Classifications

• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
  • E05B13/00—Devices preventing the key or the handle or both from being used
  • E05B13/10—Devices preventing the key or the handle or both from being used formed by a lock arranged in the handle
  • E05B13/105—Devices preventing the key or the handle or both from being used formed by a lock arranged in the handle the handle being a pushbutton
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
  • E05B27/00—Cylinder locks or other locks with tumbler pins or balls that are set by pushing the key in
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
  • E05B17/00—Accessories in connection with locks
  • E05B17/0054—Fraction or shear lines; Slip-clutches, resilient parts or the like for preventing damage when forced or slammed
  • E05B17/0058—Fraction or shear lines; Slip-clutches, resilient parts or the like for preventing damage when forced or slammed with non-destructive disengagement
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
  • E05B17/00—Accessories in connection with locks
  • E05B17/04—Devices for coupling the turning cylinder of a single or a double cylinder lock with the bolt operating member

Definitions

• Locking device with a locking cylinder which also serves as a pressure handle for actuating lock members
• the invention is directed to a locking device of the type specified in the preamble of claim 1, the locking cylinder of which has two different functions to perform.
• One function is to use key actuation to switch a cylinder core in a cylinder guide that rotates around it between a secured and an unlocked rotational position.
• the reversing movement of the cylinder core is transmitted to a driver, which only interacts with the lock members in the unlocked rotational position, but not in the secured rotational position.
• the second function of the lock cylinder is to be a push handle which, like a push button, is pressed axially into a cylinder housing against a spring force acting on it and actuates lock members when the aforementioned unlocked rotational position of the cylinder core is present.
• the known printing handle consisted only of the lock cylinder.
• the cylinder guide was rotatable, but axially fixed to the cylinder guide, and the driver was seated in a rotationally fixed and axially fixed manner directly on the cylinder core in order to carry out the key-related turning reversals starting from the cylinder core.
• the axial spring force forming the pushbutton effect had a direct effect on the cylinder guide of the lock cylinder.
• the lock cylinder was axially displaceable for the push-button effect via its circumferential cylinder guide, it was also non-rotatably guided in a cylinder housing.
• the locking cylinder of the known locking device serving as a printing handle direction were at risk of burglary.
• the guides and the tumblers located in the cylinder core could be damaged by violent rotation of the cylinder core using an intrusion tool such that the lock cylinder could no longer be used.
• An exchange of damaged individual parts of the device was often not sufficient, but required the complete replacement.
• the locking cylinder In the event of violent rotary movements of the cylinder core via a burglary tool, where the cylinder core is locked to the cylinder guide via the extended tumblers located therein, the locking cylinder is moved axially via the lifting profile. This axial displacement is used to disengage an axial coupling between the rotating member and the cylinder core. Then the locking cylinder is in the overload freewheel, can be rotated freely and does not take the rotating element with it.
• this known overload lock to devices of the present type, the locking cylinder of which also functions as a pressure handle, is not possible.
• This lock cylinder must namely be operated manually against the axial spring force acting on it in order to achieve, via its cylinder core, the required axial movements of the driver provided for this type of lock, which should only interact axially with the lock members in the unlocked rotational position. It was therefore considered necessary to dispense with an overload freewheel in the case of printing handle locking cylinders.
• the invention has for its object to develop a reliable, space-saving closure device of the type mentioned in the preamble of claim 1, which is not endangered by attempts to break open and a survives violent turning of his lock cylinder without damaging his components. This is achieved according to the invention by the measures specified in the characterizing part of claim 1, which have the following special significance.
• the printing handle consists of two axial sections, both of which are radially divided into two.
• the locking cylinder consequently forms only the axial outer section of this new printing handle and, in contrast to the known locking cylinders of this type, which are indirectly axially guided, is freely rotatably mounted in the cylinder housing with its peripheral cylinder guide.
• the locking cylinder receives its non-rotatable axial guidance in the cylinder housing only indirectly, via the axial inner section of the printing handle arranged next to it, specifically via the pressure bush there.
• This pressure bushing is under axial spring force and thus exerts the restoring force required for the push button actuation on the locking cylinder, which is supported on a circumferential inner shoulder of the cylinder housing.
• the overload freewheel is created by an axial lifting profile, which is arranged between the cylinder guide on the one hand and the pressure bush on the other.
• the inner section of the handle still includes a control pin in the center, which interacts with the cylinder core via an intermediate axial coupling.
• the control pin is rotatable, but axially fixed in the pressure bushing and therefore performs an effective lifting profile, together with its pressure bushing, for an axial movement relative to the cylinder core, as a result of which the axial coupling in between disengages.
• turning reversals of the cylinder core can no longer have an effect on the downstream control pin and, via this, on the driver.
• the driver In the secured rotational position, the driver is in an ineffective rotational position with respect to the lock members, which is why an axial actuation of the combined pressure handle is ineffective and does not act on the lock members.
• a gev / old change of direction of the driver in its unlocked rotary setting is possible by gev / old application not reachable on the lock cylinder because this movement cannot affect the inner portion of the handle.
• the axial spring serving to press the handle serves the further function of delivering the releasing force for the overload freewheeling of the lifting profile.
• FIG. 1 shows an axial section through the most important parts of the device according to the invention in the full extension position of the associated printing handle, when the components are in their normal rest position, when a printing handle is extended position, and are brought into a secured rotational position by key actuation,
• FIG. 3 shows the inner end view of the device from FIG. 1, from which the displaced section line I-I for the axial section from FIG. 1 can be seen, the unlocked rotational position also being indicated by dash-dotted lines,
• FIG. 4 shows an inner detail of the device from FIG. 1 in an uncut view, when the components are in their normal rest position
• FIG. 5 shows an axial section corresponding to FIG. 1 through the device when the components are in a violent position achieved by a break-in tool, but the rotational position and extension position of the printing handle that corresponds to FIG. 1 is present,
• FIG. 6 shows this detail in a representation corresponding to FIG. 4, when the components are in the violent position shown in FIG. 5,
• FIG. 7 shows a detail section of the device corresponding to FIG. 2 in the position shown in FIG. 5, along the section line VII-VII there,
• FIG. 8 again in a vertical section corresponding to FIG. 1, the device when the pressure handle is in its insertion position serving to actuate lock springs and the components are brought into the dash-dotted, unlocked rotary position shown in FIG. 3, and
• Fig. 1 the locking device according to the invention is shown on a trunk flap 11 of a motor vehicle, which can be held in a collapsed position by lock members (not shown in more detail).
• a push handle 20 is used to actuate the lock members and can be divided into two axial sections 21, 22 which overlap in regions.
• the pressure handle 20 is received in a fixed to the flap 1 1 Zy ndergehause 10, in which there is a helical compression spring 12.
• the compression spring 12 surrounds the inner portion 22 of the pressure handle 20 and is supported, in the interior of the cylinder housing 10, with its spring base by means of an annular disk 13 on a snap ring 14 which engages in the inner wall of the cylinder housing 10.
• the pressure spring 12 exerts an axial spring force, indicated by an arrow 15 in FIG.
• the outer section 21 of the pressure handle 20 consists of a closing cylinder 30, which is divided radially in the usual way, namely into a circumferential cylinder guide 31 and into an axial cylinder core 32.
• the cylinder core 32 is connected axially fixed to the cylinder guide 31, for which, on the one hand, a snap ring 33 provides in a circumferential groove of the Zyli ⁇ derkerns 32, which is supported on the inner end of the cylinder guide 31.
• the shoulder of a collar 34 is supported on an inner step 35 of the cylinder guide 31 via a sealing ring 16.
• the cylinder core 32 is rotatably mounted in the cylinder guide 31 and can be reversed by means of a key 17 between an unlocked and a secured rotational position, which is in a rotary adjustment 67 of a working arm 51 of the driver shown in FIG. 3
• the cylinder guide 31 has an end flange 39, best seen in FIG. 4, with which, according to FIG. 1, the closing cylinder 30 can be supported on an inner stop 19 of the cylinder housing 10 via an annular seal 18.
• the inner stop 19 serves to abut the closing cylinder end flange 39, which is under the axial spring force 15, and thus determines the extension position shown in FIG. 1.
• the outer section 21 of the handle 20 protrudes from a housing cladding 24 located on the outside of the flap 11, into which it can be pressed in according to arrow 23 of FIG. 8.
• the area protruding outwards the Schheßzviinders 30 is covered by a Panzerhulse 25, which starts from the end flange 39 u ⁇ extends to the front end of the cylinder core 32.
• the two rotational positions of the cylinder core 32 in the cylinder guide 31 can be determined by locking elements, which in the present case consist of a spring-loaded locking ball 26 and a locking groove 27 in the interior of the cylinder guide 3 1.
• the inner section 22 of the pressure handle 20 is divided radially in two, namely on the one hand into an axially central control bolt 42 and a circumferential pressure bushing 41.
• the inner end of the control bolt 42 is offset and connected to the driver 50 in a rotationally and axially fixed manner by means of round entrainments and a snap ring which can best be seen in FIG. 3.
• the two complementary elements 44, 45 of an axial coupling 40 are arranged between the outer end of the control element 42 and the inner end of the cylinder core 32. These elements consist of an end diametrical coupling cam 45 on the cylinder core 32 and an end diametrical coupling receptacle 44 in the control bolt 42.
• the control pin 42 is thus rotatably mounted, but the inner end of the Z> l inner core 32 also engages freely in the interior of the pressure bushing.
• the control bolt 42 is at the same time axially fixed to the Oruckbuch.se - 'i, for which a circumferential groove 43 in the control bolt / s' 2 UIK' a radial inner cam -IG in the pressure bush J! to care.
• the pressure bush 41 is in the cylinder housing 10 axially displaceable but non-rotatably. This is ensured by an axial guide channel 48 in the interior of the cylinder housing 10, in which a radial outer cam 47 located on the circumference of the pressure bush 41 engages.
• the outer end of the compression spring 12 engages in a circumferential annular groove 49, which is located in a widened end piece 29 of the pressure bush 41.
• the compression spring 12 is supported there on the groove bottom.
• FIGS. 4 and 6 Between the front end of the widened pressure bush end piece 29 and the end flange 39 of the cylinder guide 31 there is a special lifting profile 60, best seen in FIGS. 4 and 6, consisting of an axially profiled projection 61 on the cylinder guide 31 and an axial one Recess 62 with a counter-profile on the pressure bush 41. Because the pressure bush 41 is under the axial spring force 15, also illustrated in FIG. 4, of the compression spring 12 shown in FIG. 1, the recess 62 endeavors to come into engagement with the projection 61 . In the normal rest position, this engagement position is shown in FIG. 4. This is also retained when the pressure actuation 23 according to FIG. 8, which has already been mentioned several times, takes place.
• the engaged lifting profile 60 also ensures a defined rotational position of the cylinder guide 31 in the cylinder housing 10, because the pressure bush 41 is always held in a certain rotational position via the guide means 47, 48 mentioned. These relationships change, however, if, according to FIGS. 5 and 6, violent rotations 28 are carried out on the outer section 21 of the printing handle 20.
• Such violent applications can, as illustrated in FIG. 5, take place via an intrusion tool 58, e.g. B. a screwdriver that is inserted into the key channel 38 of the cylinder core 32.
• an intrusion tool 58 e.g. B. a screwdriver that is inserted into the key channel 38 of the cylinder core 32.
• the cylinder guide 31 Due to the Zuroise ⁇ 36 now engaging in the locking channel 37 of the cylinder guide 31, the cylinder guide 31 is also rotated in the cylinder housing 10 and automatically lifts the profiled projection 61 out of the recess 62 having a corresponding counter profile, as can best be seen in FIG. 6.
• the projection 61 namely has a trapezoidal profile with bevels 63 on both sides and automatically lifts out of the recess 62 when transitioning into this rotational position.
• the recess 62 expediently has flanks 64 with a corresponding inclination geniage.
• the pressure bush 41 is pressed back axially by a distance 65 against the acting spring force 15 in accordance with the height of the projection.
• the pressure bush 41 is supported with its end face 66 in the appropriately flat part of the crown of the axial projection 61.
• Such a pair of projections and recesses 61, 62 is preferably provided in duplicate between the cylinder guide 31 and the pressure bush 41, which is why the recesses 62 move briefly into the respective other projection 61 after half a violent rotation 28, but with the then take place again automatically turn over their run-up bevels 63 and inclined flaps 64.
• the pressure bushing 41 only carries out axial vibrations in the interior of the cylinder housing 10, without this having any effect on a rotational adjustment of the driver 50.
• the axially firmly connected control pin 42 is pushed back as well.
• the axial stroke 65 starting from the lifting profile 60 is larger than the insertion depth 59 between the receptacle 44 and the cam 45 of the axial clutch 40. 5 and thus prevents transmission of the violent rotation 28 in the outer section 21 of the pressure handle 20 to the inner section 22.
• the uncoupled control pin 42 is not influenced by the violent rotation 28 and can therefore be connected to it in a rotationally fixed manner Do not adjust driver 50. If the secured rotational position 51 of the working arm of the driver 50 is previously present, then pressure actuations 23 of the pressure handle 20 cannot fundamentally have an actuating effect on the starting member 53, as can be seen from FIG. 3. In this case, the working arm 51 lies in a radial plane which is offset by the already mentioned angle 67 in relation to the relevant actuating arm 54 of the lock start member 53. Impression operations 23 consequently go ms empty.
• the driver 50 has a cap shape.
• the cap 68 engages via an inner end piece 69 of the cylinder housing 10.
• two axial grooves 71, 72 are provided, into which a sliding block 57, which can be seen in FIG. 2 and which is located in the hood 68, engages, optionally in each case.
• the sliding block 57 is located at the outer end of the respective axial groove 71 and 72, where a passage 74 is located in the web 73 .
• the passage 74 is dimensioned according to the sliding block 57.
• the sliding block 57 is located in the axial groove 71 and, when the handle 20 is actuated 23, can perform an axial movement which is also shown in FIG. 2 by the actuating arrow 23 and is ineffective for the lock members .
• the described key actuation of the locking cylinder 30 is necessary.
• the sliding block 57 is pivoted in the region of the guide 70, corresponding to the rotary adjustment 67 which can be seen in FIG. 3 and which is also shown in the planar development of FIGS. 2 and 9 and passes through the passage 74 into the dot-dash position - on 57 'in the other axial groove 72.
• the web 73 ensures a separation of the two axial grooves 71, 72 and is particularly important when the secured rotational position 51 of the driver working arm is present. If the violent rotation 28 according to FIG. 5 is carried out on the outer section 21 of the pressure handle 20, there is already a lateral overlap 75 between the web 73 on the one hand, due to the axial stroke 65 mentioned in connection with FIG. 6 and the sliding block 57 on the other hand, as shown in FIG. 7. The web 57 is then prevented from being reversed in the direction of the arrow 67 in the direction of the unlocked rotational position 57 '. Of course, this is all the more true if a pushing-in movement of the pressure handle 20 was carried out in the secured position of the slide stem 57. In this case, the sliding block 57 executes a longitudinal displacement in its axial groove 71, while the associated working arm 51 is idle with respect to the lock start member 53 and executes its ineffective axial movement in the offset winding plane of FIG. 3.

Landscapes

• Lock And Its Accessories (AREA)
• Preventing Unauthorised Actuation Of Valves (AREA)
• Rotary Presses (AREA)

Priority Applications (6)

Applications Claiming Priority (2)

Publications (1)

Family

ID=6512936

Family Applications (1)

Country Status (11)

Cited By (3)

Families Citing this family (21)

Citations (6)

• 1994
  • 1994-03-16 DE DE4408910A patent/DE4408910A1/de not_active Withdrawn
• 1995
  • 1995-03-07 DE DE59500690T patent/DE59500690D1/de not_active Expired - Lifetime
  • 1995-03-07 JP JP52310195A patent/JP3564619B2/ja not_active Expired - Fee Related
  • 1995-03-07 AU AU18934/95A patent/AU682099B2/en not_active Ceased
  • 1995-03-07 ES ES95911304T patent/ES2106642T3/es not_active Expired - Lifetime
  • 1995-03-07 EP EP95911304A patent/EP0750711B1/de not_active Expired - Lifetime
  • 1995-03-07 BR BR9507092A patent/BR9507092A/pt not_active IP Right Cessation
  • 1995-03-07 CZ CZ19962633A patent/CZ293887B6/cs not_active IP Right Cessation
  • 1995-03-07 WO PCT/EP1995/000833 patent/WO1995025214A1/de active IP Right Grant
  • 1995-03-07 KR KR1019960704840A patent/KR100316441B1/ko not_active IP Right Cessation
  • 1995-03-07 AT AT95911304T patent/ATE158375T1/de not_active IP Right Cessation
  • 1995-03-07 CN CN95192113A patent/CN1080359C/zh not_active Expired - Fee Related

Patent Citations (6)

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