EP3942184A1 - Barrel casing pump and method for manufacturing a barrel casing pump - Google Patents
Barrel casing pump and method for manufacturing a barrel casing pumpInfo
- Publication number
- EP3942184A1 EP3942184A1 EP20711805.0A EP20711805A EP3942184A1 EP 3942184 A1 EP3942184 A1 EP 3942184A1 EP 20711805 A EP20711805 A EP 20711805A EP 3942184 A1 EP3942184 A1 EP 3942184A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- contour
- spiral
- housing
- flow space
- casing
- 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.)
- Pending
Links
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
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/06—Multi-stage pumps
- F04D1/063—Multi-stage pumps of the vertically split casing type
-
- 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
-
- 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
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/52—Outlet
Definitions
- the invention relates to a centrifugal pump with a jacket housing and at least one stage housing inserted therein.
- centrifugal pumps also known as double-casing or casing-casing pumps, are centrifugal pumps which are surrounded by a casing-like casing.
- the casing which is provided with suction and pressure ports, is closed with a cover in a plane perpendicular to the shaft.
- These are usually multistage pumps for use as high and extremely high pressure pumps, in particular also as boiler feed pumps.
- Within the jacket housing several stepped housings are arranged in series one behind the other in the axial direction.
- Each stage housing includes a pump impeller and optionally a stationary stator.
- the individual stage housings are usually designed together with the pump shaft as a coherent slide-in pump.
- the flow transition from the last stator or the last stage housing into the pressure connection usually takes place via a flow space formed in the casing.
- a separate insert for an end spiral in the transition area is used as an alternative.
- the end spiral is manufactured using a separate cast part in which the spiral contour is milled.
- the object of the invention is therefore to develop a generic pump with an end spiral that is significantly simpler and therefore also more cost-effective to manufacture.
- centrifugal pump according to the features of claim 1.
- Advantageous configurations of the centrifugal pump are the subject of the dependent claims.
- the spiral contour is not realized by a separate insert part, but instead, components that are already present are used.
- the spiral contour is not only formed by the inner contour of the casing in the transition area, but in combination with an adjoining contour of the last step casing and an adjoining contour of a cover inserted into the casing at the end.
- the end spiral is therefore composed of several, in particular of at least three, components.
- a separate spiral insert as provided in the prior art, can be completely dispensed with.
- the respective contour of the components should be produced by conventional machining processes.
- the additional costs should be kept low by the simple production.
- the pump with the multi-part, in particular three-part, end spiral should not be larger than without the end spiral, ie ideally the casing housing does not increase in size compared to a comparable pump with an end-side flow space.
- the available space in a comparable pump with a flow space is assumed to be a fixed requirement for the dimensioning of the casing.
- the invention is therefore aimed at achieving a maximum increase in the efficiency of the last pump stage with a non-ideal spiral contour. Since the end spiral can significantly reduce the amount of loss in the last stage, the influence on the overall pump efficiency is also significant.
- At least one deflection component is welded on within the jacket housing after the machining of the inner contour. It makes sense to weld on a corresponding deflection component in the area of the pump spur of the end spiral. In the ideal case, this deflecting component is the only additional component.
- the shaped spiral-shaped flow space is characterized in that it initially expands radially, starting from the spur, in the direction of flow, in particular increasingly, ideally constantly expanding. It is also preferred if the flow area has a constant axial extent over this circumference. Theoretically, however, it is also conceivable that the flow area also expands axially in this area.
- the radial extent remains constant from a defined circumferential angle, the angle in a range from approximately 45 ° to is about 135 ° and preferably has an angle of about 90 °. It is advantageous if the flow space widens axially from this angle.
- the contour of the end cover and the contour of the last stepped housing each serve as a lateral guide wall of the spiral flow space formed.
- the centrifugal pump can also comprise one or more guide wheels, with one guide wheel being provided in particular for each stage.
- at least one stator is arranged in the transition area from the last stage housing, viewed in the direction of flow, into the pressure connection.
- the inside diameter of the spiral-shaped flow space can be adapted to the stator outside diameter, i.e. correspond roughly to this.
- the centrifugal pump is a feed pump, in particular a boiler feed pump for a power plant.
- the invention therefore also includes the advantageous use of such a centrifugal pump as a feed pump, in particular a boiler feed pump, for a power plant.
- another aspect of the invention also relates to a manufacturing method for a centrifugal pump according to the invention.
- This is initially based on a conventional centrifugal pump design with a casing and a conventional flow space in the transition area between the last stage casing and the discharge nozzle. This means that for the production of the centrifugal pump according to the invention an almost identical external dimensioning of the jacket housing is assumed.
- a 3D template ie a three-dimensional model of the desired spiral space, is now first generated.
- the template is created taking into account the maximum possible flow space diameter and the available flow space width.
- the three-dimensional template is usually a digital template. If at least one stator is optionally provided in the transition area under consideration, its outer diameter must also be taken into account for the template design, in particular the inner diameter of the desired spiral space is adapted to the outer diameter of the stator.
- the template generated then serves as a template for processing the contours of the components to build the end spiral, i.e. For the machining of the inner contour of the jacket housing, the contour of the last stepped housing and the relevant contour of the cover.
- a programmable processing machine is used for the machine processing of the relevant component contours, which processes and traverses the respective contour with the appropriate tool taking into account the template. Milling of the respective contours is particularly suitable, in particular by means of shell milling cutters.
- the inner contour of the jacket housing is traversed from the inside with a milling tool that is picked up by the processing machine via an angle head, in order to generate the spiral contour.
- this component is also created beforehand based on the template, for example by milling, grinding, cold forming, laser casting, etc.
- Figure 5a / 5b a side and top view of the relevant contour of the last step housing and Figure 6a / 6b a top and side view of the relevant contour of the end cover.
- FIG. 1 shows a centrifugal pump with a casing 1, which has both a suction connection 2 and a pressure connection 3.
- the jacket housing 1 is closed at its pressure-side end by a cover 4 which is fastened, in particular screwed, to the jacket housing 1 via connecting means 5.
- each impeller 7 is of a stage housing 9 surrounded.
- Adjacent step housing 9 adjoin one another.
- the stage housing closest to the pressure connection 3 or, viewed in the direction of flow, the last stage housing is provided with the reference number 9 ′ and surrounds the impeller 7 arranged upstream of the last impeller 7 ′, seen in the direction of flow.
- the inner contour 11 of the jacket housing 1 in the transition area to the pressure port 3 is machined to a desired spiral contour 12 by milling.
- the spiral contour 12 begins in the area near a spur 13 shown in Fig. 2a on the pressure connection 3 and initially provides an area 14 which has an increasing radial expansion of an available flow space 15 over the circumference, i.e. the inner contour 11 of the jacket housing 1 provides an increasing depression of the inner contour 11 with a constant width.
- the radial expansion increases at a circumferential angle et of approximately 25 ° up to a circumferential angle a 'of 90 °.
- the area 14 is followed by an area 16 of the spiral contour 12, in which, in the embodiment shown, the radial expansion remains constant from the angle ⁇ ' ⁇ 90 ° and the spiral contour 12 instead only expands in the axial direction until the spiral contour 12 then opens into the pressure port 3.
- the original flow space 15 is narrowed in the radial direction by a deflection device 17.
- FIGS. 3a and 3b show sectional views through the installed pump according to the invention in the transition area into the pressure port 3.
- the deflection Device 17 is designed as a separate component and forms the spur 13.
- the deflecting device 17 is welded to the jacket housing 1 in the area of the pressure connection 3. Exemplary developments of the spiral contour 12 can be found in the representations of FIGS. 4a and 4b.
- FIG. 4a shows in solid lines that the area 14 and the area 16 of the spiral contour 12 are aligned centrally or symmetrically with the pressure connection 3.
- a spiral contour 12 'shown in dashed lines or a spiral contour 12 "shown in a dash-dotted line show further variants in which the area 14' or 14" are aligned eccentrically or asymmetrically with the pressure port 3.
- FIG. 4b shows that the length of the area 14 of the spiral contour 12 can vary.
- a spiral contour 12 '"shown with a dash-dotted line has an elongated area 14'", the area 16 "'being shortened. It goes without saying that the length variance shown in FIG. 4b can also be applied to the embodiments of FIG. 4a.
- Figures 5a, 5b show a partial representation of the last stepped housing 9 'in the area of a machined contour 18, which forms a guide wall of the end spiral 10 formed in the assembled pump state.
- the cover 4 with a relevant contour 19 for forming the opposite guide wall can be seen from the illustrations in FIGS. 6a, 6b.
- the multi-part, here three-part end spiral 10 utilizes a large part (approx. 80%) of the possible loss height gain of an end spiral contour without realizing the ideal spiral contour. This means that the pump does not have to be made larger. Especially in the case of multi-stage feed pumps in jacket housing design, a high gain in efficiency can be achieved. The lower the number of stages, the greater the gain in efficiency.
- the new design makes it possible to integrate an end spiral 10 even in feed pumps with radially smaller guide wheels 8 'without having to build the pump larger.
- a 3D spiral contour is first created in CAD in accordance with the existing stator outer diameter and the maximum possible flow space diameter and the flow space width in the casing 1.
- the dimensions for the flow space correspond to the specifications for the design of the pump without a spiral contour.
- the resulting pump with a spiral contour is no larger.
- the axial position between the diffuser outlet and the center of the pressure port can be freely selected when creating the 3D template.
- the generated three-dimensional spiral contour serves as a template for the construction of the three components, i.e. the jacket housing 1, the step housing 9 ‘and the pressure-side cover 4, which form the spiral flow space 15 in the assembled state.
- the components or the respective contours 11, 18 and 19 can be produced by means of a shell end mill.
- a programmable machining machine is used, with which the three-dimensional spiral contour 12 is traversed from the inside according to the template via an angle head in which the milling cutter is received.
- the deflection device 17 is also constructed beforehand with the aid of the three-dimensional template.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102019001882.6A DE102019001882A1 (en) | 2019-03-19 | 2019-03-19 | Jacketed casing pump and manufacturing method for a casing casing pump |
PCT/EP2020/055622 WO2020187562A1 (en) | 2019-03-19 | 2020-03-04 | Barrel casing pump and method for manufacturing a barrel casing pump |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3942184A1 true EP3942184A1 (en) | 2022-01-26 |
Family
ID=69845333
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20711805.0A Pending EP3942184A1 (en) | 2019-03-19 | 2020-03-04 | Barrel casing pump and method for manufacturing a barrel casing pump |
Country Status (7)
Country | Link |
---|---|
US (1) | US20220163037A1 (en) |
EP (1) | EP3942184A1 (en) |
JP (1) | JP7512303B2 (en) |
CN (1) | CN113544385A (en) |
DE (1) | DE102019001882A1 (en) |
SA (1) | SA521430361B1 (en) |
WO (1) | WO2020187562A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2022048575A (en) * | 2020-09-15 | 2022-03-28 | 三菱重工コンプレッサ株式会社 | Cabin manufacturing method |
DE102020133327B4 (en) * | 2020-12-14 | 2023-01-19 | KSB SE & Co. KGaA | pump assembly |
DE102021105623A1 (en) | 2021-03-09 | 2022-09-15 | KSB SE & Co. KGaA | Production of a stage casing in a hybrid process |
CN113266576A (en) | 2021-05-28 | 2021-08-17 | 惠州汉旭五金塑胶科技有限公司 | Liquid cooling pump cavity runner structure and liquid cooling pump |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3289923A (en) * | 1964-10-30 | 1966-12-06 | American Air Filter Co | Multi-stage pump |
DE4041545A1 (en) * | 1990-02-21 | 1991-08-22 | Klein Schanzlin & Becker Ag | CENTRIFUGAL PUMP |
US5076758A (en) * | 1990-07-18 | 1991-12-31 | Ingersoll-Rand Company | Centrifugal pumps |
DE4310467A1 (en) * | 1993-03-31 | 1994-10-06 | Klein Schanzlin & Becker Ag | Pot housing pump |
US5888053A (en) * | 1995-02-10 | 1999-03-30 | Ebara Corporation | Pump having first and second outer casing members |
DE102006021245B4 (en) * | 2006-04-28 | 2008-03-06 | Bühler Motor GmbH | rotary pump |
DE202006011858U1 (en) * | 2006-08-02 | 2007-12-13 | Sterling Fluid Systems (Germany) Gmbh | Multi-stage side channel pump with housing washers |
DE102008025249A1 (en) * | 2008-05-27 | 2009-12-03 | Siemens Aktiengesellschaft | Collecting room and process for production |
EP2233748B1 (en) * | 2009-03-10 | 2017-05-24 | Grundfos Management A/S | Multi stage centrifugal pump |
JP5889622B2 (en) * | 2010-12-14 | 2016-03-22 | 株式会社クボタ | Multistage pump |
CN102080659A (en) * | 2010-12-29 | 2011-06-01 | 荆锁祥 | Sections-distributed-in-pairs twin-volute mine wearable multi-stage pump |
ITFI20120272A1 (en) * | 2012-12-05 | 2014-06-06 | Nuovo Pignone Srl | "BACK-TO-BACK CENTRIFUGAL PUMP" |
DE102014214805A1 (en) | 2014-07-29 | 2016-02-04 | Ksb Aktiengesellschaft | Barrel casing pump |
EP3199815B1 (en) * | 2016-01-26 | 2020-07-15 | Grundfos Holding A/S | Centrifugal pump |
JP2017180237A (en) * | 2016-03-30 | 2017-10-05 | 三菱重工業株式会社 | Centrifugal compressor |
CN106837806B (en) * | 2017-02-10 | 2018-05-08 | 长沙佳能通用泵业有限公司 | A kind of sectional type parallel connection multistage pump |
US10458431B2 (en) * | 2017-04-10 | 2019-10-29 | Hamilton Sundstrand Corporation | Volutes for engine mounted boost stages |
-
2019
- 2019-03-19 DE DE102019001882.6A patent/DE102019001882A1/en active Pending
-
2020
- 2020-03-04 JP JP2021556612A patent/JP7512303B2/en active Active
- 2020-03-04 CN CN202080022217.6A patent/CN113544385A/en active Pending
- 2020-03-04 US US17/440,385 patent/US20220163037A1/en active Pending
- 2020-03-04 WO PCT/EP2020/055622 patent/WO2020187562A1/en unknown
- 2020-03-04 EP EP20711805.0A patent/EP3942184A1/en active Pending
-
2021
- 2021-09-19 SA SA521430361A patent/SA521430361B1/en unknown
Also Published As
Publication number | Publication date |
---|---|
DE102019001882A1 (en) | 2020-09-24 |
JP7512303B2 (en) | 2024-07-08 |
CN113544385A (en) | 2021-10-22 |
US20220163037A1 (en) | 2022-05-26 |
JP2022525678A (en) | 2022-05-18 |
SA521430361B1 (en) | 2023-02-19 |
WO2020187562A1 (en) | 2020-09-24 |
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