US20100002967A1 - Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets - Google Patents

Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets Download PDF

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Publication number
US20100002967A1
US20100002967A1 US12/310,146 US31014607A US2010002967A1 US 20100002967 A1 US20100002967 A1 US 20100002967A1 US 31014607 A US31014607 A US 31014607A US 2010002967 A1 US2010002967 A1 US 2010002967A1
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US
United States
Prior art keywords
bearing
channel
plain
seen
horizontal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US12/310,146
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English (en)
Inventor
Diethelm Dettmar
Bernd Lüneburg
Morched Medhioub
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.)
Siemens AG
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Siemens AG
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Filing date
Publication date
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Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DETTMAR, DIETHELM, LUNEBURG, BERND, MEDHIOUB, MORCHED
Publication of US20100002967A1 publication Critical patent/US20100002967A1/en
Abandoned legal-status Critical Current

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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
    • F16C37/00—Cooling of bearings
    • F16C37/002—Cooling of bearings of fluid 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
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • F16C17/022—Sliding-contact bearings for exclusively rotary movement for radial load only with a pair of essentially semicircular bearing sleeves
    • 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
    • F16C33/08—Attachment of brasses, bushes or linings to the bearing housing
    • 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
    • F16C33/1045—Details of supply of the liquid to the bearing
    • 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
    • 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
    • F16C33/1075—Wedges, e.g. ramps or lobes, for generating pressure
    • 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
    • F16C39/00—Relieving load on bearings
    • F16C39/04—Relieving load on bearings using hydraulic or pneumatic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • 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
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
    • F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
    • F16C32/0651—Details of the bearing area per se

Definitions

  • the invention relates to a plain bearing which has a bearing body in which a body to be borne is borne, wherein the bearing body is surrounded by a supporting body.
  • a plain bearing is a bearing in which the body which is rotating and is to be borne slides on sliding surfaces.
  • the sliding surface of the body to be borne slides on the sliding surfaces of the bearing body.
  • the bearing body is designed differently.
  • the bearing body is in the form of a bearing shell which is embedded in a housing and may be subdivided into a plurality of bearing segments.
  • a lubricant film for example an oil film, is provided between the sliding surfaces.
  • the lubricant When rotation starts, the lubricant is drawn into the gap between the sliding surfaces, and the body to be borne moves to an eccentric position in the bearing body. During this process, it passes through the range of mixed friction. As the sliding speed and the movement into the eccentric position increase, a lubricant wedge is formed between the body to be borne and the bearing body, whose pressure results in the body to be borne being lifted off the bearing body. The body to be borne then runs in a stable form in the bearing body, in the case of purely hydrodynamic lubrication without any direct contact between the bearing body and the body to be borne. This effect occurs in a radial plain bearing by a bearing clearance that is provided.
  • a plain bearing in particular a radial plain bearing of the type mentioned initially, can be used, for example, in steam-turbine, generator and gas-turbine construction.
  • the plain bearing bears rotor shafts as the bodies to borne.
  • this bearing is subject to the following additional requirements:
  • the invention is therefore based on the object of improving a plain bearing of the type mentioned initially such that it complies with the requirements mentioned above for example for large-turbine construction, preferably for steam-turbine construction.
  • the object is achieved in that the bearing body is arranged as a multiple-surface bearing with its separating joint at an angle with respect to a horizontal.
  • the bearing body is formed from two half-shells, whose separating joint is arranged at an angle with respect to the horizontal.
  • the separating joint prefferably offset, seen in cross section, in the opposite direction to a rotation direction of the body to be borne or of a rotor shaft.
  • a fixing element for example one or more pins
  • fixing element is arranged in the supporting body and engages, for fixing purposes, in the bearing body, or rests on it for fixing purposes, such that the bearing body is held in its angle position in an adequately rotationally secure manner.
  • the bearing body has a first channel, which is arranged at least in places, in its wall, seen in the circumferential direction, wherein at least one axial hole is arranged in the wall and passes through the first channel. This provides active cooling for the plain bearing and the bearing body.
  • the bearing body has at least one second channel which is at a distance from the first channel, seen in the axial direction, wherein at least one axial hole is arranged in the wall and passes through the first and the second channel, such that these channels are connected to one another via the axial hole.
  • a third or further channels to be provided, wherein the first channel is arranged between the second and third channel, seen in the axial direction, and wherein a plurality of axial holes are provided, which each pass through all three channels.
  • the first channel is advantageously incorporated in a loaded bearing shell of the bearing body and is open toward the supporting body, wherein the first channel is incorporated in a semicircular shape in the wall of the bearing body, seen in the circumferential direction, such that a semicircular groove is effectively formed
  • the first channel advantageously has bearing pockets at its opposite ends, seen in the circumferential direction, in each of which at least one injection element is arranged for injection of liquid lubricant, preferably of lubricating oil, to the body to be borne and to the rotor shaft.
  • liquid lubricant preferably of lubricating oil
  • the bearing body is advantageously in the form of a multiple-surface bearing composed of two half-shells, wherein the first channel is arranged in the loaded half-shell and extends at least at one end somewhat into the unloaded half-shell, wherein a separating joint of the multiple-surface bearing is arranged at an angle with respect to a horizontal, such that one of the bearing pockets is arranged above the horizontal, and the other bearing pocket is arranged below the horizontal, seen in cross section.
  • the bearing pockets are in this case arranged on the one hand in the loaded bearing shell and on the other hand in the unloaded bearing shell.
  • the loaded bearing shell is that shell which absorbs the nominal load, while the role of the unloaded bearing shell is restricted predominantly to guiding the body to be borne in the bearing body.
  • the bearing body is in each case arranged on its opposite bearing pockets, in the circumferential direction, with injection elements which are each arranged in a plurality of rows and spray liquid lubricant on the one hand onto the body to be borne and onto the rotor shaft and on the other hand into an outlet gap.
  • the injection elements are arranged as a plurality of two rows in the respective bearing pockets, wherein the injection elements are screwed into the bearing pockets as nozzles.
  • the injection elements and nozzles are arranged such that the required amount of oil or the required amount of liquid lubricant is sprayed at right angles onto the body to be borne or onto the rotor shaft, and on the other hand obliquely into the outlet gap of the loaded half-shell.
  • the invention preferably relates to radial plain bearings for rotating shafts with hydrodynamic lubrication.
  • the shape of the hole in each bearing can be described by the horizontal displacement of two half-shells (cylindrical or profiled).
  • the direction of the bearing separating joint in the case of split bearings is referred to as the horizontal.
  • the bearing is suitable for only one rotation direction and therefore offers the advantage of the long, very slightly convergent, pulling-in gap, which results in broadening of the hydrodynamic pressure build-up.
  • this provides a better plain bearing which has adjustable injection lubrication (directed lubrication) for a completely surrounded plain bearing, in which case it is possible to dispense with hinged segments according to the prior art.
  • fresh oil or the liquid lubricant is supplied through a hole, which is arranged on one side, through the supporting body (generally the housing) and first of all passes into a half-surrounded channel of the loaded half-shell, and then into the injection elements.
  • a plurality of these are in each case arranged in two rows in the bearing pockets, or in the bearing pockets seen in the circumferential direction, and spray the amount of oil at right angles onto the body to be borne, or onto the rotor shaft, and obliquely into the outlet gap of the loaded half-shell.
  • the obliquely directed nozzles in one of the bearing pockets are active.
  • a channel which is closed in the width direction is arranged centrally and extends over the entire circumference of the unloaded half-shell.
  • Active cooling of the bearing is achieved by means of the preferably three channels that are provided, which extend in the circumferential direction, and by means of a plurality of axial holes in the loaded half-shell, wherein the liquid lubricant which is supplied through the hole, which is arranged at one end, in the supporting body first of all passes into the first channel and is then passed through each of the axial holes which are open to the other channels, as a result of which the loaded half-shell is actively cooled.
  • the channels and axial holes therefore have a dual function. On the one hand, they are used for active cooling with fresh oil. On the other hand, they are used to supply fresh oil to the injection elements.
  • the plain bearing or the bearing body is advantageously turned into the supporting body in the opposite direction to the rotation direction of the body to be borne or the rotor shaft, and is held in an optimized angle position by the fixing element, to be precise the pin or pins.
  • the angle position, to be precise the optimized angle position is in this case different from one application to another, and can be calculated in accordance with the respective application.
  • the plain bearing according to the invention has a low friction power and low losses, and is distinguished by maintenance friendliness, because of the shell structure.
  • the noticeable reduction in the friction power is achieved by the internal ring channel in the unloaded half-shell. It is particularly advantageous
  • the plain bearing can be used by virtue of the modular design in existing bearing housings and in existing installation conditions, with very high reliability.
  • the plain bearing according to the invention can be used in steam turbines, generators and/or for example gas turbines.
  • FIG. 1 shows a cross section through a plain bearing
  • FIG. 2 shows a longitudinal section through the plain bearing shown in FIG. 1 .
  • FIG. 3 shows a graph, in which the (calculated) maximum lubricating film temperature is plotted against the specific bearing load.
  • FIG. 1 shows a plain bearing 1 which, in the illustrated exemplary embodiment, is in the form of a radial plain bearing.
  • the plain bearing 1 has a bearing body 2 in which a body 3 to be borne, which is referred to in the following text as a rotor shaft 3 , is borne.
  • the bearing body is surrounded by a supporting body 4 , which is referred in the following text as a housing 4 .
  • the housing 4 has a horizontal 6 , with the direction of the bearing separating joint in the case of split bearings being referred to as the horizontal 6 .
  • the bearing body 2 is arranged as a multiple-surface bearing with its separating joint 7 at an angle with respect to the horizontal 6 .
  • a hole 8 which is arranged at one end, is incorporated in the supporting body 4 or in the housing 4 . In the exemplary embodiment illustrated in FIG. 1 , this is arranged on the left-hand plane of the drawing, with the hole 8 being bisected by the imaginary horizontal 6 .
  • a fixing element 9 is arranged in the hole 8 such that the bearing body 2 can be fixed in its angular position.
  • the fixing element 9 is, for example, in the form of a pin which engages in a corresponding receptacle in the bearing body 2 , as a result of which this is fixed such that it is sufficiently rotationally secure.
  • FIG. 2 shows two high-pressure screw unions 25 which allow oil to be supplied at high pressure into hydrostatic pockets 29 for raising the rotor shaft.
  • the bearing body 2 is composed of two half-shells 11 , 12 , with the bearing shell 11 being referred to in the following text as the loaded bearing shell 11 , and with the bearing shell 12 being referred to in the following text as the unloaded bearing shell 12 .
  • Three outer channels 13 , 14 , 16 are arranged in the loaded bearing shell 11 and are open toward the housing 4 .
  • a first channel 13 which is illustrated in FIG. 2 , is in each case at a distance, seen in the axial direction, from the adjacent second channel 14 and third channel 16 , with the first channel 13 being arranged between the second and the third channel 14 and 16 , respectively.
  • the first channel 13 is illustrated in FIG. 1 .
  • the first channel 13 is incorporated in the wall 17 of the loaded bearing shell 11 and extends in the rotation direction 18 of the body 3 to be borne, or of the rotor shaft 3 , somewhat beyond the separating joint 7 into the unloaded bearing shell 12 .
  • Bearing pockets 19 and 21 are arranged at the opposite ends of the first channel 13 , seen in the circumferential direction,
  • bearing pocket 19 being arranged in the loaded bearing shell 11
  • bearing pocket 21 being arranged in the unloaded bearing shell 12 .
  • the second channel 14 and the third channel 16 are designed in a corresponding manner to the first channel 13 .
  • Longitudinal holes or axial holes 22 which pass through the three channels 13 , 14 and 16 , are incorporated in the wall 17 in the area of the first channel 13 , and of the second and third channels 14 and 16 respectively.
  • Injection elements 23 , 24 are arranged in the respective bearing pockets 19 and 21 , which are arranged at the end in the respective channels 13 , 14 and 16 , seen in the circumferential direction, which injection elements 23 , 24 in the preferred refinement on the one hand spray liquid lubricant or lubricating oil at right angles (injection element 23 ) onto the body 3 to be borne or onto the rotor shaft 3 , and on the other hand obliquely (injection element 24 ) into an outlet gap 26 of the loaded half-shell 11 and of the unloaded half-shell 12 , respectively.
  • injection elements 23 or nozzles which are directed at right angles in the bearing pocket 21 are not active.
  • the bearing body 2 is shifted with its separating joint 7 out of the horizontal 6 , in the opposite direction to the rotation direction 18 .
  • the bearing body 2 is therefore arranged with its separating joint 7 at an angle with respect to the horizontal 6 , wherein an angle ⁇ may have a different magnitude from one application to another, and can be determined and/or calculated separately for each specific application.
  • Fresh lubricant or oil is supplied through the hole 8 , which is arranged at one end, in the supporting body 4 or in the housing 4 , and is first of all passed into the half-surrounded first channel 13 of the loaded half-shell 11 , and then into the injection elements 23 and 24 , respectively.
  • a plurality of these are in each case arranged in two rows in the
  • All of the injection elements 23 , 24 or nozzles are preferably screwed into the respective bearing pockets 19 or 21 , thus allowing metering of the oil throughput in the inlet.
  • An internal ring channel 31 is arranged approximately centrally in FIG. 2 and is closed in the width direction, extending over the entire circumference of the unloaded half-shell 12 .
  • FIG. 3 shows the (calculated) maximum lubricating film temperature (T max [° C.]) plotted against the specific bearing load (p lat [N/mm 2 ]).
  • T max [° C.]
  • p lat specific bearing load
  • a temperature/load characteristic of a conventional plain bearing reference symbol 27
  • a temperature/load line reference symbol 28
  • the graph in FIG. 3 clearly shows that the plain bearing according to the invention is subject to considerably lower temperatures for the same load.

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  • 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)
US12/310,146 2006-08-16 2007-08-02 Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets Abandoned US20100002967A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP06017047.9 2006-08-16
EP06017047A EP1890045A1 (fr) 2006-08-16 2006-08-16 paliers radiaux hydrodynamiques pour gros turbogénérateurs
PCT/EP2007/057999 WO2008019947A2 (fr) 2006-08-16 2007-08-02 Palier lisse radial hydrodynamique ayant une charge utile maximale, destiné à des turbogénérateurs de grande taille

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/057999 A-371-Of-International WO2008019947A2 (fr) 2006-08-16 2007-08-02 Palier lisse radial hydrodynamique ayant une charge utile maximale, destiné à des turbogénérateurs de grande taille

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US13/432,001 Division US8851754B2 (en) 2006-08-16 2012-03-28 Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets
US13/432,035 Division US8876387B2 (en) 2006-08-16 2012-03-28 Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets

Publications (1)

Publication Number Publication Date
US20100002967A1 true US20100002967A1 (en) 2010-01-07

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Family Applications (3)

Application Number Title Priority Date Filing Date
US12/310,146 Abandoned US20100002967A1 (en) 2006-08-16 2007-08-02 Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets
US13/432,001 Active 2027-09-04 US8851754B2 (en) 2006-08-16 2012-03-28 Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets
US13/432,035 Active 2027-08-10 US8876387B2 (en) 2006-08-16 2012-03-28 Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets

Family Applications After (2)

Application Number Title Priority Date Filing Date
US13/432,001 Active 2027-09-04 US8851754B2 (en) 2006-08-16 2012-03-28 Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets
US13/432,035 Active 2027-08-10 US8876387B2 (en) 2006-08-16 2012-03-28 Hydrodynamic radial plain bearing with a very high load-bearing capacity of large turbine sets

Country Status (5)

Country Link
US (3) US20100002967A1 (fr)
EP (4) EP1890045A1 (fr)
JP (1) JP5052611B2 (fr)
CN (1) CN101563547B (fr)
WO (1) WO2008019947A2 (fr)

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US20120297770A1 (en) * 2009-08-27 2012-11-29 Thomas Figler Exhaust-gas power-recovery turbine for a turbo compound system
US8616777B1 (en) 2012-11-16 2013-12-31 Pratt & Whitney Canada Corp. Bearing assembly with inner ring
DE102015205223A1 (de) 2015-03-23 2016-09-29 Zf Friedrichshafen Ag Aktives Gleitlager

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EP1890045A1 (fr) 2006-08-16 2008-02-20 Siemens Aktiengesellschaft paliers radiaux hydrodynamiques pour gros turbogénérateurs
ES2395350B1 (es) * 2011-02-02 2014-09-09 Fagor, S. Coop. Prensa mecánica adaptada a procesos de conformado, en particular procesos de conformado en caliente
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
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DE102014200593A1 (de) * 2014-01-15 2015-07-16 Voith Patent Gmbh Hydrodynamisches Gleitlager
PL3094872T3 (pl) * 2014-01-15 2018-03-30 Voith Patent Gmbh Hydrodynamiczne łożysko ślizgowe
US9869190B2 (en) 2014-05-30 2018-01-16 General Electric Company Variable-pitch rotor with remote counterweights
US9726221B2 (en) 2014-07-31 2017-08-08 Hamilton Sundstrand Corporation Gear pump bearings with hybrid pads
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US9890813B2 (en) 2014-11-03 2018-02-13 Hamilton Sundstrand Corporation Gear pump bearings with hybrid pads
FR3028903B1 (fr) * 2014-11-20 2017-05-05 Snecma Palier lisse auto-centrant
US10072510B2 (en) 2014-11-21 2018-09-11 General Electric Company Variable pitch fan for gas turbine engine and method of assembling the same
JP5936725B1 (ja) * 2015-01-30 2016-06-22 三菱日立パワーシステムズ株式会社 ジャーナル軸受装置、及び、回転機械
CN104863971B (zh) * 2015-04-27 2017-05-10 张永斌 运用物理吸附形成的同心微型向心滑动轴承
US10100653B2 (en) 2015-10-08 2018-10-16 General Electric Company Variable pitch fan blade retention system
DE102017216563A1 (de) * 2017-09-19 2019-03-21 Siemens Aktiengesellschaft Turbomaschine sowie Verfahren zum Betreiben einer Turbomaschine im Drehbetrieb
US11674435B2 (en) 2021-06-29 2023-06-13 General Electric Company Levered counterweight feathering system
US11795964B2 (en) 2021-07-16 2023-10-24 General Electric Company Levered counterweight feathering system

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US8876387B2 (en) 2014-11-04
EP1890045A1 (fr) 2008-02-20
EP2787226A1 (fr) 2014-10-08
EP2052165A2 (fr) 2009-04-29
US20120183244A1 (en) 2012-07-19
US20120183245A1 (en) 2012-07-19
EP2787228A1 (fr) 2014-10-08
EP2787226B1 (fr) 2020-12-09
CN101563547A (zh) 2009-10-21
JP2010500520A (ja) 2010-01-07
US8851754B2 (en) 2014-10-07
JP5052611B2 (ja) 2012-10-17
CN101563547B (zh) 2012-11-14
WO2008019947A3 (fr) 2009-05-22
WO2008019947A2 (fr) 2008-02-21

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