US20130302160A1 - Sealing arrangement for a flow machine - Google Patents

Sealing arrangement for a flow machine Download PDF

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Publication number
US20130302160A1
US20130302160A1 US13/889,323 US201313889323A US2013302160A1 US 20130302160 A1 US20130302160 A1 US 20130302160A1 US 201313889323 A US201313889323 A US 201313889323A US 2013302160 A1 US2013302160 A1 US 2013302160A1
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US
United States
Prior art keywords
bearing
oil
baffle
sealing arrangement
shaft
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
US13/889,323
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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 MANAGEMENT AG reassignment SULZER MANAGEMENT AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MANNINEN, HEIKKI
Publication of US20130302160A1 publication Critical patent/US20130302160A1/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

    • 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
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6685—Details of collecting or draining, e.g. returning the liquid to a sump
    • 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
    • F04D29/06—Lubrication
    • F04D29/061—Lubrication 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/106—Shaft sealings especially adapted for liquid 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • 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
    • 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
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings

Definitions

  • the present invention relates to a sealing arrangement for a flow machine.
  • the sealing arrangement of the present invention is applicable for sealing bearing arrangements of centrifugal pumps, mixers, blowers etc.
  • the present invention is especially applicable in sealing a bearing assembly including two angular contact ball bearings used in back-to-back configuration.
  • a pair of angular contact ball bearings in back-to-back configuration as a thrust bearing of a centrifugal pump.
  • a thrust bearing is usually lubricated by means of an oil bath such that the oil level in an oil chamber at an axial side of the pair of bearings extends to the centerline of the roller means at their lowest rotational position.
  • the pair of angular contact ball bearings is usually positioned to the end of the flow machine closer to the coupling to the drive shaft and fastened on the shaft by means of a nut.
  • the bearing (of the pair of bearings) closer to the coupling, i.e. the outermost bearing pumps the lubrication oil towards the bearing cover by means of which the bearings are affixed to the bearing housing.
  • WO 2010051959 discusses a construction where, between the bearing and the bearing cover, there are two oil chambers separated from one another by means of a sealing ring leaving a narrow gap between itself and an axial sleeve belonging to the labyrinth seal for oil to flow from the first chamber to the second one.
  • the first chamber is adjacent the bearing and receives oil flow from the bearing.
  • the first chamber is provided with two passages for leading the oil away from the first chamber. In case the first chamber receives more oil than the passages may take out the excess oil flows via the narrow gap to the second chamber, which is, also, provided with a passage for leading oil out of the second chamber.
  • Problems relating to this construction are: 1) that the volume of the first chamber is relatively large, whereby the oil is able to circulate round the volume, which means increased friction, heat generation and, as a consequence, high pumping loss, and 2) that, irrespective of the volume of the first chamber, the construction has a high flow capacity for the oil due to the oil return passages from the first chamber, which also results in high friction losses in the various flow passages, high energy consumption and heat generation.
  • US 20080044279 discusses a shaft sealing where an isolated drain path for lubricant has been arranged between the bearing and the bearing cover.
  • the drain path is formed of a first chamber adjacent the bearing to which chamber the oil flown through or pumped by the bearing may freely enter.
  • the first chamber is limited at its side opposite to the bearing by means of a radial wall, which extends to the shaft leaving a gap between itself and the shaft for oil to flow to the second chamber.
  • the second chamber extends radially outwardly from the shaft and continues as an axial passage taking oil to the oil cavity.
  • a problem with this construction is the axial extension it requires.
  • the US document does not discuss or show any means for locking the bearing on the shaft, but in any case such means are needed.
  • the wall between the first and the second chamber extends to the close proximity of the shaft the wall has to be arranged so far from the bearing that the locking means may be left between the wall and the bearing, Therefore the volume of the first chamber grows and the distance between the bearing and the bearing cover is increased.
  • Another problem related to the discussed construction is a high oil volume rotating in the first chamber, which increases friction, energy consumption and heat generation.
  • an object of the present invention is to develop a new type of shaft sealing for a flow machine capable of avoiding at least one of the above discussed problems.
  • a further object of the present invention is to develop such a novel construction for a shaft sealing arrangement of a flow machine that is capable of returning all the oil that enters in front of the shaft sealing via the bearings back to the oil chamber at the opposite side of the bearings.
  • a still further object of the present invention is to minimize the volume of the chamber in which the oil enters from the bearing for keeping the amount of oil in contact with the rotating parts of the shaft and bearing at its minimum.
  • Yet one more object of the present invention is to minimize the energy consumption of the bearing by reducing the friction and heat generation into its minimum.
  • a sealing arrangement for a flow machine comprising at least an axis, a shaft, a thrust bearing formed of a pair of angular contact ball bearings in back-to-back configuration, the ball bearings having an inner bearing ring and an outer bearing ring, a shaft sealing, a bearing cover at an outer end of the flow machine, an oil chamber at the side of the thrust bearing opposite the bearing cover, a baffle arranged between the thrust bearing and the bearing cover for forming an oil channel between itself and the bearing cover, and a return groove or bore for returning oil from the oil channel to the oil chamber, wherein there is a gap between the baffle and the inner bearing ring for the entire oil flow from the bearing to the oil channel and further to the oil chamber.
  • FIG. 1 illustrates an end part of a shaft of a flow machine with the thrust bearing and shaft sealing in accordance with prior art
  • FIG. 1 a illustrates the shaft—thrust bearing—shaft seal assembly of FIG. 1 in an enlarged scale
  • FIG. 2 illustrates an end part of a shaft of a flow machine with the thrust bearing and shaft sealing in accordance a preferred embodiment of the present invention
  • FIG. 2 a illustrates the shaft—thrust bearing—shaft seal assembly of FIG. 2 in an enlarged scale
  • FIG. 3 a illustrates the shaft—thrust bearing—shaft seal assembly of a second preferred embodiment of the present invention in an enlarged scale
  • FIG. 3 b illustrates the shaft—thrust bearing—shaft seal assembly of a third preferred embodiment of the present invention in an enlarged scale.
  • FIGS. 1 and 1 a illustrate a partial cross section of a prior art flow machine 2 having a shaft 4 , a pair of angular contact ball bearings 6 in back-to-back configuration and a shaft sealing 8 .
  • the pair of angular contact ball bearings 6 acts as a thrust bearing of a flow machine, for instance a centrifugal pump.
  • the angular contact ball bearings are formed of an inner ring 6 i , an outer ring 6 o and bearing balls 10 therebetween.
  • the thrust bearing 6 has been fastened on the shaft 4 by tightening the inner rings 6 i against a shoulder on the shaft 4 by means of a nut 12 that is sometimes provided with a washer.
  • the outer rings 6 o of the thrust bearing 6 are positioned against the inner surface of the bearing housing 14 .
  • a bearing cover 16 having a central hole for the shaft 4 and the shaft sealing 8 has been fastened to the outer end of the bearing housing 14 , i.e. to the end of the flow machine remove from the working member, for instance the impeller of a centrifugal pump or the rotor of a mixer.
  • the shaft sealing 8 here a labyrinth seal has been shown, though also lip-type seals are sometimes used, is inserted in the central hole in the bearing cover 16 .
  • the bearing cover 16 is sealed by means of, for instance, O-rings in relation to both the shaft sealing 8 and the bearing housing 14 .
  • the bearing housing 14 is provided with a groove 18 at the outer end thereof at the side of the outer bearing ring 6 o and a groove 20 or bore leading in more or less axial direction from the groove 18 to the central oil chamber 22 .
  • the oil level L in the oil chamber 22 extends normally up to the centerline of the bearing balls 10 as shown in FIG. 1 a.
  • the above is the traditional structure of the thrust bearing—shaft sealing assembly of a flow machine.
  • the same has also been shown in U.S. Pat. No. B2-6,672,830.
  • the shaft sealing of the assembly was apt to leak.
  • the leakage related problem was tried to be solved by means of an improvement shown in FIGS. 1 and 1 a .
  • the improvement in the shaft sealing 8 comprises a lip or an axial inward extension 24 of the shaft sealing 8 that leaves a narrow circumferential gap 26 between itself and the radial side face of the inner thrust bearing ring 6 i .
  • the purpose of the gap 26 is to restrict or to throttle the oil flow from the cavity 28 between the thrust bearing 6 and the bearing cover 16 towards the shaft.
  • the right hand side ball bearing of the pair of angular contact ball bearings 6 function such that the balls 10 running along the inner surface of the outer bearing ring 6 o squeezes oil from the oil film on the inner surface of the outer bearing ring 6 o axially outwards. It means that the oil exiting the bearing ring surface has a high speed in axial direction (see arrow A in FIG. 1 a ).
  • the high speed of oil above the circular groove 18 results, in accordance with Bernoulli's law, a reduction in the pressure (i.e. a partial vacuum) above the groove 18 , which makes the oil flow along the groove 20 or a corresponding bore from the oil chamber 22 towards the shaft sealing, i.e.
  • each prior art bearing assembly has its nominal speed of rotation by which the oil level is raised up to the surface of the shaft 4 , which means, when using labyrinth type sealing, oil leakage through the sealing.
  • FIGS. 2 and 2 a illustrate a preferred embodiment of the present invention solving both the problem discussed in connection with FIGS. 1 and 1 a and the problems referred to in the background art.
  • the prior art problem leading to the increased risk of oil leakage was due to bearing balls 10 pumping oil at a high speed transverse across the groove/channel that was designed for the removal of oil, and thus creating a partial vacuum there
  • the problem is solved by cutting the direct flow connection between the interior of the bearing and the oil return groove or bore. It has been accomplished by either redesigning the bearing cover 30 to include a baffle 32 or by arranging a separate baffle between the bearing cover and the thrust bearing 6 .
  • the bearing cover 30 extends axially up to the radial face of the outer bearing ring 6 o (of the right hand side angular contact ball bearing or the angular contact ball bearing facing the bearing cover or the outer end of the flow machine or that of the bearing housing) and has a radially inwardly (towards the shaft 4 ) directed baffle 32 that extends to the side of the inner bearing ring 6 i (of the right hand side angular contact ball bearing or the angular contact ball bearing facing the bearing cover or the outer end of the flow machine or that of the bearing housing) such that the distance D 2 from the axis of the flow machine to the inner surface 34 of the baffle 32 is smaller than the outer radius of the inner bearing ring 6 i .
  • a axial gap 36 is formed between the baffle 32 and the radial side face of the inner bearing ring 6 i .
  • the dimension of the gap 36 is preferably, but not necessarily, about 0.2-0.7 mm depending on the size of the bearings, rotational speed of the flow machine, etc.
  • the bottom of the channel 38 is provided with a bore 40 extending through the bearing cover 30 to a preferably axial groove 20 arranged in the inside surface of the bearing housing 14 .
  • the groove 20 may be replaced with an axial or slightly inclined bore if desired.
  • the bore 40 and the groove 20 or bore function as the oil return passage in case oil from the thrust bearing 6 enters the channel 38 between the baffle 32 and the rest of the bearing cover 30 .
  • the channel 38 of the present invention is an open cavity having no specific pressure conditions unlike the groove 18 of the prior art flow machine where a partial vacuum created in the groove 18 was drawing oil from the groove 20 .
  • the inner circumference or inner surface 34 of the baffle 32 extends closer (dimension D 2 ) to the axis of the flow machine than the oil level L (dimension D 1 )
  • the oil entering the channel 38 raises the oil level in the channel whereafter the oil is able to return via the bore 40 and the groove 20 back to the oil chamber 22 as soon as the hydrostatic pressure in the channel 38 is higher than that in the oil chamber 22 .
  • the return channel 38 of the oil has been moved to an open position far from the rotary members and other areas of high flow velocity which would have a negative effect on the functioning of the return channel 38 .
  • the return bore 40 and the return groove 20 have to be dimensioned large enough to be capable of handling the entire oil flow.
  • baffle 32 is at a small axial distance of less than 1 mm from the inner bearing ring, the volume of the cavity where the oil is rotating is minimized. This results in minimized oil circulation between the baffle and the bearing and thereby to minimized friction, energy consumption and heat generation.
  • the bearing cover and the baffle may also be separate parts as shown in FIGS. 3 a and 3 b .
  • the functional part of the baffle i.e. the radially innermost part of the baffle is always the same, especially its dimensioning in relation to both the outer diameter of the inner bearing ring and the distance between the oil level in the oil chamber from the axis, as well as its distance from the inner bearing ring.
  • the foot part i.e. the radially outer part of the baffle may vary.
  • the separate baffle 32 ′ is pressed by the bearing cover 30 against the radially outer ring 6 o of the axially outer bearing.
  • FIG. 3 a the separate baffle 32 ′ is pressed by the bearing cover 30 against the radially outer ring 6 o of the axially outer bearing.
  • the baffle 32 ′′ is a separate part, preferably a ring arranged inside the bearing cover 30 between the bearing 6 and the bearing cover 30 .
  • the baffle 32 ′′ may extend axially from the bearing cover 30 to the level of the bearing or at a distance thereof (shown in FIG. 3 b ).
  • the baffle is a separate member, like in FIG. 3 b , but now it leaves an axial gap between itself and the bearing cover, whereby the gap may function as the oil channel 38 .
  • the baffle is, in its all structural alternatives a circular member surrounding the shaft of the flow machine, whereby also the channel 38 between the baffle and the (rest) of the bearing cover is a circular channel.
  • the groove 20 or the corresponding bore and the bore 40 at the bottom of the channel 38 are located at the lowermost positions of the inner surface of the bearing housing 14 , and the channel 38 , respectively, for ensuring the best possible recirculation of oil back to the central oil chamber.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
US13/889,323 2012-05-09 2013-05-07 Sealing arrangement for a flow machine Abandoned US20130302160A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP12167285.1 2012-05-09
EP12167285 2012-05-09

Publications (1)

Publication Number Publication Date
US20130302160A1 true US20130302160A1 (en) 2013-11-14

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Application Number Title Priority Date Filing Date
US13/889,323 Abandoned US20130302160A1 (en) 2012-05-09 2013-05-07 Sealing arrangement for a flow machine

Country Status (4)

Country Link
US (1) US20130302160A1 (zh)
EP (1) EP2662572A1 (zh)
JP (1) JP2013234757A (zh)
CN (1) CN103388628A (zh)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762788A (zh) * 2017-01-09 2017-05-31 上海第水泵厂有限公司 组合式轴承压盖
US10519968B2 (en) * 2017-09-13 2019-12-31 Fanuc Corporation Motor for suppressing entry of foreign matter
CN113565882A (zh) * 2021-07-30 2021-10-29 北京曙光航空电气有限责任公司 一种高速发电机防止渗油的前端盖密封结构

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5918744B2 (ja) * 2013-12-16 2016-05-18 株式会社荏原製作所 潤滑油流出抑制装置、回転機械、潤滑油の流出抑制方法
CN109538520A (zh) * 2019-01-02 2019-03-29 安德里茨（中国）有限公司 迷宫密封系统
CN112610611A (zh) * 2019-12-16 2021-04-06 刘超 用于水下操作的滚动轴承装置
CN111946826B (zh) * 2020-08-25 2022-05-24 珠海格力电器股份有限公司 油封装置和变速器

Citations (9)

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Publication number Priority date Publication date Assignee Title
US2845312A (en) * 1954-07-28 1958-07-29 Giddings & Lewis Mount for machine tool work support
US3614183A (en) * 1970-02-19 1971-10-19 Federal Mogul Corp Shaft seal with expandable outer periphery
US3796510A (en) * 1971-07-31 1974-03-12 Kugelfischer G Schaefer & Co Shaft mounting for water pumps and the like
US4738185A (en) * 1985-08-09 1988-04-19 Teijin Seiki Company Limited Swash plate-type pump-motor
US4872767A (en) * 1985-04-03 1989-10-10 General Electric Company Bearing support
US6328312B1 (en) * 1999-03-26 2001-12-11 Interseal Dipl. -Ing. Rolf Schmitz Gmbh Shaft seal assembly
US6672830B2 (en) * 1999-10-27 2004-01-06 Environamics Corporation Vertical pump with oil lubricant; C-seal for pump; and pump with threaded shaft position adjustment
US20080044279A1 (en) * 2006-08-17 2008-02-21 Orlowski David C Adaptor Frame
US20100040320A1 (en) * 2007-03-08 2010-02-18 Twin Disc, Inc. Bearing arrangement for heavy duty transmission

Family Cites Families (1)

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Publication number Priority date Publication date Assignee Title
DE102008055793B3 (de) 2008-11-04 2010-09-02 Voith Patent Gmbh Vorrichtung zur Abdichtung einer mit einem flüssigen Schmiermittel geschmierten Lagerung

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2845312A (en) * 1954-07-28 1958-07-29 Giddings & Lewis Mount for machine tool work support
US3614183A (en) * 1970-02-19 1971-10-19 Federal Mogul Corp Shaft seal with expandable outer periphery
US3796510A (en) * 1971-07-31 1974-03-12 Kugelfischer G Schaefer & Co Shaft mounting for water pumps and the like
US4872767A (en) * 1985-04-03 1989-10-10 General Electric Company Bearing support
US4738185A (en) * 1985-08-09 1988-04-19 Teijin Seiki Company Limited Swash plate-type pump-motor
US6328312B1 (en) * 1999-03-26 2001-12-11 Interseal Dipl. -Ing. Rolf Schmitz Gmbh Shaft seal assembly
US6672830B2 (en) * 1999-10-27 2004-01-06 Environamics Corporation Vertical pump with oil lubricant; C-seal for pump; and pump with threaded shaft position adjustment
US20080044279A1 (en) * 2006-08-17 2008-02-21 Orlowski David C Adaptor Frame
US20100040320A1 (en) * 2007-03-08 2010-02-18 Twin Disc, Inc. Bearing arrangement for heavy duty transmission

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106762788A (zh) * 2017-01-09 2017-05-31 上海第水泵厂有限公司 组合式轴承压盖
US10519968B2 (en) * 2017-09-13 2019-12-31 Fanuc Corporation Motor for suppressing entry of foreign matter
CN113565882A (zh) * 2021-07-30 2021-10-29 北京曙光航空电气有限责任公司 一种高速发电机防止渗油的前端盖密封结构

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JP2013234757A (ja) 2013-11-21
EP2662572A1 (en) 2013-11-13
CN103388628A (zh) 2013-11-13

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