EP0545899A2 - Sliding bar lock - Google Patents

Abstract

In an espagnolette lock, the espagnolette is moved by a lock cylinder between an opening position and a closing position, and vice versa, by means of a reduction gear. There is proposed a coupling of the reduction gear to the espagnolette which makes it possible, when the lock cylinder is rotated through 2 x 360 DEG , to displace the espagnolette from the opening position into the closing position and to block the espagnolette against displacement in the closing position, without a torque being introduced into the reduction gear and therefore into the lock cylinder by the blocking forces. <IMAGE>

Description

The invention relates to a connecting rod lock comprising a connecting rod which can be displaced between an open position and a closed position in connection with at least one closing element.
a lock cylinder,
a reduction gear between the lock cylinder and the drive rod for moving the drive rod between the open position and the closed position
and
a locking device for the drive rod, which locks the drive rod in the closed position against displacement in the direction of the open position without introducing torque into the reduction gear,
a control cam assembly for drive engagement in a cam engagement profiling of the drive rod on a transmission output drive rod drive pinion is appropriate
and
wherein, furthermore, a stop cam for engaging on an abutment surface of the drive rod is attached to the drive rod drive pinion on the transmission output side.

Such an espagnolette lock is known from European laid-open specification 0 l68 001. Reference is made there in particular to the illustration in FIG. 8 and to the parts of the description associated with FIG. 8.

In the known embodiment, a single control cam is attached to the drive rod drive pinion, which is in drive engagement with the drive rod for a single recess in the drive rod. Furthermore, in the known embodiment, a stop cam is attached to the drive rod drive pinion, which comes into engagement in a further recess of the drive rod when the drive rod is in its open position, so that the drive rod, which is in the open position and loads towards its closed position is supported exclusively via the stop cam in the recess of the drive rod associated therewith, without substantial supporting forces being introduced into the reduction gear.

In the known embodiment, to move the drive rod from the open position into the closed position, the locking cylinder is rotated 2 × 360 ^°, starting from a zero or key withdrawal position of the locking cylinder. In order to then block the drive rod in its locking position reached after this rotation by 2 x 360 ^o , the locking cylinder is rotated further by 360 ^o ; during this further rotation by a further 360 ^° , the stop cam then comes into the recess in the drive rod provided for it with the drive rod at a standstill.

It is perceived as uncomfortable that to lock the drive rod, after its locking position has already been reached by turning the lock cylinder twice by 360 ^° , another lock cylinder rotation by another 360 ^° must be carried out.

The invention has for its object to provide a drive rod lock of the type mentioned a structurally simpler or at least consistently simple construction that allows the transition from the open position of the drive rod to the blocking of the drive rod in the closed position with a lower number of revolutions on the lock cylinder to be able to perform.

• a) die Nockeneingriffsprofilierung mit zwei Ausnehmungen ausgeführt ist;
• b) die Antriebsnockenbaugruppe zwei auf dem Treibstangenantriebsritzel angebrachte Steuernocken aufweist, welche sukzessive in ihnen paarweise zugeordnete Ausnehmungen eingreifen;
• c) der Anschlagnocken im mittleren Bereich des Umfangsabstands zwischen den beiden Steuernocken auf dem Treibstangenantriebsritzel angeordnet ist;
• d) die in der Verschlußstellung der Treibstange steuernockenbeaufschlagte Ausnehmung mit einem Begrenzungsfinger ausgeführt ist;
• e) der Anschlagnocken in der Schließstellung der Treibstange an dem Begrenzungsfinger auf dessen von der steuernockenbeaufschlagten Ausnehmung ferner Flanke, im folgenden genannt Sperrflanke, anliegt;
• f) die Treibstange ihre Schließstellung erreicht, bevor die Schließdrehbewegung des Schließzylinders und des Treibstangenantriebsritzels beendet ist, und der Anschlagnocken nach Eintritt der Treibstange in die Schließstellung während der dann noch verfügbaren restlichen Schließdrehbewegung des Schließzylinders und des Treibstangenantriebsritzels seine Sperrstellung an der Sperrflanke des Begrenzungsfingers erreicht.

To solve this problem, the invention proposes that

• a) the cam engagement profiling is carried out with two recesses;
• b) the drive cam assembly has two control cams mounted on the drive rod drive pinion, which successively engage recesses assigned to them in pairs;
• c) the stop cam is arranged in the central region of the circumferential distance between the two control cams on the drive rod drive pinion;
• d) the recess, which is acted upon by cam control in the closed position of the drive rod, is designed with a limiting finger;
• e) the stop cam in the closed position of the drive rod rests on the limiting finger on the flank of the control cam-actuated recess, hereinafter referred to as the locking flank;
• f) the drive rod reaches its closed position before the closing rotary movement of the lock cylinder and Espagnolette drive pinion is finished, and the stop cam reaches its locking position on the locking flank of the limiting finger after the input of the driving rod in the closed position during the remaining closing rotary movement of the locking cylinder and the driving rod drive pinion still available.

In the embodiment of the espagnolette lock according to the invention, it is in particular possible that the espagnolette, starting from the open position and accordingly from a zero position (key withdrawal position) of the lock cylinder, reaches its lock position after less than 2 x 360 ^o lock cylinder rotation, and that the remaining lock cylinder rotation corresponds to the rest up to 2 x 360 ^o serves to retract the stop cam in the locking position opposite the locking flank of the limiting finger.

Although in the solution according to the invention a transition from the open position of the drive rod to the blocked state of the drive rod in the closed position can be achieved with only two lock cylinder rotations, the forces occurring within the lock can be kept low and the torque expenditure to be applied to the lock cylinder also remains low.

In order to provide a measure of a preferred design of the reduction ratio within the driving rod lock, be said that the drive rod drive pinion ^o a closing rotating movement of about 200 performs ^o during a closing rotating movement of the lock cylinder of 2 x 360th This closing rotational movement of the drive rod drive pinion is used, on the one hand, to shift the drive rod from the open position into the closed position and, on the other hand, to lock the drive rod in the closed position in that the stop cam runs onto the locking flank of the limiting finger. The remaining closing rotational movement of the drive rod drive pinion after the drive rod has entered the closed position must be small, for example approximately 20 ^° . This shows that for the movement of the drive rod from the open position to the closed position, the vast majority of the lock cylinder travel of 2 x 360 ^o is available; the latter is responsible for a favorable transmission ratio between the movement of the lock cylinder on the one hand and the drive rod on the other hand and thus for low gear forces during the opening and closing movement of the drive rod and for low torque expenditure on the lock cylinder.

The control cams and the stop cams can project axially with respect to a simple construction from an end face of the drive rod drive pinion, in which case a part of the drive rod carrying the recesses can rest against this end face of the drive rod drive pinion.

Particularly favorable forces and conditions of movement in the lock result when the control cams have a circumferential distance of approximately 90 ° and when the circumferential distance of the stop cam from the two control cams is approximately 135 ^o each. It should be noted here that these angular distances are calculated from the center of the cam to the center of the cam.

For reasons of stability, it is advantageous if the control cams are connected to one another by a web while maintaining a recess between them for the engagement of a projection lying between the two recesses.

The espagnolette lock according to the invention can be produced in particular in the form that a transom movable to the direction of movement of the espagnolette or Main bolt is provided and is displaceable between a retracted position and an extended position by the drive rod. In such an embodiment with a bolt, the bolt can be driven from the drive rod in such a way that a stationary angular lever is connected to a first arm by a pin-slot connection to a bolt tail of the bolt, and that a second arm of the angle lever , namely a control arm with a control profile of the drive rod is engaged. In this case, the control profile can have control surfaces at right angles to the direction of movement of the bolt for extending and retracting the bolt and an end surface which is essentially parallel to the direction of movement of the drive rod for locking the extended bolt.

Additional locking of the extended latch can be accomplished by attaching a shoulder to the latch and a shoulder engaging pin on the drive rod, the shoulder engaging pin engaging behind the shoulder after the latch has reached its fully extended position. Due to the simultaneous engagement of the control arm with the end face of the control profile on the one hand and the shoulder with the shoulder engagement pin on the other hand, an extremely stable blocking against a violent pushing in of the bolt is achieved, the supporting forces being distributed within the lock in such a way that there is no fear of damage to the furnishings is.

The espagnolette lock can also be equipped with at least one pivot bolt which can be pivoted between a pivoted-in and a pivoted-out position by the drive rod. In a further development of the invention, a toothed rack can be attached to the drive rod for pivoting the swivel bolt, and accordingly a toothed segment can be attached to the swivel bolt.

This toothed segment can be attached to a hub part of the hook-shaped swivel bolt.

The swivel bolt itself can be part of an additional lock attached to a faceplate of the lock.

The lock designed according to the invention can further be equipped with a latch which, in a known manner, automatically engages in a striking plate when the door equipped with the lock slams shut. This case is biased in a conventional manner under spring pressure into a closed position and can be pulled back into an open position either by turning a follower nut or from the lock cylinder. In a further development of the invention, a driver can be attached to the drive rod drive pinion, which, when the locking cylinder is rotated, strikes beyond its zero position corresponding to the open position of the drive rod, against a nose of a drop lever acting on the latch.

The latch can basically be of the usual prismatic design, that is to say that the latch in a sectional plane perpendicular to the door lock plane and parallel to the direction of movement of the latch has a triangular cross-section with a latch start slope and a latch latch flank, and furthermore that the latch is essentially parallel to this sectional plane having. With such a design of the trap it has been shown that unauthorized attempts to open it are possible in such a way that a flat bar or a plate is inserted into the space between the striking plate and the faceplate and is moved obliquely such that it acts with an edge on a trap edge, which is formed by the trap ramp on the one hand and one of the end faces on the other. The trap can then be pushed back in this way. In order to prevent such a pushing back of the trap, it is further proposed that in the through the end faces and recesses are provided by the edge areas formed by the latch stop, which lie close to the outer face surface when the latch is extended. If a flat bar or a sheet is then used in the manner described above for an unauthorized attempt to open, the edge of the flat bar or sheet that runs onto the trap hooks on the recess of the edge of the case, so that the case is pushed back after a short Path comes to a standstill and remains blocked.

The above-mentioned design of the latch should enjoy protection regardless of the features of the espagnolette lock discussed above.

The recesses on the trap can in particular be designed as grooves which run parallel to the outer surface of the faceplate and, in the presence of trap guide ribs running along the latch latch flank and along the end surfaces of the trap, end in front of or on these trap guide ribs. The trap guide ribs thus remain intact and there is no danger that they will get caught in the guides of the cuff when the trap is pulled back.

According to another aspect of the invention, the starting point is a connecting rod lock comprising a connecting rod which can be displaced between an open position and a closed position in connection with at least one closing element,
a lock cylinder,
a reduction gear between the lock cylinder and the drive rod for moving the drive rod between the open position and the closed position,
wherein the reduction gear on the lock cylinder side has a toothed ring which meshes with two output gears arranged downstream of it and has a slot designed to insert the locking bar of the lock cylinder and is open towards the edge, and wherein a drive rod drive member of the reduction gear rotatable about a fixed axis acts on the drive rod via a driving device ,
further comprehensive
a bolt which can be moved transversely to the longitudinal axis of the drive rod between a retracted position and an extended position and can be driven from the drive rod by means of movement conversion means,
more comprehensive
a case biased by spring force into a closed position, which can be retracted against the spring force from a follower and from the lock cylinder, the slot of the ring gear being adjustable from its zero degree position in at least one direction of rotation over a variation angle range of the lock bit, without the bolt being adjusted.

Such a drive rod lap is known from DE-PS 29 19 201.

In the known espagnolette lock, the adjustment of the slide bolt is when pivoting of the slot of the ring gear from its zero degree position by the variation angle range of the locking bar enables that the movement conversion means between the bolt and the drive rod are formed by an oblique slot of the drive rod and a slot follower bolt of the slide bolt and that the oblique slot of the drive rod by a extending in the direction of movement of the drive rod Niche is added, in which the pin of the slide bolt has entered in the closed end position of the slide bolt, and has axial play.

In this known solution, the trap is driven by the drive rod. To retrieve the trap, the drive rod is moved from the locking cylinder and takes the trap back with it, the slide bolt standing still in the niche thanks to the play of its pin. This embodiment is burdened with considerable disadvantages: to retract the trap, the drive rod must always be moved. This means additional effort and additional wear and tear in the espagnolette lock and requires additional adjustment of the frame-side locking plates in order to grant the espagnolette-side locking elements a corresponding movement play during the espagnolette movement necessary for the latch retraction. Another disadvantage is that in the open position of the lock when the lock cylinder is set to the key withdrawal position and the key removed, an action on the drive rod, for example as part of an attempted break-in, can lead to a reaction via the gearbox to the lock cylinder, with the result that the tumblers of the Lock cylinder be loaded.

The invention has for its object to find a solution while maintaining the variation angle range for the lock cylinder bit and while maintaining the immobility of the slide bolt when adjusting the lock cylinder bar within this variation angle range, in which effects on the drive rod in the open position do not lead to the lock cylinder load and the drive rod when Retrieving the latch from the lock cylinder stands still.

To solve this problem, it is proposed that a cam assembly attached to the drive rod drive member with two control cams and a stop cam and a cam engagement profile attached to the drive rod with two recesses associated with the control cams and two limiting fingers be formed on both sides of the recesses in such a way that when the toothed ring is rotated within the variation angle range of the locking bar, the driving connection of the control cam responsible for the start of the drive rod displacement from the open position into the closed position with the associated recess is released and the limiting finger associated with this recess interferes with the displacement of the drive rod between the stop cams and the axis of the drive rod drive member in a substantially blocking manner,
and that the trap is retractable by a driver of the drive rod drive member.

The movement conversion means between the bolt and the drive rod can comprise a conversion lever pivotally mounted on the lock housing, which on the one hand engages with the drive rod in a tooth-like manner and on the other hand is connected to the bolt by a pin / slot connection.

In order to achieve the transmission ratio between the drive rod and the bolt corresponding to a two-speed rotation of the lock cylinder core in order to achieve the smallest possible space requirement, in particular with regard to the distance of the faceplate from the lock cylinder and the follower nut, it can be provided that the tooth-like engagement between the drive rod and the Transfer lever has lost motion.

According to a first embodiment of the transfer lever solution, it is provided that the transfer lever is a double lever, which is in engagement with a counter cam with a toothing of the drive rod and has a slot in an arm, which feeds in a pin of the bolt. In this case, the toothing can have two drive cams spaced apart by a lost motion, namely a bolt-extending drive cam and a bolt-retracting drive cam.

According to another embodiment of the transfer lever solution it is provided that the tooth-like engagement between the drive rod and the transfer lever is formed by a nose of the drive rod on the one hand and two teeth of the transfer lever separated by a tooth notch on the other hand and that the transfer lever has a latch engagement arm which with a pin in an elongated hole of the bolt engages. The tooth notch can be designed as a tooth notch which guarantees lost motion.

Fig. 1

eine Ansicht, teilweise aufgebrochen, eines erfindungsgemäßen Treibstangenschlosses in der Öffnungsstellung;

Fig. 1a

eine Vergrößerung zu Fig. 1;

Fig. 2

eine Ansicht entsprechend Fig. 1 in der Verschlußstellung der Treibstange;

Fig. 3

eine Ansicht entsprechend Fig. 1 bei Rückziehung der Falle durch Drehen des Schließzylinders;

Fig. 4

ein Zusatzschloß mit einem Schwenkriegel;

Fig. 5

eine Stulpschienentreibstangeneinheit mit einem erfindungsgemäßen Treibstangenschloß und zwei Zusatzschlössern;

Fig. 6

eine Anordnung entsprechend Fig. 5 mit gegenläufigen Schwenkriegeln;

Fig. 7

eine Anordnung entsprechend Fig. 5 mit abgewandelten Schwenkriegeln;

Fig. 8

eine Anordnung entsprechend Fig. 5 mit an der Treibstange starr befestigten Schließkloben;

Fig. 9

eine Anordnung entsprechend Fig. 1 mit einer abgewandelten Gestaltung der Falle;

Fig. 10

eine Draufsicht auf die Falle in Pfeilrichtunng X der Fig. 9;

Fig. ll

eine Ausführungsform entsprechend den Figuren l und la in einem Getriebezustand, in dem sich der Schließbart in der Nullgradstellung befindet und der Schlüssel gesteckt und gezogen werden kann;

Fig. l2

den Beginn des Fallenrückzugs bei der Ausführungsform nach Figur ll in einer anderen Schnittebene;

Fig. l3

eine Abwandlung zur Ausführungsform nach Figur ll unter Verwendung eines Schließzylinders mit einem in der Schlüsselabzugsstellung unter einem Winkel von - 90^o seitlich abstehenden Schließbart;

Fig. l4

eine Abwandlung zu Figur ll mit einem in der Schlüsselabzugsstellung unter + 30^o seitlich abstehenden Schließbart;

Fig. l5

ein Schloß gemäß Figur ll bei vorgeschlossenen Schubriegel und

Fig. 16 und 17

weitere Ausführungsformen für die getriebliche Verbindung zwischen der Treibstange und dem Riegel.

The accompanying figures explain the invention using exemplary embodiments. They represent:

Fig. 1

a view, partly broken away, of an espagnolette lock according to the invention in the open position;

Fig. 1a

an enlargement to Fig. 1;

Fig. 2

a view corresponding to Figure 1 in the closed position of the drive rod.

Fig. 3

a view corresponding to Figure 1 when retracting the trap by turning the lock cylinder.

Fig. 4

an additional lock with a swivel bolt;

Fig. 5

a faceplate drive rod unit with an inventive drive rod lock and two additional locks;

Fig. 6

an arrangement corresponding to Figure 5 with counter-rotating swivel bolts.

Fig. 7

an arrangement corresponding to Figure 5 with modified swivel bolts.

Fig. 8

an arrangement corresponding to FIG 5 with the locking rod rigidly attached to the drive rod.

Fig. 9

an arrangement corresponding to Figure 1 with a modified design of the trap.

Fig. 10

a plan view of the trap in arrow direction X of Fig. 9;

Fig. Ll

an embodiment according to Figures l and la in a gear state, in which the lock bit is in the zero degree position and the key can be inserted and removed;

Fig. L2

the beginning of the retraction of the trap in the embodiment according to FIG. 11 in a different sectional plane;

Fig. L3

a modification of the embodiment according to Figure II using a lock cylinder with a lock bit protruding laterally in the key withdrawal position at an angle of - 90 ^o ;

Fig. 14

a modification to Figure 11 with a locking bit which projects laterally in the key withdrawal position below + 30 ^o ;

Fig. L5

a lock according to Figure ll with pre-closed slide bolt and

16 and 17

further embodiments for the gear connection between the drive rod and the bolt.

As shown in FIGS. 1 and 1a, the lock bit hub (not shown) of the profile cylinder 1 is surrounded by a ring gear 10 which has a slot 2 for the coupling with the lock bit, the turning circle diameter of the lock bit in the region of the two driven gear wheels 12, 12 is smaller than the root diameter of the ring gear 10. The ring gear 10 is guided with a flange on the outer circumference in a bearing 14 fixed to the housing and meshes with the two driven gear wheels 12, 12 '.

The locking and unlocking actuation of the drive rod 16 and the bolt 18 is carried out by two Rotations of the locking cylinder 1. At the end of a reduction gear A, which is formed by the gear wheels 10, 12 - 12 ', 13 and 15, a drive rod drive pinion 20 is mounted with a control element 22 which is fixedly arranged on the front face of the lock cover. The control element 22 is formed at both ends with approximately circularly shaped control cams 24, 24 'which, when actuated by the locking cylinder, engage successively in corresponding recesses 26, 26' of the drive rod 16 and displace them.

A stop cam 28 is also formed diametrically with respect to the control element 22 on the end face of the pinion 20 on the lock cover side. The recesses 26, 26 'of the drive rod 16 for the engagement of the control cams 24, 24' are delimited on the outer sides by curved limiting fingers 30, 30 'directed into the lock interior, which extend approximately up to the axis of rotation 32 of the drive rod drive pinion 20.

With the drive rod 16 moved in the closed position (FIG. 2), the upper limiting finger 30 is moved under the stop cams 28. With restoring forces acting on the drive rod 16 in this position, the limiting finger 30 is supported on the stop cam 28, as a result of which these forces are introduced into the axis 32 of the drive rod drive pinion 20. The restoring forces are therefore not transmitted as torque to the transmission A and to the lock cylinder 1.

On the axis 34 of the gear wheel 12 arranged near the drive rod 16, an angle lever 35 is pivotally mounted coaxially thereto, which partially engages over a bolt tail 36. With a fork-like arm 38, it comprises a pin 40. A second arm 50 of the angle lever 35 projects into a drive rod recess 42 of the drive rod 16, which has rectangular control surfaces 44, 44 'provided cams 46, 46' is limited.

When the drive rod 16 and the latch 18 are excluded, the lower control surface 44 of the upper cam 46 comes to bear against the second arm 50 of the angle lever 35 and pivots it counterclockwise into the position according to FIG. 2. By means of the pin-slot connection 38, 40 the bar is excluded. After double closing rotation of the profile cylinder 1, the latch 18 is fully extended, and the arm 50 is then supported on the end face 52 of the upper cam 46 (FIG. 2). At the same time, a pin 54 (FIG. 2) which is fixed to the connecting rod is pushed behind a shoulder 56 of the bolt 18.

If an attempt is now made to push the bolt back into the lock housing, then the forces which occur are introduced via the bolt pin 40 into the angle lever 35 and attempt to pivot the angle lever clockwise. However, since the free end 50 of the angle lever 35 is supported on the upper cam 46, the pivoting movement is blocked. Due to the pin 54 pushed behind the shoulder 56 at the same time, the forces acting on the bolt 18 are also transmitted to the drive rod 16 (effective direction of the force in the plane of the drawing to the right), which in turn is in the opposite direction from the arm 50 of the angle lever 35 (effective direction of the Counterforce to the left) is supported. The transmission and locking cylinder are thus relieved of the forces mentioned.

The latch control of the latch 78 (FIG. 3) can be carried out from the follower 80 of a door handle and / or from the lock cylinder 1. The latch tail 58 is fastened in a housing 64 which can be displaced between the lock base 60 and the lock cover 62, the housing 64 having two opposite longitudinal slots 66, 66 'for guiding on its broad sides, into each of which engage short guide pins 68, 68 'arranged on the lock base 60 and on the lock cover 62. In Fig. 1 the lock cover 62 is shown broken and only the guide pin 68 'attached to the lock base 60 is visible. The latch tail 58 is fastened to the rear wall 70 of the housing 64 with a screw 72, which can be loosened for the purpose of changing the latch for right / left stop. In the narrow rear wall 74 of the lock face plate 3, an opening 76 is provided for the tool passage for access to the screw 72. The latch 78 is pulled out of the lock faceplate until it can be turned by 180 ^o .

When pulling the case 78 by the door handle, the latch nut is ^o pivots 80 to about 45 in the clockwise direction and integrally molded on the handle follower 80 catch 82 engages behind a shoulder 84 of the housing 64. The spindle hole 80 is carried toward the extended latch 78 a compression spring 88 inserted into a spring housing 86 is prestressed, the displaceable spring housing 86 engaging with a plunger 90 in a recess 92 of the follower nut 80. In the normal position, the follower nut 80 is supported on a pin 94 connecting the lock base 60 and the lock cover 62.

For the latch actuation by means of the lock cylinder 1, a latch lever 96 is pivotally arranged on the lock bottom 60 coaxially with the connecting rod drive pinion 20 and rests with its free end 98 on the housing 64. The gear connection to the latch lever 96 comprises a driver 100 arranged on the end face of the drive rod pinion 20 on the lock bottom side, which comes into contact with a catch 102 of the latch lever 96 when the bolt 18 is locked and the lock cylinder is rotated further clockwise and pivots the latter in a clockwise direction.

FIGS. 4, 5 and 6 show an additional lock 104 which is provided for multiple locking and which is equipped with a hook-shaped swivel bolt 106. The drive rod 16 is guided in the area of the additional lock 104 with its narrow side on the faceplate 3 and bent in such a way that it bears directly against the lock ceiling. On the broad side of the drive rod 16 facing away from the lock cover, a toothed rack 108 is fastened (riveted) within the additional lock, which meshes with a toothed segment 110 formed on the swivel bolt 106. The extended swivel bolt 106 engages in a striking plate 112 on the frame in a known manner.

In FIG. 6, the hook-shaped swivel bolts 106 are arranged in opposite directions compared to the arrangement according to FIG. 5.

In FIG. 7, the additional bolts are designed as known, pivotable bolt tongues 114 and in FIG. 8 as locking blocks 116.

The different functions of the espagnolette lock are as follows:
In Figures 1 and 1a, the lock cylinder 1 is in the zero position in which the key can be inserted and removed. The latch 78 is in the projecting position, in which it can snap into a striking plate when the door equipped with the lock is pressed shut. This trap is biased into the projecting position by a latch spring 59 (see FIG. 1a). The drive rod 16 is in Fig. 1 and 1a in the open position, ie the highest possible position at all. The latch 18 is in the retracted position.

To transfer the drive rod 16 into the closed position, the lock cylinder is rotated counterclockwise by means of the inserted key. The gear A is driven via the ring gear 10, so that the drive rod drive pinion 20 also rotates counterclockwise. The control cam 24 engages in the recess 26 'of the drive rod 16 and presses the drive rod down towards the closed position. In the course of the further rotation of the locking cylinder in the counterclockwise direction, the control cam 24 'comes into engagement with the recess 26 of the drive rod 16, while the control cam 24 emerges from the recess 26'.

After a lock cylinder rotation of 2 × 360 ^° , the state according to FIG. 2 is reached, in which the drive rod 16 has reached its closed position, ie its lowest position. The stop cam 28 bears against the locking flank 31 of the limiting finger 30, so that in an attempt to push the drive rod 16 upward, the limit finger 30 abuts against the stop cam 28 and an upward displacement of the drive rod 16 is thus blocked. The blocking force is introduced in the radial direction with respect to the drive rod drive wheel 20 directly into the axis of rotation 32 of the drive rod drive pinion 20 and does not act as a torque which is introduced into the reduction gear A.

The drive rod 16 has already reached its closed position shown in FIG. 2 before the stop cam 28 has stepped over the limiting finger 30. This results from FIG. 2 and there in particular from the position of the control cam 24 'relative to the projection 25 located between the two recesses 26 and 26'. It can be seen there that the drive rod 16 no longer performs a downward movement even before the control cam 24 'has reached the position shown in FIG. 2. This means, that the stop cam 28 runs with the drive rod at a standstill over the limiting finger 30 and thus reaches the position shown in FIG. 2.

During the downward movement of the drive rod 16 from the position according to FIG. 1 into the closed position according to FIG. 2, the control surface 44 of the cam 46 hits the second arm 50 of the angle lever 35 and rotates it counterclockwise, so that the pin-slot connection 38 , 40 the bolt tail 36 and thus the bolt 18 is moved to the left into its closed position. The beginning of this shift depends on the position of the control surface 44 with respect to the axis 34 of the angle lever 35. As a result of the pivoting of the angle lever 35, the second arm 50 of the angle lever 35 then finally reaches the end face 52 of the cam 46. Then a further pivoting of the angle lever 35 in the counterclockwise direction no longer occurs, even if the drive rod 16 is moved further downward. However, it is no longer possible to push the bolt 18 back, because such a pushing back of the bolt 18 would result in a pivoting of the angle lever 35 in a clockwise direction, which is prevented by the second arm 50 resting against the end face 52. The drive rod 16 is driven further down by the locking cylinder 1 after the bolt 18 has already reached its fully extended end position. As shown in FIG. 2, the pin 54 of the drive rod 16 passes behind the shoulder 56 of the bolt 18. Then the bolt 18 is also prevented from being pushed back by the pin 54. The drive rod 16 is stabilized in the region of the pin 54 in that it rests with the end face 52 of the cam 46 on the second arm 50 of the angle lever 35, which in turn is supported by the pin-slot connection 38, 40.

During the downward movement of the drive rod 16 from the open position according to FIGS. 1 and 1a into the closed position according to FIG. 2, the pivot bolt 106 is also pivoted out in the counterclockwise direction, as shown in FIG. 4, in that the toothed rack 108 on the toothed segment 110 of the pivot bolt 106 rolls.

When the drive rod 16 is returned from the closed position according to FIG. 2 into the open position according to FIGS. 1 and 1a, the upward movement of the drive rod 16 begins, as can be seen from FIG. 2, only after the stop cam 28 has left the locking flank 31 of the limiting finger 30 again because the control cam 24 'only comes into engagement with the upper flank of the recess 26 formed by the limiting finger 30 after an initial rotation of the connecting rod drive pinion 20. The state according to FIGS. 1 and 1a is then reached again by further turning the locking cylinder clockwise.

If to be withdrawn from the starting condition of FIG. 1 and 1a, the latch 78, the lock cylinder 1 is rotated by about 45 ^o clockwise. 3, the driver 100, which is mounted on the side of the drive rod drive pinion 20 facing away from the control cam 24, 24 ', engages with the nose 102 of the latch lever 96 with the result that the latch lever 96 in Is pivoted clockwise and pushes the latch 78 back over the housing 64. It should be noted that during the transition from the position according to FIGS. 1 and 1a on the one hand to the position according to FIG. 3 on the other hand the control cam 24 does not carry out a driving movement on the drive rod 16 since it with the flank of the recess 26 'formed by the projection 25 does not come into contact with driving. There is therefore no movement of the drive rod 16 when the latch 78 is withdrawn from the locking cylinder.

9 and 10, the latch 78 has in its end faces 79 grooves 118 which run just outside the faceplate 3 parallel to the faceplate 3 and end at the guide ribs through which the case is guided in an opening in the faceplate. If pressure is exerted on the edge 83 with a flat bar or sheet metal in order to push the latch back, this flat bar gets into the groove 118 and prevents the latch 78 from further retracting.

The distance of the groove 118 from the outside of the faceplate 3 is approximately 1 mm when the case 78 is fully extended.

A further aspect of the invention is now dealt with below with reference to FIGS. 11 to 15. Analog parts are numbered in FIGS. 11 to 15 with the same reference numerals as in FIGS. 1 to 3.

In Figure ll, the lock bit la is in the zero degree position. It is assumed that the key can be inserted and removed in this zero degree position. The ring gear 10 is also in the zero degree position with its gap 2.

The position of a transmission output gear or drive rod drive pinion 20 is defined via the gears l2, l3 and l5. The transmission output gear 20 has 22 cams 24 and 24 'in a dumbbell-shaped arrangement. The cams 24 and 24 'are intended for engagement with a special profile P on a drive rod 16. The drive rod l6 is connected to drive rod sections l6a and l6b for common movement in the vertical direction. There are two recesses 26 and 26 'in the special profile P. Furthermore, the special profile P has two limiting fingers 30 and 30 '. A stop cam 28 is also attached to the transmission output gear 20.

The displacement of the drive rod 16 in the vertical direction is brought about by the fact that when the transmission output gear 20 is rotated, the cam 24 first engages in the recess 26 'and later the cam 24' engages in the recess 26. The reverse process takes place if the drive rod 16 is to be pushed back upwards by turning the gear output wheel 20 counterclockwise.

In the position of the drive rod 16 shown in FIG. 11, the latch parts (not shown) attached to the drive rod sections 16a and 16b do not engage in latch engagement elements of the door frame (likewise not shown). In contrast, such an engagement takes place in the lowest position of the drive rod 16.

A latch 18 is also provided. This latch 18 can be extended, as shown in Figure 15.

To close the bolt 18, a transfer lever 35 (angle lever) is provided. This transfer lever 35 pivots about an axis 34. The upper end of the transfer lever 35 is connected to the bolt 18 by a slot 38a and a pin 40.

Two drive cams 46, 46 'are attached to the drive rod 16. These drive cams 46, 46 'interact with a counter cam 50 of the transfer lever 35. A recess 42 is provided between the two drive cams 46 and 46 '.

In the unlocked state shown in FIG. 11, the drive cam 46 'bears against the counter cam 50, so that the transfer lever 35 is prevented from pivoting counterclockwise about the axis 34. If the Driving rod 16 is moved downward by turning the gear output gear 20 counterclockwise (turning is initiated by the locking cylinder via the gear wheels 12, 13 and 15), the recess 42 first moves over the counter cam 50 and then the drive cam 46 runs on the counter cam 50 on. During the free immersion of the counter cam 50 in the recess 42, the position of the transfer lever 35 is not clearly determined. It can oscillate and, accordingly, the bolt 18 can freely move back and forth.

When the drive cam 46 runs on the counter cam 50, the transfer lever 35 is pivoted counterclockwise about the axis 34 and begins to move the bolt 18 to the left in the direction of the position shown in FIG. Even during the beginning pivoting of the transfer lever 35 in the counterclockwise direction, the position of the transfer lever 35 has not yet been clearly established. The transfer lever 35 can still swing. Only when the drive cam 46 has come into engagement with the counter cam 50 with its vertically running edge is the transfer lever 35 prevented from oscillating and the latch 18 is locked in its extreme left position (see FIG. 15). Then the lock is locked.

The bolt 18 is retracted when the drive rod 16 moves upwards, the counter cam 50 passing through the recess 42, the flank 50 a being hit by the drive cam 46 and finally the drive cam 46 ′ again resting on the counter cam 50, as shown in FIG. 11. In the intermediate positions, the transfer lever 35 can also oscillate again and accordingly the bolt 18 can move in an uncontrolled manner in the horizontal direction.

The retraction of the latch 78 results from FIG. 12. The lockable 1a and with it the slot 2 of the ring gear 10 are so far in an approximately + 30 ° position that the trap 78 retreat can begin. A driver 20a is attached to the transmission output gear 20, as can be seen from FIG. This driver 20a is located on the underside of the transmission output gear 20 and therefore does not appear in FIG. The driver 20a is intended to cooperate with an expression 96a which is attached to a latch lever 96. The latch lever 96 is pivotable about the axis 32 of the transmission output wheel 20 and acts with its upper end on a latch tail 58, 64, which is also under the force of a spring 59.

When the ring gear l0 with the lock bit la has reached the + 30 ^o position shown in FIG. 12, the transmission output gear 20 has rotated so far that the driver 20a strikes the recess 96a. With further rotation of the transmission output gear 20 clockwise, the latch lever 96 also begins to pivot clockwise and the latch 78 is retracted. When the lock bit la has reached an approximately + 90 ^o position, the latch 78 is completely retracted.

• a) Die Figur ll zeigt die Grundstellung. Während sich der Schließbart la sowie der Zahnkranz l0 in der Nullgrad-Stellung befinden, in der der Schlüssel gesteckt und gezogen werden kann, ist die Treibstange l6 über das Getriebeausgangsrad 20 mit den Nocken 24 und 24' einerseits sowie das Spezialprofil P andererseits in die Entriegelungsstellung eingelegt, in der die an den Treibstangenabschnitten l6a und l6b angeordneten Riegelteile außer Eingriff mit entsprechenden Riegeleingriffselementen des Türrahmens sind. Der Begrenzungsfinger 30' des Spezialprofils P greift zwischen den Anschlag 28 des Getriebeausgangsrads 20 und die Achse 32 ein, auf dem das Getriebeausgangsrad 20 drehbar gelagert ist. Die Treibstange l6 ist allenfalls bis auf ein äußerst geringfügiges toleranzbedingtes Spiel gegen Verschiebung in vertikaler Richtung gesperrt.
  Der Riegel l8 befindet sich in der zurückgeschlossenen Stellung, und zwar dank des Eingriffs des Antriebsnockens 46' an dem Gegennocken 50 und des Eingriffs des Zapfens 40 in den Schlitz 38a. Dabei kann der Umsetzhebel 35, von allenfalls toleranzbedingten kleinen Winkelbewegungen abgesehen, nicht verschwenken, und der Riegel l8 kann sich in Querrichtung nicht verschieben, wiederum von allenfalls kleinen toleranzbedingten Hüben abgesehen, die den erwähnten kleinen toleranzbedingten Winkelbewegungen entsprechen.
  Die Falle 78 befindet sich unter der Wirkung der Feder 59 in der über die Stulpplatte 3 vorstehenden Stellung, in der sie beim Zuschlagen der Tür nach rechts gegen die Wirkung der Feder 59 ausweichen kann. Die Falle nimmt ihre in Figur ll gezeichnete Stellung deshalb ein, weil sie von dem Fallenhebel 96 nicht beeinflußt ist, denn der Fallenhebel 96 mit seiner Ausprägung 96a ist von dem Mitnehmer 20a des Getriebeausgangsrades 20 (Figur l2) nicht beaufschlagt, nimmt deshalb die in Figur l2 mit ausgezogener Linienführung dargestellte Stellung ein und wirkt nicht auf den Fallenschwanz 58, 64 ein.
• b) Wenn das Schloß gesperrt werden soll, so wird der Schlüssel ausgehend von Figur ll im Gegenuhrzeigersinn verdreht und damit dreht sich auch der Zahnkranz l0 im Gegenuhrzeigersinn. Das Getriebeausgangsrad 20 erfährt dann eine Drehung im Gegenuhrzeigersinn um die Achse 32.
  Nach einer Drehbewegung des Schließbarts la um ca. - l20^o schlägt der Nocken 24 gegen die untere Flanke der Ausnehmung 26' an, so daß eine Abwärtsbewegung der Treibstange l6 beginnt. Diese Abwärtsbewegung kann deshalb beginnen, weil sich dann der Anschlag bereits so weit im Gegenuhrzeigersinn gegenüber der Stellung gemäß Figur 11 verdreht hat, daß der Begrenzungsfinger 30' an dem Anschlag 28 vorbei nach unten wandern kann.
  Im weiteren Verlauf der Drehung des Schließbarts la im Gegenuhrzeigersinn und der dadurch veranlaßten Drehung des Getriebeausgangsrades 20 ebenfalls im Gegenuhrzeigersinn tritt dann der Nocken 24 aus der Ausnehmung 26' wieder heraus, und es tritt der Nocken 24' in die Ausnehmung 26 ein, um beim Weiterdrehen des Getriebeausgangsrades 20 im Gegenuhrzeigersinn die Treibstange l6 noch weiter nach unten zu verschieben.
  Nach einer Drehung des Schließbarts la um 360^o + 270^o ist der Zustand erreicht, der in Figur l5 dargestellt ist. Dies ist noch nicht die voll gesperrte Stellung. Erst nach einer Drehung des Schließbartes la um 2 x 360^o gegenüber dem Zustand gemäß Figur ll ist die voll gesperrte Stellung endgültig erreicht. Der Nocken 24' hat dann die Treibstange l6 gegenüber dem Zustand in Figur l5 weiter nach unten verschoben, und der Begrenzungsfinger 30 befindet sich nunmehr zwischen der Achse 32 und dem Anschlag 28. Dabei sind die an den Treibstangenabschnitten l6a und l6b angebrachten, nicht eingezeichneten Riegelteile in die Riegeleingriffselemente des Türrahmens eingetreten, und eine Einwirkung auf die Treibstange l6 kann nicht mehr zu ihrer Verschiebung führen, weil der Begrenzungsfinger 30 dann zwischen der Achse 32 und dem Anschlag 28 eingesperrt ist.
  Bei der Abwärtsbewegung der Treibstange l6 durch Drehen des Schlüssels im Gegenuhrzeigersinn und dadurch veranlaßtem Drehen auch des Getriebeausgangsrades 20 im Gegenuhrzeigersinn wird auch der Riegel l8 in Sperrstellung überführt. Wenn der Antriebsnocken 46 der Treibstange l6 nach Durchlaufen des Gegennockens 50 durch die Ausnehmung 42 auf den Gegennocken 50 trifft, beginnt eine Schwenkbewegung des Umsetzhebels 35 im Gegenuhrzeigersinn und diese Schwenkbewegung wird über die Zapfen-Schlitz-Verbindung 40, 38a in eine Verschiebebewegung des Riegels l8 umgesetzt, der sich nach links bewegt. Sobald die vertikale Kante 52 des Antriebsnockens 46 an dem Gegennocken 50 anliegt - dies ist nach etwa einer Drehung von 360^o + 270^o des Schließbartes la erreicht -, ist der Riegel 18 voll ausgefahren (s. Figur l5), so daß in der letzten Phase der Drehung des Schließbartes la von dem Zustand gemäß Figur l5 bis zur Rückkehr des Schließbartes la in die Nullgrad-Stellung (Schließbart hat sich dann um insgesamt 2 x 360^o gedreht) eine weitere Verschiebung des Riegels 18 nicht mehr stattfindet.
• c) Wenn das Schloß entsperrt werden soll, so wird der Schlüssel im Uhrzeigersinn zurückgedreht, bis der Schließbart la wieder die Stellung gemäß Figur ll erreicht hat. Alle Teile des Schlosses nehmen dann wieder die in Figur ll gezeichnete Position ein.
• d) Wenn die Türe vom Schließzylinder l aus geöffnet werden soll, muß auch die Falle 78 zurückgezogen werden. Hierzu wird der Schlüssel ausgehend von der Stellung gemäß Figur ll in die Stellung gemäß Figur l2 und noch um ca. 45^o darüber hinaus im Uhrzeigersinn verdreht. Dann wirkt gemäß Figur l2 der Mitnehmer 20a des Getriebeausgangsrades 20 auf die Einprägung 96a ein, der Fallenhebel 96 wird im Uhrzeigersinn verschwenkt, wirkt auf den Fallenschwanz 58, 64 ein und zieht damit die Falle 78 zurück.
  Zum Zurückziehen der Falle 78 ist eine Aufwärtsbewegung der Treibstange l6 nicht vorgesehen. Man erkennt dies aus den Figuren ll und l2. Wenn ausgehend von dem Zustand gemäß Figur ll das Getriebeausgangsrad 20 im Uhrzeigersinn verdreht wird, so tritt - wie man aus den Figuren ll und l2 leicht ersehen kann - keinerlei Einwirkung des Nockens 24 auf das Spezialprofil P mehr ein. Dies bedeutet, daß die Treibstange l6 nicht mehr verschoben wird. Sie kann auch gar nicht mehr verschoben werden, weil der Begrenzungsfinger 30' zwischen dem anschlag 28 und der Achse 32 unbeweglich bis auf allenfalls geringe Toleranzbeweglichkeit eigefangen ist.
  Es ist festzuhalten, daß die Zurückziehung der Falle 78 ohne Bewegung der Treibstange l6 möglich ist, weil der Antrieb für den Fallenhebel 96 nicht von der Treibstange l6 abgeleitet ist, sondern von dem Getriebeausgangsrad 20. Dies ist ein erheblicher Vorteil, weil beim Öffnen der Tür durch Zurückziehen der Falle 78 mittels des Schlüssels nur das Zahnradgetriebe bis zum Getriebeausgangsrad 20 einschließlich und der Fallenhebel 96 mit der Falle 78 bewegt werden müssen, nicht aber die Treibstange l6 mit den Treibstangenabschnitten l6a und l6b. Hierdurch wird zum einen die Betätigung des Schlüssels zum Zwecke des Zurückziehens der Falle 78 leichtgängiger; zum anderen braucht zwischen den an den Treibstangenabschnitten l6a und l6b vorgesehenen Riegelteilen und den zugehörigen Riegeleingriffselementen des Türrahmens nicht auch noch ein zusätzliches Lösespiel vorgesehen werden, das einer Bewegung der Treibstange beim Zurückziehen der Falle 78 durch Schlüsselbetätigung Rechnung trägt. Da beim Zurückziehen der Falle 78 durch Schlüsselbetätigung die Treibstange l6 nicht bewegt wird (und auch nicht bewegt werden kann), wird bei dieser Fallenzurückziehung auch der Riegel 18 nicht bewegt.
• e) Es besteht nun die Forderung, daß in der Schlüsselabzugsstellung der Schließbart la aus der Nullgrad-Stellung (Figur ll) ausgeschwenkt ist, wie etwa in Figur l3, damit er einem Durchschlagen des Schließzylinders l in Längsrichtung der Schließzylinderachse Einhalt gebieten kann. Da nun der Schließzylinder l nur dann in die entsprechende Durchstecköffnung der Schloßdecke oder des Schloßbodens 60 eingeführt werden kann, wenn der Schließbart la sich in der Nullgrad-Stellung befindet, muß also der Schließzylinder l in einem Zustand durch die Schloßdecke oder den Schloßboden 60 eingeführt werden, in dem der Schließzylinderkern mit dem Schlüssel so weit gegenüber der Schlüsselabzugsstellung verdreht ist, daß der Schließbart la die Nullgrad-Stellung einnimmt.
  Ist der Schließzylinder l auf diese Weise einmal eingeführt, so kann der Schließzylinderkern mit dem Schlüssel in die Schlüsselabzugsstellung zurückgedreht werden, in der dann der Schließbart la eine gegenüber der Nullgrad-Stellung ausgestellte Winkelposition einnimmt, wie sie etwa in Figur l3 dargestellt ist, wo sich der Schlüssel in Schlüsselabzugsstellung und der Schließbart in einer - 90^o-Stellung befinden. Auch hierbei, das heißt beim Überführen des Schließbartes in die -90^o-Stellung nach vorhergehendem Einführen des Schließzylinders l durch die Öffnung der Schloßdecke, bewegt sich der Riegel l8 nicht. Hierfür sorgt die Ausbildung des Getriebeausgangsrades 20 und des Spezialprofils P an der Treibstange l6.
  Die Einführung eines der Figur l3 entsprechenden Schließzylinders l mit einem in der Schlüsselabzugsstellung unter einem Winkel von -90^o abstehenden Schließbart la erfolgt wieder in einer der Figur ll entsprechenden Schließbartposition, in der das Einführen des Schließzylinders l allein möglich ist. Um dann den Schließzylinderkern und damit den Schlüssel in Schlüsseleinsteck- bzw. Schlüsselabzugsstellung zu bringen, wird eine Drehung des Schlüssels um 90^o vorgenommen, wobei der Schließbart von der Position gemäß Figur ll in die Position gemäß Figur l3 wandert.
  Bei dieser Wanderung bewegt sich der Nocken 24 des Getriebeausgangsrandes 20 von der in der Figur ll gezeigten Stellung in die in Figur l3 gezeigte Stellung, ohne daß eine Verschiebung der Treibstange l6 stattfindet. Man erkennt dies daran, daß gemäß Figur ll der Nocken 24 an der mittleren Erhebung 26'' des Spezialprofils P vorbeigeht, ohne einen Schub auf die Treibstange l6 auszuüben, und ferner daraus, daß in dem Zustand der Figur l3 der Nocken 24 noch nicht im Eingriff mit der unteren Flanke der Ausnehmung 26' getreten ist. Dies muß auch so sein, weil ja während des Drehwegs des Getriebeausgangsrades 20 von der Stellung gemäß Figur ll in den Zustand gemäß Figur 13 der Begrenzungsfinger 30' zwischen der Achse 32 und dem Anschlag 28 bis auf ein allenfalls geringes, toleranzbedingtes Spiel eingesperrt ist, eine Bewegung der Treibstange l6 also gar nicht stattfinden könnte, ohne daß es zu einer inneren Sperrung des ganzen Systems käme.
  Man kann sich ohne weiteres vorstellen, daß auch ein Schließzylinder l in das Schloß eingeführt werden kann, dessen Schließbart la in der Schlüsselabzugsstellung etwa um + 45^o ausgestellt ist oder um + 30^o, so wie in Figur l4 dargestellt. Wiederum müßte der Schließbart la zum Einführen des Profilschließzylinders l in die Öffnung der Schloßdecke bzw. des Schloßbodens 60 in die Nullgrad-Stellung gebracht werden, der Schließzylinderkern mit dem Schlüssel also entsprechend aus der Schlüsseleinsteck- und Schlüsselabzugsposition herausgedreht werden, so daß der Schließbart la die Position gemäß Figur ll einnimmt. Dann müßte der Schließzylinderkern mit dem Schlüssel in die Schlüsselabzugs- und Schlüsseleinsteckstellung zurückgedreht werden, wobei dann der Schließbart la in die + 45^o-Position bzw. + 30^o-Position gemäß Figur l4 gelangt.
  Man erkennt, daß beim Übergang des Schließbarts la von der Position in Figur ll zur Position in Figur l4 und auch noch in die + 45^o-Position sich der Nocken 24 völlig außerhalb des Eingriffs mit dem Spezialprofil P befindet und der Begrenzungsfinger 30' wiederum zwischen dem Anschlag 28 und der Achse 32 eingefangen ist. Eine Positionsveränderung der Treibstange l6 erfolgt somit nicht und könnte auch nicht erfolgen. Da die Position des Riegels l8 von der Position der Treibstange l6 abhängig ist, findet also auch beim Einsetzen eines Schließzylinders l mit einem in der Schlüsselabzugsstellung unter - 30^o bzw. -45^o abstehenden Schließbart la und beim nachfolgenden Zurückführen des Schlüssels in die Nullgrad-Stellung und entsprechenden Ausstellen des Schließbarts la keine Bewegung der Treibstange l6 statt.
• f) Es ist darauf hinzuweisen, daß die Ausstellmöglichkeit des Schließbarts 1a bei dem erfindungsgemäßen Treibstangenschloß beschränkt ist. Über die +30° Stellung gemäß Figur 14 hinaus kann deshalb nicht ausgestellt werden, weil dann die Einwirkung auf die Falle 78 beginnt gegen die Wirkung der Feder 59 und weil dann die Abzugsstellung des Schlüssels nicht mehr stabil wäre sondern nur unter Einwirkung auf den Schlüssel herbeigeführt werden könnte.

The following can now be determined regarding the various positions shown in FIGS. 11 to 15:

• a) Figure ll shows the basic position. While the lock bit la and the ring gear l0 are in the zero degree position in which the key can be inserted and removed, the drive rod l6 is on the one hand via the transmission output gear 20 with the cams 24 and 24 'and the special profile P on the other hand in the unlocked position inserted, in which the locking parts arranged on the drive rod sections l6a and l6b out of engagement with corresponding latch engagement elements of the door frame. The limiting finger 30 'of the special profile P engages between the stop 28 of the transmission output gear 20 and the axle 32 on which the transmission output gear 20 is rotatably mounted. The drive rod l6 is blocked at most except for an extremely slight tolerance-related play against displacement in the vertical direction.
  The latch 18 is in the closed position thanks to the engagement of the drive cam 46 'on the counter cam 50 and the engagement of the pin 40 in the slot 38a. Apart from any tolerance-related small angular movements, the transfer lever 35 cannot pivot, and the latch 18 cannot move in the transverse direction, again apart from any small tolerance-related strokes which correspond to the small tolerance-related angular movements mentioned.
  The latch 78 is under the action of the spring 59 in the position above the faceplate 3, in which it can deflect against the action of the spring 59 when the door slams to the right. The trap assumes its position shown in FIG. 11 because it is not influenced by the latch lever 96, because the latch lever 96 with its shape 96a is not acted upon by the driver 20a of the transmission output gear 20 (FIG. 12), so it takes the one in FIG l2 position shown with solid lines and does not act on the trap tail 58, 64.
• b) If the lock is to be locked, the key is turned in a counterclockwise direction starting from FIG. 11 and the sprocket also rotates l0 counterclockwise. The transmission output gear 20 then undergoes a counterclockwise rotation about the axis 32.
  After a rotary movement of the lock bit la by about - l20 ^o the cam 24 abuts against the lower edge of the recess 26 on ', so that a downward movement of the drive rod begins l6. This downward movement can begin because the stop has already rotated so far counterclockwise with respect to the position shown in FIG. 11 that the limiting finger 30 'can move down past the stop 28.
  In the further course of the rotation of the locking bar la in the counterclockwise direction and the consequent rotation of the transmission output gear 20 also in the counterclockwise direction, the cam 24 then emerges again from the recess 26 'and the cam 24' enters the recess 26 in order to continue rotating the gear output gear 20 counterclockwise to shift the drive rod l6 further down.
  After turning the locking bar la by 360 ^o + 270 ^o , the state is reached, which is shown in FIG. This is not yet the fully locked position. The fully locked position is finally reached after the locking bit la has been rotated 2 × 360 ^° relative to the state shown in FIG. The cam 24 'has then shifted the drive rod l6 further down compared to the state in FIG. L5, and the limiting finger 30 is now located between the axis 32 and the stop 28. The latch parts, not shown, attached to the drive rod sections 16a and 16b entered the latch engagement elements of the door frame, and an action on the drive rod l6 can no longer lead to its displacement because the limiting finger 30 is then locked between the axis 32 and the stop 28.
  During the downward movement of the drive rod l6 by turning the key counterclockwise and thereby also turning the transmission output gear 20 counterclockwise, the latch l8 is also transferred into the locked position. When the drive cam 46 of the drive rod 16 strikes the counter cam 50 after passing through the counter cam 50 through the recess 42, a pivoting movement of the transfer lever 35 begins in the counterclockwise direction and this pivoting movement is converted into a sliding movement of the bolt 18 via the pin-slot connection 40, 38a implemented that moves to the left. As soon as the vertical edge 52 of the drive cam 46 bears on the counter cam 50 - this is achieved after about a rotation of 360 ^o + 270 ^{o of} the locking bar la - the bolt 18 is fully extended (see FIG. 15), so that in the last one Phase of the rotation of the lock bit la from the state according to FIG. 15 until the return of the lock bit la to the zero degree position (lock bit has then rotated by a total of 2 × 360 ^° ), a further displacement of the bolt 18 no longer takes place.
• c) If the lock is to be unlocked, the key is turned clockwise until the lock bit la has reached the position shown in FIG. All parts of the castle then assume the position shown in Figure ll again.
• d) If the door is to be opened from the locking cylinder 1, the latch 78 must also be withdrawn. The key is based on the position shown in Figure ll in the position shown in Figure l2 and rotated clockwise by about 45 ^o beyond. Then, according to FIG. 12, the driver 20a of the transmission output wheel 20 acts on the indentation 96a, the latch lever 96 is pivoted clockwise, acts on the latch tail 58, 64 and thus retracts the latch 78.
  To retract the latch 78, an upward movement of the drive rod 16 is not provided. This can be seen from Figures ll and l2. If, starting from the state according to FIG. 11, the transmission output gear 20 is turned clockwise, then - as can easily be seen from FIGS. 11 and 12 - the cam 24 no longer acts on the special profile P. This means that the drive rod 16 is no longer displaced. It can also no longer be shifted because the limiting finger 30 'between the stop 28 and the axis 32 is immobile except for a slight tolerance movement.
  It should be noted that the retraction of the latch 78 is possible without moving the drive rod 16 because the drive for the latch lever 96 is not derived from the drive rod 16 but from the transmission output gear 20. This is a considerable advantage because when the door is opened by retracting the latch 78 by means of the key, only the gear transmission up to the transmission output gear 20 inclusive and the latch lever 96 with the latch 78 have to be moved, but not the drive rod l6 with the drive rod sections l6a and l6b. On the one hand, this makes the actuation of the key for the purpose of withdrawing the latch 78 easier; on the other hand needs between those provided on the drive rod sections l6a and l6b Bolt parts and the associated bolt engagement elements of the door frame are not provided with an additional loosening game, which takes into account movement of the drive rod when the latch 78 is retracted by key actuation. Since the pull rod 16 is not moved (and cannot be moved) when the latch 78 is retracted by key actuation, the latch 18 is not moved during this latch retraction.
• e) There is now a requirement that the key bit la be pivoted out of the zero degree position (FIG. 11) in the key withdrawal position, such as in FIG. 13, so that it can stop the locking cylinder 1 from striking in the longitudinal direction of the key cylinder axis. Since the lock cylinder 1 can only be inserted into the corresponding through opening of the lock cover or lock base 60 when the lock bit la is in the zero degree position, the lock cylinder 1 must be inserted through the lock cover or lock base 60 in one state , in which the lock cylinder core is rotated with the key so far relative to the key withdrawal position that the lock bit la assumes the zero degree position.
  Once the lock cylinder 1 has been inserted in this way, the lock cylinder core can be turned back with the key to the key withdrawal position, in which the lock bit la then assumes an angular position which is in relation to the zero degree position, as is shown, for example, in FIG the key is in the key withdrawal position and the lock bit is in a - 90 ^o position. Here too, that is to say when the locking bit is moved into the -90 ^o position after the previous insertion of the Lock cylinder l through the opening of the lock cover, the bolt l8 does not move. This is ensured by the design of the transmission output gear 20 and the special profile P on the drive rod l6.
  The introduction of the figure with a in the key withdrawal position at an angle of -90 ^o projecting locking cam la is again in the figure ll corresponding lock bit position in which the insertion of the lock cylinder l is solely possible l3 corresponding lock cylinder l. Then, in order to bring the lock cylinder core and the key in key insertion and key withdrawal position, a rotation of the key is carried out by 90 ^o, wherein the locking cam from the position II shown in FIG according migrates in the position of figure l3.
  During this migration, the cam 24 of the transmission output edge 20 moves from the position shown in FIG. 11 to the position shown in FIG. 13 without the drive rod 16 being displaced. This can be seen from the fact that, according to FIG. 11, the cam 24 passes the central elevation 26 ″ of the special profile P without exerting any thrust on the drive rod 16, and furthermore from the fact that in the state of FIG Engagement with the lower edge of the recess 26 'has occurred. This must also be so, because during the rotation of the transmission output gear 20 from the position according to FIG. 11 into the state according to FIG. 13, the limiting finger 30 'between the axis 32 and the stop 28 is locked in, except for a possibly small, tolerance-related play Movement of the drive rod 16 could therefore not take place without the entire system being locked internally.
  One can imagine that a lock cylinder can be l inserted into the lock, the lock bit la is about ^o exhibited in the key withdrawal position by + 45 or, as shown by + 30 ^° in Figure l4 readily. Again, the lock bit la would have to be brought into the opening of the lock cover or the lock base 60 in the zero degree position for inserting the profile lock cylinder l, so the lock cylinder core with the key should be correspondingly turned out of the key insertion and removal position, so that the lock bit la Takes position according to Figure ll. Then the lock cylinder core with the key would have to be turned back into the key withdrawal and key insertion position, the lock bit la then reaching the + 45 ^o position or + 30 ^o position according to FIG. 14.
  It can be seen that during the transition of the locking bar la from the position in FIG. 11 to the position in FIG. 14 and also in the + 45 ^o position, the cam 24 is completely out of engagement with the special profile P and the limiting finger 30 'again between the stop 28 and the axis 32 is captured. A change in position of the drive rod l6 thus does not and could not take place. Since the position of the bolt l8 is dependent on the position of the drive rod l6, there is therefore also when inserting a lock cylinder l with a lock bit la projecting in the key withdrawal position below - 30 ^o or -45 ^o and subsequently returning the key to the zero degree Position and corresponding exposing the locking bar la no movement of the drive rod l6 instead.
• f) It should be noted that the possibility of opening the lock bit 1a is limited in the espagnolette lock according to the invention. Therefore, it cannot be issued beyond the + 30 ° position according to FIG. 14, because then the action on the latch 78 begins against the action of the spring 59 and because the withdrawal position of the key would then no longer be stable, but would only be brought about by acting on the key could be.

On the other hand, it is also not possible to open the locking bar beyond the -90 ° position shown in FIG. 13, for the following reason: The lock is - as stated earlier - designed in such a way that the drive rod 16 is fully extended after a twice 360 ° rotation from the state shown in Figure 13 and then the key can be removed again. If the lock bit 1a is already in the -90 ° position of FIG. 13 at the start of the closing rotation, then after a two 360 ° turns of the key, a state is reached in which the stop 28 strikes against the flank 31 of the limiting finger 30 '. This means that if the locking bar 1a is extended beyond the 90 ° position of FIG. 13, the two 360 ° rotations could no longer be carried out fully, so that the key withdrawal position could no longer be reached. The range of variation of the lock bit 1a in the lock according to the invention is therefore limited to the range between + 30 ° according to FIG. 14 and -90 ° according to FIG. 13. This means that - as explained above - the lock bit 1a is varied only in such an angular range can, in which there is no thrust engagement between the cam 24 and the special profile P, and consequently the drive rod 16 and the bolt 18 is not moved. If, nevertheless, a lost motion is provided between the drive rod 16 and the bolt 18, which results from the width of the recess 42 between the two drive cams 46 and 46 'results, this lost motion has nothing to do with the requirement for variability of the opening angle of the locking bar 1a. The lost motion caused by the width of the recess 42 is provided from a completely different point of view. If one were to provide a constantly positive engagement between the drive cams 46, 46 'on the one hand and the counter-cam 50 on the other hand, it would not be possible, given the available space and maintaining the width of the drive rod 16 necessary for strength reasons, for the two-speed rotation of the lock cylinder core with that rotary movement of the transfer lever 35, which is necessary to have the bolt 18 in the fully extended position after two 360 ° rotations of the lock cylinder core, nothing more and nothing less.

In FIG. 16, which corresponds approximately to the position in FIG. 11, the transfer lever 235 is modified compared to the embodiment in FIG. This transfer lever 235 can again be pivoted about a fixed axis 234 and has two teeth 237, 239, namely a bolt ejection tooth 237 and a bolt retraction tooth 239. A tooth notch 241 lies between these teeth. When the lock is locked, the drive rod 216 goes down and strikes with its nose 243 against the tooth 237, so that the bolt is excluded by the transfer lever 235. If the nose 243 is in the region of the tooth notch 241, lost motion is possible again. The lost motion is provided here for the same and only for the same reason as set out above with reference to the embodiments according to FIGS. 11 to 15. The lever 235 has a latch engaging arm 245 which acts on the latch 218 via a pin / slot connection 249.

The embodiment according to FIG. 17 shows a further modification of the gear connection between the push rod 316 and the bolt 318. The position of the FIG. 17 again corresponds approximately to the position in FIG. 11. In a departure from the embodiment in FIG. 11, the counter cam 350 of the transfer lever 335 engages in a form-fitting manner between two correspondingly dimensioned drive cams 346 and 346 ′ of the drive rod 316. The lost motion between the drive rod 316 on the one hand and the transfer lever 335 and thus also the slide bolt 318 on the other hand is completely suppressed here. Nevertheless, due to the unchanged engagement conditions between the cam 324 and the special profile P, there is the same variation possibility for the position of the locking bar between + 30 ° and -90 °.

Claims (7)

Espagnolette lock, comprehensive
a drive rod (l6) which can be displaced between an open position (FIG. 11) and a closed position (FIG. 15) in connection with at least one closing element (18),
a lock cylinder (l),
a reduction gear (A) between the shooting cylinder (l) and the drive rod (l6) for moving the drive rod (l6) between the open position (Figure ll) and the closed position (Figure l5), the reduction gear (A) on the lock cylinder side a ring gear (l0 ), which meshes with two driven wheels arranged downstream of it (l2, l2 ') and has a slot (2) which is designed to insert the locking bar (la) of the locking cylinder (l) and has a slot (2) which is open around the edge, and which has a fixed axis ( 32) rotatable drive rod drive member (20) of the reduction gear (A) acts on the drive rod (16) via a driving device (24, 24 ', P),
further comprising
a bolt (l8) which can be moved transversely to the longitudinal axis of the drive rod (l6) between a retracted position (Fig. ll) and an extended position (Fig. l5) and by means of movement conversion means (46, 46 ', 38, 38a, 40) the drive rod (l6) can be driven,
and further comprehensive,
a latch (78) pretensioned by a spring force (59) into a closed position, which can be retracted against the spring force (59) by a follower (80) and by the lock cylinder (l), the slot (2) of the toothed ring (10) while the lock cylinder core remains in the key withdrawal position from its zero degree position in at least one direction of rotation over a variation angle range of the lock bit (1 a) without an adjustment of the slide bolt (16) occurring, characterized in that
that a cam assembly (22) attached to the drive rod drive member (20) with two control cams (24, 24 ') and a stop cam (28) and a cam engagement profile (P) attached to the drive rod (16) with two control cams (24, 24') ) paired recesses (26, 26 ') and two limiting fingers (30, 30') on both sides of the recesses (26, 26 ') are formed such that when the ring gear (l0) is rotated within the variation angle range of the locking bar (la) Driving connection of the control cam (24) responsible for the start of the drive rod displacement from the open position into the closed position is released with the associated recess (26 ') and the limiting finger (30') associated with this recess (26 ') detects the displacement of the drive rod (l6) in engages essentially in a blocking manner between the stop cams (28) and the axis (32) of the drive rod drive member (20),
and that the trap (78) is retractable by a driver (20a) of the drive rod drive member (20). Espagnolette lock according to claim 1, characterized in that the movement conversion means (46, 46 ', 35, 38a, 40) between the bolt (18) and the drive rod (16) comprise a conversion lever (angle lever 35) pivotably mounted on the lock housing (at 34) which, on the one hand, engages with the drive rod (16) in a tooth-like manner and, on the other hand, is connected to the bolt (18) by a pin / slot connection (38a, 40). Espagnolette lock according to claim 2, characterized in that the tooth-like engagement between the espagnolette (16) and the transfer lever (35) is subject to lost motion. Espagnolette lock according to one of claims 2 and 3, characterized in that the transfer lever (35) is a double lever which, with a counter-cam (50), engages with a toothing (46, 42, 46 ') of the espagnolette (16) and in an arm (38) has a slot (38a) which forks a pin (40) of the bolt (18). Espagnolette lock according to claim 4, characterized in that the toothing (46, 42, 46 ') has two drive cams (46, 46') spaced apart by recesses (42), namely a bolt-pushing drive cam (46) and a bolt-retracting drive cam ( 46 '). Driveline lock according to one of claims 2 and 3, characterized in that the tooth-like engagement between the drive rod (216) and the transfer lever (235) by a nose (243) of the drive rod (216) on the one hand and two teeth separated by a tooth notch (241) (239, 237) of the transfer lever (235) is formed on the other hand and that the transfer lever (235) has a latch engagement arm (245) which with a Pin engages in an elongated hole of the bolt (218) (elongated hole / pin connection 249). Espagnolette lock according to claim 6, characterized in that the tooth notch (241) is designed as a tooth notch which ensures lost motion.

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