DE2900363A1 - Machine tool hydrostatic radial and thrust bearing - has two multiple thrust bearings close to plane of radial load - Google Patents

Machine tool hydrostatic radial and thrust bearing - has two multiple thrust bearings close to plane of radial load

Info

Publication number
DE2900363A1
DE2900363A1 DE19792900363 DE2900363A DE2900363A1 DE 2900363 A1 DE2900363 A1 DE 2900363A1 DE 19792900363 DE19792900363 DE 19792900363 DE 2900363 A DE2900363 A DE 2900363A DE 2900363 A1 DE2900363 A1 DE 2900363A1
Authority
DE
Germany
Prior art keywords
radial
bearing
bearings
axial
hydrostatic
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Withdrawn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
DE19792900363
Other languages
German (de)
Inventor
Dan Aurel Dipl Ing Disescu
Dan Alexandru Dipl Ing Hincu
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.)
Institutul de Cercetare Stiintifica Inginerie Tehnologica SI Proiectare Mine pe Lignit SA
Original Assignee
Institutul de Cercetare Stiintifica Inginerie Tehnologica SI Proiectare Mine pe Lignit SA
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
Priority to NL7900043A priority Critical patent/NL7900043A/en
Application filed by Institutul de Cercetare Stiintifica Inginerie Tehnologica SI Proiectare Mine pe Lignit SA filed Critical Institutul de Cercetare Stiintifica Inginerie Tehnologica SI Proiectare Mine pe Lignit SA
Priority to DE19792900363 priority patent/DE2900363A1/en
Publication of DE2900363A1 publication Critical patent/DE2900363A1/en
Withdrawn legal-status Critical Current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
    • F16C32/0629—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
    • F16C32/0651—Details of the bearing area per se
    • F16C32/0659—Details of the bearing area per se of pockets or grooves
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • 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

Landscapes

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

Abstract

The hydrostatic radial-load and thrust bearing is esp. for machine-tool spindles. Two multiple thrust bearings (j, m) are mounted as close as possible to the plane in which the radial load on the bearing acts. There are two radial-load bearings (g, h) on the same side of the thrust bearings, near the point at which an external force acts on the spindle. The thrust bearings absorb the resultant of thrust forces and bending moments and the radial-load bearings that of the radial forces.

Description

Hydrostatisches Radial-Axial-Lager, insbesondere fürHydrostatic radial-axial bearing, especially for

Werkzeugmaschinenspindeln Die Erfindung betrifft ein hydrostatisches Radial-Axial-Lager zur AuSnahme der Radialkräfte und Axialkräfte sowie der Biegemomente, insbesondere bei Werkzeugmaschinenspindeln. Machine tool spindles The invention relates to a hydrostatic one Radial-axial bearings to absorb the radial forces and axial forces as well as the bending moments, especially with machine tool spindles.

Es sind derartige kombinierte Lager bekannt, bei denen zwei Axiallager mit kreisförmigen Aussparungen zwischen zwei Radiallagern angeordsiet sind.Such combined bearings are known in which two axial bearings are angeordsiet with circular recesses between two radial bearings.

Bei diesel hydrostatischen Lagern ist zu bemängeln, daß sie nicht genügend kompakt (massiv) sind und die Spindel auch nicht ausreichend starr, also spielfrei lagern.In the case of diesel hydrostatic bearings, it is to be criticized that they are not are sufficiently compact (massive) and the spindle is also not sufficiently rigid, i.e. store free of play.

Zur Beseitigung dieser Nachteile sind bei dem erfindungsgemäßen Lager zwei Mehrfach-Ringdruck-Lager in einem möglichst kleinen Abstand von der Ebene angeordnet, in der die Radialkraftkomponente, mit welcher die hydrostatisch gelagerte Spindel belastet ist, wirken, und es sind zwei Radiallager auf derselben Seite der Mehrfach-Ringdruck-Lager angeordnet, und zwar in der Nähe des Endes, an dem eine Außenkraft auf die Systemspindel wirkt, so daß die Mehrfach-Ringdruck-Lager die Resultierende der Axialkräfte und die Biegemomente und die Radiallager die Resultierende der Radialkräfte aufnehmers.To eliminate these disadvantages are in the camp according to the invention two multiple ring pressure bearings arranged at the smallest possible distance from the plane, in which the radial force component with which the hydrostatically mounted spindle is loaded, act, and there are two radial bearings on the same side of the multiple ring pressure bearing arranged near the end at which an external force is exerted on the system spindle acts so that the multiple ring pressure bearing is the resultant of the axial forces and the bending moments and the radial bearings the resultant of the radial forces transducer.

Weitere Ausgestaltungen sind in den Unteransprüchen angegeben.Further refinements are given in the subclaims.

Zur näheren Erläuterung wird nachfolgend ein Ausführungsbeispiel anhand der Zeichnung beschrieben. Es zeigen: Fig. 1 einen Längsschnitt durch ein erfindungsgemäßes Lager nach Linie A-A in Fig. 2; o Fig. 2 den Querschnitt nach Linie B-B in Fig. 1; Fig. 3 den Querschnitt nach Linie C-C in Fig. 1 und Fig. 4 den Längsschnitt nach Linie D-D in Fig. 3.For a more detailed explanation, an exemplary embodiment is given below described in the drawing. 1 shows a longitudinal section through an inventive device Bearing along line A-A in Fig. 2; o Fig. 2 shows the cross section along line B-B in Fig. 1; 3 shows the cross section along line C-C in FIG. 1 and FIG. 4 shows the longitudinal section Line D-D in Figure 3.

Die Lagerbüchse 1 des erfindungsgemäßen hydrostatischen Radial-Axial-Lagers weist eine axiale Bohrung e auf, welche durch radiale Bohrung c, d mit je einer am Umfang der Lagerbüchse angeordneten umlaufenden Nut a, b verbunden ist. In dem einen stirnseitigen Deckel 2 ist eine zur axialen Bohrung e koaxiale Öffnung f vorgesehen.The bearing bush 1 of the hydrostatic radial-axial bearing according to the invention has an axial bore e, which through radial bore c, d each connected to a circumferential groove a, b arranged on the circumference of the bearing bush is. In the one end cover 2 is one of the axial bore e coaxial Opening f provided.

Das Drucköl od. dgl. Flüssigkeit wird dem Lager wahlweise durch eine der Bohrungen c, d, f zugeführt, die jeweils andere Bohrung bzw. Bohrungen sind dann in bekannter Weise verschlosse Von den Ringnuteii a, b dringt das Drucköl dann durch die Kapillarröhren 3 (Drosseln) in die beiden hydrostatischen Radiallager g und h ein, die in der Bohrung der Lagerbüchse 1 ausgebildet sind. (Fig. 1 und 2) Aus der Ringnut b gelangt das Drucköl ferner über Kapillarröhren 4 und Kanäle i in ein Mehrfach-Ringdruck-Lager j (Axiallager), welches an dem einen, dem rechten Ende der Lagerbüchse 1 angeordnet ist. Ferner dringt Drucköl von der Ringnut b über Bohrung k, Abstandsstück 5, Kapillarröhren 6 und Kanal 1 in ein Mehrfach-Ringdruck-Lager m, welches neben dem rechten Deckel 7 des Lagers ausgebildet ist. (Fig. 3 und 4) Aus dem Radiallager g fließt das Drucköl od. dgl. nach links in eine Ausnehmung oder Kammer n, die mit einigen Längsbohrungei o der Lagerbüchse verbunden ist. Ferner ist zwischen den beiden Radiallagern g und h eine kreisringförmige Kammer p ausgebildet, in welche Flüssigkeit sowohl von dem linken Lager g wie von dem rechten Lager h gelangt; diese Kammer p ist durch radiale Bohrungen r mit den axialen Bohrungen o verbunden, In diese axialen Sammenbohrungen o gelangt auch das Drucköl, welches vom Radiallager h nach recht abfließt, und welches von den Axiallagern j, m abfließt. Zu diesem Zweck ist zwischen Radiallager h und dem linken Axiallager j eine umlaufende Ringkammer s ausgebildet, die durch radiale Kanäle t mit den axialen Kanälen o verbunden ist. Das vou dem rechten Axiallager m radial nach innen fließende Öl gelangt über einen umlaufenden Ringraum v und radiale Kanäle x sowie axiale Verbindungsbohrungen y, z zu den axialen Sammelbohrungen 0.The pressure oil or the like. Liquid is the camp optionally by a of the holes c, d, f supplied, each of which is the other hole or holes then closed in a known manner. The pressure oil then penetrates from the ring grooves a, b through the capillary tubes 3 (throttles) into the two hydrostatic radial bearings g and h, which are formed in the bore of the bearing bush 1. (Fig. 1 and 2) The pressurized oil also passes from the annular groove b via capillary tubes 4 and channels i into a multiple ring pressure bearing j (thrust bearing), which is attached to the one on the right The end of the bearing bush 1 is arranged. Furthermore, pressure oil penetrates from the annular groove b Bore k, spacer 5, capillary tubes 6 and channel 1 in a multiple ring pressure bearing m, which is formed next to the right cover 7 of the camp. (Fig. 3 and 4) The pressure oil or the like flows from the radial bearing g to the left into a recess or chamber n, which is connected to some longitudinal bores o of the bearing bush. Further an annular chamber p is formed between the two radial bearings g and h, into which liquid both from the left bearing g and from the right bearing h arrives; this chamber p is through radial holes r with the axial Bores o connected, The pressure oil also gets into these axial joint bores o, which flows from the radial bearing h to the right, and which flows from the axial bearings j, m drains. For this purpose there is between radial bearing h and the left axial bearing j a circumferential annular chamber s formed, which through radial channels t with the axial Channels o is connected. The vou the right axial bearing m flowing radially inward Oil passes through a circumferential annular space v and radial channels x as well as axial connecting bores y, z to the axial collecting bores 0.

Auch das von den Axiallagern j, m radial nach außen fließende Öl gelangt über einen umlaufenden Ringraum Y in die Sammelbohrungen o. Aus den Sammelkanälen o gelangt das b1 durch einen der Anschlüsse r, t, x, y, z zurück zum Tank; die jeweils nicht benötigten Anschlüsse werden verschlossen (Fig. 1, 3, 4).The oil flowing radially outward from the axial bearings j, m also arrives Via a circumferential annular space Y into the collecting bores o. From the collecting channels o the b1 gets back to the tank through one of the ports r, t, x, y, z; each Connections that are not required are closed (Fig. 1, 3, 4).

Wie Fig. 2 und 3 zeigen, sind zwei axiale Sammelkanäle o vorgesehen. Die beiden stirnseitigen Deckel 2, 7 sind mittels bekannter Dichtungen gegenüber der Welle bzw. Spindel 8 abgedichtet.As shown in FIGS. 2 and 3, two axial collecting channels o are provided. The two end covers 2, 7 are opposite by means of known seals the shaft or spindle 8 sealed.

Das erfindungsgemäße Lager hat hauptsächlich folgende Vorteile: Die Spindel ist gut unterstützt und damit ihre Steifigkeit bzw. Starrheit erhöht bzw. ihre Durchbiegung vermindert; an den Stirnflächen und am Umfang der Lagerbüchse stehen wahlweise mehrere Bohrungen zum Anschluß der Schmierflüssigkeit zur Verfügung, von denen die jeweils günstigste ausgewählt und die übrigen durch einen Stöpsel od. dgl. verschlossen werden auch kann das Schmiermedium an einer einzigen von mehreren Stellen aus dem Gehäuse abgelassen werden.The bearing according to the invention mainly has the following advantages: The The spindle is well supported and thus its rigidity or rigidity increases or their deflection is reduced; on the end faces and on the circumference the bearing bushing is optionally available with several bores for connecting the lubricant available, of which the cheapest selected and the rest by a stopper or the like. The lubricant can also be closed on a be drained from the housing from several places.

L e e r s e i t eL e r s e i t e

Claims (4)

Patentansprüche Hydrostatisches Radial-Axial-Lager, insbesondere für Werkzeugmaschinenspindeln, dadurch gekennzeichnet, daß zwei Mehrfach-Ringdruck-Lager (j, m) (Axiallager) in einem möglichst geringen Abstand von der Ebene angeordnet sind, in der die die Spindel belastende Radialkraftkompnente wirkt, und daß zwei Radiallager (g, h) auf derselben Seite der Mehrfach-Ringdruck-Lager (j, m) angeordnet sind, und zwar in der Nähe der Stelle bzw. der Stellen, an denen eine Außenkraft auf die Spindel wirkt, so daß die Mehrfach-Ringdruck-Lager (j, m) die Resultierende der Axialkräfte und der Biegemomente und die Radiallager (g, h) die Resultierende der Radialkräfte aufnehmen. Claims Hydrostatic radial-axial bearing, in particular for machine tool spindles, characterized in that two multiple ring pressure bearings (j, m) (axial bearing) arranged at the smallest possible distance from the plane are in which the radial force component loading the spindle acts, and that two Radial bearings (g, h) are arranged on the same side of the multiple ring pressure bearings (j, m) are near the point or points where an external force acts on the spindle so that the multiple ring pressure bearing (j, m) is the resultant the axial forces and the bending moments and the radial bearings (g, h) the resultant absorb radial forces. 2. Hydrostatisches Radial-Axial-Lager gemäß Anspruch 1, dadurch gekennzeichnet, daß die Lagerbüchse (1) eine - sich durch den einen Gehäusedeckel (2) hindurcherstreckende - axiale Bohrung (e) aufweist, die durch zwei radiale Bohrungen (c, d) mit zwei Ringnuten (a, b) am Außenumfang der Lagerbüchse (i) verbunden ist, zur wahlweisen Zufuhr des Drucköls.2. Hydrostatic radial-axial bearing according to claim 1, characterized in that that the bearing bush (1) one - extending through the one housing cover (2) - Has axial bore (e) through two radial bores (c, d) with two Annular grooves (a, b) on the outer circumference of the bearing bush (i) is connected to the optional Supply of the pressure oil. 3. Hydrostatisches Radial-Axial-Lager nach Anspruch 1 oder 2 dadurch gekennzeichnet, daß für den Abfluß der Schmierflüssigkeit wenigstens eine Längsbohrung (o) in der Lagerbüchse vorgesehen ist, die durch radiale Bohrungen (r, t, x) bzw. Ringkammern (n, p, s, v) einerseits mit den Lagerstellen und andererseits mit dem Außenumfang der Lagerbüchse bzw. mit wenigstens einer Anschlußbohrung (z) in Verbindung steht.3. Hydrostatic radial-axial bearing according to claim 1 or 2 thereby characterized in that at least one longitudinal bore for the drainage of the lubricating liquid (o) is provided in the bearing bush, which is provided by radial bores (r, t, x) or Annular chambers (n, p, s, v) on the one hand with the bearings and on the other hand with the Outer circumference of the bearing bush or with at least one connection bore (z) in connection stands. 4. Lager nach Anspruch 3, dadurch gekennzeichnet, daß für den Abfluß der Schmierflüssigkeit zwischen den beiden Radiallagern (g, h) ein Ringraum (p) und zwischen dem einen Axiallager (j) und dem ihm zugewandten Radiallager (h) ein weiterer Ringraum (s) vorgesehen ist, und daß die den Stirnenden der Lagerbüchse zugewandten Seiten des einen Radiallagers (g) und des anderen Axiallagers (m) mit je einem weiteren Ringraum (n bzw. v) in Verbindung stehen.4. Bearing according to claim 3, characterized in that for the drain the lubricant between the two radial bearings (g, h) an annular space (p) and between the one axial bearing (j) and the radial bearing (h) facing it further annular space (s) is provided, and that the front ends of the bearing bush facing sides of a radial bearing (g) and the other axial bearing (m) with each are connected to a further annulus (n or v).
DE19792900363 1979-01-04 1979-01-05 Machine tool hydrostatic radial and thrust bearing - has two multiple thrust bearings close to plane of radial load Withdrawn DE2900363A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
NL7900043A NL7900043A (en) 1979-01-04 1979-01-04 AXIAL HYDROSTATIC ARMY.
DE19792900363 DE2900363A1 (en) 1979-01-04 1979-01-05 Machine tool hydrostatic radial and thrust bearing - has two multiple thrust bearings close to plane of radial load

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL7900043A NL7900043A (en) 1979-01-04 1979-01-04 AXIAL HYDROSTATIC ARMY.
DE19792900363 DE2900363A1 (en) 1979-01-04 1979-01-05 Machine tool hydrostatic radial and thrust bearing - has two multiple thrust bearings close to plane of radial load

Publications (1)

Publication Number Publication Date
DE2900363A1 true DE2900363A1 (en) 1980-07-17

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Family Applications (1)

Application Number Title Priority Date Filing Date
DE19792900363 Withdrawn DE2900363A1 (en) 1979-01-04 1979-01-05 Machine tool hydrostatic radial and thrust bearing - has two multiple thrust bearings close to plane of radial load

Country Status (2)

Country Link
DE (1) DE2900363A1 (en)
NL (1) NL7900043A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0329193A1 (en) * 1985-10-22 1989-08-23 Reliance Electric Industrial Company An improved bearing assembly, such as a thrust bearing
US5078558A (en) * 1990-02-16 1992-01-07 Hitachi Seiko, Ltd. Low mass spindle and Z-axis unit

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0329193A1 (en) * 1985-10-22 1989-08-23 Reliance Electric Industrial Company An improved bearing assembly, such as a thrust bearing
US5078558A (en) * 1990-02-16 1992-01-07 Hitachi Seiko, Ltd. Low mass spindle and Z-axis unit

Also Published As

Publication number Publication date
NL7900043A (en) 1980-07-08

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