US3115097A - Corrosion resistant centrifugal pump - Google Patents

Corrosion resistant centrifugal pump Download PDF

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Publication number
US3115097A
US3115097A US47191A US4719160A US3115097A US 3115097 A US3115097 A US 3115097A US 47191 A US47191 A US 47191A US 4719160 A US4719160 A US 4719160A US 3115097 A US3115097 A US 3115097A
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United States
Prior art keywords
vanes
impeller
pumping
corrosion resistant
expeller
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Expired - Lifetime
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US47191A
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English (en)
Inventor
Zagar Irvin Frank
George M Wilfley
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AR Wilfley and Sons Inc
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Wilfley & Sons Inc A
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Filing date
Publication date
Application filed by Wilfley & Sons Inc A filed Critical Wilfley & Sons Inc A
Priority to US47191A priority Critical patent/US3115097A/en
Priority to GB8019/61A priority patent/GB903904A/en
Priority to DE19611728395 priority patent/DE1728395A1/de
Priority to DE19611403879 priority patent/DE1403879A1/de
Priority to SE3066/61A priority patent/SE300557B/xx
Priority to BE602286A priority patent/BE602286A/fr
Application granted granted Critical
Publication of US3115097A publication Critical patent/US3115097A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/14—Shaft sealings operative only when pump is inoperative
    • F04D29/146—Shaft sealings operative only when pump is inoperative especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2222—Construction and assembly
    • F04D29/2227—Construction and assembly for special materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F04D29/2255—Special flow patterns flow-channels with a special cross-section contour, e.g. ejecting, throttling or diffusing effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—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
    • F04D29/40—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
    • 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
    • F05D2260/00—Function
    • F05D2260/95—Preventing corrosion

Definitions

  • FIG 8 ATTORNEY United States Patent 0 3,1153% CQRRUSH'QEN RESETANT CENTRIFUGAL PUMP irvin Frank Zagar and George M. Wilfley, Denver, Colo., assignors to A. R. Wiliiey and Sons, inn, Denver, (Zola, a corporation of Colorado Filed Aug. 3, 196i), Ser. No. 47,191 3 (filaims. (:Cl. ltl3-ltl3)
  • the present invention relates to corrosion resistant centrifugal pumps and more particularly to pumps wherein the portions of the pump contacting the fluid to be pumped are formed of a material which is very effective in resisting corrosion.
  • centrifugal pumps of the general type according to the present invention which can effectively pump acids and other materials which have a deleterious corrosion effect on metallic pump parts. Accordingly, many efforts have been made to design a centrifugal pump wherein the portions of the pump contacting the pumped fluid may be formed of a material such as ceramic or glass which is corrosion resistant.
  • the difllculty in this respect is the fact that such corrosion resistant materials are diflicult to form and to provide with sufiicient rigidity and strength to resist the stresses and pressures applied thereto during normal pumping operations.
  • the present invention represents an improvement over US. Patent 2,571,802 to Wilfley et al., wherein a centrifugal pump of the same general type as the present invention is disclosed.
  • the aforementioned patent incorporates an arrangement wherein the drive is transmitted to an impeller shaft through a resilient spring connection, and a centrifugal control means is provided for shifting a shaft axially at predetermined speeds of the shaft.
  • the general concept employed in this type of pump is to eliminate mechanical seals and to rely solely upon a hydraulic seal when the pump is operating.
  • a centrifugal pump including a hydraulic type seal means which eliminates all friction between the parts formed of corrosion resistant material during pumping operations since there are no mechanical seals, thereby permitting the components to be constructed of such material without the accompanying dis- 3,115,097 Patented Dec. 24, 1963 advantages where mechanical contact seals are employed during pumping operations.
  • the particular construction of the present invention provides a very simple, compact and inexpensive construction which permits this type of a pump to be economically manufactured, and at the same time the arrangement provides a high degree of mechanical strength which has generally been lacking in prior art attempts to provide components formed of ceramic material.
  • the present invention provides a housing arrangement surrounding and adjacent to the impeller of the pump wherein the housing arrangement comprises a plurality of interconnected components, each of the components including an outer strong reinforcing armor of hard metallic material with an inner liner formed of corrosion resistant material. In this manner the components are provided with a high degree of mechanical strength and yet effectively resists corrosion during pumping of corrosive fluids.
  • the outer armor layer of each of these components further serves to protect the corrosion re- SlSlElflt material such as ceramic which may be quite brittle and subject to damage if struck by external objects.
  • the impeller as well as all of the various other components of the pump which contact the fluid also have surfaces formed of similar corrosion resistant material such that the entire pump can resist corrosion over very long periods of time in a manner vastly superior to prior art arrangements.
  • the various components of the present invention which are formed of corrosion resistant material may be formed of a variety of such known materials as ceramics, refractories, vitreous materials, plastics, high silica irons, and other similar materials.
  • the impeller of the present invention is of a particularly unique construction, and this particular construction has enabled this type of an impeller to be for the first time successfully manufactured completely of a corrosion resistant material in this particular environment.
  • the present invention incorporates a two-chamber type impeller wherein both pumping vanes as well as expeller vanes are incorporated therein.
  • the pumping vanes provide the primary pumping action which serves to pump the fluid through the apparatus.
  • the expeller vanes are employed for providing an eifective hydraulic seal.
  • one important feature of the present invention is to provide an impeller construction which permits the impeller to be readily formed.
  • the vanes of the present invention are formed along continuous straight lines, and in other words, the side surfaces of the vanes are substantially fiat which permits ready machining and formation thereof.
  • straightline vanes due to the employment of such straightline vanes, an additional problem arises due to the fact that curved vanes are the most efficient type, and that generally speaking, a great deal of efiiciency is lost if straight-line vanes are substituted for curved vanes. This problem is particularly acute in this type of a pump arrangement since the expeller vanes have to work against the head created by the pumping vanes.
  • the portions of the surrounding housing have been so constructed that the curved areas thereof are at a minimum, thereby providing a straight-line construction throughout the major portions of all of the components of the present apparatus which are constructed of the corrosion resistant material.
  • An object of the present invention is to provide a new and novel centrifugal pump wherein all the parts which contact the pumped fluid are formed of corrosion resistant material.
  • Another object of the invention is the provision of a corrosion resistant centrifugal pump which eliminates all friction between the parts formed of corrosion resistant material during a pumping operation.
  • a further object of the invention is to provide a corrosion resistant centrifugal pump which has a good hydraulic efficiency and wherein the construction is such as to provide a high degree of mechanical strength.
  • Still another object of the invention is to provide a corrosion resistant centrifugal pump which is quite simple and compact and furthermore, inexpensive in construction.
  • FIG. 1 is a sectional view of a centrifugal pump according to the present invention
  • FIG. 2 is a sectional view illustrating the mode of operation of the governor control means of the present invention
  • FIG. 3 is a sectional view illustrating the sealing means in one operative position
  • FIG. 4 is a view similar to FIG. 3 illustrating the sealing means in another operative position
  • FIG. 5 is a view partly broken away looking at the impeller from the forward end thereof;
  • FIG. 6 is a view partly broken away looking at the impeller from the rear end thereof;
  • FIG. 7 is a view taken substantially along line 77 of FIG. 6 looking in the direction of the arrows;
  • FIG. 8 is an enlarged portion of the structure shown in FIG. 1 of the drawings.
  • FIG. 9 is a view partially broken away of a portion of a housing means surrounding the impeller.
  • FIG. 1 the general layout of the pump according to the present invention wherein the over all housing is indicated generally by reference numeral 19, this housing consisting of several assemblies which are interconnected with one another to provide the complete assembly for enclosing the various components of the pumping apparatus.
  • the housing has a base structure including a hollow body portion 11, a foot portion 12 which is bolted to the body portion as at 13, and a top portion 14.
  • the top portion 14 in turn comprises a front bearing portion 15 formed with a vertical flange portion 16 facing forwardly, and a rear bearing portion 17.
  • the top portion 14 of the base structure further constitutes a chamber 18 herein also called the governor chamber extending etween the front and rear bearing portions 15 and 17 respectively and provided with a top plate or cover 19.
  • the front bearing portion 15 is provided with a front bearing in the form of a ball bearing 2'3 having balls 21, an inner race member 22 and an outer race member 23. This roller bearing is disposed between a front bearing plate 24 having sealing rings 24a and a rear bearing plate 25 having a sealing ring 25a, both bearing plates being held together and in place as by bolts 26.
  • the rear hearing portion 17 is provided with a rear bearing in the form of a ball bearing 27 having balls 28, an inner bearing race 29 and an outer bearing race 39.
  • the ball bearing 27 is held in place and directly confined between a front bearing plate 31 having a sealing ring 32, and a rear bearing plate 33 having a sealing ring 34, both bearing plates being held together and in place as by bolts 35.
  • a driving sleeve 36 formed with a shoulder 37 is rotatabie in the rear bearing 27 although secured against axial displacement therein as by the shoulder 37 at one side of bearing 27 and an internally threaded stop collar 38 screwed onto the sleeve member 36 at the other side of the bearing 27.
  • the driving sleeve 36 is formed at its inner or forward end with a radial projection or flange portion 39 and has a front bushing 4-0 and a rear bushing 41. In these bushings there is rotatable an impeller shaft 42.
  • These bushings or bearings consist of a known kind of self-lubricating material, for example, specially treated brass or impregnated wood or composition.
  • the impeller shaft is axially shiftable with respect to the driving sleeve 36, the extent of that shift being defined by a certain narrow range or predetermined limits hereinafter further explained.
  • the front end portion of the impeller shaft 42 is ro- I tatably supported in the front bearing 25 ⁇ which in turn is bodily shiftable with the shaft 42 relative to the base structure, the bearing 20 being unitary with the shaft by being confined directly between a shoulder 43 formed on shaft 42 and an internally threaded stop collar 44 screwed onto shaft 42.
  • the extent of the potential axial shift of shaft 42 is indicated by the clearance d noted between the bearing 20 and the adjacent bearing plate 25.
  • the impeller shaft 42 is controllably shifted axially thereof by a control device indicated generally by reference numeral c disposed within the chamber 18 which is in the nature of a centrifugal governor device responsive to the speed of rotation of the impeller shaft.
  • the control device a includes a body means having a portion 50 which is pinned by pin 51 to the shaft 42 and opposite pairs of radially extending lugs 52 are provided for supporting the swingable weight members of the centrifugal device.
  • a pair of pins 53 are supported between the pairs of lugs 52 at each side of the control device, and the swingable members 54 are pivotally supported thereon.
  • Members 54 each include a weight portion 55 and a foot or cam portion 56 which is adapted to bear against the forward face F of the flange 39 formed at the forward end of the driving sleeve 36.
  • the driving interconnection between flange portions 60 and 61 are also formed integral with the body means of the speed responsive control device, and the driving connection between fiange 39 fixed to the driving sleeve and flanges 60 and 61 comprises a pair of fiat spring elements 62 and 63 each being of multiple ply construction. These spring elements are fastened to the flange 39 by bolt and nut connections 65, the opposite ends of the spring elements being fastened to the flange portions 60 and 61 of the governor means by bolt and nut connections 66. These spring elements while allowing for a limited but sufficient relative axial movement between the driving sleeve 36 and the impeller shaft 42 also function as torque transmitting elements between the driving sleeve 36 and the impeller sha t 42. It is evident that the springs will urge the impeller shaft toward the light as seen in FIG.- 1 for a purpose hereinafter described.
  • an impeller insert "it? is formed of a corrosion resistant material and is provided with internal threads formed on the longitudinal bore extending therethrough, these internal threads on the insert cooperating with external threads 71 formed at the outermost end of the impeller shaft for securing the impeller insert to the end of the impeller shaft.
  • the insert is knurled and can be keyed or mechanically locked in place.
  • Disposed in surrounding relationship to the outermost portion of the impeller insert 7% and bonded thereto is the impeller of the present invention indicated generally by reference numeral '72, the construction of the impeller being hereinafter more fully described.
  • a rotary sealing ring '75 is secured in place about the outer surface of impeller insert 7 t), a sealing face 75' being formed on rotary seal ring '75.
  • a gasket 76 is provided between the forward end of the rotary seal ring and the adjacent portion of the impeller.
  • Rotary seal ring '75 is formed of corrosion resistant material of the type previously described.
  • a shaft sleeve dil is disposed in surrounding relationship and is secured to the impeller shaft 42, sleeve 8%) also being formed of similar corrosion resistant material and having a pair of annular grooves 81 and 3?. formed in the outer surface thereof.
  • a gasket 83 is provided between the forward end of the shaft sleeve S ll and tie adjacent portions of the impeller insert 70 and the rotary seal ring 75.
  • a bracket member 13 is fastened or bonded (the bolts not being shown) to the vertical flange portion 16 of the bearing housing.
  • An impeller housing sub-assembly indicated by letters 111 includes a front plate means indicatcd generally by reference numeral 90), a volute ring means indicated generally by reference numeral 91, and a rear plate means indicated generally by reference numeral 92., these latter three components being clamped together to provide the finished assembly by nut and bolt assemblies @5 which rigidly support the impeller housing sub-assembly from the bracket B.
  • a stationary seal ring housing 1% is attached as by bolts 1&1 rigidly to the rear plate means 92 such that the seal ring housing does not rotate during operation of the apparatus.
  • Seal ring housing 1% supports a stationary ring seal 1112 at an inner portion thereof, member 102 having an annular sealing face 1il2 formed thereon which is disposed complementary to and adapted to cooperate with the annular sealing face 75 formed on the rotary seal ring 75.
  • Stationary seal ring 1% is also formed of corrosion resistant material.
  • a pair of annular grooves 163 and 104 are formed in he stationary seal ring housing 1% adjacent to grooves d and 82 formed in shaft sleeve 89, and the surfaces of the grooves 1d nowadays and as well as the surfaces immediately adjacent to the grooves 1&3 and 1% which contact the fluid during pumping operations are all coated with a suitable corrosion resistant material as described previously.
  • the stationary seal ring housing 1% also includes a downwardly extending spout portion 1645' as seen in F113. 1 which is adapted to direct excess fluid away from the impeller shaft and out of the pump apparatus during pumping operations. In this manner, any pumped fluid which leaks past the hydraulic seal provided by the expeller vanes of the impeller will pass harmlessly outwardly out of the pump apparatus.
  • the rear plate means 92 includes an outer member 11h formed of a relatively rigid material such as cast iron, and an inner liner 111 is provided, the inner liner 111 being formed of a suitable corrosion resistant material as hereinbefore discussed.
  • the liner 111 is attached to the outer rigid armor portion 110 by cementing the liner to the outer member by means of Armstrong cement or the like.
  • liner 111 includes a circumferentially extending groove 112 which serves the function of a labyrinth means in cooperation with a portion of the impeller.
  • the liner is also provided with a relieved portion 113 which tapers inwardly toward the rear portion of the member.
  • the front plate means 96 also comprises an outer member 115 formed of a relatively rigid material such as cast iron and an inner liner 116 is secured to the outer armor portion 115 as by cementing with Armstrong adhesive.
  • liner 116 is provided with a groove 1241 which serves the function of a labyrinth means in cooperation with a portion of the impeller.
  • the liner 116 is also relieved at portion 121.
  • liner 116 defines a central bore 122 which comprises a forwardly extending suction inlet through which the pumped fluid is drawn into the pump apparatus.
  • volute ring portion 91 is formed of two halves which are bolted together by means of bolts 125.
  • the volute ring 91 includes an outer rigid portion 126 which also may be formed of cast iron or the like, and an inner liner 127 is formed of a suitable corrosion resistant material as aforedescribed, the inner liner being held in place by means of a suitable body of cement 123 such as Portland cement.
  • the portion of the liner indicated at 13% is disposed closest to the longitudinal axis 131 of the apparatus, or the rotational axis of the impeller shaft, and that following the inner surface of the liner counterclockwise frorn portion 130, the surface becomes more distant from axis 131 until the portion 132 is reached where the liner is at its maximum distance from the axis 131.
  • the remaining portions of the liner indicated by numerals 133 and 134 define the discharge outlet portion of the pump through which the pumped fluid is discharged.
  • a suitable attaching flange 135 is formed at the upper portion of the outer armor member as seen in FIG. 9.
  • FIG. 8 an enlarged cross-sectional view is provided illustrating the manner in which the various components 9t), 91 and 92 are nested together in assembled relationship to one another.
  • all the surfaces of the corrosion resistant liners of these components are formed along straight lines or flat surfaces to facilitate forming thereof.
  • small curved surfaces may be provided as long as they are of a minor nature. It will be noted that certain curved surfaces are incorporated in the construction of liner 127 as seen in FIG. 8, these small curved areas being provided between certain ofiset portions of the liner 127.
  • liner 127 includes radially inwardly extending flange portions 14% and 14-1 at the opposite sides thereof, the inner peripheries of these flanges engaging the outer surfaces of shoulders i116 and 113i of the liners 116 and 111 respectively.
  • An annularly extending recessed portion 14-2 is provided in the inner surface of liner 127, this recess being of a dimension x so as to be of a greater longitudinal extent than the discharge portions of the van-es of the impellers so that the portion of the fluid which is discharged from the vanes of the impellers will be discharged directly into this recessed portion 1452. thereby tending to carry the pumped fluid around and out through the discharge portion of the apparatus.
  • the outer surface 143 of impeller is spaced radially inwardly of the shoulder portions 16 and 111 formed on the liners 116 and 111 Referring now to FIG.
  • the impeller 7.2 includes a central portion 15 which is, as aforementioned, bonded to the outer surface of the impeller insert
  • the impeller includes a first portion 151 within which the continuous straight line or flat surface pump vanes 152 are formed and a second portion 153 is provided within which the continuous straight line flat surface expeller vanes 154 are formed. It will be noted that portion 153 within which the expeller vanes are formed extends radi- 7 ally outwardly of the portion 251 within which the pumping vanes are formed.
  • Pump vanes 52 and cxpellcr vanes 154 are of substantially similar construction as will hereinafter appear.
  • a circumferentially extending flange 155 extends forwardly of portion 15d and fits within and is spaced from the walls of the groove 129 formed in liner 116 for providing a labyrinth means therewith.
  • a circumferentially extending flange 159 extends rearwardly of portion 153 of the impeller and tits within and is spaced from the walls of groove 112 fumed in liner 111 for providing a labyrinth means therewith.
  • Varies 154 will also tend to pump out any liquid which may leak by the labyrinth means defined by flange 15S, and groove 112i thereby tending to prevent any liquid from passing toward the rear of the apparatus while the impeller is rotating in its pumping action.
  • FIGS. 5, 6 and 7 of the drawings the novel disposition of the vanes of the impeller is illustrated, and as seen in FIG. 5, four identical pumping vanes 152 are provided, these vanes extending from the inner annular surface 161 of the impeller to the outer annular surface 162 of the impeller, the opposite ends of the vanes being open as is well understood.
  • the pumping vanes include substan ally flat side surfaces 152 and end surfaces 152 which define pumping ports or passages 175 having a generally elongated rectangular crosssccrional configuration. It will be noted that these vanes are symmetrically disposed with respect to the axis 165 of the impeller which actually corres onds to the rotational axis of the impeller and the impeller shaft.
  • each of the pumping vanes has a pressure face which faces in the direction of rotation as indicated by the arrow in FIG. 5, each of the pressure faces of the pumping vanes having a radially extending mid portion 166 substantially midway between the adjacent side surfaces of the pumping vanes, such mid portions lying substantially along a line which passes through the axis 165.
  • each of the pumping vanes 152 is provided with a central or longitudinal axis aa.
  • each of the pumping means is offset with respect to the rotational axis 165 of the impeller, and in fact, each of the axes an is so disposed that it is tangential to an imaginary circle which has its center positioned on the rotational axis 165 of the impeller.
  • This novel disposition of the pumping vanes is such that even though the vanes are formed along straight lines with flat surfaces, maximum pumping eihciency is preserve Referring now to P16. 6, the disposition of the exeller vanes d is illustrated.
  • the expeliler vanes are six in number as illustrated and are symmetrically positioned about the impeller.
  • the expeller vanes 154 extend from an inner surface 170 of the impeller to the outer surface 143 of the impeller which has already been mentioned.
  • the opposite ends of the expeller vanes are also, of course, open to permit pumping of fluid outwardly by the expeller vanes.
  • the expeller vanes include substantially flat side surfaces 15 and end surfaces 154" which define expeller ports or passages 176 having a generally elongated rectangular cross-sectional configuration.
  • each of the expeller vanes has a pressure face which faces in the direction of rotation as indicated by the arrow in FIG. 6, each of the pressure faces of the expeller vanes having a radially extending mid portion 171 substantially midway between the adjacent side surfaces of the pumping vanes, such mid portions lying substantially along a line which passes through the rotational axis 155 of the impeller.
  • Each of vanes 15 has a central or longitudinal axis bb, each of these axes bb of the expcller vanes being offset with respect to the rotational axis 1.63 of the impeller and being tangential to a circle having its center along the rotational axis 165.
  • the disposition of the cxpcller vanes 15 is similar to that of the pumping vanes 152 in that in each case the central axes of the vanes are oilset with respect to the rotational axis of the impeller.
  • the expeller vanes although also being formed along straight lines and with fiat surfaces, are enabled to provide a maximum degree of hydraulic efhciency.
  • the side surfaces 152' of the pumping vanes and 15d of the expeller v..r.es are disposed in substantially parallel planes, these planes extending substantially normally to the axis of rotation of the impeller and impeller shaft.
  • the resilient drive transmitting springs 62 and 53 will urge the impeller shaft to the right into the position shown in FIG. 3 wherein the sealing faces formed on seal rings and 13 2 brought into frictional contact with one another thereby providing a positive mechanical seal which prevents passage of fluid between these two faces.
  • a corrosion resistant centrifugal pump comprising a pump housing an impeller shaft rotatably supported within said housing about an axis of rotation, an impeller formed of corrosion resistant hard-to-form material secured to one end portion of said impeller shaft and having both pumping vanes and expeller vancs formed thereon of similar construction, said vanes being defined by surfaces formed along continuous straight lines to facilitate formation of the impeller and each having a longitudinal axis which is offset with respect to said axis of rotation, the side surfaces of said pumping vanes and expeller vanes being disposed in substantially parallel planes, said planes extending substantially normally to said axis of rotation, each of said pumping and expeller vanes including end surfaces extending between said side surfaces to define therewith passages of generally elongated rectangular cross-sectional configuration, one end surface of each of said pumping and expeller vanes defining a pressure face, each of said pressure faces of the pumping and expeller vanes having a radially extending mid portion substantially midway between the adjacent side surfaces of the vanes, such
  • said housing includes an inner liner means disposed adjacent said' impeller, said inner liner means being formed of corrosion resistant material, said housing including outer reinforcing means adjacent said inner liner means for adding rigidity and strength to the pump.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US47191A 1960-08-03 1960-08-03 Corrosion resistant centrifugal pump Expired - Lifetime US3115097A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US47191A US3115097A (en) 1960-08-03 1960-08-03 Corrosion resistant centrifugal pump
GB8019/61A GB903904A (en) 1960-08-03 1961-03-06 Corrosion resistant centrifugal pumps
DE19611728395 DE1728395A1 (de) 1960-08-03 1961-03-20 Korrosionsbestaendiges Radialkreiselpumpenlaufrad
DE19611403879 DE1403879A1 (de) 1960-08-03 1961-03-20 Korrosionsbestaendige Fliehkraftpumpe
SE3066/61A SE300557B (de) 1960-08-03 1961-03-23
BE602286A BE602286A (fr) 1960-08-03 1961-04-06 Pompe centrifuge résistant à la corrosion.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US47191A US3115097A (en) 1960-08-03 1960-08-03 Corrosion resistant centrifugal pump

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US3115097A true US3115097A (en) 1963-12-24

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US47191A Expired - Lifetime US3115097A (en) 1960-08-03 1960-08-03 Corrosion resistant centrifugal pump

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US (1) US3115097A (de)
BE (1) BE602286A (de)
DE (2) DE1728395A1 (de)
GB (1) GB903904A (de)
SE (1) SE300557B (de)

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3360239A (en) * 1964-12-04 1967-12-26 Judson S Swearingen Oil free turbine assembly
US3652180A (en) * 1970-07-13 1972-03-28 Wilfley & Sons Inc A Centrifugal pump and seal means therefore
US3656861A (en) * 1970-04-15 1972-04-18 Wilfley & Sons Inc A Centrifugal pump with mating case plate volute halves and constant section impeller
US4099890A (en) * 1975-08-21 1978-07-11 Mitsui Mining & Smelting Co., Ltd. Impeller type pump having seal means and protective means
US4152096A (en) * 1975-08-21 1979-05-01 Mitsui Mining & Smelting Co., Ltd. Pump having seal means and protective means
US4212592A (en) * 1978-10-31 1980-07-15 General Electric Company Electromagnetic pump for molten metals
US5340273A (en) * 1991-12-04 1994-08-23 Environamics Corporation Sealing and pumping means and methods environmentally leak-proof pump with misting chamber defined therein
US5494299A (en) * 1994-02-22 1996-02-27 Evironamics Corporation Temperature and pressure resistant rotating seal construction for a pump
US5499901A (en) * 1994-03-17 1996-03-19 Environamics Corporation Bearing frame clearance seal construction for a pump
US5513964A (en) * 1994-10-11 1996-05-07 Environamics Corporation Pump oil mister with reduced windage
US5513954A (en) * 1994-06-10 1996-05-07 Envirotech Pumpsystems, Inc. Multilayer pump liner
US5553867A (en) * 1995-04-21 1996-09-10 Environamics Corporation Triple cartridge seal having one inboard and two concentric seals for chemical processing pump
US5591020A (en) * 1994-05-19 1997-01-07 Environamics Corporation Pump oil mister
US5599164A (en) * 1995-04-03 1997-02-04 Murray; William E. Centrifugal process pump with booster impeller
US5823539A (en) * 1995-04-21 1998-10-20 Environamics Corporation Environmentally safe pump having a bellows seal and a split ring shaft seal
US6200086B1 (en) 1999-08-04 2001-03-13 Sundyne Corporation Thermal barrier for use in a mechanical seal assembly
WO2013192503A2 (en) * 2012-06-21 2013-12-27 Flowserve Management Company Thermally compliant pump interfaces
CN103727067A (zh) * 2012-10-11 2014-04-16 闫海群 新型渣浆泵过流装置
CN104533798A (zh) * 2014-11-11 2015-04-22 胡光雄 一种复合防腐耐酸耐磨耐高温渣浆泵
US20150118367A1 (en) * 2010-02-17 2015-04-30 Koninklijke Douwe Egberts B.V. Coffee bean packaging cartridge and coffee beverage system including the same
US9980599B2 (en) 2009-02-17 2018-05-29 Koninklijke Douwe Egberts B.V. Coffee bean packaging cartridge and coffee beverage system including same
CN108412763A (zh) * 2018-05-09 2018-08-17 淄博联帮泵业有限公司 耐腐耐磨水环式真空泵
CN109114043A (zh) * 2018-08-13 2019-01-01 浙江老百姓泵业有限公司 一种旋涡泵和用于旋涡泵的组合连接部件的制造方法
CN111577609A (zh) * 2020-05-28 2020-08-25 邵玉强 一种变量离心泵

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JPS6134387A (ja) * 1984-07-26 1986-02-18 World Chem:Kk 高圧多段式シ−ルレスポンプ
GB2187231B (en) * 1986-02-28 1989-04-26 Godiva Fire Pumps Ltd Pump arrangements
DE19712324C2 (de) * 1997-03-24 2000-05-11 Renner Gmbh Umwälzpumpe oder Rührwerk für erwärmte chemische Lösungen
CN112253526A (zh) * 2020-10-16 2021-01-22 邵阳宝兴化工设备有限公司 一种非金属材料防腐泵及其制造方法
CN112648227B (zh) * 2020-12-24 2023-05-26 亿昇(天津)科技有限公司 一种叶轮与电机转子的密封结构及风机

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US2107260A (en) * 1936-03-04 1938-02-01 Ngk Insulators Ltd Corrosion resisting pump and blower
DE725507C (de) * 1941-06-27 1942-09-23 A W Mackensen Maschinenfabrik Stopfbuchsenlose Kreiselpumpe
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US2471653A (en) * 1946-04-27 1949-05-31 Vincent Palumbo Pump or the like
US2571802A (en) * 1948-04-09 1951-10-16 Wilfley & Sons Inc A Centrifugal pump
DE914214C (de) * 1941-03-26 1954-06-28 Amag Hilpert Pegnitzhuette Ag Kreiselpumpe mit entlasteter Stopfbuechse
US2835203A (en) * 1952-12-22 1958-05-20 Thompson Prod Inc Pump impeller
US2905093A (en) * 1954-08-12 1959-09-22 Union Carbide Corp Corrosion resistant pump
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US1756323A (en) * 1928-08-27 1930-04-29 Wilfley & Sons Inc A Centrifugal pump
US2029333A (en) * 1932-07-25 1936-02-04 Johnston Pump Company Turbine well pump
US1986836A (en) * 1933-01-09 1935-01-08 Fairbanks Morse & Co Method of making centrifugal pumps
US2107260A (en) * 1936-03-04 1938-02-01 Ngk Insulators Ltd Corrosion resisting pump and blower
US2433589A (en) * 1939-05-25 1947-12-30 Nash Engineering Co Pump
DE914214C (de) * 1941-03-26 1954-06-28 Amag Hilpert Pegnitzhuette Ag Kreiselpumpe mit entlasteter Stopfbuechse
DE725507C (de) * 1941-06-27 1942-09-23 A W Mackensen Maschinenfabrik Stopfbuchsenlose Kreiselpumpe
GB552902A (en) * 1941-10-24 1943-04-29 Wilfley & Sons Inc A Seal for centrifugal pumps
GB575346A (en) * 1944-03-01 1946-02-14 Aluminium Plant & Vessel Co Improvements in or relating to centrifugal pumps
US2471653A (en) * 1946-04-27 1949-05-31 Vincent Palumbo Pump or the like
US2571802A (en) * 1948-04-09 1951-10-16 Wilfley & Sons Inc A Centrifugal pump
US2835203A (en) * 1952-12-22 1958-05-20 Thompson Prod Inc Pump impeller
US2905093A (en) * 1954-08-12 1959-09-22 Union Carbide Corp Corrosion resistant pump
US3037458A (en) * 1957-04-15 1962-06-05 Goulds Pumps Glass pump
US3048384A (en) * 1959-12-08 1962-08-07 Metal Pumping Services Inc Pump for molten metal

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3360239A (en) * 1964-12-04 1967-12-26 Judson S Swearingen Oil free turbine assembly
US3656861A (en) * 1970-04-15 1972-04-18 Wilfley & Sons Inc A Centrifugal pump with mating case plate volute halves and constant section impeller
US3652180A (en) * 1970-07-13 1972-03-28 Wilfley & Sons Inc A Centrifugal pump and seal means therefore
US4099890A (en) * 1975-08-21 1978-07-11 Mitsui Mining & Smelting Co., Ltd. Impeller type pump having seal means and protective means
US4152096A (en) * 1975-08-21 1979-05-01 Mitsui Mining & Smelting Co., Ltd. Pump having seal means and protective means
US4212592A (en) * 1978-10-31 1980-07-15 General Electric Company Electromagnetic pump for molten metals
US5499902A (en) * 1991-12-04 1996-03-19 Environamics Corporation Environmentally safe pump including seal
US5340273A (en) * 1991-12-04 1994-08-23 Environamics Corporation Sealing and pumping means and methods environmentally leak-proof pump with misting chamber defined therein
US5411366A (en) * 1991-12-04 1995-05-02 Environamics Corporation Motor driven environmentally safe pump
AU671972B2 (en) * 1991-12-04 1996-09-19 Environamics Corporation Sealing and pumping means and methods
US5494299A (en) * 1994-02-22 1996-02-27 Evironamics Corporation Temperature and pressure resistant rotating seal construction for a pump
US5642888A (en) * 1994-02-22 1997-07-01 Environamics Corporation Temperature and pressure resistant rotating seal construction for a pump
US5499901A (en) * 1994-03-17 1996-03-19 Environamics Corporation Bearing frame clearance seal construction for a pump
US5591020A (en) * 1994-05-19 1997-01-07 Environamics Corporation Pump oil mister
US5513954A (en) * 1994-06-10 1996-05-07 Envirotech Pumpsystems, Inc. Multilayer pump liner
US5513964A (en) * 1994-10-11 1996-05-07 Environamics Corporation Pump oil mister with reduced windage
US5632608A (en) * 1994-10-11 1997-05-27 Environamics Corporation Pump oil mister with reduced windage
US5599164A (en) * 1995-04-03 1997-02-04 Murray; William E. Centrifugal process pump with booster impeller
US5553867A (en) * 1995-04-21 1996-09-10 Environamics Corporation Triple cartridge seal having one inboard and two concentric seals for chemical processing pump
US5727792A (en) * 1995-04-21 1998-03-17 Environamics Corporation Triple cartridge seal having one inboard and two concentric seals for chemical processing pump
US5823539A (en) * 1995-04-21 1998-10-20 Environamics Corporation Environmentally safe pump having a bellows seal and a split ring shaft seal
US6200086B1 (en) 1999-08-04 2001-03-13 Sundyne Corporation Thermal barrier for use in a mechanical seal assembly
US9980599B2 (en) 2009-02-17 2018-05-29 Koninklijke Douwe Egberts B.V. Coffee bean packaging cartridge and coffee beverage system including same
US10499763B2 (en) 2009-02-17 2019-12-10 Koninklijke Douwe Egberts B.V. Coffee bean packaging cartridge and coffee beverage system including same
US20150118367A1 (en) * 2010-02-17 2015-04-30 Koninklijke Douwe Egberts B.V. Coffee bean packaging cartridge and coffee beverage system including the same
WO2013192503A3 (en) * 2012-06-21 2014-05-01 Flowserve Management Company Thermally compliant pump interfaces
WO2013192503A2 (en) * 2012-06-21 2013-12-27 Flowserve Management Company Thermally compliant pump interfaces
CN103727067A (zh) * 2012-10-11 2014-04-16 闫海群 新型渣浆泵过流装置
CN104533798A (zh) * 2014-11-11 2015-04-22 胡光雄 一种复合防腐耐酸耐磨耐高温渣浆泵
CN108412763A (zh) * 2018-05-09 2018-08-17 淄博联帮泵业有限公司 耐腐耐磨水环式真空泵
CN109114043A (zh) * 2018-08-13 2019-01-01 浙江老百姓泵业有限公司 一种旋涡泵和用于旋涡泵的组合连接部件的制造方法
CN109114043B (zh) * 2018-08-13 2019-08-06 浙江老百姓泵业有限公司 一种旋涡泵和用于旋涡泵的组合连接部件的制造方法
CN111577609A (zh) * 2020-05-28 2020-08-25 邵玉强 一种变量离心泵

Also Published As

Publication number Publication date
GB903904A (en) 1962-08-22
SE300557B (de) 1968-04-29
BE602286A (fr) 1961-10-06
DE1728395A1 (de) 1971-08-12
DE1403879A1 (de) 1969-04-24

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