EP1910692A1 - Turbomachine - Google Patents

Turbomachine

Info

Publication number
EP1910692A1
EP1910692A1 EP06777930A EP06777930A EP1910692A1 EP 1910692 A1 EP1910692 A1 EP 1910692A1 EP 06777930 A EP06777930 A EP 06777930A EP 06777930 A EP06777930 A EP 06777930A EP 1910692 A1 EP1910692 A1 EP 1910692A1
Authority
EP
European Patent Office
Prior art keywords
bearing
shaft
shell
turbomachine
bearing 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Withdrawn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
EP06777930A
Other languages
German (de)
French (fr)
Inventor
Roland Blumenthal
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.)
Leybold GmbH
Original Assignee
Oerlikon Leybold Vacuum GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Oerlikon Leybold Vacuum GmbH filed Critical Oerlikon Leybold Vacuum GmbH
Publication of EP1910692A1 publication Critical patent/EP1910692A1/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Withdrawn legal-status Critical Current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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • 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
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
    • F04D19/048—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps comprising magnetic 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/02—Sliding-contact 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
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0442—Active magnetic bearings with devices affected by abnormal, undesired or non-standard conditions such as shock-load, power outage, start-up or touchdown
    • 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
    • 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
    • F16C39/02—Relieving load on bearings using mechanical 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
    • F16C39/00—Relieving load on bearings
    • F16C39/04—Relieving load on bearings using hydraulic or pneumatic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/50—Bearings
    • F05D2240/51—Magnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/50—Bearings
    • F05D2240/52—Axial thrust 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
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps
    • F16C2360/45—Turbo-molecular pumps

Definitions

  • the invention relates to a turbomachine with a magnetic bearing and a bearing assigned to the magnetic bearing.
  • Turbopumps such as turbomolecular pumps and turbo blowers, rotate at very high speeds of up to 80,000 revolutions per minute.
  • magnetic bearings are used, which are particularly suitable for high speeds.
  • mechanical backup bearings are provided which prevent should ensure that the pump rotor touches the pump stator in case of failure of the magnetic bearing and thereby destroyed.
  • rolling bearings As a bearing for turbomolecular pumps rolling bearings are used, which in contrast to plain bearings have inherently lower wear.
  • a disadvantage of rolling bearings is that they are relatively expensive and can make up to 10% of the total cost of turbomolecular pumps and turbo blowers.
  • the object of the invention is in contrast to provide a magnetic bearing turbomachine with a cheap fishing camp.
  • the fishing camp is not designed as a rolling bearing, but as a sliding bearing.
  • an intermediate bush is arranged, which is spaced from both the bearing shell and the bearing shaft by a circular gap.
  • the intermediate bush is rotatable both to the bearing shaft and to the bearing shell.
  • Trained as a plain bearing fishing camp according to claim 1 is effectively divided into two part bearings, namely a partial bearing, which is formed by the bearing shaft and the intermediate sleeve inside and a second part bearing, which is formed by the intermediate sleeve outer side and the bearing shell.
  • the outer circular gap between the intermediate bush and the bearing shell is as small as possible, but so large that the intermediate bush remains rotatable relative to the bearing shell under all circumstances.
  • the intermediate bushing is first accelerated by the bearing shaft.
  • the bearing bush is braked by the stator bearing shell.
  • a balance of the rotational speeds of the intermediate bush and the bearing shaft sets.
  • the speed difference of the intermediate bushing to the bearing shell and to the bearing shaft is approximately equal. Due to the rotatability of the intermediate bush, the braking work is distributed over two pairs of sliding surfaces so that the resulting wear is at least halved. Furthermore, the braking performance of the entire sliding bearing is reduced, so that the heat generation and the risk of heat build-up is reduced.
  • the surfaces of the surface pairs are designed so that the braking performance and duration are similar to rolling bearings. As a result, the heat development is similar and so low that no overheating occurs.
  • suspension elements are arranged between the intermediate bush and the bearing shell, which hold the intermediate bush spaced from the bearing shell.
  • the spring elements fix the intermediate bush in a defined position within the bearing shell. Furthermore, they dampen radial shocks of the bearing shaft when it strikes the intermediate bushing.
  • the suspension elements can also
  • the radial forces that are transmitted in the application of the bearing shaft to the intermediate sleeve are very high. Furthermore, the contact surface between the bearing shaft and the intermediate bush or between the intermediate bush and the bearing shell is not flat, but at most linear or even punctiform, which is due to the possible inclination of the bearing shaft to the intermediate bushing and the intermediate bush to the bearing shell. As a result, very high surface loads are generated. By providing suspension elements between the bearing shell and the intermediate bush, the radial impact movements of the bearing shaft are intercepted so that the surface forces occurring are considerably reduced. This also reduces the wear of the sliding bearing as a whole.
  • the gap height of the outer gap between the bearing shell and the intermediate sleeve is substantially less than the gap height of the inner gap between the bearing shaft and the intermediate sleeve.
  • the inner gap has the same function and therefore the same gap height as the bearing gap in conventional backup bearings.
  • the inner gap represents the working area of the magnetic bearing.
  • the outer additional gap allows the rotational relative movement between the intermediate sleeve and the bearing shell. This does not require a particularly high gap.
  • the gap between the pump rotor and stator can be kept low at a small gap height of said outer gap.
  • the intermediate bush is integrally formed and made of metal.
  • an unchanged inexpensive solution can be provided for a sliding-type bearing, in contrast to expensive ceramic plain bearings of conventional design.
  • FIG. 1 shows a turbomolecular pump designed as a turbomachine with two
  • FIG. 2 shows a fishing camp of the turbomachine of FIG. 1 in an enlarged
  • FIGS. 1 and 2 show a high-speed turbomachine 10 designed as a turbomolecular pump, which has a rotor 12 and a stator 14.
  • the rotor 12 consists essentially of a shaft 16 with a pump rotor 18, wherein a shaft portion forms a bearing shaft 20 in the region of the shaft bearing.
  • the bearing shaft 20 forms the rotor-side part of two magnetic bearings 22,23 and the axially between the two magnetic bearings 22,23 arranged plain bearings 26,27, which serve as a backup bearing for the two magnetic bearings 22,23.
  • the plain bearings 26,27 are each formed by the bearing shaft 20, a stator-side bearing shell 28 and a radially intermediate between the bearing shell 28 and the bearing shaft 20 cylindrical intermediate sleeve 30.
  • the bearing shell 28, the intermediate sleeve 30 and the bearing shaft 20 are made of metal.
  • the intermediate sleeve 30 is mounted with metallic suspension elements 32 in a fixed relationship to the bearing shell 28.
  • the intermediate sleeve 30 is rotatably supported both to the bearing shell 28 and to the bearing shaft 20. Between the intermediate sleeve 30 and the bearing shaft 20, a circular cylindrical gap 33 is present, which has a gap height of about 0.2 mm, which allows the required for the magnetic bearing in normal operation clearance of the bearing shaft 20.
  • the outer gap 34 between the intermediate sleeve 30 and the bearing cup 28 has a smaller radial gap height of about 0.02 mm.
  • the outer gap 34 only has to be so large that the rotatability of the intermediate bushing 30 with respect to the bearing shell 28 is barely guaranteed under all thermal conditions.
  • the plain bearing 26 shown has, in contrast to conventional plain bearings on two sliding surface pairs, to which the entire braking work and the entire bearing wear are distributed.
  • the loads in the form of heat, shock and abrasion can be reduced so that the use an inexpensive plain bearing is possible as a catch warehouse in a fast-turning gas-promoting turbomachine.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Non-Positive Displacement Air Blowers (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

Disclosed is a high-speed turbomachine comprising a magnetic bearing (22, 23) and a retainer bearing for mounting the rotor. The retainer bearing is embodied as a sliding bearing (26, 27) and encompasses a bearing shell (28) at the stator end, a bearing shaft (20) at the rotor end, and an intermediate bush (30) between the bearing shell (28) and the bearing shaft (20). Said intermediate bush (30) is spaced apart from both the bearing shaft (20) and the bearing shell (28) by means of a circular gap (33, 34). The intermediate bush (30) is rotatable relative to the bearing shell (28) and the bearing shaft (20). As a result of this design, the sliding bearing (26) is provided with two pairs of sliding surfaces, onto which all occurring dynamic forces are distributed such that wear is significantly reduced, thus allowing sliding bearings to be used as retainer bearings in a magnetically mounted high-speed turbomachine.

Description

Unser Zeichen : 061434WO/Sg/rpOur sign: 061434WO / Sg / rp
Turbomaschineturbomachinery
Die Erfindung bezieht sich auf eine Turbomaschine mit einem Magnetlager und einem dem Magnetlager zugeordneten Fanglager.The invention relates to a turbomachine with a magnetic bearing and a bearing assigned to the magnetic bearing.
Turbopumpen, beispielsweise Turbomolekularpumpen und Turbogebläse, drehen mit sehr hohen Drehzahlen von bis zu 80.000 Umdrehungen pro Minute. Für die Lagerung des Rotors werden daher gerne Magnetlager verwendet, die für hohe Drehzahlen besonders geeignet sind. Für den Fall eines Versagens des bzw. der Magnetlager sind sogenannte mechanische Fanglager vorgesehen, die verhindern sollen, dass der Pumpenrotor den Pumpenstator bei Ausfall der Magnetlagerung berührt und dadurch zerstört.Turbopumps, such as turbomolecular pumps and turbo blowers, rotate at very high speeds of up to 80,000 revolutions per minute. For the storage of the rotor therefore magnetic bearings are used, which are particularly suitable for high speeds. In the event of failure of the magnetic bearing or so-called mechanical backup bearings are provided which prevent should ensure that the pump rotor touches the pump stator in case of failure of the magnetic bearing and thereby destroyed.
Als Fanglager für Turbomolekularpumpen werden Wälzlager verwendet, die im Gegensatz zu Gleitlagern prinzipbedingt geringeren Verschleiß aufweisen. Nachteilig an Wälzlagern ist jedoch, dass sie relativ teuer sind und bei Turbomolekularpumpen und bei Turbogebläsen bis zu 10 % der Gesamtkosten ausmachen können.As a bearing for turbomolecular pumps rolling bearings are used, which in contrast to plain bearings have inherently lower wear. A disadvantage of rolling bearings, however, is that they are relatively expensive and can make up to 10% of the total cost of turbomolecular pumps and turbo blowers.
Aufgabe der Erfindung ist es demgegenüber, eine magnetgelagerte Turbomaschine mit einem preiswerten Fanglager zu schaffen.The object of the invention is in contrast to provide a magnetic bearing turbomachine with a cheap fishing camp.
Diese Aufgabe wird erfindungsgemäß mit den Merkmalen des Anspruches 1 gelöst.This object is achieved with the features of claim 1.
Bei der erfindungsgemäßen Turbomaschine ist das Fanglager nicht als Wälzlager, sondern als Gleitlager ausgebildet. Zwischen der statorseitigen Lagerschale und der rotorseitigen Lagerwelle des Gleitlagers ist eine Zwischenbuchse angeordnet, die sowohl zu der Lagerschale als auch zu der Lagerwelle durch einen zirkulären Spalt beabstandet ist. Die Zwischenbuchse ist sowohl zu der Lagerwelle als auch zu der Lagerschale drehbar.In the turbomachine according to the invention the fishing camp is not designed as a rolling bearing, but as a sliding bearing. Between the stator-side bearing shell and the rotor-side bearing shaft of the sliding bearing, an intermediate bush is arranged, which is spaced from both the bearing shell and the bearing shaft by a circular gap. The intermediate bush is rotatable both to the bearing shaft and to the bearing shell.
Der Verwendung eines Gleitlagers als Fanglager einer magnetgelagerten schnelldrehenden Turbomaschine standen bisher technische Probleme und Vorurteile entgegen. Im Einsatzfall muss von dem Fanglager ein ganz erheblicher kinetischer Energiebetrag abgebremst werden. Ferner liegt die Geschwindigkeit der Lagerwelle zu Beginn eines Einsatzfalles gegenüber der statorseitigen Lagerschale ggf. sehr hoch, nämlich im Bereich von lOOm/sec. und höher. Zusammen mit einem relativ hohen Trägheitsmoment eines Pumpenrotors einer Turbomaschine ergeben sich Bremsstrecken von 100km und länger. Das zweite Problem resultiert aus den im Bereich der Fanglager auftretenden hohen Radialkräften, die im zweistelligen kN-Bereich liegen können. Beide Umstände zusammen stellen Anforderungen an ein als Gleitlager ausgebildetes Fanglager, die mit herkömmlichen Konstruktionen als unerfüllbar galten.The use of a sliding bearing as a backup bearing a magnetically levitated high-speed turbo engine were so far contrary to technical problems and prejudices. In the application, a very significant amount of kinetic energy must be braked by the safety bearing. Further, the speed of the bearing shaft at the beginning of an application case with respect to the stator bearing shell is possibly very high, namely in the range of lOOm / sec. and higher. Along with a relatively high moment of inertia of a pump rotor of a turbomachine, braking distances of 100km and longer result. The second problem results from the high occurring in the field of fishing camp Radial forces that can be in the double-digit kN range. Both circumstances together make demands on a trained as plain bearings fishing camp, which were considered to be unfulfillable with conventional designs.
Das als Gleitlager ausgebildete Fanglager gemäß Patentanspruch 1 ist gewissermaßen in zwei Teillager unterteilt, nämlich ein Teillager, das von der Lagerwelle und der Zwischenbuchseninnenseite und ein zweites Teillager, das von der Zwischenbuchsenaußenseite und der Lagerschale gebildet wird. Der äußere zirkuläre Spalt zwischen der Zwischenbuchse und der Lagerschale ist möglichst klein, jedoch so groß, dass die Zwischenbuchse unter allen Umständen drehbar gegenüber der Lagerschale bleibt.Trained as a plain bearing fishing camp according to claim 1 is effectively divided into two part bearings, namely a partial bearing, which is formed by the bearing shaft and the intermediate sleeve inside and a second part bearing, which is formed by the intermediate sleeve outer side and the bearing shell. The outer circular gap between the intermediate bush and the bearing shell is as small as possible, but so large that the intermediate bush remains rotatable relative to the bearing shell under all circumstances.
Im Einsatzfall wird zunächst die Zwischenbuchse von der Lagerwelle beschleunigt. Gleichzeitig wird die Lagerbuchse von der statorseitigen Lagerschale gebremst. Schließlich stellt sich ein Gleichgewicht der Drehgeschwindigkeiten der Zwischenbuchse und der Lagerwelle ein. Im Idealfall ist die Geschwindigkeitsdifferenz der Zwischenbuchse zu der Lagerschale und zu der Lagerwelle ungefähr gleich. Durch die Drehbarkeit der Zwischenbuchse wird die Bremsarbeit auf zwei Gleitflächenpaare verteilt, so dass sich der hierdurch bedingte Verschleiß mindestens halbiert. Ferner verringert sich die Bremsleistung des gesamten Gleitlagers, so dass auch die Wärmeentwicklung und die Gefahr eines Wärmestaus reduziert wird. Die Oberflächen der Flächenpaare sind so gestaltet, dass die Bremsleistung und -dauer ähnlich ist wie bei Wälzlagern. Hierdurch ist auch die Wärmeentwicklung ähnlich und so gering, dass keine Überhitzung auftritt.In the application, the intermediate bushing is first accelerated by the bearing shaft. At the same time, the bearing bush is braked by the stator bearing shell. Finally, a balance of the rotational speeds of the intermediate bush and the bearing shaft sets. Ideally, the speed difference of the intermediate bushing to the bearing shell and to the bearing shaft is approximately equal. Due to the rotatability of the intermediate bush, the braking work is distributed over two pairs of sliding surfaces so that the resulting wear is at least halved. Furthermore, the braking performance of the entire sliding bearing is reduced, so that the heat generation and the risk of heat build-up is reduced. The surfaces of the surface pairs are designed so that the braking performance and duration are similar to rolling bearings. As a result, the heat development is similar and so low that no overheating occurs.
Durch die Zwischenbuchse in dem Gleitlager wird die Bremsstrecke pro Gleitflächenpaar auf ungefähr die Hälfte reduziert, wird ferner die Wärmeentwicklung verringert und werden radiale Stöße der Lagerwelle etwas gedämpft. Alle Effekte zusammen erlauben die Verwendung eines Gleitlagers anstelle eines kostspieligen Wälzlagers als Fanglager für ein Magnetlager einer schnelldrehenden gasfördernden Turbomaschine.By the intermediate bushing in the sliding bearing, the braking distance per Gleitflächenpaar is reduced to about half, the heat generation is also reduced and radial shocks of the bearing shaft are somewhat damped. All effects together allow the use of a plain bearing instead of a costly rolling bearing as a backup bearing for a magnetic bearing of a fast-rotating gas-generating turbomachine.
Ein derartig konstruiertes Gleitlager ist erheblich preiswerter herstellbar als ein entsprechendes Wälzlager. Wegen des hohen Kostenanteiles der Fanglager kann dadurch der Gesamtpreis einer entsprechenden Turbomaschine spürbar reduziert werden.Such a constructed slide bearing is considerably cheaper to produce than a corresponding rolling bearing. Because of the high cost share of the fishing camp, the total price of a corresponding turbomachine can be significantly reduced.
Gemäß einer bevorzugten Ausgestaltung sind zwischen der Zwischenbuchse und der Lagerschale Federungselemente angeordnet, die die Zwischenbuchse beabstandet von der Lagerschale halten. Die Federelemente fixieren die Zwischenbuchse in einer definierten Position innerhalb der Lagerschale. Ferner dämpfen sie radiale Stöße der Lagerwelle ab, wenn diese an die Zwischenbuchse schlägt. Die Federungselemente können zusätzlich auchAccording to a preferred embodiment, suspension elements are arranged between the intermediate bush and the bearing shell, which hold the intermediate bush spaced from the bearing shell. The spring elements fix the intermediate bush in a defined position within the bearing shell. Furthermore, they dampen radial shocks of the bearing shaft when it strikes the intermediate bushing. The suspension elements can also
Dämpfungseigenschaften aufweisen.Have damping properties.
Die radialen Kräfte, die im Einsatzfall von der Lagerwelle auf die Zwischenbuchse übertragen werden, sind sehr hoch. Ferner ist die Berührungsfläche zwischen der Lagerwelle und der Zwischenbuchse bzw. zwischen der Zwischenbuchse und der Lagerschale nicht flächig, sondern allenfalls linienförmig oder sogar nur punktförmig, was durch die mögliche Schrägstellung der Lagerwelle zu der Zwischenbuchse und der Zwischenbuchse zu der Lagerschale bedingt ist. Hierdurch werden sehr hohe Flächenlasten erzeugt. Durch Vorsehen von Federungselementen zwischen der Lagerschale und der Zwischenbuchse werden die radialen Stoßbewegungen der Lagerwelle abgefangen, so dass die auftretenden Flächenkräfte erheblich reduziert sind. Auch hierdurch wird der Verschleiß des Gleitlagers insgesamt verringert.The radial forces that are transmitted in the application of the bearing shaft to the intermediate sleeve are very high. Furthermore, the contact surface between the bearing shaft and the intermediate bush or between the intermediate bush and the bearing shell is not flat, but at most linear or even punctiform, which is due to the possible inclination of the bearing shaft to the intermediate bushing and the intermediate bush to the bearing shell. As a result, very high surface loads are generated. By providing suspension elements between the bearing shell and the intermediate bush, the radial impact movements of the bearing shaft are intercepted so that the surface forces occurring are considerably reduced. This also reduces the wear of the sliding bearing as a whole.
Gemäß einer bevorzugten Ausgestaltung ist die Spalthöhe des äußeren Spaltes zwischen der Lagerschale und der Zwischenbuchse wesentlich geringer als die Spalthöhe des inneren Spaltes zwischen der Lagerwelle und der Zwischenbuchse. Der innere Spalt hat die gleiche Funktion und daher auch die gleiche Spalthöhe wie der Lagerspalt bei herkömmlichen Fanglagern. Der innere Spalt stellt den Arbeitsbereich der Magnetlagerung dar.According to a preferred embodiment, the gap height of the outer gap between the bearing shell and the intermediate sleeve is substantially less than the gap height of the inner gap between the bearing shaft and the intermediate sleeve. The inner gap has the same function and therefore the same gap height as the bearing gap in conventional backup bearings. The inner gap represents the working area of the magnetic bearing.
Der äußere zusätzliche Spalt ermöglicht die rotatorische Relativbewegung zwischen der Zwischenbuchse und der Lagerschale. Hierfür ist kein besonders hoher Spalt erforderlich. Je geringer die Spalthöhe des äußeren Spaltes ist, desto weniger kann die Zwischenbuchse im Verhältnis zur Lagerschale kippen. Hierdurch wiederum werden möglichst kleine Aufschlagwinkel zwischen der Lagerschale und der Zwischenbuchse sowie zwischen der Zwischenbuchse und der Lagerwelle sichergestellt. Ferner kann bei kleiner Spalthöhe des genannten äußeren Spaltes auch das Spaltmaß zwischen Pumpenrotor und -Stator gering gehalten werden.The outer additional gap allows the rotational relative movement between the intermediate sleeve and the bearing shell. This does not require a particularly high gap. The smaller the gap height of the outer gap, the less the intermediate bushing can tilt in relation to the bearing shell. This in turn ensures the smallest possible impact angle between the bearing shell and the intermediate bushing and between the intermediate bushing and the bearing shaft. Furthermore, the gap between the pump rotor and stator can be kept low at a small gap height of said outer gap.
Vorzugsweise ist die Zwischenbuchse einstückig ausgebildet und aus Metall bestehend. Auf diese Weise kann eine unverändert preiswerte Lösung für ein Gleit-Fanglager zur Verfügung gestellt werden, im Gegensatz zu kostspieligen keramischen Gleitlagern herkömmlicher Bauart.Preferably, the intermediate bush is integrally formed and made of metal. In this way, an unchanged inexpensive solution can be provided for a sliding-type bearing, in contrast to expensive ceramic plain bearings of conventional design.
Im Folgenden wird unter Bezugnahme auf die Zeichnung ein Ausführungsbeispiel der Erfindung näher erläutert.In the following an embodiment of the invention will be explained in more detail with reference to the drawing.
Es zeigen :Show it :
Figur 1 eine als Turbomolekularpumpe ausgebildete Turbomaschine mit zwei1 shows a turbomolecular pump designed as a turbomachine with two
Magnetlagern und einem Fanglager, undMagnetic bearings and a fishing camp, and
Figur 2 ein Fanglager der Turbomaschine der Fig. 1 in vergrößerter2 shows a fishing camp of the turbomachine of FIG. 1 in an enlarged
Darstellung. In den Figuren 1 und 2 ist eine als Turbomolekularpumpe ausgebildete schnelldrehende Turbomaschine 10 dargestellt, die einen Rotor 12 und einen Stator 14 aufweist. Der Rotor 12 besteht im wesentlichen aus einer Welle 16 mit einem Pumpenrotor 18, wobei ein Wellen-Abschnitt im Bereich der Wellenlagerung eine Lagerwelle 20 bildet. Die Lagerwelle 20 bildet den rotorseitigen Teil zweier Magnetlager 22,23 sowie der axial zwischen den beiden Magnetlagern 22,23 angeordneten Gleitlager 26,27, die als Fanglager für die beiden Magnetlager 22,23 dienen.Presentation. FIGS. 1 and 2 show a high-speed turbomachine 10 designed as a turbomolecular pump, which has a rotor 12 and a stator 14. The rotor 12 consists essentially of a shaft 16 with a pump rotor 18, wherein a shaft portion forms a bearing shaft 20 in the region of the shaft bearing. The bearing shaft 20 forms the rotor-side part of two magnetic bearings 22,23 and the axially between the two magnetic bearings 22,23 arranged plain bearings 26,27, which serve as a backup bearing for the two magnetic bearings 22,23.
Die Gleitlager 26,27 werden jeweils gebildet von der Lagerwelle 20, einer statorseitigen Lagerschale 28 und einer radial zwischen der Lagerschale 28 und der Lagerwelle 20 angeordneten zylindrischen Zwischenbuchse 30. Die Lagerschale 28, die Zwischenbuchse 30 sowie die Lagerwelle 20 bestehen aus Metall. Die Zwischenbuchse 30 ist mit metallischen Federungselementen 32 in fester Zuordnung zu der Lagerschale 28 gelagert.The plain bearings 26,27 are each formed by the bearing shaft 20, a stator-side bearing shell 28 and a radially intermediate between the bearing shell 28 and the bearing shaft 20 cylindrical intermediate sleeve 30. The bearing shell 28, the intermediate sleeve 30 and the bearing shaft 20 are made of metal. The intermediate sleeve 30 is mounted with metallic suspension elements 32 in a fixed relationship to the bearing shell 28.
Die Zwischenbuchse 30 ist drehbar sowohl zu der Lagerschale 28 als auch zu der Lagerwelle 20 gelagert. Zwischen der Zwischenbuchse 30 und der Lagerwelle 20 ist ein zirkulärer zylinderförmiger Spalt 33 vorhanden, der eine Spalthöhe von ungefähr 0,2 mm aufweist, die das für die Magnetlagerung im Normalbetrieb erforderliche Spiel der Lagerwelle 20 gewährt. Der äußere Spalt 34 zwischen der Zwischenbuchse 30 und der Lagerschale 28 weist eine geringere radiale Spalthöhe von ungefähr 0,02 mm auf. Der äußere Spalt 34 muss nur so groß sein, dass die Drehbarkeit der Zwischenbuchse 30 gegenüber der Lagerschale 28 unter allen thermischen Umständen gerade noch sichergestellt ist.The intermediate sleeve 30 is rotatably supported both to the bearing shell 28 and to the bearing shaft 20. Between the intermediate sleeve 30 and the bearing shaft 20, a circular cylindrical gap 33 is present, which has a gap height of about 0.2 mm, which allows the required for the magnetic bearing in normal operation clearance of the bearing shaft 20. The outer gap 34 between the intermediate sleeve 30 and the bearing cup 28 has a smaller radial gap height of about 0.02 mm. The outer gap 34 only has to be so large that the rotatability of the intermediate bushing 30 with respect to the bearing shell 28 is barely guaranteed under all thermal conditions.
Das dargestellte Gleitlager 26 weist im Gegensatz zu herkömmlichen Gleitlagern zwei Gleitflächen-Paare auf, auf die die gesamte Bremsarbeit und der gesamte Lagerabrieb verteilt werden. Hierdurch können insbesondere die Belastungen in Form von Wärme, Stößen und Abrieb derart reduziert werden, dass der Einsatz eines preiswerten Gleitlagers als Fanglager in einer schnelldrehenden gasfördernden Turbomaschine ermöglicht wird. The plain bearing 26 shown has, in contrast to conventional plain bearings on two sliding surface pairs, to which the entire braking work and the entire bearing wear are distributed. As a result, in particular the loads in the form of heat, shock and abrasion can be reduced so that the use an inexpensive plain bearing is possible as a catch warehouse in a fast-turning gas-promoting turbomachine.

Claims

Patentansprüche claims
1. Turbomaschine (10) mit einem Magnetlager (22,23) und einem mechanischen Fanglager,1. turbomachine (10) with a magnetic bearing (22, 23) and a mechanical safety bearing,
d a d u r c h g e k e n n z e i c h n e t ,characterized ,
dass das Fanglager als Gleitlager (26) ausgebildet ist und eine statorseitige Lagerschale (28) und eine rotorseitige Lagerwelle (20) aufweist,the retainer bearing is designed as a plain bearing (26) and has a stator-side bearing shell (28) and a rotor-side bearing shaft (20),
dass zwischen der Lagerschale (28) und der Lagerwelle (20) eine Zwischenbuchse (30) angeordnet ist, die sowohl zu der Lagerwelle (20) als auch zu der Lagerschale (28) durch einen zirkulären Spalt (33,34) beabstandet ist, undthat between the bearing shell (28) and the bearing shaft (20) an intermediate sleeve (30) is arranged, which is spaced both to the bearing shaft (20) and to the bearing shell (28) by a circular gap (33,34), and
dass die Zwischenbuchse (30) drehbar zu der Lagerschale (28) und der Lagerwelle (20) ist.in that the intermediate bush (30) is rotatable with respect to the bearing shell (28) and the bearing shaft (20).
2. Turbomaschine (10) nach Anspruch 1, dadurch gekennzeichnet, dass zwischen der Zwischenbuchse (30) und der Lagerschale (28) Federungselemente (32) angeordnet sind, die die Zwischenbuchse (30) beabstandet von der Lagerschale (28) halten.2. turbomachine (10) according to claim 1, characterized in that between the intermediate bush (30) and the bearing shell (28) suspension elements (32) are arranged, which hold the intermediate sleeve (30) spaced from the bearing shell (28).
3. Turbomaschine (10) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Spalthöhe des äußeren Spaltes (34) zwischen der Lagerschale (28) und der Zwischenbuchse (30) kleiner ist als die Spalthöhe des inneren Spaltes (33) zwischen der Zwischenbuchse (30) und der Lagerwelle (20). 3. turbomachine (10) according to claim 1 or 2, characterized in that the gap height of the outer gap (34) between the bearing shell (28) and the intermediate sleeve (30) is smaller than the gap height of the inner gap (33) between the intermediate sleeve (30) and the bearing shaft (20).
4. Turbomaschine (10) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Zwischenbuchse (30) einstückig ist und aus Metall besteht.4. turbomachine (10) according to one of claims 1 to 3, characterized in that the intermediate bush (30) is in one piece and consists of metal.
5. Fanglager für eine Turbomaschine (10) mit magnetgelagertem Rotor, mit den Merkmalen einer der Ansprüche 1 bis 4. 5. retainer bearing for a turbomachine (10) with magnetgelagertem rotor, having the features of one of claims 1 to 4.
EP06777930A 2005-08-05 2006-07-24 Turbomachine Withdrawn EP1910692A1 (en)

Applications Claiming Priority (2)

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DE102005036942A DE102005036942A1 (en) 2005-08-05 2005-08-05 turbomachinery
PCT/EP2006/064576 WO2007017366A1 (en) 2005-08-05 2006-07-24 Turbomachine

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JP (1) JP2009503412A (en)
KR (1) KR20080034005A (en)
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DE (1) DE102005036942A1 (en)
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US8083468B2 (en) 2011-12-27
TW200716869A (en) 2007-05-01
DE102005036942A1 (en) 2007-02-15
US20100098539A1 (en) 2010-04-22
WO2007017366A1 (en) 2007-02-15
JP2009503412A (en) 2009-01-29
CN101238301A (en) 2008-08-06

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