WO2020108952A1 - Tilting-pad bearing - Google Patents

Tilting-pad bearing Download PDF

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Publication number
WO2020108952A1
WO2020108952A1 PCT/EP2019/080652 EP2019080652W WO2020108952A1 WO 2020108952 A1 WO2020108952 A1 WO 2020108952A1 EP 2019080652 W EP2019080652 W EP 2019080652W WO 2020108952 A1 WO2020108952 A1 WO 2020108952A1
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WO
WIPO (PCT)
Prior art keywords
tilting
bearing
press
fit
web
Prior art date
Application number
PCT/EP2019/080652
Other languages
German (de)
French (fr)
Inventor
Guido Daimer
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2020108952A1 publication Critical patent/WO2020108952A1/en

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Classifications

    • 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
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • F16C17/035—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings the segments being integrally formed with, or rigidly fixed to, a support-element
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1005—Construction relative to lubrication with gas, e.g. air, as lubricant

Definitions

  • the invention relates to a tilting segment bearing for supporting a shaft.
  • Tilt segment bearings are mainly used oil-lubricated at low and medium speeds or circumferential speeds up to approx. 100 m / s.
  • Air-lubricated tilting segment bearings can be used for higher peripheral speeds if the bearing load requirements are not too high. Due to the lower viscosity of the air compared to oil, the lubrication gap heights in the air-lubricated tilting segment bearings are significantly smaller than in the oil-lubricated bearings. In some cases, the lubrication gap heights are in the order of 10pm and are therefore 5 times smaller than with oil-lubricated bearings.
  • the narrower bearing gaps place high demands on the dimensional accuracy of the bearing surface for the shaft to be supported.
  • DE 32 25 423 C2 discloses a tilting segment bearing with a bearing sleeve and a plurality of tilting segments arranged within the bearing sleeve.
  • the tilting segments are each mounted in the bearing sleeve by means of a pin.
  • the tilting segment bearing according to the invention supports a shaft more robustly and thermally and dynamically more stable.
  • the tilting segment bearing has a bearing sleeve and a plurality of tilting segments arranged within the bearing sleeve.
  • the tilting segments are each connected to the bearing sleeve by means of a web, preferably monolithically.
  • the web is very narrow compared to the tilting segment, for example 20 times narrower when viewed in the circumferential direction, so that the tilting segment is connected to the bearing sleeve almost at certain points.
  • connection of the tilting segment to the bearing sleeve is made very elastic, the tilting segment can tip over the web; however, thermal expansions and relative displacements can also be better compensated for, in particular in combination with a bearing sleeve that is not pressed in over the entire circumference.
  • a plurality, preferably three, press-fit surfaces are preferably formed on an outer circumference of the bearing sleeve.
  • the tilting segment bearing or the bearing sleeve is pressed into a housing on the press-fit surfaces.
  • the press fit is therefore not carried out over the entire outer circumference of the bearing sleeve, but only on the press fit surfaces.
  • it is not the entire outer circumference that experiences the maximum radial displacement inwards during the pressing in, but only the press-fit surfaces; the radial displacement of the webs and thus also the tilting segments due to the pressing in can thus be reduced, in particular with increasing distance from the press-fitting surfaces in the circumferential direction or angular direction.
  • the number of press-fit areas thus preferably corresponds to the number of tilting segments or the number of corresponding webs.
  • a web is arranged between two press-fit surfaces in an advantageous embodiment in an angular direction of the tilting segment bearing. This means that radially outwards, a web is not followed by a press-fit area, but rather by a clearance area arranged between them, so that the outer circumference in the area of the web shrinks less than at the press-fit areas.
  • the web is arranged in the middle between two press-fit surfaces. This maximizes the effect described above and consequently minimizes the radial displacement of the web due to the pressing. Corresponding thermal relative displacements are also minimized as a result.
  • the tilting segment bearing is thus designed to be functionally more stable and robust.
  • the webs have an eccentric angular offset to the press-fit surfaces. That means a footbridge has different distances clockwise and counterclockwise to the next two press fit surfaces.
  • the web is not only displaced radially inward, but also slightly tilted tangentially. This creates a tilt pretension of the tilt segment.
  • This is particularly advantageous if there is to be a non-homogeneous lubrication gap between the shaft and the tilting segment; the lubricating gap should preferably decrease in the direction of rotation of the shaft, so that a type of lubricating wedge is formed.
  • the ends of the tilting segments interact radially outward with stop surfaces formed on the bearing sleeve.
  • the stop surfaces thus form a type of radial bearing, in particular during assembly, for the tilting segments in the outward direction. This prevents excessive deformation of the web.
  • the stop surfaces should preferably prevent the tilting segments from deflecting too strongly only when the shaft is being assembled. In operation, no contact should preferably be made here.
  • the tilting segments are arranged off-center on the associated web. This means that the two ends of a tilting segment are at a different distance from the corresponding web. This supports the formation of the lubricating wedge in the operation of the tilting segment bearing.
  • the tilting segment bearing is preferably an air-lubricated tilting segment bearing according to an embodiment of the invention.
  • FIG. 1 shows a schematic cross-sectional view of a tilting segment bearing, only the essential areas being shown;
  • FIG. 2 shows a schematic cross-sectional view of a further tilting segment bearing, only the essential areas being shown; 3 shows a schematic cross-sectional view of a tilting segment bearing in a further embodiment, only the essential areas being shown.
  • FIG. 1 shows a schematic cross-sectional view of an exemplary embodiment of a tilting segment bearing 1, which supports a shaft 20 radially, only the essential areas being shown.
  • the tilting segment bearing 1 has a bearing sleeve 2 and preferably three tilting segments 3.
  • the individual tilting segments 3 are each connected to the bearing sleeve 2 by means of a web 4, preferably the bearing sleeve 2, the tilting segments 3 and the webs 4 are formed in one piece, that is to say monolithically.
  • press-fit surfaces 5 for the arrangement of the tilting segment bearing 1 are formed in a housing (not shown). Accordingly, the press-fit areas 5 alternate over the circumference with release areas 5a, which have a smaller diameter. Ideally, the tilting segment bearing 1 is pressed into the housing at the press-fit surfaces 5.
  • the webs 4, viewed in an angular direction f of the tilting segment bearing 1 are positioned between the press-fit surfaces 5. This means that the bearing sleeve 2 and a clearance surface 5a follow a web 4 in the radial direction outwards, so that the pressing in on the press-fit surfaces 5 results in only a comparatively small radial displacement of the webs 4.
  • the press fit between the housing and the bearing sleeve 2 acts only on the press-fit surfaces 5, but not on the release surfaces 5a.
  • the outer circumference 2a of the bearing sleeve 2 is thus reduced in diameter, particularly in the area of the press-fit surfaces 5; the diameter of the outer circumference 2a in the area of the clearance areas 5a is reduced less.
  • the deformation of the bearing sleeve 2 in the area of the webs 4 is thus reduced, and thus also the radial displacement of the tilting segments 3.
  • the positioning of the tilting segments 3 with respect to the shaft 20 is thus less changed by the pressing of the tilting segment bearing 1 into the housing.
  • the position of the tilting segments 3 remains almost the same regardless of the thickness of the press fit. With temperature changes find linear Expansions instead, so that the influence on the change in gap between the tilting segments 3 and the shaft 20 still largely depends on the respective temperature expansion coefficients of the material pairing of the shaft and tilting segment bearing.
  • the webs 4 - viewed in the angular direction f - are preferably arranged centrally between two press-fit surfaces 5, so that a first angle a of the web 4 to the next press-fit surface 5 in the clockwise direction is as large as a second angle ⁇ of the web 4 to the next Press fit surface 5 counterclockwise.
  • stop surfaces 6 are formed on an inner circumference 2b of the bearing sleeve 2, which limit a radial displacement of the ends 3a, 3b of the tilting segments 3 to the outside.
  • a stop surface 6 with two ends 3a, 3b of two adjacent tilting segments 3 can cooperate.
  • the number of stop surfaces 6 is preferably the same as the number of tilting segments 3, particularly preferably three stop surfaces 6.
  • the tilting segments 3 are arranged off-center on the associated web 4. This means that a first arc length 3_1 of the tilting segment 3 from one end 3a to the respective web 4 is smaller than a second arc length 3_2 from the same web 4 to the other end 3b of the same tilting segment 3.
  • the third angle g from one end 3a of the tilting segment 3 to its web 4 is smaller than the fourth angle d from the web 4 to the other end 3b of the tilting segment 3;
  • FIG. 2 shows a schematic cross-sectional view of a further exemplary embodiment for a tilting segment bearing 1, only the essential areas being shown. in the In the following, however, only the differences to the execution according to Fiq.1 will be discussed.
  • the press-fit surfaces 5 are designed over a further circumference of the outer circumference 2a, the circumference of the relief surfaces 5a is consequently reduced. Viewed in the radial direction, the bearing sleeve 2 and a press-fit surface 5 thus follow a stop surface 6.
  • the stop surfaces 6 are designed to be very stiff and positioned robustly with small tolerances; when pressed in, this preferably results in a purely radial displacement of the stop surfaces 6.
  • FIG. 3 shows a schematic cross-sectional view of a still further exemplary embodiment of a tilting segment bearing 1, only the essential areas being shown. In the following, however, only the differences from the embodiments according to FIGS. 1 and 2 will be discussed.
  • the webs 4 have an off-center angular offset to the press-fit surfaces 5. That is, viewed in the angular direction f, the first angle a of the web 4 to the next press-fit surface 5 in the clockwise direction is greater or smaller than the second angle ⁇ of the web 4 to the next press-fit surface 5 in the counterclockwise direction, preferably several times larger or smaller .
  • the tilting segment 3 can be set obliquely or displaced tangentially in its pressed-in state. This helps to make the tilting segment bearing 1 dynamically stable during operation; to this end, the tilting segment bearing 1 is preferably monolithic.
  • the gap between tilting segment 3 and shaft 20 which narrows in the direction of rotation due to the inclination or tangential displacement leads to particularly favorable tribological conditions in the operating state; for example, a kind of lubrication pad or lubrication wedge is formed in the gap by the gas or the ambient air.
  • the abutment surfaces 6 avoid excessive deformation or displacement of the webs 4, since they limit their freedom of tilt movement. This is also advantageous as protection during the assembly of the shaft 20 in the tilting segment bearing 1. When installed, the tilting segments 3 preferably cause self-locking.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sliding-Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

The invention relates to a tilting-pad bearing (1) having a bearing sleeve (2) and a plurality of tilting pads (3) arranged within the bearing sleeve (2). The tilting pads (3) are connected in each case - preferably monolithically - to the bearing sleeve (2) by means of a web (4).

Description

Beschreibung description
Titel title
Kippsegmentlager Tilt segment bearings
Die Erfindung betrifft ein Kippsegmentlager zur Lagerung einer Welle. The invention relates to a tilting segment bearing for supporting a shaft.
Stand der Technik State of the art
Kippsegmentlager kommen vor allem ölgeschmiert bei niedrigen und mittleren Drehzahlen bzw. Umfangsgeschwindigkeiten bis ca. 100 m/s zum Einsatz. Für höhere Umfangsgeschwindigkeiten können luftgeschmierte Kippsegmentlager eingesetzt werden, wenn die Anforderungen an die Tragkraft der Lager nicht zu hoch sind. Durch die geringere Viskosität der Luft im Vergleich zu Öl sind bei den luftgeschmierten Kippsegmentlagern die Schmierspalthöhen deutlich kleiner als bei den ölgeschmierten Lagern. Zum Teil liegen die Schmierspalthöhen in der Größenordnung von 10pm und sind damit um den Faktor 5 geringer als bei den ölgeschmierten Lagern. Tilt segment bearings are mainly used oil-lubricated at low and medium speeds or circumferential speeds up to approx. 100 m / s. Air-lubricated tilting segment bearings can be used for higher peripheral speeds if the bearing load requirements are not too high. Due to the lower viscosity of the air compared to oil, the lubrication gap heights in the air-lubricated tilting segment bearings are significantly smaller than in the oil-lubricated bearings. In some cases, the lubrication gap heights are in the order of 10pm and are therefore 5 times smaller than with oil-lubricated bearings.
Die engeren Lagerspalte stellen hohe Anforderungen an die Maßhaltigkeit der Lagerfläche zu der zu lagernden Welle. The narrower bearing gaps place high demands on the dimensional accuracy of the bearing surface for the shaft to be supported.
Aus der DE 32 25 423 C2 ist ein Kippsegmentlager mit einer Lagerhülse und mehreren innerhalb der Lagerhülse angeordneten Kippsegmenten bekannt. Die Kippsegmente sind jeweils mittels eines Zapfens in der Lagerhülse gelagert. DE 32 25 423 C2 discloses a tilting segment bearing with a bearing sleeve and a plurality of tilting segments arranged within the bearing sleeve. The tilting segments are each mounted in the bearing sleeve by means of a pin.
Offenbarung der Erfindung Disclosure of the invention
Demgegenüber lagert das erfindungsgemäße Kippsegmentlager eine Welle robuster und thermisch und dynamisch stabiler. In contrast, the tilting segment bearing according to the invention supports a shaft more robustly and thermally and dynamically more stable.
Dazu weist das Kippsegmentlager eine Lagerhülse und mehrere innerhalb der Lagerhülse angeordnete Kippsegmente auf. Die Kippsegmente sind jeweils mittels eines Steges - vorzugsweise monolithisch - mit der Lagerhülse verbunden. Der Steg ist verglichen mit dem Kippsegment sehr schmal, beispielsweise in Umfangsrichtung betrachtet 20-mal schmaler, so dass das Kippsegment nahezu punktuell an der Lagerhülse angebunden ist. Dadurch ist die Verbindung von Kippsegment zur Lagerhülse sehr elastisch ausgeführt, das Kippsegment kann um den Steg kippen; es können aber auch thermische Ausdehnungen und Relativverschiebungen besser kompensiert werden, insbesondere in Kombination mit einer nicht über den gesamten Umfang eingepressten Lagerhülse. For this purpose, the tilting segment bearing has a bearing sleeve and a plurality of tilting segments arranged within the bearing sleeve. The tilting segments are each connected to the bearing sleeve by means of a web, preferably monolithically. The web is very narrow compared to the tilting segment, for example 20 times narrower when viewed in the circumferential direction, so that the tilting segment is connected to the bearing sleeve almost at certain points. As a result, the connection of the tilting segment to the bearing sleeve is made very elastic, the tilting segment can tip over the web; however, thermal expansions and relative displacements can also be better compensated for, in particular in combination with a bearing sleeve that is not pressed in over the entire circumference.
Vorzugsweise sind dazu an einem Außenumfang der Lagerhülse mehrere, bevorzugt drei, Presspassungsflächen ausgebildet. Das Kippsegmentlager bzw. die Lagerhülse wird so an den Presspassungsflächen in ein Gehäuse eingepresst. Der Pressverband ist damit nicht über den gesamten Außenumfang der Lagerhülse ausgeführt, sondern eben nur an den Presspassungsflächen. Demzufolge erfahren beim Einpressen auch nicht der gesamte Außenumfang die maximale radiale Verschiebung nach innen, sondern nur die Presspassungsflächen; die radiale Verschiebung der Stege und damit auch der Kippsegmente durch das Einpressen können somit reduziert werden, insbesondere mit in Umfangsrichtung bzw. Winkelrichtung zunehmender Entfernung zu den Presspassungsflächen. Vorzugsweise entspricht somit die Anzahl der Presspassungsflächen der Anzahl der Kippsegmente bzw. der Anzahl der entsprechenden Stege. For this purpose, a plurality, preferably three, press-fit surfaces are preferably formed on an outer circumference of the bearing sleeve. The tilting segment bearing or the bearing sleeve is pressed into a housing on the press-fit surfaces. The press fit is therefore not carried out over the entire outer circumference of the bearing sleeve, but only on the press fit surfaces. As a result, it is not the entire outer circumference that experiences the maximum radial displacement inwards during the pressing in, but only the press-fit surfaces; the radial displacement of the webs and thus also the tilting segments due to the pressing in can thus be reduced, in particular with increasing distance from the press-fitting surfaces in the circumferential direction or angular direction. The number of press-fit areas thus preferably corresponds to the number of tilting segments or the number of corresponding webs.
Dazu ist in vorteilhaften Ausführungen in einer Winkelrichtung des Kippsegmentlagers jeweils ein Steg zwischen zwei Presspassungsflächen angeordnet. Das heißt radial nach außen folgt auf einen Steg eben keine Presspassungsfläche, sondern eine zwischen diesen angeordnete Freistellungsfläche, so dass der Außenumfang im Bereich des Stegs eben weniger schrumpft als an den Presspassungsflächen. For this purpose, a web is arranged between two press-fit surfaces in an advantageous embodiment in an angular direction of the tilting segment bearing. This means that radially outwards, a web is not followed by a press-fit area, but rather by a clearance area arranged between them, so that the outer circumference in the area of the web shrinks less than at the press-fit areas.
In vorteilhaften Weiterbildungen ist der Steg jeweils mittig zwischen zwei Presspassungsflächen angeordnet. Dadurch ist der oben beschriebene Effekt maximiert und demzufolge die radiale Verschiebung des Stegs aufgrund des Einpressens minimiert. Auch entsprechende thermische Relativverschiebungen sind dadurch minimiert. Das Kippsegmentlager ist damit funktional stabiler und robuster ausgelegt. In advantageous developments, the web is arranged in the middle between two press-fit surfaces. This maximizes the effect described above and consequently minimizes the radial displacement of the web due to the pressing. Corresponding thermal relative displacements are also minimized as a result. The tilting segment bearing is thus designed to be functionally more stable and robust.
In alternativen vorteilhaften Weiterbildungen weisen die Stege zu den Presspassungsflächen einen außermittigen Winkelversatz auf. Das heißt, dass ein Steg zu den beiden nächsten Presspassungsflächen im und entgegen des Uhrzeigersinns verschiedene Abstände besitzt. Dadurch wird aufgrund der Steifigkeitsverhältnisse der Lagerhülse und der auf die Presspassungsflächen wirkenden Kontaktkräfte des Pressverbands der Steg nicht nur radial nach innen verschoben, sondern auch tangential leicht verkippt. So wird eine Kipp-Vorspannung des Kippsegments erzeugt. Dies ist insbesondere vorteilhaft, wenn ein nicht-homogener Schmierspalt zwischen Welle und Kippsegment vorliegen soll; vorzugsweise soll sich dabei der Schmierspalt in Drehrichtung der Welle verringern, so dass eine Art Schmierkeil ausgebildet wird. In alternative advantageous developments, the webs have an eccentric angular offset to the press-fit surfaces. That means a footbridge has different distances clockwise and counterclockwise to the next two press fit surfaces. As a result, due to the rigidity of the bearing sleeve and the contact forces of the press fit acting on the press-fit surfaces, the web is not only displaced radially inward, but also slightly tilted tangentially. This creates a tilt pretension of the tilt segment. This is particularly advantageous if there is to be a non-homogeneous lubrication gap between the shaft and the tilting segment; the lubricating gap should preferably decrease in the direction of rotation of the shaft, so that a type of lubricating wedge is formed.
In vorteilhaften Weitebildungen wirken die Enden der Kippsegmente radial nach außen mit an der Lagerhülse ausgebildeten Anschlagflächen zusammen. Die Anschlagflächen bilden somit eine Art Radiallager, insbesondere während der Montage, für die Kippsegmente in der Richtung nach außen. Dadurch wird eine zu starke Deformation des Steges vermieden. Die Anschlagflächen sollen dabei vorzugsweise nur bei der Montage der Welle ein zu starkes Auslenken der Kippsegmente verhindern. Im Betrieb soll hier vorzugsweise kein Kontakt hergestellt werden. In advantageous further developments, the ends of the tilting segments interact radially outward with stop surfaces formed on the bearing sleeve. The stop surfaces thus form a type of radial bearing, in particular during assembly, for the tilting segments in the outward direction. This prevents excessive deformation of the web. The stop surfaces should preferably prevent the tilting segments from deflecting too strongly only when the shaft is being assembled. In operation, no contact should preferably be made here.
In vorteilhaften Ausführungen sind die Kippsegmente außermittig an dem jeweils zugehörigen Steg angeordnet. Das heißt die beiden Enden eines Kippsegments haben einen unterschiedlichen Abstand zu dem entsprechenden Steg. Dadurch wird die Ausbildung des Schmierkeils im Betrieb des Kippsegmentlagers unterstützt. In advantageous embodiments, the tilting segments are arranged off-center on the associated web. This means that the two ends of a tilting segment are at a different distance from the corresponding web. This supports the formation of the lubricating wedge in the operation of the tilting segment bearing.
Des Weiteren ist das Kippsegmentlager bevorzugt ein luftgeschmiertes Kippsegmentlager gemäß einer Ausführungsform der Erfindung. Furthermore, the tilting segment bearing is preferably an air-lubricated tilting segment bearing according to an embodiment of the invention.
Kurze Beschreibung der Zeichnungen Brief description of the drawings
Weitere Merkmale und Vorteile der vorliegenden Erfindung werden nachfolgend anhand der Figuren erläutert. Es zeigen: Further features and advantages of the present invention are explained below with reference to the figures. Show it:
Fig. 1 eine schematische Querschnittansicht eines Kippsegmentlagers, wobei nur die wesentlichen Bereiche dargestellt sind; 1 shows a schematic cross-sectional view of a tilting segment bearing, only the essential areas being shown;
Fig. 2 eine schematische Querschnittansicht eines weiteren Kippsegmentlagers, wobei nur die wesentlichen Bereiche dargestellt sind; Fig. 3 eine schematische Querschnittansicht eines Kippsegmentlagers in einer weiteren Ausführung, wobei nur die wesentlichen Bereiche dargestellt sind. 2 shows a schematic cross-sectional view of a further tilting segment bearing, only the essential areas being shown; 3 shows a schematic cross-sectional view of a tilting segment bearing in a further embodiment, only the essential areas being shown.
Ausführungsformen der Erfindung Embodiments of the invention
In Fiq.1 ist eine schematische Querschnittansicht eines Ausführungsbeispiels für ein Kippsegmentlager 1 gezeigt, welches eine Welle 20 radial lagert, wobei nur die wesentlichen Bereiche dargestellt sind. Das Kippsegmentlager 1 weist dabei eine Lagerhülse 2 und bevorzugt drei Kippsegmente 3 auf. Die einzelnen Kippsegmente 3 sind mittels je eines Steges 4 an der Lagerhülse 2 angebunden, bevorzugt sind dabei die Lagerhülse 2, die Kippsegmente 3 und die Stege 4 einstückig, also monolithisch ausgebildet. FIG. 1 shows a schematic cross-sectional view of an exemplary embodiment of a tilting segment bearing 1, which supports a shaft 20 radially, only the essential areas being shown. The tilting segment bearing 1 has a bearing sleeve 2 and preferably three tilting segments 3. The individual tilting segments 3 are each connected to the bearing sleeve 2 by means of a web 4, preferably the bearing sleeve 2, the tilting segments 3 and the webs 4 are formed in one piece, that is to say monolithically.
An einem Außenumfang 2a der Lagerhülse 2 sind Presspassungsflächen 5 zur Anordnung des Kippsegmentlagers 1 in einem nicht dargestellten Gehäuse ausgebildet. Die Presspassungsflächen 5 wechseln sich demzufolge über den Umfang mit Freistellungsflächen 5a, welche einen geringeren Durchmesser haben, ab. Idealerweise wird das Kippsegmentlager 1 an den Presspassungsflächen 5 in das Gehäuse eingepresst. In bevorzugten Ausführungen sind die Stege 4 in einer Winkelrichtung f des Kippsegmentlagers 1 betrachtet zwischen den Presspassungsflächen 5 positioniert. Das heißt, dass in radialer Richtung nach außen auf einen Steg 4 die Lagerhülse 2 und eine Freistellungsfläche 5a folgen, so dass die Einpressung an den Presspassungsflächen 5 nur eine vergleichsweise geringe radiale Verschiebung der Stege 4 zur Folge hat. On an outer circumference 2a of the bearing sleeve 2, press-fit surfaces 5 for the arrangement of the tilting segment bearing 1 are formed in a housing (not shown). Accordingly, the press-fit areas 5 alternate over the circumference with release areas 5a, which have a smaller diameter. Ideally, the tilting segment bearing 1 is pressed into the housing at the press-fit surfaces 5. In preferred embodiments, the webs 4, viewed in an angular direction f of the tilting segment bearing 1, are positioned between the press-fit surfaces 5. This means that the bearing sleeve 2 and a clearance surface 5a follow a web 4 in the radial direction outwards, so that the pressing in on the press-fit surfaces 5 results in only a comparatively small radial displacement of the webs 4.
Der Pressverband zwischen dem Gehäuse und der Lagerhülse 2 wirkt nämlich nur auf die Presspassungsflächen 5, nicht aber auf die Freistellungsflächen 5a. Der Außenumfang 2a der Lagerhülse 2 wird somit vor allem im Bereich der Presspassungsflächen 5 in seinem Durchmesser reduziert; der Durchmesser des Außenumfangs 2a im Bereich der Freistellungsflächen 5a wird weniger stark reduziert. Die Verformung der Lagerhülse 2 im Bereich der Stege 4 ist somit reduziert und damit auch die radiale Verschiebung der Kippsegmente 3. Die Positionierung der Kippsegmente 3 zur Welle 20 wird damit durch die Einpressung des Kippsegmentlagers 1 in das Gehäuse weniger stark verändert. Idealerweise bleibt die Position der Kippsegmente 3 unabhängig von der Stärke des Pressverbandes nahezu erhalten. Bei Temperaturänderungen finden lineare Ausdehnungen statt, sodass der Einfluss auf die Spaltänderung zwischen den Kippsegmenten 3 und der Welle 20 weitestgehend noch von den jeweiligen Temperaturausdehnungskoeffizienten der Materialpaarung Welle-Kippsegmentlager abhängt. The press fit between the housing and the bearing sleeve 2 acts only on the press-fit surfaces 5, but not on the release surfaces 5a. The outer circumference 2a of the bearing sleeve 2 is thus reduced in diameter, particularly in the area of the press-fit surfaces 5; the diameter of the outer circumference 2a in the area of the clearance areas 5a is reduced less. The deformation of the bearing sleeve 2 in the area of the webs 4 is thus reduced, and thus also the radial displacement of the tilting segments 3. The positioning of the tilting segments 3 with respect to the shaft 20 is thus less changed by the pressing of the tilting segment bearing 1 into the housing. Ideally, the position of the tilting segments 3 remains almost the same regardless of the thickness of the press fit. With temperature changes find linear Expansions instead, so that the influence on the change in gap between the tilting segments 3 and the shaft 20 still largely depends on the respective temperature expansion coefficients of the material pairing of the shaft and tilting segment bearing.
Vorzugsweise sind die Stege 4 - in der Winkelrichtung f betrachtet - mittig zwischen je zwei Presspassungsflächen 5 angeordnet, so dass ein erster Winkel a des Steges 4 zu der nächsten Presspassungsfläche 5 im Uhrzeigersinn genauso groß ist wie ein zweiter Winkel ß des Steges 4 zu der nächsten Presspassungsfläche 5 entgegen des Uhrzeigersinns. Dadurch ergibt sich während des Einpressens die minimalste Verschiebung der Kippsegmente 3, so dass der Lagerspalt nur noch von den Fertigungstoleranzen des Kippsegmentlagers 1 bzw. der Welle abhängig ist. Dies ermöglicht die Einhaltung des relativ geringen Spaltbereiches, in welchem das Kippsegmentlager 1 stabil funktioniert. Der Verschleiß zwischen den Kippsegmenten 3 und der Welle 20 im Betrieb, aber vor allem auch deren Beschädigung während der Montage sind demzufolge minimiert. The webs 4 - viewed in the angular direction f - are preferably arranged centrally between two press-fit surfaces 5, so that a first angle a of the web 4 to the next press-fit surface 5 in the clockwise direction is as large as a second angle β of the web 4 to the next Press fit surface 5 counterclockwise. This results in the minimal displacement of the tilting segments 3 during the pressing in, so that the bearing gap is only dependent on the manufacturing tolerances of the tilting segment bearing 1 or the shaft. This enables compliance with the relatively small gap area in which the tilting segment bearing 1 functions stably. The wear between the tilting segments 3 and the shaft 20 during operation, but above all their damage during assembly, is consequently minimized.
In vorteilhaften Weiterbildungen sind an einem Innenumfang 2b der Lagerhülse 2 Anschlagflächen 6 ausgebildet, welche eine radiale Verschiebung der Enden 3a, 3b der Kippsegmente 3 nach außen begrenzen. Vorzugsweise kann dazu eine Anschlagfläche 6 mit zwei Enden 3a, 3b von zwei benachbarten Kippsegmenten 3 Zusammenwirken. Demzufolge ist bevorzugt die Anzahl der Anschlagflächen 6 gleich groß zur Anzahl der Kippsegmente 3, besonders bevorzugt also drei Anschlagflächen 6. In advantageous developments, stop surfaces 6 are formed on an inner circumference 2b of the bearing sleeve 2, which limit a radial displacement of the ends 3a, 3b of the tilting segments 3 to the outside. For this purpose, preferably a stop surface 6 with two ends 3a, 3b of two adjacent tilting segments 3 can cooperate. Accordingly, the number of stop surfaces 6 is preferably the same as the number of tilting segments 3, particularly preferably three stop surfaces 6.
In bevorzugten Ausführungen sind die Kippsegmente 3 außermittig an dem jeweils zugehörigen Steg 4 angeordnet. Das heißt, dass eine erste Bogenlänge 3_1 des Kippsegments 3 von einem Ende 3a bis zum jeweiligen Steg 4 kleiner ist als eine zweite Bogenlänge 3_2 vom selben Steg 4 bis zum anderen Ende 3b desselben Kippsegments 3. Oder in Winkelrichtung f betrachtet: der dritte Winkel g von einem Ende 3a des Kippsegments 3 zu seinem Steg 4 ist kleiner als der vierte Winkel d von dem Steg 4 zu dem anderen Ende 3b des Kippsegments 3; bevorzugt ist der vierte Winkel d dabei mindestens doppelt so groß wie der dritte Winkel g, es gilt also: d >= 2g. In preferred embodiments, the tilting segments 3 are arranged off-center on the associated web 4. This means that a first arc length 3_1 of the tilting segment 3 from one end 3a to the respective web 4 is smaller than a second arc length 3_2 from the same web 4 to the other end 3b of the same tilting segment 3. Or viewed in the angular direction f: the third angle g from one end 3a of the tilting segment 3 to its web 4 is smaller than the fourth angle d from the web 4 to the other end 3b of the tilting segment 3; The fourth angle d is preferably at least twice as large as the third angle g, so the following applies: d> = 2g.
Fiq.2 zeigt eine schematische Querschnittansicht eines weiteren Ausführungsbeispiels für ein Kippsegmentlager 1 , wobei nur die wesentlichen Bereiche dargestellt sind. Im Folgenden soll jedoch nur auf die Unterschiede zur Ausführung nach der Fiq.1 eingegangen werden. In der Ausführung der Fiq.2 sind die Presspassungsflächen 5 über einen weiteren Umfang des Außenumfangs 2a gestaltet, der Umfang der Freistellungsflächen 5a ist demzufolge reduziert. In radialer Richtung betrachtet folgen so auf eine Anschlagfläche 6 die Lagerhülse 2 und eine Presspassungsfläche 5. Dadurch sind die Anschlagflächen 6 sehr steif ausgeführt und robust mit geringen Toleranzen positioniert; beim Einpressen ergibt sich dadurch vorzugsweise eine rein radiale Verschiebung der Anschlagflächen 6. FIG. 2 shows a schematic cross-sectional view of a further exemplary embodiment for a tilting segment bearing 1, only the essential areas being shown. in the In the following, however, only the differences to the execution according to Fiq.1 will be discussed. In the embodiment of FIG. 2, the press-fit surfaces 5 are designed over a further circumference of the outer circumference 2a, the circumference of the relief surfaces 5a is consequently reduced. Viewed in the radial direction, the bearing sleeve 2 and a press-fit surface 5 thus follow a stop surface 6. As a result, the stop surfaces 6 are designed to be very stiff and positioned robustly with small tolerances; when pressed in, this preferably results in a purely radial displacement of the stop surfaces 6.
Fiq.3 zeigt eine schematische Querschnittansicht eines noch weiteren Ausführungsbeispiels für ein Kippsegmentlager 1 , wobei nur die wesentlichen Bereiche dargestellt sind. Im Folgenden sollen jedoch nur auf die Unterschiede zu den Ausführungen nach den Figuren 1 und 2 eingegangen werden. 3 shows a schematic cross-sectional view of a still further exemplary embodiment of a tilting segment bearing 1, only the essential areas being shown. In the following, however, only the differences from the embodiments according to FIGS. 1 and 2 will be discussed.
Der wesentliche Unterschied ist, dass die Stege 4 zu den Presspassungsflächen 5 einen außermittigen Winkelversatz aufweisen. Das heißt in der Winkelrichtung f betrachtet ist der erste Winkel a des Steges 4 zu der nächsten Presspassungsfläche 5 im Uhrzeigersinn größer oder kleiner als der zweite Winkel ß des Steges 4 zu der nächsten Presspassungsfläche 5 entgegen des Uhrzeigersinns, vorzugsweise um ein Mehrfaches größer bzw. kleiner. Dadurch kann das Kippsegment 3 in seinem eingepressten Zustand schräg gestellt bzw. tangential versetzt werden. Dies hilft das Kippsegmentlager 1 im Betrieb dynamisch stabiler zu machen; dazu ist das Kippsegmentlager 1 vorzugsweise monolithisch ausgeführt. Der durch die Schrägstellung bzw. tangentiale Versetzung sich in Drehrichtung verengende Spalt zwischen Kippsegment 3 und Welle 20 führt zu besonders günstigen tribologischen Verhältnissen im Betriebszustand; beispielsweise bildet sich dadurch in dem Spalt eine Art Schmierpolster bzw. Schmierkeil durch das Gas bzw. die Umgebungsluft aus. The main difference is that the webs 4 have an off-center angular offset to the press-fit surfaces 5. That is, viewed in the angular direction f, the first angle a of the web 4 to the next press-fit surface 5 in the clockwise direction is greater or smaller than the second angle β of the web 4 to the next press-fit surface 5 in the counterclockwise direction, preferably several times larger or smaller . As a result, the tilting segment 3 can be set obliquely or displaced tangentially in its pressed-in state. This helps to make the tilting segment bearing 1 dynamically stable during operation; to this end, the tilting segment bearing 1 is preferably monolithic. The gap between tilting segment 3 and shaft 20 which narrows in the direction of rotation due to the inclination or tangential displacement leads to particularly favorable tribological conditions in the operating state; for example, a kind of lubrication pad or lubrication wedge is formed in the gap by the gas or the ambient air.
Die Anschlagflächen 6 vermeiden eine zu starke Deformation bzw. Verschiebung der Stege 4, da sie diese in ihrer Kipp-Bewegungsfreiheit limitieren. Dies ist auch als Schutz während der Montage der Welle 20 in das Kippsegmentlager 1 vorteilhaft. Im eingebauten Zustand findet durch die Kippsegmente 3 bevorzugt eine Selbsthemmung statt. The abutment surfaces 6 avoid excessive deformation or displacement of the webs 4, since they limit their freedom of tilt movement. This is also advantageous as protection during the assembly of the shaft 20 in the tilting segment bearing 1. When installed, the tilting segments 3 preferably cause self-locking.

Claims

Ansprüche Expectations
1. Kippsegmentlager (1 ) mit einer Lagerhülse (2) und mehreren innerhalb der Lagerhülse (2) angeordneten Kippsegmenten (3), 1. tilting segment bearing (1) with a bearing sleeve (2) and several tilting segments (3) arranged within the bearing sleeve (2),
dadurch gekennzeichnet, dass die Kippsegmente (3) jeweils mittels eines Steges characterized in that the tilting segments (3) each by means of a web
(4) mit der Lagerhülse (2) verbunden sind. (4) are connected to the bearing sleeve (2).
2. Kippsegmentlager nach Anspruch 1 , 2. tilting segment bearing according to claim 1,
dadurch gekennzeichnet, dass die Kippsegmente (3) außermittig an dem jeweils zugehörigen Steg (4) angeordnet sind. characterized in that the tilting segments (3) are arranged off-center on the respectively associated web (4).
3. Kippsegmentlager nach Anspruch 1 oder 2, 3. tilt segment bearing according to claim 1 or 2,
dadurch gekennzeichnet, dass an einem Außenumfang (2a) der Lagerhülse (2) mehrere, vorzugsweise drei, Presspassungsflächen (5) ausgebildet sind. characterized in that a plurality, preferably three, press-fit surfaces (5) are formed on an outer circumference (2a) of the bearing sleeve (2).
4. Kippsegmentlager nach Anspruch 3, 4. tilting segment bearing according to claim 3,
dadurch gekennzeichnet, dass die Anzahl der Presspassungsflächen (5) der Anzahl der Kippsegmente (3) entspricht. characterized in that the number of press-fit areas (5) corresponds to the number of tilting segments (3).
5. Kippsegmentlager nach Anspruch 3 oder 4, 5. tilt segment bearing according to claim 3 or 4,
dadurch gekennzeichnet, dass in einer Winkelrichtung (f) des Kippsegmentlagers (1 ) jeweils ein Steg (4) zwischen zwei Presspassungsflächen characterized in that in one angular direction (f) of the tilting segment bearing (1) there is in each case a web (4) between two press-fit surfaces
(5) angeordnet ist. (5) is arranged.
6. Kippsegmentlager nach Anspruch 5, 6. Tilt segment bearing according to claim 5,
dadurch gekennzeichnet, dass die Stege (4) jeweils mittig zwischen zwei Presspassungsflächen (5) angeordnet sind. characterized in that the webs (4) are each arranged centrally between two press-fit surfaces (5).
7. Kippsegmentlager nach Anspruch 5, 7. tilt segment bearing according to claim 5,
dadurch gekennzeichnet, dass die Stege (4) zu den Presspassungsflächen (5) einen außermittigen Winkelversatz aufweisen. characterized in that the webs (4) have an eccentric angular offset to the press-fit surfaces (5).
8. Kippsegmentlager nach einem der Ansprüche 1 bis 7, 8. tilting segment bearing according to one of claims 1 to 7,
dadurch gekennzeichnet, dass die Lagerhülse (2) die Kippsegmente (3) und die Stege (4) monolithisch ausgebildet sind. characterized in that the bearing sleeve (2), the tilting segments (3) and the webs (4) are monolithic.
9. Kippsegmentlager nach Anspruch 8, 9. tilt segment bearing according to claim 8,
dadurch gekennzeichnet, dass die Enden (3a, 3b) der Kippsegmente (3) radial nach außen mit an der Lagerhülse (2) ausgebildeten Anschlagflächen (6) Zusammenwirken. characterized in that the ends (3a, 3b) of the tilting segments (3) interact radially outwards with stop surfaces (6) formed on the bearing sleeve (2).
PCT/EP2019/080652 2018-11-28 2019-11-08 Tilting-pad bearing WO2020108952A1 (en)

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DE102018220449.7A DE102018220449A1 (en) 2018-11-28 2018-11-28 Tilt segment bearings
DE102018220449.7 2018-11-28

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NL2027506B1 (en) * 2021-02-05 2022-09-06 Johannes Hendricus Wilhelmus Nabuurs Martinus Tilting pad bearing, assembly of a construction element and such a bearing, and a method for providing a journal opening having a desired cross-section

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3225423C2 (en) 1981-07-07 1986-11-27 Nuovo Pignone S.P.A., Florenz/Firenze Radial tilting pad bearings
WO1992003667A1 (en) * 1990-08-24 1992-03-05 Ide Russell D Self positioning beam mounted bearing and bearing and shaft assembly including the same
US5911511A (en) * 1997-09-26 1999-06-15 Alliedsignal Inc. Tilting pad foil thrust and journal bearings
WO2015046887A1 (en) * 2013-09-24 2015-04-02 (주)삼본정공 Functional plastic bearing
DE102017202740A1 (en) * 2017-02-21 2018-08-23 Robert Bosch Gmbh Tilting pad bearing and method of manufacturing a tilting pad bearing

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3225423C2 (en) 1981-07-07 1986-11-27 Nuovo Pignone S.P.A., Florenz/Firenze Radial tilting pad bearings
WO1992003667A1 (en) * 1990-08-24 1992-03-05 Ide Russell D Self positioning beam mounted bearing and bearing and shaft assembly including the same
US5911511A (en) * 1997-09-26 1999-06-15 Alliedsignal Inc. Tilting pad foil thrust and journal bearings
WO2015046887A1 (en) * 2013-09-24 2015-04-02 (주)삼본정공 Functional plastic bearing
DE102017202740A1 (en) * 2017-02-21 2018-08-23 Robert Bosch Gmbh Tilting pad bearing and method of manufacturing a tilting pad bearing

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