US20170067481A1 - Volute Design For Lower Manufacturing Cost and Radial Load Reduction - Google Patents

Volute Design For Lower Manufacturing Cost and Radial Load Reduction Download PDF

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Publication number
US20170067481A1
US20170067481A1 US15/257,646 US201615257646A US2017067481A1 US 20170067481 A1 US20170067481 A1 US 20170067481A1 US 201615257646 A US201615257646 A US 201615257646A US 2017067481 A1 US2017067481 A1 US 2017067481A1
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United States
Prior art keywords
cutwater
volute
passage
fluid
pumped
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
US15/257,646
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English (en)
Inventor
Paul J. Ruzica
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.)
Fluid Handling LLC
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Fluid Handling LLC
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Filing date
Publication date
Application filed by Fluid Handling LLC filed Critical Fluid Handling LLC
Priority to US15/257,646 priority Critical patent/US20170067481A1/en
Assigned to FLUID HANDLING LLC reassignment FLUID HANDLING LLC ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RUZICKA, PAUL J
Publication of US20170067481A1 publication Critical patent/US20170067481A1/en
Priority to US18/097,645 priority patent/US12313082B2/en
Abandoned legal-status Critical Current

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    • 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
    • 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/428—Discharge tongues

Definitions

  • the present invention relates to a volute for a pump; and more particularly relates to a pump having an improved volute design.
  • FIG. 1 shows a normal or conventional dual volute V pa having a volute wall V wall with a pump inlet represented by the label i and a pump outlet or discharge represented by the label o.
  • the conventional dual volute V pa includes a casing vane CV pa formed therein, which has a lower cutwater c 1 and an upper cutwater c 2 that are arranged on an axis A c1, c2 on opposite sides of the volute wall V wall and about 180° apart in a radial separation, e.g., consistent with that shown in FIG. 1 .
  • the radial degrees of 0°, 90°, 180°, 270° are indicated to provide the reader with an angular radial frame of reference.
  • FIG. 1 also includes a circular dashed line Iv that represents the impeller's outer peripheral vane surface.
  • FIG. 1 also shows the circled reference label 1 as a lower cutwater throat area, the circled reference label 2 as an upper cutwater throat area, the circled reference label 3 as an end of passage for lower cutwater C 1 , and the circled reference label 4 as an end of passage for upper cutwater c 2 .
  • the areas labeled 1 and 2 are equal, and these lower and upper cutwaters c 1 and c 2 are effectively arranged diametrically opposed.
  • the normal double volute V pa utilizes a typical 180 degree opposed casing cutwaters c 1 and c 2 of equal section area labeled 1 and 2 respectively.
  • FIG. 1 shows that for the conventional double volute V the sectional areas labeled 1 and 2 formed between the cutwaters c 1 and c 2 of the casing vane CV pa and the volute wall V wall are substantially equal, and the associated cutwaters c 1 and c 2 are substantially diametrically opposed.
  • sectional areas labeled 1 and 2 respectively are understood to be the minimum area as measured from the furthest radial edge of the cutwaters C 1 and c 2 to the next portion of the vertical wall V wall of the volute V pa .
  • This sectional area is known as the casing throat area.
  • volute design V pa e.g., like that shown in FIG. 1
  • the development of the opposed casing tongues results in a long passage length for cutwater farthest away from the pump discharge o, otherwise know as the upper cutwater C 2 .
  • This long length adds complexity to the casing and increases the difficulty to properly clean the casting. This results in additional costs, and if not properly cast and cleaned will result in loss of pump performance.
  • the present invention provides a new volute design that reduces the radial load on the impeller by establishing an improved pressure balance through the operating flow range of a rotodynamic pump.
  • the present invention may be characterized by the total throat section area required by the volute not being distributed equally as in the conventional known double volute (see FIG. 1 ).
  • the velocities being controlled by these equal sectional areas are also equal as half the pump flow passes through each passage.
  • the area of the throat section of the upper cutwater is increased as a function of the angular sweep as measured along the volute centerline from the cutwater closest to the discharge. As a result of the angular sweep, the rate of flow in this passage is greater than that of a conventional volute (e.g., see FIG. 1 ).
  • the throat area of the cutwater closest to the pump discharge i.e., the lower cutwater
  • the rate flow in this passage is reduced.
  • these unequal sectional areas continue to provide roughly equal velocities at both upper and lower cutwaters.
  • the area of the two passages at the pump discharge is also balanced as a function of the differing rates of flow within these two passages.
  • the present invention reduces the cost and improves the quality of the cast volute.
  • the upper half is greatly simplified as it has no cutwater and the portion of the passage contained in it, thus reducing the cost of the core, simplifying the cleaning and the tooling required to manufacture the casing half, and reducing the cost to produce the casting.
  • a volute for a pump e.g., such as a double volute pump, having the following features:
  • the casing vane may be configured to form double volutes in the volute, configured with an upper cutwater farthest from the pump discharge defining an upper cutwater throat area and an end of passage for the upper cutwater, and also configured with a lower cutwater closest to the pump discharge defining a lower cutwater throat and a corresponding end of passage for the lower cutwater.
  • the upper cutwater throat area may be dimensioned to be greater than and not equal to the lower cutwater throat area so that the upper cutwater throat area and the lower cutwater throat area provide substantially equal flow velocity at both the upper cutwater and the lower cutwater in response to an angular sweep of the fluid being pumped.
  • the end of passage for the upper cutwater may be dimensioned with an upper cutwater passage area that is greater than and not equal to a corresponding lower cutwater passage area of the corresponding end of passage for the lower cutwater so that upper and lower cutwater passage areas at the pump discharge are balanced as a function of differing rates of flow of the fluid being pumped therein and so that the fluid being pumped from associated ends of the upper and lower cutwater passage areas meets at the pump discharge with a substantially equal velocity.
  • the upper cutwater and the lower cutwater may be radially displaced at an angle ⁇ that is in a range of between about 108° and about 110°.
  • Embodiments are also envisioned in which the upper cutwater and the lower cutwater may be radially displaced at an angle ⁇ that is substantially less than 180°, e.g., consistent with that set forth herein.
  • Embodiments are also envisioned in which the upper cutwater and the lower cutwater may be radially displaced at an angle ⁇ that is in a range of between 90° and 120°, e.g., also consistent with that set forth herein.
  • the volute may be configured as part of a double volute pump, e.g., that may include an impeller having impeller vanes and being arranged in one of the double volutes in the casing.
  • the total sum of both the upper and lower casing throats are similar to that of the conventional double volute in FIG. 1 , but are distributed as the included angle of the radial sweep.
  • Similar velocities are maintained at the throat section but are not necessarily equal.
  • the net radial loads acting on the impeller are reduced by the maintenance of the velocities and the pressure balance with in the volute.
  • the exit areas are also distributed in the fraction of the flow rate and are controlled to provide an equal velocity at the end of the passages in the pump discharge.
  • FIG. 1 shows a volute for a pump that is known in the art.
  • FIG. 2 shows a new and improved volute for a pump, according to some embodiments of the present invention.
  • FIG. 2 The Basic Invention
  • FIG. 2 shows the present invention, e.g. in the form of a volute V I for configuring in relation to a pump (not shown), such as a double volute pump.
  • the volute V I may include one or more of the following features:
  • the casing vane CV I may be configured on the volute wall V wall forming double volutes in the volute V I and being configured with an upper cutwater C 2 farthest from the pump discharge o defining an upper cutwater throat area labeled 2 ′ (in a circle) and an end of passage 4 ′ (in a circle) for the upper cutwater C 2 , and also configured with a lower cutwater C 1 closest to the pump discharge o defining a lower cutwater throat labeled 1 ′ (in a circle) and a corresponding end of passage 3 ′ (in a circle) for the lower cutwater C 1 .
  • the upper cutwater throat area label 2 ′ (in a circle) may be dimensioned to be greater than and not equal to the lower cutwater throat area labeled 1 ′ (in a circle) so that the upper cutwater throat area labeled 2 ′ (in a circle) and the lower cutwater throat area labeled 1 ′ (in a circle) provide substantially equal flow velocity at both the upper cutwater C 2 and the lower cutwater C 1 in response to an angular sweep of the fluid being pumped.
  • the end 4 ′ of passage for the upper cutwater C 2 may be dimensioned with an upper cutwater passage area that is greater than and not equal to a corresponding lower cutwater passage area of the corresponding end of passage labeled 3 ′ (in a circle) for the lower cutwater C 1 so that upper and lower cutwater passage areas at the pump discharge are balanced as a function of differing rates of flow of the fluid being pumped therein and so that the fluid being pumped from associated ends of the upper and lower cutwater passage areas labeled 3 ′, 4 ′ (in respective circle) meets at the pump discharge o with a substantially equal velocity.
  • the upper cutwater C 2 and the lower cutwater C 1 are shown to be radially displaced at an angle ⁇ that is in a range of between about 108° and about 110°.
  • embodiments are envisioned, and the scope of the invention is intended to include, using the upper cutwater C 2 and the lower cutwater C 1 radially displaced at an angle ⁇ that is at least substantially less than 180°, so that the fluid being pumped from associated ends of the upper and lower cutwater passage areas labeled 3 ′, 4 ′ (in respective circle) meets at the pump discharge o with a substantially equal velocity.
  • embodiments are envisioned, and the scope of the invention is intended to include, using the upper cutwater C 2 and the lower cutwater C 1 radially displaced at an angle ⁇ that is in a range of between 100° and 120°, so that the fluid being pumped from associated ends of the upper and lower cutwater passage areas labeled 3 ′, 4 ′ (in respective circle) meets at the pump discharge o with a substantially equal velocity.
  • the scope of the invention is intended to include, embodiments having non-diametrically opposed radially displaced upper cutwater C 2 and the lower cutwater C 1 , for example, that are not radially displaced at any specific angle ⁇ that is in the range of between about 108° and about 110°, but where the fluid being pumped from associated ends of the upper and lower cutwater passage areas labeled 3 ′, 4 ′ (in respective circle) meets at the pump discharge o with a substantially equal velocity.
  • possible applications of the present invention may include the following:

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US15/257,646 2015-09-03 2016-09-06 Volute Design For Lower Manufacturing Cost and Radial Load Reduction Abandoned US20170067481A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US15/257,646 US20170067481A1 (en) 2015-09-03 2016-09-06 Volute Design For Lower Manufacturing Cost and Radial Load Reduction
US18/097,645 US12313082B2 (en) 2015-09-03 2023-01-17 Volute design for lower manufacturing cost and radial load reduction

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562213739P 2015-09-03 2015-09-03
US15/257,646 US20170067481A1 (en) 2015-09-03 2016-09-06 Volute Design For Lower Manufacturing Cost and Radial Load Reduction

Related Child Applications (1)

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US18/097,645 Continuation US12313082B2 (en) 2015-09-03 2023-01-17 Volute design for lower manufacturing cost and radial load reduction

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US20170067481A1 true US20170067481A1 (en) 2017-03-09

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US15/257,646 Abandoned US20170067481A1 (en) 2015-09-03 2016-09-06 Volute Design For Lower Manufacturing Cost and Radial Load Reduction
US18/097,645 Active 2036-09-26 US12313082B2 (en) 2015-09-03 2023-01-17 Volute design for lower manufacturing cost and radial load reduction

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US (2) US20170067481A1 (enExample)
EP (1) EP3344878B1 (enExample)
JP (1) JP6989492B2 (enExample)
CN (1) CN108026933B (enExample)
AU (1) AU2016315477B2 (enExample)
CA (1) CA2996964C (enExample)
ES (1) ES2983042T3 (enExample)
WO (1) WO2017041099A1 (enExample)

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Publication number Priority date Publication date Assignee Title
US20170363324A1 (en) * 2016-06-15 2017-12-21 Regal Beloit America, Inc. Water Heater Blower Assembly Having a Low Exhaust Port
US20210239122A1 (en) * 2018-06-08 2021-08-05 Pierburg Pump Technology Gmbh Electric coolant pump
FR3112823A1 (fr) * 2020-07-23 2022-01-28 Safran Aircraft Engines pompe centrifuge à double volute à section croissante non-linéaire
US11306944B2 (en) 2016-06-15 2022-04-19 Regal Beloit America, Inc. Water heater blower assembly having a low exhaust port
US20230235751A1 (en) * 2015-09-03 2023-07-27 Fluid Handling Llc Volute Design For Lower Manufacturing Cost and Radial Load Reduction

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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
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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230235751A1 (en) * 2015-09-03 2023-07-27 Fluid Handling Llc Volute Design For Lower Manufacturing Cost and Radial Load Reduction
US12313082B2 (en) * 2015-09-03 2025-05-27 Fluid Handling Llc Volute design for lower manufacturing cost and radial load reduction
US20170363324A1 (en) * 2016-06-15 2017-12-21 Regal Beloit America, Inc. Water Heater Blower Assembly Having a Low Exhaust Port
US10443891B2 (en) * 2016-06-15 2019-10-15 Regal Beloit America, Inc. Water heater blower assembly having a low exhaust port
US11215379B2 (en) * 2016-06-15 2022-01-04 Regal Beloit America, Inc. Water heater blower assembly having a low exhaust port
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US20210239122A1 (en) * 2018-06-08 2021-08-05 Pierburg Pump Technology Gmbh Electric coolant pump
FR3112823A1 (fr) * 2020-07-23 2022-01-28 Safran Aircraft Engines pompe centrifuge à double volute à section croissante non-linéaire

Also Published As

Publication number Publication date
CA2996964C (en) 2022-02-22
AU2016315477A1 (en) 2018-03-15
AU2016315477B2 (en) 2021-04-01
JP6989492B2 (ja) 2022-01-05
EP3344878A1 (en) 2018-07-11
EP3344878C0 (en) 2024-07-03
ES2983042T3 (es) 2024-10-21
CN108026933B (zh) 2021-04-27
WO2017041099A1 (en) 2017-03-09
EP3344878A4 (en) 2019-03-20
CA2996964A1 (en) 2017-03-09
US20230235751A1 (en) 2023-07-27
CN108026933A (zh) 2018-05-11
EP3344878B1 (en) 2024-07-03
JP2018526573A (ja) 2018-09-13
US12313082B2 (en) 2025-05-27

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