EP0999567A1 - Gear transmission for switches having at least two transmission steps - Google Patents

Gear transmission for switches having at least two transmission steps Download PDF

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Publication number
EP0999567A1
EP0999567A1 EP98120923A EP98120923A EP0999567A1 EP 0999567 A1 EP0999567 A1 EP 0999567A1 EP 98120923 A EP98120923 A EP 98120923A EP 98120923 A EP98120923 A EP 98120923A EP 0999567 A1 EP0999567 A1 EP 0999567A1
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EP
European Patent Office
Prior art keywords
gear
internal toothing
teeth
cam disc
ring gear
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.)
Granted
Application number
EP98120923A
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German (de)
French (fr)
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EP0999567B1 (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 AG
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Stromag AG
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Filing date
Publication date
Application filed by Stromag AG filed Critical Stromag AG
Priority to EP98120923A priority Critical patent/EP0999567B1/en
Priority to AT98120923T priority patent/ATE289448T1/en
Priority to DE59812577T priority patent/DE59812577D1/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

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    • 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 that is driven by a driven sun gear, by a planet carrier carrying at least one planet gear and by one with the at least one planet gear inside intermeshing ring gear arranged coaxially to the sun gear is formed, which is held fixed to the housing, and wherein the Switching stage a cam disk for actuating switching elements having.
  • Such a switch gear is in the form of a limit switch known from EP 0 355 731 B1.
  • the limit switch is made of two Gear parts assembled, the first gear part through two gear stages serving as reduction stages is formed.
  • the second gear part is through total four switching stages formed.
  • the gear parts are as planetary gear designed. It is in each switching stage a cam disk is provided, which is used to actuate a corresponding Switching element is used. Every cam is on held a planet carrier, the additional planet gears carries, each with a clutch gear serving as a sun gear and with an internal toothing on the housing Comb the specified hollow gear.
  • the object of the invention is a switch gear of the beginning to create the type mentioned, with the same size enables further improved reduction ratios.
  • the cam disc an internal toothing is provided, which is approximately the same Pitch circle diameter as the internal teeth of the Ring gear, the internal toothing of the cam disc different number of teeth to the internal toothing of the ring gear has, 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 that are identical in the reduction stages designed to limit switches according to EP 0 355 731 B1 are.
  • the number of teeth of the internal toothing the cam disc larger than the number of teeth on the internal toothing of the ring gear.
  • a further embodiment of the invention is at one Number of teeth of the internal toothing of the hollow gear of 46 and a number of teeth of the sun gear of 14 the number of teeth of the internal toothing the cam disc 49.
  • a switch gear in the form of a limit switch 1 for mechanical Actuation of switching elements, not shown 1 has a housing 2 in which two transmission parts 3, 4 are housed.
  • the first gear part 3 is through a reduction stage and the second gear part 4 formed by two switching stages.
  • the first gear part 3 is corresponding to a first transmission part according to an embodiment 10 of EP 0 355 731 B1, so that in addition to EP 0 355 731 B1 for further explanation is referred.
  • the first gear part 3 is driven by a drive shaft 5 driven, the in not shown Way is connected to a drive unit.
  • the drive unit is part of a functional unit such as in particular of a crane that perform precisely controlled movements should.
  • the transmission part 3 provides a reduction in the form of a spur gear, the reduce large jumps in the reduction of the planetary levels should. This reduction does not necessarily have to exist his.
  • the drive shaft 5 can apply force also take place directly on the sun gear 9.
  • the first gear part 3 has a stepped external toothing provided drive wheel 6, which rotatably on the Drive shaft 5 is arranged.
  • the drive wheel 6 meshes by means of its external toothing with the external toothing of an eccentric on an axis 5 parallel to the drive shaft 8 mounted gear 7, which also with a two-part, stepped external toothing is provided.
  • the axis 8 to Storage of the gear 7 is fixed to the housing 2.
  • the external toothing of the gear 7 meshes with a smaller diameter with the external toothing of a sun gear 9, which is coaxial the drive shaft 5 is rotatably mounted.
  • the sun gear 9 is rotationally locked with two coaxially connecting clutch gears 10 connected to each other as well are rotationally connected and rotatable are mounted on the drive shaft 5.
  • the sun gear 9 has a second, axially offset external toothing with opposite the external toothing meshing with the gear 7 less Diameter on.
  • the two clutch gears 10 are with correspondingly identical external gears. With the formed by the sun gear 9 and the clutch gears 10, Comb external teeth serving as a common sun gear for each switching stage 4 three each over the scope of the Sun gear 9 and the clutch gears 10 arranged distributed Planet gears 12, each on a switching stage common planet carrier 11 are held.
  • the planet carrier 11 each switching stage 4 is slidably supported on one to the drive shaft 5 coaxial ring gear 13, which with a Internal toothing 14 with the respective planet gears 12 combs.
  • the two ring gears 13 are each one External teeth, not specified, are held in place on the housing.
  • the two ring gears 13 are each in the circumferential direction held adjustable on the housing 2. There is one for each Adjusting screw 18 is provided.
  • the adjustment of the ring gears 13 corresponds in structure and function to the adjustment of Ring gears of the switching stages of the limit switch according to EP 0 355 731 B1, so that for additional explanation of structure and Function of the adjusting screws 18 on EP 0 355 731 B1 is referred.
  • the only difference is that as a worm gear Serving adjustment screws 18 for adjusting the ring gears 13 is that the corresponding gear ratio each adjusting screw 18 to the compared to the state of Technology according to EP 0 355 731 B1 changed gear reduction respective cam 15 is adapted.
  • Each switching stage 4 is assigned a cam disk 15, which, in contrast to EP 0 355 731 B1, is not due to the respective planet carrier is held, but rather by means each with an internal toothing 16 with the respective planet gears 12 each switching stage 4 combs.
  • 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 toothing 16 of each cam disk 17 is closed the number of teeth of the internal toothing 14 of the respective ring gear 13 different.
  • the internal toothing 16 of each cam disk 15 has forty-nine teeth.
  • each ring gear 13 has the number of teeth forty six on.
  • the number of teeth with the planet gears 11 meshing external teeth of the sun gear 9 and the clutch gears 10, which - as mentioned above - by the function form a common sun gear is fourteen.
  • the two cam disks 15 are each slidable held axially.
  • the cam disk 15 is supported here first switching stage 4 on the one hand on a thin support disc 19 from between the sun gear 9 and the planet gears 12 is arranged and the inner toothing 16 with its outer edge the cam disc 15 is axially supported.
  • the cam disc 15 of the second switching stage 4 is based on an unspecified one 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 disc 15 has a radially outward through a corresponding recess in the housing 2 protruding switch cams 17 on that for actuating the respective switching element is provided.
  • the number of teeth is greater than the number of teeth of the internal toothing of the associated ring gear 13 and the simultaneous combing of the cam disc 15 with the respective planet gears 12 is for each switching stage 4 created a differential gear that compared to the state of the art according to EP 0 355 731 B1 multiplied reduction ratio achieved.
  • differential gear as it is according to the invention is provided and described in detail above can, of course, in other embodiments the invention can also be used in limit switches, the known switching stages with the help of planetary gears, as they are known from EP 0 355 731 B1. It can therefore, depending on the desired switching operations in corresponding Switching stages differential gear and planetary gear can be combined with each other, so that for different Cam disks have very different reductions can result.

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 that is driven by a driven sun gear, by a planet carrier carrying at least one planet gear and by one with the at least one planet gear inside intermeshing ring gear arranged coaxially to the sun gear is formed, which is held fixed to the housing, and wherein the Switching stage a cam disk 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 known from EP 0 355 731 B1. The limit switch is made of two Gear parts assembled, the first gear part through two gear stages serving as reduction stages is formed. The second gear part is through total four switching stages formed. The gear parts are as planetary gear designed. It is in each switching stage a cam disk is provided, which is used to actuate a corresponding Switching element is used. Every cam is on held a planet carrier, the additional planet gears carries, each with a clutch gear serving as a sun gear and with an internal toothing on the housing Comb the specified hollow gear. By means of the respectively achieved Reduction is possible by means of a drive motor corresponding switching elements via the cam disk, 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 beginning to create the type mentioned, with the same size enables further improved reduction ratios.

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 an internal toothing is provided, which is approximately the same Pitch circle diameter as the internal teeth of the Ring gear, the internal toothing of the cam disc different number of teeth to the internal toothing of the ring gear has, 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 a multiplication of the reduction compared to the prior art in the at least one switching stage, so that in each Gear stage with the same dimensions an essential larger reduction can be accommodated. At the same time 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. So far, the solution according to the invention is particularly suitable for limit switches that are 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 the different switching stages of the limit switch according to the EP 0 355 731 B1 by means of a differential toothed gear, such as it is provided according to the invention to be replaced to essential to be able 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 disc larger than the number of teeth on the internal toothing of the ring gear. This results in a special one advantageously increased reduction ratio in comparison 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 one Number of teeth of the internal toothing of the hollow gear of 46 and a number of teeth of the sun gear of 14 the number of teeth of the internal toothing the cam disc 49. This makes the solution according to the invention as a limit switch with the same dimensions, as the embodiment described in detail of the prior art. According to the a reduction ratio results from the number of teeth described 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 disc with an external toothing of the ring gear intermeshing worm gear provided, the transmission ratio to the difference in the number of teeth of the cam disc Ring gear is adjusted. This makes it possible to do the same To provide cam disc adjustment as in EP 0 355 731 B1, the design according to the invention accordingly adjusted increased reduction of the cam disc 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 emerge from the claims and from the following description of a preferred exemplary embodiment of the invention, which is illustrated with the aid of 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 a cam of the limit switch according to FIG. 1, and
Fig. 3
3 shows a front view of the cam disk according to FIG. 2.

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 1 has a housing 2 in which two transmission parts 3, 4 are housed. The first gear part 3 is through a reduction stage and the second gear part 4 formed by two switching stages. The first gear part 3 is corresponding to a first transmission part according to an embodiment 10 of EP 0 355 731 B1, so that in addition to EP 0 355 731 B1 for further explanation is referred. The first gear part 3 is driven by a drive shaft 5 driven, the in not shown Way is connected to a drive unit. The drive unit is part of a functional unit such as in particular of a crane that perform precisely controlled movements should. For this purpose, switching elements for control are not shown Appropriate movements are provided in the following described in more detail by the switching stages of the second Gear part 4 are operated. The transmission part 3 provides a reduction in the form of a spur gear, the reduce large jumps in the reduction of the planetary levels should. This reduction does not necessarily have to exist his. The drive shaft 5 can apply force also take place directly on the sun gear 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 gear part 3 has a stepped external toothing provided drive wheel 6, which rotatably on the Drive shaft 5 is arranged. The drive wheel 6 meshes by means of its external toothing with the external toothing of an eccentric on an axis 5 parallel to the drive shaft 8 mounted gear 7, which also with a two-part, stepped external toothing is provided. The axis 8 to Storage of the gear 7 is fixed to the housing 2. The external toothing of the gear 7 meshes with a smaller diameter with the external toothing of a sun gear 9, which is coaxial the drive shaft 5 is rotatably mounted. The sun gear 9 is rotationally locked with two coaxially connecting clutch gears 10 connected to each other as well are rotationally connected and rotatable are mounted on the drive shaft 5. The sun gear 9 has a second, axially offset external toothing with opposite the external toothing meshing with the gear 7 less Diameter on. The two clutch gears 10 are with correspondingly identical external gears. With the formed by the sun gear 9 and the clutch gears 10, Comb external teeth serving as a common sun gear for each switching stage 4 three each over the scope of the Sun gear 9 and the clutch gears 10 arranged distributed Planet gears 12, each on a switching stage common planet carrier 11 are held. The planet carrier 11 each switching stage 4 is slidably supported on one to the drive shaft 5 coaxial ring gear 13, which with a Internal toothing 14 with the respective planet gears 12 combs. The two ring gears 13 are each one External teeth, not specified, are held in place on the housing. The two ring gears 13 are each in the circumferential direction held adjustable on the housing 2. There is one for each Adjusting screw 18 is provided. The adjustment of the ring gears 13 corresponds in structure and function to the adjustment of Ring gears of the switching stages of the limit switch according to EP 0 355 731 B1, so that for additional explanation of structure and Function of the adjusting screws 18 on EP 0 355 731 B1 is referred. The only difference is that as a worm gear Serving adjustment screws 18 for adjusting the ring gears 13 is that the corresponding gear ratio each adjusting screw 18 to the compared to the state of Technology according to EP 0 355 731 B1 changed gear reduction respective cam 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 cam disk 15, which, in contrast to EP 0 355 731 B1, is not due to the respective planet carrier is held, but rather by means each with an internal toothing 16 with the respective planet gears 12 each switching stage 4 combs. 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 toothing 16 of each cam disk 17 is closed the number of teeth of the internal toothing 14 of the respective ring gear 13 different. In the illustrated embodiment points the internal toothing 16 of each cam disk one to the number of teeth the internal toothing 14 of the respective ring gear 13 larger Number of teeth. The internal toothing 16 of each cam disk 15 has forty-nine teeth. The internal toothing 14 of each ring gear 13, however, has the number of teeth forty six on. The number of teeth with the planet gears 11 meshing external teeth of the sun gear 9 and the clutch gears 10, which - as mentioned above - by the function form a common sun gear is fourteen. The two cam disks 15 are each slidable held axially. The cam disk 15 is supported here first switching stage 4 on the one hand on a thin support disc 19 from between the sun gear 9 and the planet gears 12 is arranged and the inner toothing 16 with its outer edge the cam disc 15 is axially supported. The cam disc 15 of the second switching stage 4 is based on an unspecified one 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 disc 15 has a radially outward through a corresponding recess in the housing 2 protruding switch cams 17 on that for actuating the respective switching element is provided. By providing each cam disc 15 with an internal toothing 16, the number of teeth is greater than the number of teeth of the internal toothing of the associated ring gear 13 and the simultaneous combing of the cam disc 15 with the respective planet gears 12 is for each switching stage 4 created a differential gear that compared to the state of the art according to EP 0 355 731 B1 multiplied reduction ratio achieved. In the described Number of teeth results for the present exemplary embodiment a reduction of 69.98. Despite the essential Larger reduction is used for switching stages 4 compared to the prior art according to EP 0 355 731 B1 no larger installation space required. With the same dimensions of Cam disks 15 with the cam disks according to the switching stages of EP 0 355 731 B1 it is possible to switch the switching stages 4 to accommodate the second gear part in the same pitch, like this for the switching stages of EP 0 355 731 B1 was the case.

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 it is according to the invention is provided and described in detail above can, of course, in other embodiments the invention can also be used in limit switches, the known switching stages with the help of planetary gears, as they are known from EP 0 355 731 B1. It can therefore, depending on the desired switching operations in corresponding Switching stages differential gear and planetary gear can be combined with each other, so that for different Cam disks have very different reductions can result.

Claims (4)

Schaltergetriebe mit wenigstens einer Schaltstufe, die durch ein auf einer Antriebswelle koaxial drehfestes Sonnenrad, durch einen wenigstens ein Planetenrad tragenden Planetenträger und durch ein mit dem wenigstens einen Planetenrad innenseitig kämmendes, koaxial zur Antriebsachse angeordnetes Hohlrad gebildet ist, das gehäusefest gehalten ist, und wobei die Schaltstufe eine Nockenscheibe zur Betätigung von Schaltelementen aufweist,
dadurch gekennzeichnet,
daß die Nockenscheibe (15) mit einer Innenverzahnung (16) versehen ist, die etwa den gleichen Teilkreisdurchmesser aufweist wie die Innenverzahnung (14) des Hohlrades (13), wobei die Innenverzahnung (16) der Nockenscheibe (15) eine zu der Innenverzahnung (14) des Hohlrades (13) unterschiedliche Zähnezahl aufweist, und wobei die Nockenscheibe (15) mittels der Innenverzahnung (16) mit dem wenigstens einen Planetenrad der Schaltstufe (4) kämmt.Switch transmission with at least one switching stage, which is formed by a sun gear coaxially rotatably on a drive shaft, by a planet carrier carrying at least one planet gear, and by a ring gear arranged on the inside, meshing with the at least one planet gear, arranged coaxially to the drive axis, and which is fixed to the housing, and the Switching stage has a cam disk for actuating switching elements,
characterized,
that the cam disc (15) is provided with an internal toothing (16) which has approximately the same pitch circle diameter as the internal toothing (14) of the ring gear (13), the internal toothing (16) of the cam disc (15) being one of the internal toothing (14 ) of the ring gear (13) has a different number of teeth, and the cam disc (15) meshes with the at least one planet gear of the switching stage (4) by means of the internal toothing (16). Schaltergetriebe nach Anspruch 1, dadurch gekennzeichnet, daß die Zähnezahl der Innenverzahnung (16) der Nockenscheibe (15) größer ist als die Zähnezahl der Innenverzahnung (14) des Hohlrades (13).Switch transmission according to claim 1, characterized in that the number of teeth of the internal toothing (16) of the cam disc (15) is greater than the number of teeth on the internal toothing (14) of the ring gear (13). Schaltergetriebe nach Anspruch 2, dadurch gekennzeichnet, daß bei einer Zähnezahl der Innenverzahnung (14) des Hohlrades (13) von 46 und einer Zähnezahl des Sonnenrades (9, 10) von 14 die Zähnezahl der Innenverzahnung (16) der Nockenscheibe (15) 49 beträgt. Switch transmission according to claim 2, characterized in that with a number of teeth of the internal toothing (14) of Ring gear (13) of 46 and a number of teeth of the sun gear (9, 10) of 14 the number of teeth of the internal toothing (16) of the cam disc (15) is 49. Schaltergetriebe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß zur Verstellung der Nockenscheibe (15) ein mit einer Außenverzahnung des Hohlrades (13) kämmendes Schneckengetriebe (18) vorgesehen ist, dessen Übersetzungsverhältnis an die Zähnezahldifferenz der Nockenscheibe (15) zum Hohlrad (13) angepaßt ist.Switch transmission according to one of the preceding claims, characterized in that for adjusting the cam disc (15) one with an external toothing of the ring gear (13) Intermeshing worm gear (18) is provided, the transmission ratio to the difference in the number of teeth of the cam disc (15) is adapted to the ring gear (13).
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
AT98120923T ATE289448T1 (en) 1998-11-04 1998-11-04 SWITCH TRANSMISSION WITH AT LEAST ONE SHIFT STAGE
DE59812577T DE59812577D1 (en) 1998-11-04 1998-11-04 Switch gear with at least one switching 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)

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

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ID=8232915

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US (1) US6244984B1 (en)
EP (1) EP0999567B1 (en)
AT (1) ATE289448T1 (en)
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* 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

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US3036167A (en) * 1959-10-29 1962-05-22 Baldwin Lima Hamilton Corp Position limit switch
EP0355731B1 (en) * 1988-08-23 1994-12-28 Stromag Aktiengesellschaft Actuating device for control member
EP0684452A2 (en) * 1994-05-11 1995-11-29 Asmo Co., Ltd. Position detector and position control method for a moving body

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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
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

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Publication number Priority date Publication date Assignee Title
US3036167A (en) * 1959-10-29 1962-05-22 Baldwin Lima Hamilton Corp Position limit switch
EP0355731B1 (en) * 1988-08-23 1994-12-28 Stromag Aktiengesellschaft Actuating device for control member
EP0684452A2 (en) * 1994-05-11 1995-11-29 Asmo Co., Ltd. Position detector and position control method for a moving body

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US6244984B1 (en) 2001-06-12
ATE289448T1 (en) 2005-03-15
DE59812577D1 (en) 2005-03-24
EP0999567B1 (en) 2005-02-16

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