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
  • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
  • F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
  • F16C32/0614—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings
  • F16C32/0618—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings via porous material
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
  • F04D17/08—Centrifugal pumps
  • F04D17/10—Centrifugal pumps for compressing or evacuating
  • F04D17/12—Multi-stage pumps
  • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
  • F04D29/056—Bearings
  • F04D29/057—Bearings hydrostatic; hydrodynamic
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/08—Sealings
  • F04D29/10—Shaft sealings
  • F04D29/12—Shaft sealings using sealing-rings
  • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps
  • F04D29/124—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps with special means for adducting cooling or sealing fluid
• • 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

Definitions

• FIG. 2B is a flexible rotating element with double opposed preferred.
• FIG. 7C is an angular and axial seal compliance.
• FIG. 13C is a tilting pad externally pressurized gas bearing for rotating shaft in Turbo machinery.
• a shaft 301 that may rotate at high speeds is rotated inside of a stationary cylindrical bearing seal 310. Contamination or pressures that exist in a volume 308 are sealed and denied egress into a gap 309 by hydrostatic pressure exiting the gap 309.
• the housing or casing 311 is equipped to receive the cylindrical air bearing seal 310 directly. In an alternative embodiment, the housing or casing
• a shaft 401 which may rotate at high speeds has a blade runner 405 coupled to it using a mounting ring 413 which is fixed to the shaft by set screws 403 and or a shoulder.
• An O-ring 410 may be employed to seal clearance at 402.
• FIG. 4 There are two illustrations in FIG. 4; in view A the blade 405 is not up against the porous seal bearing face and the gap 406 allows for a view of the blade runner 405, in view B, the blade runner is in place and the gap 406 between it and the porous face 412 is as it would be in operation, less than 25 microns.
• the blade itself may be coupled directly to the shoulder if the shaft is so equipped with a shoulder (a shoulder would be the axial face created by a step in the diameter).
• a shaft 701 of a piece of equipment that is carrying with it a runner 711 that has a spherical outside diameter.
• the runner with a spherical OD couples to the shaft through two O-rings 702.
• Another advantage is that it reduces tolerance concerns for the fit at 705.
• porous media gas bearings have no orifices, grooves, steps or pockets in their face, they have the best chance of maintaining laminar flow at high relative surface velocities.
• the laminar flow regime creates significantly less drag and heat losses than the turbulent regime.
• the best way to maintain laminar flow is to have a featureless bearing face with a fine surface finish. Porous bearings enable both these requirements.
• the motor magnet bearings could be employed as the axial bearings running on the sides of the impellers 1902, much as conventional linear motors employ magnets on either side of the set coils. This has some advantages especially at high speeds when attempting to keep the magnets attached to the rotor as their centrifugal force pushes them up against a diameter machined into the impeller 1902.
• the illustration shows that the axial and radial bearings are being fed 1904 from high pressure side of the compressor. In an alternative embodiment, these bearings may be fed from a separate high pressure source (not shown).
• Carbon brushes commonly understood in the art, provide electrical contact between rotating and stationary components of DC, and some AC, machines (e.g., motors, generators, alternators, and the like). The brushes carry current into the rotating parts, and assist in the commutation process. Carbon brushes are retained by brush holders and maintain contact with a slip ring assembly or commutator.
• a stationary member 2516 allows flow 2517 through the stationary member 2516 and through rotating member 2519 which spins in the direction shown by 2526, without leakage at the face 2522.
• the stationary member retains porous media members 2523 and 2518 in the form of two concentric rings, with an annular space 2526 between said porous media rings.
• Gas 2525 is introduced to the porous media via plenum 2524 and through multiple air distribution channels to supply gas pressure to both porous media rings. This gas pressure counteracts a force acting on the top side of the rotary union 2520, which can occur from a spring, flexure, or other means.
• a shaft 2601 rotates with a runner 2602 attached to it.
• a seal housing 2604 is attached to stator 2608, and a porous media face 2603 has relative motion with runner 2602.
• a system pressure 2609 may be at 3,000 psig.
• the three channels distributing gas pressure to the porous media 2603 each are supplied with a different and adjustable pressure. These adjustable pressures are such that the resulting pressure at location 2610 will be zero psig.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Dispersion Chemistry (AREA)
• Fluid Mechanics (AREA)
• Physics & Mathematics (AREA)
• Magnetic Bearings And Hydrostatic Bearings (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
• Motor Or Generator Current Collectors (AREA)
• Turbine Rotor Nozzle Sealing (AREA)
• Sliding-Contact Bearings (AREA)
• Support Of The Bearing (AREA)

Priority Applications (7)

Applications Claiming Priority (4)

Publications (1)

Family

ID=50776545

Family Applications (1)

Country Status (8)

Cited By (14)

Families Citing this family (6)

Citations (18)

Family Cites Families (11)

• 2013
  • 2013-11-20 BR BR112015011676A patent/BR112015011676A2/pt not_active Application Discontinuation
  • 2013-11-20 KR KR1020157015707A patent/KR20150086309A/ko not_active Withdrawn
  • 2013-11-20 AU AU2013348004A patent/AU2013348004B2/en active Active
  • 2013-11-20 JP JP2015543152A patent/JP6401176B2/ja active Active
  • 2013-11-20 WO PCT/US2013/071114 patent/WO2014081901A1/en not_active Ceased
  • 2013-11-20 EP EP13802790.9A patent/EP2923095B1/en active Active
  • 2013-11-20 SG SG11201503892YA patent/SG11201503892YA/en unknown
  • 2013-11-20 CA CA2891937A patent/CA2891937C/en active Active
  • 2013-11-20 SG SG10201708489UA patent/SG10201708489UA/en unknown
  • 2013-11-20 CA CA2968755A patent/CA2968755C/en active Active
• 2018
  • 2018-03-16 AU AU2018201929A patent/AU2018201929B2/en not_active Ceased
  • 2018-09-06 JP JP2018167028A patent/JP6647357B2/ja active Active

Patent Citations (18)

Non-Patent Citations (1)

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