EP0534089B1 - Actuating mechanism for the sliding bars of a door or window fitting - Google Patents

Actuating mechanism for the sliding bars of a door or window fitting Download PDF

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Publication number
EP0534089B1
EP0534089B1 EP92112839A EP92112839A EP0534089B1 EP 0534089 B1 EP0534089 B1 EP 0534089B1 EP 92112839 A EP92112839 A EP 92112839A EP 92112839 A EP92112839 A EP 92112839A EP 0534089 B1 EP0534089 B1 EP 0534089B1
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EP
European Patent Office
Prior art keywords
gearwheel
transmission
crank
toothing
positioning bar
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
EP92112839A
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German (de)
French (fr)
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EP0534089A1 (en
Inventor
Karl-Heinz Schmidt
Jürgen Sassmannshausen
Achim Türk
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.)
Siegenia Aubi KG
Original Assignee
Siegenia Frank KG
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Publication date
Application filed by Siegenia Frank KG filed Critical Siegenia Frank KG
Publication of EP0534089A1 publication Critical patent/EP0534089A1/en
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Publication of EP0534089B1 publication Critical patent/EP0534089B1/en
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05C—BOLTS OR FASTENING DEVICES FOR WINGS, SPECIALLY FOR DOORS OR WINDOWS
    • E05C9/00—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing
    • E05C9/02—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing with one sliding bar for fastening when moved in one direction and unfastening when moved in opposite direction; with two sliding bars moved in the same direction when fastening or unfastening
    • E05C9/021—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing with one sliding bar for fastening when moved in one direction and unfastening when moved in opposite direction; with two sliding bars moved in the same direction when fastening or unfastening with rack and pinion mechanism
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B17/00—Accessories in connection with locks
    • E05B17/20—Means independent of the locking mechanism for preventing unauthorised opening, e.g. for securing the bolt in the fastening position
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05C—BOLTS OR FASTENING DEVICES FOR WINGS, SPECIALLY FOR DOORS OR WINDOWS
    • E05C9/00—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing
    • E05C9/02—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing with one sliding bar for fastening when moved in one direction and unfastening when moved in opposite direction; with two sliding bars moved in the same direction when fastening or unfastening
    • E05C9/026—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing with one sliding bar for fastening when moved in one direction and unfastening when moved in opposite direction; with two sliding bars moved in the same direction when fastening or unfastening comprising key-operated locks, e.g. a lock cylinder to drive auxiliary deadbolts or latch bolts
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05C—BOLTS OR FASTENING DEVICES FOR WINGS, SPECIALLY FOR DOORS OR WINDOWS
    • E05C9/00—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing
    • E05C9/10—Actuating mechanisms for bars
    • E05C9/16—Actuating mechanisms for bars with crank pins and connecting rods
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
    • E05D15/00—Suspension arrangements for wings
    • E05D15/48—Suspension arrangements for wings allowing alternative movements
    • E05D15/52—Suspension arrangements for wings allowing alternative movements for opening about a vertical as well as a horizontal axis
    • E05D15/522—Suspension arrangements for wings allowing alternative movements for opening about a vertical as well as a horizontal axis with disconnecting means for the appropriate pivoting parts
    • E05D15/523—Suspension arrangements for wings allowing alternative movements for opening about a vertical as well as a horizontal axis with disconnecting means for the appropriate pivoting parts using movable rods
    • E05D15/524—Actuating mechanisms
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B63/00—Locks or fastenings with special structural characteristics
    • E05B63/0017—Locks with sliding bolt without provision for latching
    • E05B63/0021—Locks with sliding bolt without provision for latching the bolt being shot over an increased length by a single turning operation of the key
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME RELATING TO HINGES OR OTHER SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS AND DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION, CHECKS FOR WINGS AND WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/10—Application of doors, windows, wings or fittings thereof for buildings or parts thereof
    • E05Y2900/13—Application of doors, windows, wings or fittings thereof for buildings or parts thereof characterised by the type of wing
    • E05Y2900/148—Windows

Definitions

  • Actuating gears of this type have long been part of the prior art for the stated purpose, such as CH-PS 324 607 shows.
  • the total travel of the drive rod is divided into two sections of equal length, which is passed through from the basic switching position to the intermediate switching position, while the other is determined by the further movement of the actuating gear from the intermediate switching position to the end switching position.
  • the actuating gear Since the installation depth of the connecting rod fittings and the actuating gear in the window profile is narrowly limited, the actuating gear must have the smallest possible backset, i.e. get by with a small distance from the axis of rotation of the drive member mounted in the transmission housing from the front end face of the transmission housing. Therefore, the drive members can only get a relatively small radius, so that the achievable total travel range for the drive rods is within relatively narrow limits. In addition, the smallest possible backbone dimension is required.
  • actuating gears have already been created which use a gearwheel having several toothed segments with differently sized pitch circle diameters as the drive member, which has groups of engagement members on the drive rod interacts, whose position on the drive rod is matched to the different pitch circle diameters of the toothed segments.
  • the aim of the invention is to design an actuating gear of the type specified at the outset, in which an uneven subdivision of the total travel range for the drive rod coupled herewith can be achieved while maintaining a relatively small backset and backset dimension and a resulting minimal installation depth.
  • a subdivision of the total travel range is sought, which is approximately at a ratio of 2: 1, in such a way that the larger travel range portion, for example when the drive member moves from its basic switching position to an angular distance of 90 ° of which has the intermediate switching position, while then the smaller portion of the travel path is passed through as it moves further from the intermediate switching position mentioned to the end switching position, which is in turn at an angle of 90 ° from it.
  • an actuating gear corresponding to the input specification with these features is that a so-called large stroke gear can be created, which can be realized with a relatively small backset and backset and consequently with a small installation depth - in the direction parallel to the wing plane. This means that it does not differ, or only insignificantly, from the dimensions of the corresponding actuating gear with a normal total travel.
  • a large-stroke gearbox for a total travel between 50 mm and 70 mm, preferably about 60 mm can be created by the specified measures, in which two successive rotation angle ranges of 90 ° for the drive member considerably different travel ranges for the drive rod can be derived. Over the two partial rotation angle ranges of the actuating gear of 90 ° each, with the help of the design according to the invention, an advantageously different force / displacement implementation achieve and consequently improve the ease of use of the espagnolette fittings for windows and doors.
  • the gearwheel - as usual - has a circular rolling area and meshes with toothed racks aligned at least approximately parallel to the sliding direction of the drive rod.
  • the gear can also have a non-circular shape, e.g. have oval rolling area and comb with gear racks that are curved or inclined to the direction of sliding of the drive rod.
  • the drawer of the straight-pull crank consists of two links connected in series, e.g. whose common connecting joint or one of the links is slidably held in a fixed guide of the gear housing.
  • This stationary guide can extend approximately parallel to the direction of displacement of the drive rod in the gear housing or can also receive a course or a position in which the connecting joint between the two drawer link members is only in the middle rotary or intermediate switching position of the drive member is on a straight line through the crank pin of the straight thrust crank and through the axis of rotation of the gear on the drawer.
  • the invention also includes an embodiment of the fixed guide in the gear housing, which has a more or less curved or curved shape and consequently additionally influences the transmission of the drive movement generated by the drive member to the drive rod.
  • a design has also proven itself in which the total length of the drawer for the straight thrust crank to the crank radius of the drive member has a ratio of about 5: 1, while the length of the two links of the drawer has a ratio of about 2: 3 to one another stands.
  • the shorter link of the drawer should be assigned to the drive link and the longer link to the gear.
  • both members of the drawer have a shape which is slightly curved or kinked in the direction of their plane of movement, their kink or curvature position being rectified. This ensures that the bearing rosette of an operating hand lever is attached to the transmission housing without obstruction.
  • crank pin of the drive member of the straight thrust crank assumes an over-center position in the end switching position of the actuating gear, while it has an under-center position when the drive element is in the basic switching position and is supported.
  • the drive member can be blocked - preferably by an additional slide bolt accommodated in the gearbox housing, whereby for the actuation of the slide bolt into the gearbox housing e.g. a so-called profile cylinder can be used afterwards.
  • the actuating gear 1 for longitudinally displaceable connecting rods 17 on fittings of windows, doors or the like shown in FIGS. 1 to 5 of the drawing each have a gear housing 2, which is, for example, essentially trough-shaped or shell-shaped and on its open broadside a cover (not shown) can be closed, the outline of which is adapted to the gear housing 2.
  • the cover is supported on frames or projecting from the bottom 3 of the gear housing 2 at right angles. Walls 4 off.
  • a faceplate 5, for example made of strip material, is connected, for example riveted or welded, to the face of the gear housing 2.
  • a drive member 6 is rotatably supported between its base 3 and the cover over an angular range of 180 °, which carries a radially projecting crank arm 7 in which a crank pin 8 is seated.
  • a drawer 9 which in turn is formed by two links 10 and 11 connected in series. These have a connecting joint 12 in common, which is held displaceably in a fixed guide 13 of the gear housing 2, for example in elongated holes or slots in the base 3 and in the cover. 1 to 3 of the drawing, the fixed guide 13 is only indicated by a dash-dotted line, which extends in a straight line in the longitudinal direction of the gear housing 2.
  • a toothed wheel 15 is rotatably mounted about a central axis 14, which meshes on the one hand with a toothing 16 which is located on the in the gear housing 2 and along the faceplate 5 longitudinally displaceable drive rod 17 is located.
  • the toothed wheel 15 is constantly in engagement with a climbing toothing 18 which is arranged in a stationary manner in the gear housing 2, for example on its rear frame or wall 4.
  • Crank arm 7 and drawer 9 together form a straight sliding crank 7/9, which can be moved from the drive member 6, for example by a square drive mandrel of an operating hand lever or also a power drive is. It is assumed that the drive member 6 in two successive switching steps, each extending over angular distances of 90 °, from a basic switching position according to FIG. 1 into an intermediate switching position according to FIG. 2 and again from the intermediate switching position according to FIG. 2 3 is rotatable in the end switch position.
  • the straight push crank 7/9 on the one hand and the gear wheel 15, the toothing 16 and the climbing toothing 18 on the other hand are provided as intermediate gear members between the drive member 6 and the drive rod 17, which should not only bring about the conversion of a rotary drive movement into a linear output movement. Rather, the intermediate gear members also have the task of producing a relatively large total actuating path a for the drive rod 17 with a small installation depth for the actuating gear 1, which in turn is composed of two different partial actuating paths b and c.
  • the translation of the partial travel x and y that can be produced by the straight thrust crank 7/9 and the total travel z in the partial travel b and c as well as the total travel a of the drive rod 17 is achieved by the gear transmission 15 arranged downstream of the straight travel crank 7/9 / 16/18 causes because the gear 15 rolls on the one hand in the fixed climbing toothing 18 and on the other hand meshes with the toothing 16 in the lockable drive rod 17.
  • the transmission ratio z: a is determined by the pitch circle radius of the diametrically opposite toothed sections of the toothed wheel 15 which are respectively engaged with the climbing toothing 18 and the toothing 16.
  • both links 10 and 11 of the drawers 9 to be designed such that they have a shape which is slightly curved or kinked in the direction of their plane of movement. Their kink or curvature positions are aligned, as can be clearly seen from FIGS. 1 to 3 of the drawing.
  • crank arm 7 While in the basic switching position of the actuating gear 1, the crank arm 7 is supported on a stop 20 inserted into the gear housing 2 (FIG. 1), the crank arm 7 supports in its end switching position the rear frame or wall of the gear housing 2 on (Fig. 3).
  • FIGS. 4 and 5 of the drawing differ from those according to FIGS. 1 to 3 in various respects.
  • a gear 15 is also used in the gear transmission 15/16/18, which has a circular rolling area and meshes with teeth 16 and climbing teeth 18 aligned parallel to the sliding direction of the drive rod 17.
  • this gear wheel 15 is mounted on the link 11 of the drawer 9 about an axis 14 arranged eccentrically to its circumference.
  • the eccentricity of the axis 14 to the circumference or pitch circle of the toothing is laid so that with the help of the gear wheel 15 over the one part of the basic switching position and on the other hand from the intermediate switching position limited first partial travel distance comes into effect than over the second partial travel which is determined by the intermediate switching position and the final switching position.
  • the fixed guide 13 of the gear housing 2 does not interact with the connecting joint 12 between the two links 10 and 11 of the drawer 9, but rather with guide webs 21, which are rigidly arranged on the gear 11 bearing member 11 of the drawer 9.
  • the outer boundary surfaces of the guide webs 21 have a spherical or convex curvature and engage in longitudinal slots on the bottom 3 and on the cover of the gear housing 2 a, which have a slightly curved course and form the stationary guide 13. It has proven useful, for example, if the lower part of the fixed guide 13 runs with an inclined position of approximately 2 degrees with respect to the longitudinal direction of the transmission housing 2 and the upper part of the same follows this with an inclined position of approximately 4 to 5 degrees.
  • the two links 10 and 11 of the drawer 9 also have an aspect ratio of about 1: 1 to one another; however, the slightly curved or kinked shape of the links 10 and 11 is also present there, so that a collision with threaded bushings 22 is avoided, into which fastening screws for the bearing rose of an operating hand lever can be screwed.
  • the actuating gear 1 according to FIGS. 4 and 5 correspond in terms of their basic structure. However, while the actuating gear 1 according to FIG. 4 is designed for a relatively small backset of 20 mm, the actuating gear 1 according to FIG. 5 is equipped for a relatively large backset of e.g. 40 mm. The backbone dimension is the same in both cases and relatively small with less than 15 mm.
  • a bridging element 24 is positively engaged, which has a toothing 25 on its opposite longitudinal edge, with which the gear wheel 15 meshes.
  • the bridging element 24 is provided in this case with longitudinal guide grooves 26 which Guide webs 27 cooperate, which are located on the inside on the bottom 3 and on the cover of the gear housing 2.
  • the gear 15 of the gear 15/16/18 can also have a non-circular, e.g. oval, rolling area are provided as well as comb with gear racks 16 and 18 which are curved or inclined to the sliding direction of the toothed rack 17.
  • the gear 15 can also have two toothings with different pitch circle diameters and be designed so that each of these toothings meshes with only one of the toothed racks 16 and 18.
  • the actuating gear 1 can, if required, be equipped with a so-called profile locking cylinder, which fits into a recess 28 in the base 3 and in the cover of the gear housing housing which is closely matched to its profile 2 can be used. Via its beard or driver attachment, which can be rotated by key actuation, this profile locking cylinder acts within the transmission housing 2 on two additionally installed locking slides 29 and 30.
  • the locking slide 29 is arranged and designed so that the crank arm 7 can be blocked against rotation with its help in the basic switching position.
  • the arrangement and design of the bolt slide 30, however, are of such a type that it can be used to directly block the drive rod 17 in its intermediate switching position against displacement. .A blockage of the actuating gear 1 via the partial travel from the intermediate switching position to the end switching position is not provided.
  • the locking slide 29 is set with a cam or a tongue 31 in its path of movement.
  • a nose 23 of the locking slide 30 engages in a cutout 33 of the drive rod 17.
  • the locking slides 29 and 30 are designed and held in operative connection with one another in such a way that they can only be moved logically via the profile locking cylinder.
  • a leg spring 34 serves the purpose of securing the disengaged basic position of both locking slides 29 and 30, as can be seen in FIGS. 4 and 5. In the engaged position, the two locking slides 29 and 30 block each other, also under the influence of the leg spring 34, as long as the profile lock cylinder is not actuated.

Abstract

What is described is an actuating mechanism 1 for longitudinally displaceable espagnolettes 17 on fittings of windows and doors or the like, which can be brought manually and/or by powerdrive into a plurality of different switching positions, so that the wing can be moved relative to the fixed frame out of a locked closing position into a plurality of different opening positions, for example a tilt-open position and a parallel set-off position or a turn-open position and, if appropriate, also a partly open ventilation position. At least the tilt-open position is to be adjustable positively via arms movable by the espagnolette 17, whilst a driving member 6 mounted rotatably in a mechanism housing 2 is rotatable out of a basic switching position via at least one intermediate switching position into an end switching position, the end switching position being at an angular distance of 180 degrees from the basic switching position, whilst the or an intermediate switching position is at an angular distance of 90 degrees between the basic switching position and the end switching position. It is proposed to keep the driving member 6 in continuous drive connection with the espagnolette 17, guided linearly in the mechanism housing 2, via intermediate mechanism members 9 to 18 which are designed for an unequal subdivision b and c of the total adjusting travel a of the espagnolette 17 over the range from the basic switch position to the intermediate switch position and from the intermediate switching position to the end switching position. As intermediate mechanism members 7 to 18, on the one hand a slider crank 7/9 actuated by the turn-driving member 6 and on the other hand a gearwheel mechanism 15/16/18 meshing with the espagnolette 17 are connected directly in series. Furthermore, a gearwheel 15 of the gearwheel mechanism 15/16/18 meshing with a rack 16 of the espagnolette 17 is supported with its rotary axle 14 on the slider plate 9 of the slider crank 7/9 and, furthermore, in its circumferential region located approximately diametrically opposite the point of engagement with the rack 16 of the espagnolette 17, is in permanent engagement with an inclined-plane toothing 18 provided at a fixed location in the mechanism housing 2. <IMAGE>

Description

Die Erfindung betrifft ein Betätigungsgetriebe mit einer längsverschiebbaren Treibstange für Beschläge von Fenstern und Türen od. dgl., die - manuell und/oder durch Kraftantrieb - in mehrere verschiedene Schaltstellungen bringbar sind, um den Flügel relativ zum feststehenden Rahmen aus einer verriegelten Schließlage in mehrere verschiedene Öffnungsstellungen bewegen zu können,

  • beispielsweise in eine Kippöffnungslage und in eine Parallelabstellage oder in eine Drehöffnungslage sowie ggf. auch noch in eine Spaltlüftungslage,
  • von denen eine Öffnungsstellung, vornehmlich die Kippöffnungslage oder die Parallelabstellage, zwangsweise - über durch die Treibstange bewegbare Arme - einstellbar ist,
  • wobei ein in einem Getriebegehäuse drehbar gelagertes Antriebsglied aus einer Grund-Schaltstellung über eine Zwischen-Schaltstellung oder mehrere Zwischen-Schaltstellungen in eine End-Schaltstellung drehbar ist und dabei die Endschaltstellung von der Grund-Schaltstellung einen Winkelabstand von 180° hat.,
  • während die Zwischen-Schaltstellung oder eine der Zwischen-Schaltstellungen mit einem Winkelabstand von 90° zwischen der Grund-Schaltstellung und der End-Schaltstellung gelegen ist.
The invention relates to an actuating gear with a longitudinally displaceable drive rod for fittings for windows and doors or the like, which - can be brought - manually and / or by power - in several different switching positions to the wing relative to the fixed frame from a locked closed position in several different To be able to move open positions
  • for example in a tilt opening position and in a parallel storage position or in a rotating opening position and possibly also in a night ventilation position,
  • of which an opening position, primarily the tilt opening position or the parallel storage position, is forcibly adjustable - via arms that can be moved by the drive rod,
  • wherein a drive member rotatably mounted in a transmission housing can be rotated from a basic switching position via an intermediate switching position or several intermediate switching positions to an end switching position and the end switching position has an angular distance of 180 ° from the basic switching position.
  • while the intermediate switching position or one of the intermediate switching positions is located at an angular distance of 90 ° between the basic switching position and the end switching position.

Betätigungsgetriebe dieser Art gehören für den genannten Einsatzzweck bereits seit langem zum Stand der Technik, wie beispielsweise die CH-PS 324 607 ausweist. Hierbei ist der Gesamt-Stellweg der Treibstange in zwei gleich lange Abschnitte unterteilt, der von der Grund-Schaltstellung in die Zwischen-Schaltstellung durchlaufen wird, während der andere durch die Weiterbewegung des Betätigungsgetriebes aus der Zwischen-Schaltstellung in die End-Schaltstellung bestimmt ist.Actuating gears of this type have long been part of the prior art for the stated purpose, such as CH-PS 324 607 shows. Here, the total travel of the drive rod is divided into two sections of equal length, which is passed through from the basic switching position to the intermediate switching position, while the other is determined by the further movement of the actuating gear from the intermediate switching position to the end switching position.

Da die Einbautiefe der Treibstangenbeschläge und des Betätigungsgetriebes in das Fensterprofil eng begrenzt ist, müssen die Betätigungsgetriebe ein möglichst geringes Dornmaß aufweisen, d.h. mit einem kleinen Abstand der Drehachse des im Getriebegehäuse gelagerten Antriebsgliedes von der vorderen Stirnfläche des Getriebegehäuses auskommen. Deshalb können die Antriebsglieder nur einen relativ geringen Radius erhalten, womit der erzielbare Gesamt-Stellweg für die Treibstangen in verhältnismäßig engen Grenzen liegt. Darüber hinaus ist in jedem Falle ein kleinstmögliches Hinterdornmaß gefordert.Since the installation depth of the connecting rod fittings and the actuating gear in the window profile is narrowly limited, the actuating gear must have the smallest possible backset, i.e. get by with a small distance from the axis of rotation of the drive member mounted in the transmission housing from the front end face of the transmission housing. Therefore, the drive members can only get a relatively small radius, so that the achievable total travel range for the drive rods is within relatively narrow limits. In addition, the smallest possible backbone dimension is required.

In bestimmten Fällen, und zwar insbesondere dann, wenn eine Öffnungsstellung des Flügels, z.B. dessen Kippöffnungslage oder Parallelabstellage, zwangsweise - über durch die Treibstangen bewegbare Arme - eingestellt werden muß, reicht der bei der Bewegung des Betätigungsgetriebes, z.B. aus seiner Grund-Schaltstellung in seine Zwischen-Schaltstellung, normalerweise verfügbare Teil des Gesamt-Stellweges der Treibstange nicht aus. Deshalb wurden, z.B. nach DE-AS 12 47 171 und DE-OS 15 59 721 auch bereits Betätigungsgetriebe geschaffen, die als Antriebsglied ein mehrere Zahnsegmente mit verschieden großen Teilkreisdurchmessern aufweisendes Zahnrad benutzen, welches mit Gruppen von Eingriffsgliedern an der Treibstange zusammenwirkt, deren Lage an der Treibstange auf die unterschiedlichen Teilkreisdurchmesser der Zahnsegmente abgestimmt sind.In certain cases, and in particular when an opening position of the wing, e.g. its tilt opening position or parallel storage position, has to be set forcibly - via arms that can be moved by the drive rods - this is sufficient when the actuating gear moves, for example from its basic switching position to its Intermediate switch position, normally available part of the total travel of the drive rod is not sufficient. Therefore, for example according to DE-AS 12 47 171 and DE-OS 15 59 721, actuating gears have already been created which use a gearwheel having several toothed segments with differently sized pitch circle diameters as the drive member, which has groups of engagement members on the drive rod interacts, whose position on the drive rod is matched to the different pitch circle diameters of the toothed segments.

Ein solches Betätigungsgetriebe ist jedoch nur realisierbar, wenn das Dornmaß, also der Abstand der Achsmitte des Zahnrades von der vorderen Stirnfläche des Getriebegehäuses auf den größten vorkommenden Zahnsegment-Radius abgestimmt wird.However, such an actuating gear can only be realized if the backset, that is the distance between the center of the gear wheel and the front end face of the gear housing, is matched to the largest tooth segment radius that occurs.

Ebenfalls bereits bekannt durch die DE-AS 12 92 034 ist ein Betätigungsgetriebe gemäß dem jeweiligen Oberbegriff der Ansprüche 1 und 2. Dieses Dokument offenbart ein Betätigungsgetriebe für längsverschiebbare Treibstangen der eingangs genannten Art, bei dem das Antriebsglied mit einer im Getriebegehäuse linear verschiebbar geführten Treibstange über Zwischengetriebeglieder in einer ständigen Antriebsverbindung gehalten ist, bei dem das Antriebsglied einen radial abstehenden Kurbelarm trägt, in dem ein Kurbelzapfen sitzt und eine Schublasche am Kurbelzapfen angreift, damit der Kurbelarm, der Kurbelzapfen und die Schublasche eine Geradschubkurbel bilden, bei dem als Zwischengetriebeglieder einerseits die vom Dreh-Antriebsglied betätigbare Geradschubkurbel und andererseits ein mit der Treibstange kämmendes Zahnradgetriebe unmittelbar hintereinander geschaltet sind, bei dem ferner ein Zahnrad des Zahnradgetriebes mit einer Verzahnung eines im Getriebegehäuses linear verschiebbar geführten und in die Treibstange formschlüssig einrückbaren Überbrückungselementes kämmt und dieses Zahnrad mit seiner Drehachse an einer Schublasche der Geradschubkurbel lagert, und bei dem dieses Zahnrad darüber hinaus in seinem der Eingriffsstelle mit der Zahnstange der Treibstange etwa diametral gegenüberliegenden Umfangsbereichen mit einer im Getriebegehäuse ortsfest vorgesehenen Kletterverzahnung in Dauereingriff steht. Dieses bekannte Betätigungsgetriebe hat eine Haupt-Einbauebene - also eine größte Baubreite - die sich in Richtung parallel zur Drehachse des Antriebsgliedes der Geradschubkurbel erstreckt.Also known from DE-AS 12 92 034 is an actuating gear according to the respective preamble of claims 1 and 2. This document discloses an actuating gear for longitudinally displaceable drive rods of the type mentioned, in which the drive member with a linearly displaceably guided drive rod in the transmission housing Intermediate gear members is held in a constant drive connection, in which the drive member carries a radially protruding crank arm, in which a crank pin is seated and a drawer engages the crank pin, so that the crank arm, the crank pin and the drawer form a straight thrust crank, in which the intermediate gear members on the one hand have the from Rotary drive member actuated straight slide crank and on the other hand a gear meshing with the drive rod are directly connected in series, in which a gear of the gear transmission with a toothing of a linearly in the gear housing Bbar guided and engages in the drive rod positively engaging bridging element and supports this gear with its axis of rotation on a drawer of the straight slide crank, and in which this gear also in its diametrically opposite circumferential areas with the engagement point with the rack of the drive rod with a fixedly provided climbing gear in the gear housing is in constant intervention. This known actuating gear has a main installation level - that is, a large overall width - which extends in the direction parallel to the axis of rotation of the drive member of the straight thrust crank.

Ziel der Erfindung ist es, ein Betätigungsgetriebe der eingangs angegebenen Gattung zu konzipieren, bei dem unter Einhaltung eines relativ geringen Dornmaßes und auch Hinterdornmaßes sowie einer daraus resultierenden minimalen Einbautiefe eine ungleiche Unterteilung des Gesamt-Stellweges für die hiermit gekuppelte Treibstange erreicht werden kann. Vorzugsweise wird dabei eine Unterteilung des Gesamt-Stellweges angestrebt, die etwa bei einem Verhältnis 2 : 1 liegt, und zwar derart, daß der größere Stellweg-Anteil sich beispielsweise bei der Bewegung des Antriebsgliedes aus seiner Grund-Schaltstellung bis in die einen Winkelabstand von 90° hiervon aufweisende Zwischen-Schaltstellung einstellt, während dann der kleinere Stellweg-Anteil bei seiner Weiterbewegung aus der erwähnten Zwischen-Schaltstellung in die wiederum mit einem Winkelabstand von 90° hiervon entfernte End-Schaltstellung durchlaufen wird.The aim of the invention is to design an actuating gear of the type specified at the outset, in which an uneven subdivision of the total travel range for the drive rod coupled herewith can be achieved while maintaining a relatively small backset and backset dimension and a resulting minimal installation depth. Preferably, a subdivision of the total travel range is sought, which is approximately at a ratio of 2: 1, in such a way that the larger travel range portion, for example when the drive member moves from its basic switching position to an angular distance of 90 ° of which has the intermediate switching position, while then the smaller portion of the travel path is passed through as it moves further from the intermediate switching position mentioned to the end switching position, which is in turn at an angle of 90 ° from it.

Erreicht wird das gesteckte Ziel nach der Erfindung grundsätzlich, wenn das Antriebsglied mit der im Getriebegehäuse linear verschiebbar geführten Treibstange über Zwischengetriebeglieder in einer ständigen Antriebsverbindung gehalten ist,

  • wenn das Antriebsglied einen radial abstehenden Kurbelarm trägt, in dem ein Kurbelzapfen sitzt und eine Schublasche am Kurbelzapfen angreift, damit der Kurbelarm, der Kurbelzapfen und die Schublasche eine Geradschubkurbel bilden,
  • wenn als Zwischengetriebeglieder einerseits die vom Dreh-Antriebsglied betätigbare Geradschubkurbel und andererseits ein mit der Treibstange kämmendes Zahnradgetriebe unmittelbar hintereinandergeschaltet sind,
  • wenn ferner ein mit einer Zahnstange der Treibstange kämmendes Zahnrad des Zahnradgetriebes mit seiner Drehachse an einer Schublasche der Geradschubkurbel lagert,
  • wenn dieses Zahnrad darüber hinaus in seinem der Eingriffsstelle mit der Zahnstange der Treibstange etwa diametral gegenüberliegenden Umfangsbereich mit einer im Getriebegehäuse ortsfest vorgesehenen Kletterverzahnung in Dauereingriff steht,
  • wenn die Zwischengetriebe-Glieder für eine ungleiche Unterteilung des Gesamt-Stellweges der Treibstange über den Bereich von der Grund-Schaltstellung zur Zwischen-Schaltstellung sowie von der Zwischen-Schaltstellung zur End-Schaltstellung ausgelegt sind,
  • und wenn schließlich die Drehachse am Zahnrad des Zahnradgetriebes exzentrisch zum Umfang bzw. Teilkreis seiner Verzahnung angeordnet ist.
The set aim according to the invention is basically achieved if the drive member is held in a constant drive connection with the drive rod, which is linearly displaceable in the transmission housing, via intermediate gear members,
  • if the drive member carries a radially projecting crank arm, in which a crank pin is seated and a drawer engages the crank pin, so that the crank arm, the crank pin and the drawer form a straight thrust crank,
  • if, on the one hand, the straight-pull crank that can be actuated by the rotary drive member and, on the other hand, a gear transmission meshing with the drive rod are connected directly in series as intermediate gear members,
  • if, in addition, a gear wheel of the gear transmission meshing with a toothed rack of the drive rod is supported with its axis of rotation on a drawer of the straight thrust crank,
  • if this gear wheel is also in permanent engagement in its circumferential area approximately diametrically opposite the point of engagement with the gear rack of the drive rod with a climbing toothing provided in the gear housing,
  • if the intermediate gear links are designed for an uneven subdivision of the total travel of the drive rod over the range from the basic switching position to the intermediate switching position and from the intermediate switching position to the final switching position,
  • and when finally the axis of rotation on the gear of the gear transmission is arranged eccentrically to the circumference or pitch circle of its toothing.

Der Vorteil eines der Eingangsspezifikation entsprechenden Betätigungsgetriebes mit diesen Merkmalen liegt darin, daß sich ein sogenanntes Großhubgetriebe schaffen läßt, welches mit relativ kleinem Dornmaß sowie Hinterdornmaß und folglich mit einer geringen Einbautiefe - in Richtung parallel zur Flügelebene - verwirklicht werden kann. Damit unterscheidet es sich nicht oder nur unwesentlich von den Abmessungen der entsprechenden Betätigungsgetriebe mit normalem Gesamt-Stellweg. Von besonderer Bedeutung ist jedoch die Tatsache, daß durch die angegebenen Maßnahmen ein Großhubgetriebe für einen Gesamt-Stellweg zwischen 50 mm und 70 mm, vorzugsweise mit etwa 60 mm, geschaffen werden kann, bei welchem aus zwei aufeinanderfolgenden Drehwinkelbereichen von je 90° für das Antriebsglied beträchtlich unterschiedliche Stellwege für die Treibstange abgeleitet werden können. Über die beiden Teil-Drehwinkelbereiche des Betätigungsgetriebes von je 90° hinweg läßt sich mit Hilfe der erfindungsgemäßen Auslegung eine in vorteilhafter Weise unterschiedliche Kraft/Weg-Umsetzung erreichen und folglich der Bedienungskomfort der Treibstangenbeschläge für Fenster und Türen verbessern.The advantage of an actuating gear corresponding to the input specification with these features is that a so-called large stroke gear can be created, which can be realized with a relatively small backset and backset and consequently with a small installation depth - in the direction parallel to the wing plane. This means that it does not differ, or only insignificantly, from the dimensions of the corresponding actuating gear with a normal total travel. Of particular importance, however, is the fact that a large-stroke gearbox for a total travel between 50 mm and 70 mm, preferably about 60 mm, can be created by the specified measures, in which two successive rotation angle ranges of 90 ° for the drive member considerably different travel ranges for the drive rod can be derived. Over the two partial rotation angle ranges of the actuating gear of 90 ° each, with the help of the design according to the invention, an advantageously different force / displacement implementation achieve and consequently improve the ease of use of the espagnolette fittings for windows and doors.

Soll ein Betätigungsgetriebe der spezifizierten Art für längsschiebbare Treibstangen an Beschlägen von Fenstern und Türen od. dgl. mit einem großen Dornmaß ausgestattet werden, dann ist das erfindungsgemäß erreichbar,

  • wenn das Antriebsglied mit der im Getriebegehäuse linear verschiebbar geführten Treibstange über Zwischengetriebeglieder in einer ständigen Antriebsverbindung gehalten ist,
  • wenn das Antriebsglied einen radial abstehenden Kurbelarm trägt, in dem ein Kurbelzapfen sitzt und eine Schublasche am Kurbelzapfen angreift, damit der Kurbelarm, der Kurbelzapfen und die Schublasche eine Geradschubkurbel bilden,
  • wenn als Zwischengetriebeglieder einerseits die vom Dreh-Antriebsglied betätigbare Geradschubkurbel und andererseits ein mit der Treibstange kämmendes Zahnradgetriebe unmittelbar hintereinander geschaltet sind,
  • wenn ferner ein Zahnrad des Zahnradgetriebes mit einer Verzahnung eines im Getriebegehäuse linear verschiebbar geführten und in die Treibstange formschlüssig einrückbaren Überbrückungselementes kämmt, und dieses Zahnrad mit seiner Drehachse an einer Schublasche der Geradschubkurbel lagert,
  • wenn dieses Zahnrad darüber hinaus in seinem der Eingriffsstellung mit der Zahnstange der Treibstange etwa diametral gegenüberliegenden Umfangsbereich mit einer im Getriebegehäuse ortsfest vorgesehenen Kletterverzahnung in Dauereingriff steht,
  • wenn die Zwischengetriebe-Glieder für eine ungleiche Unterteilung des Gesamt-Stellweges der Treibstange über den Bereich von der Grund-Schaltstellung zur Zwischen-Schaltstellung sowie von der Zwischen-Schaltstellung zur End-Schaltstellung ausgelegt sind,
  • und wenn schließlich die Drehachse am Zahnrad des Zahnradgetriebes exzentrisch zum Umfang bzw. Teilkreis seiner Verzahnung angeordnet ist.
If an actuating gear of the specified type for longitudinally sliding connecting rods on fittings for windows and doors or the like is to be equipped with a large backset, this can be achieved according to the invention,
  • if the drive member is held in a constant drive connection with the drive rod, which is guided linearly displaceably in the transmission housing, via intermediate gear members,
  • if the drive member carries a radially projecting crank arm, in which a crank pin is seated and a drawer engages the crank pin, so that the crank arm, the crank pin and the drawer form a straight thrust crank,
  • if, as intermediate gear members, on the one hand the straight thrust crank which can be actuated by the rotary drive member and, on the other hand, a gear transmission meshing with the drive rod are connected directly one behind the other,
  • if, in addition, a gearwheel of the gearwheel gear meshes with a toothing of a bridging element which is linearly displaceably guided in the gearbox housing and can be positively inserted into the drive rod, and this gearwheel is mounted with its axis of rotation on a drawer of the straight thrust crank,
  • if this gear wheel is also in permanent engagement in its circumferential area approximately diametrically opposite the engagement position with the gear rack of the drive rod with a climbing toothing provided in the transmission housing,
  • if the intermediate gear links are designed for an uneven subdivision of the total travel of the drive rod over the range from the basic switching position to the intermediate switching position and from the intermediate switching position to the final switching position,
  • and when finally the axis of rotation on the gear of the gear transmission is arranged eccentrically to the circumference or pitch circle of its toothing.

Es ist einerseits eine Ausgestaltung möglich, bei der das Zahnrad - wie üblich - einen kreisrunden Abwälzbereich hat und mit wenigstens annähernd parallel zur Schieberichtung der Treibstange ausgerichteten Zahnstangen kämmt. Andererseits kann aber das Zahnrad auch einen unrunden, z.B. ovalen Abwälzbereich aufweisen und mit angepaßt gekrümmt bzw. schräg zur Schieberichtung der Treibstange verlaufenden Zahnstangen kämmen.On the one hand, an embodiment is possible in which the gearwheel - as usual - has a circular rolling area and meshes with toothed racks aligned at least approximately parallel to the sliding direction of the drive rod. On the other hand, the gear can also have a non-circular shape, e.g. have oval rolling area and comb with gear racks that are curved or inclined to the direction of sliding of the drive rod.

Nach einem weiteren Ausgestaltungsvorschlag für das erfindungsgemäße Betätigungsgetriebe besteht die Schublasche der Geradschubkurbel aus zwei hintereinander geschalteten Gliedern, wobei z.B. deren gemeinsames Verbindungsgelenk oder eines der Glieder in einer ortsfesten Führung des Getriebegehäuses verschiebbar gehalten wird. Diese ortsfeste Führung kann sich im Getriebegehäuse etwa parallel zur Verschieberichtung der Treibstange erstrecken oder auch einen Verlauf bzw. eine Lage erhalten, bei dem bzw. der das Verbindungsgelenk zwischen den beiden Schublaschen-Gliedern ausschließlich in der mittleren Dreh- bzw. Zwischen-Schaltstellung des Antriebsgliedes etwa auf einer Verbindungsgeraden durch den Kurbelzapfen der Geradschubkurbel und durch die Drehachse des Zahnrades an der Schublasche liegt.According to a further design proposal for the actuating gear according to the invention, the drawer of the straight-pull crank consists of two links connected in series, e.g. whose common connecting joint or one of the links is slidably held in a fixed guide of the gear housing. This stationary guide can extend approximately parallel to the direction of displacement of the drive rod in the gear housing or can also receive a course or a position in which the connecting joint between the two drawer link members is only in the middle rotary or intermediate switching position of the drive member is on a straight line through the crank pin of the straight thrust crank and through the axis of rotation of the gear on the drawer.

Die Erfindung schließt aber auch eine Ausgestaltung der ortsfesten Führung im Getriebegehäuse ein, die einen mehr oder weniger bogen- bzw. kurvenförmigen Verlauf hat und folglich die Übertragung der vom Antriebsglied erzeugten Antriebsbewegung zur Treibstange hin zusätzlich beeinflußt.However, the invention also includes an embodiment of the fixed guide in the gear housing, which has a more or less curved or curved shape and consequently additionally influences the transmission of the drive movement generated by the drive member to the drive rod.

Bewährt hat sich bei einem erfindungsgemäßen Betätigungsgetriebe auch eine Ausbildung, bei der die Gesamtlänge der Schublasche für die Geradschubkurbel zum Kurbelradius des Antriebgliedes ein Verhältnis vom etwa 5:1 aufweist, während die Länge der beiden Glieder Der Schublasche zueinander in einem Verhältnis vom etwa 2 : 3 steht. In diesem Falle sollte das kürzere Glied der Schublasche dem Antriebsglied und längere Glied derselben dem Zahnrad zugeordnet werden. Selbstverständlich liegt es aber auch im Rahmen der Erfindung, für die beiden Glieder der Schublasche andere Längenverhältnisse in Gebrauch zu nehmen, insbesondere das Längenverhältnis 1 : 1.In an actuating gear according to the invention, a design has also proven itself in which the total length of the drawer for the straight thrust crank to the crank radius of the drive member has a ratio of about 5: 1, while the length of the two links of the drawer has a ratio of about 2: 3 to one another stands. In this case, the shorter link of the drawer should be assigned to the drive link and the longer link to the gear. Of course, it is also within the scope of the invention to use different aspect ratios for the two members of the drawer, in particular the aspect ratio 1: 1.

In baulicher Hinsicht hat es sich für ein Betätigungsgetriebe nach der Erfindung als zweckmäßig erwiesen, wenn beide Glieder der Schublasche eine in Richtung ihrer Bewegungsebene leicht gekrümmte oder geknickte Gestalt aufweisen, wobei ihre Knick- bzw. Krümmungslage gleichgerichtet ist. Es wird hierdurch eine behinderungsfreie Befestigung der Lagerrosette eines Bedienungshandhebels am Getriebegehäuse gewährleistet.From a structural point of view, it has proven to be expedient for an actuating gear according to the invention if both members of the drawer have a shape which is slightly curved or kinked in the direction of their plane of movement, their kink or curvature position being rectified. This ensures that the bearing rosette of an operating hand lever is attached to the transmission housing without obstruction.

Es erweist sich oft als vorteilhaft, wenn der Kurbelzapfen des Antriebsgliedes der Geradschubkurbel in der End-Schaltstellung des Betätigungsgetriebes Übertotpunktlage einnimmt, während er bei in Grund-Schaltstellung befindlichem und abgestütztem Antriebsglied eine Untertotpunktlage hat. Zumindest in der Grund-Schaltstellung bzw. der Untertotpunktlage läßt sich das Antriebsglied - vorzugsweise durch einen im Getriebegehäuse untergebrachten, zusätzlichen Schubriegel - blockieren, wobei für die Betätigung des Schubriegels in das Getriebegehäuse z.B. ein sogenannter Profilzylinder - nachträglich - eingesetzt werden kann.It often proves to be advantageous if the crank pin of the drive member of the straight thrust crank assumes an over-center position in the end switching position of the actuating gear, while it has an under-center position when the drive element is in the basic switching position and is supported. At least in the basic switching position or the bottom dead center position, the drive member can be blocked - preferably by an additional slide bolt accommodated in the gearbox housing, whereby for the actuation of the slide bolt into the gearbox housing e.g. a so-called profile cylinder can be used afterwards.

Denkbar ist aber auch, im Getriebegehäuse noch einen weiteren Schubriegel vorzusehen, der gemeinsam bzw. gleichzeitig mit dem ersten Schubriegel, z.B. unmittelbar durch den Profilzylinder-, betätigbar ist, wobei dieser zweite Schubriegel unmittelbar in die Treibstange sperrend einrückbar ist, wenn diese den Stellweg-Anteil durchlaufen hat, welcher aus der Winkeldrehung des Antriebgliedes von der Grund-Schaltstellung in die um 90 Grad hierzu versetzte Zwischen-Schaltstellung resultiert.It is also conceivable, however, to provide a further slide bolt in the gearbox housing which works together or simultaneously the first slide bolt, e.g. directly through the profile cylinder, can be actuated, this second slide bolt can be directly locked into the drive rod when it has passed through the travel path component which results from the angular rotation of the drive element from the basic switching position to the position 90 Intermediate switching position offset from this results.

In der Zeichnung sind verschiedene Ausführungsbeispiele des Gegenstandes der Erfindung dargestellt. Dabei zeigen:

Fig. 1,2 und 3
jeweils in ausführlicher Seitenansicht und bei abgenommenem Deckel des Getriebegehäuses die prinzipielle Auslegung eines Betätigungsgetriebes mit längs verschiebbarer Treibstange in der Grund-Schaltstellung, einer Zwischen-Schaltstellung und in der End-Schaltstellung. Einige Merkmale eines Betätigungsgetriebe gemäß den Figuren 1, 2 und 3 fallen nicht unter dem Gegenstand der unabhängigen Ansprüche, und sind also nicht Teil der Erfindung.
Fig. 4 und 5
jedoch eine alle Wesensmerkmale der Erfindung nutzende Bauart des Betätigungsgetriebes der Fig. 1 bis 3 in zwei verschiedenen Varianten - jeweils kurz vor Erreichen ihrer End-Schaltstellung - wiedergeben.
Various exemplary embodiments of the subject matter of the invention are shown in the drawing. Show:
Figs. 1, 2 and 3
in each case in a detailed side view and with the cover of the gear housing removed, the basic design of an actuating gear with a longitudinally displaceable drive rod in the basic switching position, an intermediate switching position and in the final switching position. Some features of an actuating gear according to Figures 1, 2 and 3 are not within the scope of the independent claims and are therefore not part of the invention.
4 and 5
1 to 3 in two different variants - each shortly before reaching their end switching position - reproduce a design of the actuating gear of FIGS. 1 to 3 that uses all the essential features of the invention.

Die in den Fig. 1 bis 5 der Zeichnung dargestellten Betätigungsgetriebe 1 für längsverschiebbare Treibstangen 17 an Beschlägen von Fenstern, Türen od. dgl. haben jeweils ein Getriebegehäuse 2, das beispielsweise im wesentlichen wannen-bzw.muschelförmig gestaltet ist und an seiner offenen Breitseite durch einen -nicht gezeigten- Deckel verschlossen werden kann, der in seiner Umrißform dem Getriebegehäuse 2 angepaßt ist. Dabei stützt sich der Deckel auf vom Boden 3 des Getriebegehäuses 2 rechtwinkelig hochragenden Zargen bzw. Wänden 4 ab. Stirnseitig ist mit dem Getriebegehäuse 2 eine, beispielsweise aus Bandmaterial bestehende Stulpschiene 5 verbunden, z.B. vernietet oder verschweißt.The actuating gear 1 for longitudinally displaceable connecting rods 17 on fittings of windows, doors or the like shown in FIGS. 1 to 5 of the drawing each have a gear housing 2, which is, for example, essentially trough-shaped or shell-shaped and on its open broadside a cover (not shown) can be closed, the outline of which is adapted to the gear housing 2. The cover is supported on frames or projecting from the bottom 3 of the gear housing 2 at right angles. Walls 4 off. A faceplate 5, for example made of strip material, is connected, for example riveted or welded, to the face of the gear housing 2.

Innerhalb des Getriebegehäuses 2 ist zwischen dessen Boden 3 und dem Deckel ein Antriebsglied 6 über einen Winkelbereich vom 180° drehbar gelagert, das einen radial abstehenden Kurbelarm 7 trägt, in dem ein Kurbelzapfen 8 sitzt.Within the gear housing 2, a drive member 6 is rotatably supported between its base 3 and the cover over an angular range of 180 °, which carries a radially projecting crank arm 7 in which a crank pin 8 is seated.

Am Kurbelzapfen 8 greift eine Schublasche 9 an, die wiederum von zwei hintereinander geschalteten Gliedern 10 und 11 gebildet wird. Diese haben ein Verbindungsgelenk 12 gemeinsam, das in einer ortsfesten Führung 13 des Getriebehäuses 2, beispielsweise in Langlöchern oder Schlitzen im Boden 3 und im Deckel, verschiebbar gehalten ist. In den Fig. 1 bis 3 der Zeichnung ist die ortsfeste Führung 13 lediglich durch eine strichpunktierte Linie angedeutet, wobei sich diese geradlinig in Längsrichtung des Getriebegehäuses 2 erstreckt.On the crank pin 8 engages a drawer 9, which in turn is formed by two links 10 and 11 connected in series. These have a connecting joint 12 in common, which is held displaceably in a fixed guide 13 of the gear housing 2, for example in elongated holes or slots in the base 3 and in the cover. 1 to 3 of the drawing, the fixed guide 13 is only indicated by a dash-dotted line, which extends in a straight line in the longitudinal direction of the gear housing 2.

Am freien Ende der Schublasche 9 bzw. des Gliedes 11 derselben ist, abweichend von der Erfindung, um eine zentrische Achse 14 ein Zahnrad 15 drehbar gelagert, welche einerseits mit einer Verzahnung 16 kämmt, die sich an der im Getriebegehäuse 2 und entlang der Stulpschiene 5 längsverschiebbaren Treibstange 17 befindet. Andererseits steht das Zahnrad 15 in seinem der Verzahnung 16 diametral gegenüberliegenden Umfangsbereich ständig mit einer Kletterverzahnung 18 in Eingriff, die ortsfest im Getriebegehäuse 2, und zwar beispielsweise an dessen rückwärtiger Zarge bzw. Wand 4 angeordnet ist.At the free end of the drawer 9 or the link 11 thereof, in contrast to the invention, a toothed wheel 15 is rotatably mounted about a central axis 14, which meshes on the one hand with a toothing 16 which is located on the in the gear housing 2 and along the faceplate 5 longitudinally displaceable drive rod 17 is located. On the other hand, in its circumferential area diametrically opposite the toothing 16, the toothed wheel 15 is constantly in engagement with a climbing toothing 18 which is arranged in a stationary manner in the gear housing 2, for example on its rear frame or wall 4.

Kurbelarm 7 und Schublasche 9 bilden miteinander eine Geradschubkurbel 7/9, die von dem Antriebsglied 6 aus, beispielsweise durch einen Vierkant-Antriebsdorn eines Bedienungshandhebels oder auch eines Kraftantriebs, bewegbar ist. Dabei wird vorausgesetzt, daß das Antriebsglied 6 in zwei sich jeweils über Winkelabstände von 90° erstreckenden, aufeinanderfolgenden Schaltschritten aus einer Grund-Schaltstellung gemäß Fig. 1 in eine Zwischen-Schaltstellung nach Fig. 2 sowie wiederum aus der Zwischen-Schaltstellung nach Fig. 2 in die End-Schaltstellung nach Fig. 3 drehbar ist.Crank arm 7 and drawer 9 together form a straight sliding crank 7/9, which can be moved from the drive member 6, for example by a square drive mandrel of an operating hand lever or also a power drive is. It is assumed that the drive member 6 in two successive switching steps, each extending over angular distances of 90 °, from a basic switching position according to FIG. 1 into an intermediate switching position according to FIG. 2 and again from the intermediate switching position according to FIG. 2 3 is rotatable in the end switch position.

Die Geradschubkurbel 7/9 einerseits sowie das Zahnrad 15, die Verzahnung 16 und die Kletterverzahnung 18 andererseits sind als Zwischengetriebeglieder zwischen dem Antriebsglied 6 und der Treibstange 17 vorgesehen, welche nicht nur die Umsetzung einer Drehantriebsbewegung in eine lineare Abtriebsbewegung herbeiführensollen. Vielmehr kommt den Zwischengetriebegliedern auch noch die Aufgabe zu, bei kleiner Einbautiefe für das Betätigungsgetriebe 1 einen relativ großen Gesamt-Stellweg a für die Treibstange 17 hervorzubringen, der sich wiederum aus zwei unterschiedlichen Teil-Stellwegen b und c zusammensetzt.The straight push crank 7/9 on the one hand and the gear wheel 15, the toothing 16 and the climbing toothing 18 on the other hand are provided as intermediate gear members between the drive member 6 and the drive rod 17, which should not only bring about the conversion of a rotary drive movement into a linear output movement. Rather, the intermediate gear members also have the task of producing a relatively large total actuating path a for the drive rod 17 with a small installation depth for the actuating gear 1, which in turn is composed of two different partial actuating paths b and c.

Allein der durch die 180° Drehung des Antriebsgliedes 6 mit Hilfe der Geradschubkurbel 7/9 hervorbringbare Gesamt-Stellweg z ist beträchtlich kleiner als der für die Treibstange 17 erforderliche Gesamt-Stellweg a. Das Charakteristikum der Geradschubkurbel 7/9 liegt jedoch darin, daß sie bei der ersten 90° Teildrehung des Antriebsgliedes 6 aus der Grund-Schaltstellung nach Fig. 1 in die Zwischen-Schaltstellung nach Fig. 2 einen größeren Teil-Stellweg x hervorbringt. als bei der zweiten 90°-Teildrehung aus der Zwischen-Schaltstellung nach Fig. 2 in die End-Schaltstellung nach Fig. 3. Hierbei wird nämlich nur ein Teil-Stellweg y durchlaufen, der einem Bruchteil, beispielsweise der Hälfte, des Teil-Stellweges x entspricht.Only the total travel z that can be produced by the 180 ° rotation of the drive member 6 with the help of the straight thrust crank 7/9 is considerably smaller than the total travel a required for the drive rod 17. The characteristic of the straight thrust crank 7/9 is, however, that it produces a larger partial travel x at the first 90 ° partial rotation of the drive member 6 from the basic switching position according to FIG. 1 to the intermediate switching position according to FIG. 2. than in the second 90 ° partial rotation from the intermediate switching position according to FIG. 2 to the final switching position according to FIG. 3. This is because only a partial travel y is covered, which is a fraction, for example half, of the partial travel x corresponds.

Die Übersetzung der von der Geradschubkurbel 7/9 hervorbringbaren Teil-Stellwege x und y sowie des Gesamt-Stellweges z in die Teil-Stellwege b und c sowie den Gesamt-Stellweg a der Treibstange 17 wird durch das der Geradschubkurbel 7/9 nachgeordnete Zahnradgetriebe 15/16/18 bewirkt, weil sich das Zahnrad 15 einerseits in der ortsfesten Kletterverzahnung 18 abwälzt und andererseits mit der Verzahnung 16 in der verschließbaren Treibstange 17 kämmt. Das Übersetzungsverhältnis z : a wird dabei bestimmt vom Teilkreisradius der jeweils mit der Kletterverzahnung 18 und der Verzahnung 16 in Eingriff befindlichen, sich diametral gegenüber liegenden Verzahnungsabschnitte des Zahnrades 15.The translation of the partial travel x and y that can be produced by the straight thrust crank 7/9 and the total travel z in the partial travel b and c as well as the total travel a of the drive rod 17 is achieved by the gear transmission 15 arranged downstream of the straight travel crank 7/9 / 16/18 causes because the gear 15 rolls on the one hand in the fixed climbing toothing 18 and on the other hand meshes with the toothing 16 in the lockable drive rod 17. The transmission ratio z: a is determined by the pitch circle radius of the diametrically opposite toothed sections of the toothed wheel 15 which are respectively engaged with the climbing toothing 18 and the toothing 16.

Wenn daher bei dem Betätigungsgetriebe 1 ein Zahnrad 15 mit kreisrundem Abwälzbereich benutzt ist, das nach Fig. 1 bis 3 lediglich zentrisch um die Achse 14 rotiert, beträgt das Übersetzungsverhältnis z : a = 1 : 2.Therefore, if a gear wheel 15 with a circular rolling area is used in the actuating gear 1, which only rotates centrally around the axis 14 according to FIGS. 1 to 3, the transmission ratio is z: a = 1: 2.

Den gleichen Übersetzungsverhältnissen unterliegen hier selbstverständlich auch die Teil-StelIwege x : b und y : c.Of course, the partial positions x: b and y: c are also subject to the same transmission ratios.

Aus den Fig. 1 bis 3 der Zeichnung geht hervor, ,daß sich die ortsfeste Führung 13 für das Verbindungsgelenk 12 sowie die Verzahnung 16 der Treibstange 17 und die Kletterverzahnung 18 im Getriebegehäuse 2 des Betätigungsgetriebes 1 parallel zu dessen Längsrichtung erstrecken. Erkennbar ist dort auch, daß das Zahnrad 15 über seinen Gesamtumfang hinweg verzahnt ist und nur einen Teilkreisdurchmesser aufweist.1 to 3 of the drawing shows that the fixed guide 13 for the connecting joint 12 and the teeth 16 of the drive rod 17 and the climbing teeth 18 in the gear housing 2 of the actuating gear 1 extend parallel to the longitudinal direction thereof. It can also be seen there that the gear wheel 15 is toothed over its entire circumference and has only a pitch circle diameter.

Bei den in den Fig. 1 bis 3 dargestellten Ausführungsbeispiel eines Betätigungsgetriebes 1 sind Vorkehrungen getroffen, nach denen die Gesamtlänge der Schublasche 9 für die Geradschubkurbel 7/9 zum Kurbelradius des Kurbelarms 7 in einem Verhältnis vom etwa 5:1 steht. Die Länge der beiden Glieder 10 und 11 der Schublasche 9 zu einander verhält sich dabei etwa wie 2:3. Das kürzere Glied 10 der Schublasche ist hier dem Kurbelarm 7 zugeordnet, während am längeren Glied 11 das Zahnrad 15 des Zahnradgetriebes 15/16/18 lagert.In the exemplary embodiment of an actuating gear 1 shown in FIGS. 1 to 3, precautions are taken according to which the total length of the drawer 9 for the straight sliding crank 7/9 is in a ratio of approximately 5: 1 to the crank radius of the crank arm 7. The length of the two Links 10 and 11 of the drawer 9 to each other behaves approximately as 2: 3. The shorter link 10 of the drawer is assigned to the crank arm 7, while the gear 15 of the gear transmission 15/16/18 is mounted on the longer link 11.

Außerdem sind Vorkehrungen getroffen, mit denen erreicht wird, daß das Verbindungsgelenk 12 zwischen den beiden Gliedern 10 und 11 der Schublasche 9 in der Zwischen-Schaltstellung nach Fig. 2 auf einer Verbindungsgeraden durch den Kurbel zapfen 8 der Geradschubkurbel 7/9 und durch die Drehachse 14 des Zahnrades 15 liegt.In addition, arrangements are made with which it is achieved that the connecting joint 12 between the two links 10 and 11 of the drawer 9 in the intermediate switching position according to FIG. 2 tap on a straight line through the crank 8 of the straight-line crank 7/9 and through the axis of rotation 14 of the gear 15 lies.

Damit die Verbindung eines über einen Vierkantdorn mit dem Antriebsglied 6 kuppelbaren Bedienungshandhebels mit dem Getriebegehäuse 2 des Betätigungsgetriebes 1 behinderungsfrei mit Hilfe von Schrauben möglich ist, die mit Eingriffslöchern 19 bzw. darin sitzenden Gewindebuchsen 22 in Wirkverbindung treten, hat es sich bewährt, beide Glieder 10 und 11 der Schublaschen 9 so auszuführen, daß sie eine in Richtung ihrer Bewegungsebene leicht gekrümmte oder geknickte Gestalt aufweisen. Dabei sind ihre Knick- bzw. Krümmungslagen gleichgerichtet, wie das deutlich aus den Fig. 1 bis 3 der Zeichnung hervorgeht.So that the connection of an operating hand lever that can be coupled to the drive member 6 via a square mandrel with the gear housing 2 of the actuating gear 1 is possible without hindrance with the aid of screws that come into operative connection with engagement holes 19 or threaded bushings 22 seated therein, it has been proven that both links 10 and 11 of the drawers 9 to be designed such that they have a shape which is slightly curved or kinked in the direction of their plane of movement. Their kink or curvature positions are aligned, as can be clearly seen from FIGS. 1 to 3 of the drawing.

Da die im Getriebegehäuse 2 vorgesehenen Löcher 19 bzw. Gewindebuchsen 22 für den Eingriff der Verbindungsschrauben ständig frei bleiben sollen, ist es auch wichtig, daß die ortsfeste Führung 13 für das Verbindungsgelenk 12 der Schublasche 9 eine seitwärts zur Stulpschiene 5 hin versetzte Lage relativ zu den Löchern 19 hat.Since the holes 19 or threaded bushings 22 provided in the gear housing 2 are to remain constantly free for the engagement of the connecting screws, it is also important that the fixed guide 13 for the connecting joint 12 of the drawer 9 has a position laterally offset from the faceplate 5 relative to the Has 19 holes.

Während in der Grund-Schaltstellung des Betätigungsgetriebes 1 der Kurbelarm 7 an einem in das Getriebegehäuse 2 eingesetzten Anschlag 20 abgestützt ist (Fig. 1) legt sich der Kurbelarm 7 in seiner End-Schaltstellung stützend gegen die rückwärtige Zarge bzw. Wand des Getriebegehäuses 2 an (Fig. 3).While in the basic switching position of the actuating gear 1, the crank arm 7 is supported on a stop 20 inserted into the gear housing 2 (FIG. 1), the crank arm 7 supports in its end switching position the rear frame or wall of the gear housing 2 on (Fig. 3).

Die in den Fig. 4 und 5 der Zeichnung gezeigten Ausführungsbeispiele eines Betätigungsgetriebes 1 weichen, von demjenigen nach den Fig. 1 bis 3 in verschiedener Hinsicht ab.The exemplary embodiments of an actuating gear 1 shown in FIGS. 4 and 5 of the drawing differ from those according to FIGS. 1 to 3 in various respects.

So ist zwar im Zahnradgetriebe 15/16/18 auch ein Zahnrad 15 verwendet, das einen kreisrunden Abwälzbereich hat und mit parallel zur Schieberichtung der Treibstange 17 ausgerichteter Verzahnung 16 und Kletterverzahnung 18 kämmt. Gegenüber dem Ausführungsbeispiel nach den Fig. 1 bis 3, welche einige nicht erfindungsgemäße Merkmale umfasst, ist dort jedoch wesentlich, daß dieses Zahnrad 15 um eine exzentrisch zu seinem Umfang angeordnete Achse 14 an dem Glied 11 der Schublasche 9 gelagert wird. Die Exzentrizität der Achse 14 zum Umfang bzw. Teilkreis der Verzahnung ist dabei so gelegt, daß mit Hilfe des Zahnrades 15 über den einerseits von der Grund-Schaltstellung und andererseits von der Zwischen-Schaltstellung eingegrenzten ersten Teil-Stellweg hinweg ein größeres Übersetzungsverhältnis zur Wirkung kommt, als über den zweiten Teil-Stellweg, welcher von der Zwischen-Schaltstellung und der End-Schaltstellung bestimmt wird.Thus, a gear 15 is also used in the gear transmission 15/16/18, which has a circular rolling area and meshes with teeth 16 and climbing teeth 18 aligned parallel to the sliding direction of the drive rod 17. Compared to the exemplary embodiment according to FIGS. 1 to 3, which includes some features not according to the invention, it is essential there that this gear wheel 15 is mounted on the link 11 of the drawer 9 about an axis 14 arranged eccentrically to its circumference. The eccentricity of the axis 14 to the circumference or pitch circle of the toothing is laid so that with the help of the gear wheel 15 over the one part of the basic switching position and on the other hand from the intermediate switching position limited first partial travel distance comes into effect than over the second partial travel which is determined by the intermediate switching position and the final switching position.

Beim Betätigungsgetriebe 1 nach den Fig. 4 und 5 ist es für eine optimale Wirkungsweise auch wichtig, daß die ortsfeste Führung 13 des Getriebegehäuses 2 nicht mit dem Verbindungsgelenk 12 zwischen den beiden Gliedern 10 und 11 der Schublasche 9 zusammenwirkt, sondern vielmehr mit Führungstegen 21, die starr an dem das Zahnrad 15 lagernden Glied 11 der Schublasche 9 angeordnet sind. Die äußeren Begrenzungsflächen der Führungsstege 21 sind zu diesem Zweck ballig bzw. konvex gewölbt gestaltet und greifen in Längsschlitze am Boden 3 und am Deckel des Getriebegehäuses 2 ein, welche einen leichtgekrümmten Verlauf haben und die ortsfeste Führung 13 bilden. Bewährt hat es sich beispielsweise, wenn der untere Teil der ortsfesten Führung 13 gegenüber der Längsrichtung des Getriebegehäuses 2 mit einer Schräglage von etwa 2 Grad verläuft und sich der obere Teil derselben hieran mit einer Schräglage von etwa 4 bis 5 Grad anschließt.4 and 5, it is also important for optimal operation that the fixed guide 13 of the gear housing 2 does not interact with the connecting joint 12 between the two links 10 and 11 of the drawer 9, but rather with guide webs 21, which are rigidly arranged on the gear 11 bearing member 11 of the drawer 9. For this purpose, the outer boundary surfaces of the guide webs 21 have a spherical or convex curvature and engage in longitudinal slots on the bottom 3 and on the cover of the gear housing 2 a, which have a slightly curved course and form the stationary guide 13. It has proven useful, for example, if the lower part of the fixed guide 13 runs with an inclined position of approximately 2 degrees with respect to the longitudinal direction of the transmission housing 2 and the upper part of the same follows this with an inclined position of approximately 4 to 5 degrees.

Beim Betätigungsgetriebe 1 nach den Fig. 4 und 5 haben darüber hinaus die beiden Glieder 10 und 11 der Schublasche 9 zueinander ein Längenverhältnis von etwa etwa 1:1; die leicht gekrümmte bzw. geknickte Gestalt der Glieder 10 und 11 ist jedoch auch dort vorhanden, damit eine Kollision mit Gewindebuchsen 22 vermieden wird, in die sich Befestigungsschrauben für die Lagerrosette eines Bedienungshandhebels eindrehen lassen.In the actuating gear 1 according to FIGS. 4 and 5, the two links 10 and 11 of the drawer 9 also have an aspect ratio of about 1: 1 to one another; however, the slightly curved or kinked shape of the links 10 and 11 is also present there, so that a collision with threaded bushings 22 is avoided, into which fastening screws for the bearing rose of an operating hand lever can be screwed.

Die Betätigungsgetriebe 1 nach den Fig. 4 und 5 stimmen von ihrem grundsätzlichen Aufbau her überein. Während jedoch das Betätigungsgetriebe 1 nach Fig. 4 für ein relativ kleines Dornmaß von 20 mm ausgelegt ist, hat das Betätigungsgetriebe 1 nach Fig. 5 eine Ausstattung für ein verhältnismäßig großes Dornmaß von z.B. 40 mm. Das Hinterdornmaß ist aber in beiden Fällen gleich und mit weniger als 15 mm relativ klein.The actuating gear 1 according to FIGS. 4 and 5 correspond in terms of their basic structure. However, while the actuating gear 1 according to FIG. 4 is designed for a relatively small backset of 20 mm, the actuating gear 1 according to FIG. 5 is equipped for a relatively large backset of e.g. 40 mm. The backbone dimension is the same in both cases and relatively small with less than 15 mm.

Bei dem Betätigungsgetriebe 1 nach Fig. 4 mit kleinem Dornmaß kämmt das Zahnrad 15 unmittelbar mit einer in die Treibstange 17 eingearbeiteten Verzahnung 16. Im Unterschied hierzu ist bei dem Betätigungsgetriebe 1 nach Fig. 5 mit großem Dornmaß in die unmittelbar in die Treibstange 17 eingearbeitete Verzahnung 16 ein Überbrückungselement 24 formschlüssig eingerückt, das an seiner gegenüberliegenden Längskante eine Verzahnung 25 trägt, mit der das Zahnrad 15 kämmt. Das Überbrückungselement 24 ist in diesem Falle mit längsverlaufenden Führungsnuten 26 versehen, die mit Führungsstegen 27 zusammenwirken, welche sich innenseitig am Boden 3 und am Deckel des Getriebegehäuses 2 befinden.4 with a small backset, the gear 15 meshes directly with a toothing 16 machined into the drive rod 17. In contrast to this, with the actuation gear 1 according to FIG. 5 with a large backset, the toothing machined directly into the driving rod 17 16, a bridging element 24 is positively engaged, which has a toothing 25 on its opposite longitudinal edge, with which the gear wheel 15 meshes. The bridging element 24 is provided in this case with longitudinal guide grooves 26 which Guide webs 27 cooperate, which are located on the inside on the bottom 3 and on the cover of the gear housing 2.

Abweichend von den in der Zeichnung dargestellten und vorstehend beschriebenen Ausführungsbeispielen von Betätigungsgetrieben 1 sind auch noch andere Ausgestaltungen möglich.Deviating from the exemplary embodiments of actuating gears 1 shown in the drawing and described above, other configurations are also possible.

So kann beispielsweise das Zahnrad 15 des Zahnradgetriebes 15/16/18 auch mit einem unrunden, z.B. ovalen, Abwälzbereich versehen werden sowie mit angepaßt gekrümmt bzw. schräg zur Schieberichtung der Teibstange 17 verlaufenden Zahnstangen 16 und 18 kämmen.For example, the gear 15 of the gear 15/16/18 can also have a non-circular, e.g. oval, rolling area are provided as well as comb with gear racks 16 and 18 which are curved or inclined to the sliding direction of the toothed rack 17.

Das Zahnrad 15 kann aber auch zwei Verzahnungen mit unterschiedlichem Teilkreisdurchmesser aufweisen und so gestaltet sein, daß jede dieser Verzahnungen mit nur einer der Zahnstangen 16 und 18 kämmt.The gear 15 can also have two toothings with different pitch circle diameters and be designed so that each of these toothings meshes with only one of the toothed racks 16 and 18.

In den Fig. 4 und 5 der Zeichnung ist auch noch zu sehen, daß sich das Betätigungsgetriebe 1 -bei Bedarf- mit einem sogenannten Profil-Schließzylinder ausstatten läßt, der in eine seinem Profil eng angepaßte Ausnehmung 28 im Boden 3 und im Deckel des Getriebegehäuses 2 eingesetzt werden kann. Über seinen durch Schlüsselbetätigung drehbaren Bart bzw. Mitnehmeransatz wirkt dieser Profil-Schließzylinder innerhalb des Getriebegehäuses 2 auf zwei zusätzlich eingebaute RiegeIschieber 29 und 30 ein. Der Riegelschieber 29 ist dabei so angeordnet und ausgebildet, daß mit seiner Hilfe in der Grund-Schaltstellung der Kurbelarm 7 gegen Verdrehung blockiert werden kann. Anordnung und Ausbildung des Riegelschiebers 30 sind hingegen von solcher Art, daß sich mit seiner Hilfe unmittelbar die Treibstange 17 in ihrer Zwischen-Schaltstellung gegen Verschieben blockieren läßt. .Eine Blockierung des Betätigungsgetriebes 1 über den Teil-Stellweg von der Zwischen-Schaltstellung zur End Schaltstellung ist jedoch nicht vorgesehen.4 and 5 of the drawing it can also be seen that the actuating gear 1 can, if required, be equipped with a so-called profile locking cylinder, which fits into a recess 28 in the base 3 and in the cover of the gear housing housing which is closely matched to its profile 2 can be used. Via its beard or driver attachment, which can be rotated by key actuation, this profile locking cylinder acts within the transmission housing 2 on two additionally installed locking slides 29 and 30. The locking slide 29 is arranged and designed so that the crank arm 7 can be blocked against rotation with its help in the basic switching position. The arrangement and design of the bolt slide 30, however, are of such a type that it can be used to directly block the drive rod 17 in its intermediate switching position against displacement. .A blockage of the actuating gear 1 via the partial travel from the intermediate switching position to the end switching position is not provided.

Für die Blockierung des Kurbelarms 7 in der Grund-Schaltstellung des Betätigungsgetriebes 1 wird der Riegelschieber 29 mit einem Nocken bzw. einer Zunge 31 in dessen Bewegungsbahn gestellt. Zur Blockierung der Treibstange 17 in der Zwischen-Schaltstellung rückt hingegen eine Nase 23 des Riegelschiebers 30 in einen Ausschnitt 33 der Treibstange 17 ein.To block the crank arm 7 in the basic switching position of the actuating gear 1, the locking slide 29 is set with a cam or a tongue 31 in its path of movement. To block the drive rod 17 in the intermediate switching position, however, a nose 23 of the locking slide 30 engages in a cutout 33 of the drive rod 17.

Die Riegelschieber 29 und 30 sind so gestaltet und miteinander in Wirkverbindung gehalten, daß sie über den Profil-Schließzylinder immer nur folgerichtig verlagert werden können. Eine Schenkelfeder 34 dient dem Zweck, die ausgerückte Grundstellung beider Riegelschieber 29 und 30, wie sie in den Fig. 4 und 5 zu sehen ist, zu sichern. In der eingerückten Wirkstellung blockieren sich die beiden Riegelschieber 29 und 30 gegenseitig, und zwar ebenfalls unter dem Einfluß der Schenkelfeder 34, so lange der Profil-Schließzylinder nicht betätigt wird.The locking slides 29 and 30 are designed and held in operative connection with one another in such a way that they can only be moved logically via the profile locking cylinder. A leg spring 34 serves the purpose of securing the disengaged basic position of both locking slides 29 and 30, as can be seen in FIGS. 4 and 5. In the engaged position, the two locking slides 29 and 30 block each other, also under the influence of the leg spring 34, as long as the profile lock cylinder is not actuated.

Claims (12)

  1. An actuating transmission (1) having a longitudinally movable positioning bar (17) for fittings of windows and doors or the like and movable manually and/or under power into a number of different operative positions in order to be able to move the leaf relatively to the fixed frame from a locked closed position into a number of different open positions, for example, into a tilted-open position and into a parallel in-line position and into a turned-open position and, if required, into a ventilation gap position, one such open position, preferably the tilted-open position or the parallel in-line position, being settable automatically by way of arms movable by the positioning bar (17),
    a drive member (6) which is rotatably mounted in a transmission casing (2) being rotatable from a normal operative position through one or more intermediate operative positions into an end operative position,
    the end operative position being at an angular distance of 180° from the normal operative position,
    while the intermediate operative position or one of the intermediate operative positions is disposed at an angular distance of 90° between the normal operative position and the end operative position,
    the drive member (6) being retained by way of intermediate transmission members (7 - 18) in permanent driving engagement with the positioning bar (17), the same being linearly movable in the transmission casing (2),
    the drive member (6) carrying a radially projecting crank arm (7) in which a crank pin (8) is disposed, a thrust link (9) engaging the crank pin (8) so that the crank arm (7), crank pin (8) and thrust link (9) form a straight thrust crank (7 - 9),
    there being connected in directly consecutive relationship as intermediate transmission members (7 - 18), on the one hand, the straight thrust crank (7 - 9) actuatable by the rotating drive member (7), and on the other hand, a gearwheel transmission (15, 16, 18) meshing with the positioning bar (17),
    a gearwheel (15) of the gearwheel transmission (15, 16, 18) which meshes with a toothed rack (16) of the positioning bar (17) being mounted by way of a pivot (14) on the thrust link (9) of the straight thrust crank (7 - 9), the gearwheel (15) also being in permanent engagement, in its peripheral zone substantially diametrically opposite the engagement zone with the said toothed rack (16) of the positioning bar (17), with a climb toothing (18) fixedly disposed in the transmission casing (2),
    characterised in that the intermediate transmission members (7 - 18) are designed to provide an unequal subdivision of the total travel (a) of the positioning bar (17) as between the zone extending from the normal operative position to the intermediate operative position and the zone extending therefrom to the end operative position and in that the pivot (14) on the gearwheel (15) of the gearwheel transmission (15, 16, 18) is disposed eccentrically of the periphery or pitch circle of its toothing.
  2. An actuating transmission (1) for longitudinally movable positioning bars (17) on fittings of windows and doors or the like and movable manually and/or under power into a number of different operative positions in order to be able to move the leaf relatively to the fixed frame from a locked closed position into a number of different open positions, for example, into a tilted-open position and into a parallel in-line position and into a turned-open position and, if required, into a ventilation gap position, one such open position, preferably the tilted-open position or the parallel in-line position, being settable automatically by way of arms movable by the positioning bar (17),
    a drive member (6) which is rotatably mounted in a transmission casing (2) being rotatable from a normal operative position through one or more intermediate operative positions into an end operative position,
    the end operative position being at an angular distance of 180° from the normal operative position while the intermediate operative position or one of the intermediate operative positions is disposed at an angular distance of 90° between the normal operative position and the end operative position,
    the drive member (6) being retained by way of intermediate transmission members (7 to 18) in permanent driving engagement with the positioning bar (17),
    the drive member (6) carrying a radially projecting crank arm (7) in which a crank pin (8) is disposed, a thrust link (9) engaging the crank pin (8) so that the crank arm (7), crank pin (8) and thrust link (9) form a straight thrust crank (7 - 9),
    there being connected in directly consecutive relationship as intermediate transmission members (7 - 18), on the one hand, the straight thrust crank (7 - 9) actuatable by the rotating drive member (6) and, on the other hand, a gearwheel transmission (15, 25, 18) meshing with the positioning bar (17),
    a gearwheel (15) of the gearwheel transmission (15, 25, 18), which gearwheel meshes with a toothing (25) of a bridging element (24) which is guided for linear movement in the transmission casing (2) and is engageable positively with the positioning bar (17), the gearwheel (15) being mounted by way of its pivot (14) on the thrust crank link (9),
    the gearwheel (15) also being in permanent engagement, in its peripheral zone substantially diametrically opposite the engagement zone with the toothing (25) of the bridging element (24), with a climb toothing (18) fixed in the transmission casing (2), characterised in that the positioning bar (17) is guidable for linear movement in the transmission casing (2), in that the intermediate transmission members (7 - 18) are designed to provide an unequal subdivision of the total travel (a) of the positioning bar (17) as between the zone extending from the normal operative position to the intermediate operative position and the zone extending therefrom to the end operative position, and in that the pivot (14) of the gearwheel (15) of the gearwheel transmission (15/25/18) is disposed eccentrically of the periphery or pitch circle of its toothing.
  3. An actuating transmission according to claim 1 or 2,
    characterised in that
    the gearwheel (15) has a circular rolling zone and meshes with the climb toothing (18) and toothed rack (16) of the positioning bar (17) or with the climb toothing (18) and the toothing (25) of the bridging element aligned parallel to the direction of movement of the positioning bar (17).
  4. An actuating transmission according to claim 1 or 2,
    characterised in that
    the gearwheel (15) has a non-circular, e.g. oval, rolling zone and meshes with the climb toothing (18) and toothed rack (16) of the positioning bar (17) or with the climb toothing (18) and the toothing (25) of the bridging element which extend with an appropriate curvature or at an inclination to the direction of movement of the positioning bar (17).
  5. An actuating transmission according to claim 1 or claims 2 and 3,
    characterised in that
    the gearwheel (15) of the gearwheel transmission (15, 18 and 16, 25) respectively has two toothings of different diameters, one toothing meshing only with the climb toothing (18) and the other toothing meshing only with the toothed rack (16) of the positioning bar (17) or with the toothing (25) of the bridging element (24).
  6. An actuating transmission according to claim 1 or 2 and at least one of claims 3 to 5,
    characterised in that
    the thrust link (9) of the straight thrust crank (7 - 9) consists of two consecutive members (10, 11) whose common connecting pivot (12) is retained in permanent displaceable engagement in a fixed guide (13) of the transmission casing (2).
  7. An actuating transmission according to claim 6,
    characterised in that
    the fixed guide (13) extends in the transmission casing (2) substantially parallel to the direction of movement of the positioning bar (17) and/or has a shape or a position such that the connecting pivot (12) received therein between the two thrust link members (10, 11) is disposed at least in the central turn position of the drive member (6) substantially on a straight line extending through the crank pin (8) of the straight thrust crank (7/9) and the pivot (14) of the gearwheel (15) of the thrust link (9) (Fig. 2).
  8. An actuating transmission according to claim 1 or 2 and claims 6 and 7,
    characterised in that
    the total length of the thrust link (9) for the straight thrust crank (7/9) is in a ratio of approximately 5 : 1 to the crank radius of the drive member (6) and the lengths of the two members (10, 11) of the thrust link (9) are in a ratio of approximately 2 : 3 to one another.
  9. An actuating transmission according to claim 8,
    characterised in that
    the shorter member (10) of the thrust link (9) is associated with the drive member (6) and the longer (11) with the gearwheel (15).
  10. An actuating transmission according to claim 1 or 2 and claims 6 to 9,
    characterised in that the two members (10, 11) of the thrust link (9) have a shape which is slightly curved or bent in the direction of their movement plane, their bending or curvature extending in the same direction.
  11. An actuating transmission according to claim 1 or 2 and at least one of claims 7 to 9,
    characterised in that
    the crank pin (8) of the drive member (6) of the straight thrust crank (7 - 9) takes up in its end operative position (Fig. 3) a top dead centre position whereas, when the drive member (6) is in the normal operative position (Fig. 1) and is supported, the crank pin (8) is in a bottom dead centre position.
  12. An actuating transmission according to claim 1 or 2 and at least one of claims 3 to 5,
    characterised in that
    the thrust link (9) of the straight thrust crank (7, 9) consists of two consecutive members (10, 11) having a common connecting pivot (12), the member (11) which is associated with the gearwheel (15) of the gearwheel transmission (15, 18 and 16 or 25) respectively being retained for movement along a fixed guide (13) in the transmission casing (2), the latter guide extending with a slight curvature and/or inclination relatively to the direction of movement of the positioning bar (17) (Figs. 4 and 5).
EP92112839A 1991-09-27 1992-07-28 Actuating mechanism for the sliding bars of a door or window fitting Expired - Lifetime EP0534089B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9112079U 1991-09-27
DE9112079U DE9112079U1 (en) 1991-09-27 1991-09-27

Publications (2)

Publication Number Publication Date
EP0534089A1 EP0534089A1 (en) 1993-03-31
EP0534089B1 true EP0534089B1 (en) 1996-11-27

Family

ID=6871725

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92112839A Expired - Lifetime EP0534089B1 (en) 1991-09-27 1992-07-28 Actuating mechanism for the sliding bars of a door or window fitting

Country Status (4)

Country Link
EP (1) EP0534089B1 (en)
AT (1) ATE145702T1 (en)
DE (2) DE9112079U1 (en)
ES (1) ES2095363T3 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202008009184U1 (en) 2008-07-09 2009-11-12 Siegenia-Aubi Kg locking device
EP3128109A1 (en) 2015-08-05 2017-02-08 Aug. Winkhaus GmbH & Co. KG Drive transmission for a fitting on a connecting rod
EP3205797A1 (en) 2016-02-11 2017-08-16 Aug. Winkhaus GmbH & Co. KG Transmission gearing for an espagnolette fitting
EP3205798A1 (en) 2016-02-11 2017-08-16 Aug. Winkhaus GmbH & Co. KG Drive gear for an espagnolette fitting

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4211464A1 (en) * 1992-04-06 1993-10-07 Schueco Int Kg Drive a locking bar fitting for a window or door
DE29600446U1 (en) 1996-01-12 1997-05-07 Siegenia Frank Kg Actuating gear for windows and / or door fittings with adjusting and / or locking linkage or the like.
DE29719611U1 (en) * 1997-11-05 1999-03-11 Gretsch Unitas Gmbh Lock, in particular mortise lock for an outer door
DE19929742A1 (en) * 1999-06-17 2000-12-21 Hautau Gmbh W Gear arrangement for a rod lock
AT408013B (en) * 1999-10-07 2001-08-27 Roto Frank Eisenwaren PUSH-OPERABLE MULTI-LOCK LOCK
DE20313119U1 (en) * 2003-08-22 2003-11-06 Siegenia Aubi Kg Espagnolette lock
DE10354185B4 (en) * 2003-11-20 2015-04-02 Aug. Winkhaus Gmbh & Co. Kg espagnolette
PL2366855T3 (en) * 2010-03-19 2014-12-31 Roto Frank Ag Fitting for a window, door or similar and window, door or similar with a fitting
FR3133636B1 (en) * 2022-03-21 2024-02-16 Ferco Device for controlling a cremone type locking system for a sliding leaf

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DE812046C (en) * 1949-10-23 1951-08-27 Friedrich Walter Korten Inlet bascule lock
CH324607A (en) * 1953-11-16 1957-10-15 Weidtmann Fa Wilhelm Tilting and rotating window sash
DE1247174B (en) * 1963-02-28 1967-08-10 Hubert Kurz Dipl Ing Dr Overhead door
DE1292034C2 (en) * 1966-10-12 1973-05-17 Gretsch Unitas Gmbh Gear for drive rod fittings of windows, doors or the like.
DE1559721B2 (en) * 1966-11-24 1976-12-16 WiIh. Frank GmbH, 7022 Leinfelden-Echterdingen DRIVE DEVICE FOR DRIVE ROD FITTING MOUNTED ON THE INSIDE OF THE FRAME OF A LEAF OF A WINDOW
DE1280706B (en) * 1966-12-13 1968-10-17 Jaeger Frank K G Gear of an espagnolette fitting for windows, doors or the like, especially for tilt and swivel sash windows
DE1559933A1 (en) * 1967-03-01 1969-10-09 Jaeger Kg Frank Gear of a drive rod fitting for windows, doors or the like., In particular for tilt-swivel-sash windows
FR2356794A1 (en) * 1976-06-29 1978-01-27 Ferco Int Usine Ferrures Actuating gear drive for window locking rods - has handle actuated gear and eccentric pinion engaging with toothed racks to increase rod travel
DE2813435C2 (en) * 1978-03-29 1986-01-02 Siegenia-Frank Kg, 5900 Siegen Transmission of window and door locks or the like.
DE3038508A1 (en) * 1980-10-11 1982-05-19 Geze Gmbh, 7250 Leonberg Window drive rod toothed driving gear - has handle neck, linking cogwheel, passing through slot in case front
DE3042829C2 (en) * 1980-11-13 1983-02-24 Siegenia-Frank Kg, 5900 Siegen Operating gear for espagnolette fittings or the like.
DE3142928A1 (en) * 1981-10-29 1983-05-19 Siegenia-Frank Kg, 5900 Siegen Fitting for a horizontal sliding wing, especially a lift sliding wing or a lift-and-tilt sliding wing, of windows, doors or the like
DE3221110A1 (en) * 1982-06-04 1983-12-08 Gretsch-Unitas GmbH Baubeschläge, 7257 Ditzingen FITTING FOR A TILTING AND FOLLOWING AT LEAST PARALLEL CANCELED WING OF A WINDOW, DOOR OR. DGL.
DE3342191A1 (en) * 1983-11-23 1985-05-30 August Bilstein GmbH & Co KG, 5828 Ennepetal Gear for espagnolettes on windows, doors or the like
DE3640895A1 (en) * 1986-11-29 1988-06-09 Fuhr Carl Gmbh & Co Espagnolette fastening
EP0367842B1 (en) * 1988-11-07 1992-01-29 W. Hautau Gmbh Handle assembly for doors, windows or the like
AT394609B (en) * 1989-01-03 1992-05-25 Roto Frank Eisenwaren GEARBOX FOR Tilt & Turn Doors
DE9001276U1 (en) * 1990-02-05 1991-06-27 Ferco International Usine De Ferrures De Batiment, Sarrebourg, Fr
DE9001279U1 (en) * 1990-02-05 1991-06-06 Ferco International Usine De Ferrures De Batiment, Sarrebourg, Fr

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202008009184U1 (en) 2008-07-09 2009-11-12 Siegenia-Aubi Kg locking device
EP2143859A2 (en) 2008-07-09 2010-01-13 Siegenia-Aubi Kg Locking device
EP3128109A1 (en) 2015-08-05 2017-02-08 Aug. Winkhaus GmbH & Co. KG Drive transmission for a fitting on a connecting rod
DE102015214936A1 (en) 2015-08-05 2017-02-09 Aug. Winkhaus Gmbh & Co. Kg Drive gear for a drive rod fitting
EP3205797A1 (en) 2016-02-11 2017-08-16 Aug. Winkhaus GmbH & Co. KG Transmission gearing for an espagnolette fitting
EP3205798A1 (en) 2016-02-11 2017-08-16 Aug. Winkhaus GmbH & Co. KG Drive gear for an espagnolette fitting
DE102016202063A1 (en) 2016-02-11 2017-08-17 Aug. Winkhaus Gmbh & Co. Kg Drive gear for a drive rod fitting
DE102016202064A1 (en) 2016-02-11 2017-08-17 Aug. Winkhaus Gmbh & Co. Kg Transmission gear for a drive rod fitting

Also Published As

Publication number Publication date
EP0534089A1 (en) 1993-03-31
ATE145702T1 (en) 1996-12-15
DE9112079U1 (en) 1993-01-28
ES2095363T3 (en) 1997-02-16
DE59207583D1 (en) 1997-01-09

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