US20140314599A1 - Centrifugal pump - Google Patents

Centrifugal pump Download PDF

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Publication number
US20140314599A1
US20140314599A1 US14/256,353 US201414256353A US2014314599A1 US 20140314599 A1 US20140314599 A1 US 20140314599A1 US 201414256353 A US201414256353 A US 201414256353A US 2014314599 A1 US2014314599 A1 US 2014314599A1
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United States
Prior art keywords
bearing
shaft
centrifugal pump
housing
recited
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
US14/256,353
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English (en)
Inventor
Heikki Manninen
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.)
Sulzer Management AG
Original Assignee
Sulzer Pumpen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sulzer Pumpen AG filed Critical Sulzer Pumpen AG
Assigned to SULZER PUMPEN AG reassignment SULZER PUMPEN AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MANNINEN, HEIKKI
Publication of US20140314599A1 publication Critical patent/US20140314599A1/en
Assigned to SULZER MANAGEMENT AG reassignment SULZER MANAGEMENT AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SULZER PUMPEN AG
Abandoned legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/003—Couplings; Details of shafts
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/049—Roller bearings
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/083—Structural association with bearings radially supporting the rotary shaft at both ends of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F16C19/166—Four-point-contact ball bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators

Definitions

  • the present invention relates to a centrifugal pump and especially to a new kind of a bearing arrangement for a centrifugal pump and a novel bearing housing. Therefore, the present invention also relates to the shaft, the housing and the rotor of the centrifugal pump.
  • centrifugal pump and an impeller thereof have been discussed as an example.
  • centrifugal pumps with regard to its drive.
  • a traditional type is a so-called “long- coupled” centrifugal pump where the shaft of the drive motor is coupled to the shaft of the centrifugal pump by means of a coupling.
  • Another type is a so-called “close-coupled” centrifugal pump, which means that the centrifugal pump and the motor utilize the same shaft and the same bearings, as shown, for instance, in WO-A1-2009127781.
  • the latter is, naturally, a preferred option nowadays, as fewer parts are needed in the pump-motor combination.
  • the long-coupled centrifugal pumps have, thus, a shaft supported on its own bearings whereas the drive motor has its own shaft on its own support bearings.
  • the bearings of the centrifugal pump have been arranged such that one of the bearings is designed to take care of the axial load, which means in practice, on the one hand, that the bearing has to be able to handle axial loads, and, on the other hand, that the bearing rings of the bearing handling the axial load are fastened immobile on the shaft and within the bearing housing.
  • the bearing carrying the axial load has to carry radial forces, too.
  • the other bearing carrying merely radial loads is fastened immobile on the shaft but either the bearing itself allows axial movement between the bearing rings (slide bearings, for instance), or the outer bearing ring is able to slide axially within the bearing housing.
  • the bearing assembly carrying both axial and radial loads i.e. the thrust bearing is most often formed of a pair of single row angular contact ball bearings arranged in back-to-back configuration. In place of angular contact ball bearings also tapered roller bearings have been used.
  • the bearing assembly is installed near the coupling i.e. close to the end of the shaft opposite to the rotor of the flow machine.
  • the bearing carrying only radial loads is typically a single row ball bearing, or a roller bearing, or a slide bearing, and is typically arranged on the shaft closer to the rotor.
  • the main reason for positioning the thrust bearing assembly farther away from the rotor is that in that way the radial forces affecting the thrust bearing assembly are smaller and in that way the bearing is not so highly stressed by forces in two dimensions.
  • the bearing arranged closer to the rotor may be designed and chosen for absorbing the radial loads only.
  • CN 2447239 Y discusses a belt-driven pump the shaft of the pump being supported on bearings such that the bearing closer to the pump impeller is a ball bearing carrying the axial load and the bearing farther away from the impeller is a roller bearing carrying only the axial load.
  • the Chinese document discusses, in connection with the axially supporting bearing, i.e. a thrust bearing, a four point contact bearing, which means basically an ordinary ball bearing having one inner ring, one outer ring and the bearing balls therebetween.
  • the grooves in the inner and outer rings are formed such that they are substantially V-shaped whereby the balls run along a circular path on the faces of the V-shaped grooves. This construction makes it possible to call the bearing a four-point contact bearing.
  • the inner groove of the bearing is machined into the shaft surface and the assembly of the Chinese bearing allows only a limited number of balls to be inserted between the inner and the outer rings, whereby the load-carrying capacity of the bearing is limited.
  • the loads subjected to the bearing may vary a great deal.
  • This means in practice that the radial and/or axial loads subjected in a certain application to a centrifugal pump may be two or three times higher than loads subjected in another application to a similar pump having identical construction.
  • This kind of change in loads means that a bearing having a high load-carrying capacity is too heavy for a pump subjected to the lighter load. In other words, the bearings have to be changed to match the load conditions.
  • moving from a bearing designed to have a high load-carrying capacity to a bearing having a low load- carrying capacity means reduction in the dimensions, i.e. the outer diameter and the axial length of the bearing provided that the shaft is maintained the same.
  • the pump manufacturer has two options, either to manufacture at least two different bearing housings for the different bearings or to manufacture fillings with which the smaller bearings may be fitted into the bearing housing dimensioned for the heaviest load, i.e. for the bearings a high load-carrying capacity. Both cases mean increased costs for the manufacture.
  • angular contact ball bearings themselves have a drawback of their own, as, when in use, they tend to pump the lubricating oil from one side of the bearing to the opposite side thereof. This is especially true when two such bearings have been positioned in back-to-back configuration.
  • the pumping of oil sets high demands on both the shaft sealing at a side of the bearing and the circulation passage returning oil back to the oil chamber.
  • the close-coupled centrifugal pumps aim, naturally, at a simplified construction and reduction in the costs of manufacture, assembly and maintenance of the centrifugal pumps, as a number of traditional components may be left out, like for instance the coupling, one shaft and two bearings.
  • a number of traditional components may be left out, like for instance the coupling, one shaft and two bearings.
  • the normal way of constructing, for instance, a close-coupled centrifugal pump is such that the centrifugal impeller is attached at the end of the shaft of the electric motor whereby the bearings of the electric motor have to be able to absorb both radial and axial loads subjected to the shaft of the motor.
  • standard electric motors which are, naturally, an attractive choice for driving centrifugal pumps due to their competitive price level, do not have a construction designed for handling the loads created by centrifugal pumps.
  • Practice has shown that either the bearings wear out very quickly or the bearing housings of the electric motors break, as they are not sturdy enough to absorb the forces subjected to them.
  • the running clearances of the bearings of an electric motor must be quite wide, of the order of 0.3-0.4 mm, when the bearings are arranged within the electric motor, as, again, the heating of an electric motor has to be taken into account.
  • the rotor of a centrifugal pump has to be provided quite wide radial and axial gaps at its perimeter so that the rotor is able to rotate without mechanical contact when starting the electric motor, i.e. when the bearings are cold.
  • an object of the present invention is to eliminate at least one of the above mentioned drawbacks or problems by means of a novel arrangement for supporting the shaft of a centrifugal pump.
  • Another object of the present invention is to develop a novel bearing housing structure applicable to both close-coupled and long-coupled centrifugal pumps.
  • a further object of the present invention is to suggest a novel bearing arrangement for a centrifugal pump.
  • a still further object of the present invention is to minimize the effects of temperature on the shaft of a centrifugal pump.
  • the present invention brings about a number of advantages, like for instance
  • FIG. 1 illustrates schematically as an example of a prior art centrifugal pump a partial cross section of a centrifugal pump
  • FIG. 2 illustrates schematically as an example of a novel centrifugal pump a partial cross section of a centrifugal pump including the bearing arrangement and the bearing housing in accordance with a preferred embodiment of the present invention
  • FIG. 3 illustrates schematically a partial cross section of the bearing assembly of FIG. 2 in an enlarged scale.
  • FIG. 1 illustrates as an example of prior art a partial cross section of a centrifugal pump 2 provided with a traditional bearing arrangement and bearing housing 4 .
  • FIG. 1 is a partial axial cross section of a centrifugal pump 2 , which comprises a shaft 6 having a rotor 8 , i.e. an impeller at its first axial end.
  • the shaft 6 if supported by the bearing housing 4 having a first axial end 4 ′ with a first bearing assembly 10 and a second axial end 4 ′′ with a second bearing assembly 12 .
  • the first bearing assembly 10 at the first end 4 ′ of the bearing housing 4 is closer to the rotor 8 than the second bearing assembly 12 such that a shaft sealing 14 is arranged between the rotor 8 and the first bearing assembly 10 .
  • the shaft sealing 14 is arranged within a seal housing 16 , which is a part of the rear wall 18 of the centrifugal pump 2 .
  • the second bearing assembly 12 is arranged at the second end 4 ′′ of the bearing housing 4 such that a sealing, preferably a labyrinth seal 20 , in connection with the bearing cover 22 , is arranged between the second bearing assembly 12 and the drive means (not shown) arranged at the end of the shaft 6 .
  • the first bearing assembly is a roller bearing 10 and has its inner bearing ring shrink-fitted on the shaft and its outer ring axially slidably on the bearing housing bore, whereby it is obvious that the first bearing assembly 10 does not absorb any axial forces subjected to the shaft 6 .
  • the second bearing assembly 12 comprises a pair of angular contact ball bearings arranged in back-to-back configuration.
  • the inner bearing rings are shrink-fitted on the shaft 6 , and additional secured in axial direction by means of a nut 24 threaded on the shaft.
  • the outer ring of the second bearing assembly 12 is secured in a housing bore by means of a bearing cover 22 bolted to the end of the bearing housing 4 .
  • the second bearing assembly 12 absorbs the axial loads subjected to the shaft 6 in addition to radial forces.
  • the bearing housing 4 is provided with means 26 for fastening an intermediate frame 28 to the bearing housing 4 .
  • the intermediate frame 28 connects the bearing housing 4 to the housing 30 of the centrifugal pump 2 at about the same radius as the rear wall 18 of the centrifugal pump is sealed (preferably, but not necessarily, by means of an 0 -ring arranged in an annular groove) to the housing 30 of the centrifugal pump 2 .
  • the fastening means 26 are bolts with which the intermediate frame 28 is attached to the bearing housing 4 .
  • FIG. 2 illustrates a partial axial cross section of a centrifugal pump 40 in accordance with a preferred embodiment of the present invention.
  • the centrifugal pump 40 comprises a shaft 42 having a rotor 44 , i.e. an impeller at its first axial end 42 ′, and drive means, i.e. an electric drive motor 46 at its second axial end 42 ′′.
  • the shaft 42 if supported by the bearing housing 48 having a first axial end 48 ′ with a first bearing assembly 50 and a second axial end 48 ′′ with a second bearing assembly 52 .
  • the first bearing assembly 50 at the first end 48 ′ of the bearing housing 48 is closer to the rotor 44 than the second bearing assembly 52 such that a shaft sealing 54 is arranged between the rotor 44 and the first bearing assembly 50 .
  • the shaft sealing 54 is arranged within a seal housing 56 , which may be a part of the rear wall 58 of the centrifugal pump 40 .
  • the second bearing assembly 52 is arranged at the second end 48 ′′ of the bearing housing 48 such that a sealing, preferably a labyrinth seal 60 , is arranged between the second bearing assembly 52 and the drive means 46 .
  • the second bearing assembly 52 has its inner ring shrink-fitted on the shaft 42 and its outer ring axially slidably on the bearing housing bore 62 , whereby it is obvious that the second bearing assembly 52 does not absorb any axial forces subjected to the shaft 42 .
  • the first bearing assembly 50 is arranged such that its inner ring is shrink-fitted on the shaft 42 , and additionally secured in axial direction by means of a distance ring 64 and a snap ring 66 arranged in an annular groove 68 on the shaft 42 (shown in more detail in FIG. 3 ).
  • the outer ring of the first bearing assembly 50 is secured in a housing bore 70 by means of a bearing cover 72 bolted on the bearing housing 48 at its first end 48 ′.
  • the first bearing assembly 50 absorbs, in addition to radial load, the axial load subjected to the shaft 42 .
  • the bearing housing 48 is provided with an outwardly extending part 76 by means of which the bearing housing 48 is attached to the housing 78 of the centrifugal pump 40 at about the same radius as the rear wall 58 of the centrifugal pump 40 is sealed (preferably, but not necessarily) by means of an O-ring 80 arranged in an annular groove in the outer circumference of the back wall 58 to the housing 78 of the centrifugal pump 40 .
  • the rear wall 58 of the centrifugal pump 40 is secured by means of bolts (not shown) to the bearing housing 48 .
  • the second end 42 ′′ of the shaft 42 is provided with means for driving the shaft 42 and the rotor 44 thereon.
  • the driving means is, in this embodiment of the present invention an electric motor 46 that is arranged at the second ends 42 ′′ and 48 ′′ of the shaft 42 and the bearing housing 48 .
  • the electric motor 46 has a rotor 82 secured on the shaft 42 at its second end 42 ′′.
  • the rotor is preferably, but not necessarily, attached on the shaft 42 by means of a taper drive sleeve.
  • the bearing housing 48 on its part, is provided with means 84 , for instance a radially outwardly extending flange, for fastening the stator 86 and frame of the electric motor 46 to the housing 48 .
  • the second end 42 ′′ of the shaft 42 is provided with a threaded central hole 88 for the shaft 90 of the fan impeller 92 arranged at the end of the electric motor 46 for circulating cooling air via the electric motor 46 .
  • the central hole 88 is also provided with a guide sleeve for ensuring the correct axial alignment of the shaft 90 .
  • the shaft 42 of the pump such that the fan impeller 92 could be arranged on the same shaft 42 as the rotor 44 of the centrifugal pump.
  • the shaft due to its extension, is not any more applicable for use with a coupling or a belt drive.
  • FIG. 3 illustrates the exemplary centrifugal pump of FIG. 2 in an enlarged scale.
  • the first bearing assembly 50 is arranged such that its inner ring is split, i.e. formed of two rings 50 i 1 and 50 i 2 , and is shrink-fitted on the shaft 42 , and additionally secured in axial direction by means of a distance ring 64 and a snap ring 66 arranged in an annular groove 68 on the shaft 42 (shown in more detail in FIG. 3 ).
  • Another option for securing the inner bearing ring on the shaft is to replace the snap ring and the distance ring with a lock nut and a lock washer (not shown).
  • the outer ring 50 o of the first bearing assembly 50 is secured in a housing bore 70 by means of a bearing cover 72 bolted on the first end 48 ′ of the bearing housing 48 .
  • the bearing cover 72 is at its radially inner perimeter facing the shaft 42 provided with a sealing, preferably but not necessarily, a labyrinth seal 74 .
  • the first bearing assembly is formed of a four-point contact ball bearing 50 , i.e. a bearing having a split inner ring 50 i , formed of two identical inner rings 50 i 1 and 50 i 2 facing one another and an outer ring 50 o .
  • the bearing also includes a number of bearing balls between the inner and the outer rings.
  • the four-point contact ball bearing is a specific form of a contact ball bearing, which has a specific property based on its construction. Now that the inner ring of the four-point contact ball bearing is split, i.e. made of two parts, the loading of the space between the inner and outer rings of the bearing with bearing balls is easier.
  • the bearing balls may be positioned between the outer ring and a first inner ring, and after the space reserved for bearing balls is filled with balls a second inner ring may be positioned in its place.
  • the number of balls in a four-point contact ball bearing is much higher than that in an ordinary ball bearing.
  • the load (both radial and axial) carrying capacity of the four-point contact ball bearings is much higher than that of a traditional ball bearing having only unitary inner and one unitary outer ring.
  • the four-point contact ball bearings having a split 6 inner ring may be used in applications requiring the use of bearings having a high load-carrying capacity.
  • the centrifugal pump may be adjusted to varying loads by selecting or choosing between two bearing types without a need to change the bearing housing or to use any specific fillings.
  • a four point contact ball bearing may be used in heavy duty applications, and a traditional single row contact ball bearing in light-duty applications

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US14/256,353 2013-04-19 2014-04-18 Centrifugal pump Abandoned US20140314599A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP13164522.8 2013-04-19
EP13164522 2013-04-19

Publications (1)

Publication Number Publication Date
US20140314599A1 true US20140314599A1 (en) 2014-10-23

Family

ID=48143136

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/256,353 Abandoned US20140314599A1 (en) 2013-04-19 2014-04-18 Centrifugal pump

Country Status (5)

Country Link
US (1) US20140314599A1 (zh)
EP (1) EP2792884A1 (zh)
CN (1) CN104295504A (zh)
BR (1) BR102014008980A2 (zh)
RU (1) RU2014114211A (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11976593B1 (en) * 2022-10-23 2024-05-07 General Electric Company Bearing assembly

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SI3081816T1 (sl) * 2015-04-13 2021-07-30 Belenos Clean Power Holding Ag Kompresor z dvema kroglama, ki podpirata gred
CN104913006A (zh) * 2015-05-12 2015-09-16 江阴尚爵机械制造有限公司 新型高精度回转支承
WO2023151750A1 (de) * 2022-02-14 2023-08-17 Schaeffler Technologies AG & Co. KG Elektrischer achsantriebsstrang

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US3959990A (en) * 1973-09-21 1976-06-01 Maschinenfabrik Ernst Thielenhaus Assembly for mounting an electric motor on a gearbox
US5971621A (en) * 1998-05-04 1999-10-26 Ford Motor Company Axial shaft retention design
US20080304986A1 (en) * 2007-06-05 2008-12-11 Resmed Limited Blower with bearing tube

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DE1653721B2 (de) * 1967-03-08 1979-07-05 Halberg Maschinenbau Gmbh & Co, 6700 Ludwigshafen Ein- oder mehrstufige Kreiselpumpe
US5494413A (en) * 1993-12-09 1996-02-27 Westinghouse Electric Corporation High speed fluid pump powered by an integral canned electrical motor
JPH084686A (ja) * 1994-06-15 1996-01-09 Keihin Seiki Mfg Co Ltd モータ式燃料ポンプにおける軸受装置
CN2447239Y (zh) 2000-07-11 2001-09-12 中国第一汽车集团公司 汽车水泵
DE10204037C5 (de) * 2002-02-01 2009-07-23 Ebm-Papst Landshut Gmbh Radialgebläse mit Elektromotor
CN201071842Y (zh) * 2007-06-28 2008-06-11 上海东方泵业(集团)有限公司 中开单级双吸离心泵
FI121645B (fi) 2008-04-18 2011-02-15 Randax Oy Menetelmä sähkökoneen rungon valmistamiseksi, sähkökone ja sähkökoneen runko
CN202140425U (zh) * 2011-07-15 2012-02-08 常州光洋轴承股份有限公司 大中型四点接触球轴承
CN202348990U (zh) * 2011-12-15 2012-07-25 西安航天泵业有限公司 分体轴瓦座式滑动轴承箱

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3959990A (en) * 1973-09-21 1976-06-01 Maschinenfabrik Ernst Thielenhaus Assembly for mounting an electric motor on a gearbox
US5971621A (en) * 1998-05-04 1999-10-26 Ford Motor Company Axial shaft retention design
US20080304986A1 (en) * 2007-06-05 2008-12-11 Resmed Limited Blower with bearing tube

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11976593B1 (en) * 2022-10-23 2024-05-07 General Electric Company Bearing assembly

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EP2792884A1 (en) 2014-10-22
CN104295504A (zh) 2015-01-21
BR102014008980A2 (pt) 2015-10-13
RU2014114211A (ru) 2015-10-20

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