DE9112079U1 - Actuating gear for longitudinally adjustable drive rods on fittings of windows and doors etc. - Google Patents

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

91 107 G

Applicant: Siegenia Frank KG, Eisenhüttenstr. 22, 5900 Siegen (DE) ANR: 1 004 808

Actuating gear for longitudinally adjustable drive rods on fittings of windows and doors or similar.

The innovation concerns an actuating gear for longitudinally displaceable drive rods on fittings of windows and doors or the like, which can be brought into several different switching positions manually and/or by power drive in order to be able to move the sash relative to the fixed frame from the locked closed position into several different opening positions, for example into a tilt opening position and into a rotary opening position or a parallel storage position and possibly also into a gap opening position, whereby a drive element rotatably mounted in a gear housing can be rotated from a basic switching position via at least one intermediate switching position into an end switching position and the end switching position has an angular distance of 180 degrees from the basic switching position, while the or an intermediate switching position is located at an angular distance of 90 degrees between the basic switching position and the end switching position.

Actuating gears of this type have long been state of the art for the above-mentioned purpose, as shown, for example, in CH-PS 324 607. The total travel of the drive rod is divided into two sections of equal length, one of which is traversed when the actuating gear moves 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.

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Since the installation depth of the drive rod fittings and the actuating gear in the window profile is strictly limited, the actuating gear must have the smallest possible backset, i.e. the distance between the axis of rotation of the drive element mounted in the gear housing and the front face of the gear housing must be small. The drive elements can therefore only have a relatively small radius, which means that the achievable total travel for the drive rods is relatively narrow. In addition, the smallest possible backset is required in every case.

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 - the part of the total travel of the drive rod that is normally available when the actuating gear moves, e.g. from its basic switching position to its intermediate switching position, is not sufficient. For this reason, actuating gears have already been created, e.g. according to DE-AS 12 47 174, which use a gear consisting of two tooth segments with different pitch circle diameters as the drive element, which interacts with two groups of engagement elements on the drive rod, the position of which on the drive rod is coordinated with the different pitch circle diameters of the tooth segments.

However, such an actuating gear can only be implemented if the backset, i.e. the distance between the center of the gear wheel and the front face of the gear housing, is adjusted to the largest possible tooth segment radius.

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The aim of the innovation is to design an actuating gear of the generic type in which an unequal division of the total travel for the drive rod coupled to it can be achieved while maintaining a relatively small spindle dimension and rear spindle dimension and a resulting minimum installation depth. Preferably, a division of the total travel is aimed for that is approximately at a ratio of 2:1, in such a way that the larger travel portion is set, for example, when the drive element moves from its basic switching position to the intermediate switching position at an angular distance of 90 degrees from this, while the smaller travel portion is then passed through when it moves further from the aforementioned intermediate switching position to the final switching position, which is again at an angular distance of 90 degrees from this.

The goal set after the innovation is basically achieved by

that the drive element is held in a permanent drive connection with the drive rod, which is guided linearly in the gear housing, via intermediate gear elements, which are designed for an unequal division 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 end switching position,
that the intermediate gear elements are, on the one hand, a straight-thrust crank operated by the rotary drive element and, on the other hand, a gear transmission meshing with the drive rod, connected directly one after the other,

that furthermore a gear of the gear transmission meshing with a rack of the drive rod is mounted with its axis of rotation on the thrust plate of the straight thrust crank,

and finally, this gearwheel is also in permanent engagement with a climbing toothing provided in a fixed position in the gear housing in its peripheral area approximately diametrically opposite the point of engagement with the rack of the drive rod.

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The advantage of an actuating gear that corresponds to this combination of features is that a so-called large stroke gear can be created, which can be implemented with a relatively small spindle dimension and rear spindle dimension and consequently with a small installation depth, and thus does not differ, or only differs insignificantly, from the corresponding dimensions of the actuating gear with a normal total travel. Of particular importance, however, is the fact that the measures specified can be used to create a large stroke gear for a total travel between 50 and 70 millimeters, preferably with around 60 millimeters, in which considerably different travels for the drive rod can be derived from two consecutive rotation angle ranges of 90 degrees each for the drive element. Across the two partial rotation angle ranges of the actuating gear of 90 degrees each, an advantageously different force/travel conversion can be achieved with the help of the design according to the invention and consequently the ease of use of the drive rod fittings for windows and doors can be improved.

According to the innovation, an actuating gear can be further developed in such a way that the axis of rotation on the gear wheel of the gear transmission is arranged eccentrically to the circumference or pitch circle of its teeth. On the one hand, a design is possible in which the gear wheel - as usual - has a circular rolling area and meshes with racks that are aligned at least approximately parallel to the sliding direction of the drive rod. On the other hand, however, the gear wheel can also have a non-circular, e.g. oval, rolling area and mesh with racks that are curved or diagonal to the sliding direction of the drive rod.

According to another possible further development of the innovation, the gear of the gear transmission

also have two gears with different diameters and each gear meshes with only one of the two racks.

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According to a further design proposal for the new operating gear, the pusher arm of the straight pusher crank consists of two links connected in series, whereby, for example, their common connecting joint or one of the links is held so that it can move in a stationary guide in the gear housing. This stationary guide can extend in the gear housing approximately parallel to the direction of movement of the drive rod or can also have a course or position in which the connecting joint between the two pusher arm links lies exclusively in the middle rotary or intermediate switching position of the drive link approximately on a connecting line through the crank pin of the straight pusher crank and through the axis of rotation of the gear on the pusher arm.

The innovation also includes a design of the stationary guide in the gear housing, which has a more or less curved or curved course and consequently additionally influences the transmission of the drive movement generated by the drive element to the drive rod.

A design that has also proven successful in an innovative actuating gear is one in which the total length of the pusher plate for the straight pusher crank has a ratio of about 5:1 to the crank radius of the drive member, while the length of the two members of the pusher plate has a ratio of about 2:3 to each other. In this case, the shorter member of the pusher plate should be assigned to the drive member and the longer member to the gear. Of course, it is also within the scope of the invention to use other length ratios for the two members of the pusher plate, in particular the length ratio of 1:1.

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From a structural point of view, it has proven to be useful for an operating gear according to the innovation if both links of the push tab have a slightly curved or kinked shape in the direction of their plane of movement, with their kink or curvature position being aligned. This ensures that the bearing rosette of an operating hand lever can be attached to the gear housing without obstruction.

It often proves to be advantageous if the crank pin of the drive element of the straight-thrust crank assumes an over-dead-center position in the final switching position of the actuating gear, while it has an under-dead-center position when the drive element is in the basic switching position and supported. At least in the basic switching position or the under-dead-center position, the drive element can be blocked - preferably by an additional sliding bolt housed in the gear housing, whereby a so-called profile cylinder can be subsequently inserted into the gear housing ζ.B to actuate the sliding bolt.

It is also conceivable to provide a further sliding bolt in the gear housing, which can be operated together or simultaneously with the first sliding bolt, e.g. directly by the profile cylinder, whereby this second sliding bolt can be directly engaged in the drive rod in a locking manner when the latter has passed through the travel portion which results from the angular rotation of the drive element from the basic switching position to the intermediate switching position offset by 90 degrees.

The drawing shows various embodiments of the subject of the innovation. The

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Fig. 1,2 and 3 each in detailed side view and at

With the gearbox cover removed,
fundamental interpretation of a
Actuating gear with longitudinally movable
Drive rod in the basic switching position, a
Intermediate switching position and in the final switching position, while the

Fig. 4 and 5 a further developed design of the

Actuating gear of Fig. 1 to 3 in two
different variants - each shortly before
reaching their final switching position.

The actuating gears 1 shown in Figures 1 to 5 of the drawing for longitudinally displaceable drive rods 17 on fittings for windows, doors or the like each have a gear housing 2 which is essentially tub-shaped or shell-shaped, for example, and can be closed on its open broad side by a cover (not shown) whose outline is adapted to the gear housing 2. The cover is supported on frames or walls 4 which protrude at right angles from the base 3 of the gear housing 2. A faceplate 5, made of strip material for example, is connected to the front of the gear housing 2, for example by riveting or welding.

Inside the gearbox housing 2, between its bottom 3 and the

Cover a drive nut 6 over an angle range of 180 degrees

rotatably mounted, which carries a radially projecting crank arm 7 in which a crank pin 8 sits.

A thrust plate 9 engages the crank pin 8, which in turn is formed by two links 10 and 11 connected in series, which have a connecting joint 12 in common, which is held displaceably in a stationary guide 13 of the gear housing 2, for example in elongated holes or slots in the base 3 and in the cover. In Figures 1 to 3 of the drawing, the stationary guide 13 is only indicated by a dash-dotted line, whereby this extends in a straight line in the longitudinal direction of the gear housing 2.

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At the free end of the sliding plate 9 or the link 11 of the same, a gear 15 is mounted so as to be rotatable about a central axis 14, which on the one hand meshes with a toothing 16 which is located on the drive rod 17 which can be moved longitudinally in the gear housing 2 and along the faceplate 5. On the other hand, the gear 15 is constantly engaged in its circumferential area diametrically opposite the toothing 16 with a climbing toothing 18 which is arranged in a fixed position in the gear housing 2, for example on its rear frame or wall 4.

Crank arm 7 and push tab 9 together form a straight push crank 7/9, which can be moved from the drive nut 6, for example by a square drive pin of an operating hand lever or also a power drive. It is assumed that the drive nut 6 can be rotated in two successive switching steps, each extending over angular distances of 90, from a basic switching position according to Figure 1 to an intermediate switching position according to Figure 2 and again from the intermediate switching position according to Figure 2 to the final switching position according to Figure 3.

The straight-thrust crank 7/9 on the one hand and the gear 15, the toothing 16 and the climbing toothing 18 on the other hand are provided as intermediate gear elements between the drive nut 6 and the drive rod 17, which are not only intended to bring about the conversion of a rotary drive movement into a linear output movement. Rather, the intermediate gear elements also have the task of producing a relatively large total travel a for the drive rod 17 with a small installation depth for the actuating gear 1, which in turn is made up of two different partial travels b and c.

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The total travel ζ that can be achieved by turning the drive nut 6 by 180 degrees 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 η during the first 90-degree partial rotation of the drive nut 6 from the basic switching position according to Figure 1 to the intermediate switching position according to Figure 2 than during the second 90-degree partial rotation from the intermediate switching position according to Figure 2 to the final switching position according to Figure 3. In this case, only a partial travel y is traversed, which corresponds to a fraction, for example half, of the partial travel η.

The translation of the partial travels x and y produced by the straight-pull crank 7/9 as well as the total travel ζ into the partial travels b and c as well as the total travel a of the drive rod 17 is effected by the gear transmission 15/16/18 arranged downstream of the straight-pull crank 7/9, because the gear 15 rolls on the one hand in the stationary climbing gear 18 and on the other hand meshes with the gear 16 in the movable drive rod 17. The transmission ratio z:a is determined by the pitch circle radius of the diametrically opposite tooth sections of the gear 15, which are in engagement with the climbing gear 18 and the gear 16.

Since the embodiment of the actuating gear 1 according to Figures 1 to 3 uses a gear 15 with a circular rolling area that rotates centrally about the axis 14, the transmission ratio is z:a = 1:2.

Of course, the partial travels x:b and y:c are also subject to the same transmission ratios.

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From Figures 1 to 3 of the drawing it can be seen that the stationary guide 13 for the connecting joint 12 as well as the toothing 16 of the drive rod 17 and the climbing toothing 18 in the gear housing 2 of the actuating gear 1 extend parallel to its longitudinal direction. It can also be seen there that the gear 15 is toothed over its entire circumference and has only one pitch circle diameter.

In the embodiment of an actuating gear 1 shown in Figures 1 to 3, provisions have been made according to which the total length of the push plate 9 for the straight push 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 push plate 9 to each other is approximately 2:3. The shorter link 10 of the push plate 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.

In addition, precautions have been taken to ensure that the connecting joint 12 between the two links 10 and 11 of the push plate 9 in the intermediate switching position according to Fig. 2 lies on a connecting straight line through the crank pin 8 of the straight push crank 7/9 and through the axis of rotation 14 of the gear wheel 15.

In order to ensure that an operating hand lever, which can be coupled to the drive nut 6 via a square mandrel, can be connected to the gear housing 2 of the operating gear 1 without hindrance using screws that come into active connection with engagement holes 19 or threaded bushings 22 located therein, it has proven useful to design both links 10 and 11 of the sliding brackets 9 in such a way that they have a slightly curved or bent shape in the direction of their plane of movement. Their bending or curvature positions are aligned, as can be clearly seen from Figures 1 to 3 of the drawing.

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Since the holes 19 or threaded bushings 22 provided in the gear housing 2 must always remain free for the engagement of the connecting screws, it is also important that the fixed guide 13 for the connecting joint 12 of the sliding bracket 9 has a position offset sideways towards the faceplate 5 relative to the holes 19.

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 (Figure 1), in its end switching position the crank arm 7 rests against the rear frame or wall 4 of the gear housing 2 (Figure 3).

Figures 4 and 5 of the drawing show embodiments of an actuating gear 1 which differ from that according to Figures 1 to 3 in various respects.

Thus, in the gear transmission 15/16/18, a gear 15 is used 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. However, in contrast to the embodiment according to Figures 1 to 3, this gear 15 is mounted on the member 11 of the sliding plate 9 around an axis 14 arranged eccentrically to its circumference.

The eccentricity of the axis 14 to the circumference or pitch circle of the

The gearing is positioned in such a way that with the help of the gear 15 over the

on the one hand from the basic switching position and on the other hand from the

Intermediate switching position limited first partial travel

larger transmission ratio comes into effect than via the

second Tei1 travel, which is determined by the intermediate switching position and the end switching position.

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In the case of the actuating gear 1 according to Figures 4 and 5, it is also important for optimal operation that the stationary guide 13 of the gear housing 2 does not interact with the connecting joint 12 between the two links 10 and 11 of the push plate 9, but rather with guide webs 21 which are rigidly arranged on the link 11 of the push plate 9 which supports the gear 15. For this purpose, the outer boundary surfaces of the guide webs 21 are designed to be spherical or convex and engage in longitudinal slots on the base 3 and on the cover of the gear housing 2, which have a slightly curved course and form the stationary guide 13. It has proven to be useful, for example, if the lower part of the stationary guide 13 runs at an inclination of approximately 2 degrees relative to the longitudinal direction of the gear housing 2 and the upper part of the same adjoins this at an inclination of approximately 4 to 5 degrees.

In the actuating gear 1 according to Figures 4 and 5, the two links 10 and 11 of the push tab 9 also have a length ratio of approximately 1:1 to one another; however, the slightly curved or bent shape of the links 10 and 11 is also present there in order to avoid a collision with threaded bushings 22 into which fastening screws for the bearing rosette of an operating hand lever can be screwed.

The actuating gears 1 according to Figures 4 and 5 are identical in terms of their basic structure. However, while the actuating gear 1 according to Figure 4 is designed for a relatively small backset of 20 mm, the actuating gear 1 according to Figure 5 is equipped for a relatively large backset of e.g. 40 mm. The rear backset is the same in both cases and relatively small at less than 15 mm.

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In the actuating gear 1 according to Figure 4 with a small backset, the gear 15 meshes directly with a toothing 16 incorporated into the drive rod 17. In contrast to this, in the actuating gear 1 according to Figure 5 with a large backset, a bridging element 24 is positively engaged in the toothing 16 incorporated directly into the drive rod 17, which has a toothing 25 on its opposite longitudinal edge with which the gear 15 meshes. In this case, the bridging element 24 is provided with longitudinal guide grooves 26 which interact with guide webs 27 which are located on the inside of the base 3 and on the cover of the gear housing 2.

Deviating from the exemplary embodiments of actuating gears 1 shown in the drawing and described above, other designs are also possible.

For example, the gear 15 of the gear transmission 15/16/18 can also be provided with a non-circular, e.g. oval, rolling area and can mesh with racks 16 and 18 that are curved or run at an angle to the sliding direction of the drive rod 17.

However, the gear 15 can also have two toothings with different pitch circle diameters and be designed such that each of these toothings meshes with only one of the racks 16 and 18.

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In Figures 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 can be inserted into a recess 28 in the base 3 and in the cover of the gear housing 2 that is closely adapted to its profile. This profile locking cylinder acts on two additionally installed locking slides 29 and 30 within the gear housing 2 via its bit or driver attachment that can be rotated by key operation. The locking slide 29 is arranged and designed in such a way that it can be used to block the crank arm 7 against rotation in the basic switching position. The arrangement and design of the locking slide 30, on the other hand, are such that it can be used to directly block the drive rod 17 against displacement in its intermediate switching position. However, blocking of the actuating gear 1 over the partial travel from the intermediate switching position to the end switching position is not provided.

To block the crank arm 7 in the basic switching position of the actuating gear 1, the locking slide 29 is placed in its path of movement with a cam or a tongue 31. 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.

The locking slides 29 and 30 are designed and operatively connected to one another in such a way that they can only be moved sequentially 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 Figures 4 and 5. In the engaged operative position, the two locking slides 29 and 30 block one another, also under the influence of the leg spring 34, as long as the profile locking cylinder is not actuated.

Claims (12)

91 107 G Applicant: SIEGENIA-FRANK KG, Eisenhüttenstr. 22, 5900 Siegen, DE ANR: 1 004 808 PROTECTION CLAIMS 1. Actuating gear (1) for longitudinally movable drive rods (17) on fittings of windows and doors or similar, which -manually and/or can be brought into several different switching positions by power drive in order to be able to move the sash relative to the fixed frame from a locked closed position into several different opening positions, for example a tilt opening position and a parallel storage position or a rotary opening position and possibly also into a gap ventilation position, of which one opening position, primarily the tilt opening position or the parallel storage position, can be set by force - via arms that can be moved by the drive rod, wherein a drive member (6) rotatably mounted in a gear housing (2) is moved from a basic switching position (Figure 1) via at least one Intermediate switching position (Figure 2) can be rotated into an end switching position (Figure 3) and the end switching position has an angular distance of 180 degrees from the basic switching position, while the or an intermediate switching position is located at an angular distance of 90 degrees between the basic switching position and the end switching position, -2- -2- characterized, that the drive member (6) is held in a permanent drive connection with the drive rod (17) which is guided in a linearly displaceable manner in the gear housing (2) via intermediate gear members (7 to 18) which are designed for an unequal division of the total travel (a) of the drive rod (17) over the range from the basic switching position (Figure 1) to the intermediate switching position (Figure Z) and from the intermediate switching position (Figure 2) to the final switching position (Figure 3), that as intermediate gear members (7 to 18) on the one hand a straight-thrust crank (7/9) which can be actuated by the rotary drive member (6) and on the other hand a gear transmission (15/16/18) which meshes with the drive rod (17) are connected directly one behind the other, that furthermore a gear (15) of the gear transmission (15/16/18) meshing with a rack (16) of the drive rod (17) is mounted with its axis of rotation (14) on a thrust plate (9) of the straight-pull crank (7/9), and that finally this gear (15) is also in permanent engagement with a climbing toothing (18) provided in a fixed position in the transmission housing (2) in its peripheral area lying approximately diametrically opposite the point of engagement with the rack (16) of the drive rod (17). 2. Actuating gear according to claim 1, characterized in that the axis of rotation (14) on the gear (15) of the gear transmission (15/16/18) is arranged eccentrically to the circumference or pitch circle of its toothing (Figures 4 and 5) 3. Actuating gear according to claim 1 or 2, characterized in that the gear (15) has a circular rolling area and meshes with racks (16 and 18) aligned parallel to the sliding direction of the drive rod (17). -3- -3- 4. Actuating gear according to claim 1 or 2, characterized in that the gear (15) has a non-circular, e.g. oval, rolling area and meshes with racks that are curved or run at an angle to the sliding direction of the drive rod (17). 5. Actuating gear according to claim 1 and 3, characterized in that the gear (15) of the gear transmission (15/16/18) has two toothings with different diameters and each toothing meshes with only one of the racks (16 and 18). 6. Actuating gear according to claim 1 and at least one of claims 2 to 5, characterized, that the push tab (9) of the straight push crank (7/9) consists of two links (10 and 11) connected in series, the common connecting joint (12) of which is constantly held displaceably in a stationary guide (13) of the gear housing (2). 7. Actuating gear according to claim 6,
characterized, that the stationary guide (13) extends in the gear housing (2) approximately parallel to the direction of displacement of the drive rod (17) and/or has a course or a position in which the connecting joint (12) accommodated therein between the two push-link members (10 and 11) lies approximately on a connecting line through the crank pin (8) of the straight push crank (7/9) and through the axis of rotation (14) of the gear wheel (15) of the push-link (9) (Fig. 2). -4- -4- 8. Actuating gear according to one of claims 1, 6 and 7, characterized in that the total length of the push tab (9) for the straight push crank (7/9) has a ratio of approximately 5:1 to the crank radius of the drive member (6) and the lengths of the two members (10 and 11) of the push tab (9) have a ratio of approximately 2:3 to one another. 9. Actuating gear according to claim 8, characterized in that the shorter member (10) of the push tab (9) is assigned to the drive member (6) and the longer member (11) thereof is assigned to the gear wheel (15). 10. Actuating gear according to one of claims 1 and 6 to 9, characterized in that both members (10 and 11) of the sliding tab (9) have a slightly curved or bent shape in the direction of their plane of movement, their bent or curved position being aligned. 11. Actuating gear according to claim 1 and at least one of claims 7 to 9, characterized in that the crank pin (8) of the drive member (6) of the straight-thrust crank (7/9) assumes an over-dead center position in its end switching position (Figure 3), while the crank pin (8) has an under-dead center position when the drive member (6) is in the basic switching position (Figure 1) and supported. -5- -5- 12. Actuating gear according to claim 1 and at least one of claims 2 to 5,
characterized, that the push tab (9) of the straight push crank (7/9) consists of two links (10 and 11) connected in series, which have a common connecting joint (12), whereby the link (11) assigned to the gear (15) of the gear transmission (15/16/18) is held displaceably along a stationary guide (13) in the transmission housing (2) (21), which runs slightly curved and/or obliquely with respect to the direction of thrust of the drive rod (17) (Figures 4 and 5).