EP0752044A1

EP0752044A1 - Cylinder lock designed particularly for vehicles

Info

Publication number: EP0752044A1
Application number: EP95912215A
Authority: EP
Inventors: Erwin Uecker
Original assignee: Huelsbeck and Fuerst GmbH and Co KG
Current assignee: Huf Huelsbeck and Fuerst GmbH and Co KG
Priority date: 1994-03-28
Filing date: 1995-03-07
Publication date: 1997-01-08
Anticipated expiration: 2015-03-07
Also published as: CN1145103A; CN1075588C; CZ273296A3; WO1995026453A1; ATE166128T1; AU1949095A; CZ290567B6; ES2116083T3; KR100400534B1; BR9507253A; DE4410783C1; DE59502177D1; EP0752044B1; JPH09510759A; KR970702416A; JP3693064B2; AU684621B2

Abstract

The lock proposed has a cylinder made up of a sleeve and a core. The core is locked to the sleeve by means of tumblers when the key is withdrawn and carries one of the elements of a longitudinal two-element coupling. When the inserted key is turned, the cylinder core is rotated and this movement is transmitted to the other element of the two-element coupling which is non-rotatably linked to an engaging lug. It is the engaging lug which carries out the vehicle-locking function. Although the cylinder sleeve is rotatably mounted in a fixed housing, it is normally prevented from rotating in the housing by means of a catch which acts as an overload protection mechanism. The catch consists of a male and a female snap-in element on the cylinder sleeve, which are spring-biased with respect to each other and normally engage in each other along a longitudinal section and can be disengaged. When turned by force, the male catch element is disengaged out of the female catch element and the cylinder is brought into a freely turning overload condition within the housing. At the same time, the two coupling elements are detached from each other. So that the cylinder does not move longitudinally in the event of an overload, the invention proposes that the cylinder sleeve is mounted in the housing so that it cannot move longitudinally. While the male catch element of the overload protection mechanism cannot be rotated, it can be displaced along the longitudinal axis of the housing. The longitudinally acting spring bias acts on the male catch element in the direction towards the female catch element which cannot move longitudinally in the housing. The coupling element mounted on the cylinder core also cannot move longitudinally, but the other coupling element can move longitudinally together with the male catch element against the bias of the spring.

Description

Locking device with a locking cylinder for a locking function that can be performed in particular on motor vehicles

The invention is directed to a locking device of the type specified in the preamble of claim 1. The design of the axial coupling and the overload protection ensure that the actuation of the locking functions can only be carried out using the correct key inserted into the cylinder core of the locking cylinder, not but through manipulation using a burglary tool. The cylinder core can be rotated by the break-in tool, but because the tumblers are not sorted into the circumference of the cylinder core, the cylinder guide is also taken along. The overload protection of the locking device ensures that the lock cylinder is freewheeled in the housing. The latching and counter-latching part of this overload safety device automatically lift axially and also release the axial coupling between the cylinder core and the driver. As a result, the violent rotation of the locking cylinder cannot result in a rotation of the driver. The overload safety device prevents the closure device from being damaged in the event of violent attempts to break open. Therefore, the device can later be used again with a proper key to perform the locking functions in the motor vehicle.

In the known closure device of this type (DE-OS 41 22 414), the overload protection was found between the cylinder guide and the housing. The axial spring load was effective between the housing and the cylinder guide. The counter-locking part located on the cylinder guide was axially displaceable in the housing during violent applications. During this axial displacement, the cylinder core was of course also moved axially, because it must always be axially fixed in the cylinder guide. Depending on whether the locking mechanism of the overload safety device was arranged at the front or rear end of the cylinder guide, the locking cylinder of the known device moved either axially outwards or axially inwards when the overload was freewheeling. That is undesirable. Due to large axial forces, in some cases the overload protection can remain engaged when using intrusion tools and the tumblers can be sheared off when the intrusion tool is turned violently. As a result, the closing functions can ultimately be undesirably exercised via the intrusion tool. In addition, the locking cylinder is destroyed by shearing the tumblers and the device cannot be operated again using a key. This risk of breaking open can be reduced by a lifting profile with particularly flat flanks, but functional problems then arise.

The invention has for its object to develop an inexpensive, compact locking device of the type mentioned in the preamble of claim 1, in which the locking cylinder no longer moves axially in the event of an overload. 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 cylinder guide is axially fixed in the housing and therefore the counter-latching part of the overload protection located on it is also axially fixed. The associated locking part of this overload protection is not an integral part of the housing, but a separate part that can be moved axially in the housing. However, the housing has an axial guide, in which this latching part is positioned axially displaceably but non-rotatably. The axial guide now acts axially on this separate latching part and loads it in the direction of the counter-latching part of the cylinder guide already axially fixed in the housing.

In the case of the invention, the cylinder core also remains axially fixed in the housing in the event of an overload, because it is axially fixedly rotatably mounted in its cylinder guide. Finally, the coupling member of the axial clutch connected to the cylinder core is axially fixed, while the mating coupling member connected to the driver is axially displaceable together with the latching part are. If the latching part is pushed back against the axial spring load in the event of an overload, the counter-coupling member is automatically released from the coupling member of the axial coupling which is axially fixed to the cylinder core. In the case of the invention, the lock cylinder does not perform any axial movements even in the event of an overload. The front end of the cylinder core can always be flush with the housing.

Further measures and advantages of the invention can be found in the further claims, the description and the drawings. The invention is shown schematically in several exemplary embodiments in the drawings. Show it:

1 shows an axial section through a first embodiment of the locking device according to the invention, shown only schematically, in a normal case where the cylinder core is actuated via a properly inserted key,

2 shows an axial section corresponding to FIG. 1, but if there is an overload where the cylinder core is actuated by force using an intrusion tool,

3, also in a schematic representation, a cross section through the device along the section line III-III of FIG. 1,

4 shows, in a parallel section offset with respect to the cylinder axis, along the jumped section line IV-IV of FIG. 3, the top view of the inner parts of the device when the normal case of FIG. 1 is present,

5 in a sectional view corresponding to FIG. 4, the conditions resulting from the overload case of FIG. 2,

6 shows a further schematic cross section through the device along the section line VI-VI of FIG. 1,

7 shows a partial cross section through the device in the event of an overload in the event of an overload along the further section line VII-VII of FIG. 2,

8 shows an inner, axial section of the device of FIG. 1 in the area of an axial coupling, with a partial breakout when the normal case of FIG. 1 is present,

9 in a representation corresponding to FIG. 8, the conditions of the overload case according to FIG. 2,

10 in an axial section similar to FIG. 4, an alternative embodiment of the overload protection device, with the omission of other disturbing components,

1 1 in an axial section corresponding to FIG. 1, an alternative embodiment of the closure device according to the invention, when the normal case is present,

FIG. 12, in a representation analogous to FIG. 2, the axial section of the device shown in FIG. 1 1 when the overload is present,

FIG. 13 in a parallel section analogous to FIG. 4, the conditions in the area of the overload protection and

14 shows, in a representation corresponding to FIG. 5, the conditions of the alternative device in the area of the overload protection when there is an overload case according to FIG. 12.

The closure device according to the invention shown in FIGS. 1 to 9 is preferably installed in motor vehicles and comprises a lock cylinder which consists of a cylinder guide 20 and a cylinder core 10 axially fixed therein. This axially fixed connection is illustrated, according to FIG. 2, by an inner collar 21 in the cylinder guide 20, which engages in an annular groove 12 of an axial bolt 11 that extends the cylinder core 10. The cylinder core 10 has a key channel 13, which can be seen in FIG. 8, for receiving a key 15, which can be seen in FIG. 1, and a group of spring-loaded, best seen in FIG. 2 Tumblers 14. When the key is removed, as shown in FIG. 2, the tumblers 14 are pressed radially outward and, due to their spring loading, engage in a locking channel 24 due to the spring loading acting on them. In the exemplary embodiment shown, two opposing blocking channels 24 are provided, into which the tumblers 14, which come diametrically out of the cylinder core 10, enter and lock the cylinder core 10 with the cylinder guide 20.

When the key 15 is inserted, the tumblers 14 are sorted onto the circumference of the cylinder core 10, which is shown in FIG. 1 can be seen. Then the cylinder core 10 is rotatable in the cylinder guide 20. When the key 15 is actuated, the rotation is transmitted to a driver 23 in a manner to be described in more detail, via a coupling member 31 of an axial coupling 30 that can best be seen in FIGS. 2 and 8. The driver 23 is transferred via the key 15 from the rest position shown in solid line in FIG. 3, in the sense of the pivoting arrows 27, 27 ', into one or more working positions 23', 23 ", which are shown in FIG. 3 The driver 23 carries out the desired locking functions via further lock members (not shown in more detail) by pivoting 27 or 27. The coupling member 31 is seated on the axial bolt 11, and is therefore rotationally and axially fixed to the cylinder core 10 The driver 23 sits, secured by a snap ring 22, axially fixed on the axial bolt 11.

The cylinder guide 20 is in itself rotatably mounted in a stationary housing 16, but normally, according to FIGS. 1 and 4, is rotationally fixed in the housing 16 via a special locking mechanism 40 to be described in more detail. The axially fixed position of the cylinder guide 20 in the housing 16, with which the cylinder core 10 is likewise axially fixed in the housing 16 via the aforementioned axially fixed connection 12, 21 of the cylinder guide 20, is significant. This is illustrated in FIG. 1 by a widened cylinder head 17 on the cylinder core 10 and an inner collar 18 in the housing 16. The cylinder head 17 can always lie flush with the outer housing 16 in the area of the key, which is emphasized in FIGS. 1 and 2 by a dash-dot line 39.

In the first exemplary embodiment from FIGS. 1 to 9, the coupling member 31 of the axial coupling 30 interacts with a pressure ring 33, which coupling member 32 of the axial clutch 30 carries. The pressure ring 33 sits on the axial bolt 1 1 and is longitudinally displaceable in the housing 16 in the sense of the arrow 34 shown in FIGS. 2 and 5. The pressure ring 33 is also non-rotatably but axially displaceably connected to the driver 23. In this first exemplary embodiment, the driver 23 always assumes an axially fixed position relative to the housing 16 and is located in front of the inner housing front end 19. The rotationally fixed and axially displaceable connection mentioned between the pressure ring 33 and the driver 23 is shown in FIG. 1 and 4 illustrated by an axial nose 35 on the pressure ring 33 and two axial fingers 25 on the driver 23. The two fingers 25 determine an axial groove 26 between them for guiding the annular nose 35.

Finally, the pressure ring 33 is under the action of an axial spring load illustrated by the arrow 50 in FIG. 1. This is generated by a helical spring 51, which also fulfills the further function of an "impulse spring". The inner end of the spring 51 is supported axially in the area of the axial bolt 11, which is the case in the exemplary embodiment in FIG.

I takes place indirectly via the driver 23 which is supported on the snap ring 22. The spring 51 encloses the axial bolt with its windings

I I and rests with its outer end on the pressure ring 33. The spring 51 has two essentially radially extending spring legs 52 which, according to FIG. 3, grip the two fingers 25 of the driver 23 mentioned between them. The two legs also encompass an axial web 19 provided in the housing 16, which is formed between two radial openings 53 in the housing 16 which are arranged in alternation with one another. The driver is held in the extended position shown in FIG. 3 by the spring legs 52 resting against the web 19. The spring legs 52 exert the mutually directed tangential forces illustrated by the force arrows 54 on the fingers 25, which leads to the described rest position 23 of the driver in FIG. 3. When the key is actuated in the two working positions 23 'and 23 ", the two fingers 25 take the respective spring leg against the effective tangential force 54, as illustrated by the dash-dotted end positions 52', 52" in FIG. 3.

The locking mechanism 40 serves as an overload protection to be explained in more detail of the lock cylinder 10, 20 and, as can best be seen from FIGS. 2 and 5, comprises a locking part 41 and a counter-locking part 42, which have a normally interlocking axial lifting profile. In this exemplary embodiment, the latching part consists of a loose body, which is designed here as a ball 41, namely two such balls 41 are provided in a position diametrically opposite one another, as shown in FIG. 2. In this case, the lifting profile is essentially provided in the counter-latching part and consists of an axial recess 43 on the inner end face of the cylinder guide 20. The recess 43 is delimited on both ends by inclined flanks 44, as best shown in FIG. 4. The two balls 41 are pressed by the mentioned, axial spring load 50 in the direction of the cylinder guide 20, the counter-latching part 42 of which is axially fixed on the cylinder guide 20, but, like the cylinder guide 20 itself, is rotatable in the housing 16 with it.

The two balls 41, however, experience their axial spring load 50 indirectly via the pressure ring 33. For this purpose, the pressure ring has an end gradation according to FIG. 9, consisting of a stepped peripheral zone 36 on the one hand and a flat, radial shoulder surface 37 on the other. The two balls 41 run on the offset surface 36 and lie against the radial shoulder surface 37, from which they receive the axial spring load 50. In addition to the aforementioned longitudinal displaceability 34 of the pressure ring 33 shown in FIG. 2, the two balls 41 are also axially displaceable. 2 and 6, the two balls 41 protrude radially beyond the pressure ring 33 and each engage in an axial groove 45 which is provided in a diametrically opposed position on the inner surface of the housing 16. The balls 41 are thus axially guided, but cannot be rotated with the pressure ring 33. 1 and 4, the balls 41 are arranged in the same axial zone of the pressure ring 33 as the axial clutch 30, but are set radially outward relative to the counter-coupling member 32 located in the pressure ring. This takes place in that the recess of this mating coupling member 32, according to FIG. 6, is axially recessed in the stepped end of the pressure ring 33 and is covered towards the balls 41 by the peripheral surface 36 of the paragraph described. In FIGS. 8 and 9, this required cutouts to show this coupling recess 32. 1, where the cylinder guide 20 is held non-rotatably in the housing 16 via the engaging locking mechanism 40. This results because, according to FIG. 4, the balls 41 are held in the axial groove 45 on the one hand and are located in the axial recess 43 of the counter-locking part 42 on the other hand. The components 20, 41 therefore normally rest in the housing 16. As already mentioned, the tumblers are sorted into the position 14 ′ shown in dashed lines in FIG. 1 via the correct key inserted in the cylinder core 10. Therefore, the cylinder core 10 can be rotated in the cylinder guide 20 using the key 15. This rotation is transmitted from the axial bolt 11 via the engaged axial coupling 30 to the pressure ring 33 and the pressure ring 30 takes the driver 23 with it when it rotates via the described rotationally fixed connection 35, 25 from FIG.

However, this changes when unauthorized persons use an intrusion tool 55 indicated in FIG. B. a screwdriver, a violent rotation of the cylinder core 10. As has already been described, there is a rotationally fixed connection between the cylinder core 10 and the cylinder guide 20 according to FIG. 2 via the extended tumblers 14. When turning violently, the overload protection of the locking mechanism 40 now comes into effect, as shown in FIGS. 2 and 5. The ball 41 is lifted out of the axial recess 43 of the cylinder core 20 at a defined torque via the inclination of the inclined flank 44 and moves onto the inner end face 28 of the cylinder guide 20.

Because the cylinder guide 20, as has already been mentioned several times, is axially fixed in the housing 16, according to FIG. 5, the pressure ring 33 is pushed back axially against the axial spring force 50 of the spring in the direction of the arrow 34 already mentioned. The axial nose 35 located on the pressure ring 33 moves into the axial gap 26 between the two fingers 25 of the driver 23. Because of this longitudinal displacement 34 of the pressure ring 33, the axial coupling 30 is also released, as can be seen from FIG. 2. The coupling member 31 located on the cylinder core 10 remains stationary axially, but the pressure coupling-side counter-coupling member 32 moves away from it in the sense of the longitudinal displacement arrow 34 already mentioned. Via the intrusion tool 55, the cylinder core 10 is together with the cylinder guide 20 in the sense of the arrow 29 shown in FIG. 2 rotated in the housing 16, but without this rotation 29 can have an effect in a corresponding actuation of the driver 23. The axial clutch 30 is namely released. The locking cylinder 10, 20 is in an overload freewheel. The spring 51 described, together with the inclination of the inclined surfaces 44, determines the limit value in the locking mechanism 40 at which the overload free-running of the locking cylinder 10, 20 occurs. This limit value is dimensioned in such a way that there is definitely no damage to the tumblers 14 of the cylinder core 10 which engage in the blocking channels 24. The lock cylinder remains operable via the key 15 after the ineffective break-in attempts have ended. It is noteworthy that the entire locking cylinder 10, 20 does not change its axial position in the housing 16 illustrated by the dash-dot line 39 in FIGS. 1 and 2.

The pressure ring 33 can only be rotated in the axial position of FIG. 1 in the housing 10 in its axial position coupled to the cylinder core 10, but is non-rotatably guided in the housing 16 even with a small displacement in the direction of the decoupling position shown in FIG. 2. An axial projection 38 on the pressure ring 33, best seen in FIGS. 8 and 9, and two radial ribs 48, best seen in FIG. 3, on the inner surface of the housing 16 are used for this purpose. The projection 38 is in the normal case, according to FIG Distance to the end of the ribs. However, if the longitudinal displacement 34 of the pressure ring 33 shown in FIG. 2 takes place, the projection 38 moves into the axial gap 49 between the two radial ribs 48 shown in FIG. 3, as can best be seen from the sectional view of FIG. 7. 2, the pressure ring 33 is therefore non-rotatably positioned in the housing 16. However, this means that because of the rotationally fixed connection 25, 35, the driver 23 also remains non-rotatably positioned in the housing 16 via the pressure ring 33. Manipulations in the area of the driver 23 are therefore unsuccessful, regardless of the intrusion tool 55.

A modified embodiment of the locking mechanism 40 'is shown as the second exemplary embodiment of FIG. 10. The same reference numerals as in the first exemplary embodiment from FIGS. 1 to 9 are used to designate corresponding components. In this respect, the previous description applies. The opposite Locking part 42 of the overload protection on the cylinder guide 20 is in the same way designed as a recess 43 with inclined surfaces 44. It is sufficient to only consider the differences of this locking mechanism 40 '.

The associated locking part 41 'is part of a special ring body 46 shown in FIG. 10, which is guided axially displaceably in the housing. The ring body 46 has two radial lugs 47 which engage in the two axial grooves 45 already mentioned on the inner surface of the housing 16. The locking part 41 'is profiled and in this case has an outline which is complementary to the described lifting profile of the counter-locking part 42. The annular body 46 is penetrated by the axial bolt 11, which can be freely rotated relative to the annular body 46 in the violent rotation 29 explained in connection with FIG. 2. In the space next to the ring body 46 of FIG. 10, for example, the pressure ring 33 described in the previous exemplary embodiment can be arranged, which, however, then no longer has the balls 41 described above. The described axial clutch 30 is then designed in a similar manner to that in the previous exemplary embodiment, namely between the axial bolt 11 and the pressure ring 33. The embodiment according to FIG. 10 could, however, also be applied to the next device which is now to be described.

11 to 14 show a third exemplary embodiment of the closure device according to the invention. Here, too, the same reference numerals are used to designate corresponding components as in the previous exemplary embodiment, which is why the previous description also applies to this extent. These figures correspond to the figures 1, 2 and 4 and 5 of the first embodiment. It is enough to only consider the differences.

The axial spring load 50 acts here via the driver 56 on the latching part of a latching device 40, which in this case is also formed as balls 41 and which has the analog overload protection already described in connection with the first exemplary embodiment in the use of force according to FIG. 12 causes. In this case, the inner end of the spring 51 is supported on the axial bolt 11 via the snap ring 22, while the outer end of the spring acts on the driver 58. Here is the driver 58 axially offset and, like the pressure ring 33 in the first exemplary embodiment, has a radially offset circumferential zone 56 which can be seen in FIG. 14 and an adjacent radial shoulder surface 47. The balls 41 of the locking mechanism are again seated in axial grooves 45 from the housing, run on the peripheral zone 56 and are supported on the sales surface

57 from.

Although the axial coupling 30 'is similar in shape and effect to that in the first exemplary embodiment, the difference is that the counter-coupling element 32', which is shown in broken lines in FIGS. 12 and 13, is a fixed component of the driver 58. The driver too

58 has an axial projection 59 which, in the normal case, according to FIG. 11, is arranged at an axial distance from the radial ribs 48 provided in the interior of the housing. In the event of an overload, as shown in FIG. 12, the projection moves

59 of the driver 58 into the free gap between the two radial ribs 48 and ensures that the driver 58 cannot be rotated in the housing 16. The arm 60 protruding from the driver 58, which is responsible for the execution of the locking functions, is therefore in the transition to an overload situation of Fig. 12 rotatably fixed relative to the housing 20.

Another difference of this third exemplary embodiment from FIGS. 11 to 14 is that the longitudinal displacement 34 in the case of overloading from FIG. 12 results in a corresponding displacement 34 of the entire driver 58. However, this axial displacement 34 of the arm 60 is of no importance for the closing function, because in the case of an overload of FIG. 12, the mentioned non-rotatability of the driver 58 is secured via the components 48, 59. You could also use this axial displacement 34 of the driver arm 60 to also set the arm 60 in freewheel with the subsequent lock member. This longitudinal displacement 34 of the driver 58 has no effect on the front area of the device of FIGS. 11 to 14. As can be seen, the cylinder guide 20 and the cylinder core 10 located therein remain in an unchanged, axially fixed position, as is also illustrated there by the corresponding dash-dot lines 39 in FIGS. 11 and 12.

Reference symbol list:

Cylinder core Axial bolt Ring groove Key channel tumbler (in locking position) '' release position of 14 keys, housing widened head of 10 inner collar of 16 inner end face of 16 cylinder guide inner collar on 20 snap ring carrier (rest position) '' first working position of 23 "second working position of 23 locking channel in 20 for 14 axial finger of 23 axial gap between 25 for 35 swivel arrow for 23 to 23 '' swivel arrow for 23 to 23 "inner end face of 20 violent rotation, rotary arrow (Fig. 9) axial coupling (Fig. 1 to 9) 'axial coupling (Fig. 1 1 to 14) coupling member of 30 mating coupling member of 30, recess 'mating coupling member of 30' in 58 pressure ring longitudinal displacement arrow axial nose on 33 offset peripheral zone of 33 radial heel surface, radial surface of 33 axial projection on 33 dash-dot line of 10 in 16 locking device Overload protection '' locking mechanism (Fig. 10) locking part, loose body, ball '' locking part on 46 (Fig. 10) opp rest of 40 (Fig. 1 to 9; 10) axial recess of 42 inclined surface in 43 axial groove in 16 ring body for 41 '(Fig. 10)

REPLACEMENT BLART (RULE 26) radial shoulder on 46 inner radial rib on 16 axial gap between 48 arrow of the axial spring load pressure pulse spring spring leg of 51 (in rest position) 'first working position of 52 "second working position of 52 breakthrough in 16 tangential force of 52 burglary tool (Fig. 2; 12 ) offset circumferential surface of 58 radial heel surface on 58 axially movable driver (FIGS. 11 to 14) axial projection on 58 working arm of 58

ERSATZBLAI7 (RULE 26)

Claims

P a t e n t a n s r u c h e:

1. Locking device with a locking cylinder for locking functions which can be carried out in particular on the motor vehicle,

The locking cylinder has a cylinder guide (20) and a cylinder core (10), which is axially fixed in rotation and serves to receive a key (15),

the cylinder core (10), when the key (15) is removed, can be locked with the cylinder guide (20) via spring-loaded tumblers (14) and is firmly connected to the one coupling member (31) of a two-part axial coupling (30),

the cylinder core (10) transmits its rotation via the coupling member (31) to a counter-coupling member (32) of the axial clutch (30), which is non-rotatably connected to a driver (23), and the Driver (23) has the function performed in the motor vehicle,

the cylinder guide (20) is rotatably mounted in a stationary housing (16), but is normally rotatably fixed there by a locking mechanism (40), which serves to protect against overload, and consists of at least one locking element (41) and a counter-locking element (42) the cylinder guide (20) exists,

and the locking and counter-locking part (41, 42) are axially spring loaded (50) to each other and have a normally interlocking axial lifting profile which, when turned violently (29), sets the cylinder guide (20) into an overload freewheel in the housing (16) and the axial coupling (30) releases,

characterized, that the cylinder guide (20) is axially fixed in the housing,

the latching part (41) of the overload protection device (40) is non-rotatably (43) but axially displaceable (34) in the housing (16),

the axial spring load (50) acts on the latching part (41), while the counter-latching part (42) seated on the cylinder guide (20) is axially fixed in the housing (16),

and the coupling member (31) of the axial coupling (30) connected to the cylinder core (10) is also axially fixed via its axially fixed mounting in the cylinder guide (16),

while the counter-coupling member (32), which is rotationally fixed to the driver (23) (25, 35), together with the latching part (41), against its spring load (50), are axially displaceable (34).

2. Device according to claim 1, characterized in that the Federbe¬ load (50) via a pressure ring (33) acts on the locking part (41), the pressure ring (33) carries the mating coupling member (32) of the axial coupling (30) and with this is axially displaceable (34) in the housing (16) (FIGS. 1 to 6).

3. Apparatus according to claim 2, characterized in that the Druck¬ ring (33) of the cylinder core (10) extending axial bolt (11) is penetrated and the coupling member (31) rotatably and axially fixed on the axial bolt (11), ( 1 to 6).

4. Apparatus according to claim 2 or 3, characterized in that the pressure ring (33) is non-rotatably but axially displaceable (34) with the driver (23) and the driver (23) rotatably sits on the axial bolt (11), ( 1 to 6).

5. The device according to one or more of claims 2 to 4, characterized in that the pressure ring (33) only in its with the cylinder core (10) coupled axial position (coupling position) in the housing

REPLACEMENT BLAπ (RULE 26) (16) is rotatable, but is already axially guided (38, 48) in the housing (16) in the housing (16) during the displacement (34) in the direction of its decoupled axial position (decoupling position).

Device according to one or more of claims 2 to 5, characterized in that the latching part (41) of the overload safety device (40) bears on an essentially flat radial surface (37) of the pressure ring (33).

Device according to Claim 1, characterized in that the axial spring load (50) acts on the latching part (41) via the driver (58), the driver (58) carries the counter-coupling member (32 ') of the axial coupling (30') and with this in the housing (16) is axially displaceable, (Fig. 1 1 to 14).

Apparatus according to claim 7, characterized in that the Mitneh¬ mer (58) is freely rotatable through an axial bolt (1 1) extending the cylinder core (10) and the coupling member (31) of the axial coupling (30 ') rotates and axially fixed on the axial bolt (1 1), (Fig. 1 1 to 14).

Apparatus according to claim 7 or 8, characterized in that the driver (58) can only be rotated in its axial position (coupling position) in the housing (16) coupled to the cylinder core (10), but already when it is moved (34) in the direction of its decoupling ¬ pelte axial position (decoupling position) is non-rotatably (48, 59) in the housing (16) axially guided (Fig. 1 1 to 14).

10. The device according to one or more of claims 1 to 9, characterized in that the lifting profile of the overload safety device (40) is only provided on the counter-locking part (42) and from at least one axial recess (43) with bilateral oblique flanks (44) in a radial surface (28) on the cylinder guide,

the locking part consists of at least one loose body (41), which normally from the pressure ring (33) or the driver (58) in the

ERSÄΓZBLAΓT (RULE 26) Recess (43) is pressed in axially (50),

and the loose body (41) projects radially beyond the pressure ring (33) or the driver (58) and engages in an axial groove (45) on the inner surface of the housing (16) (FIGS. 4, 13).

11. The device according to claim 10, characterized in that the loose body consists of a ball (41), (Fig. 1).

12. The apparatus according to claim 10 or 11, characterized in that the latching part consists of two individual balls (41),

to which two recesses (43) in the cylinder guide (20) and two axial grooves (45) in the housing (16) are assigned,

and the two recesses (43) and the two axial grooves (45) are each in a diametrical position in the cylinder guide (20) or in the housing (16), (Fig. 6).

13. The device according to one or more of claims 10 to 12, characterized in that the loose body (41) is at least partially in the same axial zone of the pressure ring (33) as the axial coupling (30), but opposite that in the pressure ring (33 ) located, engaging counter-coupling member (32) of this axial coupling (30) is set radially outwards.

14. The device according to one or more of claims 1 to 9, characterized in that the counter-latching part (42) of the overload protection (40 ') consists of at least one recess (43) in a radial surface (28) of the cylinder guide (20),

the recess (43) is delimited on both sides by inclined flanks (44) and forms one half of the lifting profile,

SPARE BLADES (RULE 26) while the latching part (41 ') is formed by an annular body (46) which is axially displaceably guided in the housing (16) and carries at least one latching projection,

which is profiled complementary to the recess (43) and forms the other half of the lifting profile (40 ') (FIG. 10).

15. The device according to one or more of claims 1 to 14, characterized in that the same axial spring load (50) both on the axial coupling (30) and on the locking and counter-locking parts (41, 42) of the overload protection (40) each acts in the sense of intervention.

16. The apparatus according to claim 15, characterized in that the axial spring load (50) also serves as a pulse spring (53) which ensures an angularly defined rest position (23) of the driver, (Fig. 3).

17. The apparatus of claim 15 or 16, characterized in that the axial spring load (50) is supported at the other end on an axial shoulder (22) which is axially fixed to the axial bolt (1 1), (Fig. 11).

REPLACEMENT BLAπ (RULE 26)