EP0952352A2 - Equilibrage de poussée axiale - Google Patents

Equilibrage de poussée axiale Download PDF

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Publication number
EP0952352A2
EP0952352A2 EP99107770A EP99107770A EP0952352A2 EP 0952352 A2 EP0952352 A2 EP 0952352A2 EP 99107770 A EP99107770 A EP 99107770A EP 99107770 A EP99107770 A EP 99107770A EP 0952352 A2 EP0952352 A2 EP 0952352A2
Authority
EP
European Patent Office
Prior art keywords
thrust balance
fluid
pressure
impeller
thrust
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
EP99107770A
Other languages
German (de)
English (en)
Other versions
EP0952352A3 (fr
EP0952352B1 (fr
Inventor
Yasushi c/oNikkiso Co. Ltd. Kubota
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.)
Nikkiso Co Ltd
Original Assignee
Nikkiso Co Ltd
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Filing date
Publication date
Application filed by Nikkiso Co Ltd filed Critical Nikkiso Co Ltd
Publication of EP0952352A2 publication Critical patent/EP0952352A2/fr
Publication of EP0952352A3 publication Critical patent/EP0952352A3/fr
Application granted granted Critical
Publication of EP0952352B1 publication Critical patent/EP0952352B1/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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons

Definitions

  • the present invention relates to a thrust balance device. More specifically, the present invention relates to a thrust balance device significantly improving thrust balance in a device such as a canned motor pump.
  • Conventional canned motor pumps include an impeller mounted on a rotating shaft.
  • a fluid is sucked through a suction opening i.e. inlet which opens axially.
  • Centrifugal force from the impeller causes discharge of the sucked fluid from radial discharging openings i.e. outlet. Since the suction opening is oriented toward an end of the rotation shaft, a force is applied on the impeller in the direction of thrust.
  • the impeller is pushed toward an inner wall of the chamber holding the impeller. This pushing force interferes with the rotation of the impeller.
  • almost all recent canned motor pumps are equipped with a thrust balance mechanism.
  • a thrust balance mechanism prevents obstruction of the rotation of the impeller caused by the pressure of the sucked fluid.
  • a thrust balance mechanism includes:
  • the centrifugal force from the rotation of the impeller causes fluid to be discharged radially.
  • a portion of the fluid discharged in the centrifugal direction flows into the thrust balance chamber via the fixed orifice.
  • the fluid which enters the thrust balance chamber flows out from the thrust balance chamber through the variable orifice.
  • the fluid exiting the thrust balance chamber passes through the balance hole and combines with the fluid to be discharged.
  • the gap in the variable orifice increases when the impeller is displaced away from the casing surface facing its rear surface, i.e., when the impeller is shifted so that it moves away from the casing surface facing the rear surface of the impeller.
  • This movement causes high-pressure fluid to flow rapidly from the variable orifice.
  • fluid pressure within the thrust balance chamber drops.
  • the pressure in the thrust direction applied to the impeller from the fluid being sucked and discharged becomes greater than the fluid pressure within the thrust balance chamber.
  • the pressure in the thrust direction causes the impeller to shift toward the casing surface facing the rear surface of the impeller.
  • the impeller changes its position according to the gap in the fixed orifice, the gap in the variable orifice, as well as the volume of the thrust balance chamber.
  • the change of position of the impeller maintains balance for the rotating axis along the thrust direction.
  • the rear surface of the impeller is a rotating surface, while the casing surface facing the impeller is a fixed surface.
  • fluid flowing into the thrust balance chamber receives an angular momentum energy from the impeller rotation.
  • fluid flowing into the thrust balance chamber rotates together with the impeller.
  • the fluid rotating in the thrust balance chamber with the impeller generates a very high flow-path resistance.
  • the flow-path resistance of the fluid interposed between the rotating surface and the fixed surface is proportional to the square of the peripheral speed of the fluid rotating with the rotating surface.
  • the flow-path resistance of the fluid in the thrust balance chamber thereof is high.
  • the flow-path resistance of the fluid in the thrust balance chamber thereof is also high. Such a high flow-path resistance prevents the thrust balance of the pump from being maintained appropriately.
  • bypass structures known as pressure-equalizing holes or pressure-decreasing holes have been conventionally formed in the fixed surface of the thrust balance chamber.
  • these pressure-equalizing holes have been unable to lower the flow-path resistance and maintain thrust balance. While forming this kind of bypass may be able to increase the independent pressure, this kind of bypass cannot significantly reduce the angular momentum of the fluid inside the thrust chamber.
  • the present invention provides a flow channel and pressure equalizing sections introducing a fluid having substantially no angular momentum into a thrust balance chamber of a thrust balance device.
  • the introduction of this fluid reduces the angular momentum of the fluid in the thrust balance chamber, facilitating the discharge of fluid out of the thrust balance chamber through the variable orifice.
  • the thrust balance chamber exerts a variable pressure onto a rear surface of an impeller of a centrifugal pump. This pressure prevents significant displacement of the impeller during pump operation. Therefore, the present invention provides a centrifugal pump with a good thrust balance property regardless of flow rate and impeller speed of the centrifugal pump.
  • a thrust balance device in a centrifugal pump comprising a fixed orifice permitting flow of a portion of a fluid passing through the centrifugal pump into a thrust balance chamber of the thrust balance device, the thrust balance chamber facing the rear surface of the impeller in the centrifugal pump, a variable orifice permitting a variable flow of the portion from the thrust balance chamber depending on a balance between a fluid pressure in the thrust balance chamber and the pressure from the fluid being pumped, and means for introducing a fluid having substantially no angular momentum into the thrust balance chamber, whereby the introduced fluid facilitates the flow of the portion to flow out through the variable orifice.
  • a thrust control device for controlling an axial position of an impeller of a centrifugal pump, comprising an impeller having a first surface exposed to a pressure of a fluid being pumped, a thrust balance chamber adjacent a second surface of the impeller, at least one balance hole communicating between the first surface and the second surface, a projection facing the second surface of the impeller, a fixed orifice permitting a controlled leakage of the fluid from an outlet of the centrifugal pump into the thrust balance chamber, a variable orifice adjusting flow rate of fluid flowing out from the thrust balance chamber when the impeller is displaced axially at a predetermined distance in the direction toward said projection, whereby the controlled leakage is enabled to increase a fluid pressure in the thrust balance chamber, and thereby to resist axial displacement of the impeller in said direction, and at least one stationary flow channel conveying a portion of the fluid with substantially reduced angular momentum to the thrust balance chamber.
  • a device for feeding fluid having substantially no angular velocity to a thrust balance chamber of a centrifugal pump comprising a radially arranged opening and a ring-shaped groove opening at the thrust balance chamber.
  • the ring-shaped groove connects the inner end of the opening with the thrust balance chamber. The fluid is accepted at the outer end of the opening and conducted to its inner end, then fed into the thrust balance chamber through the ring-shaped groove.
  • the device for feeding fluid having substantially no angular velocity to the thrust balance chamber can have a plurality of the radially arranged openings.
  • both of the opening area of the ring-shaped groove and the sum total of the cross-sectional area of the radially arranged opening(s) are preferably larger than the opening area of the balance hole of the impeller.
  • the present invention achieves these objects by providing a thrust balance device that includes the following elements:
  • a centrifugal pump 1 equipped with a thrust balance device includes an impeller 6 mounted on a rotating axis 5. Impeller 6 is positioned in a pump chamber 4 formed by a casing 2 and a liner disk 3.
  • a suction opening of centrifugal pump 1 (not shown) is formed at an axial orientation relative to impeller 6.
  • Impeller 6 includes a base 8 which has a circular shape when seen from an axial direction. Impeller 6 rotates together with rotating axis 5, discharging fluid introduced through guide path 7 in a centrifugal direction. Thus, in centrifugal pump 1, a discharging opening (not shown) is formed centrifugally in the relationship to impeller 6.
  • a cylinder 9 projects from a rear surface, i.e. the surface facing liner disk 3, of base 8, which is a section of impeller 6. Cylinder 9 projects toward liner disk 3. Furthermore, a balance hole 10 extends from the rear surface of base 8 to the front surface thereof toward guide path 7.
  • a cavity 11 is formed on a surface of liner disk 3 facing base 8.
  • Cavity 11 has a cylindrical inner perimeter surface which has an inner diameter slightly larger than a diameter of cylinder 9.
  • a slight gap is formed between an outer perimeter surface of cylinder 9 and an inner perimeter surface of cavity 11. This gap serves as a fixed orifice 12.
  • An end surface of first projection 13 facing a bottom surface of cylinder 9 has a ring shape.
  • a thrust balance chamber 15 is formed as a space created between the ring-shaped end surface of first projection 13 (this surface is also a fixed surface) and a bottom surface of cylinder 9 (this surface is the rear surface of impeller 6 and is also a rotating surface).
  • a variable orifice 16 is formed of a space between the ring-shaped end surface of second projection 14 and a bottom surface of cylinder 9, i.e. the rear surface of base 8.
  • a ring-shaped groove 17, centered on rotating axis 5, is positioned between first projection 13 and second projection 14.
  • Ring-shaped groove 17 has a space surrounded by an opening facing a ring-shaped end surface of first projection 13, an inward inner perimeter surface which is an outer perimeter surface of a cylinder, and an outward inner perimeter surface which is an inner perimeter surface of a cylinder.
  • the resulting space is a ring-shaped space centered on rotating axis 5.
  • Fig. 1 which is a longitudinal section of the centrifugal pump 1
  • a line representing a longitudinal section of an inward inner perimeter surface of ring-shaped groove 17 is parallel with a line representing a longitudinal section of an outward inner perimeter surface of ring-shaped groove 17.
  • Pressure-equalizing sections 18 are openings extending from an outer perimeter surface of first projection 13 to ring-shaped groove 17. Pressure-equalizing sections 18 are connected with ring-shaped groove 17 and cavity 11, Preferably, twelve pressure-equalizing sections 18 are formed at first projection 13. Each of pressure-equalizing sections 18 has a circular cross-sections cut along a plane perpendicular to the axis thereof. In other words, pressure-equalizing sections 18 have cylindrical inner spaces.
  • centrifugal pump 1 operates together with the thrust balance device of the present invention.
  • Rotating axis 5 rotates together with impeller 6. Fluid introduced from the suction opening flows through guide path 7 into pump chamber 4. Since impeller 6 is rotating inside pump chamber 4, the fluid is discharged through a discharging opening by centrifugal force. This is the standard operation of centrifugal pump 1.
  • the fluid passes through variable orifice 16 and balance hole 10 to return to a front side of impeller 6.
  • Fluid inside thrust balance chamber 15 rotates together with the rotation of impeller 6. Fluid rotating inside thrust balance chamber 15 has an angular momentum and generates flow-path resistance. If this flow-path resistance is high, the flow of fluid in thrust balance chamber 15 through variable orifice 16 is hindered, even when the opening in variable orifice 16 enlarges.
  • the object of the present invention is to reduce the flow-path resistance caused by the angular momentum of the fluid in thrust balance chamber 15. Ring-shaped groove 17 and pressure-equalizing sections 18 help achieve this goal. Fluid having no angular momentum flows from pressure-equalizing sections 18 into thrust balance chamber 15 via ring-shaped groove 17, mixing with fluid having angular momentum. The addition of a fluid having no angular momentum into thrust balance chamber 15 dramatically reduces the angular momentum of fluid in thrust balance chamber 15. Thus, by reducing the flow-path resistance caused by angular momentum of fluid in thrust balance chamber 15, fluid in thrust balance chamber quickly and smoothly flows out through variable orifice 16.
  • a computer was used to simulate the thrust balance in rotating axis 5 for a pump having pressure-equalizing sections 18 and ring-shaped groove 17 versus a pump having only pressure-equalizing sections 18.
  • the outgoing flow from variable orifice 16 was 290 liters/min. for the pump having only pressure-equalizing sections 18.
  • the flow pressure at the backside of impeller 6 was 2363 N (241 kgf).
  • the outgoing flow from variable orifice 16 was 301 liters/min.
  • the groove space of ring-shaped groove 17 formed on first projection 13 can be of any shape, as long as it surrounds rotating axis 5.
  • Ring-shaped groove 17 has a groove space surrounded by an opening facing the ring-shaped end surface of first projection 13, an inward inner perimeter surface corresponding to an outer perimeter surface of a cylinder co-axial with rotating axis 5, and an outward inner perimeter surface corresponding to an inner perimeter surface of a cone that is co-axial with rotating axis 5.
  • the longitudinal section of the groove space of ring-shaped groove 17 of this embodiment of the present invention forms a wedge shape as shown in Fig. 2.
  • Ring-shaped groove 17 has a groove space surrounded by an opening facing a ring-shaped end surface of first projection 13, an inward inner perimeter surface corresponding to on outer perimeter surface of a cone that is co-axial with rotating axis 5, and an outward inner perimeter surface corresponding to an inner perimeter surface of a cone that is co-axial with rotating axis 5.
  • the longitudinal section of the groove space of ring-shaped groove 17 of this embodiment forms a wedge shape having a configuration opposite of the wedge shape of the embodiment shown in Fig. 2.
  • ring-shaped groove 17 has a groove space surrounded by an opening facing a ring-shaped end surface of first projection 13, an inward inner perimeter surface corresponding to an outer perimeter surface of a cone that is co-axial with rotating axis 5, and an outward inner perimeter surface of a cone that is co-axial with rotating axis 5.
  • the longitudinal section of the groove space of ring-shaped groove 17 of this embodiment of the present Invention forms a v-shape.
  • A the sum total of the cross-sectional area of each of pressure-equalizing sections 18 cut along the plane perpendicular to the axis thereof or the circular cross-section area of pressure-equalizing sections 18 (A is calculated as n ⁇ ( ⁇ /4) ⁇ d 1 2 , where n is the number of pressure-equalizing sections 18 and d 1 is the diameter of the circular cross-section) is equal to or smaller than B, an area of the opening of ring-shaped groove 17 (B is calculated as ( ⁇ /4) ⁇ (D 2 2 -D 3 2 , where D 2 and D 3 are the outer and inner diameters of the opening of ring-shaped groove 17, respectively), i.e. A ⁇ B.
  • the present invention provides a thrust balance device having superior thrust balance properties, Furthermore, the present invention provides a thrust balance device having good thrust balance properties, regardless of the discharge from the pump. The present invention also provides a thrust balance device having good thrust balance properties, regardless of the speed of rotation of the impeller.
  • a difference between the fluid pressure in thrust balance chamber 15 and the discharge pressure at impeller 6, i.e., remaining thrust was measured with varying discharge of the canned motor pump from 10 to 140 m 3 /hr.
  • Both of A, the sum total of the areas of the circular cross section of pressure-equalizing sections 18 and B, the area of the opening of ring-shaped groove 17 were larger than the sum total of the area of the openings of balancing holes 10 on base 8. Further, A is less than B. Applying an alternating current of 50 Hz drove the canned motor pump. Results are shown in Fig.5.
  • the above canned motor pump showed a maximum remaining thrust of about 70 kgf.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP99107770A 1998-04-20 1999-04-19 Equilibrage de poussée axiale Expired - Lifetime EP0952352B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP10972098 1998-04-20
JP10972098 1998-04-20

Publications (3)

Publication Number Publication Date
EP0952352A2 true EP0952352A2 (fr) 1999-10-27
EP0952352A3 EP0952352A3 (fr) 2001-05-30
EP0952352B1 EP0952352B1 (fr) 2004-12-22

Family

ID=14517524

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99107770A Expired - Lifetime EP0952352B1 (fr) 1998-04-20 1999-04-19 Equilibrage de poussée axiale

Country Status (5)

Country Link
EP (1) EP0952352B1 (fr)
KR (1) KR100295011B1 (fr)
CN (1) CN1120937C (fr)
DE (1) DE69922729T2 (fr)
TW (1) TW406166B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010091036A1 (fr) * 2009-02-06 2010-08-12 Fluid Equipment Development Company, Llc Procédé et appareil pour lubrifier un palier de butée pour une machine rotative mettant en oeuvre un pompage
US10801512B2 (en) 2017-05-23 2020-10-13 Vector Technologies Llc Thrust bearing system and method for operating the same
US11085457B2 (en) 2017-05-23 2021-08-10 Fluid Equipment Development Company, Llc Thrust bearing system and method for operating the same

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4281614B2 (ja) * 2004-05-10 2009-06-17 株式会社日立プラントテクノロジー ポンプ装置
CN100368689C (zh) * 2004-09-16 2008-02-13 北京化工大学 一种用于旋转流体机械的压差式推力平衡装置
CN101113741B (zh) * 2006-07-26 2011-03-16 上海新沪电机厂有限公司 一种屏蔽泵轴向力的自动平衡装置
KR101509814B1 (ko) * 2009-12-02 2015-04-06 현대자동차주식회사 임펠러의 들뜸 현상이 개선된 인라인 타입 냉각수 펌프
DE102009060549A1 (de) * 2009-12-23 2011-06-30 Wilo Se, 44263 EC-Motorkreiselpumpe
KR101700332B1 (ko) 2015-07-29 2017-02-14 한국해양대학교 산학협력단 반경류 터빈의 추력감소 장치
ITUA20163303A1 (it) * 2016-05-10 2017-11-10 Ind Saleri Italo Spa Gruppo pompa ad azionamento elettrico ed azionamento meccanico con girante supportata
CN109281861A (zh) * 2018-11-28 2019-01-29 珠海格力电器股份有限公司 一种轴向力自动平衡装置、水泵及空调器
CN114483640B (zh) * 2022-01-25 2022-10-28 威乐(中国)水泵系统有限公司 一种离心泵用叶轮和紧凑型工业制冷用泵

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2105485A1 (de) * 1970-08-06 1972-04-06 Nikkiso C Ltd Axialdruckausgleichsvornchtung fur Motorpumpen
US5320482A (en) * 1992-09-21 1994-06-14 The United States Of America As Represented By The Secretary Of The Navy Method and apparatus for reducing axial thrust in centrifugal pumps
EP0688955A1 (fr) * 1994-06-23 1995-12-27 KSB Aktiengesellschaft Dispositif pour l'équilibrage de la poussée axiale dans les pompes centrifuges

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2105485A1 (de) * 1970-08-06 1972-04-06 Nikkiso C Ltd Axialdruckausgleichsvornchtung fur Motorpumpen
US5320482A (en) * 1992-09-21 1994-06-14 The United States Of America As Represented By The Secretary Of The Navy Method and apparatus for reducing axial thrust in centrifugal pumps
EP0688955A1 (fr) * 1994-06-23 1995-12-27 KSB Aktiengesellschaft Dispositif pour l'équilibrage de la poussée axiale dans les pompes centrifuges

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010091036A1 (fr) * 2009-02-06 2010-08-12 Fluid Equipment Development Company, Llc Procédé et appareil pour lubrifier un palier de butée pour une machine rotative mettant en oeuvre un pompage
US10801512B2 (en) 2017-05-23 2020-10-13 Vector Technologies Llc Thrust bearing system and method for operating the same
US11085457B2 (en) 2017-05-23 2021-08-10 Fluid Equipment Development Company, Llc Thrust bearing system and method for operating the same

Also Published As

Publication number Publication date
EP0952352A3 (fr) 2001-05-30
CN1232928A (zh) 1999-10-27
KR100295011B1 (ko) 2001-07-12
KR19990083231A (ko) 1999-11-25
DE69922729D1 (de) 2005-01-27
TW406166B (en) 2000-09-21
EP0952352B1 (fr) 2004-12-22
DE69922729T2 (de) 2005-12-01
CN1120937C (zh) 2003-09-10

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