EP0467122B1 - Sleeve for pins of hinge fittings - Google Patents

Abstract

The hinge-pin sleeve (200) is a double eccentric sleeve with an outer sleeve (3), the bore (9) of which is eccentric to its outer circumference, and an inner sleeve (11), the bore (12) of which is again eccentric to its outer circumference. Rotating the inner sleeve (11) in relation to the outer sleeve (3) makes it possible to adjust the position of the hinge pin in the transverse direction. The load of the leaf is transmitted from an upper hinge part to the lower hinge part, in which the hinge-pin sleeve (200) is arranged, by means of a flanged ring (22). The inner sleeve (11) is freely rotatable relative to the flanged ring (22), so that it can be adjusted, without the flanged ring (22), which is under considerable friction, having to rotate with it. <IMAGE>

Description

The invention relates to a hinge pin bushing of the type corresponding to the preamble of claim 1.

Such a hinge pin bushing is known from DE-C-34 12 832. The flange ring is designed as a radial flange at the upper end of the inner sleeve. The toothing of the inner sleeve is provided on a separate disk which is rotatably connected to the inner sleeve and can be displaced in relation to the latter in the axial direction until the toothing engages. When the engagement is removed, a rotary tool can engage the disc from below through an opening in the outer sleeve and twist it and thus the inner sleeve for the purpose of adjusting the wing in the frame.

It is provided here that the sleeves should be rotated relative to one another with the wing suspended, ie while the weight rests on the flange ring integral with the inner sleeve. It has been shown that with heavy wings and poor lubrication of the flange ring, the adjustment of the inner sleeve requires very high torques, which can lead to a torsional deformation of the inner sleeve. For internal reasons, the inner sleeve has only a relatively small wall thickness, at least on the eccentric outer side.

The invention has for its object to design a hinge pin bushing of the type corresponding to the preamble of claim 1 so that the adjustment of the hinge pin bushing is possible even with heavy sashes without the risk of overstraining the inner sleeve.

This object is achieved by the invention reproduced in claim 1.

Due to the free rotatability of the inner sleeve relative to the flange ring, the inner sleeve can be rotated in the outer sleeve without the flange ring, which is under the load of the wing, having to be rotated as well. This not only makes it easier to twist the inner sleeve, but also ensures that it is not overstressed by excessive torque.

The displaceability of the inner sleeve allows the cooperating toothings to be attached to the two sleeves themselves and to make do with only three parts, namely the flange ring itself and the two sleeves. A separate locking part such as the disc in the known embodiment is therefore not required.

The flange ring must be fixed in the radial direction to prevent slipping between the cooperating band parts. For this purpose, it has a cylindrical projection which engages in the inner bore of the outer sleeve. Since, however, the inner sleeve is also arranged in this inner bore, a distance between the shoulder and the inner sleeve corresponding to the engagement distance of the toothings is provided in this embodiment.

In particular, the toothing can be formed in the manner shown in claim 2. The toothing of the outer sleeve acts as a stop when the inner sleeve is inserted into the outer sleeve.

Because of the fact that the inner sleeve has play upwards in the axial direction, the case could occur that at When the wing is lifted, the inner sleeve slides up to the stop on the flange ring and stops in this upper position. Then the gears could not be brought into engagement or only with difficulty.

To avoid this, a locking device is provided according to the development according to claim 3, which holds the toothing in the operating state of the hinge pin bushing, that is, when the adjustment is finished, in engagement.

A necessary feature of the locking device is that it must be detachable, so that after adjustment, readjustment or readjustment can take place after a long time. The locking device must not be designed so that it no longer releases the inner sleeve against the direction of engagement after locking.

The preferred implementation of such a locking device is the subject of claim 4. The resilient design of the locking device enables independent engagement, but the spring property also serves to enable subsequent disengagement of the engagement and the rotation of the bushings against each other.

A possible embodiment of a resilient locking device comprises, according to claim 5, elastically push-away latching tongues which can be designed in detail according to claim 6. The undercut on the inner sleeve can be formed by a circumferential groove in the bottom part thereof (claim 7), an important further development being that the latching tongues seated on the undercut without force leave a radial distance from the base of the groove. This makes it possible, given a suitable dimensioning of the elastic properties of the outer sleeve made of plastic, to allow the latching tongues to slide further radially inward by exerting an axial pressure on the inner sleeve to loosen the toothing and thereby to gain axial play in order to Gears to get free.

In order to prevent "hinge" of the hinge pin bushing when the wing is lifted, outer projections can be provided according to claim 9 on the lower edge of the outer bush which lie against the edge of the bore in the hinge part, but radially inward when the hinge pin bushing is inserted into the hinge part until can be elastically pushed away within the circumference of the outer sleeve.

Another embodiment with a resilient locking, but in which it is not formed on the outer sleeve, is the subject of claim 10. Here, therefore, an additional spring cup is provided, which pulls the sleeves against each other in the axial direction under elastic force until the teeth engage.

The fixation against pushing out of the bore of the hinge part when lifting the wing can take place here by "extendable" locking slides (claim 11), which are held together before assembly of the hinge pin bushing by a detachable thin connecting ring (claim 12) and in the Claims 13 and 14 described manner are radially outward for locking the hinge pin bushing at the lower edge of the bore of the band part.

The inner sleeve has a thick-walled and a thin-walled side due to the eccentricity. According to the embodiment according to claim 15, it can overlap on its thick-walled side the projection of the flange ring projecting into the bore of the band part up to near the top of the flange ring. As a result, the guide length of the inner sleeve is increased by the corresponding axial distance on at least one side.

When "above" and "below" are mentioned in the present description, this means the operating position of the hinge pin bushing in a hinge part connected to the fixed frame, that of a hinge connected to the wing, is overlapped over the flange ring on the lower band part lying band part.

• Fig. 1 zeigt einen Längsschnitt durch eine erste Ausführungsform der Bandzapfenbüchse, wobei der Bandzapfen um die umgebenden Bandteile strichpunktiert angedeutet sind;
• Fig. 2 zeigt eine Ansicht auf die Bandzapfenbüchse gemäß Fig. 1 von oben;
• Fig. 3 bis 6 zeigen Querschnitte senkrecht zur Achse nach den Linien III-III, IV-IV, V-V und VI-VI in Fig. 1;
• Fig. 7 zeigt eine Ansicht auf den unteren Teil der Bandzapfenbüchse nach Fig. 1 von rechts;
• Fig. 8 zeigt einen Längsschnitt nach der Linie VIII-VIII in Fig. 5;
• Fig. 9 zeigt einen der Fig. 1 entsprechenden Längsschnitt durch eine weitere Ausführungsform in der Montagephase;
• Fig. 10 zeigt einen entsprechenden Längsschnitt im Betriebszustand, d.h. bei eingehängtem Flügel;
• Fig. 11 zeigt eine Teilansicht gemäß Fig. 9 von rechts auf den unteren Teil der äußeren Büchse;
• Fig. 12 zeigt eine Ansicht gemäß Fig. 9 von unten;
• Fig. 13 zeigt eine Ansicht gemäß Fig. 10 von unten;
• Fig. 14 zeigt einen Fig. 9 entsprechenden Längsschnitt in der Montagephase;
• Fig. 15 zeigt einen Fig. 14 entsprechenden Längsschnitt im Betriebszustand;
• Fig. 16 zeigt eine Ansicht gemäß Fig. 14 von oben;
• Fig. 17 zeigt einen Schnitt nach der Linie XVII-XVII in Fig. 15.

Exemplary embodiments of the invention are shown in the drawing.

• Fig. 1 shows a longitudinal section through a first embodiment of the hinge pin bushing, the hinge pin around the surrounding band parts are indicated by dash-dotted lines;
• FIG. 2 shows a view of the hinge pin bushing according to FIG. 1 from above;
• Fig. 3 to 6 show cross sections perpendicular to the axis along the lines III-III, IV-IV, VV and VI-VI in Fig. 1;
• Fig. 7 shows a view of the lower part of the hinge pin bushing according to Fig. 1 from the right;
• Fig. 8 shows a longitudinal section along the line VIII-VIII in Fig. 5;
• FIG. 9 shows a longitudinal section corresponding to FIG. 1 through a further embodiment in the assembly phase;
• Fig. 10 shows a corresponding longitudinal section in the operating state, ie with the wing suspended;
• FIG. 11 shows a partial view according to FIG. 9 from the right onto the lower part of the outer sleeve;
• FIG. 12 shows a view according to FIG. 9 from below;
• FIG. 13 shows a view according to FIG. 10 from below;
• FIG. 14 shows a longitudinal section corresponding to FIG. 9 in the assembly phase;
• FIG. 15 shows a longitudinal section corresponding to FIG. 14 in the operating state;
• FIG. 16 shows a view according to FIG. 14 from above;
• FIG. 17 shows a section along the line XVII-XVII in FIG. 15.

1 to 8 is a so-called double eccentric bushing and is used for mounting the fastener fastened in the upper band part 1 cylindrical hinge pin 10 in the lower hinge part 2. The hinge pin sleeve 100 consists of an outer sleeve 3 with a cylindrical outer circumferential surface which is seated in the hinge sleeve bore 4 of the lower hinge part 2. To prevent rotation, a projection 5 can be provided on the outer circumference of the outer sleeve 3, which engages in a longitudinal groove (not shown) of the band sleeve bore 4. At the upper end, the outer sleeve 3 has a bevelled all-round projection 6, which rests on a corresponding countersinking of the band sleeve bore 4.

The cylindrical outer circumference of the outer sleeve 3 has an axis 7, from which the axis 8 of the bore 9 of the outer sleeve 3 deviates by the amount of the eccentricity. In the bore 9, the inner sleeve 11 is seated with its cylindrical outer circumference, the axis of which is 8. The inner bore 12, which receives the hinge pin 10, is in turn eccentric to the outer circumference of the inner sleeve 11 and has an axis whose eccentricity in the exemplary embodiment corresponds to that of the outer sleeve 3. The inner sleeve 11 is also arranged in the setting shown in FIG. 1 so that the axis of the inner bore 12 coincides with the axis 7 of the outer periphery 4 of the outer sleeve 3.

At the lower end, the inner sleeve 11 has a bottom part 13 which has a cylindrical, i.e., coaxial to the outer peripheral surface of the inner sleeve 11. has the outer peripheral surface 14 having axis 7, which is guided in a corresponding cylindrical recess 15 at the lower end of the outer sleeve 3. A circumferential groove 16 is formed in the region of the base part 13, the base 17 of which is a cylindrical surface with the axis 8. In addition, a downwardly open hexagon recess 36 is provided in the bottom part 13 for the attack of a turning tool.

Starting from the upper flank 18 of the circumferential groove 16, a toothing 19 is formed on the outer circumference of the inner sleeve 11, which interacts with a toothing 20 which is attached to a shoulder 21 in the lower region of the outer sleeve 3 is formed, on which the outer sleeve 3 passes from the diameter of its bore 9 to the smaller diameter of the cylindrical recess 15 at the lower end. If the inner sleeve 11 is pushed sufficiently far into the outer sleeve 3, the toothings 19, 20 engage in one another, so that the sleeves 11, 3 can no longer rotate against one another. In the exemplary embodiment, the toothing comprises nine teeth distributed over the circumference, so that the inner sleeve 11 can be locked in a corresponding number of rotational positions. The scale of the figures results from the fact that the hinge pin has a diameter of 12 mm. The eccentricity, ie the transverse distance of the axes 7.8 from one another, is 0.65 mm in one embodiment, so that a maximum displacement of 1.3 mm in the transverse direction can be achieved.

At the upper end, a flange ring 22 is provided which engages over the upper end of the outer sleeve 3 and also engages a radial distance between the band parts 1,2, so that the load of the wing from the upper band part through the flange ring 22 directly into the lower band part 2 is derived without the hinge pin bushing 100 would be affected.

The flange ring 22 has an axial tubular cylindrical projection 23 which fits with its outer circumference in the bore 9 of the outer sleeve. On the outer circumference, the shoulder 23 has a rib 24 which snaps into an inner circumferential groove of the bore 9, so that the flange ring 22 is fixed on the outer sleeve 3.

The approach 23 ends with its lower edge 26 in a plane perpendicular to the axis. The same applies to the upper end 27 of the inner sleeve 11. The mutually facing edges 26, 27 have a distance 28 in the axial direction, ie in the direction of engagement of the toothings 19, 20, which allows the inner sleeve 11 according to FIG. 1 push up so far that the teeth 19.20 come apart and the inner sleeve 11 can be rotated in the outer sleeve 3.

It is important here that the inner sleeve 11 and the flange ring 22 are separated from one another and are not rotationally connected to one another. This means that the inner sleeve 11 can be rotated easily, although the flange ring 22 is held with considerable friction under the load transmitted by the upper band part 1. The adjustment by rotating the inner sleeve can thus be carried out with the wing attached, without having to rotate the flange ring 22 as well.

The inner sleeve 11 has on its thick-walled, i.e. 1 on the left-hand side has an extension 29 which extends over approximately 180 ° and extends within the extension 23 into the region of its upper end. The approach 23 has a uniform wall thickness and is overlapped by the extension 29 inside. As a result, the bearing length for the hinge pin 10 extends upwards on the left-hand side according to FIG. 1.

At the lower end of the outer sleeve 3, axially parallel incisions in the exemplary embodiment form three tongues 30 which are evenly distributed over the circumference and which have outwardly directed projections 31 at the lower end which, in the operating state, overlap the lower edge of the band sleeve bore 4 and the band journal bushing 100 in front of it preserve to be pulled out of the hinge bore 4 when the wing is detached from the hinge pin 10 upwards.

Offset by 60 ° in the circumferential direction with respect to the tongues 30, three latching tongues 40 projecting inwards in the region of the circumferential groove 16 are also provided at the lower end of the outer sleeve 3, which engage in the manner shown in FIG. 8 against the undercut 32 forming the lower one Set edge 33 of groove 16. Keeps fully inserted and free of force in the outer sleeve 3 seated inner sleeve 11, the radially inner boundary 34 of the locking tongues 40 a radial distance 35 from the base 17 of the circumferential groove 16.

All three parts 3, 11 and 22 of the hinge pin bushing 100 consist of a suitably chosen plastic. The flange ring 22 has high hardness and optimal sliding properties in order to transfer the weight of the wing well. The bushes 3.11 have a limited elasticity. The elasticity of the bushing 3 is sufficient to be able to push the tongues 30 so far inwards when inserted into the band bushing bore 4 that the projections 31 slide along the inner circumference of the band bushing bore 3 and the tongues 30 spring open again when the outer bushing 3 is fully inserted . The elasticity of the inner sleeve 11 is sufficient for the latching tongues 40 to be pushed outwards when inserted through the lower part of the cylindrical outer circumference 14. When the lower end of the latching tongues 40 has reached the lower flank 33 of the circumferential groove 16, the latching tongues 40 jump in in the manner shown in FIG. 8 and engage against the flank 33 forming the undercut 32. However, tests have shown that the elasticity of the outer sleeve 3 can be selected so that the latching tongues 40 slip when closing an axial force, the inner sleeve 11 as shown in FIG. 8 to be displaced upwards, closing the distance 35, thereby releasing an axial path for the inner sleeve, which enables the teeth 19, 20 to come free from one another.

The locking tongues 40 extend in the exemplary embodiment by approximately 45 ° downwards and inwards. On the underside of the sleeves 11 and 3, projections 43, 44 are attached, which facilitate the detection of the adjustment position of the sleeves 11, 3.

Insofar as there are functionally corresponding parts in the further exemplary embodiments, the reference numbers are the same. 9 to 17 is the illustration so that the axes 7, 8 lie one behind the other perpendicular to the plane of the drawing.

9 to 13, the toothings 19, 20 are not held in engagement by a design of the lower end of the outer sleeve 3 corresponding to the latching tongues 40 in FIGS. 1 to 8, but by a separate part, the so-called spring cup 50. The spring cup 50 consists of a suitable resilient plastic, the interior 36 of which has a hexagonal cross section (see FIGS. 12, 13) for receiving a correspondingly shaped turning tool. The outer shape is also hexagonal, and the spring cup 50 with this cup-shaped part is seated in a hexagonal part 36 'of a continuous recess of the bottom part 13 of the inner sleeve 11, designated as a whole as 37. At the "bottom" of the cup-shaped part of the spring cup 50 four resilient locking hooks 39 distributed over the circumference are formed, which engage behind an undercut 38 which is provided in the upper part of the recess 37. The spring cup 50 is thus inserted from below into the recess 37 until the latching hooks 39 snap over the undercut 38.

At the end opposite the latching hook 39, the spring cup has resilient tongues 60, three of which are distributed over the circumference in the exemplary embodiment and which extend radially outward from the edge of the spring cup. In the force-free state, the spring tongues 60 point at an angle of approximately 30 ° to the end of the spring cup 50 which has the latching tongues 39, as is indicated by dash-dotted lines in FIG. 9.

Radially displaceable locking slides 65 are provided in the circumferential areas that remain free between the resilient tongues 60 and are guided in a dovetail-shaped undercut recesses 61 on the lower edge of the outer sleeve 3 so as to be displaceable outwards (see FIGS. 11, 12). The locking slide 65 are held together by a thin detachable ring 62 which, like the locking slide 65 itself, is made of plastic. On the inside, the locking slides 65 have an inclined surface 63 which is inclined inwards and upwards and which cooperates with a conical chamfer 64 at the leading end of the base part 13 of the inner sleeve 11.

On the outside, the locking slide 65 has a bevel 66 which is intended to bear against the countersink 67, which is only indicated in FIGS. 9 and 10, at the lower end of the band sleeve bore 4.

9 shows the delivery condition of the hinge pin bushing 200. The inner sleeve 11 has at its upper edge a push-off peripheral projection 24 'which sits at the end of an axially widened peripheral groove 25' of the inside of the outer sleeve 3, which also receives the peripheral projection 24 of the shoulder 23 of the flange ring 22. Due to the circumferential projection 24 ', the inner sleeve 11 cannot slide further down. The spring cup 50 is inserted and engages over the connecting ring 62 connecting the locking slide 65 with the spring tongues 60 from the outside. The spring tongues 60 are under tension and run approximately in a plane radial to the axis, as shown in solid lines in FIG. 9. However, they have the tendency to deform into the position shown in broken lines in FIG. 9. The flange ring 22 leaves an axial distance 45 from the upper end of the outer sleeve 3.

In this prestressed state, the hinge pin bush 200 is inserted into the hinge bore 4 of the hinge part 2 (see FIGS. 1 and 8). If the wing is then hooked in, its weight presses the flange ring 22 down, closing the spacing space 45, until it rests against the upper end of the outer sleeve 3, the upper circumferential projection 24 'being pushed away and out of the inner circumferential groove 25 'reaches the cylindrical part of the bore 9 of the outer sleeve 3. The hinge pin coming into contact with the bottom of the bore 12 of the inner sleeve 11, not shown in FIGS. 9 and 10, pushes the inner sleeve 11 further downwards, with the explosion of the connecting ring 62 and sliding of the conical chamfer 64 at the lower end of the inner sleeve 11 are displaced radially outwards via the inclined surface 63. The gears 19, 20 come into engagement. In the last phase, when the bevel 66 of the locking slide 65 rests on the countersink 67 of the band part, the radially inner end of the locking slide 65 stands against the cylindrical outer circumference 14 of the bottom part 13 of the inner sleeve 11, so that there is a locking in the radial direction . Since the locking washers 65 are fixed in the axial direction by the dovetail shape of the recess 61, the hinge pin bushing 200 can no longer be pulled out of the band bushing bore upwards.

Between the upper edge of the inner sleeve 11 and the lower edge of the shoulder 23 of the flange ring 22 there is again the distance 28, which allows the inner sleeve 11 to be pushed up a distance 28 in the outer sleeve 3, which is used to loosen the teeth 19, 20 from each other is sufficient. The axial force required for this is applied by hand by means of a turning tool engaging in the recess 36 and is sufficient to insert the resilient tongues 60, which bear against an end surface 42 perpendicular to the axis, at the lower end of the outer bushing 3 into FIG. 9 deformed position to deform. When released, the spring tongues 60 pull the spring cup 50 and the associated inner sleeve 11 back into the position shown in FIG. 10.

The locking slide 65 not only have a chamfer 66 on the top of its outer end, but also a chamfer 68 on the bottom so that they do not protrude from the conical bevel 69 of the lower end of the outer sleeve 3 in the delivery state, as can be seen from FIG. 9.

Also in the case of the hinge pin bushing 200, the adjustment can be carried out in the manner described above by rotating the inner bushing 11 within the outer bushing 3 without having to turn the flange ring 22 as well.

This also applies to the hinge pin bush 300 of FIGS. 14 to 17. However, while the locking of the hinge pin bush 200 in the axial direction when inserting the inner bush 11 into the outer bush 3 took place from above, this locking takes place in the embodiment 300 by inserting the spring cup 55 into the recess 37 of the bottom part 13 from below. Three locking slides 70 distributed over the circumference are again radially displaceable in dovetail guides 61 of the lower end of the outer sleeve 3. The spring cup 55, which in turn has the hexagonal recess 36 and the radial resilient tongues 60 and can be brought into engagement by means of latching hooks on the undercut 38 of the recess 37 (see FIG. 15), widens downwards and accordingly has a conical downwards widening outer peripheral region 52, which is in the delivery state shown in FIG. 14 below the locking slide 70.

The hinge pin bush 300 is assembled by exerting an axial pressure from below with the turning tool. On the one hand, the latching hooks 39 snap into place and, on the other hand, the locking slides 70 are pushed outwards while sliding over the conical outer peripheral region 52 until their inclined surface 66 comes to rest on the countersink 67 of the band sleeve bore 4. In this final phase, the inner ends of the locking slide 70 stand against a cylindrical outer peripheral region 53 of the spring cup 55 which adjoins the conical outer peripheral region 52 downward, so that a definite locking is given in the radial direction. In this phase, the spring tongues 60 bear against the end face 42 essentially without force.

In order to carry out an adjustment when the bracket is suspended, the spring cup 55 and the inner sleeve 11 are pressed upwards by means of the rotary tool engaging in the recess 36 until the toothings have disengaged. The spring tongues 60 assume the position shown in solid lines in FIG. 9. The rotation can now take place without the flange ring 22 being taken along.

Claims (15)

1. Hinge pin bush for the hinges of doors, windows and the like,
      with an outer bush (3) for inserting in one hinge component (2) and having an internal bore (9) which is eccentric in relation to the axis (7) of its cylindrical external surface,
      with an inner bush (11) which is arranged within it and which again has an internal bore (12) which is eccentric with respect to the axis of its cylindrical external surface which fits in the bore (9) of the outer bush (3), the inner bush being designed to receive the hinge pin (10) connected to the other hinge component (1),
      with a flanged ring (22) on that end of the bushes (3, 11) which is uppermost in use and which projects radially between the hinge components (1, 2) to form the engagement for the upper hinge component (1) on the lower hinge component (2)
      and with a set of teeth provided on the ends of the bushes (3, 11) furthest from the other hinged component (1) and capable of being brought into engagement by axial insertion of the inner bush (11) into the outer bush (3) and out of engagement by axial displacement in a direction opposite to that of engagement.
      the inner bush (11) being capable of rotation relative to the outer bush (3) to adjust the flap of the door, window and the like in the frame with the flap mounted,
      characterised in that,
      the inner bush (11) is freely rotatable in relation to the flanged ring (22),
      the inner bush (11) is made in one piece and is displaceable axially within the internal bore (9) of the outer bush (3) with the flap mounted, axially against the direction of engagement far enough so that the teeth (19, 20) come out of engagement
      and that the flanged ring (22) has a cylindrical axial extension (23) exceeding in inside diameter the hinge pin (10) and engaging in the internal bore (9) of the outer bush (3) from the engagement face of the flanged ring (22) and of which the lower rim (26) has a spacing (28) from the upper rim (27) of the inner bush (11) which corresponds at least to the extent of travel for engagement of the teeth (19, 20).
2. Hinge pin bush according to claim 1, characterised in that the teeth (19) on the inner bush (11) are provided on the lower end of the outer periphery of the inner bush (11) and the teeth (20) on the outer bush (3) project inwards from the inner periphery (9) of the outer bush (3) to form a step (21) on it.
3. Hinge pin bush according to claim 1 or 2, characterised in that a detent device is provided which acts against the direction of engagement and holds the teeth (19, 20) in engagement in the operative condition of the hinge pin bush (100, 200, 300).
4. Hinge pin bush according to claim 3 characterised in that the detent device is made resilient and the inner bush (11) is displaceable by forces which can be applied by hand so far opposite the direction of engagement, overcoming the spring force, that the teeth (19, 20) come out of engagement.
5. Hinge pin bush according to claim 3 or 4, characterised in that the detent device includes resilient detent tongues (40) on the outer bush (3) which retract on insertion of the inner bush (11) into the outer bush (3) and, with the inner bush (11) fully inserted, snap in behind an undercut portion (32) facing the upper end of the hinge pin bush (100).
6. Hinge pin according to claim 5, characterised in that the detent tongues (40) project from the outer bush (3) in an inclined direction inwards in the direction of engagement.
7. Hinge pin bush according to claim 5 or 6, characterised in that the undercut portion (32) is formed by the one flank (33) of a circumferential groove (16) in the floor part (13) of the inner bush (11).
8. Hinge pin bush according to claim 7, characterised in that the detent tongues (40) seated on the undercut portion (32) in an unstressed state leave a radial spacing (35) from the base (17) of the circumferential groove (16).
9. Hinge pin bush according to one of claims 5 to 8, characterised in that resiliently retractable outward projections (31) are provided on the outer rim of the outer bush (3), engaging under the rim of the bore of the hinge component (2).
10. Hinge pin bush according to one of claims 1 to 4, characterised in that there is provided in the floor part (13) of the inner bush (11) a stepped central recess (37) of a cross-section which departs at least in part from the circular form, and in which a resilient pot (50, 55) having a corresponding external cross-section can be inserted from outside, the pot having on its leading end an overlying detent hook (39) snapping into an undercut portion (38) of the recess (37) as well as at its other end a form a shape for engagement by a rotary tool, and which engages with resilient tongues (60) against the face (42) of the outer bush (3) and can be displaced together with the inner bush (11), by forces that can be applied by hand, far enough against the direction of engagement for the teeth (19, 20) to come out of engagement.
11. Hinge pin bush according to one of claims 1 to 10, characterised in that detent plates (65, 70) are provided in undercut transverse recesses (61) on the lower end of the outer bush (3), displaceable radially outwards by the introduction into the operative position of the inner bush (11) or the resilient pot (55), the plates lying in this condition against the lower rim (67) of the hinge bush bore (4) of of the hinge component (2) and preventing the hinge pin bush (200, 300) from being pulled out of the hinge leaf component (2).
12. Hinge pin according to claim 11, characterised in that the detent plates (65, 70) are arranged distributed circumferentially and are held together in the radially inwardly withdrawn starting position by a springy thin connecting ring (62).
13. Hinge pin bush according to claim 11 or 12, characterised in that the floor part (13) of the inner bush (11) is inclined inwardly in a wedge shape on that end which leads on insertion into the outer bush (3) and its wedge face (64) exerts a radially outwardly acting force on the detent plates (65).
14. Hinge pin bush according to claim 11 or 12, characterised in that the resilient pot (55) widens out in a wedge shape downwards and outwards at the lower end and on insertion far enough to allow snap engagement of the detent hook (39) it wedge face (52) exerts a radially outwardly acting force on the detent plates (70).
15. Hinge pin bush according to one of claims 1 to 4, characterised in that the inner bush (11) has on its thick-walled side a projection (29) engaging over the extension (23) on the flanged ring (22) inwardly as far as the neighbourhood of the upper end of the flanged ring (22).

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