EP2241527A1 - Connection device - Google Patents

Abstract

The apparatus (1) has a support flange (2) swivelably arranged in a housing (4) in a rotation axis. A through-hole (15) extends axially through a bushing (5) in which a supporting bolt (10) is rotatably attached with an upper head part. The supporting bolt comprises a shank (16) with a shank region provided at an axial distance (a) from an upper end of the bushing. A radially enlarged shank diameter of a radial excess portion is partly covered radially from outside in a mounted state under axial play within the axial distance by a bushing section with a reduced inside diameter.

Description

The invention relates to a connecting device for coupling a support flange to a load, with a housing having a socket and a rotatable about this holder for the support flange, wherein the support flange is pivotable in the housing about an axis of rotation of the holder axis of rotation and axially through the sleeve, a through hole extends, in which a retaining bolt rotatably mounted with an upper head and mounted with its head facing away from the axial end for attachment a load axially over the housing, wherein the retaining pin in the assembled state in the through hole against axial withdrawal this is held positively.

Such connection devices are often used in particular for lifting loads. For this purpose, we attached the connection device to the load and then raised to its support flange, which is often designed as a support ring, by means of a lifting hook or chain o. Ä. And moved to another location.

A device of this kind is used in the EP 1 069 067 B1 described. In her, the shank of the support bolt and the socket in which he sits, are connected by means of shrinking, wherein the upper end of the sleeve rests on the head portion of the support bolt. In this known connection device, there is the disadvantage that the absolutely firm connection between the shank of the support bolt and the sleeve causes any triggering of the supporting bolt inevitably leads to a rotation of the socket. For this reason, when tightening the screw (namely when screwing the load) rotates the sleeve and thus also attached to the bottom of the socket, resting on the top of the load flange with the rotation of the screw. Thus, when tightening the screw and the friction between the flange and the load on which it rests, just in the end of the tightening of the screw must be overcome, which leads to a significant increase in the required torque of the screw. It is possible that the screw can not be completely safely biased when the flange of the socket and its contact surface with the load are not exactly parallel to each other. Is this Shrinking the bush performed on the shaft of the support bolt, the pre-assembly of this known connection device is met, ie it can be taken in the otherwise fully assembled state and attached to the load. Falling out of the shaft from the socket is not possible.

In the connection device from the US 5 248 176 A are used instead of a support pin holding sleeve two axially successively connected sleeves, each of which is provided at its axially outer end with a radially projecting annular flange. In this case, the support pin is freely movable within these formed by the two holders holder relative to these and not attached to them, which fixes the disadvantages when screwing to the load to be attached, in the above-described known connection device by the solid connection between them Parts occurred. However, only one in the US 5 248 176 A shown embodiment with a central support pin provided a positive support, with which the support pin is prevented in the assembled state of the connection device from being able to run out of the formed by the two bushings through-hole in which it is supported upwards. For this purpose, the provided at the lower end of the support bolt thread for screwing the load is continued axially to about half the length of the through hole, in a mounted in the lower sleeve depression a short coil spring of about 1 ½ threads sitting there with tight Seat is mounted from the outside in the threads of the support bolt and this projects beyond the outside, whereby a return of the support bolt from the through hole avoided and thereby a cohesion of the assembled terminal device is secured even if it is not yet attached to a load. However, this known connection device has a total of a relatively complicated structure with a plurality of individual elements. In addition, when screwing the support bolt to the load to be suspended due to the tight fit of the retaining coil spring, which is held on the support bolt between the threads, the rotation of the retaining coil spring is taken along. In this case, in the context of the prescribed tightening torque of the supporting bolt just in the last phase of tightening the support bolt between the retaining coil spring and the adjacent surface of the load to be coupled then occurring frictional forces must be additionally overcome.

A connection device of the type mentioned is in the US 4 641 986 A described. Here, only a central bushing is used, in which the support pin rotatably seated, wherein the support pin at its upper side via an intermediate ring at the upper end of the bushing supporting bolts at the lower end of the socket in an enlarged recess mounted there by means in the region of its Anschraubgewindes for embedded load to be fastened Retaining ring is secured against pulling upwards. Is screwed in this known connection device of the support bolt now to the surface of a load to be attached, this means that, especially in the last stage of tightening, a relative rotation between the snap ring and the threaded shank of the support bolt occurs, which in turn causes due to the high pull forces that also Here, a more or less large proportion of the prescribed torque for overcoming this friction must be applied, which is undesirable.

Proceeding from this, the invention proposes a terminal device which has a simple structure and in which almost no share of the prescribed tightening torque for the additional overcoming of frictional forces between the bolt to be screwed and other elements of the device must be spent in a screwing a load.

According to the invention this is achieved in a connection device of the type mentioned above in that the support pin has a shank with a provided at an axial distance from the upper end of the socket shaft portion with a radially enlarged shaft diameter, the radial projection in the assembled state within this axial distance of a Buchseabschnitt with a reduced inner diameter under axial play radially from the outside partially covered.

In the invention, first by the shape of the shank of the support bolt and by the shape of the bush in the through hole form-fitting withdrawal of the support pin upwardly out of the through hole prevented, without it - as well as with additional connecting devices - still further constructive parts (as of snap rings, tight on the thread of the support pin shank to be applied coil springs o. Ä.) Required, but the support pin can be freely rotated relative to the housing and the socket in this. In the inventive design of the connecting device takes place when screwing the support bolt in the load to be attached no additional axial power transmission between the support pin on the one hand and another part of the device, so that so far no axial friction forces around the support pin around this acting friction moments are built. Rather, the allowable torque of the screw is fully available to build the desired bias. While in known connection devices of the support pin in the through hole of the sleeve is positively held so that he can not perform any axial relative movement to the socket means used in the invention positive locking an axial slipping out of the sleeve already because of the required axial clearance not that no axial relative movement between Carrying bolt and sleeve should be possible. Rather, in the embodiment according to the invention only a complete axial run out of the sleeve is positively prevented, ie the bolt can not be pulled out of the sleeve in its entirety. An axial relative movement between the bolt and the sleeve but in such a way that the bolt does not completely run out of the sleeve, is quite permitted in the invention, so no positive retention used, which basically prevents axial relative movement between the bolt and sleeve, as in known connection devices is the case. Depending on the position within the axial distance from the upper end of the bush when mounted support bolt radially enlarged shaft portion begins, it can be determined by the interpretation of the construction according to the invention, over which axial region of the support bolt, he is once mounted , in the context of the axial clearance within the passage opening is axially movable to this.

In a particularly preferred embodiment of the connecting device according to the invention, the shaft portion with increased shaft diameter consists of an external thread whose threads form the radial enlargement, and the sleeve portion with reduced inner diameter of an internal thread corresponding to the thread on the shaft portion enlarged shaft diameter. In this embodiment, the support bolt is screwed when mounted in the device first with its shaft portion enlarged shaft diameter forming external thread through the internal thread of the female portion with reduced inner diameter until the external thread has completely passed through the internal thread. Subsequently, the support pin in the through hole of the socket without further rotation can still be moved axially until the head part of the support bolt rests on top of the socket or on an intermediate shim. If, however, the support bolt is now moved counter to its insertion direction axially in the passage opening in the direction of its upper end, this is only possible until radially beyond the other shaft diameter outwardly projecting external thread in the shaft region with radially enlarged shaft diameter against it from radially outside partially overlapping, inwardly radially projecting bushing section with reduced inner diameter comes to rest. A further axial displacement movement of the shaft in the through hole is then no longer possible, unless specifically a rotation of the support bolt for intentional unscrewing or screwing his external thread through the internal thread of the sleeve is used selectively.

Preferably, in this case, the inner diameter of the bush is formed in the region outside the bush portion with a reduced inner diameter greater than the outer diameter of the threads on the shank portion of the support bolt with enlarged shank diameter, so that in the mounted state, the shank portion with enlarged shank diameter in the surrounding bushing portion not on the inner wall of the Socket rests, but this (as well as axially) has a predetermined game, which again favors the screwing of the bolt into a load to be screwed.

A particularly simple and therefore cost-effective embodiment of the invention is that the external thread, which represents the shaft portion with increased shaft diameter, is formed directly from the thread, which is provided on the load-facing end portion of the support bolt for screwing the load, wherein the diameter of the remaining portion of the shank of the supporting bolt is smaller than the core diameter of this external thread. This has the advantage that standard screws or at least very easy to produce screws can be used, which is a great advantage.

In another embodiment of the invention, the external thread of the shaft portion is provided with enlarged shaft diameter, with mounted support pin, in a central region between the thread for screwing the load on the head part of the supporting bolt end facing away from the latter and the female portion with a reduced inner diameter. In this solution, the socket for several Anschraubgewindegröße sizes remain the same, it changes only the Anschraubgewinde, which can be an advantage in terms of cost.

For good handling and safe operation, it is recommended in this embodiment of the invention that the internal thread in the bushing portion with reduced inner diameter at least one complete thread, but preferably includes two complete threads. Equally preferably, the external thread of the shank region of the support bolt with enlarged shank diameter should have at least two, but preferably three complete threads.

Another, very advantageous embodiment of the connecting device according to the invention also consists in that on the support pin of the shaft portion is formed with radially enlarged shaft diameter cylindrical and protrudes into a correspondingly attached to the inner surface of the sleeve annular groove, wherein the radially enlarged shaft portion in the annular groove radially and axially Game is sitting. In this embodiment, the support pin in the assembled state remains slightly rotatable relative to the socket, wherein the support pin However, without additional effort can not be removed from the socket and thus always kept in this. Thus, in this embodiment, the support bolt without considerable additional effort (labor or even additional component) are held in the socket. During assembly, the support pin is inserted into the passage opening initially as far into this until its cylindrical portion sits slightly larger diameter at the beginning of the through hole, the latter, according to a further preferred embodiment of the invention, at its upper end with a rounding or chamfering, whereby a shrinkage of the shank portion of the supporting bolt is facilitated with a larger diameter. If the shaft area of enlarged diameter is cylindrical, then it is then, for. Example, by means of a suitable plastic hammer, through the narrowed part of the through hole with effort beaten until it has entered the annular groove with an enlarged diameter. It is advantageous to keep the axial length of the shaft region with an increased diameter as small as possible in order to lower the force required when driving through the upper input region of the through-bore. However, it must be ensured that in the assembled state of the shaft portion accommodated in the enlarged diameter of the support bolt in the annular groove also sits with the required axial clearance, which may possibly be relatively small, but a slight and unimpeded twisting of the support bolt in the Through hole must be ensured.

Particularly preferably, in such an embodiment of the invention, the support bolt is formed with its shaft of a material having a greater strength than that of the bushing, which facilitates the drive through the narrower opening area of the passage opening. In this case, the enlarged diameter of the shank portion of the supporting bolt is selected only radially so far protruding that a driving of the support bolt with a moderate effort through the narrower range of the passage opening is readily possible, it was found to be advantageous if the other nominal diameter of Through hole is covered by the outer diameter of the cylindrical shaft portion with enlarged diameter radially by 0.1 to 0.075 mm. It can be seen that even small differences in diameter lead to a sufficiently good axial fit of the area of the support bolt with increased diameter compared to the bushing portion with reduced inner diameter and ensure sufficient axial support against unwanted running out of the support bolt from the through hole.

A further advantageous embodiment of the invention is also the fact that the support flange is mounted in the housing so that it is self-locking supported in each of its possible pivoting positions. This is preferably achieved in that the support flange acting by means in the direction of its axis of rotation, against him supporting biasing means is placed under a self-locking in each of its possible pivotal positions him in the pivoting self-locking. This is preferably z. B. achieved in that the support flange at its lower end facing each other two, each engaging from the outside into the housing pivot pin, wherein the biasing means lying in the housing axial end surfaces of the pivot pin, z. B. by means of generated by the bias friction.

In a particularly advantageous manner and in a simple form, this can be achieved in that the biasing means comprise a spreading spring arranged on the bush, which sits in an annular groove on the outer circumference of the bush and due to their spreading against the facing axial end surfaces of the two pivot pins a corresponding bias is applied. In this case, the shape of the spring may be formed so that here no punctiform, but a flat contact (under the generated bias) is given against the pivot pin.

As a means for establishing such a bias the skilled person various possibilities are known, wherein preferably the biasing means may comprise a seated in an annular groove on the outer circumference of the socket ring spring, which has a relative to the bushing outwardly curved in cross-section, by means of which a pressing under bias can take place against the end surfaces of the pivot pin.

With sufficiently strong applied spring action of the support flange can be held relative to the housing in any pivot position and the holder relative to the socket in any possible rotational position. In addition, this also has the advantage that the individual parts do not fall apart automatically after assembly.

Is it z. Example, in such a biasing spring to a spreading spring which is annular and is seated in an annular groove on the outer circumference of the bush, this may preferably be configured so that it is substantially only in the region opposite to the end face of the associated pivot pin, respectively the annular groove protrudes and presses against this end face. Seen from above, such a spring resembles a lemon. The spring is rotated while turning the rotatable holder.

Is it the spring, however z. Example, a seated in an annular groove on the outer circumference of the socket ring spring, it is advantageous in this case, when the holder also comprises a circumferential groove which is radially opposite to the annular groove of the sleeve. The inner diameter of this groove corresponds approximately to the distance between the two pivot pins to each other, but is particularly preferably slightly larger, so that the spring the desired pressure on the Can exert bolts. In this embodiment, the annular spring protrudes over the entire circumference of the annular groove of the bushing and presses both against the facing axial end surfaces of the pivot pin, as well as (with their axial end edges) against the bottom of the annular groove of the socket. In addition to a substantially circularly curved spring, however, a slightly oval curved spring is preferably used in certain cases, in which case the spring does not necessarily have to rotate when rotating the rotatable holder.

Particularly preferably, however, the biasing means are designed and mounted so that they also produce a bias between the sleeve and rotatable holder, whereby it is achieved that the holder is held in each rotational position relative to the sleeve self-locking.

Fig. 1

ein Schnittbild einer erfindungsgemäßen Anschlußvorrichtung längs Schnittebene I-I in Fig. 4;

Fig. 2

eine vergrößerte Darstellung der Einzelheit A aus Fig. 1;

Fig. 3

eine vergrößerte Darstellung der Einzelheit B aus Fig. 1;

Fig. 4

die Schnittdarstellung IV-IV aus Fig. 1;

Fig. 5

Ausbildungsvarianten von einsetzbaren Spreizfedern in Form sogenannter "Zitronenfedern" ;

Fig. 6

eine vergrößerte Darstellung der Einzelheit B aus Fig. 1, jedoch mit einer radial nach außen gewölbten Ringfeder;

Fig.7

eine Schnittdarstellung einer zweiten Ausführungsform einer erfindungsgemäßen Anschlußvorrichtung analog zur Schnittdarstellung von Fig. 1;

Fig. 8

eine vergrößerte Darstellung der Einzelheit C aus Fig. 7;

Fig. 9

eine dritte Ausführungsvariante einer erfindungsgemäßen Anschlußvorrichtung entsprechend Schnittebene IX-IX aus Fig. 11;

Fig. 10

eine vergrößerte Darstellung der Einzelheit D aus Fig. 9, sowie

Fig. 11

eine (vergrößerte) Schnittdarstellung des Schnittes XI-XI aus Fig. 9.

The invention will now be explained in more detail by way of example with reference to the drawings in principle. Show it:

Fig. 1

a sectional view of a connecting device according to the invention along sectional plane II in Fig. 4 ;

Fig. 2

an enlarged view of the detail A from Fig. 1 ;

Fig. 3

an enlarged view of the detail B from Fig. 1 ;

Fig. 4

the sectional view IV-IV from Fig. 1 ;

Fig. 5

Training variants of deployable expanding springs in the form of so-called "lemon springs";

Fig. 6

an enlarged view of the detail B from Fig. 1 but with a radially outwardly curved annular spring;

Figure 7

a sectional view of a second embodiment of a connecting device according to the invention analogous to the sectional view of Fig. 1 ;

Fig. 8

an enlarged view of the detail C from Fig. 7 ;

Fig. 9

a third embodiment of a connecting device according to the invention according to sectional plane IX-IX Fig. 11 ;

Fig. 10

an enlarged view of the detail D from Fig. 9 , such as

Fig. 11

an (enlarged) sectional view of the section XI-XI Fig. 9 ,

In the following description of the figures, the same reference numerals are always used in the different embodiments for the same parts.

Fig. 1 shows a connection device 1 in a sectional view according to cutting position II Fig. 4 , ie in a cutting position parallel to the plane of the drawing.

The connecting device 1 comprises a support flange 2 which can be connected to a load (not shown in the figures) which is then suitably formed by means of a lifting device (not shown), for instance by means of an opening 3 formed in the support flange 2 , passed through load chain, a hook or the like can be lifted and moved to another location.

The connecting device 1 further comprises a housing 4, which comprises a central sleeve 5, which opens at its axially lower end in the drawing in a radially outwardly flared annular flange 6, which rises axially at its radially outer end portion slightly upwards again and thereby forms a circumferential annular surface 7.

Further, the housing 4 comprises a rotatable about the sleeve 5 holder 8, which rests against its upper boundary surface against the underside of a head part 9 of a support bolt 10 when the support flange 2 is lifted upwards.

The holder 8 extends almost over the entire axial length between the underside of the head part 9 and the circumferential annular surface 7 of the annular flange 6, wherein in the holder 8 at two mutually 180 ° opposite points in each case a downwardly open recess 14 (FIGS. Fig. 3 ) is provided, into which a pivot pin 11a and 11b projects. The pivot pins 11a and 11b are aligned with their center axes to each other and form with these a rotation axis 12th

The pivot pins 11 a and 11 b are attached to the lower end of the support flange 2, so that about them the support flange 2 about the rotation axis 12 relative to the housing 4 in a direction perpendicular to the longitudinal central axis 13 of the support bolt 10 is pivotable.

The pivot pins 11 a and 11 b each sit on its underside on the annular surface 7 of the annular flange 6 of the bushing 5 and otherwise positively in their respective associated recess 14 of the holder 8 (see. Fig. 3 ). However, the recesses 14 in the holder 8 in its axial length are dimensioned such that the engaging in them pivot pins 11a, 11b in them a small game s (seen in the axial direction of the support bolt 10) have (see. Fig. 3 ).

The sleeve 5 is centrally penetrated by a passage opening 15 (see. Fig. 3 ), in which the shaft 16 of the support pin 10 is received and the support pin 10 is arranged rotatably in the assembled state relative to the bush 5. The shaft 15 has at a certain axial distance a from the underside of the head part 9 of the supporting bolt 10, a shaft portion 17 with a slightly larger diameter d ₂ .

In Fig. 2 is the formation of the shaft 15 of the support bolt 10 within the passage opening 15 of the socket 5 in an enlarged view of the detail A from Fig. 1 shown. From this, the shaft region 17 with a slightly larger diameter d ₂ can be seen.

How out Fig. 2 can also be removed, the socket 5 a socket portion 18 which is formed by an annular groove 19 and thus a shaft portion 17 enlarged diameter of the support bolt 10 associated bushing area also formed with enlarged diameter d ₁ . The shank portion 17 of the support bolt 10 protrudes in the mounted state, with axial and radial play, partially into this annular groove 19, as this Fig. 2 represents. Here, the diameter d _{2 of} the shaft portion 17 is smaller than the associated diameter d _{1 of} the bushing portion 18, but larger than the diameter d _{3 of} the other shaft portion of the support bolt 10 in the through hole 15 and larger than the diameter d _{4 of} the other region of the through hole 15th ,

In the in the Fig. 1 to 4 Shown embodiment of the shaft 16 of the support bolt 10, the shaft portion 17 of increased diameter is cylindrical. However, it can also be embodied in another form, as shown below in connection with the two other embodiments which are still described ( Fig. 7 and 9 ).

In the cylindrical embodiment, which projects into the corresponding cylindrical cross-section formed annular groove 19, it has proved to be particularly advantageous if the radial penetration depth b of the shaft portion 17 of increased diameter in the annular groove 19 in the range of 0.075 mm to 0.1 mm ,

The shaft 16 of the support bolt 10 or the support bolt 10 in turn is usually made of a material which has a considerably higher strength than the material of the surrounding bushing fifth

• Sie zeigt die Verhältnisse im Bereich des Eingreifens des Drehbolzens 11 b in den Halter 8 bis zur Buchse 5 hin:
  • Die in Fig. 3 gezeigte Darstellung für den Drehbolzen 11 b gilt in völlig analoger Weise auch für die Anordnung des ihm gegenüberliegenden anderen Drehbolzens 11a und dessen Eingreifen in das Gehäuse 4.

In Fig. 3 is the detail B off Fig. 1 also shown on an enlarged scale:

• It shows the conditions in the range of the engagement of the pivot pin 11 b in the holder 8 to the socket 5 out:
  • In the Fig. 3 shown representation for the pivot pin 11 b applies in a completely analogous manner also for the arrangement of the opposite him other pivot pin 11 a and its engagement in the housing. 4

As Fig. 3 shows, between the axial end surface 20 of the pivot pin 11 b and the sleeve 5, a spreading spring 21 is provided, which, as the sectional view according to Fig. 4 (along section line IV-IV off Fig. 1 ), the sleeve 5 encloses. In this case, according to the position of the spreading spring 21, on the outer wall of the sleeve 5, a circumferential groove 22 is mounted ( Fig. 3 ), in which the spreading spring 21 partially protrudes in its circulation around the sleeve 5 around. Furthermore, it is, in accordance with assigned, also on the inner surface of the holder 8 associated with a Umlaufnut 31, in which the spreading spring 21 also protrudes. While the spreading spring 21 is also supported on the groove bottom of the circumferential groove 22, a self-locking effect also occurs when taking a relative rotational position between the holder 8 and the socket 5 (cf. Fig. 11 ). This can be further enhanced by the fact that the spreading spring 21 is formed so that it presses against the bottom of the groove 22 as well as against the bottom of the groove 31 in its circulation both against the bottom.

The spreading spring 21 transmits a bias on the axial end surfaces 20 of the two pins 11 a and 11 b, said bias is designed so that the support flange 2 in each pivotal position about the axis of rotation 12 due to the between the spreading spring 21 and the two end faces 20 of Pintle 11 a and 11 b generated friction forces self-locking position is positioned. The bias acts when the spreading spring 21 is supported on the holder 8 in the groove, but also on the holder 8 and the socket 5, whereby the holder 8 is also positionally self-locking relative to the sleeve 5 about the rotation axis 13.

• Es handelt sich dabei um sogenannte _nZitronenfedern", also um elastische Federn, die im eingebauten Wirkzustand an ihren den beiden Drehbolzen 11a, 11b zugewandten Seiten radiale Ausbuchtungen 30 nach außen hin aufweisen, mit denen dann an der jeweiligen Endfläche 20 der Drehbolzen 11 a, 11 b ein nicht mehr im wesentlichen punkt- bzw. linienförmiger, sondern ein flächiger Kontakt erreicht werden kann, der eine besonders gute Übertragung ausreichender Vorspannkräfte auf die zugewandte Endfläche 20 des jeweiligen Drehbolzens 11 a bzw. 11 b gestattet.

Instead of a spreading spring 21, as in the Fig. 1, 3 and 4 is shown, could equally well be used another form of spreading spring, for which, for example, three different variants in Fig. 5 shown are:

• These are so-called _n lemon springs ", that is to say elastic springs which, when installed, have radial bulges 30 on the sides facing the two pivot pins 11a, 11b, with which then on the respective end face 20 of the pivot pins 11a, 11 b, a contact that is no longer essentially punctiform or linear, but that achieves a planar contact, which permits a particularly good transfer of sufficient prestressing forces to the facing end face 20 of the respective pivot pin 11 a or 11 b.

• Bei der Ausführungsform nach Fig. 6 besteht die Vorspannfeder aus einer in der Nut 22 an der Außenseite der Buchse 5 sitzenden, im axialen Schnitt mit einer Wölbung radial nach außen versehenen Ringfeder 23, die sich an ihrer ausgewölbten Außenseite an der zugeordneten Endwand 20 des entsprechenden Drehbolzens 11a bzw. 11 b und an ihren beiden axialen Enden am Boden der Nut 22 in der Hülse 5 abstützt und dabei durch die Wölbung die entsprechend gewünschte elastische Anpreßkraft gegen die Endfläche 20 des zugeordneten Drehschaftes 11 a bzw. 11 b aufbaut. Die Ringfeder 23 kann auch so ausgebildet sein, daß sie zusätzlich auch noch eine Vorspannung zwischen der Buchse 5 und dem Halter 8 aufbaut und damit auch eine selbsthemmende Lagepositionierung des letzteren relativ zur Buchse 5 in jeder Relativ-Drehlage zwischen beiden gestattet.

Fig. 6 shows in one of the Fig. 3 corresponding representation of a further embodiment of the usable biasing spring:

• In the embodiment according to Fig. 6 the biasing spring consists of a seated in the groove 22 on the outside of the sleeve 5, provided in axial section with a curvature radially outwardly annular spring 23, which at its bulged outside on the associated end wall 20 of the corresponding pivot pin 11a and 11b and supported at its two axial ends at the bottom of the groove 22 in the sleeve 5, while the corresponding desired elastic contact pressure against the end face 20 of the associated rotary shaft 11 a and 11 b builds up by the curvature. The annular spring 23 may also be designed so that it additionally builds up a bias between the socket 5 and the holder 8 and thus also allows a self-locking positional positioning of the latter relative to the socket 5 in each relative rotational position between the two.

In the FIGS. 7 and 8 a further embodiment of a connecting device 1 is shown, which differs from the embodiment according to FIG Fig. 1 only by the formation of the through hole 15 and the shaft design of the supporting bolt 10 differs, wherein Fig. 8 in an enlarged view the detail C from Fig. 7 shows.

In this embodiment, the shaft portion 17 of increased diameter of the support bolt 10 of an external thread 25, the threads of which protrude radially beyond the other shaft diameter d _{3 of} the supporting bolt 10 (see. Fig. 8 ), the latter being smaller than the core diameter of the external thread 25 in the shaft portion 17.

Again, the shaft portion 17 of increased diameter at an axial distance a from the head part 9 is removed.

The upper input portion of the through hole 15 is made as shown Fig. 8 is well recognizable, also from an internally threaded portion 24 which comprises two fully circumferential threads. In this case, at the upper end of the passage opening 15 is a circumferential rounding 27, which could also be formed as a chamfer, for ease of insertion of the shaft 16 of the support bolt 10 is mounted in the passage opening 15.

This portion of an internal thread 24 in the upper input region of the through hole 15 reduces the free radial passage area of the through hole 15 there, so that this portion of the sleeve 5 in the installed state of the support bolt 10 whose area 17 with increased radius from the outside and under an axial clearance (in Installed state) radially partially covered, such as Fig. 8 good.

Here, the internal thread 24 in the upper input region of the through hole 15 is designed so that the external thread 25 of the shaft portion 17 enlarged outer diameter during insertion of the support bolt 10 in the through hole 15 can be screwed through the internal thread 24, so that in FIGS. 7 and 8 shown arrangement adjusts in the mounted state of the support bolt 10.

How out Fig. 8 can be easily seen, the support pin 10 axially from the in Fig. 8 shown Montageendstellung not simply pulled axially upwards out of the through hole 15, since its shaft portion 17 is prevented there from the radially inwardly projecting, it partially covering internal thread 24 on the withdrawal. Only by a deliberate unscrewing the external thread 25 could again passed through the internal thread 24 and then only the shaft 16 are pulled out.

As Fig. 8 also shows, engages in this embodiment, the shaft portion 17 of increased diameter turn in a socket portion with an enlarged inner diameter, namely in the form of an annular groove 19 in the inner wall of the bushing 5, where he sits there again both axially, as well as radially with clear play ,

Yet another, third embodiment of a connecting device according to the invention is in the Fig. 9 to 11 shown, where Fig. 9 again, accordingly Fig. 1 , A sectional view of the connecting device 1 according to cutting position IX-IX Fig. 11, Fig. 10 an enlarged view of the detail D from Fig. 1 and Fig. 11 a sectional view in the cutting position IX-IX from Fig. 9 shows.

This embodiment of a connecting device 1 according to the invention differs from that according to the FIGS. 7 and 8 only in that with her the shank portion 17 of the support bolt 10 is formed with an enlarged diameter of the external thread 26 at the end of the shank of the support bolt 10, which also serves for screwing the load (not shown). This external thread 26 has a core diameter which is larger than the diameter of the other shaft 16.

A screw thread for the load to be fastened is also in the embodiments of the connecting device 1 according to Fig. 1 and Fig. 7 provided there, but not indicated in the drawings.

Also in Fig. 9 is the upper input portion of the through hole 15 with an internal thread 24 (as in the embodiment according to FIG FIGS. 7 and 8 ), which projects radially inward in the passage opening 15 and radially outwardly projecting shaft portion of the end thread 26 (corresponding to the shaft portion 17 of the support bolt 10) partially covered radially inwardly.

In this embodiment, although the shaft 16 can be pulled upwardly out of the passage opening 15 by a relatively large axial distance, it is not possible to completely pull it out, since this in turn is prevented by the inwardly projecting internal thread 24.

The sectional view according to Fig. 10 shows, moreover, the use of a lemon spring 21 according to the in Fig. 5 in the middle embodiment shown as a biasing means for pressing against the end surfaces 20 of the pivot pins 11a and 11b for self-locking mounting of the support flange 2 in any rotational position occupied by him.

Claims (14)

Connecting device (1) for coupling a carrying flange (2) to a load, comprising a housing (4) which comprises a bushing (5) and a holder (8) for the carrying flange (2) which can be rotated around the latter, 4) about an axis of rotation (13) of the holder (8) lying pivot axis (12) is pivotable and through the bush (5) axially a through hole (15) extends, in which a supporting bolt (10) with an upper head part (9 Is rotatably mounted, at its the head part (9) facing away axial end for attaching a load axially beyond the housing (4) and in the assembled state against axial withdrawal from the through hole (15) is held positively, characterized in that the Carrier pin (10) has a shank (16) with a at an axial distance (a) from the upper end of the bush (5) provided shank portion (17) with a radially enlarged shank diameter (d ₂ ), the radial projection in the mounted state Within this axial distance (a) is partially covered by a bushing portion with a reduced inner diameter under axial play (s) radially from the outside partially. Connecting device according to claim 1, characterized in that the enlarged diameter shank portion (17) comprises an external thread (25) whose threads form the radial enlargement and the reduced internal diameter sleeve portion of which extends from the thread (25) on the shank portion (17). enlarged shaft diameter corresponding internal thread (24). Connecting device according to claim 1 or 2, characterized in that the inner diameter (d ₁ ) of the bushing (5) in the region outside of the bushing portion with a reduced inner diameter greater than the outer diameter (d ₂ ) of the threads (25) on the shaft portion (17) with enlarged Shank diameter is. Connecting device according to Claim 2 or 3, characterized in that the external thread is formed by an external thread (26) provided on the end region of the supporting bolt (10) facing the load, the diameter (d ₃ ) of the remaining shaft (16 ) of the support bolt (10) is smaller than the core diameter of this external thread (28). Connecting device according to claim 2 or any one of claims 3 and 4, each dependent on claim 2, characterized in that the internal thread (24) in the reduced internal diameter bushing section comprises at least one complete thread. Connecting device according to claim 1, characterized in that on the support pin (10) of the shank portion (17) with radially enlarged shank diameter is cylindrical and into a on the inner surface of the bush (5) correspondingly mounted Nutausnehmung (19) protrudes, wherein the radially enlarged shank region (17) in the Nutausnehmung (19) sits radially and axially with play. Connecting device according to one of claims 1 to 6, characterized in that the supporting bolt (10) with its shaft (16) consists of a material having a greater strength than that of the material of the bushing (5). Connecting device according to one of claims 1 to 7, characterized in that the bush (5) is provided at the upper end of its passage opening (15) with a rounding (27) or a chamfering. Connecting device according to one of claims 1 to 8, characterized in that the carrying flange (2) in the housing (4) is mounted so that it is held in a self-locking manner in each pivoting position. Connecting device according to claim 9, characterized in that the support flange (2) by means in the direction of its axis of rotation (12) acting on the support flange (2) supporting biasing means (21, 23) under one in each pivot position of the support flange (2) this in the pivoting direction self-locking bias is set. Connecting device according to claim 10, characterized in that the support flange (2) has at its lower end two mutually directed, each from the outside into the housing (4) engaging the pivot pin (11a, 11b), wherein the biasing means (21, 23) on the in the housing (4) lying axial end surfaces (20) of the pivot pin (11 a, 11 b) act. Connecting device according to Claim 10 or Claim 11, characterized in that the biasing means comprise a spreading spring (21) arranged on the bushing (5) and seated in an annular groove (22) on the outer circumference of the bushing (5). Connecting device according to Claim 10 or Claim 11, characterized in that the biasing means comprise an annular spring (23) seated in an annular groove (22) on the outer circumference of the bushing (5). Connecting device according to one of claims 10 to 13, characterized in that the biasing means (21, 23) also produce a bias voltage between the bush (5) and the rotatable holder (8).

Images