EP0902192B1 - Pompe à carter en volute - Google Patents

Pompe à carter en volute Download PDF

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Publication number
EP0902192B1
EP0902192B1 EP98115674A EP98115674A EP0902192B1 EP 0902192 B1 EP0902192 B1 EP 0902192B1 EP 98115674 A EP98115674 A EP 98115674A EP 98115674 A EP98115674 A EP 98115674A EP 0902192 B1 EP0902192 B1 EP 0902192B1
Authority
EP
European Patent Office
Prior art keywords
rib
housing
centrifugal pump
casing
rib parts
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
EP98115674A
Other languages
German (de)
English (en)
Other versions
EP0902192A2 (fr
EP0902192A3 (fr
Inventor
Stephan Dr. Bross
Peter Hergt
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.)
KSB AG
Original Assignee
KSB 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 KSB AG filed Critical KSB AG
Publication of EP0902192A2 publication Critical patent/EP0902192A2/fr
Publication of EP0902192A3 publication Critical patent/EP0902192A3/fr
Application granted granted Critical
Publication of EP0902192B1 publication Critical patent/EP0902192B1/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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers

Definitions

  • the invention relates to a centrifugal pump with a housing of the type Double spiral and with a rib arranged therein as a partition, the rib is formed at least in two parts, with between the rib parts one or more stomata are formed, and a housing spur opposite rib part is for this purpose with a gap opening Distance arranged.
  • a double spiral housing consists of two staggered by 180 ° Spiral halves in which a fluid flowing out of the impeller is collected and is supplied to a common pressure port. Because of the quasi mirror-image arrangement of the two spiral halves arises along one Impeller circumference an approximately symmetrical pressure distribution, the resulting force components cancel each other out.
  • a double spiral casing is created in that a simple spiral housing So-called rib is used as a partition, which is in the direction of rotation of the impeller seen about 180 ° after a spur forms a second spiral half. The Side of the rib facing away from the impeller, the back, limits one Bypass channel through which a fluid collected in the first spiral half in the pressure port is directed.
  • CH-A 219 739 is a rotary conveyor with a spiral housing known, in which the problem was to be solved by inside the housing cross currents to avoid the resulting losses.
  • several partition walls are used in the spiral housing, so Form constant pressure channels.
  • the dimensions of such as constant pressure channels trained guide channels are such that the cross section only in the ratio the loss of speed is changed by the friction. With such Equal pressure channels can, however, have the radial force effect of a double spiral housing not be improved.
  • the invention is therefore based on the problem of developing a double spiral housing which has a good spiral force profile with simple, in particular casting technology, production.
  • the solution to this problem provides that the wrap angle ⁇ of a rib part depending on the number n of rib parts used in the range of 0.7 ⁇ 360 ° 2 * n ⁇ 1.1 ⁇ 360 ° 2 * n lies.
  • the rib parts used can therefore be of the same length or of different lengths.
  • This solution allows for spiral casings, the rib of which is at least in two parts is formed, wherein one or more stomata between the rib parts are trained, a problem-free manufacture of a double spiral housing, the cross section of which can be of any design.
  • the well-known Rectangular, trapezoidal, pear spirals etc. can be used without any problems.
  • the rib By forming the rib as a multi-part component, which is made of at least two spaced apart, one gap opening forming rib parts is a simple placement of the rib parts possible within the spiral and there remains a balanced pressure distribution preserved along the circumference of the impeller. Furthermore, this results in opposite a simple spiral housing an improved radial force curve.
  • Accessibility is improved if the one facing the housing spur Rib part with a gap forming a gap opening is arranged. This measure improves in the area of the double spiral rib parts forming the accessibility to the flow channels created therefrom.
  • One embodiment of the invention provides that the angular position ⁇ of the first rib part, viewed in the direction of flow, relative to the housing spur in the range of 0.8 360 ° n ⁇ 360 ° n ⁇ 1.2 lies. It is then sufficient that the distance and the position of the rib parts from one another is set such that access to the flow channels delimited by the rib parts is ensured by the gap openings existing between the rib parts and between the rib part and the housing current. For this purpose, the distance between the leading edges of the rib parts is set so that sufficiently large stomata are formed in the area of the rib parts.
  • the angular difference of the rib parts ⁇ corresponds to the condition 0.8 ⁇ ⁇ 1.5 ⁇ ⁇
  • the profiles of the rib parts can have the same or different shapes, the rib length having no influence due to the reference to the blade leading edges. It has proven to be advantageous for a further reduction in the radial forces if the leading edges of the rib parts are arranged on circles with diameters D r , the ratios of which to the impeller diameter D 2 are in the range from 1.03 ⁇ D r D 2 ⁇ 1.15 lies.
  • the diameters on which the leading edges of the individual rib parts are arranged do not have to be identical, but the leading edges of the rib parts can be located on different diameters.
  • the radial forces are also reduced in that the leading edge is one of the Rib parts are always arranged on a smaller diameter than one end a rib part in front of it in the direction of flow.
  • the spiral casing is of course designed so that the limited by a rib part Bypass channel does not hinder the outflow of the fluid from the first spiral part or adversely affected.
  • the profile of the rib parts is not subject to any restrictions. It can Rib parts with a constant thickness or a predetermined thickness distribution Find use. It is also possible that the rib parts are different Can have profile shapes. Such a formation of a rib is one Very easy casting production of a double spiral housing possible. It also offers the advantage that such rib parts in a simple manner can be retrofitted. One sees an additional possibility adjustable arrangement of the rib parts in front. Depending on the arrangement of the axis of rotation on the double rib part, these can be used in their angle of attack compared to that from the Impeller emerging flow can be changed.
  • the reduction in radial force has a positive effect the invention also the measure, according to which in the from the housing spur outgoing first quadrant of the double spiral housing compared to one normal spiral development there is an increase in cross-sectional area.
  • the housing 1 shows a housing 1 of a centrifugal pump, in which the outer diameter D 2 is represented by an impeller.
  • the housing 1 is designed here in the manner of a double spiral housing, the first spiral part 3, seen in the direction of flow, starting at the housing spur 4.
  • the housing spur 4 is in the first quadrant, in which a pressure port 5 is also located.
  • the first spiral part 3 has an increasing cross-sectional enlargement, which in this example reaches its maximum at the end of the II. Quadrant. From here, a fluid is led through a bypass channel 6, 7 to the pressure port 5.
  • the bypass duct 6, 7 is delimited by the wall surface of the housing 1 and the wall surface of the rib parts 8, 9 used here. Similar to a double spiral housing, these rib parts 8, 9 form the other or second spiral part.
  • a gap opening 10 located between the rib parts 8, 9 and a gap opening 11 located between the housing spur 4 and the end of the rib part 9 enable access to the bypass channels 6, 7 during the manufacture of the housing can be easily removed and the cast surface plastered.
  • the flow-bearing surfaces can thus be given a roughness, with the aid of which the efficiency of such a pump housing can be improved.
  • the rib parts 8, 9 shown here can have a constant thickness d or, as shown, can be provided with a blade profile the same or different.
  • the rib part 8 is shown longer than the rib part 9.
  • the position of the first rib part 8 seen in the flow direction in relation to the housing spur 4 lying in the first housing quadrant is determined by the angle ⁇ .
  • This angular position ⁇ results according to formula (2).
  • the distance ⁇ shown in FIG. 1 between the leading edges 12, 13 of the rib parts 8, 9 is defined by the formula (3) listed above.
  • the leading edges 12, 13 of the rib parts 8, 9 lie on circles with a diameter D r , the ratio of which to the impeller diameter D 2 according to Formula 4 is in the range of 1.03 ⁇ D r D 2 ⁇ 1.15 lies.
  • Quadrant of the housing 1 arranged rib part 8 is shorter here, while the rib part 9 located in the fourth quadrant has a greater overall length.
  • a measure, which is shown here in the first quadrant of the housing 1, also has a positive effect on a reduction in the radial force.
  • An enlargement of the spiral cross section in this area, which increases compared to normal spiral development, is shown here by a broken line.
  • the housing spur 4 is also at a greater distance from the outer diameter D 2 of an impeller.
  • the cross-sectional area enlargement 14 in the first quadrant of the spiral housing and the position of the rib parts 8, 9 in relation to one another and on the housing spur 4 are adapted to the hydraulics of an impeller used in each case and the respective spiral shape. This allows radial force reductions to be achieved which correspond to the radial force curve of a traditional double spiral design. With the aid of variations in relation to the position of the leading edges 12, 13, the shape and the size of the rib parts 8, 9, it is possible to influence the course of the radial force.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (6)

  1. Pompe centrifuge comprenant un carter du type en double volute et comprenant une nervure disposée dans celui-ci, réalisée en tant que paroi de séparation, la nervure étant réalisée au moins en deux parties, une ou plusieurs ouvertures en forme de fente (10) étant réalisées entre les parties de nervure (8, 9), et une partie de nervure (9) opposée à un éperon du carter (4) étant disposée à cet effet avec un espace formant une ouverture en forme de fente (11), caractérisée en ce que l'angle d'enveloppement (ϕ) d'une partie de nervure (8, 9) se situe, en fonction du nombre n des parties de nervure utilisées (8, 9), dans la plage de 0,7·360°2·n ≤ϕ≤1,1·360°2·n
  2. Pompe centrifuge selon la revendication 1, caractérisée en ce que la position angulaire (τ) de la première partie de nervure (8) vue dans la direction de l'écoulement, se situe, par rapport à l'éperon du carter (4), dans la plage de 0,8·360° n ≤τ≤360° n ·1,2
  3. Pompe centrifuge selon la revendication 1 ou 2, caractérisée en ce qu'une différence angulaire Δτ entre les arêtes d'attaque (12, 13) des parties de nervure (8, 9), définissant la taille des ouvertures en forme de fente (10, 11), correspond à la relation 0,8·ϕ≤Δτ≤1,5·ϕ
  4. Pompe centrifuge selon l'une quelconque des revendications 1, 2 ou 3, caractérisée en ce que les arêtes d'attaque (12, 13) des parties de nervure (8, 9) sont disposées sur des cercles ayant des diamètres (Dr) connus en soi identiques ou différents, le rapport des diamètres Dr au diamètre du rotor D2 étant situé dans la plage de 1,03≤ Dr D 2 ≤1,15
  5. Pompe centrifuge selon l'une quelconque des revendications 1 à 4, caractérisée en ce que les parties de nervure (8, 9) sont disposées de manière déplaçable dans le carter en double volute.
  6. Pompe centrifuge selon l'une quelconque des revendications 1 à 5, caractérisée en ce qu'il se produit une augmentation de la surface en section transversale (14) dans le premier quart I partant de l'éperon (4) du carter en double volute, par rapport à un développement en volute normal.
EP98115674A 1997-09-15 1998-08-20 Pompe à carter en volute Expired - Lifetime EP0902192B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19740590 1997-09-15
DE19740590A DE19740590A1 (de) 1997-09-15 1997-09-15 Spiralgehäusepumpe

Publications (3)

Publication Number Publication Date
EP0902192A2 EP0902192A2 (fr) 1999-03-17
EP0902192A3 EP0902192A3 (fr) 1999-07-14
EP0902192B1 true EP0902192B1 (fr) 2003-06-11

Family

ID=7842447

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98115674A Expired - Lifetime EP0902192B1 (fr) 1997-09-15 1998-08-20 Pompe à carter en volute

Country Status (5)

Country Link
US (1) US6146095A (fr)
EP (1) EP0902192B1 (fr)
AT (1) ATE242845T1 (fr)
BR (1) BR9803538A (fr)
DE (2) DE19740590A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0415301D0 (en) * 2004-07-08 2004-08-11 Weir Pumps Ltd Pump casing
DE202005004180U1 (de) * 2005-03-14 2006-07-27 Ebm-Papst Landshut Gmbh Radialgebläse
AU2009215837B2 (en) * 2008-02-22 2014-06-05 Horton, Inc. Fan manufacturing and assembly
CA2703855C (fr) * 2009-07-31 2018-12-11 Rem Enterprises Inc. Pompe a vide d'air perfectionnee pour chargeuse de particules et appareillage de transfert
CN102080671B (zh) * 2009-11-27 2015-05-13 德昌电机(深圳)有限公司 离心泵
BR112012028455A8 (pt) * 2010-05-07 2017-03-01 Sulzer Pumpen Ag Invólucro de bomba em formato de voluta com nervura divisora
US9222484B2 (en) 2012-04-27 2015-12-29 Weir Minerals Australia, Ltd. Centrifugal pump casing with offset discharge
EP2954214B1 (fr) * 2013-02-08 2021-03-03 Sulzer Management AG Turbomachine et élément de guidage d'écoulement pour une turbomachine
JP6989492B2 (ja) 2015-09-03 2022-01-05 フルイド ハンドリング リミティド ライアビリティ カンパニー 低い製造コスト及び半径方向負荷低減のためのボリュートデザイン
CN105243222B (zh) * 2015-10-27 2018-08-31 湖南湘电长沙水泵有限公司 将铸造导叶改成焊接导叶的设计方法、焊接导叶及导叶体
CN108843619B (zh) * 2018-06-28 2020-05-22 西安交通大学 一种离心泵的双蜗壳结构
CN112483417B (zh) * 2020-12-14 2022-12-27 万载志成实业有限公司 一种用于硒银金生产工艺的循环泵
US11873837B1 (en) * 2021-08-02 2024-01-16 W.S. Darley & Co. Centrifugal pumps, casings and vehicles using the same

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR323504A (fr) * 1902-08-05 1903-03-07 Schaaf Wilhelm Perfectionnements aux pompes centrifuges et ventilateurs
CH219739A (de) * 1941-01-16 1942-02-28 Oerlikon Maschf Kreiselfördermaschine mit Spiralgehäuse.
US2399548A (en) * 1944-05-05 1946-04-30 Kalasign Company Centrifugal pump
FR1076154A (fr) * 1951-12-15 1954-10-25 Corps de pompe centrifuge établi en tôle
US2955540A (en) * 1957-05-27 1960-10-11 Worthington Corp Twin volute pump
US3289598A (en) * 1965-10-21 1966-12-06 Ingersoll Rand Co Centrifugal pumps
FR2102520A5 (fr) * 1970-08-06 1972-04-07 Unelec
SU623006A1 (ru) * 1977-04-21 1978-09-05 Предприятие П/Я А-7075 Центробежный нагнетатель
DE3001598C2 (de) * 1980-01-17 1983-03-17 Dietrich Dr.-Ing. 5440 Mayen Haase Radialventilator
DE3001868C2 (de) * 1980-01-19 1984-01-19 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Kreiselpumpe mit Doppelspiralgehäuse
EP0212834B1 (fr) * 1985-07-17 1990-11-14 Geoffrey Light Wilde Admission variable pour une turbine radiale

Also Published As

Publication number Publication date
ATE242845T1 (de) 2003-06-15
BR9803538A (pt) 1999-11-23
DE19740590A1 (de) 1999-03-18
EP0902192A2 (fr) 1999-03-17
EP0902192A3 (fr) 1999-07-14
US6146095A (en) 2000-11-14
DE59808677D1 (de) 2003-07-17

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