DK158622B

DK158622B - DRIVING MECHANISM FOR BLINDERS OR SIMILAR

Info

Publication number: DK158622B
Application number: DK337884A
Authority: DK
Inventors: Hans Gross
Original assignee: Hans Gross
Priority date: 1983-07-12
Filing date: 1984-07-10
Publication date: 1990-06-18
Also published as: ATE26737T1; DK337884D0; DK337884A; EP0131225B1; DE3325113A1; ES534199A0; EP0131225A3; DE3325113C2; DK158622C; DD227752A5; EP0131225A2; ES8505017A1; DE3463283D1

Abstract

1. Drive device for blinds or the like, having a drive shaft (5) which, through a planetary gear arrangement drives an output shaft (16) which has to be coupled to the blind and further comprising a first switching plate (48) driven by the planetary gear arrangement and equiaxial with the output shaft and co-operating with a limit switch (42), the switching member (44) of which is braced on an end face of the first switching plate (48), characterised in that equiaxially with the first switching plate (48) there is a further switching plate (52), of which the end face (50) lies substantially in the plane of the end face (46) of the first switching plate (48), and in that the first and the further switching plates have a radially extending depression (54, 56) and in that the further switching plate is driven at a rotary speed other than that of the first switching plate, and in that the switching member (44) is also braced on the end face (50) of the further switching plate (52) so that it can drop in to the depressions (54, 56) when these are aligned with one another.

Description

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Opfindelsen angår en drivmekanisme til persienner eller lignende med en drivaksel, som gennem et planetgear driver en til persiennen koblelig, dreven aksel, med en af planetgearet dreven og koaksialt med den drevne aksel anbragt første koblingsskive, der samvirker med en ende- 5 stillingskontakt, hvis kobleorgan støtter mod en endeflade for den første koblingsskive.BACKGROUND OF THE INVENTION 1. Field of the Invention The invention relates to a blind or similar drive mechanism having a drive shaft driving through a planetary gear shaft coupled to the venetian blind with a drive gear driven and coaxially disposed with the driven shaft cooperating with an end position contact, if coupling means supports against an end surface of the first coupling disc.

En mekanisme af denne art er kendt fra tysk offentliggørelsesskrift nr.A mechanism of this kind is known from German publication publication no.

31 39 073. I den kendte mekanisme udviser nævnte endeflade hos den 10 første koblingsskive en kileformet forhøjning, der, når den støder mod endestillingskontaktens kobleorgan, støder dette kobleorgan tilbage således at endestillingskontakten herved bringes i funktion. På grund af de tolerancer, der arbejdes med ved fremstilling af endestil lingskontakten, sker aktiveringen af endestillingskontakten for alle 15 sådanne mekanismers vedkommende dog ikke ved samme stilling af koblingsskiven, fordi kobleorganet afhængigt af de nævnte tolerancer skal trykkes mere eller mindre kraftigt ind for at få endestillingskontakten til at reagere. Herved er den nøjagtighed som kan opnås med denne drivmekanisme begrænset. Disse mekanismer anvendes fortrinsvis til 20 frakobling af persiennens drivmotor, når persiennen har nået en endestilling, som ikke kan detekteres af en endestillingskontakt, der betjenes direkte af persiennen selv.31 39 073. In the known mechanism, said end surface of the first coupling disc exhibits a wedge-shaped elevation which, when abutting the coupling means of the end position switch, bounces this coupling means so that the end position switch is actuated. However, due to the tolerances worked on in making the end switch, the activation of the end switch for all 15 of such mechanisms does not occur at the same position of the switching disc, because, depending on the said tolerances, the coupling means must be pressed more or less forcefully to the end position switch to respond. This limits the accuracy that can be achieved with this drive mechanism. These mechanisms are preferably used for disabling the blind drive motor when the blind has reached an end position which cannot be detected by an end position switch operated directly by the blind itself.

Den til grund for opfindelsen liggende opgave består i at udforme en 25 mekanisme af indledningsvist nævnte art, hvormed koblingstidspunktet kan bestemmes mere nøjagtigt. Herved skal navnlig bibeholdes den fordel der består i forbindelse med den yderst pladsbesparende anordning af den første koblingsskive. Denne opgave løses ifølge opfindelsen ved, at der er tilvejebragt en med den første koblingsskive koaksial, 30 yderligere koblingsskive, hvis endeflade er beliggende hovedsagelig i plan med den første koblingsskives endeflade, at den første og den yderligere koblingsskive har en radialt gående fordybning, at den yderligere koblingsskive drives med et andet omløbstal end den første koblingsskive, og at kobleorganet ligeledes støtter mod den yderligere 35 koblingsskives endeflade, således at den kan falde ind i begge koblingsskivens fordybninger på én gang, når disse flugter indbyrdes.The object of the invention consists in designing a mechanism of the kind mentioned in the introduction, by which the timing of the coupling can be determined more precisely. In particular, the advantage that exists in connection with the extremely space-saving device of the first coupling disc must be maintained. This object is solved according to the invention by providing a coaxial with the first coupling disc, 30 additional coupling disc, the end surface of which is arranged substantially in plane with the end surface of the first coupling disc, the first and the further coupling disc having a radially extending recess further coupling disc is operated with a different orbital number than the first coupling disc, and the coupling member also supports against the end surface of the additional coupling disc so that it can fall into the recesses of both coupling discs at the same time as they align with each other.

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22

Ifølge en udførelsesform for opfindelsen kan den yderligere koblingsskive fortrinsvis ligge radialt indenfor den førstnævnte koblingsskive.According to an embodiment of the invention, the additional coupling disc may preferably be radially within the former coupling disc.

Fordelen ved opfindelsen ligger i, at den yderligere koblingsskive kan 5 anbringes uden krav om yderligere plads, og i at kobleorganets koblebevægelse i modsætning til kendte indretninger kan foregå forholdsvis hurtigt, fordi endestillingskontakten kun aktiveres, når dennes koble-organ falder ind i begge udsparingerne, således at fremstillingstolerancernes indflydelse på tidspunktet for endestillingskontaktens akti-10 vering er kraftigt reduceret og i praksis elimineret.The advantage of the invention lies in the fact that the additional coupling disc can be placed without the need for additional space, and that the coupling movement of the coupling means, in contrast to known devices, can take place relatively quickly, because the end switch is only activated when its coupling means falls into both recesses. so that the influence of manufacturing tolerances at the time of the activation of the end switch is greatly reduced and virtually eliminated.

Princippet med at lade en endestillingskontakt hos drivmekanismer til persienner eller lignende reagerer derved at dens kobleorgan falder ind i fordybninger hos to koaksialt anbragte koblingsskiver, som drives med 15 indbyrdes ubetydeligt afvigende omløbstal, er ganske vist kendt mange steder fra, bl.a. fra fransk patentskrift nr. 1 539 452. Disse kendte mekanismer viser dog ingen pladsbesparende anordning således som hos mekanismen ifølge opfindelsen.Admittedly, the principle of allowing a terminal contact of blinds or similar drive mechanisms to react with its coupling means falling into recesses of two coaxially arranged coupling disks operated at 15 mutually differing orbital numbers is well known in many places, e.g. from French Patent No. 1,539,452. However, these known mechanisms show no space-saving device as in the mechanism according to the invention.

20 Ved en udførelsesform for opfindelsen er den yderligere koblingsskive koblet drejefast til den drevne aksel, og den første koblingsskive udviser på i og for sig kendt måde en inderfortanding, hvormed et af planetgearets planethjul er i indgreb, hvilket hjul samtidigt er i indgreb med en stationær inderfortanding, hvis tandantal kun afviger ube-25 tydeligt fra tandantallet for den første koblingsskives inderfortand-ing.In one embodiment of the invention, the additional clutch disc is coupled pivotally to the driven shaft, and the first clutch disc exhibits, in a manner known per se, an inner tooth with which one of the planetary gear wheels engages, which wheel simultaneously engages a stationary internal teeth, the number of teeth differing only slightly from the number of teeth of the inner tooth of the first coupling disc.

Fordelen ved denne udførelsesform ligger deri, at persiennens åbningslængde på simpel måde kan overføres på et antal omdrejninger af den 30 første koblingsskive, hvorigennem der opnås stor koblingsnøjagtighed, nemlig en koblingsnøjagtighed på nogle få mm.The advantage of this embodiment lies in the fact that the opening length of the blind can be simply transferred to a number of revolutions of the first coupling disk, through which a high coupling accuracy is obtained, namely a coupling accuracy of a few mm.

Yderligere træk og fordele ved opfindelsen vil fremgå af den efterfølgende beskrivelse af et udførelseseksempel på opfindelsen under henvis-35 ning til tegningen, som viser de for opfindelsen væsentlige enkeltheder, og af kravene. De enkelte træk kan realiseres enkeltvist ellerFurther features and advantages of the invention will become apparent from the following description of an exemplary embodiment of the invention with reference to the drawings which illustrate the essential features of the invention and the claims. The individual features can be realized individually or

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3 flere af dem i en vilkårlig kombination til en udførelsesform for opfindelsen. På tegningen viser fig. 1 et længdesnit med delvist borttagne dele af et udførelseseksempel for en drivmekanisme til persienner, 5 fig. 2 et længdesnit gennem en første koblingsskive, hvor snittet er lagt i samme plan som i fig. 1, fig. 3 den første koblingsskive set fra enden i retning ad en pil III i fig. 2, fig. 4 et brudstykke set i retning ad pilene IV-IV i fig. 3, 10 fig. 5 den yderligere koblingsskive set fra enden svarende til se-stråleretningen i fig. 3', fig. 6 et brudstykke af fig. 5 set i retning ad pilene VI-VI i fig. 5, og fig. 7 et til sestråleretningen i figurerne 3 og 3 svarende billede af 15 det med den drevne aksel koblede trin af planetgearets sidste afsnit, hvor de foran liggende dele er fjernet.3 several of them in any combination for one embodiment of the invention. In the drawing, FIG. 1 is a longitudinal section with partially removed parts of an exemplary embodiment of a blinds drive mechanism; FIG. 2 is a longitudinal section through a first coupling disc, the section being laid in the same plane as in FIG. 1, FIG. 3 shows the first coupling disc seen from the end in the direction of an arrow III in FIG. 2, FIG. 4 is a fragmentary view in the direction of arrows IV-IV in FIG. 3, 10 FIG. 5 shows the additional coupling disc seen from the end corresponding to the beam direction of FIG. 3 ', FIG. 6 is a fragment of FIG. 5 seen in the direction of arrows VI-VI in FIG. 5, and FIG. Fig. 7 is a view corresponding to the jet beam direction of Figures 3 and 3 of the step of coupling with the driven shaft of the last section of the planetary gear, in which the preceding parts are removed.

Et i det væsentlige rørformet hus 1 for drivmekanismen indeholder et leje 2,3 for den ind i huset 1 ragende venstre ende af en rørformet 20 drivaksel 5, hvis ikke viste højre ende er indrettet til sammenkobling med en elektromotor. Drivakslen 5 har i sin venstre ende en yder-fortanding 6, som danner solhjulet for et første planetgear. I indgreb med denne yderfortanding 6 findes der nogle planethjul, hvoraf der kun kan ses et i fig. 1, nemlig planethjulet 8. Dette planethjul er i 25 indgreb med en i en indsats 10 tilvejebragt, stationær inderfortanding 12, i hvilket det foretager en rullende bevægelse og derigennem bevæger en kurv 14, hvorpå planethjulet 8 er lejret. Kurven 14 er lejret drejeligt på en dreven aksel 16, som forløber gennem hele huset, og har på et rørstudsformet afsnit 18, der tjener til dennes lejring, en 30 yderfortanding 20, der danner solhjulet for et andet trin i planet-gearet, og som desuden driver et antal planethjul, hvoraf kun planethjulet 22 kan ses på tegningen. Planethjulet 22 støtter sig til en yderligere i indsatsen 10 tilvejebragt, stationær inderfortanding 24 og driver derigennem en anden kurv 26. Denne anden kurv er koblet 35 drejefast til et rørstykke 28, som er lejret drejeligt på den drevne aksel 16 og har en yderfortanding 30, som danner solhjulet for etA substantially tubular housing 1 for the drive mechanism includes a bearing 2,3 for the left end of the tubing 20 of a tubular drive shaft 5, the right end of which is not shown for coupling with an electric motor. The drive shaft 5 has at its left end an outer tooth 6 which forms the sun gear for a first planetary gear. In engagement with this outer tooth 6 there are some planet wheels, of which only one in FIG. 1, namely the planetary wheel 8. This planetary wheel engages with a stationary inner tooth 12 provided in an insert 10, in which it makes a rolling motion and thereby moves a basket 14 on which the planetary wheel 8 is mounted. The basket 14 is pivotally mounted on a driven shaft 16 extending throughout the housing, and has on a tubular section 18 serving for its bearing, an outer tooth 20 forming the sun gear for a second stage of the planetary gear, and which moreover, a number of planet wheels operate, of which only planet wheel 22 can be seen in the drawing. The planetary wheel 22 relies on a further stationary inner tooth 24 provided in the insert 10 and thereby drives a second basket 26. This second basket is coupled 35 pivotally to a pipe piece 28 which is pivotally mounted on the driven shaft 16 and has an outer tooth 30. which forms the sun wheel for one

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4 tredje trin i planetgearet samt driver et antal planethjul, af hvilke fig. 1 viser planethjulet 32 i tegningens øverste del i dennes rigtige stilling, medens det i fig. l's nederste del synlige planethjul 34 for forenklingens skyld er vist 60° forskudt. Dette tredje trin i 5 planetgearet har i alt tre planethjul. Også planethjulene 32 og 34 er i indgreb med inderfortandingen 24, således at en kurv 36 på grund af det multible omsætningsforhold drives med et omløbstal, der er kraftigt reduceret i forhold til omløbstallet for drivakslen 5. Kurven 36 er forbundet drejefast med den drevne aksel 16 gennem en 10 savtak-fortanding. Den drevne aksel 16 rager ud gennem begge ender af huset 1 og kan kobles sammen med persiennen på ikke nærmere vist måde.4 shows a third stage in the planetary gear and drives a number of planetary wheels, of which fig. 1 shows the planet wheel 32 in the upper part of the drawing in its correct position, while in FIG. The lower part of the visible planet wheel 34 for simplification is shown 60 ° offset. This third stage of the 5 planetary gear has a total of three planetary wheels. Also, the planet wheels 32 and 34 engage with the internal gear 24 so that a basket 36 is driven by the turnover ratio with a rotational number which is greatly reduced relative to the rotational number of the drive shaft 5. The curve 36 is connected pivotally to the driven shaft 16 through a 10 sawtooth tooth. The driven shaft 16 protrudes through both ends of the housing 1 and can be coupled to the blinds in a manner not shown.

I mekanismens venstre endedel er der tilvejebragt en med huset 1 fast forbundet og derfor drejefast kappe 40, som i den på figuren øverste 15 del indeholder en første endestillingskontakt 42, hvis kobleorgan 44, som i tegningens plan bevæger sig i vandret retning, rager til højre. Kobleorganet 44 ligger på samme tid an mod den i fig. 1 mod venstre vendende endeflade 46 hos en første koblingsskive 48 og mod en ligeledes mod venstre i fig. 1 vendende endeflade 50 af en yderligere kob- 20 lingsskive 52. Endefladen 50 forløber med undtagelse af de fordyb ninger, der skal beskrives nærmere i det følgende, i samme plan som endefladen 46 og går i radial retning direkte over i endefladen 46. I endefladen 46 er der tilvejebragt en fordybning 54, som ikke er meget bredere end den første endestillingskontakt 42's kobleorgan 44 regnet i 25 anordningens periferiretning. I endefladen 50 for den yderligere koblingsskive 52 er der tilvejebragt en fordybning 56, som er ligeså dyb som fordybningen 54 men betydeligt bredere end sidstnævnte. Medens fordybningen 54 totalt set, altså inklusive dens skrå flanker 60, har en bredde på 3,5 mm, har fordybningen 56 inklusive dennes flanker 62 en 30 bredde på 10 mm. Fordybningen 56 er netop gjort så bred, at kob leorganet 44, når først det er faldet ind i begge fordybninger samtidigt - hvilket bevirker en frakobling af den elektriske drivmotor - ikke igen på grund af elektromotorens oftest uundgåelige efterløb indtil fuldstændig stilstand trykkes ud af fordybningen 56, hvilket ellers 35 kunne ske, dersom fordybningen 56 blot var forholdsvis smal. Den yderligere koblingsskive 52 ligger med sin bort fra fordybningen 56 venden-In the left end portion of the mechanism, there is provided a fixedly attached and therefore pivotal casing 40 which in the upper part of the figure contains a first end position contact 42, whose coupling means 44, which in the drawing plane in the horizontal direction, protrudes to the right. . At the same time, the coupling means 44 abuts against that of FIG. 1 to the left-facing end surface 46 of a first coupling disk 48 and to a similarly to the left of FIG. 1, with the exception of the recesses to be described in the following, in the same plane as the end face 46 and in a radial direction directly into the end face 46. In the end face 46, a recess 54 is provided which is not much wider than the coupling means 44 of the first end position switch 42 calculated in the peripheral direction of the device. In the end face 50 of the additional coupling disc 52 there is provided a recess 56 which is as deep as the recess 54 but considerably wider than the latter. While the recess 54 as a whole, ie including its inclined flanks 60, has a width of 3.5 mm, the recess 56 including its flanks 62 has a width of 10 mm. The recess 56 is just so wide that the coupling means 44, once it has fallen into both recesses at the same time - causing a disconnection of the electric drive motor - is not again due to the most inevitable aftermath of the electric motor until complete standstill is pushed out of the recess 56 otherwise 35 could occur if the recess 56 was merely relatively narrow. The additional coupling disc 52, with its away from the recess 56, faces

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5 de endeflade 53 an mod en skulder 55 hos den først koblingsskive og med sin cirkulærcylindriske yderflade 57 an mod en cylindrisk flade 59 hos den første koblingsskive.5, the end face 53 abuts a shoulder 55 of the first coupling disc and with its circular cylindrical outer surface 57 abuts a cylindrical surface 59 of the first coupling disc.

5 Den første koblingsskive 48 drives rundt derved at den med sin inder-fortanding 64, hvis aktive diameter stemmer overens med inderfortandingen 24's diameter, griber ind i planethjulene 32 og 34's fortandin-ger, hvor inderfortandingen 64 dog har et tandantal, der afviger ubetydeligt for det for inderfortandingen 21 gældende således at den første 10 koblingsskive 48 i forhold til kurven 36 har langt ringere omløbstal.5 The first coupling disc 48 is driven around by engaging with its inner tooth 64, the active diameter of which corresponds to the diameter of the inner tooth 24, in the teeth of the planet wheels 32 and 34, the inner tooth 64 having, however, a number of teeth which deviates that applies to the inner tooth 21 so that the first 10 coupling disc 48 with respect to the curve 36 has far inferior circulation figures.

Den yderligere koblingsskive 52 har diametralt overfor fordybningen 56 to indadragende fremspring 68, som går ud over den i øvrigt cirkulærcylindriske indre flade 67, hvilke fremspring med en plan flade 70 ligger 15 an mod en plan flade 72 (fig. 7) i kurven 36, således at denne y- derligere koblingsskive 52 er koblet ikke-roterbart til kurven 36. Den helt frem til de plane flader 72 cylindriske yderflade 73 for kurvens skive formede del er beliggende radialt indenfor den yderligere koblingsskive 52's flade 67.The additional coupling disc 52 has diametrically opposite the recess 56 two inwardly extending projections 68 which extend beyond the otherwise circular cylindrical inner surface 67, which projections with a flat surface 70 abut a flat surface 72 (Fig. 7) in the curve 36. such that this additional coupling disc 52 is non-rotatably coupled to the curve 36. The cylindrical outer surface 73 of the curved disc shaped portion 73 of the curved disc surface is located radially within the surface 67 of the further coupling disc 52.

2020

Medens lejeboltene for planethjulene på kurven 14 og på kurven 26 er udformet ud i ét med disse kurve indeholder kurven 36 særlige i boringer 74 indskudte lejebolte 76 for planethjulene 32 og 34.While the bearing bolts for the planet wheels on the curve 14 and on the curve 26 are formed integrally with these curves, the curve 36 contains special bearing bolts 76 for the planet wheels 32 and 34 inserted in bores 74.

25 I kappen 40's nederste del findes der en yderligere endestillingskontakt 80, hvis kobleorgan 82 samvirker med et i kappen 40 lejret, line ært forskydelig betjeningselement 84, som ved ophejsning af persiennen, når denne har nået sin øverste stilling, forskydes ind mod kappen 40's indre, således at denne endestillingskontakt 80 aktiveres.In the lower part of the sheath 40, there is a further end switch 80, the coupling means 82 cooperating with a linearly displaceable operating element 84 which is mounted in the sheath 40, which, when raised by the blind when it has reached its upper position, is displaced towards the interior of the sheath 40 so that this end switch 80 is activated.

3030

Yderdiameteren for den yderligere koblingsskive 52, som kan måles i fig. 5, andrager i det her viste eksempel 44 mm. Den yderligere koblingsskive 52's tykkelse er 2,8 mm. Den yderligere koblingsskive optager derfor kun meget lidt plads. Andre mål kan aflæses af de målfaste 35 tegninger. Alle dele består af formstof.The outer diameter of the additional coupling disc 52, which can be measured in FIG. 5, in the example shown here is 44 mm. The thickness of the additional coupling disc 52 is 2.8 mm. The additional clutch disk therefore occupies very little space. Other dimensions can be read from the 35 solid drawings. All parts are made of plastic.

Claims

A drive mechanism for blinds or the like having a drive shaft (5) which drives through a planetary gear, a shaft (5) coupled to the shutter (16), with one driven by the planetary gear and coaxially disposed with the driven shaft (48), which cooperates with an end position switch (42), whose coupling means (44) abut against an end surface of the first coupling disc, characterized in that a coaxial one with the first coupling disc (48) is provided, an additional 10 wiring disc (52) whose end surface (50) ) is located substantially in plane with the end surface (46) of the first coupling disc (48), that the first and the further coupling disc have a radially recessed groove (54,56), that the additional coupling disc is driven by a different number of turns than the first coupling disc, and that the coupling means (44) also supports 15 against the end surface (50) of the additional coupling disc (52) so that it can fall into the recesses (54,56) as they align with one another.

Drive mechanism according to claim 1, characterized in that the additional coupling disc (52) is coupled pivotally to the driven shaft (16) and that the first coupling disc (48) exhibits in a known manner an inner tooth (64) with which one of the planetary gear wheels (32, 34) is engaged, which wheel is also engaged with a stationary inner tooth (24), the number of teeth differing only slightly from the tooth number of the first coupling disc (48) inner tooth 25 (64).