WO2014120302A2 - Palier à gaz compensant la dilatation thermique et induite par un rayonnement - Google Patents

Palier à gaz compensant la dilatation thermique et induite par un rayonnement Download PDF

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Publication number
WO2014120302A2
WO2014120302A2 PCT/US2013/066766 US2013066766W WO2014120302A2 WO 2014120302 A2 WO2014120302 A2 WO 2014120302A2 US 2013066766 W US2013066766 W US 2013066766W WO 2014120302 A2 WO2014120302 A2 WO 2014120302A2
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WO
WIPO (PCT)
Prior art keywords
bearing
gas
elements
pressure
pressure source
Prior art date
Application number
PCT/US2013/066766
Other languages
English (en)
Other versions
WO2014120302A3 (fr
Inventor
Paul Rosso
Original Assignee
Lawrence Livermore National Security, Llc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Lawrence Livermore National Security, Llc filed Critical Lawrence Livermore National Security, Llc
Publication of WO2014120302A2 publication Critical patent/WO2014120302A2/fr
Publication of WO2014120302A3 publication Critical patent/WO2014120302A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C32/0622—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 nozzles, restrictors
    • 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
    • F16C32/0662—Details of hydrostatic bearings independent of fluid supply or direction of load
    • F16C32/0677—Details of hydrostatic bearings independent of fluid supply or direction of load of elastic or yielding bearings or bearing supports

Definitions

  • NIF National Ignition Facility
  • DT deuterium and tritium
  • Inertial confinement fusion power plants have been proposed. The equipment, systems and support necessary for the deployment of such a fusion power plant are now being investigated and designed at LLNL.
  • ICF inertial confinement fusion
  • a fusion fuel capsule containing DT is held inside a hohlraum; the two together being referred to as a "target.”
  • the targets are injected into a fusion chamber and fired upon by a bank of lasers.
  • the hohlraum absorbs and re-radiates the energy as x-rays onto the fuel capsule.
  • the outer surface of the fuel capsule ablates, compressing and heating the DT fuel to cause a fusion reaction.
  • Coolants to control the fusion chamber environment and fluids used for transfer of thermal energy produced from the reaction become activated during plant operation. These activated fluids travel through processing equipment that must be developed to handle thermal gradients and irradiation.
  • This invention relates to the injection of targets used as fuel for fusion reactions, and in particular to gas-bearing or air-bearings used in injectors for such applications, including self-compensating or self-regulating gas bearings.
  • Embodiments of the present invention are applicable to process equipment for fusion energy production such as gas separation centrifuges, reactor coolant pumping, and the injection of targets used as fuel for fusion reactions, and in particular to gas-bearing or air-bearings used in such applications. More particularly, embodiments of the present invention relate to gas bearing, for example, air bearings, that compensate for expansion resulting from neutron absorption and thermal load.
  • a gas bearing includes flexure elements that balance flexural stiffness with gas-bearing pressure.
  • a gas bearing element includes bifurcated radial arms that deform to balance internal pressure with the pressure at the bearing interface.
  • Embodiments of the present invention are applicable to a wide variety of bearing applications including radial and longitudinal bearings.
  • a gas bearing is provided.
  • the gas bearing includes a central hub operable to receive a pressurized gas and a gas containment structure disposed around the central hub.
  • the gas containment structure comprises a plurality of flexural elements each having an entrance orifice adjacent the central hub, a central region including a set of cantilevered spring elements extending distally from the entrance orifice, and a distal nozzle surrounded by a bearing pad.
  • the gas bearing also includes a bearing race surrounding the gas containment structure.
  • the gas bearing also includes a set of toroidal discs, each of the set of toroidal discs being adjacent a side of the gas containment structure.
  • the plurality of flexural elements can be self-sealed in other embodiments.
  • the bearing pad can be made of porous material and the distal nozzle can be formed as a plurality of openings in the porous material, providing for diffuse flow through the bearing pad.
  • the plurality of flexural elements can each comprise two cantilevered spring elements separated by a gas passage.
  • a gas bearing is provided.
  • the gas bearing includes a central hub operable to receive a pressurized gas and a bearing element disposed around the central hub.
  • the bearing element comprises a plurality of bifurcated flexure elements each having an entrance orifice adjacent the central hub, a central region extending distally from the entrance orifice, and a distal nozzle.
  • the gas bearing also includes a bearing race surrounding the bearing element.
  • the gas bearing can also include a set of toroidal discs on opposing sides of the bearing element.
  • the bifurcated flexure elements can be self-sealed in other embodiments.
  • the pressurized gas can include at least one of air, nitrogen, argon, or combinations thereof.
  • the plurality of birfurcated flexure elements can further include a bearing plate surrounding the nozzle. In this embodiment, the bearing plate forms a hydrostatic pressure region between the bearing plate and the bearing race.
  • method of operating a gas bearing includes providing a source of pressurized gas and pressurizing a central hub of the gas bearing with the pressurized gas.
  • the method also includes flowing the gas through a plurality of flexural elements in fluid communication with the central hub and forming a bearing region characterized by a pressure equal to a first hydrostatic pressure and disposed between each of the flexural elements and a bearing race.
  • the method further includes increasing the pressure in the bearing region to a second hydrostatic pressure greater than the first hydrostatic pressure, deforming the plurality of flexural elements, and restoring the pressure in the bearing region to the first hydrostatic pressure.
  • an air bearing structure which compensates for temperature induced expansion and contraction.
  • the air bearing structure includes a plurality of members each including an inlet for allowing pressurized gas to enter the element and a nozzle to provide the air bearing by allowing the pressurized gas to escape against an air bearing surface.
  • the flexural stiffness of each element between the inlet and the nozzle balances with air-bearing pressure to maintain a constant air-bearing separation between the nozzle and the air bearing surface.
  • a gas bearing includes a pressure source region operable to receive a pressurized gas and a gas containment structure in fluid communication with the pressure source region.
  • the gas containment structure comprises a plurality of flexural elements each having an entrance orifice adjacent the pressure source region, a central region including a set of cantilevered spring elements extending distally from the entrance orifice, and a distal nozzle surrounded by a bearing pad.
  • the gas bearing also includes a bearing race adjacent the bearing pads of the plurality of flexural elements.
  • a gas bearing is provided.
  • the gas bearing includes a pressure source region operable to receive a pressurized gas and a bearing element in fluid communication with the pressure source region.
  • the bearing element comprises a plurality of bifurcated flexure elements each having an entrance orifice adjacent the pressure source region, a central region extending distally from the entrance orifice, and a distal nozzle.
  • the gas bearing also includes a bearing race adjacent the distal nozzle.
  • embodiments of the present invention provide gas bearings that are self-compensating for neutron absorption and thermal expansion.
  • FIG. 1 A is a simplified schematic diagram illustrating an exploded view of a gas bearing according to an embodiment of the present invention.
  • FIG. IB is a simplified schematic diagram of a flexural element undergoing deflection according to an embodiment of the present invention.
  • FIG. 1C is a simplified schematic diagram illustrating components of the flexural element illustrated in FIG. IB.
  • FIG. 2A is a simplified plan view of a gas bearing including bearing elements with bifurcated radial arms according to an embodiment of the present invention.
  • FIG. 2B is a simplified schematic diagram illustrating self-regulation of a gas bearing element according to an embodiment of the present invention.
  • FIG. 2C is a simplified schematic diagram illustrating flexing of a gas bearing element during operation.
  • FIG. 3 is a simplified flowchart illustrating a method of operating a gas bearing according to an embodiment of the present invention.
  • inertial confinement fusion target designers must consider many engineering requirements in addition to the physics requirements for a successful target implosion. Among these considerations is injection of the targets to the center of the chamber where the laser beams can implode the fusion fuel. For the fuel to implode and create a fusion reaction, the fuel capsule must be irradiated evenly with energy to ablate its surface to compress and heat the DT fuel. [0023] In such a system, the 10-15 fusion reactions per second in the chamber create intense heat and radiation which can damage targets waiting to be injected.
  • Systems may protect the targets from damage from the fusion reactions by providing a "shutter” to block the heat and radiation from the fusion reaction from reaching targets yet to be injected. These targets are positioned immediately outside the fusion chamber in the injector mechanism.
  • One such shutter provides a revolving structure which enables the targets to pass from the injection mechanism and into the chamber without ever exposing yet-to-be-injected targets to the heat and radiation.
  • Such a shutter is described in commonly assigned and co-pending PCT Patent Application No. PCT/US2013/064544, filed on October 11, 2013, and entitled “Irradiation Shutter for Target Injection into a Fusion Chamber," the disclosure of which is hereby incorporated by reference in its entirety for all purposes.
  • a design challenge in implementing such a shutter is to provide a low friction mechanism for rotating the shutter, for example, by using an air bearing or gas bearing.
  • the design challenges to implementing such a shutter are numerous.
  • the large thermal variations and radiation cause any shutter materials to expand and contract.
  • the tolerances required for a properly functioning gas-bearing or air-bearing drive the need to develop a solution for these expansions and contractions occurring in the bearing components.
  • Embodiments of the present invention utilize compliant features within the bearing design to balance bearing gas pressure and compliant component spring rates to compensate for changes in the materials during bearing operation.
  • the invention herein has applicability for use in environments that would typically disable the use of close-tolerance air/gas bearing concepts due to thermal load or irradiated material deformations. Mechanical operation in a high energy, high flux neutron
  • FIG. 1 A is a simplified schematic diagram illustrating an exploded view of a gas bearing according to an embodiment of the present invention.
  • the gas bearing 100 balances flexural stiffness with gas bearing pressure to maintain desired bearing surfaces.
  • the force of the hydrostatic effect on the bearing plate reacts against the flexural stiffness in the flexural element, analogous to a leaf spring. This hydrostatic force counteracts the stiffness of the flexural element to maintain the preloading in the gas bearing.
  • the gas bearing 100 illustrated in FIG. 1 A which may be an air bearing, is suitable for applications in which neutron flux and thermal load result in expansion or swelling and/or contraction of the bearing during operation.
  • the gas bearing 100 includes a gas containment structure 110 and two toroidal discs 120 and 122.
  • the gas containment structure 110 is made up of a plurality of radially disposed flexural elements that are described more fully in relation to FIGS. IB and 1C.
  • the gas containment structure 110 is surrounded by a bearing race 112 that opposes the bearing plates to provide a gas bearing effect. In FIG. 1 A, the bearing race 112 has been slid to a position below the gas bearing for purposes of clarity.
  • FIG. IB is a simplified schematic diagram of a flexural element of the gas bearing undergoing deflection according to an embodiment of the present invention.
  • flexural element 150 is one of the plurality of flexural elements making up the gas containment structure 110.
  • the flexural element 150 includes a radial arm 160 with a nozzle plate 165 (also referred to as a bearing plate) including a nozzle 170.
  • pressurized gas flows from the central region 105 of the gas bearing 100 through a gas passage 193 in the center of the radial arm 160 and out the nozzle 170.
  • FIG. 1C is a simplified schematic diagram illustrating components of the flexural element illustrated in FIG. IB.
  • two cantilever spring elements 190 and 192 extend from the base of the flexural element where pressurized gas enters from the central region 105 of the gas bearing and passes to the nozzle 170.
  • the two cantilever springs can be compared to leaf springs.
  • An air gap 193 is formed between the two cantilever spring elements providing a passage for the gas from the entrance orifice 167 to the nozzle 170.
  • the two toroidal discs provide covers that define the top and bottom of the gas passage.
  • the flexure element can be fabricated with a central gas passage surrounded on four sides by flexible materials that provide the spring action desired and confine the gas flowing through the hollow fiexure element to and subsequently through the nozzle in the bearing plate.
  • embodiments provide multiple ways to transport the gas from the pressurized gas source to the bearing surface defined by the bearing plate and the bearing race, thereby providing a hydrostatic effect at each bearing plate.
  • One of ordinary skill in the art would recognize many variations, modifications, and alternatives.
  • FIG. IB pressure induced deflection of the flexural element occurs as the flexural elements expands, for example, from neutron absorption and/or thermal swell.
  • Embodiments balance flexural stiffness with gas bearing pressure as described herein.
  • the initial (unflexed) position of the flexural element is illustrated using dashed lines 180 and the position of the flexural element after expansion is illustrated using solid lines 185.
  • the gap between the bearing plate and the bearing race decreases. This results in an increase in pressure in the bearing region between the bearing plate and bearing race.
  • the flexure elements is designed to enable the bearing plate 165 to maintain a constant orientation during expansion and contraction.
  • the fiexure element is designed such that during expansion and contraction, the bearing plate moves in a substantially radial direction while maintaining substantially the same orientation. In other words, expansion of the flexure element decreases the gap between the bearing plate and the bearing race, but maintains the orientation of the bearing plate with respect to the bearing race.
  • an embodiment of the present invention uses the bearing material spring-rate and deflection force to counteract the force generated within the bearing race to maintain the gas-bearing flow gaps. Geometry optimization with regard to material selection and material coefficients of thermal expansion and irradiation effects impact the final performance of the bearing design.
  • the flexural stiffhess on each of the flexural elements 150 compensates for expansion of the materials.
  • the pressurized gas enters the gas bearing 100 in the center 105 of the containment structure 110 and is trapped between the two toroidal discs 120 and 122.
  • the gas enters entrance orifices (illustrated as reference number 167 in FIG. 1C) on the portion of the flexural elements proximal to the center 105, passes through a gas passage 193 defined in the central region of the radial arm 160, which can also be referred to as the central regions of the flexural elements, and emerges from the nozzles 170.
  • the bearing plate 165 can be fabricated from a porous material, providing a porous media through with gas flows from the gas passage to the bearing race.
  • the "nozzle" may be a plurality of openings in the porous media, providing for diffuse gas flow through the "nozzles" of the bearing plate.
  • FIG. 1 A The embodiment of the present invention illustrated in FIG. 1 A operates using static pressure.
  • An external pressure source (not shown) provides pressurized gas that is fed into the center bearing cavity 105.
  • the high-pressure gas flows outward radially through the flexure elements and the nozzles 170 of the flexure elements to the bearing plates, which can also be referred to as bearing race pads.
  • the pressure force on the bearing plate is then used to regulate flow gaps.
  • FIG. 1 A illustrates a gas bearing utilizing a circular race bearing and a radial configuration
  • embodiments of the present invention can be adapted to linear configurations for thrust and linear bearings as appropriate to the particular application.
  • One of ordinary skill in the art would recognize many variations, modifications, and alternatives.
  • the internal bearing cavity pressure forces are used to generate deflections that regulate the gas-bearing race flow gaps.
  • changes in the hydrostatic pressure at the bearing plate / bearing race region result in pressure changes in a region of the flexure element, resulting in deformation of the flexure element and self-regulation.
  • FIG. 2A is a simplified plan view of a gas bearing with bearing elements including bifurcated radial arms according to an embodiment of the present invention.
  • This top view illustrates a central hub 205, which is in fluid communication with a source of pressurized gas, for example, pressurized air, nitrogen, argon, or the like.
  • the gas bearing includes a plurality of bearing elements that are attached to the central hub and arrayed substantially radially.
  • the gas bearing includes a bearing race 203 that surrounds the bearing elements and opposes the plurality of bearing plates 221. A gas bearing is thus provided between the bearing plates and the bearing race.
  • the gas bearing includes a set of toroidal discs that provide top and bottom seals to the bearing elements.
  • FIG. 2 utilizes a gas flow from the central hub through the bearing elements to the bearing race, this particular outward flow
  • pressurized gas is provided to the region between the bearing race and the bearing elements, which can be referred to as a peripheral ring.
  • the pressurization of the peripheral ring serves as a pressure source for gas flow through the bearing elements, which are reversed with respect to the implementation illustrated in FIG. 2A, with the entrance orifice facing the illustrated bearing race and the nozzle facing the illustrated central hub.
  • the bearing region is formed between the nozzles and a bearing race positioned where the central hub s illustrated in FIG. 2A.
  • the pressure inside a cavity in the bearing elements and deformation of this cavity will provide for a self-regulation of the gas bearing as the bearing plate position changes with respect to the bearing race.
  • FIG. 2B is a simplified schematic diagram illustrating self-regulation of an element of a gas bearing according to an embodiment of the present invention.
  • the gas enters at the entrance orifice 218 of the element, which is in fluid communication with a pressure source, flows through the central portion 220 of the element between the bifurcated radial arms 230 and 232, and emerges from the nozzle 223 in the bearing plate 221, also referred to as an exit orifice, of the element.
  • bifurcated arms are referred to as bifurcated radial arms in this radial configuration, this is not required by the present invention and they may be utilized in non-radial implementations while still serving their function as bifurcated arms.
  • One of ordinary skill in the art would recognize many variations, modifications, and alternatives.
  • FIG. 2C is a simplified schematic diagram illustrating flexing of a gas bearing element during operation. As the radial arms flex, the flexing maintains the gas bearing clearance between the bearing plates and the bearing race as described herein.
  • the position of the bifurcated arms is shown at an initial position 212 as well as a flexed position 214 after expansion of the central region 220. The separation of the bifurcated arms results in radial contraction of the bearing plate 221 as illustrated by the solid lines in FIG. 2C.
  • the embodiment illustrated in FIGS. 2A-2C provides for pressure balanced compensation.
  • the internal pressure in curved tubes can be used to cause a straightening effect in the tubes.
  • the swelling changes the hydrostatic pressure in the gap between the bearing plates and the bearing race.
  • an increase in the internal channel pressure in the bearing flow gaps will result in an increase in pressure in the central portion 220 of the flexure element, forcing the arms of the element to increase their separation.
  • the increased bowing of the arms will result in shortening of the flexure element, producing a decrease in the internal channel pressure in the bearing flow gaps.
  • self-regulation and compensation is provided by the embodiment illustrated in FIGS. 2A-2C.
  • Embodiments of the present invention as illustrated in FIG. 2A are applicable for use in several portions of the LIFE architecture, including as bearings for the loading mechanism, bearings for the rotating shutter mechanism, or the like.
  • the geometry is suitable (e.g., optimized) to create the correct bearing surface motion as pressure due to thermal expansion and expansion resulting from neutron absorption causes deformation of the gas bearing elements.
  • the embodiment of the present invention illustrated in FIG. 2A operates using static pressure.
  • An external pressure source (not shown) provides pressurized gas that is fed into the center bearing cavity 205. The high-pressure gas then flows outward radially through the central portion of the element and exits at the nozzle 221 to the bearing race.
  • FIG. 3 is a simplified flowchart illustrating a method of operating a gas bearing according to an embodiment of the present invention.
  • the method includes pressurizing a pressure source of the gas bearing with pressurized gas (312).
  • the pressure source can be a central hub of the gas bearing or a peripheral ring of the gas bearing.
  • the method also includes flowing the gas through a plurality of flexural elements in fluid communication with the pressure sournce (314) and forming a bearing region characterized by a pressure equal to a first hydrostatic pressure and disposed between each of the flexural elements and a bearing race (316).
  • the first hydrostatic pressure can be a preload pressure for the gas bearing.
  • Flowing the gas through the plurality of flexural elements can include, for each of the plurality of flexural elements, flowing the gas through an orifice in each of the plurality of flexural elements, flowing the gas through a radial portion of each of the plurality of flexural elements, and flowing the gas through a nozzle in each of the plurality of flexural elements.
  • the nozzle is a porous bearing plate.
  • the method further includes increasing the pressure in the bearing region to a second hydrostatic pressure greater than the first hydrostatic pressure (318), deforming the plurality of flexural elements (320), and restoring the pressure in the bearing region to the first hydrostatic pressure (322).
  • Increasing the pressure in the bearing region can result from thermal expansion of the plurality of flexure elements.
  • Deforming the plurality of flexural elements can include compressing the plurality of elements as discussed in relation to FIG. IB.
  • each of the plurality of flexure elements can include a set of radially arrayed cantilevered springs having a radial gas passage disposed therebetween.
  • deforming the plurality of flexural elements can include increasing the flexure in a set of cantilevered springs as discussed in relation to FIGS. 2B and 2C. In these embodiments, increasing the flexure in the set of cantilevered springs results from an increase in pressure in a region between the set of cantilevered springs.
  • each of the plurality of flexure elements comprises a plurality of bifurcated flexure elements each having an entrance orifice adjacent the pressure source, a central region extending distally from the entrance orifice, and a distal nozzle.
  • FIG. 3 provides a particular method of operating a gas bearing according to an embodiment of the present invention.
  • Other sequences of steps may also be performed according to alternative embodiments.
  • alternative embodiments of the present invention may perform the steps outlined above in a different order.
  • the individual steps illustrated in FIG. 3 may include multiple sub-steps that may be performed in various sequences as appropriate to the individual step.
  • additional steps may be added or removed depending on the particular applications.
  • One of ordinary skill in the art would recognize many variations, modifications, and alternatives.
  • the pressure source region rather than being the central hub, with the bearing element being disposed around the central hub, and the bearing race surrounding the bearing element, could be a peripheral ring, with the bearing element disposed inside the peripheral ring, and the bearing race being disposed inside the bearing element.
  • the flexural elements / bifurcated flexure elements described in relation to FIGS. 1A-1B and 2A-2C can either be oriented with the entrance orifice on the periphery of the bearing element or on the inner portion of the bearing element as illustrated in the figures.

Abstract

La présente invention se rapporte à un procédé permettant de faire fonctionner un palier à gaz, ledit procédé consistant à mettre sous pression une source de pression du palier à gaz avec un gaz sous pression. Le procédé consiste également à faire circuler le gaz à travers une pluralité d'éléments de flexion en communication fluidique avec la source de pression et à former une partie palier caractérisée par une pression égale à une première pression hydrostatique et disposée entre chacun élément de flexion et un chemin de roulement. Le procédé consiste en outre à augmenter la pression dans la partie palier à une seconde pression hydrostatique supérieure à la première pression hydrostatique, à déformer la pluralité d'éléments de flexion et à rétablir la pression dans la partie palier à la première pression hydrostatique.
PCT/US2013/066766 2012-10-26 2013-10-25 Palier à gaz compensant la dilatation thermique et induite par un rayonnement WO2014120302A2 (fr)

Applications Claiming Priority (2)

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US201261719250P 2012-10-26 2012-10-26
US61/719,250 2012-10-26

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WO2014120302A3 WO2014120302A3 (fr) 2014-11-13

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3324062A1 (fr) * 2016-11-22 2018-05-23 Fischer Engineering Solutions AG Système rotatif avec palier radial à gaz
WO2021099011A1 (fr) * 2019-11-18 2021-05-27 Robert Bosch Gmbh Palier à patins oscillants
US11428264B2 (en) 2016-10-31 2022-08-30 Fischer Engineering Solutions Ag Rotary system with axial gas bearing

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3620581A (en) * 1970-10-12 1971-11-16 Us Air Force Porous hydrostatic bearing
US4099799A (en) * 1977-04-28 1978-07-11 Nasa Cantilever mounted resilient pad gas bearing
US8083413B2 (en) * 2007-10-23 2011-12-27 General Electric Company Compliant hybrid gas journal bearing using integral wire mesh dampers

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3620581A (en) * 1970-10-12 1971-11-16 Us Air Force Porous hydrostatic bearing
US4099799A (en) * 1977-04-28 1978-07-11 Nasa Cantilever mounted resilient pad gas bearing
US8083413B2 (en) * 2007-10-23 2011-12-27 General Electric Company Compliant hybrid gas journal bearing using integral wire mesh dampers

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11428264B2 (en) 2016-10-31 2022-08-30 Fischer Engineering Solutions Ag Rotary system with axial gas bearing
EP3324062A1 (fr) * 2016-11-22 2018-05-23 Fischer Engineering Solutions AG Système rotatif avec palier radial à gaz
WO2018095841A1 (fr) 2016-11-22 2018-05-31 Fischer Engineering Solutions Ag Système de rotation à palier à gaz radial
CN110382888A (zh) * 2016-11-22 2019-10-25 费希尔工程解决方案公司 具有径向气体轴承的旋转系统
US10767693B2 (en) 2016-11-22 2020-09-08 Fischer Engineering Solutions Ag Rotation system having radial gas bearing
WO2021099011A1 (fr) * 2019-11-18 2021-05-27 Robert Bosch Gmbh Palier à patins oscillants

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