EP0386651B1 - Handle - Google Patents

Description

The present invention relates to an operating handle, in the form of a window handle of the type specified in the preamble of claim 1.

Lockable or lockable handles are known for example from DE-U-8 624 544 and DE-U-8 514 560. When the handle is actuated, the associated device, for example a window gear, a lock nut or the like. rotated along. In a stop body, with which the handle is axially fixed, there is a latching device in order to determine preferred angular positions of the handle. For windows with tilt and turn fittings, the zero degree locking position is usually given when the window handle is facing downwards; if it is moved by 90 ° into a horizontal position, the window can be swiveled around the vertical axis, ie opened. If only limited room ventilation is to take place, the window can be tilted around a horizontal axis by swiveling the handle upwards (into the 180 ° position).

Switching through the handle rotary positions in this way is not desirable in some applications. One reason for this is that in the daily operation of the window, the tilt position is more common than the turn position. With newer operating handles, the tilt position is already reached in a 90 ° position of the handle, which prevents incorrect operation - namely the jumping out of the window from the front tilt joint of a conventional window mechanism. In a known embodiment, the handle can only be turned further upwards if a button on the handle head has previously been pressed.

Lockable window handles have been developed especially for rooms that need to be secured from the inside, and can only be moved from the zero degree position to the 90 ° position. This then corresponds to the tilting position of the window, which can be tilted for ventilation without a key; but it remains closed. Room ventilation can therefore also be carried out by operating personnel who do not have a key.

There is now a need for an improved construction that is simple on the one hand, but on the other hand ensures ease of use and increased safety. It is an important object of the invention to provide an operating handle that meets these requirements. Opening or swinging open a window provided with the handle should only be possible if it is unlocked; for permanent ventilation by tilting the window, a handle adjustability is also desirable even when the handle is closed.

Basic ideas of the invention are specified in the characterizing part of independent claim 1. Refinements are the subject of claims 2 to 27.

The invention provides according to claim 1 that the rings of a clutch enclosing the handle neck for engagement and disengagement in or from given angular positions of the handle with control tracks are provided, which take effect when turning the handle and cause the locking and unlocking in the desired function without - as usual - an additional control element on the outside of the handle would have to be operated. Their structure is compact, so that they can be designed with a pleasing appearance, especially on the handle head, without sacrificing safety.

It is advantageous here if the control tracks are arranged on or on mutually facing end faces of narrow cylinders which are each connected to the coupling rings in a rotationally fixed manner and enclose them tightly. The control path cylinders are optionally in one piece with the coupling rings according to claim 3. With regard to manufacture and assembly, it is also advantageous if the lower or inner coupling ring is in one piece with the stop body, so that a special component is unnecessary. These measures result in precise control with a small overall space requirement; they can also be easily implemented in the narrow interior of a handle head.

The function can be significantly supported by the fact that the clutch rings or the control rail cylinders are spring-loaded, namely by a compression spring supported in the handle neck, which ensures a secure locking function in any case.

According to an important feature of the invention specified in claim 5, the control tracks consist of alternating circular arc segments which are raised and deepened in the circumferential direction and have transition sections therebetween, which are designed in particular as circumferential slopes or ramps. The consequence of this is that the control path cylinders or the coupling rings can change their angular position to one another if the raised circular arc segments are seated against one another, while locking takes place as soon as the control cylinders engage in one another. Advantageously, according to claim 6, two mutually vertically offset pairs of diametrically opposite each other the circular arc segments. Even if the locking bolt of the lock or bolt unit is closed at the bottom, the handle can be moved 90 ° to the right or left in the tilted position. Shortly before the end position of the handle is reached, the control track of the coupling ring connected to it in a rotationally fixed manner moves downwards via a slope on the control track connected to the stop body. The handle cannot be turned further than 90 °, but it is possible to turn it back into the closed position via the control track slopes. To open the window, the locking pin must be closed; then the clutch is released.

According to claim 7, the form-locking elements of the coupling rings or the like as sawtooth-shaped noses, claws or the like. formed, preferably each coupling ring according to claim 8 each substantially distributed over half the circumference has a sequence of claws and a smooth path in the plane of the claw bottom. According to claim 9, these claw sequences can be divided into two 90 ° sectors, the saw tooth inclination of which faces away from one another and which adjoin one another with a wedge-shaped recess. This design ensures secure engagement and the transmission of very high torques of 100 Nm or more, for example. The last claws in the circumferential direction and the wedge-shaped recesses can, according to claim 12, be designed symmetrically, in particular with flanks running at 45 ° to the axial direction and of opposite shape to the V-recesses. This ensures that it can be turned evenly to the left or right. The same purpose is served if, according to claim 11, the angle of inclination of the circumferential slopes to the axial direction is in each case approximately 45 °, so that the control tracks rise or slide optimally against one another.

To prevent rotation, the upper or outer coupling ring according to claim 12 can have a radial extension for attachment to the locking pin and also on the periphery lugs that dip into the associated radial recesses of a handle neck recess, as known per se from DE-U-8 514 560.

A further development of the invention is characterized in accordance with claim 13 further by such a toothing of the two coupling rings that the one coupling ring has only lugs in the form of radial spur gear teeth and the other coupling ring has at least one positive notch between the opposite radial saw tooth sequences. This enables the two coupled rings to be supported in an extremely stable manner, in each of the possible coupling positions. This means that very high torques can be transmitted, which far exceed the limit values of conventional designs and can easily reach or exceed 200 Nm even with very compact dimensions.

A favorable further development is according to claim 14 that each nose and the notch has flanks which are substantially perpendicular to the ring plane, while each sawtooth has a substantially vertical and an oblique flank. The engagement position of the clutch is thus extremely precisely defined.

According to claim 15, the one coupling ring can have a closed sequence of similar lugs, the center of which diametrically opposes an individual lug, to which a continuously smooth path adjoins on both sides. This is an important prerequisite for the possibility of reliably specifying predetermined angular positions for the main body of the handle.

In the claims 16 and 17 details of advantageous gear designs are given. The ∩-shape of the lugs and the opposite shape of the base of the sawtooth allow for easy manufacture as well as a tight fit in terms of function.

Very favorable embodiments of the nose or tooth distribution on the circumference of each coupling ring are specified in claims 18 to 23. A symmetry is preferably used which combines an odd number of noses with a number of saw teeth which is larger by one, ie even; is particular According to claim 18, a grouping of seven lugs is provided on one coupling ring, while the other coupling ring has two groups of four saw teeth directed towards each other on both sides of a notch. Together with a diametrically opposed individual nose according to claim 19 or a second notch according to claims 20 and 21, an arrangement is obtained such that in each coupling position of the two rings four essentially vertical surfaces are supported on a counter element. This results, in particular, in the arrangements of claims 22 and 23 in an extraordinarily high load-bearing capacity of the handle.

In a particularly simple structure according to claim 24, the one, lower coupling ring is formed by the upper end of the bearing bush of the stop body and the other, upper coupling ring is slidably arranged on a locking pin and is loaded upwards by a spring acting on it. In addition, according to claim 25, a further spring is mounted inside the handle head, which loads the upper coupling ring towards the lower. The two springs are appropriately dimensioned so that the desired locking and closing functions can be achieved easily. The lock cylinder, which in turn is supported on the inside of the handle head by a spring, can thus be pressed inwards in the 0 ° closed position of the handle and rotated with the aid of a key, so that the handle is locked or locked. If the cylinder is only pressed, the handle can be positioned 90 ° (i.e. horizontally to the left or right), so that a window provided with the handle can be tilted. It can only be swiveled out when the locking cylinder is unlocked and the window handle has been moved up to the 180 ° position.

Yet another further development provides, according to claim 27, a compression spring which acts from the grip head on the cover plate of the stop body and therefore holds it down in order to usually cover the screw fastening, but to be able to expose it for assembly work.

• Fig. 1 eine Teil-Axialschnittansicht einer Betätigungshandhabe im verschlossenen Zustand,
• Fig. 2 eine geteilte Axialschnittansicht ähnlich Fig. 1 zur Veranschaulichung zweier Betriebszustände,
• Fig. 3 eine auseinandergezogene Schrägansicht von Kupplungsteilen,
• Fig. 4a und 4b je eine Steuerbahn-Abwicklung im entriegelten bzw. verriegelten Zustand einer Kupplung entsprechend Fig. 3,
• Fig. 5 eine Teil-Axialschnittansicht einer Handhabe,
• Fig. 6 eine Schräg-Untersicht eines oberen Kupplungsringes,
• Fig. 7a eine Abwicklung zweier Kupplungsringe in entkuppelter Anordnung,
• Fig. 7b eine Abwicklung der beiden Kupplungsringe von Fig. 7a in winkelversetzter und gekuppelter Stellung,
• Fig. 8a eine Draufsicht auf einen Anschlagkörper,
• Fig. 8b eine Schnittansicht entsprechend der Linie VIIIb-VIIIb in Fig. 8a,
• Fig. 8c eine Schnittansicht entsprechend der Linie VIIIc-VIIIc in Fig. 8a und
• Fig. 9 eine Teil-Axialschnittansicht ähnlich Fig. 5, jedoch von einer abgewandelten Ausführungsform.

Further features, details and advantages of the invention result from the wording of the claims and from the following description of exemplary embodiments with reference to the drawing. In it show:

• 1 is a partial axial sectional view of an operating handle in the closed state,
• 2 shows a split axial sectional view similar to FIG. 1 to illustrate two operating states,
• 3 is an exploded oblique view of coupling parts,
• 4a and 4b each a control path development in the unlocked or locked state of a clutch according to FIG. 3,
• 5 is a partial axial sectional view of a handle,
• 6 is an oblique bottom view of an upper coupling ring,
• 7a a development of two coupling rings in a disengaged arrangement,
• 7b a development of the two coupling rings of FIG. 7a in an angularly offset and coupled position,
• 8a is a plan view of a stop body,
• 8b is a sectional view along the line VIIIb-VIIIb in Fig. 8a,
• Fig. 8c is a sectional view taken along the line VIIIc-VIIIc in Fig. 8a and
• Fig. 9 is a partial axial sectional view similar to Fig. 5, but of a modified embodiment.

1 and 2, a window handle, generally designated 10, is shown with its main part 11 in different operating states. It has a grip head 12 and a neck 14, in which there is a recess 15 for receiving components described below. There is also a square hole 16 into which a square pin 18 can be inserted. Parallel to the axial direction A, but outside the axis of rotation of the handle 10, a bolt or lock unit 20 is inserted into the head 12, with which a locking bolt 22 can be moved back and forth.

On the handle neck 14 is a slide or spacer ring 24, which can be designed as a brass sleeve. A compression spring 26 supports a cover plate 28 which covers the upper side of a stop body 30 above a plastic frame 32 so that it can pivot. Finger recesses 34 are provided on the narrow sides of the plastic frame 32 for a better grip.

The stop body 30 has cams 36 with screw holes 37 for attachment to a surface, e.g. on the frame of a window. In the middle, the stop body 30 guides a bottom locking ring bushing 38, which cooperates with a counter locking ring 40 which is loaded by a spring ring 42. By means of a crimping bush 44, the handle neck 14 is fixed axially on the stop body 30 by a crimping 45, but is rotatable. Comparable arrangements are described in DE-B-2 752 213 and in DE-U-8 514 560.

Surrounding the sliding ring 24 is an upper coupling ring 50 of a coupling K, the lower coupling ring 52 of which is rigidly connected to the stop body 30 or is in one piece. The upper coupling ring 50 has a radial extension 54 with a bore 56 which is penetrated by the locking pin 22, which carries a locking washer 58 at the end.

As can be seen from FIG. 3, an upper cam track cylinder 60 is assigned to the upper clutch ring 50 and a lower cam track cylinder 62 is assigned to the lower clutch ring 52. Each control path cylinder 60 and 62 has between circular arc segments 60a, 60b and 62a, 62b, respectively recessed circular arc segments 60c, 60d and 62c, 62d with transitions in the form of bevels 64, in particular at 45 ° to the axial direction A.

The two coupling rings 50, 52 carry mutually facing claws 66, which are generally sawtooth-shaped and are each divided into two 90 ° sectors 66 ', 66˝. Where these sectors connect to each other, there is a V-shaped wedge recess 68, which is designed opposite to a roof claw 70. The roof claws 70 are in the circumferential direction at the ends of the sequence of claws 66, before the latter merge into a flat track 72 at the claw bottom.

To prevent rotation, the upper coupling ring 50 has radially outwardly directed lugs 76 (FIG. 3 above) which dip into the associated radial recesses 74 in the handle neck recess 15 (FIGS. 1 and 2).

The special design of the toothing of the clutch K can be seen from FIGS. 4a and 4b. 4a shows the unlocked state, corresponding to the right half of the sectional view of FIG. 2, while FIG. 4b shows the locked state, corresponding to the left half of FIG. 2. It can be seen that the symmetrically designed roof claws 70 and V- Recesses 68 allow decoupling or unlocking, while the sawtooth-shaped claws 66 of the sectors 66 ', 66˝ alternately take over the locking on the left or right. The circumferential direction U is shown schematically with the angular positions of the handle 10.

If, in the 0 ° position, the locking pin 22 of the bolt or lock unit 20 is closed at the bottom, the upper coupling ring 50 remains in the drawn locking position under the pressure of the spring 26 supported on it (FIG. 1). This is also the position that the upper coupling ring 50 assumes in the unlocked state (FIG. 2 right), the raised circular arc segments 60a, b and 62a, b abutting one another and the compression spring 48 being compressed. In this uncoupled state (see FIG. 4a), it is possible to move the handle 10 from the 0 ° position to the left or right to the 90 ° position.

Shortly before reaching the end position of the handle 10, the upper cam track cylinder 60, which is at least rotatably connected to the upper coupling ring 50, slides along with its raised circular arc segments 60a, 60b on the corresponding circular arc segments 62a, 62b of the lower cam track cylinder 62 firmly connected to the stop body 30 or in one piece is. The movement ends when the circular arc segments slide off at intersections 64 that meet, so that the handle 10 cannot be rotated further beyond the 90 ° position. On the other hand, it is possible to turn it back into the unlocked position via the slopes 64 of the control tracks (FIGS. 4a and 2 on the right). The compression spring 48 loads the upper coupling ring 50 downward for secure engagement of the respective claw sectors (66 'in the position shown in Fig. 4b).

In order to be able to open the window, the locking bolt 22 must be closed upwards by actuating the bolt or lock unit 20 (FIG. 1). Then the coupling rings 50, 52 are unlocked (see FIG. 4a), so that their claws cannot engage in the respective counter teeth.

It should be mentioned that the above-mentioned components are fixed after assembly by deforming the end of the handle neck 14 on the flanging ring 44 in the axial direction A except for the minimum play necessary for turning the handle 10. Preference is given to the components made of die-cast zinc that are loaded during actuation, so that high forces or torques of, for example, at least 100 Nm can be transmitted.

In the exemplary embodiment in FIG. 5, the window handle 10 generally has the same structure as described above. In the handle head 12, a bolt or lock unit 20 is inserted with a lock cylinder 21, which carries a locking pin 22 at its lower end and is loaded from below by a cone spring 23. On the outer circumference of the sliding or spacer ring 24, the upper coupling ring or locking ring 50 is slidably mounted, which cooperates with the lower coupling ring 52 to form the coupling K. This is preferably in one piece with the upper end of a bearing bush 31, which in turn can be in one piece with the stop body 30. Details of the structure can also be seen in FIGS. 8a to 8c. The stop body 30 is elongated and is provided with a pivotable cover 28 which overlaps the bearing bush 31.

The upper coupling ring 50, shown individually in FIG. 6, can slide with its radial extension 54 on the locking pin 22 of the locking cylinder 21 and is loaded from below by the support spring 25, which is supported on the locking disk 58 on the locking pin 22. From above, the locking ring or upper coupling ring 50 overlaps an upper control track cylinder 60, on which the spring 48 mounted in a recess 46 of the grip head 12 acts (FIG. 5). As a result, the upper control track cylinder 60 is non-positively held on the lower control track 62, which is also designed as a cylinder and is rigidly connected or integrally with the lower coupling ring 52. The two coupling rings 50, 52 carry engagement elements, which are generally referred to in FIG. 5 as claws 66 and are explained below with reference to FIGS. 6, 7a, 7b and 8a. To prevent rotation, the upper coupling ring 50 in turn has radially outwardly directed lugs 76 (FIG. 6) which dip into associated (not shown here) radial recesses in the handle neck recess 15.

The lower coupling ring 52 is provided with a straight tooth sequence of seven adjacent lugs 88, the middle or 0 ° lug facing a single lug 89 (FIG. 7a). This arrangement is overlapped by the upper coupling ring 50, which on both sides has a notch 84 which is shaped in the opposite manner to the lugs and has sawtooth segments 86a, 86b, each with four opposing saw teeth. The latter each have an essentially vertical flank and an oblique flank, the foot width corresponding to the distance between the lugs of the sequence 88 of the lower coupling ring 52. Whose individual nose 89 is in the arrangement of Fig. 7a a single notch 84 'opposite, which is formed by the substantially vertical flnaks of two saw teeth, to which a further group of saw teeth 86a', 86b 'each connect with a V-shaped transition 87 . The last-mentioned segments each have two saw teeth in the same direction as the four saw teeth of segments 86a, 86b facing each other, pointing towards the 0 ° notch 84.

It can be seen that the coupling K comes into engagement by moving the rings 50, 52, which are shown separately in FIG. 7a. In this case, four substantially vertical flanks of the sawtooth segments 86a, 86b and the nose sequence 88 bear against one another in a form-fitting manner in both circumferential directions U. In addition, there is a positive connection between the single tooth 89 and the single notch 84 '.

By disengaging in the axial direction A and rotating the coupling rings 50, 52 relative to one another by 90 °, the coupling K can be brought into the position in FIG. 7b. The coupling rings are hatched in the opposite direction only for the sake of clarity in order to better recognize the engagement elements. The sequence of lugs 88 of the lower coupling ring 52 is in engagement with the sawtooth segments 86b, 86b 'of the upper coupling ring 50, so that in turn a full surface closure between three substantially vertical pairs of flanks in the range between 0 ° and 90 ° and between two further vertical edge pairs in the range between 90 ° and 180 ° of the upper coupling ring 50. An opposite locking is possible if the upper coupling ring 50 is displaced by 90 ° with respect to the 0 ° position of the lower coupling ring 52 to the other side (to the right in FIG. 7b). The angular positions given relate to the position of the handle 10 mentioned at the outset.

FIG. 9 illustrates a modified embodiment in which the handle 10 generally also has the structure described. In the locking ring 50, however, the radial extension 54 is provided with a transverse bore 91 which receives a locking pin 92 between the slide or spacer ring 24 and the locking pin 22. The slide ring 24 has locking recesses 93 into which the locking pin 92 can enter when it is moved to the side by a projection 94 attached to it when the locking bolt 22 is raised. You can see that this preferred locking positions of the upper coupling ring 50 are set, in particular for the 90 ° position of the handle 10 when the locking cylinder 21 is unlocked.

The invention is not limited to the specified angular positions or rotational positions. Rather, it is also possible to provide the control tracks 60, 62 and the interlocking elements 66 in a different number and different angular distribution if other rotational positions for the handle 10 are desired.

Claims (27)

1. Operating handle (10) in the form of a window handle having a handle neck (14) pivotally supported in a mounting base (30) with axial restraint and adapted to receive a square drive shaft (18) for rotating a component to be operated (espagnolette mechanism, lock nut or the like), including a handle head (12) in which a locking member (22) is movable parallel to an axial direction (A) by means of a locking or bolting unit (20) and including a coupling device (K) that encompasses the handle neck and comprises opposing rings (50, 52) having form-fit elements such as dogs, catches, etc. (66, 68, 70) as well as smooth paths (72) arranged therebetween, the upper or outer ring (50) being axially restrained to the locking bolt (22) and the lower or inner ring (52) being axially restrained to the mounting base (30), wherein the coupling rings (50, 52) are provided, at portions facing each other, with cams (60a to 62d) that become effective upon turning the handle, causing the coupling device (K) to engage in given angular positions or to disengage, respectively.

2. Handle according to claim 1, wherein the cams (60a to 62d) are arranged at or on facing portions of narrow cylinders (60, 62) opposite each other, which cylinders are connected to the coupling rings (50, 52) for rotation therewith and snugly encompass the latter.

3. Handle according to claim 2, wherein the cam cylinders (60, 62) are integral with the coupling rings (50, 52) and/or wherein the lower or inner coupling ring (52) is integral with the mounting base (30).

4. Handle according to any one of claims 1 to 3, wherein the coupling rings (50, 52) and/or the cam cylinders (60, 62) are spring-loaded, in particular by a compression spring (48) supported in the handle neck (14).

5. Handle according to any one of claims 1 to 4, wherein the cams consist of raised and recessed arc segments (60a to 62d) alternating in a peripheral direction (U) and of transition sections therebetween, the latter being in particular peripheral slants or ramps (64 in Fig. 3).

6. Handle according to claim 5, comprising two pairs of arc segments (60a,b/60c,d; 62a,b/62c,d) diametrically opposing one another, which pairs are height-shiftable relative to each other in an axial direction (A).

7. Handle according to any one of claims 1 to 6, wherein the form-fit elements of the coupling rings (50, 52) are shaped as dogs, catches (66) or the like serrated in an axial direction (A).

8. Handle according to claim 7, wherein each coupling ring (50, 52) comprises, extending essentially over half the periphery, a series of catches (66) and a smooth path (72) in the catch bottom plane.

9. Handle according to claim 8, wherein each series of catches (66) is subdivided into two sectors (66′, 66˝) preferably extending over a circumferential angle of 90 degrees each, the sectors having opposing serration slopes and being joined by a V-shaped recess (68).

10. Handle according to claim 9, wherein the last catches (70), as seen in a peripheral direction (U), of either series and the V-shaped recesses (68) are symmetrically shaped, especially with flanks inclined at 45 degrees relative to the axial direction (A), said last catches (70) of either series being rooflike and countershaped to the V-shaped recesses (68).

11. Handle according to any one of claims 5 to 10, wherein the inclination angle of the peripheral slants (64) relative to an axial direction (A) is in the range between 40 and 50 degrees and preferably is 45 degrees.

12. Handle according to at least one of claims 1 to 11, wherein the upper or outer coupling ring (50) includes a radial lug (54) by which it is attached to the locking bolt (22) and wherein said ring (50) comprises peripheral projections (76) adapted to fit into associated radial recesses (74) of a handle-neck hollow (15).

13. Handle according to at least one of claims 7 to 12, wherein one coupling ring (e.g. 52) includes only dogs in the manner of a radial spur toothing (88, 89) and wherein the other coupling ring (e.g. 50) includes at least one matching notch (84, 84′) between radial serration series (86a, 86b; 86a′, 86b′) of opposite orientations.

14. Handle according to claim 13, wherein each dog (88, 89) as well as the notch (84; 84′) comprises flanks substantially vertical to the ring plane, whereas each serration has a substantially vertical flank as well as a slanted one.

15. Handle according to claim 13 or 14, wherein said one coupling ring (52) includes a closed series (88) of uniform dogs, wherein a single nose (89) diametrically opposes a central nose (0°) and wherein between the single nose and said series, there extends - in either peripheral direction (U) - a continuous smooth path (72) in the plane of the tooth or dog bottom (Fig. 7a).

16. Handle according to any one of claims 13 to 15, wherein the part pitch is defined by the sum of the serration bottom width and the width of the dog (89), whereby neighbouring serrations of either series (86a, 86b; 86a′, 86b′) of said other coupling ring (50) are offset by one dog width each.

17. Handle according to any one of claims 13 to 16, wherein the dogs of the radial spur toothing (88, 89) of said one coupling ring (52) are ∩-shaped with uniformly rounded or flattened crowns to which the bottoms of the serration series (86a, 86b; 86a′, 86b′) of said other coupling ring (50) are countershaped.

18. Handle according to any one of claims 13 to 17, wherein the circumferences of both coupling rings (50, 52) are subdivided by a maximum of sixteen dogs (88, 89) and serrations (86a, etc.), wherein the spur toothing (88) of said one coupling ring (52) comprises seven dogs lined up at a spacing of one serration bottom width each and wherein the serration series (86a, 86b) of said other coupling ring (50) arranged on either side of the one notch (84) include four uniformly oriented serrations.

19. Handle according to any one of claims 15 to 18, wherein the continuous smooth path (72) is provided on either side of the single dog (89) and wherein the peripheral sector adjacent to the closed dog series (88), of uniform pitch, is devoid of four dogs each so that each smooth path (72) of said one coupling ring (52) extends over a peripheral sector of more than four part pitches, preferably over less than five part pitches.

20. Handle according to any one of claims 13 to 19, wherein diametrically opposite to the one notch (84) of said other coupling ring (50), there is an identical second notch (84′).

21. Handle according to claims 18 and 20, wherein the second notch (84′) is formed by the vertical flanks of two serrations which are followed on either side by a V-shaped transition (87) to one series each of counteroriented serrations (86a′, 86b′).

22. Handle according to claim 21, wherein the series (86a′, 86b′) adjacent to the V-shaped transition (87) each include two serrations of identical orientation.

23. Handle according to any one of claims 16 to 22, wherein identically oriented serration series (86a, 86a′; 86b, 86b′) are separated from one another by a smooth path (gap 72) having the width of one part pitch.

24. Handle according to any one of claims 13 to 24, wherein said one, lower coupling ring (52) is formed by the upper end of the bearing bush (31) of the mounting base (30) and wherein the other, upper coupling ring (50) is adapted to slide at a locking bolt (22) and is upwardly biassed by a spring (25) supported by the latter.

25. Handle according to any one of claims 13 to 24, wherein the upper coupling ring (50) is downwardly biassed by a spring (48) that encompasses the handle neck (14).

26. Handle according to any one of claims 13 to 25, wherein at its inner face side in the handle head (12), the lock cylinder (21) is upwardly biassed by a spring (23), in particular by a conical spring.

27. Handle according to any one of claims 13 to 26, wherein the lower coupling ring (52) or the bearing bush (31) of the mounting base (30) is encompased by a compression spring (26) which biasses the cover (28) and is supported by the bottom of the handle head (12).

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