US3655250A - Thrust bearing - Google Patents

Thrust bearing Download PDF

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Publication number
US3655250A
US3655250A US56898A US3655250DA US3655250A US 3655250 A US3655250 A US 3655250A US 56898 A US56898 A US 56898A US 3655250D A US3655250D A US 3655250DA US 3655250 A US3655250 A US 3655250A
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United States
Prior art keywords
bearing
rocker
bars
rockers
bar
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Expired - Lifetime
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US56898A
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English (en)
Inventor
Walter Sprenger
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Brown Boveri Sulzer Turbomaschinen AG
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Brown Boveri Sulzer Turbomaschinen AG
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    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/06—Sliding-contact bearings for exclusively rotary movement for axial load only with tiltably-supported segments, e.g. Michell 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/02—Arrangements for equalising the load on a plurality of bearings or their elements

Definitions

  • a E SPRENGE/Q TIIRUST BEARING Thrust bearings have been known in which a thrust collar fixedly mounted on a shaft has slid on the bearing surfaces on a number of bearing segments which have been grouped in annular array around the shaft. These bearing segments have been pivotally mounted to a limited extent in order to allow for alignment relative to the positions of the thrust collar bearing surfaces and to the resultant lubricant wedge therebetween. To this end, each of the bearing segments have been supported on a supporting bar by means of a joint in the zone of the lubricant wedge pressure center while each supporting bar has had at least one support surface on an approximately radially oriented side bearing on a corresponding mating surface on one side of a rocker which has been common to a pair of such supporting bars.
  • rockers have become locked in the deflected position in the event of a fault due to deflection of the shaft axis relative to the housing axis.
  • the supporting structure of the rockers and bars together with the bearing segments can be returned into the normal position only after the bearing has been relieved of the load.
  • Thrust bearings have also been known in which the supporting positions of the rockers on the bearing housing and the mating supporting surfaces at the ends of the rocker on which the bars are supported have been disposed in a plane which is perpendicular to the axes of the bearing housing and shaft when the relative position of the bearing housing and shaft have been parallel.
  • the supporting positions have been formed by the spherical end surfaces of bolts set into the bearing housing.
  • Such spherical surfaces permit the rockers to execute tilting motions to each side so that the motions of the rocker system have not been confined to the tangential direction. For this reason, however, the supporting structure of these bearings can nevertheless perfon'n motions which cause self-locking of the bearing in deflected positions.
  • the invention provides a thrust bearing which util izes the common application of three characteristics which prevent self-locking of the bearing when deflected relative to the bearing housing.
  • the thrust hearing which is constructed of bearing elements, supporting bars and rockers in a relation similar to that above first mounts each rocker on at least one radially directed roller in a tangentially pivotal manner in the middle zone of the bearing housing. Further, each bar is provided on one radially orientated side with one limited abutment member in the middle zone and on the opposite side with two limited abutment members so that each bar bears at three points on adjacent rockers.
  • the axes of inclination between the rollers and the rockers and the mating support surfaces on the ends of the rockers are disposed in a plane which is perpendicular to the axes of the bearing housing and slzhaft when the housing and shaft are axially parallel to each 0 er.
  • the three-point method of support of the bars on the rockers is obtained by providing each bar with one protruberance in the middle zone on one radially orientated abutment side and with two protruberances on the oppositely disposed abutment side.
  • the same effect can be obtained by providing each rocker with one protruberance on one radially orientated abutment side in the middle zone and with two protruberances on oppositely disposed abutment side.
  • the limited abutment members may also be lightly barrelled.
  • a mating abutment surface which bears on a barrelled abutment surface may be equally barrelled in the same direction to produce a limited surface contact.
  • FIG. 1 illustrates a cross-sectional view taken on line I of FIG. 2 of a shaft bearing according to the invention
  • FIG. 2 illustrates a longitudinal section through the shaft and bearing taken along line II in FIG.
  • FIG. 3 illustrates a developed cross-sectional view through the bars and rockers of the thrust bearing taken along the curved line III of FIG. 1;
  • FIG. 4a illustrates a view of a rocker bearing system on an enlarged scale according to the invention
  • FIG. 4b illustrates a fragmentary view of the rocker taken on line IV -1V of FIG. 4a;
  • FIGS. 5a to 50 illustrates a developed view of the axis of the bar and rockers on half the bearing circumference between the highest and lowest point of the collar during a deflection of the shaft;
  • FIG. 6 illustrates a view of a rocker and two bars with the thrust collar inclined in accordance with FIG. 5;
  • FIG. 7 illustrates a view towards the shaft collar of a bar with limited supporting members
  • FIG. 8 illustrates a view towards the bearing housing of a rocker with limited supporting members
  • FIG. 9 illustrates a meshing of the bevel gear surfaces of bar and rocker
  • FIG. 10 illustrates a view of the supporting surfaces of a bar and rocker having rounded edges according to the invention.
  • FIG. 11 illustrates a view of a bar and rocker utilizing a bevel tooth and a meshing tooth gap according to the invention.
  • a rotatable shaft 2 is axially supported in a bearing housing 1 by means of a thrust collar 3 with the shaft 2 and thrust collar 3 being in accurate coaxial alignment with each other.
  • the shaft 2 and thrust collar 3 may be constructed. integrally or may be joined in a suitable manner from two parts.
  • a thrust hearing which journals the collar 3 in the housing 1 includes a double system of ten bearing segments 10 29 each, as well as 10 supporting bars 30 49 each, and I0 rockers 50 69 in order to transmit the thrust forces of the shaft 2 via the collar 3 to the bearing housing 1.
  • the bearing segments 10 29 are each supported on one associated supporting bar 30 49 by means of a joint 4 which provides allround movability to a limited extent.
  • the all-round movability of the bearing segments 10 29 is necessary in order to define a lubricant wedge between the thrust collar 3 and the sliding surfaces of the bearing segments 10 29; the lubricant wedge corresponding to the physical properties of the lubricant, the applied loading and the rotational speed.
  • the two supporting bars 30 49 of adjacent bearing segments 10 29 are supported at the inwardly facing radially oriented sides 71 by supporting surfaces 72- which rest on a corresponding mating supporting surface 73 on one axially orientated side 74 each of a common rocker 50 69.
  • the middle zone of the rockers 50 69 is
  • the joint 4 between each bearing segment and the supporting bar is provided with a supporting plate 78 of hard metal inserted into a bore of the bearing segment and a journal 79 also constructed of hard metal which is inserted into a bore of the bar and extends into the oppositely disposed bore of the bearing segment to abut against the plate 78 by means of a rounded end as shown.
  • the bearing segment is pivotable or inclinable to a small extent in a universal mannerrelative to the bar but is retained in the radial axial and tangential directions
  • the plate 78 contacts the journal 79 at a point located in an imaginary cylinder 9 Referring to FIG.
  • the bearing segments 29 bear on the cylinder internal walls 91, 92 of the annular groove 70 on two oppositely disposed sides 90 with a slight clearance.
  • the position of the bearing segments 10 29 within the bearing is thus defined to the extent that such segments can be inclined only to a limited extent universally and can be displaced in the axial direction.
  • the absolute magnitude of the limited freedom of movement depends on the deviation between the axes of the shaft 2 and the bearing housing 1 which occurs during installation and arise subsequently under the operating loads. In most cases, the angular deviations, even in bearings for large machines, will be substantially or far less than 5 mm. per 1 m. or below the limit of one degree of arc.
  • the rockers 50 69 are also placed into the annular grooves 70 with the clearance of the rockers 50 69 between the walls 91, 92 of each annular groove 70 being so dimensioned as to provide only a limited freedom of movement in the same way as for the bars 30 49.
  • each rocker 50 69 is provided with a radial groove 93 into which a pair of rollers 94 are placed to transmit the axial thrust of the shaft 2 to the housing 1.
  • the rollers 94 pivotally support the rocker 50-69 on an axis of the joint 5 which lies in a common plane 84 with the axes of the remaining joints 5.
  • a pin 95 is inserted in the bearing housing I to engage in a bore 96 of the rocker located between the rollers 94.
  • This pin 95 which is of a diameter equal to the diameter of the bore 95 is provided with a spherical periphery 95 where the pin 95 is received in the rocker.
  • the spherical periphery 95' is of a diameter equal to the bore diameter and the mid-point is situated in the plane 84 (FIG. 4b) so that the rocker is tangentially located in the annular groove 70 while being capable of executing angular motions to a limited extent in the tangential direction through the rollers 94.
  • the supporting surfaces 72 of the bars 30 49 and the mating supporting surfaces 73 of the rockers 50 69, as well as the supporting positions of the bearing segments 10 29 on the bars 30 49 and of the rockers on the base surface 89 of the groove 70 and the bearing segments themselves are so disposed and dimensioned as to permit the formation of lubricant wedges between the sliding surfaces of the bearing seg ments l0 29 and thrust collar 3.
  • the sliding surfaces of the collar 3 are thus able to slide on the lubricant wedges without physical contact with the bearing segments 10 29.
  • the axis 6 of the shaft 2 is identical with the axis of the bearing housing 1 so that the bearing elements on one side of the thrust collar 3 are positioned accurately symmetrically to those of the other side of the collar 3 in relation to the central plane 97 of the thrust collar 3.
  • the supporting surfaces 72 and mating supporting surfaces 73 of the respective bars and rockers are disposed in common planes 77 while the centers of the joints 4, 5 of the bars and rockers are disposed on a central cylinder 9 of the cylindrical annular grooves 70.
  • the planes 77 are coincident with the planes 84 so that each roller contacts the respective rocker on an axis perpendicular to the axis of the shaft while being located in the same plane of the mating contact surfaces of the bars and rockers.
  • the shaft axis 6 may incline relative to the axis of the housing 1 and, in appropriate cases, may be displaced transversely to the position of the bearing center 99.
  • This causes the thrust collar 3 to be inclined through a small angle relative to the shaft axis 6 with the axial distances between the sliding surfaces of the collar 3 and the base surface 89 of the grooves 70 varying in the same manner. That is, the axial distances will increase on one hearing side and will be reduced on the other bearing side.
  • the pattern formed by the bars 30 49 and rockers 50 69 in section with the cylinder surface 9 (FIG. 2) in the inclined position of the axis of the shaft 2 relative to the housing axis 6, in the interests of simplification is illustrated as a straight line although strictly speaking the line of intersection between the plane 77 and the cylinder 9 being an oblique section through a cylinder, would yield an ellipse and in developed form would yield a sinusoidal line.
  • the deviation from a straight line is so small that no noticeable falsification of the results is produced.
  • the vertical deviations of the bearing segments 10 29 from their symmetrical normal position are shown in greatly exaggerated form relative to any deviation which could actually occur. Only negligeable, secondary deviations will therefore occur in the end result.
  • FIG. 5 is based on an inclination of the shaft 2 and of the thrust collar 3 in which the joints 4 of the bars 30 and 35 being on diametrically opposite sides of the bearing experience the greatest axial deviations (namely the amount h) to one or the other side of the original position, i.e. from the plane 84.
  • the new locations of the pivoting points of the bars 30 35 are provided on' one side of the axis of symmetry 7 7 with the following ordinates:
  • the bars and rockers form respective lines 3035 and 50 54, such that, as shown, for reasons of geometry the line is centrally symmetrical relative to the pivoting point of the rocker 52.
  • the the event of a relative change of angle of the axes of the shaft 2 and bearing housing 1 within the limitations of the technically permissible changes of form, the inclination of the segment mm on one side as well as the inclination of the segment rim on the other side of the thrust collar 30 can vary within the position of the groove base 89 having to be modified. Accordingly, and because of the adjustability described hereinabove, the individual segments will support equal parts of the overall axial thrust of the shaft 2 even when these segments are in the modified position.
  • the abutment surfaces at the radially oriented sides 71 of the bars 30 49 are substantially reduced by recessing so that two supporting members 83 remain on one side 71 while one supporting member 82 remains on the opposite side 71.
  • the surface of these supporting members 82, 83 is limited to the extent that the plane of the bar 30 49 can easily adapt to the mating supporting surfaces 73 of the rockers which support the bars.
  • the rockers 50 69 can alternatively be provided with three limited supporting members 87, 88 respectively, as above instead of the bars 30 49. In sucha case, the rockers will adapt to the corresponding bar abutment planes.
  • At least one of the limited supporting members can be constructed in slightly barrelled form with the mating supporting member barrelled in the opposite sense to produce a surface contact between the two supporting members. This surface contact will also simultaneously secure the tangential distance between a rocker and the bar supported thereon. The tangential location of the rockers at the same time also locates the tangential position of the bars.
  • the bars 30 49 and the rockers 50 69 may also be provided with supporting surfaces 72, 73, respectively of the three-point support, the profile of which is constructed in the form of a gearwheel flank.
  • the adjacent bars and rockers contact along contact axes located on the abutment surfaces 72, 73, respectively, which contact axes 110, 111 are located in respective pitch circles 90, 98, and in an axial plane 116.
  • the contact axes 110, 111 will remain in the axial plane 116 if a suitable flank profile is provided since the effective length of the lever arm of one bar and of the rocker supported thereon remain equal among themselves under all conditions of deflection from the central axis 84.
  • the gearwheel flanks of the support surfaces 72, 73 thus use only a limited part of the tooth flank for physical contact even with the largest deflections from the central position.
  • the three-point supporting surfaces of the bars and rockers can also be provided with a greater or lesser rounding having of the edges on the lateral surfaces 71 or 74 as such provides approximately the same effect as the strictly accurate shape complying with a gearwheel flank profile as described with respect to FIG. 9.
  • a thrust bearing comprising a plurality of bearing segments disposed in a spaced apart annular array
  • each bar pivotally supporting a respective bearing segment thereon in a universal manner
  • each rocker having a radially oriented groove therein and mounting a pair of adjacent supporting bars on opposite radial sides thereof in pivotal relation, each said rocker pivotally mounting one of said pair of bars at one point and the other of said pair of bars at two points, said points being disposed in a common plane;
  • each roller being disposed in a respective rocker in said groove thereof to pivotally mount said rocker in a direction tangentially of the thrust bearing about an axis located in said common plane.
  • each said bar has one limited abutment member in the middle zone of one radially oriented side bearing on one adjacent rocker and a pair of limited abutment members on the opposite side bearing on another adjacent rocker.
  • each rocker has one protuberance in the middle zone of one radially oriented side bearing on an adjacent bar and a pair of protuberances on the opposite side bearing on another adjacent bar.
  • a thrust bearing mounted in said housing coaxially of said collar, said bearing including a plurality of an nularly spaced bearing segments opposite said collar, a plurality of supporting bars, a joint between each of said bars and a respective one of said bearing segments for pivotally mounting said bearing segment on said bar in a zone of lubricant wedge pressure center a plurality of rockers, each said rocker being positioned between a pair of said bars and having a surface at two opposite ends thereof pivotally mounting an end of each of said pair of bars thereon, and a joint means between each of said rockers and said bearing housing including at least one radially oriented roller for pivotally mounting said rockers in the middle zone thereof on said bearing housing and tangentially of said collar, each supporting bar having one limited abutment member in the middle of one radially oriented side bearing on one of said rockers and two limited abutment members on the opposite side bearing on an adjacent rocker whereby each supporting bar has a three
  • each said roller contacts said respective rocker on an axis perpendicular to said axis of said shaft and located in said plane of said mating contact surfaces of said bore and said rockers.
  • a thrust bearing comprising a plurality of bearing segments disposed in a spaced apart annular array
  • each joint being disposed between a respective bearing segment and a supporting bar for pivotally mounting said bearing segment on said supporting bar in a universal manner;
  • each rocker mounting a pair of adjacent supporting bars on opposite radial sides thereof in pivotal relation, each said bar said supporting one protuberance projecting from the middle zone of one radially oriented side bearing on one adjacent rocker and a pair of a plurality of rockers, each rocker mounting a pair of adjacent supporting bars on opposite radial sides thereof in pivotal relation, each rocker having one protuberance in the middle zone of one radially oriented side bearing on an adjacent bar and a pair of protuberances on the opposite side bearing on another adjacent bar;
  • each joint being disposed in one of said rockers to pivotally mount said rocker in a direction tangentially of the thrust bearing.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Sliding-Contact Bearings (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rolls And Other Rotary Bodies (AREA)
US56898A 1969-07-31 1970-07-21 Thrust bearing Expired - Lifetime US3655250A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH1172869A CH511378A (de) 1969-07-31 1969-07-31 Axiallager, in welchem der Spurkragen auf einer Anzahl um die Welle gruppierter Gleitsegmente abgestützt ist

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US3655250A true US3655250A (en) 1972-04-11

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US56898A Expired - Lifetime US3655250A (en) 1969-07-31 1970-07-21 Thrust bearing

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US (1) US3655250A (nl)
JP (1) JPS4841170B1 (nl)
CA (1) CA923952A (nl)
CH (1) CH511378A (nl)
FR (1) FR2053348B1 (nl)
GB (1) GB1274589A (nl)
NL (1) NL141620B (nl)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3912344A (en) * 1974-02-19 1975-10-14 Kingsbury Inc Thrust bearing assembly
US4335925A (en) * 1978-11-02 1982-06-22 The Glacier Metal Company, Limited Thrust bearing
US4403873A (en) * 1982-01-11 1983-09-13 Waukesha Bearings Corporation Tilting pad thrust bearing
US5046864A (en) * 1991-02-08 1991-09-10 Boller C William Tilting pad thrust bearing assemblies
US5741116A (en) * 1996-12-18 1998-04-21 Delaware Capital Formation Inc. Compressor thrust bearings
CN102878196A (zh) * 2012-09-28 2013-01-16 上海大学 推力轴承平衡机构
US20130315518A1 (en) * 2012-04-18 2013-11-28 Sulzer Pumpen Ag Bearing pad, support body, bearing arrangement and pump
EP3296581A1 (en) * 2016-09-15 2018-03-21 Doosan Skoda Power S.r.o. Thrust bearing assembly

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52119374U (nl) * 1976-03-09 1977-09-09
JPS5780896A (en) * 1980-11-06 1982-05-20 Sharp Corp Small-size speaker for sound synthesis
CN110529493A (zh) * 2019-08-23 2019-12-03 东方电气集团东方汽轮机有限公司 一种均载推力轴承

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1421695A (en) * 1918-01-23 1922-07-04 Kingsbury Albert Bearing
US1666521A (en) * 1925-06-17 1928-04-17 Westinghouse Electric & Mfg Co Thrust bearing
GB822399A (en) * 1954-07-01 1959-10-21 Westinghouse Electric Int Co Improvements in or relating to bearings
US3160450A (en) * 1962-11-16 1964-12-08 Mechanical Tech Inc Thrust bearing

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1421695A (en) * 1918-01-23 1922-07-04 Kingsbury Albert Bearing
US1666521A (en) * 1925-06-17 1928-04-17 Westinghouse Electric & Mfg Co Thrust bearing
GB822399A (en) * 1954-07-01 1959-10-21 Westinghouse Electric Int Co Improvements in or relating to bearings
US3160450A (en) * 1962-11-16 1964-12-08 Mechanical Tech Inc Thrust bearing

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3912344A (en) * 1974-02-19 1975-10-14 Kingsbury Inc Thrust bearing assembly
US4335925A (en) * 1978-11-02 1982-06-22 The Glacier Metal Company, Limited Thrust bearing
US4403873A (en) * 1982-01-11 1983-09-13 Waukesha Bearings Corporation Tilting pad thrust bearing
US5046864A (en) * 1991-02-08 1991-09-10 Boller C William Tilting pad thrust bearing assemblies
US5741116A (en) * 1996-12-18 1998-04-21 Delaware Capital Formation Inc. Compressor thrust bearings
US20130315518A1 (en) * 2012-04-18 2013-11-28 Sulzer Pumpen Ag Bearing pad, support body, bearing arrangement and pump
US9599150B2 (en) * 2012-04-18 2017-03-21 Sulzer Management Ag Bearing pad, support body, bearing arrangement and pump
CN102878196A (zh) * 2012-09-28 2013-01-16 上海大学 推力轴承平衡机构
EP3296581A1 (en) * 2016-09-15 2018-03-21 Doosan Skoda Power S.r.o. Thrust bearing assembly
US10247231B2 (en) 2016-09-15 2019-04-02 Doosan Skoda Power S.R.O. Thrust bearing assembly

Also Published As

Publication number Publication date
FR2053348A1 (nl) 1971-04-16
NL141620B (nl) 1974-03-15
DE1942958B2 (de) 1972-06-15
NL6914171A (nl) 1971-02-02
FR2053348B1 (nl) 1973-04-27
CH511378A (de) 1971-08-15
JPS4841170B1 (nl) 1973-12-05
CA923952A (en) 1973-04-03
GB1274589A (en) 1972-05-17
DE1942958A1 (de) 1971-02-04

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