EP1675704A1 - Machine tool gear mechanism - Google Patents

Machine tool gear mechanism

Info

Publication number
EP1675704A1
EP1675704A1 EP04765685A EP04765685A EP1675704A1 EP 1675704 A1 EP1675704 A1 EP 1675704A1 EP 04765685 A EP04765685 A EP 04765685A EP 04765685 A EP04765685 A EP 04765685A EP 1675704 A1 EP1675704 A1 EP 1675704A1
Authority
EP
European Patent Office
Prior art keywords
spindle
output shaft
gear
machine tool
transmission
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Withdrawn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
EP04765685A
Other languages
German (de)
French (fr)
Inventor
Harald Eckert
Ulrich Ludwig Kuchelmeister
Eckhard FÖRSTER
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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 claimed from DE2003148757 external-priority patent/DE10348757A1/en
Priority claimed from DE2003148755 external-priority patent/DE10348755A1/en
Priority claimed from DE200410003685 external-priority patent/DE102004003685A1/en
Priority claimed from DE200410003684 external-priority patent/DE102004003684A1/en
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP1675704A1 publication Critical patent/EP1675704A1/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Withdrawn legal-status Critical Current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
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • 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
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
    • 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
    • B23Q1/0009—Energy-transferring means or control lines for movable machine parts; Control panels or boxes; Control parts
    • B23Q1/0018—Energy-transferring means or control lines for movable machine parts; Control panels or boxes; Control parts comprising hydraulic means
    • B23Q1/0027—Energy-transferring means or control lines for movable machine parts; Control panels or boxes; Control parts comprising hydraulic means between moving parts between which an uninterrupted energy-transfer connection is maintained
    • B23Q1/0036—Energy-transferring means or control lines for movable machine parts; Control panels or boxes; Control parts comprising hydraulic means between moving parts between which an uninterrupted energy-transfer connection is maintained one of those parts being a tool
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • 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
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T408/00—Cutting by use of rotating axially moving tool
    • Y10T408/44—Cutting by use of rotating axially moving tool with means to apply transient, fluent medium to work or product
    • Y10T408/45—Cutting by use of rotating axially moving tool with means to apply transient, fluent medium to work or product including Tool with duct
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T408/00—Cutting by use of rotating axially moving tool
    • Y10T408/91—Machine frame
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/30—Milling
    • Y10T409/309352—Cutter spindle or spindle support
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/30—Milling
    • Y10T409/309352—Cutter spindle or spindle support
    • Y10T409/309408—Cutter spindle or spindle support with cutter holder
    • Y10T409/309464—Cutter spindle or spindle support with cutter holder and draw bar

Definitions

  • the present invention relates to a machine tool gear, in particular a spindle gear according to the preamble of claim 1.
  • such transmissions which usually comprise a two-stage planetary gear and a corresponding switching device, are arranged axially parallel to the spindle, the force being transmitted to the spindle by means of belts or gear wheels.
  • the high drive torques require high tensile strength and biased "belt and a wide support base for the wide-scale pulleys.
  • cylindrical roller bearings or similar bearings are needed in the transmission output because the belt forces are high.
  • the present invention has for its object to provide a machine tool gear, in particular a spindle gear, in which the disadvantages of the prior art are avoided.
  • the noise level is to be reduced in the transmission according to the invention; furthermore, undesirable vibrations are to be largely avoided.
  • the manufacturing costs are to be reduced and the required installation space optimized.
  • a spindle gear in which the Kraft upon the output shaft of the gearbox to the spindle, the spindle preferably being arranged coaxially with the output shaft.
  • the output shaft of the gearbox is directly connected to the spindle; the torsion-proof connection between the spindle and the output shaft can be positive or non-positive.
  • a connecting part can also be provided between the spindle and the output shaft.
  • an output shaft which is mounted in a short bearing housing and which drives the spindle. This has the advantage that the overall length of the transmission is noticeably reduced.
  • bearings which are almost free of play such as angular contact ball bearings, are suitable for mounting the output shaft; this allows the torque to be transferred to the spindle without vibration.
  • the design according to the invention eliminates the need for a belt or gear drive for the spindle, so that the vibrations and noises caused thereby, the temperature increase due to the flexing work of the belt and the design-related speed limitation are avoided. Furthermore, the elimination of the belt, belt disc or gears achieved significant cost savings; for example, no additional lubrication and cooling of the gears on the output is necessary.
  • a further advantage of the invention is the extensive reduction in oil splash losses between the bearings, since there is a smaller amount of oil in this area.
  • the transmission advantageously requires no maintenance on the output; state-of-the-art gearboxes require retensioning or belt replacement.
  • the direct torque transmission prevents incorrect settings of the belt pretensioning forces, which can damage the spindle bearings on the one hand and cause the belt to slip on the other.
  • the spindle bearing life is increased because no transverse forces due to belt, tooth circumference and axial forces act on the spindle bearings.
  • all parts of the transmission are arranged in a housing, which results in an independence of the operation from external influences.
  • a coolant mist could cause the belt to slip.
  • the arrangement in a housing also increases occupational safety since there are no freely rotating parts.
  • Planetary gears such as those used in machine tool gears, in particular spindle gears, are known to the person skilled in the art. for example from the applicant's EP 1 169582 B1. However, other types of gears can also be used.
  • the figure shows a spindle gear 1, which comprises an input shaft 2, an output shaft 3 and a two-stage planetary gear arranged in the direction of force flow between the input shaft and the input shaft.
  • the planetary gear has a sun gear 4 connected to the drive shaft, a ring gear 5 mounted in a ring gear bearing 6 and a planet carrier 7 with planet 8 which forms the output of the planetary gear.
  • a sliding sleeve 9, a shift fork 10 and a brake disc 11 are provided; the switching unit comprises a solenoid 12, which acts on a shift lever 13 connected to the shift fork 10.
  • the sliding sleeve can assume a neutral position, a first switching position in which the ring gear 5 is coupled to the gear housing 14 and a second switching position in which the ring gear 5 is coupled to the sun gear 4.
  • the output shaft 3 is supported by means of angular contact ball bearings 16, 17 arranged in a bearing housing 15; as a result, the torque can be transmitted from the output shaft 3 to the spindle in a vibration-free manner, which enables a direct connection of the output shaft 3 to the spindle and thus a coaxial and space-saving arrangement.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)
  • Auxiliary Devices For Machine Tools (AREA)

Abstract

The invention relates to a machine tool gear mechanism, especially a spindle gear mechanism, wherein power and/or torque is transferred from the drive shaft (3) of the gear mechanism (1) directly onto the spindle (15). The spindle (15) is arranged in a coaxial manner on the drive shaft (3).

Description

Werkzeugmaschinengetriebe Machine tools gear
Die vorliegende Erfindung betrifft ein Werkzeugmaschinengetriebe, insbesondere ein Spindelgetriebe gemäß dem Oberbegriff des Patentanspruchs 1.The present invention relates to a machine tool gear, in particular a spindle gear according to the preamble of claim 1.
Nach dem Stand der Technik werden derartige Getriebe, die üblicherweise ein zweistufiges Planetengetriebe und eine entsprechende Schalteinrichtung umfassen, achsparallel zur Spindel angeordnet, wobei die Kraftübertragung auf die Spindel mittels Riemen oder Zahnräder erfolgt. Bei Verwendung von Riemen zur Kraftübertragung erfordern die hohen Antriebsdrehmomente zugfeste und vorgespannte" Riemen sowie eine breite Lagerbasis für die breit dimensionierten Riemenscheiben. Des weiteren werden im Getriebeabtrieb Zylinderrollenlager oder ähnliche Wälzlager benötigt, da die Riemenkräfte hoch sind. In nachteiliger Weise sind jedoch größere Wälzlager bei hohen Drehzahlen nur beschränkt einsetzbar. Zudem weisen Wälzlager naturgemäß ein Radialspiel auf, was in Unwuchten und Schwingungen im Planetenträger des Getriebbs resultiert. Bei einem Zahnradantrieb der Spindel entstehen zudem bei Zahnrädern mit Schrägverzahnung Axialkräfte am Getriebeabtrieb, welche zusätzlich aufgefangen werden müssen. Diese Lösungen weisen den weiteren Nachteil auf, dass aufgrund der Kraftübertragung zwischen Getriebe und Spindel das Geräuschniveau im allgemeinen hoch ist.According to the prior art, such transmissions, which usually comprise a two-stage planetary gear and a corresponding switching device, are arranged axially parallel to the spindle, the force being transmitted to the spindle by means of belts or gear wheels. When using belts for power transmission, the high drive torques require high tensile strength and biased "belt and a wide support base for the wide-scale pulleys. Furthermore, cylindrical roller bearings or similar bearings are needed in the transmission output because the belt forces are high. However, are disadvantageously larger rolling bearings at high speeds can only be used to a limited extent In addition, rolling bearings naturally have a radial play, which results in unbalance and vibrations in the planet carrier of the gearbox.With a gear drive of the spindle, gearwheels with helical teeth also generate axial forces on the gearbox output, which must also be absorbed Another disadvantage is that the noise level is generally high due to the power transmission between the gearbox and spindle.
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, ein Werkzeugmaschinengetriebe, insbesondere ein Spindelgetriebe anzugeben, bei dem die Nachteile des Standes der Technik vermieden werden. Insbesondere soll bei dem erfindungsgemäßen Getriebe das Geräuschniveau reduziert werden; ferner sollen unerwünschte Schwingungen weitgehend vermieden werden. Zudem sollen die Herstellungskosten reduziert und der erforderliche Bauraum optimiert werden.The present invention has for its object to provide a machine tool gear, in particular a spindle gear, in which the disadvantages of the prior art are avoided. In particular, the noise level is to be reduced in the transmission according to the invention; furthermore, undesirable vibrations are to be largely avoided. In addition, the manufacturing costs are to be reduced and the required installation space optimized.
Diese Aufgabe wird durch die Merkmale des Patentanspruchs 1 gelöst. Weitere Ausgestaltungen und Vorteile gehen aus den Unteransprüchen hervor.This object is achieved by the features of patent claim 1. Further configurations and advantages emerge from the subclaims.
Demnach wird ein Spindelgetriebe vorgeschlagen, bei dem die Kraftbzw. Momentenübertragung von der Abtriebswelle des Getriebes auf die Spindel direkt erfolgt, wobei die Spindel vorzugsweise koaxial zur Abtriebswelle angeordnet ist.Accordingly, a spindle gear is proposed, in which the Kraftbzw. Torque is transmitted directly from the output shaft of the gearbox to the spindle, the spindle preferably being arranged coaxially with the output shaft.
Hierbei ist die Abtriebswelle des Getriebes mit der Spindel direkt verbunden; die verdrehfeste Verbindung zwischen Spindel und Abtriebswelle kann form- oder kraftschlüssig erfolgen. Es kann auch zwischen Spindel und Abtriebswelle ein Verbindungsteil vorgesehen sein.Here, the output shaft of the gearbox is directly connected to the spindle; the torsion-proof connection between the spindle and the output shaft can be positive or non-positive. A connecting part can also be provided between the spindle and the output shaft.
Gemäß einer besonders vorteilhaften Ausführungsform der Erfindung ist eine in einem kurzen Lagergehäuse gelagerte Abtriebswelle vorgesehen, welche die Spindel antreibt. Dadurch entsteht der Vorteil, dass die Gesamtlänge des Getriebes merklich verkürzt wird.According to a particularly advantageous embodiment of the invention, an output shaft, which is mounted in a short bearing housing and which drives the spindle, is provided. This has the advantage that the overall length of the transmission is noticeably reduced.
Erfindungsgemäß eignen sich für die Lagerung der Abtriebswelle nahezu spielfreie Lager, wie beispielsweise Schrägkugellager; dadurch kann das Drehmoment schwingungsfrei auf die Spindel übertragen werden.According to the invention, bearings which are almost free of play, such as angular contact ball bearings, are suitable for mounting the output shaft; this allows the torque to be transferred to the spindle without vibration.
Durch die erfindungsgemäße Konzeption entfällt die Notwendigkeit eines Riemen- oder Zahnradantrißbs für die Spindel, so dass die dadurch verursachten Schwingungen und Geräusche, die Temperaturerhöhung durch die Walkarbeit des Riemens und die konstruktionsbedingte Drehzahlbegrenzung vermieden werden. Des weiteren wird durch den Wegfall der Riemen, Riemen- scheibe oder Zahnräder eine signifikante Kosteneinsparung erzielt; beispielsweise ist keine zusätzliche Schmierung und Kühlung der Zahnräder am Abtrieb notwendig.The design according to the invention eliminates the need for a belt or gear drive for the spindle, so that the vibrations and noises caused thereby, the temperature increase due to the flexing work of the belt and the design-related speed limitation are avoided. Furthermore, the elimination of the belt, belt disc or gears achieved significant cost savings; for example, no additional lubrication and cooling of the gears on the output is necessary.
Als weiterer Vorteil der Erfindung ist die weitgehende Reduzierung der Ölpantschverluste zwischen den Lagern zu nennen, da sich in diesem Bereich eine geringere Ölmenge befindet.A further advantage of the invention is the extensive reduction in oil splash losses between the bearings, since there is a smaller amount of oil in this area.
Das Getriebe erfordert in vorteilhafter Weise keine Wartung am Abtrieb; bei Getrieben nach dem Stand der Technik ist ein Nachspannen oder ein Austausch des Riemens erforderlich. Außerdem werden durch die direkte Drehmomentübertragung falsche Einstellungen der Riemenvorspannkräfte, die einerseits zur Schädigung der Spindellager und andererseits zum Durchrutschen des Riemens führen können, vermieden. Die Spindellagerlebensdauer wird erhöht, da keine Querkräfte durch Riemen-, Zahnumfangs- und Axialkräfte auf die Spindellager wirken.The transmission advantageously requires no maintenance on the output; state-of-the-art gearboxes require retensioning or belt replacement. In addition, the direct torque transmission prevents incorrect settings of the belt pretensioning forces, which can damage the spindle bearings on the one hand and cause the belt to slip on the other. The spindle bearing life is increased because no transverse forces due to belt, tooth circumference and axial forces act on the spindle bearings.
Gemäß der Erfindung sind sämtliche Teile des Getriebes in einem Gehäuse angeordnet, was eine Unabhängigkeit des Betriebs von äußeren Einflüssen zur Folge hat. (Beispielsweise konnte bei Riemenantrieben ein Kühlmittelnebel zu einem Durchrutschen des Riemens führen). Durch die Anordnung in einem Gehäuse wird auch die Arbeitssicherheit erhöht, da keine freidrehenden Teile existieren.According to the invention, all parts of the transmission are arranged in a housing, which results in an independence of the operation from external influences. (For example, with belt drives, a coolant mist could cause the belt to slip). The arrangement in a housing also increases occupational safety since there are no freely rotating parts.
Die Erfindung wird im folgenden anhand der beigefügten Figur, welche eine schematische Schnittansicht einer bevorzugten Ausführungsform eines Getriebes gemäß der vorliegenden Erfindung darstellt, beispielhaft näher erläutert. Planetengetriebe, wie sie bei Werkzeugmaschinengetrieben, insbesondere Spindelgetrieben eingesetzt werden, sind dem Fachmann bekannt, bei- spielsweise aus der EP 1 169582 B1 der Anmelderin. Es können aber auch weitere Arten von Getrieben eingesetzt werden.The invention is explained in more detail below with reference to the attached figure, which shows a schematic sectional view of a preferred embodiment of a transmission according to the present invention. Planetary gears, such as those used in machine tool gears, in particular spindle gears, are known to the person skilled in the art. for example from the applicant's EP 1 169582 B1. However, other types of gears can also be used.
Die Figur zeigt ein Spindelgetriebe 1 , welches eine Antriebswelle 2, eine Abtriebswelle 3 und ein in Kraftflussrichtung zwischen der Antriebswelle und der Antriebswelle angeordnetes zweistufiges Planetengetriebe umfasst. Das Planetengetriebe weist ein mit der Antriebswelle verbundenes Sonnenrad 4, ein in einer Hohlradlagerung 6 gelagertes Hohlrad 5 und einen Planetenträger 7 mit Planeten 8 auf, der den Abtrieb des Planetengetriebes bildet.The figure shows a spindle gear 1, which comprises an input shaft 2, an output shaft 3 and a two-stage planetary gear arranged in the direction of force flow between the input shaft and the input shaft. The planetary gear has a sun gear 4 connected to the drive shaft, a ring gear 5 mounted in a ring gear bearing 6 and a planet carrier 7 with planet 8 which forms the output of the planetary gear.
Zum Schalten des Getriebes sind eine Schiebemuffe 9, eine Schaltgabel 10 und eine Bremsscheibe 11 vorgesehen; die Schalteinheit umfasst einen Hubmagneten 12, welcher auf einen mit der Schaltgabel 10 verbundenen Schalthebel 13 wirkt. Hierbei kann die Schiebemuffe eine Neutralstellung, eine erste Schaltstellung, bei der das Hohlrad 5 mit dem Getriebegehäuse 14 gekoppelt wird und eine zweite Schaltstellung, bei der das Hohlrad 5 mit dem Sonnenrad 4 gekoppelt wird, annehmen.To shift the transmission, a sliding sleeve 9, a shift fork 10 and a brake disc 11 are provided; the switching unit comprises a solenoid 12, which acts on a shift lever 13 connected to the shift fork 10. Here, the sliding sleeve can assume a neutral position, a first switching position in which the ring gear 5 is coupled to the gear housing 14 and a second switching position in which the ring gear 5 is coupled to the sun gear 4.
Die Abtriebswelle 3 wird mittels in einem Lagergehäuse 15 angeordneter Schrägkugellager 16, 17 gelagert; dadurch kann das Drehmoment von der Abtriebswelle 3 schwingungsfrei auf die Spindel übertragen werden, was eine direkte Verbindung der Abtriebswelle 3 mit der Spindel und somit eine koaxiale und bauraumsparende Anordnung ermöglicht.The output shaft 3 is supported by means of angular contact ball bearings 16, 17 arranged in a bearing housing 15; as a result, the torque can be transmitted from the output shaft 3 to the spindle in a vibration-free manner, which enables a direct connection of the output shaft 3 to the spindle and thus a coaxial and space-saving arrangement.
Selbstverständlich fällt auch jede konstruktive Ausbildung, insbesondere jede räumliche Anordnung der Getriebekomponenten, der Schaltung und der Schalteinheit an sich sowie zueinander und soweit technisch sinnvoll, unter den Schutzumfang der vorliegenden Ansprüche ohne die Funktion des Getriebes, wie sie in den Ansprüchen angegeben ist, zu beeinflussen, auch wenn diese Ausbildungen nicht explizit in den Figuren oder in der Beschreibung dargestellt sind. Of course, every constructive training, in particular every spatial arrangement of the transmission components, the gearshift and the switching unit per se and with each other and as far as technically meaningful, also falls under the scope of protection of the present claims without influencing the function of the transmission, as specified in the claims, even if these designs are not explicitly shown in the figures or in the description.
BezuαszeichenBezuαszeichen
1 Werkzeugmaschinengetriebe 2 Antriebswelle 3 Abtriebswelle 4 Sonnenrad 5 Hohlrad 6 Hohlradlagerung 7 Planetenträger 8 Planet 9 Schiebemuffe 10 Schaltgabel 11 Bremsscheibe 12 Hubmagnet 13 Schalthebel 14 Getriebegehäuse 15 Lagergehäuse 16 Schrägkugellager 17 Schrägkugellager 1 machine tool gear 2 drive shaft 3 output shaft 4 sun gear 5 ring gear 6 ring gear bearing 7 planet carrier 8 planet 9 sliding sleeve 10 shift fork 11 brake disc 12 lifting magnet 13 shift lever 14 gear housing 15 bearing housing 16 angular contact ball bearing 17 angular contact ball bearing

Claims

Patentansprüche claims
1. Werkzeugmaschinengetriebe, insbesondere Spindelgetriebe, dadurch gekennzeichnet, dass die Kraft- bzw. Momentenübertragung von der Abtriebswelle (3) des Getriebes auf die Spindel direkt erfolgt, wobei die Spindel vorzugsweise koaxial zur Abtriebswelle (3) angeordnet ist.1. Machine tool gear, in particular spindle gear, characterized in that the force or torque transmission from the output shaft (3) of the gear to the spindle takes place directly, wherein the spindle is preferably arranged coaxially to the output shaft (3).
2. Werkzeugmaschinengetriebe nach Anspruch 1 , dadurch gekennzeichnet, dass die Abtriebswelle (3) des Getriebes (1 ) mit der Spindel verbunden ist, wobei die verdrehfeste Verbindung zwischen Spindel und Abtriebswelle (3) form- oder kraftschlüssig erfolgt.2. Machine tool gearbox according to claim 1, characterized in that the output shaft (3) of the gearbox (1) is connected to the spindle, the non-rotatable connection between the spindle and the output shaft (3) being positive or non-positive.
3. Werkzeugmaschinengetriebe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Abtriebswelle (3) in einem Lagergehäuse (15) gelagert ist, wobei sie kurz dimensioniert ist, sodass die Gesamtlänge des Getriebes (1 ) verkürzt wird.3. Machine tool transmission according to claim 1 or 2, characterized in that the output shaft (3) is mounted in a bearing housing (15), wherein it is of short dimensions, so that the total length of the transmission (1) is shortened.
4. Werkzeugmaschinengetriebe nach Anspruch 1 , 2 oder 3, dadurch gekennzeichnet, dass für die Lagerung der Abtriebswelle (3) Schrägkugellager (16, 17) vorgesehen sind. 4. Machine tool transmission according to claim 1, 2 or 3, characterized in that angular contact ball bearings (16, 17) are provided for the mounting of the output shaft (3).
EP04765685A 2003-10-21 2004-09-29 Machine tool gear mechanism Withdrawn EP1675704A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE2003148757 DE10348757A1 (en) 2003-10-21 2003-10-21 Planetary gear drive mechanism for machine tool has fixed housing with oil inlet connected to oil pump and supplying oil to output shaft bearings and planet- and ring-gear bearings
DE2003148755 DE10348755A1 (en) 2003-10-21 2003-10-21 Machine tool gear mechanism for transferring power and/or torque from a driven shaft of the gear mechanism to a spindle comprises an integrated rotary transmission leadthrough that serves as a supply device for coolants, oil or air
DE200410003685 DE102004003685A1 (en) 2004-01-24 2004-01-24 Machine tool gear mechanism for transferring power and/or torque from a driven shaft of the gear mechanism to a spindle comprises an integrated rotary transmission leadthrough that serves as a supply device for coolants, oil or air
DE200410003684 DE102004003684A1 (en) 2004-01-24 2004-01-24 Machine tool gear mechanism for transferring power and/or torque from a driven shaft directly onto a spindle comprises a spindle arranged coaxially to a driven shaft
PCT/EP2004/010886 WO2005049266A1 (en) 2003-10-21 2004-09-29 Machine tool gear mechanism

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EP1675704A1 true EP1675704A1 (en) 2006-07-05

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EP04765683A Active EP1676051B1 (en) 2003-10-21 2004-09-29 Planetary gear
EP04765684A Expired - Fee Related EP1675703B1 (en) 2003-10-21 2004-09-29 Machine tool gear mechanism
EP04765685A Withdrawn EP1675704A1 (en) 2003-10-21 2004-09-29 Machine tool gear mechanism
EP04787049A Expired - Fee Related EP1676059B1 (en) 2003-10-21 2004-09-29 Planetary gear

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EP04765683A Active EP1676051B1 (en) 2003-10-21 2004-09-29 Planetary gear
EP04765684A Expired - Fee Related EP1675703B1 (en) 2003-10-21 2004-09-29 Machine tool gear mechanism

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US (4) US7404779B2 (en)
EP (4) EP1676051B1 (en)
JP (4) JP2007508951A (en)
KR (1) KR101098617B1 (en)
DE (3) DE502004006794D1 (en)
ES (3) ES2303953T3 (en)
WO (4) WO2005050066A1 (en)

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US20070099744A1 (en) 2007-05-03
DE502004007086D1 (en) 2008-06-19
US20060270518A1 (en) 2006-11-30
JP4772685B2 (en) 2011-09-14
WO2005050061A1 (en) 2005-06-02
US20070142160A1 (en) 2007-06-21
WO2005049265A1 (en) 2005-06-02
EP1676051B1 (en) 2008-05-07
ES2307046T3 (en) 2008-11-16
US20070032336A1 (en) 2007-02-08
EP1676059B1 (en) 2008-05-07
JP4918362B2 (en) 2012-04-18
EP1676051A1 (en) 2006-07-05
JP2007509293A (en) 2007-04-12
DE502004006794D1 (en) 2008-05-21
US7404779B2 (en) 2008-07-29
KR20060103258A (en) 2006-09-28
EP1675703B1 (en) 2008-04-09
US7360977B2 (en) 2008-04-22
US7445576B2 (en) 2008-11-04
EP1676059A1 (en) 2006-07-05
KR101098617B1 (en) 2011-12-23
JP2007508949A (en) 2007-04-12
EP1675703A1 (en) 2006-07-05
WO2005050066A1 (en) 2005-06-02
DE502004007084D1 (en) 2008-06-19
JP2007508950A (en) 2007-04-12
WO2005049266A1 (en) 2005-06-02
ES2305861T3 (en) 2008-11-01
JP2007508951A (en) 2007-04-12
ES2303953T3 (en) 2008-09-01

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