EP0999567B1 - Gear transmission for switches having at least one switching stage - Google Patents

Gear transmission for switches having at least one switching stage Download PDF

Info

Publication number
EP0999567B1
EP0999567B1 EP98120923A EP98120923A EP0999567B1 EP 0999567 B1 EP0999567 B1 EP 0999567B1 EP 98120923 A EP98120923 A EP 98120923A EP 98120923 A EP98120923 A EP 98120923A EP 0999567 B1 EP0999567 B1 EP 0999567B1
Authority
EP
European Patent Office
Prior art keywords
gear
internal
internal toothing
toothing
cam disc
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.)
Expired - Lifetime
Application number
EP98120923A
Other languages
German (de)
French (fr)
Other versions
EP0999567A1 (en
Inventor
Günter Dieterich
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.)
Stromag GmbH
Original Assignee
Stromag GmbH
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 Stromag GmbH filed Critical Stromag GmbH
Priority to EP98120923A priority Critical patent/EP0999567B1/en
Priority to DE59812577T priority patent/DE59812577D1/en
Priority to AT98120923T priority patent/ATE289448T1/en
Priority to US09/427,172 priority patent/US6244984B1/en
Publication of EP0999567A1 publication Critical patent/EP0999567A1/en
Application granted granted Critical
Publication of EP0999567B1 publication Critical patent/EP0999567B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/32—Driving mechanisms, i.e. for transmitting driving force to the contacts
    • H01H3/40—Driving mechanisms, i.e. for transmitting driving force to the contacts using friction, toothed, or screw-and-nut gearing
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H19/00—Switches operated by an operating part which is rotatable about a longitudinal axis thereof and which is acted upon directly by a solid body external to the switch, e.g. by a hand
    • H01H19/02—Details
    • H01H19/10—Movable parts; Contacts mounted thereon
    • H01H19/14—Operating parts, e.g. turn knob
    • H01H19/18—Operating parts, e.g. turn knob adapted for actuation at a limit or other predetermined position in the path of a body, the relative movement of switch and body being primarily for a purpose other than the actuation of the switch, e.g. door switch, limit switch, floor-levelling switch of a lift

Definitions

  • the invention relates to a switch gear with at least a switching stage driven by a driven sun gear, by a planet carrier carrying at least one planetary gear and by a with the at least one planet inside meshing, arranged coaxially with the sun gear ring gear is formed, which is held fixed to the housing, and wherein the Switching stage a cam for actuating switching elements having.
  • Such a switch gear is in the form of a limit switch from EP 0 355 731 B1.
  • the limit switch is made of two Gear parts assembled, wherein the first gear part by two gear stages serving as reduction stages is formed.
  • the second transmission part is through in total formed four switching stages.
  • the gear parts are as planetary gear designed. It is in each switching stage respectively a cam plate provided for actuating a corresponding Switching element is used.
  • Each cam is on a planet carrier, in addition planetary gears carries, each with a serving as a sun gear clutch gear and with an internal toothing on the housing combed fixed ring gear.
  • the object of the invention is a switch gear of the above to create said type, the same size further improved reduction ratios allows.
  • the cam disc with an internal toothing is provided, which is about the same Partial diameter has as the internal toothing of the Ring gear, wherein the internal teeth of the cam disc a to the internal teeth of the ring gear different numbers of teeth and wherein the cam disc by means of the internal toothing with the at least one planetary gear of the switching stage combs.
  • the solution according to the invention is particularly suitable for limit switches identical in the reduction stages designed to limit switches according to EP 0 355 731 B1 are.
  • the planetary gear can the various switching stages of the limit switch according to EP 0 355 731 B1 by a differential gear each, such as it is provided according to the invention, to be replaced substantially to achieve higher reductions.
  • the number of teeth of the internal toothing the cam larger than the number of teeth of the internal teeth of the ring gear.
  • a further embodiment of the invention is at a Number of teeth of the internal teeth of the ring gear of 46 and a number of teeth of the sun gear of 14, the number of teeth of the internal teeth the cam plate 49.
  • This is the suitable Solution according to the invention as a limit switch with the same dimensions, like the embodiment described in detail of the prior art. In accordance with the embodiment described number of teeth results in a reduction ratio of 69.98 per gear stage.
  • a further embodiment of the invention is for adjustment the cam plate with an external toothing of the ring gear meshing worm gear provided whose transmission ratio to the tooth number difference of the cam disk for Ring gear is adapted.
  • a switch gear in the form of a limit switch 1 for mechanical Actuation of switching elements, not shown has, according to FIG. 1, a housing 2 in which two gear parts 3, 4 are housed.
  • the first transmission part 3 is by a reduction stage and the second transmission part. 4 formed by two switching stages.
  • the first transmission part 3 is according to a first transmission part according to an embodiment designed according to Fig. 10 of EP 0 355 731 B1, so that for further explanation in addition to EP 0 355 731 B1 is referenced.
  • the first transmission part 3 is driven by a drive shaft 5 driven, the not shown in detail Way is connected to a drive unit.
  • the drive unit is part of a functional unit such as in particular of a crane performing precisely controlled movements should.
  • the transmission part 3 provides a Voruntersburg in the form of a Stirnradvorcut, the reduce large jumps in the reductions of the planetary stages should. This precompilation does not necessarily exist be. An introduction of force can from the drive shaft. 5 also be done directly on the sun 9.
  • the first transmission part 3 has a stepped outer toothing provided drive wheel 6, the rotationally fixed on the Drive shaft 5 is arranged.
  • the drive wheel 6 meshes by means its external teeth with the external teeth of an eccentric on an axis parallel to the drive shaft 5 axis 8 stored gear 7, which also has a two-part, stepped outer toothing is provided.
  • the axis 8 to Storage of the gear 7 is fixed to the housing 2.
  • the external toothing the gear 7 meshes with a smaller diameter with the external teeth of a sun gear 9, the coaxial the drive shaft 5 is rotatably mounted.
  • the sun wheel 9 is rotationally locked with two coaxial connecting clutch gears 10 connected to each other as well are rotationally connected to each other and rotatable are mounted on the drive shaft 5.
  • the sun gear 9 points a second, axially offset external teeth with opposite the meshing with the gear 7 outer teeth lesser Diameter up.
  • the two clutch gears 10 are with provided according to identical external teeth. With the formed by the sun gear 9 and the clutch gears 10, combing external teeth serving as a common sun gear for each switching stage 4 three each over the circumference of Sun gear 9 and the clutch gears 10 arranged distributed Planetary gears 12, each per switching stage on one common planet carrier 11 are held.
  • the planet carrier 11 each shift stage 4 is slidably supported on a to the drive shaft 5 coaxial ring gear 13 from that with a Internal toothing 14 with the respective planet wheels 12th combs.
  • the two ring gears 13 are each by means of one Unspecified external teeth held fixed to the housing.
  • the two ring gears 13 are each in the circumferential direction adjustably held on the housing 2.
  • each Adjusting screw 18 is provided.
  • the adjustment of the ring gears 13 corresponds in structure and function of the adjustment of Ring gears of the switching stages of the limit switch according to EP 0 355 731 B1, so that for supplementary explanation of structure and Function of the adjusting screws 18 to EP 0 355 731 B1 is referenced.
  • Only difference than the worm gear serving adjusting screw 18 for adjusting the ring gears 13 is that the corresponding gear ratio each adjustment screw 18 to the opposite of the state of Technique according to EP 0 355 731 B1 changed reduction of the respective cam plate 15 is adapted.
  • Each switching stage 4 is assigned a respective cam disk 15, which, unlike EP 0 355 731 B1, does not correspond to respective planet carrier is held, but rather by means in each case an internal toothing 16 with the respective planetary gears 12 of each switching stage 4 meshes.
  • the internal toothing 16 has the same pitch circle diameter as the internal toothing 14 of the adjacent ring gear 13.
  • the number of teeth However, the internal teeth 16 of each cam 17 is too the number of teeth of the internal teeth 14 of the respective ring gear 13 different.
  • In the illustrated embodiment has the internal teeth 16 of each cam one to the number of teeth the internal teeth 14 of the respective ring gear 13 larger Number of teeth on.
  • the internal teeth 16 of each cam 15 has the number of teeth forty-nine.
  • the internal toothing 14 of each ring gear 13, however, has the number of teeth forty-six.
  • the number of teeth of the planetary gears 11 meshing external teeth of the sun gear 9 and the clutch gears 10, which - as stated above - of the function forming a common sun wheel is fourteen.
  • the two cams 15 are each slidable held axially.
  • the cam plate 15 is supported by the first switching stage 4 on the one hand to a thin support disk 19 from which between the sun gear 9 and the planet gears 12th is arranged and with its outer edge, the internal toothing 16th the cam plate 15 axially supports.
  • the cam 15 of the second switching stage 4 is supported by an unspecified Ring web on the ring gear 13 of the first switching stage 4 and with its opposite end face on the ring gear 13 of the second switching stage 4 axially slidably.
  • Each cam 15 has a radially outwardly through a corresponding recess in the housing 2 projecting switching cam 17, which is for actuating the respective switching element is provided.
  • the switching stages 4th accommodate the second transmission part in the same pitch, as for the switching stages of EP 0 355 731 B1 the case was.
  • differential gear as in the invention is provided and described in detail above
  • the invention can also be used in limit switches, the known switching stages with the aid of planetary gears, as are known from EP 0 355 731 B1. It
  • differential gear and planetary gear be combined with each other, so that for different Cams very different ratios can result.

Landscapes

  • Retarders (AREA)
  • Structure Of Transmissions (AREA)
  • Switches With Compound Operations (AREA)
  • Keying Circuit Devices (AREA)

Abstract

The mechanism includes a cam plate (15) for actuating switching elements in a switching stage. The cam plate comprises internal toothing (16) having the same reference diameter as the internal toothing (14) of an internal geared wheel (13). The internal toothing of the cam plate has a different number of teeth than the internal geared wheel. The cam disc meshes via the internal toothing with at least one planetary wheel of a switching stage (4).

Description

Die Erfindung betrifft ein Schaltergetriebe mit wenigstens einer Schaltstufe, die durch ein angetriebenes Sonnenrad, durch einen wenigstens ein Planetenrad tragenden Planetenträger und durch ein mit dem wenigstens einen Planetenrad innenseitig kämmendes, koaxial zum Sonnenrad angeordnetes Hohlrad gebildet ist, das gehäusefest gehalten ist, und wobei die Schaltstufe eine Nockenscheibe zur Betätigung von Schaltelementen aufweist.The invention relates to a switch gear with at least a switching stage driven by a driven sun gear, by a planet carrier carrying at least one planetary gear and by a with the at least one planet inside meshing, arranged coaxially with the sun gear ring gear is formed, which is held fixed to the housing, and wherein the Switching stage a cam for actuating switching elements having.

Ein solches Schaltergetriebe ist in Form eines Endschalters aus der EP 0 355 731 B1 bekannt. Der Endschalter ist aus zwei Getriebeteilen zusammengesetzt, wobei der erste Getriebeteil durch zwei als Untersetzungsstufen dienende Getriebestufen gebildet ist. Der zweite Getriebeteil ist durch insgesamt vier Schaltstufen gebildet. Die Getriebeteile sind als Planetengetriebe gestaltet. Dabei ist in jeder Schaltstufe jeweils eine Nockenscheibe vorgesehen, die zur Betätigung eines entsprechenden Schaltelementes dient. Jede Nockenscheibe ist an einem Planetenträger gehalten, der zusätzlich Planetenräder trägt, die jeweils mit einem als Sonnenrad dienenden Kupplungszahnrad und mit einer Innenverzahnung eines am Gehäuse festgelegten Hohlzahnrades kämmen. Mittels der jeweils erzielten Untersetzungen ist es möglich, mittels eines Antriebsmotors über die Nockenscheibe entsprechende Schaltelemente, insbesondere für die Bewegungssteuerung von Kränen oder für andere Vorrichtungen oder Maschinen, anzusteuern.Such a switch gear is in the form of a limit switch from EP 0 355 731 B1. The limit switch is made of two Gear parts assembled, wherein the first gear part by two gear stages serving as reduction stages is formed. The second transmission part is through in total formed four switching stages. The gear parts are as planetary gear designed. It is in each switching stage respectively a cam plate provided for actuating a corresponding Switching element is used. Each cam is on a planet carrier, in addition planetary gears carries, each with a serving as a sun gear clutch gear and with an internal toothing on the housing combed fixed ring gear. By means of each achieved Reductions it is possible by means of a drive motor via the cam corresponding switching elements, especially for the movement control of cranes or for other devices or machines.

Aufgabe der Erfindung ist es, ein Schaltergetriebe der eingangs genannten Art zu schaffen, das bei gleicher Baugröße weiter verbesserte Untersetzungsverhältnisse ermöglicht.The object of the invention is a switch gear of the above to create said type, the same size further improved reduction ratios allows.

Diese Aufgabe wird dadurch gelöst, daß die Nockenscheibe mit einer Innenverzahnung versehen ist, die etwa den gleichen Teilkreisdurchmesser aufweist wie die Innenverzahnung des Hohlrades, wobei die Innenverzahnung der Nockenscheibe eine zu der Innenverzahnung des Hohlrades unterschiedliche Zähnezahl aufweist, und wobei die Nockenscheibe mittels der Innenverzahnung mit dem wenigstens einen Planetenrad der Schaltstufe kämmt. Durch die erfindungsgemäße Lösung ergibt sich gegenüber dem Stand der Technik eine Vervielfachung der Untersetzung in der wenigstens einen Schaltstufe, so daß in jeder Getriebestufe bei gleichen Abmessungen eine wesentlich größere Untersetzung untergebracht werden kann. Gleichzeitig ist es durch entsprechend gleiche Abmessungen möglich, die Schaltstufe gemäß der Erfindung im gleichen Teilungsmaß zu integrieren, wie dies eine Schaltstufe beim Stand der Technik hatte. Die erfindungsgemäße Lösung eignet sich soweit insbesondere für Endschalter, die in den Untersetzungsstufen identisch zu Endschaltern gemäß der EP 0 355 731 B1 gestaltet sind. In einfacher Weise können lediglich die Planetengetriebe der verschiedenen Schaltstufen des Endschalters gemäß der EP 0 355 731 B1 durch jeweils ein Differenzzahngetriebe, wie es erfindungsgemäß vorgesehen ist, ersetzt werden, um wesentlich höhere Untersetzungen erzielen zu können.This object is achieved in that the cam disc with an internal toothing is provided, which is about the same Partial diameter has as the internal toothing of the Ring gear, wherein the internal teeth of the cam disc a to the internal teeth of the ring gear different numbers of teeth and wherein the cam disc by means of the internal toothing with the at least one planetary gear of the switching stage combs. The solution according to the invention results over the prior art, a multiplication of the reduction in the at least one switching stage, so that in each Gear stage with the same dimensions a significant larger reduction can be accommodated. simultaneously It is possible by correspondingly the same dimensions, the Switching stage according to the invention in the same pitch integrate, as this is a switching stage in the prior art would have. The solution according to the invention is particularly suitable for limit switches identical in the reduction stages designed to limit switches according to EP 0 355 731 B1 are. In a simple way, only the planetary gear can the various switching stages of the limit switch according to EP 0 355 731 B1 by a differential gear each, such as it is provided according to the invention, to be replaced substantially to achieve higher reductions.

In Ausgestaltung der Erfindung ist die Zähnezahl der Innenverzahnung der Nockenscheibe größer als die Zähnezahl der Innenverzahnung des Hohlrades. Dadurch ergibt sich ein besonders vorteilhaft erhöhtes Untersetzungsverhältnis im Vergleich zum Stand der Technik.In an embodiment of the invention, the number of teeth of the internal toothing the cam larger than the number of teeth of the internal teeth of the ring gear. This results in a special Advantageously increased reduction ratio in comparison to the state of the art.

In weiterer Ausgestaltung der Erfindung beträgt bei einer Zähnezahl der Innenverzahnung des Hohlzahnrades von 46 und einer Zähnezahl des Sonnenrades von 14 die Zähnezahl der Innenverzahnung der Nockenscheibe 49. Dadurch eignet sich die erfindungsgemäße Lösung als Endschalter mit gleichen Dimensionierungen, wie sie das ausführlich beschriebene Ausführungsbeispiel des Standes der Technik aufweist. Bei der gemäß der Ausgestaltung beschriebenen Zähnezahl ergibt sich ein Untersetzungsverhältnis von 69,98 pro Getriebestufe.In a further embodiment of the invention is at a Number of teeth of the internal teeth of the ring gear of 46 and a number of teeth of the sun gear of 14, the number of teeth of the internal teeth the cam plate 49. This is the suitable Solution according to the invention as a limit switch with the same dimensions, like the embodiment described in detail of the prior art. In accordance with the embodiment described number of teeth results in a reduction ratio of 69.98 per gear stage.

In weiterer Ausgestaltung der Erfindung ist zur Verstellung der Nockenscheibe ein mit einer Außenverzahnung des Hohlrades kämmendes Schneckengetriebe vorgesehen, dessen Übersetzungsverhältnis an die Zähnezahldifferenz der Nockenscheibe zum Hohlrad angepaßt ist. Dadurch ist es möglich, die gleiche Nockenscheibenverstellung wie bei der EP 0 355 731 B1 vorzusehen, wobei die erfindungsgemäße Ausgestaltung an die entsprechend vergrößerte Untersetzung der Nockenscheibe angepaßt ist.In a further embodiment of the invention is for adjustment the cam plate with an external toothing of the ring gear meshing worm gear provided whose transmission ratio to the tooth number difference of the cam disk for Ring gear is adapted. This makes it possible to do the same To provide cam disk adjustment as in EP 0 355 731 B1, wherein the embodiment of the invention to the corresponding enlarged reduction of the cam adapted is.

Weitere Vorteile und Merkmale der Erfindung ergeben sich aus den Ansprüchen sowie aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung, das anhand der Zeichnungen dargestellt ist.

Fig. 1
zeigt in einem Teilschnitt eine Ausführungsform eines erfindungsgemäßen Schaltergetriebes in Form eines Endschalters,
Fig. 2
in einer Schnittdarstellung eine Nockenscheibe des Endschalters nach Fig. 1, und
Fig. 3
eine Frontansicht der Nockenscheibe nach Fig. 2.
Further advantages and features of the invention will become apparent from the claims and from the following description of a preferred embodiment of the invention, which is illustrated by the drawings.
Fig. 1
shows in a partial section an embodiment of a switch gear according to the invention in the form of a limit switch,
Fig. 2
in a sectional view of a cam of the limit switch of FIG. 1, and
Fig. 3
a front view of the cam of Fig. 2nd

Ein Schaltergetriebe in Form eines Endschalters 1 zur mechanischen Betätigung von nicht dargestellten Schaltelementen weist gemäß Fig. 1 ein Gehäuse 2 auf, in dem zwei Getriebeteile 3, 4 untergebracht sind. Der erste Getriebeteil 3 ist durch eine Untersetzungsstufe und der zweite Getriebeteil 4 durch zwei Schaltstufen gebildet. Der erste Getriebeteil 3 ist entsprechend einem ersten Getriebeteil gemäß einer Ausführungsform nach Fig. 10 der EP 0 355 731 B1 gestaltet, so daß zur näheren Erläuterung ergänzend auf die EP 0 355 731 B1 verwiesen wird. Der erste Getriebeteil 3 wird durch eine Antriebswelle 5 angetrieben, die in nicht näher dargestellter Weise mit einer Antriebseinheit verbunden ist. Die Antriebseinheit ist Teil einer Funktionseinheit wie insbesondere eines Kranes, der genau gesteuerte Bewegungen durchführen soll. Dazu sind nicht dargestellte Schaltelemente zur Steuerung entsprechender Bewegungen vorgesehen, die in nachfolgend näher beschriebener Weise durch die Schaltstufen des zweiten Getriebeteiles 4 betätigt werden. Der Getriebeteil 3 stellt eine Voruntersetzung in Form einer Stirnradvorstufe dar, die große Sprünge in den Untersetzungen der Planetenstufen reduzieren soll. Diese Voruntersetzung muß nicht zwingend vorhanden sein. Eine Krafteinleitung kann von der Antriebswelle 5 auch direkt auf das Sonnenrad 9 erfolgen.A switch gear in the form of a limit switch 1 for mechanical Actuation of switching elements, not shown has, according to FIG. 1, a housing 2 in which two gear parts 3, 4 are housed. The first transmission part 3 is by a reduction stage and the second transmission part. 4 formed by two switching stages. The first transmission part 3 is according to a first transmission part according to an embodiment designed according to Fig. 10 of EP 0 355 731 B1, so that for further explanation in addition to EP 0 355 731 B1 is referenced. The first transmission part 3 is driven by a drive shaft 5 driven, the not shown in detail Way is connected to a drive unit. The drive unit is part of a functional unit such as in particular of a crane performing precisely controlled movements should. These are not shown switching elements for control corresponding movements provided in the following closer manner described by the switching stages of the second Transmission parts 4 are operated. The transmission part 3 provides a Voruntersetzung in the form of a Stirnradvorstufe, the reduce large jumps in the reductions of the planetary stages should. This precompilation does not necessarily exist be. An introduction of force can from the drive shaft. 5 also be done directly on the sun 9.

Der erste Getriebeteil 3 weist ein mit einer gestuften Außenverzahnung versehenes Antriebsrad 6 auf, das drehfest auf der Antriebswelle 5 angeordnet ist. Das Antriebsrad 6 kämmt mittels seiner Außenverzahnung mit der Außenverzahnung eines exzentrisch auf einer zur Antriebswelle 5 achsparallelen Achse 8 gelagerten Zahnrad 7, das ebenfalls mit einer zweigeteilten, gestuften Außenverzahnung versehen ist. Die Achse 8 zur Lagerung des Zahnrades 7 ist am Gehäuse 2 festgelegt. Die Außenverzahnung des Zahnrades 7 mit kleinerem Durchmesser kämmt mit der Außenverzahnung eines Sonnenrades 9, das koaxial auf der Antriebswelle 5 drehbeweglich gelagert ist. Das Sonnenrad 9 ist drehschlüssig mit zwei koaxial anschließenden Kupplungszahnrädern 10 verbunden, die untereinander ebenfalls drehschlüssig miteinander verbunden sind und drehbeweglich auf der Antriebswelle 5 gelagert sind. Das Sonnenrad 9 weist eine zweite, axial versetzte Außenverzahnung mit gegenüber der mit dem Zahnrad 7 kämmenden Außenverzahnung geringerem Durchmesser auf. Die beiden Kupplungszahnräder 10 sind mit entsprechend identischen Außenverzahnungen versehen. Mit der durch das Sonnenrad 9 und die Kupplungszahnräder 10 gebildeten, als gemeinsames Sonnenrad dienenden Außenverzahnung kämmen für jede Schaltstufe 4 jeweils drei über den Umfang des Sonnenrades 9 und der Kupplungszahnräder 10 verteilt angeordnete Planetenräder 12, die pro Schaltstufe jeweils auf einem gemeinsamen Planetenträger 11 gehalten sind. Der Planetenträger 11 jeder Schaltstufe 4 stützt sich gleitbeweglich an einem zur Antriebswelle 5 koaxialen Hohlrad 13 ab, das mit einer Innenverzahnung 14 mit den jeweiligen Planetenrädern 12 kämmt. Die beiden Hohlräder 13 sind mittels jeweils einer nicht näher bezeichneten Außenverzahnung gehäusefest gehalten. Die beiden Hohlräder 13 sind jeweils in Umfangsrichtung verstellbar am Gehäuse 2 gehalten. Hierzu ist jeweils eine Verstellschnecke 18 vorgesehen. Die Verstellung der Hohlräder 13 entspricht in Aufbau und Funktion der Verstellung der Hohlräder der Schaltstufen des Endschalters nach der EP 0 355 731 B1, so daß zur ergänzenden Erläuterung von Aufbau und Funktion der Verstellschnecken 18 auf die EP 0 355 731 B1 verwiesen wird. Einziger Unterschied der als Schneckengetriebe dienenden Verstellschnecken 18 zur Verstellung der Hohlräder 13 ist es, daß das entsprechende Übersetzungsverhältnis jeder Verstellschnecke 18 an die gegenüber dem Stand der Technik gemäß der EP 0 355 731 B1 veränderte Untersetzung der jeweiligen Nockenscheibe 15 angepaßt ist.The first transmission part 3 has a stepped outer toothing provided drive wheel 6, the rotationally fixed on the Drive shaft 5 is arranged. The drive wheel 6 meshes by means its external teeth with the external teeth of an eccentric on an axis parallel to the drive shaft 5 axis 8 stored gear 7, which also has a two-part, stepped outer toothing is provided. The axis 8 to Storage of the gear 7 is fixed to the housing 2. The external toothing the gear 7 meshes with a smaller diameter with the external teeth of a sun gear 9, the coaxial the drive shaft 5 is rotatably mounted. The sun wheel 9 is rotationally locked with two coaxial connecting clutch gears 10 connected to each other as well are rotationally connected to each other and rotatable are mounted on the drive shaft 5. The sun gear 9 points a second, axially offset external teeth with opposite the meshing with the gear 7 outer teeth lesser Diameter up. The two clutch gears 10 are with provided according to identical external teeth. With the formed by the sun gear 9 and the clutch gears 10, combing external teeth serving as a common sun gear for each switching stage 4 three each over the circumference of Sun gear 9 and the clutch gears 10 arranged distributed Planetary gears 12, each per switching stage on one common planet carrier 11 are held. The planet carrier 11 each shift stage 4 is slidably supported on a to the drive shaft 5 coaxial ring gear 13 from that with a Internal toothing 14 with the respective planet wheels 12th combs. The two ring gears 13 are each by means of one Unspecified external teeth held fixed to the housing. The two ring gears 13 are each in the circumferential direction adjustably held on the housing 2. For this is one each Adjusting screw 18 is provided. The adjustment of the ring gears 13 corresponds in structure and function of the adjustment of Ring gears of the switching stages of the limit switch according to EP 0 355 731 B1, so that for supplementary explanation of structure and Function of the adjusting screws 18 to EP 0 355 731 B1 is referenced. Only difference than the worm gear serving adjusting screw 18 for adjusting the ring gears 13 is that the corresponding gear ratio each adjustment screw 18 to the opposite of the state of Technique according to EP 0 355 731 B1 changed reduction of the respective cam plate 15 is adapted.

Jeder Schaltstufe 4 ist jeweils eine Nockenscheibe 15 zugeordnet, die im Unterschied zur EP 0 355 731 B1 nicht an dem jeweiligen Planetenträger gehalten ist, sondern vielmehr mittels jeweils einer Innenverzahnung 16 mit den jeweiligen Planetenrädern 12 jeder Schaltstufe 4 kämmt. Die Innenverzahnung 16 weist den gleichen Teilkreisdurchmesser wie die Innenverzahnung 14 des benachbarten Hohlrades 13 auf. Die Zähnezahl der Innenverzahnung 16 jeder Nockenscheibe 17 ist jedoch zu der Zähnezahl der Innenverzahnung 14 des jeweiligen Hohlrades 13 verschieden. Beim dargestellten Ausführungsbeispiel weist die Innenverzahnung 16 jeder Nockenscheibe eine zu der Zähnezahl der Innenverzahnung 14 des jeweiligen Hohlrades 13 größere Zähnezahl auf. Die Innenverzahnung 16 jeder Nockenscheibe 15 weist die Zähnezahl neunundvierzig auf. Die Innenverzahnung 14 jedes Hohlrades 13 hingegen weist die Zähnezahl sechsundvierzig auf. Die Zähnezahl der mit den Planetenrädern 11 kämmenden Außenverzahnung des Sonnenrades 9 und der Kupplungszahnräder 10, die - wie oben angeführt - von der Funktion her ein gemeinsames Sonnenrad bilden, beträgt vierzehn. Die beiden Nockenscheiben 15 sind jeweils gleitbeweglich axial gehalten. Dabei stützt sich die Nockenscheibe 15 der ersten Schaltstufe 4 zum einen an einer dünnen Stützscheibe 19 ab, die zwischen dem Sonnenrad 9 und den Planetenrädern 12 angeordnet ist und mit ihrem Außenrand die Innenverzahnung 16 der Nockenscheibe 15 axial stützt. Die Nockenscheibe 15 der zweiten Schaltstufe 4 stützt sich mit einem nicht näher bezeichneten Ringsteg an dem Hohlrad 13 der ersten Schaltstufe 4 und mit ihrer gegenüberliegenden Stirnfläche an dem Hohlrad 13 der zweiten Schaltstufe 4 axial gleitbeweglich ab.Each switching stage 4 is assigned a respective cam disk 15, which, unlike EP 0 355 731 B1, does not correspond to respective planet carrier is held, but rather by means in each case an internal toothing 16 with the respective planetary gears 12 of each switching stage 4 meshes. The internal toothing 16 has the same pitch circle diameter as the internal toothing 14 of the adjacent ring gear 13. The number of teeth However, the internal teeth 16 of each cam 17 is too the number of teeth of the internal teeth 14 of the respective ring gear 13 different. In the illustrated embodiment has the internal teeth 16 of each cam one to the number of teeth the internal teeth 14 of the respective ring gear 13 larger Number of teeth on. The internal teeth 16 of each cam 15 has the number of teeth forty-nine. The internal toothing 14 of each ring gear 13, however, has the number of teeth forty-six. The number of teeth of the planetary gears 11 meshing external teeth of the sun gear 9 and the clutch gears 10, which - as stated above - of the function forming a common sun wheel is fourteen. The two cams 15 are each slidable held axially. In this case, the cam plate 15 is supported by the first switching stage 4 on the one hand to a thin support disk 19 from which between the sun gear 9 and the planet gears 12th is arranged and with its outer edge, the internal toothing 16th the cam plate 15 axially supports. The cam 15 of the second switching stage 4 is supported by an unspecified Ring web on the ring gear 13 of the first switching stage 4 and with its opposite end face on the ring gear 13 of the second switching stage 4 axially slidably.

Jede Nockenscheibe 15 weist einen radial nach außen durch eine entsprechende Aussparung im Gehäuse 2 abragenden Schaltnocken 17 auf, der zur Betätigung des jeweiligen Schaltelementes vorgesehen ist. Durch das Versehen jeder Nockenscheibe 15 mit einer Innenverzahnung 16, deren Zähnezahl größer ist als die Zähnezahl der Innenverzahnung des zugeordneten Hohlrades 13 und das gleichzeitige Kämmen der Nockenscheibe 15 mit den jeweiligen Planetenrädern 12 wird für jede Schaltstufe 4 ein Differenzzahngetriebe geschaffen, das im Vergleich zum Stand der Technik gemäß der EP 0 355 731 B1 ein vervielfachtes Untersetzungsverhältnis erzielt. Bei den beschriebenen Zähnezahlen ergibt sich für das vorliegende Ausführungsbeispiel eine Untersetzung von 69,98. Trotz der wesentlich größeren Untersetzung wird für die Schaltstufen 4 gegenüber dem Stand der Technik gemäß der EP 0 355 731 B1 kein größerer Bauraum benötigt. Bei gleichen Abmessungen der Nockenscheiben 15 mit den Nockenscheiben der Schaltstufen gemäß der EP 0 355 731 B1 ist es möglich, die Schaltstufen 4 des zweiten Getriebeteiles im gleichen Teilungsmaß unterzubringen, wie dies für die Schaltstufen der EP 0 355 731 B1 der Fall war.Each cam 15 has a radially outwardly through a corresponding recess in the housing 2 projecting switching cam 17, which is for actuating the respective switching element is provided. By providing each cam 15 with an internal toothing 16 whose number of teeth is larger as the number of teeth of the internal teeth of the associated ring gear 13 and the simultaneous combing of the cam disk 15th with the respective planet gears 12 is for each switching stage 4 a differential gear mechanism created in comparison to the state of the art according to EP 0 355 731 B1 multiplied reduction ratio achieved. In the described Numbers of teeth results for the present embodiment a reduction of 69.98. Despite the essential larger reduction is for the switching stages 4 compared with the prior art according to EP 0 355 731 B1 no larger space required. With the same dimensions of Cams 15 with the cams of the switching stages according to EP 0 355 731 B1, it is possible, the switching stages 4th accommodate the second transmission part in the same pitch, as for the switching stages of EP 0 355 731 B1 the case was.

Das Vorsehen eines Differenzzahngetriebes, wie es erfindungsgemäß vorgesehen ist und vorstehend ausführlich beschrieben worden ist, kann selbstverständlich bei anderen Ausführungsformen der Erfindung auch in Endschaltern eingesetzt werden, die bekannte Schaltstufen mit Hilfe von Planetengetrieben, wie sie aus der EP 0 355 731 B1 bekannt sind, aufweisen. Es können somit je nach gewünschten Schaltvorgängen in entsprechenden Schaltstufen Differenzzahngetriebe und Planetengetriebe miteinander kombiniert werden, so daß sich für verschiedene Nockenscheiben stark unterschiedliche Untersetzungen ergeben können.The provision of a differential gear, as in the invention is provided and described in detail above Of course, in other embodiments the invention can also be used in limit switches, the known switching stages with the aid of planetary gears, as are known from EP 0 355 731 B1. It Thus, depending on the desired switching operations in appropriate Gear stages differential gear and planetary gear be combined with each other, so that for different Cams very different ratios can result.

Claims (4)

  1. Gear transmission for switches, having at least one switching stage (4) which is formed by a sun wheel (9) which is coaxially rotationally secure on a drive shaft (5), by a planet carrier (11) carrying at least one planet wheel (12), and by an internal gear (13) which meshes on the inside with the at least one planet wheel (12) and which is arranged coaxially with the drive shaft and which is held in a manner secured to a housing, and the switching stage (4) having a cam disc (15) for operating switching elements, characterised in that the cam disc (15) is provided with internal toothing (16) which has approximately the same pitch diameter as the internal toothing (14) of the internal gear (13), the internal toothing (16) of the cam disc (15) having a tooth number which differs from that of the internal toothing (14) of the internal gear (13), and the cam disc (15) meshing by means of its internal toothing (16) with the at least one planet wheel of the switching stage (4).
  2. Gear transmission for switches according to claim 1, characterised in that the tooth number of the internal toothing (16) of the cam disc (15) is larger than the tooth number of the internal toothing (14) of the internal gear (13).
  3. Gear transmission for switches according to claim 2, characterised in that with a tooth number of the internal toothing (14) of the internal gear (13) of 46 and a tooth number of the sun wheel (9, 10) of 14, the tooth number of the internal toothing (16) of the cam disc (15) is 49.
  4. Gear transmission for switches according to any one of the preceding claims, characterised in that a worm gear (18) which meshes with external toothing of the internal gear (13) and whose transmission ratio is adapted to the difference in tooth number between the cam disc (15) and the internal gear (13) is provided to adjust the cam disc (15).
EP98120923A 1998-11-04 1998-11-04 Gear transmission for switches having at least one switching stage Expired - Lifetime EP0999567B1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP98120923A EP0999567B1 (en) 1998-11-04 1998-11-04 Gear transmission for switches having at least one switching stage
DE59812577T DE59812577D1 (en) 1998-11-04 1998-11-04 Switch gear with at least one switching stage
AT98120923T ATE289448T1 (en) 1998-11-04 1998-11-04 SWITCH TRANSMISSION WITH AT LEAST ONE SHIFT STAGE
US09/427,172 US6244984B1 (en) 1998-11-04 1999-10-25 Switch gear with at least two gear stages

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP98120923A EP0999567B1 (en) 1998-11-04 1998-11-04 Gear transmission for switches having at least one switching stage

Publications (2)

Publication Number Publication Date
EP0999567A1 EP0999567A1 (en) 2000-05-10
EP0999567B1 true EP0999567B1 (en) 2005-02-16

Family

ID=8232915

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98120923A Expired - Lifetime EP0999567B1 (en) 1998-11-04 1998-11-04 Gear transmission for switches having at least one switching stage

Country Status (4)

Country Link
US (1) US6244984B1 (en)
EP (1) EP0999567B1 (en)
AT (1) ATE289448T1 (en)
DE (1) DE59812577D1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6796921B1 (en) 2003-05-30 2004-09-28 One World Technologies Limited Three speed rotary power tool
TWM466909U (en) * 2013-06-19 2013-12-01 Yi-De Pan Improved structure of planetary limit switch
DE202014006109U1 (en) 2014-07-28 2014-08-07 I-Te Pan Planet-limit switch
US11076509B2 (en) 2017-01-24 2021-07-27 The Research Foundation for the State University Control systems and prediction methods for it cooling performance in containment

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3036167A (en) * 1959-10-29 1962-05-22 Baldwin Lima Hamilton Corp Position limit switch
US4616528A (en) * 1982-05-03 1986-10-14 Vapor Corporation Valve actuator with continuous manual override
US4742730A (en) * 1982-09-30 1988-05-10 The Boeing Company Failsafe rotary actuator
US4869139A (en) * 1987-06-19 1989-09-26 Alexander S. Gotman Rotating driver with automatic speed and torque switching
DE3828508C1 (en) * 1988-08-23 1989-12-07 Maschinenfabrik Stromag Gmbh, 4750 Unna, De
JP3182294B2 (en) * 1994-05-11 2001-07-03 アスモ株式会社 Moving object position detection device
US5800305A (en) * 1995-12-29 1998-09-01 Koon-Woo Kang Reduction gear with coaxial input and output shafts and combining planetary and nonplanetary gearing
US5779587A (en) * 1996-08-30 1998-07-14 Curtiss Wright Flight Systems, Inc. Jam tolerant rotary actuator with shear pins and disengagement coupling

Also Published As

Publication number Publication date
DE59812577D1 (en) 2005-03-24
ATE289448T1 (en) 2005-03-15
EP0999567A1 (en) 2000-05-10
US6244984B1 (en) 2001-06-12

Similar Documents

Publication Publication Date Title
EP1000280B1 (en) Modular gear system with contrate gear
EP2918871A1 (en) Gear unit for a group transmission
WO1987003661A1 (en) Multi-step gear-box
EP0962298B1 (en) Drive for twin screw extruder
EP2066919B1 (en) Multi-speed reduction gear
WO2003044394A1 (en) System for generating a rotational movement of a shaft
DE4026886A1 (en) Planetary gear with support - has at least one planetary wheel with two central wheels with inner and outer cogging
EP2066925B1 (en) Multi-stage reduction gear
EP0999567B1 (en) Gear transmission for switches having at least one switching stage
DE3828508C1 (en)
DE19701767A1 (en) Auxiliary transmission for motor vehicle
DE2714021C2 (en) Device for switching off the rotary movement of a driven shaft
DE102021003333B3 (en) Transmission device with a shaft
DE10393143T5 (en) Vehicle transmission systems
EP0319750B1 (en) Low-backlash speed-reducing two-stage planetary gearing
DE3508767C2 (en)
DE3011133C2 (en) Device for actuating current switches, in particular control current limit switches
DE19959394C2 (en) Drive device for a forming machine
DE2452738C3 (en) Timer, in particular digital stove timer
DE19938323A1 (en) Planetary gear train has four planet wheels in individual gear stages for high torque transmission and increased stiffness
DE102021211713A1 (en) electric vehicle transmission
DE102022203377A1 (en) Motor vehicle transmission for an at least partially electrically driven motor vehicle
DE102021208061A1 (en) electric vehicle transmission
DE102022204851A1 (en) Motor vehicle transmission, in particular axle transmission for a drive axle of an at least partially electrically driven motor vehicle
DE102021212164A1 (en) electric vehicle transmission

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20000614

AKX Designation fees paid

Free format text: AT BE CH DE FR GB IT LI LU NL SE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RTI1 Title (correction)

Free format text: GEAR TRANSMISSION FOR SWITCHES HAVING AT LEAST ONE SWITCHING STAGE

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: ZIMMERLI, WAGNER & PARTNER AG

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REF Corresponds to:

Ref document number: 59812577

Country of ref document: DE

Date of ref document: 20050324

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20050608

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20051117

REG Reference to a national code

Ref country code: CH

Ref legal event code: PFA

Owner name: STROMAG AG

Free format text: STROMAG AG#HANSASTRASSE 120#59425 UNNA (DE) -TRANSFER TO- STROMAG AG#HANSASTRASSE 120#59425 UNNA (DE)

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59812577

Country of ref document: DE

Representative=s name: PATENTANWAELTE RUFF, WILHELM, BEIER, DAUSTER &, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59812577

Country of ref document: DE

Representative=s name: PATENTANWAELTE RUFF, WILHELM, BEIER, DAUSTER &, DE

Effective date: 20120330

Ref country code: DE

Ref legal event code: R081

Ref document number: 59812577

Country of ref document: DE

Owner name: GKN STROMAG AG, DE

Free format text: FORMER OWNER: STROMAG AG, 59425 UNNA, DE

Effective date: 20120330

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: WAGNER PATENT AG, CH

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20151123

Year of fee payment: 18

Ref country code: LU

Payment date: 20151125

Year of fee payment: 18

Ref country code: IT

Payment date: 20151124

Year of fee payment: 18

Ref country code: CH

Payment date: 20151123

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20151124

Year of fee payment: 18

Ref country code: NL

Payment date: 20151124

Year of fee payment: 18

Ref country code: FR

Payment date: 20151124

Year of fee payment: 18

Ref country code: SE

Payment date: 20151123

Year of fee payment: 18

Ref country code: AT

Payment date: 20151120

Year of fee payment: 18

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20161201

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 289448

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161104

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20161104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20170731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161105

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161104

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161104

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20171122

Year of fee payment: 20

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20161130

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59812577

Country of ref document: DE