US20080224556A1 - Methods of controlling the instability in fluid film bearings - Google Patents
Methods of controlling the instability in fluid film bearings Download PDFInfo
- Publication number
- US20080224556A1 US20080224556A1 US12/121,976 US12197608A US2008224556A1 US 20080224556 A1 US20080224556 A1 US 20080224556A1 US 12197608 A US12197608 A US 12197608A US 2008224556 A1 US2008224556 A1 US 2008224556A1
- Authority
- US
- United States
- Prior art keywords
- bearing
- fluid film
- bearings
- magnetic
- instability
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
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
- F16C32/00—Bearings not otherwise provided for
- F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
- F16C32/0402—Bearings not otherwise provided for using magnetic or electric supporting means combined with other supporting means, e.g. hybrid bearings with both magnetic and fluid supporting 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
-
- 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
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
-
- 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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
- F16C23/04—Sliding-contact bearings self-adjusting
-
- 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
-
- 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
- F16C39/06—Relieving load on bearings using magnetic means
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49636—Process for making bearing or component thereof
- Y10T29/49639—Fluid bearing
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49636—Process for making bearing or component thereof
- Y10T29/49696—Mounting
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49764—Method of mechanical manufacture with testing or indicating
- Y10T29/49778—Method of mechanical manufacture with testing or indicating with aligning, guiding, or instruction
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49764—Method of mechanical manufacture with testing or indicating
- Y10T29/49778—Method of mechanical manufacture with testing or indicating with aligning, guiding, or instruction
- Y10T29/4978—Assisting assembly or disassembly
Definitions
- This invention is related to fluid film bearings, in particular, to controlling well known instability in fluid film bearings by using magnetic bearings and by using a unique method involving the use of an intentional misaligned journal in the bearing.
- a unique feature of rotor vibration is the presence of a rotor, which by definition has to rotate, sometimes at very high speeds, to allow the machine to conduct its function. This rotation has two major implications. One implication is that a huge amount of kinetic energy is stored in the rotating machine. If a mechanism allows some of this energy to be transferred from the rotation to the rotor vibration, this would certainly lead to instability of the machine. Some mechanisms that allow this energy transfer and result in instability of rotating machines are: internal damping, aerodynamic cross coupling, seals, high speed journal bearings, intershaft squeeze film dampers, etc.
- instability and unbalance excitation result in the need to control rotor vibrations. If left uncontrolled, the unbalance excitation may result in excessive transmitted force; the critical speeds may result in excessive vibration amplitude, while instability may result in machine destruction.
- the second problem with fluid film bearings is their speed dependent characteristics.
- the stiffness and damping properties of fluid film bearings depend on the Sommerfeld number, which is a nondimensional speed/load factor.
- the difficulty of determining accurate stiffness and damping properties of fluid film bearings is prevalent up to the present time, both due to the difficulty of the CFD calculations using Finite Difference and Finite Element Methods, as well as the speed dependent properties which affect the prediction of critical speeds of rotors mounted on fluid film bearings.
- the squeeze film damper is an oil film surrounding the outer race of a rolling element bearing which is constrained from rotation but allowed to vibrate. Thus, it can be classified as a class of fluid film bearings, without the load carrying capacity or the instability caused by rotation.
- the squeeze film damper allowed the designer of aircraft engines to introduce damping to the rotating machine as a method of vibration control.
- the introduction of the soft support allowed judicial placement of the critical speeds.
- the combination of the squeeze film damper and soft support provided the designer with stiffness and damping to control the rotor vibration passively.
- the magnetic bearings can provide continuously variable stiffness and damping properties for active vibration control, add to that the non-contact characteristics, as well as a large load carrying capacity and the possibility of using an oil free machine, and it becomes clear that magnetic bearings are probably the best choice for the support and active control of rotating machine vibrations.
- magnetic bearings have various shortcomings. These include: the cost of magnetic bearings, which are considerably more expensive than conventional bearings; the cost of failure, which probably would mean complete replacement of the machine; the weight of the large bearings and associated controls; the sensitivity of magnetic bearings to high temperatures; the need to establish their reliability, as well as the need to establish a parallel support system, called a “catcher-bearing”, to carry the rotor in case of failure.
- One embodiment of the present invention is a combined magnetic-fluid film bearing; another embodiment is a stable fluid film bearing.
- the magnetic bearings are probably the best support for rotating machines.
- their shortcomings, essentially concerning reliability, preclude their usage in many applications, particularly in aircraft engines.
- fluid film bearings have stability problems, that preclude their use in high speed applications.
- the invention actually relies on the advantages and shortcomings of both devices.
- the invention is to use a fluid film bearing (whether it is a cylindrical journal bearing, an elliptic bearing, an offset-half bearing, a multi-lobe bearing, or a tilting-pad bearing, does not really matter) as a primary load carrying bearing, and to use a magnetic bearing in combination with the fluid film bearing to control the instability.
- a fluid film bearing whether it is a cylindrical journal bearing, an elliptic bearing, an offset-half bearing, a multi-lobe bearing, or a tilting-pad bearing, does not really matter
- This should be quite an efficient combination, where the combination results in bearings that can be used at high speeds without having neither stability nor reliability problems.
- Hybrid foil-magnetic bearing is an exception.
- both the foil bearing and the magnetic bearing are used as load carrying elements. It is possible to do so to carry large load, such that each of the foil bearing and the magnetic bearing carry part of the load.
- the hybrid foil-magnetic bearing although capable of operating at high speeds, still suffers from the same disadvantages of magnetic bearings.
- fluid film bearings and magnetic bearings are well known devices, yet it is not obvious that they can be used in a combined form, since the current technology is that these are competing devices not complementing devices. Both are considered load carrying devices that have certain control capabilities (passive control for fluid film bearings and active control for magnetic bearings). It is thus an invention to consider the magnetic bearing only as a controlling device, and the fluid film bearing as only a load carrying device. Their combined effect is to have bearings with the advantages of large load carrying capacity, excellent reliability, and use at high speeds without instability, in addition to all the known advantages of fluid film bearings and magnetic bearings. Moreover, an additional advantage will appear, since the magnetic bearing is not used as a load carrying element, the power requirements will be reduced, and thus smaller, lighter magnetic bearings can be used that can control the rotor vibrations reliably.
- This combination can take the form of two adjacent or non-adjacent bearings, one fluid film bearing and the other magnetic bearing, or it can have the form of one integral bearing having the fluid film bearing within the magnetic bearing, such that the fluid for the fluid film bearing passes over the rotor of the magnetic bearing, and within the clearance between the rotor and stator in the magnetic bearing.
- fluid film bearings have an instability problem called oil whirl and oil whip.
- Many patents describe methods to design fluid film bearings that are more stable, for example:
- a sleeve (journal) bearing is manufactured such that the bearing axis is skewed with the shaft axis.
- the shaft axis is straight horizontally, while the bearing axis is tilted in the vertical direction, with a predetermined slope.
- One end is lower than the shaft axis, while the other end is higher than the shaft axis.
- the same invention applies for a fixed geometry bearing, but in the horizontal direction.
- the bearing axis is tilted sideways (to the right) thus presenting a predetermined horizontal misalignment at the bearing.
- a variable geometry bearing allows for bearing angular misalignment.
- the basic idea is quite simple. Suppose the predetermined slope for the bearings is not known beforehand, and requires adjustment in the field. In this case, consider a simple cylindrical journal bearing, where the fixing bolts are allowed a certain passageway such that it is possible to skew the whole cylindrical journal bearing (or any type fluid bearing) whereby the bearing axis has a certain slope to the shaft axis, and this slope is adjustable. When the appropriate slope is selected, the fixing bolts are used to fix the bearing body (and the passageway) to the skid or pedestal.
- this invention opens the door to many other possibilities in designing fluid film bearings.
- This includes the introduction of two offset halves of the bearing, just by simply introducing a skewness between the upper and lower portions (this is in contrast to the current technology where the offset halves are offset horizontally).
- Other embodiments include introducing elliptic, multi-lobe, pressure dam, and tilting pads in the axial rather than the circumferential directions as current technology implies. Any possibility of modifying or disturbing the flow along the axis of the bearing for controlling oil whirl and oil whip is an embodiment of this invention.
- FIG. 1 is an elevation view of one embodiment of the invention depicting the adjacent magnetic-journal bearing support of a rotor, showing a cross-sectional view of the embodiment;
- FIG. 2 a is an elevation view of another embodiment of the invention depicting the non-adjacent magnetic-journal bearing support of a rotor, showing a cross-sectional view of the embodiment;
- FIG. 2 b is a detailed view of detail B taken from FIG. 2 a;
- FIG. 3 is an elevation view of another embodiment of the invention depicting an integrated magnetic-journal bearing, showing a cross-sectional view of the embodiment;
- FIGS. 4 a - 4 c collectively depict the vertically inclined fixed geometry assembly embodiment of the invention
- FIGS. 5 a - 5 d collectively depict the horizontally inclined fixed geometry bearing assembly embodiment of the invention
- FIGS. 6 a - 6 c collectively depict the tilting housing bearing embodiment of the invention
- FIGS. 7 a - 7 e collectively depict the upper tilting half bearing embodiment of the invention.
- FIGS. 8 a - 8 d collectively depict the inclined pressure dam bearing embodiment of the invention.
- FIGS. 9 a - 9 d collectively depict the inclined multi-lobe bearing embodiment of the invention.
- FIGS. 10 a - 10 c collectively depict the converging-diverging bearing assembly embodiment of the invention
- FIGS. 11 a - 11 d collectively depict the diverging-converging bearing assembly embodiment of the invention.
- FIGS. 12 a - 12 d collectively depict the convergent bearing embodiment of the invention
- FIGS. 13 a - 13 d collectively depict the divergent bearing assembly embodiment of the invention
- FIGS. 14 a - 14 d collectively depict the tilting pad bearing embodiment of the invention.
- FIGS. 15 a - 15 d show a tilting pad bearing assembly with a Divergent-Convergent pad that rocks on the bearing axially, and/or has an axial Divergent-Convergent profile
- FIGS. 16 a - 16 d show a tilting pad bearing assembly with a Convergent-Divergent pad that rocks on the bearing axially, and/or has an axial Convergent-Divergent profile
- FIGS. 17 a - 17 d show a tilting pad bearing assembly with an axially twisted pad
- FIGS. 18 a - 18 d show a tilting pad bearing assembly with an axially stepped pad.
- the invention is a method of controlling the instability in fluid film bearings by using a magnetic bearing in combination with a fluid film bearing (whether it is a cylindrical journal bearing, an elliptic bearing, an offset-half bearing, a multi-lobe bearing, foil bearing or a tilting-pad bearing, does not really matter), wherein the fluid film bearing serves as the primary load carrying bearing and the magnetic bearing controls the instability of the fluid film bearing.
- An alternative method of controlling the instability in fluid film bearings is to disturb the flow in the axial direction, for example, a sleeve (journal) bearing can be manufactured such that the bearing axis is skewed with the shaft axis or a variable geometry bearing can be manufactured to allow for bearing angular misalignment.
- a sleeve (journal) bearing can be manufactured such that the bearing axis is skewed with the shaft axis or a variable geometry bearing can be manufactured to allow for bearing angular misalignment.
- FIGS. 1 to 3 depict the various embodiments of the combined Magnetic Bearing-Fluid Film Bearing invention, in the Adjacent, Non-Adjacent and Integral embodiments, respectively.
- FIG. 1 shows the configuration of the Adjacent Magnetic Bearing-Fluid Film Bearing configuration.
- the elevation view is shown in FIG. 1 , where a magnetic bearing assembly 12 comprising an electro-magnetic stator 12 a is fixed in a housing 12 b , and is used to control the rotor 12 c , mounted on the shaft 16 .
- the load carrying element is the fluid film bearing assembly 18 , supported by the housing 18 a .
- the load is carried by the fluid film bearing 18 , while the magnetic bearing 12 is used to control the instability that occurs in the fluid film bearing 18 at high speeds.
- FIGS. 2 a - 2 b show the configuration of the Non-Adjacent Magnetic Bearing-Fluid Film Bearing configuration.
- FIG. 2 a shows the elevation view, where a magnetic bearing assembly 12 comprising an electro-magnetic stator 12 a is fixed in a housing 12 b , and is used to control the rotor 12 c , mounted on the shaft 16 .
- the load-carrying element is the fluid film bearing assembly 18 , supported by the housing 18 a .
- the load is carried by the fluid film bearing 18 , while the magnetic bearing 12 is used to control the instability that occurs in the fluid film bearing 18 at high speeds.
- FIG. 1 shows the elevation view, where a magnetic bearing assembly 12 comprising an electro-magnetic stator 12 a is fixed in a housing 12 b , and is used to control the rotor 12 c , mounted on the shaft 16 .
- the load-carrying element is the fluid film bearing assembly 18 , supported by the housing 18 a .
- the load is
- FIG. 2 b shows the detail of the magnetic bearing stator 12 a with windings, rotor 12 c , housing 12 b and shaft 16 .
- the main difference between FIG. 1 and FIG. 2 is that in FIG. 1 , the Magnetic Bearing and the Fluid Film Bearing are adjacent (close to each other); while in FIG. 2 , the Magnetic Bearing and the Fluid Film Bearing are non-adjacent (relatively far or distantly spaced-apart from each other).
- FIG. 3 shows the configuration of the Integral Magnetic Bearing-Fluid Film Bearing assembly 14 configuration.
- the elevation view is shown in FIG. 3 , where a magnetic bearing 14 d comprising an electromagnetic stator 14 a is fixed in a housing 14 b , and is used to control the rotor 14 c , mounted on the shaft 16 .
- the load carrying element is the fluid film bearing 14 e , where the fluid film is filling the clearance between the stator 14 a and the rotor 14 c .
- the load is carried by the fluid film bearing 14 e , while the magnetic bearing 14 d is used to control the instability that occurs in the fluid film bearing 14 e at high speeds. This is a compact configuration with the fluid film bearing 14 e integrated into the magnetic bearing 14 d.
- FIGS. 4 to 18 depict the various examples of embodiments of the Stable Fluid Film Bearing, including the Vertically Inclined Fixed Geometry Bearing, the Horizontally Inclined Fixed Geometry Bearing, the Tilting Housing Bearing, the Upper Tilted Half Bearing, the Inclined Pressure Dam Bearing, the Inclined Multi-Lobed Bearing, the Converging-Diverging Bearing, the Diverging Converging Bearing, the Converging Bearing, the Diverging Bearing, and the Axially Tilting Pad Bearing and variants.
- FIGS. 4 a - 4 c An example of the Vertically Inclined Fixed Geometry Bearing assembly 20 embodiment is shown in FIGS. 4 a - 4 c .
- the bearing 20 a is vertically inclined to promote the stability of the system (see section C-C, FIG. 4 b ).
- the fluid film 20 b is carrying the shaft 20 c , on the bearing 20 a , and is sealed using the sealing 20 d .
- the housing halves, housing lower part 20 e and housing upper part 20 f are part of the bearing assembly 20 and carry the bearing 20 a .
- the shaft axis 20 g in this case for a horizontal machine would be horizontal, but the bearing itself is inclined vertically to promote stability.
- FIGS. 5 a - 5 d An example of the Horizontally Inclined Fixed Geometry Bearing assembly 30 embodiment is shown in FIGS. 5 a - 5 d .
- the bearing 30 a is horizontally inclined to promote the stability of the system (see section B-B, FIG. 5 c ).
- the fluid film 30 b is carrying the shaft 30 c , on the bearing 30 a , and is sealed using the sealing 30 d .
- the housing halves, housing lower part 30 e and housing upper part 30 f are part of the bearing assembly 30 and carry the bearing 30 a .
- FIG. 5 d shows a schematic of the two bearing halves with the horizontal inclination.
- the shaft axis 30 g in this case for a horizontal machine would be horizontal and the bearing itself is inclined horizontally to the machine axis to promote stability.
- FIGS. 6 a - 6 c show an example of the Tilting Housing Bearing assembly 40 embodiment.
- the bearing 40 a is straight, and the housing, comprising housing lower part 40 b and housing upper part 40 c , is adjustable.
- Two bolts 40 d are used to fix the housing to the support.
- a curved groove in the housing parts 40 b , 40 c is used for the bolt 40 d .
- By loosening the bolts 40 d it is possible to twist the housing parts 40 b , 40 c (and consequently the bearing 40 a ) with respect to the shaft 40 e , and then tightening them again to fix the amount of twist as desired. This should lead to a stable bearing that can have the angular misalignment of the bearing adjusted.
- FIGS. 7 a - 7 e show an example of the Upper Tilting Half Bearing assembly 50 embodiment.
- the upper bearing half 50 a is tilted and misaligned to the shaft 50 c axis, while the lower bearing half 50 b is normal.
- FIGS. 7 d and 7 e show oil film 50 d and housing upper and lower parts 50 e , 50 f .
- the current technology allows for the upper half to be offset, however, the claimed invention is the upper half 50 a tilted (axis skewed to shaft axis).
- the drawings provided are for a bearing that has an upper half 50 a that is both offset and tilted.
- FIGS. 8 a - 8 d show an example of the Inclined Pressure Dam Bearing assembly 60 embodiment.
- This bearing 60 a is essentially a cylindrical bearing, but with a dam 60 d .
- the purpose of the dam is to disturb the flow and load the bearing, thus improving its stability characteristics.
- the current technology allows for the dam.
- the invention claimed is in a dam that has its edges tilted with respect to the axis 60 c of the shaft 60 b , thus providing for the angular loading and axial flow disturbance.
- Section A-A of FIG. 8 b , and enlarged in FIG. 8 c show the dam.
- the oil film is shown as 60 e in FIG. 8 c .
- the details of the inclined dam are shown in FIG. 8 d.
- FIGS. 9 a - 9 d show an example of the Inclined Multi-Lobe Bearing assembly 70 embodiment.
- the current technology allows for the multi-lobe bearing 70 a to be consisting of several lobes, each lobe has its center of curvature in a different position, thus providing circumferential disturbance to the flow, and improving stability. This is in contrast to the cylindrical bearing, which has only one center.
- the multi-lobe bearing can have two-lobes (which is the elliptic bearing, in which the upper and lower halves have two different centers), three-lobes, four-lobes (as depicted in FIGS. 9 a - 9 d ), or more.
- each lobe has its own center of curvature (see 70 b in FIG. 9 d ), but also each lobe is tilted axially, such as to disturb the flow axially, as clearly illustrated in FIG. 9 d , and the sections A-A and B-B shown in FIGS. 9 b and 9 c , respectively.
- the Convergent-Divergent Bearing Assembly 80 ( FIGS. 10 a - 10 c ), the Divergent-Convergent Bearing assembly 90 ( FIGS. 11 a - 11 d ), the Convergent Bearing assembly 100 ( FIGS. 12 a - 12 d ), and the Divergent Bearing assembly 110 ( FIGS. 13 a - 13 d ).
- the corresponding bearing 80 a , 90 a , 100 a , 110 a has the axial disturbance of the flow suggested by each of their names respectively, with respect to the respective shaft 80 b , 90 b , 100 b , 110 b.
- FIGS. 14 a - 14 d representationally show this embodiment, which allows appreciable rocking in the axial direction, thus disturbing the flow axially.
- FIG. 14 d shows the tilting pads 120 b that are allowed to rock axially on the outer casing 120 c.
- FIGS. 15 , 16 , 17 and 18 show a tilting pad bearing assembly 130 with a Divergent-Convergent pad 130 b that rocks on the bearing 130 c axially, and/or has an axial Divergent-Convergent profile
- FIGS. 16 a - 16 d show a tilting pad bearing assembly 140 with a Convergent-Divergent pad 140 b that rocks on the bearing 140 c axially, and/or has an axial Convergent-Divergent profile
- FIGS. 17 a - 17 d show a tilting pad bearing assembly 150 with an axially twisted pad 150 b
- FIGS. 18 a - 18 d show a tilting pad bearing assembly 160 with an axially stepped pad 160 b.
- the present invention can also be applied to foil bearings using the conceptual embodiments described above.
- the inventive configurations described above of axial flow disturbance can be applied to foil bearings, through axial flow disturbance, by twisting or tilting as discussed above.
Abstract
A method of controlling the instability in fluid film bearings by using a magnetic bearing in combination with a fluid film bearing (whether it is a cylindrical journal bearing, an elliptic bearing, an offset-half bearing, a multi-lobe bearing, foil bearing or a tilting-pad bearing, does not really matter), wherein the fluid film bearing serves as the primary load carrying bearing and the magnetic bearing controls the instability of the fluid film bearing. This efficient combination results in bearings that can be used at high speeds without having neither stability nor reliability problems. An alternative method of controlling the instability in fluid film bearings is to disturb the flow in the axial direction, for example, a sleeve (journal) bearing can be manufactured such that the bearing axis is skewed with the shaft axis or a variable geometry bearing can be manufactured to allow for bearing angular misalignment.
Description
- This application is a divisional application of U.S. patent application Ser. No. 11/147,762 filed Jun. 8, 2005, which in turn claims the priority benefit of U.S. Provisional Patent Application Ser. No. 60/579,866 filed Jun. 15, 2004
- This invention is related to fluid film bearings, in particular, to controlling well known instability in fluid film bearings by using magnetic bearings and by using a unique method involving the use of an intentional misaligned journal in the bearing.
- A unique feature of rotor vibration is the presence of a rotor, which by definition has to rotate, sometimes at very high speeds, to allow the machine to conduct its function. This rotation has two major implications. One implication is that a huge amount of kinetic energy is stored in the rotating machine. If a mechanism allows some of this energy to be transferred from the rotation to the rotor vibration, this would certainly lead to instability of the machine. Some mechanisms that allow this energy transfer and result in instability of rotating machines are: internal damping, aerodynamic cross coupling, seals, high speed journal bearings, intershaft squeeze film dampers, etc.
- The other implication of rotation is the perpetual presence of an exciting force on the rotating machine. There is always some residual unbalance in the rotor; this residual unbalance forces the rotor at different speeds and possibly excites the critical speeds.
- The presence of these two unique features of rotor vibrations: instability and unbalance excitation, result in the need to control rotor vibrations. If left uncontrolled, the unbalance excitation may result in excessive transmitted force; the critical speeds may result in excessive vibration amplitude, while instability may result in machine destruction.
- Since the early work of Rankine, who suggested that machines would never be able to cross critical speeds, major strides have occurred in the development of rotor-bearing systems. Nowadays, high speed-high performance rotating machines such as gas turbines, compressors, steam turbines, turbo expanders, and turbochargers, etc., routinely cross as many as six critical speeds during their normal operating procedures.
- To control the vibration of such high-speed machines, many turbomachinery manufacturers resort to either passive or active vibration control. Perhaps the first method of vibration control was the introduction of fluid film bearings in the late nineteenth century. The first application of “non-contact” journal bearings was hailed as a major breakthrough at the time, with suggestions that this should lead to the solution of all rotating machinery problems. However, soon thereafter the problems of journal bearings and fluid film bearings in general became apparent. Two basic characteristics obscured the success of fluid film bearings. One is the tendency of journal bearings to cause oil whirl and oil whip, which can be destructive instability mechanisms in rotor-bearing systems. This led to the introduction of more sophisticated fluid film bearings such as the elliptic bearing, offset-half bearing, pressure dam bearing, multi-lobe bearing and tilting pad bearing, and more recently the foil bearing. These fluid film bearings provide progressively improved stability characteristics, at the cost of lower load carrying capacity and reduced damping at critical speeds.
- The second problem with fluid film bearings is their speed dependent characteristics. The stiffness and damping properties of fluid film bearings depend on the Sommerfeld number, which is a nondimensional speed/load factor. The difficulty of determining accurate stiffness and damping properties of fluid film bearings is prevalent up to the present time, both due to the difficulty of the CFD calculations using Finite Difference and Finite Element Methods, as well as the speed dependent properties which affect the prediction of critical speeds of rotors mounted on fluid film bearings.
- Large, heavy rotors have to use fluid film bearings because of the load carrying capacity. However, smaller and faster rotors are mounted on rolling element bearings. Unfortunately, rolling element bearings, do not provide any vibration control, because of their high stiffness and virtually no damping characteristics. This did not cause problems with smaller machines, such as electric motors, but with the advent of gas turbine jet engines, which necessitated the use of high speed, light rotors, it became apparent that aircraft engines need a method of vibration control. Fluid film bearings were eliminated as a possible control method in aircraft engines because of the instability mechanisms of oil whip, which would be destructive for high-speed engines.
- The time was ripe in the nineteen sixties for the introduction of the squeeze film damper and soft support as a method for passive vibration control. The squeeze film damper is an oil film surrounding the outer race of a rolling element bearing which is constrained from rotation but allowed to vibrate. Thus, it can be classified as a class of fluid film bearings, without the load carrying capacity or the instability caused by rotation. The squeeze film damper allowed the designer of aircraft engines to introduce damping to the rotating machine as a method of vibration control. In addition, the introduction of the soft support allowed judicial placement of the critical speeds. Thus the combination of the squeeze film damper and soft support provided the designer with stiffness and damping to control the rotor vibration passively.
- In the nineteen eighties, researchers started toying with the idea of using magnetic bearings as supports for rotating machines. This opened the door for active control of rotating machine vibration, because of the possibility of actively controlling the stiffness and damping properties of magnetic bearings through the control of the current to the bearings. In addition, it is somewhat natural to consider active control of electromagnetic systems, due to the ease of interface with control system components.
- A wealth of research exists in the literature on the active control of rotating machinery using magnetic bearings. Actually, it is the inventor's personal belief that magnetic bearings, despite their various shortcomings, are probably the best method available to control rotor vibration in land based applications.
- The magnetic bearings can provide continuously variable stiffness and damping properties for active vibration control, add to that the non-contact characteristics, as well as a large load carrying capacity and the possibility of using an oil free machine, and it becomes clear that magnetic bearings are probably the best choice for the support and active control of rotating machine vibrations.
- However, magnetic bearings have various shortcomings. These include: the cost of magnetic bearings, which are considerably more expensive than conventional bearings; the cost of failure, which probably would mean complete replacement of the machine; the weight of the large bearings and associated controls; the sensitivity of magnetic bearings to high temperatures; the need to establish their reliability, as well as the need to establish a parallel support system, called a “catcher-bearing”, to carry the rotor in case of failure.
- These shortcomings affect the application of magnetic bearings in aircraft engines, and to date, with over twenty years of aggressive research and development, no magnetic bearings have been introduced in aircraft engines. However, many rotating machines, particularly retrofit compressors, have been employed using magnetic bearings in the field and have shown considerable success.
- In an excellent paper, Y. Hori in 1959 provided a theory of oil whip, and described the history of fluid film bearing instability. According to Hori, the phenomena of oil whirl and oil whip were first reported in 1925. Although it has been three quarters of a century since the instability has been reported, yet this subject is still of current interest. G. Kirk in 2003 explained that this interest lies essentially in answering the following two questions: “Are there any possibilities that the rotor system can transgress the threshold speed? Can the rotor system operate above this threshold speed?”. These two questions are also the motivation for this work presented herein, in addition to the need to understand the parameters that influence the onset of instability.
- Perhaps the interest in studying the stability of fixed geometry fluid film bearing lies in its historical significance. They allowed the development of rotating machines in the nineteenth century. Actually, in his book on the theory of lubrication, D. D. Fuller suggests that the fluid film bearing is probably the single most important element in the recent technological development, only comparable in its significance to the effect of electricity. Early fluid film bearings were designed to carry the loads, and were hailed as low-friction devices possibly capable of continuously carrying the machine. However, with the increased speed of rotating machines in the twentieth century, it became evident that the journal bearing itself can cause the problems of oil whirl and oil whip. This has caused many researchers to investigate, experimentally and theoretically, the phenomena of oil whirl and oil whip.
- In his paper, Hori's main result was to explain the experimental results reported at that time. Hori reports that B. L. Newkirk and J. F. Lewis in 1956 reported experimental cases in which the rotating speed reached five or six times the first critical speed before the instability occurred, while O. Pinkus in 1953 and 1956 reported cases where whipping disappeared and resumed again, and cases of stable and unstable states separated by regions of transient whip. According to Hori, Newkirk and Pinkus experiments were contradictory in many senses; even on the effect of temperature. Newkirk and Lewis reported that hotter oil provides a greater range of stable operation, while the Pinkus experiments reported in 1956 showed that cooler oil provides a greater range of stable operation. Y. Hori in 1959 provided a theory of oil whip, trying to explain the gap between Newkirk and Pinkus.
- Since then, in the sixties and seventies, significant work on alternative fluid film bearing designs to control the instability were conducted. Moreover, significant efforts went into calculating linearized bearing coefficients and in predicting rotor dynamic response.
- In the eighties, renewed interest in the journal bearing instability was triggered. A. Muszynska performed extensive testing on journal bearing supported rotors. She illustrated the presence of second mode whirl. Also, in the eighties, major advances in understanding the nonlinear dynamics of journal bearings through bifurcation analysis and Hopf Bifurcation were made.
- One embodiment of the present invention is a combined magnetic-fluid film bearing; another embodiment is a stable fluid film bearing.
- As discussed in the background, the magnetic bearings are probably the best support for rotating machines. However, their shortcomings, essentially concerning reliability, preclude their usage in many applications, particularly in aircraft engines. Also, as discussed above, fluid film bearings have stability problems, that preclude their use in high speed applications.
- The invention actually relies on the advantages and shortcomings of both devices. The invention is to use a fluid film bearing (whether it is a cylindrical journal bearing, an elliptic bearing, an offset-half bearing, a multi-lobe bearing, or a tilting-pad bearing, does not really matter) as a primary load carrying bearing, and to use a magnetic bearing in combination with the fluid film bearing to control the instability. This should be quite an efficient combination, where the combination results in bearings that can be used at high speeds without having neither stability nor reliability problems.
- Many patents cover magnetic bearings, e.g.,
- U.S. Pat. No. 6,737,777 Magnetic bearing and use thereof;
- U.S. Pat. No. 6,727,617 Method and apparatus for providing three axis magnetic bearing having permanent magnets mounted on radial pole stock;
- U.S. Pat. No. 6,720,695 Rotor spinning device with a contact less, passive, radial bearing for the spinning rotor;
- U.S. Pat. No. 6,717,311 Combination magnetic radial and thrust bearing;
- U.S. Pat. No. 6,707,200 Integrated magnetic bearing;
- U.S. Pat. No. 6,703,736 Magnetic bearing;
- U.S. Pat. No. 6,653,756 Magnetic bearing device; and
- U.S. Pat. No. 6,606,536 Magnetic bearing device and magnetic bearing control device.
- However, none of these patents discuss the use of magnetic bearings as a means of controlling journal bearings instability. Actually, most of the state-of-the-art, and the current development efforts in magnetic bearings, are for the use of magnetic bearings as a primary load carrying element, and to use the excess control action to provide some desirable stability benefits in rotating machines.
- Also, many patents cover fluid film bearings, e.g.,
- U.S. Pat. No. 6,089,756 Plain bearing;
- U.S. Pat. No. 5,879,085 Tilt pad hydrodynamic bearing for rotating machinery;
- U.S. Pat. No. 5,879,076 Tilt pad hydrodynamic bearing for rotating machinery;
- U.S. Pat. No. 5,772,334 Fluid film bearings;
- U.S. Pat. No. 5,743,657 Tilting pad journal bearing;
- U.S. Pat. No. 5,743,654 Hydrostatic and active control movable pad bearing;
- U.S. Pat. No. 5,634,723 Hydrodynamic fluid film bearings;
- U.S. Pat. No. 5,549,392 Shaft seal for hydrodynamic bearing unit;
- U.S. Pat. No. 5,531,523 Rotor journal bearing having adjustable bearing pads;
- U.S. Pat. No. 5,516,212 Hydrodynamic bearing with controlled lubricant pressure distribution;
- U.S. Pat. No. 5,489,155 Tilt pad variable geometry bearings, having tilting bearing pads and methods of making same;
- U.S. Pat. No. 5,480,234 Journal bearing;
- U.S. Pat. No. 5,322,371 Fluid film bearing;
- U.S. Pat. No. 5,201,585 Fluid film journal bearing with squeeze film damper for turbo machinery;
- U.S. Pat. No. 5,096,309 Hydrodynamic bearing system;
- U.S. Pat. No. 5,032,028 Fluid film bearing;
- U.S. Pat. No. 4,961,122 Hydrodynamic grooved bearing device;
- U.S. Pat. No. 4,828,403 Resiliently mounted fluid bearing assembly;
- U.S. Pat. No. 4,880,320 Fluid film journal bearings;
- U.S. Pat. No. 4,767,223 Hydrodynamicjournal bearings;
- U.S. Pat. No. 4,597,676 Hybrid bearing;
- U.S. Pat. No. 4,526,483 Fluid foil bearing;
- U.S. Pat. No. 4,415,281 Hydrodynamic fluid film bearing;
- U.S. Pat. No. 4,300,808 Tilting-pad bearings;
- U.S. Pat. No. 4,034,228 Tilting pad bearing; and
- U.S. Pat. No. 3,969,804 Bearing housing assembly method for high speed rotating shafts.
- However, none of these patents suggest the use of magnetic bearings as a means of controlling fluid film instabilities.
- Actually, the development of magnetic bearings and the development of fluid film bearings are two completely separate items, and investigators in both areas do not appreciate the developments in the other area, as if they are two different islands.
- U.S. Pat. No. 6,353,273, Hybrid foil-magnetic bearing is an exception. In that invention, it is suggested that both the foil bearing and the magnetic bearing are used as load carrying elements. It is possible to do so to carry large load, such that each of the foil bearing and the magnetic bearing carry part of the load. However, in the opinion of this inventor, that is not a good solution. The hybrid foil-magnetic bearing, although capable of operating at high speeds, still suffers from the same disadvantages of magnetic bearings.
- Although fluid film bearings and magnetic bearings are well known devices, yet it is not obvious that they can be used in a combined form, since the current technology is that these are competing devices not complementing devices. Both are considered load carrying devices that have certain control capabilities (passive control for fluid film bearings and active control for magnetic bearings). It is thus an invention to consider the magnetic bearing only as a controlling device, and the fluid film bearing as only a load carrying device. Their combined effect is to have bearings with the advantages of large load carrying capacity, excellent reliability, and use at high speeds without instability, in addition to all the known advantages of fluid film bearings and magnetic bearings. Moreover, an additional advantage will appear, since the magnetic bearing is not used as a load carrying element, the power requirements will be reduced, and thus smaller, lighter magnetic bearings can be used that can control the rotor vibrations reliably.
- This combination can take the form of two adjacent or non-adjacent bearings, one fluid film bearing and the other magnetic bearing, or it can have the form of one integral bearing having the fluid film bearing within the magnetic bearing, such that the fluid for the fluid film bearing passes over the rotor of the magnetic bearing, and within the clearance between the rotor and stator in the magnetic bearing.
- However, in this case a design issue will appear, since the magnetic bearing will require a large clearance to dissipate generated heat, and the fluid film bearing will require a small clearance to improve load carrying capacity. This design issue can be tackled in two ways, one is to select a compromise clearance between the two conflicting requirements, and the other is to use a small clearance for load carrying in the fluid film bearing, and use an increased fluid flow to dissipate the generated heat in the magnetic bearing.
- As discussed in the previous pages, fluid film bearings have an instability problem called oil whirl and oil whip. Many patents describe methods to design fluid film bearings that are more stable, for example:
- U.S. Pat. No. 6,089,756 Plain bearing
- U.S. Pat. No. 5,879,085 Tilt pad hydrodynamic bearing for rotating machinery
- U.S. Pat. No. 5,879,076 Tilt pad hydrodynamic bearing for rotating machinery
- U.S. Pat. No. 5,772,334 Fluid film bearings
- U.S. Pat. No. 5,743,657 Tilting pad journal bearing
- U.S. Pat. No. 5,743,654 Hydrostatic and active control movable pad bearing
- U.S. Pat. No. 5,634,723 Hydrodynamic fluid film bearings
- U.S. Pat. No. 5,549,392 Shaft seal for hydrodynamic bearing unit
- U.S. Pat. No. 5,531,523 Rotor journal bearing having adjustable bearing pads
- U.S. Pat. No. 5,516,212 Hydrodynamic bearing with controlled lubricant pressure distribution
- U.S. Pat. No. 5,489,155 Tilt pad variable geometry bearings, having tilting bearing pads and methods of making same
- U.S. Pat. No. 5,480,234 Journal bearing
- U.S. Pat. No. 5,322,371 Fluid film bearing
- U.S. Pat. No. 5,201,585 Fluid film journal bearing with squeeze film damper for turbo machinery
- U.S. Pat. No. 5,096,309 Hydrodynamic bearing system
- U.S. Pat. No. 5,032,028 Fluid film bearing
- U.S. Pat. No. 4,961,122 Hydrodynamic grooved bearing device
- U.S. Pat. No. 4,828,403 Resiliently mounted fluid bearing assembly
- U.S. Pat. No. 4,880,320 Fluid film journal bearings
- U.S. Pat. No. 4,767,223 Hydrodynamic journal bearings
- U.S. Pat. No. 4,597,676 Hybrid bearing
- U.S. Pat. No. 4,526,483 Fluid foil bearing
- U.S. Pat. No. 4,415,281 Hydrodynamic fluid film bearing
- U.S. Pat. No. 4,300,808 Tilting-pad bearings
- U.S. Pat. No. 4,034,228 Tilting pad bearing
- U.S. Pat. No. 3,969,804 Bearing housing assembly method for high speed rotating shafts
- However, all these patents, including the tilting pad bearing, which is the most stable fluid film bearing, all have a common feature, that is to disturb the flow in the circumferential direction to control the instability (or, in case of the foil bearing, use resilience in series with the fluid film). In fact, ASME Journal of Tribology, Vol. 126, pp. 125-131 (2004) describes a study for obtaining the optimal clearance configuration in the circumferential direction to improve the stability characteristics of fluid film bearings. Yet no one thought of trying to disturb the flow in the axial direction to control the instability.
- The inventor herein has conducted experiments where angular misalignment at the coupling virtually eliminated the instability in cylindrical journal bearings, which are notorious for having instability problems. These experiments were reported in a paper presented by the inventor herein at the Proceedings of ASME Turbo Expo, Vienna, Austria, paper GT-2004-53644, which is incorporated by reference herein. A pre-publication copy of this paper was filed and integrated into U.S. provisional patent application No. 60/579,866 filed Jun. 15, 2004 from which, this application claims priority benefit. This is in contrast to the current technology, where having the precise alignment at the coupling is considered to be good practice for all rotating machines. In fact, U.S. Pat. No. 4,033,042, entitled “Shaft alignment apparatus and method” describes techniques to improve alignment between rotors at the coupling.
- The invention described herein is quite simple and straightforward. The idea is to disturb the flow in the axial direction, thus improving the instability. In its simplest form, a sleeve (journal) bearing is manufactured such that the bearing axis is skewed with the shaft axis. Thus the shaft axis is straight horizontally, while the bearing axis is tilted in the vertical direction, with a predetermined slope. One end is lower than the shaft axis, while the other end is higher than the shaft axis. The same invention applies for a fixed geometry bearing, but in the horizontal direction. The bearing axis is tilted sideways (to the right) thus presenting a predetermined horizontal misalignment at the bearing.
- In another embodiment, a variable geometry bearing allows for bearing angular misalignment. The basic idea is quite simple. Suppose the predetermined slope for the bearings is not known beforehand, and requires adjustment in the field. In this case, consider a simple cylindrical journal bearing, where the fixing bolts are allowed a certain passageway such that it is possible to skew the whole cylindrical journal bearing (or any type fluid bearing) whereby the bearing axis has a certain slope to the shaft axis, and this slope is adjustable. When the appropriate slope is selected, the fixing bolts are used to fix the bearing body (and the passageway) to the skid or pedestal.
- The above described embodiments are the simplest forms of the invention and are further supported by the experiments described in the above mentioned technical paper presented at the Proceedings 2004 ASME Turbo Expo Power for Land, Sea and Air on Jun. 15, 2004.
- However, this invention opens the door to many other possibilities in designing fluid film bearings. This includes the introduction of two offset halves of the bearing, just by simply introducing a skewness between the upper and lower portions (this is in contrast to the current technology where the offset halves are offset horizontally). Other embodiments include introducing elliptic, multi-lobe, pressure dam, and tilting pads in the axial rather than the circumferential directions as current technology implies. Any possibility of modifying or disturbing the flow along the axis of the bearing for controlling oil whirl and oil whip is an embodiment of this invention.
- In the accompanying drawings:
-
FIG. 1 is an elevation view of one embodiment of the invention depicting the adjacent magnetic-journal bearing support of a rotor, showing a cross-sectional view of the embodiment; -
FIG. 2 a is an elevation view of another embodiment of the invention depicting the non-adjacent magnetic-journal bearing support of a rotor, showing a cross-sectional view of the embodiment; -
FIG. 2 b is a detailed view of detail B taken fromFIG. 2 a; -
FIG. 3 is an elevation view of another embodiment of the invention depicting an integrated magnetic-journal bearing, showing a cross-sectional view of the embodiment; -
FIGS. 4 a-4 c collectively depict the vertically inclined fixed geometry assembly embodiment of the invention; -
FIGS. 5 a-5 d collectively depict the horizontally inclined fixed geometry bearing assembly embodiment of the invention; -
FIGS. 6 a-6 c collectively depict the tilting housing bearing embodiment of the invention; -
FIGS. 7 a-7 e collectively depict the upper tilting half bearing embodiment of the invention; -
FIGS. 8 a-8 d collectively depict the inclined pressure dam bearing embodiment of the invention; -
FIGS. 9 a-9 d collectively depict the inclined multi-lobe bearing embodiment of the invention; -
FIGS. 10 a-10 c collectively depict the converging-diverging bearing assembly embodiment of the invention; -
FIGS. 11 a-11 d collectively depict the diverging-converging bearing assembly embodiment of the invention; -
FIGS. 12 a-12 d collectively depict the convergent bearing embodiment of the invention; -
FIGS. 13 a-13 d collectively depict the divergent bearing assembly embodiment of the invention; -
FIGS. 14 a-14 d collectively depict the tilting pad bearing embodiment of the invention; -
FIGS. 15 a-15 d show a tilting pad bearing assembly with a Divergent-Convergent pad that rocks on the bearing axially, and/or has an axial Divergent-Convergent profile; -
FIGS. 16 a-16 d show a tilting pad bearing assembly with a Convergent-Divergent pad that rocks on the bearing axially, and/or has an axial Convergent-Divergent profile; -
FIGS. 17 a-17 d show a tilting pad bearing assembly with an axially twisted pad; and -
FIGS. 18 a-18 d show a tilting pad bearing assembly with an axially stepped pad. - The invention is a method of controlling the instability in fluid film bearings by using a magnetic bearing in combination with a fluid film bearing (whether it is a cylindrical journal bearing, an elliptic bearing, an offset-half bearing, a multi-lobe bearing, foil bearing or a tilting-pad bearing, does not really matter), wherein the fluid film bearing serves as the primary load carrying bearing and the magnetic bearing controls the instability of the fluid film bearing. This efficient combination results in bearings that can be used at high speeds without having neither stability nor reliability problems. An alternative method of controlling the instability in fluid film bearings is to disturb the flow in the axial direction, for example, a sleeve (journal) bearing can be manufactured such that the bearing axis is skewed with the shaft axis or a variable geometry bearing can be manufactured to allow for bearing angular misalignment.
- Now referring to the drawings,
FIGS. 1 to 3 depict the various embodiments of the combined Magnetic Bearing-Fluid Film Bearing invention, in the Adjacent, Non-Adjacent and Integral embodiments, respectively. -
FIG. 1 shows the configuration of the Adjacent Magnetic Bearing-Fluid Film Bearing configuration. The elevation view is shown inFIG. 1 , where amagnetic bearing assembly 12 comprising an electro-magnetic stator 12 a is fixed in ahousing 12 b, and is used to control therotor 12 c, mounted on theshaft 16. The load carrying element is the fluidfilm bearing assembly 18, supported by thehousing 18 a. The load is carried by the fluid film bearing 18, while themagnetic bearing 12 is used to control the instability that occurs in the fluid film bearing 18 at high speeds. -
FIGS. 2 a-2 b show the configuration of the Non-Adjacent Magnetic Bearing-Fluid Film Bearing configuration.FIG. 2 a shows the elevation view, where amagnetic bearing assembly 12 comprising an electro-magnetic stator 12 a is fixed in ahousing 12 b, and is used to control therotor 12 c, mounted on theshaft 16. The load-carrying element is the fluidfilm bearing assembly 18, supported by thehousing 18 a. The load is carried by the fluid film bearing 18, while themagnetic bearing 12 is used to control the instability that occurs in the fluid film bearing 18 at high speeds.FIG. 2 b shows the detail of themagnetic bearing stator 12 a with windings,rotor 12 c,housing 12 b andshaft 16. The main difference betweenFIG. 1 andFIG. 2 is that inFIG. 1 , the Magnetic Bearing and the Fluid Film Bearing are adjacent (close to each other); while inFIG. 2 , the Magnetic Bearing and the Fluid Film Bearing are non-adjacent (relatively far or distantly spaced-apart from each other). -
FIG. 3 shows the configuration of the Integral Magnetic Bearing-FluidFilm Bearing assembly 14 configuration. The elevation view is shown inFIG. 3 , where amagnetic bearing 14 d comprising anelectromagnetic stator 14 a is fixed in ahousing 14 b, and is used to control therotor 14 c, mounted on theshaft 16. The load carrying element is the fluid film bearing 14 e, where the fluid film is filling the clearance between thestator 14 a and therotor 14 c. The load is carried by the fluid film bearing 14 e, while themagnetic bearing 14 d is used to control the instability that occurs in the fluid film bearing 14 e at high speeds. This is a compact configuration with the fluid film bearing 14 e integrated into themagnetic bearing 14 d. -
FIGS. 4 to 18 depict the various examples of embodiments of the Stable Fluid Film Bearing, including the Vertically Inclined Fixed Geometry Bearing, the Horizontally Inclined Fixed Geometry Bearing, the Tilting Housing Bearing, the Upper Tilted Half Bearing, the Inclined Pressure Dam Bearing, the Inclined Multi-Lobed Bearing, the Converging-Diverging Bearing, the Diverging Converging Bearing, the Converging Bearing, the Diverging Bearing, and the Axially Tilting Pad Bearing and variants. - An example of the Vertically Inclined Fixed
Geometry Bearing assembly 20 embodiment is shown inFIGS. 4 a-4 c. The bearing 20 a is vertically inclined to promote the stability of the system (see section C-C,FIG. 4 b). Thefluid film 20 b is carrying theshaft 20 c, on the bearing 20 a, and is sealed using the sealing 20 d. The housing halves, housinglower part 20 e and housingupper part 20 f, are part of the bearingassembly 20 and carry the bearing 20 a. Theshaft axis 20 g in this case for a horizontal machine would be horizontal, but the bearing itself is inclined vertically to promote stability. - An example of the Horizontally Inclined Fixed
Geometry Bearing assembly 30 embodiment is shown inFIGS. 5 a-5 d. The bearing 30 a is horizontally inclined to promote the stability of the system (see section B-B,FIG. 5 c). Thefluid film 30 b is carrying theshaft 30 c, on the bearing 30 a, and is sealed using the sealing 30 d. The housing halves, housinglower part 30 e and housingupper part 30 f, are part of the bearingassembly 30 and carry the bearing 30 a. FIG. 5 d shows a schematic of the two bearing halves with the horizontal inclination. Theshaft axis 30 g in this case for a horizontal machine would be horizontal and the bearing itself is inclined horizontally to the machine axis to promote stability. -
FIGS. 6 a-6 c show an example of the TiltingHousing Bearing assembly 40 embodiment. The bearing 40 a is straight, and the housing, comprising housinglower part 40 b and housingupper part 40 c, is adjustable. Twobolts 40 d, on each side, are used to fix the housing to the support. A curved groove in thehousing parts bolt 40 d. By loosening thebolts 40 d, it is possible to twist thehousing parts shaft 40 e, and then tightening them again to fix the amount of twist as desired. This should lead to a stable bearing that can have the angular misalignment of the bearing adjusted. -
FIGS. 7 a-7 e show an example of the Upper TiltingHalf Bearing assembly 50 embodiment. In this embodiment, only theupper bearing half 50 a is tilted and misaligned to theshaft 50 c axis, while thelower bearing half 50 b is normal. This is best seen inFIGS. 7 d and 7 e. These latter two drawings further depictoil film 50 d and housing upper andlower parts upper half 50 a tilted (axis skewed to shaft axis). Actually, the drawings provided are for a bearing that has anupper half 50 a that is both offset and tilted. -
FIGS. 8 a-8 d show an example of the Inclined PressureDam Bearing assembly 60 embodiment. This bearing 60 a is essentially a cylindrical bearing, but with adam 60 d. The purpose of the dam is to disturb the flow and load the bearing, thus improving its stability characteristics. The current technology allows for the dam. However, the invention claimed is in a dam that has its edges tilted with respect to theaxis 60 c of theshaft 60 b, thus providing for the angular loading and axial flow disturbance. Section A-A ofFIG. 8 b, and enlarged inFIG. 8 c show the dam. The oil film is shown as 60 e inFIG. 8 c. The details of the inclined dam are shown inFIG. 8 d. -
FIGS. 9 a-9 d show an example of the InclinedMulti-Lobe Bearing assembly 70 embodiment. The current technology allows for the multi-lobe bearing 70 a to be consisting of several lobes, each lobe has its center of curvature in a different position, thus providing circumferential disturbance to the flow, and improving stability. This is in contrast to the cylindrical bearing, which has only one center. The multi-lobe bearing can have two-lobes (which is the elliptic bearing, in which the upper and lower halves have two different centers), three-lobes, four-lobes (as depicted inFIGS. 9 a-9 d), or more. Our claim for the invention is that not only that each lobe has its own center of curvature (see 70 b inFIG. 9 d), but also each lobe is tilted axially, such as to disturb the flow axially, as clearly illustrated inFIG. 9 d, and the sections A-A and B-B shown inFIGS. 9 b and 9 c, respectively. - To complete the ideas for disturbing the flow axially, one can envision a convergent bearing, a divergent bearing, a convergent-divergent bearing, or a divergent-convergent bearing. There are no similar bearings in the current technology, but such embodiments can improve the stability through the axial flow disturbance.
- As alluded to above, these embodiments are shown as follows: the Convergent-Divergent Bearing Assembly 80 (
FIGS. 10 a-10 c), the Divergent-Convergent Bearing assembly 90 (FIGS. 11 a-11 d), the Convergent Bearing assembly 100 (FIGS. 12 a-12 d), and the Divergent Bearing assembly 110 (FIGS. 13 a-13 d). In all these bearing assemblies, the corresponding bearing 80 a,90 a,100 a,110 a, has the axial disturbance of the flow suggested by each of their names respectively, with respect to therespective shaft - Another embodiment example is a tilting
pad bearing assembly 120. These bearings are designed to havemultiple pads 120 b that essentially can rock circumferentially, thus disturbing the flow circumferentially.FIGS. 14 a-14 d representationally show this embodiment, which allows appreciable rocking in the axial direction, thus disturbing the flow axially.FIG. 14 d shows thetilting pads 120 b that are allowed to rock axially on theouter casing 120 c. - To further accentuate the axial flow disturbance in tilting pad bearings, further embodiments of the invention are shown in
FIGS. 15 , 16, 17 and 18.FIGS. 15 a-15 d show a tiltingpad bearing assembly 130 with a Divergent-Convergent pad 130 b that rocks on thebearing 130 c axially, and/or has an axial Divergent-Convergent profile, whileFIGS. 16 a-16 d show a tiltingpad bearing assembly 140 with a Convergent-Divergent pad 140 b that rocks on thebearing 140 c axially, and/or has an axial Convergent-Divergent profile.FIGS. 17 a-17 d show a tiltingpad bearing assembly 150 with an axiallytwisted pad 150 b, whileFIGS. 18 a-18 d show a tiltingpad bearing assembly 160 with an axially steppedpad 160 b. - These embodiments are all different embodiments of the current invention that provide progressively enhanced stability by disturbing the axial flow.
- The present invention can also be applied to foil bearings using the conceptual embodiments described above. The inventive configurations described above of axial flow disturbance can be applied to foil bearings, through axial flow disturbance, by twisting or tilting as discussed above.
- It should be understood that the preceding is merely a detailed description of one or more embodiments of this invention and that numerous changes to the disclosed embodiments can be made in accordance with the disclosure herein without departing from the spirit and scope of the invention. The preceding description, therefore, is not meant to limit the scope of the invention. Rather, the scope of the invention is to be detennined only by the appended claims and their equivalents.
Claims (5)
1. A method of controlling the instability in radial fluid film bearings, including fluid film bearings used in high speed rotor or shaft assemblies, the method comprising:
using a magnetic bearing in combination with a radial fluid film bearing,
wherein the radial fluid film bearing is adapted to serve as a primary load carrying bearing; and
wherein the magnetic bearing is adapted to serve as means for tangentially controlling the instability in the radial fluid film bearing, by withstanding tangential loads causing the instability arising from the radial fluid film bearing.
2. The method according to claim 1 , wherein the radial fluid film bearing is selected from the group consisting of cylindrical journal bearings, elliptic bearings, offset-half bearings, multi-lobe bearings, tilting-pad bearings, and foil bearings.
3. The method according to claim 1 , wherein the combination is in the form of two adjacent or non-adjacent bearings, one being the radial fluid film bearing and the other being the magnetic bearing.
4. The method according to claim 1 , wherein the combination is in the form of one integral bearing having the fluid film bearing within the magnetic bearing, such that a fluid for the fluid film bearing passes over a rotor of the magnetic bearing, and within a clearance between the rotor and a stator in the magnetic bearing.
5-28. (canceled)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/121,976 US20080224556A1 (en) | 2004-06-15 | 2008-05-16 | Methods of controlling the instability in fluid film bearings |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US57986604P | 2004-06-15 | 2004-06-15 | |
US11/147,762 US7836601B2 (en) | 2004-06-15 | 2005-06-08 | Methods of controlling the instability in fluid film bearings |
US12/121,976 US20080224556A1 (en) | 2004-06-15 | 2008-05-16 | Methods of controlling the instability in fluid film bearings |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/147,762 Division US7836601B2 (en) | 2004-06-15 | 2005-06-08 | Methods of controlling the instability in fluid film bearings |
Publications (1)
Publication Number | Publication Date |
---|---|
US20080224556A1 true US20080224556A1 (en) | 2008-09-18 |
Family
ID=35459816
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/147,762 Expired - Fee Related US7836601B2 (en) | 2004-06-15 | 2005-06-08 | Methods of controlling the instability in fluid film bearings |
US12/121,976 Abandoned US20080224556A1 (en) | 2004-06-15 | 2008-05-16 | Methods of controlling the instability in fluid film bearings |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/147,762 Expired - Fee Related US7836601B2 (en) | 2004-06-15 | 2005-06-08 | Methods of controlling the instability in fluid film bearings |
Country Status (9)
Country | Link |
---|---|
US (2) | US7836601B2 (en) |
EP (1) | EP1792093A4 (en) |
JP (2) | JP5069103B2 (en) |
KR (1) | KR20070039922A (en) |
BR (1) | BRPI0511385A (en) |
CA (1) | CA2570052A1 (en) |
IL (1) | IL179953A0 (en) |
RU (1) | RU2399803C2 (en) |
WO (1) | WO2005122684A2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9279289B2 (en) | 2013-10-03 | 2016-03-08 | Renegade Manufacturing, LLC | Combination mud motor flow diverter and tiled bearing, and bearing assemblies including same |
WO2017201151A1 (en) * | 2016-05-17 | 2017-11-23 | Aly El-Shafei | Integrated journal bearing |
Families Citing this family (35)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007092646A (en) * | 2005-09-29 | 2007-04-12 | Jtekt Corp | Supercharger for fuel cell |
WO2011044423A2 (en) * | 2009-10-09 | 2011-04-14 | Dresser-Rand Company | Auxiliary bearing system with oil ring for magnetically supported rotor system |
WO2011044432A2 (en) * | 2009-10-09 | 2011-04-14 | Dresser-Rand Company | Auxiliary bearing system with plurality of inertia rings for magnetically supported rotor system |
WO2011044428A2 (en) * | 2009-10-09 | 2011-04-14 | Dresser-Rand Company | Auxiliary bearing system for magnetically supported rotor system |
EP2486296A4 (en) * | 2009-10-09 | 2015-07-15 | Dresser Rand Co | Auxiliary bearing system with oil reservoir for magnetically supported rotor system |
DK200970278A (en) * | 2009-12-17 | 2010-12-13 | Vestas Wind Sys As | Vibration damping of wind turbine shaft |
EP2524148A4 (en) | 2010-01-15 | 2015-07-08 | Dresser Rand Co | Bearing assembly support and adjustment system |
GR1007565B (en) * | 2010-09-08 | 2012-03-26 | ΠΑΝΕΠΙΣΤΗΜΙΟ ΠΑΤΡΩΝ (κατά ποσοστό 40%), | Hybrid sliding-contact bearing |
WO2013109235A2 (en) | 2010-12-30 | 2013-07-25 | Dresser-Rand Company | Method for on-line detection of resistance-to-ground faults in active magnetic bearing systems |
US8994237B2 (en) | 2010-12-30 | 2015-03-31 | Dresser-Rand Company | Method for on-line detection of liquid and potential for the occurrence of resistance to ground faults in active magnetic bearing systems |
WO2012138545A2 (en) | 2011-04-08 | 2012-10-11 | Dresser-Rand Company | Circulating dielectric oil cooling system for canned bearings and canned electronics |
WO2012166236A1 (en) | 2011-05-27 | 2012-12-06 | Dresser-Rand Company | Segmented coast-down bearing for magnetic bearing systems |
US8574118B2 (en) | 2011-05-31 | 2013-11-05 | United Technologies Corporation | Journal pin for gear system |
US8851756B2 (en) | 2011-06-29 | 2014-10-07 | Dresser-Rand Company | Whirl inhibiting coast-down bearing for magnetic bearing systems |
FR2989296B1 (en) * | 2012-04-13 | 2014-05-02 | Alstom Hydro France | FRET FOR HYDROSTATIC OR HYDRODYNAMIC BEARING, METHOD OF MOUNTING SUCH FREIGHT ON A SHAFT, ASSEMBLY FORMED OF SUCH FREIGHT AND TREE |
WO2014040641A1 (en) * | 2012-09-14 | 2014-03-20 | Statoil Petroleum As | Bearing system for rotor in rotating machines |
RU2518053C1 (en) * | 2012-10-04 | 2014-06-10 | Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Уфимский государственный авиационный технический университет" | Method and device for control of rotor position at magnetic bearings |
US9404534B2 (en) | 2012-11-30 | 2016-08-02 | Honeywell International Inc. | Rotating assemblies of turbomachinery, foil journal bearing assemblies thereof, and methods for producing journals of the foil journal bearing assemblies |
US9657594B2 (en) * | 2013-03-12 | 2017-05-23 | Rolls-Royce Corporation | Gas turbine engine, machine and self-aligning foil bearing system |
TWI603909B (en) | 2013-10-14 | 2017-11-01 | Chan Li Machinery Co Ltd | Folding wheel with modular bearing unit |
CN103883880B (en) * | 2014-04-14 | 2016-11-09 | 东北石油大学 | The cold defeated fluidization equipment of poly-repelling crude oil |
CN108779801B (en) | 2016-02-02 | 2021-03-09 | 博格华纳公司 | Bearing and process for making and using same |
CN105570300B (en) | 2016-03-16 | 2018-01-02 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of axial magnetic suspension bearing |
WO2018057717A1 (en) * | 2016-09-24 | 2018-03-29 | Radiant Physics Inc. | Pressurized gas bearings for rotating machinery |
US10612420B2 (en) * | 2016-11-17 | 2020-04-07 | General Electric Company | Support structures for rotors |
US20180216484A1 (en) | 2017-01-31 | 2018-08-02 | General Electric Company | Systems and methods to detect a fluid induced instability condition in a turbomachine |
JP6899235B2 (en) * | 2017-03-24 | 2021-07-07 | 三菱重工業株式会社 | Bearing pads for tilting pad bearings, tilting pad bearings and rotating machinery |
RU2656871C1 (en) * | 2017-04-28 | 2018-06-07 | федеральное государственное бюджетное образовательное учреждение высшего образования "Уфимский государственный авиационный технический университет" | Method of controlling the rotor position of electric machine on non-contact bearings (variants) and electric machine for its implementation |
RU185576U1 (en) * | 2018-06-18 | 2018-12-11 | Федеральное государственное автономное образовательное учреждение высшего образования "Сибирский федеральный университет" | ADAPTIVE DEVICE-DAMPER |
CN109210078A (en) * | 2018-10-08 | 2019-01-15 | 西安科技大学 | A kind of efficiently cooling radial passive Permanent-magnet bearing structure of big damping |
CN110488853B (en) * | 2019-08-29 | 2021-06-08 | 北京航空航天大学 | Hybrid inertial navigation system stability control instruction calculation method for reducing rotating shaft vortex influence |
CN111122157B (en) * | 2019-11-26 | 2020-12-18 | 燕山大学 | Magnetic-liquid double-suspension bearing experiment table |
US11585235B2 (en) | 2020-11-18 | 2023-02-21 | Rolls-Royce North American Technologies Inc. | Magnetic shaft mode control |
CN112555273A (en) * | 2020-12-03 | 2021-03-26 | 武汉理工大学 | Magnetic suspension and elastic foil gas mixing bearing experiment platform |
WO2022199997A1 (en) * | 2021-03-26 | 2022-09-29 | Sulzer Management Ag | Vertical pump |
Citations (81)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2983832A (en) * | 1958-01-28 | 1961-05-09 | Air Glide Inc | Fluid supported rotor |
US3302865A (en) * | 1964-07-16 | 1967-02-07 | Union Carbide Corp | Gas-bearing assembly |
US3357756A (en) * | 1962-08-22 | 1967-12-12 | Commissariat Energie Atomique | Bearing means for vertically mounted motors |
US3395949A (en) * | 1964-07-16 | 1968-08-06 | Union Carbide Corp | Gas-bearing assembly |
US3845997A (en) * | 1972-03-20 | 1974-11-05 | Padana Ag | Magnetic bearing assembly for journalling a rotor in a stalor |
US3969804A (en) * | 1973-12-27 | 1976-07-20 | Rajay Industries, Inc. | Bearing housing assembly method for high speed rotating shafts |
US4033042A (en) * | 1974-10-10 | 1977-07-05 | Bently Nevada Corporation | Shaft alignment apparatus and method |
US4034228A (en) * | 1974-09-30 | 1977-07-05 | Siemens Aktiengesellschaft | Tubus for determining the boundaries of a beam of penetrating rays |
US4128280A (en) * | 1977-01-17 | 1978-12-05 | Sulzer Brothers Limited | Self-pressurizing floating gas bearing having a magnetic bearing therein |
US4320927A (en) * | 1980-03-21 | 1982-03-23 | Sertich Anthony T | Dental drill with magnetic air turbine having magnetic bearings |
US4378091A (en) * | 1980-05-21 | 1983-03-29 | Toyota Jidosha Kabushiki Kaisha | Rotary type electrostatic spray painting device |
US4415281A (en) * | 1981-11-23 | 1983-11-15 | United Technologies Corporation | Hydrodynamic fluid film bearing |
US4523800A (en) * | 1982-07-20 | 1985-06-18 | Tokyo Shibaura Denki Kabushiki Kaisha | Polygonal mirror optical deflector |
US4526483A (en) * | 1981-06-29 | 1985-07-02 | Shimadzu Corporation | Fluid foil bearing |
US4597676A (en) * | 1984-04-30 | 1986-07-01 | General Electric Company | Hybrid bearing |
US4608835A (en) * | 1983-11-02 | 1986-09-02 | Hermen Kooy | Cabinet for cooling goods, etc. |
US4767223A (en) * | 1986-12-03 | 1988-08-30 | National Research Development Corporation | Hydrodynamic journal bearings |
US4781077A (en) * | 1986-12-19 | 1988-11-01 | Massachusetts Institute Of Technology | Stable intershaft squeeze film damper |
US4820950A (en) * | 1987-03-03 | 1989-04-11 | Copal Company Limited | Fluid Bearing |
US4827169A (en) * | 1986-12-31 | 1989-05-02 | Societe De Mecanique Magnetique | Hybrid fluid bearing with stiffness modified by electromagnetic effect |
US4828403A (en) * | 1987-04-03 | 1989-05-09 | Schwartzman Everett H | Resiliently mounted fluid bearing assembly |
US4839550A (en) * | 1982-11-11 | 1989-06-13 | Seiko Seiki Kabushiki Kaisha | Controlled type magnetic bearing device |
US4841212A (en) * | 1986-09-12 | 1989-06-20 | Hitachi, Ltd. | Electromagnetic bearing control apparatus |
US4880320A (en) * | 1987-03-10 | 1989-11-14 | British Aerospace Plc | Fluid film journal bearings |
US4885491A (en) * | 1987-10-28 | 1989-12-05 | National Aerospace Laboratory | Unstable vibration prevention apparatus for magnetic bearing system |
US4910449A (en) * | 1987-05-18 | 1990-03-20 | Ebara Corporation | System for preventing unbalance vibrations and synchronous disturbance vibrations |
US4961122A (en) * | 1987-05-11 | 1990-10-02 | Hitachi, Ltd. | Hydrodynamic grooved bearing device |
US4999534A (en) * | 1990-01-19 | 1991-03-12 | Contraves Goerz Corporation | Active vibration reduction in apparatus with cross-coupling between control axes |
US5032028A (en) * | 1988-09-20 | 1991-07-16 | Abg Semca S.A. | Fluid film bearing |
US5059845A (en) * | 1990-05-07 | 1991-10-22 | Mechanical Technology Incorporated | Active magnetic bearing device for controlling rotor vibrations |
US5084643A (en) * | 1991-01-16 | 1992-01-28 | Mechanical Technology Incorporated | Virtual rotor balancing in magnetic bearings |
US5096309A (en) * | 1989-04-03 | 1992-03-17 | Canon Kabushiki Kaisha | Hydrodynamic bearing system |
US5104284A (en) * | 1990-12-17 | 1992-04-14 | Dresser-Rand Company | Thrust compensating apparatus |
US5126612A (en) * | 1987-04-09 | 1992-06-30 | Societe Europeenne De Propulsion | Active radial magnetic bearing combined with a back-up bearing |
US5142177A (en) * | 1988-04-22 | 1992-08-25 | Toshiro Higuchi | Magnetically controlled bearing unit |
US5181783A (en) * | 1990-07-16 | 1993-01-26 | Lincoln Laser Co. | Apparatus for eliminating whirl instability in a gas supported bearing |
US5201585A (en) * | 1991-12-31 | 1993-04-13 | General Electric Company | Fluid film journal bearing with squeeze film damper for turbomachinery |
US5202824A (en) * | 1990-06-21 | 1993-04-13 | Mechanical Technology Incorporated | Rotating force generator for magnetic bearings |
US5223758A (en) * | 1990-03-05 | 1993-06-29 | Ebara Corporation | Spindle motor |
US5300808A (en) * | 1992-05-04 | 1994-04-05 | Motorola, Inc. | EPROM package and method of optically erasing |
US5321329A (en) * | 1993-03-25 | 1994-06-14 | Hovorka Patent Trust | Permanent magnet shaft bearing |
US5322371A (en) * | 1988-12-23 | 1994-06-21 | Abg Semca Sa | Fluid film bearing |
US5345127A (en) * | 1992-07-23 | 1994-09-06 | The Glacier Metal Company Limited | Magnetic bearing back-up |
US5441453A (en) * | 1993-06-03 | 1995-08-15 | W.S. Tyler, Incorporated | Vibrating shaft assembly having magnetic compensation for reducing shaft bearing loads |
US5480234A (en) * | 1994-08-15 | 1996-01-02 | Ingersoll-Rand Company | Journal bearing |
US5489155A (en) * | 1987-05-29 | 1996-02-06 | Ide; Russell D. | Tilt pad variable geometry bearings having tilting bearing pads and methods of making same |
US5516212A (en) * | 1995-09-18 | 1996-05-14 | Western Digital Corporation | Hydrodynamic bearing with controlled lubricant pressure distribution |
US5531523A (en) * | 1995-06-02 | 1996-07-02 | Westinghouse Electric Corporation | Rotor journal bearing having adjustable bearing pads |
US5549392A (en) * | 1995-05-02 | 1996-08-27 | Nastec, Inc. | Resilient mount pad journal bearing |
US5634723A (en) * | 1995-06-15 | 1997-06-03 | R & D Dynamics Corporation | Hydrodynamic fluid film bearing |
US5660481A (en) * | 1987-05-29 | 1997-08-26 | Ide; Russell D. | Hydrodynamic bearings having beam mounted bearing pads and sealed bearing assemblies including the same |
US5743657A (en) * | 1994-08-06 | 1998-04-28 | The Glacier Metal Company Limited | Tilting pad journal bearing |
US5743654A (en) * | 1987-05-29 | 1998-04-28 | Kmc, Inc. | Hydrostatic and active control movable pad bearing |
US5772334A (en) * | 1994-04-27 | 1998-06-30 | British Technology Group Limited | Fluid film bearings |
US5879076A (en) * | 1995-02-08 | 1999-03-09 | Flexalite Technology Corporation | Method and appartus for light transmission |
US5879085A (en) * | 1995-10-13 | 1999-03-09 | Orion Corporation | Tilt pad hydrodynamic bearing for rotating machinery |
US5977677A (en) * | 1996-06-26 | 1999-11-02 | Allison Engine Company | Combination bearing for gas turbine engine |
US6005315A (en) * | 1997-05-30 | 1999-12-21 | Electric Boat Corporation | Fault-tolerant magnetic bearing control system architecture |
US6089756A (en) * | 1997-03-18 | 2000-07-18 | Daido Metal Company Ltd. | Plain bearing |
US6135640A (en) * | 1995-06-30 | 2000-10-24 | Alliedsignal Inc. | Hybrid foil/magnetic bearing |
US6194801B1 (en) * | 1998-10-15 | 2001-02-27 | Skf Nova Ab | Device for limiting shaft whirl |
US6236130B1 (en) * | 1998-02-03 | 2001-05-22 | Sulzer Electronics Ag | Method and arrangement for the excitation of the journalling winding and the drive winding systems in electrical machines with magnetic journalling, and an electrical drive |
US6288465B1 (en) * | 1997-04-28 | 2001-09-11 | Ntn Corporation | Combined externally pressurized gas-magnetic bearing assembly and spindle device utilizing the same |
US6353273B1 (en) * | 1997-09-15 | 2002-03-05 | Mohawk Innovative Technology, Inc. | Hybrid foil-magnetic bearing |
US20020174734A1 (en) * | 1999-11-16 | 2002-11-28 | David Chinery | Swashplate design |
US20030038552A1 (en) * | 2000-08-21 | 2003-02-27 | Board Of Trustees Operating Michigan State University | Adaptive compensation of sensor run-out and mass unbalance in magnetic bearing systems without changing rotor speed |
US6590366B1 (en) * | 2000-11-02 | 2003-07-08 | General Dyanmics Advanced Technology Systems, Inc. | Control system for electromechanical arrangements having open-loop instability |
US6606536B1 (en) * | 1999-02-25 | 2003-08-12 | Seiko Instruments Inc. | Magnetic bearing device and magnetic bearing control device |
US6653756B2 (en) * | 2000-01-14 | 2003-11-25 | Koyo Seiko Co., Ltd. | Magnetic bearing device |
US6686674B2 (en) * | 2000-12-04 | 2004-02-03 | Kura Laboratory Corporation | Motor having single cone fluid dynamic bearing balanced with magnetic attraction |
US6703736B2 (en) * | 2001-12-24 | 2004-03-09 | Industrial Technology Research Institute | Magnetic bearing |
US6707200B2 (en) * | 2000-11-14 | 2004-03-16 | Airex Corporation | Integrated magnetic bearing |
US6717311B2 (en) * | 2001-06-14 | 2004-04-06 | Mohawk Innovative Technology, Inc. | Combination magnetic radial and thrust bearing |
US6720695B2 (en) * | 2000-07-04 | 2004-04-13 | W. Schlafhorst Ag & Co. | Rotor spinning device with a contactless, passive, radial bearing for the spinning rotor |
US6737777B2 (en) * | 1998-10-14 | 2004-05-18 | Jenoptik Ldt Gmbh | Magnetic bearing and use thereof |
US6737617B1 (en) * | 2000-01-24 | 2004-05-18 | General Electric Company | Methods and apparatus for a signal distortion based detection system |
US6749339B1 (en) * | 1999-09-03 | 2004-06-15 | Sumitomo Electric Industries, Ltd. | Hydrodynamic bearing assembly and spindle motor having the same |
US6770992B2 (en) * | 2000-10-16 | 2004-08-03 | Boc Edwards Japan Limited | Magnetic bearing apparatus |
US6786642B2 (en) * | 2002-08-30 | 2004-09-07 | Pratt & Whitney Canada Corp. | Compliant foil-fluid bearing support arrangement |
US6948853B2 (en) * | 2002-10-03 | 2005-09-27 | R & D Dynamics Corporation | High load capacity stacked foil thrust bearing assembly |
US7217039B2 (en) * | 2001-06-15 | 2007-05-15 | Societe De Mecanique Magnetique | Axial load-insensitive emergency bearing |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3360309A (en) * | 1966-05-11 | 1967-12-26 | Gen Motors Corp | Self-aligning eternally pressurized fluid bearing |
US3659910A (en) * | 1970-05-06 | 1972-05-02 | Gen Motors Corp | Retainer for spherical adapter |
US3746407A (en) * | 1971-08-13 | 1973-07-17 | Litton Systems Inc | Ferrohydrodynamic low friction bearing |
US4274683A (en) * | 1978-12-29 | 1981-06-23 | Mechanical Technology Incorporated | Support element for compliant hydrodynamic journal bearings |
JPS55135225A (en) * | 1979-04-06 | 1980-10-21 | Hitachi Ltd | Tilting pad journal bearing |
US4247155A (en) * | 1979-06-13 | 1981-01-27 | United Technologies Corporation | Resilient foil bearings |
US4502795A (en) * | 1982-09-30 | 1985-03-05 | The Garrett Corporation | Foil bearing alignment |
FR2609133B1 (en) | 1986-12-31 | 1989-12-15 | Mecanique Magnetique Sa | ELECTROMAGNETIC DEVICE FOR REDUCING VIBRATION IN A ROTATING MACHINE EQUIPPED WITH FLUID BEARINGS |
JPH04258525A (en) * | 1991-02-13 | 1992-09-14 | Ricoh Co Ltd | Light deflection device |
JPH0655309A (en) * | 1992-08-04 | 1994-03-01 | Seiko Seiki Co Ltd | Spindle supporting device |
JP3693384B2 (en) * | 1995-06-14 | 2005-09-07 | Ntn株式会社 | Magnetic bearing spindle device |
US5915841A (en) * | 1998-01-05 | 1999-06-29 | Capstone Turbine Corporation | Compliant foil fluid film radial bearing |
US6190048B1 (en) * | 1998-11-18 | 2001-02-20 | Capstone Turbine Corporation | Compliant foil fluid film radial bearing |
US6224263B1 (en) * | 1999-01-22 | 2001-05-01 | Alliedsignal Inc. | Foil thrust bearing with varying circumferential and radial stiffness |
US6168403B1 (en) * | 1999-05-10 | 2001-01-02 | Carrier Corporation | Rotating compressor bearing with dual taper |
JP2002352488A (en) * | 2001-05-25 | 2002-12-06 | Matsushita Electric Ind Co Ltd | Pinch roller |
US6727617B2 (en) * | 2002-02-20 | 2004-04-27 | Calnetix | Method and apparatus for providing three axis magnetic bearing having permanent magnets mounted on radial pole stack |
JP2003214428A (en) * | 2002-12-26 | 2003-07-30 | Ibiden Co Ltd | High-speed rotating body |
-
2005
- 2005-06-08 BR BRPI0511385-7A patent/BRPI0511385A/en not_active IP Right Cessation
- 2005-06-08 RU RU2006146875/11A patent/RU2399803C2/en not_active IP Right Cessation
- 2005-06-08 CA CA002570052A patent/CA2570052A1/en not_active Abandoned
- 2005-06-08 EP EP05781597A patent/EP1792093A4/en not_active Withdrawn
- 2005-06-08 KR KR1020077000874A patent/KR20070039922A/en active Search and Examination
- 2005-06-08 JP JP2007516079A patent/JP5069103B2/en not_active Expired - Fee Related
- 2005-06-08 US US11/147,762 patent/US7836601B2/en not_active Expired - Fee Related
- 2005-06-08 WO PCT/IB2005/002732 patent/WO2005122684A2/en active Search and Examination
-
2006
- 2006-12-10 IL IL179953A patent/IL179953A0/en unknown
-
2008
- 2008-05-16 US US12/121,976 patent/US20080224556A1/en not_active Abandoned
-
2012
- 2012-05-10 JP JP2012108503A patent/JP2012177480A/en active Pending
Patent Citations (82)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2983832A (en) * | 1958-01-28 | 1961-05-09 | Air Glide Inc | Fluid supported rotor |
US3357756A (en) * | 1962-08-22 | 1967-12-12 | Commissariat Energie Atomique | Bearing means for vertically mounted motors |
US3302865A (en) * | 1964-07-16 | 1967-02-07 | Union Carbide Corp | Gas-bearing assembly |
US3395949A (en) * | 1964-07-16 | 1968-08-06 | Union Carbide Corp | Gas-bearing assembly |
US3845997A (en) * | 1972-03-20 | 1974-11-05 | Padana Ag | Magnetic bearing assembly for journalling a rotor in a stalor |
US3969804A (en) * | 1973-12-27 | 1976-07-20 | Rajay Industries, Inc. | Bearing housing assembly method for high speed rotating shafts |
US4034228A (en) * | 1974-09-30 | 1977-07-05 | Siemens Aktiengesellschaft | Tubus for determining the boundaries of a beam of penetrating rays |
US4033042A (en) * | 1974-10-10 | 1977-07-05 | Bently Nevada Corporation | Shaft alignment apparatus and method |
US4128280A (en) * | 1977-01-17 | 1978-12-05 | Sulzer Brothers Limited | Self-pressurizing floating gas bearing having a magnetic bearing therein |
US4320927A (en) * | 1980-03-21 | 1982-03-23 | Sertich Anthony T | Dental drill with magnetic air turbine having magnetic bearings |
US4378091A (en) * | 1980-05-21 | 1983-03-29 | Toyota Jidosha Kabushiki Kaisha | Rotary type electrostatic spray painting device |
US4526483A (en) * | 1981-06-29 | 1985-07-02 | Shimadzu Corporation | Fluid foil bearing |
US4415281A (en) * | 1981-11-23 | 1983-11-15 | United Technologies Corporation | Hydrodynamic fluid film bearing |
US4523800A (en) * | 1982-07-20 | 1985-06-18 | Tokyo Shibaura Denki Kabushiki Kaisha | Polygonal mirror optical deflector |
US4839550A (en) * | 1982-11-11 | 1989-06-13 | Seiko Seiki Kabushiki Kaisha | Controlled type magnetic bearing device |
US4608835A (en) * | 1983-11-02 | 1986-09-02 | Hermen Kooy | Cabinet for cooling goods, etc. |
US4597676A (en) * | 1984-04-30 | 1986-07-01 | General Electric Company | Hybrid bearing |
US4841212A (en) * | 1986-09-12 | 1989-06-20 | Hitachi, Ltd. | Electromagnetic bearing control apparatus |
US4767223A (en) * | 1986-12-03 | 1988-08-30 | National Research Development Corporation | Hydrodynamic journal bearings |
US4781077A (en) * | 1986-12-19 | 1988-11-01 | Massachusetts Institute Of Technology | Stable intershaft squeeze film damper |
US4827169A (en) * | 1986-12-31 | 1989-05-02 | Societe De Mecanique Magnetique | Hybrid fluid bearing with stiffness modified by electromagnetic effect |
US4820950A (en) * | 1987-03-03 | 1989-04-11 | Copal Company Limited | Fluid Bearing |
US4880320A (en) * | 1987-03-10 | 1989-11-14 | British Aerospace Plc | Fluid film journal bearings |
US4828403A (en) * | 1987-04-03 | 1989-05-09 | Schwartzman Everett H | Resiliently mounted fluid bearing assembly |
US5126612A (en) * | 1987-04-09 | 1992-06-30 | Societe Europeenne De Propulsion | Active radial magnetic bearing combined with a back-up bearing |
US4961122A (en) * | 1987-05-11 | 1990-10-02 | Hitachi, Ltd. | Hydrodynamic grooved bearing device |
US4910449A (en) * | 1987-05-18 | 1990-03-20 | Ebara Corporation | System for preventing unbalance vibrations and synchronous disturbance vibrations |
US5489155A (en) * | 1987-05-29 | 1996-02-06 | Ide; Russell D. | Tilt pad variable geometry bearings having tilting bearing pads and methods of making same |
US5743654A (en) * | 1987-05-29 | 1998-04-28 | Kmc, Inc. | Hydrostatic and active control movable pad bearing |
US5660481A (en) * | 1987-05-29 | 1997-08-26 | Ide; Russell D. | Hydrodynamic bearings having beam mounted bearing pads and sealed bearing assemblies including the same |
US4885491A (en) * | 1987-10-28 | 1989-12-05 | National Aerospace Laboratory | Unstable vibration prevention apparatus for magnetic bearing system |
US5142177A (en) * | 1988-04-22 | 1992-08-25 | Toshiro Higuchi | Magnetically controlled bearing unit |
US5032028A (en) * | 1988-09-20 | 1991-07-16 | Abg Semca S.A. | Fluid film bearing |
US5322371A (en) * | 1988-12-23 | 1994-06-21 | Abg Semca Sa | Fluid film bearing |
US5096309A (en) * | 1989-04-03 | 1992-03-17 | Canon Kabushiki Kaisha | Hydrodynamic bearing system |
US4999534A (en) * | 1990-01-19 | 1991-03-12 | Contraves Goerz Corporation | Active vibration reduction in apparatus with cross-coupling between control axes |
US5223758A (en) * | 1990-03-05 | 1993-06-29 | Ebara Corporation | Spindle motor |
US5059845A (en) * | 1990-05-07 | 1991-10-22 | Mechanical Technology Incorporated | Active magnetic bearing device for controlling rotor vibrations |
US5202824A (en) * | 1990-06-21 | 1993-04-13 | Mechanical Technology Incorporated | Rotating force generator for magnetic bearings |
US5181783A (en) * | 1990-07-16 | 1993-01-26 | Lincoln Laser Co. | Apparatus for eliminating whirl instability in a gas supported bearing |
US5104284A (en) * | 1990-12-17 | 1992-04-14 | Dresser-Rand Company | Thrust compensating apparatus |
US5084643A (en) * | 1991-01-16 | 1992-01-28 | Mechanical Technology Incorporated | Virtual rotor balancing in magnetic bearings |
US5201585A (en) * | 1991-12-31 | 1993-04-13 | General Electric Company | Fluid film journal bearing with squeeze film damper for turbomachinery |
US5300808A (en) * | 1992-05-04 | 1994-04-05 | Motorola, Inc. | EPROM package and method of optically erasing |
US5345127A (en) * | 1992-07-23 | 1994-09-06 | The Glacier Metal Company Limited | Magnetic bearing back-up |
US5321329A (en) * | 1993-03-25 | 1994-06-14 | Hovorka Patent Trust | Permanent magnet shaft bearing |
US5441453A (en) * | 1993-06-03 | 1995-08-15 | W.S. Tyler, Incorporated | Vibrating shaft assembly having magnetic compensation for reducing shaft bearing loads |
US5772334A (en) * | 1994-04-27 | 1998-06-30 | British Technology Group Limited | Fluid film bearings |
US5743657A (en) * | 1994-08-06 | 1998-04-28 | The Glacier Metal Company Limited | Tilting pad journal bearing |
US5480234A (en) * | 1994-08-15 | 1996-01-02 | Ingersoll-Rand Company | Journal bearing |
US5879076A (en) * | 1995-02-08 | 1999-03-09 | Flexalite Technology Corporation | Method and appartus for light transmission |
US5549392A (en) * | 1995-05-02 | 1996-08-27 | Nastec, Inc. | Resilient mount pad journal bearing |
US5531523A (en) * | 1995-06-02 | 1996-07-02 | Westinghouse Electric Corporation | Rotor journal bearing having adjustable bearing pads |
US5634723A (en) * | 1995-06-15 | 1997-06-03 | R & D Dynamics Corporation | Hydrodynamic fluid film bearing |
US6135640A (en) * | 1995-06-30 | 2000-10-24 | Alliedsignal Inc. | Hybrid foil/magnetic bearing |
US5516212A (en) * | 1995-09-18 | 1996-05-14 | Western Digital Corporation | Hydrodynamic bearing with controlled lubricant pressure distribution |
US5879085A (en) * | 1995-10-13 | 1999-03-09 | Orion Corporation | Tilt pad hydrodynamic bearing for rotating machinery |
US5977677A (en) * | 1996-06-26 | 1999-11-02 | Allison Engine Company | Combination bearing for gas turbine engine |
US6089756A (en) * | 1997-03-18 | 2000-07-18 | Daido Metal Company Ltd. | Plain bearing |
US6288465B1 (en) * | 1997-04-28 | 2001-09-11 | Ntn Corporation | Combined externally pressurized gas-magnetic bearing assembly and spindle device utilizing the same |
US6005315A (en) * | 1997-05-30 | 1999-12-21 | Electric Boat Corporation | Fault-tolerant magnetic bearing control system architecture |
US6353273B1 (en) * | 1997-09-15 | 2002-03-05 | Mohawk Innovative Technology, Inc. | Hybrid foil-magnetic bearing |
US6770993B1 (en) * | 1997-09-15 | 2004-08-03 | Mohawk Innovative Technology, Inc. | Hybrid foil-magnetic bearing with improved load sharing |
US6236130B1 (en) * | 1998-02-03 | 2001-05-22 | Sulzer Electronics Ag | Method and arrangement for the excitation of the journalling winding and the drive winding systems in electrical machines with magnetic journalling, and an electrical drive |
US6737777B2 (en) * | 1998-10-14 | 2004-05-18 | Jenoptik Ldt Gmbh | Magnetic bearing and use thereof |
US6194801B1 (en) * | 1998-10-15 | 2001-02-27 | Skf Nova Ab | Device for limiting shaft whirl |
US6606536B1 (en) * | 1999-02-25 | 2003-08-12 | Seiko Instruments Inc. | Magnetic bearing device and magnetic bearing control device |
US6749339B1 (en) * | 1999-09-03 | 2004-06-15 | Sumitomo Electric Industries, Ltd. | Hydrodynamic bearing assembly and spindle motor having the same |
US20020174734A1 (en) * | 1999-11-16 | 2002-11-28 | David Chinery | Swashplate design |
US6653756B2 (en) * | 2000-01-14 | 2003-11-25 | Koyo Seiko Co., Ltd. | Magnetic bearing device |
US6737617B1 (en) * | 2000-01-24 | 2004-05-18 | General Electric Company | Methods and apparatus for a signal distortion based detection system |
US6720695B2 (en) * | 2000-07-04 | 2004-04-13 | W. Schlafhorst Ag & Co. | Rotor spinning device with a contactless, passive, radial bearing for the spinning rotor |
US20030038552A1 (en) * | 2000-08-21 | 2003-02-27 | Board Of Trustees Operating Michigan State University | Adaptive compensation of sensor run-out and mass unbalance in magnetic bearing systems without changing rotor speed |
US6770992B2 (en) * | 2000-10-16 | 2004-08-03 | Boc Edwards Japan Limited | Magnetic bearing apparatus |
US6590366B1 (en) * | 2000-11-02 | 2003-07-08 | General Dyanmics Advanced Technology Systems, Inc. | Control system for electromechanical arrangements having open-loop instability |
US6707200B2 (en) * | 2000-11-14 | 2004-03-16 | Airex Corporation | Integrated magnetic bearing |
US6686674B2 (en) * | 2000-12-04 | 2004-02-03 | Kura Laboratory Corporation | Motor having single cone fluid dynamic bearing balanced with magnetic attraction |
US6717311B2 (en) * | 2001-06-14 | 2004-04-06 | Mohawk Innovative Technology, Inc. | Combination magnetic radial and thrust bearing |
US7217039B2 (en) * | 2001-06-15 | 2007-05-15 | Societe De Mecanique Magnetique | Axial load-insensitive emergency bearing |
US6703736B2 (en) * | 2001-12-24 | 2004-03-09 | Industrial Technology Research Institute | Magnetic bearing |
US6786642B2 (en) * | 2002-08-30 | 2004-09-07 | Pratt & Whitney Canada Corp. | Compliant foil-fluid bearing support arrangement |
US6948853B2 (en) * | 2002-10-03 | 2005-09-27 | R & D Dynamics Corporation | High load capacity stacked foil thrust bearing assembly |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9279289B2 (en) | 2013-10-03 | 2016-03-08 | Renegade Manufacturing, LLC | Combination mud motor flow diverter and tiled bearing, and bearing assemblies including same |
WO2017201151A1 (en) * | 2016-05-17 | 2017-11-23 | Aly El-Shafei | Integrated journal bearing |
US10612592B2 (en) | 2016-05-17 | 2020-04-07 | Aly El-Shafei | Integrated journal bearing |
US10954999B2 (en) | 2016-05-17 | 2021-03-23 | Aly El-Shafei | Integrated journal bearing |
Also Published As
Publication number | Publication date |
---|---|
BRPI0511385A (en) | 2007-12-04 |
US20050275300A1 (en) | 2005-12-15 |
RU2006146875A (en) | 2008-07-20 |
CA2570052A1 (en) | 2005-12-29 |
RU2399803C2 (en) | 2010-09-20 |
WO2005122684A2 (en) | 2005-12-29 |
EP1792093A4 (en) | 2011-10-26 |
JP2012177480A (en) | 2012-09-13 |
JP5069103B2 (en) | 2012-11-07 |
US7836601B2 (en) | 2010-11-23 |
IL179953A0 (en) | 2007-05-15 |
JP2008503693A (en) | 2008-02-07 |
WO2005122684A3 (en) | 2007-08-16 |
EP1792093A2 (en) | 2007-06-06 |
KR20070039922A (en) | 2007-04-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7836601B2 (en) | Methods of controlling the instability in fluid film bearings | |
US8449190B2 (en) | Centering mechanisms for turbocharger bearings | |
JP4554583B2 (en) | Thrust bearing device | |
EP2738403B1 (en) | Rotating assemblies of turbomachinery, foil journal bearing assemblies thereof, and methods for producing journals of the foil journal bearing assemblies | |
CN101069023A (en) | Multi-thickness film layer bearing cartridge and housing | |
EP2203653A2 (en) | Anisotropic bearing supports for turbochargers | |
JP2011237035A (en) | Bearing | |
US4385787A (en) | Radial bearing for high-speed turbomachinery | |
CN101132870A (en) | Methods of controlling the instability in fluid film bearings | |
US9394914B2 (en) | Cage positioned tilting pad bearing | |
JP2017501340A (en) | Bearing device for exhaust gas turbocharger and exhaust gas turbocharger | |
US20060153479A1 (en) | Fluid dynamic bearing system | |
CN115992846A (en) | Double-rotation-direction foil pneumatic dynamic bearing | |
Zeidan | Fluid Film Bearings Fundamentals | |
Nicholas | Hydrodynamic journal bearings, types, characteristics and applications | |
Hu et al. | On the characteristics of gas foil conical bearings considering misalignment | |
JP2006077871A (en) | Bearing structure | |
JP2013137100A (en) | Journal bearing, and steam turbine | |
KR101279252B1 (en) | Tilting pad bearing for turbocharger | |
Cao et al. | Reduction of vibration and power loss in industrial turbochargers with improved tilting pad bearing design | |
JP2010156214A (en) | Rotary machine bearing structure | |
Subbiah et al. | Fluid-Film, Steam and/or Gas Seal Influences on Rotor Dynamics | |
KR20240042412A (en) | Rotor for high-speed electric machines | |
Agahi et al. | Turboexpanders with pressurized magnetic bearings for off-shore applications | |
Brown | Effect of Bearings and Seals on Rotor Response and Stability |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |