EP0443354A1 - Pompe centrifuge - Google Patents

Pompe centrifuge Download PDF

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Publication number
EP0443354A1
EP0443354A1 EP91101345A EP91101345A EP0443354A1 EP 0443354 A1 EP0443354 A1 EP 0443354A1 EP 91101345 A EP91101345 A EP 91101345A EP 91101345 A EP91101345 A EP 91101345A EP 0443354 A1 EP0443354 A1 EP 0443354A1
Authority
EP
European Patent Office
Prior art keywords
flow
impeller
centrifugal pump
pressure
housing
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
EP91101345A
Other languages
German (de)
English (en)
Other versions
EP0443354B1 (fr
Inventor
Karlheinz Becker
Gunter Pfeiffer-Müller
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 EP0443354A1 publication Critical patent/EP0443354A1/fr
Application granted granted Critical
Publication of EP0443354B1 publication Critical patent/EP0443354B1/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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/428—Discharge tongues
    • 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

Definitions

  • the invention relates to a centrifugal pump according to the preamble of the main claim.
  • a semi-axial impeller for energy conversion is followed by a stator, from which the pumped medium enters a pipe bend (44), which in turn opens into a pressure port that radially emerges from the outer housing.
  • the pumped medium must first flow through the stator and then flow around an inner housing arranged within the outer housing and receiving the shaft bearing. This complex construction has a low efficiency due to the flow.
  • AT-PS 347 268 shows a pump of axial or semi-axial type.
  • An inner housing carrying the pump shaft and the impeller is arranged in an outer housing with an axial suction nozzle and a radial pressure nozzle.
  • the inner casing referred to in the document as a support tube has a cross-section which increases steadily from the impeller outlet to the pressure port.
  • Between the inner housing and the outer housing there is also a deflection plate which interacts with flow channels incorporated in the outer housing and has a wedge opposite the diffuser outlet.
  • a flow emerging from the impeller is directed in the downstream guide apparatus and flows almost axially parallel into the space between the inner and outer housing.
  • the wedge of the deflection plate is arranged on the side opposite the pressure port, and the wedge on the side remote from the pressure port Leaving conveying medium on the side of the diffuser into two partial streams and feeds them around the inner housing to the pressure port.
  • two flow channels are incorporated in the outer housing for low-loss flow control. As a result, there is a difficult to create outer housing with bulges on the side remote from the pressure port.
  • the diffuser and the deflection plate increase the overall length of the pump considerably.
  • a ball housing for reactor pumps is known in which the inflow and outflow space are arranged in the same housing. Are inside the ball housing, such as. B. Fig. 7 shows, arranged in the inlet flow control elements.
  • the outflow chamber also has corresponding components.
  • the invention is based on the object of developing a housing design for a centrifugal pump of the generic type which, with the smallest dimensions, has an efficiency-optimized guide device arranged downstream of the impeller. This object is achieved in accordance with the characterizing part of the main claim.
  • the conveying medium flowing out of the impeller flows with very little losses into the space located behind the impeller and having one or more flow-guiding elements.
  • a corresponding number of elements are used in accordance with the number of pressure ports. If there is only one pressure nozzle, shock losses only occur at the leading edge of an element.
  • the mode of operation of the wall surface of the element which extends from the leading edge in the flow direction is comparable to a spiral space which increases in the axial direction.
  • the thread flanks extend with a slope in the longitudinal direction; in the subject of the invention with a slope in the direction of the pump shaft. Due to the offset of the inflow edge and / or inflow surface laterally with respect to the center of the pressure nozzle, the flow-like guidance to the pressure nozzle takes place, similar to a thread.
  • the other surface of the flow-guiding element which is closest to the pressure port, leads that part of the pumped medium which emerges from the impeller in the area of the pressure port directly to the pressure port. In relation to the impeller level, this surface has a significantly steeper slope than the opposite other flow-carrying surface of the element.
  • the steeper wall surface of the element which extends from the leading edge to a certain extent counter to the direction of flow, runs almost axially and separatingly through the flow space downstream of the impeller. Since the number of elements corresponds to the number of pressure ports, one element is assigned to each pressure port.
  • a conveying medium emerging from the impeller is thus guided on the wall surface of the element to the pressure port, while the wall surface of the element which runs counter to the direction of flow prevents circulation of the conveying medium within the flow space downstream of the impeller.
  • the flow-carrying wall surfaces can even be curved.
  • the slope of a wall surface can be constant or not constant; this depends on the total space available.
  • the offset of the leading edge and / or the leading surface of the element with respect to a pressure nozzle center axis ensures that the largest possible space is available after the impeller, within which the conversion of the medium emerging from the impeller at high speed into a medium emerging from the pressure nozzle higher pressure takes place.
  • the flow space downstream of the impeller is subdivided directly after the opening of the pressure port, so that the cross section of the pressure port inlet is never blocked by the element.
  • the offset takes place here in the impeller plane or in a plane parallel to the impeller plane.
  • the flow-guiding surface emanating from the leading edge and / or the inflow surface is of stepped design, with a wall surface part running on a smaller diameter having greater axial distances from the outlet of the impeller than a wall surface part arranged on a larger diameter. This measure results in a further improvement in efficiency. As a result, a stable flow is formed in the flow space, which avoids turbulence within the flow space and causes a favorable flow guidance to the pressure port inlet.
  • the embodiment according to claim 5 indicates the maximum lateral offset of the surfaces of the element to be flown first.
  • the offset is preferably carried out in such a way that the surface of the element closest to the pressure port ensures a trouble-free transfer of the flow into the pressure port.
  • the configurations described in claims 6 to 8 deal with the design of the element as a separate component or as an integral part of the inner and / or outer housing.
  • the pressure-loaded housing can be designed as an easy-to-test component, while the element or elements can be separate or integral elements of the inner housing.
  • the suction port is not shown here and can be designed in any way.
  • An inner housing (4) is inserted into this outer housing (1) from the drive side and accommodates a bearing (5) for a pump shaft (6).
  • this surrounds an impeller (7) which adjoins the pressure-side cover disk (9) on the end (8) of the inner housing remote from the drive.
  • the impeller (7) is designed here as a semi-axial and open wheel. However, other, axial and radial, open or closed designs can also be used.
  • the outer casing (10) of the inner housing (4) has a contour which corresponds to an increasing cross-sectional expansion of the inner housing in the direction of the pressure port (2, 3) or outer housing (1).
  • the area of the flow space (11) between the impeller outlet and the pressure port (2) has none of the usual guide wheels.
  • a transition (12) can be seen in the outer housing (1), the cross section of which narrows in the direction of flow from the flow space (11) to the pressure port (2) or (3) in a funnel shape. This ensures a streamlined transition between the flow space (11) and the pressure port. Viewed from the opposite direction, the pressure port expands in the direction of the flow space.
  • the flow-carrying wall surfaces of the element or elements (14, 15) run between the diameters D1 and D2 and extend from the impeller outlet to the pressure port and thereby limit the flow space (11).
  • D1 corresponds to the outer diameter of the inner housing (4) at the inlet. This diameter increases with increasing axial extension.
  • D2 corresponds to the inside diameter of the outer housing (1) and is largely constant in this example.
  • FIG. 2 shows a view into an open pump housing, from which the impeller has been removed for better understanding. Furthermore, the wall surfaces explained in more detail below were provided with contour lines from the inner housing and from the flow-guiding elements in order to be able to trace the course of the wall surfaces.
  • the spur-like inflow edge (13) and an inflow surface (23) of the elements (14, 15) with a larger diameter are arranged offset to the left in the direction of flow relative to a pressure nozzle center line corresponding to the pressure nozzle width. This is the maximum lateral offset.
  • the wall surface extending from the spur-like inflow edge (13) or inflow surface (23) in the direction of flow is stepped here, the wall surface parts (16, 18) lying on a smaller diameter being arranged deeper in relation to the plane of the drawing than those on the larger diameter Wall surface parts (17, 19). Looking at the plane of the drawing, the wall surface parts (16, 18) arranged here on a smaller diameter are further back and thus closer to the pressure port level than the wall surface parts (17, 19) located on a larger diameter.
  • the outer jacket (10) of the inner housing (4) has increasing diameters towards the pressure ports, which are illustrated by the annular contour lines.
  • the wall surfaces (20, 21) emanating from the spur-like trailing edge (13) or inflow surface (23), facing the pressure port or closest and separating the flow space (11) to a certain extent in the axial direction, have a shape here that is comparable to a fillet .
  • the same is also the case with the flow-carrying wall surfaces (16-19). This ensures that a medium flowing into the pressure connection (2, 3) is gently deflected and the flow is not passed in an obstructive manner into the inlet cross section of the pressure connection.
  • these wall surfaces (20, 21) run almost parallel to the pump shaft (6) or have a slightly curved shape. With a different impeller shape, a slightly different course can also arise here.
  • FIG. 3 shows a section along the line III-III of FIG. 2.
  • the element (14) shown here can be formed as a separate individual part or an integral part of the outer housing (1) and / or the inner housing (4). This depends on the type of manufacture chosen.
  • the cross section shown in FIG. 4 corresponds to the section line IV-IV shown in FIG. 2. Relative to the outlet cross section of the impeller, the depth graduation of the wall surfaces (16, 17) extending from the leading edge (13) or inflow surface (23) and extending in the direction of flow can be seen here.
  • the smaller diameter and to the inner housing (4) adjacent wall surface (16) is further away from the impeller outlet than the wall surface (17) located on a larger diameter and adjacent to the outer casing (1).
  • the impeller outlet corresponds approximately to the plane of the end (8) of the inner housing (4) remote from the drive.
  • the wall surfaces (17, 19) arranged on a larger diameter can run inclined to the pump shaft axis.
  • the course of the wall surfaces is comparable to a spiral extending in the axial direction, if one takes into account that the cross section of the flowed through space increases with increasing distance from the impeller. Practical tests have shown that with such a housing design higher efficiencies can be achieved compared to known solutions.
  • FIG. 5 corresponds to the section V-V from FIG. 2. This section is made shortly before the end of the wall surface (17) with a larger diameter. The wall surface (16) with a smaller diameter then directs the flow medium to the pressure port alone. As the contour lines from FIG. 2 also show, the surfaces (16, 17) can be concavely curved for better flow guidance.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP91101345A 1990-02-21 1991-02-01 Pompe centrifuge Expired - Lifetime EP0443354B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4005414 1990-02-21
DE4005414 1990-02-21
DE4041545A DE4041545A1 (de) 1990-02-21 1990-12-22 Kreiselpumpe
DE4041545 1990-12-22

Publications (2)

Publication Number Publication Date
EP0443354A1 true EP0443354A1 (fr) 1991-08-28
EP0443354B1 EP0443354B1 (fr) 1995-09-06

Family

ID=25890366

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91101345A Expired - Lifetime EP0443354B1 (fr) 1990-02-21 1991-02-01 Pompe centrifuge

Country Status (5)

Country Link
US (1) US5114311A (fr)
EP (1) EP0443354B1 (fr)
JP (1) JP3069383B2 (fr)
CN (1) CN1023508C (fr)
DE (2) DE4041545A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019001882A1 (de) * 2019-03-19 2020-09-24 KSB SE & Co. KGaA Mantelgehäusepumpe und Herstellungsverfahren für eine Mantelgehäusepumpe

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4310467A1 (de) * 1993-03-31 1994-10-06 Klein Schanzlin & Becker Ag Topfgehäusepumpe
US8398361B2 (en) 2008-09-10 2013-03-19 Pentair Pump Group, Inc. High-efficiency, multi-stage centrifugal pump and method of assembly
CN101825117B (zh) * 2009-03-02 2012-10-24 重庆江利圣特机械制造有限责任公司 汽车发动机水泵总成腔室结构
WO2014074204A1 (fr) * 2012-11-10 2014-05-15 Carrier Corporation Pompe centrifuge avec avant-bec incliné anticavitation
JP6051056B2 (ja) 2013-01-15 2016-12-21 株式会社荏原製作所 渦巻ポンプ
CN104196761A (zh) * 2014-08-22 2014-12-10 广东海信家电有限公司 一种双进风离心风机
DE102014114801B4 (de) * 2014-10-13 2017-08-31 Lutz Pumpen Gmbh Strömungsmaschine mit halbaxialem Laufrad
CN114776597B (zh) * 2022-03-09 2024-03-12 山东省科学院海洋仪器仪表研究所 一种磷虾无损混输装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1534509A (en) * 1975-12-23 1978-12-06 Girdlestone Pumps Ltd Axial flow pumps or fans
EP0017829A1 (fr) * 1979-04-09 1980-10-29 Arthur Milz Pompe centrifuge et son carter
DE3920941A1 (de) * 1988-07-05 1990-01-11 Volkswagen Ag Kreiselpumpe, insbesondere kuehlfluessigkeitspumpe fuer eine brennkraftmaschine

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7217110U (de) * 1973-05-24 Klein Schanzlin & Becker Ag Kreiselpumpengehause
GB180823A (en) * 1921-03-31 1922-06-08 George Ure Reid Improvements in centrifugal pumps
US1496633A (en) * 1922-10-20 1924-06-03 Franklin H Hertzler Pump
US3859008A (en) * 1971-07-06 1975-01-07 Andritz Ag Maschf Pump with offset inflow and discharge chambers
BE792709A (fr) * 1971-12-14 1973-06-14 Westinghouse Electric Corp Pompe centrifuge
NL7408835A (nl) * 1974-07-01 1976-01-05 Sneek Landustrie Schroefpomp.
AT347268B (de) * 1974-12-24 1978-12-27 Rudolf Dr Wieser Pumpe
AT346268B (de) * 1975-02-08 1978-11-10 Werner & Pfleiderer Zum uebertragen von teigstuecken von einem ersten auf ein nachfolgendes zweites foerderband bestimmte vorrichtung
DE2710514A1 (de) * 1976-03-16 1977-09-22 Nuclear Power Co Risley Ltd Stroemungsmittelumwaelz- bzw. zirkuliervorrichtung
JPS5552078U (fr) * 1978-10-03 1980-04-07

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1534509A (en) * 1975-12-23 1978-12-06 Girdlestone Pumps Ltd Axial flow pumps or fans
EP0017829A1 (fr) * 1979-04-09 1980-10-29 Arthur Milz Pompe centrifuge et son carter
DE3920941A1 (de) * 1988-07-05 1990-01-11 Volkswagen Ag Kreiselpumpe, insbesondere kuehlfluessigkeitspumpe fuer eine brennkraftmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019001882A1 (de) * 2019-03-19 2020-09-24 KSB SE & Co. KGaA Mantelgehäusepumpe und Herstellungsverfahren für eine Mantelgehäusepumpe

Also Published As

Publication number Publication date
CN1054653A (zh) 1991-09-18
DE4041545A1 (de) 1991-08-22
EP0443354B1 (fr) 1995-09-06
DE4041545C2 (fr) 1992-07-23
US5114311A (en) 1992-05-19
CN1023508C (zh) 1994-01-12
JP3069383B2 (ja) 2000-07-24
JPH06117390A (ja) 1994-04-26
DE59106391D1 (de) 1995-10-12

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