EP2002136A1 - Palier à glissement axial hydrodynamique et procédé d'utilisation correspondant - Google Patents

Palier à glissement axial hydrodynamique et procédé d'utilisation correspondant

Info

Publication number
EP2002136A1
EP2002136A1 EP07727135A EP07727135A EP2002136A1 EP 2002136 A1 EP2002136 A1 EP 2002136A1 EP 07727135 A EP07727135 A EP 07727135A EP 07727135 A EP07727135 A EP 07727135A EP 2002136 A1 EP2002136 A1 EP 2002136A1
Authority
EP
European Patent Office
Prior art keywords
lubricant
bearing
bearing segment
gap
region
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.)
Withdrawn
Application number
EP07727135A
Other languages
German (de)
English (en)
Inventor
Kamil Matyscak
Dr.Axel Günter Albert FUERST
Andreas Schubert
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.)
GE Vernova GmbH
Original Assignee
Alstom Technology 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 Alstom Technology AG filed Critical Alstom Technology AG
Publication of EP2002136A1 publication Critical patent/EP2002136A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F16C17/04—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
    • 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
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/108—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid with a plurality of elements forming the bearing surfaces, e.g. bearing pads

Definitions

  • the invention relates to a hydrodynamic axial plain bearing, which is designed in particular for high loads. Such an axial sliding bearing is particularly applicable for the storage of waves of large electrical machines, such as hydrogen generators.
  • the invention also relates to a method for operating such a hydrodynamic thrust bearing.
  • hydrodynamic axial plain bearings are used to absorb the axial forces, in particular when the respective shaft is arranged vertically, ie with a vertical axis of rotation.
  • the bearing relative to one another bearing segments have facing planar sliding surfaces, between which builds a sustainable hydrodynamic lubricant film during operation.
  • the lubricant film thickness depends on a number of factors, in particular the load of the axial sliding bearing.
  • ADJUSTED SHEET (RULE 91) ISA / EP as a result of the significant shear stress of the enforced between the stationary rotating components lubricant a significant heating of the same, which usually requires an internal or an external cooling of the lubricant to prevent excessive heating with the result of thermal damage thereof and the operability of the Axial sliding bearing to ensure reliable at all.
  • the invention deals with the problem of providing an improved embodiment for a hydrodynamic thrust bearing or for an associated operating method, which allows in particular compared to conventional plain bearings of the same dimension with at least constant running safety increased stress.
  • ADJUSTED SHEET (RULE 91) ISA / EP The invention is based on the general idea of subtracting a partial stream of the lubricant within the lubricant gap in a region of a relatively high pressure of the lubricant and returning it to a region of relatively low pressure of the lubricant again in the lubricant gap.
  • the invention makes use of the fact that during operation of the thrust bearing within the lubricant gap, a significant pressure gradient is formed.
  • a typical pressure curve within the lubricant gap of a conventional axial plain bearing is shown by way of example in FIG.
  • at least one inlet opening is arranged in a compensation channel which penetrates the bearing segment at a distance from the sliding surface or extends within the bearing segment and again at least one outlet opening at a point of relatively low pressure the lubricant gap occurs.
  • a circulation flow of a part of the lubricant is initiated by a partial flow of the same in the range of high pressure from the lubricant gap in the compensation passage, this flows against the main flow direction of the lubricant in the lubricant gap to finally in a region of the bearing segment with a lower Pressure to re-enter the lubricant gap and to unite with the existing lubricant there.
  • ADJUSTED SHEET (RULE 91) ISA / EP within the lubricant gap of the respective bearing segment of the axial sliding bearing.
  • the system is self-regulating. Depending on the prevailing pressure conditions, the flow cross sections and the viscosity of the lubricant, an equilibrium state automatically arises during operation. Additional control measures are therefore not required.
  • the inventive measure causes an enlargement of the lubricant gap compared to a comparable Axialgieitlager without the inventive measure. This results in the additional benefits of increased running safety due to the thicker lubricating film as well as the resulting possibility of higher load on the thrust bearing.
  • an increase in the lubricant gap causes increased throughput of lubricant through the lubricant gap.
  • This increases the supply of fresh, cold lubricant, which on the one hand, the temperature and thus the thermal stress of the lubricant itself decreases and on the other hand, so that the temperature of the sliding surfaces decreases.
  • This has the consequence that the thermal stress of the respective bearing segment and concomitantly, in the case of large-scale bearing segments, the risk of deformation due to high differences in body temperature is reduced.
  • the warm lubricant flowing through the respective bearing segment in the at least one compensation channel contributes to a balanced body temperature within the respective bearing segment.
  • 1 is an axial plan view of a bearing segment of a thrust bearing
  • FIG. 2 is a sectional view of the bearing segment according to section lines D - D in Fig. 1,
  • FIG. 3 is a view of the bearing segment in the circumferential direction according to a viewing direction III in Fig. 2,
  • FIG. 5 is a sectional view of the position segment according to section lines C - C in Fig. 3,
  • FIG. 6 is a diagram illustrating the pressure ratios within a lubricant gap in a conventional bearing segment
  • FIG. 7 shows a diagram for illustrating the pressure conditions within a lubricant gap in the bearing segment according to the invention.
  • FIGS. 1 to 5 show a support segment or bearing segment 1 of an otherwise not shown, highly loadable hydrodynamic axial plain bearing, as may be used, for example, on a vertical electric machine, such as a hydrogenerator.
  • a vertical electric machine such as a hydrogenerator.
  • several of these bearing segments 1 are arranged annularly with respect to a rotation axis of a rotor, not shown, of this machine.
  • Said rotor is supported axially on these bearing segments 1 of the axial sliding bearing.
  • the bearing segments 1 of the thrust bearing itself in turn rest on a solid surface, so are stationary.
  • the thrust bearing is immersed in lubricating oil.
  • a friction-reducing lubricant film which is fed from a lubricant bath and / or channels of high-pressure lubrication in a conventional manner.
  • the rotor rotates in a direction of rotation 2 indicated in FIG. 1 by an arrow. This results in a leading edge 3 and an outflow edge 4 for the stationary bearing segment 1 for the lubricant conveyed by the rotation of the rotor.
  • the respective bearing segment 1 is at its end in Fig. 1 the viewer facing sliding surface 5 chamfered.
  • a corresponding chamfer line is designated 6 in FIG.
  • the respective axial sliding bearing thus comprises two relatively mutually adjustable assemblies, namely a rotating assembly and a stationary assembly.
  • the rotating assembly is formed with its sliding surfaces on the rotor, while the stationary assembly includes the bearing segments 1 with their sliding surfaces 5.
  • ADJUSTED SHEET (RULE 91) ISA / EP In a conventional axial sliding bearing, which is equipped with conventional bearing segments 1, the pressure distribution shown in FIG. 6 is established on the sliding surface 5 of the respective bearing segment 1 during operation. Recognizable increases the pressure from the leading edge 3 to the trailing edge 4 first and then from again. Its maximum reaches the pressure curve approximately in the middle of the downstream third of the respective bearing segment. 1
  • a subset of the lubricant is now removed within the lubricant gap from a region of relatively high hydrostatic pressure and returned to a region of relatively low hydrostatic pressure within the lubricant gap.
  • the removal of the lubricant and the introduction of the lubricant in each case take place within such a bearing segment 1, in particular in each of these bearing segments 1 of the axial sliding bearing.
  • a lubricant path 7 may preferably be formed within the respective bearing segment 1, which runs in the interior of the respective bearing segment 1 and via which the removal of lubricant from the high-pressure region and the introduction of lubricant into the low-pressure region.
  • the respective bearing segment 1 contains at least one compensation channel 8.
  • the respective compensation channel 8 extends inside the respective bearing segment 1 at a distance from the sliding surface 5.
  • the respective compensation channel 8 serves to connect the high-pressure region in FIG Lubricant gap with the low-pressure region in the lubricant gap, so that during operation lubricant can flow from the high pressure area to the low pressure area, and indeed contrary
  • ADJUSTED SHEET (RULE 91) ISA / EP the general, the direction of rotation 2 corresponding flow direction of the lubricant in the lubricant gap.
  • FIG. 7 now shows the pressure curve in the lubricant gap along the sliding surface 5 in the bearing segment 1 according to the invention or in an axial sliding bearing according to the invention.
  • the removal of the lubricant from the lubricant gap whereby the high-pressure region has a significant slump and now has two maxima instead of a maximum.
  • the lubricant is introduced into the lubricant gap, which significantly raises the mean pressure in this low pressure region; At the same time, a (smaller) pressure maximum can also be formed there. Overall, thus results within the sliding surface 5 of the respective bearing segment 1, a certain pressure compensation.
  • the pressure level in the low-pressure region that is to say in an upstream or front region of the respective bearing segment 1
  • the pressure level in the high-pressure region that is to say in a downstream or rear region of the bearing segment 1
  • a more favorable pressure distribution results within the lubricant gap, which increases the load capacity and the service life of the axial sliding bearing.
  • bearing segments 1 which are mounted pivotably about a bearing axis oriented radially with respect to the axis of rotation
  • the pressure displacement leads against the flow to a tilting moment, which increases the lubricant gap upstream of the respective bearing segment 1 and thereby improves the lubricant entry into the lubricant gap.
  • an enlargement of the lubricant gap can also be observed, which also leads to a reduction of the load and to an extension of the life of the axial sliding bearing.
  • the respective bearing segment 1 has at least one inlet opening 11, which is arranged in the high-pressure region of the lubricant gap and through which the lubricant passes from the lubricant gap into the compensation channel 8. Furthermore, the bearing segment 1 has at least one outlet opening 12, which is arranged in the low-pressure region of the lubricant gap and through which the lubricant is returned from the compensation channel 8 into the lubricant gap.
  • the compensating channel 8 thus connects the inlet opening 11 communicating with the lubricant gap with the outlet opening 12 also communicating with the lubricant gap.
  • the inlet opening 11 is arranged on the bottom of an inlet groove 13 formed in the sliding surface 5, for example in FIG the bearing segment 1 is milled.
  • an outlet groove 14 can also be provided for the outlet opening 12, which is formed in the sliding surface 5, for example, is machined into the bearing segment 1 by milling.
  • At least one of these grooves 13, 14, in the example both grooves 13, 14, is rectilinear and thereby oriented radially to the axis of rotation of the rotor or the rotating assembly.
  • the respective groove 13, 14 extends over a comparatively large area of the radial width of the respective bearing segment 1. The pressure compensation thereby takes place within comparatively large areas through the grooves 13, 14.
  • At least one of the grooves 13, 14 preferably both grooves 13, 14 each have a profile 15 which is concavely curved in longitudinal section 1 towards the sliding surface 5, which is clearly removable, for example, from FIGS. 2 and 3.
  • the respective opening that is to say the inlet opening 11 and / or the outlet opening 12, is preferably arranged approximately centrally between the longitudinal ends of the respective groove 13 or 14.
  • the respective inlet opening 11 is positioned in the high-pressure region of the lubricant gap within the sliding surface 5 of the respective bearing element 1.
  • the arrangement of the respective inlet opening 1 1 thus takes place in a downstream third of the sliding surface 5.
  • the inlet opening 1 1 is arranged approximately centrally in the downstream third of the sliding surface 5.
  • the respective outlet opening 12 is arranged in the low-pressure region of the lubricant gap within the sliding surface 5 of the respective bearing segment 1.
  • the respective outlet opening 12 is thus positioned within an upstream third of the sliding surface 5.
  • the outlet opening 12 is arranged approximately centrally in the upstream third of the sliding surface 5.
  • the compensation channel 8 can be closed, for example, according to Rg. 1 by means of a closure element 16, which may be configured for example as a set screw.
  • a closure element 16 is screwed into a corresponding receiving opening 17, which can be seen in FIG. 5.
  • a suitable screwing tool can be used for insertion of the closure element 16.
  • the sliding surface of the rotating component that is, of the rotor, lies directly on the sliding surface 5 of the respective bearing segment 1 in the individual bearing segments 1; in this direct contact the lubricant gap is not present.
  • the lubricant gap must be produced.
  • the lubricant gap is generated, which allows a start of the machine.
  • the rotating member rotates, it delivers lubricant through the chamfer 6 into the lubricant gap. ever
  • the pumping device can now be connected to at least one of the compensation channels 8 at least in one of the bearing segments 1.
  • the pumping device can thus convey lubricant under high pressure via the compensation channel 8 and thus in particular via the inlet opening 11 and the outlet opening 12 and optionally via the inlet groove 13 and the outlet groove 14 into the lubricant gap.
  • the lubricant path 7 designed for pressure equalization in the respective bearing segment 1 is used for injecting lubricant into the lubricant gap.
  • the pumping device can be switched off, so that via the respective compensation channel 8 and the lubricant path 7 again the desired pressure equalization of the lubricant gap.
  • the respective pump device is connected via at least one suitable, corresponding non-return device to the lubricant path 7 or to the respective compensation channel 8.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

L'invention concerne un segment de palier (1) destiné à un palier à glissement axial hydrodynamique résistant à des contraintes élevées, notamment un moteur électrique tel qu'un hydrogénérateur, comportant deux modules pouvant être réglés l'un par rapport à l'autre, un des modules décrivant un mouvement rotatif et l'autre module comportant au moins un tel segment de palier (1) connecté à une base solide. En fonctionnement, un espace de lubrifiant se forme entre des surfaces de glissement opposées des deux modules. Pour améliorer le palier à glissement axial, le segment de palier (1) présente au moins un canal de compensation (8) destiné au lubrifiant, connectant une zone de pression relativement élevée dans l'espace de lubrifiant à une zone de pression relativement faible dans l'espace de lubrifiant.
EP07727135A 2006-03-31 2007-03-20 Palier à glissement axial hydrodynamique et procédé d'utilisation correspondant Withdrawn EP2002136A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006015531 2006-03-31
PCT/EP2007/052658 WO2007113103A1 (fr) 2006-03-31 2007-03-20 Palier à glissement axial hydrodynamique et procédé d'utilisation correspondant

Publications (1)

Publication Number Publication Date
EP2002136A1 true EP2002136A1 (fr) 2008-12-17

Family

ID=38325833

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07727135A Withdrawn EP2002136A1 (fr) 2006-03-31 2007-03-20 Palier à glissement axial hydrodynamique et procédé d'utilisation correspondant

Country Status (6)

Country Link
US (1) US20090080820A1 (fr)
EP (1) EP2002136A1 (fr)
JP (1) JP2009531623A (fr)
CN (1) CN101432535A (fr)
CA (1) CA2647751A1 (fr)
WO (1) WO2007113103A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1395716B1 (it) * 2009-09-22 2012-10-19 Nuovo Pignone Spa Cuscinetto, meccanismo di fissaggio e metodo per fissare almeno un pattino.
IT1395717B1 (it) * 2009-09-22 2012-10-19 Nuovo Pignone Spa Cuscinetto, meccanismo di distribuzione olio e metodo.
US8490516B2 (en) * 2009-09-30 2013-07-23 Hitachi Koki Co., Ltd. Screw driving machine having combustion-type power mechanism and electric power mechanism
DE102011009070A1 (de) * 2011-01-20 2012-07-26 Schottel Gmbh Ruderpropeller mit einem ein Planetengetriebe umfassenden Unterwassergetriebe
KR101811451B1 (ko) * 2011-06-29 2017-12-21 엘지이노텍 주식회사 볼 조인트 유닛
KR101676986B1 (ko) 2013-01-31 2016-11-16 미츠비시 히타치 파워 시스템즈 가부시키가이샤 틸팅 패드 베어링 장치
CN103216537A (zh) * 2013-03-04 2013-07-24 哈尔滨电机厂有限责任公司 大型抽水蓄能机组发电电动机双向泵瓦结构
US9618048B2 (en) * 2014-08-12 2017-04-11 Lufkin Industries, Llc Reverse bypass cooling for tilted pad journal and tilting pad thrust bearings
JP6038088B2 (ja) * 2014-09-22 2016-12-07 三菱重工業株式会社 軸受及び軸受パッド
DE102016206139A1 (de) * 2016-04-13 2017-10-19 Robert Bosch Gmbh Vorrichtung mit einem Reibkontakt und Verfahren zum Betreiben einer Vorrichtung mit einem Reibkontakt
CN106438677B (zh) * 2016-11-17 2019-03-08 中国长江动力集团有限公司 推力支撑轴承和汽缸
NL2018947B1 (en) * 2017-05-19 2018-11-28 Univ Delft Tech Bearing device
US12065940B2 (en) * 2018-12-03 2024-08-20 BMTS Technology GmbH & Co. KG Exhaust gas turbocharger having a hydrodynamic plain bearing or a hydrodynamic plain bearing
IT201900007995A1 (it) * 2019-06-04 2020-12-04 Nuovo Pignone Tecnologie Srl Un cuscinetto con tacchetti aventi al proprio interno micro-canali di refrigerazione e metodo

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US3339990A (en) * 1964-07-13 1967-09-05 Worthington Corp Lubricated bearing shoe
DE2211414A1 (de) * 1972-03-06 1973-09-13 Siemens Ag Hydrodynamisches spurlager mit mittig unterstuetzten kippsegmenten fuer eine in zwei drehrichtungen rotierende welle
US4323286A (en) * 1980-07-28 1982-04-06 General Electric Co. Thrust bearing cooling apparatus
SE442328B (sv) * 1983-09-29 1985-12-16 Jan R Schnittger Hydrodynamisk lagerenhet
CA2324322C (fr) * 2000-10-26 2008-12-30 General Electric Canada Inc. Bague de butee
US7160031B2 (en) * 2003-11-20 2007-01-09 Matsushita Electric Industrial Co., Ltd. Thrust dynamic pressure bearing, spindle motor using the same, and information recording and reproducing apparatus using them

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Also Published As

Publication number Publication date
JP2009531623A (ja) 2009-09-03
US20090080820A1 (en) 2009-03-26
CA2647751A1 (fr) 2007-10-11
CN101432535A (zh) 2009-05-13
WO2007113103A1 (fr) 2007-10-11

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