WO2001071207A1 - Palier hydrostatique - Google Patents

Palier hydrostatique Download PDF

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Publication number
WO2001071207A1
WO2001071207A1 PCT/AT2001/000089 AT0100089W WO0171207A1 WO 2001071207 A1 WO2001071207 A1 WO 2001071207A1 AT 0100089 W AT0100089 W AT 0100089W WO 0171207 A1 WO0171207 A1 WO 0171207A1
Authority
WO
WIPO (PCT)
Prior art keywords
insert
component
hydrostatic
insert part
bearing according
Prior art date
Application number
PCT/AT2001/000089
Other languages
German (de)
English (en)
Inventor
Heinrich Gregor Hochleitner
Original Assignee
Heinrich Gregor Hochleitner
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 Heinrich Gregor Hochleitner filed Critical Heinrich Gregor Hochleitner
Priority to AU43933/01A priority Critical patent/AU4393301A/en
Publication of WO2001071207A1 publication Critical patent/WO2001071207A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
    • F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure

Definitions

  • the invention relates to a hydrostatic bearing according to the preamble of claim 1.
  • the vibrating loads with
  • aerostatic bearings are already known, in which the storage takes place by means of a gas, preferably air, supplied under pressure. Hiebei has already been proposed to surround the component to be stored by a sleeve made of porous material through which the gas is pressed. The gas pressure must be greater than the load pressure that the component to be stored exerts on the porous material.
  • the disadvantage of such aerostatic bearings is that the air begins to vibrate. It is therefore necessary to minimize the volume of air that develops the load-bearing capacity in order to avoid such vibrations.
  • air has no emergency running properties and the load capacity of such aerostatic bearings is very low.
  • hydrostatic bearings In order to ensure friction and wear-free mounting of components, hydrostatic bearings are already known, in which the mounting is carried out by means of a pressurized fluid which is provided in a cavity of a bearing body. This cavity is connected to an opening for the supply of the pressure fluid and has sealing gaps at its boundaries opposite in the direction of the component axis, through which the pressure fluid supplied via the opening can emerge again.
  • four bearing bodies each offset by 90 °, are generally provided, but designs with three such bearing bodies are also known, which are arranged offset from one another by 120 °.
  • the pressure of the fluid in front of the throttling points should therefore be greater than in the cavities, so that the functioning of the hydrostatic bearing is guaranteed, and the throttling points must be optimized depending on the sealing gaps, so that there is a balance between the fluid supplied via the throttling points and the fluid flowing off via the sealing edges or gaps. If the diameter of the throttling points is too large, there is no pressure drop in the unloaded zone, ie in the cavity, and therefore there is no build-up of a pressure gradient which acts counter to an external load. If the diameter of the throttling points is too small, the reaction speed of the hydrostatic bearing is too slow in the event of a sudden application of the load and the component hits the wall of a sealing gap. In the unloaded state of the component, the pressure in the
  • Cavities of all bearing bodies are the same size, so that there is a balance between the fluid supplied via the throttle points and the fluid discharged via the sealing edges or gaps.
  • the component is in a position in which the sealing gaps are the same size along the entire circumference of the component.
  • the width of the sealing gaps changes along the circumference of the component, so that the system is no longer in equilibrium and the pressure distribution changes as a result, so that several are distributed over the circumference of the component arranged bearing body with cavities provided therein, there is a partial decrease in pressure, and in some cases an increase in pressure, until the pressure differences are compensated for by supplying the fluid via the throttle points until there is equilibrium with the external load.
  • the pressure in a cavity can only reach a maximum of the pressure in front of the throttle point. In this case, however, the storage is no longer stable.
  • the present invention has for its object to provide a hydrostatic bearing for components that is simple in structure and therefore much cheaper than the known hydrostatic bearings and in which also the contacting of the component occurring in the known bearings with sudden loading is avoided ,
  • the invention proposes the features of the characterizing part of patent claim 1.
  • the pressurized fluid penetrates through the pores of the insert part and, with appropriate porosity, forms a hydrostatic support for the component in a large number of miniature storage pockets.
  • the porous pressure fluid-permeable insert part thus forms the required throttle point, so that no separate one is present in the pressure fluid supply to the insert part Throttle point is to be provided.
  • the porosity of the insert must of course be matched to the loads and the size of the component.
  • the insert part is preferably formed by a sleeve surrounding the component, which is received by a cavity of the bearing body having a corresponding cross section, so that the component is supported uniformly over the entire circumference.
  • the supply of the pressure fluid to the insert made of porous material is expediently carried out in that recesses are formed in the wall of the bearing body or in the insert itself, preferably formed by grooves, which are connected to the pressure fluid supply or receive the pressure fluid.
  • Such a design offers the possibility of dividing the recesses into individual grooves or sections, each section being connected to the pressure fluid supply. This makes it possible to support the component along its longitudinal and / or transverse extension with different pressures and thus different load capacities if necessary, and pressure equalization can take place where the division into the sections takes place.
  • the present invention makes it possible to provide the porous insert part with barrier layers crossing the wall thereof, specifically in the axial direction and / or in the circumferential direction or in the longitudinal and / or transverse direction.
  • barrier layers can be formed, for example, from a curable material introduced into the porous insert part in a flowable state, for example a lacquer, or from barrier parts made of metal or plastic, which are also sintered in during manufacture.
  • Cover for example made of metal, polyester paint, or the like. Or made of or with sintered cover parts made of metal or plastic.
  • the porous insert part can be formed from different materials.
  • the porous insert part preferably consists of a sintered metal, but it can also consist of an aluminum which is joined by an epoxy resin and which is sprayed, of sintered stainless steel particles, for example made of stainless steel material, or of glass fibers connected by an epoxy resin, for example in the form of a glass fiber mat made of sintered bronze.
  • Sintered ceramic or sintered hard metal can be formed.
  • Water, oil, other liquids or liquid mixtures with a pressure of about 50 to 500 bar or more can be supplied as the pressure fluid.
  • FIG. 1 shows a hydrostatic bearing according to the invention in longitudinal section
  • FIG. 2 shows a cross section along the line II-II in FIG. 1.
  • FIG. 3 shows in longitudinal section the pressure distribution when the component is deformed.
  • 4 shows in longitudinal section a modified embodiment of the hydrostatic bearing according to the invention.
  • FIGS. 5 and 6 show different designs of the insert part in cross-section
  • FIGS. 7 and 8 show different cross-sectional shapes of the insert part
  • FIGS. 9 to 11 design variants of the bearing
  • Fig.12 a special insert.
  • 13 to 15 show further embodiments of a hydrostatic bearing according to the invention in longitudinal section.
  • the hydrostatic bearing according to the invention for a component 1 having the shape of a cylinder has a bearing body 2, into which a sleeve-shaped insert 4 surrounding the component 1 is inserted, forming an intermediate space or pressure fluid space 5.
  • the pressure fluid chamber 5 is formed as a recess in the wall of the bearing body 2 and is connected via an opening 6 to a pressure fluid supply, for example for water or oil.
  • the fluid supplied via the opening 6 reaches or passes through the porous, sleeve-shaped insert 4.
  • the pores on the surface of the insert 4 facing the component form micro-bearing pockets for the component 1 filled with the pressure fluid, as a result of which a hydrostatic bearing of the component 1 is achieved with a uniform pressure distribution, which pressure distribution is indicated at 9.
  • the pressure fluid emerges laterally from the bearing gap 8 and is collected or recycled. There are no sealing gaps.
  • FIG. 3 shows the pressure distribution in the event of deformation or one-sided loading of the component 1.
  • the pressure can drop in this (right) area when the bearing gap 8 is enlarged, however, not over the entire length of the porous insert 4, since the pressure fluid causing the load-bearing capacity is distributed over the numerous miniature storage pockets in the porous insert 4.
  • An additional pressure build-up or a stabilizing pressure arises in the more heavily loaded (left) area of the bearing gap 8.
  • Figure 4 shows an embodiment in which the recess 5 through a wall
  • FIG. 5 shows a sleeve-shaped insert 4 with an annular cross section, which is divided into segments 17 by essentially radially extending barrier layers 11. These segments can be subjected to different fluid pressures, with which a different pressure build-up in the circumferential direction of component 1 can be achieved; Subdivisions with barrier layers can also be formed in the longitudinal direction of the component 1 or the bearing body 2. Furthermore, the load capacity of the bearing is increased depending on the number of barrier layers.
  • the barrier layers 11 can be produced, for example, by introducing a curable material, for example a lacquer, into the porous insert 4 in a flowable state and subsequently allowing it to harden. Barrier layers, e.g. made of metal or plastic, can also be sintered in.
  • This support body 12 can be formed, for example, by a perforated plate.
  • certain areas of the sleeve-shaped insert 4 can be provided on the outside with a fluid-tight cover 13, so that these areas are then not flowed through by the pressure fluid.
  • This cover can consist of metal or plastic films or plates which have been applied to the outside of the insert or have been sintered in near the surface, or of polyester lacquer.
  • the pore sizes in insert 4 are 5 to 100 ⁇ m. Deviations from these sizes are possible.
  • the thickness of the insert body 4 is determined by the respective application; In practice, it has been shown that such insert bodies 4 have a thickness of 1 to 50 mm, depending on the length of the insert bodies 4 or on the weight of the components 1 to be stored.
  • FIG. 7 shows a cylindrical component 1, which extends over part of its circumference an insert body 4 is supported.
  • the insert body 4 is provided with radially extending barrier layers 11 in order to avoid that fluid flows themselves arise within the porous insert body 4.
  • barrier layers 11 the pressure fluid supplied to a sector 17 of the insert body 4 from the outside is guided through the sector 17 and emerges on the surface facing the component 1 and in this way supports the component 1 essentially without friction. If there is a fluid flow in the circumferential direction in the insert body 4, the pressure fluid could flow out under pressure, for example, from the lower region of the insert body into the lateral region of the insert body 4; the pressure in the bearing gap would then drop in the lower region.
  • the bearing gap 8 shows the mounting of a square component 1 in a sleeve-shaped insert body 4 with a square inner cross section.
  • the bearing gap 8 lies on all sides between the insert body 4 and the surface of the component 1. It thus becomes clear that the cross-sectional shape of the component 1 to be stored can take on a wide variety of shapes; it is only essential that the pressure fluid flows through the pressure fluid-permeable porous insert body 4 and forms the bearing gap 8.
  • Fig. 9 shows an embodiment in which an elongated, e.g. flat or planar component 1, e.g. a tool slide is mounted in or on an insert body 4, which insert body 4 causes the support and also the lateral guidance of the component 1.
  • a lateral escape of the pressure fluid by means of applications 13 on the lateral outer surfaces and the upper outer surfaces of the insert body 4 is prevented. It can e.g. are sintered metal pads.
  • the insert body 4 is inserted into the bearing body 4 only with its end regions, and the pressure fluid is fed through the opening 6 into the pressure fluid chamber 5.
  • the pressure fluid chamber 5 or the recess for mounting the insert body 4 in the bearing body 2 are formed.
  • the bearing body 2 is designed in the form of a flat surface into which the pressure fluid opening 6 opens.
  • the insert body 4 is designed in the form of an inverted U and delimits the pressure fluid space 5 with its longitudinal extension and its two lateral legs.
  • the insert body is covered on the side with corresponding barrier pads or layers 13; the pressure fluid can only appear on the upward-facing surface of the insert body in order to support the component 1 arranged there.
  • FIG. 11 shows an embodiment in which the bearing body 2 is a series of Has supports 20; these supports can be designed in the form of a thread, so that the pressure fluid supplied through the opening 6 can spread over the entire length of the insert body. Such an arrangement becomes
  • FIG. 12 shows the mounting or support of an insert body 4 by means of projections 18 molded onto the bearing body 2; these projections 18 each delimit pressurized fluid spaces 5, which can be fed via their own pressurized fluid supply openings 6, if necessary with different pressures.
  • the barrier layers 11 prevent pressure fluid from being able to pass from the individual sectors of the insert body 4 into adjacent sectors.
  • the pressurized fluid exits through the areas of the insert body 4 that are free of support parts 12 and supports the component 1, forming the bearing gap 8.
  • the support body 12 and the locking components 11 can be formed in one piece.
  • Fig. 13 shows an embodiment in which between two in the direction of
  • Arrow 21 moving transport sieves 22, 23 a fiber suspension 24 to be squeezed is provided.
  • the transport screen 23 is supported on a hydrostatic bearing according to the invention, which is similar to the hydrostatic bearing shown in FIG. 1.
  • An insert 4 made of a porous material, on which the transport screen 23 is supported, is arranged in a bearing body 2 to form an intermediate space or pressure fluid space 5.
  • the pressure fluid is supplied to the pressure fluid chamber 5 via an opening 6.
  • 14 shows an embodiment in which the porous insert part 4 is arranged in a rotating hollow shaft 27.
  • the pressure fluid is supplied to the pressure fluid space 5 via a channel 28 and openings 29 opening into this channel 28.
  • the porous insert part 4 is supported by spring elements 31 provided in a bearing body 30.
  • a rotating component 32 is supported on two hydrostatic bearings.
  • Each of the hydrostatic bearings has a porous, sleeve-shaped insert part 4, which is supported in a bearing body 2 with the interposition of a pressure fluid space 5, to which the pressure fluid is supplied via a channel 33.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

L'invention concerne un palier hydrostatique et vise plus particulièrement à obtenir un tel palier exempt le plus possible de frottement et à simplifier sa construction. A cet effet, l'invention est caractérisée en ce qu'il est prévu dans un espace creux (3) d'un corps de palier (2) pour un composant (1), une pièce d'insertion (4) en un matériau poreux, servant de support audit composant (1). La pièce d'insertion en un matériau poreux (4) est soumise à l'action d'un fluide sous pression lequel pénètre à travers les pores de ladite pièce (4). Ces pores forment des poches d'appui miniatures permettant ainsi au fluide sous pression se trouvant à l'intérieur de celles-ci de jouer le rôle de support pour le composant (1).
PCT/AT2001/000089 2000-03-24 2001-03-26 Palier hydrostatique WO2001071207A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU43933/01A AU4393301A (en) 2000-03-24 2001-03-26 Hydrostatic bearing

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA506/2000 2000-03-24
AT5062000 2000-03-24

Publications (1)

Publication Number Publication Date
WO2001071207A1 true WO2001071207A1 (fr) 2001-09-27

Family

ID=3675465

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AT2001/000089 WO2001071207A1 (fr) 2000-03-24 2001-03-26 Palier hydrostatique

Country Status (2)

Country Link
AU (1) AU4393301A (fr)
WO (1) WO2001071207A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150023617A1 (en) * 2013-07-17 2015-01-22 Metal Industries Research And Development Centre Hydrostatic bearing
EP2829752B1 (fr) * 2013-07-24 2017-09-06 ess-micromechanik GmbH Palier aérostatique
US10557501B1 (en) * 2018-12-21 2020-02-11 Metal Industries Research & Development Centre Noncontact fluid bearing and manufacturing method thereof

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3407013A (en) * 1967-02-15 1968-10-22 Apex Bearing Company Bearing systems
DE1425043A1 (de) * 1963-07-09 1968-12-12 Kernreaktor Bau Und Betr Sgmbh Schwebelagerung
DE8132123U1 (de) * 1981-11-03 1985-04-25 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Gaslagerung relativ zueinander sich bewegender Bauteile
US4848932A (en) * 1987-08-03 1989-07-18 Interatom Gmbh Gas-static and gas-dynamic bearing
US5028148A (en) * 1989-04-10 1991-07-02 Hitachi, Ltd. Slide bearing device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1425043A1 (de) * 1963-07-09 1968-12-12 Kernreaktor Bau Und Betr Sgmbh Schwebelagerung
US3407013A (en) * 1967-02-15 1968-10-22 Apex Bearing Company Bearing systems
DE8132123U1 (de) * 1981-11-03 1985-04-25 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Gaslagerung relativ zueinander sich bewegender Bauteile
US4848932A (en) * 1987-08-03 1989-07-18 Interatom Gmbh Gas-static and gas-dynamic bearing
US5028148A (en) * 1989-04-10 1991-07-02 Hitachi, Ltd. Slide bearing device

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150023617A1 (en) * 2013-07-17 2015-01-22 Metal Industries Research And Development Centre Hydrostatic bearing
EP2829752B1 (fr) * 2013-07-24 2017-09-06 ess-micromechanik GmbH Palier aérostatique
US10557501B1 (en) * 2018-12-21 2020-02-11 Metal Industries Research & Development Centre Noncontact fluid bearing and manufacturing method thereof

Also Published As

Publication number Publication date
AU4393301A (en) 2001-10-03

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