EP2052165A2 - Hydrodynamic radial plain bearing having a maximum bearing capacity for large turbo-generators - Google Patents

Hydrodynamic radial plain bearing having a maximum bearing capacity for large turbo-generators

Info

Publication number
EP2052165A2
EP2052165A2 EP07788164A EP07788164A EP2052165A2 EP 2052165 A2 EP2052165 A2 EP 2052165A2 EP 07788164 A EP07788164 A EP 07788164A EP 07788164 A EP07788164 A EP 07788164A EP 2052165 A2 EP2052165 A2 EP 2052165A2
Authority
EP
European Patent Office
Prior art keywords
bearing
channel
horizontal
stored
shell
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Withdrawn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
EP07788164A
Other languages
German (de)
French (fr)
Inventor
Morched Medhioub
Bernd LÜNEBURG
Diethelm Dettmar
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
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Priority to EP07788164A priority Critical patent/EP2052165A2/en
Priority to EP14002235.1A priority patent/EP2787226B1/en
Priority to EP14002234.4A priority patent/EP2787228A1/en
Publication of EP2052165A2 publication Critical patent/EP2052165A2/en
Withdrawn legal-status Critical Current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
    • 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 sliding bearing, which has a bearing body in which a body to be stored is mounted, wherein the bearing body is covered by a support body.
  • a plain bearing is a bearing in which the rotating and bearing body slides on sliding surfaces.
  • the sliding surface of the body to be stored slides on the sliding surfaces of the bearing body.
  • the bearing body is designed differently depending on the type of sliding bearing.
  • a radial sliding bearing ⁇ the bearing body is designed as embedded in a housing bearing shell, which can be designed divided into several bearing segments.
  • a lubricant film for example an oil film, is brought between the sliding surfaces.
  • the lubricant is drawn into the gap between the sliding surfaces, and the body to be stored moves into an eccentric position in the bearing body. He goes through the area of mixed friction. With increase of the sliding speed and the transition in the exzentri ⁇ specific position, a lubricant wedge, through the pressure of the body to be supported is lifted from the bearing body forms between about lagerndem body and the bearing body. The body to be stored then runs stable in the bearing body, with purely hydrodynamic lubrication without direct contact of the bearing body and body to be stored. This effect occurs in a radial slide bearing through an existing bearing clearance.
  • a plain bearing in particular a radial plain bearing of the type mentioned is used for example in steam turbine, generator and gas turbine.
  • the plain bearing stored rotor shafts as a body to be stored.
  • the invention has for its object to verbes ⁇ a sliding bearing of the type mentioned to the effect that this meets the above requirements, for example in large turbine construction, preferably in steam turbine.
  • Bearing body is arranged as a multi-surface bearing with its parting line relative to a horizontal angle.
  • the parting line is arranged at an angle relative to the horizontal. It is expedient for the purposes of the invention, when seen in cross-section, the parting line is offset against a direction of rotation of the body to be supported or a rotor shaft.
  • the bearing member is fixed with its parting line in the relative arranged on the horizontal angular position, for fixing a fixing element, wherein ⁇ play as one or more pins may be used, which is arranged in the support body and engages fixing into the bearing body, or . Fixing abuts on this, so that the bearing body is held sufficiently secure against rotation in its angular position.
  • the bearing body seen in the circumferential direction in its wall has an at least partially ange ⁇ arranged first channel, wherein in the wall at least one axial bore is arranged, which penetrates the first channel.
  • the La ⁇ gerraj seen in the axial direction at least one spaced apart from the first channel second channel, wherein fertil in the convertible at least one axial bore is arranged, which penetrates the ers ⁇ th channel and the second channel, that they communicate with each other via the axial bore.
  • a third or further channels are provided, wherein the first channel is arranged between the second and the third channel in the axial direction, and wherein a plurality of axial bores are provided, which penetrate all three channels.
  • the first channel in a loaded bearing shell of the bearing body is introduced and opened to the support body, wherein the first channel is seen in the circumferential direction semicircular introduced into the wall of the bearing body, so that a quasi-semi-circular groove is formed, which extends somewhat into the wall of an unloaded bearing shell, ie the second half-shell.
  • the first channel at its seen in the circumferential direction opposing ends bearing pockets, in each of which at least one injection element for a ⁇ inject liquid lubricant, preferably arranged lubricating oil to be stored body or to the rotor shaft.
  • the bearing body is formed as a multi-surface bearing of two half-shells, wherein the first channel is disposed in the loaded half-shell and at least one side something in the unloaded half-shell extends into, a parting of the multi-surface bearing is arranged at an angle relative to a horizontal, so that one of Storage bags in the
  • the bearing pockets are in this case due to the configuration of at least the first channel on the one hand in the loaded bearing shell and the other hand, in the unloaded bearing shell arranged ⁇ .
  • the loaded bearing shell according to the invention is the shell, which receives the nominal load, while the role of the unloaded bearing shell mainly limited to the leadership of the body to be stored in the bearing body.
  • the bearing body are each assigned to multi-row arranged injection elements at its opposite in the circumferential direction bearing pockets, the liquid lubricant on the one hand to be stored body or on the rotor shaft and the other in an outlet gap sprit ⁇ zen.
  • the Einspritzele ⁇ elements are arranged in a double row in the respective bearing pockets in a plurality, wherein the injection elements are screwed as nozzles in the bearing pockets.
  • the injection elements or nozzles are arranged such that the required amount of oil or the required amount of liquid lubricant is injected perpendicular to the body to be stored or on the rotor shaft and the other obliquely into the exit gap of the loaded half ⁇ shell.
  • the invention preferably relates to radial plain bearings for rotating shafts with hydrodynamic lubrication.
  • the bore shape of each bearing can be described by the horizontal displacement of two half shells (cylindrical or profiled). As horizontal while the direction of the La ⁇ gerteilfuge is called at shared bearings.
  • the bearing is only suitable for one direction of rotation and thus offers the advantage of the long, very weakly convergent intake gap, which results in a widening of the hydrodynamic pressure build-up.
  • an improved slide bearings for Availability checked ⁇ supply which has an adjustable injection lubrication (ge ⁇ directed lubrication) for a fully enclosed sleeve bearing on ⁇ wherein ver ⁇ can be dispensed on tilting pads of the prior art.
  • fresh oil or the liquid lubricant is supplied through a bore arranged on one side through the support body (generally the housing) and first enters a half-enclosed channel of the loaded half shell and then into the injection elements.
  • Active cooling of the bearing is achieved by means of the preferably three channels provided which extend in the circumferential direction and by means of a plurality of axial bores in the loaded half shell, wherein the liquid lubricant supplied through the bore arranged on one side in the support body first enters the first channel and is passed through each open to the other channels axial bores, so that the loaded half-shell is actively cooled.
  • the channels or axial bores therefore has a double function. On the one hand, these are used for active cooling with fresh oil. On the other hand, these serve to supply the injection elements with fresh oil.
  • the slide bearing or the bearing body is advantageously rotated against the direction of rotation of the body to be stored or the rotor shaft in the support body and held by the fixing or the or the pins in an optimized angular position.
  • the angular position or the angle optimized Posi ⁇ tion is in this case of application to application under ⁇ differently and can be calculated according to the respective application.
  • a plain bearing which even at high examplessgeschwindigkei ⁇ th has a high stability in a wide load range and very good rotor dynamic performance with maximum load capacity.
  • the invention he ⁇ contemporary plain bearings or low frictional energy losses and is characterized by ease of service to ⁇ due to the shell construction.
  • the noticeable Redu ⁇ cation of the friction power is achieved by the inner ring channel in the unloaded half shell.
  • the slide bearing can be used by the modular design of the existing bearing housings in existing installation conditions, with a very high accident safety is present.
  • the sliding bearing according to the invention can be used in steam turbines, generators and / or, for example, gas turbines.
  • Fig. 2 shows the slide bearing of FIG. 1 in a longitudinal section
  • Fig. 3 is a graph in which the (calculated) maximum
  • Lubricating film temperature is plotted against the specific bearing load.
  • Figure 1 shows a plain bearing 1, which is designed in the illustrated embodiment as a radial sliding bearing.
  • the sliding bearing 1 has a bearing body 2, in which a body 3 to be supported, which is referred to below as the rotor shaft 3, is mounted.
  • the bearing body 2 is surrounded by a support body 4, which is referred to below as the housing 4.
  • the housing 4 has a horizontal 6, wherein as Hori ⁇ zontale 6, the direction of the Lagerteilfuge is referred to in shared bearings.
  • the bearing body 2 is arranged as a multi-surface bearing with its parting line 7 relative to the horizontal 6 at an angle.
  • a unilaterally arranged bore 8 is introduced in the support body 4 and in the housing 4 . This is arranged in the embodiment shown in Figure 1 on the left plane of the drawing, wherein the bore 8 is bisected by the imaginary horizontal 6.
  • a fixing element 9 is arranged, so that the bearing body 2 is fixable in its angular position.
  • the fixing element 9 is embodied as a pin which engages in a corresponding receptacle of the bearing body 2 is a ⁇ so that it is sufficiently fixed against rotation. 2, two high-pressure fittings 25 can be removed, which allow the oil supply under high pressure in the hydrostatic pockets 29 for raising the rotor shaft.
  • the bearing body 2 is composed in the illustrated embodiment of two half-shells 11, 12, wherein the bearing shell 11 is hereinafter referred to as loaded bearing shell 11 and the bearing shell 12 hereinafter referred to as unloaded bearing shell 12.
  • first channel 13 is seen in the axial direction in each case to the adjacent second channel 14 and third channel 16 spaced, wherein the first channel 13 between the second and the third channel 14 and 16 is arranged.
  • first channel 13 is shown due to the selected cross-section.
  • the first channel 13 is introduced into the wall 17 of the loaded bearing shell 11 and it ⁇ extends in the rotational direction 18 of the body 3 to be stored or the rotor shaft 3 about the parting line 7 in addition, the unloaded bearing shell 12th
  • bearing pockets 19 and 21 are arranged, wherein the bearing pocket 19 in the loaded bearing shell 11 and the bearing pocket 21 in the unloaded bearing shell 12 is arranged ⁇ .
  • the second channel 14 and the third channel 16 are executed corresponding to the first channel 13.
  • longitudinal bores or axial bores 22 are introduced into the wall 17 and penetrate the three channels 13, 14 and 16.
  • each end in the channels 13, 14 and 16 arranged bearing pockets 19 and 21 are injection elements 23, preferably nozzles 24, arranged in a preferred embodiment for a liquid lubricant or lubricating oil vertically (injection element 23) on the to be stored body 3 or on the rotor shaft 3 and the other ⁇ ren obliquely (injector 24) into an outlet gap 26 of the loaded half shell 11 and the unloaded half shell 12 inject.
  • injection element 23 preferably nozzles 24
  • injector 24 into an outlet gap 26 of the loaded half shell 11 and the unloaded half shell 12 inject.
  • the bearing body 2 is moved with its parting line 7 against the direction of rotation 18 of the horizontal 6.
  • the bearing body 2 is arranged with its parting line 7 relative to the horizontal 6 at an angle, wherein an angle ⁇ from application to application may have a different amount and for each specific application separately determinier ⁇ bar or calculable.
  • the single-disposed bore 8 in the support body 4 and in the housing 4 fresh lubricant or oil is supplied, and first passes into the semi-enclosed ers ⁇ th channel 13 of the loaded half-shell 11 and then into the injector elements 23 and 24.
  • injector elements 23 and 24 are in the warehouse see 19 and 21 respectively arranged in a plurality of double rows and inject the required amount of oil perpendicular to the rotor ⁇ shaft 3 and obliquely into the exit slit 26 of the loaded half-shell 11.
  • All injection elements 23, 24 or nozzles are preferably in the bearing pockets 19 and 21, which allows metering of the oil throughput in the inlet.
  • an inner ring channel 31 is arranged, which is closed in the width direction, and extends over the entire circumference of the unloaded half-shell 12.
  • FIG. 3 shows, by way of example, the (calculated) maximum lubricant film temperature (T max [° C]) over the specific bearing load (Pquer [N / mm 2 ]).
  • T max [° C] the maximum lubricant film temperature
  • Pquer [N / mm 2 ] the specific bearing load
  • a temperature / load characteristic curve of a conventional slide bearing (reference numeral 27) in comparison to a temperature / load line (Beyakszei ⁇ chen 28) of the inventively designed plain bearing, or radial plain bearing with hydrodynamic lubrication is shown. It can be clearly seen from the graph of Figure 3 that the sliding bearing according to the invention is exposed to significantly lower temperatures at the same load.

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

The invention relates to a sliding bearing (1) which comprises a bearing body (2) in which a body (3) which is to be mounted is arranged. Said bearing body (2) is surrounded by a support body (4). The aim of the invention is to improve a sliding bearing of the above-mentioned type such that, in particular, the bearing capacity thereof is improved. This is achieved by virtue of the fact that the bearing body (2) is arranged at an angle in relation to the horizontal (6) with the joint (7) thereof. Said sliding bearing comprises an active cooling system. Also, the sliding bearing is further improved by means of an articulated lubrication system.

Description

Beschreibungdescription
Hydrodynamische Radialgleitlager höchster Tragfähigkeit für große TurbosätzeHydrodynamic radial sliding bearings of highest load capacity for large turbo sets
Die Erfindung betrifft ein Gleitlager, das einen Lagerkörper aufweist, in dem ein zu lagernder Körper gelagert wird, wobei der Lagerkörper von einem Stützkörper umfasst ist.The invention relates to a sliding bearing, which has a bearing body in which a body to be stored is mounted, wherein the bearing body is covered by a support body.
Ein Gleitlager ist ein Lager, bei dem der sich drehende und zu lagernde Körper auf Gleitflächen gleitet. Hierbei gleitet die Gleitfläche des zu lagernden Körpers auf den Gleitflächen des Lagerkörpers. Der Lagerkörper ist je nach Art des Gleit- lagers unterschiedlich ausgestaltet. Bei einem Radialgleit¬ lager ist der Lagerkörper als in einem Gehäuse eingebettete Lagerschale ausgeführt, die in mehrere Lagersegmente geteilt ausgeführt sein kann.A plain bearing is a bearing in which the rotating and bearing body slides on sliding surfaces. Here, the sliding surface of the body to be stored slides on the sliding surfaces of the bearing body. The bearing body is designed differently depending on the type of sliding bearing. In a radial sliding bearing ¬ the bearing body is designed as embedded in a housing bearing shell, which can be designed divided into several bearing segments.
Bei Betrieb des Gleitlagers reibt die Gleitfläche des zu lagernden Körpers auf den Gleitflächen des Lagerkörpers. Um diese Reibung, und damit auch den Verschleiß des Gleitlagers, so gering wie möglich zu halten, wird zwischen die Gleitflächen ein Schmiermittelfilm, beispielsweise ein Ölfilm ge- bracht.During operation of the sliding bearing rubs the sliding surface of the body to be stored on the sliding surfaces of the bearing body. In order to keep this friction, and thus also the wear of the sliding bearing, as low as possible, a lubricant film, for example an oil film, is brought between the sliding surfaces.
Bei Beginn der Rotation wird der Schmierstoff in den Spalt zwischen den Gleitflächen gezogen, und der zu lagernde Körper geht in eine exzentrische Position im Lagerkörper über. Er durchläuft dabei den Bereich der Mischreibung. Mit Erhöhung der Gleitgeschwindigkeit und des Übergangs in die exzentri¬ sche Position bildet sich zwischen zu lagerndem Körper und dem Lagerkörper ein Schmierstoffkeil, durch dessen Druck der zu lagernde Körper vom Lagerkörper abgehoben wird. Der zu lagernde Körper läuft dann stabil im Lagerkörper, bei rein hydrodynamischer Schmierung ohne direkten Kontakt von Lagerkörper und zu lagerndem Körper. Dieser Effekt tritt in einem Radialgleitlager durch ein vorhandenes Lagerspiel auf. Ein Gleitlager, insbesondere ein Radialgleitlager der eingangs genannten Art ist beispielsweise in Dampfturbinen-, Generatoren- und Gasturbinenbau einsetzbar. Hierbei lagert das Gleitlager Rotorwellen als zu lagernde Körper.At the beginning of the rotation, the lubricant is drawn into the gap between the sliding surfaces, and the body to be stored moves into an eccentric position in the bearing body. He goes through the area of mixed friction. With increase of the sliding speed and the transition in the exzentri ¬ specific position, a lubricant wedge, through the pressure of the body to be supported is lifted from the bearing body forms between about lagerndem body and the bearing body. The body to be stored then runs stable in the bearing body, with purely hydrodynamic lubrication without direct contact of the bearing body and body to be stored. This effect occurs in a radial slide bearing through an existing bearing clearance. A plain bearing, in particular a radial plain bearing of the type mentioned is used for example in steam turbine, generator and gas turbine. Here, the plain bearing stored rotor shafts as a body to be stored.
Die Zielsetzung aktueller Neuentwicklungen im Dampfturbinenbau für die Stromerzeugung besteht darin, den Wirkungsgrad deutlich zu steigern und die Energie effizient umzusetzen. Dabei ist eine hohe Betriebssicherheit zu gewährleisten und Kosteneinsparungen zu realisieren. Diese Entwicklung hat zur Folge, dassThe objective of current new developments in steam turbine construction for power generation is to significantly increase the efficiency and to efficiently convert the energy. At the same time, a high level of operational safety is to be ensured and cost savings to be realized. This development has the consequence that
a) die Rotoren länger werden, der Lagerabstand wird größera) the rotors are getting longer, the bearing distance gets bigger
b) die Abdampfquerschnitte insbesondere im Niederdruckbereich größer werden, undb) the Abdampfquerschnitte are larger, especially in the low pressure region, and
c) die spezifische Leistung der einzelnen Teilturbinen ange- hoben wird.c) the specific power of the individual turbine sections is increased.
Bei gleichzeitiger Beibehaltung eines so genannten Monoblock- bauprinzips insbesondere im Niederdruckbereich von Dampfturbinen führt diese Entwicklung letztendlich zu einer signifi- kanten Erhöhung der spezifischen Lagerlasten. Damit werden die Lager bzw. deren maximale Tragfähigkeit begrenzend bei der Turbinenentwicklung insbesondere im Niederdruckbereich. Eine ähnliche Entwicklung ist auch bei den Generatoren und den Gasturbinen zu beobachten. Die Tragfähigkeit der Gleit- lager ist von der Maximaltemperatur, der maximalen spezifischen Lagerbelastung und der minimalen Schmierfilmdicke begrenzt .While maintaining a so-called monoblock construction principle, especially in the low pressure range of steam turbines, this development ultimately leads to a significant increase in the specific bearing loads. Thus, the bearings or their maximum load capacity are limiting in turbine development, especially in the low pressure range. A similar development can also be observed with the generators and the gas turbines. The bearing capacity of the plain bearings is limited by the maximum temperature, the maximum specific bearing load and the minimum lubricant film thickness.
Neben der signifikanten Erhöhung der Tragfähigkeit werden folgende zusätzliche Anforderungen an dieses Lager gestellt:In addition to the significant increase in carrying capacity, the following additional requirements are imposed on this warehouse:
hohe Stabilität für alle Lastbereiche bzw. gute rotordyna¬ mische Eigenschaften, Servicefreundlichkeit,high stability for all load ranges and good rotordyna ¬ mix properties Serviceability,
- höchste Betriebsverfügbarkeit/verschleißfreier Betrieb, Anhebung der Rotoren durch Hochdrucköl im Turnbetrieb,- Highest operating availability / wear-free operation, lifting of the rotors by high-pressure oil in turn operation,
- hohe Störfallsicherheit (Integrität des Turbosatzes bei hohen Unwuchten) ,- high level of accident safety (integrity of the turbo set at high imbalances),
- Verwendung im existierenden Lagergehäuse, und Nachrüstbarkeit .- Use in existing bearing housing, and retrofitting.
Um den vorgenannten Anforderungen und einer signifikanten Er- höhung der Tragfähigkeit der Gleitlager zu entsprechen, sind z. B. folgende Maßnahmen bekannt:To meet the above requirements and a significant increase in the carrying capacity of the plain bearings, z. B. the following measures:
Reduzierung des Rotorgewichtes, Verwendung höherviskoser Öle, - größere Lagerbreiten und/oder Lagerzapfendurchmesser, niedrigere Ölzuführtemperatur, und gerichtete (gelenkte) Schmierung (bei Kippsegmentla¬ gern) .Reduction of the rotor weight, use of higher viscous oils, - larger bearing widths and / or bearing journal diameter, lower oil supply temperature, and directed (steered) lubrication (Kippsegmentla ¬ like).
Diese Standardmaßnahmen zur Erhöhung der Tragfähigkeit haben sich in der Praxis bewährt, stoßen aber immer häufiger an Grenzen .These standard measures for increasing the load-bearing capacity have been proven in practice, but are increasingly reaching their limits.
Von daher liegt der Erfindung die Aufgabe zugrunde, ein Gleitlager der eingangs genannten Art dahingehend zu verbes¬ sern, dass dieses den oben genannten Anforderungen beispielsweise im Großturbinenbau, vorzugsweise im Dampfturbinenbau gerecht wird.Therefore, the invention has for its object to verbes ¬ a sliding bearing of the type mentioned to the effect that this meets the above requirements, for example in large turbine construction, preferably in steam turbine.
Erfindungsgemäß wird die Aufgabe dadurch gelöst, dass derAccording to the invention the object is achieved in that the
Lagerkörper als Mehrflächenlager mit seiner Teilfuge bezogen auf eine Horizontale winklig angeordnet ist.Bearing body is arranged as a multi-surface bearing with its parting line relative to a horizontal angle.
Günstig im Sinne der Erfindung ist, wenn der Lagerkörper aus zwei Halbschalen gebildet ist, deren Teilfuge bezogen auf die Horizontale winklig angeordnet ist. Zweckmäßig im Sinne der Erfindung ist, wenn die Teilfuge im Querschnitt gesehen entgegen einer Drehrichtung des zu lagernden Körpers bzw. einer Rotorwelle versetzt ist.Favorable in the context of the invention is when the bearing body is formed of two half-shells, the parting line is arranged at an angle relative to the horizontal. It is expedient for the purposes of the invention, when seen in cross-section, the parting line is offset against a direction of rotation of the body to be supported or a rotor shaft.
Vorteilhaft ist, wenn der Lagerkörper mit seiner Teilfuge in der bezogen auf die Horizontale angeordneten Winkelposition fixiert wird, wobei zur Fixierung ein Fixierelement, bei¬ spielsweise ein oder mehrere Stifte verwendet werden können, welcher im Stützkörper angeordnet ist und in den Lagerkörper fixierend eingreift, bzw. fixierend an diesem anliegt, so dass der Lagerkörper hinreichend drehsicher in seiner Winkelposition gehalten ist.It is advantageous if the bearing member is fixed with its parting line in the relative arranged on the horizontal angular position, for fixing a fixing element, wherein ¬ play as one or more pins may be used, which is arranged in the support body and engages fixing into the bearing body, or . Fixing abuts on this, so that the bearing body is held sufficiently secure against rotation in its angular position.
In einer weiteren vorteilhaften Ausgestaltung der Erfindung ist vorgesehen, dass der Lagerkörper in seiner Wandung in Um- fangsrichtung gesehen einen zumindest abschnittsweise ange¬ ordneten ersten Kanal aufweist, wobei in der Wandung zumindest eine Axialbohrung angeordnet ist, die den ersten Kanal durchdringt. Damit wird eine aktive Kühlung des Gleitlagers bzw. des Lagerkörpers zur Verfügung gestellt.In a further advantageous embodiment of the invention it is provided that the bearing body seen in the circumferential direction in its wall has an at least partially ange ¬ arranged first channel, wherein in the wall at least one axial bore is arranged, which penetrates the first channel. For an active cooling of the sliding bearing or the bearing body is provided.
Zweckmäßig im Sinne der Erfindung ist hierbei, wenn der La¬ gerkörper in Axialrichtung gesehen zumindest einen zum ersten Kanal beabstandeten zweiten Kanal aufweist, wobei in der Wan- düng zumindest eine Axialbohrung angeordnet ist, die den ers¬ ten Kanal und zweiten Kanal durchdringt, so dass diese über die Axialbohrung miteinander in Verbindung stehen. Natürlich kann aber auch vorgesehen sein, dass ein dritter oder weitere Kanäle vorgesehen sind, wobei der erste Kanal in Axialrich- tung gesehen zwischen dem zweiten und dem dritten Kanal angeordnet ist, und wobei mehrere Axialbohrungen vorgesehen sind, die jeweils alle drei Kanäle durchdringen.Suitably, in the context of the invention is in this case, when the La ¬ gerkörper seen in the axial direction at least one spaced apart from the first channel second channel, wherein fertil in the convertible at least one axial bore is arranged, which penetrates the ers ¬ th channel and the second channel, that they communicate with each other via the axial bore. Of course, however, it can also be provided that a third or further channels are provided, wherein the first channel is arranged between the second and the third channel in the axial direction, and wherein a plurality of axial bores are provided, which penetrate all three channels.
Günstigerweise ist der erste Kanal in einer belasteten Lager- schale des Lagerkörpers eingebracht und zum Stützkörper hin geöffnet, wobei der erste Kanal in Umfangsrichtung gesehen halbkreisförmig in die Wandung des Lagerkörpers eingebracht ist, so dass quasi eine halbkreisförmige Nut gebildet ist, die sich etwas in die Wandung einer unbelasteten Lagerschale, also der zweiten Halbschale hinein erstreckt.Conveniently, the first channel in a loaded bearing shell of the bearing body is introduced and opened to the support body, wherein the first channel is seen in the circumferential direction semicircular introduced into the wall of the bearing body, so that a quasi-semi-circular groove is formed, which extends somewhat into the wall of an unloaded bearing shell, ie the second half-shell.
Vorteilhafterweise weist der erste Kanal an seinen in Um- fangsrichtung gesehen gegenüberliegenden Enden Lagertaschen auf, in denen jeweils zumindest ein Einspritzelement zum Ein¬ spritzen flüssigen Schmiermittels, vorzugsweise von Schmieröl zum zu lagernden Körper bzw. zur Rotorwelle angeordnet sind.Advantageously, the first channel at its seen in the circumferential direction opposing ends bearing pockets, in each of which at least one injection element for a ¬ inject liquid lubricant, preferably arranged lubricating oil to be stored body or to the rotor shaft.
Vorteilhaft ist der Lagerkörper als Mehrflächenlager aus zwei Halbschalen gebildet, wobei der erste Kanal in der belasteten Halbschale angeordnet ist und sich zumindest einseitig etwas in die unbelastete Halbschale hinein erstreckt, wobei eine Teilfuge des Mehrflächenlagers bezogen auf eine Horizontale winklig angeordnet ist, so dass eine der Lagertaschen imAdvantageously, the bearing body is formed as a multi-surface bearing of two half-shells, wherein the first channel is disposed in the loaded half-shell and at least one side something in the unloaded half-shell extends into, a parting of the multi-surface bearing is arranged at an angle relative to a horizontal, so that one of Storage bags in the
Querschnitt gesehen oberhalb der Horizontalen und die andere Lagertasche unterhalb der Horizontalen angeordnet ist. Die Lagertaschen sind hierbei aufgrund der Ausgestaltung zumindest des ersten Kanals einerseits in der belasteten Lager- schale und andererseits in der unbelasteten Lagerschale ange¬ ordnet. Die belastete Lagerschale im Sinne der Erfindung ist die Schale, welche die nominelle Last aufnimmt, während sich die Rolle der unbelasteten Lagerschale vorwiegend auf die Führung des zu lagernden Körpers in dem Lagerkörper be- schränkt.Cross-section seen above the horizontal and the other bearing pocket is arranged below the horizontal. The bearing pockets are in this case due to the configuration of at least the first channel on the one hand in the loaded bearing shell and the other hand, in the unloaded bearing shell arranged ¬. The loaded bearing shell according to the invention is the shell, which receives the nominal load, while the role of the unloaded bearing shell mainly limited to the leadership of the body to be stored in the bearing body.
In einer weiteren vorteilhaften Ausgestaltung der Erfindung ist vorgesehen, dass dem Lagerkörper an seinen in Umfangs- richtung gegenüberliegenden Lagertaschen jeweils mehrreihig angeordnete Einspritzelemente zugeordnet sind, die flüssiges Schmiermittel zum einen auf den zu lagernden Körper bzw. auf die Rotorwelle und zum anderen in einen Austrittsspalt sprit¬ zen .In a further advantageous embodiment of the invention it is provided that the bearing body are each assigned to multi-row arranged injection elements at its opposite in the circumferential direction bearing pockets, the liquid lubricant on the one hand to be stored body or on the rotor shaft and the other in an outlet gap sprit ¬ zen.
Günstig im Sinne der Erfindung ist, wenn die Einspritzele¬ mente in den jeweiligen Lagertaschen in Mehrzahl zweireihig angeordnet sind, wobei die Einspritzelemente als Düsen in den Lagertaschen eingeschraubt sind. In bevorzugter Ausgestaltung sind die Einspritzelemente bzw. Düsen derart angeordnet, dass die erforderliche Ölmenge bzw. die erforderliche Menge an flüssigem Schmiermittel senkrecht auf den zu lagernden Körper bzw. auf die Rotorwelle und zum anderen schräg in den Austrittsspalt der belasteten Halb¬ schale gespritzt wird.Favorable in the context of the invention is when the Einspritzele ¬ elements are arranged in a double row in the respective bearing pockets in a plurality, wherein the injection elements are screwed as nozzles in the bearing pockets. In a preferred embodiment, the injection elements or nozzles are arranged such that the required amount of oil or the required amount of liquid lubricant is injected perpendicular to the body to be stored or on the rotor shaft and the other obliquely into the exit gap of the loaded half ¬ shell.
Insgesamt betrifft die Erfindung bevorzugt Radialgleitlager für rotierende Wellen mit hydrodynamischer Schmierung. Die Bohrungsform jedes Lagers lässt sich durch die horizontale Verschiebung zweier Halbschalen (zylindrisch oder profiliert) beschreiben. Als Horizontale wird dabei die Richtung der La¬ gerteilfuge bei geteilten Lagern bezeichnet. Das Lager ist lediglich für eine Drehrichtung geeignet und bietet damit den Vorteil, des langen, sehr schwach konvergenten Einzugspalts, was eine Verbreiterung des hydrodynamischen Druckaufbaus zur Folge hat.Overall, the invention preferably relates to radial plain bearings for rotating shafts with hydrodynamic lubrication. The bore shape of each bearing can be described by the horizontal displacement of two half shells (cylindrical or profiled). As horizontal while the direction of the La ¬ gerteilfuge is called at shared bearings. The bearing is only suitable for one direction of rotation and thus offers the advantage of the long, very weakly convergent intake gap, which results in a widening of the hydrodynamic pressure build-up.
Insgesamt wird somit ein verbessertes Gleitlager zur Verfü¬ gung gestellt, das eine einstellbare Einspritzschmierung (ge¬ lenkte Schmierung) für ein voll umschlossenes Gleitlager auf¬ weist, wobei auf Kippsegmente nach dem Stand der Technik ver¬ zichtet werden kann. Hierbei wird frisches Öl bzw. das flüs- sige Schmiermittel durch eine einseitig angeordnete Bohrung durch den Stützkörper (allgemein Gehäuse) zugeführt und gelangt erst in einen halb umschlossenen Kanal der belasteten Halbschale und anschließend in die Einspritzelemente. Diese sind in den Lagertaschen bzw. in den in Umfangsrichtung gese- hen Lagertaschen jeweils in Mehrzahl zweireihig angeordnet und spritzen die Ölmenge senkrecht auf den zu lagernden Kör¬ per bzw. auf die Rotorwelle und schräg in den Austrittsspalt der belasteten Halbschale. Dabei sind in einer der Lagertaschen nur die schräg gerichteten Düsen aktiv. Bevorzugter- weise ist dies die Lagertasche, welche im fixierten Zustand des Lagerkörpers unterhalb der Horizontalen angeordnet ist. Alle Düsen werden eingeschraubt, wodurch eine Dosierung des Öldurchsatzes im Zulauf ermöglicht wird. Mittels eines Tragspiegels wird ein Einlaufverschleiß bzw. ein unkontrollierter Verschleiß im Betrieb vorteilhaft ver¬ hindert. Ein in Breitenrichtung geschlossener Kanal (Innen- ringkanal) ist mittig angeordnet und erstreckt sich über den ganzen Umfang der unbelasteten Halbschale.Overall, therefore, an improved slide bearings for Availability checked ¬ supply is provided, which has an adjustable injection lubrication (ge ¬ directed lubrication) for a fully enclosed sleeve bearing on ¬ wherein ver ¬ can be dispensed on tilting pads of the prior art. In this case, fresh oil or the liquid lubricant is supplied through a bore arranged on one side through the support body (generally the housing) and first enters a half-enclosed channel of the loaded half shell and then into the injection elements. These are arranged in two rows each in plurality in the bearing pockets or in the GeSe hen in the circumferential direction of the bearing pockets and inject the amount of oil perpendicular to the product to be stored Kör ¬ by or to the rotor shaft and obliquely in the exit gap of the loaded half-shell. In this case, only the obliquely directed nozzles are active in one of the bearing pockets. Preferably, this is the bearing pocket, which is arranged in the fixed state of the bearing body below the horizontal. All nozzles are screwed in, allowing a metering of the oil flow in the inlet. Means of a supporting mirror is a running-in wear and uncontrolled wear during operation advantageously prevents ¬ ver. A channel closed in the width direction (inner ring channel) is arranged centrally and extends over the entire circumference of the unloaded half shell.
Mittels der bevorzugterweise drei vorgesehenen Kanäle, welche sich in Umfangsrichtung erstrecken und mittels mehrerer Axi- albohrungen in der belasteten Halbschale wird eine aktive Kühlung des Lagers erreicht, wobei das durch die einseitig angeordnete Bohrung in dem Stützkörper zugeführte flüssige Schmiermittel zunächst in den ersten Kanal gelangt und durch die jeweils zu den anderen Kanälen geöffneten Axialbohrungen geleitet wird, so dass die belastete Halbschale aktiv gekühlt wird. Den Kanälen bzw. Axialbohrungen kommt demnach eine Doppelfunktion zu. Zum einen dienen diese zur aktiven Kühlung mit frischem Öl. Zum anderen dienen diese zur Versorgung der Einspritzelemente mit frischem Öl.Active cooling of the bearing is achieved by means of the preferably three channels provided which extend in the circumferential direction and by means of a plurality of axial bores in the loaded half shell, wherein the liquid lubricant supplied through the bore arranged on one side in the support body first enters the first channel and is passed through each open to the other channels axial bores, so that the loaded half-shell is actively cooled. The channels or axial bores therefore has a double function. On the one hand, these are used for active cooling with fresh oil. On the other hand, these serve to supply the injection elements with fresh oil.
Das Gleitlager bzw. der Lagerkörper wird vorteilhaft gegen die Drehrichtung des zu lagernden Körpers bzw. der Rotorwelle in den Stützkörper gedreht und durch das Fixierelement bzw. den oder die Stifte in einer optimierten Winkelposition gehalten. Die Winkelposition bzw. die optimierte Winkelposi¬ tion ist hierbei von Anwendungsfall zu Anwendungsfall unter¬ schiedlich und kann entsprechend dem jeweiligen Anwendungsfall berechnet werden.The slide bearing or the bearing body is advantageously rotated against the direction of rotation of the body to be stored or the rotor shaft in the support body and held by the fixing or the or the pins in an optimized angular position. The angular position or the angle optimized Posi ¬ tion is in this case of application to application under ¬ differently and can be calculated according to the respective application.
Damit wird ein Gleitlager zur Verfügung gestellt, welches bei höchster Tragfähigkeit auch bei hohen Umfangsgeschwindigkei¬ ten eine hohe Stabilität im weiten Lastbereich bzw. sehr gute rotordynamische Eigenschaften aufweist. Zudem weist das er¬ findungsgemäße Gleitlager geringe Reibleistung bzw. Verluste auf und kennzeichnet sich durch Servicefreundlichkeit auf¬ grund der Schalenbauweise. Insbesondere die merkliche Redu¬ zierung der Reibleistung wird durch den Innenringkanal in der unbelasteten Halbschale erreicht. Besonders vorteilhaft ist, dass das Gleitlager durch den modularen Aufbau bei den existierenden Lagergehäusen bei vorhandenen Einbaubedingungen eingesetzt werden kann, wobei eine sehr hohe Störfallsicherheit vorliegt. Das erfindungsgemäße Gleitlager ist in Dampf- turbinen, Generatoren und/oder z.B. Gasturbinen einsetzbar.For a plain bearing is provided, which even at high Umfangsgeschwindigkei ¬ th has a high stability in a wide load range and very good rotor dynamic performance with maximum load capacity. In addition, the invention he ¬ contemporary plain bearings or low frictional energy losses and is characterized by ease of service to ¬ due to the shell construction. In particular, the noticeable Redu ¬ cation of the friction power is achieved by the inner ring channel in the unloaded half shell. It is particularly advantageous that the slide bearing can be used by the modular design of the existing bearing housings in existing installation conditions, with a very high accident safety is present. The sliding bearing according to the invention can be used in steam turbines, generators and / or, for example, gas turbines.
Weitere vorteilhafte Ausgestaltungen sind in den Unteransprü¬ chen und der folgenden Figurenbeschreibungen offenbart. Es zeigen :Further advantageous embodiments are disclosed in the Unteransprü ¬ chen and the following description of the figures. Show it :
Fig. 1 ein Gleitlager in einem Querschnitt,1 is a plain bearing in a cross section,
Fig. 2 das Gleitlager aus Fig. 1 in einem Längsschnitt, undFig. 2 shows the slide bearing of FIG. 1 in a longitudinal section, and
Fig. 3 eine Grafik, bei der die (gerechnete) maximaleFig. 3 is a graph in which the (calculated) maximum
Schmierfilmtemperatur über der spezifischen Lagerlast aufgetragen ist.Lubricating film temperature is plotted against the specific bearing load.
In den unterschiedlichen Figuren sind gleiche Teile stets mit denselben Bezugszeichen versehen, so dass diese in der Regel auch nur einmal beschrieben werden.In the different figures, the same parts are always provided with the same reference numerals, so that these are usually described only once.
Figur 1 zeigt ein Gleitlager 1, das in dem dargestellten Ausführungsbeispiel als Radialgleitlager ausgeführt ist. Das Gleitlager 1 weist einen Lagerkörper 2 auf, in dem ein zu lagernder Körper 3, der im Folgenden als Rotorwelle 3 bezeichnet wird, gelagert ist. Der Lagerkörper 2 ist von einem Stützkörper 4 umgeben, der im Folgenden als Gehäuse 4 bezeichnet wird.Figure 1 shows a plain bearing 1, which is designed in the illustrated embodiment as a radial sliding bearing. The sliding bearing 1 has a bearing body 2, in which a body 3 to be supported, which is referred to below as the rotor shaft 3, is mounted. The bearing body 2 is surrounded by a support body 4, which is referred to below as the housing 4.
Das Gehäuse 4 weist eine Horizontale 6 auf, wobei als Hori¬ zontale 6 die Richtung der Lagerteilfuge bei geteilten Lagern bezeichnet wird.The housing 4 has a horizontal 6, wherein as Hori ¬ zontale 6, the direction of the Lagerteilfuge is referred to in shared bearings.
Der Lagerkörper 2 ist als Mehrflächenlager mit seiner Teilfuge 7 bezogen auf die Horizontale 6 winklig angeordnet. In dem Stützkörper 4 bzw. in dem Gehäuse 4 ist eine einseitig angeordnete Bohrung 8 eingebracht. Diese ist in dem in Figur 1 dargestellten Ausführungsbeispiel auf der linken Zeichnungsebene angeordnet, wobei die Bohrung 8 von der gedachten Horizontalen 6 halbiert wird.The bearing body 2 is arranged as a multi-surface bearing with its parting line 7 relative to the horizontal 6 at an angle. In the support body 4 and in the housing 4 a unilaterally arranged bore 8 is introduced. This is arranged in the embodiment shown in Figure 1 on the left plane of the drawing, wherein the bore 8 is bisected by the imaginary horizontal 6.
In der Bohrung 8 ist ein Fixierelement 9 angeordnet, so dass der Lagerkörper 2 in seiner winkligen Position fixierbar ist. Das Fixierelement 9 ist beispielsweise als Stift ausgeführt, der in eine entsprechende Aufnahme des Lagerkörpers 2 ein¬ greift, so dass dieser hinreichend drehsicher fixiert ist. Der Figur 2 sind zwei Hochdruckverschraubungen 25 entnehmbar, welche die Ölzuführung unter hohem Druck in hydrostatische Taschen 29 für die Anhebung der Rotorwelle ermöglichen.In the bore 8, a fixing element 9 is arranged, so that the bearing body 2 is fixable in its angular position. The fixing element 9 is embodied as a pin which engages in a corresponding receptacle of the bearing body 2 is a ¬ so that it is sufficiently fixed against rotation. 2, two high-pressure fittings 25 can be removed, which allow the oil supply under high pressure in the hydrostatic pockets 29 for raising the rotor shaft.
Der Lagerkörper 2 ist in dem dargestellten Ausführungsbeispiel aus zwei Halbschalen 11, 12 zusammengesetzt, wobei die Lagerschale 11 im Folgenden als belastete Lagerschale 11 und die Lagerschale 12 im Folgenden als unbelastete Lagerschale 12 bezeichnet wird.The bearing body 2 is composed in the illustrated embodiment of two half-shells 11, 12, wherein the bearing shell 11 is hereinafter referred to as loaded bearing shell 11 and the bearing shell 12 hereinafter referred to as unloaded bearing shell 12.
In der belasteten Lagerschale 11 sind drei Außenkanäle, 13, 14, 16 (Figur 2) angeordnet, die zum Gehäuse 4 hin geöffnet sind. Ein in Figur 2 dargestellter erster Kanal 13 ist in Axialrichtung gesehen jeweils zu dem benachbarten zweiten Kanal 14 und dritten Kanal 16 beabstandet, wobei der erste Kanal 13 zwischen dem zweiten und dem dritten Kanal 14 bzw. 16 angeordnet ist.In the loaded bearing shell 11, three outer channels, 13, 14, 16 (Figure 2) are arranged, which are open to the housing 4 out. A shown in Figure 2 first channel 13 is seen in the axial direction in each case to the adjacent second channel 14 and third channel 16 spaced, wherein the first channel 13 between the second and the third channel 14 and 16 is arranged.
In Figur 1 ist aufgrund des gewählten Querschnittes lediglich der erste Kanal 13 dargestellt. Der erste Kanal 13 ist in der Wandung 17 der belasteten Lagerschale 11 eingebracht und er¬ streckt sich in Drehrichtung 18 des zu lagernden Körpers 3 bzw. der Rotorwelle 3 etwas über die Teilfuge 7 hinaus in die unbelastete Lagerschale 12.In Figure 1, only the first channel 13 is shown due to the selected cross-section. The first channel 13 is introduced into the wall 17 of the loaded bearing shell 11 and it ¬ extends in the rotational direction 18 of the body 3 to be stored or the rotor shaft 3 about the parting line 7 in addition, the unloaded bearing shell 12th
An den in Umfangsrichtung gesehen gegenüberliegenden Enden des ersten Kanals 13 sind Lagertaschen 19 bzw. 21 angeordnet, wobei die Lagertasche 19 in der belasteten Lagerschale 11 und die Lagertasche 21 in der unbelasteten Lagerschale 12 ange¬ ordnet ist.At the opposite ends of the first channel 13 seen in the circumferential direction bearing pockets 19 and 21 are arranged, wherein the bearing pocket 19 in the loaded bearing shell 11 and the bearing pocket 21 in the unloaded bearing shell 12 is arranged ¬ .
Der zweite Kanal 14 und der dritte Kanal 16 sind entsprechend zum ersten Kanal 13 ausgeführt.The second channel 14 and the third channel 16 are executed corresponding to the first channel 13.
Im Bereich des ersten Kanals 13 bzw. des zweiten und dritten Kanals 14 bzw. 16 sind in der Wandung 17 Längsbohrungen bzw. Axialbohrungen 22 eingebracht, welche die drei Kanäle 13, 14 und 16 durchdringen.In the region of the first channel 13 and of the second and third channels 14 and 16, longitudinal bores or axial bores 22 are introduced into the wall 17 and penetrate the three channels 13, 14 and 16.
In den in Umfangsrichtung gesehen jeweils endseitig in den Kanälen 13, 14 bzw. 16 angeordneten Lagertaschen 19 bzw. 21 sind Einspritzelemente 23, 24 vorzugsweise Düsen, angeordnet, die in bevorzugter Ausgestaltung zum einen flüssiges Schmiermittel bzw. Schmieröl senkrecht (Einspritzelement 23) auf den zu lagernden Körper 3 bzw. auf die Rotorwelle 3 und zum ande¬ ren schräg (Einspritzelement 24) in einen Austrittsspalt 26 der belasteten Halbschale 11 bzw. der unbelasteten Halbschale 12 spritzen. Dabei sind nur die senkrecht gerichteten Einspritzelemente 23 bzw. Düsen in der Lagertasche 21 nicht ak¬ tiv .In the circumferentially each end in the channels 13, 14 and 16 arranged bearing pockets 19 and 21 are injection elements 23, preferably nozzles 24, arranged in a preferred embodiment for a liquid lubricant or lubricating oil vertically (injection element 23) on the to be stored body 3 or on the rotor shaft 3 and the other ¬ ren obliquely (injector 24) into an outlet gap 26 of the loaded half shell 11 and the unloaded half shell 12 inject. Here, not only the perpendicular ak ¬ tiv directed injection nozzle elements 23 or in the bearing pocket 21st
Bei dem in Figur 1 dargestellten Ausführungsbeispiel ist der Lagerkörper 2 mit seiner Teilfuge 7 entgegen der Drehrichtung 18 aus der Horizontalen 6 verschoben. Somit ist der Lagerkörper 2 mit seiner Teilfuge 7 bezogen auf die Horizontale 6 winklig angeordnet, wobei ein Winkel α von Anwendungsfall zu Anwendungsfall einen unterschiedlichen Betrag aufweisen kann und zu jedem speziellen Anwendungsfall gesondert determinier¬ bar bzw. berechenbar ist.In the embodiment shown in Figure 1, the bearing body 2 is moved with its parting line 7 against the direction of rotation 18 of the horizontal 6. Thus, the bearing body 2 is arranged with its parting line 7 relative to the horizontal 6 at an angle, wherein an angle α from application to application may have a different amount and for each specific application separately determinier ¬ bar or calculable.
Durch die einseitig angeordnete Bohrung 8 in dem Stützkörper 4 bzw. in dem Gehäuse 4 wird frisches Schmiermittel bzw. Öl zugeführt und gelangt zunächst in den halbumschlossenen ers¬ ten Kanal 13 der belasteten Halbschale 11 und anschließend in die Einspritzelemente 23 bzw. 24. Diese sind in den Lagerta- sehen 19 bzw. 21 jeweils in Mehrzahl zweireihig angeordnet und spritzen die geforderte Ölmenge senkrecht auf die Rotor¬ welle 3 und schräg in den Austrittsspalt 26 der belasteten Halbschale 11. Alle Einspritzelemente 23, 24 bzw. Düsen wer- den bevorzugt in den Lagertaschen 19 bzw. 21 eingeschraubt, wodurch eine Dosierung des Öldurchsatzes im Zulauf möglich ist .The single-disposed bore 8 in the support body 4 and in the housing 4 fresh lubricant or oil is supplied, and first passes into the semi-enclosed ers ¬ th channel 13 of the loaded half-shell 11 and then into the injector elements 23 and 24. These are in the warehouse see 19 and 21 respectively arranged in a plurality of double rows and inject the required amount of oil perpendicular to the rotor ¬ shaft 3 and obliquely into the exit slit 26 of the loaded half-shell 11. All injection elements 23, 24 or nozzles are preferably in the bearing pockets 19 and 21, which allows metering of the oil throughput in the inlet.
Etwa mittig ist in Figur 2 ein Innenringkanal 31 angeordnet, der in Breitenrichtung geschlossen ist, und sich über den ganzen Umfang der unbelasteten Halbschale 12 erstreckt.Approximately centrally in Figure 2, an inner ring channel 31 is arranged, which is closed in the width direction, and extends over the entire circumference of the unloaded half-shell 12.
In Figur 3 ist beispielhaft die (gerechnete) maximale Schmierfilmtemperatur (Tmax[°C]) über die spezifische Lager- last (Pquer [N/mm2]) gezeigt. Hierbei ist eine Temperatur/Last Kennlinie eines konventionellen Gleitlagers (Bezugszeichen 27) im Vergleich zu einer Temperatur/Last Linie (Bezugszei¬ chen 28) des erfindungsgemäß ausgeführten Gleitlagers, bzw. Radialgleitlagers mit hydrodynamischer Schmierung darge- stellt. Deutlich entnehmbar ist der Grafik aus Figur 3, dass das erfindungsgemäße Gleitlager bei gleicher Last erheblich niedrigeren Temperaturen ausgesetzt ist. FIG. 3 shows, by way of example, the (calculated) maximum lubricant film temperature (T max [° C]) over the specific bearing load (Pquer [N / mm 2 ]). In this case, a temperature / load characteristic curve of a conventional slide bearing (reference numeral 27) in comparison to a temperature / load line (Bezugszei ¬ chen 28) of the inventively designed plain bearing, or radial plain bearing with hydrodynamic lubrication is shown. It can be clearly seen from the graph of Figure 3 that the sliding bearing according to the invention is exposed to significantly lower temperatures at the same load.

Claims

Patentansprüche claims
1. Gleitlager, das einen Lagerkörper (2) aufweist, in dem ein zu lagernder Körper (3) gelagert ist, wobei der Lagerkörper (2) von einem Stützkörper (4) umfasst ist, dadurch gekennzeichnet, dass der Lagerkörper (2) als Mehrflächenlager mit seiner Teilfuge (7) bezogen auf eine Horizontale (6) winklig angeord¬ net ist.1. sliding bearing having a bearing body (2) in which a body to be stored (3) is mounted, wherein the bearing body (2) by a support body (4) comprises, characterized in that the bearing body (2) as a multi-surface bearing with its parting line (7) with respect to a horizontal (6) angeord ¬ net is angeord ¬ net.
2. Gleitlager nach Anspruch 1, dadurch gekennzeichnet, dass der Lagerkörper (2) aus zwei Halbschalen (11, 12) gebildet ist, deren Teilfuge (7) bezogen auf die Horizontale (6) winklig angeordnet ist.2. plain bearing according to claim 1, characterized in that the bearing body (2) consists of two half-shells (11, 12) is formed, the parting line (7) relative to the horizontal (6) is arranged at an angle.
3. Gleitlager nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Teilfuge (7) im Querschnitt gesehen entgegen einer Drehrichtung (18) des zu lagernden Körpers (3) versetzt ist .3. plain bearing according to claim 1 or 2, characterized in that the parting line (7) seen in cross section against a direction of rotation (18) of the body to be stored (3) is offset.
4. Gleitlager nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Lagerkörper (2) in seiner bezogen auf die Horizontale (6) angeordneten Winkelposition fixierbar ist. 4. plain bearing according to one of the preceding claims, characterized in that the bearing body (2) in its relative to the horizontal (6) arranged angular position is fixable.
5. Gleitlager, das einen Lagerkörper (2) aufweist, in dem ein zu lagernder Körper (3) gelagert ist, wobei der Lagerkörper (2) von einem Stützkörper (4) umfasst ist, insbesondere nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Lagerkörper (2) in seiner Wandung (17) in Umfangsrich- tung gesehen einen zumindest abschnittsweise angeordneten ersten Kanal (13) aufweist, wobei in der Wandung (17) zumindest eine Axialbohrung (22) angeordnet ist, die den ersten Kanal (13) durchdringt.5. plain bearing having a bearing body (2) in which a body to be stored (3) is mounted, wherein the bearing body (2) by a support body (4) is included, in particular according to one of the preceding claims, characterized in that the bearing body (2) has an at least partially arranged first channel (13) in its wall (17) in the circumferential direction, wherein at least one axial bore (22) is arranged in the wall (17), which defines the first channel (13). penetrates.
6. Gleitlager nach Anspruch 5, dadurch gekennzeichnet, dass der Lagerkörper (2) in Axialrichtung gesehen zumindest einen zum ersten Kanal (13) beabstandeten zweiten Kanal6. plain bearing according to claim 5, characterized in that the bearing body (2) seen in the axial direction at least one of the first channel (13) spaced second channel
(14) aufweist, wobei in der Wandung (17) zumindest eine Axialbohrung (22' angeordnet ist, die den ersten und zweiten Kanal (13, 14) durchdringt .(14), wherein in the wall (17) at least one axial bore (22 'is arranged, which penetrates the first and second channels (13, 14).
7. Gleitlager nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass der erste Kanal (13) in einer belasteten Lagerschale (11) des Lagerkörpers (2) eingebracht ist und zum Stützkörper (4) hin geöffnet ist, wobei der erste Kanal (13) in Umfangsrichtung gesehen halbkreisförmig in der Wandung (17) eingebracht ist, so dass quasi eine halbkreisförmige Nut gebildet ist, die sich etwas in eine unbelastete Lagerschale (12) erstreckt. 7. sliding bearing according to claim 5 or 6, characterized in that the first channel (13) in a loaded bearing shell (11) of the bearing body (2) is introduced and to the support body (4) is opened out, wherein the first channel (13) As seen in the circumferential direction is introduced semicircular in the wall (17), so that virtually a semicircular groove is formed, which extends somewhat into an unloaded bearing shell (12).
Gleitlager nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass der erste Kanal (13) an seiner in Umfangsrichtung gesehen gegenüberliegenden Enden Lagertaschen (19, 21) aufweist, in denen zumindest ein Einspritzelement (23, 24) zum Einsprit¬ zen flüssiger Schmiermittels zum zu lagernden Körper (3) angeordnet ist. Sliding bearing according to one of claims 5 to 7, characterized in that the first channel (13) seen at its opposite ends in the circumferential direction bearing pockets (19, 21), in which at least one injection element (23, 24) for injection ¬ zen liquid lubricant is arranged to be stored body (3).
9. Gleitlager nach einem der Ansprüche 5 bis 8, dadurch gekennzeichnet, dass der Lagerkörper (2) als Mehrflächenlager aus zwei Halbschalen (11, 12) gebildet ist, wobei der erste Kanal (13) in der belasteten Halbschale (11) angeordnet ist, und wobei eine Teilfuge (7) bezogen auf eine Horizontale (6) winklig angeordnet ist, so dass eine der Lagertaschen (19) im Querschnitt gesehen oberhalb der Horizontalen (6) und die andere Lagertasche (21) unterhalb der Horizontalen (6) angeordnet ist.9. plain bearing according to one of claims 5 to 8, characterized in that the bearing body (2) as a multi-surface bearing of two half-shells (11, 12) is formed, wherein the first channel (13) in the loaded half-shell (11) is arranged and wherein a parting line (7) with respect to a horizontal (6) is arranged at an angle, so that one of the bearing pockets (19) seen in cross-section above the horizontal (6) and the other bearing pocket (21) below the horizontal (6) is arranged ,
10. Gleitlager, das einen Lagerkörper (2) aufweist, in dem ein zu lagernder Körper (3) gelagert ist, wobei der Lagerkörper (2) von einem Stützkörper (4) umfasst ist, insbesondere nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Lagerkörper (2) an seinen in Umfangsrichtung gesehen gegenüberliegenden Lagertaschen (19, 21) jeweils mehrreihig angeordnete Einspritzelemente (23, 24) aufweist, die flüs¬ siges Schmiermittel zum einen auf den zu lagernden Körper (3) und zum anderen in einen Austrittsspalt (26) spritzen. 10. Sliding bearing having a bearing body (2) in which a body to be stored (3) is mounted, wherein the bearing body (2) by a support body (4) is included, in particular according to one of the preceding claims, characterized in that the bearing body (2) at its circumferentially opposite bearing pockets (19, 21) each more multi-row injection elements arranged (23, 24), the liq ¬ siges lubricant on the one to the body to be stored (3) and the other in an outlet gap ( 26) splash.
11. Gleitlager nach Anspruch 10, dadurch gekennzeichnet, dass die Einspritzelemente (23, 24) in den jeweiligen Lagerta¬ schen (19, 21) in Mehrzahl zweireihig angeordnet sind, wobei die Einspritzelemente (23, 24) als Düsen in den Lagertaschen (19, 21) eingeschraubt sind.11. plain bearing according to claim 10, characterized in that the injection elements (23, 24) in the respective Lagerta ¬ rule (19, 21) are arranged in a plurality of double rows, wherein the injection elements (23, 24) as nozzles in the bearing pockets (19 , 21) are screwed.
12. Gleitlager nach Anspruch 10 oder 11, dadurch gekennzeichnet, dass das Einspritzelement (23) derart angeordnet ist, dass dieses flüssiges Schmiermittel senkrecht auf den zu lagernden Körper (3) spritzt, wobei das Einspritzelement (24) derart angeordnet ist, dass dieses flüssiges Schmiermittel schräg in einen Aus¬ trittspalt (26) der belasteten Halbschale (11) spritzt, wobei hier bevorzugt nur die schräg gerichteten Einspritzelemente (24) in einer der Lagertaschen aktiv sind, wobei dies bevorzugterweise die Lagertasche (21) ist, wel- che im fixierten Zustand des Lagerkörpers (2) im Quer¬ schnitt gesehen unterhalb der Horizontalen (6) angeordnet ist . 12. plain bearing according to claim 10 or 11, characterized in that the injection element (23) is arranged such that this liquid lubricant perpendicular to the body to be stored (3) injected, wherein the injection element (24) is arranged such that this liquid Lubricant obliquely into a Aus ¬ trough gap (26) of the loaded half-shell (11) injected, in which case only the obliquely directed injection elements (24) in one of the bearing pockets are preferably active, this is preferably the bearing pocket (21), which in is arranged seen fixed state of the bearing body (2) in cross-section ¬ below the horizontal (6).
EP07788164A 2006-08-16 2007-08-02 Hydrodynamic radial plain bearing having a maximum bearing capacity for large turbo-generators Withdrawn EP2052165A2 (en)

Priority Applications (3)

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EP07788164A EP2052165A2 (en) 2006-08-16 2007-08-02 Hydrodynamic radial plain bearing having a maximum bearing capacity for large turbo-generators
EP14002235.1A EP2787226B1 (en) 2006-08-16 2007-08-02 Hydrodynamic journal bearing for large turbo-generators
EP14002234.4A EP2787228A1 (en) 2006-08-16 2007-08-02 Hydrodynamic journal bearing for large turbo-generators

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP06017047A EP1890045A1 (en) 2006-08-16 2006-08-16 hydrodynamic journal bearings for large turbo sets
PCT/EP2007/057999 WO2008019947A2 (en) 2006-08-16 2007-08-02 Hydrodynamic radial plain bearing for large turbo-generators
EP07788164A EP2052165A2 (en) 2006-08-16 2007-08-02 Hydrodynamic radial plain bearing having a maximum bearing capacity for large turbo-generators

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EP14002234.4A Division EP2787228A1 (en) 2006-08-16 2007-08-02 Hydrodynamic journal bearing for large turbo-generators
EP14002235.1A Division EP2787226B1 (en) 2006-08-16 2007-08-02 Hydrodynamic journal bearing for large turbo-generators

Publications (1)

Publication Number Publication Date
EP2052165A2 true EP2052165A2 (en) 2009-04-29

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EP14002234.4A Withdrawn EP2787228A1 (en) 2006-08-16 2007-08-02 Hydrodynamic journal bearing for large turbo-generators
EP14002235.1A Active EP2787226B1 (en) 2006-08-16 2007-08-02 Hydrodynamic journal bearing for large turbo-generators
EP07788164A Withdrawn EP2052165A2 (en) 2006-08-16 2007-08-02 Hydrodynamic radial plain bearing having a maximum bearing capacity for large turbo-generators

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EP14002235.1A Active EP2787226B1 (en) 2006-08-16 2007-08-02 Hydrodynamic journal bearing for large turbo-generators

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US (3) US20100002967A1 (en)
EP (4) EP1890045A1 (en)
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Also Published As

Publication number Publication date
US20120183245A1 (en) 2012-07-19
US8851754B2 (en) 2014-10-07
EP2787226A1 (en) 2014-10-08
US20100002967A1 (en) 2010-01-07
CN101563547B (en) 2012-11-14
WO2008019947A2 (en) 2008-02-21
CN101563547A (en) 2009-10-21
EP2787226B1 (en) 2020-12-09
EP2787228A1 (en) 2014-10-08
WO2008019947A3 (en) 2009-05-22
US8876387B2 (en) 2014-11-04
JP2010500520A (en) 2010-01-07
JP5052611B2 (en) 2012-10-17
EP1890045A1 (en) 2008-02-20
US20120183244A1 (en) 2012-07-19

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