EP0907815A1

EP0907815A1 - Closure for doors, bonnets, tailgates or the like, in particular of vehicles, such as motor vehicles

Info

Publication number: EP0907815A1
Application number: EP97923859A
Authority: EP
Inventors: Wolfgang Uwe Spies
Original assignee: Huf Huelsbeck and Fuerst GmbH and Co KG
Current assignee: Huf Huelsbeck and Fuerst GmbH and Co KG
Priority date: 1996-07-04
Filing date: 1997-05-09
Publication date: 1999-04-14
Anticipated expiration: 2017-05-09
Also published as: DE59705565D1; WO1998001642A1; ES2164343T3; PT907815E; EP0907815B1; DE19626914C1

Abstract

The invention concerns a closure comprising a lock cylinder with a cylinder core (33) which can be actuated by a key (34) and can also be moved into a so-called safely secured position (74), with a handle (10) which sometimes acts on a lock transmission member (20), with a switching cam (42) used to actuate a microswitch (50, 50'), and finally with a central-locking member (60) of a central-locking system, which member can be moved into an inactive position (60') and cannot be actively reset again in the safely secured position (74). According to the invention, in order to eliminate the risk of defective operations, the switching cam (42) is provided on a spring-loaded control member (40) which, when the key is turned, can be moved out of a coupling plane (69) into an uncoupling plane (67) where it is uncoupled from the cylinder core (33) and springs back into a normal position as the result of spring force. For other switching functions, the switching cam (42) can carry out lifting movements as the key is turned further after uncoupling. At least part of the transmission member (20) is deflected out of the actuation direction of the handle (10) when the central-locking member (60) is in the inactive position. An abutment face on the control member (40) holds the transmission member (20) in its uncoupling plane in that it located in a second, raised plane. As a result, a previously actuated microswitch is overtravelled without functioning.

Description

Closure for doors, hoods, flaps or the like, in particular for vehicles, such as motor vehicles

The invention relates to a closure of the type specified in the preamble of claim 1, which is used particularly as a rear closure in the trunk lid of a motor vehicle. With this lock, the cylinder core arranged in the locking cylinder can be turned into three working positions by means of a proper key from a zero position, which is determined by an impulse spring. After pulse-wise rotation into a first working position, which is referred to as the "unlocked position", the lock can be opened by actuating a handle, because a transmission element of the lock is moved by the handle and acts on the lock. This does not apply to the second and third working positions, which are to be referred to below as "secure position" on the one hand and "safe position" on the other. In these cases, the handle does not hit the transmission member when it is actuated and does not act on the lock. Inserting the key into the cylinder core and pulling it out again is possible in the zero position, into which the cylinder core automatically returns from the unlocked or secured position due to its pulse spring, or in the safe position, in which the cylinder core remains after a corresponding key rotation .

However, this closure can also be actuated via a so-called "central locking device" which interacts with all other closures arranged in the same motor vehicle. This central locking system comprises a rotary coaxial with the locking cylinder of each lock. gertes Zentralverπegelungsghed, which will be called "ZV member" below. Similar to the cylinder core, the ZV link can be turned, but only between two positions. In the first position of the ZV link, actuating the handle causes the transfer link to move, which opens the lock. For this reason, this position will be referred to below as the "effective position". In contrast, in the other position of the ZV link, the lock cannot be opened by actuating the handle, which is why this position is to be called "ineffective position" below. The ZV link can be rotated between its effective and ineffective position in two ways, first by turning the key over the cylinder core.

The other way of rotating the ZV link is via a central drive, which is part of the central locking device provided in the motor vehicle. If the cylinder core of one of the other locks combined in the central locking device is transferred from the unlocked to its secured position using a key, this is reported to the control of this central locking device via the associated central locking element, which then uses the central drive to control the central locking. Links of all other closures transferred to the ineffective position. An actuation of the ZV limbs from the ineffective position into their effective position is only possible if the safe position is not present in the closure under consideration. By turning the cylinder core using a key in the other locks, the ZV link of the lock which is in the safe position cannot be moved back into the effective position. The safe position is referred to below as "safe position". In this safe position, the lock can neither be released from its handle nor via the central locking device by key actuation of the other locks. There is a super-secure position of the ZV link, which reminds of the security against theft of a "safe", which is why this term is used to identify the relevant position of the cylinder core. When the lock is in the safe position, the actuation of the associated handle remains ineffective and the associated lock cannot be opened. This is only possible if the associated cylinder core is returned from the safe position to the secured position using the key. Then actuate the closing ice on the other closures above the Central drive also the ZV-Ghed of the lock in question can be transferred from an ineffective to its effective position, where an actuation of the handle opens the lock.

In the closure of this type, a switching cam is finally to be moved by key rotation of the cylinder core, which actuates a microswitch belonging to an electrical device of the vehicle, such as an anti-theft alarm system. This actuation of the microswitch takes place at least during the transition between the zero position and the secured position of the cylinder core, but advantageously also between the unlocked position and the zero position of the cylinder core, for which a further microswitch is generally used.

The known closure of the type mentioned in the preamble of claim 1 has the special feature that the locking cylinder is axially spring-loaded and at the same time serves as a "handle". The locking cylinder acts like a push button. There are of course separate handles for closures of other types, but these closures do not have the above-described special structure according to the preamble of claim 1. The known lock acts, after rotation of the cylinder core in the unlocked position, by impressing the lock cylinder on the ZV-Ghed on the transmission member used to open the lock. Here, the transmission element is designed as an angle lever which can be pivoted in an axial plane of the Schheßzyhnders. In the effective position, the ZV link hits the transmission link when the lock cylinder is pressed, but not in the ineffective position. The safe position then exists in the known closure that the ZV link is blocked in its ineffective position and therefore, as in the secured position of the cylinder core, does not act on the transmission link when the push-button actuation of the pushing cylinder is actuated, but instead goes into nothing. The known closure of this type has numerous disadvantages.

First of all, in the connection of the known closure going to the central drive, the blockage of the ZV link in the safe position of the associated pusher must be observed. If the cylinder cores are rotated by turning the key in the other locks of this central locking device and therefore the ZV gates there are also moved, then it can be done the common central drive does not affect the blocked ZV-Ghed of the lock in question, which is in the safe position. In the known closure, this requires special control means in the central locking device. In addition, additional construction work is required in the mechanics of the closure, because the pulse spring must be decoupled from the cylinder core in the safe position. As mentioned at the beginning, the key can be removed from the cylinder core not only in the zero position, but also in the safe position. For this reason, the cylinder core in the safe position must be separated from its restoring pulse spring. Another major disadvantage of the known lock is that contradictory control commands result when the key quickly transfers the cylinder core from its safe position back to the unlocked position and again passes through the locked position. The switching cam that moves with the cylinder core therefore undesirably acts again on the microswitch mentioned and switches the anti-theft alarm system on again, although the anti-theft alarm system is to be switched off by a further microswitch when the cylinder core of the switching cam is further unlocked. This requires intelligent components in the control of the electronics. Additional components are therefore required which are space-consuming.

The invention has for its object to develop a reliable, space-saving closure of the type mentioned in the preamble of claim 1, which manages with as few components and a rotation of the cylinder core between the zero position in the three working positions mentioned above and the ZV-Ghed between it allows effective and ineffective position without causing control problems in the switching cam moved by the cylinder core. This is achieved according to the invention by the measures specified in the characterizing part of claim 1, which have the following special meaning.

Because the control element is in the safe position of the cylinder core in a decoupling plane, where it is decoupled from the cylinder core, and the impulse spring only acts on the control element, additional locking springs are unnecessary, which had to decouple the impulse spring from the cylinder core in the safe position. There can also be no contradictory control commands to the central locking device, because starting from the safe position, because of the control ghed located in the uncoupling level, the switching cam provided on the control element is located at a free distance from the microswitch. The control element with its switch cam is automatically moved back into a normal position by the pulse spring, which corresponds to the zero position of the cylinder core, but leaves the microswitch inactive. If the cylinder core is returned to the zero position using the correct key from the safe position via the secured position, it no longer needs to move the control g ed provided with the switching cam, since this is already in its normal position aligned with it. In the zero position of the cylinder core, coupling with the control ghed occurs again automatically because the control element is moved back into its coupling plane by the spring load acting on it. When the cylinder core is turned further into the unlocked position, the control gate then moves on again in its clutch plane and can actuate another microswitch with its switch cam, which then clearly reverses the electrical device of the vehicle and z. B. sets the anti-theft alarm system ineffective again.

The ZV-Ghed of the lock can also be easily adjusted between its effective and ineffective position in the safe position of the cylinder core from the central drive of the central locking device, because in this case there is a clearance between the ZV-G ed and the one that is still in the decoupling level, but already Steuerghed located in the normal position. As desired, when the lock is in the safe position, the clearance ensures that this lock cannot be returned to a unlocked position via the central locking device, where opening of the lock would be possible via the associated handle. The central locking device also has a simple structure in the invention.

Further measures and advantages of the invention result from the subclaims, the following description and the drawings. In the drawings, the invention is shown in two exemplary embodiments and - to clarify the particular mode of operation according to the invention - in a diagram. Show it: 1 is a perspective rear view of a first embodiment of the closure according to the invention in a starting position where the cylinder core is in the zero position and the handle has not yet been actuated,

2 is an exploded view of the cylinder core and all other components of the lock shown in FIG. 1 which are coaxially connected to it before they are assembled,

3, in a rear perspective corresponding to FIG. 2, a ZV link integrated coaxially into the inner components of FIG. 2, on which a central drive of a central locking device, not shown, engages, known.

4 again in a rear perspective corresponding to FIGS. 1 and 2, the closure housing, in or around which the components of FIGS. 2 and 3 are arranged,

5 and 6, also in Fig. 1 from the rear perspective, in exploded view two levers, which after assembly form a transmission member which is actuated by the handle shown in Fig. 1 and then in the zero position and unlocked position of the cylinder core can act on the lock belonging to the closure according to the invention and open the lock,

7 to 16b show, in a simplified circuit diagram, the mode of operation of the components provided in the closure of FIGS. 1 to 6 in different working positions of the cylinder core and two positions of the associated ZV link,

17 shows the closure housing of a second embodiment of the closure according to the invention, which is used instead of the closure housing shown in FIG. 4, also in perspective, but in a front view opposite to FIG. 4, with a view of the cylinder core already installed in the closure housing, 18 shows a single combination lever, acting as a transmission member, of this second exemplary embodiment of the closure, the combination lever taking care of the effect of the two levers of the first exemplary embodiment shown in FIGS. 5 and 6, as shown in FIGS. 7 to 9,

19 in a perspective representation analogous to FIG. 3, but viewed in the opposite direction, a ZV-Ghed for the second exemplary embodiment of the closure in FIGS. 17 and 18,

20 schematically, in fragmentary form, a cross section along the section line XX-XX of FIG. 18 with the most essential components interacting therewith of the closure housing shown in FIG. 17,

21 schematically shows a further cross section through the combination lever shown in FIG. 18 along the section line XX1-XXI from FIG. 18 with associated essential components, namely also the top view of the ZV-Ghed recognizable in FIG. 19 and finally

Fig. 22 is a sectional view through the combination lever of Fig. 18 along the section line XII-XII there together with the most essential components, namely a Steuerghed and the inner end of the cooperating cylinder core.

The closure comprises a handle 10 which can be seen in FIG. 8 and which partially closes the opening of a hollow 12 which can be seen in FIG. 1 in a handle housing 11 with a handle 13 which is useful for the attack of the human hand. On the back, through an outbreak, the handle protrudes with a working arm 14 on the rear side of the housing 11 in order to be able to cooperate with a transmission member 20 which, in the first exemplary embodiment from FIGS. 1 to 6, is composed of two levers 21, 22. The handle 10 is tiltably mounted on a shaft 15 attached to the handle housing 11. The shaft 15 extends essentially perpendicular to the axis of the cylinder 30 of a beating cylinder of this closure to be described in more detail. By means of a return spring, not shown in detail, the handle 10 is shown in FIG. 1 Starting position held. In this starting position, the aforementioned handle plate 13 is in the trough opening on the front side of the handle housing, which cannot be seen in FIG. 1 because of the rear view of the closure. In Fig. 8, the handle housing 1 1 is omitted for clarity.

In addition, in this figure, as in the remaining FIGS. 7 to 16b, the closure is shown schematically, in a simplified form. 7 and 8 compared to the actual design of the closure in FIGS. 1 to 6, that the two levers 21, 22 of the transfer member 20 mentioned are not shown one above the other, but flat, side by side in the plane of the drawing, to better illustrate the mode of action. While FIG. 8 shows a top view of some of the components of the closure, partly in cutout, FIG. 7 shows a partially sectioned front view of these components of FIG. 8, namely along the broken line VII-VII of FIG. 8. As a result 7, the handle plate 13 is invisible and therefore only indicated by dash-dotted lines. By gripping the handle plate with the human hand, as shown in Fig. 1, a tilting movement in the direction of arrows 16 of Figs. 1 and 7 is carried out around the housing shaft 1 5, which on the working arm 14 acts against the aforementioned return spring downward movement of the Handle 14 in the sense of the arrow 17 shown in FIGS. 7 and 1 generated. Normally, the lever 21 is located in a plane 23, which is aligned with the downward movement arrow 17 and is indicated by dash-dotted lines in FIG. 1 and also in the diagram of FIG. 8, which shall hereinafter be referred to as "alignment plane" for short. Then the lever 21 is in the position shown in solid lines in FIG. 8.

As can be seen from FIGS. 1 and 8, the two levers 21, 22 are mounted together on a pivot bearing 24 on a lock housing 31, which is assembled with the handle housing 11 described above. The pivot bearing 24 thus determines a pivot axis for the transmission member 20 formed from the two levers 21, 22, the position 24 of which is also illustrated in FIG. 7. The aforementioned downward movement 17 guides the working arm 14 in FIG. 7 into the downward position 14 'indicated by dash-dotted lines and normally moves the lever 21 into its pivoting position 21' of FIG. 7. This connects it to it via a swivel joint 25 other levers 22 are taken and transferred into the upward pivoting position 22 ′ shown in FIG. 7. 7 and 8, the pivoting movement 26 of the transmission member 20 is shown, in the diagram of FIG. 7 in the plane of the drawing of the levers 21, 22 which are stretched relative to one another. This pivoting plane is the alignment plane 23 described above, which 1, as evidenced by the pivoting arrow 26 there, runs in a radial plane to the cylinder axis 30 already mentioned. According to the tilting movement arrow 16, on the other hand, the actuation direction of the handle 10 is arranged essentially in a plane parallel to the cylinder axis 30. On the lever 22, as shown by the arrow 18 in Fig. 1, engages a linkage of a lock, not shown, which normally holds the door provided with the lock in the closed position. 7 and 8, this attack 18 is illustrated by a tie rod.

The closed position of the lock prevails when the handle 10 is not actuated. Then the transmission member 20 is in its pivot position shown in FIG. 1, which is illustrated in FIGS. 7 and 8 by the solid lines of the levers 21, 22. This starting position of the transmission member 20 is secured by a return spring 19 which is tensioned between the lever 22 and the lock housing 31 in the present case. The pivoted lever 22 will hereinafter be referred to briefly as the "deflection lever" and the other lever 21 which can be actuated by the handle as the "pivot lever". These two levers 21, 22 are shown in FIGS. 5 and 6 in an exploded view with their pin determining the swivel 25. The two levers 21, 22 are otherwise held by a torsion spring 27 in the alignment plane 23 described above, ie brought together in the contact position in the concrete closure of FIG. 1 and held in the extended position to one another in the simplified diagram of FIGS. 7 and 8. By actuating 16 the handle 10, the lock is transferred to the pull rod 18 in the open position via the pivoting 26 of the transmission member 20. Then a door or tailgate of the vehicle provided with the lock can be opened. However, this is only possible if the locking cylinder already mentioned and to be described in more detail has reached its zero position caused by an impulse spring via a preceding so-called "unlocked position" and not via the "secured position" Stel ment "or is even in the safe position already mentioned.

The complete lock cylinder comprises a cylindrical part 32 of the lock housing, which is to be called "cylinder housing" below. The cylinder housing 32 also determines the cylinder axis 30 mentioned. The numerous components recognizable from FIG. 2 are arranged in or on the cylinder housing 32, to which, in any case, the one by a correct conclusion! 34 rotatable cylinder core 33 and a Steuerghed 40 belong. The cylinder core 33 has the usual spring-loaded tumblers 36, which can only be seen in the special embodiment of FIG. 13b and, due to their spring load, without a key inserted, normally protrude into locking channels 37 which can also be seen in FIG. 13b. In the simplest case, the blocking channels 37 are integrated directly in the cylinder housing 32, but for reasons which will be mentioned later, in the present case, as shown in FIGS. 2 and 13b, a channel sleeve 38, which is axially fixed but rotatably mounted, is used for this purpose in the present case. In addition to the channel sleeve 38, a sliding 39 is also provided, which is axially movable in the cylinder housing 32, but is non-rotatably mounted. The components 38, 39, 40 are pushed onto the corresponding radially offset sections of the cylinder core 33, to which a pulse-compression spring 46 designed as a torsion spring then comes. A locking washer 47, which engages in an annular groove at the inner end of the Zyhπderkerns 33, holds the components 33, 38, 39, 40, 46 together and ensures that the Steuerghed 40 with a clutch receptacle 45 in the sense by the pulse-compression spring 46 of the force arrow 43 is printed against a coupling projection 35 of the cylinder core 33 and normally holds these two parts in engagement. In the present case, the coupling projections 35 and the coupling receptacles 45 are provided twice on the components 33 and 40 in a diametrically opposed position.

In Fig. 1, the locking washer 47 mounted on the inner end of the cylinder core 33 can be seen in the interior of the cylinder housing 32 from the closure housing 31. The cylindrical part of the control member 40 can not be seen, but only two radially extending, diametrically opposed lifting cams 41, 41 ', which represent the one component of control means which ensure an axial stroke of the control member 40. One lifting cam 41 is extended radially and there carries a switching cam 42 for two microswitches 50, 50 'shown in the diagram of FIG. 10b. The two microswitches 50, 50 'are located at the assembly points marked 52, 52' of the in Flg. 4 recognizable lock housing 31, specifically in the circumferential area at the inner end of the cylinder housing 32. They are omitted in the illustration of FIG. 1 and are to be thought of in the axial zone in addition to the switching cam 42, which is also indicated by dashed lines. At the inner end of the cylinder house 32 there are also double axial cam 51 fixed to the housing because of the double lifting cams 41, but only one cam 51 shown in FIGS. 1 and 4 and the other broken away.

The above-described pulse-compression spring 46, which exerts the already mentioned axial force, illustrated in FIG. 2 by the arrow 43, on the control ched 40 in the sense of engagement of the clutch 35, 45 between the control ched 40 and the cylinder core 33, presses the lifting cams 41 against its control cam 51. However, as already mentioned, the impulse compression spring 46 is also a torsion spring which holds the control ged 40 with its switching cam 42 in a defined normal position according to FIG. 1. This normal position is also drawn in solid lines in the diagram to be described in more detail in FIG. 10b. This is provided on the pulse-compression spring 46 provided by spring legs 48, 49, of which one 48 is supported on the one flank 58 of the one lifting cam 41, while the other spring leg 49 is positioned fixed to the housing and in the embodiment of FIG. 2 with the Flank 59 of a slide ring 39, which is mounted on the non-rotatably mounted in the cylinder housing 32 and cooperates.

A special function on the two lifting cams 41, 41 'is provided on the side stop faces 44, 44' in connection with a ZV-Ghed 60 rotatably mounted on the inside end of the cylinder housing of a central locking device (not shown in more detail), which is shown in FIG. 1 in the installed state and in Flg. 3 can be recognized as a single part. The ZV-G ed is connected with an articulation point 61 to the central drive of the central locking device and is adjustable between the effective position 60 shown in FIG. 1 and an inactive position 60 'to be explained in more detail. The ZV-G ed 60 has two end stops 64, 64 ', which are assigned to the two abovementioned stops 44, 44' of the control element 40 3 and are arranged at an angular distance 62, which can be seen in FIG. 3, which correspond to the angular distance between the effective and ineffective position of the ZV link. Finally, the ZV link 60 has a guide curve 63 which interacts with a guide edge 53 provided on the pivoting lever 21 of the transmission link 20. In the specific exemplary embodiment of FIGS. 3 and 6, the axial slope is provided in the guide curve 63, while the guide edge 53 cooperating therewith from the deflection lever 22 can be essentially flat. The control resulting therefrom is illustrated in the simplified diagram in FIGS. 7 to 12b.

The simplification in the diagram of FIGS. 7 to 12b is, as already mentioned, that the levers 21, 22 shown in FIGS. 7 to 9 are not shown in the contact position, as in FIG. 1, but in the extended position. A further simplification is that the rotatable control member 40 is shown as a flat slide in FIGS. 10b to 15b, which is under the restoring effect of the spring 46 shown schematically here. The pressure effect of the above-described pulse pressure spring 46, which is illustrated in FIG. 1 by the arrow 43, also plays a role in the diagram. The representation in the diagram can thus be interpreted as a flat development of the cylindrical control element 40 from FIGS. 1 and 2. Finally, in the schematic drawings of FIGS. 8 to 12b, the ZV link 60 shown in the specific embodiment of the closure in FIGS. 1 and 3 is also shown as a slide movable in the plane of the drawing, and its axially fixed rotary bearing on the inner end of the cylinder housing 32 by a simple one Slide guide 65 in the lock housing 31 illustrates, from which the ZV link 60, as shown in FIG. 10b, protrudes with its articulation point 61 serving to connect the central drive. FIG. 10b also schematically shows the microswitches 50, 50 ', which cannot be seen in FIG. 1, at the assembly points 52, 52' of the closure housing 31 described above, together with their switching elements 55, 55 'to be controlled by the switching cam 42 of the control element 40. . The two microswitches 50, 50 'are switched on in the electrical circuit of an anti-theft alarm system.

In the diagram shown in FIGS. 8 and 9, the axial slope between the guide curve 63 belonging to the ZV link 60 on the one hand and the guide edge 53 belonging to the pivoting lever 21 is opposite the concrete one Embodiment of Figures 1 to 6 have been interchanged; In FIG. 8, the guide edge 53 of the lever 21 has the entire slope, while the guide curve 63 from the ZV-G ed shown there only in parts is illustrated only as the tip of a finger, which also applies to the subsequent FIGS. 9 to 12b of the diagram applies. Despite their different form, the terms introduced in the specific exemplary embodiment of FIGS. 1 to 6 are also to be used in the diagram of FIGS. 7 to 12b.

10a shows a front view of the cylinder core 33 in its zero position, which is illustrated by an auxiliary line 70 determined by the position of the key channel 28. The position of the components in this zero position 70 is drawn in solid lines in the diagram of FIG. 10b. The control unit 40 is normally held in its normal position already mentioned above, which is drawn in solid lines in FIG. 10b, via its impulse compression spring 46. In this normal position, the switching cam 42 provided on it is in a neutral position between the two microswitches 50, 50 '. The pulse-compression spring 46 also ensures, via the engaged clutch 45, 35, that the cylinder core 33 is in a defined position, which, as can be seen in FIG. 10b, is held precisely in its zero position 70, which can be seen in FIG. 10a.

In Fig. 10b the ZV-G ed 60 is in its effective position described above, which can be non-positively fixed by latching elements 63, 56, 56 '. These locking elements are not shown in the specific embodiment of FIGS. 1 to 6. In FIG. 10b, these latching elements are illustrated by an elastic latching elevation 66 indicated on the ZV-G ed 60 and a first latching depression 56 in the closure housing 31 receiving the latching elevation 66 in this case.

10a shows two working positions 71, 72 of the cylinder core 33 on both sides of the zero position 70, which can be achieved by rotating the key in the cylinder channel 28 in the sense of the two mutually opposite rotating arrows 75, 75 'relative to the zero position 70. When the cylinder core 33 rotates 75 to the first working position 71 of FIG. 10 a, the control ghed 40 is also taken in via the engaged coupling 35, 45 and comes out of the normal position 40 shown in solid lines in FIG. 10 b into the first working position indicated by dash-dotted lines 40 '. As a result, the switching cam 42 is also shifted from its normal position into the first working position 42 ', also indicated by dash-dotted lines, and actuates the switching element 55 of the microswitch 50, which then switches on the connected anti-theft alarm system mentioned. At the same time, the control ghed also moves the ZV-Ghed over its end stop 64 when it moves into its first working position 40 'via the abutment surface 44 described above, so that it moves from its effective position 60 into the ineffective position which is also shown in broken lines in FIG. 10b 60 'is transferred. This ineffective position 60 'of the ZV-Ghed is also fixed by latching elements, because the above-described raster elevation 66 engages in a correspondingly offset latching recess 56' of the lock housing 31. Accordingly, there is also an offset of the guide curve 63 in the position 63 ', which is also indicated by dash-dotted lines in FIG. 10b.

These relationships are also illustrated in the diagram in FIG. 8. The position of the guide curve in its offset position 63 'is also indicated there by dash-dotted lines. In this offset position, the guide curve 63 'moves against the guide edge 53 of the pivot lever 21 and rotates it with respect to the described pivot joint 25, according to the pivot arrow 57, into the angular position 21 ", which is also indicated by dash-dotted lines in FIG. 8, the angle lever is removed from the Alignment plane 23 described above transferred into an angled plane 23 ". The angled pivot lever 21 "is now no longer in alignment with the working arm 14 of FIG. 8, which is why its downward movement described in connection with FIG. 7 no longer hits the pivot lever 21" in the direction of arrow 17. An actuation 16 of the handle 10 according to FIG. 1 is therefore ineffective. In the concrete illustration of FIG. 1, the pivoting lever 21 arrives from its alignment plane 23, which is also shown there and has already been described, into the angled plane 23 ″, where it is angled relative to the deflection lever 22 and is no longer aligned with the working arm 14 of the handle 10 The deflection lever 22 remains at rest, despite actuation of the handle 10. The first working position 71 of the cylinder core 33 from FIG. 10a thus proves to be the "secured position" of the cylinder core 33 described at the beginning.

Let go of the key after reaching secure position 71 the impulse-compression spring 46 also initially guides the control member from its first working position 40 'back to the normal position 40 shown in solid lines in FIG. 10b. Because of the clutch 45, 35, which is still engaged, the cylinder core 33 is also returned indirectly, via the control member 40, back to the normal position shown in extended form in FIG. 10b. Although the stop surface 44 on the control heddle 40 now also moves back into its normal position from FIG. 10b, the ZV link remains in its inactive position 60 ', where it is engaged by the latching elements 56, 66 from FIG. 10b is held. This means that the pivot lever remains in its angled position 21 "and the handle 10 is idle to the transmission member

20 is located.

This only changes again when the cylinder core 33 is transferred via the key, according to FIG. 10 a, in the direction of the arrow 75 to the zero position 70 into a second working position 72. Via the clutch 35, 45, which is also engaged in this case, the control element is also transferred from its zero position 70 from FIG. 10b to the second working position 40 ", which is highlighted there with dots. When switching to this second working position 72, the control element comes in with its switching cam the second working position designated 42 "in FIG. 10b. As a result, the switching element 55 'of the second microswitch 50' is actuated, which switches the anti-theft alarm system off again. If the ZV link was in the above-described ineffective position 60 ', its other stop surface 44', as illustrated by dash-dotted lines in FIG. 10b, was in contact with the end stop 64 'of the ZV link. Therefore, with the key rotation 75 'from FIG. 10a via 44', 64 ', the ZV link is also returned from its previous ineffective position 60' back to the effective position 60 shown in solid lines. The guide curve comes back into the extended position 63 drawn in FIG. 8, as a result of which the pivoted lever 21 ″ angled up to that point is returned to its initial position via the torsion spring 27

21 arrives in the alignment plane 23 of FIGS. 8 and 1. The lock can thus be opened again by actuating the handle 10. This working position 72 thus proves to be the "unlocked position" of the closure mentioned at the beginning. If you let go of the key after the rotation 75 ', the cylinder core 33 is also returned to its zero position via the pulse-compression spring 46 and the control member via the coupling 45, 35 70 returned.

In Fig. 1 1 a, the cylinder core 33 is again shown in front view, but in a secured position 71 with respect to the above-described secured position because of the limit position designated 73, which is distant from the larger rotary arrow 76, in which, as can be seen from FIG. 1 1 b, was clarified Schemes, the limbs of the closure are in a borderline situation. The control unit 40 has been transferred to its limit position 40 ″. The axial control means between the closure housing 31 and the control unit 40 take effect. In the specific exemplary embodiment according to FIGS. 1 to 6, the two lifting cams 41, 41 ′ run from the control unit 40 onto the 10 associated control cams 51 from cylinder housing 32 in Tig 4. These are illustrated in the diagram according to FIGS. 10b to 15b by inclined surfaces 51, 41. In the limit position of the cylinder core 33 from FIG b shows that the lifting cam 41 moves as far along the house-side control cam 51. This is illustrated in Fig. 11b by the axial lifting arrow 77. There is sufficient play between the axially fixed position of the ZV-Ghed 60 and the axially lifting-moving control box 40 , so that this lifting movement 77 of the control member 40 is not hindered by the ZV-Ghed 60.

As a result of this lifting movement 77 of the control member 40 '", the coupling projection 35 of the axially fixedly positioned cylinder core 33 has almost uncoupled from the coupling receptacle 45 of the axially moving control member. If the cylinder core 33 is rotated beyond the limit position 73 of FIG 12a up to a third working position 74 with the key, so when the limit position 73 is exceeded, a decoupling occurs between the coupling projection 35 and the coupling receptacle 45. The control mechanism which is moved up to the limit position 40 '"is now free and is, as shown in FIG. 12b, returned to its normal position 40 by the action of the pulse pressure spring 46, but the axial stroke 77 is retained for the following reason.

As has already been said and illustrated with the aid of the force arrow 43 from FIG. 2, in the specific closure according to FIGS. 1 to 6 the impulse-compression spring 46 also exerts a pressure effect indicated by the force arrow 43 there, which is also shown in the diagram of 1 1 b and 12b is. In Fig. 1 1b, the Steuerhed up to the limit position 40 '"rises against the action of this force 43 in the sense of the lifting arrow 77. After uncoupling, this force 43 remains effective even in the normal position 40 of the control member of Fig. 12b, but The control ged 40 is now supported axially on the coupling projection 35 of the end face of the cylinder core 33 which is axially fixed but rotatably mounted in the housing 31. The control ged 40 is now in Fig. 12b in a decoupling plane 67 determined by the height of the coupling projection 35. This is opposite the preceding coupling plane 69, which is drawn in both in Fig. 12b and in Fig. 10a, offset by the axial distance 68 with respect to the original plane 69. For this reason, the normal position of the control member 40 is additionally referred to as "safe" in Fig. 12b in order to distinguish them from the normal position 40 in the coupling plane 69 of Fig. 10b This term "safe" is explained in more detail.

At the transition from the limit position 73 with the position of the links shown in FIG. 11b to the third working position 74 of the tooth core 32 shown in FIG. 12a, special conditions are present. Even in the limit position 40 '"of FIG. 11b, the switching cam 42'" has moved at an axial distance 68 from the switching element 55 of the microswitch 50, which is why when the switching element is later returned to the normal position 40 "Safe" from FIG. 12b the movement takes place in the uncoupling plane 67. The switching cam thus achieves its normal position 42 shown in FIG. 11b in a corresponding axial distance 68, which is determined by the height difference between the two planes 67, 69, which is also designated as "safe" in FIG. 12b. The cam 42 indeed moves back to its normal position "safe" on the microswitch 50, but at a free distance 68 without actuation of the switching element 55 from the microswitch 50. The activation of the anti-theft alarm system that previously occurred during the transition to the secured position 71 is therefore retained and Microswitch 50 is not operated again.

As can be seen from Fig. 12b, there is another special feature of the closure in the ZV-Ghed. There, the ZV-Ghed was first transferred to its inactive position 60 'by the transition described in connection with FIG. 10b into the secured position 71 of the cylinder core 33, which when turning 76 further, both in the limit position of FIG. 1 1b and even more so in the third working position of Fig. 12b is maintained. Although the normal position 40 "safe" of the control element is present again, however in the uncoupling plane 67, the ZV-G ed is still in its inactive position 60 ', unaffected by the key rotation 76 of FIG. 12a. This is because the stop surface 44 'of the control heddle in FIG. 12b has also moved back, but was not able to move the associated end stop 64' of the ineffective ZV-G eds 60 '. The ZV-Ghed remains in its inactive position 60 ', where its raster elevation 66 engages elastically in the latching recess 56' which characterizes this position. At its point of attack 61, the ZV-G ed can be easily moved into its effective position 60 by the drive of the central locking device by actuating another key belonging to this system. In FIG. 12b, the reversal path 78 of the ZV-Ghed is drawn from its inactive position 60 'into its effective position 60, which is indicated by dash-dotted lines. This reversal movement has no effect on a switching movement of the two microswitches 50, 50 '. The control heddle remains at rest, namely in its normal position 40 "safe" from FIG. 12b.

The third working position 74 of the cylinder core 33 thus proves to be the super-secured position of the closure mentioned at the outset, where the present closure cannot be transferred to its unlocked position via the other locking cylinders of this system. In Fig. 12b there is the "safe position", but with the peculiarity that there is no blockage here, but rather that the ZV-G ed is released to the extent of the required reversal path 78 between the two positions 60, 60 '.

Manipulations in the safe position also do not make it possible to change the angular position 21 "of the swivel lever from the plane 23". An additional safe security even occurs, as can be seen from FIG. 9. Fig. 9 shows, however in solid lines, in Fig. 8 dash-dotted angle position 21 "of the pivot lever relative to the unchanged in its pivot plane order to control lever 22. Drawn in the ineffective position 63 'of the guide curve, which the pivot lever in the described Angle plane 23 "has rotated. In the safe position 74 of the cylinder core 33 from Flg. 12a and the associated FIG. 12b, as has been described, the control element ed in the normal position 40 has been lifted by the axial distance 68 from the cylinder core 33. Therefore, a butt surface 54 provided on the control unit 40 of FIG. 2 is also axially printed out. This butt surface 54 from the control unit 40 is illustrated in FIG. 9 as a finger and is shown in this safe position. As can be seen, the abutting surface 54 now comes to rest on the angled pivot lever 21 "and secures it in its angled plane 23". If, as has already been discussed with reference to the reversing path 78 from FIG. 12b, the ZV-Ghed is pushed back into its effective position 60, with which its guide curve 63 also releases the angled pivot lever 21 ", this means that the pivot lever does not return from the angling plane 23 "in its alignment plane 23 from FIG. 9; the butt surface 54 holds the pivot lever 21 "in its angled plane 23". Despite the possible adjustment 63, 63 'of the guideway belonging to the ZV-Ghed in the safe position, the associated handle 10 of this closure remains ineffective.

2, this butting surface 54 consists of an essentially flat end surface of the one lifting cam 41. In the axial stroke 77 explained with reference to FIG. 11b, the lifting cam 41 presses with its butting surface 54 which is shown in broken lines in FIG. 6 indicated abutting edge 53 'away from the pivot lever 21 and holds it, analogously to FIG. 9, in the angled plane 23 "shown in FIG. 1.

FIG. 13a shows the cylinder core 33 in its safe position 74 and therefore in FIG. 13b the associated control ghed in the uncoupling plane 67 in its normal position 40. The same conditions therefore exist as in the diagram of FIG. 12b. The difference then is that FIG. 13b also shows the mode of operation of the components 38, 39 already explained in connection with FIG. 2. 13b to 16b show a so-called overload protection on the lock cylinder 33. The sliding ring 39 is guided, for example by radial lugs 29, in corresponding longitudinal grooves 79 of the lock housing 31, but non-rotatably, which has already been mentioned above. As already mentioned, the channel sleeve 38 is arranged axially fixed but rotatable in the closure housing 31. The overload protection consists first of all in that the sliding ring 39 and the channel sleeve 38 has a mutually complementary lifting profile 81, 82 on their mutually facing end faces. As can also be seen in FIG. 2, this consists of an approximately trapezoidal recess 82 in the channel sleeve 38 and a complementary elevation 81 in the sliding ring 39. As shown in FIG. 2, two lifting profiles 81, 82 which are diametrically mutually advantageous are expedient Art provided. As a further component of this overload protection, a compression spring 80 is provided, which, for. B. on the mentioned radial lugs 29 of the sliding ring 39 and this spring-loaded in the direction of arrow 83 of Fig. 14b. As long as the proper key is not in the key channel 28 of FIG. 13a, the tumblers 36 already mentioned engage in the locking channel 37 of the channel sleeve 38, as shown in FIG. 13b, and thus ensure a rotationally fixed connection between the cylinder core 33 and the channel sleeve 38 .

If the cylinder core 33 is now rotated not by the correct key but by a burglary tool in the direction of arrow 86, the channel sleeve 38 is also rotated via the engaging tumblers 36 and therefore, when a certain limit load is exceeded, the lifting profile 81, 82 against the spring force 83 of the compression spring 80 is raised. This situation is shown in Fig. 14b. Now the sliding ring 39 supports the control member 40 with its end face 89 opposite the lifting profile 81. As a result, even in the event of a break-in, the control member 40 is kept unchanged in its normal position 40, which can already be seen in FIG. 13b, in the decoupling plane 67, but not only via the coupling projection 35 from Cylinder core 33, but also from this end face 89 of the sliding ring 39. The safe position thus remains ensured even in the event of a break-in. As FIG. 14 a shows, the cylinder core 33 can be rotated by the burglary tool according to the rotation case 86 without the ineffectiveness of the handle actuation being eliminated; the lock remains locked.

15b to 16b show further measures of the overload protection described above. The channel sleeve 38 is provided here with an opening 84, which is penetrated by a synchronization member designed here as a roller 85. The breech housing 31 here has a first recess 87 for one end of the roller 85 and the peripheral surface of the cylinder core 33 a second recess 88 for the opposite end of the roller 85. In the safe position 74 of the tooth core illustrated in FIG. 15a, during a violent rotation 86 by means of a burglary tool, the conditions shown in cross-section from FIG. 16b on the one with XVlb-XVIb marked position of Fig. 15b. If, as has already been said in connection with FIG. 14b, the cylinder core 33 is connected in a rotationally fixed manner to the channel sleeve 38 via the engaging tumblers, then these parts are rotated together, as the rotation arrow 86 of FIG. 16b shows. The roller 85 leaves the recess 87 on the house side and moves completely into the recess 88 on the core side.

FIG. 16a shows the situation at the same point as FIG. 16b if the conditions explained in connection with FIGS. 10b to 12b are present, where the cylinder core 33 is rotated by means of a proper key. In this case, the tumblers 36 already described several times in connection with FIG. 13b are sorted onto the circumference of the tooth core 33 and can be rotated with respect to the channel sleeve 38. This ensures roll 85. It now deviates into the recess 87 on the building side, but still engages in the opening 84 to a sufficient extent in order to secure the channel sleeve 38 in a rotationally fixed manner with respect to the closure housing 31. The roller 85 in FIG. 16a clears the other recess 88 and therefore allows the above-described rotation 76 of the cylindrical core 33 relative to its channel sleeve 38.

17 to 22 show a second specific exemplary embodiment of the closure according to the invention, which is similar in many respects to the structure and mode of operation of the preceding first exemplary embodiment according to FIGS. 1 to 6, which is why the previous description applies first. The same reference numerals as in the first exemplary embodiment are used to designate analog components. It is enough to only consider the differences.

The main difference of this second exemplary embodiment from the first is that here the transmission link does not consist of two levers, but of a single combination lever 90, the appearance of which can best be seen in FIG. 18. The associated housing 31 has a ball joint for the combination lever 90, for which z. B. 17 has a ball head 91 and the combination lever 90 of FIG. 18 has a ball socket 92. The cohesion of these components can be ensured by a tension spring 93. There is a defined starting position of the combination lever 90, which is illustrated in the extended position shown in the schematic FIGS. 20, 21, 22 and again determines an alignment plane 23 indicated by dash-dotted lines in these figures. The combination lever 90 has a shoulder 94 which can be seen in FIG. 18 and which meets the working arm 14 illustrated in FIG. 18 in the alignment plane 23 when the handle is actuated in the direction of the arrow 17. In this case, the pivoting movement of the combination lever 90, which is indicated by the arrow 26, comes about again. The combination lever 90 takes a rod 18 leading to the lock, which is attached to a special point of attack 95 provided on it.

This attachment is carried out by an arc-shaped tab 95, which is provided on the combination ched 90 and has an elongated hole 96, as shown in FIGS. 18 and 22. This slot 96 is positively penetrated by a pin 97 of a connecting member 98, which takes the rod 18 with it when pivoting 29 of the combination lever 90 and thereby opens the lock. 18, the connecting member 98 is shown in the uncoupled position relative to the tab 95. With this pivoting 26, an axle pin 101 plays a role, which engages in a laterally open receptacle 99 on the housing shown in FIG. 17 and is also illustrated in FIGS. 20 and 21. This receptacle 99 practically consists of a U-hook, the hook opening of which forms the receptacle 99. In the initial case l, according to FIG. 20, the axle pin 101 is in axial alignment with the ball joint 91, which is drawn in dash-dot lines in FIG. 20 in a coaxial position with the axle pin 101. Axle pin 101 is kept pressed in the base of hook-shaped receptacle 99 by tension spring 93. When pivoting via the actuated handle, the axle pin 101 on the combination lever 90 is moved into the pivot position 101 'indicated by dashed lines t. Because of the tension spring 93 in FIG. 20, however, the axle pin is returned to its starting position 101 at the inner end of the receptacle 99 after the handle has been released.

Also with this closure, a ZV-Ghed 100 is provided, the appearance of which in the individual drawing of FIG Scheme can be seen in Fig. 21. In this case, the guide curve is designed as a groove-like forced guide 103 for a guide pin 102 which, as shown in FIG. 18, is located on the combination lever 90, essentially in a parallel position to the axis pin 101. This can also be seen in FIG. 21 , where the ZV-G ed 100, drawn in solid lines, is in its effective position. During the aforementioned pivoting movement 26 of the combination lever 90 in the alignment plane 23, the guide pin 102 also moves radially from the forced guide 103 cut free at this point in FIG. 21 into the pivoted position 102 ', which is indicated by the dashed lines, and which is also indicated in FIG. 20 .

However, if the ZV-Ghed 100 in FIG. 21 is moved into its ineffective dash-dotted position 100 'in the sense of the rotary arrow 104, the guide pin moves to the position 102 ", also shown in dash-dotted lines in FIG. 21. The guide pin 101 now determines in the Because of the receptacle 99 together with the ball joint 91, a vertical axis of rotation 108 in FIG. 21, through which the combination lever 90 is transferred into its bent position 90 ″, indicated by dash-dotted lines, in the sense of the double arrow 107. The entire combination lever 90 "is now in the angled plane 23" illustrated in FIG. 21, where it can no longer be actuated by the working arm 14 belonging to the handle 10 as in FIG. 18. In this bending plane 23 ", the combination lever 90" with its shoulder 94 of FIG. 18 is outside the movement path 17. The combination lever 90 "can no longer be pivoted. The associated lock remains at rest.

This rotary adjustment 104 of the ZV-Ghed in FIGS. 21 and 19 can again be carried out either via the key through the cylinder core 33 also shown in FIG. 2 or via the drive member of a central locking system, for which the ZV-Ghed 100 has a suitable point of attack 109 . The ZV-Ghed 100 also has locking lugs 105, 106 which can be seen in FIG. 19 and which lock it in certain rotational positions on the cylinder housing 32 of the locking housing 31 of FIG. 17, as was the case in the previous exemplary embodiment with reference to the locking elements explained in FIG. 10b 63 and 56, 56 'was explained. In all other respects, the same conditions prevail as in the first exemplary embodiment. 22 shows the meaning of the special connection 98 described on the tab 95 of the combination lever 90. If the combination lever is in its angled position 90 ″, the slot 96 in the link 95 allows an undisturbed rotary movement 107 from the alignment plane 23 into the angled plane 23 ". The rod 18 leading to the castle remains at rest.

In this case too, in the safe position, as has been explained in the schematic drawing of FIG. 12b, the control heddle 40 is drawn from the clutch plane 69 drawn in FIG. 22 in the sense of the lifting arrow 77 via control curves on the house side from the one shown in FIG. 22 dash-dotted clutch level 69 lifted into the uncoupling level 67 also shown there. In this decoupling plane 67, the control head is supported at the end of the uncoupled coupling projection 35 from the cylinder core 33 and can be returned by the pulse-compression spring 46, which is also provided in this case, to the normal position 40 "Safe", indicated by dash-dotted lines in FIG. 22. Now the control ghed is supported with its abutting surface 54 on the combination lever located in its angled position 90 ", as indicated by" Safe "in Fig. 22. When the control ged 40 is in the preceding coupling plane 69, where it is in Fig. 22 is drawn in an extended manner, the abutting surface 54 is axially set back and therefore the combination lever 90 is returned to its rest position shown in an extended state in Fig. 22. Then the control lever 40 is again engaged with the coupling projection 35 of the cylindrical core 33. This corresponds to that in Fig. 10b starting situation explained.

Reference symbol list:

Handle handle housing trough handle plate of 10 working arm of 10 (rest position) 'working position of 14 shaft for 10 arrow of actuation of 10 arrow of downward movement of 14 attack arrow, pull rod return spring for 20 transmission link from 21, 22 first lever, swivel lever (rest position)' Swivel position of 21 "deflection position of 21 second lever, lever (rest position) 'Swivel position of 22 alignment level of 21" deflection level of 21 "swivel bearing from 20 to 31 swivel joint between 21, 22, pin arrow of the swivel movement of 20 torsion spring between 21, 22 key channel in 33 radial nose on 39 cylinder axis lock housing cylinder housing of 31 cylinder core key first coupling part, coupling protrusion on 33 lock in 33 (Fig. 13b) locking channel in 38 channel sleeve sliding ring control member (normal position) 'first working position of 40 "second working position of 40"' Limit position of 40, 41 'lifting cams on 40 switching cams on 40 (normal position)' first working position of 4 2 ", 42"'limit position of 42 (Fig. 1 1 b) arrow of the axial force on 40 (Fig. 1 1b), 44 'stop surface on 41 or 41' second coupling part, coupling receptacle on 40 pulse spring of 40 lock washer first spring leg of 46 second spring leg of 46, 50 'microswitch control curve from 32 for 41, 52' assembly point for 50 or 50 'leading edge from 21 for 53 (Fig. 6)' butt edge from 21 for 54 (FIG. 6) abutting surface on 40, 55 'switching element of 50 or 50', 56 'latching recess for 60 or 60' rotary arrow between 23, 23 "(FIG. 8) flank on 41 for 48 (FIG. 2) Flank for 49 at 39 (Fig. 2) ZV-G ed (effective position) 'ineffective position of 60 point of attack for central drive at 60 distance between 64, 64' (Fig. 3) guide curve at 60 (in active position) ' ineffective position of 63, 64 'end stop at 60 for 44, 44' thrust guide for 60 in the diagram (Fig. 10b) grid elevation at 60 for 63 or 63 'uncoupling level of 40 (Fig. 12b) axial offset distance between 67, 69 coupling level of 40 (Fig. 12b) zero position of 33 first working position of 33, secured position second work position of 33, unlocked position limit position of 33 third working position of 33, safe position of the arrow at 71 in Fig. 71 (Fig. 10a) 'counter-rotation arrow of the key in 72 (FIG. 10a) rotation arrow of the key in 73 or 74 (FIG. 11a, 12a) stroke arrow of 40 (FIG. 11b, 22) reversal path between 60, 60' (FIG . 12b) Long groove for 29 in 31 (Fig. 13b) compression spring for 39 (Fig. 13b) lifting profile, overload lifting in 39 lifting profile in 38, overload recess spring force of 80 opening in 38 (Fig. 14b) synchronization ghed, roller rotating arrow of 33 (Fig. 15a) first cut-out for 85 in 31 (Fig. 15b) second cut-out for 85 in 33 supporting end face of 39 (Fig. 14b) combination lever (rest position, Fig. 18) "angular position of 90 (Fig. 21) ball joint, Ball head on 31 (Fig. 17) ball joint, ball socket on 90 (Fig. 18) tension spring between 31, 90 shoulder on 90 for 14 (Fig. 18) point of attack on 90 for 18, backdrop 96 slot in 95

97 pins on 98

98 link between 18 and 95 (Fig. 18)

99 recording at 31 for 101

100 ZV link (effective position)

100 'ineffective position of 100 (Fig. 21)

101 axle pin at 90 (starting position) 101 'pivot position of 101 (FIG. 21)

102 Guide pin at 90 (effective position) 102 'swivel position from 102

102 "ineffective position of 102 (Fig. 21)

103 positive control for 102 in 100

104 arrow of 100 (Fig. 21)

105 latch on 100

106 latch on 100

107 rotation between 90 and 90 "(Fig. 22)

108 axis of rotation from 90 for 107 (FIG. 21)

109 point of attack for central transmission (Fig. 19)

Claims

Patent claims *

1. closure for doors, hoods, flaps or the like, in particular of vehicles, such as motor vehicles,

with a locking cylinder, the cylinder core (33) of which can be rotated into three working positions (71, 72, 74) by means of a proper key (34) from a zero position (70), which is determined by an impulse spring (46), namely one unlocked (72), a secured one

(71) and a safe position (safe position 74),

with a handle (10) which, when actuated, in the unlocked position

(72) of the cylindrical core (33) meets a pivotably mounted (26) transmission member (20) and opens a lock connected to the transmission member (20), but does not hit in the secured position (71) and safe position (74) and that Makes the lock inaccessible,

with a central locking gear (ZV-G ed 60) which is rotatably mounted coaxially to the cylinder core (33) and which can be turned by turning the key (75, 75 ', 76) of the gear core (33) as well as directly on the ZV-Ghed (60 ) attacking (61) central drive of a central locking device with respect to the ZV-Ghed (60) between an effective (60) for the lock actuation and an ineffective position (60 ') is adjustable, but in the safe position (74) not from its ineffective (60 ') can be transferred into its effective position (60)

and with a switching cam (42) which is moved by the cylinder core (33) by means of a key rotation (75, 75 ', 76) and which, during the transition between the zero position (70) and the secured (71) and possibly unlocked (72) position of the tooth core ( 33) actuates a microswitch (50, 50 ') of an electrical device of the vehicle, such as an anti-theft alarm system, characterized,

that a control gear (40) carrying the switching cam (42) can be adjusted by turning the key (76) via control means (41, 41 ', 51) between two spaced planes (69, 67),

namely, on the one hand, a clutch plane (69), in which the control geth is coupled (35, 45) to the cylinder core (33) in the zero position (70) and in the secured (71) and unlocked (72) position,

and on the other hand a decoupling plane (67) into which the control gate (40) reaches the safe position (74) at the transition and is then uncoupled from the cylinder core (33),

that the pulse spring (46) with the Steuer ed (40) is always connected to the switching cam (42) in one with the zero position (70) of

To spring back normal core (33) aligned normal position, namely in the two levels (69, 67), namely

with a small turn of the key (75, 75 ') between the zero position (70) and the secured (71) or unlocked (72) position in the coupling plane (69) with actuation of the microswitch (50, 50')

and with a large key rotation (76) into the safe position (74) in the decoupling plane (67) at a free distance (68), without actuating the microswitch (50),

that, in the two planes (69, 67), the Steuerghed (40) with the ZV-Ghed (60) is always coupled by two end stops (64, 64 '), the one in the distance between the effective (60) and inactive position (60 ') of the ZV-G eds corresponding distance (62) to each other,

that at least a part (21) of the transmission member (20) is not only pivotable (26), but also rotatable transversely thereto (57) and the ZV-G member (60) has a guide track (63) which rotates the Part (21) of the transmission link (20)

on the one hand, when the ZV-Ghed is in an effective position (60), spring-loaded (27) in an alignment plane (23) aligned with the handle (10) so that it can pivot (26),

but on the other hand, in the ineffective position (60 ') of the ZV-Ghed, against the spring load (27), pushes it away into an angled plane (23 ") offset from the handle and does not make it pivotable (26),

and that when the cylinder core (33) is in safe position, the rotatable part (21) of the transmission member (20) is held in the angled plane (23 ") by an abutment surface (54) provided on the control geth (40) even when the ZV -Ghed by the central drive from its ineffective (60 ') to its effective position (60).

2. Closure according to claim 1, characterized in that the control gate (40) between its coupling and decoupling plane (69, 67) is axially movable in the direction of the cylinder axis (77) and - in the safe position (74) of the cylinder core ( 33) - is held against an axial spring force (43) by the uncoupled coupling part (35) in its decoupling plane (67).

3. Closure according to claim 2, characterized in that the control means for the axial stroke (77) of the control member (40) between its coupling and decoupling plane (69, 67) consist of at least one lifting cam (41, 41 ') through an axial spring force (43) is pressed against a control cam (51) fixed to the housing.

4. Closure according to claim 3, characterized in that the switching cam (42) is arranged in the radial extension of the lifting cam (41) on the control heddle (40).

5. Closure according to claim 3 or 4, characterized in that the lifting cam (41) also carries the abutment surface (54) with which the rotatable part (21) of the transmission member (20) in the safe position (74) of the cylinder core (33) m the ineffective angular position (21 ") is held.

6. Closure according to one or more of claims 3 to 5, characterized in that the rare flanks of two diametrically provided lifting cams (41, 41 ') form the stop faces (44, 44') for the ZV-Ghed (60).

7. Closure according to one or more of claims 1 to 6, characterized in that the pivoting actuating direction (16) of the handle (10) extends substantially in a parallel plane to the cylinder axis (30), while the actuating (16) of the handle (10) certain swivel plane (26) of the transmission member (20) is arranged in a radial plane running perpendicular to the cylinder axis (30) (alignment plane 23).

8. Closure according to claim 7, characterized in that the angled plane (23 ") of the rotatable part (21") of the transmission member (20) inclined to the cylinder axis (30).

9. Closure according to one or more of claims 1 to 8, characterized in that the transmission member (20) consists of two levers (21, 22), namely a on the housing (31) pivotally mounted lever (22) on the one hand and an articulated thereon ( 24), which can be actuated by the handle (10), on the other hand, the pivot lever (21) having on one arm a guide edge (53) for the guide track (63) provided on the ZV-Ghed (60) and has a butt edge (53 ') for the butt surface (54) provided on the control heddle (40).

10. Closure according to one or more of claims 1 to 8, characterized in that the transmission member consists of a single combination lever (90) which is spatially movable by means of a ball joint (91, 92), namely when actuated (16) by the Handle (10), in a swivel plane (alignment plane 23) running perpendicular to the cylinder axis (30) and, by actuating (104) the ZV-G eds (100) or of the control element (40) rotated by the key, can be rotated (107) into an inclination plane (23 ") which is inclined thereto.

1 1. Closure according to claim 10, characterized in that the combination lever (90) has an axle pin (101) which is mounted in a fixed, laterally open receptacle (99) and together with the ball joint (91, 92) the axis of rotation ( 108) for rotating the combination lever (90) into the angled plane (23 "), and the axis pin (101) when pivoting (107) the combination lever through the handle (10) in the swivel plane (alignment plane 23) from the opening of the receptacle ( 99), against a restoring spring force (93), pivots out (101 ').

12. Closure according to claim 10 or 1 1, characterized in that the combination lever (90) has a guide pin (102) which engages in the guideway designed as a positive guide (103) from the ZV-Ghed (100).

13. Closure according to one or more of claims 1 to 12, characterized in that in the housing (31, 32) of the Schheßzyhnders a channel sleeve (38) is axially fixed but rotatable (86), which encloses the cylinder core (33) and at least has a blocking channel (37) for the tumblers (36) in the cylinder core (33),

that axially next to the channel sleeve (38) in the housing (31, 32), a sliding ring (39) is axially movably and non-rotatably mounted, which likewise encloses the cylinder core (33) and is axially supported by a compression spring (80) against the end face of the channel sleeve (38) is printed

that a lifting profile (81, 82) is arranged between the channel sleeve (38) and the sliding ring (39), which connects the two parts (38, 39) in a rotationally fixed manner up to a load limit, but in the event of an overload the two parts (38, 39) lost against the compression spring (80),

and that the sliding ring (39) with its lifting profile (81) opposite end (89) is directed against the control gate (40) and in the event of an overload, the control gate (40) is printed in its decoupling plane (67).

14. Closure according to claim 13, characterized in that an opening (84) is arranged in the channel sleeve for free accommodation of a synchronization member (85) and the synchronization member (85) both in the housing (31, 32) and in the cylinder core (33) A recess (87, 88) is assigned to each

and upon rotation (75, 75 ', 76) of the cylinder core (33) with a proper key (34) the synchronization ghed (85) into the recess

(87) of the housing (31, 32) evades and fixes the channel sleeve (38) in the housing (31, 32), but releases the cylinder core (33) (Fig. 16a),

in the event of an overload, the synchronization element (85) into the recess

(88) of the cylinder core (33) evades and connects the channel sleeve (38) to the cylinder core (33) in a rotationally fixed manner (Fig. 16b).

15. Closure according to claim 14, characterized in that the synchronization ghed is a disk-shaped roller or ball (85).