EP1084322A1

EP1084322A1 - Closing device for closing functions in vehicles in particular

Info

Publication number: EP1084322A1
Application number: EP99925013A
Authority: EP
Inventors: Reinhard Wittwer; Mathias LÖW
Original assignee: Huf Huelsbeck and Fuerst GmbH and Co KG
Current assignee: Huf Huelsbeck and Fuerst GmbH and Co KG
Priority date: 1998-05-30
Filing date: 1999-05-20
Publication date: 2001-03-21
Anticipated expiration: 2019-05-20
Also published as: EP1084322B1; CN1303458A; ES2171329T3; BR9910839A; AU4144899A; WO1999063187A1; JP2002517641A; US6439016B1; SK17072000A3; SK286193B6; CZ298358B6; CZ20004423A3; CN1211555C; JP4221691B2; AU747009B2; PT1084322E

Abstract

The invention relates to a closing device (71), wherein the closing cylinder (70) comprises a free bushing (20) and a core (10) that is provided with followers (15). The free bushing (20) is rotationally mounted in a housing (30). Normally, said bushing is rotationally fixed by a spring-loaded locking and controlling member (61') pertaining to an overload interlock (60). The closing functions are carried out by means of a working member (50) that co-operates with a rotationally fixed displaceable slider (40) that is arranged in the working member (50). In order to create a space-saving device (71) that has a low axial construction height, the locking and control member (61') is placed in a radially free position and loading is carried out directly by means of a blade-shaped spring (37). This enables the locking and controlling member (61') to be displaced independently from the slider (40) in a section of the cylinder where the followers (15) are also arranged. An axial connection (80) allows the spring loading to be transmitted from the overload interlock (60) to the slider (40).

Description

Locking device for locking functions that can be performed in particular on vehicles

The invention is directed to a locking device of the type specified in the preamble of claim 1. If the proper key is fully inserted in the cylinder core and the key is turned, the rotation is transmitted in this direction to a working member which acts on a lock and there locking functions executes. If the locking cylinder is turned violently by burglary tools, an overload lock ensures that the cylinder core is rotated together with the freewheel sleeve, but this rotation is not transmitted to the working member. As a result, a closing function is not carried out. In addition, in the event of an overload, manipulation of the working member is also not possible because it is in a locking position; it is held in the housing. This overload protection ensures that the north direction is not damaged in the event of violent opening attempts using burglary tools; the device is then ready to be operated as intended using a proper key. Devices of the type specified in the preamble of claim 1 (DE 44 12 609 A) have proven themselves, but have the disadvantage of a relatively large axial length. In this direction, the overload lock must be arranged in an axial extension of the cylinder core, which is arranged behind the cylinder section having the tumblers. The slide is arranged in a recess of the working member designed as a lever. A compression spring must also be arranged in the recess, which is supported between the slide and the working member and generates the radial spring load for the locking control member of the overload lock there. The spring load of the overload lock is therefore generated indirectly via the slide. For reasons of space, the compression spring can only be made small, which is why its radial spring loading is limited. In order to set this spring load effectively, the slide has an axial tab which is supported on the locking control element. The supporting tab of the slide is in the same section as the locking control link. In the same axial section are also the locking surfaces between a locking tongue provided on the slide and an outer sleeve of the housing and finally also an inner sleeve of the housing with the radial cutout for the locking control member. In addition to the overload lock, the known north direction also had a detent position designed as a roller, which was pressed into a detent recess of the freewheel sleeve by a leaf spring. This latching position was axially removed from the overload lock and could have no control effects on the slide. The known north direction was space-consuming and could not exert a sufficiently high spring load on the overload lock.

The invention has for its object to develop a reliable, space-saving Norrichtung of the type mentioned in the preamble of claim 1, which is characterized above all by a small axial length. This is achieved according to the invention by the measures specified in the characterizing part of claim 1, which have the following special significance. In the invention, the locking control member can be arranged independently of the location of the slide and can therefore be easily arranged in that cylinder section of the cylinder core where the tumblers are also located. This saves an axial space in the north direction. In this cylinder section, the locking control member is exposed radially outward and is covered by a leaf-shaped spring which directly exerts the radial spring force of the overload lock on the locking control member. The slide can be axially removed from the locking control member. The spring load of the overload lock, which now acts independently of the slide, can be as large as desired by appropriately dimensioning the leaf-shaped spring. In addition, it is now also readily possible to use the same or a separate leaf-shaped spring to effectively set a plurality of locking control elements in the overload lock, for example a diametrically arranged pair of elements. The spring loading of the leaf-shaped spring acting directly on the locking control member is used in the invention to control the slide. An axial connection is used for this, which bridges the distance between the slide and the locking control element. This axial connection can be designed in various ways, each of these options having its own inventive meaning.

A first possibility for this axial connection is set out in claim 6. This consists of an actuator which is arranged radially outside of the housing and is either formed in one piece with the leaf-shaped spring acting on the locking control element or is connected in several pieces but in one unit. If the locking control element lifts out of the radial recess of the freewheel sleeve in the event of an overload, the actuator and the spring carry out a common radial movement and this movement is transmitted to the slide via the actuator.

A second possibility for the axial connection is set out in claim 2. she consists of a direct positive connection between the locking control member and the slide. In this case, the spring acting on the locking control element has a double function. On the one hand, as already mentioned in connection with claim 1, it serves as a radial spring load of the overload lock. Due to the positive locking, the spring also has the new function of generating the restoring force already mentioned in the preamble of claim 1, which keeps the slide pressed in its coupling position. In the event of an overload, the slide is transferred to its locking position via this form fit, in which the slide is fixed in the housing and at the same time the working member is locked in the housing. A particularly simple embodiment of this form-fitting connection between the slide and the locking control element results from claim 3.

Further measures and advantages of the invention result from the subclaims, the following description and the drawings. The invention is illustrated in three exemplary embodiments in the drawings. Show it:

Fig. 1 shows a schematic longitudinal section through a first

Embodiment of the device according to the invention along the section line I - I of FIG. 2, but when the key shown in FIG. 2 is removed,

Fig. 2 shows a first cross section through the device along the

Section line II - II of Fig. 1, but after the correct key has been inserted,

3 shows a second cross section through the device of FIG. 1 along the section line III - III there,

Fig. 4 is a longitudinal section corresponding to FIG. 1 through the

Device if, due to a violent rotation of a intrusion tool, not shown, an overload lock has been brought into a freewheeling position,

Fig. 5 is a cross section according to FIG. 2 executed along the

Section line V - V of FIG. 4 through the device with inserted burglary tool when the device is in the freewheel position of FIG. 4, and

Fig. 6 shows a second cross-section analogous to Fig. 3 in its

4 located along the section line VI - VI,

Fig. 7, in analogy to Fig. 1, a longitudinal section through a second

Embodiment of the nor direction according to the invention, the cutting of which is illustrated by the cutting line NU - NU in FIG. 8, but again with the key removed,

Fig. 8 shows a cross section through the north direction of Fig. 7 along the

Section line NIII - VIII, after the correct key has been reinserted,

Fig. 9 is a perspective view of the device according to the invention of Fig. 7 and

Fi 'sg. 10 shows an axial section through a third device according to the invention, likewise only shown schematically, with the key removed, in a modification of the device shown in FIG. 7.

The three devices 71, 72, 73 shown in FIGS. 1 to 10 are preferably installed in vehicle doors and have regard to their Lock cylinder 70 has a substantially matching structure. The locking cylinder 70 initially consists of a freewheel sleeve 20 and a cylinder core 10 which is axially fixedly mounted therein. The axially fixed connection is produced by inner shoulder surfaces between the components. For this purpose, the cylinder core is offset and comprises a widened cylinder head 11, a cylinder section 12 having spring-loaded tumblers 15 and a radially offset cylinder end 13. The cylinder core 10 has a key channel 14 for receiving a key 16, which is only shown in cross section in FIG. 2 16 pulled out, the tumblers 15 are pressed radially outwards due to their spring loading and engage, as shown at 15 'in FIG. 2, in locking channels 22 of the freewheel sleeve 20. Then the cylinder core 10 is locked with the freewheel sleeve 20.

The freewheel sleeve 20 is rotatably supported by a stationary cylindrical housing 30, but is normally prevented from doing so by an overload lock 60 in the housing 30. The freewheel sleeve 20 is therefore normally fixed in the housing 30. A working member 50 is rotatably mounted on the cylinder end 13. In the first device 71, the working member 50 consists of a shaft which is axially fixed to the cylinder end 13 by a mounting means 65 which can be seen in FIG. 1. The working member 50 engages with a tab 66 in a recess 67 of a slide 40 which can best be seen in FIG. 3, the meaning and mode of operation of which will be described in more detail below. This results in the rotationally fixed connection shown in FIG. 3 between the working member 50 and the slide 40.

Normally, the cylinder core 10 is in a zero position shown in FIGS. 1 and 2, which can be determined, for example, by a pulse spring 75 shown in FIG. 1. With its windings, the impulse spring 75 wraps around the working member 50 and its two legs, and grips two axial tabs 68, 74 between the slide 40 and the housing 30 between them. In the zero position, the correct key 16 can be inserted into the key channel 14 or again be pulled out. When the key is inserted, the tumblers 15, as shown in FIG. 2, are sorted onto the circumference of the cylinder core 10. Then the cylinder core 10 is rotatable in the direction of arrow 18 in the freewheel sleeve 20. When the key 16 is actuated, the cylinder core can then be transferred to various angular positions which correspond to specific working positions of the gearwheel 50 and the lock in engagement therewith. This rotation 18 of the cylinder core 10 is normally transmitted to the working member 50 in the following way.

The already mentioned slide 40 is located on an inner end face of a shoulder surface between the cylinder section 12 and the cylinder end 13 of the freewheel sleeve 20 and the housing 30, as a result of which a radial guide 54 is created for the slide 40. The slide 40 is force-loaded in the direction of arrow 44 of FIG. 3, which occurs in a special way in this device 71 and will be explained in more detail. The dome surfaces 17, 47 shown in FIG. 1 come into engagement with one another. The dome surface 47 belonging to the slide 40 consists of a nose pointing into the recess 67 which engages in a radial recess 17 in the region of the cylinder end 13. As a result, the starting rotational position of the working member 50 is also defined in the zero position of the cylinder core 10. During the key-related rotation 18 of the cylinder core 10, the working member 50 is rotated by the cylinder core 10 via the engaged coupling 17, 47 and 66, 67 and thereby performs the desired locking functions on the lock members.

The above-mentioned overload lock 60 has the following special structure shown in FIGS. 1 and 2. In the present case, this includes two blocking control elements 61, 61 ', the number of which can be increased as required or can only be replaced by one element. In the present case, the two links, as can best be seen from FIG. 2, are arranged diametrically with respect to one another and oriented in a mirror-image manner to one another. They are in the direction of the two arrows 33, 33 'in the direction of the Dash-dotted cylinder axis 19 of FIG. 1 is spring-loaded. Because of their identical structure, it is sufficient to consider the locking control element 61.

The locking control member 61 in the present case consists of a rolling element, namely a roller. This roller 61 is loosely located in a radial cutout 31 of the housing 30 which is adapted to its outline dimensions intervenes.

The above-mentioned spring load 33 in the device 71 is based on a slotted annular spring 37 which, as shown in the cross section shown in FIG. 2, largely encloses the housing 30 in a radial plane, namely the sectional plane II-II of FIG. 1, and with it the ring slot separated, radially resilient ring segments are supported on the two locking control members 61, 61 '. The associated radial cutout 31 in the housing is namely open to the outer surface 77 of the housing shown in FIG. 2, which is why the two locking control members 61, 61 'are exposed with their respective radial outer ends 63 and are covered by the leg ends of the slotted annular spring 37. The ring spring thus acts directly on the locking control member 61 or 61 'and thus exerts the radial spring loading 33 or 33' of the overload lock 60. The two locking control members 61, 61 'are located radially next to the axial section having the tumblers 12. This applies not only to this device 71 but also to the two alternative devices 72 and 73 shown in FIGS. 7 and 10. In all three cases 71 to 73, the slide 40 is arranged in an axially offset section 69 of the locking cylinder 70, 1 and 7 show, but there is an axial connection between one of the two members 61 'and 61 and the respective slide 40, which is different from one another in the devices 71 to 73. In the exemplary embodiment of the device 71 from FIGS. 1 to 6, there is a positive connection 80 between the locking control member 61 'and the slide 40. This connection 80 consists, as can best be seen from FIG. 3, of an axial pin 81 which engages in a link guide 82 of the slide 40. The length of the link guide 82 takes into account the extent of the rotational movement 18 provided by the cylinder core 10. Through this form fit 80, the spring load 33 'acting directly on the locking control element 61' according to FIG. 2 also has an indirect effect on the slide 40; there arises the already mentioned restoring force 44 shown in FIG. 3, which normally holds the mentioned coupling surfaces 17, 47 in their engaging coupling position.

This control of the slide 40 by the locking control member 61 'applies not only to the normal case but, as is apparent from FIGS. 4 to 6, also to the overload case. If, by means of an intrusion tool 16 'indicated in FIG. 5, a violent rotation 18' is exerted on the cylinder core 10 according to FIG. 5, the tumblers 15 are locked in the locking channels 22 of the freewheel sleeve 20, as already mentioned. As a result, both components of the lock cylinder 70, namely the cylinder core 10 together with the freewheel sleeve 20, are rotated 18 'in the housing 30. This is possible because the overload lock 60 reaches the freewheeling position shown in FIG. 5 when a torque is exerted during the violent rotation 18 ′ that exceeds a certain limit value. This limit is determined by the spring loading 33, 33 'and the profile of the two radial recesses 21 and 21' in the freewheel sleeve 20 which can be seen in FIG. 5. The radial recesses 21, 21 'have a suitable lifting profile from which the rollers 61, 61' turn when this limit torque is exceeded. Then the roller 61 changes from the normally present engagement position according to FIG. 2 to the lifting position shown in FIG. 5 in the event of an overload. The two ends of the slotted annular spring 37 are spread apart, as a result of which the spring load 33, 33 'of the links 61, 61' increases. The members 61, 61 'roll on the peripheral region 64 of the freewheel sleeve 20 during the rotation 18'. In order to be able to withstand the surface pressure at the high spring load 33, 33 ', the radial recesses 21, 21' in the freewheel sleeve 20 are provided with steel inserts 78. In the event of an overload, the spreading movement of the locking member 61 'is transmitted to the slide 40 by the pin 81 of the positive connection 80, as can be seen from FIG. 6. In this case, locking surfaces 42 provided on the slide 40 come into engagement with counter-locking surfaces 32 of the housing 30. These counter-locking surfaces 32 consist of a slot 76 of the axial tab 74, which can be seen in FIG. 3. The locking surfaces 42 of the slide 40, on the other hand, consist of a radial one Nose 79 from the slide 40. In the event of an overload, the slide 40 is locked. Due to the described positive engagement between the working member 50 and the slide 40 via the mentioned tab 66, the working member 50 is also locked in the event of an overload according to FIG. 6. In this locking position, the coupling surfaces 17, 47 are uncoupled between the slide 40 and the cylinder core 10; in the event of an overload, the cylinder core 10 rotates in freewheel mode. There is no entrainment of the working member 50. The device 71 therefore does not perform a closing function in the vehicle despite the rotation 18 ′ of the cylinder core 10.

This device 71 has the advantage that the spring loading 33, 33 'of the overload lock 60, as has already been said, also automatically generates the restoring force 44 for the slide 40. An additional spring which resets the slide 40 is saved. In the device 71, the leaf-shaped ring spring 37 has a double function. It should also be noted that the connection 80 in the exemplary embodiment of the device 71, the described movement of the locking control member 61 'between the engaged position of FIG. 2 and the lifting position of FIG. 5 for the complete control movement of the slide 40 between its coupling position in FIG Fig. 3 and its locking position of Fig. 5 is used. In the two other devices 72, 73 there is partial control of the slide 40 by the locking control member 61 there of the same structure, it is sufficient for the devices 72, 73 to only deal with the differences. In all other respects, the description of the device 71 applies.

In the devices 72, 73, the working member 50 'consists of a gear, which can best be seen from FIG. 9. The gearwheel 50 is supported on the rear end of the housing 30, a clip connection 51 or the like being able to ensure that the components are held together axially. The gear wheel 50 has a circumferential toothing 52, which is in meshing engagement with further lock members, not shown in detail, the position of which is illustrated by the arrow 53 in FIG. 7. As best shown in FIG. 9, a radial guide for a slide 40 is integrated into the gearwheel 50. As best shown in FIG. 7, there is a receptacle 55 for a compression spring 45 in the guide 54. The compression spring 45 is supported on opposite radial shoulders 46, 56 of the slide 40 and the guide 54. As a result, the slide 40 is loaded in the direction of the arrow 44 in FIG. 7.

In the second device 72 shown in FIGS. 7 to 9, there is an indirect axial connection 83 between the locking control member 61 there and the slide 40, for which an actuator 23 is used. In this exemplary embodiment, this actuator consists of a spring tongue 23 which is arranged radially outside the housing 30 and which generates the spring load 33 of the overload lock 60 already described. This applies mutatis mutandis to the diametrically opposite locking control member 61 ', which has its own spring tongue 23'. The spring tongues 23 and 23 'are fastened with their one tongue end 24 in the circumferential area of the housing 30 and can be pivoted with their opposite free spring ends 25 in a radial plane of the locking cylinder, which is illustrated by the sectional plane VII - VII of FIG. 8. One spring tongue 23 is provided with an extension 35, which in this case also performs control functions on the slide 40. The slider 40 projects radially beyond the cylindrical housing and has a radial shoulder 41 which extends from the Extension 35 of the actuator 23 is engaged. The aforementioned compression spring 45 ensures permanent contact at 41 between the extension 35 of the actuator 23 and the slide 40.

The actuating movement of the locking control member, likewise formed here as a roller 61 or 61 ', between the engaged position of FIGS. 7 and 8 and a lifting position not shown in detail, but which results in analogy to FIG. 5, is in this case also via the transmit axial connection 83 on the shoulders 40. This causes the spring tongue 23, which is supported on the outer end 63 of the roller 61. The locking surfaces 32, 42 also provided here come into their locking position between the slide 40 and the housing 30. The gear 50 'is then locked in rotation. The return movement of the slide 40 from such a locking position into the coupling position of FIG. 7 is done actively by the compression spring 45, but in coordination with the retraction movement of the spring tongue 23.

As can be seen from FIG. 7, the locking point 32 for the slide 40 in the housing 30 is arranged radially closer to the cylinder axis 19 than the previously described contact point 41 between the slide 40 and the free tongue end 25. The gear 50 'is located, as shown in FIG. 9 shows, at the inner end 27 of the cylinder core 10; it is coaxial with the cylinder axis 19, rotatably mounted on the cylinder journal 13 there. The attachment point 34 of the tongue 23 is located on the opposite, outer end region 28. The cylinder head 11 located there is covered by a dust cap 29. An elastic ring seal 39 in an annular groove between the cylinder head 11 and the housing 30 provides protection against dirt.

It goes without saying that the number of the rollers 61, 61 'determining the limit torque and the associated spring tongues 23, 23' could be any number. Several such tongues 23, 23 'could also be generated by an axially slotted spring washer, which is a common fastening of all tongues in the circumferential area of the Housing 30 allows. Instead of a flexible spring tongue 23, one could also use a pivotable arm which is spring-loaded by spring means in the direction of the cylinder axis 19 and which produces the spring load described by the arrows 33 and 33 '.

The third embodiment of the device 73 according to the invention shown in FIG. 10 is partly designed in accordance with the second exemplary embodiment according to FIGS. 7 and 8 and partly with the first exemplary embodiment according to FIGS. 1 to 6. As far as the same reference numerals are used, the previous descriptions apply. It is enough to deal with the differences. The radial spring force 33, 33 'is also generated in this case by a slotted ring spring 37 which transmits via the support point 43, 43' to the two links 61, 61 ', of which the 61 again performs control functions.

In the event of an overload, the annular spring 37 widens radially; it "breathes" during the transition from normal to overload. The ring spring 37 has, on its ring inner surface 57, as shown in FIG. 10, various support points 43, 43 'for the individual locking members 61, 61'. Furthermore, the ring spring 37 is axial approach provided 48 which cooperates in the manner already described in connection with the preceding embodiment analogous manner at the contact point 41 with the slider 40. the freewheel sleeve 20 has, as Fig. 6 shows a peripheral groove 49 into which a for its part in _'a engages the snap ring 58 or the like seated in the radial receptacle 59 of the housing 30. This snap ring 58 ensures axial cohesion between the stationary housing 30 and the freewheel sleeve 20 which is rotatable therein in the event of an overload. Reference list

Cylinder core cylinder head of 10 cylinder section of 10 with 15 cylinder end of 10 key channel for 16 in 10 tumbler in 12 (sorted position) 'locking position of 15 (Fig.2) key for 10' burglary tool (Fig.5) coupling surface of 10, radial recess key- Rotation of 10 (normal case) 'violent rotation of 10 and 20 (overload, Fig. 5) cylinder axis of 10 freewheel sleeve, 21' radial recess in 20 locking channel in 20 for 15 actuator, spring tongue, leaf-shaped spring 'second spring tongue fixed tongue end of 23 free end from 23

inner end of 10 outer end area of 10 dust cap on 12 (Fig. 7) housing, 31 'radial cutout in 30 for 61, 61' counter-locking surface on 30 for 40 , 33 'arrow of the spring load of 23 or 23' fastening point for 24 extension of 23 axial offset between 61 and 61 '(Fig. 10) slotted ring spring (Fig. 2 and 10)

Ring seal between 12, 30 (Fig. 7) slide radial shoulder for 25, contact point locking surface on 40 for 30, 43 'support point from 37 to 61, 61' (Fig. 10) arrows of the restoring force of 40 (Fig. 3) compression spring for 44 radial shoulder for 45 on 40 coupling surface of 40 axial shoulder on 37 for 40 (Fig. 10) circumferential groove in 20 (Fig. 10) working member, pin (Fig. 1 to 6) 'working member, gear (Fig. 7 to 9) clip connection between 10, 50 '(Fig. 7 to 10) circumferential teeth of 50 arrow for lock members on 50 radial guidance from 40 to 50, 50' receptacle for 45 in 54 radial shoulder for 45 on 54 ring inner surface of 37 (Fig. 10) snap ring (Fig 10) radial mounting in 30 (FIG. 10) overload lock, 61 'lock control element for 60, roller Radial inner end of 61 radial outer end of 61 circumferential area of 20 mounting means between 13, 50 (Fig. 1) tab of 50 (Fig. 1, 3) recess in 40 (Fig. 1, 3) tab on 40 (Fig. 1) section of 40 at 70 (Fig. 1, 7) lock cylinder first device second device third device tab on 30 (Fig. 1) pulse spring slot for 32 in 74 (Fig. 3) housing outer surface (Fig. 2) steel insert in 21, 21 '(Fig. 5) radial nose for 42 to 40 (FIG. 2) positive axial connection in 71 (FIGS. 1, 3) axial pin on 61 ′ (FIG. 3) link guide for 81 in 40 (FIG. 3) indirect connection between 40, 61 in 72 or 73 (FIG. 7)

Claims

P atent claims:

1. Locking device (71, 72, 73) for locking functions that can be carried out in particular on vehicles, with a locking cylinder (70),

wherein the locking cylinder (70) comprises a freewheel sleeve (20) and an axially fixed cylinder core (10) with a cylinder section (12) having tumblers (15).

and the tumblers (15) can be controlled by inserting a key (16) and lock (15) the cylinder core (10) with the freewheel sleeve (20) when the key (16) is removed,

with a stationary housing (30) which rotatably accommodates the freewheel sleeve (20), but in which the freewheel sleeve (20) is normally rotationally fixed by a radially spring-loaded (33) locking control member (61; 61 ') of an overload lock (60). is,

wherein the locking control member (61; 61 ') is located loosely in a radial cutout (31; 31') of the housing (30) and - in the normal case - with its radial inner end (62) due to the radial spring load (33) in a , a radial recess (21; 21 ') of the freewheel sleeve (20) which has a lifting profile engages, but - in the event of an overload - moves from this engagement position, against its spring load (33), into a lifting position in the peripheral area (64) of the freewheel sleeve (20),

with a working member (50) that carries out the closing function in the vehicle and with a slide (40) connected to the working member (50; 50') in a rotationally fixed but displaceable manner, which is normally in a rotationally fixed coupling position with the cylinder core (10) due to a restoring force (44), but in the event of an overload it is uncoupled by means of the locking control element (61; 61') and into one in the housing (30). reaches a rotationally fixed locking position, in which the working member (50; 50') may also be locked (32, 42),

characterized ,

that the radial opening (31; 31') for the locking control member (61; 61') is open to the housing outer surface (77) and the locking control member (61; 61') is exposed radially outwards, but is covered by a leaf-shaped spring (37; 23, 23 '),

wherein the spring (37; 23, 23') is arranged in the peripheral area of the housing (77) and acts directly on the locking control member (61; 61'),

that the locking control member (61; 61') is arranged radially next to the cylinder section (12) of the cylinder core (10) which has the tumblers (15),

and that the slide (40) lies in a section (69) of the locking cylinder (70) which is axially offset relative to the locking control member (61) and an axial connection (80; 83) determines the distance between the locking control member ( 61; 61') and the slider (40).

2. Device (71) according to claim 1, characterized in that there is a direct, positive connection (80) between the locking control member (61 ') and the slide (40). and that the spring (37) of the overload lock (60) acting on the locking control element (61 ') at the same time generates the restoring force (44) through the positive connection (80), which brings the slide (40) into the coupling position with the cylinder core (10) presses.

3. Device (71) according to claim 2, characterized in that the positive connection (80) consists of an axial pin (81) on the locking control member (61 ') and a link guide (82) in the slide (40). , whereby the pin (81) engages in the link guide (82).

4. Device (71, 72, 73) according to one or more of claims 1 to 3, characterized in that the axial connection (80; 83) between the locking control member (61; 61 ') and the slide (40 ) is arranged in the same section of the locking cylinder (10) as the coupling means (17, 47) between the slide (40) and the cylinder core (10) and / or the locking means (42, 32) between the slide (40) and the housing (30).

Device (71, 72, 73) according to one or more of claims 1 to 4, characterized in that to increase the force exerted by the spring (37) of the overload lock (60) on the locking control member (61; 61 '). Surface pressure the radial recess (21) in the freewheel sleeve (20) is provided with a steel insert (78).

6. Device (72, 73) according to claim 1, characterized in that an actuator (23) creates an indirect axial connection (83) between the locking control member (61) and the slide (40), wherein the actuator (23) is arranged radially outside the housing (30) and is connected to the spring (23) of the overload lock (60) acting on the locking control member (61) and is movable together with it.

7. Device (72, 73) according to claim 6, characterized in that the slide (40) projects radially beyond the cylindrical housing (30).

and that the actuator (23) engages behind a radial shoulder (41) of the slide (40).

and that the slide (40) is force-loaded (44) in the direction of contact of its contact point (41) with the actuator (23).

8. Device (72, 73) according to claim 6 or 7, characterized in that the locking point (42, 32) between the slide (40) and the housing (30) is arranged radially closer to the cylinder axis (19) than the contact point (41) between the slide (40) and the actuator (23).

9. Device (72, 73) according to one or more of claims 6 to 8, characterized in that the actuator (23) consists of a one-piece or multi-piece extension (35) of a resilient tongue (23),

and that the tongue (23) can be pivoted in a radial plane of the locking cylinder (70) and is sprung (33) in the direction of the cylinder axis (19).

0. Device (71, 73) according to one or more of claims 1 to 9, characterized in that the spring of the overload lock (60) is a particularly slotted annular spring (37) which encloses the housing (30) in a radial plane

and that the ring spring (37) with a ring segment is supported on the locking control member (61; 61 ') and exerts the radial spring force (38) on the locking control member (61; 61 ').

11. Device (73) according to claim 10, characterized in that the annular spring (37) has an axial extension (48) which cooperates with the slide (40).

12. Device (71, 72, 73) according to one or more of claims 1 to 14, characterized in that the overload lock (60) has two or more locking control elements (61; 61 ') with its own radial breakout (31, 31 ') in the housing (30) and with its own radial recesses (21, 21 ') in the freewheel sleeve (20).

13. Device (71, 72, 73) according to claim 12, characterized in that the individual locking members (61, 61 ') are arranged evenly distributed over the circumference of the locking cylinder and that in the case of two locking members (61, 61 ') these are relative to each other lie diametrically.

14. Device (72, 73) according to claim 12 or 13, characterized in that the various locking members (61, 61 ') are arranged on the lock cylinder in an axial offset (36) to one another.

5. Device (72, 73) according to one or more of claims 1 to 14, characterized in that the working member is a gear (50 ') which is rotatably mounted on a stepped inner end (13) of the cylinder core (10).

and that a radial guide (54) for the slide (40) is integrated into the gear (50 ').

16. Device according to one or more of claims 1 to 16, characterized in that the locking control member (61; 61 ') is a rolling body, such as a roller (61) or a ball.