US20180128271A1 - High efficiency double suction impeller - Google Patents

High efficiency double suction impeller Download PDF

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Publication number
US20180128271A1
US20180128271A1 US15/730,139 US201715730139A US2018128271A1 US 20180128271 A1 US20180128271 A1 US 20180128271A1 US 201715730139 A US201715730139 A US 201715730139A US 2018128271 A1 US2018128271 A1 US 2018128271A1
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US
United States
Prior art keywords
impeller
double suction
inter
blade channels
suction impeller
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.)
Abandoned
Application number
US15/730,139
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English (en)
Inventor
Lorenzo Bergamini
Marco TORRESI
Tommaso CAPURSO
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.)
Nuovo Pignone SRL
Nuovo Pignone Technologie SRL
Original Assignee
Nuovo Pignone SRL
Nuovo Pignone Technologie SRL
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 Nuovo Pignone SRL, Nuovo Pignone Technologie SRL filed Critical Nuovo Pignone SRL
Assigned to NUOVO PIGNONE SRL reassignment NUOVO PIGNONE SRL ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BERGAMINI, LORENZO, CAPURSO, Tommaso, TORRESI, Marco
Publication of US20180128271A1 publication Critical patent/US20180128271A1/en
Abandoned 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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/006—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps double suction 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
    • F04D29/007—Details, component parts, or accessories 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F04D29/2255—Special flow patterns flow-channels with a special cross-section contour, e.g. ejecting, throttling or diffusing effect
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

Definitions

  • the present disclosure relates to a high efficiency double suction impeller, e.g. one that may be used for centrifugal pumps.
  • Radial flow turbo machinery devices are particularly adapted to convert shaft power to kinetic energy (and vice versa) by accelerating (or decelerating) a fluid in a revolving device called impeller.
  • impellers When used as power-absorbing machines, impellers are commonly used to raise the pressure of a fluid or induce a fluid flow in a piping system.
  • the impeller is the device, within the turbo machinery, that, rotating, exchanges energy with the fluid.
  • the impeller comprises a plurality of blades fitted onto a hub plate.
  • the shape and the geometry of impeller blades can be of many different types depending on the use, the rating, the performance of the turbo machinery.
  • NS nQ 1 / 2 1.1618 ⁇ H 3 / 4
  • n rotating speed in revolution per minute
  • Q volumetric flow rate in [m 3 /h]
  • H differential head [m] for centrifugal pumps of capacity larger than 10 m ⁇ 3/h designed with low or medium specific speed values (e.g. NS ⁇ 1600) and a double suction configuration
  • an impeller with a small number of blades is required in order to keep the head vs flow rate stable and continuously rising towards zero flow. This requirement is very important especially in case of more than one centrifugal pump employed in parallel, each working with a fraction of the available flow.
  • centrifugal pumps of large capacity designed for low or medium specific speed values and for medium or high values of hydraulic head require impellers having large diameters and narrow exit width.
  • Double suction impellers are usually composed by two single suction impellers each elaborating half of the total flow and arranged in a back-to-back configuration.
  • Impellers of this kind often show an unstable head vs flow rate characteristic curve.
  • another drawback of this kind of impellers lies in the low blade exit angles (normally between 15° and 20°) and corresponding large wrap angles (normally between 120° and 270°) that are required to maintain acceptable slip factor values.
  • the hydraulic efficiency of the state-of-the-art impeller of this kind is typically smaller than 95%.
  • the achievable head coefficient can be increased by employing conventional split blades impellers, but this choice does not solve the problem of the narrow b 2 /D 2 and poor head curve stability. Moreover, the number of leading edges of conventional split blades impellers is doubled, causing additional hydraulic losses.
  • Embodiments of the present invention therefore relate to a double suction impeller having the channels between the blades starting from both inlets and crossing the median axis of the impeller exit in such a way that, as a result, the equivalent blades number is doubled with respect to a conventional configuration obtained by the coupling of two single suction impellers.
  • embodiments of the new impeller do not introduce any additional leading edge and corresponding losses.
  • the new shape of the inter-blade channels of the impeller is such that the hydraulic diameter is increased and the length of each channel reduced, thus reducing the hydraulic losses with respect conventional impellers.
  • the main application for the new double suction impeller is within centrifugal pumps and hydraulic power recovery turbines especially, but not exclusively, intended for refinery, petrochemical and pipelines. However, other applications are possible and contemplated.
  • FIG. 1 illustrates a meridional section of a state of the art double suction impeller
  • FIG. 2 illustrates a view of the inter-blade channel of the state of the art double suction impeller
  • FIG. 3 illustrates a detail of the outer diameter arrangement of a state of the art double suction impeller
  • FIG. 4 illustrates a detail of the section of an embodiment of a new double suction impeller
  • FIG. 5 illustrates a view of the inter-blade channel of another embodiment of the new double suction impeller
  • FIG. 6 illustrates a detail of the outer diameter arrangement of another embodiment of the new double suction impeller
  • FIG. 7 illustrates a first front view of another embodiment of the new double suction impeller
  • FIG. 8 illustrates a meridional cross section of an embodiment of the new double suction impeller
  • FIG. 9 illustrates a side view of an embodiment of the new double suction impeller.
  • embodiments of the present invention relate to new a double suction impeller, in particular for centrifugal pumps, wherein the flow-path arrangement is characterized by inter-blade channels intersecting each other at the impeller outer diameter.
  • the new double suction impeller comprises channels between the blades starting from both inlets and intersecting at the outer diameter of the impeller in such a way that the equivalent blade number is doubled with respect to a conventional configuration obtained by simply adjoining to a central rib two single suction impellers, as illustrated in enclosed FIGS. 1, 2 and 3 .
  • the new double suction impeller includes a shrouded impeller 10 .
  • the shrouded impeller 10 may further include a hub 11 associated with a tubular center bore 12 .
  • the tubular center bore 12 may be adapted to receive the impeller drive shaft which is drivingly connected thereto, generally by a key and a keyway.
  • the shrouded impeller 10 can be made either of one single piece—or assembly—or it can be made of a plurality of assemblies, e.g. comprising one left shroud, one right shroud and a central core.
  • the new impeller is made of one single assembly, and the hub 11 further includes a plurality of blades 13 integrally attached to the hub 11 and to a pair of integral shrouds, a left side shroud 14 and a right side shroud 15 .
  • Each one of the integral shrouds 14 , 15 is provided with a center aperture 16 , 31 that constitutes the impeller eye.
  • the impeller eye is adjacent to said tubular center bore 12 and comprises an aperture edge 17 with an aperture edge radius and an aperture rim 18 with an aperture rim radius.
  • the left side shroud 14 defines the left side aperture and the right side shroud 15 defines the right side aperture of the double suction impeller according to the present invention.
  • the outer edge of said left side shroud 14 and the outer edge of said right side shroud 15 define the impeller exit, said impeller exit having a width 19 and a median plane 20 .
  • each pair of adjacent blades 13 of said plurality of blades 13 define a plurality of inter-blade channels, referred to in enclosed FIG. 5 .
  • Said inter-blade channels are adapted to connect a plurality of input apertures, located within the center apertures of both said left side shroud 14 and said right side shroud 15 , to a plurality of output apertures located on said impeller exit.
  • said inter-blade channels comprise left side inter-blade channels 21 , having their respective input apertures 22 located within the center aperture of said left side shroud 14 , and right side inter-blade channels 24 , having their respective input apertures 25 located within the center aperture of said right side shroud 15 .
  • said left side inter-blade channels 21 and said right side inter-blade channels 24 are such as intersecting the median plane 20 of said impeller exit in a way to dispose the output apertures 23 of said left side inter-blade channels 21 aligned and alternated with the output apertures 26 of said right side inter-blade channels 24 , on said impeller exit.
  • impeller In operation, when rotated, fluid will be drawn axially into the impeller as indicated by the arrows 27 , 28 , impelled by the plurality of blades 13 passing between the hub 11 and said left and right shrouds 14 , 15 and finally expelled radially through said exit as indicated by the arrows 29 .
  • the impeller runs in the direction of arrow 30 in a suitable housing having axial inlets and a circumferential volute or diffuser outlet passage.
  • the effect connected to the crossing by said inter-blade channels of the median axis of the impeller exit is such that the equivalent blades number is doubled with respect to a conventional configuration obtained by the coupling of two single suction impellers.
  • section 33 corresponds to the inlet of a channel of an impeller of the state of the art
  • area 32 corresponds to the outlet of a channel of an impeller of the state of the art.
  • the section 35 corresponds to the inlet of a channel of the new impeller
  • area 34 corresponds to the outlet of a channel of the new impeller.
  • the outlet area 34 of the inter-blade channels of the new double suction impeller has a rectangular shape with an aspect ratio much closer to 1 with respect to that of a state of the art impeller.
  • benefits introduced by the new double suction impeller include, inter alia, reduction of the slip factor and reduction of hydraulic losses. These reductions may translate to an efficiency increase of about 3% to 4% and, ultimately, to a lower operating expenditure and lower capital expenditure.
US15/730,139 2016-11-07 2017-10-11 High efficiency double suction impeller Abandoned US20180128271A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT102016000111763A IT201600111763A1 (it) 2016-11-07 2016-11-07 Girante a doppia aspirazione, ad alta efficienza
IT102016000111763 2016-11-07

Publications (1)

Publication Number Publication Date
US20180128271A1 true US20180128271A1 (en) 2018-05-10

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US15/730,139 Abandoned US20180128271A1 (en) 2016-11-07 2017-10-11 High efficiency double suction impeller
US16/404,097 Active 2037-11-08 US10941777B2 (en) 2016-11-07 2019-05-06 High efficiency double suction impeller
US17/193,292 Active US11536273B2 (en) 2016-11-07 2021-03-05 High efficiency double suction impeller

Family Applications After (2)

Application Number Title Priority Date Filing Date
US16/404,097 Active 2037-11-08 US10941777B2 (en) 2016-11-07 2019-05-06 High efficiency double suction impeller
US17/193,292 Active US11536273B2 (en) 2016-11-07 2021-03-05 High efficiency double suction impeller

Country Status (5)

Country Link
US (3) US20180128271A1 (fr)
EP (1) EP3535497B1 (fr)
JP (2) JP2018105298A (fr)
IT (1) IT201600111763A1 (fr)
WO (1) WO2018083306A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11525455B2 (en) 2018-11-30 2022-12-13 Samsung Electronics Co., Ltd. Double suction fan and air conditioner having the same
CN116628895A (zh) * 2023-07-20 2023-08-22 北京航空航天大学 一种带分流叶片的斜流或径流压气机叶轮性能预估方法

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201600111763A1 (it) * 2016-11-07 2018-05-07 Nuovo Pignone Tecnologie Srl Girante a doppia aspirazione, ad alta efficienza
JP7364504B2 (ja) 2020-03-17 2023-10-18 株式会社神戸製鋼所 インペラ、及びインペラの製造方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2791183A (en) * 1952-02-09 1957-05-07 Skoglund & Olsson Ab Impeller for centrifugal pumps
US4322200A (en) * 1976-02-09 1982-03-30 Stiegelmeier Owen E Heavy duty impeller
WO2015052081A1 (fr) * 2013-10-10 2015-04-16 Nuovo Pignone Srl Turbine de récupération d'énergie hydraulique à boîtier de palier-embrayage intégré

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
GB190018343A (en) * 1900-10-15 1900-12-22 Edward Seitz Improvements in Centrifugal Pumps.
US1003542A (en) * 1911-06-05 1911-09-19 Joseph J Stoetzel Centrifugal pump or blower.
GB191318343A (en) 1913-08-12 1914-08-12 Albert George Mcgregor Improvements in Photographic Plate or Print Washers.
CH218636A (de) * 1940-11-09 1941-12-31 Scintilla Ag Schleuderrad zur Förderung zweier zu mischender Flüssigkeiten oder Gase.
JPS5551994A (en) * 1978-10-13 1980-04-16 Kobe Steel Ltd Centrifugal compressor with-two-suction-port
JPS58155298A (ja) * 1982-03-10 1983-09-14 Kubota Ltd 両吸込ポンプの羽根車
JPH0530046A (ja) 1991-07-19 1993-02-05 Nippon Telegr & Teleph Corp <Ntt> 基地局試験システム
JPH0687694U (ja) * 1993-06-04 1994-12-22 三菱重工業株式会社 両吸込型遠心流体機械
JPH0731994A (ja) 1993-07-20 1995-02-03 Toshiba Corp 廃水処理装置
JP2012132368A (ja) * 2010-12-22 2012-07-12 Mitsubishi Heavy Ind Ltd 両吸込型遠心流体機械
IT201600111763A1 (it) * 2016-11-07 2018-05-07 Nuovo Pignone Tecnologie Srl Girante a doppia aspirazione, ad alta efficienza

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2791183A (en) * 1952-02-09 1957-05-07 Skoglund & Olsson Ab Impeller for centrifugal pumps
US4322200A (en) * 1976-02-09 1982-03-30 Stiegelmeier Owen E Heavy duty impeller
WO2015052081A1 (fr) * 2013-10-10 2015-04-16 Nuovo Pignone Srl Turbine de récupération d'énergie hydraulique à boîtier de palier-embrayage intégré

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11525455B2 (en) 2018-11-30 2022-12-13 Samsung Electronics Co., Ltd. Double suction fan and air conditioner having the same
CN116628895A (zh) * 2023-07-20 2023-08-22 北京航空航天大学 一种带分流叶片的斜流或径流压气机叶轮性能预估方法

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US10941777B2 (en) 2021-03-09
JP2020500271A (ja) 2020-01-09
US20190257311A1 (en) 2019-08-22
EP3535497B1 (fr) 2021-03-24
JP2018105298A (ja) 2018-07-05
US20210190073A1 (en) 2021-06-24
EP3535497A1 (fr) 2019-09-11
JP6793254B2 (ja) 2020-12-02
US11536273B2 (en) 2022-12-27
WO2018083306A1 (fr) 2018-05-11
IT201600111763A1 (it) 2018-05-07

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