EP1045996A1 - Palier hydrostatique pour absorber des forces axiales et radiales - Google Patents

Palier hydrostatique pour absorber des forces axiales et radiales

Info

Publication number
EP1045996A1
EP1045996A1 EP98900061A EP98900061A EP1045996A1 EP 1045996 A1 EP1045996 A1 EP 1045996A1 EP 98900061 A EP98900061 A EP 98900061A EP 98900061 A EP98900061 A EP 98900061A EP 1045996 A1 EP1045996 A1 EP 1045996A1
Authority
EP
European Patent Office
Prior art keywords
bearing
shaft
forces
hydrostatic
water
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP98900061A
Other languages
German (de)
English (en)
Inventor
Ulrich Raess
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP1045996A1 publication Critical patent/EP1045996A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
    • F16C32/0696—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for both radial and axial load
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
    • B23Q1/70—Stationary or movable members for carrying working-spindles for attachment of tools or work
    • 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
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators

Definitions

  • the prior invention relates to bearings and in particular it relates to bearings for grinding and milling spindles in machine tools for machining technology as defined in the claims.
  • machine tools are used, among other things, for machining components such as metal components.
  • Such machine tools often have a grinding or milling spindle which is driven by a high-speed motor and which work spindle can be connected to an adapter for receiving a workpiece or a tool
  • Such work spindles of machine tools are guided over bearings. These bearings perform a variety of tasks.
  • the bearings give the components 5 that are used to perform the cutting and feed movements an exact path of movement, they also bear the weight of the spindle shaft and surrounding components, and the bearings also take any stresses that arise - exert vibration-free forces.
  • a high degree of rigidity and a high level of damping are therefore required, perpendicular and parallel to the guideway.
  • Ball bearing bearings are less suitable for the work area at high speeds. They are quite voluminous and therefore limit their inclusion in the machine tool. In order to meet the requirements for low friction at high revolutions with ball and roller bearings and to absorb axial and radial forces, several small ball bearings are often arranged to accommodate an axial or radial force component.
  • Such ball or roller bearings have point and line pressure contact with the work spindle. They therefore have a line stiffness, which can lead to tilting and deflection and further, consequent disadvantages under moment loads.
  • This shock sensitivity essentially determines the relatively short lifespan of the ball or Bearings.
  • additional stabilizing bearings are arranged. All of these disadvantages make the use of ball and roller bearings uneconomical with today's ever increasing demands on cutting speeds.
  • Magnetic bearings can only be used to a limited extent for use in a milling tool. High forces are generated during milling, which requires a high load capacity and high radial and axial rigidity of the bearing.
  • a disadvantage of magnetic bearings is that they are relatively soft and only lightly resilient. In addition, they are quite expensive and can only be controlled by electronics.
  • Hydrostatic bearings with hydraulic oil are preferred in machine tools that operate in the lower speed range.
  • a disadvantage of an application in high-speed machine tools is that the oil generates frictional heat due to its high viscosity and the resulting frictional heat is poorly transported away.
  • hydrostatic bearings only accept force components in one direction.
  • the warehouse should have a simple and compact structure and it should be economical to purchase and maintain.
  • the warehouse should be compatible and integrable with common processes in the tool industry. This object is achieved by the invention as defined in the claims.
  • the idea of the invention is to provide a single bearing for receiving the force components that occur.
  • the bearing is preferably designed in one piece and receives axial and / or radial force components which occur on a shaft and adjacent elements. This is a departure from known designs, where several separate bearings are used for such purposes.
  • the movement of the shaft in the bearing can be compared to a gyroscopic movement.
  • the center of the shaft in the area of the bearing represents the stop point of the gyro, which is why gyro equations can be used to describe the movement and to take precession and nutation into account.
  • the bearing is provided with specially arranged bearing areas, which effectively compensate for shaft precession and nutation.
  • the present invention can thus be used in a high-speed machine tool for machining technology, advantageously direct power transmission via a flange from the shaft to a machine tool.
  • the camp is advantageously hydrostatic and is operated with water. It is thus possible to preload the bearing in the idle state of the shaft by means of turbulent flowing water which flows through nozzles into a bearing gap between the shaft and the bearing.
  • the shaft is mounted on the water film so that it is flat.
  • the bearing gap allows the external forces acting on the spindle shaft to be balanced with the preload of the bearing unit. This enables hydrostatically controlled compensation of the forces acting on the bearing from the outside.
  • the gap width can be controlled in a simple and uncomplicated manner by means of pocket printing, without disturbing resonances and / or rocking of the shaft occurring during operation.
  • Fig. 1 general view through part of a preferred embodiment of a machine tool with a work spindle and with a bearing in vertical section.
  • FIGS. 1 and 2 show the arrangement of opposite areas of a bearing according to FIGS. 1 and 2.
  • FIGS. 1 to 3 shows the overall view of part of an exemplary embodiment of a bearing 2 according to the invention in exemplary use in a machine tool with a spindle shaft 3, with a pressure feed flange 9, a housing 5 with a high-frequency motor 1 and a first flange 4.
  • a bearing 2 according to the invention in exemplary use in a machine tool with a spindle shaft 3, with a pressure feed flange 9, a housing 5 with a high-frequency motor 1 and a first flange 4.
  • the rotor of the motor 1, the bearing 2 and a first flange 4 adjoining the bearing 2 on the end face are connected to one another via the spindle shaft 3 with axis AA ′.
  • the pressure feed flange 9 is screwed onto the housing by means of screws 15. These screws are located in the outer area of the pressure feed flange 9.
  • the bearing 2 with axis BB ' is preferably a hydrostatic bearing.
  • This bearing 2 absorbs radial and axial forces via the shaft 3 and axial forces via the element or first flange 4 adjoining the end of the bearing 2, which are transmitted during the generation of cutting and forming movements of the rotating components.
  • Water is preferably used as the medium for operating the hydrostatic bearing 2.
  • the motor unit 1 is located in a motor housing 5, the rotor of which is connected directly to the spindle shaft 3, for example by means of a shrink fit, and later rotates it.
  • the stator of the motor encloses the rotor.
  • the pressure feed flange 9 enables the pressure medium to be fed in and out via the seal 10.
  • the hydrostatic bearing 2 is sealed towards the motor housing and outwards via labyrinths 7 and 13.
  • the hydrostatic bearing 2 consists of a one-piece body in the exemplary form of a flange with a feed channel 14 at the end of which there are several channels. A detailed description of the bearing 2 and its elements is given in the description according to FIGS. 2 and 2a.
  • This one-piece body transmits the forces to the next assembly, for example to the machine tool 11, and is screwed onto the machine tool by means of screws 6.
  • the person skilled in the art is free to design the bearing body in several pieces; this may be necessary for assembly reasons, for example.
  • the diameter of the spindle shaft 3 is reinforced in the contact area between the bearing and the motor, so that on this surface the axial force which is generated in particular by the weight of the motor and can be absorbed by the bearing via the spindle shaft.
  • a cover 8 sits on the flange 12, which is fastened to the housing 5 by means of screws 16 by the bearing flange 2.
  • the simple and compact design of the bearing 2 ensures that a high-speed motor is connected directly to the spindle shaft and that the hydrostatic bearing 2 operates without contact in the area of high speed indicators.
  • Non-contact means that the spindle shaft 3 has no contact with the bearing material. Since the shaft and bearing work without contact, a long service life can be expected.
  • 2 and 2a show the functional principle of the hydrostatic bearing 2 according to FIG. 1.
  • the feed channel 14 of the bearing 2 has several channels.
  • a first channel 17 forms the continuation of the feed channel. This channel 17 ends in a nozzle 18. This nozzle is a fixed pre-throttle.
  • nozzles 18, 22, 23 are open to the outside by means of known techniques, ie to the spindle 3 or to the first flange 4.
  • This gap 19-24.25 is flowed through with the medium water during the operating phase. The water advantageously flows through these nozzles.
  • the bearing of the spindle shaft 3 shown by way of example thus functions via a water film which is established in columns 19, 24, 25 between nozzles 18, 22, 23 and spindle shaft 3 and the first flange 4.
  • this bearing 2 is advantageously ensured by the fact that bearing areas arranged in a ring in the bearing absorb the axial and radial forces.
  • bearing areas arranged in a ring in the bearing absorb the axial and radial forces.
  • three to eight storage areas are arranged at a distance from one another and are advantageously made in one piece without separation channels. The missing separation channels counteract a loss of rigidity.
  • First bearing areas which point largely perpendicular to the axis AA 'of the spindle shaft 3, absorb forces acting radially on the spindle shaft 3.
  • Further bearing areas which point largely parallel to the axis AA 'of the spindle shaft 3, absorb axially acting forces.
  • This bearing 2 thus absorbs radial and axial forces from the spindle 3 via first bearing regions and absorbs and gives axial forces from the flange 4 via further bearing regions these forces again via the further flange 2, which is connected to the machine tool 11.
  • these bearing areas have been optimized.
  • a first channel 17 forms the continuation of the feed channel 14 in the direction of the spindle shaft 3 along the axis BB '.
  • the other two channels 20, 21 protrude perpendicularly from the lower area of the feed channel. These channels also each end in columns 24, 25 via a nozzle opening 22, 23.
  • One channel 21 is on the flange side, the other channel 20 is oriented on the motor side.
  • These gaps 19, 24, 25 are filled with water and allow the absorption of the radial and axial forces which are transmitted to the flange on the one hand during tool machining and on the other hand absorb the axial forces which are transmitted via the spindle shaft. Due to the high forces that arise during the grinding or milling process, high surface stiffness of the bearing is required, which can be achieved via the pressure medium water.
  • Water is characterized by a suitable E-module of approx. 2.1 10 * 5 N / cm 2 and a suitable kinematic viscosity of 1.0 mm 2 / s at 20 ° C.
  • E-module of approx. 2.1 10 * 5 N / cm 2
  • suitable kinematic viscosity of 1.0 mm 2 / s at 20 ° C.
  • the bearing 2 is biased by water pressure in the idle state.
  • the contact between shaft 3 and the solid material of the bearing 2 is only given over water and is referred to as non-contact and thus as frictionless.
  • the flow speed and the amount of water are retained even when the bearing is working under load.
  • the person skilled in the art is free to choose other dimensions and ratios of gap height and pocket width.
  • the shaft 3 presses on the small gap h 0 along the axis BB '.
  • the gap h reduces its distance from the shaft 3 by delta h.
  • This reduction in the gap height reduces the outflow of water and increases the pocket pressure in the larger gap area H.
  • This pressure increase counteracts the external force F r , which causes the gap to be reduced.
  • the gap increases again automatically and the pocket pressure in the warehouse decreases.
  • the described pressure compensation works smoothly and therefore hardly causes any heat to be generated.
  • the temperature rise of the bearing is avoided by the circulation of the flowing water with turbulent flow.
  • FIG. 3 An exemplary arrangement of the bearing 2 around the work spindle 3 can be seen in FIG. 3.
  • Fig. 3 is based on the previous description and refers to this.
  • the bearing 2 lies in a ring around the working shaft 3.
  • a radial force application F r is compensated for via a plurality of first bearing areas which are largely radial to the axis AA' of the shaft 3.
  • a grain pensation of an axial force application F. over several other bearing areas, which are largely axial to the axis AA 'of the shaft 3.
  • FIG. 4 shows a diagram on which the force relationships of two exemplary regions of the bearing 2 lying opposite one another can be seen.
  • Fig. 4 is based on the previous description and refers to this.
  • the gap width h of the bearing areas changes depending on the external force F acting.
  • the force axis points upwards and is designated by F.
  • the axis of the gap height is drawn to the right and named with h. If the external force F 1 rises in a first bearing area, for example, the force F 2 drops to the same extent in an opposite bearing area, for example in a second bearing area.
  • the central position of the gap h m can be read, which occurs during the phase of the preload F v in both areas of the bearing 2.
  • An operating force F B occurs during the operation of the rotating shaft 3 and is the sum of the external force and the pocket force that builds up in the bearing 2. With this operating force, the new column height deviates by a delta h from the central position of the gap h m . To the same extent that the gap h of the first storage area becomes smaller, the opposite gap h of the second storage area becomes larger.
  • the machine tool and its elements are made, for example, from known and proven materials such as metal (Cr-Ni steel, etc.). Of course, other realizations of a machine tool and its elements with other materials are also available to the person skilled in the art with knowledge of the present invention.

Landscapes

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

Abstract

L'invention concerne un palier pour un arbre à indice de vitesse élevé, qui absorbe des forces extérieures s'exerçant sur l'arbre. Il est prévu un palier hydrostatique (2) monobloc pour absorber des forces axiales et radiales en cas d'indice de vitesse élevé, ainsi qu'un arbre (3) à monter, qui est disposé sans contact par l'intermédiaire d'eau, comme fluide hydraulique. Un corps de palier comporte plusieurs canaux (17, 20, 21) qui débouchent dans des ajutages (18, 22, 23) . Entre les ajutages (18, 22, 23) et un arbre (3) à monter et/ou d'autres éléments, il se trouve une fente (19, 24, 25) présentant différentes hauteurs (H, h). De l'eau s'écoule par des ajutages et porte l'arbre (3) à monter sur une pellicule d'eau. L'ensemble de la force de ce palier est absorbée par un flasque vissé sur la machine-outil.
EP98900061A 1998-01-06 1998-01-06 Palier hydrostatique pour absorber des forces axiales et radiales Withdrawn EP1045996A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CH1998/000003 WO1999035413A1 (fr) 1998-01-06 1998-01-06 Palier hydrostatique pour absorber des forces axiales et radiales

Publications (1)

Publication Number Publication Date
EP1045996A1 true EP1045996A1 (fr) 2000-10-25

Family

ID=4551299

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98900061A Withdrawn EP1045996A1 (fr) 1998-01-06 1998-01-06 Palier hydrostatique pour absorber des forces axiales et radiales

Country Status (5)

Country Link
US (1) US6419396B1 (fr)
EP (1) EP1045996A1 (fr)
JP (1) JP2002500328A (fr)
AU (1) AU5305298A (fr)
WO (1) WO1999035413A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110299806A1 (en) * 2010-06-08 2011-12-08 Leonid Kashchenevsky Spindle, shaft supporting device and method of supporting a rotatable shaft
TWI560019B (en) * 2014-11-21 2016-12-01 Ind Tech Res Inst Hydraulic hydrostatic pressure rotation module
JP6775276B2 (ja) * 2019-03-15 2020-10-28 株式会社ソディック 静圧流体軸受装置
CN111408743B (zh) * 2020-05-13 2021-05-11 浙江双正科技股份有限公司 一种机床

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1072684A (en) * 1963-12-10 1967-06-21 Interwood Ltd Improvements in or relating to fluid bearings
US3472565A (en) * 1967-09-05 1969-10-14 Harold E G Arneson Externally pressurized bearing structure
DE1965580A1 (de) * 1968-12-30 1970-07-02 Toernkvist Dipl Ing Rolf Lagereinrichtung fuer hydrostatische Lagerung zweier zueinander beweglicher Teile
US3785708A (en) * 1971-10-12 1974-01-15 Y Miyasaki Static fluid pressure bearings
US3827767A (en) 1973-01-29 1974-08-06 Hoesch Werke Ag Hydrostatic bearing
US4206953A (en) 1979-02-12 1980-06-10 General Motors Corporation Hydrostatic bearing support for a work tool
DE3763967D1 (de) * 1986-11-24 1990-08-30 Philips Nv Wellenlagerung mit hydrostatischen lagern.
JPH0726650B2 (ja) * 1989-01-20 1995-03-29 エヌティエヌ株式会社 静圧気体軸受スピンドル
US5073036A (en) * 1990-03-30 1991-12-17 Rockwell International Corporation Hydrostatic bearing for axial/radial support
JP3517263B2 (ja) * 1994-02-03 2004-04-12 Ｎｔｎ株式会社 静圧気体軸受スピンドル
JPH1113764A (ja) * 1997-06-23 1999-01-22 Ntn Corp 静圧空気軸受

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9935413A1 *

Also Published As

Publication number Publication date
US6419396B1 (en) 2002-07-16
JP2002500328A (ja) 2002-01-08
AU5305298A (en) 1999-07-26
WO1999035413A1 (fr) 1999-07-15

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