EP2489882A2 - Verbesserungen bei Zentrifugalpumpen - Google Patents

Verbesserungen bei Zentrifugalpumpen Download PDF

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Publication number
EP2489882A2
EP2489882A2 EP20110195562 EP11195562A EP2489882A2 EP 2489882 A2 EP2489882 A2 EP 2489882A2 EP 20110195562 EP20110195562 EP 20110195562 EP 11195562 A EP11195562 A EP 11195562A EP 2489882 A2 EP2489882 A2 EP 2489882A2
Authority
EP
European Patent Office
Prior art keywords
sealing ring
turbine
housing
angular
centrifugal pumps
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.)
Withdrawn
Application number
EP20110195562
Other languages
English (en)
French (fr)
Inventor
Marina Soler Álvarez
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.)
DESARROLLOS EMPRESARIALES VALAR SL
Original Assignee
DESARROLLOS EMPRESARIALES VALAR SL
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 DESARROLLOS EMPRESARIALES VALAR SL filed Critical DESARROLLOS EMPRESARIALES VALAR SL
Publication of EP2489882A2 publication Critical patent/EP2489882A2/de
Withdrawn legal-status Critical Current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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel

Definitions

  • the present invention refers to some improvements in centrifugal pumps which are specifically made in a characteristic sealing ring that prevents part of the pumped fluid from passing through an undue area from the discharge chamber to the suction chamber, thereby achieving an increase of the driven flow rate of around 10%, as well as an increase in the hydraulic performance of the pump of around 8%.
  • the typical sealing ring made of a polyamide material, prevents leakage of fluid from the discharge chamber with higher pressure to the suction chamber at a lower pressure, through an undue area corresponding to the support of the front face of the turbine coupled within a housing attached by its axis to a rear support.
  • Centrifugal pumps generally include a pump housing or body (static part) and a centrifugal turbine or runner (rotating part), so that the better the fit between both elements, the better the performance of the pump will be.
  • This intermediate element provided a seal between the suction chamber and the discharge chamber by maintaining a constant radial friction in the suction mouth of the turbine.
  • the invention proposes some improvements in centrifugal pumps that are of the type having a turbine placed inside a housing having a inlet mouth for a fluid and an outlet mouth for the same fluid, in an front support that separates a suction chamber corresponding to the inlet mouth and a discharge chamber corresponding to an internal hole of the body pump wherein the turbine is located, and by a rear support through the motor shaft.
  • the improvements are characterized in that they comprise an axial fluid-tight sealing ring with an angular profile that provides a perimeter sealing between said chambers, while such sealing ring is located in an angular hole established in correspondence with the front support of the turbine.
  • That angular hole is defined between the suction mouth of the turbine and an angular recess of the housing, with the sealing ring being coupled with a certain tightening in the suction mouth of the turbine that rotates dragging the mentioned sealing ring, front section of which axially contacts by its outer flat face against a flat front section of the angular recess of the housing.
  • This axial contact provides the perimeter sealing between the suction chamber and the discharge chamber, such sealing ring being placed into the angular hole of the front support of the turbine with an axial clearance and with a radial clearance as well.
  • the radial clearance of the sealing ring will be delimited between the outer face of its annular path radial section and the curved surface, having also an annular path, of the angular recess of the housing corresponding to the front support of the turbine.
  • the radial clearance of the sealing ring will be between 0.1 mm and 0.8 mm. While the axial clearance of the sealing ring being higher, because of the pressure differences between the two chambers, it is axially moved against the flat front section of the angular recess of the pump housing getting smaller adjustments at 0.1 mm.
  • the sealing ring includes in one of its second embodiments, an axial driving spring device that is integral with said sealing ring itself, pushing the same at all times against the flat front section of the angular recess in the pump housing.
  • the referred spring device is characterized in that it comprises several cantilever elastic wings arranged in the same annular plane of the radial section of the sealing ring, such elastic wings being joined by their ends to some angular extensions starting from the radial section radial of the sealing ring, such elastic wings contacting at all times a front seat that outside limits the terminal portion of the turbine.
  • the elastic wings of the spring device comprise pairs of sections that converge on common raised areas by one end, with this areas being elastically deformed in their support on the front seat of the turbine.
  • the sealing ring is made in all its embodiments of a polyamide material.
  • the mentioned improvements of the invention achieve an increase of the driven flow rate of around 10%, as well as an increase in the pump hydraulic performance of around 8%, because undue leakage of fluid is prevented from the discharge chamber with a higher pressure to the suction chamber with a lower pressure of the fluid.
  • a centrifugal pump 1 comprises in principle a housing 2 as a static element, and a turbine 3 as a dynamic element that rotates by a driving element not shown in the figures, with the interposition of an intermediate shaft 4, so that the housing 2 is closed on the rear side corresponding to the intermediate shaft 4 via a rear cover 5, while on the front side of the housing 2 is located the inlet mouth 6 for the fluid.
  • An outlet mouth 7 for the fluid is radially placed in the housing 2.
  • the turbine is located in an inner hole of the housing 2 establishing the discharge chamber 8, setting the turbine 3 on a rear support 9 of the rear cover 5 and on a front support 10 of the housing 2 with the interposition of a sealing ring 11-12, which as stated earlier, prevents some of the fluid from perimeter passing from the discharge chamber 8 with a higher pressure of the fluid to a suction chamber 13 with a lower pressure of the fluid, with the discharge chamber 8 corresponding with the inner hole of the housing 2 wherein the turbine 3 is located. It should be also note that the inlet mouth 6 for the fluid is continued by the suction chamber 13.
  • the front support 10, wherein the characteristic sealing ring 11-12 is located includes an annular recess 14 faced with a terminal portion 15 of the turbine 3, generating between said annular recess 14 of the housing 2 and the terminal portion 15 of the turbine 3, a small angular hole 16 wherein the sealing ring 11-12 is set with an undetermined axial clearance and with a radial clearance of about 0.5 mm, existing between the annular outer face of the sealing ring 11-12 and the annular surface of the angular recess 14 of the housing 2.
  • the radial clearance can be as large as desired, within reasonable limits, since the sealing ring 11-12 does not generate any radial sealing, but axial, as will be described in detail below.
  • the obstruction on the front support 10 is achieved by the axial pressure exerted by the sealing ring 11-12 against a flat front section 18 of the angular recess 14 made inside the housing 2.
  • the sealing ring 11-12 is freely coupled with some adjustment to the terminal portion 15 of the turbine 3, so that it partially draws on its rotation at all times the sealing ring 11-12.
  • the sealing ring 11 comprises an angular profile consisting of a radial section and a front section.
  • the axial adjustment of the sealing ring 11 against the flat front section 18 of the angular recess 14 of the housing 2 is produced as a result of the pressure differences between the two discharge and suction chambers.
  • the sealing ring 12 comprises an angular structure formed in principle by a radial section and a front section, combined with the addition of an axial driving spring device 17 that is part of the sealing ring 12 itself, such spring device 17 section from the radial section.
  • the spring device 17 always tends to axially the sealing ring 12 against the flat front section 18 of the angular recess 14 of the housing 2 in the centrifugal pump 1, even when it is inactive, thus also avoiding in this position undue leakage of the fluid.
  • the spring device 17 abuts against a front seat 19 which externally defines the terminal portion 15 of the turbine 3.
  • the said spring device 17 comprises several cantilevered elastic wings 20 arranged in the same annular plane as the radial section of the sealing ring 12, such wings being joined by their ends to angular extensions 21 that also start from the radial section of the sealing ring 12.
  • the cantilevered elastic wings 20 comprise pairs of sections that converge on common raised areas by one of their ends, with these areas being elastically deformed on their support against the front seat 19 of the turbine 3, thereby the support of the elastic wings 20 against the front seat 19 axially pushes the sealing ring 12 against the flat front section 18 of the angular recess 14 in the housing 2, thereby producing a more effective seal between the suction chamber 13 with a lower pressure and the discharge chamber 8 with a higher pressure.
  • the sealing ring 11-12 is made of polyamide by using an injection molding process, without excluding other plastic materials.
  • the sealing between the suction chamber 13 and the discharge chamber 8 is the result of the axial friction between the outer side of the front section of the sealing ring 11-12 and flat front section 18 of the angular recess 14 made in the casing 2 of the pump 1.
  • the sealing ring has a sliding fit with the outer area of the mouth of the centrifugal turbine or runner 15, so that the sealing ring will be axially moved until axially rubbing against the flat front section of the angular recess 14 in the housing 2 of the pump 1, resulting in the sealing or hydraulic separation of the suction and discharge chambers.
  • the sealing ring includes into its most advantageous embodiment the spring device 17, so even when the pump at rest, the axial contact between the sealing ring 12 and the flat front section 18 of the angular recess 14 in the housing of the pump is guaranteed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP20110195562 2011-02-21 2011-12-23 Verbesserungen bei Zentrifugalpumpen Withdrawn EP2489882A2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ES201130216A ES2402976B1 (es) 2011-02-21 2011-02-21 Mejoras introducidas en bombas centrífugas

Publications (1)

Publication Number Publication Date
EP2489882A2 true EP2489882A2 (de) 2012-08-22

Family

ID=45491300

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20110195562 Withdrawn EP2489882A2 (de) 2011-02-21 2011-12-23 Verbesserungen bei Zentrifugalpumpen

Country Status (3)

Country Link
EP (1) EP2489882A2 (de)
CN (1) CN102644602A (de)
ES (1) ES2402976B1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112431789A (zh) * 2020-11-25 2021-03-02 上海凯士比泵有限公司 一种具有高效密封性能的密封环

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2869471A (en) * 1957-02-01 1959-01-20 Robert D Copeland Impeller pump, seal and wear ring
US4305595A (en) * 1980-04-30 1981-12-15 Hydril Company Composite seal
US5915921A (en) * 1997-09-26 1999-06-29 Goulds Pumps, Incorporated Wearing ring for volute pump
US6158743A (en) * 1998-06-22 2000-12-12 Stemco Inc Hub seal with low installation load and rotation prevention structure
CN101657661B (zh) * 2007-04-09 2013-02-13 Nok株式会社 密封装置

Also Published As

Publication number Publication date
CN102644602A (zh) 2012-08-22
ES2402976B1 (es) 2014-09-02
ES2402976A2 (es) 2013-05-10
ES2402976R1 (es) 2013-10-04

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