US20080019831A1 - Centrifugal Pump - Google Patents

Centrifugal Pump Download PDF

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Publication number
US20080019831A1
US20080019831A1 US11/631,483 US63148304A US2008019831A1 US 20080019831 A1 US20080019831 A1 US 20080019831A1 US 63148304 A US63148304 A US 63148304A US 2008019831 A1 US2008019831 A1 US 2008019831A1
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US
United States
Prior art keywords
centrifugal pump
main shaft
casing
pump according
outer barrel
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
US11/631,483
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English (en)
Inventor
Kenichi Kajiwara
Junya Kawabata
Sou Kuroiwa
Tetsutaro Fujiwara
Shoji Ito
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.)
Ebara Corp
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Individual
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Filing date
Publication date
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Assigned to EBARA CORPORATION reassignment EBARA CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ITO, SHOJI, KAJIWARA, KENICHI, FUJIWARA, TETSUTARO, KAWABATA, JUNYA, KUROIWA, SOU
Publication of US20080019831A1 publication Critical patent/US20080019831A1/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
    • 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
    • F04D29/4286—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps inside lining, e.g. rubber
    • 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
    • F04D1/066—Multi-stage pumps of the vertically split casing type the casing consisting of a plurality of annuli bolted together
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials 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
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals
    • 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
    • F05D2230/00—Manufacture
    • F05D2230/20—Manufacture essentially without removing material
    • F05D2230/23—Manufacture essentially without removing material by permanently joining parts together
    • F05D2230/232—Manufacture essentially without removing material by permanently joining parts together by welding
    • F05D2230/234—Laser welding
    • 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
    • F05D2260/00—Function
    • F05D2260/95—Preventing corrosion
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/10—Metals, alloys or intermetallic compounds
    • F05D2300/17—Alloys
    • F05D2300/171—Steel alloys

Definitions

  • the present invention relates to a centrifugal pump, and more particularly to a centrifugal pump having at least one impeller fixed to a main shaft and at least one casing which houses the impeller and is formed through press working (press forming) of sheet metal such as a steel plate.
  • a multistage pump which comprises a plurality of impellers fixed to a main shaft coupled to a prime mover such as a motor and a plurality of stacked interstage casings for housing the respective impellers.
  • FIG. 9 is a vertical cross-sectional view showing an example of a conventional vertical-type multistage pump disclosed in Japanese laid-open patent publication No. 2003-214383.
  • the conventional vertical-type multistage pump comprises a plurality of vertically stacked interstage casings 101 which are formed through press working of a steel plate, an upper casing 102 provided on the uppermost interstage casing 101 , a lower casing 103 provided under the lowermost interstage casing 101 , and an outer casing 104 which houses the vertically stacked interstage casings 101 and the upper casing 102 and is connected to the lower casing 103 .
  • a casing cover 105 is provided at upper open ends of the upper casing 102 and the outer casing 104 to seal the upper casing 102 and the outer casing 104 hermetically.
  • a plurality of impellers 111 are fixed to a main shaft 110 , and each of the impellers 111 is housed in each of the interstage casings 101 .
  • a mechanical seal 112 is mounted on the upper portion of the main shaft 110 to perform a shaft seal of the portion where the main shaft 110 passes through the casing cover 105 .
  • a motor base 106 for supporting a motor (not shown) is provided on the casing cover 105 .
  • liquid drawn in from the suction port 103 a of the lower casing 103 is introduced into the first-stage impeller 111 through the lower casing 103 , and is pressurized by the first-stage impeller 111 rotated by the main shaft 110 .
  • the pressurized liquid passes through passages defined by the return blades 134 , and is then introduced into the next-stage impeller 111 .
  • the liquid is pressurized by each of the impellers 111 in each of the interstage casings 101 , and the pressure head of the liquid is recovered while the liquid passes through the passages defined by the return blades 134 .
  • the liquid passes through the upper casing 102 and then the annular passage 155 defined between the outer casing 104 and the multistage interstage casings 101 , and is then discharged from the discharge port 103 b of the lower casing 103 to the outside of the pump.
  • the upper open ends of the upper casing 102 and the outer casing 104 are hermetically sealed by the casing cover 105 which is formed through press working of a stainless steel plate.
  • the casing cover 105 since high fluid pressure created by the multistage impellers is applied to the casing cover 105 , the casing cover 105 is required to have relatively high rigidity.
  • the mechanical seal 112 is provided at the portion where the main shaft 110 passes through the casing cover 105 .
  • the mechanical seal 112 is required to be replaced in such a state that the multistage impellers 111 and the multistage interstage casings 101 are removed from the pump.
  • replacement work of the mechanical seal 112 is complicated and troublesome.
  • the interstage casing 101 is substantially in the form of a cylindrical receptacle, and the bottom portion 101 a of the interstage casing 101 is formed into a flat shape. Therefore, the bottom portion 101 a of the interstage casing 101 is liable to be deformed in an axial direction (downward direction) of the interstage casing 101 .
  • the present invention has been made in view of the above drawbacks. It is therefore of an object of the present invention to provide a centrifugal pump which can not only enhance rigidity of a member having a function of a casing cover for hermetically sealing upper open ends of an upper casing and an outer casing but also reduce material cost of such a member, can facilitate replacement of a mechanical seal to improve maintenance efficiency, and can increase pressure resistance of a bottom portion of an interstage casing.
  • a centrifugal pump comprising: at least one impeller fixed to a main shaft coupled to a prime mover; at least one casing provided so as to correspond to the impeller; a casing cover configured to seal an open end of the casing hermetically; and a shaft seal device provided at a portion where the main shaft passes through the casing cover; wherein the casing cover comprises a thick member made of castings, and a thin corrosion-resistant lining member which is tightly fixed to the thick member.
  • the casing cover for covering the open end of the pump casing tightly comprises a thick member made of castings, and a thin corrosion-resistant lining member made of a pressed component and adhering to an outer surface of the thick member, rigidity and corrosion resistance of the casing cover can be ensured, and press working of the thin lining member can be easily performed. Further, since the lining member comprises a thin-wall member, material cost of the lining member can be reduced.
  • the lining member may comprise a press-formed member.
  • the lining member may be tightly fixed to said thick member by press fitting.
  • the thick member may have a hollow cylindrical portion which allows the main shaft to pass therethrough, and the lining member may have an annular portion which is fitted over the hollow cylindrical portion.
  • an end portion of the annular portion of the lining member may *be expanded radially outwardly so that said lining member is not detached from said thick member.
  • the end portion of the annular portion of the lining member may be expanded radially outwardly in a tapered shape so that the end portion of the annular portion of the lining member serves to guide a gasket of the shaft seal device when the gasket is inserted into the annular portion of the lining member.
  • the thick member of the casing cover may have a communication hole through which an atmospheric side and a liquid side communicate with each other, a corrosion-resistant pipe may be fitted into the communication hole, and the pipe and the corrosion-resistant lining member may be joined by welding.
  • the welding may be laser welding.
  • a centrifugal pump may further comprise an outer barrel for preventing pressure liquid generated by operation of the pump from leaking to the outside of the pump, the outer barrel having at least one formed portion for mounting an O-ring at one end or both ends of the outer barrel.
  • an end portion of the formed portion of the outer barrel may be expanded -radially outwardly to prevent the O-ring from falling off.
  • a tapered portion expanded radially outwardly may be formed on a member to which the outer barrel is attached so that insertion of the O-ring held by said outer barrel is facilitated.
  • a centrifugal pump comprising: at least one impeller fixed to a main shaft coupled to a prime mover; at least one casing provided so as to correspond to the impeller; the centrifugal pump comprising a multistage pump; the casing including a plurality of stacked interstage casings which house a plurality of impellers, respectively; the interstage casing comprising a first cylindrical portion, a first bottom portion which is held in contact with an axial end face of an adjacent interstage casing, a second cylindrical portion extending axially from the first bottom portion, and a second bottom portion extending radially inward from the second cylindrical portion; and the second bottom portion of the interstage casing being formed into a curved shape of a hemisphere or substantially a hemisphere.
  • a plurality of stacked interstage casings which house a plurality of impellers are substantially in the form of a cylindrical receptacle having a bottom portion, and the bottom portion of each interstage casing is formed into a curved shape of a hemisphere or substantially a hemisphere, and hence the interstage casing has a high pressure resistance. Therefore, the optimum interstage casing configured to accommodate high pressure liquid can be constructed.
  • a suction plate may be attached to the second bottom portion of the interstage casing so that an outer circumferential end face of the suction plate is held in contact with an inner surface of a first cylindrical portion of the adjacent interstage casing; and the suction plate, the second cylindrical portion, the first bottom portion, and the inner surface of the first cylindrical portion of the adjacent interstage casing may form a space for accommodating an O-ring.
  • return guide vanes may be interposed between the suction plate and a side plate.
  • a baffle may be provided in the interstage casing so as to cover at least one formed portion located at a corner between the first cylindrical portion and the second bottom portion.
  • the baffle may have a plurality of notches at a radially inner portion thereof.
  • the maximum diameter of the notch may be smaller than the outer diameter of the impeller.
  • a centrifugal pump comprising: at least one impeller fixed to a main shaft coupled to a prime mover; at least one casing provided so as to correspond to the impeller; a casing cover configured to seal an open end of the casing hermetically; and a mechanical seal provided at a portion where the main shaft passes through the casing cover; wherein the mechanical seal comprises a sleeve which holds a rotating seal ring and is fixed to the main shaft, and a holder configured to hold a stationary seal ring, the holder comprising a cylindrical member which holds a seal member for sealing liquid between the casing cover and the cylindrical member, and a disk member; and wherein the cylindrical member and the disk member are joined together to form the holder.
  • the mechanical seal comprises a cartridge type mechanical seal
  • the cartridge type mechanical seal can be mounted on or detached from the main shaft from the location above the main shaft. Therefore, it is not necessary to remove the multistage interstage casings, the multistage impellers, and the like in order to replace the mechanical seal.
  • the holder which holds the stationary assembly (including the stationary seal ring) of the mechanical seal comprises the cylindrical member and the disk member which are joined together, the cylindrical member can be formed by working a pipe slightly, and the disk member can be easily formed by blanking or the like. Therefore, the holder having a flange can be manufactured by minimum working processes, and thus manufacturing cost can be greatly reduced.
  • the disk member may comprise a flat plate made of sheet metal.
  • the cylindrical member and the disk member may be welded by lasers.
  • a gap which is longer than the overall length of the mechanical seal may be formed between the main shaft of the pump and a main shaft of the prime mover, and the mechanical seal may be removed through the gap by removing a coupling which couples the main shaft of the pump and the main shaft of the prime mover.
  • a centrifugal pump comprising: at least one impeller fixed to a main shaft coupled to a prime mover; at least one casing provided so as to correspond to the impeller; a casing cover configured to seal an open end of the casing hermetically; a mechanical seal provided at a portion where the main shaft passes through the casing cover; wherein the mechanical.
  • seal comprises a sleeve which holds a rotating seal ring and is fixed to the main shaft, and a holder configured to hold a stationary seal ring, the holder comprising a cylindrical member which holds a seal member for sealing liquid between the casing cover and the cylindrical member, and a disk member; and wherein a positioning member is attached to the main shaft, and the sleeve of the mechanical seal is held into contact with the positioning member, thereby positioning the mechanical seal.
  • the mechanical seal when the mechanical seal is mounted on the main shaft of the pump, the end portion of the mechanical seal is brought into contact with the positioning member fixed to the main shaft. Therefore, the mechanical seal can be disposed at an exact position with respect to the main shaft. Thus, the stationary seal ring and the rotating seal ring are held at optimum positions.
  • the holder may have a step-like portion for holding the stationary seal ring.
  • a centrifugal pump comprising: at least one impeller fixed to a main shaft coupled to a prime mover, the main shaft having a plurality of grooves in an outer circumferential surface thereof for allowing the impeller to be fitted over and allowing the impeller to be prevented from being rotated with respect to the main shaft; at least one casing provided so as to correspond to the impeller; a positioning member for positioning the impeller with respect to an axial direction of the main shaft; and a retainer having a circular disk portion which is brought into contact with an end surface of the positioning member, and a cylindrical portion extending from the circular disk portion so as to enclose an outer peripheral portion of the positioning member.
  • a positioning member for positioning the impeller with respect to an axial direction of the main shaft is mounted on the main shaft of the pump, and there is provided a retainer which has a circular disk portion which is brought into contact with an end surface of the positioning member, and a cylindrical portion extending from the circular disk portion so as to enclose an outer peripheral portion of the positioning member. Because the positioning member is tightly fitted in the main shaft in such a state that the positioning member is enclosed by the retainer, even if a fastening force for fixing the impellers is applied to the positioning member, the positioning member is prevented from being deformed.
  • the retainer may have an inner diameter shape which is fitted over the groove shape of the main shaft.
  • the cylindrical portion of the retainer may be brought into contact with the outer peripheral portion of the positioning member or may be located in close proximity to the outer peripheral portion of the positioning member.
  • FIG. 1 is a vertical cross-sectional view of a vertical-type multistage pump according to an embodiment of the present invention
  • FIG. 2 is an enlarged cross-sectional view of adjacent interstage casings shown in FIG. 1 ;
  • FIG. 3 is a view showing the interior of the interstage casing, as viewed from an arrow III of FIG. 2 ;
  • FIG. 4 is an enlarged fragmentary cross-sectional view of the multistage pump shown in FIG. 1 ;
  • FIG. 5 is a vertical cross-sectional view showing a first modified example of the vertical-type multistage pump shown in FIG. 1 ;
  • FIG. 6 is a vertical cross-sectional view showing a second modified example of the vertical-type multistage pump shown in FIG. 1 ;
  • FIG. 7 is an exploded perspective view of a main shaft, a split ring and a ring presser
  • FIG. 8 is a perspective view partly in section showing the state in which the main shaft, the split ring and the ring presser are assembled.
  • FIG. 9 is a vertical cross-sectional view showing an example of a conventional multistage pump.
  • centrifugal pump according to embodiments of the present invention will be described in detail with reference to the accompanying drawings.
  • a vertical-type multistage pump which comprises a plurality of vertically stacked interstage casings formed through press working of a steel plate and a plurality of impellers housed in the respective interstage casings will be described.
  • FIGS. 1 through 8 like or corresponding parts are denoted by like or corresponding reference numerals throughout views, and repetitive description is eliminated.
  • FIG. 1 is a vertical cross-sectional view of a vertical-type multistage pump according to an embodiment of the present invention.
  • a vertical-type multistage pump according to the present embodiment comprises a plurality of vertically stacked interstage casings 1 which are formed through press working of a steel plate, an upper casing 2 provided on the uppermost interstage casing 1 , a lower casing 3 provided under the lowermost interstage casing 1 , and an outer casing 4 which houses the stacked interstage casings 1 and the upper casing 2 and is connected to the lower casing 3 .
  • a pump base 5 is provided under the lower casing 3
  • a motor base 6 for supporting a motor (not shown) is provided above the outer casing 4 and the upper casing 2 .
  • the pump base 5 and the motor base 6 are coupled to each other by a plurality of casing bolts 8 and a plurality of nuts 9 .
  • the lower ends of the casing bolts 8 are screwed into the pump base 5 and the nuts 9 are screwed over the respective upper ends of the casing bolts 8 , whereby the multistage interstage casings 1 , the upper casing 2 and the lower casing 3 are held between the pump base 5 and the motor base 6 .
  • the upper and lower ends of the outer casing 4 are fitted into the lower casing 3 and the motor base 6 , respectively, so that the outer casing 4 is supported between the lower casing 3 and the motor base 6 .
  • O-rings 7 and 7 are provided at the fitting portion of the outer casing 4 and the lower casing 3 and the fitting portion of the outer casing 4 and the motor base 6 .
  • the outer casing 4 constitutes an outer barrel for preventing pressure water (pressurized liquid) generated by operation of the pump from leaking to the outside of the pump.
  • the outer casing 4 constituting the outer barrel have both end portions which are pressed into formed portions 4 f , 4 f for mounting the O-rings 7 , 7 for sealing.
  • the formed portions 4 f , 4 f have ends which are expanded radially outwardly to prevent the O-rings 7 , 7 from dropping therefrom.
  • a tapered portion expanded radially outwardly is formed on an end portion of a member (the lower casing 3 or a lining member 40 (described later)) for receiving the outer casing 4 so that the O-ring 7 held by the formed portion 4 f can be easily inserted into the member (the lower casing 3 or the lining member 40 ) when the outer casing 4 is attached to the lower casing 3 and the motor base 6 .
  • a plurality of impellers 11 are fixed to a main shaft 10 , and each of the impellers 11 is housed in each of the interstage casings 1 .
  • the main shaft 10 comprises a spline shaft, and each of the impellers 11 has a plurality of grooves fitted over the spline shaft at the inner peripheral portion thereof.
  • a mechanical seal 12 is mounted on the upper portion of the main shaft 10 to perform a shaft seal of the portion where the main shaft 10 passes through the pump casing.
  • the upper end of the main shaft 10 is coupled to a main shaft 15 of a motor (not shown) through a coupling 14 .
  • a suction nozzle 17 and a discharge nozzle 18 are fixed to the lower casing 3 , and a suction flange 19 and a discharge flange 20 are fixed to the forward ends of the suction nozzle 17 and the discharge nozzle 18 , respectively.
  • FIG. 2 is an enlarged cross-sectional view showing a portion of the structure including the interstage casings 1 shown in FIG. 1 .
  • each of the interstage casings 1 is substantially in the form of a cylindrical receptacle.
  • each of the interstage casings 1 includes a first cylindrical portion 21 , a protruding portion 22 protruding radially outward from the first cylindrical portion 21 , a first bottom portion 23 extending radially inward from the protruding portion 22 , a second cylindrical portion 24 extending axially from the first bottom portion 23 , and a second bottom portion 25 extending radially inward from the second cylindrical portion 24 .
  • the interstage casings 1 are made of stainless steel plates by press forming.
  • the protruding portion 22 has a maximum outside diameter larger than the outside diameter of the first cylindrical portion 21 .
  • the second cylindrical portion 24 has an outside diameter slightly smaller than the inside diameter of the first cylindrical portion 21 .
  • the first bottom portion 23 is arranged so as to be perpendicular to the first cylindrical portion 21 .
  • the first cylindrical portion 21 has an axial end face 21 a which is held in contact with a first bottom portion 23 of an adjacent interstage casing 1 substantially over the entire surface of the axial end face 21 a .
  • the first bottom portion 23 may be inclined at a predetermined angle with respect to the first cylindrical portion 21 rather than perpendicular to the first cylindrical portion 21 .
  • the second bottom portion 25 of the interstage casing 1 is formed into a curved shape of a hemisphere or substantially a hemisphere.
  • a suction plate 30 is attached to the second bottom portion 25 by welding.
  • a plurality of return guide vanes 34 are interposed between the suction plate 30 and a side plate 32 and attached to the suction plate 30 and the side plate 32 by welding.
  • the suction plate 30 is also formed into a curved shape of a hemisphere or substantially a hemisphere so as to be held in contact with a surface of the second bottom portion 25 .
  • the suction plate 30 has an outer circumferential end face 30 a which is held in contact with an inner surface of a first cylindrical portion 21 of an adjacent interstage casing 1 .
  • the interstage casing 1 has a simple structure which can be manufactured simply through press forming. Accordingly, it is possible to readily form a space for an O-ring disposed between adjacent interstage casings with high accuracy. Thus, it is possible to maintain stable sealing capability and stable sealing accuracy. Such a space for an O-ring may be changed in shape such that a commercially available O-ring is fitted in the space. Thus, since any commercially available O-ring can be used, manufacturing cost of the pump can be reduced. Further, since the second bottom portion 25 of the interstage casing 1 is formed into a curved shape of a hemisphere or substantially a hemisphere, the interstage casing 1 has a high pressure resistance.
  • a liner ring 28 is mounted on an innermost portion 26 of the second bottom portion 25 of the interstage casing 1 to prevent water having a high pressure from leaking into the suction side of the impeller 11 .
  • a baffle 36 is disposed in the interstage casing 1 so as to cover the protruding portion 22 , the first bottom portion 23 , the second cylindrical portion 24 , and an outer peripheral portion of the second bottom portion 25 .
  • the baffle 36 is bonded to the second bottom portion 25 of the interstage casing 1 by welding. Even if solid matter such as stones flows into the interstage casing 1 , the baffle 36 can protect the protruding portion 22 , the first bottom portion 23 , the second cylindrical portion 24 , and the outer peripheral portion of the second bottom portion 25 from the solid matter. Particularly, the baffle 36 protects a stepped portion formed at a corner of the interstage casing 1 .
  • the baffle 36 may be eliminated depending on purposes of the pump.
  • FIG. 3 is a view taken in a direction of an arrow III of FIG. 2 .
  • FIG. 3 shows an interior of the interstage casing 1 .
  • the baffle 36 has a spline structure at a radially inner portion thereof.
  • the baffle 36 has a number of notches (grooves) 36 a extending radially outward.
  • the second bottom portion 25 of the interstage casing 1 is exposed at the notches 36 a of the baffle 36 and covered with the baffle 36 at portions other than the notches 36 a of the baffle 36 .
  • depressions and projections are formed on a surface of the second bottom portion 25 facing the impeller 11 by the notches 36 a of the baffle 36 .
  • the depth of the depressions and the thickness of the projections correspond to the thickness of the baffle 36 .
  • Rotational energy is applied to a fluid in a space between the impeller 11 and the second bottom portion 25 by rotation of the impeller 11 .
  • the depressions and projections formed on the surface of the second bottom portion 25 can reduce the rotational energy of the fluid between the impeller 11 and the second bottom portion 25 . Accordingly, it is possible to prevent a static pressure of the fluid between the impeller 11 and the second bottom portion 25 from being lowered. Thus, a thrust force applied to the impeller 11 can be reduced.
  • FIG. 4 is an enlarged fragmentary cross-sectional view of the multistage pump shown in FIG. 1 .
  • a lining member 40 which is manufactured through press working of a stainless steel plate adheres to a liquid contact portion of the motor base 6 .
  • the motor base 6 comprises castings of gray cast iron, and the motor base 6 and the lining member 40 comprising a pressed component constitute a casing cover for covering an open end of the pump casing tightly.
  • the lining member 40 adheres to the motor base 6 by press fitting.
  • An annular portion 40 a is formed at the inner peripheral portion of the lining member 40 , and covers a hollow cylindrical portion 44 h of the mechanical seal holder 44 .
  • the end portion of the annular portion 40 a of the lining member 40 is expanded radially outwardly so that the lining member 40 does not fall out from the motor base 6 .
  • the outer peripheral portion 40 b of the lining member 40 is expanded radially outwardly in a tapered shape so that the O-ring 7 can be easily inserted into the annular portion 40 a .
  • a cartridge type mechanical seal 12 is mounted on the upper part of the main shaft 10 to perform a shaft seal of the portion (hollow cylindrical portion 6 h ) where the main shaft 10 passes through the casing cover (composed of the motor base 6 and the lining member 40 ).
  • the casing cover for covering the open end of the pump casing tightly comprises the motor base 6 comprising a thick member made of castings, and the lining member 40 comprising a thin member made of a pressed component and adhering to the outer surface of the motor base 6 , rigidity and corrosion resistance of the casing cover can be ensured, and press working of the lining member 40 can be easily performed. Further, since the lining member 40 comprises a thin-wall member, material cost of the stainless steel plate can be reduced.
  • the motor base 6 has a vertical hole 6 b and a lateral hole 6 c for priming and air-bleeder.
  • a pipe 51 made of stainless steel is fitted into the vertical hole 6 b
  • a cylindrical receptacle-like member 52 made of stainless steel is fitted into the lateral hole 6 c .
  • a plug 53 is screwed into the open end of the cylindrical receptacle-like member 52 .
  • the pipe 51 and the cylindrical receptacle-like member 52 which are made of stainless steel are provided in the liquid contact portion. Therefore, even if the motor base 6 is made of gray cast iron having a poor corrosion resistance, the liquid contact portion in the motor base 6 is entirely lined with a material made of stainless steel, thus ensuring corrosion resistance of the liquid contact portion.
  • the contacting portion of the lining member 40 and the pipe 51 and the contacting portion of the pipe 51 and the cylindrical receptacle-like member 52 are welded by lasers to ensure water-tightness.
  • the cartridge type mechanical seal 12 comprises a cartridge sleeve 41 which is mounted on the main shaft 10 and rotates together with the main shaft 10 , a rotating assembly 42 including a rotating seal ring which is mounted on the cartridge sleeve 41 and rotates together with the cartridge sleeve 41 , a stationary assembly 43 including a stationary seal ring which is brought into sliding contact with the rotating assembly 42 , and a holder 44 which holds the stationary assembly 43 and is fixed to the motor base 6 .
  • the holder 44 comprises a cylindrical member 44 a which holds the stationary assembly 43 including the stationary seal ring and has an O-ring 45 thereon, and a circular plate 44 b welded to the cylindrical member 44 a by lasers.
  • the cylindrical member 44 a has a step portion 44 s for holding the stationary assembly 43 including the stationary seal ring.
  • the holder 44 is fixed to the motor base 6 by fastening the circular plate 44 b to the motor base 6 with a plurality of bolts 46 .
  • a sleeve presser 47 is provided on the upper end of the cartridge sleeve 41 , and a plurality of setscrews 48 are screwed into the sleeve presser 47 .
  • the cartridge sleeve 41 has through-holes 41 h at the locations corresponding to the setscrews 48 .
  • the sleeve presser 47 rotates together with the main shaft 10 to cause the cartridge sleeve 41 to rotate together with the main shaft 10 .
  • the rotating seal ring is pressed against the stationary seal ring by a compression spring (not shown).
  • an adjustment sleeve 49 is provided between the rotating assembly 42 including the rotating seal ring and the cartridge sleeve 41 .
  • the coupling 14 is removed from the main shaft 10 and the main shaft 15 , and then the motor (not shown) is removed from the motor base 6 .
  • the motor (not shown) is removed from the motor base 6 .
  • the setscrews 48 are loosened, the sleeve presser 47 becomes in a free state with respect to the main shaft 10 , and then the bolts 46 are removed from the motor base 6 .
  • the holder 44 is lifted using a driver or the like.
  • the inner peripheral portion of the circular plate 44 b of the holder 44 is brought into close contact with the end surface of the sleeve presser 47 .
  • the holder 44 , the sleeve presser 47 , and the cartridge sleeve 41 are integrally lifted.
  • the holder 44 is further lifted, and thus the cartridge type mechanical seal 12 in its entirety is removed upwardly from the main shaft 10 .
  • the cartridge sleeve 41 which holds the rotating assembly 42 including the rotating seal ring, the holder 44 which holds the stationary assembly 43 including the stationary seal ring, and the sleeve presser 47 mounted on the upper end of the cartridge sleeve 41 are integrated in advance, and in this state, the integrated assembly including the cartridge sleeve 41 , the holder 44 and the sleeve presser 47 is fitted over the main shaft 10 from the upper end of the main shaft 10 . Thereafter, the bolts 46 are screwed into the pump base 6 , and the setscrews 48 are tightened against the main shaft 10 .
  • annular portion 40 a of the lining member 40 has an end portion which is expanded radially outwardly, when the mechanical seal 12 is mounted, the O-ring 45 held by the holder 44 can be easily inserted into the annular portion 40 a of the lining member 40 .
  • a double-split ring 91 (described later on) is attached to the main shaft 10 , and when the cartridge type mechanical seal 12 is mounted on the main shaft 10 , the lower end portion of the cartridge type mechanical seal 12 is brought into close contact with the double-split ring 91 , thereby positioning the cartridge type mechanical seal 12 .
  • the cartridge type mechanical seal having the above structure, only by removing the coupling 14 and the motor (not shown) fixed to the motor base 6 , the cartridge type mechanical seal 12 can be mounted on or detached from the main shaft 10 from the location above the main shaft 10 . Therefore, it is not necessary to remove the multistage interstage casings 1 , the impellers 11 , and the like in order to replace the mechanical seal.
  • the holder 44 which holds the stationary assembly (including the stationary seal ring) of the mechanical seal comprises the cylindrical member 44 a and the circular plate 44 b which are joined together by laser welding, the cylindrical member 44 a can be formed by working a pipe slightly, and the circular plate 44 b can be easily formed by blanking or the like. Therefore, the holder 44 having a flange can be manufactured by minimum working processes, and thus manufacturing cost can be greatly reduced.
  • liquid drawn in from the suction nozzle 17 is introduced into the lower casing 3 , and is pressurized by the first-stage impeller 11 in the lowermost interstage casing 1 .
  • the liquid discharged from the first-stage impeller 11 passes through passages defined by the return blades 34 provided between the suction plate 30 and the side plate 32 , and is then introduced into the next-stage impeller 11 .
  • the liquid is pressurized by each of the impellers 11 in each of the interstage casings 1 , and the pressure head of the liquid is recovered while the liquid passes through the passages defined by the return blades 34 and the like.
  • the liquid is pressurized by the final-stage impeller 11 located at the uppermost stage, and the pressure head of the liquid is recovered after passing through the final-stage passages defined by the return blades 34 and the like. Thereafter, the liquid flows into the upper casing 2 .
  • a plurality of discharge holes 2 a are formed in the upper casing 2 .
  • the liquid in the upper casing 2 passes through the discharge holes 2 a and then the annular passage 55 defined between the outer casing 4 and the multistage interstage casings 1 , and is then discharged from the discharge nozzle 18 to the outside.
  • the vertical-type multistage pump has been described in the above embodiments, this pump can also be used as a horizontal type multistage pump.
  • FIG. 5 is a vertical cross-sectional view showing a first modified example of the vertical-type multistage pump shown in FIG. 1 .
  • the cartridge type mechanical seal 12 can be removed from the main shaft 10 without detaching the motor (not shown) from the motor base 6 . Further, when the cartridge type mechanical seal 12 is mounted on the main shaft 10 of the pump, the motor is not required to be detached from the motor base 6 .
  • a gap L 1 which is longer than the overall length of the cartridge type mechanical seal 12 is formed between the main shaft 10 of the pump and the main shaft 15 of the motor. Therefore, the cartridge type mechanical seal 12 can be removed in such a state that the motor is mounted on the motor base 6 . Specifically, the double-split coupling 14 is removed from the main shaft 10 and the main shaft 15 , and then the cartridge type mechanical seal 12 in its entirety is lifted to the space between the main shaft 10 of the pump and the main shaft 15 of the motor, whereby the cartridge type mechanical seal 12 can be removed from the main shaft 10 .
  • Rectangular windows 6 w are formed in the side wall of the motor base 6 , and hence the cartridge type mechanical seal 12 which has been lifted is taken out laterally through one of the windows 6 w .
  • the cartridge type mechanical seal 12 is mounted on the main shaft 10 , the cartridge type mechanical seal 12 is introduced into the motor base 6 through the window 6 w , and then the cartridge type mechanical seal 12 is mounted on the main shaft 10 through the space between the main shaft 10 and the main shaft 15 .
  • the motor which is a heavy object is not required to be moved, and the mechanical seal can be inspected or replaced only by removing the coupling.
  • FIG. 6 is a vertical cross-sectional view showing a second modified example of the vertical-type multistage pump shown in FIG. 1 .
  • a housing bracket 80 is fixed to the motor base 6 , and a large ball bearing 81 for receiving a thrust load generated in the pump is housed in the housing bracket 80 .
  • the main shaft 10 of the pump and the main shaft 15 of the motor are coupled by a first coupling 82 and a second coupling 83 .
  • a gap L 2 which is longer than the overall length of the cartridge type mechanical seal 12 is formed between the upper end of the main shaft 10 and the lower end of the first coupling 82 . Therefore, the cartridge type mechanical seal 12 can be removed in such a state that the motor is mounted on the housing bracket 80 .
  • the double-split type second coupling 83 is removed from the main shaft 10 and the first coupling 82 , and then the cartridge type mechanical seal 12 in its entirety is lifted to the space between the main shaft 10 of the pump and the first coupling 82 , whereby the cartridge type mechanical seal 12 can be removed from the main shaft 10 .
  • Rectangular windows 6 w are formed in the side wall of the motor base 6 , and hence the cartridge type mechanical seal 12 which has been lifted is taken out laterally through one of the windows 6 w .
  • the cartridge type mechanical seal 12 is mounted on the main shaft 10 , the cartridge type mechanical seal 12 is introduced into the motor base 6 through the window 6 w , and then the cartridge type mechanical seal 12 is mounted on the main shaft 10 through the space between the main shaft 10 and the first coupling 82 .
  • the motor which is a heavy object is not required to be moved, and the mechanical seal can be inspected or replaced only by removing the coupling.
  • the housing bracket 80 having the large ball bearing 81 therein the thrust load generated in the pump can be received by the large ball bearing 81 , and hence the general-purpose small motor which is available in low cost on the market can be used.
  • the range of selection of the motor can be broaden, and the reduction of the cost of the pump including the motor can be achieved.
  • FIGS. 7 and 8 are views showing the structure for fixing the uppermost impeller 11 to the main shaft 10 of the pump.
  • FIG. 7 is an exploded perspective view of the main shaft 10 , a double-split ring 91 and a ring presser 92
  • FIG. 8 is a perspective view partly in section showing the state in which the main shaft 10 , the double-split ring 91 and the ring presser 92 are assembled.
  • a circular groove 10 g is formed in the main shaft 10 at the location near the upper end of the spline section 10 s .
  • the double-split ring 91 is fitted in the circular groove 10 g .
  • the double-split ring 91 constitutes a positioning member for positioning the final-stage impeller 11 with respect to the main shaft 10 in an axial direction of the main shaft 10 .
  • the ring presser 92 constitutes a retainer for retaining the double-split ring 91 mounted on the main shaft 10 .
  • the ring presser 92 constituting the retainer has a plurality of spline grooves serving as an inner diameter shape which is fitted over the spline grooves provided in the spline section 10 s of the main shaft 10 .
  • the ring presser 92 is moved upwardly along the spline section 10 s , and the ring presser 92 is brought into close contact with the double-split ring 91 mounted on the main shaft 10 .
  • the cylindrical portion 92 b of the ring presser 92 is brought into contact with the outer peripheral portion of the double-split ring 91 or is located in close proximity to the outer peripheral portion of the double-split ring 91 .
  • the multistage impellers 11 are mounted on the main shaft 10 , and finally, a nut 93 is threaded over the lower end of the main shaft 10 , thereby fixing the multistage impellers 11 to the main shaft 10 .
  • a C-type snap ring 94 located above the main shaft 10 in FIG. 7 may be used.
  • the multistage impellers 11 are fixed to the main shaft 10 by fastening the nut 93 .
  • the fastening force of the nut 93 is transmitted to the double-split ring 91 through the ring presser 92 .
  • the double-split ring 91 is tightly fitted in the circular groove 10 g of the main shaft 10 in such a state that the double-split ring 91 is enclosed by the ring presser 92 , the double-split ring 91 is prevented from being deformed.
  • the double-split ring 91 serves also as a positioning member for positioning the lower end portion of the cartridge type mechanical seal 12 .
  • the present invention is applicable to a centrifugal pump having at least one impeller fixed to a main shaft and at least one casing which houses the impeller and is formed through press working (press forming) of sheet metal such as a steel plate.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US11/631,483 2004-07-16 2004-11-12 Centrifugal Pump Abandoned US20080019831A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2004-210735 2004-07-16
JP2004210735A JP4633396B2 (ja) 2004-07-16 2004-07-16 遠心式ポンプ
PCT/JP2004/017203 WO2006008843A1 (en) 2004-07-16 2004-11-12 Centrifugal pump

Publications (1)

Publication Number Publication Date
US20080019831A1 true US20080019831A1 (en) 2008-01-24

Family

ID=34959225

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/631,483 Abandoned US20080019831A1 (en) 2004-07-16 2004-11-12 Centrifugal Pump

Country Status (5)

Country Link
US (1) US20080019831A1 (de)
EP (1) EP1774181A1 (de)
JP (1) JP4633396B2 (de)
CN (1) CN1989347A (de)
WO (1) WO2006008843A1 (de)

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US20110008165A1 (en) * 2008-12-30 2011-01-13 Nathan Wesley Ottow Engine case system for a gas turbine engine
US20110182725A1 (en) * 2010-01-25 2011-07-28 Grundfos Management A/S Refrigerant pump assembly
US8398361B2 (en) 2008-09-10 2013-03-19 Pentair Pump Group, Inc. High-efficiency, multi-stage centrifugal pump and method of assembly
EP2481931A3 (de) * 2011-02-01 2013-06-19 E.G.O. Elektro-Gerätebau GmbH Heizeinrichtung für eine Pumpe und Pumpe
US20150354583A1 (en) * 2014-06-09 2015-12-10 A.R. Wilfley And Sons, Inc. Centrifugal pump with governor actuated seal
US20190024665A1 (en) * 2017-07-20 2019-01-24 Ge Oil & Gas Esp, Inc. Pumping System Shaft Conversion Adapter
EP3181908B1 (de) * 2015-12-17 2020-05-13 Grundfos Holding A/S Mehrstufige kreiselpumpe mit aus blech gebildeten zugankern
CN117823415A (zh) * 2024-03-04 2024-04-05 山东华立供水设备有限公司 一种多级离心泵

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JP5074218B2 (ja) * 2008-01-25 2012-11-14 株式会社日立産機システム 多段ポンプ
EP2112380A1 (de) 2008-04-21 2009-10-28 DP Industries B.V. Mehrstufige Kreiselpumpe in Inline-Bauart
JP5421673B2 (ja) * 2008-07-04 2014-02-19 ホシザキ電機株式会社 オーガ式製氷機
EP2143959B1 (de) 2008-07-10 2018-05-02 Grundfos Management A/S Pumpenaggregat und Verfahren zum modularen Aufbau eines Pumpenaggregates
EP2228538B1 (de) * 2009-03-10 2015-09-16 Grundfos Management A/S Mehrstufiges Kreiselpumpenaggregat
IT1398811B1 (it) * 2010-03-18 2013-03-18 Calpeda A Spa Pompa multistadio a tenuta perfezionata
DE102012108354B4 (de) * 2012-09-07 2016-05-12 Herborner Pumpenfabrik J. H. Hoffmann Gmbh & Co. Kg Pumpe und Protektor für Pumpe
JP2017089839A (ja) * 2015-11-16 2017-05-25 株式会社荏原製作所 カートリッジ式メカニカルシール、ポンプ装置およびカートリッジ式メカニカルシールの製造方法
CN105485505B (zh) * 2016-01-03 2017-09-01 詹白勺 阀芯阀盖密封的快速启动立式多级离心油泵
KR101818075B1 (ko) * 2016-02-04 2018-01-12 주식회사 세고산업 입형다단펌프의 더블 실링 구조
JP6646505B2 (ja) * 2016-03-31 2020-02-14 株式会社荏原製作所 軸組立体、モータ軸、モータ、モータポンプ、および軸組立体の製造方法
KR101743008B1 (ko) * 2017-03-07 2017-06-15 주식회사 에스피케이 입형 원심펌프
JP6608015B1 (ja) * 2018-08-22 2019-11-20 株式会社川本製作所 縦型多段ポンプ
CN109209988B (zh) * 2018-11-22 2024-04-12 无锡市海星船舶动力有限公司 具有叶片均匀分布检测功能的压缩机叶轮
CN114423952A (zh) * 2019-09-26 2022-04-29 株式会社荏原制作所 立式多级泵
JP7373983B2 (ja) * 2019-12-11 2023-11-06 株式会社荏原製作所 立形多段ポンプ
KR102459346B1 (ko) * 2020-08-18 2022-10-28 김지흥 마이크로버블 발생용 수중펌프

Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2378974A (en) * 1944-08-01 1945-06-26 Fairbanks Morse & Co Mounting means for pump impellers and the like
US2526751A (en) * 1949-05-27 1950-10-24 Ingersoll Rand Co Mounting device for pump impellers
US2658454A (en) * 1948-05-14 1953-11-10 Pfaudler Co Inc Glass-lined pump
US3551067A (en) * 1969-01-22 1970-12-29 Duriron Co Lined corrosion resistant pump
US3918272A (en) * 1972-12-16 1975-11-11 Klein Schanzlin Becker Aktieng Centrifugal pump assembly for use in nuclear reactor plants or the like
US4124318A (en) * 1978-03-23 1978-11-07 General Motors Corporation Splined assembly with retaining rings
US4574648A (en) * 1984-01-13 1986-03-11 Debello Robert J Pinion gear retainer assembly for a starter motor of an internal combustion engine
US4653980A (en) * 1985-08-29 1987-03-31 Borg-Warner Industrial Products, Inc. Mechanical seal for pumps and method of fabricating same
US4655684A (en) * 1984-08-02 1987-04-07 Haentjens Walter D Centrifugal pump for wide range of operating conditions
US4877372A (en) * 1987-09-04 1989-10-31 Grundfos International A/S Multi-stage rotary pump
US5201848A (en) * 1991-10-01 1993-04-13 Conoco Inc. Deep well electrical submersible pump with uplift generating impeller means
US5256033A (en) * 1990-11-25 1993-10-26 Ebara Corporation Sheet metal interstage casing for a pump
US5558491A (en) * 1993-09-17 1996-09-24 Andrews; Darrell G. Unitized product seal for pumps
US5779445A (en) * 1993-09-13 1998-07-14 Kabushiki Kaisha Yokota Seisakusho Noncontaminative centrifugal pump
US6082964A (en) * 1997-09-30 2000-07-04 Ebara Corporation Centrifugal pump having a floating seal ring
US20050002789A1 (en) * 2002-01-21 2005-01-06 Kenichi Kajiwara Impeller
US20050147505A1 (en) * 2002-01-21 2005-07-07 Sou Kuroiwa Multistage pump

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1453784B2 (de) * 1962-01-17 1970-02-12 Klein, Schanzlin & Becker AG, 67IO Frankenthal Laufradbefestigung für Kreiselpumpen
CH408650A (it) * 1964-02-15 1966-02-28 Gabbioneta Roberto Girante con mozzo riportato per una pompa per fluidi
CS251416B1 (en) * 1985-08-12 1987-07-16 Josef Trnka Runner's fastening on pump's shaft
JPH0640958Y2 (ja) * 1988-03-09 1994-10-26 株式会社荏原製作所 ガイドベーンを備えたポンプケーシング
JPH07224782A (ja) * 1994-02-15 1995-08-22 Kawamoto Seisakusho:Kk 多段うず巻きポンプ

Patent Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2378974A (en) * 1944-08-01 1945-06-26 Fairbanks Morse & Co Mounting means for pump impellers and the like
US2658454A (en) * 1948-05-14 1953-11-10 Pfaudler Co Inc Glass-lined pump
US2526751A (en) * 1949-05-27 1950-10-24 Ingersoll Rand Co Mounting device for pump impellers
US3551067A (en) * 1969-01-22 1970-12-29 Duriron Co Lined corrosion resistant pump
US3918272A (en) * 1972-12-16 1975-11-11 Klein Schanzlin Becker Aktieng Centrifugal pump assembly for use in nuclear reactor plants or the like
US4124318A (en) * 1978-03-23 1978-11-07 General Motors Corporation Splined assembly with retaining rings
US4574648A (en) * 1984-01-13 1986-03-11 Debello Robert J Pinion gear retainer assembly for a starter motor of an internal combustion engine
US4655684A (en) * 1984-08-02 1987-04-07 Haentjens Walter D Centrifugal pump for wide range of operating conditions
US4653980A (en) * 1985-08-29 1987-03-31 Borg-Warner Industrial Products, Inc. Mechanical seal for pumps and method of fabricating same
US4877372A (en) * 1987-09-04 1989-10-31 Grundfos International A/S Multi-stage rotary pump
US5256033A (en) * 1990-11-25 1993-10-26 Ebara Corporation Sheet metal interstage casing for a pump
US5344678A (en) * 1990-12-25 1994-09-06 Ebara Corporation Shaft sleeve made of ceramics
US5201848A (en) * 1991-10-01 1993-04-13 Conoco Inc. Deep well electrical submersible pump with uplift generating impeller means
US5779445A (en) * 1993-09-13 1998-07-14 Kabushiki Kaisha Yokota Seisakusho Noncontaminative centrifugal pump
US5558491A (en) * 1993-09-17 1996-09-24 Andrews; Darrell G. Unitized product seal for pumps
US6082964A (en) * 1997-09-30 2000-07-04 Ebara Corporation Centrifugal pump having a floating seal ring
US20050002789A1 (en) * 2002-01-21 2005-01-06 Kenichi Kajiwara Impeller
US20050147505A1 (en) * 2002-01-21 2005-07-07 Sou Kuroiwa Multistage pump

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8398361B2 (en) 2008-09-10 2013-03-19 Pentair Pump Group, Inc. High-efficiency, multi-stage centrifugal pump and method of assembly
US20110008165A1 (en) * 2008-12-30 2011-01-13 Nathan Wesley Ottow Engine case system for a gas turbine engine
US8613593B2 (en) * 2008-12-30 2013-12-24 Rolls-Royce North American Technologies Inc. Engine case system for a gas turbine engine
US20110182725A1 (en) * 2010-01-25 2011-07-28 Grundfos Management A/S Refrigerant pump assembly
EP2481931A3 (de) * 2011-02-01 2013-06-19 E.G.O. Elektro-Gerätebau GmbH Heizeinrichtung für eine Pumpe und Pumpe
US20150354583A1 (en) * 2014-06-09 2015-12-10 A.R. Wilfley And Sons, Inc. Centrifugal pump with governor actuated seal
US9790960B2 (en) * 2014-06-09 2017-10-17 A.R. Wilfley & Sons, Inc. Centrifugal pump with governor actuated seal
EP3181908B1 (de) * 2015-12-17 2020-05-13 Grundfos Holding A/S Mehrstufige kreiselpumpe mit aus blech gebildeten zugankern
US10808703B2 (en) * 2015-12-17 2020-10-20 Grundfos Holding A/S Multi-stage centrifugal pump having tie rods formed from sheet metal
US20190024665A1 (en) * 2017-07-20 2019-01-24 Ge Oil & Gas Esp, Inc. Pumping System Shaft Conversion Adapter
CN117823415A (zh) * 2024-03-04 2024-04-05 山东华立供水设备有限公司 一种多级离心泵

Also Published As

Publication number Publication date
WO2006008843A1 (en) 2006-01-26
CN1989347A (zh) 2007-06-27
JP2006029241A (ja) 2006-02-02
EP1774181A1 (de) 2007-04-18
JP4633396B2 (ja) 2011-02-16

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