for example, 190 mm rests on both ends of housing ribs 66, 66 s in such a way that an annular space 15 is formed between the housing insert 64 and the pump housing 14 suction-side housing rib 66 s is sealed to the interior 12 by means of an O-ring 62 and has passages 68 in the area of the other housing rib 66. Otherwise, the housing insert 64 is held with its pressure-side edge 64 d between the housing rib 66 and the flange 38.
  • Material inserts 70 made of wear-resistant - preferably ceramic - material are provided between the housing insert 64 and the spindles 16, 18.
  • the material inserts 70 are in themselves disk-like and are provided with receiving bores (not shown for reasons of clarity) for the spindles 16, 18 passing through them.
  • Several of these material inserts 70 are arranged coaxially in the pump housing 14.
  • the material inserts 70 are fixed by means of a plastic layer indicated at 71, which is introduced through bores 72 between the housing insert 64 and the material insert 70.
  • the described annular space 15 is - as can be seen in FIG. 1 - connected to the blind bore 56 of the pump cover 20 by means of an axially parallel longitudinal bore 74 in the pump housing 14.
  • FIG. 2 shows the suction space inlet 76 and - at the deepest of the annular space 15 - the outlet 78; between the two lies that housing insert 64, so that the fluid between the suction chamber inlet 76 and the outlet 78 is forced to flow through the passage 68 of the housing insert 64 into the annular space 15 and over almost the entire length b of the housing insert 64 to the outlet 78.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP90110215A 1989-06-26 1990-05-30 Pompe à rotors hélicoidaux Expired - Lifetime EP0405160B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90110215T ATE92594T1 (de) 1989-06-26 1990-05-30 Schraubenspindelpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3920900A DE3920900A1 (de) 1989-06-26 1989-06-26 Schraubenspindelpumpe
DE3920900 1989-06-26

Publications (2)

Publication Number Publication Date
EP0405160A1 true EP0405160A1 (fr) 1991-01-02
EP0405160B1 EP0405160B1 (fr) 1993-08-04

Family

ID=6383606

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90110215A Expired - Lifetime EP0405160B1 (fr) 1989-06-26 1990-05-30 Pompe à rotors hélicoidaux

Country Status (3)

Country Link
EP (1) EP0405160B1 (fr)
AT (1) ATE92594T1 (fr)
DE (2) DE3920900A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0870929A3 (fr) * 1997-04-11 1998-11-04 Leistritz Aktiengesellschaft Ascensseur à cable sous commande hydraulique
WO2006128441A1 (fr) * 2005-06-02 2006-12-07 Joh. Heinr. Bornemann Gmbh Pompe a broches helicoidales
CN104863847A (zh) * 2014-02-25 2015-08-26 莱斯特里兹泵有限责任公司 螺旋心轴泵
WO2021001204A1 (fr) * 2019-07-04 2021-01-07 Nidec Gpm Gmbh Pompe à vis à liquide de refroidissement intégrée
EP4095384A1 (fr) * 2021-05-27 2022-11-30 Jung & Co. Gerätebau GmbH Pompe à broche hélicoïdale de construction en simple flux
EP4198309A1 (fr) * 2021-12-14 2023-06-21 Leistritz Pumpen GmbH Pompe à vis

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103758758B (zh) * 2014-01-17 2015-11-25 西安交通大学 一种交流伺服直驱型电液泵
DE102020133555A1 (de) 2020-12-15 2022-06-15 Leistritz Pumpen Gmbh Schraubenspindelpumpe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB578057A (en) * 1944-04-05 1946-06-13 Stothert & Pitt Ltd Improvements in screw displacement pumps
US2592476A (en) * 1948-02-07 1952-04-08 Laval Steam Turbine Co Series arrangement of positive and nonpositive screw pumps
US2873909A (en) * 1954-10-26 1959-02-17 Svenska Rotor Maskiner Ab Rotary devices and casing structures therefor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1245458A (fr) * 1959-02-04 1960-11-04 Imo Industri Ab Pompe à engrenages hélicoïdaux
DE2520667C2 (de) * 1975-05-09 1984-11-29 Allweiler Ag, 7760 Radolfzell Schraubenspindelpumpe
DE3737358A1 (de) * 1987-11-04 1989-05-18 Allweiler Ag Laufgehaeuse fuer eine innengelagerte schraubenspindelpumpe und verfahren zu seiner herstellung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB578057A (en) * 1944-04-05 1946-06-13 Stothert & Pitt Ltd Improvements in screw displacement pumps
US2592476A (en) * 1948-02-07 1952-04-08 Laval Steam Turbine Co Series arrangement of positive and nonpositive screw pumps
US2873909A (en) * 1954-10-26 1959-02-17 Svenska Rotor Maskiner Ab Rotary devices and casing structures therefor

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0870929A3 (fr) * 1997-04-11 1998-11-04 Leistritz Aktiengesellschaft Ascensseur à cable sous commande hydraulique
WO2006128441A1 (fr) * 2005-06-02 2006-12-07 Joh. Heinr. Bornemann Gmbh Pompe a broches helicoidales
JP2008542605A (ja) * 2005-06-02 2008-11-27 ヨハン・ハインリヒ・ボーネマン・ゲーエムベーハー スクリューポンプ
DE102005025816B4 (de) * 2005-06-02 2010-06-02 Joh. Heinr. Bornemann Gmbh Schraubenspindelpumpe
US7862315B2 (en) 2005-06-02 2011-01-04 Joh.Heinr.Bornemann Gmbh Screw displacement pump
KR101158957B1 (ko) * 2005-06-02 2012-06-21 조.하인리히 보르네만 게엠베하 나사 스핀들 펌프
NO337323B1 (no) * 2005-06-02 2016-03-07 Itt Bornemann Gmbh Skruepumpe
CN104863847A (zh) * 2014-02-25 2015-08-26 莱斯特里兹泵有限责任公司 螺旋心轴泵
WO2021001204A1 (fr) * 2019-07-04 2021-01-07 Nidec Gpm Gmbh Pompe à vis à liquide de refroidissement intégrée
EP4095384A1 (fr) * 2021-05-27 2022-11-30 Jung & Co. Gerätebau GmbH Pompe à broche hélicoïdale de construction en simple flux
EP4198309A1 (fr) * 2021-12-14 2023-06-21 Leistritz Pumpen GmbH Pompe à vis

Also Published As

Publication number Publication date
EP0405160B1 (fr) 1993-08-04
ATE92594T1 (de) 1993-08-15
DE3920900A1 (de) 1991-01-03
DE59002169D1 (de) 1993-09-09

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